WO2012128610A1 - Sous-refroidisseur de conduite de liquide et procédé permettant d'effectuer un sous-refroidissement d'un fluide de travail entrant dans un appareil de mesure - Google Patents

Sous-refroidisseur de conduite de liquide et procédé permettant d'effectuer un sous-refroidissement d'un fluide de travail entrant dans un appareil de mesure Download PDF

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Publication number
WO2012128610A1
WO2012128610A1 PCT/MY2012/000064 MY2012000064W WO2012128610A1 WO 2012128610 A1 WO2012128610 A1 WO 2012128610A1 MY 2012000064 W MY2012000064 W MY 2012000064W WO 2012128610 A1 WO2012128610 A1 WO 2012128610A1
Authority
WO
WIPO (PCT)
Prior art keywords
evaporator
subcooler
working fluid
metering device
liquid line
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/MY2012/000064
Other languages
English (en)
Inventor
Keng Seng CHUA
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
THERMO HYGRO CONSULTANTS Sdn Bhd
Original Assignee
THERMO HYGRO CONSULTANTS Sdn Bhd
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 THERMO HYGRO CONSULTANTS Sdn Bhd filed Critical THERMO HYGRO CONSULTANTS Sdn Bhd
Publication of WO2012128610A1 publication Critical patent/WO2012128610A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F28D1/0478—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • 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—Component parts or details not otherwise provided for in this subclass
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • 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

  • This invention relates to heat transfer systems using refrigeration principles or the like to extract heat from heat sources, and is more particularly concerned with a refrigeration systems employing heat exchanging liquid line subcooler that uses the working fluid that flows through the evaporator to further subcool the working fluid exiting the condenser prior to the working fluid entering the metering device to improve system cooling capacity without additional expenditure of energy when the working fluid evaporates in the evaporator. Consequently, the additional cooling capacity will provide more heat extraction capacity at the energy source and eventually turn into more heat capacity for the heating of water or air.
  • thermodynamic characteristics of a typical refrigeration system are illustrated by the pressure-enthalpy diagram as shown in FIG 1.
  • Gaseous working fluids at low pressure travel along the suction line from the evaporator to the compressor at a slightly superheated condition and undergo polytropic compression in process 1 1-12.
  • the gaseous working fluid is then compressed to condensing pressure at point 12.
  • Heat is rejected at constant pressure along the condensation process 12-13, where the working fluid condenses from superheated vapor state into saturated liquid state.
  • the working fluid in liquid form at point 13 is passed through a metering device where the pressure is reduced at constant enthalpy along the process 13-14 to the system suction pressure at point 14.
  • the working fluid which consists of a mixture of liquid and vapor is then evaporated at constant pressure 14- 1 1 to complete the refrigeration cycle.
  • the evaporation of the liquid working fluid in process 14-1 1 represents the useful work of heat absorption in the evaporator.
  • a metering device disposed downstream of condenser could be used to throttles the high pressure working fluid in liquid form to a much lower pressure to achieve the required low temperature for the purpose of absorbing heat from the heat source. Due to this throttling process, a portion of the working fluid in liquid form is converted to vapor form. Since it is this liquid portion that will subsequently evaporate to cause the cooling, the gaseous portion does not do any useful work in the system, further subcooling of the liquid portion prior to the throttling process will serve to reduce this gaseous portion of the mixture and thus increase useful work.
  • the present invention relates to a heat transfer system utilizing a novel approach for subcooling working fluid by heat exchange between the high pressured working fluid in liquid form and the working fluid that flow through the evaporator.
  • a conventional heat transfer system using refrigeration principles comprises a compressor, a condenser, a metering device, and an evaporator interconnected in that sequence in a closed loop with a working fluid circulating therein.
  • the heat transfer system is further provided with a liquid line subcooler that facilitates subcooling of the working fluid exiting the condenser prior to entering metering device by using the working fluid that flow through the evaporator.
  • a metering device are an expansion valve or a capillary tube.
  • the subcooler is physically disposed in the path of forced air passing through the evaporator to facilitate heat transfer by forced convection between the liquid working fluid in the subcooler and the cold air.
  • the subcooler is in thermal contact with the evaporator and also disposed in the path of forced air passing through the evaporator to facilitate heat transfer by conduction and by forced convection to further reduce the temperature of working fluid prior to entering metering device such as an expansion valve or a capillary tube.
  • One advantage of the present invention is the increase in the proportion of liquid in the liquid/vapor mixtures of the working fluid leaving the metering device without incurring more energy expenditure for the compressor as the subcooling results in a greater heat extraction capacity at the evaporator.
  • Another advantage of the present invention is that the heat transfer system will have a better cooling effect on the compressor and thus helps to prolong its life span.
  • Yet another further advantage of the present invention is the resulting increase in the Coefficient of Performance (COP) of the system and the resultant energy saving.
  • COP Coefficient of Performance
  • FIG 1 is a pressure-enthalpy diagram of a refrigeration process with the effect of the present invention shown in dotted lines.
  • FIG 2 is a schematic view of a conventional heat transfer system employing refrigeration principles.
  • FIG 3 is a schematic view of a heat transfer system provided with a subcooler in accordance to one embodiment of the present invention
  • FIG 4 is a schematic view of a heat transfer system provided with a subcooler in accordance to another embodiment of the present invention
  • FIG 5 is a schematic view of one example of a series of cooling fins facilitating thermal contact between the evaporator and the subcooler.
  • FIG 6 is a schematic view of another example of a series of cooling fins facilitating thermal contact between the evaporator and the subcooler.
  • FIG 7 is the front view of FIG 6.
  • a conventional heat transfer system (20) employing refrigeration principles is shown to include a compressor (21), a condenser (22), a metering device (24), and an evaporator (25) connected within a closed circuit.
  • the compressor (21) the working fluid in vapour form is compressed into a high pressure and temperature vapour prior to entering the condenser (22).
  • This high pressure and high temperature vapour then flows into the condenser (22) along the line (26).
  • heat is rejected to outdoor air (32) so that the working fluid in vapour form can condense back into liquid form.
  • the liquefied working fluid then enters a metering device (24) which can be an expansion valve or a capillary tube or any other type of metering device used in refrigeration circuits.
  • This metering device (24) restricts the flow by forcing the refrigerant to go through a small aperture which causes a flash throttling to occur where the liquid working fluid undergoes a reduction both in pressure and temperature, resulting in two-phase fluid (mixture of liquid and vapor phases). At this reduced pressure, the liquid portion of the mixture can evaporate at low temperature enabling it to absorb heat from the heat source within the evaporator. After evaporation, the gaseous working fluid is then routed back to the compressor (21) along the vapor line (31) to complete the refrigeration cycle.
  • a liquid line subcooler (23) is included between the condenser (22) and the metering device (24) in the conventional refrigeration system described in FIG. 2 above. More particularly, the subcooler (23) of the present invention is located in close proximity to the evaporator (25) and in the path of cold air (33) passing through and out from the evaporator (25) so as to facilitate subcooling of the working fluid flowing through the subcooler (23) by forced convection before the working fluid flows into the metering device. This will result in an increase in the liquid portion of the liquid-vapor mixture in the working fluid that flows through line (28) and into the metering device (24).
  • the forced convection could be generated by an external source such as pump, fan, suction device, etc.
  • the subcooling referred to above can be achieved by forced convection and/or conduction as shown in FIG 4.
  • the subcooler (23) is also located in the path of cold air (33) passing through and out from the evaporator (25) so as to subcool the working fluid flowing in the subcooler (23) by forced convection before the working fluids flow into the metering device (24).
  • the subcooler (23) is arranged to be physically abutting the evaporator (25) so that the subcooler (23) is in thermal contact with the evaporator (25). This thermal contact with the evaporator (25) further enhances subcooling of the working fluid flowing in the subcooler (23) as heat exchange in this embodiment is effected both by forced convection and thermal conduction.
  • each of the fins (50) has one or more columns of vertically aligned holes (52, 53) configured to receive the tubing of the evaporator (25).
  • the tubing of the evaporator (25) passes through correspondingly positioned holes (52) in each of the series of cooling fins (50) with the ends of intermediate tubing joined to the end of the adjacent tubing in the next row.
  • the same series of cooling fins (50) is provided with one or more columns of vertically aligned holes (53) through which the tubing of the subcooler (23) passes through.
  • FIG. 5 illustrates an evaporator with two rows of coil and a subcooler with one row of coil.
  • each of the vertically aligned holes (52) for the row of evaporator (25) coil adjacent to the subcooler (23) coil share the same opening with the corresponding vertically aligned holes (53) for the subcooler (23) coil.
  • one row of evaporator (25) coil has an edge in direct contact with an edge of the row of subcooler (23) coil.
  • thermal conduction is effected by direct thermal conduction between the evaporator (25) and subcooler
  • FIG. 5 illustrates tubing of evaporator (25) coil and subcooler (23) coil having square cross section.
  • the holes (52, 53) are appropriately sized and shaped to accommodate square tubing of evaporator (25) coil and subcooler (23) coil.
  • the contact area increases to the length of a side of the square multiply by the length of the tubing in contact.
  • the contact area therefore increases substantially compared to that along a tangential line in the case of tubing with circular cross section.
  • non circular cross section such as a square cross section
  • subcooling is the process of cooling condensed gas beyond what is required for the condensation process.
  • the purpose of subcooling is to assure that no vapor will be left behind at the end of the condensing phase, thus assuring maximum capacity at the metering device (24).
  • a liquid line subcooler (23) which is the subject of the present invention is used to further subcool the working fluid into the liquid form as shown in dotted line 13-15. As the high pressure subcooled liquid from the condenser is reduced in pressure along the line 15-16, its corresponding temperature is reduced and the head load on the condenser (22) is greater than that of the evaporator (25) and eventually turned into more heating capacity for the water or air.
  • the invention also relates to a method for subcooling the working fluid in a heat transfer system (20) by placing a liquid line subcooler (23) between said condenser (22) and said metering device (24) with said liquid line subcooler (23) physically abutting the evaporator (25) and/or located in the path of cold air passing through and out from the evaporator (25) so as to further reduce the temperature of the working fluid flowing in the subcooler (23) through heat exchange between the evaporator (25) and the subcooler (23) by forced convection and/or thermal conduction to increase the liquid portion of the liquid-vapor mixture in the working fluid entering the metering device (24).

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

La présente invention a trait à un système caloporteur (20) qui emploie les principes de réfrigération, lequel système inclut un compresseur, un condensateur, un appareil de mesure (24) et un évaporateur (25) utilisant un sous-refroidisseur de conduite de liquide à échange de chaleur (23) permettant d'effectuer un sous-refroidissement du fluide de travail circulant entre le condensateur et l'appareil de mesure (24). Selon un mode de réalisation, le sous-refroidisseur (23) est situé à proximité étroite de l'évaporateur et sur la trajectoire de l'air froid traversant l'évaporateur (25). Selon un autre mode de réalisation, le sous-refroidisseur (23) vient physiquement buter contre l'évaporateur (25) et est situé sur la trajectoire de l'air froid traversant l'évaporateur (25) de manière à pouvoir réduire davantage la température du fluide de travail circulant dans le sous-refroidisseur (23) grâce à l'échange de chaleur entre l'évaporateur (25) et le sous-refroidisseur (23) par convection forcée et conduction thermique en vue d'augmenter la partie liquide du mélange liquide-vapeur dans le fluide de travail entrant dans l'appareil de mesure (24).
PCT/MY2012/000064 2011-03-23 2012-03-23 Sous-refroidisseur de conduite de liquide et procédé permettant d'effectuer un sous-refroidissement d'un fluide de travail entrant dans un appareil de mesure Ceased WO2012128610A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
MYPI2011700029 2011-03-23
MYPI2011700029 2011-03-23

Publications (1)

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WO2012128610A1 true WO2012128610A1 (fr) 2012-09-27

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PCT/MY2012/000064 Ceased WO2012128610A1 (fr) 2011-03-23 2012-03-23 Sous-refroidisseur de conduite de liquide et procédé permettant d'effectuer un sous-refroidissement d'un fluide de travail entrant dans un appareil de mesure

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015053610A1 (fr) * 2013-10-11 2015-04-16 Thermo Hygro Consultants Sdn Bhd Appareil de chauffage à pompe à chaleur
CN104613699A (zh) * 2013-11-04 2015-05-13 Lg电子株式会社 冰箱
US9857103B2 (en) 2013-11-04 2018-01-02 Lg Electronics Inc. Refrigerator having a condensation loop between a receiver and an evaporator
CN113769995A (zh) * 2021-10-19 2021-12-10 西安稳能微电子科技有限公司 半导体晶圆涂胶整体式精密恒温恒湿气液体输出装置
PL439961A1 (pl) * 2021-12-23 2023-06-26 Szkoła Główna Gospodarstwa Wiejskiego w Warszawie Mikrokanałowy lamelowy wymiennik ciepła o zredukowanej masie czynnika chłodniczego i zespół wymienników ciepła

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DE2758737A1 (de) * 1977-12-29 1979-07-05 Siemens Ag Verfahren zum betreiben einer waermepumpe
DE2921257A1 (de) * 1979-05-25 1980-12-04 Sueddeutsche Kuehler Behr Verfahren zum betreiben einer waermepumpen-heizungsanlage und vorrichtung zur durchfuehrung des verfahrens
US5243837A (en) * 1992-03-06 1993-09-14 The University Of Maryland Subcooling system for refrigeration cycle
EP0760452A2 (fr) * 1995-08-30 1997-03-05 Carrier Corporation Circuit de contrÔle d'un réfrigérant latent pour un système de conditionnement d'air
EP0846923A2 (fr) * 1996-12-04 1998-06-10 Carrier Corporation Dispositif de récupération de chaleur
US6446450B1 (en) 1999-10-01 2002-09-10 Firstenergy Facilities Services, Group, Llc Refrigeration system with liquid temperature control
US20030061822A1 (en) * 2001-09-29 2003-04-03 Rafalovich Alexander P. Climate control system
US20050198976A1 (en) * 2004-03-15 2005-09-15 John J. Sheridan & Associates, Inc. System for the dehumification of air
US7013658B2 (en) 2004-02-03 2006-03-21 Carrier Corporation Refrigerant subcooling by condensate
EP2306125A1 (fr) * 2009-09-28 2011-04-06 Vaillant GmbH Pompe à chaleur

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Publication number Priority date Publication date Assignee Title
DE2758737A1 (de) * 1977-12-29 1979-07-05 Siemens Ag Verfahren zum betreiben einer waermepumpe
DE2921257A1 (de) * 1979-05-25 1980-12-04 Sueddeutsche Kuehler Behr Verfahren zum betreiben einer waermepumpen-heizungsanlage und vorrichtung zur durchfuehrung des verfahrens
US5243837A (en) * 1992-03-06 1993-09-14 The University Of Maryland Subcooling system for refrigeration cycle
EP0760452A2 (fr) * 1995-08-30 1997-03-05 Carrier Corporation Circuit de contrÔle d'un réfrigérant latent pour un système de conditionnement d'air
EP0846923A2 (fr) * 1996-12-04 1998-06-10 Carrier Corporation Dispositif de récupération de chaleur
US6446450B1 (en) 1999-10-01 2002-09-10 Firstenergy Facilities Services, Group, Llc Refrigeration system with liquid temperature control
US20030061822A1 (en) * 2001-09-29 2003-04-03 Rafalovich Alexander P. Climate control system
US7013658B2 (en) 2004-02-03 2006-03-21 Carrier Corporation Refrigerant subcooling by condensate
US20050198976A1 (en) * 2004-03-15 2005-09-15 John J. Sheridan & Associates, Inc. System for the dehumification of air
EP2306125A1 (fr) * 2009-09-28 2011-04-06 Vaillant GmbH Pompe à chaleur

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2534785A (en) * 2013-10-11 2016-08-03 Thermo Hygro Consultants Sdn Bhd Heat-pump heating apparatus
GB2534785B (en) * 2013-10-11 2020-04-29 Thermo Hygro Consultants Sdn Bhd Heat-pump heating apparatus
WO2015053610A1 (fr) * 2013-10-11 2015-04-16 Thermo Hygro Consultants Sdn Bhd Appareil de chauffage à pompe à chaleur
US9857103B2 (en) 2013-11-04 2018-01-02 Lg Electronics Inc. Refrigerator having a condensation loop between a receiver and an evaporator
CN104613699B (zh) * 2013-11-04 2017-04-12 Lg电子株式会社 冰箱
US9746226B2 (en) 2013-11-04 2017-08-29 Lg Electronics Inc. Refrigerator
EP2868997A3 (fr) * 2013-11-04 2015-09-23 LG Electronics Inc. Réfrigérateur
CN104613699A (zh) * 2013-11-04 2015-05-13 Lg电子株式会社 冰箱
EP3779339A1 (fr) 2013-11-04 2021-02-17 LG Electronics Inc. Réfrigérateur
EP4006467A1 (fr) 2013-11-04 2022-06-01 LG Electronics Inc. Réfrigérateur
CN113769995A (zh) * 2021-10-19 2021-12-10 西安稳能微电子科技有限公司 半导体晶圆涂胶整体式精密恒温恒湿气液体输出装置
CN113769995B (zh) * 2021-10-19 2022-06-17 西安稳能微电子科技有限公司 半导体晶圆涂胶整体式精密恒温恒湿气液体输出装置
PL439961A1 (pl) * 2021-12-23 2023-06-26 Szkoła Główna Gospodarstwa Wiejskiego w Warszawie Mikrokanałowy lamelowy wymiennik ciepła o zredukowanej masie czynnika chłodniczego i zespół wymienników ciepła

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