Surged vapor compression heat transfer systems with reduced defrost requirements
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IPC분류정보
국가/구분
United States(US) Patent
등록
국제특허분류(IPC7판)
F25D-021/06
F25D-021/00
F25B-041/00
F25B-047/00
F25B-047/02
F25D-021/04
출원번호
US-0914362
(2010-10-28)
등록번호
US-9127870
(2015-09-08)
발명자
/ 주소
Wightman, David
출원인 / 주소
XDX Global, LLC
대리인 / 주소
Blanchard & Associates
인용정보
피인용 횟수 :
0인용 특허 :
175
초록▼
Surged vapor compression heat transfer systems, devices, and methods are disclosed having refrigerant phase separators that generate at least one surge of vapor phase refrigerant into the inlet of an evaporator after the initial cool-down of an on cycle of the compressor. This surge of vapor phase r
Surged vapor compression heat transfer systems, devices, and methods are disclosed having refrigerant phase separators that generate at least one surge of vapor phase refrigerant into the inlet of an evaporator after the initial cool-down of an on cycle of the compressor. This surge of vapor phase refrigerant, having a higher temperature than the liquid phase refrigerant, increases the temperature of the evaporator inlet, thus reducing frost build up in relation to conventional refrigeration systems lacking a surged input of vapor phase refrigerant to the evaporator.
대표청구항▼
1. A method of operating a heat transfer system during a cooling cycle, comprising: compressing a refrigerant;expanding the refrigerant;at least partially separating liquid and vapor phases of the refrigerant;introducing at least one surge of the vapor phase of the refrigerant into an initial portio
1. A method of operating a heat transfer system during a cooling cycle, comprising: compressing a refrigerant;expanding the refrigerant;at least partially separating liquid and vapor phases of the refrigerant;introducing at least one surge of the vapor phase of the refrigerant into an initial portion of an evaporator with an expanded refrigerant transfer system, where the initial portion of the evaporator is a volume of the evaporator;introducing the liquid phase of the refrigerant into the initial portion of the evaporator with the expanded refrigerant transfer system; andheating the initial portion of the evaporator in response to the at least one surge of the vapor phase of the refrigerant. 2. The method of claim 1, further comprising heating the initial portion of the evaporator to within at most about 5° C. of a temperature of a first external medium. 3. The method of claim 1, further comprising heating the initial portion of the evaporator to a temperature greater than a first external medium. 4. The method of claim 1, further comprising heating the initial portion of the evaporator to a temperature greater than a dew point temperature of a first external medium. 5. The method of claim 1, where a temperature difference between an inlet portion of the evaporator and an outlet portion of the evaporator is from about 0° C. to about 3° C. 6. The method of claim 1, further comprising operating the system where a slope of the temperature of the initial portion of the evaporator includes negative and positive values. 7. The method of claim 1, further comprising removing frost from the initial portion of the evaporator. 8. The method of claim 1, further comprising sublimating frost from the initial portion of the evaporator, where the temperature of the initial portion of the evaporator is at most about 0° C. 9. The method of claim 1, where the initial portion of the evaporator is less than about 30% of the volume of the evaporator. 10. The method of claim 1, where the initial portion of the evaporator is less than about 10% of the volume of the evaporator. 11. The method of claim 1, where the initial portion of the evaporator has at least one intermittent temperature maximum, andwhere the at least one intermittent temperature maximum is responsive to the at least one surge of the vapor phase of the refrigerant, andwhere the intermittent temperature maximum is within at most about 5° C. of a temperature of a first external medium. 12. The method of claim 11, where the at least one intermittent temperature maximum is greater than the temperature of the first external medium. 13. The method of claim 11, where the at least one intermittent temperature maximum is greater than a dew point temperature of the first external medium. 14. The method of claim 11, where a temperature difference between the initial 10% of the volume of the evaporator and the last 10% of the volume of the evaporator is from about 0° C. to about 3° C. 15. The method of claim 11, where the relative humidity of the first external medium is greater than the relative humidity of the first external medium when surges of the vapor phase refrigerant are not introduced to the initial portion of the evaporator. 16. The method of claim 11, where the temperature of the first external medium is lower than the temperature of the first external medium when surges of the vapor phase refrigerant are not introduced to the initial portion of the evaporator and an active defrost cycle is not used. 17. The method of claim 11, further comprising operating the system where a slope of the temperature of the initial portion of the evaporator includes negative and positive values. 18. The method of claim 11, further comprising removing frost from the initial portion of the evaporator in response to the intermittent temperature maximum. 19. The method of claim 11, further comprising sublimating frost from the initial portion of the evaporator in response to the intermittent temperature maximum, where the temperature of the initial portion of the evaporator is at most about 0° C. 20. The method of claim 11, where the initial portion of the evaporator is less than about 30% of the volume of the evaporator. 21. The method of claim 11, where the initial portion of the evaporator is less than about 10% of the volume of the evaporator. 22. The method of claim 1, where the at least one surge of the vapor phase of the refrigerant includes at least 75% vapor. 23. The method of claim 1, where the average heat transfer coefficient from the initial portion to an outlet portion of the evaporator is from about 1.9 Kcalth h−1 m−2° C.−1 to about 4.4 Kcalth h−1 m−2° C.−1 and where the initial portion of the evaporator is less than about 10% of the volume of the evaporator, and wherethe outlet portion of the evaporator is less than about 10% of the volume of the evaporator. 24. A method of defrosting an evaporator in a heat transfer system during a cooling cycle, comprising: at least partially separating liquid and vapor phases of a refrigerant;introducing at least one surge of the vapor phase of the refrigerant into an initial portion of an evaporator with an expanded refrigerant transfer system, where the initial portion of the evaporator is a volume of the evaporator;introducing the liquid phase of the refrigerant into the initial portion of the evaporator with the expanded refrigerant transfer system;heating the initial portion of the evaporator in response to the at least one surge of the vapor phase of the refrigerant; andremoving frost from the evaporator. 25. A heat transfer system, comprising: a compressor having an inlet and an outlet;a condenser having an inlet and an outlet;an evaporator having an inlet, an initial portion having a first volume, a later portion having a second volume, and an outlet, the outlet of the compressor in fluid communication with the inlet of the condenser, the outlet of the condenser in fluid communication with the inlet of the evaporator, and the outlet of the evaporator in fluid communication with the inlet of the compressor;a metering device in fluid communication with the condenser and the evaporator, where the metering device expands a refrigerant, the refrigerant having vapor and liquid portions; anda phase separator in fluid communication with the metering device and the evaporator,where the phase separator is capable of separating a portion of the vapor from the expanded refrigerant, and wherethe phase separator is capable of introducing during a cooling cycle at least one surge of the vapor to the initial portion of the evaporator between operating periods of introducing the expanded refrigerant into the initial portion of the evaporator that include a substantially increased liquid component in relation to the at least one surge of the vapor. 26. The method of claim 1, where the at least partial separation of the liquid and vapor phases of the refrigerant causes a net cooling of the liquid phase of the refrigerant and a net heating of the vapor phase of the refrigerant. 27. The method of claim 24, where the at least partial separation of the liquid and vapor phases of the refrigerant causes a net cooling of the liquid phase of the refrigerant and a net heating of the vapor phase of the refrigerant. 28. The heat transfer system of claim 25, where the phase separator is capable of raising the temperature of the vapor portion of the refrigerant while lowering the temperature of the liquid portion of the refrigerant. 29. The method of claim 24, further comprising heating the initial portion of the evaporator to within at most about 5° C. of a temperature of a first external medium. 30. The method of claim 24, further comprising heating the initial portion of the evaporator to a temperature greater than a first external medium. 31. The method of claim 24, further comprising heating the initial portion of the evaporator to a temperature greater than a dew point temperature of a first external medium. 32. The method of claim 24, where a temperature difference between an inlet volume of the evaporator and an outlet volume of the evaporator is from about 0° C. to about 3° C. 33. The method of claim 24, where a slope of the temperature of the initial portion of the evaporator includes negative and positive values. 34. The method of claim 24, further comprising sublimating frost from the initial portion of the evaporator. 35. The method of claim 24, further comprising sublimating frost from the initial portion of the evaporator, where the temperature of the initial portion of the evaporator is at most about 0° C. 36. The method of claim 24, where the initial portion of the evaporator is less than about 30% of the volume of the evaporator. 37. The method of claim 24, where the initial portion of the evaporator is less than about 10% of the volume of the evaporator. 38. The method of claim 24, where the at least one surge includes at least 75% vapor. 39. The heat transfer system of claim 25, where the phase separator has a body portion defining a separator inlet, a separator outlet, and a separator refrigerant storage chamber; where the separator refrigerant storage chamber has a longitudinal dimension;where a ratio of a diameter of the separator inlet to a diameter of the separator outlet is about 1:1.4 to 4.3 or about 1:1.4 to 2.1; andwhere a ratio of the diameter of the separator inlet to the longitudinal dimension is about 1:7 to 13. 40. The heat transfer system of claim 39, where a ratio of the diameter of the separator inlet to a refrigerant mass flow rate is about 1:1 to 12. 41. The heat transfer system of claim 25, where the at least one surge removes frost from the initial portion of the evaporator. 42. The heat transfer system of claim 25, where the at least one surge sublimates frost from the initial portion of the evaporator, where the temperature of the initial portion of the evaporator is at most about 0° C. 43. The heat transfer system of claim 25, where the phase separator is capable of introducing at least two surges of the vapor to the initial portion of the evaporator during an operation cycle of the compressor. 44. The heat transfer system of claim 25, where the initial portion of the evaporator is at most 30% of the total volume of the evaporator. 45. The heat transfer system of claim 25, where the initial portion of the evaporator is at most 10% of the total volume of the evaporator. 46. The heat transfer system of claim 25, where the at least one vapor surge introduced to the initial portion of the evaporator raises the initial portion of the evaporator to at least one intermittent temperature maximum within at most 5° C. of a temperature of a first external medium. 47. The heat transfer system of claim 25, where the at least one vapor surge introduced to the initial portion of the evaporator raises the initial portion of the evaporator to at least one intermittent temperature maximum greater than the temperature of a first external medium. 48. The heat transfer system of claim 25, where the at least one vapor surge introduced to the initial portion of the evaporator raises the initial portion of the evaporator to at least one intermittent temperature maximum greater than the dew point temperature of a first external medium. 49. The heat transfer system of claim 25, where the temperature difference between the initial 10% of the total volume of the evaporator and the last 10% of the total volume of the evaporator is from 0° C. to 3° C. 50. The heat transfer system of claim 25, where the at least one surge includes at least 75% vapor.
Shaw Allan (5th Floor ; Security House ; 233 North Terrace Adelaide AUX) Luxton Russell E. (5th Floor ; Security House ; 233 North Terrace Adelaide AUX) Luxton Russell E. (Adelaide AUX), Air conditioning and method of dehumidifier control.
Lancia Frederick N. (Columbus OH) Kesterson Albert O. (Columbus OH) Feeney Edward K. (Worthington OH) Liebert Ralph C. (Worthington OH), Control system for an air conditioning system having supplementary, ambient derived cooling.
Barthel Richard C. (Harwood Heights IL) Malone Peter J. (Rosemont IL) Orth Charles D. (Cedarburg WI) Jarosch George W. (Elkgrove IL), Controlling refrigeration.
Khrustalev, Dmitry; Cologer, Pete; Garzon, Jessica Maria; Stouffer, Charles; Feenan, Dave; Baker, Jeff; Beres, Matthew C., Evaporator for use in a heat transfer system.
Ares Roland A. (St. Charles MO) Cromer James M. (Florissant MO) Schaeffer Wayne G. (Creve Coeur MO) Wehmeier William C. (St. Charles MO), Flow-through surge receiver.
Bussjager Ruddy C. (Chittenango NY) McKallip James M. (Pompey NY) Miller Lester N. (East Syracuse NY), High latent refrigerant control circuit for air conditioning system.
Mei Viung C. (Oak Ridge TN) Chen Fang C. (Knoxville TN), Liquid over-feeding refrigeration system and method with integrated accumulator-expander-heat exchanger.
Shaw Allan (5th Floor ; Security House ; 233 North Terrace Adelaide ; State of South Australia AUX) Luxton Russell E. (5th Floor ; Security House ; 233 North Terrace Adelaide ; State of South Austral, Method and means of air conditioning.
Boris Siniakevith UA; Mark Khaskin IL; Daniel Goldman IL; Benjamin Doron IL; Lucien Y. Bronicki IL; Eli Yaffe IL, Method of and means for producing combustible gases from low grade fuel.
Zimmern Bernard (6 New St. East Norwalk CT 06855) Picouet Jean L (Bridgeport CT), Method of using a thermal expansion valve device, evaporator and flow control means assembly and refrigerating machine.
Cur Nihat O. (Royalton Township ; Berrien County MI) Kuehl Steven J. (Lincoln Township ; Berrien County MI) LeClear Douglas D. (St. Joseph Township ; Berrien County MI), Multi-temperature evaporator refrigeration system with variable speed compressor.
Bennett Douglas L. (Allentown PA) Ludwig Keith A. (Emmaus PA) Weimer Robert F. (Allentown PA), Process and apparatus for producing nitrogen and oxygen.
Schaeffer Wayne G. (Ballwin MO) Wehmeier William C. (St. Charles MO) Broccard Terry J. (St. Louis MO) Behr John A. (Defiance MO), Strategic modular commercial refrigeration.
Swenson Paul F. (20431 Almar Shaker Heights OH 44122) Eversole George H. (800 W. Shannon Dr. Bridgeport WV 26330), System for fast-filling compressed natural gas powered vehicles.
Wightman, David A., Vapor compression systems, expansion devices, flow-regulating members, and vehicles, and methods for using vapor compression systems.
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