US20080314062A1 - Water Condenser - Google Patents

Water Condenser Download PDF

Info

Publication number
US20080314062A1
US20080314062A1 US11/996,950 US99695006A US2008314062A1 US 20080314062 A1 US20080314062 A1 US 20080314062A1 US 99695006 A US99695006 A US 99695006A US 2008314062 A1 US2008314062 A1 US 2008314062A1
Authority
US
United States
Prior art keywords
air
air flow
water
heat exchanger
flow
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US11/996,950
Other languages
English (en)
Inventor
Jonathan G. Ritchey
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Freedom Water Co Ltd
Original Assignee
Freedom Water Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Freedom Water Co Ltd filed Critical Freedom Water Co Ltd
Priority to US11/996,950 priority Critical patent/US20080314062A1/en
Assigned to FREEDOM WATER COMPANY LTD. reassignment FREEDOM WATER COMPANY LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: RICHEY, JONATHAN G.
Publication of US20080314062A1 publication Critical patent/US20080314062A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • BPERFORMING OPERATIONS; TRANSPORTING
    • B01PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01DSEPARATION
    • B01D53/00Separation of gases or vapours; Recovering vapours of volatile solvents from gases; Chemical or biological purification of waste gases, e.g. engine exhaust gases, smoke, fumes, flue gases, aerosols
    • B01D53/26Drying gases or vapours
    • B01D53/265Drying gases or vapours by refrigeration (condensation)
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28BSTEAM OR VAPOUR CONDENSERS
    • F28B1/00Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/06Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28BSTEAM OR VAPOUR CONDENSERS
    • F28B1/00Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/02Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using water or other liquid as the cooling medium
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00Evaporators; Condensers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00Evaporators; Condensers
    • F25B39/02Evaporators
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00Evaporators; Condensers
    • F25B39/04Condensers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00Arrangement or mounting of control or safety devices
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25DREFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/14Collecting or removing condensed and defrost water; Drip trays
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28BSTEAM OR VAPOUR CONDENSERS
    • F28B11/00Controlling arrangements with features specially adapted for condensers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28BSTEAM OR VAPOUR CONDENSERS
    • F28B9/00Auxiliary systems, arrangements, or devices
    • F28B9/08Auxiliary systems, arrangements, or devices for collecting and removing condensate
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0066Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28DHEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0066Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • F28D7/0083Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids with units having particular arrangement relative to a supplementary heat exchange medium, e.g. with interleaved units or with adjacent units arranged in common flow of supplementary heat exchange medium
    • F28D7/0091Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids with units having particular arrangement relative to a supplementary heat exchange medium, e.g. with interleaved units or with adjacent units arranged in common flow of supplementary heat exchange medium the supplementary medium flowing in series through the units
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02Header boxes; End plates
    • F28F9/026Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0265Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
    • F28F9/0268Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box in the form of multiple deflectors for channeling the heat exchange medium
    • CCHEMISTRY; METALLURGY
    • C02TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
    • C02FTREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
    • C02F1/00Treatment of water, waste water, or sewage
    • C02F1/001Processes for the treatment of water whereby the filtration technique is of importance
    • CCHEMISTRY; METALLURGY
    • C02TREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
    • C02FTREATMENT OF WATER, WASTE WATER, SEWAGE, OR SLUDGE
    • C02F1/00Treatment of water, waste water, or sewage
    • C02F1/30Treatment of water, waste water, or sewage by irradiation
    • C02F1/32Treatment of water, waste water, or sewage by irradiation with ultraviolet light
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00Problems to be solved
    • F25B2500/18Optimization, e.g. high integration of refrigeration components
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02WCLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO WASTEWATER TREATMENT OR WASTE MANAGEMENT
    • Y02W10/00Technologies for wastewater treatment
    • Y02W10/30Wastewater or sewage treatment systems using renewable energies
    • Y02W10/37Wastewater or sewage treatment systems using renewable energies using solar energy

Definitions

  • the earth's atmosphere contains 326 million cubic miles of water and of this, 97% is saltwater and only 3% is fresh water. Of the 3% that is fresh water, 70% is frozen in Antarctica and of the remaining 30% only 0.7% is found in liquid form. Atmospheric air contains 0.16% of this 0.7% or 4,000 cubic miles of water which is 8 times the amount of water found in all the rivers of the world. Of the remaining 0.7%, 0.16% is found in the atmosphere; 0.8% is found in soil moisture; 1.4% is found in lakes; and 97.5% is found in groundwater.
  • the present invention is a device that extracts moisture vapour from atmospheric air for use as a fresh water source.
  • the device may utilize the sun as the primary energy source thereby eliminating the need for costly fuels, hydro or battery power sources.
  • the water collection device of the present invention provides flexibility over prior devices, allowing for productive installations in most regions of the world. As the water collection device's preferred power source is solar energy, the amount of available power for the device increases as installations of the device are closer to the equator where there is more sunlight year round.
  • the invention is designed to allow one small water cooler sized unit to provide cooking and drinking water for a family, simply by harvesting the water vapour from humid air. Private individuals, industries and communities could control their own water supply through the use of the device's technology. It is also practical for many uses in domestic, commercial or military applications and offers ease of use and clean water of a highest quality anywhere, anytime.
  • the modular design of these devices allow for increased capacity, simply by adding more modules.
  • a 12 Volt compressor in the cooling system within the device may be replaced with a larger 110 Volt compressor with the appropriately sized other components such as the evaporator and the condenser, and the unit will be capable of condensing larger quantities of water as electrical power is more readily available.
  • the device's solar water powered condenser technology may be applied to a variety of uses from residential to recreational and from commercial and agricultural to military and life saving in extreme water deprived regions of the world.
  • This invention may be used for obtaining pure drinking water, for cooking purposes or for other household uses such as cleaning or bathing.
  • the system may also be used on boats or in vacation areas, on camping trips, trekking, and places where drinking water delivery systems are not developed.
  • the unit may be used to produce fresh water for bottling purposes or for large commercial applications such as restaurants, offices, schools, hotel lobbies, cruise ships, hospitals and other public buildings.
  • the system may also be used in playing fields and sports arenas.
  • the device may be used to augment the supply of water used to irrigate selected crops using micro or drip irrigation systems. These systems deliver the right amount of water at the right time, directly to the roots of plants. As well, the technology may be used to for bottled water production or virtually any other application where water is needed.
  • the present invention offers a practical and affordable solution to many of the world's water supply problems.
  • the heat that is used to bring air temperature down to the dew point is “specific heat”.
  • the heat used to bring the temperature of air below the dew point is “latent heat” and represents a dynamic variable in the condensation process.
  • the optimal condensation process uses as little “latent heat” as is possible.
  • the dew point of air is the temperature at which the water vapour in the air becomes saturated and condensation begins.
  • specific heat means the amount of heat, measured in calories, required to raise the temperature of one gram of a substance by one Celsius degree.
  • Latent heat means: The quantity of beat absorbed or released by a substance undergoing a change of state, such as ice changing to water or water to steam, at constant temperature and pressure. This is also called heat of transformation.
  • the water condenser is portable and the refrigeration cycle may be driven by a 12 Volt compressor that allows for an efficient condensation process for creating a potable water supply.
  • the input source energy for the compressor may be supplied from many sources such as a wind turbine, batteries, or a photovoltaic panel.
  • the design may be fitted with transformers to accommodate other power supplies such as 110 Volt or 220 Volt systems when such electrical power is available, or the device may be sized or scaled up so as to accommodate such electrical power sources directly.
  • the device might use a 110 Volt compressor and simply have the device's other components scaled-up to accommodate the larger compressor.
  • the device filters the atmospheric air then provides a condensation process that lowers the temperature of that air to below dew point of the air flow.
  • the air is then exposed to an adequate sized, cooled surface area upon which to condense, and the water is harvested as gravity pulls the water into a storage compartment.
  • the disclosed invention creates a high quality water supply through a process of filtering air rather than water.
  • the device may be fitted with a screen to keep out larger contaminates. Downstream of the screen may be a pre-filter.
  • the pre-filter may be removable for cleaning. Downstream of the pre-filter may be a high quality filter such as a HEPA filter to ensure the air flow is pure and depleted of contaminates that might lower the quality of water that is created by the condensation process downstream of the air filtration.
  • the device according to the present invention may be fitted with an automatic suction valve so as to allow for the device to adapt to varying loads created by different environments.
  • the condensation process is to provide efficient processing of atmospheric, that is ambient air.
  • the intake air flow downstream of the air filtration may be pre-cooled, prior to entering a refrigerant evaporator used to condense moisture out of the intake air flow, by passing the intake air flow through an air-to-air beat exchanger, itself cooled by cooled air leaving the evaporator.
  • Air-to-air heat exchangers may be constructed to be very efficient, reaching 80% efficiency, and therefore reducing the temperature of the incoming air flow towards the dew point prior to the air flow entering the refrigerant evaporator, reduces the temperature differential, or temperature drop that must obtained by passing the air over cooled surfaces in the refrigerant evaporator to obtain the dew point temperature, and thus may have a significant impact upon the efficiency of the condensation process and thus the efficiency of the device.
  • the device may thus be optimized to increase the air flow rate and still be able to reduce the air flow temperature to the dew point, or the device will be able to handle very hot inflow temperatures and still reduce the dew point temperature of a reasonable air flow volume over time so as to harvest a useful amount of moisture.
  • Sensors provide temperature, for example ambient, inlet temperatures, refrigerant evaporator inlet and refrigerant evaporator outlet temperatures, humidity, and fan speed or other air flow rate indicators to the process to optimize and balance those variables to maximize harvested moisture volume.
  • Embodiments of the present invention may thus include varying the flow of air through the system such that the device has a prescribed amount of air passing through the refrigerant evaporator and a different flow of air passing through the refrigerant condenser of the corresponding refrigerant circuit, allowing for optimized function.
  • the water condenser may be characterized in one aspect as including at least two cooling stages, or first cooling a primary or first air flow flowing through the upstream or first stage of the two stages using an air-to-air heat exchanger, and feeding the primary air flow, once cooled in the heat exchanger, of one first stage in a refrigerant evaporator wherein the primary air flow is further cooled in the refrigerant evaporator to its dew point so as to condense moisture in the primary air flow onto cooled surfaces of the refrigerant evaporator, whereupon the primary air flow, upon exiting the refrigerant evaporator of the second stage, enters the air-to-air heat exchanger of the first stage to cool the incoming primary air flow, thereby reducing the temperature differential between the temperature of the incoming primary air flow entering the first stage and the dew point temperature of the primary air flow in the second stage.
  • a secondary or auxiliary air flow which in one embodiment may be mixed or joined (collectively referred to herein as being mixed) with the primary air flow, downstream of the first and second stages so as to increase the volume of air flow entering a refrigerant condenser in the refrigerant circuit corresponding to the refrigerant evaporator of the second stage.
  • the mass flow rate of the combined air flow entering the refrigerant condenser is the sum of the first and second mass flow rates, that is greater than the first mass flow rate in the two cooling stages.
  • the two cooling stages may be contained in one or separate housings as long as the primary air flow is in fluid communication between the two stages.
  • One housing includes a first air intake for entry of the primary air flow.
  • the first air intake is mounted to the air-to-air heat exchanger.
  • a first refrigeration or cooling unit such as the refrigerant evaporator cooperates with the pre-refrigeration set of air conduits for passage of the primary air flow from a downstream end of the pre-refrigeration set of conduits into an upstream end of the first refrigeration unit.
  • the first refrigeration unit includes first refrigerated or cooled (herein collectively or alternatively referred to as refrigerated) surfaces, for example one or more cooled plates, over which the primary air flow passes as it flows from the upstream end of the first refrigeration unit to the downstream end of the first refrigeration unit.
  • the already pre-cooled primary air flow is further cooled in the first refrigeration unit below a dew point of the primary air flow so as to commence condensation of moisture in the primary air flow onto the refrigerated surfaces for gravity-assisted collection of the moisture into a moisture collector, for example a drip late or pan mounted under or in a lower part of the housing.
  • the downstream end of the first refrigeration unit cooperates with, for passage of the primary air flow into, an upstream end of the post-refrigeration set of air conduits, for example to then enter the air-to-air heat exchanger so as to pre-cool the primary air flow before the primary air flow engages the first refrigeration unit. Because of pre-cooling by the heat exchanger, condensate may be collected with minimal power requirements.
  • a second air-to-air heat exchanger may further increase system performance.
  • the pre-refrigeration and post-refrigeration sets of air conduits form the first cooling stage, and collectively the plate or plates of the refrigerant evaporator form the second cooling stage.
  • An air-to-water heat exchanger may be provided cooperating with the air-to-air heat exchanger for cooling the primary air flow wherein the primary air flow is passed through the air-to-water heat exchanger and the cold moisture from the moisture collector is simultaneously passed through the air-to-water heat exchanger so that the moisture cools the first air flow.
  • the air-to-water heat exchanger may be either upstream or downstream of the air-to-air heat exchanger along the primary air flow.
  • a manifold or air plenum having opposite upstream and downstream ends cooperates in fluid communication with the downstream end of the post-refrigeration set of conduits. That is, the upstream end of the air plenum cooperates with the downstream end of the post-refrigeration set of conduits so that the primary air flow flows into the air plenum at the upstream end of the plenum.
  • the plenum has a secondary or auxiliary air intake into the plenum for mixing of the auxiliary air flow with, or addition of the auxiliary air flow in parallel to, the primary air flow in the plenum so as to provide the combined mass flow rate into the refrigerant condenser, to extract heat from the refrigerant in the refrigerant circuit to re-condense the refrigerant for delivery under pressure to the refrigerant evaporator in the second cooling stage, the refrigerant pressurized between the refrigerant evaporator and condenser by a refrigerant compressor (herein referred to as the compressor).
  • the compressor a refrigerant compressor
  • An air flow primer mover such as a fan or blower (herein collectively a fan) urges the primary air flow through the two cooling stages.
  • a single air flow prime mover such as a fan on the refrigerant condenser may be employed, otherwise, where only the auxiliary air flow flows through the refrigerant condenser, separate air flow prime movers are provided for the primary and auxiliary air flows.
  • the air flow prime mover may be selectively controllable and the processor may regulate the primary, auxiliary or combined air flow so as to minimize the air temperature of the primary air flow from dropping too far below the dew point for the primary air flow to minimize condensation within the heat exchanger, and so as to optimize or maximize the volume of moisture condensation in the refrigeration unit.
  • the first refrigeration unit may be adjacent the heat exchanger, the heat exchanger may be adjacent the plenum, the plenum may be adjacent the refrigerant condenser, and the refrigerant condenser may be adjacent the air flow prime mover. These elements may be inter-leaved in closely adjacent array.
  • FIG. 1 is, in perspective view, one embodiment of the water condenser according to the present invention.
  • FIG. 2 b is a sectional view along line 2 b - 2 b in FIG. 2 .
  • FIG. 3 is a sectional view along line 3 - 3 in FIG. 1 .
  • FIG. 3 b is an enlarged view of a portion of FIG. 3 a.
  • FIG. 3 c is, in perspective view, the internal air conduits of the upstream side of manifold of the water condenser of FIG. 1 .
  • FIG. 5 is the view of FIG. 3 in an alternative embodiment wherein the air flow manifold feeding the refrigerant condenser is partitioned between the primary and auxiliary air flows.
  • FIG. 7 is, in partially cut away front right side perspective view, an alternative embodiment of the present invention wherein two separate fans draw the primary and auxiliary air flows through the evaporator and condenser respectively.
  • FIG. 10 is a partially cut away rear perspective view of the embodiment of FIG. 7 .
  • FIG. 10 a is a sectional view along line 10 a - 10 a in FIG. 10 .
  • FIG. 12 is a graph of Temperature vs. Time showing the interrelation of Evaporator Temperature, Processed Air Temperature, Relative Humidity (RH) %, Dew Point Temperature, and Environmental Temperature in the device of FIG. 1 .
  • FIG. 13 is a block diagram showing an embodiment of control system for a water condenser according to the invention.
  • FIG. 14 is a block diagram showing an alternative embodiment of a control system according to the invention.
  • FIG. 15 is a perspective view of a sensor used in the water condenser according to the invention.
  • FIG. 16 is a front perspective view of an alternative embodiment of the invention.
  • FIG. 17 is a front perspective view of the embodiment shown in FIG. 16 , wherein the cover has been removed.
  • FIG. 18 is a front view of the embodiment shown in FIG. 17 .
  • FIG. 19 is a top view of the embodiment shown in FIG. 17 .
  • FIG. 20 is a perspective view of a portion of the embodiment shown in FIG. 17 showing the placement of the condenser relative to the condenser fan and compressor.
  • FIG. 21 a is an enlarged view of a portion of FIG. 21 .
  • FIG. 22 is a perspective view of a portion of the embodiment shown in FIG. 17 .
  • FIG. 23 is a perspective view of a heat exchange system according to the embodiment of FIG. 17 .
  • FIG. 23 a is an enlarged view of a portion of FIG. 23 .
  • FIG. 24 is a side view of the embodiment shown in FIG. 17 .
  • FIG. 25 is a partial cutaway side view of the embodiment shown in FIG. 17 showing the air flow.
  • the primary air flow is pre-cooled in the air-to-air heat exchanger, and also in the air-to-water heat exchanger in the alternative embodiment.
  • Humidity in the ambient air drawn in as the primary air flow through intake 18 is condensed in refrigerant evaporator 14 .
  • Water droplets which condense are gravity fed in direction F into a collection plate, pan or trough 26 for outflow through spout 26 a .
  • the addition of ambient air drawn in as the auxiliary air flow in direction B into manifold 20 provides the higher volumetric air flow rate needed to efficiently operate refrigerant condenser 24 .
  • the primary air flow is drawn in through the upstream air intake 18 of evaporator 14 in direction A and passes between the hollow air-to-air heat exchanger plates 30 .
  • an air-to-water heat exchanger 90 may cooperate with air-to-air heat exchanger 16 and there may be one, two, three or more plates 30 in heat exchanger 16 .
  • Plates 30 are preferably parallel and are spaced apart to form flow channels therebetween, and between the outermost plates 30 a and the walls 32 a of the housing 32 of the heat exchanger.
  • plates 34 are refrigerated by the evaporation of refrigerant flowing into cooling coils 34 a .
  • Plates 30 themselves are rigidly supported in parallel spaced apart array sandwiched by and between planar end plates 38 .
  • the end plates have an array of apertures 38 a therethrough.
  • the apertures align with the open ends of sealed conduits 30 b through the plates, as best seen in FIGS. 3 , 3 a and 3 b , so that, once the air flow has turned one hundred eighty degrees in direction H through upstream side manifold 40 , the air flow then passes in direction J through apertures 38 a and along the length, of conduits 30 b (the post-refrigeration set of air conduits) so as to exit from the corresponding apertures 38 a downstream in the opposite end plate 38 ′.
  • side manifold 40 in the illustrated embodiment of FIG.
  • 3 c which is not intended to be limiting, segregates air flow in direction H into three flows H 1 , H 2 and H 3 so as to enter into corresponding conduits 30 b , themselves arranged in three banks 30 b 1 , 30 2 and 30 b 3 arranged vertically one on top of the other as seen in FIG. 2 .
  • Fences 40 b divide air flows H 1 , H 2 and H 3 from one another and align the air flows with their corresponding bank of sealed conduits 30 b , so that air flows H 1 , H 2 and H 3 are aligned for flow into, respectively, conduit banks 30 b 1 , 30 b 2 and 30 b 3 .
  • Fences 40 b also align with plates 34 so as to partially segregate the infeed to air flows H 1 , H 2 and H 3 to come from, respectively, between the outside plate 34 and the outside wall 14 a , between the inside and outside plates 34 , and between the inside plate 34 and the inside wall 14 b .
  • a lower cap 40 a seals the end of pan 26 and channels moisture collected from side manifold 40 into pan 26 , as seen in FIG. 2 b .
  • Air-to-air heat transfer in direction K occurs through the solid walls of plates 30 so that the primary air flow in conduits 30 b cools the primary air flow between the plates.
  • the air flow is again turned approximately one hundred eighty degrees in direction C by and within downstream side manifold 42 which extends the height of end plate 38 ′.
  • Side manifold 42 directs air flow into manifold 20 through a port 44 leading into the upstream end of manifold 20 .
  • An ambient air intake 22 feeds ambient air in direction B into manifold 20 so as to, in one combined air flow embodiment, mix with the air flow from heat exchanger 16 with ambient air from auxiliary air intake 22 .
  • the flow rate of the auxiliary air flow through intake 22 is selectively regulated by actuation of damper 22 a (shown in FIG. 3 in its closed position in dotted outline and in its open position in solid outline).
  • the mixed air flow is then drawn in direction D into refrigerant condenser 24 so as to pass between the louvers 24 a or coils or the like.
  • Condenser 24 condenses refrigerant flowing in lines 46 a (illustrated diagrammatically in dotted outline in FIG. 4 ) once compressed by compressor 46 .
  • the combined air flow then enters the in-line fan 12 and exhausts from the fan in direction E.
  • the primary air flow may be exhausted entirely from the system without flowing through condenser 24 without significantly affecting performance, or if the primary air flow is somewhat cool, it may be used to assist in cooling condenser 24 . If the air that has passed through the evaporator 14 and heat exchanger 16 is exhausted upstream of condenser 24 , the condenser 24 will draw its own air stream, which is the auxiliary air flow, directly from the ambient air outside the system.
  • the use of the two air streams, primary and auxiliary has advantages in allowing a significant increase in air flow through the condenser versus the evaporator.
  • a controller 48 may do multiple tasks and the system may require multiple controllers if it is not beneficial or practical to build them all into the same unit.
  • the controller 48 may be designed to accommodate a varying power input such as would be the case if the unit was hooked up directly to a photovoltaic panel. Controller 48 may also ensure that the refrigeration system pressures are maintained.
  • These pressures may be controlled to some degree by controlling the pressures within the system and through controlling the flow of refrigerant.
  • the high side or discharge may be controlled by regulating the quantity and temperature of the air that passes through the condenser. If the discharge pressure is too low (below 120 psi) the cooling system becomes compromised and functions below its capability. In this case the controller is designed to turn the fan off and allow the pressure to rise. If the pressure gets too high the controller will turn the fan on and the pressure will drop. This is a simple and inexpensive way to control the system discharge pressure.
  • Controller 48 may also find the optimal air flow rate through the condenser so as to moderate the discharge (also called backpressure) to an acceptable range (150 psi may be optimal). In this design the fan is kept at the optimal speed rather than turning off and on, so as to ensure proper system pressures and optimal operation of the refrigeration system.
  • Controller 48 may be part of control system 130 of the water condenser to manage the air flow through a series of control elements allowing the water vapour within the ambient air to be condensed into a containing element, such as collection plate 26 . As seen in FIG.
  • Control system 130 also includes a plurality of sensors, a microcontroller/processor (not shown) capable of receiving input from the sensors and outputting information to control the air flow system which, in turn, varies the flow rate.
  • Water extraction control system 130 takes information from subsystems of the water condenser, including air intake measurement system 140 , air movement control system 150 , and exhaust measurement system 160 , and uses this information to control each subsystem.
  • Control system 130 may also include display 170 and user interface 180 , with input means such as buttons 190 , dials, or the like, for allowing local user control of the water condenser.
  • Control system 130 may also include an external control system 195 for wired or wireless communication with control system 130 within the water condenser, or with control interface 180 .
  • External control system 195 may be, but is not limited to, a local or networked personal computing device, such as system controllers, PLCs, personal computers (PC's) or handheld devices.
  • the control system further includes both mechanical and electrical components.
  • the mechanical components control air flow as instructed by the electrical or electronic components of the control system, to condense water vapour extracted from the air and collected within the mechanical components.
  • the control system measures properties in the incoming, or intake ambient air flow, including humidity and temperature, and compares these properties to the exhaust air flow using the same parameters to determine the optimal flow rate to maximize water extraction.
  • the control system may also measure pressure changes between the intake air flow and exhaust to determine the efficiency of the exchange properties and further determine if system components require maintenance.
  • Using the control system includes measuring the humidity differential between the intake and exhaust, determining the optimal air speed through the water condenser's mechanical system.
  • Optimal air speed is the air speed velocity which produces the greatest amount of condensation in the mechanical (condensing) system, thereby maximizing water extraction.
  • the sensors contain circuitry to convert measurement devices within into signals that can be transmitted (for example along a cable) to the system controller/processor 48 .
  • Signal conversion at the sensor generally includes an electronic devices reacting with the electrical properties of an individual sensing device and creating a signal which can be communicated along a wired interface cable. In a general form, this means converting an analog property to a digital signal.
  • a typical sensor is shown in FIG. 15 .
  • a temperature sensor may be present having detection electrodes locate on substrates whose properties react to changing thermal conditions and can be converted or measured electrically.
  • the differential temperature is used, in conjunction with differential humidity (either absolute or relative), to determine optimal parameters for water vapour extraction.
  • a pressure sensor may also be present, in particular, to measure the differential pressure between the air flow intake and exhaust and, in part, to determine the properties of the particulate filtration replacement system.
  • control system reads input from the sensors, which are measuring intake and exhaust signals related to temperature, humidity and pressure. Further, the control system controls the air flow rate through the mechanical system of the water condenser. The air flow rate may be controlled by any or all of the parameters capable of being measured by the intake and/or exhaust circuits.
  • the intake sensing systems includes analog signal conditioners, which are passive to active converters whose properties are converted from passive uncompensated and raw measurement parameters to digital signals measurable by a controlling device, for example a digital signal processor or a microprocessor or microcontroller.
  • analog signal conditioners which are passive to active converters whose properties are converted from passive uncompensated and raw measurement parameters to digital signals measurable by a controlling device, for example a digital signal processor or a microprocessor or microcontroller.
  • a preferred signal conditioning system includes a passive sensor, active signal converters, and error sensing circuits, which use error signals to generate compensated signals indicative of the presence of water vapour; an amplifier associated with the sensor, for extracting the error signal from the active signal to generate a compensated signal, which indicates the presence of water vapour within a vicinity of the water condenser; an output signal conditioning circuit for receiving the compensated signal from the amplifier and generating a conditioned signal thereof for transmission to a microprocessor, which instructs the controller system to control a variable air flow rate transducer in the water condenser in response to a differential input and output of the conditioned signal to the microprocessor from the amplifier.
  • the air flow is controlled with mechanical devices under the control of the control system.
  • the air flow is measured as a percentage of the maximum speed or flow rate as directed by the mechanical devices: 100% being the maximum speed or flow rate through the mechanical system of the water condenser.
  • a PID control system is a common feedback loop component in industrial control systems. In this process the control system compares measured values from a process with a reference set point value. The PID controller can adjust process outputs based on the history and rate of change in an error signal.
  • the PID algorithm is used when the control system is being used to obtain a set point humidity or temperature differential. This is different from the time rate variable system which is used when the control system is maximizing its differential humidity and/or temperature values.
  • the time-rate-variable (TRV) system includes elements of PID control theory however in this instance there is no known set point value.
  • the set point is not predetermined but is dynamic within the control system and changes depending on the air qualities. Further, this ‘set point’ is continually optimized to maximize water extraction based on humidity and temperature. If the control system includes a pressure sensor, this sensor is used to assist the primary control algorithm as the air flow rate through the system may be reduced due to pressure build up in the exchange chambers.
  • New Flow Rate (%) (((100% ⁇ Current Flow Rate)/2)+Current Flow Rate) (%)
  • Formula 1 Flow Rate Control:Increasing Adjustment
  • a value proportional to T 1 ⁇ T 0 a new set of sensor measurements are used to compare the previous humidity differential with the new humidity differential to determine if these differential values are increasing or decreasing.
  • the goal of the control system is to increase this humidity differential to its maximum value.
  • the maximum value is the value at which if the flow rate was increased, the measured humidity differential would fall.
  • the control system then increases the air flow according to the formula 1 listed above but the Current Flow Rate will be the last flow rate used to control the mechanical system. This has the effect of increasing the flow towards 100% in decreasing steps which are effectively half way between where it is currently set and 100%.
  • New Flow Rate ((Current Flow Rate ⁇ Last Flow Rate)/2) ⁇ Current Flow Rate) ⁇ K
  • K is a constant to guarantee there is at least a differential control state
  • the constant K, in formula 2 causes the algorithm will step the air flow rate down in the event the previous air flow rate and the current flow rate are the same. This differs from the increasing formula (formula 1) because in the increasing air flow rate case, 100% maximum can continue to be used as long as the humidity differential appears to be a maximum at the maximum air flow rate.
  • the controller recognizes the humidity of the incoming air and the discharged air, strives to control the air volume and maximize the performance of the water condenser by adjusting the air volume (e.g., controlled by the fan) until there is a maximum difference between the humidity of the incoming air (ambient air) and the humidity of the discharged air. This difference represents the “most water removed” from the ambient air.
  • sensors could be comparing temperatures, rather than humidity.
  • air passages or inlets could be opened or closed.
  • the ideal location within the system will be determined for where the internal air flow should be reaching its dew point.
  • This location might be between the heat exchanger and the evaporator plates (in the first pass) but other locations are usable.
  • a controller with sensors monitors environmental conditions and calculates internally what the dew point is. Sensors are placed within the system such as mentioned above, allowing the controller to monitor the sensors, and thereby determining the temperature with respect to the dew point.
  • the optimal system function is to create a dew point near the sensor the controller will slow down or speed up the fan in a continual effort to optimize the system.
  • a pressure differential gauge may be used to offer feedback to the control system assisting in its function to optimize the air flow.
  • the present system is designed to keep the air flow just below the dew point and to track the dew point continuously as conditions change. As seen in the test data set of FIG. 12 , the dew point is continuously tracked by the processed air temperature ensuring optimal operation.
  • the primary air flow passes through hollow conduits 66 a across the width of the heat exchanger, exiting conduit 66 a in direction P so as to be turned one hundred eighty degrees in end manifold 70 .
  • the primary air flow then flows between refrigerant evaporator plates 72 in direction Q wherein the primary air flow is cooled below its dew point without freezing. Moisture thus condenses out of the primary air flow onto plates 72 and is harvested through a spout 74 into a collection pan or the like (not shown).
  • the primary air flow exits from the refrigerant evaporator through slot 76 and travels in direction R downwards between conduits 66 a so as to exit heat exchanger 66 in direction S through slot 78 .
  • the primary air flow is then drawn through fan housing 80 and fan 82 so as to exit as exhaust from fan 82 in direction T.
  • the de-linking of the primary and auxiliary air flows so as to require separate fans, respectively fans 82 and 60 , provide for condenser 62 functioning at a greater capacity without affecting optimization of the balance of the cooling between the first and second cooling stages of, respectively, the heat exchanger 66 and the evaporator plates 72 .
  • the lower volume fan 82 may be controlled by a processor (not shown) to determine the current environmental conditions affecting optimization of cooling and condensation for example by varying the power supplied to fan 82 to thereby control the velocity and mass flow rate of the primary air flow through the two cooling stages.
  • Environmental conditions are monitored by the system and at an appropriate point in the system, such as between the heat exchanger and the evaporator (first pass) the temperature relative to dew point is monitored. If the air at this point is too far above dew point the fan that draws air through this section of the unit may decrease its speed thus slowing the air and allowing more time for the air to cool prior to reaching the evaporator plates. If the air at this point is below dew point then the system may increase the fan speed and continue to optimize the air flow stream. Other conditions throughout the device may be monitored as well and this information may be used by controller 48 to further tune the device. Humidity levels leaving the system may be used as a means to determine exactly how much water has been extracted from the air and with this information, the system may modify its configuration thus ensuring optimal performance.
  • air-to-water heat exchanger 90 is mounted upstream of the air-to-air heat exchanger along the primary air flow.
  • Water collected in moisture collector 26 is directed for example by conduit 26 a into water reservoir 90 a from which the water may be collected for end use.
  • the water in reservoir 90 a is chilled, having just been condensed into and recovered from the evaporate plates.
  • the primary air flow passing through air conduits 90 b in direction A′ is cooled by the water cooling the conduits 90 b before the primary air flow enters the air-to-air heat exchanger for further pre-cooling as described above. This further improves the efficiency of the condenser as it takes advantage of the cold temperature of the collected water.
  • FIGS. 16 through 25 A further embodiment of a water condenser according to the invention is illustrated in FIGS. 16 through 25 , which can be mounted on a wall or the like.
  • ambient air is drawn into the water condenser through air grill 201 where it then passes through the intake air filter designed to clean the incoming air.
  • an access door on the front of the device (removed in FIG. 16 ). This door covers encasement 202 holding replaceable water filter housing 203 , replaceable UV light housing 206 , and LCD display 204 .
  • Replaceable water filter housing 203 allows access to remove and replace the water filter.
  • LCD display 204 offers relevant information regarding the status of the water condenser to the user.
  • Touch control 205 allows the user to scroll through the various functions offered by the controller mechanism.
  • evaporator 218 is divided into three independent sections, which allow air flow to only travel downward through the sections having cooling plates.
  • the air flow will travel down through the first section 219 of the evaporator 218 and then upward through middle section 220 where no plates are present, and then travel down through the third section 221 , which has plates, thereby allowing air to only travel downward through cooling plates thus alleviating the negative pressure water bottleneck that diminishes system efficiency and creates less water.
  • tapping or vibrating member used to shake water off plates 244 .
  • Tapping member could be an offset weight attached to a small motor timed to vibrate for a short duration at set intervals or may be a coil wrapped around a movable magnetic rod that with short bursts of current produced by the water condenser (e.g. collected in a capacitor) will tap evaporator 218 thus assisting in removing water from plates 244 .
  • Outgoing water line 223 is where water exits the condenser. This water line may exit the device from its side rather than underneath the device should the design call for the device to sit on a flat surface such as a countertop. Additionally, there may be a water containment system with similar dimensions to the device directly beneath the device to collect water created and allow users easy access.
  • the condenser may draw water from such containment system and circulate this water through the filtration part of the condenser to ensure the quality of the water even if it has been sitting for a period of time. This could be done for short periods of time on set intervals (e.g. 20 min/day).
  • Base 224 a of the device includes means to control air flow and to capture water.
  • Base 224 a is positioned below heat exchanger 212 capturing water that might be created by heat exchanger 212 .
  • Above heat exchanger 212 is ducting mechanism 224 b that creates air flow through various components as needed by the device.
  • the device may include a water pump 225 to move water through various components, such as through water filter 207 .
  • the heat exchange system that provides for increased efficiency of the device is seen in FIG. 23 .
  • the device pre-cools the incoming air flow moving in direction Y with the outgoing waste air flow X.
  • This heat exchanger 212 is able to bypass the heat exchange system through upper front vent 232 should it be beneficial for the device given the current environmental conditions.
  • both incoming air flow Y and processed outgoing air flow X move upward through the device through separate vents respectively 228 and 229 , such that air flows X and Y do not come in contact with each other.
  • the device may incorporate a horizontally sliding door with overlapable vanes covering intakes 228 and 232 wherein intake 228 would close as the intake 232 would open. This could be controlled with a bimetal strip utilizing air temperature to mechanically move the door.
  • Titanium dioxide is the naturally occurring oxide of titanium, chemical formula TiO 2 . Approved by the food testing laboratory of the United States Food and Drug Administration (FDA), Titanium Dioxide is considered a safe substance and harmless to humans.
  • FDA United States Food and Drug Administration
  • this substance may be used for the inner lining of tubing that carries the water from the evaporator plates to the storage container and may become part of the UV purification system.
  • This material has an extremely high index of refraction with an optical dispersion higher than diamond so in order to enhance its desired effects, coiled tubing that surrounds the light source, may be encased in a reflective material so as to ensure that light is given an adequate opportunity to come in contact with the surface of the material and thus create the desired effect.
  • Other materials may be used also having desirable attributes within the device. These may include hydrophobic coatings (water repelling), and a variety of antimicrobial elements proven to suppress the growth and migration of bacteria. These substances may include silver or other compounds known to reduce bacterial growth as well as a variety of corrosion proofing materials.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Combustion & Propulsion (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
  • Air Conditioning Control Device (AREA)
  • Physical Water Treatments (AREA)
  • Treatment Of Water By Oxidation Or Reduction (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Devices For Blowing Cold Air, Devices For Blowing Warm Air, And Means For Preventing Water Condensation In Air Conditioning Units (AREA)
US11/996,950 2005-07-29 2006-07-31 Water Condenser Abandoned US20080314062A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US11/996,950 US20080314062A1 (en) 2005-07-29 2006-07-31 Water Condenser

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US85330305P 2005-07-29 2005-07-29
US11/996,950 US20080314062A1 (en) 2005-07-29 2006-07-31 Water Condenser
PCT/CA2006/001285 WO2007012202A1 (fr) 2005-07-29 2006-07-31 Condenseur d'eau

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/CA2006/001285 A-371-Of-International WO2007012202A1 (fr) 2005-07-29 2006-07-31 Condenseur d'eau

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US13/627,951 Continuation US20130145782A1 (en) 2005-07-29 2012-09-26 Water condenser

Publications (1)

Publication Number Publication Date
US20080314062A1 true US20080314062A1 (en) 2008-12-25

Family

ID=37682972

Family Applications (3)

Application Number Title Priority Date Filing Date
US11/996,950 Abandoned US20080314062A1 (en) 2005-07-29 2006-07-31 Water Condenser
US13/627,951 Abandoned US20130145782A1 (en) 2005-07-29 2012-09-26 Water condenser
US14/326,369 Expired - Fee Related US9605904B2 (en) 2005-07-29 2014-07-08 Water condenser

Family Applications After (2)

Application Number Title Priority Date Filing Date
US13/627,951 Abandoned US20130145782A1 (en) 2005-07-29 2012-09-26 Water condenser
US14/326,369 Expired - Fee Related US9605904B2 (en) 2005-07-29 2014-07-08 Water condenser

Country Status (10)

Country Link
US (3) US20080314062A1 (fr)
EP (1) EP1913323A4 (fr)
JP (1) JP2009503293A (fr)
KR (1) KR20080046171A (fr)
CN (1) CN101278164B (fr)
AU (1) AU2006274424B2 (fr)
BR (1) BRPI0614319A2 (fr)
CA (1) CA2616887A1 (fr)
WO (1) WO2007012202A1 (fr)
ZA (1) ZA200801584B (fr)

Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090241580A1 (en) * 2008-03-25 2009-10-01 Hill James W Atmospheric Water Harvesters
US20090260385A1 (en) * 2008-03-25 2009-10-22 Hill James W Atmospheric water harvesters with variable pre-cooling
WO2011078771A1 (fr) * 2009-12-21 2011-06-30 Wallenius Water Aktiebolag Échangeur de chaleur à plaques comprenant des éléments de génération d'uv
US20120011865A1 (en) * 2009-03-27 2012-01-19 Set Ip Holdings, Llc Combined Water Extractor and Electricity Generator
US20120042691A1 (en) * 2010-08-20 2012-02-23 Carol Diane Krumbholz Vapor recovery system utilizing compression-condensation processes and related methods
US20120125268A1 (en) * 2010-11-24 2012-05-24 Grand Mate Co., Ltd. Direct vent/power vent water heater and method of testing for safety thereof
US20130312451A1 (en) * 2012-05-24 2013-11-28 Michael D. Max Multiple Panel Heat Exchanger
US20140109857A1 (en) * 2011-03-10 2014-04-24 Valeo Systemes Thermiques Cover for an Intake Housing
US20140123688A1 (en) * 2011-05-16 2014-05-08 Kjaerulf Pedersen A/S Cooled storing system for photo catalytic decomposition of ethylene
US20140338387A1 (en) * 2013-05-15 2014-11-20 Jish-Shyan Jiang Assembled temperature controlling device
US20150000317A1 (en) * 2012-02-22 2015-01-01 Fuji Electric Co., Ltd. Integrated air conditioning system and control device thereof
US9086068B2 (en) 2011-09-16 2015-07-21 Grand Mate Co., Ltd. Method of detecting safety of water heater
US9664144B2 (en) 2011-03-10 2017-05-30 Valeo Systemes Thermiques Intake housing including a heat exchanger
US20170246934A1 (en) * 2014-07-29 2017-08-31 Hanon Systems Air conditioner system for vehicle
US9777698B2 (en) 2013-11-12 2017-10-03 Daniel Keith Schlak Multiple motor gas turbine engine system with auxiliary gas utilization
WO2017173239A1 (fr) * 2016-03-31 2017-10-05 Oceaneering International, Inc. Climatiseur à microgravité à membrane
US20180282144A1 (en) * 2016-04-15 2018-10-04 Automatic Bar Controls, Inc. Nitrogen generator and uses thereof
WO2019046643A1 (fr) * 2017-08-30 2019-03-07 Tsunami Products Condensation d'humidité atmosphérique et germination hydroponique
US10495361B2 (en) 2012-05-24 2019-12-03 Maxsystems, Llc Multiple panel heat exchanger
US10619332B2 (en) * 2018-02-02 2020-04-14 Rocky Research Method and system for obtaining water from air
US20200370761A1 (en) * 2017-12-29 2020-11-26 Ji Yang Device for heating by absorbing latent heat of solidification of water and heat pump
US10987610B1 (en) * 2016-05-03 2021-04-27 Richard Arthur MAYER Atmospheric water generation having multi-stage pathogens neutralizing elements
WO2021163290A1 (fr) * 2020-02-14 2021-08-19 The University Of Akron Ensemble de récupération d'eau douce utilisant un matériau de sorption d'eau à l'intérieur d'un composant hiérarchique
WO2022183134A3 (fr) * 2021-02-28 2022-10-06 Face International Corporation Système et procédé d'élimination et de filtrage à haute efficacité d'agents pathogènes en suspension dans l'air contenu dans un volume de gaz
US11490574B2 (en) * 2017-11-03 2022-11-08 Republic Of Korea(Management : Rural Development Administration) Flower water receiver
US11674699B2 (en) 2017-10-24 2023-06-13 Politecnico Di Torino Method for production of water from air based on low-temperature heat, and machine and system thereof
US11857918B2 (en) * 2022-03-28 2024-01-02 Harbin Institute Of Technology Liquid water harvester based on valve-controlled active air supply

Families Citing this family (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2217763A4 (fr) * 2007-10-10 2013-05-15 Eternair Water Pte Ltd Déshumidificateur atmosphérique mobile à économie d'énergie et écologique pour un générateur d'eau et à des fins de production de boisson
EP2440864A1 (fr) * 2009-06-08 2012-04-18 Humano Water Corporation Générateur d'eau atmosphérique
WO2012123849A2 (fr) * 2011-03-11 2012-09-20 EcoloBlue, Inc. Systèmes et procédés de production d'eau potable
US9993744B2 (en) * 2013-03-15 2018-06-12 Seas Société De L'eau Aerienne Suisse Sa Atmospheric water generation systems
CN103196168B (zh) * 2013-03-26 2015-05-27 中山市爱美泰电器有限公司 一种方便安装的冷暖分集水器
JP6178979B2 (ja) * 2013-06-28 2017-08-16 パナソニックIpマネジメント株式会社 燃料処理装置
US10532935B2 (en) 2013-10-14 2020-01-14 John R. Ackerman Water harvester and purification system and method of making and using same
WO2015057502A2 (fr) * 2013-10-14 2015-04-23 John Ackerman Système de collecte et d'épuration d'eau
FR3014758B1 (fr) * 2013-12-12 2015-12-18 Valeo Systemes Thermiques Systeme de rafraichissement et d'humidification de l'air d'une enceinte par nebulisation integrant des moyens de decontamination du liquide de nebulisation
CN103759448B (zh) * 2014-01-27 2016-04-13 苏州明威医疗科技有限公司 一种x光机双冷却系统
CN104154773B (zh) * 2014-05-15 2016-04-06 东南大学常州研究院 用于水冷式垂直冷凝管外的除液装置
US10993441B2 (en) 2014-11-04 2021-05-04 Allied Bioscience, Inc. Antimicrobial coatings comprising organosilane homopolymers
US10980236B2 (en) 2014-11-04 2021-04-20 Allied Bioscience, Inc. Broad spectrum antimicrobial coatings comprising combinations of organosilanes
US10258046B2 (en) * 2014-11-04 2019-04-16 Allied Bioscience, Inc. Antimicrobial coatings comprising quaternary silanes
US10252611B2 (en) * 2015-01-22 2019-04-09 Ford Global Technologies, Llc Active seal arrangement for use with vehicle condensers
EP3741816A1 (fr) 2015-02-11 2020-11-25 Allied Bioscience, Inc Revêtement anti-microbien et procédé de formation de celui-ci
WO2017201405A1 (fr) * 2016-05-20 2017-11-23 Zero Mass Water, Inc. Systèmes et procédés de commande d'extraction d'eau
WO2018025770A1 (fr) * 2016-08-04 2018-02-08 有限会社テル Générateur d'eau et fontaine à eau
CN107816760A (zh) * 2016-09-06 2018-03-20 深圳市昊昱环保科技有限公司 一种四季型水冷式除湿系统及其控制方法
ES2667560B1 (es) * 2016-11-10 2019-02-20 Schein Gabriel Edgardo Procupetz Sistema generador de agua enriquecida con ozono y de aire ionizado para cultivos en zonas aridas.
US11447407B2 (en) 2017-07-14 2022-09-20 Source Global, PBC Systems for controlled treatment of water with ozone and related methods therefor
WO2019212718A1 (fr) * 2018-05-02 2019-11-07 Allied Bioscience, Inc. Revêtements antimicrobiens comprenant des silanes quaternaires
JP6766097B2 (ja) * 2018-06-21 2020-10-07 矢崎エナジーシステム株式会社 構造体
US20200039841A1 (en) * 2018-08-05 2020-02-06 Dariush Habibollah Zadeh Distillation and Desalination of Sea Water using Refrigeration units
CN109138051A (zh) * 2018-09-10 2019-01-04 肖丹宁 一种基于信息智能化的石漠化综合治理系统
JP2020062586A (ja) * 2018-10-16 2020-04-23 株式会社Mizuha 飲料水提供装置
US20200124566A1 (en) 2018-10-22 2020-04-23 Zero Mass Water, Inc. Systems and methods for detecting and measuring oxidizing compounds in test fluids
DE102019110236A1 (de) * 2019-04-18 2020-10-22 Güntner Gmbh & Co. Kg Wärmeübertrageranordnung mit wenigstens einem Mehrpass-Wärmeübertrager und Verfahren zum Betrieb einer Wärmeübertrageranordnung
KR102033307B1 (ko) * 2019-07-03 2019-10-17 김원용 농약 분무 노즐용 손상 방지구조
CZ33284U1 (cs) * 2019-08-21 2019-10-07 Táňa Milatová Zařízení pro kondenzaci vody
CN110538551B (zh) * 2019-09-19 2022-02-22 中国核动力研究设计院 一种放射性热空气冷凝除雾器
US20210354080A1 (en) * 2020-05-14 2021-11-18 Water Global Solutions, S.L. Air Humidity Condensing and Potabilizing Machine
CN112113370B (zh) * 2020-08-26 2022-03-15 张帅 一种具有热交换结构的新能源汽车用水冷式冷凝器
AU2022210999A1 (en) 2021-01-19 2023-08-24 Source Global, PBC Systems and methods for generating water from air
CN113446584A (zh) * 2021-06-24 2021-09-28 华能秦煤瑞金发电有限责任公司 一种电厂锅炉水循环系统
CN113280571B (zh) * 2021-07-26 2021-09-17 南通吉利新纺织有限公司 一种固定式余热回收再循环使用的冰水机
CN116201204B (zh) * 2023-02-15 2023-10-24 明光浩淼安防科技股份公司 一种空气制水装置

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3675442A (en) * 1971-02-12 1972-07-11 Rollin J Swanson Atmospheric water collector
US4572766A (en) * 1982-06-02 1986-02-25 W. Schmidt Gmbh & Co. K.G. Plate evaporator or condenser
US5259203A (en) * 1992-05-14 1993-11-09 Engel Daniel R Apparatus and method for extracting potable water from atmosphere
US5400607A (en) * 1993-07-06 1995-03-28 Cayce; James L. System and method for high-efficiency air cooling and dehumidification
US6182453B1 (en) * 1996-04-08 2001-02-06 Worldwide Water, Inc. Portable, potable water recovery and dispensing apparatus
US6238524B1 (en) * 1998-12-14 2001-05-29 Ovation Products Corporation Rotating plate heat exchanger
US20020020185A1 (en) * 2000-08-08 2002-02-21 Instatherm Company Interfacing of thermal storage systems with air conditioning units
US20020164944A1 (en) * 1994-01-31 2002-11-07 Haglid Klas C. Ventilator system and method
US6743467B1 (en) * 1999-08-20 2004-06-01 Unisearch Limited Hydrophobic material
US20050000681A1 (en) * 2001-05-31 2005-01-06 Venmar Ventilation Inc. Air handling systems or devices intermingling fresh and stale air

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999043990A1 (fr) * 1998-02-27 1999-09-02 Watermaster Technologies Limited Appareil de production d'eau
WO2001063059A1 (fr) * 2000-02-21 2001-08-30 Dil Sham Ventures Appareil d'extraction d'eau potable a partir de l'air ambiant
AU2004232788B2 (en) * 2003-04-16 2009-05-28 James J. Reidy Thermoelectric, high-efficiency, water generating device
JP2005023711A (ja) * 2003-06-30 2005-01-27 Masanobu Matsuzaki 空気中の水蒸気凝縮による造水

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3675442A (en) * 1971-02-12 1972-07-11 Rollin J Swanson Atmospheric water collector
US4572766A (en) * 1982-06-02 1986-02-25 W. Schmidt Gmbh & Co. K.G. Plate evaporator or condenser
US5259203A (en) * 1992-05-14 1993-11-09 Engel Daniel R Apparatus and method for extracting potable water from atmosphere
US5400607A (en) * 1993-07-06 1995-03-28 Cayce; James L. System and method for high-efficiency air cooling and dehumidification
US20020164944A1 (en) * 1994-01-31 2002-11-07 Haglid Klas C. Ventilator system and method
US6182453B1 (en) * 1996-04-08 2001-02-06 Worldwide Water, Inc. Portable, potable water recovery and dispensing apparatus
US6238524B1 (en) * 1998-12-14 2001-05-29 Ovation Products Corporation Rotating plate heat exchanger
US6743467B1 (en) * 1999-08-20 2004-06-01 Unisearch Limited Hydrophobic material
US20020020185A1 (en) * 2000-08-08 2002-02-21 Instatherm Company Interfacing of thermal storage systems with air conditioning units
US20050000681A1 (en) * 2001-05-31 2005-01-06 Venmar Ventilation Inc. Air handling systems or devices intermingling fresh and stale air

Cited By (42)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8627673B2 (en) 2008-03-25 2014-01-14 Water Generating Systems LLC Atmospheric water harvesters
US20090260385A1 (en) * 2008-03-25 2009-10-22 Hill James W Atmospheric water harvesters with variable pre-cooling
US7954335B2 (en) 2008-03-25 2011-06-07 Water Generating Systems LLC Atmospheric water harvesters with variable pre-cooling
US20090241580A1 (en) * 2008-03-25 2009-10-01 Hill James W Atmospheric Water Harvesters
US20120011865A1 (en) * 2009-03-27 2012-01-19 Set Ip Holdings, Llc Combined Water Extractor and Electricity Generator
WO2011078771A1 (fr) * 2009-12-21 2011-06-30 Wallenius Water Aktiebolag Échangeur de chaleur à plaques comprenant des éléments de génération d'uv
US8709135B2 (en) * 2010-08-20 2014-04-29 Carol Diane Krumbholz Vapor recovery system utilizing compression-condensation processes and related methods
US20120042691A1 (en) * 2010-08-20 2012-02-23 Carol Diane Krumbholz Vapor recovery system utilizing compression-condensation processes and related methods
US9249988B2 (en) * 2010-11-24 2016-02-02 Grand Mate Co., Ted. Direct vent/power vent water heater and method of testing for safety thereof
US20120125268A1 (en) * 2010-11-24 2012-05-24 Grand Mate Co., Ltd. Direct vent/power vent water heater and method of testing for safety thereof
US20140109857A1 (en) * 2011-03-10 2014-04-24 Valeo Systemes Thermiques Cover for an Intake Housing
US10711743B2 (en) * 2011-03-10 2020-07-14 Valeo Systemes Thermiques Cover for an intake housing
US9664144B2 (en) 2011-03-10 2017-05-30 Valeo Systemes Thermiques Intake housing including a heat exchanger
US9651293B2 (en) * 2011-05-16 2017-05-16 Kjaerulf Pedersen A/S Cooled storing system for photo catalytic decomposition of ethylene
US20140123688A1 (en) * 2011-05-16 2014-05-08 Kjaerulf Pedersen A/S Cooled storing system for photo catalytic decomposition of ethylene
US9086068B2 (en) 2011-09-16 2015-07-21 Grand Mate Co., Ltd. Method of detecting safety of water heater
US20150000317A1 (en) * 2012-02-22 2015-01-01 Fuji Electric Co., Ltd. Integrated air conditioning system and control device thereof
US9810463B2 (en) * 2012-02-22 2017-11-07 Fuji Electric Co., Ltd. Integrated air conditioning system and control device thereof
US20130312451A1 (en) * 2012-05-24 2013-11-28 Michael D. Max Multiple Panel Heat Exchanger
US10495361B2 (en) 2012-05-24 2019-12-03 Maxsystems, Llc Multiple panel heat exchanger
US20140338387A1 (en) * 2013-05-15 2014-11-20 Jish-Shyan Jiang Assembled temperature controlling device
US9777698B2 (en) 2013-11-12 2017-10-03 Daniel Keith Schlak Multiple motor gas turbine engine system with auxiliary gas utilization
US10766340B2 (en) * 2014-07-29 2020-09-08 Hanon Systems Air conditioner system for vehicle
US20170246934A1 (en) * 2014-07-29 2017-08-31 Hanon Systems Air conditioner system for vehicle
WO2017173239A1 (fr) * 2016-03-31 2017-10-05 Oceaneering International, Inc. Climatiseur à microgravité à membrane
US10752484B2 (en) * 2016-04-15 2020-08-25 Automatic Bar Controls, Inc. Nitrogen generator and uses thereof
US20180282144A1 (en) * 2016-04-15 2018-10-04 Automatic Bar Controls, Inc. Nitrogen generator and uses thereof
US11066287B2 (en) 2016-04-15 2021-07-20 Automatic Bar Controls, Inc. Nitrogen generator and uses thereof
US11045743B1 (en) 2016-05-03 2021-06-29 Richard Arthur MAYER Atmospheric water generation and remote operation
US11857909B2 (en) 2016-05-03 2024-01-02 Richard Arthur MAYER Atmospheric water generation and remote operation
US10987610B1 (en) * 2016-05-03 2021-04-27 Richard Arthur MAYER Atmospheric water generation having multi-stage pathogens neutralizing elements
US10994220B1 (en) * 2016-05-03 2021-05-04 Richard Arthur MAYER Atmospheric water generation having indoor subsystems and outdoor subsystems
US11519634B2 (en) 2017-08-30 2022-12-06 Tsunami Products Atmospheric moisture condensing and hydroponic germination
WO2019046643A1 (fr) * 2017-08-30 2019-03-07 Tsunami Products Condensation d'humidité atmosphérique et germination hydroponique
US11674699B2 (en) 2017-10-24 2023-06-13 Politecnico Di Torino Method for production of water from air based on low-temperature heat, and machine and system thereof
US11490574B2 (en) * 2017-11-03 2022-11-08 Republic Of Korea(Management : Rural Development Administration) Flower water receiver
US20200370761A1 (en) * 2017-12-29 2020-11-26 Ji Yang Device for heating by absorbing latent heat of solidification of water and heat pump
US11674725B2 (en) * 2017-12-29 2023-06-13 Ji Yang Heat pump
US10619332B2 (en) * 2018-02-02 2020-04-14 Rocky Research Method and system for obtaining water from air
WO2021163290A1 (fr) * 2020-02-14 2021-08-19 The University Of Akron Ensemble de récupération d'eau douce utilisant un matériau de sorption d'eau à l'intérieur d'un composant hiérarchique
WO2022183134A3 (fr) * 2021-02-28 2022-10-06 Face International Corporation Système et procédé d'élimination et de filtrage à haute efficacité d'agents pathogènes en suspension dans l'air contenu dans un volume de gaz
US11857918B2 (en) * 2022-03-28 2024-01-02 Harbin Institute Of Technology Liquid water harvester based on valve-controlled active air supply

Also Published As

Publication number Publication date
US20160097595A1 (en) 2016-04-07
US9605904B2 (en) 2017-03-28
EP1913323A4 (fr) 2010-08-04
CA2616887A1 (fr) 2007-02-01
CN101278164A (zh) 2008-10-01
ZA200801584B (en) 2008-12-31
KR20080046171A (ko) 2008-05-26
AU2006274424B2 (en) 2013-05-16
AU2006274424A1 (en) 2007-02-01
EP1913323A1 (fr) 2008-04-23
US20130145782A1 (en) 2013-06-13
CN101278164B (zh) 2011-01-05
JP2009503293A (ja) 2009-01-29
WO2007012202A1 (fr) 2007-02-01
BRPI0614319A2 (pt) 2012-11-27

Similar Documents

Publication Publication Date Title
US9605904B2 (en) Water condenser
CA2516002C (fr) Condenseur d'eau
US6931756B2 (en) Combination dehydrator and condensed water dispenser
AU2010321841B2 (en) Atmospheric water generator
US20210354080A1 (en) Air Humidity Condensing and Potabilizing Machine
CN1774401A (zh) 高效的热电水生成装置
US20110048038A1 (en) Multipurpose adiabatic potable water production apparatus and methods
US20100059358A1 (en) Potable water distiller
US20080184720A1 (en) Combination dehydrator and condensed water dispenser
EP3830490B1 (fr) Systeme et procede de refroidissement avec un dessicant liquide
AU2003213855A1 (en) Combination dehydrator and consensed water dispenser
WO2008108740A1 (fr) Système et procédé pour une production d'eau atmosphérique sur une plage étendue de températures ambiantes
AU2013205382A1 (en) Water condenser
WO2011025196A2 (fr) Dispositif de production d'eau potable polyvalent permettant d'économiser l'énergie
ES1279265U (es) Maquina condensadora y potabilizadora de la humedad del aire

Legal Events

Date Code Title Description
AS Assignment

Owner name: FREEDOM WATER COMPANY LTD., CANADA

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:RICHEY, JONATHAN G.;REEL/FRAME:021404/0502

Effective date: 20080728

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION