US20170268808A1 - Improved dircet expansion evaporator based chiller system - Google Patents

Improved dircet expansion evaporator based chiller system Download PDF

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Publication number
US20170268808A1
US20170268808A1 US15/505,445 US201415505445A US2017268808A1 US 20170268808 A1 US20170268808 A1 US 20170268808A1 US 201415505445 A US201415505445 A US 201415505445A US 2017268808 A1 US2017268808 A1 US 2017268808A1
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US
United States
Prior art keywords
refrigerant
evaporator
chiller system
vapor
separator
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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
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US15/505,445
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English (en)
Inventor
Charbel Rahhal
Richard G. Lord
Jack Leon Esformes
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.)
Carrier Corp
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Carrier Corp
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Filing date
Publication date
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Publication of US20170268808A1 publication Critical patent/US20170268808A1/en
Assigned to CARRIER CORPORATION reassignment CARRIER CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: LORD, RICHARD G., ESFORMES, JACK LEON, RAHHAL, Charbel
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
    • F25B40/06—Superheaters
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • 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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0012—Ejectors with the cooled primary flow at high pressure
    • 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
    • F25B2400/23—Separators

Definitions

  • the invention relates generally to air conditioning and refrigeration systems and, more particularly, to an air conditioning and refrigeration system that enables the use of immiscible oil.
  • refrigerant vapor from an evaporator is drawn in by a compressor, which then delivers the compressed refrigerant to a condenser (or a gas cooler for transcritical applications).
  • a condenser heat is exchanged between a secondary fluid, such as air or water, and the refrigerant.
  • the refrigerant typically in a liquid state passes to an expansion device, where the refrigerant is expanded to a lower pressure and temperature before being provided to the evaporator.
  • air conditioning applications heat is exchanged within the evaporator between the refrigerant and air or another secondary fluid, such as water, glycol, or brine for example, to condition the indoor air of a space.
  • the refrigerant compressor since the refrigerant compressor necessarily involves moving parts, it is typically required to provide lubrication to these parts by means of lubricating oil that is mixed with or entrained in the refrigerant passing through the compressor.
  • lubricating oil that is mixed with or entrained in the refrigerant passing through the compressor.
  • the lubricant is normally not useful within the system other than in the compressor, its presence in low concentrations in the system does not generally detract from the flow, heat transfer, and properties of the refrigerant as it passes through the system in a conventional vapor compression cycle.
  • a heat exchanger such as direct expansion and flooded heat exchangers for example, may be used as evaporators in HVAC systems.
  • the refrigerant typically surrounds the exterior of the tubes positioned within a shell and the secondary fluid to be cooled, such as water for example, flows through the tubes.
  • the secondary fluid to be cooled such as water for example
  • the refrigerant is expanded within the tubes while the chilled second fluid is circulated through the shell.
  • the typical approach temperature in a direct expansion heat exchanger is between 4° K and 6° K to ensure vapor phase at compressor suction.
  • refrigerants Due to environmental global warming potential concerns, new types of refrigerants are being considered for use in air conditioning applications. These new refrigerants include refrigerants that result in the coexistence of vapor and liquid phases through the compression process or refrigerants that have lower discharge gas temperatures and higher miscibility with lubricants compared to conventional refrigerants. Examples of these new refrigerants include, but are not limited to Hydrofluoroolefins (HFOs), and blends of HFOs and Hydrofluorocarbons (HFCs), or other refrigerants and/or refrigerant blends commonly referred to as “wet refrigerants” that have similar properties.
  • HFOs Hydrofluoroolefins
  • HFCs Hydrofluorocarbons
  • a chiller system including a vapor compression circuit consisting of a fluidly coupled compressor, condenser, expansion valve, and evaporator.
  • a refrigerant circulates through the vapor compression circuit.
  • the evaporator is a direct exchange heat exchanger.
  • Refrigerant provided at an outlet of the evaporator is a two-phase mixture including liquid refrigerant and vapor refrigerant.
  • the vapor refrigerant comprises less than or equal to 85% of the two-phase mixture.
  • a refrigerant to refrigerant heat exchanger is fluidly coupled to the circuit.
  • the refrigerant to refrigerant heat exchanger is configured to convert the refrigerant provided at the outlet of the evaporator into a superheated vapor.
  • the refrigerant has a low global warming potential.
  • the refrigerant includes at least one of a Hydrofluoroolefin (HFO) and an HFO blend.
  • HFO Hydrofluoroolefin
  • the chiller system includes a lubrication system having an oil separator arranged generally downstream from the compressor.
  • the oil separator is configured to supply oil separated from the refrigerant to one or more moving components of the compressor.
  • the oil is an immiscible oil.
  • a chiller system including a vapor compression circuit consisting of a fluidly coupled compressor, condenser, expansion valve, and evaporator.
  • a refrigerant circulates through the vapor compression circuit.
  • the evaporator is a direct exchange heat exchanger.
  • Refrigerant provided at an outlet of the evaporator is a two-phase mixture including liquid refrigerant and vapor refrigerant.
  • the vapor refrigerant comprises less than or equal to 85% of the two-phase mixture.
  • An efficiency circuit includes a separator configured to separate the two-phase mixture of refrigerant into liquid refrigerant and vapor refrigerant.
  • the efficiency circuit is operably coupled to the outlet of the evaporator and is configured to recirculate liquid refrigerant from the separator through the evaporator to improve the efficiency of the evaporator and chiller system.
  • the refrigerant has a low global warming potential.
  • the refrigerant includes at least one of a Hydrofluoroolefin (HFO) and an HFO blend.
  • HFO Hydrofluoroolefin
  • the chiller system includes a lubrication system having an oil separator arranged generally downstream from the compressor.
  • the oil separator is configured to supply oil separated from the refrigerant to one or more moving components of the compressor.
  • the oil is an immiscible oil.
  • the separator is operably coupled to the compressor and is configured to supply a refrigerant vapor thereto.
  • the efficiency circuit further includes an ejector having a first inlet and a second inlet.
  • the ejector is positioned generally downstream from the condenser and upstream from the separator.
  • a first outlet of the separator is operably coupled to the second inlet of the ejector and is configured to supply liquid refrigerant thereto.
  • the separator is arranged generally downstream from the evaporator and upstream from the compressor.
  • the ejector is positioned generally upstream from the expansion device.
  • outlet of the evaporator is operably coupled to the second inlet of the ejector.
  • the separator is arranged generally downstream of the ejector and generally upstream from the expansion device.
  • the chiller system includes a refrigerant to refrigerant heat exchanger fluidly coupled to the vapor compression circuit and the efficiency circuit.
  • the refrigerant to refrigerant heat exchanger is configured to convert the vapor refrigerant provided from an outlet of the separator into a superheated vapor.
  • FIG. 1 is a schematic diagram of a chiller refrigeration system according to an embodiment of the invention
  • FIG. 2 is a cross-sectional view of an evaporator of the chiller refrigeration system of FIG. 1 according to an embodiment of the invention
  • FIG. 3 is a schematic diagram of another chiller refrigeration system according to an embodiment of the invention.
  • FIG. 4 is a schematic diagram of another chiller refrigeration system according to an embodiment of the invention.
  • FIG. 5 is a schematic diagram of another chiller refrigeration system according to an embodiment of the invention.
  • a refrigerant R is configured to circulate through the chiller system 20 such that the refrigerant R absorbs heat when evaporated at a low temperature and pressure and releases heat when condensed at a higher temperature and pressure.
  • the refrigerant has a low global warming potential, such as a Hydrofluoroolefin (HFO) or an HFO blend refrigerant for example.
  • HFO Hydrofluoroolefin
  • the refrigerant R flows in a counterclockwise direction as indicated by the arrows.
  • the compressor 25 receives refrigerant vapor from the evaporator 40 and compresses it to a higher temperature and pressure, with the relatively hot vapor then passing to the condenser 30 where it is cooled and condensed to a liquid state by a heat exchange relationship with a cooling medium, such as air or water for example.
  • the liquid refrigerant R then passes from the condenser 30 to an expansion valve 35 , wherein the refrigerant R is expanded to a low temperature two phase liquid/vapor state as it passes to the evaporator 40 .
  • low pressure vapor then returns to the compressor 25 where the cycle is repeated.
  • the compressor 25 , condenser 30 , expansion device 35 and evaporator 40 form a vapor compression circuit.
  • the evaporator 40 is a direct expansion heat exchanger. As illustrated in FIG. 2 , the evaporator 40 includes a connected first shell 100 a and second shell 100 b, and a coupled first plurality of tubes 105 a and second plurality of tubes 105 b, arranged within each of the shells 100 a, 100 b, respectively. However, embodiments having any number of shells 100 a, 100 b are within the scope of the invention. In embodiments where the evaporator 40 includes multiple shells, such as shell 100 a and 100 b for example, the shells are fluidly coupled to one another and the tubes 105 a, 105 b within each respective shell 105 a, 105 are fluidly coupled.
  • a plurality of large baffles 107 and small baffles 109 generally receive and support the tubes 105 a, 105 b to maintain the position of the tubes 105 a, 105 b along the length of the shell 100 a, 100 b.
  • the large baffle 107 is configured to receive each of the plurality of tubes 105 a, 105 b within a shell 100 a, 100 b and the small baffle 109 is configured to receive only a portion, such as a central portion for example, of the plurality of tubes 105 a, 105 b within a shell 100 a, 100 b.
  • the refrigerant of the chiller system 20 is configured to pass from an inlet header 110 , through the one or more plurality of tubes 105 b, 105 a, and out an outlet header 115 .
  • a heating medium such as water for example, is pumped into the interior 120 of the shell 100 via an inlet 125 , through the one or more shells 100 a, 100 b, and out an outlet 130 .
  • the heating medium is configured to flow from the second shell 100 b to the first shell 100 a
  • the refrigerant is configured to flow from the first plurality of tubes 105 a to the second plurality of tubes 105 b.
  • the illustrated and described evaporator 40 has a counter flow configuration to maximize the heat transfer between the heating medium and the refrigerant.
  • the refrigerant provided at the outlet header 115 of the evaporator 40 may be a two-phase mixture including both liquid and vapor refrigerant. In one embodiment, 85 percent or less of the two-phase mixture is vaporized refrigerant.
  • the system 20 includes an additional heat exchanger 45 configured to receive a first flow of refrigerant and a second flow of refrigerant.
  • the heat exchanger 45 may be positioned within the system 20 such that the first flow of refrigerant is provided from the outlet of the condenser 30 .
  • the first flow of refrigerant is configured to pass through the heat exchanger 45 before being supplied to the expansion valve 35 .
  • the second flow of refrigerant within the heat exchanger 45 is generally provided from the outlet of the evaporator 40 .
  • the second flow of refrigerant is configured to pass through the heat exchanger 45 before being supplied to the compressor 25 .
  • the warm liquid refrigerant from the condenser 30 in a heat transfer relationship with the refrigerant vapor or two-phase mixture exiting the evaporator 40 , heat from the first flow of refrigerant transfers to the second flow of refrigerant.
  • the second flow of refrigerant supplied from the heat exchanger 45 to the compressor 25 is generally a superheated vapor.
  • a lubrication system may be integrated into the chiller system 20 .
  • an oil separator 55 is positioned directly downstream from the compressor 20 .
  • the oil separator 55 is integrally formed with an outlet of the compressor 25 .
  • the refrigerant separated by the oil separator 55 is provided to the condenser 30 , and the lubricant isolated by the oil separator 55 is recirculated to the moving portions (not shown) of the compressor 25 , such as to the rotating bearings for example, where the lubricant becomes entrained in the refrigerant R and the lubricant cycle is repeated.
  • the chiller system 20 additionally includes a circuit 58 configured to recirculate liquid refrigerant of the two-phase mixture provide at the outlet 115 of the evaporator 40 to improve the efficiency of the chiller system 20 .
  • the circuit 58 includes a flash gas refrigerant separator 60 configured to separate the liquid and vapor phases of the refrigerant.
  • the separator 60 is arranged generally downstream from the expansion device 35 and upstream from the evaporator 40 such that the two-phase refrigerant passes from the expansion device 35 into the separator 60 .
  • a pump 65 is configured to draw the liquid refrigerant from a first outlet 66 of the separator 60 and supply it to the evaporator 40 .
  • the outlet of the evaporator 40 is also connected to the separator 60 and configured to supply a two-phase refrigerant mixture thereto.
  • the liquid refrigerant is separated from the liquid and vapor mixture and recirculated through the evaporator 40 repeatedly until it is vaporized.
  • a second outlet 68 of the separator 60 is operably coupled to the compressor 25 such that the separated vaporized refrigerant is supplied directly thereto. In such instances, the vaporized refrigerant bypasses the evaporator 40 .
  • the chiller system 20 includes a refrigerant to refrigerant heat exchanger 45
  • the vaporized refrigerant from the separator 60 may pass through the heat exchanger 45 before being supplied to the compressor 25 .
  • the flash gas separator 60 is positioned generally downstream from the evaporator 40 and generally upstream from the compressor 25 relative to the flow of refrigerant.
  • the additional circuit 58 of the chiller system 20 also includes an ejector 70 arranged within the refrigerant flow path between the condenser 30 and the expansion valve 35 . Refrigerant from the condenser 30 is provided to a first inlet 72 of the ejector 70 . As the refrigerant flows through the ejector 70 , the flow is accelerated and the pressure of the flow is decreased, such that the refrigerant supplied to the expansion device 35 is generally a liquid-vapor mixture.
  • the refrigerant passes to the flash gas separator 60 for separation into a liquid refrigerant and a vapor refrigerant.
  • a first outlet 66 of the separator 60 is fluidly connected to a second inlet 74 of the ejector 70 .
  • the high velocity and pressure reduction of the refrigerant flow through the first inlet 72 of the ejector 70 draws the liquid refrigerant from the separator 60 into the ejector 70 through the second inlet 74 . Therefore any liquid refrigerant provided at the outlet 115 of the evaporator 40 will repeatedly cycle through the circuit 58 and the evaporator 40 until being vaporized.
  • a second outlet 68 of the separator 60 is configured to supply the vaporized refrigerant within the separator 60 to the compressor 25 .
  • the liquid refrigerant from the condenser 30 may pass through the heat exchanger 45 as the first flow of refrigerant before being supplied to the ejector 70 and the vaporized refrigerant provided at the second outlet 68 of the separator 60 may pass through the heat exchanger 45 as the second flow of refrigerant before being supplied to the compressor 25 .
  • the flash gas separator 60 is positioned generally downstream from the condenser 30 and generally upstream from the expansion device 35 relative to the flow of refrigerant.
  • the ejector 70 is arranged generally downstream from the condenser 30 and generally upstream from the separator 60 relative to the flow of refrigerant. Refrigerant from the condenser 30 is provided to the first inlet 72 of the ejector 70 and refrigerant from the outlet 115 of the evaporator 40 is provided to the second inlet 74 of the ejector 70 .
  • a liquid-vapor refrigerant mixture is supplied from the ejector 70 to the separator 60 where it is divided into liquid refrigerant and vapor refrigerant.
  • the liquid refrigerant within the separator 60 is provided to the expansion device 35 via a first outlet 66 in the separator 60 .
  • the refrigerant is provided to the second inlet 74 of the ejector 70 .
  • the high velocity and pressure reduction of the refrigerant flow through the ejector 70 draws the mixture of two phase refrigerant from the evaporator 40 through the second inlet 74 of the ejector 70 .
  • the refrigerant then returns to the separator 60 , where it is separated into liquid refrigerant and vapor refrigerant. Consequently, the liquid refrigerant provided at the outlet 115 of the evaporator 40 will continue to cycle through circuit 58 and the evaporator 40 until it is entirely vaporized.
  • the vapor compression cycle further benefits from this configuration in that the placement of the ejector 70 reduces the compression ratio of the compressor 25 , thereby increasing the system coefficient of performance.
  • a second outlet 68 of the separator 60 is configured to supply the vaporized refrigerant to the compressor 25 .
  • the vaporized refrigerant bypasses the expansion device 35 and the evaporator 40 .
  • the liquid refrigerant from the condenser 30 may pass through the heat exchanger 45 as the first flow of refrigerant before being supplied to the ejector 70 and the vaporized refrigerant provided at the second outlet 68 of the separator 60 may pass through the heat exchanger 45 as the second flow of refrigerant before being supplied to the compressor 25 .
  • the various embodiments of a chiller system 20 described herein have an efficiency or performance level at least equal to conventional systems that include a flooded evaporator.
  • the chiller system 20 is compatible with immiscible oil, which reduces the amount of oil needed by the system and therefore the cost.
  • the design of the lubrication system 50 may be simplified.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Lubricants (AREA)
US15/505,445 2014-08-21 2014-08-21 Improved dircet expansion evaporator based chiller system Abandoned US20170268808A1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/IB2014/001842 WO2016027116A1 (en) 2014-08-21 2014-08-21 Improved direct expansion evaporator based chiller system

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US20170268808A1 true US20170268808A1 (en) 2017-09-21

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US15/505,445 Abandoned US20170268808A1 (en) 2014-08-21 2014-08-21 Improved dircet expansion evaporator based chiller system

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US (1) US20170268808A1 (zh)
EP (1) EP3183514B1 (zh)
CN (1) CN106662365B (zh)
ES (1) ES2886603T3 (zh)
WO (1) WO2016027116A1 (zh)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160223239A1 (en) * 2015-01-31 2016-08-04 Trane International Inc. Indoor Liquid/Suction Heat Exchanger
US20170328616A1 (en) * 2016-05-12 2017-11-16 General Electric Company Air Conditioner Units with Improved Efficiency
US20190360433A1 (en) * 2016-05-03 2019-11-28 Carrier Corporation Integrated compressed gas transport refrigeration unit for compressed gas fueled vehicles
US10712051B2 (en) * 2017-09-04 2020-07-14 Bsh Hausgeraete Gmbh Refrigeration appliance with multiple temperature zones
CN111602011A (zh) * 2018-01-15 2020-08-28 大金工业株式会社 制冰系统
WO2024092271A1 (en) * 2022-10-28 2024-05-02 Evapco, Inc. Oil separator and return for ejector-based direct expansion (dx) evaporator

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DE102016123277A1 (de) * 2016-12-01 2018-06-07 Wurm Gmbh & Co. Kg Elektronische Systeme Kälteanlage und Verfahren zur Regelung einer Kälteanlage
WO2019023618A1 (en) 2017-07-28 2019-01-31 Carrier Corporation LUBRICATION SUPPLY SYSTEM
AT522615A1 (de) * 2019-05-29 2020-12-15 Ait Austrian Inst Tech Gmbh Verfahren zur Dampferzeugung
CN113028665A (zh) * 2019-12-24 2021-06-25 青岛海尔空调电子有限公司 冷水机组
WO2021174067A1 (en) * 2020-02-26 2021-09-02 Johnson Controls Technology Company Free cooling system for hvac system

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US6457325B1 (en) * 2000-10-31 2002-10-01 Modine Manufacturing Company Refrigeration system with phase separation
US6835484B2 (en) * 2002-07-09 2004-12-28 General Motors Corporation Supersonic vapor compression and heat rejection cycle
US6799435B2 (en) * 2002-09-12 2004-10-05 Denso Corporation Vapor compression refrigeration system
US20070095087A1 (en) * 2005-11-01 2007-05-03 Wilson Michael J Vapor compression cooling system for cooling electronics
US20080078192A1 (en) * 2006-10-02 2008-04-03 Kirill Ignatiev Injection system and method for refrigeration system compressor
US8516841B2 (en) * 2008-04-18 2013-08-27 Valeo Systems Thermiques Heating and air conditioning unit for an automotive vehicle
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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20160223239A1 (en) * 2015-01-31 2016-08-04 Trane International Inc. Indoor Liquid/Suction Heat Exchanger
US20190360433A1 (en) * 2016-05-03 2019-11-28 Carrier Corporation Integrated compressed gas transport refrigeration unit for compressed gas fueled vehicles
US20170328616A1 (en) * 2016-05-12 2017-11-16 General Electric Company Air Conditioner Units with Improved Efficiency
US10712051B2 (en) * 2017-09-04 2020-07-14 Bsh Hausgeraete Gmbh Refrigeration appliance with multiple temperature zones
CN111602011A (zh) * 2018-01-15 2020-08-28 大金工业株式会社 制冰系统
CN111602011B (zh) * 2018-01-15 2022-06-24 大金工业株式会社 制冰系统
WO2024092271A1 (en) * 2022-10-28 2024-05-02 Evapco, Inc. Oil separator and return for ejector-based direct expansion (dx) evaporator

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EP3183514A1 (en) 2017-06-28
WO2016027116A1 (en) 2016-02-25
EP3183514B1 (en) 2021-06-30
ES2886603T3 (es) 2021-12-20
CN106662365B (zh) 2021-04-27
CN106662365A (zh) 2017-05-10

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