EP1869375A2 - Method of determining optimal coefficient of performance in a transcritical vapor compression system - Google Patents

Method of determining optimal coefficient of performance in a transcritical vapor compression system

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Publication number
EP1869375A2
EP1869375A2 EP06735014A EP06735014A EP1869375A2 EP 1869375 A2 EP1869375 A2 EP 1869375A2 EP 06735014 A EP06735014 A EP 06735014A EP 06735014 A EP06735014 A EP 06735014A EP 1869375 A2 EP1869375 A2 EP 1869375A2
Authority
EP
European Patent Office
Prior art keywords
gas cooler
refrigerant
high pressure
exit temperature
recited
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP06735014A
Other languages
German (de)
French (fr)
Other versions
EP1869375A4 (en
EP1869375B1 (en
Inventor
Young K. Park
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carrier Corp
Original Assignee
Carrier Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Carrier Corp filed Critical Carrier Corp
Publication of EP1869375A2 publication Critical patent/EP1869375A2/en
Publication of EP1869375A4 publication Critical patent/EP1869375A4/en
Application granted granted Critical
Publication of EP1869375B1 publication Critical patent/EP1869375B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • 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
    • F25B2700/21—Temperatures
    • F25B2700/2102—Temperatures at the outlet of the gas cooler

Definitions

  • the present invention relates generally to a method for optimizing the coefficient of performance of a transcritical vapor compression system by detecting a gas cooler exit temperature and determining an optimal high side pressure of the vapor compression system based solely on the gas cooler exit temperature to optimize the coefficient of performance.
  • Carbon dioxide is an environmentally friendly refrigerant that is commonly used in transcritical vapor compression systems. Carbon dioxide has a low critical point, and most vapor compression systems utilizing carbon dioxide as the refrigerant run transcritically or partially above the critical point.
  • the pressure of a subcritical fluid is a function of temperature under saturated conditions (when both liquid and vapor are present). However, when the temperature of the fluid is higher than the critical temperature (supercritical), the pressure becomes a function of the density of the fluid and is independent of the heat sink temperature. Therefore, for any set of heat sink conditions, it is possible to operate at many high side pressures. However, a maximum coefficient of performance exists that corresponds to one high side pressure. Therefore, it is important to regulate the high side pressure of the transcritical vapor compression system because the high side pressure has a large effect on the capacity and efficiency of the system.
  • both the temperature and the pressure of the refrigerant at the outlet of the gas cooler is measured. From both these measurements, the optimal high side pressure is determined. The high side pressure is then adjusted to the optimal high side based on both these measurements according to a pre-determined control strategy to optimize the coefficient of performance. The optimal high side pressure is selected to optimize the capacity and efficiency of the vapor compression system for a cooling mode. In another prior vapor compression system, the high side pressure and the low side pressure are measured and then coupled according to a pre-determined control strategy to optimize the coefficient of performance.
  • a drawback to prior vapor compression systems is that at least two sensors are needed to determine the optimal high side pressure.
  • both a temperature sensor and a pressure sensor are needed to determine that optimal high side pressure.
  • two pressure sensors are needed to determine the optimal high side pressure.
  • a transcritical vapor compression system includes a compressor, a gas cooler, an expansion device, and a condenser.
  • Refrigerant circulates through the closed circuit vapor compression system.
  • carbon dioxide is employed as the refrigerant.
  • High pressure refrigerant flowing through the gas cooler is cooled by a fluid, such as water, that flows in an opposing direction through a heat sink.
  • the refrigerant exits the gas cooler at a gas cooler exit temperature.
  • the high side pressure is independent of the operating conditions of the vapor compression system. Therefore, for any set of operating conditions, it is possible to operate the system at a wide range of high side pressures. However, there is an optimal high side pressure which corresponds to an optimal coefficient of performance.
  • the optimal high side pressure is dependent on the gas cooler exit temperature, regardless of the outdoor air temperature. For any gas cooler exit temperature, a single optimal high side pressure optimizes the coefficient of performance of the vapor compression system.
  • the dependence of the optimal high side pressure as a function of the gas cooler exit temperature is programmed into a control based on values obtained experimentally or obtained through a pre-determined model.
  • a sensor measures the gas cooler exit temperature. Based on the measured gas cooler exit temperature and the information programmed into the control, the optimal high side pressure is determined. The high side pressure is determined solely on the gas cooler exit temperature. The high side pressure is not sampled. The high side pressure is only changed based on the measured gas cooler exit temperature.
  • Figure 1 illustrates a schematic diagram of a transcritical vapor compression system of the present invention
  • Figure 2 illustrates a graph relating high side pressure to a coefficient of performance in the transcritical vapor compression system for a specific set of operating conditions
  • Figure 3 illustrates a graph relating a gas cooler exit temperature to an optimal high side pressure at various outdoor air temperatures
  • Figure 4 illustrates a flow chart of the method of the present invention.
  • Figure 1 illustrates a schematic diagram of a vapor compression system 20.
  • the vapor compression system 20 includes a compressor 22, a gas cooler 24, an expansion device 26, and an evaporator 28.
  • Refrigerant circulates though the closed circuit vapor compression system 20.
  • the refrigerant exits the compressor 22 at a high pressure and a high enthalpy and flows through the gas cooler 24 and loses heat, exiting the gas cooler 24 at a low enthalpy and a high pressure.
  • a fluid medium accepts heat from the refrigerant passing through the gas cooler 24.
  • the refrigerant then passes through the expansion device 26 and is expanded to a low pressure. After expansion, the refrigerant flows through the evaporator 28 and rejects heat to a fluid medium.
  • the refrigerant exits the evaporator 28 at a high enthalpy and a low pressure. The refrigerant then enters the compressor 22, completing the cycle.
  • carbon dioxide is used as the refrigerant. While carbon dioxide is described, other refrigerants may benefit from this invention. Because carbon dioxide has a low critical point, vapor compression systems utilizing carbon dioxide as the refrigerant usually run transcritically.
  • the high side pressure is independent of the operating conditions (such as the outdoor air temperature) of the vapor compression system 20. Therefore, for any set of operating conditions, it is possible to operate the vapor compression system 20 at many high side pressures. However, for any set of operating conditions, there is an optimal high side pressure which corresponds to an optimal coefficient of performance of the vapor compression system 20.
  • the coefficient of performance represents the efficiency of the vapor compression system 20.
  • the coefficient of performance equals the total useful heat transferred by the vapor compression system 20 divided by the work put into the vapor compression system 20 by system components, such as fans.
  • the high side pressure influences the coefficient of performance, and it is therefore important to regulate the high side pressure to optimize the coefficient of performance of the vapor compression system 20.
  • Figure 2 illustrates the relationship between the high side pressure of the vapor compression system 20 and the coefficient of performance at a given set of operating conditions.
  • one high side pressure corresponds to the optimum coefficient of performance.
  • the coefficient of performance varies between approximately 2.7 and 3.1 and reaches a maximum of approximately 3.1 at a high side pressure of approximately 1350 psia.
  • the optimal high side pressure of the vapor compression system depends strongly on the gas cooler exit temperature.
  • the gas cooler exit temperature is the temperature of the refrigerant exiting the gas cooler 24 and is measured by a sensor 30.
  • Figure 3 illustrates the relationship between the gas cooler exit temperature and the optimum high side pressure at various outdoor air temperatures.
  • the optimal high side pressure is independent of the outdoor air temperature.
  • the outdoor air temperature has an effect on the optimal high side pressure. Therefore, the optimal high side pressure is generally only a function of the gas cooler exit temperature.
  • Figure 4 illustrates a flowchart showing the method of determining the optimal high side pressure of the vapor compression system 20.
  • the dependence of the optimal high side pressure as a function of the gas cooler exit temperature (the heat sink temperature) is determined based on the performance of the compressor 22 and the gas cooler 24.
  • the dependence can be obtained either experimentally or through a pre-determined model.
  • the results of the previous testing or the pre-determined model are programmed into a control 32.
  • a correlation is constructed that relates the gas cooler exit temperature to the optimal high side pressure. This information generates the graph shown in Figure 3. An outdoor air temperature correction factor can also be included in the correlation if needed. This information is also programmed in the control 32.
  • the gas cooler exit temperature is then detected by the sensor 30.
  • the constructed correlation is then used to relate the gas cooler exit temperature detected by the sensor 30 to determine the optimal high side pressure that optimizes the coefficient of performance.
  • the constructed correlation is based solely on the gas cooler exit temperature and not on the pressure.
  • the sensor 30 detects the gas cooler exit temperature and provides this information to the control 32.
  • the control 32 uses the correlation to determine the optimal high side pressure based on the data preset into the control 32 and the detected gas cooler exit temperature. This approach is implemented using the linear relationship between the optimal high side pressure and the gas cooler exit temperature, as shown in Figure 3.
  • the optimal high side pressure is determined and selected independent of the outdoor air conditions.
  • the optimal high side pressure of the vapor compression system 20 is determined based solely on measured gas cooler exit temperature detected by the sensor 30.
  • the high side pressure is not sampled when determining the optimal high side pressure. Therefore, the efficiency and the capacity of the vapor compressor system 20 can be maximized when running in a heating mode.
  • control 32 determines that the gas cooler exit temperature measured by the sensor 30 changes, the control 32 uses the detected gas cooler exit temperature to determine the new optimal high side pressure based on the data programmed unto the control 32. The control 32 then determines the proper expansion device 26 setting and adjusts the expansion device 26 to change the high side pressure to the optimal high side pressure. The high side pressure is adjusted until the gas cooler exit temperature detected by the control is the optimal high side pressure. By determining the optimal high side pressure by measuring the gas cooler exit temperature with the sensor 30 and adjusting the expansion device 26 to maintain the optimal high side pressure, the optimum coefficient of performance can be maintained over a wide range of operating conditions.
  • the control 32 sends a signal to the expansion device 26 to open the expansion device 26 and allow more refrigerant to flow through the expansion device 26. This decreases the high side pressure.
  • the high side pressure is adjusted until the gas cooler exit temperature detected by the control 32 is the optimal high side pressure.
  • the control 32 sends a signal to the expansion device 26 to close the expansion device 26 and allow less refrigerant to flow through the expansion device 26. This increases the high side pressure.
  • the high side pressure is adjusted until the gas cooler exit temperature detected by the control 32 is the optimal high side pressure.
  • the sensor 30 detects the heat sink temperature to determine the optimal high side pressure to maximize the coefficient of performance. This is the temperature of the fluid in the gas cooler 24.
  • the fluid can be water or air.

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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)
  • Air-Conditioning For Vehicles (AREA)
  • Fuel Cell (AREA)

Abstract

The high side pressure of a vapor compression system is selected to optimize the coefficient of performance by measuring the gas cooler exit temperature with a temperature sensor. For any gas cooler exit temperature, a single optimal high side pressure optimizes the coefficient of performance. The optimal high side pressure for each gas cooler exit temperature is preset into a control and is based on data obtained by previous testing. A temperature sensor measures the gas cooler exit temperature. The control determines the optimal high side pressure based solely on the gas cooler exit temperature and the data preset into the control.

Description

METHOD FOR DETERMINING OPTIMAL COEFFICIENT
OF PERFORMANCE IN A TRANSCRITICAL
VAPOR COMPRESSION SYSTEM
BACKGROUND OF THE INVENTION
The present invention relates generally to a method for optimizing the coefficient of performance of a transcritical vapor compression system by detecting a gas cooler exit temperature and determining an optimal high side pressure of the vapor compression system based solely on the gas cooler exit temperature to optimize the coefficient of performance.
Carbon dioxide is an environmentally friendly refrigerant that is commonly used in transcritical vapor compression systems. Carbon dioxide has a low critical point, and most vapor compression systems utilizing carbon dioxide as the refrigerant run transcritically or partially above the critical point. The pressure of a subcritical fluid is a function of temperature under saturated conditions (when both liquid and vapor are present). However, when the temperature of the fluid is higher than the critical temperature (supercritical), the pressure becomes a function of the density of the fluid and is independent of the heat sink temperature. Therefore, for any set of heat sink conditions, it is possible to operate at many high side pressures. However, a maximum coefficient of performance exists that corresponds to one high side pressure. Therefore, it is important to regulate the high side pressure of the transcritical vapor compression system because the high side pressure has a large effect on the capacity and efficiency of the system.
In one prior vapor compression system, both the temperature and the pressure of the refrigerant at the outlet of the gas cooler is measured. From both these measurements, the optimal high side pressure is determined. The high side pressure is then adjusted to the optimal high side based on both these measurements according to a pre-determined control strategy to optimize the coefficient of performance. The optimal high side pressure is selected to optimize the capacity and efficiency of the vapor compression system for a cooling mode. In another prior vapor compression system, the high side pressure and the low side pressure are measured and then coupled according to a pre-determined control strategy to optimize the coefficient of performance.
A drawback to prior vapor compression systems is that at least two sensors are needed to determine the optimal high side pressure. In the first example, both a temperature sensor and a pressure sensor are needed to determine that optimal high side pressure. In the second example, two pressure sensors are needed to determine the optimal high side pressure.
There is a need for a method of optimizing the coefficient of performance of a vapor compression system that optimizes the capacity and efficiency during a heating mode, that uses only one sensor and that overcomes the drawbacks and shortcomings of the prior art.
SUMMARY OF THE INVENTION
A transcritical vapor compression system includes a compressor, a gas cooler, an expansion device, and a condenser. Refrigerant circulates through the closed circuit vapor compression system. Preferably, carbon dioxide is employed as the refrigerant. High pressure refrigerant flowing through the gas cooler is cooled by a fluid, such as water, that flows in an opposing direction through a heat sink. The refrigerant exits the gas cooler at a gas cooler exit temperature. In a transcritical vapor compression system, the high side pressure is independent of the operating conditions of the vapor compression system. Therefore, for any set of operating conditions, it is possible to operate the system at a wide range of high side pressures. However, there is an optimal high side pressure which corresponds to an optimal coefficient of performance. The optimal high side pressure is dependent on the gas cooler exit temperature, regardless of the outdoor air temperature. For any gas cooler exit temperature, a single optimal high side pressure optimizes the coefficient of performance of the vapor compression system.
The dependence of the optimal high side pressure as a function of the gas cooler exit temperature is programmed into a control based on values obtained experimentally or obtained through a pre-determined model. A sensor measures the gas cooler exit temperature. Based on the measured gas cooler exit temperature and the information programmed into the control, the optimal high side pressure is determined. The high side pressure is determined solely on the gas cooler exit temperature. The high side pressure is not sampled. The high side pressure is only changed based on the measured gas cooler exit temperature.
These and other features of the present invention will be best understood from the following specification and drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
The various features and advantages of the invention will become apparent to those skilled in the art from the following detailed description of the currently preferred embodiment. The drawings that accompany the detailed description can be briefly described as follows:
Figure 1 illustrates a schematic diagram of a transcritical vapor compression system of the present invention;
Figure 2 illustrates a graph relating high side pressure to a coefficient of performance in the transcritical vapor compression system for a specific set of operating conditions;
Figure 3 illustrates a graph relating a gas cooler exit temperature to an optimal high side pressure at various outdoor air temperatures; and
Figure 4 illustrates a flow chart of the method of the present invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
Figure 1 illustrates a schematic diagram of a vapor compression system 20.
The vapor compression system 20 includes a compressor 22, a gas cooler 24, an expansion device 26, and an evaporator 28. Refrigerant circulates though the closed circuit vapor compression system 20. The refrigerant exits the compressor 22 at a high pressure and a high enthalpy and flows through the gas cooler 24 and loses heat, exiting the gas cooler 24 at a low enthalpy and a high pressure. A fluid medium accepts heat from the refrigerant passing through the gas cooler 24. The refrigerant then passes through the expansion device 26 and is expanded to a low pressure. After expansion, the refrigerant flows through the evaporator 28 and rejects heat to a fluid medium. The refrigerant exits the evaporator 28 at a high enthalpy and a low pressure. The refrigerant then enters the compressor 22, completing the cycle.
Preferably, carbon dioxide is used as the refrigerant. While carbon dioxide is described, other refrigerants may benefit from this invention. Because carbon dioxide has a low critical point, vapor compression systems utilizing carbon dioxide as the refrigerant usually run transcritically.
In a transcritical vapor compression system 20, the high side pressure is independent of the operating conditions (such as the outdoor air temperature) of the vapor compression system 20. Therefore, for any set of operating conditions, it is possible to operate the vapor compression system 20 at many high side pressures. However, for any set of operating conditions, there is an optimal high side pressure which corresponds to an optimal coefficient of performance of the vapor compression system 20.
The coefficient of performance represents the efficiency of the vapor compression system 20. The coefficient of performance equals the total useful heat transferred by the vapor compression system 20 divided by the work put into the vapor compression system 20 by system components, such as fans. The high side pressure influences the coefficient of performance, and it is therefore important to regulate the high side pressure to optimize the coefficient of performance of the vapor compression system 20.
Figure 2 illustrates the relationship between the high side pressure of the vapor compression system 20 and the coefficient of performance at a given set of operating conditions. For the given set of operating conditions, one high side pressure (the optimal high side pressure) corresponds to the optimum coefficient of performance. In the illustrated example, the coefficient of performance varies between approximately 2.7 and 3.1 and reaches a maximum of approximately 3.1 at a high side pressure of approximately 1350 psia.
The optimal high side pressure of the vapor compression system depends strongly on the gas cooler exit temperature. The gas cooler exit temperature is the temperature of the refrigerant exiting the gas cooler 24 and is measured by a sensor 30. Figure 3 illustrates the relationship between the gas cooler exit temperature and the optimum high side pressure at various outdoor air temperatures. At gas cooler exit temperatures less than 100° F, the optimal high side pressure is independent of the outdoor air temperature. However, at gas cooler exit temperatures greater than 1000F, the outdoor air temperature has an effect on the optimal high side pressure. Therefore, the optimal high side pressure is generally only a function of the gas cooler exit temperature.
Figure 4 illustrates a flowchart showing the method of determining the optimal high side pressure of the vapor compression system 20. First, the dependence of the optimal high side pressure as a function of the gas cooler exit temperature (the heat sink temperature) is determined based on the performance of the compressor 22 and the gas cooler 24. The dependence can be obtained either experimentally or through a pre-determined model. The results of the previous testing or the pre-determined model are programmed into a control 32.
A correlation is constructed that relates the gas cooler exit temperature to the optimal high side pressure. This information generates the graph shown in Figure 3. An outdoor air temperature correction factor can also be included in the correlation if needed. This information is also programmed in the control 32.
The gas cooler exit temperature is then detected by the sensor 30. The constructed correlation is then used to relate the gas cooler exit temperature detected by the sensor 30 to determine the optimal high side pressure that optimizes the coefficient of performance. The constructed correlation is based solely on the gas cooler exit temperature and not on the pressure. The sensor 30 detects the gas cooler exit temperature and provides this information to the control 32. Based only on the gas cooler exit temperature detected by the sensor 30, the control 32 uses the correlation to determine the optimal high side pressure based on the data preset into the control 32 and the detected gas cooler exit temperature. This approach is implemented using the linear relationship between the optimal high side pressure and the gas cooler exit temperature, as shown in Figure 3. The optimal high side pressure is determined and selected independent of the outdoor air conditions. The optimal high side pressure of the vapor compression system 20 is determined based solely on measured gas cooler exit temperature detected by the sensor 30. The high side pressure is not sampled when determining the optimal high side pressure. Therefore, the efficiency and the capacity of the vapor compressor system 20 can be maximized when running in a heating mode.
If the control 32 determines that the gas cooler exit temperature measured by the sensor 30 changes, the control 32 uses the detected gas cooler exit temperature to determine the new optimal high side pressure based on the data programmed unto the control 32. The control 32 then determines the proper expansion device 26 setting and adjusts the expansion device 26 to change the high side pressure to the optimal high side pressure. The high side pressure is adjusted until the gas cooler exit temperature detected by the control is the optimal high side pressure. By determining the optimal high side pressure by measuring the gas cooler exit temperature with the sensor 30 and adjusting the expansion device 26 to maintain the optimal high side pressure, the optimum coefficient of performance can be maintained over a wide range of operating conditions.
If the high side pressure is above the optimal high side pressure, the control 32 sends a signal to the expansion device 26 to open the expansion device 26 and allow more refrigerant to flow through the expansion device 26. This decreases the high side pressure. The high side pressure is adjusted until the gas cooler exit temperature detected by the control 32 is the optimal high side pressure.
Alternately, if the high side pressure is below the optimal high side pressure, the control 32 sends a signal to the expansion device 26 to close the expansion device 26 and allow less refrigerant to flow through the expansion device 26. This increases the high side pressure. The high side pressure is adjusted until the gas cooler exit temperature detected by the control 32 is the optimal high side pressure.
Alternately, the sensor 30 detects the heat sink temperature to determine the optimal high side pressure to maximize the coefficient of performance. This is the temperature of the fluid in the gas cooler 24. The fluid can be water or air.
The foregoing description is only exemplary of the principles of the invention. Many modifications and variations of the present invention are possible in light of the above teachings. The preferred embodiments of this invention have been disclosed, however, so that one of ordinary skill in the art would recognize that certain modifications would come within the scope of this invention. It is, therefore, to be understood that within the scope of the appended claims, the invention may be practiced otherwise than as specially described. For that reason the following claims should be studied to determine the true scope and content of this invention.

Claims

1. A transcritical vapor compression system comprising: a compression device to compress a refrigerant to a high pressure; a gas cooler for cooling the refrigerant, and the refrigerant exits the gas cooler at a gas cooler exit temperature; an expansion device for reducing the refrigerant to a low pressure; an evaporator for evaporating the refrigerant; and a control to determine a desired high pressure of the refrigerant based solely on a characteristic indicative of the gas cooler exit temperature of the refrigerant and to adjust the high pressure to the desired high pressure.
2. The system as recited in claim 1 wherein the gas cooler exit temperature is measured by a temperature sensor.
3. The system as recited in claim 1 wherein the control adjusts the high pressure to the desired high pressure by adjusting the expansion device.
4. The system as recited in claiml wherein the desired high pressure corresponds to an optimal coefficient of performance.
5. The system as recited in claim 1 wherein the refrigerant is carbon dioxide.
6. The system as recited in claim 1 wherein the characteristic indicative of the gas cooler exit temperature is the gas cooler exit temperature.
7. The system as recited in claim 1 wherein the desired high pressure is determined based on preset data programmed in the control relating the desired high side pressure to the gas cooler exit temperature.
8. The system as recited in claim 1 wherein the desired high pressure is selected to optimize a capacity and an efficiency of the vapor compression system when operating in a heating mode.
9. A transcritical vapor compression system comprising: a compression device to compress a refrigerant to a high pressure; a gas cooler for cooling the refrigerant, and the refrigerant exits the gas cooler at a gas cooler exit temperature; an expansion device for reducing the refrigerant to a low pressure; an evaporator for evaporating the refrigerant; a temperature sensor for measuring the gas cooler exit temperature; and a control to determine a desired high pressure of the refrigerant based solely on a characteristic indicative of the gas cooler exit temperature of the refrigerant and to adjust the high pressure to the desired high pressure by adjusting the expansion device, wherein the desired high pressure corresponds to an optimal coefficient of performance.
10. The system as recited in claim 9 wherein the refrigerant is carbon dioxide.
11. The system as recited in claim 9 wherein the desired high pressure is determined based on preset data programmed in the control relating the desired high side pressure to the gas cooler exit temperature.
12. The system as recited in claim 9 wherein the desired high pressure is selected to optimize a capacity and an efficiency of the vapor compression system when operating in a heating mode.
13. A method of optimizing a coefficient of performance of a transcritical vapor compression system comprising the steps of: compressing a refrigerant to a high pressure; cooling the refrigerant in a gas cooler, and the refrigerant exits the gas cooler at a gas cooler exit temperature; expanding the refrigerant to a low pressure; evaporating the refrigerant; measuring a characteristic indicative of the gas cooler exit temperature of the refrigerant; determining a desired high pressure of the refrigerant based solely on the characteristic indicative of the gas cooler exit inlet temperature; and adjusting the high pressure to the desired high pressure.
14. The method as recited in claim 13 wherein the step of adjusting the high pressure includes adjusting a degree of expansion of an expansion device.
15. The method as recited in claim 13 wherein the refrigerant is carbon dioxide.
16. The method as recited in claim 13 wherein the characteristic indicative of the gas cooler exit temperature is the gas cooler exit temperature.
17. The method as recited in claim 13 further including the step of programming data relating the gas cooler exit temperature to the desired high pressure.
18. The method as recited in claim 13 wherein the desired high pressure corresponds to an optimal coefficient of performance.
19. The method as recited in claim 13, further including the step of optimizing a capacity and an efficiency of the vapor compression system when operating in a heating mode.
EP06735014.0A 2005-04-14 2006-02-14 Method of determining optimal coefficient of performance in a transcritical vapor compression system and a transcritical vapor compression system Not-in-force EP1869375B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US11/106,422 US20060230773A1 (en) 2005-04-14 2005-04-14 Method for determining optimal coefficient of performance in a transcritical vapor compression system
PCT/US2006/005158 WO2006112924A2 (en) 2005-04-14 2006-02-14 Method of determining optimal coefficient of performance in a transcritical vapor compression system

Publications (3)

Publication Number Publication Date
EP1869375A2 true EP1869375A2 (en) 2007-12-26
EP1869375A4 EP1869375A4 (en) 2010-09-01
EP1869375B1 EP1869375B1 (en) 2015-10-21

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US (1) US20060230773A1 (en)
EP (1) EP1869375B1 (en)
CN (1) CN101160496A (en)
CA (1) CA2597572A1 (en)
DK (1) DK1869375T3 (en)
WO (1) WO2006112924A2 (en)

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US20080223074A1 (en) * 2007-03-09 2008-09-18 Johnson Controls Technology Company Refrigeration system
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EP1869375A4 (en) 2010-09-01
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US20060230773A1 (en) 2006-10-19
CA2597572A1 (en) 2006-10-26
DK1869375T3 (en) 2015-12-14
WO2006112924A3 (en) 2007-09-20
EP1869375B1 (en) 2015-10-21

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