EP2434232A2 - Steuerung eines transkritischen Dampfverdichtersystems - Google Patents

Steuerung eines transkritischen Dampfverdichtersystems Download PDF

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Publication number
EP2434232A2
EP2434232A2 EP11250667A EP11250667A EP2434232A2 EP 2434232 A2 EP2434232 A2 EP 2434232A2 EP 11250667 A EP11250667 A EP 11250667A EP 11250667 A EP11250667 A EP 11250667A EP 2434232 A2 EP2434232 A2 EP 2434232A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
compressor
energy
proximate
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP11250667A
Other languages
English (en)
French (fr)
Inventor
Michal Hegar
Michal Kolda
Marketa Kopecka
Vaclav Rajtmajer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Thermo King Corp
Original Assignee
Thermo King Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Thermo King Corp filed Critical Thermo King Corp
Publication of EP2434232A2 publication Critical patent/EP2434232A2/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • 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
    • F25B2600/17—Control issues by controlling the pressure 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
    • F25B2700/19—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
    • F25B2700/19—Pressures
    • F25B2700/197—Pressures of the 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
    • 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
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator

Definitions

  • the present invention relates to control of a transcritical vapor compression system.
  • a transcritical vapor compression system is controlled to optimize the coefficient of performance (COP).
  • COP coefficient of performance
  • control methods include measuring various parameters and comparing the measured parameter to a stored value representative of an efficient system. For example, if the measured parameter is significantly higher than the stored value, then the system is operating inefficiently and operating parameters are adjusted accordingly.
  • the invention provides a transcritical vapor compression system.
  • the transcritical vapor compression system includes a compressor for compressing a refrigerant, a first heat exchanger for cooling the refrigerant, an expansion device for decreasing the pressure of the refrigerant, a second heat exchanger for absorbing heat into the refrigerant, and a controller programmed to calculate a first energy difference across the second heat exchanger and a second energy difference across the compressor, to calculate an energy ratio by dividing the first energy difference by the second energy difference, to compare the energy ratio to a previously calculated energy ratio, and to adjust operating parameters of the system based on the comparison of the energy ratio with respect to the previously calculated energy ratio.
  • the transcritical vapor compression system may further comprise a first blower for directing a first fluid over the first heat exchanger, and a second blower for directing a second fluid over the second heat exchanger, wherein the controller is programmed to adjust at least one of speed of the first blower, speed of the second blower, speed of the compressor and opening of the expansion device based on the comparison of the energy ratio with respect to the previously calculated energy ratio.
  • the transcritical vapor compression system may further comprise a first temperature sensor and a first pressure sensor positioned proximate an inlet to the compressor for measuring temperature and pressure, respectively; a second temperature sensor and a second pressure sensor positioned proximate an outlet of the compressor for measuring temperature and pressure, respectively; a third temperature sensor positioned proximate an inlet to the second heat exchanger for measuring temperature; a fourth temperature sensor positioned proximate an outlet of the second heat exchanger for measuring temperature; and a third pressure sensor positioned proximate one of the inlet and the outlet to the second heat exchanger for measuring pressure.
  • the controller may be programmed to calculate the internal energy of the refrigerant proximate the inlet to the compressor, the outlet of the compressor, the inlet of the second heat exchanger and the outlet of the second heat exchanger based on the measurements of temperature and pressure.
  • the controller may be programmed to calculate the first energy difference by subtracting the internal energy of refrigerant proximate the inlet to the second heat exchanger from the internal energy of refrigerant proximate the outlet of the second heat exchanger, and wherein the controller is programmed to calculate the second energy difference by subtracting the internal energy of refrigerant proximate the inlet to the compressor from the internal energy of the refrigerant proximate the outlet of the compressor.
  • the first heat exchanger may be built to withstand pressures greater than or equal to 7.38 MPa (1070 pisa).
  • the invention provides a method of controlling a transcritical vapor compression system.
  • the method includes providing a compressor for compressing a refrigerant, providing a first heat exchanger for cooling the refrigerant, providing an expansion device for decreasing the pressure of the refrigerant, providing a second heat exchanger for absorbing heat into the refrigerant, calculating a first energy difference across the second heat exchanger, calculating a second energy difference across the compressor, calculating an energy ratio by dividing the first energy difference by the second energy difference, comparing the energy ratio to a previously calculated energy ratio, and adjusting operating parameters of the system based on the comparison of the energy ratio with respect to the previously calculated energy ratio.
  • the method may further comprise providing a first blower for directing a first fluid over the first heat exchanger, providing a second blower for directing a second fluid over the second heat exchanger, adjusting at least one of speed of the first blower, speed of the second blower, speed of the compressor and opening of the expansion device based on the comparison of the energy ratio with respect to the previously calculated energy ratio.
  • the method may further comprise measuring temperature and pressure proximate an inlet to the compressor, measuring temperature and pressure proximate an outlet of the compressor, measuring temperature proximate an inlet to the second heat exchanger, measuring temperature proximate an outlet of the second heat exchanger, and measuring pressure proximate one of the inlet and the outlet to the second heat exchanger.
  • the method may further comprise calculating the internal energy of the refrigerant proximate the inlet to the compressor, the outlet of the compressor, the inlet of the second heat exchanger and the outlet of the second heat exchanger based on the measurements of temperature and pressure.
  • the method may further comprise calculating the first energy difference by subtracting the internal energy of refrigerant proximate the inlet to the evaporator from the internal energy of refrigerant proximate the outlet of the evaporator, and calculating the second energy difference by subtracting the internal energy of refrigerant proximate the inlet to the compressor from the internal energy of the refrigerant proximate the outlet of the compressor.
  • the invention provides a transcritical vapor compression system.
  • the transcritical vapor compression system includes a compressor for compressing a refrigerant, a first heat exchanger for cooling the refrigerant, an expansion device for decreasing the pressure of the refrigerant, a second heat exchanger for absorbing heat into the refrigerant, a first blower for directing a first fluid over the first heat exchanger, a second blower for directing a second fluid over the second heat exchanger, a first temperature sensor and a first pressure sensor positioned proximate an inlet to the compressor for measuring temperature and pressure, respectively, a second temperature sensor and a second pressure sensor positioned proximate an outlet of the compressor for measuring temperature and pressure, respectively, a third temperature sensor positioned proximate an inlet to the second heat exchanger for measuring temperature, a fourth temperature sensor positioned proximate an outlet of the second heat exchanger for measuring temperature, a third pressure sensor positioned proximate one of the inlet and the outlet to the second heat exchanger for measuring
  • the controller is programmed to calculate the internal energy of the refrigerant proximate the inlet to the compressor, the outlet of the compressor, the inlet of the second heat exchanger and the outlet of the second heat exchanger based on the measurements of temperature and pressure, to calculate a first energy difference by subtracting the internal energy of refrigerant proximate the inlet to the second heat exchanger from the internal energy of refrigerant proximate the outlet of the second heat exchanger, to calculate a second energy difference by subtracting the internal energy of refrigerant proximate the inlet to the compressor from the internal energy of the refrigerant proximate the outlet of the compressor, to calculate an energy ratio by dividing the first energy difference by the second energy difference, to compare the energy ratio to a previously calculated energy ratio, and to adjust at least one of speed of the first blower, speed of the second blower, speed of the compressor and opening of the expansion device based on the comparison of the energy ratio with respect to the previously calculated energy ratio.
  • FIG. 1 is a schematic diagram of a transcritical vapor compression system in accordance with the invention.
  • FIG. 2 is a diagram of internal energy and pressure of the transcritical vapor compression system shown in FIG. 1 .
  • FIG. 1 illustrates a transcritical vapor compression system 10.
  • the transcritical vapor compression system 10 is a closed circuit single stage vapor compression cycle preferably utilizing carbon dioxide (CO 2 ) as a refrigerant, although other refrigerants suitable for a transcritical vapor compressor system may be employed, as are known in the art.
  • the system 10 includes a compressor 14, a gas cooler 18, an expansion valve 22, an evaporator 26 and an accumulator tank 30 connected in series.
  • Temperature sensors 42a-42e and pressure sensors 46a-46e are located at the compressor inlet 1, the compressor outlet 2, the gas cooler outlet 3, the evaporator inlet 4 and the evaporator outlet 5, respectively.
  • CO 2 refrigerant exits the evaporator coil 26 as a heated gas and is drawn into a suction port of the compressor 14, such as a variable speed compressor.
  • the temperature and pressure of the CO 2 refrigerant are measured at the compressor inlet 1 by the temperature and pressure sensors 42a, 46a, respectively.
  • the compressor 14 pressurizes and discharges heated CO 2 refrigerant gas into the gas cooler 18.
  • the temperature and pressure of the heated CO 2 refrigerant are measured at the compressor outlet 2 by the temperature and pressure sensors 42b, 46b, respectively.
  • the heated CO 2 refrigerant is cooled to a lower temperature gas as a result of a forced flow of air 34 flowing over the gas cooler 18 and generated by blowers 36, such as variable speed blowers.
  • the gas cooler 18 can include one or more heat exchanger coils having any suitable construction, as is known in the art.
  • the temperature and pressure of the cooled CO 2 refrigerant are measured at the gas cooler outlet 3 by the temperature and pressure sensors 42c, 46c, respectively.
  • the cooled CO 2 is throttled through the expansion valve 22, such as an electronic expansion valve, and directed toward the evaporator coil 26 at a decreased pressure as a liquid-vapor mixture.
  • the temperature and pressure of the cooled CO 2 refrigerant are measured at the evaporator inlet 4 by the temperature and pressure sensors 42d, 46d, respectively.
  • the cooled CO 2 refrigerant is heated to a higher temperature gas as a result of a forced flow of air 38 generated by blowers 40, such as variable speed blowers.
  • blowers 40 such as variable speed blowers.
  • the CO 2 passing through the evaporator coil 26 absorbs the heat from the flow of air 38 such that the flow of air 38 is cooled.
  • the evaporator coil 26 can include one or more heat exchanger coils having any suitable construction, as is known in the art.
  • the temperature of the heated CO 2 refrigerant is measured at the evaporator outlet 5 by the temperature sensor 42e and, optionally, the pressure is measured by the pressure sensor 46e.
  • the pressure sensor 46e is measured by the pressure sensor 46e.
  • CO 2 refrigerant does not change phase to a liquid in the transcritical CO 2 refrigeration cycle.
  • the CO 2 refrigerant behaves as a single-phase refrigerant in a transcritical CO 2 refrigeration cycle, as opposed to the two-phase behavior of refrigerant in a reverse-Rankine refrigeration cycle.
  • the transcritical refrigeration cycle requires higher operating pressures compared to a reverse-Rankine refrigeration cycle.
  • the pressure of the refrigerant in the gas cooler 18 is in the supercritical region of the refrigerant, i.e., at or above the critical temperature and critical pressure of the refrigerant.
  • the critical point of CO 2 occurs at approximately 7.38 MPa (1070 psia) and approximately 31.1 degrees Ceslius (88 degrees Fahrenheit).
  • the pressure of refrigerant in the gas cooler 18 is approximately 8.5 MPa (1233 psia).
  • the pressure of refrigerant in the evaporator 26 is also higher than pressures seen in a reverse-Rankine refrigeration cycle.
  • the pressure of refrigerant in the evaporator 26 is approximately 2.7 MPa (392 psia).
  • the gas cooler 18 and evaporator coil 26 employ a heavy-duty construction to withstand the higher pressures.
  • the gas cooler 18 is built to withstand pressures of at least 7.38 MPa (1070 pisa) and the evaporator 26 is built to withstand pressures of at least 2.7 MPa (392 psia).
  • the transcritical vapor compression system 10 is controlled by a controller 50.
  • the controller 50 controls the opening of the expansion valve 22, the speed of the blowers 36, 40 and the speed of the compressor 14, and receives input signals from the temperature sensors 42a-42e and the pressure sensors 46a-46e, as will be described in greater detail below.
  • FIG. 2 is a diagram illustrating the saturated liquid line 54 for CO 2 , the saturated vapor line 58 for CO 2 , and the relationship between internal energy and pressure of the CO 2 refrigerant throughout the cycle of the transcritical vapor compression system 10.
  • the controller 50 is programmed to calculate the internal energy of the refrigerant at each of the compressor inlet 1, the compressor outlet 2, the gas cooler outlet 3, the evaporator inlet 4 and the evaporator outlet 5 from the respective temperature and pressure measurements from the respective temperature and pressure sensors 42a-42e, 46a-46e, in a manner well understood in the art.
  • the controller 50 is programmed to calculate the change in energy ( ⁇ E evaporator ) across the evaporator 26 and the change in energy ⁇ E compressor ) across the compressor 14, as shown in FIG. 2 .
  • the change in energy ( ⁇ E evaporator ) across the evaporator 26 is calculated as the difference between the internal energy calculated at the evaporator outlet 5 and the internal energy calculated at the evaporator inlet 4.
  • the change in energy ( ⁇ E compressor ) across the compressor 14 is calculated as the difference between the internal energy calculated at the compressor outlet 2 and the internal energy calculated at the compressor inlet 1.
  • the controller 50 is programmed to calculate an energy ratio across the evaporator 26 and compressor 14 by dividing the energy change across the evaporator ( ⁇ E evaporator ) by the energy change across the compressor ( ⁇ E compressor ).
  • the controller 50 is programmed to compare the energy ratio to a previous energy ratio, more specifically, to the immediately previous energy ratio calculated. Then, the controller is programmed to adjust operating parameters, such as the opening of the expansion valve 22, the compressor speed of the compressor 14 and the blower speed of the blowers 36, 40, based on the energy ratio and, more specifically, based on the comparison between the current and previous energy ratios. Specifically, the controller 50 is programmed to adjust the operating parameters to optimize the energy balance, i.e., reach a desired efficiency of the transcritical vapor compression system 10. The controller 50 is programmed to repeat the above steps to continuously adjust the operating parameters based on the difference between the current and previous energy ratios, as described above, in order to maintain the efficiency of the system 10.
  • the invention provides, among other things, a transcritical vapor compression system and a controller therefor programmed to adjust the operating parameters of the system based on the energy ratio across the evaporator and compressor.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
EP11250667A 2010-09-23 2011-07-20 Steuerung eines transkritischen Dampfverdichtersystems Withdrawn EP2434232A2 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US12/888,733 US20120073316A1 (en) 2010-09-23 2010-09-23 Control of a transcritical vapor compression system

Publications (1)

Publication Number Publication Date
EP2434232A2 true EP2434232A2 (de) 2012-03-28

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP11250667A Withdrawn EP2434232A2 (de) 2010-09-23 2011-07-20 Steuerung eines transkritischen Dampfverdichtersystems

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US (1) US20120073316A1 (de)
EP (1) EP2434232A2 (de)
CN (1) CN102434991A (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014087168A1 (en) * 2012-12-07 2014-06-12 Elstat Electronics Ltd Co2 refrigeration system

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EP3054238B1 (de) * 2015-02-03 2021-03-24 Rolls-Royce Corporation Ladesteuerungssystem für transkritische dampfzyklussysteme
CN104950933B (zh) * 2015-05-29 2020-07-14 湖北绿色家园材料技术股份有限公司 一种系统蒸汽压力的稳定装置
US11683915B1 (en) * 2021-04-03 2023-06-20 Nautilus True, Llc Data center liquid conduction and carbon dioxide based cooling apparatus and method
CN114234400B (zh) * 2021-12-23 2023-05-30 珠海格力电器股份有限公司 多模块机组控制方法、装置、计算机设备和存储介质

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JP4670329B2 (ja) * 2004-11-29 2011-04-13 三菱電機株式会社 冷凍空調装置、冷凍空調装置の運転制御方法、冷凍空調装置の冷媒量制御方法
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014087168A1 (en) * 2012-12-07 2014-06-12 Elstat Electronics Ltd Co2 refrigeration system
US9933194B2 (en) 2012-12-07 2018-04-03 Elstat Limited CO2 refrigeration system

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Publication number Publication date
CN102434991A (zh) 2012-05-02
US20120073316A1 (en) 2012-03-29

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