US2655795A - Refrigerator condensing unit cooler - Google Patents

Refrigerator condensing unit cooler Download PDF

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US2655795A
US2655795A US264562A US26456252A US2655795A US 2655795 A US2655795 A US 2655795A US 264562 A US264562 A US 264562A US 26456252 A US26456252 A US 26456252A US 2655795 A US2655795 A US 2655795A
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case
temperature
compartment
pad
air
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US264562A
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Dyer John
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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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/041—Details of condensers of evaporative condensers

Definitions

  • Another object is to provide evaporative cooling mechanism within said case so that when the temperature rises above a predetermined level the air passing over the condenser will be cooled by evaporation of water so that its actual temperature as it contacts the condenser coils will be lower than the outside air which would otherwise be forced over the condenser coils;
  • Another object is to provide an insulated case for an air cooled refrigeration unit which has an air inlet provided with an evaporative cooler pad over which water may be flowed and through which air may be drawn into the case, and an exhaust stack having a fan adapted to force air therefrom; the case being arranged generally to v maintain a temperature suitable for the efficient operation of the refrigeration unit.
  • Figure 2 a longitudinal sectional view thereof taken substantially on line 2-2 of Figure 1;
  • Figure 3 a diagrammatic representation of a compartment to be cooled.
  • the case 2 is rectangular and has bottom 3, top 4, side walls 5, as well as one end wall 6, composed of insulating material I, such as cork or glass wool, confined between outer and inner metal sheets 9 and I respectively.
  • the cut lines XX in Figures 2 and 3 represent an indeterminate distance from case 2 to compartment 43.
  • the case is divided interiorly by a partition l2 into an outer compartment l4 and an inner compartment l5.
  • Refrigeration apparatus is disposed within compartment I5 and includes compressor I6 driven by motor l1, condenser I8, receiver [9, and thermostat control switch 20.
  • the condenser is positioned in an opening in partition 12.
  • Motor I! has a fan I8 adapted to draw air through the condenser from outer compartment l4 to inner compartment [5. This air then exhausts through ventilator 23. When desired this is accelerated by electrically driven fan l9. Fluid refrigerant leaves the receiver through pipe 20 and goes to the evaporator 40 in the compartment 43 which is to be cooled through expansion or metering valve 42. Thereafter expanded refrigerant is drawn through pipe 2i to the compressor.
  • the open end 8 of case 2 is provided with an evaporative pad 22 composed of fibrous material 23, such as excelsior or the like, which is confined between screens 24 and 25.
  • a sump 263 is in the bottom of the case part [4 and water is pumped from this by an electric motor-driven pump 2'! and delivered into perforated trough 28 at the top of pad 22. This Water trickles down through the pad and returns to the sump. Fresh water may be added when the water in the sump falls below a predetermined level by operation of float valve 30 which is in water supply line 3
  • Bulb 36 and bellows 35 may be supplanted by a bi-metal strip or any other heat sensitive control mechanism desired.
  • the capacity-of the device is determined by the expansion or -metering valve. This is set or selected-to provide the results required, under averageconditions, with a certain pressure drop acrosa-the-valve.
  • the pressure drop ismaintainedibythe difference between the suction orintake pressure. oi -the compressor and the output orhead pressure.
  • acrosa-the-valve the difference between the suction orintake pressure. oi -the compressor and the output orhead pressure.
  • the temperatureto be maintained by the evaporator to-be 40 FL, then when-outside air temperaturesare high, ,say 85 -F.,,-there-cou1d be a head pressure of L35 pounds per square inch, and a suction pressure of 251 pounds per square inch, resulting in a 1 pressure drop ofr 110 pounds per square inch which would operate through the expansion valve with good efiiciency.
  • thev head pressure might well be 72 poundsper square inch while the suction pressure. would-be-only, 23 pounds per square inch, resulting in a-pressure drop of only 49 poundsper square-inch. This would be inefiicientwith the same metering valve. Since commercial refrigeration here concerned, are for the-most part, installedroutside of heated habitations they are subjectedtofiuctuations of the weather including the-temperature changes abovementioned; Thedevicahere disclosed provides a means for;- overcoming; the inefficiencies caused. bythese. weather. changes and automatically compensatesv for: them:: and.
  • a refrigerator condensing, unit comprising an insulated case, an intermediateipartition. dividing the interior into an outer compartment and an inner compartment; a-condenserypositioned in an opening in said partition, the said outer compartment being provided with an inlet opening enclosing a refrigerating evaporating pad, a water sump and a motor drawn pump for pumping water on to said pad and a shutter for closing said inlet opening; said inner compartment being provided with an outlet opening, a compressor, a receiver and fans for drawing air from said-outer compartment:- and: circulating it therethrough and: forcingdt out of said outlet opening, and a thermostat mechanism for controlling the operation of said circulating fans,
  • said pump motor for moistening said evaporative padj'and'said shutter, whereby when the temperature within the case rises above a predetermined: degree, said fans will operate, said pump will pump water to moisten said evaporative pad 'and'said 'shutters will open admitting air into said-outer compartment through said evaporating pad and forcing it over the surface of said condenser;v said fans operating to circulateair within said' insulated case when the temperature within-it falls below a predetermined degree.
  • a refrigeration mechanism including. a compressor, a 'conderisenfa receiver, an expansion valve'andan evaporatorina compartment to be cooled;jthe combinationtherewith of. an insulatedcase having a partition, including said condensenjdividing the iiiterior into an outer compartment and 'aninner, compartment,. said outer compartment havingIan inleto'pening ineluding an evaporating, refrigerating pad, a water sumpdn the-bottom, a motor drive'nipum'p for circulating water from saidsum'p, over said pad,,and-a normally, closedshutter operative by heatsens'itivet.
  • compressorliaving' av fan adapted'to: draw air from said outer 'com'pjart ment into, saidinneri compartment and; force it out of" saidi outlet. vent; and to circulate: air within'said' case 'wnenisaidshutterisclosed;

Description

Oct. 20, 1953 J, DY 2,655,795
REFRIGERATOR CONDENSING UNIT COOLER Filed Jan. 2, 1952 Patented Oct. 20, 1953 REFRIGERATOR CONDENSING UNIT COOLER John Dyer, Tucson, Ariz.
Application January 2, 1952, Serial No. 264,562
2 Claims.
denser and a liquid receiver all contained within an insulated case together with control thermostats, and arranged so that if the temperature drops below a certain point the heat developed by the compressor will be confined and retained within the case so that the temperature of the condenser will not drop below that of the area to be cooled and the pressure drop across the metering valve will remain within an efficient operating range;
Another object is to provide evaporative cooling mechanism within said case so that when the temperature rises above a predetermined level the air passing over the condenser will be cooled by evaporation of water so that its actual temperature as it contacts the condenser coils will be lower than the outside air which would otherwise be forced over the condenser coils;
Another object is to provide an insulated case for an air cooled refrigeration unit which has an air inlet provided with an evaporative cooler pad over which water may be flowed and through which air may be drawn into the case, and an exhaust stack having a fan adapted to force air therefrom; the case being arranged generally to v maintain a temperature suitable for the efficient operation of the refrigeration unit.
Other objects will appear hereinafter.
I attain the foregoing objects by means of the devices and construction shown in the accompanying drawing in which- Figure 1 is an end view of the refrigeration unit case;
Figure 2, a longitudinal sectional view thereof taken substantially on line 2-2 of Figure 1; and
Figure 3, a diagrammatic representation of a compartment to be cooled.
Similar numerals refer to similar parts in the different views.
The case 2 is rectangular and has bottom 3, top 4, side walls 5, as well as one end wall 6, composed of insulating material I, such as cork or glass wool, confined between outer and inner metal sheets 9 and I respectively. The cut lines XX in Figures 2 and 3 represent an indeterminate distance from case 2 to compartment 43.
The case is divided interiorly by a partition l2 into an outer compartment l4 and an inner compartment l5.
Refrigeration apparatus is disposed within compartment I5 and includes compressor I6 driven by motor l1, condenser I8, receiver [9, and thermostat control switch 20. The condenser is positioned in an opening in partition 12. Motor I! has a fan I8 adapted to draw air through the condenser from outer compartment l4 to inner compartment [5. This air then exhausts through ventilator 23. When desired this is accelerated by electrically driven fan l9. Fluid refrigerant leaves the receiver through pipe 20 and goes to the evaporator 40 in the compartment 43 which is to be cooled through expansion or metering valve 42. Thereafter expanded refrigerant is drawn through pipe 2i to the compressor.
The open end 8 of case 2 is provided with an evaporative pad 22 composed of fibrous material 23, such as excelsior or the like, which is confined between screens 24 and 25. A sump 263 is in the bottom of the case part [4 and water is pumped from this by an electric motor-driven pump 2'! and delivered into perforated trough 28 at the top of pad 22. This Water trickles down through the pad and returns to the sump. Fresh water may be added when the water in the sump falls below a predetermined level by operation of float valve 30 which is in water supply line 3|. Air is drawn through pad 22 so long as hinged louver slats 33 are open, as shown in Figure 2. These slats are operated in unison by rod 34 and this, in turn, by bellows 35 which is expanded or contracted by gas in bulb 36, which may be either within or outside of case 2. When the temperature within the box exceeds a predetermined temperature, say 66 F., the bellows 35 opens the slats. So long as the temperature within the box stays below the pump 21, controlled by electrical thermostat 20, does not operate, and fan Is merely draws outside air through the case and over the condenser. When the temperature rises above 85 pump 21 starts and pumps water over pad 22 and exhaust fan 19 starts. Evaporation of water in this pad effectively reduces the temperature of the air circulating over the condenser and thus increases the efficiency of the condensing unit.
Bulb 36 and bellows 35 may be supplanted by a bi-metal strip or any other heat sensitive control mechanism desired.
I have determined by test that with outside air temperatures as high as F., the efiective tem-- perature within the case 2 will not run over 88 F. The temperature differential between the receiver and the evaporator is thus kept within an efficient range, and there is less power consumed by motor H. The small amount of power consumed by fan motor [9, and motor driven pump 21 is more than offset by the saving in power consumed by compressor motor l7. With the more effective pressure differential between the interior of case 2 and the compartment to be cooled less running time per unit of time (hour or day) is required to keep the required amount of refrigerant condensed in receiver 19.
In cold weather gas in bulb 36 contracts and bellows 35 contracts so as to close louver slats 33. Pump 2"! andZ-motor: l9 are'shutcfiby ther mostat The heat generated by" compressor I6 and motor I! is sufiicient when conserved by the insulated case 2 to keep the temperature within the case above that of the compartment to be cooled. Thus there is a temperature drop between the condenser I8 and the evaporator 40' sufiicient to keep the expansion valve'fl opem Otherwise, I have found, that-when the temperature of the compressor unit drops to or below the temperature where the evaporator isposi; tioned the pressure in the condenser becomes so low relative to-that-inithe evaporator that'the expansion valve does notoperate and requires servicing.
In commercial installations the capacity-of the device is determined by the expansion or -metering valve. This is set or selected-to provide the results required, under averageconditions, with a certain pressure drop acrosa-the-valve. The pressure drop ismaintainedibythe difference between the suction orintake pressure. oi -the compressor and the output orhead pressure. Assuming the temperatureto be maintained by the evaporator to-be 40 FL, then when-outside air temperaturesare high, ,say 85 -F.,,-there-cou1d be a head pressure of L35 pounds per square inch, and a suction pressure of 251 pounds per square inch, resulting in a 1 pressure drop ofr 110 pounds per square inch which would operate through the expansion valve with good efiiciency. However, with outside air at 409 EL, thev head pressure might well be 72 poundsper square inch while the suction pressure. would-be-only, 23 pounds per square inch, resulting in a-pressure drop of only 49 poundsper square-inch. This would be inefiicientwith the same metering valve. Since commercial refrigeration here concerned, are for the-most part, installedroutside of heated habitations they are subjectedtofiuctuations of the weather including the-temperature changes abovementioned; Thedevicahere disclosed provides a means for;- overcoming; the inefficiencies caused. bythese. weather. changes and automatically compensatesv for: them:: and.
minimizes the eifects of temperature extremes.
Thus, I have provided astructureand arrangement of parts which-greatelyadds to-the efficiency of refrigeratorcompressor unit installations, particularly in climatessuch asencountered in southwestern portions :of theeUnited States where the higher summer temperatures range from- 100 F. to LZOff E HandlQ er. winter temperatures range from 20 to 40 F.-
l. A refrigerator condensing, unit comprising an insulated case, an intermediateipartition. dividing the interior into an outer compartment and an inner compartment; a-condenserypositioned in an opening in said partition, the said outer compartment being provided with an inlet opening enclosing a refrigerating evaporating pad, a water sump and a motor drawn pump for pumping water on to said pad and a shutter for closing said inlet opening; said inner compartment being provided with an outlet opening, a compressor, a receiver and fans for drawing air from said-outer compartment:- and: circulating it therethrough and: forcingdt out of said outlet opening, and a thermostat mechanism for controlling the operation of said circulating fans,
said pump motor for moistening said evaporative padj'and'said shutter, whereby when the temperature within the case rises above a predetermined: degree, said fans will operate, said pump will pump water to moisten said evaporative pad 'and'said 'shutters will open admitting air into said-outer compartment through said evaporating pad and forcing it over the surface of said condenser;v said fans operating to circulateair within said' insulated case when the temperature within-it falls below a predetermined degree.
2; In a refrigeration mechanism including. a compressor, a 'conderisenfa receiver, an expansion valve'andan evaporatorina compartment to be cooled;jthe combinationtherewith of. an insulatedcase having a partition, including said condensenjdividing the iiiterior into an outer compartment and 'aninner, compartment,. said outer compartment havingIan inleto'pening ineluding an evaporating, refrigerating pad, a water sumpdn the-bottom, a motor drive'nipum'p for circulating water from saidsum'p, over said pad,,and-a normally, closedshutter operative by heatsens'itivet. mechanism to opie'n when the temperatureoutside saidcase exceeds a predetermined degree; I said inner compartment? enclosing said compressor andreceiver, having an outlet vent providedwithlafan driven bya motor and a thermostat connected to said evaporating pad, pump motor andjsaid outlet vent fan motorsc that when the temperature-within. said "case'ex' ceeds I a predetermined degree Said" motors; O'DBI' ate' to producerefrigeration by; evaporation and force air? cooled byf"'sair1evaporating pad over said condensery said; compressorliaving' av fan adapted'to: draw air from said outer 'com'pjart ment into, saidinneri compartment and; force it out of" saidi outlet. vent; and to circulate: air within'said' case 'wnenisaidshutterisclosed;
JOHN "DYEBLJ References Cited in meme-or thispatent
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Cited By (45)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2778203A (en) * 1954-04-13 1957-01-22 William F R Griffith Air conditioning system having a cooling tower or the like
US2892324A (en) * 1955-05-31 1959-06-30 Lester K Quick Refrigeration system with heat reclaiming means
US3100386A (en) * 1959-06-29 1963-08-13 Chausson Usines Sa Evaporation heat exchanger
US3108451A (en) * 1960-07-20 1963-10-29 Leslie Hill H Air conditioning system and apparatus
US3115757A (en) * 1962-04-04 1963-12-31 C A Olsen Mfg Co Air cooled condenser
US3299650A (en) * 1965-06-04 1967-01-24 Kramer Trenton Co Air cooled condenser fan arrangement for control of head pressure in a refrigeration or air conditioning system and method of installing the same
US3427005A (en) * 1967-04-17 1969-02-11 Edward A Kuykendall Precooler
US3913345A (en) * 1974-04-29 1975-10-21 William H Goettl Air conditioner
US3990257A (en) * 1973-05-09 1976-11-09 Inland Steel Company Method for cooling workpieces in a liquid bath
US4056946A (en) * 1975-11-14 1977-11-08 General Electric Company Low temperature cooler/condenser
US4123917A (en) * 1977-08-10 1978-11-07 Npi Corporation Produce cooler
US4182131A (en) * 1978-11-27 1980-01-08 Consoli Ronald P High efficiency air conditioner
US4204409A (en) * 1978-07-26 1980-05-27 Satama Kauko K Air conditioning apparatus and system
US4317334A (en) * 1980-06-16 1982-03-02 Silva Restaurant Equipment Co., Inc. Remote refrigeration system with controlled air flow
US4353219A (en) * 1980-05-19 1982-10-12 Patrick Jr Robert L Self-contained ambient precooler attachment for air-cooled condensing units
US4726197A (en) * 1986-11-03 1988-02-23 Megrditchian Dennis L Apparatus for treating air
EP0257715A1 (en) * 1986-08-21 1988-03-02 Polacel B.V. A cooling or condensation device with a precooler for the cooling air
US5050398A (en) * 1990-09-04 1991-09-24 Specialty Equipment Companies, Inc. Ice making machine with remote vent
US5131463A (en) * 1991-06-03 1992-07-21 Carrier Corporation Corrosion protection filter for heat exchangers
US5309726A (en) * 1992-12-15 1994-05-10 Southern Equipment Company Air handler with evaporative air cooler
US5311747A (en) * 1992-06-30 1994-05-17 Pringle Robert D Water-assisted condenser cooler
US5520007A (en) * 1992-12-23 1996-05-28 Schulak; Edward R. Energy transfer system for refrigeration components
US5666817A (en) * 1996-12-10 1997-09-16 Edward R. Schulak Energy transfer system for refrigerator/freezer components
US5743109A (en) * 1993-12-15 1998-04-28 Schulak; Edward R. Energy efficient domestic refrigeration system
US5775113A (en) * 1992-12-23 1998-07-07 Schulak; Edward R. Energy efficient domestic refrigeration system
US5791154A (en) * 1992-12-23 1998-08-11 Schulak; Edward R. Energy transfer system for refrigeration components
US5937662A (en) * 1996-12-10 1999-08-17 Edward R. Schulak Energy transfer system for refrigerator/freezer components
US5964101A (en) * 1996-12-10 1999-10-12 Edward R. Schulak Energy transfer system for refrigerator/freezer components
EP1415121A1 (en) 2001-07-13 2004-05-06 Müller Industries Pty Ltd. System and method of cooling
US6823684B2 (en) 2002-02-08 2004-11-30 Tim Allan Nygaard Jensen System and method for cooling air
WO2005005905A1 (en) * 2003-07-09 2005-01-20 Muller Industries Australia Pty Ltd System and method of cooling
WO2007110034A1 (en) * 2006-03-20 2007-10-04 Gea Energietechnik Gmbh Condenser which is exposed to air
US20080034776A1 (en) * 2005-08-09 2008-02-14 Tim Allan Nygaard Jensen Prefilter System for Heat Transfer Unit and Method
US20080256963A1 (en) * 2007-04-20 2008-10-23 Theodore William Mettier Performance enhancement product for an air conditioner
US7441412B2 (en) 2005-01-26 2008-10-28 Tim Allan Nygaard Jensen Heat transfer system and method
US20080307816A1 (en) * 2005-11-25 2008-12-18 Shirou Kashiwa Outdoor Unit of Air Conditioner
US20090188651A1 (en) * 2008-01-29 2009-07-30 Yi-Hsiung Lin Cooler
US20100126693A1 (en) * 2008-11-21 2010-05-27 Young Gerald A Cool cap for outdoor heat exchangers
US20100162737A1 (en) * 2007-06-14 2010-07-01 Muller Industries Australia Pty Ltd. System and method of wetting adiabatic material
US20110168354A1 (en) * 2008-09-30 2011-07-14 Muller Industries Australia Pty Ltd. Modular cooling system
US20130091889A1 (en) * 2011-10-14 2013-04-18 Donghwi KIM Outdoor unit for air conditioner
US20180066876A1 (en) * 2016-09-08 2018-03-08 Robert Neil MCLELLAN Evaporative cooling system
JP2019023549A (en) * 2017-07-24 2019-02-14 比克準有限公司 Purifying and cooling structure of heat radiator
US11231211B2 (en) * 2019-04-02 2022-01-25 Johnson Controls Technology Company Return air recycling system for an HVAC system
US11493212B1 (en) * 2018-03-27 2022-11-08 Clark N. Harper Air filtration and cooling system

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US1874803A (en) * 1931-01-12 1932-08-30 Reed Frank Maynard Heat exchange mechanism
US2009882A (en) * 1932-06-20 1935-07-30 Edward G Burghard Refrigerant cooler
US2059839A (en) * 1933-11-15 1936-11-03 Carrier Engineering Corp Multipurpose heat transfer unit
US2120767A (en) * 1937-05-01 1938-06-14 York Ice Machinery Corp Refrigeration apparatus
US2238808A (en) * 1938-08-05 1941-04-15 Fulton Sylphon Co Refrigerating system
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Cited By (58)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2778203A (en) * 1954-04-13 1957-01-22 William F R Griffith Air conditioning system having a cooling tower or the like
US2892324A (en) * 1955-05-31 1959-06-30 Lester K Quick Refrigeration system with heat reclaiming means
US3100386A (en) * 1959-06-29 1963-08-13 Chausson Usines Sa Evaporation heat exchanger
US3108451A (en) * 1960-07-20 1963-10-29 Leslie Hill H Air conditioning system and apparatus
US3115757A (en) * 1962-04-04 1963-12-31 C A Olsen Mfg Co Air cooled condenser
US3299650A (en) * 1965-06-04 1967-01-24 Kramer Trenton Co Air cooled condenser fan arrangement for control of head pressure in a refrigeration or air conditioning system and method of installing the same
US3427005A (en) * 1967-04-17 1969-02-11 Edward A Kuykendall Precooler
US3990257A (en) * 1973-05-09 1976-11-09 Inland Steel Company Method for cooling workpieces in a liquid bath
US3913345A (en) * 1974-04-29 1975-10-21 William H Goettl Air conditioner
US4056946A (en) * 1975-11-14 1977-11-08 General Electric Company Low temperature cooler/condenser
US4123917A (en) * 1977-08-10 1978-11-07 Npi Corporation Produce cooler
US4204409A (en) * 1978-07-26 1980-05-27 Satama Kauko K Air conditioning apparatus and system
US4182131A (en) * 1978-11-27 1980-01-08 Consoli Ronald P High efficiency air conditioner
US4353219A (en) * 1980-05-19 1982-10-12 Patrick Jr Robert L Self-contained ambient precooler attachment for air-cooled condensing units
US4317334A (en) * 1980-06-16 1982-03-02 Silva Restaurant Equipment Co., Inc. Remote refrigeration system with controlled air flow
EP0257715A1 (en) * 1986-08-21 1988-03-02 Polacel B.V. A cooling or condensation device with a precooler for the cooling air
US4726197A (en) * 1986-11-03 1988-02-23 Megrditchian Dennis L Apparatus for treating air
US5050398A (en) * 1990-09-04 1991-09-24 Specialty Equipment Companies, Inc. Ice making machine with remote vent
US5131463A (en) * 1991-06-03 1992-07-21 Carrier Corporation Corrosion protection filter for heat exchangers
US5311747A (en) * 1992-06-30 1994-05-17 Pringle Robert D Water-assisted condenser cooler
US5309726A (en) * 1992-12-15 1994-05-10 Southern Equipment Company Air handler with evaporative air cooler
US5520007A (en) * 1992-12-23 1996-05-28 Schulak; Edward R. Energy transfer system for refrigeration components
US5791154A (en) * 1992-12-23 1998-08-11 Schulak; Edward R. Energy transfer system for refrigeration components
US5775113A (en) * 1992-12-23 1998-07-07 Schulak; Edward R. Energy efficient domestic refrigeration system
US5743109A (en) * 1993-12-15 1998-04-28 Schulak; Edward R. Energy efficient domestic refrigeration system
US6230514B1 (en) 1996-12-10 2001-05-15 Edward R. Schulak Energy transfer system for refrigerator freezer components
US5964101A (en) * 1996-12-10 1999-10-12 Edward R. Schulak Energy transfer system for refrigerator/freezer components
US5666817A (en) * 1996-12-10 1997-09-16 Edward R. Schulak Energy transfer system for refrigerator/freezer components
US5937662A (en) * 1996-12-10 1999-08-17 Edward R. Schulak Energy transfer system for refrigerator/freezer components
US20080115921A1 (en) * 2001-07-13 2008-05-22 Hall Grant D System and method of cooling
EP1415121A1 (en) 2001-07-13 2004-05-06 Müller Industries Pty Ltd. System and method of cooling
US20050000683A1 (en) * 2001-07-13 2005-01-06 Hall Grant David System and method of cooling
US6823684B2 (en) 2002-02-08 2004-11-30 Tim Allan Nygaard Jensen System and method for cooling air
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