EP3477221B1 - Système de circulation de milieu thermique - Google Patents

Système de circulation de milieu thermique Download PDF

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Publication number
EP3477221B1
EP3477221B1 EP16906300.5A EP16906300A EP3477221B1 EP 3477221 B1 EP3477221 B1 EP 3477221B1 EP 16906300 A EP16906300 A EP 16906300A EP 3477221 B1 EP3477221 B1 EP 3477221B1
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EP
European Patent Office
Prior art keywords
water
heat medium
heat exchanger
flow rate
inlet
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.)
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Application number
EP16906300.5A
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German (de)
English (en)
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EP3477221A1 (fr
EP3477221A4 (fr
Inventor
Yoshio Yamano
Yasushi Okoshi
Takuya Ito
Takahito HIKONE
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP3477221A4 publication Critical patent/EP3477221A4/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/41—Defrosting; Preventing freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/46—Improving electric energy efficiency or saving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/85—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using variable-flow pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/64—Electronic processing using pre-stored data
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/10—Pressure
    • F24F2140/12—Heat-exchange fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/20—Heat-exchange fluid temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/50—Load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2203/00—Devices or apparatus used for air treatment
    • F24F2203/02—System or Device comprising a heat pump as a subsystem, e.g. combined with humidification/dehumidification, heating, natural energy or with hybrid system
    • F24F2203/021—Compression cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
    • F24F5/001—Compression cycle type

Definitions

  • the present invention relates to a heat medium cycle system including a refrigeration cycle circuit and a heat medium cycle circuit.
  • Examples of known heat medium cycle systems such as a water cycle air-conditioning system, include an air-conditioning system including a chilling unit, serving as a heat source.
  • an air-conditioning system is used in, for example, a building or a large commercial facility.
  • the air-conditioning system circulates water, serving as a heat medium, through a structure in such a manner that heat from the water is used for cooling or heating through a fan coil unit or an air handling unit, serving as a load-side device.
  • a plurality of chilling units are typically installed parallel to each other in a single water cycle circuit. Water through the water cycle circuit is circulated through the plurality of chilling units via header pipes.
  • the use of an inverter-driven compressor and an inverter-driven water circulating pump is effective in saving power.
  • To control inverters for the compressor and the water circulating pump the temperature of the water is measured and the optimum control for a load is performed on the basis of the measured water temperature.
  • the air-conditioning system including the plurality of chilling units, not only the inverters but also the number of chilling units that are being operated are controlled to achieve power saving.
  • An effective manner to save power includes adjusting the flow rate of the water through the chilling units on the basis of a load. For example, reducing the water flow rate is effective when the load is small, to reduce water sending power. However, when the water flowing through the chilling units is cold, a reduction in water flow rate may cause a water heat exchanger to freeze and break.
  • a known technique for protecting the water heat exchanger includes measuring the difference in water pressure between an inlet and an outlet of the water heat exchanger by using two water pressure sensors each provided at a corresponding one of the inlet and the outlet of the water heat exchanger, converting the pressure difference into a water flow rate, and keeping the compressor from being activated when the water flow rate has not reached a predetermined value (refer to Patent Literature 1, for example).
  • Patent Literature 1 discloses a heat medium cycle system that uses water pressure sensors only to inhibit a compressor from being operated when water in a water heat exchanger is frozen. Disadvantageously, the provided water pressure sensors are not effectively used for other purposes, and no consideration is given to preventing the water from freezing in the water heat exchanger. Once the water is frozen in the water heat exchanger, the heat medium cycle system inconveniently cannot be used until the frozen water is eliminated.
  • the present invention aims to overcome the above-described disadvantages and to provide a heat medium cycle system capable of being continuously operated while a heat medium is being prevented from freezing in a heat medium heat exchanger by using a pressure difference of the heat medium obtained from a measurement value of an inlet pressure sensor provided at an inlet of the heat medium heat exchanger and a measurement value of an outlet pressure sensor provided at an outlet of the heat medium heat exchanger.
  • a heat medium cycle system according to the present invention is as set forth in claim 1.
  • the controller under the first condition where the heat medium is to freeze in the heat medium heat exchanger, the controller obtains the minimum on-state flow rate at which the heat medium is kept from freezing in the heat medium heat exchanger, on the basis of the temperature of the heat medium at the heat medium inlet measured by the inlet temperature sensor and the evaporating temperature of the refrigerant detected by the evaporating temperature sensor. Then, the controller controls the pump in such a manner that the minimum on-state flow rate is maintained to make the pressure difference of the heat medium obtained from the measurement values of the input pressure sensor and the outlet pressure sensor into the minimum on-state pressure difference.
  • the pressure difference of the heat medium obtained from the measurement values of the inlet pressure sensor placed at the inlet of the heat medium heat exchanger and the outlet pressure sensor placed at the outlet of the heat medium heat exchanger is used to prevent the heat medium from freezing in the heat medium heat exchanger, thus preventing the heat medium cycle system from being stopped.
  • Fig. 1 is a schematic diagram illustrating an exemplary configuration of a water cycle air-conditioning system 100 according to Embodiment 1 of the present invention.
  • the water cycle air-conditioning system 100 will be described as an example of a heat medium cycle system according to the present invention.
  • the water cycle air-conditioning system 100 includes a chilling unit 1 and a water circuit 2 including the chilling unit 1.
  • the water circuit 2 corresponds to a heat medium cycle circuit in the present invention.
  • Water circulated through the water circuit 2 corresponds to a heat medium in the present invention.
  • the chilling unit 1 includes a refrigeration cycle circuit 10, a water circulating pump 3, and a controller 20, and constitutes part of the water circuit 2.
  • the refrigeration cycle circuit 10 includes a compressor 11, a heat-source-side heat exchanger 12, an expansion device 13, and a water heat exchanger 14 connected by pipes in such a manner that refrigerant is circulated through the refrigeration cycle circuit 10.
  • the compressor 11 compresses the refrigerant, serving as heat-source-side refrigerant, such as chlorofluorocarbon.
  • the compressor 11 is inverter-controlled by the controller 20.
  • the heat-source-side heat exchanger 12 exchanges heat between the refrigerant and air, such as outside air.
  • An air-sending fan 15 sending the air to the heat-source-side heat exchanger 12 is disposed next to the heat-source-side heat exchanger 12.
  • the air-sending fan 15 is inverter-controlled by the controller 20.
  • the expansion device 13 adjusts the pressure of the refrigerant. Opening and closing of the expansion device 13 is controlled by the controller 20.
  • a valve whose opening degree is adjustable for example, a linear expansion valve (LEV), can be used.
  • LEV linear expansion valve
  • the expansion device 13 include a capillary tube whose opening degree is fixed.
  • the water heat exchanger 14 exchanges heat between the refrigerant and water different from the refrigerant.
  • the water heat exchanger 14 cools the water circulated through the water circuit 2 to a target temperature by using heat from the refrigerant.
  • the water heat exchanger 14 corresponds to a heat medium heat exchanger in the present invention.
  • the water circuit 2 includes the chilling unit 1, a load-side heat exchanger 4, and a control valve 5 connected by pipes in such a manner that the water is circulated through the water circuit 2.
  • the water circulating pump 3 of the chilling unit 1 circulates the water for heat exchange in the water heat exchanger 14 through the water circuit 2.
  • the water circulating pump 3 is inverter-controlled by the controller 20.
  • a heat exchanger that cools indoor air in a structure by using the water circulated through the water circuit 2 is used.
  • the control valve 5 adjusts the flow rate of the water flowing through the load-side heat exchanger 4.
  • the opening degree of the control valve 5 is adjusted toward an open position or a closed position by the controller 20.
  • the controller 20 includes a microcomputer including a central processing unit (CPU), a read-only memory (ROM), a random access memory (RAM), and an input-output (I/O) port.
  • CPU central processing unit
  • ROM read-only memory
  • RAM random access memory
  • I/O input-output
  • the controller 20 is connected to various sensors by wired or wireless control signal lines 21 in such a manner that the controller can receive measurement values from the sensors.
  • the sensors include an inlet temperature sensor 22, an outlet temperature sensor 23, an inlet pressure sensor 24, an outlet pressure sensor 25, and a refrigerant temperature sensor 26.
  • the controller 20 is connected to the compressor 11, the air-sending fan 15, the expansion device 13, and the water circulating pump 3 by wired or wireless control signal lines 21 in such a manner that the controller can transmit operation instructions to these components.
  • the controller 20 stores a table from which a minimum on-state flow rate is obtained on the basis of the temperature of the water at a water inlet measured by the inlet temperature sensor 22 and the evaporating temperature of the refrigerant detected by the refrigerant temperature sensor 26.
  • the inlet temperature sensor 22 measures the temperature of the water at the water inlet of the water heat exchanger 14.
  • the outlet temperature sensor 23 measures the temperature of the water at a water outlet of the water heat exchanger 14.
  • the inlet pressure sensor 24 measures the pressure of the water at the water inlet of the water heat exchanger 14.
  • the outlet pressure sensor 25 measures the pressure of the water at the water outlet of the water heat exchanger 14.
  • the refrigerant temperature sensor 26 detects the evaporating temperature of the refrigerant in the water heat exchanger 14.
  • the refrigerant temperature sensor 26 corresponds to an evaporating temperature sensor in the present invention.
  • a refrigerant pressure sensor that measures the pressure of the refrigerant at a refrigerant outlet of the water heat exchanger 14 may be used.
  • the controller 20 calculates optimum operating conditions on the basis of measurement values of the inlet temperature sensor 22, the outlet temperature sensor 23, the inlet pressure sensor 24, and the outlet pressure sensor 25, and a detection value of the refrigerant temperature sensor 26. Furthermore, the controller 20 outputs operation instructions for the calculated optimum operating conditions to the compressor 11, the air-sending fan 15, the expansion device 13, and the water circulating pump 3, and controls these components.
  • the controller 20 is connected in communication with a remote control 6 by a wireless control signal line 27.
  • the controller 20 changes condition settings of the operating conditions in response to a user operation on the remote control 6, and enables the changed condition settings to be displayed on the remote control 6.
  • the controller 20 measures temperatures, which vary depending on the amount of heat required for the load-side heat exchanger 4, of the water circulated through the water circuit 2 by using the inlet temperature sensor 22 placed at the water inlet of the water heat exchanger 14 and the outlet temperature sensor 23 placed at the water outlet of the water heat exchanger 14. Then, the controller 20 calculates, on the basis of the measurement values of the inlet temperature sensor 22 and the outlet temperature sensor 23, the rotation frequency of the compressor 11, the rotation frequency of the air-sending fan 15, the opening degree of the expansion device 13, and the rotation frequency of the water circulating pump 3 for an optimum operating efficiency. The controller 20 transmits operation instructions based on the calculation results to the compressor 11, the air-sending fan 15, the expansion device 13, and the water circulating pump 3. The controller 20 controls the compressor 11, the air-sending fan 15, the expansion device 13, and the water circulating pump 3 so that the measurement value of the outlet temperature sensor 23 reaches a target water temperature.
  • a reduction in load during operation of the water cycle air-conditioning system 100 leads to a reduction in difference between the temperature of the water at the water outlet and that at the water inlet of the water heat exchanger 14. For this reason, the rotation frequency of the compressor 11, the rotation frequency of the air-sending fan 15, and the rotation frequency of the water circulating pump 3 are reduced.
  • a reduction in rotation frequency of the water circulating pump 3 results in a reduction in flow rate of the water through the water heat exchanger 14.
  • the water freezes in the water heat exchanger 14, possibly causing the water heat exchanger 14 to be broken.
  • the controller 20 can estimate the flow rate of the water through the water circuit 2 on the basis of a water pressure difference obtained from the measurement values of the inlet pressure sensor 24 and the outlet pressure sensor 25 by using Bernoulli's theorem. Consequently, under operating conditions where the temperature of the refrigerant is below freezing, that is, the water is to freeze in the water heat exchanger 14 of the chilling unit 1 in the water circuit 2, the controller 20 adjusts the rotation frequency of the water circulating pump 3 to maintain the minimum on-state flow rate of the water at which the water is kept from freezing in the water heat exchanger 14.
  • the controller 20 calculates the minimum on-state flow rate at which the water is kept from freezing in the water heat exchanger 14. Then, the controller 20 adjusts the rotation frequency of the water circulating pump 3 to maintain the minimum on-state flow rate in such a manner that the water pressure difference obtained from the measurement values of the inlet pressure sensor 24 and the outlet pressure sensor 25 is at a minimum on-state pressure difference.
  • the minimum on-state flow rate of the water at which the water is kept from freezing in the water heat exchanger 14 varies depending on the relationship between the evaporating temperature of the refrigerant and the temperature of the water at the water inlet of the water heat exchanger 14.
  • Fig. 2 is a characteristic graph showing the relationship between the refrigerant evaporating temperature, the inlet water temperature, and the minimum on-state flow rate of the water in Embodiment 1 of the present invention.
  • the controller 20 stores the table representing the relationship in the characteristic graph of Fig. 2 .
  • the controller 20 receives an inlet water temperature that is a measurement value of the inlet temperature sensor 22 and a refrigerant temperature that is a measurement value of the refrigerant temperature sensor 26, and applies the temperatures to the table in Fig. 2 , thus automatically calculating the minimum on-state flow rate. At high inlet water temperatures, therefore, the minimum on-state flow rate can be reduced, thus reducing the power consumption.
  • the minimum on-state flow rate obtained from the table in Fig. 2 is the flow rate maintained to keep the water from freezing in the water heat exchanger 14 even when the rotation frequency of the water circulating pump 3 can be further reduced under conditions where the load decreases and the opening degree of the control valve 5 adjusting the flow rate of the water flowing through the load-side heat exchanger 4 is adjusted toward the closed position.
  • the inlet temperature sensor 22 and the inlet pressure sensor 24 are arranged in the pipe adjacent to the water inlet of the water heat exchanger 14.
  • the outlet temperature sensor 23 and the outlet pressure sensor 25 are arranged in the pipe adjacent to the water outlet of the water heat exchanger 14.
  • the refrigerant temperature sensor 26 is disposed adjacent to a refrigerant passage in the water heat exchanger 14.
  • the controller 20 calculates optimum operating conditions from the measurement values of the inlet temperature sensor 22, the outlet temperature sensor 23, the inlet pressure sensor 24, and the outlet pressure sensor 25, and the detection value of the refrigerant temperature sensor 26 connected by the control signal lines 21.
  • the controller 20 transmits operation instructions based on the calculated optimum operating conditions to the compressor 11, the air-sending fan 15, the expansion device 13, and the water circulating pump 3.
  • the controller 20 controls the compressor 11, the air-sending fan 15, the expansion device 13, and the water circulating pump 3 so that the measurement value of the outlet temperature sensor 23 reaches the target water temperature.
  • the controller 20 calculates the minimum on-state flow rate at which the water is kept from freezing in the water heat exchanger 14. Then, the controller 20 adjusts the rotation frequency of the water circulating pump 3 to maintain the minimum on-state flow rate in such a manner that the water pressure difference obtained from the measurement values of the inlet pressure sensor 24 and the outlet pressure sensor 25 is at the minimum on-state pressure difference. Consequently, the minimum on-state flow rate at which the water is kept from freezing in the water heat exchanger 14 can be maintained, thus achieving high efficiency of the water cycle air-conditioning system 100. Furthermore, the water is prevented from freezing in the water heat exchanger 14. This operation enables the water cycle air-conditioning system 100 to be continuously operated, thus enhancing convenience.
  • Fig. 3 is a flowchart illustrating control for the water cycle air-conditioning system 100 according to Embodiment 1 of the present invention.
  • step S1 the controller 20 measures an outlet water temperature of the water heat exchanger 14 by using the outlet temperature sensor 23.
  • step S2 the controller 20 determines whether the measured outlet water temperature of the water heat exchanger 14 has reached a target water temperature. When the outlet water temperature has reached the target water temperature, the process proceeds to step S3. When the outlet water temperature has not reached the target water temperature, the process proceeds to step S4.
  • step S4 the controller 20 increases the rotation frequency of the compressor 11 and the rotation frequency of the air-sending fan 15. After step S4, the process returns to step S1.
  • step S3 the controller 20 determines whether the rotation frequency of the water circulating pump 3 can be reduced. Whether the rotation frequency of the water circulating pump 3 can be reduced is determined on the basis of, for example, determination on whether the difference between the outlet water temperature and an inlet water temperature of the water heat exchanger 14 is less than a set value.
  • the process proceeds to step S5.
  • the process returns to step S1.
  • step S5 the controller 20 reduces the rotation frequency of the water circulating pump 3.
  • step 5 may be taken under operating conditions where the temperature of the refrigerant is below freezing, that is, the water is to freeze in the water heat exchanger 14 of the water circuit 2.
  • the rotation frequency of the compressor 11 and that of the air-sending fan 15 can be reduced in addition to the rotation frequency of the water circulating pump 3.
  • the rotation frequency of the water circulating pump 3 is adjusted to maintain the minimum on-state flow rate.
  • the minimum on-state flow rate is automatically calculated by applying the inlet water temperature that is the measurement value of the inlet temperature sensor 22 and the refrigerant temperature that is the measurement value of the refrigerant temperature sensor 26 to the table in Fig. 2 .
  • the process proceeds step S6.
  • step S6 the controller 20 determines a water pressure difference between the pressure of the water inlet and that of the water outlet of the water heat exchanger 14.
  • This step in which the water pressure difference is obtained from the measurement values of the inlet pressure sensor 24 and the outlet pressure sensor 25, is taken to estimate the actual flow rate of the water through the water circuit 2 on the basis of the obtained water pressure difference by using Bernoulli's theorem.
  • the water pressure difference obtained in this step is the minimum on-state pressure difference at which the flow rate of the water through the water circulating pump 3 is at the minimum on-state flow rate.
  • step S7 the controller 20 determines whether the water flow rate estimated in step S6 meets the minimum on-state flow rate.
  • the minimum on-state flow rate is automatically calculated by applying the inlet water temperature that is the measurement value of the inlet temperature sensor 22 and the refrigerant temperature that is the measurement value of the refrigerant temperature sensor 26 to the table in Fig. 2 .
  • the controller 20 determines whether the water flow rate estimated in step S6 is greater than or equal to the calculated minimum on-state flow rate.
  • the process proceeds to step S8.
  • the process proceeds to step S9.
  • step S9 the controller 20 increases the rotation frequency of the water circulating pump 3, thus allowing the water flow rate to meet the minimum on-state flow rate. After step S9, the process returns to step S3.
  • step S8 the controller 20 maintains a state in which the water flow rate estimated in step S6 meets the minimum on-state flow rate. Consequently, even under conditions where the rotation frequency of the water circulating pump 3 is reduced and the water is to freeze in the water heat exchanger 14, the controller 20 adjusts the rotation frequency of the water circulating pump 3 to maintain the minimum on-state flow rate in such a manner that the water pressure difference is at the minimum on-state pressure difference. After step S8, the process terminates.
  • the water cycle air-conditioning system 100 includes the refrigeration cycle circuit 10, through which the refrigerant is circulated, including the compressor 11, the heat-source-side heat exchanger 12, the expansion device 13, and the water heat exchanger 14 connected by the pipes.
  • the water cycle air-conditioning system 100 includes the water circuit 2, through which the water is circulated, including the water circulating pump 3 circulating the water, the water heat exchanger 14, and the load-side heat exchanger 4 connected by the pipes.
  • the water cycle air-conditioning system 100 includes the inlet temperature sensor 22 measuring the temperature of the water at the water inlet of the water heat exchanger 14.
  • the water cycle air-conditioning system 100 includes the inlet pressure sensor 24 measuring the pressure of the water at the water inlet of the water heat exchanger 14.
  • the water cycle air-conditioning system 100 includes the outlet pressure sensor 25 measuring the pressure of the water at the water outlet of the water heat exchanger 14.
  • the water cycle air-conditioning system 100 includes the refrigerant temperature sensor 26 detecting the evaporating temperature of the refrigerant in the water heat exchanger 14.
  • the water cycle air-conditioning system 100 includes the controller 20, which obtains the minimum on-state flow rate at which the water is kept from freezing in the water heat exchanger 14, on the basis of the water temperature at the water inlet measured by the inlet temperature sensor 22 and the refrigerant evaporating temperature detected by the refrigerant temperature sensor 26 under conditions where the water is to freeze in the water heat exchanger 14.
  • the controller 20 controls the water circulating pump 3 in such a manner that the minimum on-state flow rate is maintained to make the water pressure difference obtained from the measurement values of the inlet pressure sensor 24 and the outlet pressure sensor 25 into the minimum on-state pressure difference.
  • the above-described configuration prevents the water from freezing in the water heat exchanger 14 by using the water pressure difference obtained from the measurement values of the inlet pressure sensor 24 placed at the water inlet of the water heat exchanger 14 and the outlet pressure sensor 25 placed at the water outlet of the water heat exchanger 14, thus preventing the water cycle air-conditioning system 100 from being stopped. Furthermore, the water heat exchanger 14 can be prevented from being broken by freezing of the water in the water heat exchanger 14.
  • the controller 20 controls the water circulating pump 3 in such a manner that the minimum on-state flow rate is maintained. Consequently, an excess of power for driving the water circulating pump 3 can be reduced, thus reducing the power consumption. This operation achieves high efficiency of the water cycle air-conditioning system 100.
  • Embodiment 1 in the case where the load decreases and the opening degree of the control valve 5 adjusting the flow rate of the water flowing through the load-side heat exchanger 4 is adjusted toward the closed position, the controller 20 controls the water circulating pump 3 in such a manner that the minimum on-state flow rate is maintained.
  • the controller 20 has the table from which the minimum on-state flow rate is obtained on the basis of the water temperature at the water inlet measured by the inlet temperature sensor 22 and the refrigerant evaporating temperature detected by the refrigerant temperature sensor 26.
  • the controller 20 obtains the minimum on-state flow rate by using the table.
  • Such a configuration enables the controller 20 to automatically obtain the minimum on-state flow rate from the table in Fig. 2 on the basis of the inlet water temperature at the water inlet measured by the inlet temperature sensor 22 and the refrigerant evaporating temperature detected by the refrigerant temperature sensor 26, thus achieving high efficiency of the water cycle air-conditioning system 100.
  • Fig. 4 is a schematic diagram illustrating an exemplary configuration of a water cycle air-conditioning system 200 according to Embodiment 2 of the present invention.
  • Embodiment 2 a description of the same components as those in Embodiment 1 is omitted. The following description will focus on differences between Embodiment 1 and Embodiment 2.
  • the water circuit 2 of the water cycle air-conditioning system 200 includes a plurality of chilling units 1, each including the refrigeration cycle circuit 10 and the water circulating pump 3, arranged in parallel to the load-side heat exchanger 4.
  • the plurality of chilling units 1 each have the configuration described in Embodiment 1.
  • each chilling unit 1 includes the refrigeration cycle circuit 10 and the water circulating pump 3 and constitutes part of the water circuit 2.
  • a water outlet pipe extending from the chilling unit 1 has no check valve.
  • the number of chilling units 1 is controlled on the basis of the amount of heat required for the load-side heat exchanger 4 in such a manner that one or more chilling units 1 can be stopped.
  • Embodiment 2 in a case where the compressor 11 is stopped in a corresponding one or more chilling units 1 of the plurality of chilling units 1, under conditions where the water is to flow in the direction opposite to the water sending direction, that is, the measurement value of the outlet pressure sensor 25 is greater than the measurement value of the inlet pressure sensor 24, the controller 20 of each of the corresponding one or more chilling units 1 calculates a minimum off-state flow rate at which the water is kept from flowing in the opposite direction, on the basis of a water pressure difference obtained from measurement values of the inlet pressure sensor 24 and the outlet pressure sensor 25.
  • each chilling unit 1 in which the compressor 11 is stopped would also be stopped in a traditional configuration.
  • the water circulating pump 3 is slightly operated to maintain the minimum off-state flow rate at which the water is kept from flowing in the opposite direction. This configuration enables omission of a check valve that prevents the water from flowing in the opposite direction.
  • the minimum off-state flow rate ensures that the water is kept from freezing in the water heat exchanger 14, similar to the minimum on-state flow rate in Embodiment 1.
  • the minimum off-state flow rate is a flow rate of greater than 0 at which only heat generated by operating the water circulating pump 3 is rejected.
  • the water circuit 2 includes the plurality of chilling units 1, each including the refrigeration cycle circuit 10 and the water circulating pump 3, arranged in parallel to the load-side heat exchanger 4.
  • the controller 20 of each of the corresponding one or more chilling units 1 obtains the minimum off-state flow rate at which the water is kept from flowing in the opposite direction, on the basis of the water pressure difference obtained from the measurement values of the inlet pressure sensor 24 and the outlet pressure sensor 25. Then, the controller 20 of each of the corresponding one or more chilling units 1, in each of which the compressor 11 is stopped, controls the water circulating pump 3 in such a manner that the minimum off-state flow rate is maintained.
  • Such a configuration prevents the water through the water circuit 2 from flowing in the opposite direction and thus enables omission of check valves.
  • the minimum off-state flow rate ensures that the water is kept from freezing in the water heat exchanger 14, similar to the minimum on-state flow rate. This operation prevents the water from freezing in the water heat exchanger 14, thus preventing the water cycle air-conditioning system 200 from being stopped. Furthermore, the water heat exchanger 14 can be prevented from being broken by freezing of the water in the water heat exchanger 14.
  • the minimum off-state flow rate is a flow rate of greater than 0 at which only heat generated by operating the water circulating pump 3 is rejected.
  • the minimum off-state flow rate at which the water is kept from flowing in the opposite direction can be calculated, and the water circulating pump 3 can be slightly operated in such a manner that the water does not flow in the direction opposite to the water sending direction in which the water circulating pump 3 sends the water, thus reducing the power consumption.
  • heat generated by the water circulating pump 3 that is being operated can be cooled.
  • the water cycle air-conditioning systems 100 and 200 have been described as examples.
  • the water cycle air-conditioning systems 100 and 200 include one or more chilling units 1 of an air heat source type that includes the water heat exchanger 14 for cooling the water to a target temperature by using heat from the heat-source-side refrigerant, such as chlorofluorocarbon.
  • Other applications include a water cycle air-conditioning system including, as a heat source, a chilling unit of a water heat source type in which a heat-source-side heat exchanger exchanges heat between water and heat-source-side refrigerant.
  • the water cycle air-conditioning system may include a four-way valve provided in the refrigeration cycle circuit so that heat from the heat-source-side refrigerant, such as chlorofluorocarbon, can be used not only to cool the water to a target temperature but also to heat the water to a target temperature.
  • the heat medium brine may be used instead of the water circulated through the water circuit.
  • Applications of the heat medium cycle system according to the present invention include systems through which the heat medium is circulated, including water cycle air-conditioning systems.
  • chilling unit 2 water circuit 3 water circulating pump 4 load-side heat exchanger 5 control valve 6 remote control 10 refrigeration cycle circuit 11 compressor 12 heat-source-side heat exchanger 13 expansion device 14 water heat exchanger 15 air-sending fan 20 controller 21 control signal line 22 inlet temperature sensor 23 outlet temperature sensor 24 inlet pressure sensor 25 outlet pressure sensor 26 refrigerant temperature sensor 27 control signal line 100 water cycle air-conditioning system 200 water cycle air-conditioning system

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Claims (5)

  1. Système de cycle de milieu thermique (100), comprenant :
    un circuit de cycle de réfrigération (10) à travers lequel du réfrigérant est mis en circulation, le circuit de cycle de réfrigération (10) comprenant un compresseur (11), un échangeur de chaleur côté source de chaleur (12), un dispositif de détente (13) et un échangeur de chaleur à milieu thermique (14) reliés par des tuyaux ;
    un circuit de cycle de milieu thermique (2) à travers lequel un milieu thermique est mis en circulation, le circuit de cycle de milieu thermique (2) comprenant une pompe (3) faisant circuler le milieu thermique, l'échangeur de chaleur à milieu thermique (14) et un échangeur de chaleur côté charge (4) reliés par des tuyaux ;
    un capteur de température d'entrée (22) configuré pour mesurer une température du milieu thermique au niveau d'une entrée de milieu thermique de l'échangeur de chaleur à milieu thermique (14) ;
    un capteur de pression d'entrée (24) configuré pour mesurer une pression du milieu thermique au niveau de l'entrée de milieu thermique de l'échangeur de chaleur à milieu thermique (14) ;
    un capteur de pression de sortie (25) configuré pour mesurer une pression du milieu thermique au niveau d'une sortie de milieu thermique de l'échangeur de chaleur à milieu thermique (14) ;
    un capteur de température d'évaporation (26) configuré pour détecter une température d'évaporation du réfrigérant dans l'échangeur de chaleur à milieu thermique (14) ; et
    un dispositif de commande (20) ; caractérisé en ce que
    le dispositif de commande (20) est configuré pour, dans une première condition dans laquelle le milieu thermique doit geler dans l'échangeur de chaleur (14), obtenir un débit d'écoulement minimum à l'état de marche auquel le milieu thermique est empêché de geler sous l'effet dans l'échangeur de chaleur à milieu thermique (14), sur la base de la température du milieu thermique à l'entrée de milieu thermique mesurée par le capteur de température d'entrée (22) et de la température d'évaporation du réfrigérant détectée par le capteur de température d'évaporation (26), et pour commander la pompe (3) de telle manière qu'un débit d'écoulement du milieu thermique estimé sur la base d'une différence de pression du milieu thermique obtenue à partir d'une valeur de mesure du capteur de pression d'entrée (24) et d'une valeur de mesure du capteur de pression de sortie (25) soit supérieur ou égal au débit d'écoulement minimum à l'état de marche.
  2. Système de cycle de milieu thermique (100) selon la revendication 1, dans lequel le dispositif de commande (20) est configuré pour commander la pompe (3) de telle manière que le débit d'écoulement minimum à l'état de marche soit maintenu dans un cas où une charge diminue et un degré d'ouverture d'une vanne de commande (5) configurée pour ajuster un débit d'écoulement du milieu thermique circulant à travers l'échangeur de chaleur côté charge (4) est ajusté dans une position fermée.
  3. Système de cycle de milieu thermique (100) selon l'une quelconque des revendications 1 à 2, dans lequel le dispositif de commande (20) a une table à partir de laquelle le débit d'écoulement minimum à l'état de marche est obtenu sur la base de la température du milieu thermique au niveau de l'entrée de milieu thermique mesurée par le capteur de température d'entrée (22) et de la température d'évaporation du réfrigérant détectée par le capteur de température d'évaporation (26), et est configuré pour obtenir le débit d'écoulement minimum à l'état de marche en utilisant la table.
  4. Système de cycle de milieu thermique (200) selon l'une quelconque des revendications 1 à 3,
    dans lequel le circuit de cycle de milieu thermique (2) comprend une pluralité d'unités de refroidissement (1) comprenant chacune le circuit de cycle de réfrigération (10) et la pompe (3), et la pluralité d'unités de refroidissement (1) est disposée parallèlement à l'échangeur de chaleur côté charge (4), et
    dans lequel, dans un cas où le compresseur (11) est arrêté dans une ou plusieurs unités de refroidissement correspondantes (1) de la pluralité d'unités de refroidissement (1), dans une seconde condition où le milieu thermique doit s'écouler dans une direction opposée à une direction d'envoi de milieu thermique dans laquelle la pompe (3) envoie le milieu thermique, le dispositif de commande (20) de chacune des une ou plusieurs unités de refroidissement correspondantes (1) est configuré pour obtenir un débit d'écoulement minimum à l'état d'arrêt dans lequel le milieu thermique est empêché de s'écouler dans la direction opposée à la direction d'envoi de milieu thermique, sur la base de la différence de pression du milieu thermique obtenue à partir de la valeur de mesure du capteur de pression d'entrée (24) et de la valeur de mesure du capteur de pression de sortie (25), et commander la pompe (3) de manière à maintenir le débit d'écoulement minimum à l'état d'arrêt.
  5. Système de cycle de milieu thermique (200) selon la revendication 4, dans lequel le débit d'écoulement à l'état d'arrêt est un débit d'écoulement supérieur à 0 auquel seule de la chaleur générée par le fonctionnement de la pompe (3) est rejetée.
EP16906300.5A 2016-06-23 2016-06-23 Système de circulation de milieu thermique Active EP3477221B1 (fr)

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JPWO2017221383A1 (ja) 2019-01-31
WO2017221383A1 (fr) 2017-12-28
EP3477221A1 (fr) 2019-05-01
EP3477221A4 (fr) 2019-07-24

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