US20200096241A1 - Rooftop liquid desiccant systems and methods - Google Patents
Rooftop liquid desiccant systems and methods Download PDFInfo
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- US20200096241A1 US20200096241A1 US16/399,165 US201916399165A US2020096241A1 US 20200096241 A1 US20200096241 A1 US 20200096241A1 US 201916399165 A US201916399165 A US 201916399165A US 2020096241 A1 US2020096241 A1 US 2020096241A1
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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
- F25B30/04—Heat pumps of the sorption type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F3/1411—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by absorbing or adsorbing water, e.g. using an hygroscopic desiccant
- F24F3/1417—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by absorbing or adsorbing water, e.g. using an hygroscopic desiccant with liquid hygroscopic desiccants
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F3/147—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification with both heat and humidity transfer between supplied and exhausted air
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
- F24F11/63—Electronic processing
- F24F11/65—Electronic processing for selecting an operating mode
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F2003/1435—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification comprising semi-permeable membrane
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F2003/144—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by dehumidification only
- F24F2003/1446—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by dehumidification only by condensing
- F24F2003/1452—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by dehumidification only by condensing heat extracted from the humid air for condensing is returned to the dried air
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F2003/1458—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification using regenerators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2221/00—Details or features not otherwise provided for
- F24F2221/54—Heating and cooling, simultaneously or alternatively
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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
- F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
- F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
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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
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
- F25B29/006—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the sorption type system
Definitions
- the present application relates generally to the use of liquid desiccant membrane modules to dehumidify and cool an outside air stream entering a space. More specifically, the application relates to the use of micro-porous membranes to keep separate a liquid desiccant that is treating an outside air stream from direct contact with that air stream while in parallel using a conventional vapor compression system to treat a return air stream.
- the membrane allows for the use of turbulent air streams wherein the fluid streams (air, optional cooling fluids, and liquid desiccants) are made to flow so that high heat and moisture transfer rates between the fluids can occur.
- the application further relates to combining cost reduced conventional vapor compression technology with a more costly membrane liquid desiccant and thereby creating a new system at approximately equal cost but with much lower energy consumption.
- Liquid desiccants have been used in parallel with conventional vapor compression HVAC (heating, ventilation, and air conditioning) equipment to help reduce humidity in spaces, particularly in spaces that either require large amounts of outdoor air or that have large humidity loads inside the building space itself.
- Humid climates such as for example Miami, Fla. require a large amount of energy to properly treat (dehumidify and cool) the fresh air that is required for a space's occupant comfort.
- Conventional vapor compression systems have only a limited ability to dehumidify and tend to overcool the air, oftentimes requiring energy intensive reheat systems, which significantly increase the overall energy costs because reheat adds an additional heat-load to the cooling coil.
- Liquid desiccant systems have been used for many years and are generally quite efficient at removing moisture from the air stream.
- liquid desiccant systems generally use concentrated salt solutions such as solutions of LiCl, LiBr or CaCl2 and water.
- Such brines are strongly corrosive, even in small quantities so numerous attempt have been made over the years to prevent desiccant carry-over to the air stream that is to be treated.
- One approach generally categorized as closed desiccant systems—is commonly used in equipment dubbed absorption chillers, places the brine in a vacuum vessel which then contains the desiccant and since the air is not directly exposed to the desiccant; such systems do not have any risk of carry-over of desiccant particles to the supply air stream.
- a micro-porous membrane to the surface of these open liquid desiccant systems has several advantages. First it prevents any desiccant from escaping (carrying-over) to the air stream and becoming a source of corrosion in the building. And second, the membrane allows for the use of turbulent air flows enhancing heat and moisture transfer, which in turn results in a smaller system since it can be build more compactly.
- the micro-porous membrane retains the desiccant typically by being hydrophobic to the desiccant solution and breakthrough of desiccant can occur but only at pressures significantly higher than the operating pressure. The water vapor in an air stream that is flowing over the membrane diffuses through the membrane into the underlying desiccant resulting in a drier air stream. If the desiccant is at the same time cooler than the air stream, a cooling function will occur as well, resulting in a simultaneous cooling and dehumidification effect.
- U.S. Patent Application Publication No. 2012/0132513, and PCT Application No. PCT/US11/037936 by Vandermeulen et al. disclose several embodiments for plate structures for membrane dehumidification of air streams.
- RTUs Conventional Roof Top Units
- MAUs Make Up Air
- DOAS Dedicated Outside Air Systems
- RTUs are the only equipment utilized simply because of their lower initial cost since the owner of the building and the entity paying for the electricity are often different. But the use of RTUs often results in poor energy performance, high humidity and buildings that feel much too cold. Upgrading a building with LED lighting for example can possibly lead to humidity problems and the cold feeling is increased because the internal heat load from incandescent lighting which helps heat a building, largely disappears when LEDs are installed.
- RTUs generally do not humidify in winter operation mode. In winter the large amount of heating that is applied to the air stream results in very dry building conditions which can also be uncomfortable. In some buildings humidifiers are installed in ductwork or integrated to the RTU to provide humidity to the space. However, the evaporation of water in the air significantly cools that air requiring additional heat to be applied and thus increases energy costs.
- the liquid desiccant runs down the face of a support plate as a falling film in a conditioner for treating an air stream.
- the liquid desiccant is covered by a microporous membrane so that liquid desiccant is unable to enter the air stream, but water vapor in the air stream is able to be absorbed into the liquid desiccant.
- the liquid desiccant is directed over a plate structure containing a heat transfer fluid.
- the heat transfer fluid is thermally coupled to a liquid to refrigerant heat exchanger and is pumped by a liquid pump.
- the refrigerant in the heat exchanger is cold and picks up heat through the heat exchanger.
- the warmer refrigerant leaving the heat exchanger is directed to a refrigerant compressor.
- the compressor compresses the refrigerant and the exiting hot refrigerant is directed to another heat transfer fluid in a refrigerant heat exchanger.
- the heat exchanger heats the hot heat transfer fluid.
- the hot heat transfer fluid is directed to a liquid desiccant regenerator through a liquid pump.
- a liquid desiccant in a regenerator is directed over a plate structure containing the hot heat transfer fluid.
- the liquid desiccant in the regenerator runs down the face of a support plate as a falling film.
- the liquid desiccant in the regenerator is also covered by a microporous membrane so that liquid desiccant is unable to enter the air stream, but water vapor in the air stream is able to be desorbed from the liquid desiccant.
- the liquid desiccant is transported from the conditioner to the regenerator and from the regenerator back to the conditioner.
- the liquid desiccant is pumped by a pump.
- the liquid desiccant is pumped through a heat exchanger between the conditioner and the regenerator.
- the air exiting the conditioner is directed to a second air stream.
- the second air stream is a return air stream from a space.
- a portion of said return air stream is exhausted from the system and the remaining air stream is mixed with the air stream from the conditioner.
- the exhausted portion is between 5 and 25% of the return air stream.
- the exhausted portion is directed to the regenerator. In one or more embodiments, the exhausted portion is mixed with an outside air stream before being directed to the regenerator. In accordance with one or more embodiments the mixed air stream between the return air and the conditioner air is directed through a cooling or evaporator coil. In one or more embodiments, the cooling coil receives cold refrigerant from a refrigeration circuit. In one or more embodiments, the cooled air is directed back to the space to be cooled. In accordance with one or more embodiments the cooling coil receives cold refrigerant from an expansion valve or similar device. In one or more embodiments, the expansion valve receives liquid refrigerant from a condenser coil.
- the condenser coil receives hot refrigerant gas from a compressor system. In one or more embodiments, the condenser coil is cooled by an outside air stream. In one or more embodiments, the hot refrigerant gas from the compressor is first directed to the refrigerant to liquid heat exchanger from the regenerator. In one or more embodiments, multiple compressors are used. In one or more embodiments, separate compressors serve the liquid to refrigerant heat exchangers from the compressors serving the evaporator and condenser coils. In one or more embodiments, the compressors are variable speed compressors. In one or more embodiments, the air streams are moved by a fan or blower. In one or more embodiments, such fans are variable speed fans.
- a liquid desiccant runs down the face of a support plate as a falling film in a conditioner for treating an air stream.
- the liquid desiccant is covered by a microporous membrane so that liquid desiccant is unable to enter the air stream, but water vapor in the air stream is able to be absorbed into the liquid desiccant.
- the liquid desiccant is directed over a plate structure containing a heat transfer fluid.
- the heat transfer fluid is thermally coupled to a liquid to refrigerant heat exchanger and is pumped by a liquid pump.
- the refrigerant in the heat exchanger is hot and rejects heat to the conditioner and hence to the air stream passing through said conditioner.
- the air exiting the conditioner is directed to a second air stream.
- the second air stream is a return air stream from a space.
- a portion of said return air stream is exhausted from the system and the remaining air stream is mixed with the air stream from the conditioner.
- the exhausted portion is between 5 and 25% of the return air stream.
- the exhausted portion is directed to the regenerator. In one or more embodiments, the exhausted portion is mixed with an outside air stream before being directed to the regenerator. In accordance with one or more embodiments the mixed air stream between the return air and the conditioner air is directed through a condenser coil. In one or more embodiments, the condenser coil receives hot refrigerant from a refrigeration circuit. In one or more embodiments, the condenser coil warms the mixed air stream coming from the conditioner and the remaining return air from the space. In one or more embodiments, the warmer air is directed back to the space to be cooled. In accordance with one or more embodiments the condenser coil receives hot refrigerant from the liquid to refrigerant heat exchanger.
- the condenser coil receives hot refrigerant gas from a compressor system directly.
- the colder, liquid refrigerant leaving the condenser coil is directed to an expansion valve or similar device.
- the refrigerant expands in the expansion valve and is directed to an evaporator coil.
- the evaporator coil also receives an outside air stream from which it pulls heat to heat the cold refrigerant from the expansion valve.
- the warmer refrigerant from the evaporator coil is directed to a liquid to refrigerant heat exchanger.
- the liquid to refrigerant heat exchanger receives the refrigerant from the evaporator and absorbs additional heat from a heat transfer fluid loop.
- the heat transfer fluid loop is thermally coupled to a regenerator.
- the regenerator collects heat and moisture from an air stream.
- the liquid desiccant in the regenerator is directed over a plate structure containing the cold heat transfer fluid.
- the liquid desiccant in the regenerator runs down the face of a support plate as a falling film.
- the liquid desiccant in the regenerator is also covered by a microporous membrane so that liquid desiccant is unable to enter the air stream, but water vapor in the air stream is able to be desorbed from the liquid desiccant.
- the air stream is an air stream rejected from the return air stream.
- the air stream is an outside air stream.
- the air stream is a mixture of the rejected air stream and an outside air stream.
- the refrigerant leaving the liquid to refrigerant heat exchanger is directed to a refrigerant compressor.
- the compressor compresses the refrigerant which is then directed to a conditioner heat exchanger.
- the heat exchanger heats the hot heat transfer fluid.
- the hot heat transfer fluid is directed to the liquid desiccant conditioner through a liquid pump.
- the liquid desiccant is transported from the conditioner to the regenerator and from the regenerator back to the conditioner.
- the liquid desiccant is pumped by a pump.
- the liquid desiccant is pumped through a heat exchanger between the conditioner and the regenerator.
- separate compressors serve the liquid to refrigerant heat exchangers from the compressors serving the evaporator and condenser coils.
- the compressors are variable speed compressors.
- the air streams are moved by a fan or blower.
- such fans are variable speed fans.
- multiple compressors are used.
- the cooler refrigerant leaving the heat exchanger is directed to a condenser coil.
- the condenser coil is receiving an air stream and the still hot refrigerant is used to heat such an air stream.
- water is added to the desiccant during operation. In one or more embodiments, water is added during winter heating mode. In one or more embodiments, water is added to control the concentration of the desiccant. In one or more embodiments, water is added during dry hot weather.
- the liquid desiccant runs down the face of a support plate as a falling film in a conditioner for treating an air stream.
- the liquid desiccant is covered by a microporous membrane so that liquid desiccant is unable to enter the air stream, but water vapor in the air stream is able to be absorbed into the liquid desiccant.
- the liquid desiccant is thermally coupled to a desiccant to refrigerant heat exchanger and is pumped by a liquid pump.
- the refrigerant in the heat exchanger is cold and picks up heat through the heat exchanger.
- the warmer refrigerant leaving the heat exchanger is directed to a refrigerant compressor.
- the compressor compresses the refrigerant and the exiting hot refrigerant is directed to another refrigerant to desiccant heat exchanger.
- the heat exchanger heats a hot desiccant.
- the hot desiccant is directed to a liquid desiccant regenerator through a liquid pump.
- a liquid desiccant in a regenerator is directed over a plate structure.
- the liquid desiccant in the regenerator runs down the face of a support plate as a falling film.
- the liquid desiccant in the regenerator is also covered by a microporous membrane so that liquid desiccant is unable to enter the air stream, but water vapor in the air stream is able to be desorbed from the liquid desiccant.
- the liquid desiccant is transported from the conditioner to the regenerator and from the regenerator back to the conditioner.
- the liquid desiccant is pumped by a pump.
- the liquid desiccant is pumped through a heat exchanger between the conditioner and the regenerator.
- the air exiting the conditioner is directed to a second air stream.
- the second air stream is a return air stream from a space.
- a portion of said return air stream is exhausted from the system and the remaining air stream is mixed with the air stream from the conditioner.
- the exhausted portion is between 5 and 25% of the return air stream.
- the exhausted portion is directed to the regenerator.
- the exhausted portion is mixed with an outside air stream before being directed to the regenerator.
- the mixed air stream between the return air and the conditioner air is directed through a cooling or evaporator coil.
- the cooling coil receives cold refrigerant from a refrigeration circuit.
- the cooled air is directed back to the space to be cooled.
- the cooling coil receives cold refrigerant from an expansion valve or similar device.
- the expansion valve receives liquid refrigerant from a condenser coil.
- the condenser coil receives hot refrigerant gas from a compressor system.
- the condenser coil is cooled by an outside air stream.
- the hot refrigerant gas from the compressor is first directed to the refrigerant to desiccant heat exchanger from the regenerator.
- multiple compressors are used.
- separate compressors serve the desiccant to refrigerant heat exchangers from the compressors serving the evaporator and condenser coils.
- the compressors are variable speed compressors.
- the air streams are moved by a fan or blower.
- such fans are variable speed fans.
- the flow direction of the refrigerant is reversed for a winter heating mode.
- water is added to the desiccant during operation.
- water is added during winter heating mode.
- water is added to control the concentration of the desiccant.
- water is added during dry hot weather.
- the liquid desiccant runs down the face of a support plate as a falling film in a conditioner for treating an air stream.
- the liquid desiccant is covered by a microporous membrane so that liquid desiccant is unable to enter the air stream, but water vapor in the air stream is able to be absorbed into the liquid desiccant.
- the liquid desiccant is thermally coupled to a refrigerant heat exchanger embedded in the conditioner.
- the refrigerant in the conditioner is cold and picks up heat from the desiccant and hence from the air stream flowing through the conditioner.
- the warmer refrigerant leaving the conditioner is directed to a refrigerant compressor.
- the compressor compresses the refrigerant and the exiting hot refrigerant is directed to a regenerator.
- the hot refrigerant is embedded into a structure in the regenerator.
- a liquid desiccant in the regenerator is directed over a plate structure.
- the liquid desiccant in the regenerator runs down the face of a support plate as a falling film.
- the liquid desiccant in the regenerator is also covered by a microporous membrane so that liquid desiccant is unable to enter the air stream, but water vapor in the air stream is able to be desorbed from the liquid desiccant.
- the liquid desiccant is transported from the conditioner to the regenerator and from the regenerator back to the conditioner.
- the liquid desiccant is pumped by a pump.
- the liquid desiccant is pumped through a heat exchanger between the conditioner and the regenerator.
- the air exiting the conditioner is directed to a second air stream.
- the second air stream is a return air stream from a space.
- a portion of said return air stream is exhausted from the system and the remaining air stream is mixed with the air stream from the conditioner.
- the exhausted portion is between 5 and 25% of the return air stream.
- the exhausted portion is directed to the regenerator.
- the exhausted portion is mixed with an outside air stream before being directed to the regenerator.
- the mixed air stream between the return air and the conditioner air is directed through a cooling or evaporator coil.
- the cooling coil receives cold refrigerant from a refrigeration circuit. In one or more embodiments, the cooled air is directed back to the space to be cooled. In accordance with one or more embodiments the cooling coil receives cold refrigerant from an expansion valve or similar device. In one or more embodiments, the expansion valve receives liquid refrigerant from a condenser coil. In one or more embodiments, the condenser coil receives hot refrigerant gas from a compressor system. In one or more embodiments, the condenser coil is cooled by an outside air stream. In one or more embodiments, the hot refrigerant gas from the compressor is first directed to the refrigerant to desiccant heat exchanger from the regenerator.
- multiple compressors are used. In one or more embodiments, separate compressors serve the desiccant to refrigerant heat exchangers from the compressors serving the evaporator and condenser coils. In one or more embodiments, the compressors are variable speed compressors. In one or more embodiments, the air streams are moved by a fan or blower. In one or more embodiments, such fans are variable speed fans. In one or more embodiments, the flow direction of the refrigerant is reversed for a winter heating mode. In one or more embodiments, water is added to the desiccant during operation. In one or more embodiments, water is added during winter heating mode. In one or more embodiments, water is added to control the concentration of the desiccant. In one or more embodiments, water is added during dry hot weather.
- a set of pairs of channels for liquid transport are provided wherein the one side of the channel pair receives a water stream and the other side of the channel pair receives a liquid desiccant.
- the water is tap water, sea water, waste water and the like.
- the liquid desiccant is any liquid desiccant that is able to absorb water.
- the elements of the channel pair are separated by a membrane selectively permeable to water but not to any other constituents.
- the membrane is a reverse osmosis membrane, or some other convenient selective membrane.
- multiple pairs can be individually controlled to vary the amount of water that is added to the desiccant stream from the water stream.
- other driving forces besides concentration potential differences are used to assist the permeation of water through the membrane.
- such driving forces are heat or pressure.
- a water injector comprising a series of channel pairs is connected to a liquid desiccant circuit and a water circuit wherein one half of the channel pairs receives a liquid desiccant and the other half receives the water.
- the channel pairs are separated by a selective membrane.
- the liquid desiccant circuit is connected between a regenerator and a conditioner.
- the water circuit receives water from a water tank through a pumping system.
- excess water that is not absorbed through the selective membrane is drained back to the water tank.
- the water tank is kept full by a level sensor or float switch.
- precipitates or concentrated water is drained from the water tank by a drain valve also known as a blow-down procedure.
- a water injector comprising a series of channel triplets is connected to two liquid desiccant circuits and a water circuit wherein a third of the channel triplets receives a hot liquid desiccant, a second third of the triplets receives a cold liquid desiccant and the remaining third of the triplets receives the water.
- the channel triplets are separated by a selective membrane.
- the liquid desiccant channels are connected between a regenerator and a conditioner.
- the water circuit receives water from a water tank through a pumping system. In one or more embodiments, excess water that is not absorbed through the selective membrane is drained back to the water tank. In one or more embodiments, the water tank is kept full by a level sensor or float switch. In one or more embodiments, precipitates or concentrated water is drained from the water tank by a drain valve also known as a blow-down procedure.
- a liquid desiccant stream is split into a larger and a smaller stream.
- the larger stream is directed into a heat transfer channel that is constructed to provide fluid flow in a counter-flow direction to an air stream.
- the larger stream is a horizontal fluid stream and the air stream is a horizontal stream in a direction counter to the fluid stream.
- the larger stream is flowing vertically upward or vertically downward, and the air stream is flowing vertically downward or vertically upward in a counter-flow orientation.
- the mass flow rates of the larger stream and the air flow stream are approximately equal within a factor of two.
- the larger desiccant stream is directed to a heat exchanger coupled to a heating or cooling device.
- the heat or cooling device is a heat pump, a geothermal source, a hot water source, and the like.
- the heat pump is reversible.
- the heat exchanger is made from a non-corrosive material.
- the material is titanium or any suitable material non-corrosive to the desiccant.
- the desiccant itself is non-corrosive.
- the smaller desiccant stream is simultaneously directed to a channel that is flowing downward by gravity.
- the smaller stream is bound by a membrane that has an air flow on the opposite side.
- the membrane is a micro-porous membrane.
- the mass flow rate of the smaller desiccant stream is between 1 and 10% of the mass flow rate of the larger desiccant stream.
- the smaller desiccant stream is directed to a regenerator for removing excess water vapor after exiting the (membrane) channel.
- a liquid desiccant stream is split into a larger and a smaller stream.
- the larger stream is directed into a heat transfer channel that is constructed to provide fluid flow in a counter-flow direction to an air stream.
- the smaller stream is directed to a membrane bound channel.
- the membrane channel has an air stream on the opposite side of the desiccant.
- the larger stream is directed to a heat pump heat exchanger after leaving the heat transfer channel and is directed back to the heat transfer channel after being cooled or heated by the heat pump heat exchanger.
- the air stream is an outside air stream.
- the air stream after being treated by the desiccant behind the membrane is directed into a larger air stream that is returning from a space.
- the larger air stream is subsequently cooled by a coil that is coupled to the same heat pump refrigeration circuit as the heat exchanger heat pump.
- the desiccant stream is a single desiccant stream and the heat transfer channel is configured as a two-way heat and mass exchanger module.
- the two-way heat and mass exchanger module is bound by a membrane.
- the membrane is a micro-porous membrane.
- the two-way heat and mass exchanger module is treating an outside air stream.
- the air stream after being treated by the desiccant behind the membrane is directed into a larger air stream that is returning from a space.
- the larger air stream is subsequently cooled by a coil that is coupled to the same heat pump refrigeration circuit as the heat exchanger heat pump.
- FIG. 1 illustrates an exemplary 3-way liquid desiccant air conditioning system using a chiller or external heating or cooling sources.
- FIG. 2 shows an exemplary flexibly configurable membrane module that incorporates 3-way liquid desiccant plates.
- FIG. 3 illustrates an exemplary single membrane plate in the liquid desiccant membrane module of FIG. 2 .
- FIG. 4A schematically illustrates a conventional mini-split air conditioning system operating in a cooling mode.
- FIG. 4B schematically illustrates a conventional mini-split air conditioning system operating in a heating mode.
- FIG. 5A schematically illustrates an exemplary chiller assisted liquid desiccant air conditioning system for 100% outside air in a summer cooling mode.
- FIG. 5B schematically illustrates an exemplary chiller assisted liquid desiccant air conditioning system for 100% outside air in a winter heating mode.
- FIG. 6 schematically illustrates an exemplary chiller assisted partial outside air liquid desiccant air conditioning system using a 3-way heat and mass exchanger in a summer cooling mode in accordance with one or more embodiments.
- FIG. 7 schematically illustrates an exemplary chiller assisted partial outside air liquid desiccant air conditioning system using a 3-way heat and mass exchanger in a heating mode in accordance with one or more embodiments.
- FIG. 8 illustrates the psychrometric processes involved in the cooling of air for a conventional RTU and the equivalent processes in a liquid-RTU.
- FIG. 9 illustrates the psychrometric processes involved in the heating of air for a conventional RTU and the equivalent processes in a liquid-RTU.
- FIG. 10 schematically illustrates an exemplary chiller assisted partial outside air liquid desiccant air conditioning system using a 2-way heat and mass exchanger in a summer cooling mode in accordance with one or more embodiments wherein the liquid desiccant is pre-cooled and pre-heated before entering the heat and mass exchangers.
- FIG. 11 schematically illustrates an exemplary chiller assisted partial outside air liquid desiccant air conditioning system using a 2-way heat and mass exchanger in a summer cooling mode in accordance with one or more embodiments wherein the liquid desiccant is cooled and heated inside the heat and mass exchangers.
- FIG. 12 illustrates a water extraction module that pulls pure water into the liquid desiccant for use in winter humidification mode.
- FIG. 13 shows how the water extraction module of FIG. 12 can be integrated into the system of FIG. 7 .
- FIG. 14 illustrates two sets of channel triplets that simultaneously provide a heat exchange and desiccant humidification function.
- FIG. 15 shows two of the 3-way membrane modules of FIG. 3 integrated into a DOAS, wherein the heat transfer fluid and the liquid desiccant fluid have been combined into a single desiccant fluid system, while retaining the advantage of separate paths for the fluid that is performing the dehumidification function and the fluid that is doing the heat transfer function.
- FIG. 16 shows the system of FIG. 15 integrated to the system of FIG. 6 .
- FIG. 1 depicts a new type of liquid desiccant system as described in more detail in U.S. Patent Application Publication No. 20120125020, which is incorporated by reference herein.
- a conditioner 101 comprises a set of plate structures that are internally hollow.
- a cold heat transfer fluid is generated in cold source 107 and entered into the plates.
- Liquid desiccant solution at 114 is brought onto the outer surface of the plates and runs down the outer surface of each of the plates.
- the liquid desiccant runs behind a thin sheet of material such as a membrane that is located between the air flow and the surface of the plates.
- the sheet of material can also comprise a hydrophilic material or a flocking material in which case the liquid desiccant runs more or less inside the material rather than over its surface.
- the liquid desiccant conditioner 101 and regenerator 102 are generally known as 3-way liquid desiccant heat and mass exchangers, because they exchange heat and mass between the air stream, the desiccant, and a heat transfer fluid, so that there are three fluid streams involved. Two-way heat and mass exchangers generally have only a liquid desiccant and an air stream involved as will be seen later.
- the liquid desiccant is collected at the lower end of each plate at 111 without the need for either a collection pan or bath so that the air flow can be horizontal or vertical.
- Each of the plates may have a separate desiccant collector at a lower end of the outer surfaces of the plate for collecting liquid desiccant that has flowed across the surfaces.
- the desiccant collectors of adjacent plates are spaced apart from each other to permit airflow therebetween.
- the liquid desiccant is then transported through a heat exchanger 113 to the top of the regenerator 102 to point 115 where the liquid desiccant is distributed across the plates of the regenerator.
- Return air or optionally outside air 105 is blown across the regenerator plate and water vapor is transported from the liquid desiccant into the leaving air stream 106 .
- An optional heat source 108 provides the driving force for the regeneration.
- the hot heat transfer fluid 110 from the heat source can be put inside the plates of the regenerator similar to the cold heat transfer fluid on the conditioner. Again, the liquid desiccant is collected at the bottom of the plates 102 without the need for either a collection pan or bath so that also on the regenerator the air flow can be horizontal or vertical.
- An optional heat pump 116 can be used to provide cooling and heating of the liquid desiccant, however it is generally more favorable to connect a heat pump between the cold source 107 and the hot source 108 , which is thus pumping heat from the cooling fluids rather than from the desiccant.
- FIG. 2 describes a 3-way heat and mass exchanger as described in further detail in U.S. Patent Application Publication Nos. 2014-0150662 filed on Jun. 11, 2013, 2014-0150656 filed on Jun. 11, 2013, and US 2014-0150657 filed on Jun. 11, 2013, which are all incorporated by reference herein.
- a liquid desiccant enters the structure through ports 304 and is directed behind a series of membranes as described in FIG. 1 .
- the liquid desiccant is collected and removed through ports 305 .
- a cooling or heating fluid is provided through ports 306 and runs counter to the air stream 301 inside the hollow plate structures, again as described in FIG. 1 and in more detail in FIG. 3 .
- the cooling or heating fluids exit through ports 307 .
- the treated air 302 is directed to a space in a building or is exhausted as the case may be.
- FIG. 3 describes a 3-way heat exchanger as described in more detail in U.S. Provisional Patent Applications Ser. No. 61/771,340 filed on Mar. 1, 2013 and U.S. Patent Application Publication No. US 2014-0245769, which are incorporated by reference herein.
- the air stream 251 flows counter to a cooling fluid stream 254 .
- Membranes 252 contain a liquid desiccant 253 that is falling along the wall 255 that contain a heat transfer fluid 254 .
- Water vapor 256 entrained in the air stream is able to transition the membrane 252 and is absorbed into the liquid desiccant 253 .
- the heat of condensation of water 258 that is released during the absorption is conducted through the wall 255 into the heat transfer fluid 254 .
- Sensible heat 257 from the air stream is also conducted through the membrane 252 , liquid desiccant 253 and wall 255 into the heat transfer fluid 254 .
- FIG. 4A illustrates a schematic diagram of a conventional packaged Roof-Top Unit (RTU) air conditioning system as is frequently installed on buildings, operating in a cooling mode.
- the unit comprises a set of components that generate cool, dehumidified air and a set of components that release heat to the environment.
- the cooling and heating components are generally inside a single enclosure. It is however possible to separate the cooling and heating components into separate enclosures or locate them in separate locations.
- the cooling components comprise a cooling (evaporator) coil 405 through which a fan 407 pulls return air (labeled RA) 401 that has been returned (usually through a duct work—which is not shown) from a space.
- RA return air
- the cooling coil 405 Prior to reaching the cooling coil 405 , some of the return air RA is exhausted from the system as exhaust air EA 2 402 , which is replaced by outside air OA 403 which is mixed with the remaining return air to a mixed air stream MA 404 . In summer, this outside air OA is often warm and humid and adds a significant contribution to the cooling load on the system.
- the cooling coil 405 cools the air and condenses water vapor on the coil which is collected in drain pan 424 and ducted to the outside 425 .
- the resulting cooler, drier air CC 408 however, is now cold and very close to 100% relative humidity (saturated).
- the air CC 408 coming directly from the cooling coil 10 can be uncomfortably cold.
- the air 408 is re-heated to a warmer temperature.
- a hot water coil with hot water fed from a boiler or a steam coil receiving heat from a steam generator or by using electric resistance heaters. This heating of air results in an additional heat load on the cooling system.
- More modern systems use an optional re-heat coil 409 which contains hot refrigerant from a compressor 416 .
- the re-heat coil 409 heats the air stream 408 to a warmer air stream HC 410 , which is then recirculated back to the space, provides occupant comfort and allows one to better control humidity in the space.
- the compressor 416 receives a refrigerant through line 423 and receives power through conductor 417 .
- the refrigerant can be any suitable refrigerant such as R410A, R407A, R134A, R1234YF, Propane, Ammonia, CO 2 , etc.
- the refrigerant is compressed by the compressor 416 and compressed refrigerant is conducted to a condenser coil 414 through line 418 .
- the condenser coil 414 receives outside air OA 411 , which is blown through the coil 414 by fan 413 , which receives power through conductor 412 .
- the resulting exhaust air stream EA 415 carries with it the heat of compression generated by the compressor.
- the refrigerant condenses in the condenser coil 414 and the resulting cooler, (partially) liquid refrigerant 419 is conducted to the re-heat coil 409 where additional heat is removed from the refrigerant, which turns into a liquid in this stage.
- the liquid refrigerant in line 420 is then conducted to expansion valve 421 before reaching the cooling coil 405 .
- the cooling coil 405 receives liquid refrigerant at pressure of typically 50-200 psi through line 422 .
- the cooling coil 405 absorbs heat from the air stream MA 404 which re-evaporates the refrigerant which is then conducted through line 423 back to the compressor 416 .
- the pressure of the refrigerant in line 418 is typically 300-600 psi.
- the system can have multiple cooling coils 405 , fans 407 and expansion valves 421 as well as compressors 416 and condenser coils 414 and condenser fans 413 .
- the system also has additional components in the refrigerant circuit or the sequence of components is ordered differently which are all well known in the art. As will be shown later, one of these components can be a diverter valve 426 which bypasses the re-heat coil 409 in winter mode.
- recirculating rooftop units generally have a cooling coil that condenses moisture and introduce a small amount of outside air that is added to a main air stream that returns from the space, is cooled and dehumidified and the ducted back to the space. In many instances the larges load is the dehumidification of outside air and dealing with the reheat energy, as well as the average fan power required to move the air.
- the primary electrical energy consuming components are the compressor 416 through electrical line 417 , the condenser fan electrical motor through supply line 412 and the evaporator fan motor through line 406 .
- the compressor uses close to 80% of the electricity required to operate the system, with the condenser and evaporator fans taking about 10% of the electricity each at peak load. However when one averages power consumption over the year, the average fan power is closer to 40% of the total load since fans generally run all the time and the compressor switches off on an as needed basis.
- the air flow RA is around 4,000 CFM.
- the amount of outside air OA mixed in is between 5% and 25% so between 200 and 1,000 CFM.
- the condenser coil 414 is generally operated with a larger air flow than the evaporator coil 405 of about 2,000 CFM for a 10 ton RTU. This allows the condenser to be more efficient and reject the heat of compression more efficiently to the outside air OA.
- FIG. 4B is a schematic diagram of the system of FIG. 4A operating in a winter heating mode as a heat pump.
- Not all RTUs are heat pumps, and generally a cooling only system as shown in FIG. 4A can be used, possibly supplemented with a simple gas or electric furnace air heater.
- heat pumps are gaining popularity particularly in moderate climates since they can provide heating as well as cooling with better efficiency than electric heat and without the need to run gas lines to the RTU.
- the flow of refrigerant from the compressor 417 has simply been reversed. In actuality the refrigerant is usually diverted by a 4 -way valve circuit which accomplishes the same effect.
- the compressor produces hot refrigerant in line 423 which is now conducted to the coil 405 , which is now functioning as a condenser rather than an evaporator.
- the heat of compression is carried to the mixed air stream MA 404 resulting in a warm air stream CC 408 .
- the mixed air stream MA 404 is the result of removing some air EA 2 402 from the return air RA 401 and replacing it with outside air OA 403 .
- the warm air stream CC 408 however is now relatively dry because heating by the condenser coil 405 results in air with low relative humidity and thus oftentimes a humidification system 427 is added to provide the required humidity for occupant comfort.
- the humidification system 427 requires a water supply 428 .
- FIG. 5A illustrates a schematic representation of a liquid desiccant air conditioner system.
- a 3-way heat and mass exchanger conditioner 503 (which is similar to the conditioner 101 of FIG. 1 ) receives an air stream 501 from the outside (“OA”). Fan 502 pulls the air 501 through the conditioner 503 wherein the air is cooled and dehumidified. The resulting cool, dry air 504 (“SA”) is supplied to a space for occupant comfort.
- SA cool, dry air 504
- the 3-way conditioner 503 receives a concentrated desiccant 527 in the manner explained under FIGS. 1-3 . It is preferable to use a membrane on the 3-way conditioner 503 to contain the desiccant and inhibit it from being distributed into the air stream 504 .
- the diluted desiccant 528 which contains the captured water vapor is transported to a heat and mass exchanger regenerator 522 . Furthermore chilled water 509 is provided by pump 508 , which enters the conditioner module 503 where it picks up heat from the air as well as latent heat released by the capture of water vapor in the desiccant 527 .
- the warmer water 506 is brought to the heat exchanger 507 on the chiller system 530 .
- the system of FIG. 5A does not require a condensate drain line like line 425 in FIG. 4A . Rather, any moisture that is condensed into the desiccant is removed as part of the desiccant itself. This also eliminates problems with mold growth in standing water that can occur in the conventional RTU condensate pan 424 systems of FIG. 4A .
- the liquid desiccant 528 leaves the conditioner 503 and is moved through the optional heat exchanger 526 to the regenerator 522 by pump 525 .
- the chiller system 530 comprises a water to refrigerant evaporator heat exchanger 507 which cools the circulating cooling fluid 506 .
- the liquid, cold refrigerant 517 evaporates in the heat exchanger 507 thereby absorbing the thermal energy from the cooling fluid 506 .
- the gaseous refrigerant 510 is now re-compressed by compressor 511 .
- the compressor 511 ejects hot refrigerant gas 513 , which is liquefied in the condenser heat exchanger 515 .
- the liquid refrigerant exiting the condenser 514 then enters expansion valve 516 , where it rapidly cools and exits at a lower pressure.
- the condenser heat exchanger 515 now releases heat to another cooling fluid loop 519 which brings hot heat transfer fluid 518 to the regenerator 522 .
- Circulating pump 520 brings the heat transfer fluid back to the condenser 515 .
- the 3-way regenerator 522 thus receives a dilute liquid desiccant 528 and hot heat transfer fluid 518 .
- a fan 524 brings outside air 521 (“OA”) through the regenerator 522 .
- the outside air picks up heat and moisture from the heat transfer fluid 518 and desiccant 528 which results in hot humid exhaust air (“EA”) 523 .
- EA hot humid exhaust air
- the compressor 511 receives electrical power 512 and typically accounts for 80% of electrical power consumption of the system.
- the fans 502 and 524 also receive electrical power 505 and 529 respectively and account for most of the remaining power consumption.
- Pumps 508 , 520 and 525 have relatively low power consumption.
- the compressor 511 will operate more efficiently than the compressor 416 in FIG. 4A for several reasons: the evaporator 507 in FIG. 5A will typically operate at higher temperature than the evaporator 405 in FIG. 4A because the liquid desiccant will condense water at much higher temperature without needing to reach saturation levels in the air stream. Furthermore the condenser 515 in FIG. 5A will operate at lower temperatures than the condenser 414 in FIG. 4A because of the evaporation occurring on the regenerator 522 which effectively keeps the condenser 515 cooler. As a result the system of FIG. 5A will use about 40% less electricity than the system of FIG. 4A for similar compressor isentropic efficiencies.
- FIG. 5B shows essentially the same system as FIG. 5A except that the compressor 511 's refrigerant direction has been reversed as indicated by the arrows on refrigerant lines 514 and 510 .
- Reversing the direction of refrigerant flow can be achieved by a 4-way reversing valve (not shown) or other convenient means in the chiller 530 .
- the system is now working as a heat pump, pumping heat from the outside air 521 to the space supply air 504 .
- the air stream 411 contains water vapor and if the evaporator coil 414 gets too cold, this moisture will condense on the surfaces and create ice formation on the coil.
- the same moisture in the regenerator 522 of FIG. 5B will condense in the liquid desiccant which—when managed properly—will not crystalize until ⁇ 60° C. for some desiccants such as LiCl and water. This will allow the system to continue to operate at much lower outside air temperatures without freezing risk.
- outside air 501 is directed through the conditioner 503 by fan 502 which is operated by electrical power 505 .
- the compressor 511 discharges hot refrigerant through line 510 into condenser heat exchanger 507 and out through line 510 .
- the heat exchanger rejects heat to heat transfer fluid circulated by pump 508 through line 509 into the conditioner 503 which results in the air stream 501 picking up heat and moisture from the desiccant.
- Dilute desiccant is supplied by line 527 to the conditioner.
- the dilute desiccant is directed from regenerator 522 by pump 525 through heat exchanger 526 .
- regenerator 522 takes in either outside air OA or preferably return air RA 521 which is directed through the regenerator by fan 524 which is powered by electrical connection 529 . Return air is preferred because is usually much warmer and contains much more moisture than outside air, which allows the regenerator to capture more heat and moisture from the air stream 521 .
- the regenerator 522 thus produces colder, drier exhaust air EA 523 .
- a heat transfer fluid in line 518 absorbs heat from the regenerator 522 which is pumped by pump 520 to heat exchanger 515 .
- the heat exchanger 515 received cold refrigerant from expansion valve 516 through line 514 and the heated refrigerant is conducted through line 513 back to the compressor 511 which receives power from conductor 512 .
- FIG. 6 illustrates an air-conditioning system in accordance with one or more embodiments wherein a modified liquid desiccant section 600 A is connected to a modified RTU section 600 B but wherein the two systems share a single chiller system 600 C.
- the outside air OA 601 which as shown in FIG. 4A is typically 5-25% of the return air stream RA 604 , is now directed through the conditioner 602 which is similar in construction to the 3-way heat and mass exchange conditioner described in FIG. 2 .
- the conditioner 602 can be significantly smaller than the conditioner 503 of FIG. 5A because the air stream 601 is much smaller than in the 100% outside air stream 501 of FIG. 5A .
- the conditioner 602 produces a colder, dehumidified air stream SA 603 which is mixed with the return air RA 604 to make mixed air MA 2 606 .
- Excess return air 605 is directed out of the system or towards the regenerator 612 .
- the mixed air MA 2 is pulled by fan 608 through evaporator coil 607 which primarily provides sensible only cooling so that the coil 607 can be much shallower and less expensive than the coil 405 in FIG. 4A which needs to be deeper to allow moisture to condense.
- the resulting air stream CC 2 609 is ducted to the space to be cooled.
- the regenerator 612 receives either outside air OA 610 or the excess return air 605 or a mixture 611 thereof.
- the regenerator air stream 611 can be pulled through the regenerator 612 which again is similar in construction to the 3-way heat and mass exchanger described in FIG. 2 by a fan 637 and the resulting exhaust air stream EA 2 613 is generally much warmer and contains more water vapor than the mixed air stream 611 that is entering. Heat is provided by circulating a heat transfer fluid through line 621 using pump 622 .
- the compressor 618 compresses a refrigerant similar to the compressors in FIG. 4A and FIG. 5A .
- the hot refrigerant gas is conducted through line 619 to a condenser heat exchanger 620 .
- a smaller amount of heat is conducted through this liquid-to-refrigerant heat exchanger 620 into the heat transfer fluid in circuit 621 .
- the still hot refrigerant is now conducted through line 623 to a condenser coil 616 , which receives outside air OA 614 from fan 615 .
- the resulting hot exhaust air EA 3 617 is ejected into the environment.
- the refrigerant which is now a cooler liquid after exiting the condenser coil 616 is conducted through line 624 to an expansion valve 625 , where it is expanded and becomes cold.
- the cold liquid refrigerant is conducted through line 626 to the evaporator coil 607 where it absorbs heat from the mixed air stream MA 2 606 .
- the still relatively cold refrigerant which has partially evaporated in the coil 607 is now conducted through line 627 to evaporator heat exchanger 628 where additional heat is removed from the heat transfer fluid circulating in line 629 by pump 630 .
- the gaseous refrigerant exiting the heat exchanger 628 is conducted through line 631 back to the compressor 618 .
- a liquid desiccant is circulated between the conditioner 602 and the regenerator 612 through lines 635 , the heat exchanger 633 and is circulated back to the conditioner by pump 632 and through line 634 .
- a water-injection module 636 can be added to one or both of the desiccant lines 634 and 635 .
- Such a module injects water into the desiccant in order to reduce the concentration of the desiccant and is described in FIG. 12 in more detail. Water injection is useful in conditions in which the desiccant concentration gets higher than desired, e.g., in hot, dry conditions such as can occur in the summer or in cold, dry conditions such as can occur in winter which will be described in more detail in FIG. 7 .
- FIG. 7 illustrates an embodiment of the present invention of FIG. 6 , wherein a modified liquid desiccant section 700 A is connected to a modified RTU section 700 B but wherein the two systems share a single chiller system 700 C operating in a heating mode.
- the outside air OA 701 which as shown in FIG. 4B is typically 5-25% of the return air stream RA 704 , is now directed through the conditioner 702 which is similar in construction to the 3-way heat and mass exchange conditioner described in FIG. 2 .
- the conditioner 702 can be significantly smaller than the conditioner 503 of FIG. 5B because the air stream 701 is much smaller than in the 100% outside air stream 501 of FIG. 5B .
- the conditioner 702 produces a warmer, humidified air stream RA 3 703 which is mixed with the return air RA 704 to make mixed air MA 3 706 .
- Excess return air RA 705 is directed out of the system or towards the regenerator 712 .
- the mixed air MA 3 706 is pulled by fan 708 through condenser coil 707 which provides sensible only heating.
- the resulting air stream SA 2 709 is ducted to the space to be heated and humidified.
- the regenerator 712 receives either outside air OA 710 or the excess return air RA 705 or a mixture 711 thereof.
- the regenerator air stream 711 can be pulled through the regenerator 712 which again is similar in construction to the 3-way heat and mass exchanger described in FIG. 2 by a fan 737 and the resulting exhaust air stream EA 2 713 is generally much colder and contains less water vapor than the mixed air stream 711 that is entering. Heat is removed by circulating a heat transfer fluid through line 721 using pump 722 .
- the compressor 718 compresses a refrigerant similar to the compressors in FIG. 4B and FIG. 5B .
- the hot refrigerant gas is conducted through line 731 to a condenser heat exchanger 728 , which is the same heat exchanger 628 in FIG. 6 , but used as a condenser instead of an evaporator.
- a smaller amount of heat is conducted through this liquid-to-refrigerant heat exchanger 728 into the heat transfer fluid in circuit 729 by using pump 730 .
- the still hot refrigerant is now conducted through line 727 to a condenser coil 707 , which receives the mixed return air MA 3 706 .
- the resulting hot supply air SA 2 709 is directed through a duct to the space to be heated and humidified.
- the refrigerant which is now a cooler liquid after exiting the condenser coil 707 is conducted through line 726 to an expansion valve 725 , where it is expanded and becomes cold.
- the cold liquid refrigerant is conducted through line 724 to the evaporator coil 716 where it absorbs heat from the outside air stream OA 714 resulting in a cold exhaust air stream EA 717 which is emitted to the environment by using fan 715 .
- the still relatively cold refrigerant which has partially evaporated in the coil 716 is now conducted through line 723 to evaporator heat exchanger 720 where additional heat is removed from the air stream 711 going through the regenerator 712 by transfer fluid circulating in line 721 by using pump 722 . Finally the gaseous refrigerant exiting the heat exchanger 720 is conducted through line 719 back to the compressor 718 .
- a liquid refrigerant is circulated between the conditioner 702 and the regenerator 712 through lines 735 , the heat exchanger 733 and is circulated back to the conditioner by pump 732 and through line 734 .
- the conditioner 702 provides more moisture to the space than is collected in the regenerator 712 . In that case a provision for adding water 736 is required to maintain the desiccant at the proper concentration.
- a provision for adding water 736 can be provided in any location that gives convenient access to the desiccant, however the water added, should be relatively pure since a lot of water will evaporate, which is why reverse osmosis or de-ionized or distilled water would be preferable to straight tap water. This provision for adding water 736 will be discussed in more detail in FIG. 12 .
- the advantages of integrating a system in the configuration of FIG. 6 and FIG. 7 are several.
- the combination of 3-way liquid desiccant heat exchanger modules and a shared compressor system allows one to combine the advantages of dehumidification without condensation that are possible in the 3-way heat and mass exchanger with the inexpensive construction of a conventional RTU, whereby the integrated solution becomes very cost competitive.
- the coil 607 can be thinner, since no moisture condensation is needed, and the condensate pan and drain from FIG. 4A can be eliminated.
- the overall cooling capacity of the compressor can be reduced and the condenser coil can be smaller as well.
- the heating mode of the system adds humidity to the air stream unlike any other heat pump in the market today.
- the refrigerant, desiccant and heat transfer fluid circuits are actually simpler than those in the systems of FIGS. 4A, 4B, 5A and 5B , and the supply air stream 609 and 709 encounter fewer components than the conventional systems of FIGS. 4A and 4B , which means less pressure drop in the air stream leading to additional energy savings.
- FIG. 8 illustrates a psychrometric chart of the processes of FIG. 4A and FIG. 6 .
- the horizontal axis denotes temperature in degrees Fahrenheit and the vertical axis denotes humidity in grains of water per pound of dry air.
- outside air OA is provided at 95 F and 60% relative humidity (or 125 gr/lb).
- a 1,000 CFM supply air requirement with a 25% outside air contribution (250 CFM) to the space at 65 F and 70% RH (65 gr/lb).
- the conventional system of FIG. 4A takes in 1,000 CFM of return air RA at 80 F and 50% RH (78 gr/lb).
- 250 CFM of this return air RA is discarded as EA 2 (the stream EA 2 402 in FIG. 4A ).
- 750 CFM of the return air RA is mixed with 250 CFM of outside air (the stream OA 403 in FIG. 4A ) resulting in a mixed air condition MA (the stream MA 404 in FIG. 4A ).
- the mixed air MA is directed through the evaporator coil resulting in a cooling and dehumidification process resulting in air CC leaving the coil at 55 F and 100% RH (65 gr/lb).
- RH 65 gr/lb
- the system of FIG. 6 under the same outside air conditions will create a supply air stream SA leaving the conditioner ( 602 in FIG. 6 ) at 65 F and 43% RH (40 gr/lb).
- This relatively dry air is now mixed with the 750 CFM of return air RA ( 604 in FIG. 6 ) resulting in mixed air condition MA 2 (MA 2 606 in FIG. 6 ).
- the mixed air MA 2 is now directed through the evaporator coil ( 607 in FIG. 6 ) which sensible cools the air to supply air condition CC 2 (CC 2 , 609 in FIG. 6 ).
- the cooling power of the conventional system is 48.7 kBTU/hr
- the cooling power of the system of FIG. 6 is 35.6 kBTU/hr (23.2 kBTU/hr for the outside air OA and 12.4 kBTU/hr for the mixed air MA 2 ) thus requiring about a 27% smaller compressor.
- FIG. 8 Also shown in FIG. 8 is the change in the outside air OA used to reject heat.
- the conventional system of FIG. 4A use about 2,000 CFM through the condenser 414 to reject heat to the outside air OA (OA 411 in FIG. 4A ) resulting in exhaust air EA at 119 F and 25% RH (125 gr/lb) (EA 415 in FIG. 4A ).
- the system of FIG. 6 rejects two air streams, the regenerator 612 rejects air EA 2 at 107 F and 49% RH (178 gr/lb) (EA 2 613 in FIG. 6 ) which is hot and moist, as well as air stream EA 3 at 107 F and 35% RH (125 gr/lb) (EA 3 617 in FIG. 6 ).
- FIG. 9 illustrates a psychrometric chart of the processes of FIG. 4B and FIG. 7 .
- the horizontal axis denotes temperature in degrees Fahrenheit and the vertical axis denotes humidity in grains of water per pound of dry air.
- outside air OA is provided at 30 F and 60% relative humidity (or 14 gr/lb).
- a 1,000 CFM supply air requirement with a 25% outside air contribution (250 CFM) to the space at 120 F and 12% RH (58 gr/lb).
- the conventional system of FIG. 4B takes in 1,000 CFM of return air RA at 80 F and 50% RH (78 gr/lb).
- 250 CFM of this return air RA is discarded as EA 2 (the stream EA 2 402 in FIG. 4B ).
- 750 CFM of the return air RA is mixed with 250 CFM of outside air (the stream OA 403 in FIG. 4B ) resulting in a mixed air condition MA (the stream MA 404 in FIG. 4B ).
- the mixed air MA is directed through the condenser coil ( 405 in FIG. 4B ) resulting in a heating process resulting in air SA leaving the coil at 128 F and 8% RH (46 gr/lb).
- a humidification system 427 in FIG.
- the heating power of the conventional system is 78.3 kBTU/hr
- the heating power of the system of FIG. 7 is 79.3 kBTU/hr (20.4 kBTU/hr for the outside air OA and 58.9 kBTU/hr for the mixed air MA 2 ) essentially the same as the system of FIG. 4B .
- FIG. 9 Also shown in FIG. 9 is the change in the outside air OA used to absorb heat.
- the conventional system of FIG. 4B use about 2,000 CFM through the evaporator 414 to absorb heat from the outside air OA (OA 411 in FIG. 4B ) resulting in exhaust air EA at 20 F and 100% RH (9 gr/lb) (EA 415 in FIG. 4B ).
- the system of FIG. 6 absorbs heat from two air streams
- the regenerator 612 absorbs heat from air stream between MA 2 (which comprises 250 CFM of RA air at 65 F and 60% RH or 55 gr/lb and 150 CFM of OA air at 30 F and 60% RH or 14 gr/lb for a mixed air condition MA 2 ( 711 in FIG.
- the conditioner 702 is absorbing moisture from the mixed air stream MA 2 which is subsequently released in the air stream MA 3 , eliminating the need for makeup water.
- the evaporator coil 405 is condensing moisture as can be seen from the process between OA and CC in the figure. In practice this results in ice formation on the coil and the coil will thus have to be heated the remove ice buildup, which is usually done by switching the refrigerant flow in the direction of FIG. 6 .
- the coil 707 does not reach saturation and will thus not have to be heated. As a result the actual cooling in coil 405 in the system of FIG.
- FIG. 10 illustrates an alternate embodiment of the system in FIG. 6 , wherein the 3-way heat and mass exchangers 602 and 612 of FIG. 6 have been replaced by 2-way heat and mass exchangers.
- a desiccant is exposed directly to an air stream, sometimes with a membrane therebetween and sometimes without.
- two-way heat and mass exchangers exhibit an adiabatic heat and mass transfer process since there often is no place for the latent heat of condensation to be absorbed, safe for the desiccant itself. This usually increases the required desiccant flow rate because the desiccant now has to function as a heat transfer fluid as well.
- Outside air 1001 is directed through the conditioner 1002 which produces a colder, dehumidified air stream SA 1003 which is mixed with the return air RA 1004 to make mixed air MA 2 1006 .
- Excess return air 1005 is directed out of the system or towards the regenerator 1012 .
- the mixed air MA 2 is pulled by fan 1008 through evaporator coil 1007 which primarily provides sensible only cooling.
- the resulting air stream CC 2 1009 is ducted to the space to be cooled.
- the regenerator 1012 receives either outside air OA 1010 or the excess return air 1005 or a mixture 1011 thereof.
- the regenerator air stream 1011 can be pulled through the regenerator 1012 which again is similar in construction to the 2-way heat and mass exchanger as used as a conditioner 1002 by a fan (not shown) and the resulting exhaust air stream EA 2 1013 is generally much warmer and contains more water vapor than the mixed air stream 1011 that is entering.
- the compressor 1018 compresses a refrigerant similar to the compressors in FIG. 4A , FIG. 5A and FIG. 6 .
- the hot refrigerant gas is conducted through line 1019 to a condenser heat exchanger 1020 .
- a smaller amount of heat is conducted through this liquid-to-refrigerant heat exchanger 1020 into the desiccant in line 1031 . Since desiccant is often highly corrosive, the heat exchanger 1020 is made from Titanium or other suitable material.
- the still hot refrigerant is now conducted through line 1021 to a condenser coil 1016 , which receives outside air OA 1014 from fan 1015 .
- the resulting hot exhaust air EA 3 1017 is ejected into the environment.
- the refrigerant which is now a cooler liquid after exiting the condenser coil 1016 is conducted through line 1022 to an expansion valve 1023 , where it is expanded and becomes cold.
- the cold liquid refrigerant is conducted through line 1024 to the evaporator coil 1007 where it absorbs heat from the mixed air stream MA 2 1006 .
- the still relatively cold refrigerant which has partially evaporated in the coil 1007 is now conducted through line 1025 to evaporator heat exchanger 1026 where additional heat is removed from the liquid desiccant that is circulated to the conditioner 1002 .
- the heat exchanger 1026 will have to be constructed from a corrosion resistant material such as Titanium.
- the gaseous refrigerant exiting the heat exchanger 1026 is conducted through line 1027 back to the compressor 1018 .
- a liquid desiccant is circulated between the conditioner 1002 and the regenerator 1012 through lines 1030 , the heat exchanger 1029 and is circulated back to the conditioner by pump 1028 and through line 1031 .
- FIG. 11 illustrates an alternate embodiment of the system in FIG. 10 , wherein the 2-way heat and mass exchanger 1002 and the liquid to liquid heat exchangers 1026 of FIG. 10 have been integrated into single 3-way heat and mass exchangers where the air, the desiccant and the refrigerant exchange heat and mass simultaneously.
- this is similar to using a refrigerant instead of a heat transfer fluid in FIG. 6 .
- the same integration can be done on the regenerator 1012 and the heat exchanger 1020 . These integrations essentially eliminate a heat exchanger on each side making the system more efficient.
- Outside air 1101 is directed through the conditioner 1102 which produces a colder, dehumidified air stream SA 1103 which is mixed with the return air RA 1104 to make mixed air MA 2 1106 .
- Excess return air 1105 is directed out of the system or towards the regenerator 10112 .
- the mixed air MA 2 is pulled by fan 10108 through evaporator coil 1107 which primarily provides sensible only cooling.
- the resulting air stream CC 2 1109 is ducted to the space to be cooled.
- the regenerator 11012 receives either outside air OA 1110 or the excess return air 1105 or a mixture 1111 thereof.
- the regenerator air stream 1111 can be pulled through the regenerator 1112 which again is similar in construction to the 2-way heat and mass exchanger as used as a conditioner 1102 by a fan (not shown) and the resulting exhaust air stream EA 2 1113 is generally much warmer and contains more water vapor than the mixed air stream 1111 that is entering.
- the compressor 1118 compresses a refrigerant similar to the compressors in FIG. 4A , FIG. 5A , FIG. 6 and FIG. 10 .
- the hot refrigerant gas is conducted through line 1119 to a 3-way condenser heat and mass exchanger 1112 .
- a smaller amount of heat is conducted through this regenerator 1120 into the refrigerant in line 1119 .
- the regenerator 1112 needs to be constructed as for example is shown in FIG. 80 of application Ser. No. 13/915,262.
- the still hot refrigerant is now conducted through line 1120 to a condenser coil 1116 , which receives outside air OA 1114 from fan 1115 .
- the resulting hot exhaust air EA 3 1117 is ejected into the environment.
- the refrigerant which is now a cooler liquid after exiting the condenser coil 1116 is conducted through line 1121 to an expansion valve 1122 , where it is expanded and becomes cold.
- the cold liquid refrigerant is conducted through line 1123 to the evaporator coil 1107 where it absorbs heat from the mixed air stream MA 2 1106 .
- the still relatively cold refrigerant which has partially evaporated in the coil 1107 is now conducted through line 1124 to the evaporator heat exchanger/conditioner 1102 where additional heat is removed from the liquid desiccant.
- the gaseous refrigerant exiting the conditioner 1102 is conducted through line 1125 back to the compressor 1118 .
- liquid desiccant is circulated between the conditioner 1102 and the regenerator 1112 through lines 1129 , the heat exchanger 1128 and is circulated back to the conditioner by pump 1127 and through line 1126 .
- the systems from FIG. 10 and FIG. 11 are also reversible for winter heating mode similar to the system in FIG. 7 .
- additional water should be added to maintain proper desiccant concentration because if too much water is evaporated in dry conditions, the desiccant is at risk of crystalizing.
- one option is to simply add reverse osmosis or de-ionized water to keep the desiccant dilute, but the processes to generate this water are also very energy intensive.
- FIG. 12 illustrates an embodiment of a much simpler water injection system that generates pure water directly into the liquid desiccant by taking advantage of the desiccants' ability to attract water.
- the structure in FIG. 12 (which was labeled 736 in FIG. 7 ) comprises a series of parallel channels, which can be flat plates or rolled up channels. Water enters the structure at 1201 and is distributed to several channels through distribution header 1202 .
- This water can be tap water, sea water or even filtered waste water or any water containing fluid that has primarily water as a constituent and if any other materials are present, those materials are not transportable through the selective membrane 1210 as will be explained shortly.
- the water is distributed to each of the even channels labeled “A” in the figure.
- concentrated desiccant is introduced at 1205 , which is distributed through header 1206 to each of the channels labeled “B” in the figure.
- the concentrated desiccant 1209 flows along the B channels.
- the wall between the “A” and the “B: channels comprises a selective membrane 1210 which is selective to water so that water molecules can come through the membrane but ions or other materials cannot. This thus prevents for example Lithium and Chloride ions from crossing the membrane into the water “A” channel and vice versa prevents Sodium and Chloride ions from seawater crossing into the desiccant in the “B” channel.
- the concentration of Lithium Chloride in the desiccant is typically 25-35%, this provides a strong driving force for the diffusion of water from the “A” to the “B” channel since the concentration of for example Sodium Chloride in sea water is typically less than 3%.
- Selective membranes of this type are commonly found in membrane distillation or reverse osmosis processes and are well known in the art.
- the structure of FIG. 12 can be executed in many form factors such as a flat plate structure or a concentric stack of channels or any other convenient form factor. It is also possible to construct the plate structure of FIG. 3 by replacing the wall 255 with a selective membrane as is shown in FIG. 12 . However, such a structure would only make sense if one wants to continuously add water to the desiccant.
- the membrane may be a microporous hydrophobic structure comprising a polypropylene, a polyethylene, or an ECTFE (Ethylene ChloroTriFluoroEthylene) membrane.
- FIG. 13 illustrates how the water injection system from FIG. 12 can be integrated to the desiccant pumping subsystem of FIG. 7 .
- the desiccant pump 732 pumps desiccant through the water injection module 1301 and through the heat exchanger 733 as was shown in FIG. 7 .
- the desiccant returns from the conditioner ( 702 in FIG. 7 ) through line 735 and through the heat exchanger 733 back to the regenerator ( 712 in FIG. 7 ).
- a water reservoir 1304 is filled with water 1305 or a water containing liquid.
- a pump 1302 pumps the water to the water injection system 1301 , where it enters through port 1201 (as shown in FIG. 12 ).
- the water flows through the “A” channels in FIG.
- the water injection system 1301 is sized in such a way that the diffusion of water through the selective membranes 1210 is matched to the amount of water that would have to be added to the desiccant.
- the water injection system can comprise several independent sections that are individually switchable so that water could be added to the desiccant in several stages.
- the water 1304 flowing through the injection module 1301 is partially transmitted through the selective membranes 1210 . Any excess water exits through the drain line 1204 and falls back in the tank 1303 . As the water is pumped from the tank 1304 again by pump 1302 , less and less water will return to the tank.
- a float switch 1307 such as is commonly used on cooling towers can be used to maintain a proper water level in the tank. When the float switch detects a low water level, it opens valve 1308 which lets additional water in from supply water line 1306 . However, since the selective membrane only pass pure water through, any residuals such as Calcium Carbonates, or other non-passible materials will collect in the tank 1303 .
- a blow-down valve 1305 can be opened to get rid of these unwanted deposits as is commonly done on cooling towers.
- water injection system of FIG. 12 can be used in other liquid desiccant system architectures for example in those described in Ser. No. 13/115,686, US 2012/0125031 A1, Ser. No. 13/115,776, and US 2012/0125021 A1.
- FIG. 14 illustrates how the water injection system from FIG. 12 and FIG. 13 can be integrated to the desiccant to desiccant heat exchanger 733 from FIG. 13 .
- the water flows through the “A” channels 1402 in FIG. 14 and exits through a port after which is drains back to the tank as described in FIG. 13 .
- a cold desiccant is introduced in the “B” channels 1401 in FIG. 14 and a warm desiccant is introduced in the “C” channels in FIG. 14 .
- the walls 1404 between the “A” and “B” and “A” and “C” channels respectively are again constructed with a selectively permeable membrane.
- the wall 1405 between the “B” and the “C” channel is a non-permeable membrane such as a plastic sheet which can conduct heat but not water molecules.
- the structure of FIG. 14 thus accomplishes two tasks simultaneously: it provides a heat exchange function between the hot and the cold desiccant and it transmit water from the water channel to the two desiccant channels in each channel triplet.
- FIG. 15 illustrates an embodiment wherein two of the membrane modules of FIG. 3 have been integrated into a DOAS but wherein the heat transfer fluid and the desiccant that were two separate fluids in FIGS. 1, 2 and 3 (the desiccant—labeled 114 and 115 in FIG. 1 —is typically a lithium chloride/water solution and the heat transfer fluid—labeled 110 in FIG. 1 is typically water or a water/glycol mixture) are combined in a single fluid (which would typically be lithium chloride and water, but any suitable liquid desiccant will do).
- the desiccant pump for example 632 in FIG. 6 ), can be eliminated.
- a 3-way membrane module in a 3-way membrane module, it is possible to create a counter-flow between the air stream and a heat transfer fluid stream, while a small desiccant stream (typically 5-10% of the mass flow of the heat transfer fluid stream) is mostly absorbing or desorbing the latent energy from or to the air stream.
- a small desiccant stream typically 5-10% of the mass flow of the heat transfer fluid stream
- the primary air and heat transfer fluid flows are arranged in a counter-flow arrangement, and the small desiccant stream that is absorbing or desorbing the latent energy may still be in a cross-flow arrangement, but because the mass flow rate of the small desiccant stream is small, the effect on efficiency is negligible.
- an air stream 1501 which can be outside air, or return air from a space or a mixture between the two, is directed over a membrane structure 1503 .
- the membrane structure 1503 is the same structure from FIG. 3 .
- the membrane structure (only a single plate structure is shown although generally multiple plate structures would be used in parallel) is now supplied by pump 1509 with a large desiccant stream 1511 through tank 1513 .
- This large desiccant stream runs in the heat transfer channel 1505 counter to the air stream 1501 .
- a smaller desiccant stream 1515 is also simultaneously pumped by the pump 1509 to the top of the membrane plate structures 1503 where it flows by gravity behind the membranes 1532 in flow channel 1507 .
- the flow channel 1507 is generally vertical; however the heat transfer channel 1505 can be either vertical or horizontal, depending on whether the air stream 1501 is vertical or horizontal.
- the desiccant exiting the heat transfer channel 1505 is now directed to a condenser heat exchanger 1517 , which, because of the corrosive nature of most liquid desiccants such as lithium chloride, is usually made from Titanium or some other non-corrosive material.
- an overflow device 1528 can be employed that results in excess desiccant being drained through tube 1529 back to the tank 1513 .
- Desiccant that has desorbed latent energy into the air stream 1501 is now directed through drain line 1519 through heat exchanger 1521 to pump 1508 .
- the heat exchanger 1517 is part of a heat pump comprising compressor 1523 , hot gas line 1524 , liquid line 1525 , expansion valve 1522 , cold liquid line 1526 , evaporator heat exchanger 1518 and gas line 1527 which directs a refrigerant back to the compressor 1523 .
- the heat pump assembly can be reversible as described earlier for allowing switching between a summer operation mode and a winter operation mode.
- a second air stream 1502 which can also be outside air, or return air from a space or a mixture between the two, is directed over a second membrane structure 1504 .
- the membrane structure 1504 is the same structure from FIG. 3 .
- the membrane structure (only a single plate structure is shown although generally multiple plate structures would be used in parallel) is now supplied by pump 1510 with a large desiccant stream 1512 through tank 1514 .
- This large desiccant stream runs in heat transfer channel 1506 counter to the air stream 1502 .
- a smaller desiccant stream 1516 is also pumped by the pump 1510 to the top of the membrane plate structures 1504 where it flows by gravity behind the membranes 1533 in flow channel 1508 .
- the flow channel 1508 is generally vertical; however the heat transfer channel 1506 can be either vertical or horizontal, depending on whether the air stream 1502 is vertical or horizontal.
- the desiccant exiting the heat transfer channel 1506 is now directed to a evaporator heat exchanger 1518 , which, because of the corrosive nature of most liquid desiccants such as lithium chloride, is usually made from Titanium or some other non-corrosive material.
- an overflow device 1531 can be employed that results in excess desiccant being drained through tube 1530 back to the tank 1514 .
- Desiccant that has absorbed latent energy from the air stream 1502 is now directed through drain line 1520 through heat exchanger 1521 to pump 1509 .
- the structure described above has several advantages in that the pressure on the membranes 1532 and 1533 is very low and can even be negative essentially syphoning the desiccant through the channels 1507 and 1508 . This makes the membrane structure significantly more reliable since the pressure on the membranes will be minimized or even be negative resulting in performance similar to that described in application 13 / 915 , 199 . Furthermore, since the main desiccant streams 1505 and 1506 are counter to the air flow 1501 and 1502 respectively, the effectiveness of the membrane plate structures 1503 and 1504 is much higher than a cross-flow arrangement would be able to achieve.
- FIG. 16 illustrates how the system from FIG. 15 can be integrated to the system in FIG. 6 (or FIG. 7 for winter mode).
- the major components from FIG. 15 are labeled in the figure as are the components from FIG. 6 .
- the system 1600 A is added as an outside air treatment system where the outside air OA ( 1502 ) is directed over the conditioner membrane plates 1504 .
- the main desiccant stream 1506 is pumped by pump 1510 in counter-flow to the air stream 1502 and the small desiccant stream 1508 is carrying off the latent energy from the air stream 1502 .
- the small desiccant stream is directed through heat exchanger 1521 to pump 1509 where it is pumped through regenerator membrane plate structure 1503 .
- the main desiccant stream 1505 is again counter to the air stream 1501 , which comprises an outside air stream 1601 mixed with a return air stream 605 .
- a small desiccant stream 1507 is now used to desorb moisture from the desiccant.
- the system of FIG. 16 is reversible by reversing the direction of the heat pump system comprising compressor 1523 , heat exchangers 1517 and 1518 , and coils 616 and 607 as well as expansion valve 625 .
- modules 1503 and 1504 could be employed in lieu of modules 1503 and 1504 .
- Such a two-way liquid desiccant module could have a membrane or could have no membrane and are well known in the art.
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Abstract
Description
- This application is a divisional of U.S. patent application Ser. No. 14/664219, filed on Mar. 20, 2015 entitled ROOFTOP LIQUID DESICCANT SYSTEMS AND METHODS, which claims priority from U.S. Provisional Patent Application No. 61/968,333 filed on Mar. 20, 2014 entitled METHODS AND SYSTEMS FOR LIQUID DESICCANT ROOFTOP UNIT, and from U.S. Provisional Patent Application No. 61/978,539 filed on Apr. 11, 2014 entitled METHODS AND SYSTEMS FOR LIQUID DESICCANT ROOFTOP UNIT, all of which are hereby incorporated by reference.
- The present application relates generally to the use of liquid desiccant membrane modules to dehumidify and cool an outside air stream entering a space. More specifically, the application relates to the use of micro-porous membranes to keep separate a liquid desiccant that is treating an outside air stream from direct contact with that air stream while in parallel using a conventional vapor compression system to treat a return air stream. The membrane allows for the use of turbulent air streams wherein the fluid streams (air, optional cooling fluids, and liquid desiccants) are made to flow so that high heat and moisture transfer rates between the fluids can occur. The application further relates to combining cost reduced conventional vapor compression technology with a more costly membrane liquid desiccant and thereby creating a new system at approximately equal cost but with much lower energy consumption.
- Liquid desiccants have been used in parallel with conventional vapor compression HVAC (heating, ventilation, and air conditioning) equipment to help reduce humidity in spaces, particularly in spaces that either require large amounts of outdoor air or that have large humidity loads inside the building space itself. Humid climates, such as for example Miami, Fla. require a large amount of energy to properly treat (dehumidify and cool) the fresh air that is required for a space's occupant comfort. Conventional vapor compression systems have only a limited ability to dehumidify and tend to overcool the air, oftentimes requiring energy intensive reheat systems, which significantly increase the overall energy costs because reheat adds an additional heat-load to the cooling coil. Liquid desiccant systems have been used for many years and are generally quite efficient at removing moisture from the air stream. However, liquid desiccant systems generally use concentrated salt solutions such as solutions of LiCl, LiBr or CaCl2 and water. Such brines are strongly corrosive, even in small quantities so numerous attempt have been made over the years to prevent desiccant carry-over to the air stream that is to be treated. One approach—generally categorized as closed desiccant systems—is commonly used in equipment dubbed absorption chillers, places the brine in a vacuum vessel which then contains the desiccant and since the air is not directly exposed to the desiccant; such systems do not have any risk of carry-over of desiccant particles to the supply air stream. Absorption chillers however tend to be expensive both in terms of first cost and maintenance costs. Open desiccant systems allow a direct contact between the air stream and the desiccant, generally by flowing the desiccant over a packed bed similar to those used in cooling towers and evaporators. Such packed bed systems suffer from other disadvantages besides still having a carry-over risk: the high resistance of the packed bed to the air stream results in larger fan power and pressure drops across the packed bed, thus requiring more energy. Furthermore, the dehumidification process is adiabatic, since the heat of condensation that is released during the absorption of water vapor into the desiccant has no place to go. As a result both the desiccant and the air stream are heated by the release of the heat of condensation. This results in a warm, dry air stream where a cool dry air stream was desired, necessitating the need for a post-dehumidification cooling coil. Warmer desiccant is also exponentially less effective at absorbing water vapor, which forces the system to supply much larger quantities of desiccant to the packed bed which in turn requires larger desiccant pump power, since the desiccant is doing double duty as a desiccant as well as a heat transfer fluid. But the larger desiccant flooding rate also results in an increased risk of desiccant carryover. Generally air flow rates need to be kept well below the turbulent region (at Reynolds numbers of less than ˜2,400) to prevent carryover. Applying a micro-porous membrane to the surface of these open liquid desiccant systems has several advantages. First it prevents any desiccant from escaping (carrying-over) to the air stream and becoming a source of corrosion in the building. And second, the membrane allows for the use of turbulent air flows enhancing heat and moisture transfer, which in turn results in a smaller system since it can be build more compactly. The micro-porous membrane retains the desiccant typically by being hydrophobic to the desiccant solution and breakthrough of desiccant can occur but only at pressures significantly higher than the operating pressure. The water vapor in an air stream that is flowing over the membrane diffuses through the membrane into the underlying desiccant resulting in a drier air stream. If the desiccant is at the same time cooler than the air stream, a cooling function will occur as well, resulting in a simultaneous cooling and dehumidification effect.
- U.S. Patent Application Publication No. 2012/0132513, and PCT Application No. PCT/US11/037936 by Vandermeulen et al. disclose several embodiments for plate structures for membrane dehumidification of air streams. U.S. Patent Application Publication Nos. 2014-0150662, 2014-0150657, 2014-0150656, and 2014-0150657, PCT Application No. PCT/US13/045161, and U.S. Patent Application Nos. 61/658,205, 61/729,139, 61/731,227, 61/736,213, 61/758,035, 61/789,357, 61/906,219, and 61/951,887 by Vandermeulen et. al. disclose several manufacturing methods and details for manufacturing membrane desiccant plates. Each of these patent applications is hereby incorporated by reference herein in its entirety.
- Conventional Roof Top Units (RTUs), which are a common means of providing cooling, heating, and ventilation to a space are inexpensive systems that are manufactured in high volumes. However, these RTUs are only able to handle small quantities of outside air, since they are generally not very good at dehumidifying the air stream and their efficiency drops significantly at higher outside air percentages. Generally RTUs provide between 5 and 20% outside air, and specialty units such as Make Up Air (MAUs) or Dedicated Outside Air Systems (DOAS) exist that specialize in providing 100% outside air and they can do so much more efficiently. However, the cost of a MAU or DOAS is often well over $2,000 per ton of cooling capacity compared to less than $1,000 per ton of a RTU. In many applications RTUs are the only equipment utilized simply because of their lower initial cost since the owner of the building and the entity paying for the electricity are often different. But the use of RTUs often results in poor energy performance, high humidity and buildings that feel much too cold. Upgrading a building with LED lighting for example can possibly lead to humidity problems and the cold feeling is increased because the internal heat load from incandescent lighting which helps heat a building, largely disappears when LEDs are installed.
- Furthermore, RTUs generally do not humidify in winter operation mode. In winter the large amount of heating that is applied to the air stream results in very dry building conditions which can also be uncomfortable. In some buildings humidifiers are installed in ductwork or integrated to the RTU to provide humidity to the space. However, the evaporation of water in the air significantly cools that air requiring additional heat to be applied and thus increases energy costs.
- There thus remains a need for a system that provides cost efficient, manufacturable and thermally efficient methods and systems to capture moisture from an air stream, while simultaneously cooling such an air stream in a summer operating mode, while also heating and humidifying an air stream in a winter operating mode and while also reducing the risk of contaminating such an air stream with desiccant particles.
- Provided herein are methods and systems used for the efficient dehumidification of an air stream using liquid desiccants. In accordance with one or more embodiments the liquid desiccant runs down the face of a support plate as a falling film in a conditioner for treating an air stream. In accordance with one or more embodiments, the liquid desiccant is covered by a microporous membrane so that liquid desiccant is unable to enter the air stream, but water vapor in the air stream is able to be absorbed into the liquid desiccant. In accordance with one or more embodiments the liquid desiccant is directed over a plate structure containing a heat transfer fluid. In accordance with one or more embodiments the heat transfer fluid is thermally coupled to a liquid to refrigerant heat exchanger and is pumped by a liquid pump. In accordance with one or more embodiments the refrigerant in the heat exchanger is cold and picks up heat through the heat exchanger. In accordance with one or more embodiments the warmer refrigerant leaving the heat exchanger is directed to a refrigerant compressor. In accordance with one or more embodiments the compressor compresses the refrigerant and the exiting hot refrigerant is directed to another heat transfer fluid in a refrigerant heat exchanger. In accordance with one or more embodiments the heat exchanger heats the hot heat transfer fluid. In accordance with one or more embodiments the hot heat transfer fluid is directed to a liquid desiccant regenerator through a liquid pump. In accordance with one or more embodiments a liquid desiccant in a regenerator is directed over a plate structure containing the hot heat transfer fluid. In accordance with one or more embodiments the liquid desiccant in the regenerator runs down the face of a support plate as a falling film. In accordance with one or more embodiments, the liquid desiccant in the regenerator is also covered by a microporous membrane so that liquid desiccant is unable to enter the air stream, but water vapor in the air stream is able to be desorbed from the liquid desiccant. In accordance with one or more embodiments the liquid desiccant is transported from the conditioner to the regenerator and from the regenerator back to the conditioner. In one or more embodiments, the liquid desiccant is pumped by a pump. In one or more embodiments, the liquid desiccant is pumped through a heat exchanger between the conditioner and the regenerator. In accordance with one or more embodiments the air exiting the conditioner is directed to a second air stream. In accordance with one or more embodiments the second air stream is a return air stream from a space. In accordance with one or more embodiments a portion of said return air stream is exhausted from the system and the remaining air stream is mixed with the air stream from the conditioner. In one or more embodiments, the exhausted portion is between 5 and 25% of the return air stream. In one or more embodiments, the exhausted portion is directed to the regenerator. In one or more embodiments, the exhausted portion is mixed with an outside air stream before being directed to the regenerator. In accordance with one or more embodiments the mixed air stream between the return air and the conditioner air is directed through a cooling or evaporator coil. In one or more embodiments, the cooling coil receives cold refrigerant from a refrigeration circuit. In one or more embodiments, the cooled air is directed back to the space to be cooled. In accordance with one or more embodiments the cooling coil receives cold refrigerant from an expansion valve or similar device. In one or more embodiments, the expansion valve receives liquid refrigerant from a condenser coil. In one or more embodiments, the condenser coil receives hot refrigerant gas from a compressor system. In one or more embodiments, the condenser coil is cooled by an outside air stream. In one or more embodiments, the hot refrigerant gas from the compressor is first directed to the refrigerant to liquid heat exchanger from the regenerator. In one or more embodiments, multiple compressors are used. In one or more embodiments, separate compressors serve the liquid to refrigerant heat exchangers from the compressors serving the evaporator and condenser coils. In one or more embodiments, the compressors are variable speed compressors. In one or more embodiments, the air streams are moved by a fan or blower. In one or more embodiments, such fans are variable speed fans.
- Provided herein are methods and systems used for the efficient humidification of an air stream using liquid desiccants. In accordance with one or more embodiments a liquid desiccant runs down the face of a support plate as a falling film in a conditioner for treating an air stream. In accordance with one or more embodiments, the liquid desiccant is covered by a microporous membrane so that liquid desiccant is unable to enter the air stream, but water vapor in the air stream is able to be absorbed into the liquid desiccant. In accordance with one or more embodiments the liquid desiccant is directed over a plate structure containing a heat transfer fluid. In accordance with one or more embodiments the heat transfer fluid is thermally coupled to a liquid to refrigerant heat exchanger and is pumped by a liquid pump. In accordance with one or more embodiments the refrigerant in the heat exchanger is hot and rejects heat to the conditioner and hence to the air stream passing through said conditioner. In accordance with one or more embodiments the air exiting the conditioner is directed to a second air stream. In accordance with one or more embodiments the second air stream is a return air stream from a space. In accordance with one or more embodiments a portion of said return air stream is exhausted from the system and the remaining air stream is mixed with the air stream from the conditioner. In one or more embodiments, the exhausted portion is between 5 and 25% of the return air stream. In one or more embodiments, the exhausted portion is directed to the regenerator. In one or more embodiments, the exhausted portion is mixed with an outside air stream before being directed to the regenerator. In accordance with one or more embodiments the mixed air stream between the return air and the conditioner air is directed through a condenser coil. In one or more embodiments, the condenser coil receives hot refrigerant from a refrigeration circuit. In one or more embodiments, the condenser coil warms the mixed air stream coming from the conditioner and the remaining return air from the space. In one or more embodiments, the warmer air is directed back to the space to be cooled. In accordance with one or more embodiments the condenser coil receives hot refrigerant from the liquid to refrigerant heat exchanger. In one or more embodiments, the condenser coil receives hot refrigerant gas from a compressor system directly. In one or more embodiments, the colder, liquid refrigerant leaving the condenser coil is directed to an expansion valve or similar device. In one or more embodiments, the refrigerant expands in the expansion valve and is directed to an evaporator coil. In one or more embodiments, the evaporator coil also receives an outside air stream from which it pulls heat to heat the cold refrigerant from the expansion valve. In one or more embodiments, the warmer refrigerant from the evaporator coil is directed to a liquid to refrigerant heat exchanger. In one or more embodiments, the liquid to refrigerant heat exchanger receives the refrigerant from the evaporator and absorbs additional heat from a heat transfer fluid loop. In one or more embodiments, the heat transfer fluid loop is thermally coupled to a regenerator. In one or more embodiments, the regenerator collects heat and moisture from an air stream. In accordance with one or more embodiments the liquid desiccant in the regenerator is directed over a plate structure containing the cold heat transfer fluid. In accordance with one or more embodiments the liquid desiccant in the regenerator runs down the face of a support plate as a falling film. In accordance with one or more embodiments, the liquid desiccant in the regenerator is also covered by a microporous membrane so that liquid desiccant is unable to enter the air stream, but water vapor in the air stream is able to be desorbed from the liquid desiccant. In one or more embodiments, the air stream is an air stream rejected from the return air stream. In one or more embodiments, the air stream is an outside air stream. In one or more embodiments, the air stream is a mixture of the rejected air stream and an outside air stream. In one or more embodiments, the refrigerant leaving the liquid to refrigerant heat exchanger is directed to a refrigerant compressor. In one or more embodiments, the compressor compresses the refrigerant which is then directed to a conditioner heat exchanger. In accordance with one or more embodiments the heat exchanger heats the hot heat transfer fluid. In accordance with one or more embodiments the hot heat transfer fluid is directed to the liquid desiccant conditioner through a liquid pump. In accordance with one or more embodiments the liquid desiccant is transported from the conditioner to the regenerator and from the regenerator back to the conditioner. In one or more embodiments, the liquid desiccant is pumped by a pump. In one or more embodiments, the liquid desiccant is pumped through a heat exchanger between the conditioner and the regenerator. In one or more embodiments, separate compressors serve the liquid to refrigerant heat exchangers from the compressors serving the evaporator and condenser coils. In one or more embodiments, the compressors are variable speed compressors. In one or more embodiments, the air streams are moved by a fan or blower. In one or more embodiments, such fans are variable speed fans. In one or more embodiments, multiple compressors are used. In accordance with one or more embodiments the cooler refrigerant leaving the heat exchanger is directed to a condenser coil. In accordance with one or more embodiments the condenser coil is receiving an air stream and the still hot refrigerant is used to heat such an air stream. In one or more embodiments, water is added to the desiccant during operation. In one or more embodiments, water is added during winter heating mode. In one or more embodiments, water is added to control the concentration of the desiccant. In one or more embodiments, water is added during dry hot weather.
- Provided herein are methods and systems used for the efficient dehumidification of an air stream using liquid desiccants. In accordance with one or more embodiments the liquid desiccant runs down the face of a support plate as a falling film in a conditioner for treating an air stream. In accordance with one or more embodiments, the liquid desiccant is covered by a microporous membrane so that liquid desiccant is unable to enter the air stream, but water vapor in the air stream is able to be absorbed into the liquid desiccant. In accordance with one or more embodiments the liquid desiccant is thermally coupled to a desiccant to refrigerant heat exchanger and is pumped by a liquid pump. In accordance with one or more embodiments the refrigerant in the heat exchanger is cold and picks up heat through the heat exchanger. In accordance with one or more embodiments the warmer refrigerant leaving the heat exchanger is directed to a refrigerant compressor. In accordance with one or more embodiments the compressor compresses the refrigerant and the exiting hot refrigerant is directed to another refrigerant to desiccant heat exchanger. In accordance with one or more embodiments the heat exchanger heats a hot desiccant. In accordance with one or more embodiments the hot desiccant is directed to a liquid desiccant regenerator through a liquid pump. In accordance with one or more embodiments a liquid desiccant in a regenerator is directed over a plate structure. In accordance with one or more embodiments the liquid desiccant in the regenerator runs down the face of a support plate as a falling film. In accordance with one or more embodiments, the liquid desiccant in the regenerator is also covered by a microporous membrane so that liquid desiccant is unable to enter the air stream, but water vapor in the air stream is able to be desorbed from the liquid desiccant. In accordance with one or more embodiments the liquid desiccant is transported from the conditioner to the regenerator and from the regenerator back to the conditioner. In one or more embodiments, the liquid desiccant is pumped by a pump. In one or more embodiments, the liquid desiccant is pumped through a heat exchanger between the conditioner and the regenerator. In accordance with one or more embodiments the air exiting the conditioner is directed to a second air stream. In accordance with one or more embodiments the second air stream is a return air stream from a space. In accordance with one or more embodiments a portion of said return air stream is exhausted from the system and the remaining air stream is mixed with the air stream from the conditioner. In one or more embodiments, the exhausted portion is between 5 and 25% of the return air stream. In one or more embodiments, the exhausted portion is directed to the regenerator. In one or more embodiments, the exhausted portion is mixed with an outside air stream before being directed to the regenerator. In accordance with one or more embodiments the mixed air stream between the return air and the conditioner air is directed through a cooling or evaporator coil. In one or more embodiments, the cooling coil receives cold refrigerant from a refrigeration circuit. In one or more embodiments, the cooled air is directed back to the space to be cooled. In accordance with one or more embodiments the cooling coil receives cold refrigerant from an expansion valve or similar device. In one or more embodiments, the expansion valve receives liquid refrigerant from a condenser coil. In one or more embodiments, the condenser coil receives hot refrigerant gas from a compressor system. In one or more embodiments, the condenser coil is cooled by an outside air stream. In one or more embodiments, the hot refrigerant gas from the compressor is first directed to the refrigerant to desiccant heat exchanger from the regenerator. In one or more embodiments, multiple compressors are used. In one or more embodiments, separate compressors serve the desiccant to refrigerant heat exchangers from the compressors serving the evaporator and condenser coils. In one or more embodiments, the compressors are variable speed compressors. In one or more embodiments, the air streams are moved by a fan or blower. In one or more embodiments, such fans are variable speed fans. In one or more embodiments, the flow direction of the refrigerant is reversed for a winter heating mode. In one or more embodiments, water is added to the desiccant during operation. In one or more embodiments, water is added during winter heating mode. In one or more embodiments, water is added to control the concentration of the desiccant. In one or more embodiments, water is added during dry hot weather.
- Provided herein are methods and systems used for the efficient dehumidification of an air stream using liquid desiccants. In accordance with one or more embodiments the liquid desiccant runs down the face of a support plate as a falling film in a conditioner for treating an air stream. In accordance with one or more embodiments, the liquid desiccant is covered by a microporous membrane so that liquid desiccant is unable to enter the air stream, but water vapor in the air stream is able to be absorbed into the liquid desiccant. In accordance with one or more embodiments the liquid desiccant is thermally coupled to a refrigerant heat exchanger embedded in the conditioner. In accordance with one or more embodiments the refrigerant in the conditioner is cold and picks up heat from the desiccant and hence from the air stream flowing through the conditioner. In accordance with one or more embodiments the warmer refrigerant leaving the conditioner is directed to a refrigerant compressor. In accordance with one or more embodiments the compressor compresses the refrigerant and the exiting hot refrigerant is directed to a regenerator. In accordance with one or more embodiments the hot refrigerant is embedded into a structure in the regenerator. In accordance with one or more embodiments a liquid desiccant in the regenerator is directed over a plate structure. In accordance with one or more embodiments the liquid desiccant in the regenerator runs down the face of a support plate as a falling film. In accordance with one or more embodiments, the liquid desiccant in the regenerator is also covered by a microporous membrane so that liquid desiccant is unable to enter the air stream, but water vapor in the air stream is able to be desorbed from the liquid desiccant. In accordance with one or more embodiments the liquid desiccant is transported from the conditioner to the regenerator and from the regenerator back to the conditioner. In one or more embodiments, the liquid desiccant is pumped by a pump. In one or more embodiments, the liquid desiccant is pumped through a heat exchanger between the conditioner and the regenerator. In accordance with one or more embodiments the air exiting the conditioner is directed to a second air stream. In accordance with one or more embodiments the second air stream is a return air stream from a space. In accordance with one or more embodiments a portion of said return air stream is exhausted from the system and the remaining air stream is mixed with the air stream from the conditioner. In one or more embodiments, the exhausted portion is between 5 and 25% of the return air stream. In one or more embodiments, the exhausted portion is directed to the regenerator. In one or more embodiments, the exhausted portion is mixed with an outside air stream before being directed to the regenerator. In accordance with one or more embodiments the mixed air stream between the return air and the conditioner air is directed through a cooling or evaporator coil. In one or more embodiments, the cooling coil receives cold refrigerant from a refrigeration circuit. In one or more embodiments, the cooled air is directed back to the space to be cooled. In accordance with one or more embodiments the cooling coil receives cold refrigerant from an expansion valve or similar device. In one or more embodiments, the expansion valve receives liquid refrigerant from a condenser coil. In one or more embodiments, the condenser coil receives hot refrigerant gas from a compressor system. In one or more embodiments, the condenser coil is cooled by an outside air stream. In one or more embodiments, the hot refrigerant gas from the compressor is first directed to the refrigerant to desiccant heat exchanger from the regenerator. In one or more embodiments, multiple compressors are used. In one or more embodiments, separate compressors serve the desiccant to refrigerant heat exchangers from the compressors serving the evaporator and condenser coils. In one or more embodiments, the compressors are variable speed compressors. In one or more embodiments, the air streams are moved by a fan or blower. In one or more embodiments, such fans are variable speed fans. In one or more embodiments, the flow direction of the refrigerant is reversed for a winter heating mode. In one or more embodiments, water is added to the desiccant during operation. In one or more embodiments, water is added during winter heating mode. In one or more embodiments, water is added to control the concentration of the desiccant. In one or more embodiments, water is added during dry hot weather.
- Provided herein are methods and systems used for the efficient humidification of a desiccant stream using water and selective membranes. In accordance with one or more embodiments a set of pairs of channels for liquid transport are provided wherein the one side of the channel pair receives a water stream and the other side of the channel pair receives a liquid desiccant. In one or more embodiments, the water is tap water, sea water, waste water and the like. In one or more embodiments, the liquid desiccant is any liquid desiccant that is able to absorb water. In one or more embodiments, the elements of the channel pair are separated by a membrane selectively permeable to water but not to any other constituents. In one or more embodiments, the membrane is a reverse osmosis membrane, or some other convenient selective membrane. In one or more embodiments, multiple pairs can be individually controlled to vary the amount of water that is added to the desiccant stream from the water stream. In one or more embodiments, other driving forces besides concentration potential differences are used to assist the permeation of water through the membrane. In one or more embodiments, such driving forces are heat or pressure.
- Provided herein are methods and systems used for the efficient humidification of a desiccant stream using water and selective membranes. In accordance with one or more embodiments, a water injector comprising a series of channel pairs is connected to a liquid desiccant circuit and a water circuit wherein one half of the channel pairs receives a liquid desiccant and the other half receives the water. In one or more embodiments, the channel pairs are separated by a selective membrane. In accordance with one or more embodiments the liquid desiccant circuit is connected between a regenerator and a conditioner. In one or more embodiments, the water circuit receives water from a water tank through a pumping system. In one or more embodiments, excess water that is not absorbed through the selective membrane is drained back to the water tank. In one or more embodiments, the water tank is kept full by a level sensor or float switch. In one or more embodiments, precipitates or concentrated water is drained from the water tank by a drain valve also known as a blow-down procedure.
- Provided herein are methods and systems used for the efficient humidification of a desiccant stream using water and selective membranes while at the same time providing a heat transfer function between two desiccant streams. In accordance with one or more embodiments, a water injector comprising a series of channel triplets is connected to two liquid desiccant circuits and a water circuit wherein a third of the channel triplets receives a hot liquid desiccant, a second third of the triplets receives a cold liquid desiccant and the remaining third of the triplets receives the water. In one or more embodiments, the channel triplets are separated by a selective membrane. In accordance with one or more embodiments the liquid desiccant channels are connected between a regenerator and a conditioner. In one or more embodiments, the water circuit receives water from a water tank through a pumping system. In one or more embodiments, excess water that is not absorbed through the selective membrane is drained back to the water tank. In one or more embodiments, the water tank is kept full by a level sensor or float switch. In one or more embodiments, precipitates or concentrated water is drained from the water tank by a drain valve also known as a blow-down procedure.
- Provided herein are methods and systems used for the efficient dehumidification or humidification of an air stream using liquid desiccants. In accordance with one or more embodiments a liquid desiccant stream is split into a larger and a smaller stream. In accordance with one or more embodiments, the larger stream is directed into a heat transfer channel that is constructed to provide fluid flow in a counter-flow direction to an air stream. In one or more embodiments, the larger stream is a horizontal fluid stream and the air stream is a horizontal stream in a direction counter to the fluid stream. In one or more embodiments, the larger stream is flowing vertically upward or vertically downward, and the air stream is flowing vertically downward or vertically upward in a counter-flow orientation. In one or more embodiments, the mass flow rates of the larger stream and the air flow stream are approximately equal within a factor of two. In one or more embodiments, the larger desiccant stream is directed to a heat exchanger coupled to a heating or cooling device. In one or more embodiments, the heat or cooling device is a heat pump, a geothermal source, a hot water source, and the like. In one or more embodiments, the heat pump is reversible. In one or more embodiments, the heat exchanger is made from a non-corrosive material. In one or more embodiments, the material is titanium or any suitable material non-corrosive to the desiccant. In one or more embodiments, the desiccant itself is non-corrosive. In one or more embodiments, the smaller desiccant stream is simultaneously directed to a channel that is flowing downward by gravity. In one or more embodiments, the smaller stream is bound by a membrane that has an air flow on the opposite side. In one or more embodiments, the membrane is a micro-porous membrane. In one or more embodiments, the mass flow rate of the smaller desiccant stream is between 1 and 10% of the mass flow rate of the larger desiccant stream. In one or more embodiments, the smaller desiccant stream is directed to a regenerator for removing excess water vapor after exiting the (membrane) channel.
- Provided herein are methods and systems used for the efficient dehumidification or humidification of an air stream using liquid desiccants. In accordance with one or more embodiments a liquid desiccant stream is split into a larger and a smaller stream. In one or more embodiments, the larger stream is directed into a heat transfer channel that is constructed to provide fluid flow in a counter-flow direction to an air stream. In one or more embodiments, the smaller stream is directed to a membrane bound channel. In one or more embodiments, the membrane channel has an air stream on the opposite side of the desiccant. In one or more embodiments, the larger stream is directed to a heat pump heat exchanger after leaving the heat transfer channel and is directed back to the heat transfer channel after being cooled or heated by the heat pump heat exchanger. In one or more embodiments, the air stream is an outside air stream. In one or more embodiments, the air stream after being treated by the desiccant behind the membrane is directed into a larger air stream that is returning from a space. In one or more embodiments, the larger air stream is subsequently cooled by a coil that is coupled to the same heat pump refrigeration circuit as the heat exchanger heat pump. In one or more embodiments, the desiccant stream is a single desiccant stream and the heat transfer channel is configured as a two-way heat and mass exchanger module. In one or more embodiments, the two-way heat and mass exchanger module is bound by a membrane. In one or more embodiments, the membrane is a micro-porous membrane. In one or more embodiments, the two-way heat and mass exchanger module is treating an outside air stream. In one or more embodiments, the air stream after being treated by the desiccant behind the membrane is directed into a larger air stream that is returning from a space. In one or more embodiments, the larger air stream is subsequently cooled by a coil that is coupled to the same heat pump refrigeration circuit as the heat exchanger heat pump.
- In no way is the description of the applications intended to limit the disclosure to these applications. Many construction variations can be envisioned to combine the various elements mentioned above each with its own advantages and disadvantages. The present disclosure in no way is limited to a particular set or combination of such elements.
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FIG. 1 illustrates an exemplary 3-way liquid desiccant air conditioning system using a chiller or external heating or cooling sources. -
FIG. 2 shows an exemplary flexibly configurable membrane module that incorporates 3-way liquid desiccant plates. -
FIG. 3 illustrates an exemplary single membrane plate in the liquid desiccant membrane module ofFIG. 2 . -
FIG. 4A schematically illustrates a conventional mini-split air conditioning system operating in a cooling mode. -
FIG. 4B schematically illustrates a conventional mini-split air conditioning system operating in a heating mode. -
FIG. 5A schematically illustrates an exemplary chiller assisted liquid desiccant air conditioning system for 100% outside air in a summer cooling mode. -
FIG. 5B schematically illustrates an exemplary chiller assisted liquid desiccant air conditioning system for 100% outside air in a winter heating mode. -
FIG. 6 schematically illustrates an exemplary chiller assisted partial outside air liquid desiccant air conditioning system using a 3-way heat and mass exchanger in a summer cooling mode in accordance with one or more embodiments. -
FIG. 7 schematically illustrates an exemplary chiller assisted partial outside air liquid desiccant air conditioning system using a 3-way heat and mass exchanger in a heating mode in accordance with one or more embodiments. -
FIG. 8 illustrates the psychrometric processes involved in the cooling of air for a conventional RTU and the equivalent processes in a liquid-RTU. -
FIG. 9 illustrates the psychrometric processes involved in the heating of air for a conventional RTU and the equivalent processes in a liquid-RTU. -
FIG. 10 schematically illustrates an exemplary chiller assisted partial outside air liquid desiccant air conditioning system using a 2-way heat and mass exchanger in a summer cooling mode in accordance with one or more embodiments wherein the liquid desiccant is pre-cooled and pre-heated before entering the heat and mass exchangers. -
FIG. 11 schematically illustrates an exemplary chiller assisted partial outside air liquid desiccant air conditioning system using a 2-way heat and mass exchanger in a summer cooling mode in accordance with one or more embodiments wherein the liquid desiccant is cooled and heated inside the heat and mass exchangers. -
FIG. 12 illustrates a water extraction module that pulls pure water into the liquid desiccant for use in winter humidification mode. -
FIG. 13 shows how the water extraction module ofFIG. 12 can be integrated into the system ofFIG. 7 . -
FIG. 14 illustrates two sets of channel triplets that simultaneously provide a heat exchange and desiccant humidification function. -
FIG. 15 shows two of the 3-way membrane modules ofFIG. 3 integrated into a DOAS, wherein the heat transfer fluid and the liquid desiccant fluid have been combined into a single desiccant fluid system, while retaining the advantage of separate paths for the fluid that is performing the dehumidification function and the fluid that is doing the heat transfer function. -
FIG. 16 shows the system ofFIG. 15 integrated to the system ofFIG. 6 . -
FIG. 1 depicts a new type of liquid desiccant system as described in more detail in U.S. Patent Application Publication No. 20120125020, which is incorporated by reference herein. Aconditioner 101 comprises a set of plate structures that are internally hollow. A cold heat transfer fluid is generated incold source 107 and entered into the plates. Liquid desiccant solution at 114 is brought onto the outer surface of the plates and runs down the outer surface of each of the plates. The liquid desiccant runs behind a thin sheet of material such as a membrane that is located between the air flow and the surface of the plates. The sheet of material can also comprise a hydrophilic material or a flocking material in which case the liquid desiccant runs more or less inside the material rather than over its surface.Outside air 103 is now blown through the set of plates. The liquid desiccant on the surface of the plates attracts the water vapor in the air flow and the cooling water inside the plates helps to inhibit the air temperature from rising. The treated air 104 is put into a building space. Theliquid desiccant conditioner 101 andregenerator 102 are generally known as 3-way liquid desiccant heat and mass exchangers, because they exchange heat and mass between the air stream, the desiccant, and a heat transfer fluid, so that there are three fluid streams involved. Two-way heat and mass exchangers generally have only a liquid desiccant and an air stream involved as will be seen later. - The liquid desiccant is collected at the lower end of each plate at 111 without the need for either a collection pan or bath so that the air flow can be horizontal or vertical. Each of the plates may have a separate desiccant collector at a lower end of the outer surfaces of the plate for collecting liquid desiccant that has flowed across the surfaces. The desiccant collectors of adjacent plates are spaced apart from each other to permit airflow therebetween. The liquid desiccant is then transported through a heat exchanger 113 to the top of the
regenerator 102 to point 115 where the liquid desiccant is distributed across the plates of the regenerator. Return air or optionally outsideair 105 is blown across the regenerator plate and water vapor is transported from the liquid desiccant into the leavingair stream 106. Anoptional heat source 108 provides the driving force for the regeneration. The hotheat transfer fluid 110 from the heat source can be put inside the plates of the regenerator similar to the cold heat transfer fluid on the conditioner. Again, the liquid desiccant is collected at the bottom of theplates 102 without the need for either a collection pan or bath so that also on the regenerator the air flow can be horizontal or vertical. Anoptional heat pump 116 can be used to provide cooling and heating of the liquid desiccant, however it is generally more favorable to connect a heat pump between thecold source 107 and thehot source 108, which is thus pumping heat from the cooling fluids rather than from the desiccant. -
FIG. 2 describes a 3-way heat and mass exchanger as described in further detail in U.S. Patent Application Publication Nos. 2014-0150662 filed on Jun. 11, 2013, 2014-0150656 filed on Jun. 11, 2013, and US 2014-0150657 filed on Jun. 11, 2013, which are all incorporated by reference herein. A liquid desiccant enters the structure throughports 304 and is directed behind a series of membranes as described inFIG. 1 . The liquid desiccant is collected and removed throughports 305. A cooling or heating fluid is provided throughports 306 and runs counter to theair stream 301 inside the hollow plate structures, again as described inFIG. 1 and in more detail inFIG. 3 . The cooling or heating fluids exit throughports 307. The treatedair 302 is directed to a space in a building or is exhausted as the case may be. -
FIG. 3 describes a 3-way heat exchanger as described in more detail in U.S. Provisional Patent Applications Ser. No. 61/771,340 filed on Mar. 1, 2013 and U.S. Patent Application Publication No. US 2014-0245769, which are incorporated by reference herein. Theair stream 251 flows counter to a coolingfluid stream 254.Membranes 252 contain aliquid desiccant 253 that is falling along thewall 255 that contain aheat transfer fluid 254.Water vapor 256 entrained in the air stream is able to transition themembrane 252 and is absorbed into theliquid desiccant 253. The heat of condensation ofwater 258 that is released during the absorption is conducted through thewall 255 into theheat transfer fluid 254.Sensible heat 257 from the air stream is also conducted through themembrane 252,liquid desiccant 253 andwall 255 into theheat transfer fluid 254. -
FIG. 4A illustrates a schematic diagram of a conventional packaged Roof-Top Unit (RTU) air conditioning system as is frequently installed on buildings, operating in a cooling mode. The unit comprises a set of components that generate cool, dehumidified air and a set of components that release heat to the environment. In a packaged unit, the cooling and heating components are generally inside a single enclosure. It is however possible to separate the cooling and heating components into separate enclosures or locate them in separate locations. The cooling components comprise a cooling (evaporator)coil 405 through which afan 407 pulls return air (labeled RA) 401 that has been returned (usually through a duct work—which is not shown) from a space. Prior to reaching thecooling coil 405, some of the return air RA is exhausted from the system asexhaust air EA2 402, which is replaced byoutside air OA 403 which is mixed with the remaining return air to a mixedair stream MA 404. In summer, this outside air OA is often warm and humid and adds a significant contribution to the cooling load on the system. The coolingcoil 405 cools the air and condenses water vapor on the coil which is collected indrain pan 424 and ducted to the outside 425. The resulting cooler,drier air CC 408 however, is now cold and very close to 100% relative humidity (saturated). Oftentimes and particularly in outdoor conditions that are not very warm but humid such as on a rainy spring day, theair CC 408 coming directly from the coolingcoil 10 can be uncomfortably cold. In order to increase occupant comfort and control space humidity, theair 408 is re-heated to a warmer temperature. There are several ways to accomplish this, such as using a hot water coil with hot water fed from a boiler or a steam coil receiving heat from a steam generator or by using electric resistance heaters. This heating of air results in an additional heat load on the cooling system. More modern systems use anoptional re-heat coil 409 which contains hot refrigerant from acompressor 416. There-heat coil 409 heats theair stream 408 to a warmerair stream HC 410, which is then recirculated back to the space, provides occupant comfort and allows one to better control humidity in the space. - The
compressor 416 receives a refrigerant throughline 423 and receives power throughconductor 417. The refrigerant can be any suitable refrigerant such as R410A, R407A, R134A, R1234YF, Propane, Ammonia, CO2, etc. The refrigerant is compressed by thecompressor 416 and compressed refrigerant is conducted to acondenser coil 414 throughline 418. Thecondenser coil 414 receivesoutside air OA 411, which is blown through thecoil 414 byfan 413, which receives power throughconductor 412. The resulting exhaustair stream EA 415 carries with it the heat of compression generated by the compressor. The refrigerant condenses in thecondenser coil 414 and the resulting cooler, (partially)liquid refrigerant 419 is conducted to there-heat coil 409 where additional heat is removed from the refrigerant, which turns into a liquid in this stage. The liquid refrigerant inline 420 is then conducted toexpansion valve 421 before reaching thecooling coil 405. The coolingcoil 405 receives liquid refrigerant at pressure of typically 50-200 psi throughline 422. The coolingcoil 405 absorbs heat from theair stream MA 404 which re-evaporates the refrigerant which is then conducted throughline 423 back to thecompressor 416. The pressure of the refrigerant inline 418 is typically 300-600 psi. In some instances the system can have multiple cooling coils 405,fans 407 andexpansion valves 421 as well ascompressors 416 andcondenser coils 414 andcondenser fans 413. Oftentimes the system also has additional components in the refrigerant circuit or the sequence of components is ordered differently which are all well known in the art. As will be shown later, one of these components can be adiverter valve 426 which bypasses there-heat coil 409 in winter mode. There are many variations of the basic design described above, but all recirculating rooftop units generally have a cooling coil that condenses moisture and introduce a small amount of outside air that is added to a main air stream that returns from the space, is cooled and dehumidified and the ducted back to the space. In many instances the larges load is the dehumidification of outside air and dealing with the reheat energy, as well as the average fan power required to move the air. - The primary electrical energy consuming components are the
compressor 416 throughelectrical line 417, the condenser fan electrical motor throughsupply line 412 and the evaporator fan motor throughline 406. In general the compressor uses close to 80% of the electricity required to operate the system, with the condenser and evaporator fans taking about 10% of the electricity each at peak load. However when one averages power consumption over the year, the average fan power is closer to 40% of the total load since fans generally run all the time and the compressor switches off on an as needed basis. In a typical RTU of 10 ton (35 kW) cooling capacity, the air flow RA is around 4,000 CFM. The amount of outside air OA mixed in is between 5% and 25% so between 200 and 1,000 CFM. Clearly the larger the amount of outside air results in larger cooling loads on the system. The return air that is exhausted EA2 is roughly equal to the amount of outside air taken in so between 200 and 1,000 CFM. Thecondenser coil 414 is generally operated with a larger air flow than theevaporator coil 405 of about 2,000 CFM for a 10 ton RTU. This allows the condenser to be more efficient and reject the heat of compression more efficiently to the outside air OA. -
FIG. 4B is a schematic diagram of the system ofFIG. 4A operating in a winter heating mode as a heat pump. Not all RTUs are heat pumps, and generally a cooling only system as shown inFIG. 4A can be used, possibly supplemented with a simple gas or electric furnace air heater. However, heat pumps are gaining popularity particularly in moderate climates since they can provide heating as well as cooling with better efficiency than electric heat and without the need to run gas lines to the RTU. For ease of illustration, the flow of refrigerant from thecompressor 417 has simply been reversed. In actuality the refrigerant is usually diverted by a 4-way valve circuit which accomplishes the same effect. As the compressor produces hot refrigerant inline 423 which is now conducted to thecoil 405, which is now functioning as a condenser rather than an evaporator. The heat of compression is carried to the mixedair stream MA 404 resulting in a warmair stream CC 408. Again, the mixedair stream MA 404 is the result of removing someair EA2 402 from thereturn air RA 401 and replacing it withoutside air OA 403. The warmair stream CC 408 however is now relatively dry because heating by thecondenser coil 405 results in air with low relative humidity and thus oftentimes ahumidification system 427 is added to provide the required humidity for occupant comfort. Thehumidification system 427 requires awater supply 428. However this humidification also results in a cooling effect, meaning that theair stream 408 has to be overheated to compensate for the cooling effect of thehumidifier 427. The refrigerant 422 leaving thecoil 405 then enters theexpansion valve 421 which results in a cold refrigerant stream inline 420, which is whydiverter valve 426 can be used to bypass there-heat coil 409. This diverts the cold refrigerant tocoil 414 which is now functioning as an evaporator coil. The coldoutside air OA 411 is blown byfan 413 through theevaporator coil 414. The cold refrigerant inline 419 now results in theexhaust air EA 415 to be even colder. This effect can result in water vapor in theoutside air OA 411 to condense on thecoil 414 which now runs the risk of ice formation on the coil. For that reason, in heat pumps, the refrigerant flow is regularly switched back from heating mode to cooling mode resulting in a warming of thecoil 414 which allows ice to fall off the coil, but also resulting in much worse energy performance in winter. Furthermore, particularly in cold climates, it is common that the heating capacity of a system for winter heating needs to be about twice the cooling capacity of the system for summer cooling. It is therefore common to findsupplemental heating systems 429 that heat theair stream EV 410 further before it returns to the space. Such supplemental systems can be gas furnaces, electric resistance heaters and the like. These additional components add a significant amount to the air stream pressure drop resulting in more power required forfan 407. The reheat coil—even if not active—can still be in the air stream as are the humidification system and heating components. -
FIG. 5A illustrates a schematic representation of a liquid desiccant air conditioner system. A 3-way heat and mass exchanger conditioner 503 (which is similar to theconditioner 101 ofFIG. 1 ) receives anair stream 501 from the outside (“OA”).Fan 502 pulls theair 501 through theconditioner 503 wherein the air is cooled and dehumidified. The resulting cool, dry air 504 (“SA”) is supplied to a space for occupant comfort. The 3-way conditioner 503 receives aconcentrated desiccant 527 in the manner explained underFIGS. 1-3 . It is preferable to use a membrane on the 3-way conditioner 503 to contain the desiccant and inhibit it from being distributed into theair stream 504. The diluteddesiccant 528, which contains the captured water vapor is transported to a heat andmass exchanger regenerator 522. Furthermore chilledwater 509 is provided bypump 508, which enters theconditioner module 503 where it picks up heat from the air as well as latent heat released by the capture of water vapor in thedesiccant 527. Thewarmer water 506 is brought to theheat exchanger 507 on thechiller system 530. It is worth noting that the system ofFIG. 5A does not require a condensate drain line likeline 425 inFIG. 4A . Rather, any moisture that is condensed into the desiccant is removed as part of the desiccant itself. This also eliminates problems with mold growth in standing water that can occur in the conventionalRTU condensate pan 424 systems ofFIG. 4A . - The
liquid desiccant 528 leaves theconditioner 503 and is moved through theoptional heat exchanger 526 to theregenerator 522 bypump 525. - The
chiller system 530 comprises a water to refrigerantevaporator heat exchanger 507 which cools the circulatingcooling fluid 506. The liquid,cold refrigerant 517 evaporates in theheat exchanger 507 thereby absorbing the thermal energy from the coolingfluid 506. Thegaseous refrigerant 510 is now re-compressed bycompressor 511. Thecompressor 511 ejects hotrefrigerant gas 513, which is liquefied in thecondenser heat exchanger 515. The liquid refrigerant exiting thecondenser 514 then entersexpansion valve 516, where it rapidly cools and exits at a lower pressure. Thecondenser heat exchanger 515 now releases heat to another coolingfluid loop 519 which brings hotheat transfer fluid 518 to theregenerator 522. Circulatingpump 520 brings the heat transfer fluid back to thecondenser 515. The 3-way regenerator 522 thus receives a diluteliquid desiccant 528 and hotheat transfer fluid 518. Afan 524 brings outside air 521 (“OA”) through theregenerator 522. The outside air picks up heat and moisture from theheat transfer fluid 518 anddesiccant 528 which results in hot humid exhaust air (“EA”) 523. - The
compressor 511 receiveselectrical power 512 and typically accounts for 80% of electrical power consumption of the system. Thefans electrical power Pumps compressor 511 will operate more efficiently than thecompressor 416 inFIG. 4A for several reasons: theevaporator 507 inFIG. 5A will typically operate at higher temperature than theevaporator 405 inFIG. 4A because the liquid desiccant will condense water at much higher temperature without needing to reach saturation levels in the air stream. Furthermore thecondenser 515 inFIG. 5A will operate at lower temperatures than thecondenser 414 inFIG. 4A because of the evaporation occurring on theregenerator 522 which effectively keeps thecondenser 515 cooler. As a result the system ofFIG. 5A will use about 40% less electricity than the system ofFIG. 4A for similar compressor isentropic efficiencies. -
FIG. 5B shows essentially the same system asFIG. 5A except that thecompressor 511's refrigerant direction has been reversed as indicated by the arrows onrefrigerant lines chiller 530. It is also possible to instead of reversing the refrigerant flow to direct the hotheat transfer fluid 518 to theconditioner 503 and the coldheat transfer fluid 506 to theregenerator 522. This will provide heat to the conditioner which will now create hot,humid air 504 for the space for operation in winter mode. In effect the system is now working as a heat pump, pumping heat from theoutside air 521 to thespace supply air 504. However unlike the system ofFIG. 4A , which is oftentimes also reversible, there is much less of a risk of the coil freezing because the desiccant usually has much lower crystallization limit than water vapor. In the system ofFIG. 4B , theair stream 411 contains water vapor and if theevaporator coil 414 gets too cold, this moisture will condense on the surfaces and create ice formation on the coil. The same moisture in theregenerator 522 ofFIG. 5B will condense in the liquid desiccant which—when managed properly—will not crystalize until −60° C. for some desiccants such as LiCl and water. This will allow the system to continue to operate at much lower outside air temperatures without freezing risk. - As before in
FIG. 5A , outsideair 501 is directed through theconditioner 503 byfan 502 which is operated byelectrical power 505. Thecompressor 511 discharges hot refrigerant throughline 510 intocondenser heat exchanger 507 and out throughline 510. The heat exchanger rejects heat to heat transfer fluid circulated bypump 508 throughline 509 into theconditioner 503 which results in theair stream 501 picking up heat and moisture from the desiccant. Dilute desiccant is supplied byline 527 to the conditioner. The dilute desiccant is directed fromregenerator 522 bypump 525 throughheat exchanger 526. However in winter conditions it is possible that not enough water is recovered in theregenerator 522 to compensate for the water lost in theconditioner 503 which is whyadditional water 531 can be added to the liquid desiccant inline 527. Concentrated liquid desiccant is collected from theconditioner 503 and drained throughline 528 andheat exchanger 526 to theregenerator 522. Theregenerator 522 takes in either outside air OA or preferably returnair RA 521 which is directed through the regenerator byfan 524 which is powered byelectrical connection 529. Return air is preferred because is usually much warmer and contains much more moisture than outside air, which allows the regenerator to capture more heat and moisture from theair stream 521. Theregenerator 522 thus produces colder, drierexhaust air EA 523. A heat transfer fluid inline 518 absorbs heat from theregenerator 522 which is pumped bypump 520 toheat exchanger 515. Theheat exchanger 515 received cold refrigerant fromexpansion valve 516 throughline 514 and the heated refrigerant is conducted throughline 513 back to thecompressor 511 which receives power fromconductor 512. -
FIG. 6 illustrates an air-conditioning system in accordance with one or more embodiments wherein a modifiedliquid desiccant section 600A is connected to a modifiedRTU section 600B but wherein the two systems share asingle chiller system 600C. Theoutside air OA 601 which as shown inFIG. 4A is typically 5-25% of the returnair stream RA 604, is now directed through theconditioner 602 which is similar in construction to the 3-way heat and mass exchange conditioner described inFIG. 2 . Theconditioner 602 can be significantly smaller than theconditioner 503 ofFIG. 5A because theair stream 601 is much smaller than in the 100% outsideair stream 501 ofFIG. 5A . Theconditioner 602 produces a colder, dehumidifiedair stream SA 603 which is mixed with thereturn air RA 604 to makemixed air MA2 606.Excess return air 605 is directed out of the system or towards theregenerator 612. The mixed air MA2 is pulled byfan 608 throughevaporator coil 607 which primarily provides sensible only cooling so that thecoil 607 can be much shallower and less expensive than thecoil 405 inFIG. 4A which needs to be deeper to allow moisture to condense. The resultingair stream CC2 609 is ducted to the space to be cooled. Theregenerator 612 receives eitheroutside air OA 610 or theexcess return air 605 or amixture 611 thereof. - The
regenerator air stream 611 can be pulled through theregenerator 612 which again is similar in construction to the 3-way heat and mass exchanger described inFIG. 2 by afan 637 and the resulting exhaustair stream EA2 613 is generally much warmer and contains more water vapor than themixed air stream 611 that is entering. Heat is provided by circulating a heat transfer fluid throughline 621 usingpump 622. - The
compressor 618 compresses a refrigerant similar to the compressors inFIG. 4A andFIG. 5A . The hot refrigerant gas is conducted throughline 619 to acondenser heat exchanger 620. A smaller amount of heat is conducted through this liquid-to-refrigerant heat exchanger 620 into the heat transfer fluid incircuit 621. The still hot refrigerant is now conducted throughline 623 to acondenser coil 616, which receives outsideair OA 614 fromfan 615. The resulting hotexhaust air EA3 617 is ejected into the environment. The refrigerant which is now a cooler liquid after exiting thecondenser coil 616 is conducted through line 624 to anexpansion valve 625, where it is expanded and becomes cold. The cold liquid refrigerant is conducted throughline 626 to theevaporator coil 607 where it absorbs heat from the mixedair stream MA2 606. The still relatively cold refrigerant which has partially evaporated in thecoil 607 is now conducted throughline 627 toevaporator heat exchanger 628 where additional heat is removed from the heat transfer fluid circulating inline 629 bypump 630. Finally the gaseous refrigerant exiting theheat exchanger 628 is conducted throughline 631 back to thecompressor 618. - In addition, a liquid desiccant is circulated between the
conditioner 602 and theregenerator 612 through lines 635, theheat exchanger 633 and is circulated back to the conditioner bypump 632 and throughline 634. Optionally a water-injection module 636 can be added to one or both of thedesiccant lines 634 and 635. Such a module injects water into the desiccant in order to reduce the concentration of the desiccant and is described inFIG. 12 in more detail. Water injection is useful in conditions in which the desiccant concentration gets higher than desired, e.g., in hot, dry conditions such as can occur in the summer or in cold, dry conditions such as can occur in winter which will be described in more detail inFIG. 7 . -
FIG. 7 illustrates an embodiment of the present invention ofFIG. 6 , wherein a modifiedliquid desiccant section 700A is connected to a modifiedRTU section 700B but wherein the two systems share asingle chiller system 700C operating in a heating mode. Theoutside air OA 701 which as shown inFIG. 4B is typically 5-25% of the returnair stream RA 704, is now directed through theconditioner 702 which is similar in construction to the 3-way heat and mass exchange conditioner described inFIG. 2 . Theconditioner 702 can be significantly smaller than theconditioner 503 ofFIG. 5B because theair stream 701 is much smaller than in the 100% outsideair stream 501 ofFIG. 5B . Theconditioner 702 produces a warmer, humidifiedair stream RA3 703 which is mixed with thereturn air RA 704 to makemixed air MA3 706. Excessreturn air RA 705 is directed out of the system or towards theregenerator 712. Themixed air MA3 706 is pulled byfan 708 throughcondenser coil 707 which provides sensible only heating. The resultingair stream SA2 709 is ducted to the space to be heated and humidified. Theregenerator 712 receives eitheroutside air OA 710 or the excessreturn air RA 705 or amixture 711 thereof. - The
regenerator air stream 711 can be pulled through theregenerator 712 which again is similar in construction to the 3-way heat and mass exchanger described inFIG. 2 by afan 737 and the resulting exhaustair stream EA2 713 is generally much colder and contains less water vapor than themixed air stream 711 that is entering. Heat is removed by circulating a heat transfer fluid throughline 721 usingpump 722. - The
compressor 718 compresses a refrigerant similar to the compressors inFIG. 4B andFIG. 5B . The hot refrigerant gas is conducted throughline 731 to acondenser heat exchanger 728, which is thesame heat exchanger 628 inFIG. 6 , but used as a condenser instead of an evaporator. A smaller amount of heat is conducted through this liquid-to-refrigerant heat exchanger 728 into the heat transfer fluid incircuit 729 by usingpump 730. The still hot refrigerant is now conducted throughline 727 to acondenser coil 707, which receives the mixedreturn air MA3 706. The resulting hotsupply air SA2 709 is directed through a duct to the space to be heated and humidified. The refrigerant which is now a cooler liquid after exiting thecondenser coil 707 is conducted throughline 726 to anexpansion valve 725, where it is expanded and becomes cold. The cold liquid refrigerant is conducted through line 724 to theevaporator coil 716 where it absorbs heat from the outsideair stream OA 714 resulting in a cold exhaustair stream EA 717 which is emitted to the environment by usingfan 715. The still relatively cold refrigerant which has partially evaporated in thecoil 716 is now conducted throughline 723 toevaporator heat exchanger 720 where additional heat is removed from theair stream 711 going through theregenerator 712 by transfer fluid circulating inline 721 by usingpump 722. Finally the gaseous refrigerant exiting theheat exchanger 720 is conducted throughline 719 back to thecompressor 718. - In addition, a liquid refrigerant is circulated between the
conditioner 702 and theregenerator 712 throughlines 735, theheat exchanger 733 and is circulated back to the conditioner bypump 732 and throughline 734. In some conditions, for example when both thereturn air RA 705 and theoutside air OA 710 are relatively dry, it is possible that theconditioner 702 provides more moisture to the space than is collected in theregenerator 712. In that case a provision for addingwater 736 is required to maintain the desiccant at the proper concentration. A provision for addingwater 736 can be provided in any location that gives convenient access to the desiccant, however the water added, should be relatively pure since a lot of water will evaporate, which is why reverse osmosis or de-ionized or distilled water would be preferable to straight tap water. This provision for addingwater 736 will be discussed in more detail inFIG. 12 . - The advantages of integrating a system in the configuration of
FIG. 6 andFIG. 7 are several. The combination of 3-way liquid desiccant heat exchanger modules and a shared compressor system allows one to combine the advantages of dehumidification without condensation that are possible in the 3-way heat and mass exchanger with the inexpensive construction of a conventional RTU, whereby the integrated solution becomes very cost competitive. As mentioned before, thecoil 607 can be thinner, since no moisture condensation is needed, and the condensate pan and drain fromFIG. 4A can be eliminated. Furthermore as will be seen inFIG. 8 , the overall cooling capacity of the compressor can be reduced and the condenser coil can be smaller as well. In addition, the heating mode of the system adds humidity to the air stream unlike any other heat pump in the market today. The refrigerant, desiccant and heat transfer fluid circuits are actually simpler than those in the systems ofFIGS. 4A, 4B, 5A and 5B , and thesupply air stream FIGS. 4A and 4B , which means less pressure drop in the air stream leading to additional energy savings. -
FIG. 8 illustrates a psychrometric chart of the processes ofFIG. 4A andFIG. 6 . The horizontal axis denotes temperature in degrees Fahrenheit and the vertical axis denotes humidity in grains of water per pound of dry air. As can be seen in the figure, and by way of example, outside air OA is provided at 95 F and 60% relative humidity (or 125 gr/lb). Also by example we selected a 1,000 CFM supply air requirement with a 25% outside air contribution (250 CFM) to the space at 65 F and 70% RH (65 gr/lb). The conventional system ofFIG. 4A takes in 1,000 CFM of return air RA at 80 F and 50% RH (78 gr/lb). 250 CFM of this return air RA is discarded as EA2 (thestream EA2 402 inFIG. 4A ). 750 CFM of the return air RA is mixed with 250 CFM of outside air (thestream OA 403 inFIG. 4A ) resulting in a mixed air condition MA (thestream MA 404 inFIG. 4A ). The mixed air MA is directed through the evaporator coil resulting in a cooling and dehumidification process resulting in air CC leaving the coil at 55 F and 100% RH (65 gr/lb). In many cases that air is reheated (possibly by a small condenser coil as was shown inFIG. 4A ) resulting in the actual supply air HC at 65F and 70% RH (65 gr/lb). - The system of
FIG. 6 under the same outside air conditions will create a supply air stream SA leaving the conditioner (602 inFIG. 6 ) at 65 F and 43% RH (40 gr/lb). This relatively dry air is now mixed with the 750 CFM of return air RA (604 inFIG. 6 ) resulting in mixed air condition MA2 (MA2 606 inFIG. 6 ). The mixed air MA2 is now directed through the evaporator coil (607 inFIG. 6 ) which sensible cools the air to supply air condition CC2 (CC2, 609 inFIG. 6 ). As can be seen in the figure and calculated from the psychrometrics, the cooling power of the conventional system is 48.7 kBTU/hr, whereas the cooling power of the system ofFIG. 6 is 35.6 kBTU/hr (23.2 kBTU/hr for the outside air OA and 12.4 kBTU/hr for the mixed air MA2) thus requiring about a 27% smaller compressor. - Also shown in
FIG. 8 is the change in the outside air OA used to reject heat. The conventional system ofFIG. 4A use about 2,000 CFM through thecondenser 414 to reject heat to the outside air OA (OA 411 inFIG. 4A ) resulting in exhaust air EA at 119 F and 25% RH (125 gr/lb) (EA 415 inFIG. 4A ). However, the system ofFIG. 6 rejects two air streams, theregenerator 612 rejects air EA2 at 107 F and 49% RH (178 gr/lb) (EA2 613 inFIG. 6 ) which is hot and moist, as well as air stream EA3 at 107 F and 35% RH (125 gr/lb) (EA3 617 inFIG. 6 ). Because of the lower compressor capacity, less heat has to be rejected to the outside air resulting in a lower condenser temperature. The effects of lower compressor power and higher evaporator temperatures and lower condenser temperature as well as lower pressure drop in the main air stream inFIG. 6 combine make a system with much better energy performance than a conventional RTU as was shown inFIG. 4A . - Likewise,
FIG. 9 illustrates a psychrometric chart of the processes ofFIG. 4B andFIG. 7 . The horizontal axis denotes temperature in degrees Fahrenheit and the vertical axis denotes humidity in grains of water per pound of dry air. As can be seen in the figure, and by way of example, outside air OA is provided at 30 F and 60% relative humidity (or 14 gr/lb). Also by example we again selected a 1,000 CFM supply air requirement with a 25% outside air contribution (250 CFM) to the space at 120 F and 12% RH (58 gr/lb). The conventional system ofFIG. 4B takes in 1,000 CFM of return air RA at 80 F and 50% RH (78 gr/lb). 250 CFM of this return air RA is discarded as EA2 (thestream EA2 402 inFIG. 4B ). 750 CFM of the return air RA is mixed with 250 CFM of outside air (thestream OA 403 inFIG. 4B ) resulting in a mixed air condition MA (thestream MA 404 inFIG. 4B ). The mixed air MA is directed through the condenser coil (405 inFIG. 4B ) resulting in a heating process resulting in air SA leaving the coil at 128 F and 8% RH (46 gr/lb). In many cases that air is too dry for occupant comfort and the air is receiving moisture from a humidification system (427 inFIG. 4B ) resulting in the actual supply air EV at 120 F and 12% RH (58 gr/lb). Humidification can be done to a higher level, but as will be clear that would possibly result in an additional heating requirement. The water consumption of the evaporation in this example is around 1.0 gallon per hour. - The system of
FIG. 7 under the same outside air conditions will create a supplyair stream RA3 703 leaving the conditioner (702 inFIG. 7 ) at 70 F and 48% RH (63 gr/lb). This relatively moist air is now mixed with the 750 CFM of return air RA (704 inFIG. 7 ) resulting in mixed air condition MA3 (MA3 706 inFIG. 7 ). The mixed air MA3 is now directed through the condenser coil (707 inFIG. 7 ) which sensible heats the air to supply air condition SA2 (SA2, 709 inFIG. 7 ). As can be seen in the figure and calculated from the psychrometrics, the heating power of the conventional system is 78.3 kBTU/hr, whereas the heating power of the system ofFIG. 7 is 79.3 kBTU/hr (20.4 kBTU/hr for the outside air OA and 58.9 kBTU/hr for the mixed air MA2) essentially the same as the system ofFIG. 4B . - Also shown in
FIG. 9 is the change in the outside air OA used to absorb heat. The conventional system ofFIG. 4B use about 2,000 CFM through theevaporator 414 to absorb heat from the outside air OA (OA 411 inFIG. 4B ) resulting in exhaust air EA at 20 F and 100% RH (9 gr/lb) (EA 415 inFIG. 4B ). However, the system ofFIG. 6 absorbs heat from two air streams, theregenerator 612 absorbs heat from air stream between MA2 (which comprises 250 CFM of RA air at 65 F and 60% RH or 55 gr/lb and 150 CFM of OA air at 30 F and 60% RH or 14 gr/lb for a mixed air condition MA2 (711 inFIG. 7 ) of 400 CFM of 52 F air at 70% RH or 40 gr/lb) and air stream EA2 at 20 F and 50% RH (10 gr/lb) (EA2 713 inFIG. 7 ) which is cool and dry, as well as air stream EA at 20 F and 95% RH (14 gr/lb) (EA 717 inFIG. 7 ). As can be seen in the figure this setup has three effects: the temperature of EA and EA2 is higher than the temperature CC, and thus theevaporator coil 707 ofFIG. 6B runs at a higher temperature as theevaporator coil 405 which improves efficiency. Furthermore, theconditioner 702 is absorbing moisture from the mixed air stream MA2 which is subsequently released in the air stream MA3, eliminating the need for makeup water. And lastly, theevaporator coil 405 is condensing moisture as can be seen from the process between OA and CC in the figure. In practice this results in ice formation on the coil and the coil will thus have to be heated the remove ice buildup, which is usually done by switching the refrigerant flow in the direction ofFIG. 6 . Thecoil 707 does not reach saturation and will thus not have to be heated. As a result the actual cooling incoil 405 in the system ofFIG. 4B is around 21.7 kBRU/hr, whereas the combination ofcoil 707 andconditioner 702 results in 45.2 kBTU/hr in the system ofFIG. 7 . This means a significantly better Coefficient of Performance (CoP) even though the heating output is the same and no water is consumed in the system ofFIG. 7 . -
FIG. 10 illustrates an alternate embodiment of the system inFIG. 6 , wherein the 3-way heat andmass exchangers FIG. 6 have been replaced by 2-way heat and mass exchangers. In two way heat and mass exchangers which are well known in the art, a desiccant is exposed directly to an air stream, sometimes with a membrane therebetween and sometimes without. Typically two-way heat and mass exchangers exhibit an adiabatic heat and mass transfer process since there often is no place for the latent heat of condensation to be absorbed, safe for the desiccant itself. This usually increases the required desiccant flow rate because the desiccant now has to function as a heat transfer fluid as well.Outside air 1001 is directed through theconditioner 1002 which produces a colder, dehumidifiedair stream SA 1003 which is mixed with thereturn air RA 1004 to makemixed air MA2 1006.Excess return air 1005 is directed out of the system or towards theregenerator 1012. The mixed air MA2 is pulled byfan 1008 throughevaporator coil 1007 which primarily provides sensible only cooling. The resultingair stream CC2 1009 is ducted to the space to be cooled. Theregenerator 1012 receives eitheroutside air OA 1010 or theexcess return air 1005 or amixture 1011 thereof. - The
regenerator air stream 1011 can be pulled through theregenerator 1012 which again is similar in construction to the 2-way heat and mass exchanger as used as aconditioner 1002 by a fan (not shown) and the resulting exhaustair stream EA2 1013 is generally much warmer and contains more water vapor than themixed air stream 1011 that is entering. - The
compressor 1018 compresses a refrigerant similar to the compressors inFIG. 4A ,FIG. 5A andFIG. 6 . The hot refrigerant gas is conducted throughline 1019 to acondenser heat exchanger 1020. A smaller amount of heat is conducted through this liquid-to-refrigerant heat exchanger 1020 into the desiccant inline 1031. Since desiccant is often highly corrosive, theheat exchanger 1020 is made from Titanium or other suitable material. The still hot refrigerant is now conducted throughline 1021 to acondenser coil 1016, which receives outsideair OA 1014 fromfan 1015. The resulting hotexhaust air EA3 1017 is ejected into the environment. The refrigerant which is now a cooler liquid after exiting thecondenser coil 1016 is conducted through line 1022 to anexpansion valve 1023, where it is expanded and becomes cold. The cold liquid refrigerant is conducted throughline 1024 to theevaporator coil 1007 where it absorbs heat from the mixed air stream MA2 1006. The still relatively cold refrigerant which has partially evaporated in thecoil 1007 is now conducted throughline 1025 toevaporator heat exchanger 1026 where additional heat is removed from the liquid desiccant that is circulated to theconditioner 1002. As before theheat exchanger 1026 will have to be constructed from a corrosion resistant material such as Titanium. Finally the gaseous refrigerant exiting theheat exchanger 1026 is conducted throughline 1027 back to thecompressor 1018. - In addition, a liquid desiccant is circulated between the
conditioner 1002 and theregenerator 1012 throughlines 1030, theheat exchanger 1029 and is circulated back to the conditioner bypump 1028 and throughline 1031. -
FIG. 11 illustrates an alternate embodiment of the system inFIG. 10 , wherein the 2-way heat andmass exchanger 1002 and the liquid toliquid heat exchangers 1026 ofFIG. 10 have been integrated into single 3-way heat and mass exchangers where the air, the desiccant and the refrigerant exchange heat and mass simultaneously. In concept this is similar to using a refrigerant instead of a heat transfer fluid inFIG. 6 . The same integration can be done on theregenerator 1012 and theheat exchanger 1020. These integrations essentially eliminate a heat exchanger on each side making the system more efficient. -
Outside air 1101 is directed through theconditioner 1102 which produces a colder, dehumidifiedair stream SA 1103 which is mixed with the return air RA 1104 to makemixed air MA2 1106.Excess return air 1105 is directed out of the system or towards the regenerator 10112. The mixed air MA2 is pulled by fan 10108 throughevaporator coil 1107 which primarily provides sensible only cooling. The resultingair stream CC2 1109 is ducted to the space to be cooled. The regenerator 11012 receives eitheroutside air OA 1110 or theexcess return air 1105 or amixture 1111 thereof. - The
regenerator air stream 1111 can be pulled through theregenerator 1112 which again is similar in construction to the 2-way heat and mass exchanger as used as aconditioner 1102 by a fan (not shown) and the resulting exhaustair stream EA2 1113 is generally much warmer and contains more water vapor than themixed air stream 1111 that is entering. - The
compressor 1118 compresses a refrigerant similar to the compressors inFIG. 4A ,FIG. 5A ,FIG. 6 andFIG. 10 . The hot refrigerant gas is conducted throughline 1119 to a 3-way condenser heat andmass exchanger 1112. A smaller amount of heat is conducted through thisregenerator 1120 into the refrigerant inline 1119. Since desiccant is often highly corrosive, theregenerator 1112 needs to be constructed as for example is shown in FIG. 80 of application Ser. No. 13/915,262. The still hot refrigerant is now conducted throughline 1120 to acondenser coil 1116, which receives outsideair OA 1114 fromfan 1115. The resulting hotexhaust air EA3 1117 is ejected into the environment. The refrigerant which is now a cooler liquid after exiting thecondenser coil 1116 is conducted through line 1121 to anexpansion valve 1122, where it is expanded and becomes cold. The cold liquid refrigerant is conducted throughline 1123 to theevaporator coil 1107 where it absorbs heat from the mixed air stream MA2 1106. The still relatively cold refrigerant which has partially evaporated in thecoil 1107 is now conducted throughline 1124 to the evaporator heat exchanger/conditioner 1102 where additional heat is removed from the liquid desiccant. Finally the gaseous refrigerant exiting theconditioner 1102 is conducted throughline 1125 back to thecompressor 1118. - In addition, the liquid desiccant is circulated between the
conditioner 1102 and theregenerator 1112 throughlines 1129, theheat exchanger 1128 and is circulated back to the conditioner bypump 1127 and throughline 1126. - The systems from
FIG. 10 andFIG. 11 are also reversible for winter heating mode similar to the system inFIG. 7 . Under some conditions in the winter heating mode, additional water should be added to maintain proper desiccant concentration because if too much water is evaporated in dry conditions, the desiccant is at risk of crystalizing. As mentioned, one option is to simply add reverse osmosis or de-ionized water to keep the desiccant dilute, but the processes to generate this water are also very energy intensive. -
FIG. 12 illustrates an embodiment of a much simpler water injection system that generates pure water directly into the liquid desiccant by taking advantage of the desiccants' ability to attract water. The structure inFIG. 12 (which was labeled 736 inFIG. 7 ) comprises a series of parallel channels, which can be flat plates or rolled up channels. Water enters the structure at 1201 and is distributed to several channels throughdistribution header 1202. This water can be tap water, sea water or even filtered waste water or any water containing fluid that has primarily water as a constituent and if any other materials are present, those materials are not transportable through theselective membrane 1210 as will be explained shortly. The water is distributed to each of the even channels labeled “A” in the figure. The water exits the channels labeled “A” through a manifold 1203 and is collected indrain line 1204. At the same time concentrated desiccant is introduced at 1205, which is distributed throughheader 1206 to each of the channels labeled “B” in the figure. Theconcentrated desiccant 1209 flows along the B channels. The wall between the “A” and the “B: channels comprises aselective membrane 1210 which is selective to water so that water molecules can come through the membrane but ions or other materials cannot. This thus prevents for example Lithium and Chloride ions from crossing the membrane into the water “A” channel and vice versa prevents Sodium and Chloride ions from seawater crossing into the desiccant in the “B” channel. Since the concentration of Lithium Chloride in the desiccant is typically 25-35%, this provides a strong driving force for the diffusion of water from the “A” to the “B” channel since the concentration of for example Sodium Chloride in sea water is typically less than 3%. Selective membranes of this type are commonly found in membrane distillation or reverse osmosis processes and are well known in the art. The structure ofFIG. 12 can be executed in many form factors such as a flat plate structure or a concentric stack of channels or any other convenient form factor. It is also possible to construct the plate structure ofFIG. 3 by replacing thewall 255 with a selective membrane as is shown inFIG. 12 . However, such a structure would only make sense if one wants to continuously add water to the desiccant. It would make little sense in summer mode when one is trying to remove water from the desiccant. It is therefore easier to implement the structure ofFIG. 12 in a separate module as is shown inFIG. 7 andFIG. 13 which can be bypassed in a summer cooling mode. Although in some instances adding water to the desiccant in summer cooling mode may also make sense for example if the outdoor temperature is very hot but also very dry as in a desert. The membrane may be a microporous hydrophobic structure comprising a polypropylene, a polyethylene, or an ECTFE (Ethylene ChloroTriFluoroEthylene) membrane. -
FIG. 13 illustrates how the water injection system fromFIG. 12 can be integrated to the desiccant pumping subsystem ofFIG. 7 . Thedesiccant pump 732 pumps desiccant through thewater injection module 1301 and through theheat exchanger 733 as was shown inFIG. 7 . The desiccant returns from the conditioner (702 inFIG. 7 ) throughline 735 and through theheat exchanger 733 back to the regenerator (712 inFIG. 7 ). Awater reservoir 1304 is filled withwater 1305 or a water containing liquid. Apump 1302 pumps the water to thewater injection system 1301, where it enters through port 1201 (as shown inFIG. 12 ). The water flows through the “A” channels inFIG. 12 and exits throughport 1204 after which is drains back to thetank 1303. Thewater injection system 1301 is sized in such a way that the diffusion of water through theselective membranes 1210 is matched to the amount of water that would have to be added to the desiccant. The water injection system can comprise several independent sections that are individually switchable so that water could be added to the desiccant in several stages. - The
water 1304 flowing through theinjection module 1301 is partially transmitted through theselective membranes 1210. Any excess water exits through thedrain line 1204 and falls back in thetank 1303. As the water is pumped from thetank 1304 again bypump 1302, less and less water will return to the tank. Afloat switch 1307 such as is commonly used on cooling towers can be used to maintain a proper water level in the tank. When the float switch detects a low water level, it opensvalve 1308 which lets additional water in fromsupply water line 1306. However, since the selective membrane only pass pure water through, any residuals such as Calcium Carbonates, or other non-passible materials will collect in thetank 1303. A blow-downvalve 1305 can be opened to get rid of these unwanted deposits as is commonly done on cooling towers. - It should be clear to those skilled in the art that the water injection system of
FIG. 12 can be used in other liquid desiccant system architectures for example in those described in Ser. No. 13/115,686, US 2012/0125031 A1, Ser. No. 13/115,776, and US 2012/0125021 A1. -
FIG. 14 illustrates how the water injection system fromFIG. 12 andFIG. 13 can be integrated to the desiccant todesiccant heat exchanger 733 fromFIG. 13 . The water flows through the “A”channels 1402 inFIG. 14 and exits through a port after which is drains back to the tank as described inFIG. 13 . A cold desiccant is introduced in the “B”channels 1401 inFIG. 14 and a warm desiccant is introduced in the “C” channels inFIG. 14 . Thewalls 1404 between the “A” and “B” and “A” and “C” channels respectively are again constructed with a selectively permeable membrane. Thewall 1405 between the “B” and the “C” channel is a non-permeable membrane such as a plastic sheet which can conduct heat but not water molecules. The structure ofFIG. 14 thus accomplishes two tasks simultaneously: it provides a heat exchange function between the hot and the cold desiccant and it transmit water from the water channel to the two desiccant channels in each channel triplet. -
FIG. 15 illustrates an embodiment wherein two of the membrane modules ofFIG. 3 have been integrated into a DOAS but wherein the heat transfer fluid and the desiccant that were two separate fluids inFIGS. 1, 2 and 3 (the desiccant—labeled 114 and 115 inFIG. 1 —is typically a lithium chloride/water solution and the heat transfer fluid—labeled 110 inFIG. 1 is typically water or a water/glycol mixture) are combined in a single fluid (which would typically be lithium chloride and water, but any suitable liquid desiccant will do). By using a single fluid the pumping system can be simplified because the desiccant pump (for example 632 inFIG. 6 ), can be eliminated. However, it is desirable to still maintain a counter-flow arrangement between theair stream 1501 and/or 1502 and theheat transfer path 1505 and/or 1506. In two-way membrane modules the desiccant is oftentimes not able to maintain a counter-flow path to the air stream, since the desiccant generally moves vertical with gravity and the air stream often is desired to be horizontal resulting in a cross-flow arrangement. As described in application 61/951,887 (for example inFIG. 400 andFIG. 900 ), in a 3-way membrane module, it is possible to create a counter-flow between the air stream and a heat transfer fluid stream, while a small desiccant stream (typically 5-10% of the mass flow of the heat transfer fluid stream) is mostly absorbing or desorbing the latent energy from or to the air stream. By using the same fluid for the latent absorption and the heat transfer but having separate paths for each, one can obtain a much better efficiency of the membrane module since the primary air and heat transfer fluid flows are arranged in a counter-flow arrangement, and the small desiccant stream that is absorbing or desorbing the latent energy may still be in a cross-flow arrangement, but because the mass flow rate of the small desiccant stream is small, the effect on efficiency is negligible. - Specifically, in
FIG. 15 , anair stream 1501 which can be outside air, or return air from a space or a mixture between the two, is directed over amembrane structure 1503. Themembrane structure 1503 is the same structure fromFIG. 3 . However, the membrane structure (only a single plate structure is shown although generally multiple plate structures would be used in parallel) is now supplied bypump 1509 with alarge desiccant stream 1511 throughtank 1513. This large desiccant stream runs in theheat transfer channel 1505 counter to theair stream 1501. Asmaller desiccant stream 1515 is also simultaneously pumped by thepump 1509 to the top of themembrane plate structures 1503 where it flows by gravity behind themembranes 1532 inflow channel 1507. Theflow channel 1507 is generally vertical; however theheat transfer channel 1505 can be either vertical or horizontal, depending on whether theair stream 1501 is vertical or horizontal. The desiccant exiting theheat transfer channel 1505 is now directed to acondenser heat exchanger 1517, which, because of the corrosive nature of most liquid desiccants such as lithium chloride, is usually made from Titanium or some other non-corrosive material. To prevent excessive pressure behind themembranes 1532, anoverflow device 1528 can be employed that results in excess desiccant being drained throughtube 1529 back to thetank 1513. Desiccant that has desorbed latent energy into theair stream 1501 is now directed throughdrain line 1519 throughheat exchanger 1521 to pump 1508. - The
heat exchanger 1517 is part of a heatpump comprising compressor 1523,hot gas line 1524,liquid line 1525,expansion valve 1522,cold liquid line 1526,evaporator heat exchanger 1518 andgas line 1527 which directs a refrigerant back to thecompressor 1523. The heat pump assembly can be reversible as described earlier for allowing switching between a summer operation mode and a winter operation mode. - Further, in
FIG. 15 , asecond air stream 1502 which can also be outside air, or return air from a space or a mixture between the two, is directed over asecond membrane structure 1504. Themembrane structure 1504 is the same structure fromFIG. 3 . However, the membrane structure (only a single plate structure is shown although generally multiple plate structures would be used in parallel) is now supplied bypump 1510 with alarge desiccant stream 1512 throughtank 1514. This large desiccant stream runs inheat transfer channel 1506 counter to theair stream 1502. Asmaller desiccant stream 1516 is also pumped by thepump 1510 to the top of themembrane plate structures 1504 where it flows by gravity behind themembranes 1533 inflow channel 1508. Theflow channel 1508 is generally vertical; however theheat transfer channel 1506 can be either vertical or horizontal, depending on whether theair stream 1502 is vertical or horizontal. The desiccant exiting theheat transfer channel 1506 is now directed to aevaporator heat exchanger 1518, which, because of the corrosive nature of most liquid desiccants such as lithium chloride, is usually made from Titanium or some other non-corrosive material. To prevent excessive pressure behind themembranes 1533, anoverflow device 1531 can be employed that results in excess desiccant being drained throughtube 1530 back to thetank 1514. Desiccant that has absorbed latent energy from theair stream 1502 is now directed throughdrain line 1520 throughheat exchanger 1521 to pump 1509. - The structure described above has several advantages in that the pressure on the
membranes channels main desiccant streams air flow membrane plate structures -
FIG. 16 illustrates how the system fromFIG. 15 can be integrated to the system inFIG. 6 (orFIG. 7 for winter mode). The major components fromFIG. 15 are labeled in the figure as are the components fromFIG. 6 . As can be seen in the figure, thesystem 1600A is added as an outside air treatment system where the outside air OA (1502) is directed over theconditioner membrane plates 1504. As before, themain desiccant stream 1506 is pumped bypump 1510 in counter-flow to theair stream 1502 and thesmall desiccant stream 1508 is carrying off the latent energy from theair stream 1502. The small desiccant stream is directed throughheat exchanger 1521 to pump 1509 where it is pumped through regeneratormembrane plate structure 1503. Themain desiccant stream 1505 is again counter to theair stream 1501, which comprises anoutside air stream 1601 mixed with areturn air stream 605. Asmall desiccant stream 1507 is now used to desorb moisture from the desiccant. As before inFIG. 6 , the system ofFIG. 16 is reversible by reversing the direction of the heat pumpsystem comprising compressor 1523,heat exchangers expansion valve 625. - It should also be clear from
FIG. 16 that a conventional two-way liquid desiccant module could be employed in lieu ofmodules - Having thus described several illustrative embodiments, it is to be appreciated that various alterations, modifications, and improvements will readily occur to those skilled in the art. Such alterations, modifications, and improvements are intended to form a part of this disclosure, and are intended to be within the spirit and scope of this disclosure. While some examples presented herein involve specific combinations of functions or structural elements, it should be understood that those functions and elements may be combined in other ways according to the present disclosure to accomplish the same or different objectives. In particular, acts, elements, and features discussed in connection with one embodiment are not intended to be excluded from similar or other roles in other embodiments. Additionally, elements and components described herein may be further divided into additional components or joined together to form fewer components for performing the same functions. Accordingly, the foregoing description and attached drawings are by way of example only, and are not intended to be limiting.
Claims (22)
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Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10753624B2 (en) | 2010-05-25 | 2020-08-25 | 7Ac Technologies, Inc. | Desiccant air conditioning methods and systems using evaporative chiller |
US10760830B2 (en) | 2013-03-01 | 2020-09-01 | 7Ac Technologies, Inc. | Desiccant air conditioning methods and systems |
US10921001B2 (en) | 2017-11-01 | 2021-02-16 | 7Ac Technologies, Inc. | Methods and apparatus for uniform distribution of liquid desiccant in membrane modules in liquid desiccant air-conditioning systems |
US10941948B2 (en) | 2017-11-01 | 2021-03-09 | 7Ac Technologies, Inc. | Tank system for liquid desiccant air conditioning system |
US11022330B2 (en) | 2018-05-18 | 2021-06-01 | Emerson Climate Technologies, Inc. | Three-way heat exchangers for liquid desiccant air-conditioning systems and methods of manufacture |
US11098909B2 (en) | 2012-06-11 | 2021-08-24 | Emerson Climate Technologies, Inc. | Methods and systems for turbulent, corrosion resistant heat exchangers |
WO2021252464A1 (en) * | 2020-06-08 | 2021-12-16 | United States Of America As Represented By The Administrator Of Nasa | Systems and methods for oxygen concentration with electrochemical stacks in series gas flow |
US20230194108A1 (en) * | 2021-12-17 | 2023-06-22 | Emerson Climate Technologies, Inc. | Conditioning system including vapor compression system and humidity control system |
Families Citing this family (27)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9506697B2 (en) | 2012-12-04 | 2016-11-29 | 7Ac Technologies, Inc. | Methods and systems for cooling buildings with large heat loads using desiccant chillers |
WO2014152888A1 (en) | 2013-03-14 | 2014-09-25 | 7 Ac Technologies, Inc. | Methods and systems for liquid desiccant air conditioning system retrofit |
CN105121979B (en) * | 2013-03-14 | 2017-06-16 | 7Ac技术公司 | For the method and system of differential body liquid drier air adjustment |
ES2759926T3 (en) | 2013-06-12 | 2020-05-12 | 7Ac Tech Inc | Liquid Desiccant Air Conditioning System |
EP3120083B1 (en) | 2014-03-20 | 2020-07-01 | 7AC Technologies, Inc. | Rooftop liquid desiccant systems and methods |
KR20150141064A (en) * | 2014-06-09 | 2015-12-17 | 한국과학기술연구원 | Desiccant cooling system |
CA2897710C (en) * | 2014-07-22 | 2018-11-06 | Johnson Controls Technology Company | System and method for continuously removing a particular type of gas molecules from a gas stream |
WO2016081933A1 (en) | 2014-11-21 | 2016-05-26 | 7Ac Technologies, Inc. | Methods and systems for mini-split liquid desiccant air conditioning |
GB2547456B (en) * | 2016-02-18 | 2018-09-19 | Chilltechnologies Ltd | An absorption chiller |
US11391474B2 (en) * | 2016-08-04 | 2022-07-19 | Energy Wall Llc | System, components, and methods for air, heat, and humidity exchanger |
DE102016122965A1 (en) * | 2016-11-29 | 2018-05-30 | Autefa Solutions Germany Gmbh | Textile fiber drying |
JP2018118246A (en) * | 2017-01-26 | 2018-08-02 | ダイキン工業株式会社 | Humidity controller |
CN108507047B (en) * | 2017-02-28 | 2020-10-02 | 青岛海尔智能技术研发有限公司 | Air conditioning system and control method thereof |
DE102017212412A1 (en) | 2017-07-19 | 2019-01-24 | Weiss Umwelttechnik Gmbh | Humidifier and method for conditioning air |
WO2019089980A1 (en) * | 2017-11-01 | 2019-05-09 | 7Ac Technologies, Inc. | Methods and systems for liquid desiccant air conditioning |
US10722839B2 (en) * | 2018-01-26 | 2020-07-28 | Ingersoll-Rand Industrial U.S., Inc. | Parallel split flow combination gas dryer |
US11648506B2 (en) | 2018-02-07 | 2023-05-16 | Palo Alto Research Center Incorporated | Electrochemical desalination system |
US10941961B2 (en) * | 2018-05-22 | 2021-03-09 | Johnson Controls Technology Company | Ultrasonic condensate management system and method |
CN108954527A (en) * | 2018-08-16 | 2018-12-07 | 中山路得斯空调有限公司 | System for small split type liquid dehumidification air conditioner and use method thereof |
US20220003435A1 (en) * | 2018-12-04 | 2022-01-06 | Nortek Air Solutions Canada, Inc. | Systems and methods for air dehumidification in an enclosed space |
JP7185773B2 (en) * | 2019-04-23 | 2022-12-07 | シャープ株式会社 | Humidity control device |
KR102524857B1 (en) * | 2020-08-24 | 2023-04-24 | 원철호 | Geothermal heat pump system and control method thereof |
US20220082268A1 (en) * | 2020-09-11 | 2022-03-17 | Waterfurnace International, Inc. | Variable capacity heat pump system |
US20220243932A1 (en) * | 2021-01-29 | 2022-08-04 | Palo Alto Research Center Incorporated | Electrochemical dehumidifier with multiple air contactors |
US11872528B2 (en) | 2021-11-09 | 2024-01-16 | Xerox Corporation | System and method for separating solvent from a fluid |
US11944934B2 (en) | 2021-12-22 | 2024-04-02 | Mojave Energy Systems, Inc. | Electrochemically regenerated liquid desiccant dehumidification system using a secondary heat pump |
US20230332779A1 (en) * | 2022-04-19 | 2023-10-19 | Emerson Climate Technologies, Inc. | Desiccant heat exchanger for high efficiency dehumidification |
Family Cites Families (298)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1791086A (en) | 1926-10-11 | 1931-02-03 | Koppers Co Inc | Process for dehydrating gas |
US2221787A (en) | 1936-08-31 | 1940-11-19 | Calorider Corp | Method and apparatus for conditioning air and other gases |
US2235322A (en) | 1940-01-29 | 1941-03-18 | J F Pritchard & Company | Air drying |
US2433741A (en) | 1943-02-13 | 1947-12-30 | Robert B P Crawford | Chemical dehumidifying method and means |
US2634958A (en) | 1948-12-03 | 1953-04-14 | Modine Mfg Co | Heat exchanger |
US2660159A (en) | 1950-06-30 | 1953-11-24 | Surface Combustion Corp | Unit heater with draft hood |
US2708915A (en) | 1952-11-13 | 1955-05-24 | Manville Boiler Co Inc | Crossed duct vertical boiler construction |
US2939686A (en) | 1955-02-04 | 1960-06-07 | Cherry Burrell Corp | Double port heat exchanger plate |
US2988171A (en) | 1959-01-29 | 1961-06-13 | Dow Chemical Co | Salt-alkylene glycol dew point depressant |
US3119446A (en) | 1959-09-17 | 1964-01-28 | American Thermocatalytic Corp | Heat exchangers |
GB990459A (en) | 1960-06-24 | 1965-04-28 | Arnot Alfred E R | Improvements in or relating to water dispensers |
US3193001A (en) | 1963-02-05 | 1965-07-06 | Lithonia Lighting Inc | Comfort conditioning system |
US3409969A (en) | 1965-06-28 | 1968-11-12 | Westinghouse Electric Corp | Method of explosively welding tubes to tube plates |
GB1172247A (en) | 1966-04-20 | 1969-11-26 | Apv Co Ltd | Improvements in or relating to Plate Heat Exchangers |
US3410581A (en) | 1967-01-26 | 1968-11-12 | Young Radiator Co | Shell-and-tube type heat-exchanger |
US3455338A (en) | 1967-06-19 | 1969-07-15 | Walter M Pollit | Composite pipe composition |
US3718181A (en) | 1970-08-17 | 1973-02-27 | Du Pont | Plastic heat exchange apparatus |
US4100331A (en) | 1977-02-03 | 1978-07-11 | Nasa | Dual membrane, hollow fiber fuel cell and method of operating same |
FR2405081A1 (en) | 1977-10-06 | 1979-05-04 | Commissariat Energie Atomique | GAS SEPARATION PROCESS IN A MIXTURE |
US4164125A (en) * | 1977-10-17 | 1979-08-14 | Midland-Ross Corporation | Solar energy assisted air-conditioning apparatus and method |
US4176523A (en) | 1978-02-17 | 1979-12-04 | The Garrett Corporation | Adsorption air conditioner |
US4209368A (en) | 1978-08-07 | 1980-06-24 | General Electric Company | Production of halogens by electrolysis of alkali metal halides in a cell having catalytic electrodes bonded to the surface of a porous membrane/separator |
US4222244A (en) | 1978-11-07 | 1980-09-16 | Gershon Meckler Associates, P.C. | Air conditioning apparatus utilizing solar energy and method |
US4205529A (en) | 1978-12-04 | 1980-06-03 | The United States Of America As Represented By The United States Department Of Energy | LiCl Dehumidifier LiBr absorption chiller hybrid air conditioning system with energy recovery |
US4259849A (en) | 1979-02-15 | 1981-04-07 | Midland-Ross Corporation | Chemical dehumidification system which utilizes a refrigeration unit for supplying energy to the system |
US4324947A (en) | 1979-05-16 | 1982-04-13 | Dumbeck Robert F | Solar energy collector system |
US4435339A (en) | 1979-08-06 | 1984-03-06 | Tower Systems, Inc. | Falling film heat exchanger |
US4235221A (en) | 1979-08-23 | 1980-11-25 | Murphy Gerald G | Solar energy system and apparatus |
US4882907A (en) | 1980-02-14 | 1989-11-28 | Brown Ii William G | Solar power generation |
US4444992A (en) | 1980-11-12 | 1984-04-24 | Massachusetts Institute Of Technology | Photovoltaic-thermal collectors |
US4429545A (en) | 1981-08-03 | 1984-02-07 | Ocean & Atmospheric Science, Inc. | Solar heating system |
US4399862A (en) | 1981-08-17 | 1983-08-23 | Carrier Corporation | Method and apparatus for proven demand air conditioning control |
US4730600A (en) | 1981-12-16 | 1988-03-15 | The Coleman Company, Inc. | Condensing furnace |
US4612019A (en) | 1982-07-22 | 1986-09-16 | The Dow Chemical Company | Method and device for separating water vapor from air |
US5020333A (en) * | 1982-07-30 | 1991-06-04 | Geophysical Engineering Company | Method of and means for controlling the condition of air in an enclosure |
JPS6099328A (en) | 1983-11-04 | 1985-06-03 | Toyota Central Res & Dev Lab Inc | Separating apparatus for condensable gas |
US5181387A (en) | 1985-04-03 | 1993-01-26 | Gershon Meckler | Air conditioning apparatus |
US4786301A (en) | 1985-07-01 | 1988-11-22 | Rhodes Barry V | Desiccant air conditioning system |
US4649899A (en) | 1985-07-24 | 1987-03-17 | Moore Roy A | Solar tracker |
US4607132A (en) | 1985-08-13 | 1986-08-19 | Jarnagin William S | Integrated PV-thermal panel and process for production |
US4766952A (en) | 1985-11-15 | 1988-08-30 | The Furukawa Electric Co., Ltd. | Waste heat recovery apparatus |
US4660390A (en) | 1986-03-25 | 1987-04-28 | Worthington Mark N | Air conditioner with three stages of indirect regeneration |
JPS62297647A (en) | 1986-06-18 | 1987-12-24 | Ohbayashigumi Ltd | Dehumidification system of building |
US4987750A (en) | 1986-07-08 | 1991-01-29 | Gershon Meckler | Air conditioning apparatus |
US4832115A (en) | 1986-07-09 | 1989-05-23 | Albers Technologies Corporation | Method and apparatus for simultaneous heat and mass transfer |
US4744414A (en) | 1986-09-02 | 1988-05-17 | Arco Chemical Company | Plastic film plate-type heat exchanger |
US4691530A (en) | 1986-09-05 | 1987-09-08 | Milton Meckler | Cogeneration and central regeneration multi-contactor air conditioning system |
WO1988003253A1 (en) | 1986-10-22 | 1988-05-05 | Alfa-Laval Thermal Ab | Plate heat exchanger with a double-wall structure |
US4703629A (en) | 1986-12-15 | 1987-11-03 | Moore Roy A | Solar cooling apparatus |
US4910971A (en) | 1988-02-05 | 1990-03-27 | Hydro Thermal Engineering Pty. Ltd. | Indirect air conditioning system |
US4900448A (en) | 1988-03-29 | 1990-02-13 | Honeywell Inc. | Membrane dehumidification |
US5605628A (en) | 1988-05-24 | 1997-02-25 | North West Water Group Plc | Composite membranes |
US4872578A (en) | 1988-06-20 | 1989-10-10 | Itt Standard Of Itt Corporation | Plate type heat exchanger |
SE464853B (en) | 1988-08-01 | 1991-06-24 | Ahlstroem Foeretagen | PROCEDURE FOR DEHUMATING A GAS, SPECIAL AIR |
US4971142A (en) | 1989-01-03 | 1990-11-20 | The Air Preheater Company, Inc. | Heat exchanger and heat pipe therefor |
US4955205A (en) | 1989-01-27 | 1990-09-11 | Gas Research Institute | Method of conditioning building air |
US4887438A (en) | 1989-02-27 | 1989-12-19 | Milton Meckler | Desiccant assisted air conditioner |
US4966007A (en) | 1989-05-12 | 1990-10-30 | Baltimore Aircoil Company, Inc. | Absorption refrigeration method and apparatus |
US4939906A (en) | 1989-06-09 | 1990-07-10 | Gas Research Institute | Multi-stage boiler/regenerator for liquid desiccant dehumidifiers |
JPH0391660A (en) | 1989-09-04 | 1991-04-17 | Nishiyodo Kuuchiyouki Kk | Adsorption type heat storage device and adsorption type heat storage system with the same device |
US4941324A (en) | 1989-09-12 | 1990-07-17 | Peterson John L | Hybrid vapor-compression/liquid desiccant air conditioner |
US4984434A (en) * | 1989-09-12 | 1991-01-15 | Peterson John L | Hybrid vapor-compression/liquid desiccant air conditioner |
JPH0759996B2 (en) | 1989-10-09 | 1995-06-28 | ダイキン工業株式会社 | Humidity controller |
JPH03213921A (en) | 1990-01-18 | 1991-09-19 | Mitsubishi Electric Corp | Air-conditioner with display screen |
JPH04273555A (en) | 1991-02-28 | 1992-09-29 | Nec Corp | Commitment system |
US5471852A (en) | 1991-07-05 | 1995-12-05 | Meckler; Milton | Polymer enhanced glycol desiccant heat-pipe air dehumidifier preconditioning system |
US5191771A (en) | 1991-07-05 | 1993-03-09 | Milton Meckler | Polymer desiccant and system for dehumidified air conditioning |
US5221520A (en) | 1991-09-27 | 1993-06-22 | North Carolina Center For Scientific Research, Inc. | Apparatus for treating indoor air |
US5186903A (en) | 1991-09-27 | 1993-02-16 | North Carolina Center For Scientific Research, Inc. | Apparatus for treating indoor air |
US5182921A (en) | 1992-04-10 | 1993-02-02 | Industrial Technology Research Institute | Solar dehumidifier |
JPH0674522A (en) | 1992-06-26 | 1994-03-15 | Sanyo Electric Co Ltd | Controlling method for air conditioner |
US5582026A (en) | 1992-07-07 | 1996-12-10 | Barto, Sr.; Stephen W. | Air conditioning system |
US5351497A (en) | 1992-12-17 | 1994-10-04 | Gas Research Institute | Low-flow internally-cooled liquid-desiccant absorber |
US5448895A (en) | 1993-01-08 | 1995-09-12 | Engelhard/Icc | Hybrid heat pump and desiccant space conditioning system and control method |
US5361828A (en) | 1993-02-17 | 1994-11-08 | General Electric Company | Scaled heat transfer surface with protruding ramp surface turbulators |
US5534186A (en) | 1993-12-15 | 1996-07-09 | Gel Sciences, Inc. | Gel-based vapor extractor and methods |
GB9405249D0 (en) | 1994-03-17 | 1994-04-27 | Smithkline Beecham Plc | Container |
DE4409848A1 (en) | 1994-03-22 | 1995-10-19 | Siemens Ag | Device for metering and atomizing fluids |
US5528905A (en) * | 1994-03-25 | 1996-06-25 | Essex Invention S.A. | Contactor, particularly a vapour exchanger for the control of the air hygrometric content, and a device for air handling |
AUPM592694A0 (en) | 1994-05-30 | 1994-06-23 | F F Seeley Nominees Pty Ltd | Vacuum dewatering of desiccant brines |
US5462113A (en) | 1994-06-20 | 1995-10-31 | Flatplate, Inc. | Three-circuit stacked plate heat exchanger |
CA2127525A1 (en) | 1994-07-06 | 1996-01-07 | Leofred Caron | Portable air cooler |
JPH08105669A (en) | 1994-10-04 | 1996-04-23 | Tokyo Gas Co Ltd | Regenerator for absorption refrigerator |
US5638900A (en) | 1995-01-27 | 1997-06-17 | Ail Research, Inc. | Heat exchange assembly |
US5685152A (en) | 1995-04-19 | 1997-11-11 | Sterling; Jeffrey S. | Apparatus and method for converting thermal energy to mechanical energy |
US6018954A (en) | 1995-04-20 | 2000-02-01 | Assaf; Gad | Heat pump system and method for air-conditioning |
US5661983A (en) | 1995-06-02 | 1997-09-02 | Energy International, Inc. | Fluidized bed desiccant cooling system |
TR199800400T1 (en) | 1995-09-06 | 1998-05-21 | Universal Air Technology, Inc | Photocatalytic air disinfection. |
US5901783A (en) | 1995-10-12 | 1999-05-11 | Croyogen, Inc. | Cryogenic heat exchanger |
US6004691A (en) | 1995-10-30 | 1999-12-21 | Eshraghi; Ray R. | Fibrous battery cells |
NL1001834C2 (en) | 1995-12-06 | 1997-06-10 | Indupal B V | Flow-through heat exchanger, device comprising it and evaporation device. |
US5641337A (en) | 1995-12-08 | 1997-06-24 | Permea, Inc. | Process for the dehydration of a gas |
US5595690A (en) | 1995-12-11 | 1997-01-21 | Hamilton Standard | Method for improving water transport and reducing shrinkage stress in membrane humidifying devices and membrane humidifying devices |
JPH09184692A (en) | 1995-12-28 | 1997-07-15 | Ebara Corp | Heat exchanging element |
US5816065A (en) | 1996-01-12 | 1998-10-06 | Ebara Corporation | Desiccant assisted air conditioning system |
US5950442A (en) | 1996-05-24 | 1999-09-14 | Ebara Corporation | Air conditioning system |
US6083387A (en) | 1996-06-20 | 2000-07-04 | Burnham Technologies Ltd. | Apparatus for the disinfection of fluids |
US5860284A (en) * | 1996-07-19 | 1999-01-19 | Novel Aire Technologies, L.L.C. | Thermally regenerated desiccant air conditioner with indirect evaporative cooler |
JPH10220914A (en) | 1997-02-07 | 1998-08-21 | Osaka Gas Co Ltd | Plate type evaporator and absorbing device of absorbing type freezer |
US5860285A (en) | 1997-06-06 | 1999-01-19 | Carrier Corporation | System for monitoring outdoor heat exchanger coil |
US6012296A (en) | 1997-08-28 | 2000-01-11 | Honeywell Inc. | Auctioneering temperature and humidity controller with reheat |
WO1999015848A1 (en) | 1997-09-19 | 1999-04-01 | Millipore Corporation | Heat exchange apparatus |
JPH11132500A (en) * | 1997-10-24 | 1999-05-21 | Ebara Corp | Dehumidifying air conditioner |
IL122065A (en) | 1997-10-29 | 2000-12-06 | Agam Energy Systems Ltd | Heat pump/engine system and a method utilizing same |
JPH11137948A (en) | 1997-11-07 | 1999-05-25 | Daikin Ind Ltd | Dehumidifier |
IL141579A0 (en) | 2001-02-21 | 2002-03-10 | Drykor Ltd | Dehumidifier/air-conditioning system |
AU4963397A (en) * | 1997-11-16 | 1999-06-07 | Drykor Ltd. | Dehumidifier system |
US6134903A (en) | 1997-12-04 | 2000-10-24 | Fedders Corporation | Portable liquid desiccant dehumidifier |
US6138470A (en) | 1997-12-04 | 2000-10-31 | Fedders Corporation | Portable liquid desiccant dehumidifier |
US6216489B1 (en) | 1997-12-04 | 2001-04-17 | Fedders Corporation | Liquid desiccant air conditioner |
US6216483B1 (en) | 1997-12-04 | 2001-04-17 | Fedders Corporation | Liquid desiccant air conditioner |
JPH11197439A (en) | 1998-01-14 | 1999-07-27 | Ebara Corp | Dehumidification air-conditioner |
US6171374B1 (en) | 1998-05-29 | 2001-01-09 | Ballard Power Systems Inc. | Plate and frame fluid exchanging assembly with unitary plates and seals |
JP3305653B2 (en) | 1998-06-08 | 2002-07-24 | 大阪瓦斯株式会社 | Plate type evaporator and absorber of absorption refrigerator |
WO2000000774A1 (en) * | 1998-06-30 | 2000-01-06 | Ebara Corporation | Heat exchanger, heat pump, dehumidifier, and dehumidifying method |
IL125927A0 (en) | 1998-08-25 | 1999-04-11 | Agam Energy Systems Ltd | An evaporative media and a cooling tower utilizing same |
US6417423B1 (en) | 1998-09-15 | 2002-07-09 | Nanoscale Materials, Inc. | Reactive nanoparticles as destructive adsorbents for biological and chemical contamination |
US6488900B1 (en) | 1998-10-20 | 2002-12-03 | Mesosystems Technology, Inc. | Method and apparatus for air purification |
US6156102A (en) | 1998-11-10 | 2000-12-05 | Fantom Technologies Inc. | Method and apparatus for recovering water from air |
JP4273555B2 (en) | 1999-02-08 | 2009-06-03 | ダイキン工業株式会社 | Air conditioning system |
US6199388B1 (en) * | 1999-03-10 | 2001-03-13 | Semco Incorporated | System and method for controlling temperature and humidity |
JP4359398B2 (en) * | 1999-03-14 | 2009-11-04 | ドライコー リミテッド | Dehumidification / air conditioning system |
US6513339B1 (en) | 1999-04-16 | 2003-02-04 | Work Smart Energy Enterprises, Inc. | Solar air conditioner |
US20030000230A1 (en) | 1999-06-25 | 2003-01-02 | Kopko William L. | High-efficiency air handler |
KR100338794B1 (en) | 1999-08-16 | 2002-05-31 | 김병주 | Falling film-type heat and mass exchanger using capillary force |
US6723441B1 (en) | 1999-09-22 | 2004-04-20 | Nkk Corporation | Resin film laminated metal sheet for can and method for fabricating the same |
US6684649B1 (en) | 1999-11-05 | 2004-02-03 | David A. Thompson | Enthalpy pump |
US6244062B1 (en) | 1999-11-29 | 2001-06-12 | David Prado | Solar collector system |
US6103969A (en) | 1999-11-29 | 2000-08-15 | Bussey; Clifford | Solar energy collector |
US6926068B2 (en) | 2000-01-13 | 2005-08-09 | Denso Corporation | Air passage switching device and vehicle air conditioner |
JP3927344B2 (en) | 2000-01-19 | 2007-06-06 | 本田技研工業株式会社 | Humidifier |
IL134196A (en) | 2000-01-24 | 2003-06-24 | Agam Energy Systems Ltd | System for dehumidification of air in an enclosure |
DE10026344A1 (en) | 2000-04-01 | 2001-10-04 | Membraflow Gmbh & Co Kg Filter | Filter module |
US6568466B2 (en) | 2000-06-23 | 2003-05-27 | Andrew Lowenstein | Heat exchange assembly |
US6497107B2 (en) | 2000-07-27 | 2002-12-24 | Idalex Technologies, Inc. | Method and apparatus of indirect-evaporation cooling |
US6453678B1 (en) | 2000-09-05 | 2002-09-24 | Kabin Komfort Inc | Direct current mini air conditioning system |
US6592515B2 (en) | 2000-09-07 | 2003-07-15 | Ams Research Corporation | Implantable article and method |
US7197887B2 (en) | 2000-09-27 | 2007-04-03 | Idalex Technologies, Inc. | Method and plate apparatus for dew point evaporative cooler |
US6514321B1 (en) | 2000-10-18 | 2003-02-04 | Powermax, Inc. | Dehumidification using desiccants and multiple effect evaporators |
CA2428280A1 (en) | 2000-11-13 | 2002-05-16 | Mcmaster University | Gas separation device |
US6739142B2 (en) | 2000-12-04 | 2004-05-25 | Amos Korin | Membrane desiccation heat pump |
JP3348848B2 (en) | 2000-12-28 | 2002-11-20 | 株式会社西部技研 | Indirect evaporative cooling system |
JP5189719B2 (en) | 2001-01-22 | 2013-04-24 | 本田技研工業株式会社 | Fuel cell system |
US6557365B2 (en) * | 2001-02-28 | 2003-05-06 | Munters Corporation | Desiccant refrigerant dehumidifier |
US6711907B2 (en) | 2001-02-28 | 2004-03-30 | Munters Corporation | Desiccant refrigerant dehumidifier systems |
CN101022879A (en) | 2001-03-13 | 2007-08-22 | 戴斯-分析公司 | Heat and moisture exchange device |
US6497749B2 (en) | 2001-03-30 | 2002-12-24 | United Technologies Corporation | Dehumidification process and apparatus using collodion membrane |
JP3765531B2 (en) | 2001-03-30 | 2006-04-12 | 本田技研工業株式会社 | Humidification module |
US6539731B2 (en) | 2001-03-30 | 2003-04-01 | Arthus S. Kesten | Dehumidification process and apparatus |
JP4732609B2 (en) | 2001-04-11 | 2011-07-27 | 株式会社ティラド | Heat exchanger core |
MXPA03009675A (en) | 2001-04-23 | 2004-05-24 | Drykor Ltd | Apparatus for conditioning air. |
FR2823995B1 (en) | 2001-04-25 | 2008-06-06 | Alfa Laval Vicarb | IMPROVED DEVICE FOR EXCHANGING AND / OR REACTING BETWEEN FLUIDS |
IL144119A (en) | 2001-07-03 | 2006-07-05 | Gad Assaf | Air conditioning system |
US6660069B2 (en) | 2001-07-23 | 2003-12-09 | Toyota Jidosha Kabushiki Kaisha | Hydrogen extraction unit |
US6766817B2 (en) | 2001-07-25 | 2004-07-27 | Tubarc Technologies, Llc | Fluid conduction utilizing a reversible unsaturated siphon with tubarc porosity action |
AU2002331628A1 (en) | 2001-08-20 | 2003-03-03 | Idalex Technologies, Inc. | Method of evaporative cooling of a fluid and apparatus therefor |
US6595020B2 (en) | 2001-09-17 | 2003-07-22 | David I. Sanford | Hybrid powered evaporative cooler and method therefor |
JP2003161465A (en) | 2001-11-26 | 2003-06-06 | Daikin Ind Ltd | Humidity conditioning device |
WO2003056249A1 (en) | 2001-12-27 | 2003-07-10 | Drykor Ltd. | High efficiency dehumidifiers and combined dehumidifying/air-conditioning systems |
US6938434B1 (en) | 2002-01-28 | 2005-09-06 | Shields Fair | Cooling system |
US6848265B2 (en) | 2002-04-24 | 2005-02-01 | Ail Research, Inc. | Air conditioning system |
CA2384712A1 (en) | 2002-05-03 | 2003-11-03 | Michel St. Pierre | Heat exchanger with nest flange-formed passageway |
US20050218535A1 (en) | 2002-08-05 | 2005-10-06 | Valeriy Maisotsenko | Indirect evaporative cooling mechanism |
US20040061245A1 (en) | 2002-08-05 | 2004-04-01 | Valeriy Maisotsenko | Indirect evaporative cooling mechanism |
SE523674C2 (en) | 2002-09-10 | 2004-05-11 | Alfa Laval Corp Ab | Flat heat exchanger with two separate draw plates and method of manufacturing the same |
US7448441B2 (en) | 2002-09-17 | 2008-11-11 | Alliance For Sustainable Energy, Llc | Carbon nanotube heat-exchange systems |
KR20040026242A (en) | 2002-09-23 | 2004-03-31 | 주식회사 에어필 | Liquid dessicant cooling system using heat pump |
NL1022794C2 (en) | 2002-10-31 | 2004-09-06 | Oxycell Holding Bv | Method for manufacturing a heat exchanger, as well as heat exchanger obtained with the method. |
IL152885A0 (en) | 2002-11-17 | 2003-06-24 | Agam Energy Systems Ltd | Air conditioning systems and methods |
ES2301696T3 (en) | 2002-12-02 | 2008-07-01 | Lg Electronics Inc. | THERMAL EXCHANGER OF A VENTILATION SYSTEM. |
US6837056B2 (en) | 2002-12-19 | 2005-01-04 | General Electric Company | Turbine inlet air-cooling system and method |
KR100463550B1 (en) | 2003-01-14 | 2004-12-29 | 엘지전자 주식회사 | cooling and heating system |
US7306650B2 (en) | 2003-02-28 | 2007-12-11 | Midwest Research Institute | Using liquid desiccant as a regenerable filter for capturing and deactivating contaminants |
MXPA05010972A (en) | 2003-04-16 | 2006-03-08 | James J Reidy | Thermoelectric, high-efficiency, water generating device. |
US6986428B2 (en) | 2003-05-14 | 2006-01-17 | 3M Innovative Properties Company | Fluid separation membrane module |
DE10324300B4 (en) | 2003-05-21 | 2006-06-14 | Thomas Dr. Weimer | Thermodynamic machine and method for absorbing heat |
AU2004243388B2 (en) | 2003-05-26 | 2010-09-16 | Logos-Innovationen Gmbh | Device for the extraction of water from atmospheric air |
KR100510774B1 (en) | 2003-05-26 | 2005-08-30 | 한국생산기술연구원 | Hybrid dehumidified cooling system |
US6854279B1 (en) | 2003-06-09 | 2005-02-15 | The United States Of America As Represented By The Secretary Of The Navy | Dynamic desiccation cooling system for ships |
ITTO20030547A1 (en) | 2003-07-15 | 2005-01-16 | Fiat Ricerche | AIR CONDITIONING SYSTEM WITH A COMPRESSION CIRCUIT |
US20050109052A1 (en) | 2003-09-30 | 2005-05-26 | Albers Walter F. | Systems and methods for conditioning air and transferring heat and mass between airflows |
JP4341373B2 (en) | 2003-10-31 | 2009-10-07 | ダイキン工業株式会社 | Humidity control device |
US7258923B2 (en) | 2003-10-31 | 2007-08-21 | General Electric Company | Multilayered articles and method of manufacture thereof |
US7186084B2 (en) | 2003-11-19 | 2007-03-06 | General Electric Company | Hot gas path component with mesh and dimpled cooling |
US7279215B2 (en) | 2003-12-03 | 2007-10-09 | 3M Innovative Properties Company | Membrane modules and integrated membrane cassettes |
JP3668786B2 (en) | 2003-12-04 | 2005-07-06 | ダイキン工業株式会社 | Air conditioner |
US20050133082A1 (en) | 2003-12-20 | 2005-06-23 | Konold Annemarie H. | Integrated solar energy roofing construction panel |
JP4209339B2 (en) * | 2004-02-03 | 2009-01-14 | 独立行政法人科学技術振興機構 | Air humidity control medium and its use |
JP4200214B2 (en) * | 2004-02-04 | 2008-12-24 | 独立行政法人産業技術総合研究所 | Particle circulation adsorption heat pump |
US20050210907A1 (en) | 2004-03-17 | 2005-09-29 | Gillan Leland E | Indirect evaporative cooling of a gas using common product and working gas in a partial counterflow configuration |
CN1997861A (en) * | 2004-04-09 | 2007-07-11 | 艾尔研究公司 | Heat and mass exchanger |
WO2005114072A2 (en) | 2004-05-22 | 2005-12-01 | Gerald Landry | Desiccant-assisted air conditioning system and process |
US7143597B2 (en) | 2004-06-30 | 2006-12-05 | Speakman Company | Indirect-direct evaporative cooling system operable from sustainable energy source |
IL163015A (en) | 2004-07-14 | 2009-07-20 | Gad Assaf | Systems and methods for dehumidification |
US6935131B1 (en) * | 2004-09-09 | 2005-08-30 | Tom Backman | Desiccant assisted dehumidification system for aqueous based liquid refrigerant facilities |
CN101076701A (en) | 2004-10-12 | 2007-11-21 | Gpm股份有限公司 | Cooling assembly |
JP2006263508A (en) | 2005-03-22 | 2006-10-05 | Seiichiro Deguchi | Moisture absorbing device, drying box, air drier and air conditioner |
NL1030538C1 (en) | 2005-11-28 | 2007-05-30 | Eurocore Trading & Consultancy | Device for indirectly cooling an air stream through evaporation. |
MY151856A (en) | 2005-12-22 | 2014-07-14 | Oxycom Beheer Bv | Evaporative cooling device |
SE530820C2 (en) | 2005-12-22 | 2008-09-16 | Alfa Laval Corp Ab | A mixing system for heat exchangers |
US8648209B1 (en) | 2005-12-31 | 2014-02-11 | Joseph P. Lastella | Loop reactor for making biodiesel fuel |
US20090000732A1 (en) | 2006-01-17 | 2009-01-01 | Henkel Corporation | Bonded Fuel Cell Assembly, Methods, Systems and Sealant Compositions for Producing the Same |
US20070169916A1 (en) | 2006-01-20 | 2007-07-26 | Wand Steven M | Double-wall, vented heat exchanger |
US8623210B2 (en) | 2006-03-02 | 2014-01-07 | Sei-ichi Manabe | Pore diffusion type flat membrane separating apparatus |
US20090238685A1 (en) | 2006-05-08 | 2009-09-24 | Roland Santa Ana | Disguised air displacement device |
NL2000079C2 (en) | 2006-05-22 | 2007-11-23 | Statiqcooling B V | Enthalpy exchanger. |
JP2008020138A (en) | 2006-07-13 | 2008-01-31 | Daikin Ind Ltd | Humidity adjusting device |
US7758671B2 (en) | 2006-08-14 | 2010-07-20 | Nanocap Technologies, Llc | Versatile dehumidification process and apparatus |
CN100419340C (en) * | 2006-08-31 | 2008-09-17 | 上海理工大学 | Air condition system by using latent energy of exhaustion to retrieve liquid and extract moisture |
US20080085437A1 (en) | 2006-09-29 | 2008-04-10 | Dean James F | Pleated heat and humidity exchanger with flow field elements |
GB0622355D0 (en) | 2006-11-09 | 2006-12-20 | Oxycell Holding Bv | High efficiency heat exchanger and dehumidifier |
US20080127965A1 (en) | 2006-12-05 | 2008-06-05 | Andy Burton | Method and apparatus for solar heating air in a forced draft heating system |
WO2008083219A2 (en) | 2006-12-27 | 2008-07-10 | Dennis Mcguire | Portable, self-sustaining power station |
KR100826023B1 (en) | 2006-12-28 | 2008-04-28 | 엘지전자 주식회사 | Heat exchanger for a ventilating apparatus |
US8500960B2 (en) | 2007-01-20 | 2013-08-06 | Dais Analytic Corporation | Multi-phase selective mass transfer through a membrane |
US20080203866A1 (en) | 2007-01-26 | 2008-08-28 | Chamberlain Cliff S | Rooftop modular fan coil unit |
US20080302357A1 (en) | 2007-06-05 | 2008-12-11 | Denault Roger | Solar photovoltaic collector hybrid |
US20090056919A1 (en) | 2007-08-14 | 2009-03-05 | Prodigy Energy Recovery Systems Inc. | Heat exchanger |
US8268060B2 (en) * | 2007-10-15 | 2012-09-18 | Green Comfort Systems, Inc. | Dehumidifier system |
GB0720627D0 (en) | 2007-10-19 | 2007-11-28 | Applied Cooling Technology Ltd | Turbulator for heat exchanger tube and method of manufacture |
US20090200290A1 (en) | 2007-10-19 | 2009-08-13 | Paul Gregory Cardinal | Variable voltage load tap changing transformer |
US20090126913A1 (en) | 2007-11-16 | 2009-05-21 | Davis Energy Group, Inc. | Vertical counterflow evaporative cooler |
US8353175B2 (en) | 2008-01-08 | 2013-01-15 | Calvin Wade Wohlert | Roof top air conditioning units having a centralized refrigeration system |
EP2250446B1 (en) | 2008-01-25 | 2020-02-19 | Alliance for Sustainable Energy, LLC | Indirect evaporative cooler |
JP5294191B2 (en) | 2008-01-31 | 2013-09-18 | 国立大学法人東北大学 | Wet desiccant air conditioner |
FR2927422B1 (en) | 2008-02-08 | 2014-10-10 | R & I Alliance | DEVICE FOR SAMPLING A SAMPLE OF GAS, AND METHOD FOR RETURNING A SAMPLE DRAWN. |
JP5183236B2 (en) | 2008-02-12 | 2013-04-17 | 国立大学法人 東京大学 | Replacement air conditioning system |
DE102008022504B4 (en) | 2008-05-07 | 2012-11-29 | Airbus Operations Gmbh | Switchable vortex generator and array formed therewith and uses thereof |
JP4384699B2 (en) | 2008-05-22 | 2009-12-16 | ダイナエアー株式会社 | Humidity control device |
JP4374393B1 (en) | 2008-05-27 | 2009-12-02 | ダイナエアー株式会社 | Humidity control device |
JP2009293831A (en) | 2008-06-03 | 2009-12-17 | Dyna-Air Co Ltd | Humidity conditioning device |
JP2010002162A (en) | 2008-06-22 | 2010-01-07 | Kiyoshi Yanagimachi | Air conditioning facility |
KR20110034006A (en) * | 2008-06-24 | 2011-04-04 | 솔트워크스 테크놀로지스 인코포레이티드 | Method, apparatus and plant for desalinating saltwater using concentration difference energy |
US20100000247A1 (en) | 2008-07-07 | 2010-01-07 | Bhatti Mohinder S | Solar-assisted climate control system |
US8283555B2 (en) | 2008-07-30 | 2012-10-09 | Solaris Synergy Ltd. | Photovoltaic solar power generation system with sealed evaporative cooling |
US8887523B2 (en) | 2008-08-08 | 2014-11-18 | Khaled Gommed | Liquid desiccant dehumidification system and heat/mass exchanger therefor |
JP2010054136A (en) | 2008-08-28 | 2010-03-11 | Univ Of Tokyo | Dry type desiccant device and air heat source heat pump device |
US20100051083A1 (en) | 2008-09-03 | 2010-03-04 | Boyk Bill | Solar tracking platform with rotating truss |
US20100077783A1 (en) | 2008-09-30 | 2010-04-01 | Bhatti Mohinder S | Solid oxide fuel cell assisted air conditioning system |
US8550153B2 (en) | 2008-10-03 | 2013-10-08 | Modine Manufacturing Company | Heat exchanger and method of operating the same |
RU2529537C2 (en) | 2008-10-13 | 2014-09-27 | Шелл Интернэшнл Рисерч Маатсхаппий Б.В. | Systems for treatment of underground bed with circulating heat transfer fluid |
JP4502065B1 (en) | 2009-01-30 | 2010-07-14 | ダイキン工業株式会社 | Drainless air conditioner |
ITMI20090563A1 (en) | 2009-04-08 | 2010-10-09 | Donato Alfonso Di | HEATING AND / OR CONDITIONING AND / OR AIR TREATMENT WITH PHOTOCATALYTIC SUBSTANCES USING PHOTOVOLTAIC PLANTS WITH CONCENTRATION WITH COOLING WITH HEAT PUMP AND / OR AIR DRYING |
JP4799635B2 (en) | 2009-04-13 | 2011-10-26 | 三菱電機株式会社 | Liquid desiccant regenerator and desiccant dehumidifier air conditioner |
JP4958934B2 (en) * | 2009-04-13 | 2012-06-20 | 三菱電機株式会社 | Dehumidifying air conditioner |
SE534745C2 (en) | 2009-04-15 | 2011-12-06 | Alfa Laval Corp Ab | Flow Module |
KR101018475B1 (en) | 2009-08-28 | 2011-03-02 | 기재권 | Water storage tank having solar voltaic generator |
CN102481494B (en) | 2009-09-14 | 2014-09-10 | 兰登姆科技有限责任公司 | Apparatus and methods for changing the concentration of gases in liquids |
JP4536147B1 (en) | 2009-09-15 | 2010-09-01 | ダイナエアー株式会社 | Humidity control device |
KR101184925B1 (en) | 2009-09-30 | 2012-09-20 | 한국과학기술연구원 | Heat exchanger for a dehumidifier using liquid desiccant and the dehumidifier using liquid desiccant using the same |
JP5089672B2 (en) | 2009-10-27 | 2012-12-05 | ダイナエアー株式会社 | Dehumidifier |
AU2010313335B2 (en) * | 2009-10-30 | 2016-04-14 | Oasys Water LLC | Osmotic separation systems and methods |
US8286442B2 (en) | 2009-11-02 | 2012-10-16 | Exaflop Llc | Data center with low power usage effectiveness |
EP2504630A1 (en) | 2009-11-23 | 2012-10-03 | Carrier Corporation | Method and device for air conditioning with humidity control |
JP5417213B2 (en) | 2010-02-10 | 2014-02-12 | 株式会社朝日工業社 | Indirect evaporative cooling type external air conditioning system |
JP5697481B2 (en) | 2010-02-23 | 2015-04-08 | 中部電力株式会社 | Heating and cooling device |
CN110220254A (en) | 2010-05-25 | 2019-09-10 | 7Ac技术公司 | The method and system of air conditioning and other processing is carried out using liquid drier |
WO2011161547A2 (en) | 2010-06-24 | 2011-12-29 | Venmar, Ces Inc. | Liquid-to-air membrane energy exchanger |
JP5621413B2 (en) | 2010-08-25 | 2014-11-12 | 富士通株式会社 | Cooling system and cooling method |
DE102010050042A1 (en) * | 2010-10-29 | 2012-05-03 | Aaa Water Technologies Ag | Apparatus for drying and / or cooling gas |
US8641806B2 (en) | 2010-11-12 | 2014-02-04 | The Texas A&M University System | Systems and methods for multi-stage air dehumidification and cooling |
AP2013006932A0 (en) * | 2010-11-23 | 2013-06-30 | Ducool Ltd | Air conditioning system |
US8141379B2 (en) | 2010-12-02 | 2012-03-27 | King Fahd University Of Petroleum & Minerals | Hybrid solar air-conditioning system |
AU2010365411A1 (en) | 2010-12-13 | 2013-08-01 | Ducool Ltd. | Method and apparatus for conditioning air |
CN102147134A (en) * | 2011-01-05 | 2011-08-10 | 东南大学 | Solution dehumidifying and regenerating device |
US8695363B2 (en) | 2011-03-24 | 2014-04-15 | General Electric Company | Thermal energy management system and method |
KR20120113608A (en) | 2011-04-05 | 2012-10-15 | 한국과학기술연구원 | Heat exchanger having a dehumidifying liquid and a dehumidifier having the same |
CN202229469U (en) | 2011-08-30 | 2012-05-23 | 福建成信绿集成有限公司 | Compression heat pump system with liquid dehumidifying function |
US9810439B2 (en) | 2011-09-02 | 2017-11-07 | Nortek Air Solutions Canada, Inc. | Energy exchange system for conditioning air in an enclosed structure |
JP2013064549A (en) | 2011-09-16 | 2013-04-11 | Daikin Industries Ltd | Air conditioning system |
CN103827588A (en) * | 2011-09-16 | 2014-05-28 | 大金工业株式会社 | Humidity control module, and humidity control device |
DE102012019541A1 (en) | 2011-10-24 | 2013-04-25 | Mann+Hummel Gmbh | Humidifying device for a fuel cell |
WO2013172789A1 (en) | 2012-05-16 | 2013-11-21 | Nanyang Technological University | A dehumidifying system, a method of dehumidifying and a cooling system |
ES2755800T3 (en) | 2012-06-11 | 2020-04-23 | 7Ac Tech Inc | Methods and systems for turbulent and corrosion resistant heat exchangers |
US20130340449A1 (en) * | 2012-06-20 | 2013-12-26 | Alliance For Sustainable Energy, Llc | Indirect evaporative cooler using membrane-contained liquid desiccant for dehumidification and flocked surfaces to provide coolant flow |
US9816760B2 (en) | 2012-08-24 | 2017-11-14 | Nortek Air Solutions Canada, Inc. | Liquid panel assembly |
US20140054004A1 (en) | 2012-08-24 | 2014-02-27 | Venmar Ces, Inc. | Membrane support assembly for an energy exchanger |
SE538217C2 (en) | 2012-11-07 | 2016-04-05 | Andri Engineering Ab | Heat exchangers and ventilation units including this |
US9506697B2 (en) | 2012-12-04 | 2016-11-29 | 7Ac Technologies, Inc. | Methods and systems for cooling buildings with large heat loads using desiccant chillers |
US9511322B2 (en) | 2013-02-13 | 2016-12-06 | Carrier Corporation | Dehumidification system for air conditioning |
CN108443996B (en) | 2013-03-01 | 2021-04-20 | 7Ac技术公司 | Desiccant air conditioning method and system |
US9267696B2 (en) * | 2013-03-04 | 2016-02-23 | Carrier Corporation | Integrated membrane dehumidification system |
US9523537B2 (en) | 2013-03-11 | 2016-12-20 | General Electric Company | Desiccant based chilling system |
US9140471B2 (en) | 2013-03-13 | 2015-09-22 | Alliance For Sustainable Energy, Llc | Indirect evaporative coolers with enhanced heat transfer |
US20140262125A1 (en) | 2013-03-14 | 2014-09-18 | Venmar Ces, Inc. | Energy exchange assembly with microporous membrane |
US10352628B2 (en) | 2013-03-14 | 2019-07-16 | Nortek Air Solutions Canada, Inc. | Membrane-integrated energy exchange assembly |
CN105121979B (en) * | 2013-03-14 | 2017-06-16 | 7Ac技术公司 | For the method and system of differential body liquid drier air adjustment |
WO2014152888A1 (en) | 2013-03-14 | 2014-09-25 | 7 Ac Technologies, Inc. | Methods and systems for liquid desiccant air conditioning system retrofit |
US10584884B2 (en) | 2013-03-15 | 2020-03-10 | Nortek Air Solutions Canada, Inc. | Control system and method for a liquid desiccant air delivery system |
US9279598B2 (en) | 2013-03-15 | 2016-03-08 | Nortek Air Solutions Canada, Inc. | System and method for forming an energy exchange assembly |
US11408681B2 (en) | 2013-03-15 | 2022-08-09 | Nortek Air Solations Canada, Iac. | Evaporative cooling system with liquid-to-air membrane energy exchanger |
US20140360373A1 (en) | 2013-06-11 | 2014-12-11 | Hamilton Sundstrand Corporation | Air separation module with removable core |
ES2759926T3 (en) | 2013-06-12 | 2020-05-12 | 7Ac Tech Inc | Liquid Desiccant Air Conditioning System |
CN203408613U (en) * | 2013-07-15 | 2014-01-29 | 叶立英 | Membrane-based liquid dehumidifying device |
CN105765309B (en) | 2013-11-19 | 2019-07-26 | 7Ac技术公司 | Method and system for turbulence type corrosion-resistance heat exchanger |
EP3120083B1 (en) | 2014-03-20 | 2020-07-01 | 7AC Technologies, Inc. | Rooftop liquid desiccant systems and methods |
WO2016081933A1 (en) | 2014-11-21 | 2016-05-26 | 7Ac Technologies, Inc. | Methods and systems for mini-split liquid desiccant air conditioning |
US20170106639A1 (en) | 2015-10-20 | 2017-04-20 | 7Ac Technologies, Inc. | Methods and systems for thermoforming two and three way heat exchangers |
-
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KR102391093B1 (en) | 2022-04-27 |
KR102641608B1 (en) | 2024-02-28 |
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EP3120083A4 (en) | 2017-11-29 |
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