EP2491318B1 - Parameter control in transport refrigeration system and methods for same - Google Patents
Parameter control in transport refrigeration system and methods for same Download PDFInfo
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- EP2491318B1 EP2491318B1 EP10771264.8A EP10771264A EP2491318B1 EP 2491318 B1 EP2491318 B1 EP 2491318B1 EP 10771264 A EP10771264 A EP 10771264A EP 2491318 B1 EP2491318 B1 EP 2491318B1
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- refrigerant
- heat exchanger
- vapor compression
- temperature
- compression system
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
Description
- This invention relates generally to transport refrigeration systems and methods for same and, more particularly, to methods and apparatus for controlling vapor compression systems.
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EP 1965158 A1 discloses a refrigerant vapor compression system in accordance with the preamble ofclaim 1. - 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. 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. In one form of an economizer cycle, a flash tank is used to perform the separation. In an economizer cycle with flash tank, 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. Such 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.
- Due to the thermophysical properties of CO2, 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. In 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.
- In view of the background, at least preferred embodiments of the present invention provide a transport refrigeration system, transport refrigeration unit, and methods of operating the same that can maintain cargo quality by selectively controlling transport refrigeration system components.
- One embodiment 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.
- In at least preferred embodiments of the invention, operations of components of a transport refrigeration system can be directly measured (e.g., sensors) and/or indirectly verified (e.g., without sensors).
- In accordance with one embodiment of the invention, an economizer includes a control for controlling operations of the economizer responsive to pressure in a compressor.
- In accordance with a first aspect of the present invention, there is provided a refrigerant vapor compression system comprising: a refrigerant compression device; a refrigerant heat rejection heat exchanger downstream of said compression device; a refrigerant heat absorption heat exchanger downstream of said refrigerant heat rejection heat exchanger; a first expansion device disposed downstream of said refrigerant heat rejection heat exchanger and upstream of said 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 operations of the refrigeration vapor compression system, said controller operative to indirectly verify the measured refrigerant temperature, characterized in that the compression device includes a first compression stage and a second compression stage, and in that the refrigerant temperature at the output of the heat rejection heat exchanger is first determined by measurement using the sensor, and is second determined by calculation using ambient temperature and vapor compression system capacity.
- In accordance with a second aspect of the present invention, there is provided 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 said compression device, a refrigerant heat absorption heat exchanger downstream of said refrigerant heat rejection heat exchanger, a sensor to sense the characteristic to determine a system capacity of the refrigerant vapor compression system during operation, said characteristic being a refrigerant temperature at an output of the heat rejection heat exchanger, and interconnecting refrigerant lines as active components, the method comprising: 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 refrigerant temperature at the output of the heat rejection heat exchanger using ambient temperature and vapor compression system capacity; comparing the sensed value of the refrigerant temperature at the output of the heat rejection heat exchanger against said indirectly determined value of refrigerant temperature at the output of the heat rejection heat exchanger; and determining an error condition of a corresponding sensor when a result of the comparison does not match.
- In accordance with a third aspect of the present invention, there is provided 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 comprising: operating the transport refrigeration unit in a mode where a refrigerant is circulating within a refrigerant circuit; sensing a refrigerant temperature at an output of a heat rejection heat exchanger to determine a system capacity of the transport refrigeration unit during operation; indirectly determining the refrigerant temperature at the output of the heat rejection heat exchanger using ambient temperature and vapor compression system capacity; comparing the sensed value of the refrigerant temperature at the output of the heat rejection heat exchanger against said indirectly determined value; and determining an error condition of a corresponding sensor when a result of the comparison does not match.
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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; and -
FIG. 6 is a flow diagram showing an embodiment of a method for operating a transport refrigeration system according to the application. - Reference will now be made in detail to exemplary embodiments of the application, examples of which are illustrated in the accompanying drawings. Whenever possible, the same reference numerals will be used throughout the drawings to refer to the same or like parts.
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FIG. 1 is a diagram that shows an embodiment of a transport refrigeration system. As shown inFIG. 1 ,transport refrigeration system 100 can include atransport refrigeration unit 10 coupled to an enclosed space within acontainer 12. Thetransport refrigeration system 100 may be of the type commonly employed on refrigerated trailers. As shown inFIG. 1 , thetransport refrigeration unit 10 is configured to maintain a prescribed thermal environment within the container 12 (e.g., cargo in an enclosed volume). - In
FIG. 1 , thetransport refrigeration unit 10 is connected at one end of thecontainer 12. Alternatively, thetransport refrigeration unit 10 can be coupled to a prescribed position on a side or more than one side of thecontainer 12. In one embodiment, a plurality of transport refrigeration units can be coupled to asingle container 12. Alternatively, a singletransport refrigeration unit 10 can be coupled to a plurality ofcontainers 12 or multiple enclosed spaces within a single container. Thetransport 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 thetransport refrigeration unit 10 will be warmer than the inducted air such that thetransport refrigeration unit 10 is employed to warm the air in thecontainer 12. In one embodiment, the exhaust air from thetransport refrigeration unit 10 will be cooler than the inducted air such that thetransport refrigeration unit 10 is employed to cool the air in thecontainer 12. Thetransport refrigeration unit 10 can induct air from thecontainer 12 having a return temperature Tr (e.g., first temperature) and exhaust air to thecontainer 12 having a supply temperature Ts (e.g., second temperature). - In one embodiment, 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 inFIG. 1 , afirst temperature sensor 24 of thetransport refrigeration unit 10 can provide the supply temperature Ts and asecond temperature sensor 22 of thetransport refrigeration unit 10 can provide the return temperature Tr to thetransport 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 incontainer 12. As known to one skilled in the art, the transport refrigeration system 100 (e.g., controller 250) 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. As shown inFIG. 2 , atransport refrigeration system 200 can include atransport refrigeration unit 210 coupled to acontainer 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). Thecontainer 212 can include an enclosedvolume 214 for the transport/storage of such goods. The enclosedvolume 214 may be an enclosed space having an interior atmosphere isolated from the outside (e.g., ambient atmosphere or conditions) of thecontainer 212. - The
transport refrigeration unit 210 is located so as to maintain the temperature of the enclosedvolume 214 of thecontainer 212 within a predefined temperature range. In one embodiment, thetransport refrigeration unit 210 can include acompressor 218, a condenserheat exchanger unit 222, acondenser fan 224, an evaporationheat exchanger unit 226, anevaporation fan 228, and acontroller 250. Alternatively, thecondenser 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. Thecompressor 218 may be a scroll compressor, a rotary compressor, a reciprocal compressor, or the like. Thetransport 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 thecompressor 218. The evaporatorheat exchanger unit 226 can be operatively coupled to an input port of thecompressor 218. Anexpansion valve 230 can be connected between an output of the condenserheat exchanger unit 222 and an input of the evaporatorheat exchanger unit 226. - The
condenser fan 224 can be positioned to direct an air stream onto the condenserheat exchanger unit 222. The air stream from thecondenser fan 224 can allow heat to be removed from the coolant circulating within the condenserheat exchanger unit 222. - The
evaporator fan 228 can be positioned to direct an air stream onto the evaporationheat exchanger unit 226. Theevaporator fan 228 can be located and ducted so as to circulate the air contained within theenclosed volume 214 of thecontainer 212. In one embodiment, theevaporator fan 230 can direct the stream of air across the surface of the evaporatorheat exchanger unit 226. Heat can thereby be removed from the air, and the reduced temperature air can be circulated within theenclosed volume 214 of thecontainer 212 to lower the temperature of theenclosed volume 214. - The
controller 250 such as, for example, a MicroLink.TM 2i or Advanced controller, can be electrically connected to thecompressor 218, thecondenser fan 224, and/or theevaporator fan 228. Thecontroller 250 can be configured to operate thetransport refrigeration unit 210 to maintain a predetermined environment (e.g., thermal environment) within theenclosed volume 214 of thecontainer 212. Thecontroller 250 can maintain the predetermined environment by selectively controlling operations of thecondenser fan 224, and/or theevaporator fan 228 to operate at a low speed or a high speed. For example, if increased cooling of theenclosed volume 214 is required, thecontroller 250 can increase electrical power to thecompressor 218, thecondenser fan 224, and theevaporator fan 228. In one embodiment, an economy mode of operation of thetransport refrigeration unit 210 can be controlled by thecontroller 250. In another embodiment, variable speeds of components of thetransport refrigeration unit 210 can be adjusted by thecontroller 250. In another embodiment, a full cooling mode for components of thetransport refrigeration unit 210 can be controlled by thecontroller 250. In one embodiment, theelectronic controller 250 can adjust a flow of coolant supplied to thecompressor 218. -
FIG. 3 is a diagram that shows an embodiment of a vapor compression system according to the application. As shown inFIG. 3 , an exemplary embodiment of a refrigerantvapor compression system 300 designed for operation in a transcritical cycle with a low critical point refrigerant, such as for example, but not limited to, carbon dioxide and refrigerant mixtures containing carbon dioxide. However, it is to be understood that the refrigerantvapor 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 controlledenclosed volume 214 such as a cargo space of a truck, trailer, container, or the like for transporting perishable/frozen goods. The refrigerantvapor 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 amulti-stage compression device 320, a refrigerant heatrejection heat exchanger 330, a refrigerant heatabsorption heat exchanger 350, also referred to herein as an evaporator, and aprimary expansion valve 355, such as for example an electronic expansion valve as depicted inFIG. 3 , operatively associated with theevaporators 350, withrefrigerant lines FIG. 3 , the refrigerantvapor compression system 300 may also include an unloadbypass line 316 that establishes refrigerant flow communication between an intermediate pressure stage of themulti-stage compression device 320 and the suction pressure portion of the refrigerant circuit, which constitutesrefrigerant line 306 extending from the outlet of theevaporator 350 to the inlet of thecompression device 320. - Additionally, the refrigerant
vapor compression system 300 can include an economizer circuit having aneconomizer device 340, asecondary expansion valve 345 and a refrigerantvapor injection line 314. As shown inFIG. 3 , the economizer circuit includes aflash tank economizer 340 interdisposed inrefrigerant line 304 of the primary refrigerant circuit downstream with respect to refrigerant flow of the refrigerant heatrejection heat exchanger 330 and upstream with respect to refrigerant flow of the refrigerant heatabsorption heat exchanger 350. Thesecondary expansion device 345 is interdisposed inrefrigerant line 304 in operative association with and upstream of the economizer. Thesecondary expansion device 345 may be an expansion valve, such as a high pressure electronic expansion valve as depicted inFIG. 3 . Refrigerant traversing thesecondary 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. Theflash tank economizer 340 includes aseparation chamber 342 wherein refrigerant in the liquid state collects in a lower portion of theseparation chamber 342 and refrigerant in the vapor state collects in the portion of theseparation chamber 342 above the liquid refrigerant. - The refrigerant
vapor injection line 314 establishes refrigerant flow communication between an upper portion of theseparation chamber 342 of theflash tank economizer 340 and an intermediate stage of the compression process. A vapor injectionflow control device 343 is interdisposed invapor injection line 314. The vapor injectionflow control device 343 may comprise a flow control valve selectively positionable between an open position where refrigerant vapor flow may pass through the refrigerantvapor injection line 314 and a closed position where refrigerant vapor flow through the refrigerantvapor injection line 314 is reduced or blocked. In one embodiment, the vapor injectionflow 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 inrefrigerant line 306 at a location between the outlet of the refrigeration heatabsorption heat exchanger 350 and an inlet to thecompression device 320. In the exemplary embodiment depicted inFIG. 3 , thesuction modulation valve 323 is positioned inrefrigerant line 306 between the outlet of theevaporator 350 and the point at which the compressor unloadbypass line 316 intersectsrefrigerant line 306. In one embodiment, thesuction modulation valve 323 may comprise a pulse width modulated solenoid valve. - In a refrigerant vapor compression system operating in a transcritical cycle, 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. In a refrigerant vapor compression system operating in a subcritical cycle, the refrigerant heatrejection 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 inFIG. 3 , the refrigerant heatrejection heat exchanger 330 includes a finnedtube 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 finnedtube heat exchanger 332 by the fan(s) 334 associated with anexemplary gas cooler 330. - Whether the refrigerant
vapor compression system 300 is operating in a transcritical cycle or a subcritical cycle, the refrigerant heatabsorption 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 inFIG. 3 the refrigerant heatabsorption heat exchanger 350 comprises a finnedtube heat exchanger 352 through which refrigerant passes in heat exchange relationship with air drawn from and returned to therefrigerated container 212 by the evaporator fan(s) 354 associated with theevaporator 350. The finnedtube 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. In the embodiment depicted inFIG. 3 , thecompression 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 afirst compression stage 320a and asecond compression stage 320b. The first and second compression stages are disposed in series refrigerant flow relationship with the refrigerant leaving thefirst compression stage 320a passing directly to thesecond compression stage 320b for further compression. Alternatively, thecompression device 320 may comprise a pair ofindependent compressors first compressor 320a in refrigerant flow communication with an inlet port (e.g. the suction inlet port) of thesecond compressor 320b. In the independent compressor embodiment, thecompressors FIG. 3 , the refrigerantvapor compression system 300 includes arefrigerant bypass line 316 providing a refrigerant flow passage from an intermediate pressure stage of thecompression device 320 back to the suction side of thecompression device 320. An unloadvalve 327 is interdisposed in thebypass line 316. The unloadvalve 327 may be selectively positioned in an open position in which refrigerant flow passes through thebypass line 316 and a closed position in which refrigerant flow through thebypass line 316 is reduced or blocked. - In the embodiment depicted in
FIG. 3 , the refrigerantvapor compression system 300 further includes a refrigerantliquid injection line 318. The refrigerantliquid injection line 318 can tap intorefrigerant line 304 at location downstream of theflash tank economizer 340 and upstream of theprimary expansion valve 355 and open into an intermediate stage of the compression process. Thus, the refrigerantliquid injection line 318 can establish refrigerant flow communication between a lower portion of theseparation chamber 342 of theflash tank economizer 340 and an intermediate pressure stage of thecompression device 320. In one embodiment, the refrigerantliquid injection line 318 can establish refrigerant flow communication between a lower portion of theseparation chamber 342 of theflash tank economizer 340 and a compressor suction line (e.g., an inlet to the compression device). A liquid injectionflow control device 353 can be interdisposed in refrigerantliquid injection line 318. The liquid injectionflow control device 353 may comprise a flow control valve selectively positionable between an open position wherein refrigerant liquid flow may pass through theliquid injection line 318 and a closed position wherein refrigerant liquid flow through the refrigerantliquid injection line 318 is reduced or blocked. In an embodiment, the liquid injectionflow control device 353 comprises a two-position solenoid valve of the type selectively positionable between a first open position and a second closed position. - In the exemplary embodiment of the refrigerant
vapor compression system 300 depicted inFIG. 3 , 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 thefirst compression stage 320a into thesecond compression stage 320b of thecompression device 320. - Liquid refrigerant collecting in the lower portion of the
flash tank economizer 340 can pass therefrom throughrefrigerant line 304 and traverse the primary refrigerantcircuit expansion valve 355 interdisposed inrefrigerant line 304 upstream with respect to refrigerant flow of theevaporator 350. As this liquid refrigerant traverses thefirst expansion device 355, it expands to a lower pressure and temperature before entering theevaporator 350. Theevaporator 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. As in conventional practice, theprimary expansion valve 355 meters the refrigerant flow through therefrigerant line 304 to maintain a desired level of superheat in the refrigerant vapor leaving theevaporator 350 to ensure that no liquid is present in the refrigerant leaving the evaporator. The low pressure refrigerant vapor leaving theevaporator 350 returns throughrefrigerant line 306 to the input port of the first compression stage orfirst compressor 320a of thecompression device 320 in the embodiment depicted inFIG. 3 . - The refrigerant
vapor compression system 300 also includes a control system operatively associated therewith for controlling operation of the refrigerantvapor compression system 300. The control system can include acontroller 390 that can determine the desired mode of operation in which to operate the refrigerantvapor compression system 300 based upon consideration of refrigeration load requirements, ambient conditions and various sensed system operating parameters. As shown inFIG. 3 , thecontroller 390 also includes various sensors operatively associated with thecontroller 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, apressure sensor 392 disposed in operative association with theflash tank economizer 340 to sense the pressure within theseparation chamber 342, atemperature sensor 393 and apressure sensor 394 for sensing the refrigerant inlet or suction temperature and pressure, respectively, and atemperature sensor 395 and apressure sensor 396 for sensing refrigerant discharge temperature and pressure, respectively. In transport refrigeration applications, the refrigeration vapor compression system may also include atemperature sensor 397a for sensing the temperature of the air returning to the evaporator from thecontainer 212 and atemperature sensor 397b for sensing a temperature of the air being supplied to thecontainer 212. Sensors (not shown) may also be provided for monitoring ambient outdoor conditions, such as or example ambient outdoor air temperature and humidity. By way of example but not limitation; thepressure sensors temperature sensors - The
controller 390 processes the data received from the various sensors and controls operation of thecompression device 320, operation of the fan(s) 334 associated with the refrigerant heatrejection heat exchanger 330, operation of the fan(s) 354 associated with theevaporator 350, operation of theprimary expansion device 355, operation of thesecondary expansion device 345, and operation of thesuction modulation valve 323. Thecontroller 390 also controls the positioning of thevapor injection valve 343 andliquid injection valve 353. Thecontroller 390 positions thevapor injection valve 343 in an open position for selectively permitting refrigerant vapor to pass from theflash tank economizer 340 through refrigerantvapor injection line 314 for injection into an intermediate stage of the compression process. Similarly, thecontroller 390 positions theliquid injection valve 353 in an open position for selectively permitting refrigerant liquid to pass from theflash tank economizer 340 through refrigerantliquid injection line 318 for injection into an intermediate pressure stage of the compression process. In theFIG. 3 embodiment, thecontroller 390 can also control the positioning of the unloadvalve 327 to selectively open the unloadvalve 327 to bypass refrigerant from an intermediate pressure stage of thecompression device 320 throughbypass line 316 back to the suction side of thecompression device 320 when it is desired to unload the first stage of thecompression device 320. - According to embodiments of the application, there are selected operation characteristics in a transport refrigeration system that can affect performance or overall system performance. During transport refrigeration system operations, it is desirable to check such characteristics to determine proper component or system functions and/or operations. In one embodiment, 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.
- For example, a compressor mid-stage pressure and gas cooler exit temperature can be used to control or optimize CO2 economized refrigeration system operations for capacity and/or efficiency. In one embodiment, gas cooler exit temperature is used to determine a prescribed compressor discharge pressure. In an embodiment, compressor mid-stage pressure is used to determine whether economized mode can/is entered by a vapor compression system.
- In a refrigeration system, the refrigerant temperature exiting the heat rejection heat exchanger reflects the heat exchanger coil and fan performance. When the transport refrigeration system operates in a transcritical application, then 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. In one embodiment, 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). Therefore, for a majority or almost all of designed operating conditions, the heat rejection heat exchanger is oversized. As determined by the inventors, 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. Thus, in one embodiment, 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 thesystem 300. In one embodiment, the highest offset can occur at highest cooling capacity conditions. As shown inFIG. 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 ofsystem 300 cooling capacity. In one embodiment, the temperature difference (RTS-STS) is directly related (e.g., a prescribed relationship) to the transport refrigeration system cooling capacity. - In one embodiment, 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 thesystem 300 shown inFIG. 3 to measure the refrigerant temperature exiting heatrejection heat exchanger 330. Thesensor 382 can be a temperature sensor. Alternatively, thesensor 382 can be a pressure sensor where the temperature can be determined using the pressure. In one embodiment, a calculated temperature can be compared to the temperature provided using thesensor 382. When corresponding values do not match, an error condition in thesensor 382 can be identified by thecontroller 390 provided to an operator or the like. - In an economized refrigeration system, 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. For at least this reason, the
controller 390 can operate to verify proper compressor functions determined through a compressor mid stage pressure performance check duringsystem 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. - An exemplary indirect determination for the compressor mid-stage pressure will now be described.
FIG. 5 shows the compressor mid-stage pressure as a function of the compressor discharge pressure for various compressor suction pressures. As shown inFIG. 5 , the compressor mid-stage pressure can be determined when the suction and discharge pressure of thecompressor 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 P Discharge 1 P Mid-Stage 1,1 P Mid-Stage 1,2 P Mid-Stage 1,3 P Mid-Stage 1,4 P Discharge 2 P Mid-Stage 2,1 P Mid-Stage 2,2 P Mid-Stage 2,3 P Mid-Stage 2,4 P Discharge 3 P Mid-Stage 3,1 P Mid-Stage 3,2 P Mid-Stage 3,3 P Mid-Stage 3,4 P Discharge 4 P Mid-Stage 4,1 P Mid-Stage 4,2 P Mid-Stage 4,3 P Mid-Stage 4,4 - It should be understood that the values of the suction, discharge, and mid-stage pressures are specific to the compressor design and operating conditions (e.g., compressor 320). When the operating conditions for a given compressor machine change, for instance if the suction superheat changes, 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. In this case, an additional dimension can be added to the graph or lookup table. For example, an additional dimension can be accomplished by providing additional graphs or tables, each for a constant value of the additional variable.
- A
sensor 384 can be provided in thesystem 300 shown inFIG. 3 to measure the compressor mid-stage pressure. Thesensor 384 can be a pressure sensor. In one embodiment, a calculated compressor mid-stage pressure can be compared to the compressor mid-stage pressure provided using thesensor 384. When corresponding values do not match, an error condition in thesensor 384 can be determined by thecontroller 390 provided to an operator or the like. - 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 inFIG. 3 , however, the method embodiment is not intended to be limited thereby. - Referring now to
FIG. 6 , a process as performed by thecontroller 390 can be shown in block diagram form. After a process starts during system operations, 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 inoperation block 630 is negative, an error condition can be processed (operation block 640). When the determination inoperation block 630 is affirmative or fromoperation block 640, a delay period (operations block 650) can be processed before control returns tooperation block 610. - In one embodiment, a calculated measurement for a system characteristic can be more accurate than a measured value. Thus, the error condition can be processed in
operation block 640 by having thecontroller 390 stop using the measure value Cm and begin using the calculated value Cc. - In one embodiment, a calculated or indirect measurement of selected characteristics (e.g., compressor unit stage pressure and/or gas cooler refrigerant exit temperature) of transport refrigeration systems including refrigerant vapor compression systems can be determined with sufficient accuracy that sensors can be reduced or eliminated from the system, which may increase reliability and decrease size and cost. In one embodiment, 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. - 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, as known to one skilled in the art, can communicate with a controller (e.g., transport refrigeration unit 10) through wire or wireless communications. For example, 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. In one embodiment, remote sensors may monitor additional criteria such as humidity, species concentration or the like. - It should be recognized that selected procedures described herein may result in some liquid refrigerant entering the compressor inlet. Although this is generally undesirable, it may occur for short periods of time without any significant damage to the compressor.
- While the present invention has been described with reference to a number of specific embodiments, it will be understood that the scope of the invention should be determined only with respect to claims that can be supported by the present specification. Further, while in numerous cases herein wherein systems and apparatuses and methods are described as having a certain number of elements it will be understood that such systems, apparatuses and methods can be practiced with fewer than the mentioned certain number of elements. Also, while a number of particular embodiments have been set forth, it will be understood that features and aspects that have been described with reference to each particular embodiment can be used with each remaining particularly set forth embodiment. For example, features or aspects described with respect to
FIG. 3 can be used, combined with or replace features described usingFIGS. 4-6 .
Claims (13)
- A refrigerant vapor compression system comprising:a refrigerant compression device (320);a refrigerant heat rejection heat exchanger (330) downstream of said compression device;a refrigerant heat absorption heat exchanger (350) downstream of said refrigerant heat rejection heat exchanger (330);a first expansion device (355) disposed downstream of said refrigerant heat rejection heat exchanger (330) and upstream of said refrigerant heat absorption heat exchanger (350);a sensor (382) coupled to an output of the heat rejection heat exchanger (330), the sensor to measure a refrigerant temperature; anda controller (390) to control operations of the refrigeration vapor compression system, said controller operative to indirectly verify the measured refrigerant temperature,characterized in that the compression device includes a first compression stage (320a) and a second compression stage (320b), and in that the refrigerant temperature at the output of the heat rejection heat exchanger (330) is first determined by measurement using the sensor (382), and is second determined by calculation using ambient temperature and vapor compression system capacity.
- The refrigerant vapor compression system of claim 1, where said vapor compression system capacity has a prescribed relationship with an operating mode or difference between supply air temperature (Ts) and return air temperature (Tr); and wherein an offset is added to the ambient temperature responsive to the vapor compression system capacity.
- The refrigerant vapor compression system of claim 2, the controller (390) being configured to operate the vapor compression system with the calculated value for the refrigerant temperature when the measured refrigerant temperature is different from the calculated temperature value.
- The vapor compression system of claim 1, 2 or 3, where said sensor (382) is a pressure sensor or a temperature sensor.
- The refrigerant vapor compression system of any preceding claim, comprising a second sensor (384) to measure a compressor mid stage pressure, said controller (390) being configured to indirectly verify said measured compressor mid stage pressure.
- The refrigerant vapor compression system of claim 5, where the compressor mid stage pressure is calculated using a discharge pressure and an inlet pressure of the compressor (320).
- The refrigerant vapor compression system of claim 5 or 6, wherein the controller (390) is configured to operate the vapor compression system using the verified value of the compressor mid stage pressure where the measured compressor mid stage pressure does not match the indirectly verified value.
- The refrigerant vapor compression system of any preceding claim, comprising:a second valve (345) disposed downstream of the heat rejection heat exchanger(330);and an economizer circuit (340) disposed downstream of the second valve (345) and upstream of the first expansion device (355), the economizer circuit including a refrigerant injection line (314,318) to open to an intermediate pressure stage of the compression device and a flow control valve (343,353) disposed in the refrigerant injection line.
- The refrigerant vapor compression system of claim 8, said controller (390) being configured to close the flow control valve (343,353) when the compressor mid-stage pressure is operative to cause refrigerant flow toward the economizer circuit.
- The refrigerant vapor compression system of any of claims 1 to 7, comprising:
a flash tank economizer (340) disposed in serial flow relationship between the heat rejection heat exchanger (330) and the first expansion device (355), said flash tank economizer including:a flash tank (342);a first flow control device (345) disposed between the heat rejection heat exchanger (330) and said flash tank (342);an economizer vapor line (314) to fluidly interconnect said flash tank to a mid-stage of the compressor; anda second flow control device (342) disposed in said economizer vapor line. - A method for determining a characteristic of a refrigerant vapor compression system having a refrigerant circuit including a refrigerant compression device (320), a refrigerant heat rejection heat exchanger (330) downstream of said compression device, a refrigerant heat absorption heat exchanger (350) downstream of said refrigerant heat rejection heat exchanger, a sensor (382) to sense the characteristic to determine a system capacity of the refrigerant vapor compression system during operation, said characteristic being a refrigerant temperature at an output of the heat rejection heat exchanger (330), and interconnecting refrigerant lines as active components, the method comprising: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 refrigerant temperature at the output of the heat rejection heat exchanger (330) using ambient temperature and vapor compression system capacity;comparing the sensed value of the refrigerant temperature at the output of the heat rejection heat exchanger (330) against said indirectly determined value of refrigerant temperature at the output of the heat rejection heat exchanger (330); anddetermining an error condition of a corresponding sensor when a result of the comparison does not match.
- The method of claim 11, comprising subsequently using the indirectly determined value in operating the vapor compression system.
- 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 comprising:operating the transport refrigeration unit in a mode where a refrigerant is circulating within a refrigerant circuit;sensing a refrigerant temperature at an output of a heat rejection heat exchanger (330) to determine a system capacity of the transport refrigeration unit during operation;indirectly determining the refrigerant temperature at the output of the heat rejection heat exchanger (330) using ambient temperature and vapor compression system capacity;comparing the sensed value of the refrigerant temperature at the output of the heat rejection heat exchanger (330) against said indirectly determined value; anddetermining an error condition of a corresponding sensor when a result of the comparison does not match.
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- 2010-10-12 CN CN201080047706.3A patent/CN102575887B/en active Active
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US20120227427A1 (en) | 2012-09-13 |
EP2491318A1 (en) | 2012-08-29 |
WO2011049778A1 (en) | 2011-04-28 |
CN102575887A (en) | 2012-07-11 |
HK1172943A1 (en) | 2013-05-03 |
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