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US20090025405A1 - Economized Vapor Compression Circuit - Google Patents

Economized Vapor Compression Circuit Download PDF

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Publication number
US20090025405A1
US20090025405A1 US12/041,978 US4197808A US2009025405A1 US 20090025405 A1 US20090025405 A1 US 20090025405A1 US 4197808 A US4197808 A US 4197808A US 2009025405 A1 US2009025405 A1 US 2009025405A1
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US
United States
Prior art keywords
refrigerant
economizer
heat exchanger
stream
evaporator
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.)
Abandoned
Application number
US12/041,978
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English (en)
Inventor
Mustafa Kemal Yanik
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.)
Johnson Controls Technology Co
Original Assignee
Johnson Controls Technology Co
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 Johnson Controls Technology Co filed Critical Johnson Controls Technology Co
Priority to US12/041,978 priority Critical patent/US20090025405A1/en
Priority to PCT/US2008/070244 priority patent/WO2009017968A1/fr
Priority to TW097127919A priority patent/TW200921030A/zh
Publication of US20090025405A1 publication Critical patent/US20090025405A1/en
Priority to US13/479,722 priority patent/US8713963B2/en
Abandoned 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
    • 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
    • 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
    • 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
    • F28D1/053—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 straight
    • F28D1/0535—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 straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/007—Auxiliary supports for elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • 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—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • F25B31/008—Cooling of compressor or motor by injecting a liquid

Definitions

  • HVAC&R heating, ventilation, air conditioning and refrigeration
  • Vapor compression refrigeration cycles typically require sub-cooling (i.e. cooling the refrigerant to a temperature lower than the saturation temperature at the condenser pressure) at the condenser outlet for stable operation of metering devices, such as expansion valves; sub-cooling also increases the refrigeration effect of refrigerant in the evaporator. Due to a low heat transfer coefficient of liquid refrigerants and small temperature differences between the refrigerant and the cooling fluid, the surface area of the condenser to achieve the desired level of sub-cooling can become considerable and a significant portion of the condenser surface can be dedicated to sub-cooling the refrigerant. Thus, the efficiency of the condenser, and in turn the entire system, is restricted.
  • More recent condenser coil technologies such as multi-channel heat exchangers, operate at a lower condensing temperature, which reduces the temperature difference between the liquid refrigerant and air. This, in turn, increases the importance of sub-cooling in systems using such heat exchangers.
  • liquid refrigerant may need to be piped over relatively long distances.
  • phase changes can occur at undesired locations, which may be avoided by first adequately subcooling the refrigerant.
  • One embodiment relates to an economized vapor compression circuit that includes an evaporator, a compressor, a condenser and an economizer.
  • the evaporator, compressor, condenser and economizer are fluidly connected by a refrigerant line containing refrigerant, wherein liquid refrigerant leaving the economizer is split into a first stream and second stream.
  • the first stream of refrigerant flows in a heat exchange relationship with refrigerant to be provided to the evaporator in which the first stream of liquid refrigerant expands and evaporates, subcooling refrigerant to be provided to the evaporator, the second stream of liquid refrigerant leaving the economizer flows to the evaporator.
  • the economizer is a heat exchanger in which the sub-cooling also takes place.
  • the economizer is a flash tank and a separate sub-cooling heat exchanger is employed.
  • Another embodiment relates to a method for operating a vapor compression circuit that includes providing a refrigerant circuit having a condenser, an evaporator, an economizer, an expansion device, and a compressor fluidly connected by a refrigerant line containing refrigerant, directing substantially all refrigerant leaving the condenser to a first side of the economizer, diverting a minority portion of liquid refrigerant leaving the first side of the economizer to expand and enter a second side of the economizer to exchange heat with refrigerant in the first side of the economizer, and sub-cooling refrigerant in the first side of the economizer.
  • Still another embodiment relates to an economized vapor compression circuit that includes a compressor, a condenser, an economizer, an expansion device and an evaporator connected in a closed refrigeration loop.
  • the economizer is configured to receive all refrigerant leaving the condenser and to provide sub-cooled liquid refrigerant to the evaporator. A portion of the liquid refrigerant leaving the economizer is diverted back to the economizer to exchange heat with the refrigerant entering the economizer from the condenser to sub-cool refrigerant being provided to the evaporator.
  • Certain advantages of some embodiments described herein include that by reducing or eliminating the need for sub-cooling at the condenser outlet permits the discharge pressure at the compressor to be lowered, resulting in better efficiency of the overall system.
  • the size of the condenser surface may also be reduced so that the corresponding cost of the condenser is lowered.
  • the sub-cooling may permit liquid refrigerant to be piped over longer distances.
  • FIG. 1 depicts a cutaway view of a building that is equipped with an HVAC&R system.
  • FIG. 2 is a schematic illustration of a vapor compression circuit.
  • FIG. 3 is a schematic illustration of a vapor compression circuit according to an exemplary embodiment.
  • FIG. 4 is a schematic illustration of a vapor compression circuit according to another exemplary embodiment.
  • FIG. 5 is a schematic illustration of a vapor compression circuit according to yet another exemplary embodiment.
  • FIG. 1 shows an exemplary HVAC&R system 10 for a building 11 in a typical commercial setting.
  • a chiller 20 circulates a cooling fluid, such as water, to a heat exchanger contained in an air handler 40 in fluid communication with chiller 20 by conduits 22 .
  • HVAC&R system 10 is shown with a separate air handler 40 on each floor of building 11 , but it will be appreciated that these components may be shared between or among floors.
  • Air handler 40 uses ducting 70 to draw outside air into HVAC&R system 10 that is mixed with air returned from within building 11 in air return duct 60 .
  • the cooling fluid absorbs heat from the mixture of outside air and returned air, cooling that mixture which is then provided throughout building 11 ; in turn, the warmed cooling fluid returns to chiller 20 , where it is cooled again by a refrigerant.
  • a boiler 30 may be used to circulate a heated fluid for providing heating to the building 11 .
  • the warmed cooling fluid returning to chiller 20 is cooled by a refrigerant, which refrigerant is itself warmed and cooled in a closed loop within chiller 20 .
  • the refrigerant in the closed loop undergoes cyclic state changes within chiller 20 from vapor to liquid and then from liquid back to vapor depending on whether the refrigerant is absorbing or releasing energy as heat.
  • This closed loop is known as a refrigerant cycle, and is sometimes more generically referred to as a vapor compression cycle.
  • the basic circuit 100 includes a compressor 102 , a condenser 104 , and an evaporator 106 which are fluidly connected to one another, typically by one or more lines of piping.
  • Compressor 102 compresses refrigerant in vapor form and delivers the vapor to condenser 104 through a discharge line.
  • the refrigerant vapor is delivered by compressor 102 to condenser 104 where it enters into a heat exchange relationship with a fluid, such as the outside air surrounding building 11 .
  • the compressed vapor undergoes a phase change to a refrigerant liquid as a result of the heat exchange relationship with the fluid.
  • the condensed liquid refrigerant from condenser 104 flows through an expansion device 108 to evaporator 106 .
  • the condensed liquid refrigerant delivered to evaporator 106 enters into a heat exchange relationship with a second fluid.
  • the second fluid is the warmed water returning to chiller 20 from air handler(s) 40 .
  • the heat absorbed from the water causes the liquid refrigerant to undergo a phase change to a refrigerant vapor (and thereby cooling the water for distribution back to the air handler(s) 40 as discussed above).
  • the vapor refrigerant exits evaporator 106 and returns to compressor 102 by a suction line to complete the cycle.
  • Compressor 102 can be driven by a motor (not shown).
  • exemplary embodiments of the invention are capable of being implemented in any situation in which a vapor compression cycle is used and that reference to the specific HVAC&R system 10 and the chiller 20 of FIG. 1 is for context only.
  • FIGS. 3 and 4 illustrate exemplary embodiments of circuits that modify the vapor compression cycle to accomplish sub-cooling of refrigerant other than at the outlet of condenser 104 .
  • sub-cooling elsewhere in the circuit greater system efficiency and a greater realization of the advantages provided by sub-cooling can be achieved.
  • refrigerant leaving condenser 104 may be a saturated liquid or may be a two-phase mixture with low vapor quality. In either case, substantially the entire flow of refrigerant leaving condenser 104 is directed to a “warm” side 110 a of an economizer/sub-cooler heat exchanger 110 and the refrigerant is generally not appreciably sub-cooled when it leaves the outlet of condenser 104 . That is, while some sub-cooling at the condenser 104 may occur, there is generally less than about 5° F. sub-cooling.
  • economizer/sub-cooler heat exchanger 110 enables refrigerant from condenser 104 to be sub-cooled in economizer/sub-cooler 110 , not in condenser 104 .
  • the sub-cooled liquid refrigerant flow is divided into two streams. A minor portion forms a first stream that goes to an expansion valve 114 that supplies the “cool” side 110 b of the economizer/sub-cooler 110 , while the majority of the flow forms a second stream that passes to the evaporator, usually via the expansion valve 108 .
  • the “warm side” and “cool side” of a heat exchanger refer to the manner in which two streams of fluid flow through the heat exchanger without being in physical contact with one another, but are in thermal contact to exchange heat.
  • warm side is meant that the refrigerant enters one end of a heat exchanger warmer than it will leave the other end of the heat exchanger and is separated from the “cool” side, which refers to the separate flow path of a fluid that enters the heat exchanger that will be warmed during its residence time within the heat exchanger.
  • the refrigerant flowing through the cool side 110 b of economizer/sub-cooler 110 is in a heat exchange relationship with refrigerant entering the warm side of economizer/sub-cooler 110 and thus absorbs heat from the refrigerant entering economizer/sub-cooler 110 from condenser 104 .
  • the refrigerant entering the cool side 110 b of economizer/sub-cooler 110 is evaporated by the heat absorbed from the refrigerant flowing through the warm side 110 a.
  • the amount of refrigerant diverted back to the cool side 110 b of economizer/sub-cooler 110 may vary depending on the conditions and capacity of the particular HVAC&R system 10 in which the vapor compression cycle will be employed. In some embodiments, the amount diverted is about 10% to about 20% (by mass) of the liquid refrigerant stream leaving economizer/sub-cooler 110 .
  • the stream of evaporated refrigerant leaving the cool side 110 b of economizer/sub-cooler 110 is pulled to compressor 102 .
  • the evaporated refrigerant may be supplied to compressor 102 at the same or a different point, or intermediate pressure, than suction line refrigerant entering compressor 102 from evaporator 106 .
  • the evaporated stream of refrigerant leaving economizer/sub-cooler 110 is pulled to a secondary or auxiliary compressor 302 that discharges compressed refrigerant back into the discharge line leaving compressor 102 .
  • a receiver 116 is optionally positioned between economizer/sub-cooler 110 and the expansion and return valves 108 , 114 , as shown in FIG. 3 . If used, the receiver 116 serves as a collection/temporary holding tank for liquid refrigerant prior to delivery to evaporator 106 or to the cool side 110 b of economizer/sub-cooler 110 .
  • the exemplary vapor compression cycles illustrated in the circuits of FIGS. 3 and 4 differ from a traditional economizer cycle in that in a traditional economizer cycle, the refrigerant flow is split into two streams before entering an economizer, requiring the refrigerant to be sub-cooled prior to the economizer, i.e. in the condenser. That is, in the illustrated exemplary embodiments, the refrigerant flow is split after flowing through the warm side 110 a of economizer/sub-cooler 110 , which permits the refrigerant at the condenser outlet to have little to no sub-cooling.
  • the saturated condensing temperature will be comparatively less, as will the discharge pressure from compressor(s) 102 , 302 , resulting in an increase in the coefficient of performance for the circuit.
  • the coefficient of performance could be maintained, but a smaller condenser could be used.
  • some combination of increased performance and smaller condenser size could be achieved.
  • FIG. 5 illustrates yet another exemplary embodiment of a vapor compression circuit 400 having an economizer that is a flash tank 410 instead of a heat exchanger.
  • This embodiment may be advantageous for use in a vapor compression cycle that employs evaporator 106 located at an extended distance away from flash tank 410 .
  • the pressure drop caused by liquid refrigerant flowing to evaporator 106 at a remote location may result in a phase change from liquid to vapor occurring within the piping prior to reaching evaporator 106 , resulting in improper system operation.
  • the refrigerant leaves condenser 104 and is sent to flash tank 410 .
  • flash tank 410 a portion of the refrigerant is vaporized and returned to compressor 102 , while the remaining liquid refrigerant leaves flash tank 410 as a saturated liquid.
  • the liquid refrigerant from flash tank 410 is split into two streams.
  • a first stream is formed in which a small amount of the liquid refrigerant leaving a liquid outlet of flash tank 410 is diverted, then expanded through an expansion valve 414 .
  • This diverted refrigerant flows through the cool side 411 b of a sub-cooler heat exchanger 411 .
  • the majority of the liquid refrigerant from flash tank 410 is undiverted, forming a second stream to be provided to evaporator 106 but which is first supplied to the warm side 411 a of sub-cooler 411 .
  • a separate, dedicated sub-cooling heat exchanger is employed after the refrigerant is first economized in the flash tank 410 .
  • the diverted liquid refrigerant of the first stream enters the cool side 411 b of sub-cooler 411 and absorbs heat from the liquid refrigerant flowing through the warm side 411 a of sub-cooler 411 .
  • the absorbed heat causes the cool side refrigerant to expand and evaporate, and in turn causes the warm side refrigerant to be sub-cooled.
  • the refrigerant leaving sub-cooler 411 is sufficiently sub-cooled to have enough pressure available to travel through piping that connects sub-cooler 411 to remote evaporator 106 .
  • the refrigerant evaporated in the cool side 411 b of sub-cooler 411 may be connected to the compressor suction line to mix with the rest of the refrigerant coming from evaporator 106 as shown in FIG. 5 , or may be supplied at an intermediate point in compressor 102 , such as shown in FIG. 3 .
  • condenser 104 can be any style of heat exchanger that condenses the refrigerant.
  • condenser 104 comprises one or more multi-channel heat exchangers, such as a mini-channel heat exchanger.
  • condenser 104 could also be a fin and tube heat exchanger, a water cooled heat exchanger, or any other suitable heat exchanger.
  • evaporator 106 can also be a heat exchanger of any suitable configuration, e.g., multi-channel heat exchanger, fin and tube heat exchanger, water cooled heat exchanger, etc.
  • multichannel heat exchanger refers to arrangements in which heat transfer tubes include a plurality of flow paths between manifolds that distribute flow to and collect flow from the tubes.
  • a number of other terms may be used in the art for similar arrangements.
  • Such alternative terms might include “microchannel” (sometimes intended to imply having fluid passages on the order of a micrometer and less), and “microport”.
  • multichannel tubes will include flow paths disposed along the width or in a plane of a generally flat, planar tube, although, again, the invention is not intended to be limited to any particular geometry unless otherwise specified in the appended claims.
  • Compressor 102 can be any suitable type of compressor, e.g., rotary compressor, screw compressor, reciprocating compressor, centrifugal compressor, swing link compressor, scroll compressor, turbine compressor, or any other suitable compressor.
  • the refrigerant may be any suitable refrigerant, including R134a or R410A by way of example only.
  • any suitable heat exchanger such as a shell and tube heat exchanger, tube and tube heat exchanger or plate heat exchanger may be used.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)
US12/041,978 2007-07-27 2008-03-04 Economized Vapor Compression Circuit Abandoned US20090025405A1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US12/041,978 US20090025405A1 (en) 2007-07-27 2008-03-04 Economized Vapor Compression Circuit
PCT/US2008/070244 WO2009017968A1 (fr) 2007-07-27 2008-07-17 Circuit de compression de vapeur économique
TW097127919A TW200921030A (en) 2007-07-27 2008-07-23 Economized vapor compression circuit
US13/479,722 US8713963B2 (en) 2007-07-27 2012-05-24 Economized vapor compression circuit

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US95228007P 2007-07-27 2007-07-27
US12/041,978 US20090025405A1 (en) 2007-07-27 2008-03-04 Economized Vapor Compression Circuit

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US13/479,722 Division US8713963B2 (en) 2007-07-27 2012-05-24 Economized vapor compression circuit

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US20090025405A1 true US20090025405A1 (en) 2009-01-29

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US12/041,978 Abandoned US20090025405A1 (en) 2007-07-27 2008-03-04 Economized Vapor Compression Circuit
US12/179,984 Active 2033-01-26 US8844306B2 (en) 2007-07-27 2008-07-25 Heat exchanger support
US13/479,722 Active 2028-03-29 US8713963B2 (en) 2007-07-27 2012-05-24 Economized vapor compression circuit

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Application Number Title Priority Date Filing Date
US12/179,984 Active 2033-01-26 US8844306B2 (en) 2007-07-27 2008-07-25 Heat exchanger support
US13/479,722 Active 2028-03-29 US8713963B2 (en) 2007-07-27 2012-05-24 Economized vapor compression circuit

Country Status (3)

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US (3) US20090025405A1 (fr)
TW (2) TW200921030A (fr)
WO (3) WO2009017968A1 (fr)

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US20110048055A1 (en) * 2008-05-08 2011-03-03 Daikin Industries, Ltd. Refrigeration apparatus
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US20130061610A1 (en) * 2010-05-26 2013-03-14 Ping Zhang Screw Type Wind-Chilling Water Chiller Unit and Refrigeration Method Thereof
WO2013039572A1 (fr) * 2011-09-16 2013-03-21 Danfoss Turbocor Compressors B.V. Circuits de refroidissement et de sous-refroidissement de moteur pour compresseur
US20150075190A1 (en) * 2013-08-26 2015-03-19 Allen John Mahncke Air conditioning companion stabilizer system
US20150121947A1 (en) * 2013-11-04 2015-05-07 Henry C. Chu Auxiliary air conditioning device for vehicle
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US20160084539A1 (en) * 2014-09-22 2016-03-24 Liebert Corporation Cooling system having a condenser with a micro-channel cooling coil and sub-cooler having a fin-and-tube heat cooling coil
WO2016077281A1 (fr) * 2014-11-14 2016-05-19 Carrier Corporation Cycle économique avec stockage d'énergie thermique
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EP3196568A1 (fr) * 2016-01-19 2017-07-26 Heatcraft Refrigeration Products LLC Système de refroidissement à faible charge de température
WO2017143018A1 (fr) * 2016-02-16 2017-08-24 Honeywell International Inc. Système de climatisation multi-étagé à faible prg
CN109073284A (zh) * 2016-02-16 2018-12-21 霍尼韦尔国际公司 多级低gwp空气调节系统
US10907869B2 (en) * 2018-05-24 2021-02-02 Honeywell International Inc. Integrated vapor cycle and pumped two-phase cooling system with latent thermal storage of refrigerants for transient thermal management
US20230053834A1 (en) * 2021-08-21 2023-02-23 Carrier Corporation Enhanced economizer operation in a chiller
US20230204268A1 (en) * 2021-12-27 2023-06-29 Hyundai Motor Company Gas injection type heat management system for vehicle
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US8360833B2 (en) * 2009-05-28 2013-01-29 American Power Conversion Corporation Method and apparatus for attachment and removal of fans while in operation and without the need for tools
US7944692B2 (en) 2009-06-12 2011-05-17 American Power Conversion Corporation Method and apparatus for installation and removal of overhead cooling equipment
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WO2012094806A1 (fr) * 2011-01-11 2012-07-19 American Power Conversion Corporation Procédé et unité de refroidissement
US20130256423A1 (en) 2011-11-18 2013-10-03 Richard G. Lord Heating System Including A Refrigerant Boiler
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US20120234036A1 (en) 2012-09-20
WO2009018159A2 (fr) 2009-02-05
TW200921030A (en) 2009-05-16
WO2009017968A1 (fr) 2009-02-05
TW200923302A (en) 2009-06-01
WO2009018147A2 (fr) 2009-02-05
WO2009018159A3 (fr) 2009-04-23
US8844306B2 (en) 2014-09-30
US20090025418A1 (en) 2009-01-29
WO2009018147A3 (fr) 2009-05-28
US8713963B2 (en) 2014-05-06

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