Abstract:
A refrigerating method and system using compressed, filtered, dehumidified, turbo expanded and re-circulated air for the enclosed refrigerated environment. Compressed air passes via a series of moisture-removal devices ( 12, 24, 32 ), dust filter ( 52 ), heat exchanger ( 60 ), turbine expander ( 65 ), impeller fan ( 92 ), vacuum refrigeration chamber ( 70 ) and muffler ( 98 ).

Description:
BACKGROUND OF THE INVENTION 
     This invention relates to subzero refrigeration and cooling systems using compressed air as a coolant instead of environment-damaging and expensive systems using freon, liquid nitrogen, ammonia or other substances. 
     The inventor was experimenting with the air-based refrigerating devices for more than thirty years. This honing and fine tuning process has resulted in the present invention. The prior art is replete with refrigeration devices employing air for heat transfer. For example, U.S. Pat. No. 5,438,845 by Kirschner et al. discloses a refrigeration device with compressed and turbo expanded air based on a venturi-like ejector circulating the refrigerant within the refrigeration chamber. 
     U.S. Pat. No. 4,430,867 by Warner disclosed an air cycle refrigeration system for aircraft cabins including a sink and circulation heat exchangers for melting ice in the exhaust air and exhaust air from the system&#39;s turbine. 
     U.S. Pat. No. 5,718,116 by Grassi at al. disclosed an open loop, air refrigerant, heat pump process for a food freezer employing cold expander discharge to cool air feed to the expander prior to suing this portion as a regeneration gas for adsorbent-containing drier. 
     U.S. Pat. No. 4,829,775 by Defrancesco disclosed an air-conditioning system with a filter of compressed air coming from a heater and passing through a second re-heater downstream of the filter and upstream of the turbine for maximizing efficiency of the turbine. 
     U.S. Pat. No. 5,699,672 by Foerster et al. revealed a refrigeration apparatus and method in which compressed air is subjected to isothermal compression in a water-injected screwtype compressor with subsequent adiabatic and isentropic expansion in a high-speed turbine. 
     U.S. Pat. No. 5,921,093 by Jonqueres disclosed an air cycle system using a re-heater condensing water vapor extracted from compressed air and then cooled by a sub-cooler heat exchanger and re-heated in the re-heater condenser before its expansion in a turbine for enclosure conditioning. 
     However, none of the prior art references known to the inventor discloses the present invention shown and described herein. 
     SUMMARY OF THE INVENTION 
     A novel system and method employing compressed air as primary refrigerant dramatically reduces exploitation cost, increases efficiency and produces pollution-free discharge in contradistinction with existing systems using freon, liquid nitrogen or other chemical substances. Compressed air travels through three dehumidifying steps including a passage through a pre-cooler for initial dehumidification, moisture separator, and dryers regenerated by independent heaters or system exhaust air drying off the moisture-absorbing material. Then, the air travels through a dust filter, turbine expander, refrigeration chamber with a sinusoidal path channel, impeller fan, heat exchanger and a noise-attenuating muffler. The unique design resolves technical problems previously preventing mass production of noise-free and inexpensive air-based refrigeration systems. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     A schematic illustration of one embodiment of an air-based refrigeration system in accordance with the present invention is shown in FIG.  1 . 
    
    
     DESCRIPTION OF THE INVENTION 
     As shown in FIG. 1, a refrigeration system comprises a compressed air line  10  conveying air from a standard compressor to an air pre-cooler  12 . The compressed air temperature is about 70° to 80° C. A tap water line  14  passes through the air pre-cooler  12  in order to chill out the hot compressed air. The temperature of the tap water is about 18-20° C. or lower. The tap water coils or pipelines  14  cool the air traveling through the air pre-cooler  12 , thereby dehumidifying that air. Condensate descending down the walls leaves the air pre-cooler through an outlet  16  at or slightly above the atmospheric pressure. A condensate line  18  starting from the outlet  16  ends in a drain sump (not shown) or discharged into the ambient atmosphere. 
     The air leaves the pre-cooler through an outlet  20 . This completes the initial stage of air dehumidification. A cooled air conduit  22  connects the air pre-cooler with a moisture or water extractor  24  for the next stage of dehumidification. The air propelled into the water extractor  24  passes through a moisture separator cylinder  26 . The cylinder  26  has an entry screen blocking the vaporized water and oil droplets from entering an outlet  28  leading to a conduit  30 . This completes the second phase of air dehumidification. The water condensate accumulated on and flowing down the walls is removed from the moisture extractor  24  through a port  31  in the same manner and through the same condensate drainage system  18  as the air pre-cooler condensate. 
     The conduit  30  brings the air still laden with water and oil vapor to an air dryer  32  for final dehumidification. The air dryer  32  is interconnected with one or more of identical backup dryers to insure the system&#39;s continuous operation during a downtime of one of them. Each of these dryers  32  includes a drying sand-like column  34  of silica gel or similar moisture-absorbing material. 
     An air entry screen  36  supports the column  34 . A lid screen  38  compacts and retains the drying material or absorber inside the dryer. The lid  38  applies continuous and constant pressure on the absorber column. This unidirectional pressure can be achieved either by a spring-loaded or weight-bearing lid. Compressed air comes into an air entry chamber  40  preceding the absorber support screen  36  and then moves through the absorber column  34 , which absorbs the remaining water and oil vapor. 
     An exit chamber  42  collects the air forced through the absorber column  34 . The absorber crumbles into dust in time. This dust is carried away by airflow. The dryer must be periodically refilled with fresh absorber. The absorber becomes moisturized eventually and needs to be dried up for its further exploitation. This drying or regeneration process is accomplished during one dryer&#39;s maintenance (regeneration) stops by heated air coming from an independent heater  44  or hot air exiting from the subject system. The heater  44  receives the air from the moisture extractor  24  through a line  46  connected to the conduit  30 , heats the air with its electric heating elements  48  and discharges the heated air into the dryer&#39;s exit chamber  42  through a line  49 . The hot air is forced to move down from the exit chamber  42  toward the support screen  36 , i.e. in a reverse-to-normal flow direction. Then this air is exhausted into the drainage system  18  through the outlet pipes. 
     When the absorber drying process is finished, the dryer  32  is ready to resume its operation and take over the backup dryer switched over during this dryer&#39;s silica gel regeneration stop. The air dehumidified by the dryer  32  is exhausted into a line  50  leading to a dust filter  52 . The dust filter  52  has a metal screen  54  with tiny apertures (approximately 0.0016 mm in diameter) preventing the entry of suspended absorber dust into the air system. This air filtering process reduces abrasion and jamming of a turbine expander rotated by the air, thereby increasing the expander&#39;s working life and reliability. Dust caught by the dust filter  52  is removed through the combined drainage system  18  through lines  56 . 
     An air pipe  58  brings the filtered and dried air to a heat exchanger  60  for cooling and reducing the air medium temperature. The cooled, dried and cleaned air is ejected through injector nozzles  62  into a turbine  64 . The ejected air rotates the turbine blades and generates cold due to the adiabatic expansion of compressed air losing its speed and pressure. The refrigerated air, supplied by the turbo expander  65  via an inlet line  66 , absorbs heat load from the items or objects  68  stored in a chamber  70  of the refrigerator  72 . Such items may include food products, airplane elements tested for subzero temperature operation, or lubricants. 
     Then the air flows into a channel  74  through the opening  76  in the metal floor or partition  78  of the refrigeration chamber  70 . The channel  74  guides the air into a sinusoidal or wave-like path by its staggered fins  80 , which are attached to the metal partition  78  and channel walls. The sinusoidal path in that channel delays exit of the refrigerated air out of refrigerator and thereby increases efficiency of the air refrigerant cooling the partition  78 . This wave-like passage continues until air reaches the refrigerator outlet  82 . A waste collector  84  is affixed to the channel  74  for removing of snowflakes or other particles suspended in the exiting air. The collector accumulates waste through a series of openings  86  in the channel wall  87 . The refrigerator outlet line  88  delivers the refrigerated air into a cooling chamber  90  of the heat exchanger  60  for cooling off of the air pipelines  58  coming into the turbo expander from the dust filter  52 . 
     The refrigerated air is then drawn out of the exchanger chamber  90  and ejected onto the blades of an impeller fan  92  through the conduit  94 . The fan can create a vacuum in the refrigeration chamber, because it is more powerful than the turbine  64  supplying the refrigerated air to the chamber. The impeller fan  92  is sharing its shaft  95  with the turbine  64 . A wall  93  separates an impeller chamber and a turbine expander  65 . The fan  92  compresses the air to the higher than atmospheric pressure and releases it into the atmosphere through a line  96  and muffler  98 . The hot air exiting the muffler can be also directed into the dryer for drying the absorber through the line  99 . This re-circulation process saves energy by reducing the need for the heater  44 . The muffler  98  attenuates the noise (approximately 400-500 decibels) of turbine expander exiting air without causing any significant frictional resistance to the airflow and reduction of the turbo expander&#39;s power. 
     Temperature in the refrigeration chamber  70  fluctuates within 0.5° C. The system can produce refrigeration temperature up to −135° C. or lower. Selected temperature level is maintained by controlling means including a refrigerator chamber thermometer-sensor  100  connected to a controller  102  by a signal line  104 . The controller generates signals to an air valve  106  for adjusting airflow supplied to the turbo expander  64  via the line  58 . The controlling means can automatically shut down the airflow and the turbine, or restart the compressed air-refrigerant supply depending on the refrigerator chamber temperature or commercial needs. A pressure relief valve  108  has a dual function of releasing air from the refrigerator when the inside pressure exceeds a predetermined level. The valve  108  also lets the outside air enter the refrigerator when the vacuum pressure reaches a certain level. 
     A turbine expander temperature differential between the entering and exiting air is set at −60° C. If the air initially entering the turbine expander is about 20° C., then the temperature of the air coming off the turbine expander will be approximately −40° C. The air further cools down to about −60° C. during regular operation of the expander. The temperature of the air entering the expander  64  after the start up will be continuously decreased by the heat exchanger  60 . For instance, if the temperature of the air entering the heat exchanger  60  is reduced by the refrigerated air exiting from the refrigeration chamber  70  to 5° C., then the temperature of the air exiting the turbine expander will be at about −55° C. due to the set differential of −60° C. Maximum operational temperature should not exceed −135° C. 
     The set temperature differential of −60° C. is reached within 2 to 20 minutes instead of 4 to 5 hours minimum in refrigerators using freon, ammonia and other fluocarbons or hydrofluocarbons as coolants. These coolants or refrigerants also leak through de-hermetized pipe connections and evaporates into the ambient environment and atmosphere. This escape is unavoidable and leading to often replacement of this expensive chemical substance. Such leakage of compressed air would be harmless to health and practically causing no extra expense. Freon or ammonia pollution is detrimental to the health of people and atmosphere. Hydrofluocarbons or fluocarbons refrigerant systems require their defrosting and consequent prolonged downtime of the refrigerator. The air refrigerant on the other hand is ecologically clean, explosion-resistant, fire proof, nontoxic, cheap and fast-cooled to facilitate quick startup of the system. The system needs no downtime for defrosting. The subject air-based system provides continuous or interruptible-on-demand and practically maintenance-free mode of operation. 
     Although the present invention has been described with reference to a preferred embodiment, it will be understood by those skilled in the art that numerous changes, omissions and additions may be made without departing from the spirit and scope of the subject invention.