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WO2016004349A1 - Évaporateur et ses procédés d'utilisation - Google Patents

Évaporateur et ses procédés d'utilisation Download PDF

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Publication number
WO2016004349A1
WO2016004349A1 PCT/US2015/039056 US2015039056W WO2016004349A1 WO 2016004349 A1 WO2016004349 A1 WO 2016004349A1 US 2015039056 W US2015039056 W US 2015039056W WO 2016004349 A1 WO2016004349 A1 WO 2016004349A1
Authority
WO
WIPO (PCT)
Prior art keywords
evaporator
expansion device
refrigerant
condenser
coils
Prior art date
Application number
PCT/US2015/039056
Other languages
English (en)
Inventor
Gesualdo RICOTTA
Original Assignee
Ricotta Gesualdo
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ricotta Gesualdo filed Critical Ricotta Gesualdo
Publication of WO2016004349A1 publication Critical patent/WO2016004349A1/fr

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Classifications

    • 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
    • F25B39/02—Evaporators
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components

Definitions

  • the present application relates generally to vapor-compression refrigeration systems and methods and, in particular, an improved evaporator.
  • a conventional vapor-compression refrigeration system typically includes a compressor, a condenser, an expansion device and an evaporator interconnected to form a closed loop system through which refrigerant continuously circulates.
  • the main steps of a vapor-compression system are compression of the refrigerant by the compressor, heat rejection of the refrigerant in the condenser, metering of the refrigerant by the expansion device and absorption of heat by the refrigerant in the evaporator.
  • Such vapor- compression systems are commonly used in air conditioning systems found in buildings, vehicles, and domestic and commercial refrigerators, among others.
  • the present invention provides vapor-compression refrigeration systems and methods for improving the efficiency of such systems.
  • vapor-compression refrigeration apparatus utilizing a fluid refrigerant and comprising a compressor, a condenser, an expansion device and an evaporator arranged in succession and in fluid communication within a closed loop in order to circulate the fluid refrigerant.
  • the apparatus comprises at least one line within the closed loop that is in operable communication with the condenser for reducing temperature of at least a portion of the fluid refrigerant prior to the fluid refrigerant entering the expansion device.
  • the at least one line within the closed loop that is in operable communication with the condenser traverses at least a portion of the evaporator prior to operable communication with the expansion device.
  • the apparatus further comprise a cooling device within the closed loop, interposed between the condenser and the expansion device, wherein the cooling device is operably linked to the at least one line disposed in operable communication with the condenser for reducing temperature of at least a portion of the fluid refrigerant prior to the fluid refrigerant entering the expansion device.
  • the present invention also provides methods of increasing the efficiency of a vapor-compression refrigeration apparatus, the method comprising at least the step of reducing temperature of at least a portion of the fluid refrigerant prior to the fluid refrigerant entering the expansion device.
  • the method comprises the step of reducing temperature of at least a portion of the fluid refrigerant prior to the fluid refrigerant entering the expansion device by traversing at least a portion of the fluid refrigerant through at least a portion of the evaporator prior to the refrigerant entering the expansion device.
  • the method provides reducing temperature of at least a portion of the fluid refrigerant prior to the fluid refrigerant entering the expansion device by traversing at least a portion of the fluid refrigerant through a cooling device.
  • the present invention also provides an evaporator comprising a plurality of coils, wherein at least one of the plurality of coils is configured within the evaporator so that fluid refrigerant traverses at least a portion of the evaporator in a direction substantially opposite the flow direction of the refrigerant through the remaining plurality of coils.
  • the invention provides an evaporator comprising a plurality of coils housed inside a radiator frame and a sub-cooling coil external to and in contact with the radiator frame, wherein the subcooling coil is configured to receive refrigerant from a condenser and to deliver refrigerant to an expansion device.
  • the present invention provides an evaporator comprising a plurality of coils, wherein at least one of the plurality of coils is configured proximate to the evaporator so fluid refrigerant from the condenser traverses proximate to at least a portion of the evaporator prior to the fluid refrigerant.
  • FIG. 1 is a block diagram of a conventional vapor-compression refrigeration system comprising an evaporator 100, a compressor 200, a condenser 300 and an expansion device 400.
  • FIG. 2 is depiction of a cross section of a conventional A coil evaporator 201 comprising two vertical risers 203, each vertical riser 203 comprising a plurality of coils 202 (e.g. coil 202a, coil 202b and coil 202c).
  • coils 202 e.g. coil 202a, coil 202b and coil 202c.
  • FIG. 3 is a depiction of a cross section of a conventional A coil evaporator 201 and coil inlets 103 which connect the expansion device 400, via the capillary tubes 210, to the plurality of coils 202 to and further including a coil outlets 104, which connect the plurality of coils to the compressor 200.
  • FIG. 4 is a depiction of a cross section of a modified A coil evaporator 401 .
  • the condenser 300 is connected by the condenser inlet line 405 to at least one of the plurality of coils 202, for example coil 202b, via coil inlet 103b.
  • the expansion device 400 is directly linked to coil 202b via the coil outlet 104b and by expansion inlet line 115.
  • FIG. 5 is a depiction of a vapor-compression refrigeration system comprising of a cooling device 501 in operable communication with a condenser 300 and an expansion device 400.
  • FIG. 6 is a depiction of a cross section of a modified A coil evaporator 401 comprising an additional coil 202d which connects the condenser 300 to the expansion device 400 via an expansion inlet line 115.
  • Coil 202d is located proximate to the frame 601 of the modified A coil evaporator 401 and can be in contact with the exterior surface of the radiator frame or in close proximity to it.
  • FIG. 7 is a depiction of a cross section of a modified A coil evaporator 401 comprising an additional coil 202d which connects the condenser 300 to the expansion device 400 via an expansion inlet line 115.
  • Coil 202d is located within the frame 601 of the modified A coil evaporator 401.
  • FIG. 8 is a depiction of a cross section of a modified evaporator 801 comprising an additional coil 202d which connects the condenser 300 to the expansion device 400 via an expansion inlet line 115.
  • Coil 202d is located within the frame 601 of the modified evaporator 801.
  • FIG. 9 is a depiction of a cross section of a modified evaporator 801 comprising an additional coil 202d which connects the condenser 300 to the expansion device 400 via an expansion inlet line 115.
  • Coil 202d is located proximate to the frame 601 of the modified evaporator 801.
  • FIG. 10 is a block diagram of a vapor-compression refrigeration system comprising a modified evaporator 401 , a compressor 200, a condenser 300 and an expansion device 400, having the condenser 300 connected by the condenser inlet line 405, which passes through the modified evaporator 401 , and expansion inlet line 115 to the expansion device 400 and having the condenser 300 directly connected to the expansion device 400.
  • FIG. 1 1 is a block diagram of a vapor-compression refrigeration system comprising a modified evaporator 401 , a compressor 200, a condenser 300 and an expansion device 400 having the condenser 300 connected by the condenser inlet line 405 and expansion inlet line 115 to the expansion device 400.
  • FIG. 12 is a block diagram of a vapor-compression refrigeration system comprising an evaporator 100, a compressor 200, a condenser 300 and an expansion device 400 having the condenser 300 connected to a cooling device 501 and to the expansion device 400.
  • FIG. 13 is another block diagram of a vapor-compression refrigeration system comprising an evaporator 100, a compressor 200, a condenser 300 and an expansion device 400 with the condenser 300 connected to a cooling device 501.
  • FIG. 14 is a depiction of a cross section of a modified A coil evaporator 401.
  • the condenser 300 is connected by the condenser inlet line 405 to at least one of the plurality of coils 202, for example coil 202b, via coil inlet 103b.
  • the expansion device 400 is directly linked to coil 202b via the coil outlet 104b and by expansion inlet line 115.
  • FIG. 15 is a depiction of a cross section of another vapor-compression refrigeration system comprising a cooling device 501 in operable communication with a condenser 300 and an expansion device 400.
  • FIG. 16 is a depiction of yet another vapor-compression refrigeration system comprising a cooling device 1601 in operable communication with a condenser 300, an expansion device 400, compressor 200, and an evaporator.
  • operable communication means that the particular elements communicate or are connected in such a way that they cooperate to achieve their intended function or functions.
  • the "connection” may be direct, or indirect or remote.
  • FIG. 1 a flow diagram of a conventional vapor- compression system is illustrated.
  • the four major components of a conventional vapor- compression refrigeration system include: an evaporator 100, a compressor 200, a condenser 300 and an expansion device 400. Arrows connecting the component parts indicate the typical flow of fluid refrigerant within the system.
  • refrigerant enters an evaporator 100 in the form of a cool, low pressure mixture of liquid and vapor. Heat is transferred to the refrigerant from the relatively warm air that is being cooled, causing the liquid refrigerant to boil.
  • the resulting refrigerant vapor is then pumped from the evaporator 100 by the compressor 200, which increases the pressure and temperature of the vapor.
  • the resulting hot, high pressure refrigerant vapor enters the condenser 300 where heat is transferred to ambient air, which is at a lower temperature than the refrigerant.
  • the refrigerant vapor condenses into a warm liquid. This warm liquid refrigerant then flows from the condenser 300 to the expansion device 400.
  • the expansion device 400 removes pressure from the liquid refrigerant to allow expansion or change of state from a liquid to a vapor in the evaporator 100.
  • the high-pressure liquid refrigerant entering the expansion device 400 is warm, which may be verified by feeling the liquid line at its connection to the expansion device 400.
  • the liquid refrigerant leaving the expansion device 400 is cold.
  • the orifice within the valve does not remove heat, but only reduces pressure. Heat molecules contained in the liquid refrigerant are thus allowed to spread as the refrigerant moves out of the orifice. Under a greatly reduced pressure the liquid refrigerant is at its coldest as it leaves the expansion device 400 and enters the evaporator 100.
  • Pressures at the inlet and outlet of the expansion device 400 will closely approximate gauge pressures at the inlet and outlet of the compressor in most systems. The similarity of pressures is caused by the closeness of the components to each other. The slight variation in pressure readings of a very few pounds is due to resistance, causing a pressure drop in the lines and coils of the evaporator 100 and condenser 200.
  • the expansion device 400 creates a pressure drop that reduces the pressure of the refrigerant to that of the evaporator 100. At this low pressure, a small portion of the refrigerant boils (or flashes), cooling the remaining liquid refrigerant to the desired evaporator temperature. The cool mixture of liquid and vapor refrigerant enters the evaporator 100 to repeat the cycle.
  • An evaporator 100 typically comprises at least one long coil tube, more typically a plurality of coiled tubes, through which the fluid refrigerant flows and absorbs heat from a volume of ambient air that is desired to be cooled.
  • An example of an evaporator 100 is an A coil evaporator 201 illustrated in Figure 2 comprising two vertical risers 203 with each vertical riser comprising a plurality of coils 202 (e.g. coil 202a, coil 202b and coil 202c). Referring to Figure 3, in one embodiment, each of the plurality of coils 202 (e.g.
  • coil 202a, coil 202b and coil 202c has a coil inlet 103 and a corresponding coil outlet 104.
  • the expansion device 400 is connected via capillary tubes 210 to the plurality of coils 202 by coil inlets 103.
  • the temperature of the refrigerant In order to absorb heat from a volume of ambient air, the temperature of the refrigerant must be lower than that of ambient air when it enters the evaporator 100.
  • the present invention provides for a modified system and method of using such modified system which lowers the temperature of the refrigerant prior to entry of the refrigerant into the evaporator as compared to conventional vapor-compression refrigeration systems.
  • the invention provides an improved vapor-compression refrigeration apparatus wherein at least one tube (e.g., the condenser inlet line 405) within the closed loop is in operable communication with the condenser and converts at least a portion of the fluid refrigerant to a lower temperature prior to the fluid refrigerant entering the expansion device 400.
  • the invention provides a modified evaporator 401.
  • the condenser 300 is in direct communication with at least one of the plurality of coils 202, for example coil 202b via coil inlet 103b, for receiving warm liquid refrigerant directly (i.e. without passing through the expansion device 400) from the condenser 300.
  • the condenser inlet line 405 connects the condenser 300 in direct communication with at least one of the plurality of coils 202.
  • the expansion device 400 is in direct communication with at least one of the plurality of coils 202, for example coil 202b via corresponding coil outlet 104b, for receiving liquid refrigerant after it has passed through the modified evaporator 401.
  • any and/or one or more, of the plurality of coils 202 could be directly linked to the condenser 300 and/or expansion device 400.
  • the refrigerant could traverse proximate to (e.g., not directly through, adjacent, nearby, etc.) an evaporator 100.
  • one or more additional coils 202d may be positioned proximate to or within the frame 601 of the evaporator 100, for example a modified evaporator 801 or modified A coil evaporator 401 (See, e.g., Figures 6-9).
  • liquid refrigerant from condenser 300 can enter a coil 202d through an inlet 103d proximate to or within the frame of the modified evaporator 801 or modified A coil evaporator 401 without first passing through the expansion device 400.
  • the expansion device 400 is in direct communication with coil 202d via corresponding coil outlet 104d, for receiving liquid refrigerant after it has passed through the modified evaporator 801 or modified A coil evaporator 401.
  • the liquid refrigerant exits coil 202b or 202d via the corresponding coil outlets 104b or 104d and is directly linked to the expansion device 400 by expansion inlet line 115.
  • the remaining plurality of coils 202 for example coil 202a and coil 202c, are in operative communication with the expansion device 400, via corresponding coil inlets 103, for receiving cold low pressure refrigerant that has passed through the coils 202b or 202d as described above and been received by the expansion device 400.
  • expansion device 400 is in operative communication with a plurality of coil inlets 103, for example by connection with capillary tubes 210 as described above.
  • the capillary tubes 210 are copper tubes of small internal diameter, for example from about 0.5 to 2.28 mm (0.020 to 0.09 inches).
  • the condenser inlet line 405 is positioned substantially at the top of the modified evaporator 401.
  • at least one of a plurality of coils 202 e.g., coil 202b
  • coil inlet 103b is in operative communication with coil inlet 103b and corresponding coil outlet 104b that is in operative communication with the expansion device 400, for example by the expansion inlet line 115.
  • coil outlet 104b is positioned substantially at the bottom of the modified evaporator 401.
  • the remaining plurality of the coils 202 are in operative communication with the expansion device 400 via the capillary tubes 210.that are operably connected to the remaining inlets 103 positioned at the bottom of the evaporation with corresponding outlets 104 positioned at the top of the evaporator. Therefore, in some embodiments the fluid refrigerant may flow through one or more coils (e.g., coil 202b) in the direction opposite (e.g., transverse, cross-wise) that of the remaining plurality of coils 202 (e.g, coil 202a and coil 202c). For example, the fluid refrigerant can flow downward through coil 202b but upward through coils 202a and 202c. In other embodiments, the opposite orientation can be achieved. In yet further embodiments, the refrigerant can flow in the substantially same direction or orientation (e.g., parallel) through all the coils.
  • the fluid refrigerant can flow through one or more coils (e.g., coil 202b) in the direction opposite (e.
  • the apparatus further comprises a cooling device 501 (e.g., heat exchanger, water condenser, etc.) within the closed loop and interposed between the condenser 300 and the expansion device 400.
  • a cooling device 501 e.g., heat exchanger, water condenser, etc.
  • the cooling device 501 may be operably linked to a condenser inlet line 405 which connects the condenser 300 to the cooling device 501.
  • an expansion inlet line 115 connects the cooling device 501 with the expansion device 400.
  • the cooling device 501 is a separate, self- containing vapor-compression refrigeration system, a fan, heat exchanger, water condenser, or the like. Referring to Figures 10-1 1 , in other embodiments, the inlet lines 405 and/or 115 can be used without the cooling device 501.
  • Figure 14 illustrates a modified evaporator 401 similar to the embodiment of Figure 4 but with one or more different features.
  • the modified evaporator 401 includes a line 1412 connecting two or more coils 202b and 202a (e.g., such that refrigerant from condenser inlet line 405 traverses two or more coils before being received by the expansion device 400).
  • the condenser 300 is operably connected by the condenser inlet line 405 to at least one of the plurality of coils 202, for example coil 202b, via coil inlet 103b. Refrigerant or other fluid flows through from the condenser 300 through the evaporation 401 without first passing through the expansion device 400.
  • Refrigerant flows through coil 202b from inlet 103b to outlet 104b where it flows into the inlet 103a of coil 202a via the line 1412.
  • the refrigerant or other fluid continues to flow through the second coil 202a to the outlet 104a and then to the expansion device 400.
  • the expansion device 400 is directly linked to coil 202a via the coil outlet 104a and expansion inlet line 115. Flowing the refrigerant or other fluid through two or more coils can increase cooling relative to flow through one coil.
  • the other outlets 104 can be connected to the compressor 200 such that fluid flows upward or downward from the other inlets 103 of the other coils 202 to the outlets 104 as described above.
  • the other corresponding inlets 103 can be connected to the expansion device 400 as in a conventional system such that the cooled refrigerant is provided to the evaporator accordingly.
  • three, four, or more coils can be linked such that the refrigerant can flow through even more coils before reaching the expansion device 400.
  • FIG. 15 is a depiction of a cross section of another vapor-compression refrigeration system comprising a cooling device 501 in operable communication with a condenser 300 and an expansion device 400 (e.g., metering or other distribution device).
  • the cooling device 501 e.g., heat exchanger, water condenser, etc.
  • the cooling device 501 may be operably linked to a condenser inlet line 405 which connects the condenser 300 to the cooling device 501.
  • One or more expansion inlet and outlet lines 115, 116 connect the cooling device 501 with the expansion device 400 to cool the cooling device 501 and/or fluid flowing therethrough and to provide the cooled fluid (e.g., refrigerant) to the expansion device 400 with direction of flow indicated by the broken arrows.
  • the expansion device 400 can then provide pre-cooled or sub-cooled fluid to the evaporator through the inlets 103 of the coils 202 where the fluid flows through the coils 202 and out the outlets 104 to the compressor 200.
  • the cooling device 501 is a separate, self-containing vapor-compression refrigeration system, a fan, heat exchanger, water condenser, or the like.
  • FIG. 16 is a depiction of another vapor-compression refrigeration system comprising a cooling device 1601 (e.g., water condenser, heat exchanger, etc.) in operable communication with a compressor 200 and an evaporator.
  • a cooling device 1601 e.g., water condenser, heat exchanger, etc.
  • One or more coils 202 via their corresponding outlets 104 are connected to an inlet of the cooling device 1601 to cool the cooling device 1601 and/or fluid (e.g., refrigerant) flowing therethrough to the compressor 200.
  • the fluid flowing therethrough can flow from the condenser 300 through the cooling device 1601 to be cooled before entering the expansion device 400 or other metering or distribution device which can provide the refrigerant to the evaporator through inlets 103.
  • the remaining coils 202 and their corresponding outlets 104 can be connected to the compressor 200 for receiving the refrigerant and fluid can flow therethrough to circulate in a conventional manner without passing through the cooling device
  • the flash gas produced in the evaporator 100 creates inefficiency in a vapor-compression refrigeration system.
  • the invention provides a method of reducing flash gas and improving efficiency by pre-cooling warm refrigerant coming from the condenser 300 prior to the refrigerant entering the expansion device 400.
  • the method of increasing the efficiency of a vapor- compression refrigeration apparatus comprises at least the step of reducing temperature of at least a portion of the fluid refrigerant prior to the fluid refrigerant entering the expansion device 400.
  • the temperature of the fluid refrigerant entering the expansion device of the present invention is reduced by about 5%, about 10%, about 20%, about 30%, about 40%, about 50%, or about 60% as compared to the temperature the fluid refrigerant that enters the expansion device in a traditional vapor-compression refrigeration apparatus.
  • the method of increasing the efficiency of a vapor-compression refrigeration apparatus further comprises reducing the pressure of at least a portion of the fluid refrigerant prior to the fluid refrigerant entering the expansion device.
  • the refrigerant can traverse proximate to (e.g., not directly through) an evaporator 100 prior to the fluid refrigerant entering the expansion device 400.
  • the method involves reducing the temperature of at least a portion of the fluid refrigerant prior to the fluid refrigerant entering the expansion device 400 by traversing at least a portion of the fluid refrigerant through at least a portion of the modified evaporator 401 prior to entering the expansion device 400.
  • the method involves reducing the temperature of at least a portion of the fluid refrigerant prior to the fluid refrigerant entering the expansion device 400 by traversing at least a portion of the fluid refrigerant through a cooling device 501, 1601.
  • the cooling device 501 , 1601 is a separate, self- containing vapor-compression refrigeration system, a fan, heat exchanger, water condenser, or the like.
  • the present invention also provides an evaporator 100, more particularly a modified evaporator 401 , comprising a plurality of coils 202, wherein at least one of the plurality of coils, for example coil 202b, is configured within the modified evaporator 401 so that fluid refrigerant traverses at least a portion of the modified evaporator 401 in a direction substantially opposite the flow direction of the refrigerant through the remaining plurality of coils 202, for example coil 202a and coil 202c.
  • a modified evaporator 401 comprising a plurality of coils 202, wherein at least one of the plurality of coils, for example coil 202b, is configured within the modified evaporator 401 so that fluid refrigerant traverses at least a portion of the modified evaporator 401 in a direction substantially opposite the flow direction of the refrigerant through the remaining plurality of coils 202, for example coil 202a and coil 202c.
  • At least one of the plurality of coils 202, for example coil 202b, of the modified evaporator 401 is in direct communication with a condenser 300 via a coil inlet, for example coil inlet 103b, for receiving warm liquid refrigerant directly (i.e. without passing through an expansion device 400) from the condenser 300.
  • the at least one of the plurality of coils 202, for example coil 202b, of the modified evaporator 401 is in direct communication with the expansion device 400 via coil outlet 104b.
  • the at least one of the plurality of coils 202, for example coil 202b, of the modified evaporator 401 may be directly linked to the expansion device 400 by expansion inlet line 115.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)

Abstract

La présente invention concerne un évaporateur et ses procédés d'utilisation. Un appareil de réfrigération à compression de vapeur, selon un mode de réalisation de la présente invention, utilise un fluide frigorigène et peut comprendre un compresseur, un condenseur, un dispositif d'expansion et un évaporateur agencés successivement et en communication fluidique à l'intérieur d'une boucle fermée afin de faire circuler le fluide frigorigène. L'appareil peut comprendre au moins une ligne à l'intérieur de la boucle fermée en communication fonctionnelle avec le condenseur, afin de réduire la température d'au moins une partie du fluide frigorigène provenant du condenseur, avant que le fluide frigorigène entre dans le dispositif d'expansion.
PCT/US2015/039056 2014-07-02 2015-07-02 Évaporateur et ses procédés d'utilisation WO2016004349A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201462020274P 2014-07-02 2014-07-02
US62/020,274 2014-07-02

Publications (1)

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WO2016004349A1 true WO2016004349A1 (fr) 2016-01-07

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US5408836A (en) * 1994-01-14 1995-04-25 Thermo King Corporation Methods and apparatus for operating a refrigeration system characterized by controlling engine coolant
US20030115895A1 (en) * 2001-12-26 2003-06-26 York International Corporation Self-tuning pull-down fuzzy logic temperature control for refrigeration systems
US20060032245A1 (en) * 2004-08-11 2006-02-16 Lawrence Kates Method and apparatus for monitoring refrigerant-cycle systems
US20070074536A1 (en) * 2002-11-11 2007-04-05 Cheolho Bai Refrigeration system with bypass subcooling and component size de-optimization
US20070256432A1 (en) * 2002-12-09 2007-11-08 Kevin Zugibe Method and apparatus for optimizing refrigeration systems
US20090241568A1 (en) * 2008-04-01 2009-10-01 Trane International Inc. Floating restriction for a refrigerant line

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US5212965A (en) * 1991-09-23 1993-05-25 Chander Datta Evaporator with integral liquid sub-cooling and refrigeration system therefor
US5243837A (en) * 1992-03-06 1993-09-14 The University Of Maryland Subcooling system for refrigeration cycle
US5406805A (en) * 1993-11-12 1995-04-18 University Of Maryland Tandem refrigeration system
KR20000055341A (ko) * 1999-02-05 2000-09-05 윤종용 인터쿨러 냉장고의 제어방법
US9234673B2 (en) * 2011-10-18 2016-01-12 Trane International Inc. Heat exchanger with subcooling circuit
EP2690212B1 (fr) * 2012-07-23 2016-11-09 Whirlpool Corporation Procédé pour commander un sèche-linge avec système de pompe à chaleur et sèche-linge commandé par un tel procédé

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5408836A (en) * 1994-01-14 1995-04-25 Thermo King Corporation Methods and apparatus for operating a refrigeration system characterized by controlling engine coolant
US20030115895A1 (en) * 2001-12-26 2003-06-26 York International Corporation Self-tuning pull-down fuzzy logic temperature control for refrigeration systems
US20070074536A1 (en) * 2002-11-11 2007-04-05 Cheolho Bai Refrigeration system with bypass subcooling and component size de-optimization
US20070256432A1 (en) * 2002-12-09 2007-11-08 Kevin Zugibe Method and apparatus for optimizing refrigeration systems
US20060032245A1 (en) * 2004-08-11 2006-02-16 Lawrence Kates Method and apparatus for monitoring refrigerant-cycle systems
US20090241568A1 (en) * 2008-04-01 2009-10-01 Trane International Inc. Floating restriction for a refrigerant line

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