EP3183514A1 - Improved direct expansion evaporator based chiller system - Google Patents

Improved direct expansion evaporator based chiller system

Info

Publication number
EP3183514A1
EP3183514A1 EP14809083.0A EP14809083A EP3183514A1 EP 3183514 A1 EP3183514 A1 EP 3183514A1 EP 14809083 A EP14809083 A EP 14809083A EP 3183514 A1 EP3183514 A1 EP 3183514A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
evaporator
chiller system
vapor
separator
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.)
Granted
Application number
EP14809083.0A
Other languages
German (de)
French (fr)
Other versions
EP3183514B1 (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
Original Assignee
Carrier Corp
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 Carrier Corp filed Critical Carrier Corp
Publication of EP3183514A1 publication Critical patent/EP3183514A1/en
Application granted granted Critical
Publication of EP3183514B1 publication Critical patent/EP3183514B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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. Although 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. [004] Various types of heat exchangers, 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 By immersing the tubes of a flooded heat exchanger within the "boiling" liquid refrigerant, only a very small approach temperature (.5°K - 1.5°K) between the refrigerant and the chilled secondary fluid is required, thereby improving heat transfer efficiency.
  • a direct expansion heat exchanger 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.
  • 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.
  • 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
  • HFO blend refrigerant for example.
  • 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 100a and second shell 100b, and a coupled first plurality of tubes 105a and second plurality of tubes 105b, arranged within each of the shells 100a, 100b, respectively. However, embodiments having any number of shells 100a, 100b are within the scope of the invention. In embodiments where the evaporator 40 includes multiple shells, such as shell 100a and 100b for example, the shells are fluidly coupled to one another and the tubes 105 a, 105b 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, 105b to maintain the position of the tubes 105a, 105b along the length of the shell 100a, 100b.
  • the large baffle 107 is configured to receive each of the plurality of tubes 105a, 105b within a shell 100a, 100b and the small baffle 109 is configured to receive only a portion, such as a central portion for example, of the plurality of tubes 105a, 105b within a shell 100a, 100b.
  • the refrigerant of the chiller system 20 is configured to pass from an inlet header
  • 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 100a, 100b, and out an outlet 130.
  • the heating medium is configured to flow from the second shell 100b to the first shell 100a
  • the refrigerant is configured to flow from the first plurality of tubes 105 a to the second plurality of tubes 105b.
  • 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. Because lubricant may become entrained in the refrigerant as it passes through the compressor 25, an oil separator 55 is positioned directly downstream from the compressor 20. In one embodiment, 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. [0037] In another embodiment, illustrated in FIG.
  • 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 chiller system 20 includes a refrigerant to refrigerant heat exchanger 45
  • 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.

Landscapes

  • 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)

Abstract

A chiller system is provided 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 vapor refrigerant provided at the outlet of the evaporator into a superheated vapor.

Description

IMPROVED DIRECT EXPANSION EVAPORATOR BASED CHILLER SYSTEM
BACKGROUND OF THE INVENTION
[001] 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.
[002] In a vapor compression system, 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). In the condenser, heat is exchanged between a secondary fluid, such as air or water, and the refrigerant. From the condenser, 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. In 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.
[003] 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. Although 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. [004] Various types of heat exchangers, such as direct expansion and flooded heat exchangers for example, may be used as evaporators in HVAC systems. In a flooded heat exchanger, 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. By immersing the tubes of a flooded heat exchanger within the "boiling" liquid refrigerant, only a very small approach temperature (.5°K - 1.5°K) between the refrigerant and the chilled secondary fluid is required, thereby improving heat transfer efficiency. In a direct expansion heat exchanger, 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.
[005] 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.
[006] Due to their higher miscibility, these new "wet refrigerants" tend to absorb significant amounts of oil making the viscosity requirements of the oil-refrigerant mixture difficult to achieve. Use of immiscible oil, which does not mix with these refrigerants will improve the viscosity of the oil; however, at the same time use of immiscible oil significantly and permanently reduces the performance of air conditioning and refrigeration systems that employ modern flooded type evaporators. Use of direct exchange evaporators instead of flooded evaporators may allow the use of immiscible oils in a refrigeration system. In such instances, the oil return is driven by the velocity of refrigerant through the heat exchanger tubes.
BRIEF DESCRIPTION OF THE INVENTION [007] According to an aspect of the invention, a chiller system is provided 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. [008] In addition to one or more of the features described above, or as an alternative, in further embodiments the refrigerant has a low global warming potential.
[009] In addition to one or more of the features described above, or as an alternative, in further embodiments, the refrigerant includes at least one of a Hydrofluoroolefin (HFO) and an HFO blend.
[0010] In addition to one or more of the features described above, or as an alternative, in further embodiments 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. [0011] In addition to one or more of the features described above, or as an alternative, in further embodiments the oil is an immiscible oil.
[0012] According to another embodiment of the invention, a chiller system is provided 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.
[0013] In addition to one or more of the features described above, or as an alternative, in further embodiments the refrigerant has a low global warming potential.
[0014] In addition to one or more of the features described above, or as an alternative, in further embodiments, the refrigerant includes at least one of a Hydrofluoroolefin (HFO) and an HFO blend. [0015] In addition to one or more of the features described above, or as an alternative, in further embodiments 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.
[0016] In addition to one or more of the features described above, or as an alternative, in further embodiments the oil is an immiscible oil.
[0017] In addition to one or more of the features described above, or as an alternative, in further embodiments the separator is operably coupled to the compressor and is configured to supply a refrigerant vapor thereto.
[0018] In addition to one or more of the features described above, or as an alternative, in further embodiments 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.
[0019] In addition to one or more of the features described above, or as an alternative, in further embodiments a first outlet of the separator is operably coupled to the second inlet of the ejector and is configured to supply liquid refrigerant thereto.
[0020] In addition to one or more of the features described above, or as an alternative, in further embodiments the separator is arranged generally downstream from the evaporator and upstream from the compressor.
[0021] In addition to one or more of the features described above, or as an alternative, in further embodiments the ejector is positioned generally upstream from the expansion device.
[0022] In addition to one or more of the features described above, or as an alternative, in further embodiments the outlet of the evaporator is operably coupled to the second inlet of the ejector.
[0023] In addition to one or more of the features described above, or as an alternative, in further embodiments the separator is arranged generally downstream of the ejector and generally upstream from the expansion device. [0024] In addition to one or more of the features described above, or as an alternative, in further embodiments 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.
[0025] These and other advantages and features will become more apparent from the following description taken in conjunction with the drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
[0026] The subject matter, which is regarded as the invention, is particularly pointed out and distinctly claimed in the claims at the conclusion of the specification. The foregoing and other features, and advantages of the invention are apparent from the following detailed description taken in conjunction with the accompanying drawings in which:
[0027] FIG. 1 is a schematic diagram of a chiller refrigeration system according to an embodiment of the invention; [0028] 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;
[0029] FIG. 3 is a schematic diagram of another chiller refrigeration system according to an embodiment of the invention;
[0030] FIG. 4 is a schematic diagram of another chiller refrigeration system according to an embodiment of the invention; and
[0031] FIG. 5 is a schematic diagram of another chiller refrigeration system according to an embodiment of the invention.
DETAILED DESCRIPTION OF THE INVENTION
[0032] Referring now to the FIGS., an improved chiller refrigeration system 20 configured for use with either a miscible or immiscible oil is illustrated. 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. In one embodiment, the refrigerant has a low global warming potential, such as a Hydrofluoroolefin (HFO) or an HFO blend refrigerant for example. Within this chiller system 20, 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. After the addition of heat in the evaporator 40, low pressure vapor then returns to the compressor 25 where the cycle is repeated. Together the compressor 25, condenser 30, expansion device 35 and evaporator 40 form a vapor compression circuit. [0033] In the illustrated embodiments of the chiller system 20, the evaporator 40 is a direct expansion heat exchanger. As illustrated in FIG. 2, the evaporator 40 includes a connected first shell 100a and second shell 100b, and a coupled first plurality of tubes 105a and second plurality of tubes 105b, arranged within each of the shells 100a, 100b, respectively. However, embodiments having any number of shells 100a, 100b are within the scope of the invention. In embodiments where the evaporator 40 includes multiple shells, such as shell 100a and 100b for example, the shells are fluidly coupled to one another and the tubes 105 a, 105b 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, 105b to maintain the position of the tubes 105a, 105b along the length of the shell 100a, 100b. In one embodiment, the large baffle 107 is configured to receive each of the plurality of tubes 105a, 105b within a shell 100a, 100b and the small baffle 109 is configured to receive only a portion, such as a central portion for example, of the plurality of tubes 105a, 105b within a shell 100a, 100b.
[0034] The refrigerant of the chiller system 20 is configured to pass from an inlet header
110, through the one or more plurality of tubes 105b, 105a, and out an outlet header 115.
Similarly, 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 100a, 100b, and out an outlet 130. In the illustrated, non-limiting embodiment, the heating medium is configured to flow from the second shell 100b to the first shell 100a, and the refrigerant is configured to flow from the first plurality of tubes 105 a to the second plurality of tubes 105b. 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.
[0035] Referring again to FIG. 1, 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. In the illustrated, non-limiting embodiment, 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. By arranging 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. As a result, the second flow of refrigerant supplied from the heat exchanger 45 to the compressor 25 is generally a superheated vapor.
[0036] A lubrication system, illustrated schematically at 50, may be integrated into the chiller system 20. Because lubricant may become entrained in the refrigerant as it passes through the compressor 25, an oil separator 55 is positioned directly downstream from the compressor 20. In one embodiment, 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. [0037] In another embodiment, illustrated in FIG. 3, 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. In the illustrated, non-limiting embodiment, 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. Within the separator 60, 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. In embodiments where 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.
[0038] Referring now to FIG. 4, in another embodiment of the chiller system 20, 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. In such embodiments, 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.
[0039] After the refrigerant passes through the evaporator 40, 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. In embodiments where the chiller system 20 includes a refrigerant to refrigerant heat exchanger 45, 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.
[0040] In another embodiment, illustrated in FIG. 5, 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. In such embodiments of the circuit 58, 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. After passing through the expansion device 35 and the evaporator 40, the refrigerant is provided to the second inlet 74 of the ejector 70. As previously described, 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.
[0041] A second outlet 68 of the separator 60 is configured to supply the vaporized refrigerant to the compressor 25. In such instances, the vaporized refrigerant bypasses the expansion device 35 and the evaporator 40. In embodiments where the chiller system 20 includes a refrigerant to refrigerant heat exchanger 45, 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.
[0042] 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. In addition, the chiller system 20 is compatible with immiscible oil, which reduces the amount of oil needed by the system and therefore the cost. As a result, the design of the lubrication system 50 may be simplified.
[0043] While the invention has been described in detail in connection with only a limited number of embodiments, it should be readily understood that the invention is not limited to such disclosed embodiments. Rather, the invention can be modified to incorporate any number of variations, alterations, substitutions or equivalent arrangements not heretofore described, but which are commensurate with the spirit and scope of the invention. Additionally, while various embodiments of the invention have been described, it is to be understood that aspects of the invention may include only some of the described embodiments. Accordingly, the invention is not to be seen as limited by the foregoing description, but is only limited by the scope of the appended claims.

Claims

CLAIMS:
1. A chiller system comprising: a vapor compression circuit including a compressor, a condenser, an expansion valve, and an evaporator fluidly coupled and having a refrigerant circulating there through, the evaporator being a direct exchange heat exchanger such that the refrigerant provided at an outlet of the evaporator is a two-phase mixture of liquid refrigerant and vapor refrigerant, and the vapor refrigerant comprises less than or equal to about 85% of the two-phase mixture; and a refrigerant to refrigerant heat exchanger fluidly coupled to the circuit, the refrigerant to refrigerant heat exchanger being configured to convert the vapor refrigerant provided at the outlet of the evaporator into a superheated vapor.
2. The chiller system according to claim 1, wherein the refrigerant has a low global warming potential.
3. The chiller system according to claim 2, wherein the refrigerant includes at least one of a Hydrofluoroolefin (HFO) or an HFO blend.
4. The chiller system according to claim 1, further comprising a lubrication system including an oil separator arranged generally downstream from the compressor, the oil separator being configured to supply oil separated from the refrigerant to one or more moving components of the compressor.
5. The chiller system according to claim 4, wherein the oil is an immiscible oil.
6. A chiller system comprising: a vapor compression circuit including a compressor, a condenser, an expansion valve, and an evaporator fluidly coupled and having a refrigerant circulating there through, the evaporator being a direct exchange heat exchanger such that the refrigerant provided at an outlet of the evaporator is a two-phase mixture of liquid refrigerant and vapor refrigerant, and the vapor refrigerant comprises less than or equal to about 85% of the two-phase mixture; and an efficiency circuit including a separator configured to separate the two-phase mixture into liquid refrigerant and vapor refrigerant, the efficiency circuit being operably coupled to the outlet of the evaporator and configured to recirculate liquid refrigerant from the separator through the evaporator to improve the efficiency of the chiller system.
7. The chiller system according to claim 6, wherein the refrigerant has a low global warming potential.
8. The chiller system according to claim 7, wherein the refrigerant includes an HFO.
9. The chiller system according to claim 6, further comprising a lubrication system including an oil separator arranged generally downstream from the compressor, the oil separator being configured to supply oil separated from the refrigerant to one or more moving components of the compressor.
10. The chiller system according to claim 9, wherein the oil is immiscible oil.
11. The chiller system according to claim 6, wherein the separator is operably coupled to the compressor and is configured to supply vapor refrigerant thereto.
12. The chiller system according to claim 11, wherein the efficiency circuit further includes an ejector having a first inlet and a second inlet, the ejector being positioned generally downstream from the condenser and upstream from the separator.
13. The chiller system according to claim 12, wherein a first outlet of the separator is operably coupled to the second inlet of the ejector and is configured to supply liquid refrigerant thereto.
14. The chiller system according to claim 13, wherein the separator is arranged generally downstream from the evaporator and upstream from the compressor.
15. The chiller system according to claim 14, wherein the ejector is positioned generally upstream from the expansion device.
16. The chiller system according to claim 12, wherein the outlet of the evaporator is operably coupled to the second inlet of the ejector.
17. The chiller system according to claim 16, wherein the separator is arranged generally downstream of the ejector and generally upstream from the expansion device.
18. The chiller system according to claim 6, further comprising: a refrigerant to refrigerant heat exchanger fluidly coupled to the vapor compression circuit and the efficiency circuit, the refrigerant to refrigerant heat exchanger being configured to convert the vapor refrigerant provided from an outlet of the separator into a superheated vapor.
EP14809083.0A 2014-08-21 2014-08-21 Chiller system Active EP3183514B1 (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

Publications (2)

Publication Number Publication Date
EP3183514A1 true EP3183514A1 (en) 2017-06-28
EP3183514B1 EP3183514B1 (en) 2021-06-30

Family

ID=52014149

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14809083.0A Active EP3183514B1 (en) 2014-08-21 2014-08-21 Chiller system

Country Status (5)

Country Link
US (1) US20170268808A1 (en)
EP (1) EP3183514B1 (en)
CN (1) CN106662365B (en)
ES (1) ES2886603T3 (en)
WO (1) WO2016027116A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11306950B2 (en) 2017-07-28 2022-04-19 Carrier Corporation Lubrication supply system

Families Citing this family (10)

* 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
WO2017192570A1 (en) * 2016-05-03 2017-11-09 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
DE102016123277A1 (en) * 2016-12-01 2018-06-07 Wurm Gmbh & Co. Kg Elektronische Systeme Refrigeration system and method for controlling a refrigeration system
DE102017215488A1 (en) * 2017-09-04 2019-03-07 BSH Hausgeräte GmbH Refrigerating appliance with several temperature zones
JP6540872B1 (en) * 2018-01-15 2019-07-10 ダイキン工業株式会社 Ice making system
AT522615A1 (en) * 2019-05-29 2020-12-15 Ait Austrian Inst Tech Gmbh Process for generating steam
CN113028665A (en) * 2019-12-24 2021-06-25 青岛海尔空调电子有限公司 Water chilling unit
EP4111110A4 (en) * 2020-02-26 2024-03-06 Johnson Controls Tyco IP Holdings LLP Free cooling system for hvac system
WO2024092271A1 (en) * 2022-10-28 2024-05-02 Evapco, Inc. Oil separator and return for ejector-based direct expansion (dx) evaporator

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20040052656A1 (en) * 2002-09-12 2004-03-18 Mika Saito Vapor compression refrigeration system
WO2006128457A1 (en) * 2005-05-30 2006-12-07 Johnson Controls Denmark Aps Oil separation in a cooling circuit

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3751936A (en) * 1972-01-18 1973-08-14 J Simard Oil separator apparatus and method for low miscibility refrigerant systems
EP0626443B1 (en) * 1992-11-27 1999-01-27 Japan Energy Corporation Ammonia refrigerating unit, working fluid composition to be used in said unit, and lubrication of ammonia compressor
US6457325B1 (en) * 2000-10-31 2002-10-01 Modine Manufacturing Company Refrigeration system with phase separation
JP3903851B2 (en) * 2002-06-11 2007-04-11 株式会社デンソー Heat exchanger
US6835484B2 (en) * 2002-07-09 2004-12-28 General Motors Corporation Supersonic vapor compression and heat rejection cycle
DE10344590A1 (en) * 2003-09-25 2005-04-28 Bosch Gmbh Robert Air conditioning and method of operating an air conditioner
DE102006029973B4 (en) * 2005-06-30 2016-07-28 Denso Corporation ejector cycle
US20070095087A1 (en) * 2005-11-01 2007-05-03 Wilson Michael J Vapor compression cooling system for cooling electronics
US7647790B2 (en) * 2006-10-02 2010-01-19 Emerson Climate Technologies, Inc. Injection system and method for refrigeration system compressor
WO2009049096A1 (en) * 2007-10-09 2009-04-16 Advanced Thermal Sciences Corp. Thermal control system and method
ATE552993T1 (en) * 2008-04-18 2012-04-15 Valeo Systemes Thermiques IMPROVED HEATING AND AIR COOLING UNIT FOR AN AUTOMOBILE
US8980119B2 (en) * 2010-11-30 2015-03-17 Daikin Industries, Ltd. HFO refrigerant composition having improved slidability
US8522564B2 (en) * 2011-06-07 2013-09-03 Thermo King Corporation Temperature control system with refrigerant recovery arrangement

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20040052656A1 (en) * 2002-09-12 2004-03-18 Mika Saito Vapor compression refrigeration system
WO2006128457A1 (en) * 2005-05-30 2006-12-07 Johnson Controls Denmark Aps Oil separation in a cooling circuit

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2016027116A1 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11306950B2 (en) 2017-07-28 2022-04-19 Carrier Corporation Lubrication supply system

Also Published As

Publication number Publication date
CN106662365B (en) 2021-04-27
CN106662365A (en) 2017-05-10
EP3183514B1 (en) 2021-06-30
US20170268808A1 (en) 2017-09-21
WO2016027116A1 (en) 2016-02-25
ES2886603T3 (en) 2021-12-20

Similar Documents

Publication Publication Date Title
US20170268808A1 (en) Improved dircet expansion evaporator based chiller system
US10101060B2 (en) Cooling system
EP2543941B1 (en) Chiller
CN104508400B (en) Use the electronic cooling of shell and tube evaporator lubricant backflow
CN106321499B (en) Turbine and refrigeration cycle device
EP3204702B1 (en) Internal liquid suction heat exchanger
CN108369043B (en) Heat exchanger with water tank
EP3343129B1 (en) Refrigeration cycle apparatus
US9638445B2 (en) Oil return management in a HVAC system
EP2984419B1 (en) Combined vapor absorption and mechanical compression cycle design
CN105698424A (en) Ultralow-temperature refrigeration type single-cooling split air conditioner and ultralow-temperature refrigeration method thereof
AU2017439363B2 (en) Subcritical CO2 refrigeration system using thermal storage
WO2017179631A1 (en) Condenser, and turbo-refrigerating apparatus equipped with same
US20240183360A1 (en) Compressor lubrication supply system and compressor thereof
CN205481964U (en) Take gas -liquid separation's regenerator structure and use refrigeration air conditioner system of this regenerator
KR101891795B1 (en) Apparatus for separating oil of a refrigerant-oil mixture in a refrigerant circuit and arrangement with the apparatus and a heat exchanger for cooling the oil
US20170234586A1 (en) Oil return management in a hvac system
US20180274820A1 (en) Refrigeration cycle apparatus
CN105674633B (en) Regenerator with gas-liquid separating function and the refrigerated air-conditioning system using the regenerator
CN113994150A (en) Chiller system with multiple compressors
CN114174733A (en) Series flow refrigerator system
JP2007198670A (en) Refrigerating system and air conditioner for vehicle
NO344191B1 (en) Apparatus and method for transferring heat
KR20060069699A (en) Air conditioner having function for recovering oil

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20170317

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20200727

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20210112

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1406695

Country of ref document: AT

Kind code of ref document: T

Effective date: 20210715

Ref country code: DE

Ref legal event code: R096

Ref document number: 602014078462

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: NL

Ref legal event code: FP

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG9D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210630

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210630

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210930

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1406695

Country of ref document: AT

Kind code of ref document: T

Effective date: 20210630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210930

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210630

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210630

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20211001

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 20210818

Year of fee payment: 8

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2886603

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20211220

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210630

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210630

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210630

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210630

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20211102

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210630

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210630

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20210819

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210630

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602014078462

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210630

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20210930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210821

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210630

26N No opposition filed

Effective date: 20220331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210821

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210930

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20220721

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20220720

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 20220720

Year of fee payment: 9

REG Reference to a national code

Ref country code: SE

Ref legal event code: EUG

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220822

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210630

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220831

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20140821

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210630

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20230901

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20230720

Year of fee payment: 10

Ref country code: DE

Payment date: 20230720

Year of fee payment: 10

REG Reference to a national code

Ref country code: NL

Ref legal event code: MM

Effective date: 20230901

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210630

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20230831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230901

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230901