WO2011049778A1 - Commande de paramètre dans un système de réfrigération de transport et procédés associés - Google Patents

Commande de paramètre dans un système de réfrigération de transport et procédés associés Download PDF

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Publication number
WO2011049778A1
WO2011049778A1 PCT/US2010/052267 US2010052267W WO2011049778A1 WO 2011049778 A1 WO2011049778 A1 WO 2011049778A1 US 2010052267 W US2010052267 W US 2010052267W WO 2011049778 A1 WO2011049778 A1 WO 2011049778A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
vapor compression
compression system
temperature
Prior art date
Application number
PCT/US2010/052267
Other languages
English (en)
Inventor
Lucy Yi Liu
Suresh Duraisamy
Gilbert B. Hofsdal
Hans-Joachim Huff
Original Assignee
Carrier Corporation
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 Corporation filed Critical Carrier Corporation
Priority to US13/498,680 priority Critical patent/US20120227427A1/en
Priority to CN201080047706.3A priority patent/CN102575887B/zh
Priority to DK10771264.8T priority patent/DK2491318T3/en
Priority to EP10771264.8A priority patent/EP2491318B1/fr
Publication of WO2011049778A1 publication Critical patent/WO2011049778A1/fr
Priority to HK12113599.4A priority patent/HK1172943A1/zh

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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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/005—Arrangement or mounting of control or safety devices of safety devices
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical 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
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/026—Compressor control by controlling unloaders
    • F25B2600/0261—Compressor control by controlling unloaders external to the compressor
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser valves
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2102—Temperatures at the outlet of the gas cooler
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21172—Temperatures of an evaporator of the fluid cooled by the evaporator at the inlet
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21173—Temperatures of an evaporator of the fluid cooled by the evaporator at the outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • F25B31/008—Cooling of compressor or motor by injecting a liquid
    • 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
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • This invention relates generally to transport refrigeration systems and methods for same and, more particularly, to methods and apparatus for controlling vapor compression systems.
  • a particular difficulty of transporting perishable items is that such items must be maintained within a temperature range to reduce or prevent, depending on the items, spoilage or conversely damage from freezing.
  • a transport refrigeration unit is used to maintain proper temperatures within a transport cargo space.
  • the transport refrigeration unit can be under the direction of a controller.
  • the controller ensures that the transport refrigeration unit maintains a certain environment (e.g. thermal environment) within the transport cargo space.
  • the controller can operate a transport refrigeration system and/or components thereof responsive to sensors disposed in the system.
  • a vapor compression system can include a compressor, a heat rejection heat exchanger (e.g., condenser or gas cooler), an expansion device, and an evaporator.
  • a heat rejection heat exchanger e.g., condenser or gas cooler
  • Economizer cycles are sometimes employed to increase the efficiency and/or capacity of the system.
  • Economizer cycles operate by expanding the refrigerant leaving the heat rejecting heat exchanger to an intermediate pressure and separating the refrigerant flow into two streams. One stream is sent to the heat absorbing heat exchanger, and the other is sent to cool the flow between two compression stages.
  • a flash tank is used to perform the separation.
  • a refrigerant discharged from the gas cooler passes through a first expansion device, and its pressure is reduced. Refrigerant collects in the flash tank as part liquid and part vapor.
  • the vapor refrigerant is used to cool refrigerant exhaust as it exits a first compression device, and the liquid refrigerant is further expanded by a second expansion device before entering the evaporator.
  • a flash tank economizer is particularly useful when operating in transcritical conditions, such as are required when carbon dioxide is used as the working fluid.
  • the refrigeration system can operate in both the subcritical and transcritical modes.
  • the subcritical mode is similar to the operation of systems with conventional refrigerants.
  • the transcritical mode the refrigerant pressure in the heat rejection heat exchanger, and possibly in the flash tank, is above the critical pressure, while the evaporator operates as in the subcritical mode.
  • One embodiment according to the application can include a control module for a transport refrigeration system.
  • the control module includes a controller for controlling the transport refrigeration system to selectively verify operations of components thereof.
  • operations of components of a transport refrigeration system can be directly measured (e.g., sensors) and/or indirectly verified (e.g., without sensors).
  • an economizer includes a control for controlling operations of the economizer responsive to pressure in a compressor.
  • a refrigerant vapor compression system that can include a refrigerant compression device to include a first compression stage and a second compression stage, a refrigerant heat rejection heat exchanger downstream of the compression device, a refrigerant heat absorption heat exchanger downstream of the refrigerant heat rejection heat exchanger, a first expansion device disposed downstream of the refrigerant heat rejection heat exchanger and upstream of the refrigerant heat absorption heat exchanger, a sensor coupled to an output of the heat rejection heat exchanger, the sensor to measure a refrigerant temperature, and a controller to control operation of the refrigeration vapor compression system, the controller operative to indirectly verify the measured refrigerant temperature.
  • a computer program product comprising a computer usable storage medium to store a computer readable program that, when executed on a computer, causes the computer to perform operations to operate a transport refrigeration unit, the operations that can include operating the transport refrigeration unit in a mode where a refrigerant is circulating within a refrigerant circuit, sensing a characteristic used to determine a system capacity of the transport refrigeration unit during operation, indirectly determining the characteristic used to determine the system capacity, comparing the sensed value of the characteristic used to determine the system capacity against the indirectly determined value, and determining an error condition of a corresponding sensor when a result of the comparison does not match.
  • a method for determining a characteristic of a refrigerant vapor compression system having a refrigerant circuit including a refrigerant compression device, a refrigerant heat rejection heat exchanger downstream of the compression device, a refrigerant heat absorption heat exchanger downstream of the refrigerant heat rejection heat exchanger, a sensor to sense a characteristic used to determine a system capacity of the refrigerant vapor compression system and interconnecting refrigerant lines as active components, the method that can include operating the refrigerant vapor compression system in a mode where the refrigerant is circulating within the active components of the refrigerant circuit, indirectly determining the characteristic used to determine the system capacity, comparing the sensed value of the characteristic used to determine the system capacity against the indirectly determined value of the characteristic, and determining an error condition of a corresponding sensor when a result of the comparison does not match.
  • FIG. 1 is a diagram that shows an embodiment of a transport refrigeration system according to the application
  • FIG. 2 is a diagram that shows another embodiment of a transport refrigeration system according to the application;
  • FIG. 3 is a schematic illustration of an embodiment of a vapor compression system according to the application;
  • FIG. 4 is a diagram graphically showing exemplary refrigerant temperature exiting a heat rejection heat exchanger as a function of system capacity
  • FIG. 5 is a diagram graphically showing exemplary compressor mid-stage pressure as a function of compressor discharge pressure for various compressor suction pressures according to embodiments of the application.
  • FIG. 6 is a flow diagram showing an embodiment of a method for operating a transport refrigeration system according to the application.
  • FIG. 1 is a diagram that shows an embodiment of a transport refrigeration system.
  • transport refrigeration system 100 can include a transport refrigeration unit 10 coupled to an enclosed space within a container 12.
  • the transport refrigeration system 100 may be of the type commonly employed on refrigerated trailers.
  • the transport refrigeration unit 10 is configured to maintain a prescribed thermal environment within the container 12 (e.g., cargo in an enclosed volume).
  • the transport refrigeration unit 10 is connected at one end of the container 12.
  • the transport refrigeration unit 10 can be coupled to a prescribed position on a side or more than one side of the container 12.
  • a plurality of transport refrigeration units can be coupled to a single container 12.
  • a single transport refrigeration unit 10 can be coupled to a plurality of containers 12 or multiple enclosed spaces within a single container.
  • the transport refrigeration unit 10 can operate to induct air at a first temperature and to exhaust air at a second temperature. In one embodiment, the exhaust air from the transport refrigeration unit 10 will be warmer than the inducted air such that the transport refrigeration unit 10 is employed to warm the air in the container 12.
  • the exhaust air from the transport refrigeration unit 10 will be cooler than the inducted air such that the transport refrigeration unit 10 is employed to cool the air in the container 12.
  • the transport refrigeration unit 10 can induct air from the container 12 having a return temperature Tr (e.g., first temperature) and exhaust air to the container 12 having a supply temperature Ts (e.g., second temperature).
  • the transport refrigeration unit 10 can include one or more temperature sensors to continuously or repeatedly monitor the return temperature Tr and/or the supply temperature Ts. As shown in FIG. 1, a first temperature sensor 24 of the transport refrigeration unit 10 can provide the supply temperature Ts and a second temperature sensor 22 of the transport refrigeration unit 10 can provide the return temperature Tr to the transport refrigeration unit 10, respectively. Alternatively, the supply temperature Ts and the return temperature Tr can be determined using remote sensors.
  • a transport refrigeration system 100 can provide air with controlled temperature, humidity or/and species concentration into an enclosed chamber where cargo is stored such as in container 12.
  • the transport refrigeration system 100 e.g., controller 250
  • the transport refrigeration system 100 is capable of controlling a plurality of the environmental parameters or all the environmental parameters within corresponding ranges with a great deal of variety of cargos and under all types of ambient conditions.
  • FIG. 2 is a diagram that shows an embodiment of a transport refrigeration system.
  • a transport refrigeration system 200 can include a transport refrigeration unit 210 coupled to a container 212, which can be used with a trailer, an intermodal container, a train railcar, a ship or the like, used for the transportation or storage of goods requiring a temperature controlled environment, such as, for example foodstuffs and medicines (e.g., perishable or frozen).
  • the container 212 can include an enclosed volume 214 for the transport/storage of such goods.
  • the enclosed volume 214 may be an enclosed space having an interior atmosphere isolated from the outside (e.g., ambient atmosphere or conditions) of the container 212.
  • the transport refrigeration unit 210 is located so as to maintain the temperature of the enclosed volume 214 of the container 212 within a predefined temperature range.
  • the transport refrigeration unit 210 can include a compressor 218, a condenser heat exchanger unit 222, a condenser fan 224, an evaporation heat exchanger unit 226, an evaporation fan 228, and a controller 250.
  • the condenser 222 can be implemented as a gas cooler.
  • the compressor 218 can be powered by single phase electric power, three phase electrical power, and/or a diesel engine and can, for example, operate at a constant speed.
  • the compressor 218 may be a scroll compressor, a rotary compressor, a reciprocal compressor, or the like.
  • the transport refrigeration system 200 requires electrical power from, and can be connected to a power supply unit (not shown) such as a standard commercial power service, an external power generation system (e.g., shipboard), a generator (e.g., diesel generator), or the like.
  • the condenser heat exchanger unit 222 can be operatively coupled to a discharge port of the compressor 218.
  • the evaporator heat exchanger unit 226 can be operatively coupled to an input port of the compressor 218.
  • An expansion valve 230 can be connected between an output of the condenser heat exchanger unit 222 and an input of the evaporator heat exchanger unit 226.
  • the condenser fan 224 can be positioned to direct an air stream onto the condenser heat exchanger unit 222.
  • the air stream from the condenser fan 224 can allow heat to be removed from the coolant circulating within the condenser heat exchanger unit 222.
  • the evaporator fan 228 can be positioned to direct an air stream onto the evaporation heat exchanger unit 226.
  • the evaporator fan 228 can be located and ducted so as to circulate the air contained within the enclosed volume 214 of the container 212.
  • the evaporator fan 230 can direct the stream of air across the surface of the evaporator heat exchanger unit 226. Heat can thereby be removed from the air, and the reduced temperature air can be circulated within the enclosed volume 214 of the container 212 to lower the temperature of the enclosed volume 214.
  • the controller 250 such as, for example, a MicroLink.TM 2i or Advanced controller, can be electrically connected to the compressor 218, the condenser fan 224, and/or the evaporator fan 228.
  • the controller 250 can be configured to operate the transport refrigeration unit 210 to maintain a predetermined environment (e.g., thermal environment) within the enclosed volume 214 of the container 212.
  • the controller 250 can maintain the predetermined environment by selectively controlling operations of the condenser fan 224, and/or the evaporator fan 228 to operate at a low speed or a high speed.
  • the controller 250 can increase electrical power to the compressor 218, the condenser fan 224, and the evaporator fan 228.
  • an economy mode of operation of the transport refrigeration unit 210 can be controlled by the controller 250.
  • variable speeds of components of the transport refrigeration unit 210 can be adjusted by the controller 250.
  • a full cooling mode for components of the transport refrigeration unit 210 can be controlled by the controller 250.
  • the electronic controller 250 can adjust a flow of coolant supplied to the compressor 218.
  • FIG. 3 is a diagram that shows an embodiment of a vapor compression system according to the application.
  • a low critical point refrigerant such as for example, but not limited to, carbon dioxide and refrigerant mixtures containing carbon dioxide.
  • the refrigerant vapor compression system 300 may also be operated in a subcritical cycle with a higher critical point refrigerant such as conventional hydrochlorofluorocarbon and hydrofluorocarbon refrigerants.
  • the refrigerant vapor compression system 300 is particularly suitable for use in a transport refrigeration system for refrigerating the air or other gaseous atmosphere within the temperature controlled enclosed volume 214 such as a cargo space of a truck, trailer, container, or the like for transporting perishable/frozen goods.
  • the refrigerant vapor compression system 300 is also suitable for use in conditioning air to be supplied to a climate controlled comfort zone within a residence, office building, hospital, school, restaurant or other facility.
  • the refrigerant vapor compression system could also be employed in refrigerating air supplied to display cases, merchandisers, freezer cabinets, cold rooms or other perishable/frozen product storage areas in commercial establishments.
  • the refrigerant vapor compression system 300 includes a multi-stage compression device 320, a refrigerant heat rejection heat exchanger 330, a refrigerant heat absorption heat exchanger 350, also referred to herein as an evaporator, and a primary expansion valve 355, such as for example an electronic expansion valve as depicted in FIG. 3, operatively associated with the evaporators 350, with refrigerant lines 302, 304, and 306 connecting the aforementioned components in a primary refrigerant circuit. As depicted in FIG.
  • the refrigerant vapor compression system 300 may also include an unload bypass line 316 that establishes refrigerant flow communication between an intermediate pressure stage of the multi-stage compression device 320 and the suction pressure portion of the refrigerant circuit, which constitutes refrigerant line 306 extending from the outlet of the evaporator 350 to the inlet of the compression device 320.
  • the refrigerant vapor compression system 300 can include an economizer circuit having an economizer device 340, a secondary expansion valve 345 and a refrigerant vapor injection line 314.
  • the economizer circuit includes a flash tank economizer 340 interdisposed in refrigerant line 304 of the primary refrigerant circuit downstream with respect to refrigerant flow of the refrigerant heat rejection heat exchanger 330 and upstream with respect to refrigerant flow of the refrigerant heat absorption heat exchanger 350.
  • the secondary expansion device 345 is interdisposed in refrigerant line 304 in operative association with and upstream of the economizer.
  • the secondary expansion device 345 may be an expansion valve, such as a high pressure electronic expansion valve as depicted in FIG. 3. Refrigerant traversing the secondary expansion device 345 is expanded to a lower pressure sufficient to establish a mixture of refrigerant in a vapor state and refrigerant in a liquid state.
  • the flash tank economizer 340 includes a separation chamber 342 wherein refrigerant in the liquid state collects in a lower portion of the separation chamber 342 and refrigerant in the vapor state collects in the portion of the separation chamber 342 above the liquid refrigerant.
  • the refrigerant vapor injection line 314 establishes refrigerant flow
  • a vapor injection flow control device 343 is interdisposed in vapor injection line 314.
  • the vapor injection flow control device 343 may comprise a flow control valve selectively positionable between an open position where refrigerant vapor flow may pass through the refrigerant vapor injection line 314 and a closed position where refrigerant vapor flow through the refrigerant vapor injection line 314 is reduced or blocked.
  • the vapor injection flow control valve 343 comprises a two-position solenoid valve of the type selectively positionable between a first open position and a second closed position.
  • the refrigeration vapor compression system 300 can also include an optional variable flow device (VFD) or a suction modulation valve (SMV) 323 interdisposed in refrigerant line 306 at a location between the outlet of the refrigeration heat absorption heat exchanger 350 and an inlet to the compression device 320.
  • VFD variable flow device
  • SMV suction modulation valve
  • the suction modulation valve 323 is positioned in refrigerant line 306 between the outlet of the evaporator 350 and the point at which the compressor unload bypass line 316 intersects refrigerant line 306.
  • the suction modulation valve 323 may comprise a pulse width modulated solenoid valve.
  • the refrigerant heat rejection heat exchanger 330 constitutes a gas (refrigerant vapor) cooler through which supercritical refrigerant passes in heat exchange relationship with a cooling medium, such as for example, but not limited to ambient gas or liquid (e.g., air or water), and may be also referred to herein as a gas cooler.
  • a cooling medium such as for example, but not limited to ambient gas or liquid (e.g., air or water)
  • the refrigerant heat rejection heat exchanger 330 can constitute a refrigerant condensing heat exchanger through which hot, high pressure refrigerant vapor passes in heat exchange relationship with the cooling medium and is condensed to a liquid. As shown in FIG.
  • the refrigerant heat rejection heat exchanger 330 includes a finned tube heat exchanger 332, such as for example a fin and round tube heat exchange coil or a fin and mini-channel flat tube heat exchanger, through which the refrigerant passes in heat exchange relationship with ambient air being drawn through the finned tube heat exchanger 332 by the fan(s) 334 associated with an exemplary gas cooler 330.
  • a finned tube heat exchanger 332 such as for example a fin and round tube heat exchange coil or a fin and mini-channel flat tube heat exchanger, through which the refrigerant passes in heat exchange relationship with ambient air being drawn through the finned tube heat exchanger 332 by the fan(s) 334 associated with an exemplary gas cooler 330.
  • the refrigerant heat absorption heat exchanger 350 serves an evaporator wherein refrigerant liquid or a mixture of refrigerant liquid and vapor is passed in heat exchange relationship with a fluid to be cooled, most commonly air, drawn from and to be returned to a temperature controlled environment, such as a cargo box of a refrigerated transport truck, trailer or container, or a display case, merchandiser, freezer cabinet, cold room or other perishable/frozen product storage area in a commercial establishment, or to a climate controlled comfort zone within a residence, office building, hospital, school, restaurant or other facility. As shown in FIG.
  • the refrigerant heat absorption heat exchanger 350 comprises a finned tube heat exchanger 352 through which refrigerant passes in heat exchange relationship with air drawn from and returned to the refrigerated container 212 by the evaporator fan(s) 354 associated with the evaporator 350.
  • the finned tube heat exchanger 352 may comprise, for example, a fin and round tube heat exchange coil or a fin and mini-channel flat tube heat exchanger.
  • the compression device 320 functions to compress the refrigerant and to circulate refrigerant through the primary refrigerant circuit as described in detail herein.
  • the compression device 320 may comprise a single multiple stage refrigerant compressor, such as for example a screw compressor or a reciprocating compressor disposed in the primary refrigerant circuit and having a first compression stage 320a and a second compression stage 320b.
  • the first and second compression stages are disposed in series refrigerant flow relationship with the refrigerant leaving the first compression stage 320a passing directly to the second compression stage 320b for further compression.
  • the compression device 320 may comprise a pair of independent compressors 320a and 320b, connected in series refrigerant flow relationship in the primary refrigerant circuit via a refrigerant line connecting the discharge outlet port of the first compressor 320a in refrigerant flow communication with an inlet port (e.g. the suction inlet port) of the second compressor 320b.
  • the compressors 320a and 320b may be scroll compressors, screw compressors, reciprocating compressors, rotary compressors or any other type of compressor or a combination of any such compressors. In the embodiment depicted in FIG.
  • the refrigerant vapor compression system 300 includes a refrigerant bypass line 316 providing a refrigerant flow passage from an intermediate pressure stage of the compression device 320 back to the suction side of the compression device 320.
  • An unload valve 327 is interdisposed in the bypass line 316. The unload valve 327 may be selectively positioned in an open position in which refrigerant flow passes through the bypass line 316 and a closed position in which refrigerant flow through the bypass line 316 is reduced or blocked.
  • the refrigerant vapor compression system 300 further includes a refrigerant liquid injection line 318.
  • the refrigerant liquid injection line 318 can tap into refrigerant line 304 at location downstream of the flash tank economizer 340 and upstream of the primary expansion valve 355 and open into an intermediate stage of the compression process.
  • the refrigerant liquid injection line 318 can establish refrigerant flow communication between a lower portion of the separation chamber 342 of the flash tank economizer 340 and an intermediate pressure stage of the compression device 320.
  • the refrigerant liquid injection line 318 can establish refrigerant flow communication between a lower portion of the separation chamber 342 of the flash tank economizer 340 and a compressor suction line (e.g., an inlet to the compression device).
  • a liquid injection flow control device 353 can be interdisposed in refrigerant liquid injection line 318.
  • the liquid injection flow control device 353 may comprise a flow control valve selectively positionable between an open position wherein refrigerant liquid flow may pass through the liquid injection line 318 and a closed position wherein refrigerant liquid flow through the refrigerant liquid injection line 318 is reduced or blocked.
  • the liquid injection flow control device 353 comprises a two-position solenoid valve of the type selectively positionable between a first open position and a second closed position.
  • injection of refrigerant vapor or refrigeration liquid into the intermediate pressure stage of the compression process would be accomplished by injection of the refrigerant vapor or refrigerant liquid into the refrigerant passing from the first compression stage 320a into the second compression stage 320b of the compression device 320.
  • Liquid refrigerant collecting in the lower portion of the flash tank economizer 340 can pass therefrom through refrigerant line 304 and traverse the primary refrigerant circuit expansion valve 355 interdisposed in refrigerant line 304 upstream with respect to refrigerant flow of the evaporator 350.
  • the evaporator 350 constitutes a refrigerant evaporating heat exchanger through which expanded refrigerant passes in heat exchange relationship with the air to be cooled, whereby the refrigerant is vaporized and typically superheated.
  • the primary expansion valve 355 meters the refrigerant flow through the refrigerant line 304 to maintain a desired level of superheat in the refrigerant vapor leaving the evaporator 350 to ensure that no liquid is present in the refrigerant leaving the evaporator.
  • the low pressure refrigerant vapor leaving the evaporator 350 returns through refrigerant line 306 to the input port of the first compression stage or first compressor 320a of the compression device 320 in the embodiment depicted in FIG. 3.
  • the refrigerant vapor compression system 300 also includes a control system operatively associated therewith for controlling operation of the refrigerant vapor
  • the control system can include a controller 390 that can determine the desired mode of operation in which to operate the refrigerant vapor compression system 300 based upon consideration of refrigeration load requirements, ambient conditions and various sensed system operating parameters. As shown in FIG. 3, the controller 390 also includes various sensors operatively associated with the controller 390 and disposed at selected locations throughout the system for monitoring various operating parameters by use of various sensors operatively associated with the controller.
  • the control system may include, by way of example but not limitation, a pressure sensor 392 disposed in operative association with the flash tank economizer 340 to sense the pressure within the separation chamber 342, a temperature sensor 393 and a pressure sensor 394 for sensing the refrigerant inlet or suction temperature and pressure, respectively, and a temperature sensor 395 and a pressure sensor 396 for sensing refrigerant discharge temperature and pressure, respectively.
  • the refrigeration vapor compression system may also include a temperature sensor 397a for sensing the temperature of the air returning to the evaporator from the container 212 and a temperature sensor 397b for sensing a temperature of the air being supplied to the container 212.
  • Sensors may also be provided for monitoring ambient outdoor conditions, such as or example ambient outdoor air temperature and humidity.
  • the pressure sensors 392, 394, 396 may be conventional pressure sensors, such as for example, pressure transducers, and the temperature sensors 393, 395 may be conventional temperature sensors, such as for example, thermocouples or thermistors.
  • the controller 390 processes the data received from the various sensors and controls operation of the compression device 320, operation of the fan(s) 334 associated with the refrigerant heat rejection heat exchanger 330, operation of the fan(s) 354 associated with the evaporator 350, operation of the primary expansion device 355, operation of the secondary expansion device 345, and operation of the suction modulation valve 323.
  • the controller 390 also controls the positioning of the vapor injection valve 343 and liquid injection valve 353.
  • the controller 390 positions the vapor injection valve 343 in an open position for selectively permitting refrigerant vapor to pass from the flash tank economizer 340 through refrigerant vapor injection line 314 for injection into an intermediate stage of the compression process.
  • the controller 390 positions the liquid injection valve 353 in an open position for selectively permitting refrigerant liquid to pass from the flash tank economizer 340 through refrigerant liquid injection line 318 for injection into an intermediate pressure stage of the compression process.
  • the controller 390 can also control the positioning of the unload valve 327 to selectively open the unload valve 327 to bypass refrigerant from an intermediate pressure stage of the compression device 320 through bypass line 316 back to the suction side of the compression device 320 when it is desired to unload the first stage of the compression device 320.
  • a transport refrigeration system there are selected operation characteristics in a transport refrigeration system that can affect performance or overall system performance.
  • a measured value and a calculated value for a component/system performance characteristic can be determined and compared, and then a judgment can be made responsive to or based on the comparison.
  • a compressor mid-stage pressure and gas cooler exit temperature can be used to control or optimize CO 2 economized refrigeration system operations for capacity and/or efficiency.
  • gas cooler exit temperature is used to determine a prescribed compressor discharge pressure.
  • compressor mid-stage pressure is used to determine whether economized mode can/is entered by a vapor compression system.
  • the refrigerant temperature exiting the heat rejection heat exchanger reflects the heat exchanger coil and fan performance.
  • the refrigerant temperature exiting the heat rejection heat exchanger is in the function that can determine or optimize compressor discharge pressure in the refrigeration system for either higher cooling capacity or higher energy efficiency. For at least this reason, embodiments of the application can determine or verify that this performance characteristic (e.g., refrigerant temperature exiting the gas cooler) is within a prescribed range or a system design range.
  • the heat rejection heat exchanger is sized for the highest capacity conditions of the system 300 (e.g., under which the system can be intended to operate).
  • the heat rejection heat exchanger is oversized.
  • the refrigerant temperature exiting heat rejection heat exchanger (e.g., shown as GCXT in the graph in FIG. 4) was determined (e.g., tested) to be only slightly higher than ambient temperature.
  • the exiting temperature of refrigerant for the heat rejection heat exchanger can be calculated or verified using ambient temperature plus a variable offset.
  • the variable offset can be determined to have a prescribed relationship to the cooling capacity of the system 300.
  • the highest offset can occur at highest cooling capacity conditions. As shown in FIG. 4, an offset is shown on the Y axis and can be defined as (Tamb-GCXT).
  • the temperature difference between evaporator return air temperature (RTS) and supply air temperature (STS) is shown on X axis.
  • the temperature difference (RTS-STS) is one exemplary measurement of system 300 cooling capacity.
  • the temperature difference (RTS-STS) is directly related (e.g., a prescribed relationship) to the transport refrigeration system cooling capacity.
  • the transport refrigeration system capacity can be determined responsive to an operating mode of the transport refrigeration system.
  • a sensor 382 can be provided in the system 300 shown in FIG. 3 to measure the refrigerant temperature exiting heat rejection heat exchanger 330.
  • the sensor 382 can be a temperature sensor.
  • the sensor 382 can be a pressure sensor where the temperature can be determined using the pressure.
  • a calculated temperature can be compared to the temperature provided using the sensor 382. When corresponding values do not match, an error condition in the sensor 382 can be identified by the controller 390 provided to an operator or the like.
  • compressor mid stage pressure is an operation characteristic that can be monitored because the compressor mid stage pressure affects whether the system can transition into economized mode for higher capacity and higher energy efficiency.
  • the controller 390 can operate to verify proper compressor functions determined through a compressor mid stage pressure performance check during system 300 operations which can be executed according to embodiments of the application by a comparison of a measured value and a calculated (e.g., indirect) value for the compressor mid-stage pressure.
  • FIG. 5 shows the compressor mid-stage pressure as a function of the compressor discharge pressure for various compressor suction pressures.
  • the compressor mid-stage pressure can be determined when the suction and discharge pressure of the compressor 320 are known. The same information can be written in the form of an exemplary two-dimensional lookup table below.
  • P Suction 1 P Suction 2
  • P Suction 3 P Suction 4
  • the values of the suction, discharge, and mid-stage pressures are specific to the compressor design and operating conditions (e.g., compressor 320).
  • the values of the mid-stage pressure for a particular combination of suction and discharge pressure may change. This can be more pronounced if the compressor design allows to independently control the speed of the two compressor stages, for instance if the two stages are driven by different motors, for which the speed can be adjusted independently from each other.
  • an additional dimension can be added to the graph or lookup table. For example, an additional dimension can be
  • a sensor 384 can be provided in the system 300 shown in FIG. 3 to measure the compressor mid-stage pressure.
  • the sensor 384 can be a pressure sensor. In one
  • a calculated compressor mid-stage pressure can be compared to the compressor mid-stage pressure provided using the sensor 384.
  • an error condition in the sensor 384 can be determined by the controller 390 provided to an operator or the like.
  • FIG. 6 An embodiment of a method of operating a transport refrigeration unit according to the application will now be described.
  • the method embodiment shown in FIG. 6, can be implemented in and will be described using a refrigerant vapor compression system embodiment shown in FIG. 3, however, the method embodiment is not intended to be limited thereby.
  • an operating characteristic of the system can be measured (e.g., Cm) (operation block 610). Then, the operating characteristic of the system can be indirectly determined or calculated (e.g., Cc) from other system components and/or characteristics according to a prescribed relationship (operation block 620). It can be determined whether Cm and Cc match (operation block 630). When the determination in operation block 630 is negative, an error condition can be processed (operation block 640). When the determination in operation block 630 is affirmative or from operation block 640, a delay period (operations block 650) can be processed before control returns to operation block 610.
  • a calculated measurement for a system characteristic can be more accurate than a measured value.
  • the error condition can be processed in operation block 640 by having the controller 390 stop using the measure value Cm and begin using the calculated value Cc.
  • the controller 390 can be responsive to a pressure difference between the flash tank and a mid-stage of the compressor to protect or prevent operation of the economizer during periods in which the pressure at the mid-stage is greater than the pressure in the flash tank or control operations of a flow control device (e.g., flow control device 343, 353) coupled thereto.
  • a flow control device e.g., flow control device 343, 353
  • Embodiments according to the application can use remote sensors to respectively measure an environment within the container 12 such as the return air temperature RTS and the supply air temperature STS.
  • Remote sensors can communicate with a controller (e.g., transport refrigeration unit 10) through wire or wireless communications.
  • wireless communications can include one or more radio transceivers such as one or more of 802.11 radio transceiver, Bluetooth radio transceiver, GSM/GPS radio transceiver or WIMAX (802.16) radio transceiver.
  • Information collected by remote sensor(s) can be used as input parameters for a controller to control various components in transport refrigeration systems.
  • remote sensors may monitor additional criteria such as humidity, species concentration or the like.

Abstract

Selon des modes de réalisation de la présente invention, des systèmes, un appareil de réfrigération de transport et/ou des procédés associés peuvent fournir une vérification exemplaire en ce qui concerne leurs caractéristiques fonctionnelles. Selon un mode de réalisation, une pression calculée à mi-étage d'un compresseur peut être vérifiée en utilisant une relation prescrite pour d'autres caractéristiques de système de réfrigération de transport.
PCT/US2010/052267 2009-10-23 2010-10-12 Commande de paramètre dans un système de réfrigération de transport et procédés associés WO2011049778A1 (fr)

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US13/498,680 US20120227427A1 (en) 2009-10-23 2010-10-12 Parameter control in transport refrigeration system and methods for same
CN201080047706.3A CN102575887B (zh) 2009-10-23 2010-10-12 在运输冷藏系统中的参数控制以及用于运输冷藏系统的方法
DK10771264.8T DK2491318T3 (en) 2009-10-23 2010-10-12 PARAMETER CONTROL IN TRANSPORT COOLING SYSTEM AND PROCEDURES
EP10771264.8A EP2491318B1 (fr) 2009-10-23 2010-10-12 Commande de paramètre dans un système de réfrigération de transport et procédés associés
HK12113599.4A HK1172943A1 (zh) 2009-10-23 2012-12-31 在運輸冷藏系統中的參數控制以及用於運輸冷藏系統的方法

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US25428009P 2009-10-23 2009-10-23
US61/254,280 2009-10-23

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US (1) US20120227427A1 (fr)
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HK (1) HK1172943A1 (fr)
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EP2491318A1 (fr) 2012-08-29
CN102575887A (zh) 2012-07-11
CN102575887B (zh) 2015-11-25
HK1172943A1 (zh) 2013-05-03
DK2491318T3 (en) 2018-06-25
US20120227427A1 (en) 2012-09-13

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