WO2005031225A1 - Procede et appareil de deshydratation de l'air du type a refrigeration - Google Patents

Procede et appareil de deshydratation de l'air du type a refrigeration Download PDF

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Publication number
WO2005031225A1
WO2005031225A1 PCT/US2004/030715 US2004030715W WO2005031225A1 WO 2005031225 A1 WO2005031225 A1 WO 2005031225A1 US 2004030715 W US2004030715 W US 2004030715W WO 2005031225 A1 WO2005031225 A1 WO 2005031225A1
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WO
WIPO (PCT)
Prior art keywords
air
refrigerant
exchanger
phase change
change material
Prior art date
Application number
PCT/US2004/030715
Other languages
English (en)
Inventor
James W. Barnwell
Original Assignee
Flair Corporation
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Filing date
Publication date
Application filed by Flair Corporation filed Critical Flair Corporation
Publication of WO2005031225A1 publication Critical patent/WO2005031225A1/fr

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Classifications

    • 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
    • F24F3/1405—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 in which the humidity of the air is exclusively affected by contact with the evaporator of a closed-circuit cooling system or heat pump circuit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D53/00—Separation of gases or vapours; Recovering vapours of volatile solvents from gases; Chemical or biological purification of waste gases, e.g. engine exhaust gases, smoke, fumes, flue gases, aerosols
    • B01D53/26—Drying gases or vapours
    • B01D53/265—Drying gases or vapours by refrigeration (condensation)
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D16/00—Devices using a combination of a cooling mode associated with refrigerating machinery with a cooling mode not associated with refrigerating machinery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0016—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being bent
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/103—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of more than two coaxial conduits or modules of more than two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/24—Storage receiver heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2111—Temperatures of a heat storage receiver
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0038—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for drying or dehumidifying gases or vapours
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/14—Thermal energy storage

Definitions

  • the present invention relates generally to drying systems. More particularly, the present invention is directed to a refrigeration-type air dryer comprising a heat storage medium phase change material.
  • Air dryers are generally utilized to remove water vapor typically from compressed air or gas. Where refrigerant-type air dryers are employed, a refrigerant system is used to lower the temperature of the air or gas being dried to a temperature at or below the condensation temperature of water therein. At such temperatures, water vapor in the undried air condenses on a surface within a condenser where it can be collected and purged from the system. [0003] hi order to sufficiently lower the temperature of the undried air or gas, many refrigerant systems comprise a heat exchanger where heat is drawn from the air or gas being dried to a refrigerant.
  • heat from undried air is coupled to the evaporation of a colder refrigerant in an evaporator.
  • the liquid refrigerant As the liquid refrigerant is vaporized, it removes heat from the undried air or gas and cools the air in the process.
  • the air or gas reaches a temperature at or below the condensation temperature of water therein, the net result is that the water vapor therein begins to condense (or separate) from the air or gas and is collected in a condenser or separator.
  • a common problem with refrigeration-type dryers is determining how to suspend cooling (i.e., "de-energize" the system) during times of no load or low load conditions. For example, the demand for refrigeration is low or nonexistent when little to no air is flowing through the refrigerator dryer or when the incoming air is already cool.
  • a cycling-type refrigeration dryer In a cycling refrigeration-type dryer system, a thermostatic temperature device causes de-energizing of a refrigerant compressor when the undried air has been cooled to a predetermined temperature. The same device can then cause the compressor to be re-energized when the temperature in the evaporator elevates to a predetermined temperature, indicating further cooling is required to remove moisture from the incoming air.
  • a refrigeration compressor may cycle on and off about thirty to forty times per hour.
  • the number of cycles per hour is significant because frequent cycling adds costs associated with wear and tear on the compressor, control systems, and valves. As a xesult, the life without maintenance of the refrigeration system is drastically reduced. Accordingly, it would be desirable to provide a refrigerant air dryer system and method that extends the life of its refrigeration system. [0008] Moreover, the greater the number of times a refrigeration system cycles, the greater the amount of energy that is consumed. Lower energy consumption has both cost and environmental benefits. Accordingly it would also be desirable to provide a refrigeration dryer system and method that reduces the amount of energy consumed.
  • an air drying apparatus comprising a refrigerant system and a heat exchanger further comprising a phase change material, wherein the refrigerant system is adapted for cooling the heat exchanger.
  • the air dryer may dry air or gas which may optionally be compressed air or gas.
  • air dryers of the present invention may comprise a condensate separator, preferably including a wire mesh.
  • the phase change material can change between solid and liquid phases.
  • the phase change material is an organic paraffin.
  • a method of drying air which comprises providing a refrigerant system and a heat exchanger comprising a phase change material and using the refrigerant system to cool the heat exchanger.
  • the method may be used to dry air or gas which may optionally be compressed air or gas.
  • method of air drying of the present invention may comprise a condensate separator, preferably including a wire mesh.
  • the phase change material can change between solid and liquid phases.
  • the phase change material is an organic paraffin.
  • a means for drying air comprising a refrigeration means and a heat exchanger means comprising a phase change material, wherein the refrigeration means is adapted for cooling the heat exchanger means.
  • the air drying means may dry air or gas which may optionally be compressed air or gas.
  • air dryer means of the present invention may comprise a condensate separator means, preferably including a wire mesh.
  • the phase change material can change between solid and liquid phases.
  • the phase change material is an organic paraffin.
  • FIG. 1 is a cut-away of an evaporator of a refrigerated air dryer in accordance with the present invention.
  • FIG. 2 is a cut-away of refrigeration chiller of a refrigerated air dryer in accordance with the present invention, in accordance with the present invention.
  • FIG. 3 is a cut-away of refrigeration chiller of a refrigerated air dryer in accordance with the present invention, in accordance with the present invention.
  • FIG.4 is cut-away of refrigeration chiller of a refrigerated air dryer in accordance with the present invention, in accordance with the present invention.
  • An embodiment in accordance with the present invention provides a refrigeration system 10 operationally coupled to a heat exchanger 20 to cool undried compressed air to a temperature sufficient to separate and remove any water therein by virtue of its condensation at such sufficient temperature.
  • the heat exchanger 20 may be of multiple embodiments, some of which will be described below.
  • the heat exchanger 20 comprises an air- to-air (“air/air”) exchanger 30 and an air-to-refrigerant (“air/refrigerant”) exchanger 40.
  • the exchanger 40 further comprises a thermal jacket 50, which in the embodiment shown, is directly cooled by the refrigerant system 10.
  • air gas, including compressed air and gas, or generally, any vapor in need of drying
  • the air then travels through the exchanger 30 to the exchanger 40.
  • the air traverses a path 61 through the exchanger 30, adapted in a manner such that heat from the hotter, undried air entering the inlet 60 can be transferred to the cooler, dried air exiting an outlet 70.
  • air entering the inlet 60 may be greater than 40 to 70 degrees Fahrenheit hotter than air exiting the outlet 70.
  • Such a temperature differential can provide motive for significant heat transfer without the need for further mechanical intervention.
  • the exchanger 40 is designed to draw heat from the incoming air to the refrigerant 11 supplied by the refrigerant system 10.
  • the refrigerant 11 cools the thermal jacket 50.
  • Contents of the thermal jacket may comprise any material known and present in the art that can be cooled to a temperature at or lower than the dew point of the vapor (i.e., water) being condensed. Suitable materials include, but are not limited to, glycols and mixtures thereof.
  • the thermal jacket 50 may comprise a phase change material (PCM).
  • PCMs are heat storage media that can absorb or diffuse heat by changing from a solid to a liquid, or vice versa.
  • the phase change material absorbs heat from the undried air, it begins to change phase from a solid to a liquid.
  • the thermal jacket 50 can maintain a constant temperature during the transition. The process can take minutes to hours depending on the PCM, ambient temperature of the air, and workload.
  • PCMs that can absorb the greatest amount of heat over the smallest temperature range are preferred.
  • PCMs that remain in the solid phase longer for a given amount of heat are desirable.
  • the thermal conductivity of a fluid increases significantly when in a solid phase as opposed to a liquid.
  • Water for example, has a thermal conductivity of 0.326 BTU/hr-ft-°F at 32°F, whereas ice has a thermal conductivity of 1.18 BTU/hr-ft-°F at the same temperature. Because of their ability to absorb heat at both a solid state (high thermal conductivity) and a liquid state (lower thermal conductivity), PCMs can more rapidly and efficiently absorb the heat of condensation than materials that do not undergo a phase change.
  • the refrigerant 11 cools (or "charges") the thermal jacket 50 so that the PCM therein becomes solid, thereby allowing the thermal jacket 50 to draw heat from the incoming air 61.
  • the heat from the incoming air 61 is transferred through the PCM/thermal jacket 50 to the heat absorbing refrigerant 11.
  • the refrigerant system 10 can shut off.
  • the predetermined temperature may be chosen to signal that no further cooling by the refrigerant system 10 is needed, for example, at times when the temperature of refrigerant 11 entering the thermal jacket 50 nears the temperature of the refrigerant 12 exiting the jacket 50.
  • the PCM can continue to absorb heat from the undried air. In other words, the PCM can supply the necessary cooling by absorbing heat in the solid phase while maintaining a low constant temperature before changing to liquid.
  • this invention can allow for the extension of time periods where the refrigerant system 10 may remain deenergized
  • the refrigerant system 10 can reenergize and the PCM can be relatively quickly recharged (i.e., solidified) by the refrigerant system 10.
  • the net effect of this system is that the cycle periods can be extended and less energy can be consumed than convention refrigeration-type air dryers that do not use PCMs,
  • the compressor cycling rate can be reduced from thirty or forty times per hour to, for example, five to fifteen cycles per hour, or maybe even less.
  • Heat storage mediums can be developed to change state at a chosen temperature.
  • a medium can be of a composition to freeze at +4°C that would preclude water freezing, or icing, in the exchanger 40.
  • PCMs which change states between liquid and solid are manufactured by many companies, for example PCM Thermal Solutions of Naperville, IL.
  • the PCM A4 is an organic paraffin which freezes at +4°C and is composed of a blend of heavy cut hydrocarbons.
  • the types E7 and E8 that change state at +7°C and +8°C, respectively, are composed of ammonia and sodium sulfate salts.
  • low temperature PCMs can be used including TEA-29 that freezes at -29°C.
  • the TEA media are composed of inorganic hydrated salt solutions, such as calcium chloride in water.
  • inorganic hydrated salt solutions such as calcium chloride in water.
  • the return path for cooled air 62 may optionally be adapted in the exchanger 30 such that heat may be transferred from the incoming air 61 to the exiting air 62. In such a way, not only is the exiting air heated closer to the temperature of the air 61 as it enters the exchanger 20, but the air 61 entering the exchanger 20 is precooled before entering exchanger 40.
  • a conventional refrigeration system 10 is depicted in the embodiment of FIG. 1.
  • Refrigerant gas 12 is pressurized by a compressor 13.
  • the compressor 13 compresses the refrigerant gas 12.
  • the compression process raises the refrigerant 12 pressure and also the temperature.
  • the refrigerant 12 is channeled through a condenser 14, which is a heat exchanging means that allows the refrigerant 12 to dissipate the heat of pressurization.
  • a condenser 14 which is a heat exchanging means that allows the refrigerant 12 to dissipate the heat of pressurization.
  • the refrigerant gas 12 cools into a refrigerant liquid 11.
  • the refrigerant 11 is then dried and/or filtered of contaminants by a filter/dryer means 15.
  • the liquid refrigerant 11 is then passed through an expansion valve 16 which transfers the liquid refrigerant 11 from a high pressure zone to a low pressure zone, thereby vaporizing the refrigerant 11.
  • the refrigerant 11 draws heat, preferably from the thermal jacket 50 and/or the undried air 61.
  • refrigeration systems will also comprise a sensing valve 17.
  • the sensing valve 17 is generally a temperature sensing valve that can determine the temperature of the return refrigerant 12.
  • the sensing valve 17 is able to compare the temperature of the cooled refrigerant 11 with the return refrigerant 12 and has the means to shut-off and/or turn-on the system 10 when a pre-determined temperature(s) is reached.
  • Shown in FIG. 2 is an embodiment of a heat exchanger 120 in accordance with the present invention.
  • the heat exchanger 120 comprises an air/air heat exchanger 130, an air/refrigerant heat exchanger 140, and a condensate separator 180.
  • the air/refrigerant exchanger 140 is known as a "braized plate” heat exchanger and comprises a series of stacked plates.
  • the plates may be comprised of any materials that are sturdy when pressurized, heated, and cooled, and can conduct heat efficiently.
  • metal plates are used, and more specifically, stainless steel or copper plates.
  • a braised plate exchanger comprises alternating stainless steel and copper plates fused together creating "gaps" or "slits" between the plates. In some embodiments of the present invention, at least three such gaps are envisioned. A. first of the gaps is utilized to contain an incoming flow of air to be dried. A second of the gaps can contain a refrigerant and a third one of the gaps may contain a PCM.
  • the refrigerant plate contacts the PCM plate which contacts the air plate, however, alternate combinations are also possible.
  • an inlet pipe 160 may be attached to the air/air exchanger 130 evaporator to allow incoming air to flow into any chamber designated to hold incoming air.
  • the incoming air follows a course counter-flow to the outgoing air. This adaptation functions as an air/air heat exchange thereby pre-cooling the incoming air before it enters exchanger 140.
  • the incoming air then moves through the braized plate heat exchanger 150.
  • the braized plate heat exchanger 150 comprises a series of stacked plates creating chambers therefrom.
  • a probe 155 may also be incorporated in the exchanger 150 to sense and/or report a status of the refrigerant and/or the PCM therein.
  • the probe 155 is a phase change temperature sensing probe and is located at a location within exchanger 150 where the PCM would be warmest.
  • probe 155 may be adapted for use in any location within heat exchanger 120. In any event, once having traversed the heat exchanger 140, the exiting air is cooled to permit condensation of the water.
  • a condensate separator 180 may be coupled to the exchanger 120 via an outlet port 190.
  • the separator 180 separates the condensed water from the air stream.
  • a mesh 181 may be introduced into the separator 180 to aid condensation.
  • the mesh 181 may comprise any material, preferably materials that will not rust or fail when wet, and need not be limited to any one particular design. Stainless steel wire meshes may be utilized in some embodiments.
  • a drain 182 may be provided to allow the condensate to exit the separator 180.
  • Piping 100 may be coupled to the separator 180 to allow dried air to re-enter the exchanger 130, and exit through an outlet port 170.
  • An air/air exchanger 130 is provided to allow the outgoing cool dry air to pre-cool incoming warm air. [0039] Shown in FIG.
  • the heat exchanger 220 comprises an air/air heat exchanger 230, an air/refrigerant heat exchanger 240, and tubes 221 and 222 that permit that transfer of air between the exchangers 230 and 240.
  • the heat exchanger design of FIG.3 comprises an inlet port 260 that receives an incoming flow of a fluid, for example, compressed air.
  • the inlet 260 is coupled to tubing 231 within exchanger 230 that is adapted for air/air heat exchange between the warmer, undried air entering the exchanger 220 and the cooler, dried air exiting the exchanger 220.
  • air entering may be designed to flow through the tubes 231 through the center or periphery of exchanger 230, the sum of the tubes 231 being surrounded by cooler air exiting an outlet 270.
  • the entering air and the exiting air are arranged in a counter-flow arrangement so as to maximize heat transfer.
  • Such designs are commonly referred to as "shell-and- tube” or “multitube-in-tube” heat exchangers in the art.
  • the exchanger 240 can be constructed with three concentric tubes such that the refrigerant flows through the inner-most tube, a PCM is retained between the first and second tube, and the air passes through the annular space between the third and second tubes.
  • the triple tube design can be constructed in a coiled manner, or it can be designed as a straight tube construction as shown.
  • Refrigerant is circulated through the exchanger 240 through inlet/outlet ports 241.
  • the refrigerant cools a jacket 245 containing the PCM and/or the undried air traversing the exchanger 240.
  • the air As heat is drawn from the incoming air to the refrigerant and/or the PCM, the air is cooled to or below its dew point and moisture (e.g., water) begins to condense.
  • the condensed water is collected within the exchanger 240 and can be drained from the system though a condensate drain 242.
  • the exchanger 240 may also include a fluid fill/vent 243.
  • the fill/vent 243 may be adapted to allow filling or refilling of PCM as is required, and also allow for venting of gases or heat contained therein.
  • a probe 243 is incorporated into the air/refrigerant exchanger 240.
  • the probe 243 is a phase change temperature sensing probe and is located at a location within the exchanger 240 where the PCM would be warmest.
  • the probe 243 may be adapted for use in any location within heat exchanger 120.
  • the probe 243 may also signal shut-off or operation of the refrigerant system in some embodiments.
  • the cooled air may be directed by another connecting tube 222 back to the exchanger 230.
  • the cooled air is fed counter-flow to the incoming air in tubes 231 within the exchanger 230. This process not only cools air within the tubes 231 , but also warms the dried air exiting the exchanger 220 though the outlet 270.
  • FIG.4 depicts a heat exchanger 320.
  • the heat exchanger 320 comprises an air/refrigerant exchanger 340 and a separator 380, and may optionally include an air/air exchanger as well.
  • the exchanger 340 can be constructed with three coined tubes bundled together as illustrated in the figure. One of the three tubes 361 passes the air as it enters the exchanger 320 and exits drier. The air may enter/exit the exchanger 320 via an inlet/outlet 365 which can comprise a tube within a tube design.
  • One of the other tubes, 351, contains a PCM
  • the other of the two tubes, 311 contains a refrigerant.
  • the tubes 311, 351, and 361 are made from copper, and all three tubing lines are positioned such that one line of tubing does not overlap another line of material.
  • the three lines of tubing may all be made from any other material, or each of the three lines of tubing may be made from different materials. It should also be understood by one of ordinary skill in the art that the positioning of the three lines of tubing may also vary.
  • the exchanger 320 embodied in FIG.

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  • Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Analytical Chemistry (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Drying Of Solid Materials (AREA)
  • Drying Of Gases (AREA)

Abstract

L'invention concerne un procédé, un appareil et un moyen de déshydratation de l'air. Elle porte sur un système réfrigérant conçu pour refroidir un échangeur de chaleur comprenant un matériau à changement de phase. Les fluides à l'état de vapeur, dont l'air et les gaz comprimés, peuvent être refroidis par les procédé et appareil de l'invention.
PCT/US2004/030715 2003-09-26 2004-09-20 Procede et appareil de deshydratation de l'air du type a refrigeration WO2005031225A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US10/670,255 2003-09-26
US10/670,255 US20050066668A1 (en) 2003-09-26 2003-09-26 Refrigeration-type dryer apparatus and method

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DE102017007031B3 (de) 2017-07-25 2018-12-20 Messer Group Gmbh Vorrichtung und Verfahren zum Abscheiden von Dämpfen aus einem Gasstrom
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