EP2693136A1 - Dispositif de commande de détendeur, machine de source de chaleur, et procédé de commande de détendeur - Google Patents

Dispositif de commande de détendeur, machine de source de chaleur, et procédé de commande de détendeur Download PDF

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Publication number
EP2693136A1
EP2693136A1 EP12764195.9A EP12764195A EP2693136A1 EP 2693136 A1 EP2693136 A1 EP 2693136A1 EP 12764195 A EP12764195 A EP 12764195A EP 2693136 A1 EP2693136 A1 EP 2693136A1
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EP
European Patent Office
Prior art keywords
degree
refrigerant
expansion valve
opening
expansion
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Withdrawn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
EP12764195.9A
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German (de)
English (en)
Inventor
Hitoi Ono
Kenji Ueda
Noriyuki Matsukura
Minoru Matsuo
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP2693136A1 publication Critical patent/EP2693136A1/fr
Withdrawn legal-status Critical Current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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2515—Flow valves

Definitions

  • the present invention relates to an expansion-valve control device, a heat-source unit, and an expansion-valve control method.
  • a heat-source unit for example, a refrigerator
  • an expansion valve for expanding a high-temperature, high-pressure refrigerant that has been condensed at a condenser after being compressed at a compressor in order to make it low-temperature, low pressure refrigerant.
  • the expansion valve needs to be held at an appropriate degree-of-opening in accordance with the load and external conditions.
  • the degree-of-opening of the expansion valve is too large, the flow volume of the refrigerant becomes excessive, and thus, it is possible that the coefficient of performance (COP (coefficient of performance)) deteriorates as a result of the motive power of the refrigerator becoming excessive, that so-called liquid back occurs, in which the compressor draws in liquid-phase refrigerant, and that gas bypass occurs, in which a portion of the refrigerant flows into an evaporator in the gas phase without being turned into the liquid phase in a condenser due to insufficient supercooling at the condenser.
  • COP coefficient of performance
  • Patent Literature 1 discloses a technique in which a turbo refrigerator is provided with a control device that controls the degree-of-opening of an expansion valve so that the degree of intake superheating achieves a predetermined target degree of superheating, and the control device changes the target degree of superheating so as to be decreased when the intake flow volume of refrigerant steam for a turbo compressor is changed so as to be increased and changes the target degree of superheating so as to be increased when the intake flow volume of the refrigerant steam therefor is changed so as to be decreased.
  • Patent Literature 2 discloses a technique in which a control portion in an air conditioner has, for individual times in the day, a predicted degree-of-opening that is calculated from set conditions set in accordance with the load connected to a condenser, a current degree-of-opening that is calculated from current conditions, and a command degree-of-opening that is calculated based on both the predicted degree-of-opening and the current degree-of-opening and that is given to an expansion valve, and, when the predicted degree-of-opening changes suddenly or stepwise during the heat-pump operation, the control portion gives a degree-of-opening that is smaller than the predicted degree-of-opening to the expansion valve as a command degree-of-opening.
  • the degree of superheating for the refrigerant to be taken into the compressor is calculated from the temperature and pressure of the refrigerant to be taken into the compressor, the target degree of superheating is calculated from a set value of the degree-of-opening of a vane that controls the outlet temperature of cold water, and the expansion valve is feedback-controlled so that the degree of superheating achieves the target degree of superheating.
  • Patent Literature 1 controls the expansion valve solely by the feedback control that utilizes only the output information of the refrigerator, such as the outlet temperature of cold water, the temperature and pressure of the refrigerant, and so forth, tracking performance thereof has been insufficient with respect to fluctuations in the load on the refrigerator, such as the inlet temperature of cold water, the flow volume of cold water, and so forth, and external conditions, such as the inlet temperature of cooling water, the flow volume of cooling water, and so forth.
  • Patent Literature 2 if there are deviations between the specification of actual machinery and parameters set in advance, such as a calculation formula, set conditions, and so forth, for calculating the degree-of-opening, the expansion valve cannot be held at an appropriate degree-of-opening, and thus, the deterioration of the COP cannot be avoided.
  • the present invention has been conceived in light of the above-described circumstances, and an object thereof is to provide an expansion-valve control device, a heat-source unit, and an expansion-valve control method with which the degree-of-opening of an expansion valve can be set to an appropriate degree-of-opening regardless of a load and external conditions for a heat-source unit.
  • an expansion-valve control device In order to solve the above-described problems, an expansion-valve control device, a heat-source unit, and an expansion-valve control method according to the present invention employ the following solutions.
  • an expansion-valve control device is an expansion-valve control device that, in a heat-source unit including a compressor that compresses a refrigerant, a condenser that condenses a compressed refrigerant by means of a heat-source medium, an evaporator that evaporates a condensed refrigerant and also performs heat exchange between this refrigerant and a heating medium, and an expansion valve that causes a liquid-phase refrigerant retained in the condenser to expand, controls a degree-of-opening of the expansion valve, the expansion-valve control device including a first calculating portion that calculates a degree-of-opening of the expansion valve based on the difference between a target value of a degree of superheating for the refrigerant to be taken into the compressor and a measured value of the degree of superheating; a second calculating portion that calculates a degree-of-opening of the expansion valve based on an estimated value of a
  • the expansion-valve control device controls the degree-of-opening of the expansion valve in the heat-source unit that is provided with the compressor that compresses the refrigerant, the condenser that condenses the compressed refrigerant by means of the heat-source medium, the evaporator that evaporates the condensed refrigerant and also performs heat exchange between this refrigerant and the heating medium, and the expansion valve that causes the liquid-phase refrigerant retained in the condenser to expand.
  • the degree-of-opening of the expansion valve is calculated by the first calculating portion based on the difference between the target value of the degree of superheating of the refrigerant that is taken into the compressor and the measured value of the degree of superheating.
  • the degree-of-opening of the expansion valve is calculated by the second calculating portion based on the estimated value of the flow volume of the refrigerant that is allowed to pass through the expansion valve.
  • the first calculating portion performs feedback control for the degree-of-opening of the expansion valve based on the degree of superheating which tends to change in accordance with the load and external conditions for the heat-source unit
  • the second calculating portion performs feedforward control for the degree-of-opening of the expansion valve based on the estimated value of flow volume of the refrigerant which tends to change in accordance with the load and external conditions for the heat-source unit.
  • the command-value calculating portion calculates the command value for controlling the degree-of-opening of the expansion valve from the degree-of-opening of the expansion valve calculated by the first calculating portion and the degree-of-opening of the expansion valve calculated by the second calculating portion.
  • the degree-of-opening of the expansion valve is controlled by means of feedback control, which maintains the stability thereof, and also by using, in combination therewith, feedforward control in which the input information for the heat-source unit is utilized, the degree-of-opening of the expansion valve can be set to an appropriate degree-of-opening regardless of the load and external conditions for the heat-source unit.
  • the target value of the degree of superheating may be calculated based on the temperature of the heating medium that flows into the evaporator.
  • the temperature of the heating medium that flows into the evaporator is related to the load on the heat-source unit. Accordingly, with the first aspect described above, because the target value of the degree of superheating is calculated based on the temperature of the heating medium that flows into the evaporator, effective feedback control can be performed to control the degree-of-opening of the expansion valve.
  • the target value of the degree of superheating may be calculated so as to take a greater value with a decrease in the temperature of the heating medium that flows into the evaporator.
  • the degree of superheating is low, the possibility of the compressor drawing in the liquid-phase refrigerant increases; however, if the temperature difference between the heating medium and the refrigerant that flow into the evaporator is small, it is difficult to increase the degree of superheating.
  • the target value of the degree of superheating is calculated so as to take a greater value with a decrease in the temperature of the heating medium that flows into the evaporator, it is possible to prevent the liquid-phase refrigerant from being drawn into the compressor (liquid back).
  • the flow volume may be calculated based on at least one of the temperature of the heating medium that flows into the evaporator and the temperature of the heat-source medium that flows into the condenser.
  • the flow volume of the refrigerant that is allowed to pass through the expansion valve changes depending on the load and external conditions for the heat-source unit, that is, the temperature of the heating medium that flows into the evaporator and the temperature of the heat-source medium that flows into the condenser. Accordingly, with the first aspect described above, because this flow volume is calculated based on at least one of the temperature of the heating medium that flows into the evaporator and the temperature of the heat-source medium that flows into the condenser, effective feedforward control can be performed to control the degree-of-opening of the expansion valve.
  • the flow volume may be calculated so as to take a smaller value with a decrease in the temperature of the heating medium that flows into the evaporator and so as to take a greater value with a decrease in the temperature of the heat-source medium that flows into the condenser.
  • the case in which the temperature of the heating medium that flows into the evaporator is decreased is a case in which the load on the heat-source unit is decreased, and thus, the flow volume of the refrigerant can be decreased.
  • the flow volume of the refrigerant needs to be increased by increasing the degree-of-opening of the expansion valve, because the internal pressure of the condenser is decreased when the temperature of the heat-source medium that flows into the condenser is decreased, which decreases the pressure on the upstream side of the expansion valve, thus decreasing the degree of supercooling (increasing the specific volume).
  • the flow volume of the refrigerant that is allowed to pass through the expansion valve is calculated so as to take a smaller value with a decrease in the temperature of the heating medium that flows into the evaporator and so as to take a greater value with a decrease in the temperature of the heat-source medium that flows into the condenser, it is possible to increase the precision of the feedforward control for the degree-of-opening of the expansion valve.
  • the heat-source unit may be provided with a bypass pipe that forms a bypass path between a refrigerant intake port of the compressor and a refrigerant exhaust port of the compressor; and the measured value of the degree of superheating may be calculated based on the temperature of the heating medium that has flowed out from the evaporator and the pressure of the refrigerant to be compressed at the compressor.
  • the heat-source unit by providing the heat-source unit with the bypass pipe that forms a bypass path between the refrigerant intake port of the compressor and the refrigerant exhaust port of the compressor, the refrigerant in which the gas-phase refrigerant at the outlet of the compressor and the gas-phase refrigerant at the outlet of the evaporator are mixed is taken into the compressor. Because of this, if the temperature of the refrigerant to be compressed at the compressor is used to measure the degree of superheating, the temperature of the above-described mixed refrigerant, that is, a temperature differing from the temperature of the refrigerant at the outlet of the evaporator, would be used, and thus, the degree of superheating would not be measured correctly.
  • the temperature of the refrigerant at the outlet of the evaporator and the temperature of the heating medium that has flowed out of the evaporator are assumed to be equivalent, and the measured value of the degree of superheating is calculated based on the temperature of the heating medium that has flowed out of the evaporator and the pressure of the refrigerant to be compressed at the compressor; therefore, even though the heat-source unit is provided with the bypass pipe, the degree of superheating can be measured with high precision.
  • a heat-source unit is provided with a compressor that compresses a refrigerant; a condenser that condenses a compressed refrigerant by means of a heat-source medium; an evaporator that evaporates a condensed refrigerant and also performs heat exchange between this refrigerant and a heating medium; an expansion valve that causes a liquid-phase refrigerant retained in the condenser to expand; and the above-described expansion-valve control device.
  • an expansion-valve control method is an expansion-valve control method of controlling, in a heat-source unit including a compressor that compresses a refrigerant, a condenser that condenses a compressed refrigerant by means of a heat-source medium, an evaporator that evaporates a condensed refrigerant and also performs heat exchange between this refrigerant and a heating medium, and an expansion valve that causes a liquid-phase refrigerant retained in the condenser to expand, a degree-of-opening of the expansion valve, the expansion-valve control method including a first step of calculating a degree-of-opening of the expansion valve based on the difference between a target value of a degree of superheating for the refrigerant to be taken into the compressor and a measured value of the degree of superheating; a second step of calculating a degree-of-opening of the expansion valve based on an estimated value of a flow volume of the ref
  • the present invention affords an excellent advantage in that the degree-of-opening of an expansion valve can be set to an appropriate degree-of-opening regardless of the load and external conditions for a heat-source unit.
  • Fig. 1 shows the configuration of a turbo refrigerator 10, which is an example of a heat-source unit according to the first embodiment.
  • the turbo refrigerator 10 is provided with a turbo compressor 12 that compresses refrigerant; a condenser 14 that, by means of cooling water serving as heat-source medium, condenses gas-phase refrigerant (gaseous refrigerant) compressed at the turbo compressor 12 into liquid-phase refrigerant (liquid refrigerant; an evaporator 16 that evaporates the refrigerant condensed at the condenser 14 and also performs heat exchange between this refrigerant and cold water serving as heating medium; and an expansion valve 18 that causes the liquid refrigerant retained in the condenser 14 to expand.
  • a turbo compressor 12 that compresses refrigerant
  • a condenser 14 that, by means of cooling water serving as heat-source medium, condenses gas-phase refrigerant (gaseous refrigerant) compressed at the turbo compressor 12 into liquid-phase refrigerant (liquid refrigerant
  • an evaporator 16 that evaporates the refrigerant condensed at the condenser 14 and
  • the turbo compressor 12 is, as an example, a centrifugal two-stage compressor, and is driven by an electric motor.
  • a compressor inlet vane 20 IGV that controls the flow volume of the refrigerant to be taken thereinto is provided, thus enabling capacity control for the turbo compressor 12.
  • the refrigerant intake port of the turbo compressor 12 is provided with a compressor-intake-temperature measuring portion 22 that measures the temperature of refrigerant to be compressed (hereinafter, referred to as "compressor-intake temperature”) and a compressor-intake-pressure measuring portion 24 that measures the pressure of the refrigerant to be compressed (hereinafter, referred to as "compressor-intake pressure").
  • a cooling heat-transmitting pipe 26 in which the cooling water flows is inserted into the condenser 14.
  • the temperature of the cooling water that flows into the condenser 14 (hereinafter, referred to as “cooling-water inlet temperature”) is measured by a cooling-water-inlet-temperature measuring portion 28, and the temperature of the cooling water that flows out of the condenser 14 (hereinafter, referred to as “cooling-water outlet temperature ”) is measured by a cooling-water-outlet-temperature measuring portion 30. Note that the cooling water that has flowed out of the condenser 14 is guided to the condenser 14 again after externally exhausting the heat thereof at a cooling tower (not shown).
  • a cold-water heat-transmitting pipe 32 for cooling, by means of the refrigerant, the cold water to be supplied to an external load is inserted into the evaporator 16.
  • the temperature of the cold water that flows into the evaporator 16 (hereinafter referred to as "cold-water inlet temperature”) is measured by a cold-water-inlet-temperature measuring portion 34 and the temperature of the cold water that flows out of the evaporator 16 (hereinafter, referred to as "cold-water outlet temperature”) is measured by a cold-water-outlet-temperature measuring portion 36.
  • turbo compressor 12 is provided with a control device 40 that performs overall control of the turbo compressor 12.
  • the control device 40 is provided with a vane degree-of-opening control portion 42 that controls the degree-of-opening of the compressor inlet vane 20 and an expansion-valve degree-of-opening control portion 44 that controls the degree-of-opening of the expansion valve 18.
  • the vane degree-of-opening control portion 42 calculates a command value for controlling the degree-of-opening of the compressor inlet vane 20 (hereinafter, referred to as "vane degree-of-opening command value") by means of feedback control based on the cold-water outlet temperature.
  • the expansion-valve degree-of-opening control portion 44 calculates the degree-of-opening of the expansion valve 18 based on the difference between a target value of the degree of superheating for the refrigerant that is taken into the turbo compressor 12 and the measured value of the degree of superheating thereof, and calculates the degree-of-opening of the expansion valve 18 based on a planned CV value, which is an estimated value of the flow volume of the refrigerant that is allowed to pass through the expansion valve 18.
  • expansion-valve degree-of-opening control portion 44 calculates a command value for controlling the degree-of-opening of the expansion valve 18 (hereinafter, referred to as "expansion-valve degree-of-opening command value") from the above-described two types of degree-of-opening calculated for the expansion valve 18.
  • the expansion-valve degree-of-opening control portion 44 performs feedback control for the degree-of-opening of the expansion valve 18 based on the degree of superheating which tends to change in accordance with the load and external conditions for the turbo refrigerator 10, and performs feedforward control therefor based on the planned CV value, that is, an estimated value of the flow volume of the refrigerant which tends to change in accordance with the load and external conditions for the turbo refrigerator 10.
  • Fig. 2 is a block diagram showing the configurations of the vane degree-of-opening control portion 42 and the expansion-valve degree-of-opening control portion 44 according to the first embodiment.
  • the vane degree-of-opening control portion 42 is provided with a target-cold-water-outlet-temperature-value setting portion 50, a subtraction portion 52, and a PI control portion 54.
  • the target-cold-water-outlet-temperature-value setting portion 50 sets a target value for the cold-water outlet temperature, and outputs the set target value to the subtraction portion 52.
  • the target value for the cold-water outlet temperature is input by, for example, an operator of the turbo refrigerator 10 via an operation input portion (not shown), and the input target value serves as a set value.
  • the subtraction portion 52 receives an input of the cold-water outlet temperature measured by the cold-water-outlet-temperature measuring portion 36, subtracts the target value for the cold-water outlet temperature from this cold-water outlet temperature, and outputs the subtraction result to the PI control portion 54.
  • the PI control portion 54 calculates a vane degree-of-opening command value based on the subtraction result input from the subtraction portion 52, and outputs it to the compressor inlet vane 20.
  • the compressor inlet vane 20 changes the degree-of-opening thereof in accordance with the vane degree-of-opening command value.
  • the vane degree-of-opening control portion 42 calculates the vane degree-of-opening command value by means of feedback control based on the cold-water outlet temperature.
  • the expansion-valve degree-of-opening control portion 44 is provided with a target-degree-of-superheating calculating portion 60, the degree-of-superheating calculating portion 62, a subtraction portion 64, a PI control portion 66, a planned-CV-value calculating portion 68, an expansion-valve degree-of-opening calculating portion 70, and an addition portion 72.
  • the target-degree-of-superheating calculating portion 60 calculates a target value of the degree of superheating (hereinafter, referred to as "target degree of superheating") based on the cold-water inlet temperature measured by the cold-water-inlet-temperature measuring portion 34.
  • the target-degree-of-superheating calculating portion 60 calculates the target degree of superheating so as to take a greater value with a decrease in the cold-water inlet temperature. The reason for this will be described below.
  • turbo refrigerator 10 be operated so that the degree of superheating at the outlet of the evaporator 16 becomes 0 (zero) in order to maximize the COP.
  • degree of superheating becomes 0, the possibility of liquid back occurring increases, and, if the liquid back occurs, motive power of the turbo compressor 12 increases, which makes it likely that an overload trip occurs in the turbo refrigerator 10.
  • the target-degree-of-superheating calculating portion 60 calculates the target degree of superheating so as to take a greater value with a decrease in the temperature of cold water that flows into the evaporator 16.
  • the target-degree-of-superheating calculating portion 60 stores, in advance, table information or function information that indicates the relationship between the target degree of superheating and the cold-water inlet temperature in accordance with the characteristics of the turbo refrigerator 10, and calculates the target degree of superheating based on the table information or the function information.
  • the degree-of-superheating calculating portion 62 calculates a measured value of the degree of superheating (hereinafter, referred to as "measured degree of superheating") based on the compressor intake temperature (the temperature of the refrigerant at the outlet of the evaporator 16) measured by the compressor-intake-temperature measuring portion 22 and the compressor intake pressure measured by the compressor-intake-pressure measuring portion 24.
  • the degree-of-superheating calculating portion 62 stores, in advance, physical-property information, for example, a p-h diagram (Mollier diagram) or the like, and calculates the measured degree of superheating from the information about the compressor intake temperature and the compressor intake pressure, as well as the stored physical property information.
  • physical-property information for example, a p-h diagram (Mollier diagram) or the like.
  • the subtraction portion 64 receives inputs of the target degree of superheating calculated by the target-degree-of-superheating calculating portion 60 and the measured degree of superheating calculated by the degree-of-superheating calculating portion 62, subtracts the target degree of superheating from the measured degree of superheating, and outputs the subtraction result to the PI control portion 66.
  • the PI control portion 66 calculates the degree-of-opening of the expansion valve 18 based on the subtraction result input from the subtraction portion 64, and outputs it to the addition portion 72.
  • the expansion-valve degree-of-opening control portion 44 performs feedback control for the degree-of-opening of the expansion valve 18 based on the degree of superheating by means of the target-degree-of-superheating calculating portion 60, the degree-of-superheating calculating portion 62, the subtraction portion 64, and the PI control portion 66.
  • the planned-CV-value calculating portion 68 calculates the planned CV value based on the cold-water inlet temperature measured by the cold-water-inlet-temperature measuring portion 34 and the cooling-water inlet temperature measured by the cooling-water-inlet-temperature measuring portion 28.
  • Fig. 3 is a graph showing the relationship between the planned CV value and the cold-water inlet temperature and also the cooling-water inlet temperature according to the first embodiment.
  • the planned-CV-value calculating portion 68 calculates the planned CV value so as to take a smaller value with a decrease in the cold-water inlet temperature and so as to take a greater value with a decrease in the cooling-water inlet temperature.
  • the reason for decreasing the planned CV value with a decrease in the cold-water inlet temperature is that the flow volume of cold water can be decreased, because the case in which the cold-water inlet temperature is decreased is a case in which the load on the turbo refrigerator 10 is decreased.
  • the reason for increasing the planned CV value with a decrease in the cooling-water inlet temperature is to increase the flow volume of the refrigerant by increasing the degree-of-opening of the expansion valve 18, because the internal pressure of the condenser 14 is decreased when the cooling-water inlet temperature is decreased, which decreases the pressure on the upstream side of the expansion valve 18, thus decreasing the degree of supercooling (increasing the specific volume).
  • the planned-CV-value calculating portion 68 stores, in advance, information that indicates the relationship between the planned CV value and the cold-water inlet temperature and also the cooling-water inlet temperature, such as the one shown in Fig. 3 , and calculates the planned CV value based on that information.
  • the expansion-valve degree-of-opening calculating portion 70 calculates the degree-of-opening of the expansion valve 18 based on the planned CV value calculated by the planned-CV-value calculating portion 68.
  • Fig. 4 is a graph showing the relationship between the CV value and the degree-of-opening of the expansion valve 18 according to the first embodiment, which shows that the degree-of-opening of the expansion valve 18 increases with an increase in the CV value.
  • the expansion-valve degree-of-opening calculating portion 70 stores, in advance, information that indicates the CV value and the degree-of-opening of the expansion valve 18, such as the one shown in Fig. 4 , and calculates the degree-of-opening of the expansion valve 18 based on that information.
  • the expansion-valve degree-of-opening control portion 44 performs feedforward control for the degree-of-opening of the expansion valve 18 based on the estimated value of the flow volume of the refrigerant by means of the planned-CV-value calculating portion 68 and the expansion-valve degree-of-opening calculating portion 70.
  • the addition portion 72 calculates the sum of the degree-of-opening of the expansion valve 18 input from the PI control portion 66 and the degree-of-opening of the expansion valve 18 input from the expansion-valve degree-of-opening calculating portion 70, and outputs it to the expansion valve 18.
  • the expansion valve 18 changes the degree-of-opening thereof in accordance with the expansion-valve degree-of-opening command value.
  • the turbo refrigerator 10 calculates the degree-of-opening of the expansion valve 18 based on the difference between the target degree of superheating and the measured degree of superheating, calculates the degree-of-opening of the expansion valve 18 based on the planned CV value, and calculates the expansion-valve degree-of-opening command value from the above-described two types of degree-of-opening calculated for the expansion valve 18.
  • the degree-of-opening of the expansion valve 18 is controlled by means of feedback control, which maintains the stability thereof, and also by using, in combination therewith, feedforward control in which the input information for the turbo refrigerator 10 is utilized, the degree-of-opening of the expansion valve 18 can be set to an appropriate degree-of-opening regardless of the load and external conditions for the turbo refrigerator 10.
  • turbo refrigerator 10 calculates the target degree of superheating based on the cold-water inlet temperature, which is related to the load on the turbo refrigerator 10, effective feedback control can be performed to control the degree-of-opening of the expansion valve 18.
  • turbo refrigerator 10 calculates the target degree of superheating so as to take a greater value with a decrease in the cold-water inlet temperature, it is possible to prevent the liquid-phase refrigerant from being drawn into the turbo compressor 12 (liquid back).
  • turbo refrigerator 10 calculates the planned CV value based on the cold-water inlet temperature and the cooling-water inlet temperature, effective feedforward control can be performed to control the degree-of-opening of the expansion valve 18 in accordance with the load and external conditions.
  • turbo refrigerator 10 calculates the planned CV value so as to take a smaller value with a decrease in the cold-water inlet temperature and so as to take a greater value with a decrease in the cooling-water inlet temperature, it is possible to increase the precision of the feedforward control for the degree-of-opening of the expansion valve 18.
  • Fig. 5 shows the configuration of a turbo refrigerator 10 according to the second embodiment. Note that components in Fig. 5 that are the same as those in Fig. 1 are given the same reference signs as in Fig. 1 , and descriptions thereof will be omitted.
  • the turbo refrigerator 10 is provided with a hot-gas bypass pipe 80 that forms a bypass path between a refrigerant intake port of the turbo compressor 12 and a refrigerant exhaust port of the turbo compressor 12 (between a gas-phase portion in the condenser 14 and a gas-phase portion in the evaporator 16). Also, the hot-gas bypass pipe 80 is provided with a hot-gas bypass valve 82 for controlling the flow volume of the refrigerant that flows in the hot-gas bypass pipe 80.
  • turbo refrigerator 10 With the turbo refrigerator 10 according to the second embodiment, by adjusting the flow volume of bypassed hot gas by means of the hot-gas bypass valve 82, it is possible to perform capacity control of an extremely small region that cannot be sufficiently controlled with the compressor inlet vane 20.
  • refrigerant in which the gas-phase refrigerant at the outlet of the turbo compressor 12 and the gas-phase refrigerant at the outlet of the evaporator 16 are mixed is taken into the turbo compressor 12. Because of this, if the temperature of the refrigerant to be compressed at the turbo compressor 12 is used to measure the degree of superheating, the temperature of the above-described mixed refrigerant, that is, a temperature differing from the temperature of the refrigerant at the outlet of the evaporator 16, would be used, and thus, the degree of superheating would not be measured correctly.
  • the temperature of the refrigerant at the outlet of the evaporator 16 and the cold-water outlet temperature are assumed to be equivalent, and the measured degree of superheating is calculated based on the cold-water outlet temperature and the compressor intake pressure.
  • Fig. 6 shows the configurations of a vane degree-of-opening control portion 42 and an expansion-valve degree-of-opening control portion 44 according to the second embodiment. Note that components in Fig. 6 that are the same as those in Fig. 2 are given the same reference signs as in Fig. 2 , and descriptions thereof will be omitted.
  • the expansion-valve degree-of-opening control portion 44 according to the second embodiment is provided with a compressor-intake-saturation-temperature calculating portion 84 instead of the degree-of-superheating calculating portion 62 provided in the expansion-valve degree-of-opening control portion 44 according to the first embodiment.
  • the compressor-intake-saturation-temperature calculating portion 84 calculates the saturation temperature of the refrigerant to be taken into the compressor (hereinafter, referred to as "compressor-intake saturation temperature") based on the compressor intake pressure measured by the compressor-intake-pressure measuring portion 30.
  • the compressor-intake-saturation-temperature calculating portion 84 stores, in advance, physical-property information that indicates the relationship between the pressure and saturation temperature of the refrigerant, and calculates the compressor-intake saturation temperature based on the compressor intake pressure and that physical-property information.
  • expansion-valve degree-of-opening control portion 44 is provided with a subtraction portion 86.
  • the subtraction portion 86 receives inputs of the compressor-intake saturation temperature calculated by the compressor-intake-saturation-temperature calculating portion 84 and the cold-water outlet temperature measured by the cold-water-outlet-temperature measuring portion 36, and calculates the measured degree of superheating by subtracting the compressor-intake saturation temperature from the cold-water outlet temperature.
  • the subtraction portion 64 receives inputs of the target degree of superheating calculated by the target-degree-of-superheating calculating portion 60 and the measured degree of superheating calculated by the subtraction portion 86, subtracts the target degree of superheating from the measured degree of superheating, and outputs the subtraction result to the PI control portion 66.
  • the turbo refrigerator 10 calculates the measured degree of superheating based on the cold-water outlet temperature and the compressor intake pressure, even though the hot-gas bypass pipe 80 is provided, the degree of superheating can be measured with high precision.
  • the present invention is not limited thereto, and a form in which the planned CV value is calculated by using only one of the cold-water inlet temperature and the cooling-water inlet temperature may be employed.
  • the present invention is not limited thereto, and a form in which the heat-source medium is assumed to be gas (external air) and the condenser is assumed to be an air heat exchanger may be employed.
  • a measuring portion that measures the gas (external air) serving as the heat-source medium is provided instead of the cooling-water-inlet-temperature measuring portion 28, and the thus-measured gas temperature is used instead of the cooling-water inlet temperature used in the individual embodiments described above.
  • the present invention may be employed in a heat-pump turbo refrigerator that is also capable of heat-pump operation.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
EP12764195.9A 2011-03-28 2012-03-15 Dispositif de commande de détendeur, machine de source de chaleur, et procédé de commande de détendeur Withdrawn EP2693136A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011070604A JP2012202672A (ja) 2011-03-28 2011-03-28 膨張弁制御装置、熱源機、及び膨張弁制御方法
PCT/JP2012/056764 WO2012132944A1 (fr) 2011-03-28 2012-03-15 Dispositif de commande de détendeur, machine de source de chaleur, et procédé de commande de détendeur

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EP2693136A1 true EP2693136A1 (fr) 2014-02-05

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US (1) US20130180272A1 (fr)
EP (1) EP2693136A1 (fr)
JP (1) JP2012202672A (fr)
KR (1) KR20130037730A (fr)
CN (1) CN103443563A (fr)
WO (1) WO2012132944A1 (fr)

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6071741B2 (ja) * 2013-05-16 2017-02-01 株式会社神戸製鋼所 ヒートポンプシステム
DE102013210175A1 (de) * 2013-05-31 2014-12-18 Siemens Aktiengesellschaft Wärmepumpe zur Verwendung von umweltverträglichen Kältemitteln
TR201819850T4 (tr) * 2013-09-27 2019-01-21 Toshiba Carrier Corp Dondurma çevrimi cihazı.
KR20150124390A (ko) * 2014-04-25 2015-11-05 주식회사 서남 극저온 냉동 시스템
EP3140025B1 (fr) * 2014-05-09 2018-12-12 Atlas Copco Airpower Procédé et dispositif pour sécher à froid un gaz avec un liquide de refroidissement en circulation avec une ligne de dérivation
JP6433709B2 (ja) * 2014-07-30 2018-12-05 三菱重工サーマルシステムズ株式会社 ターボ冷凍機及びその制御装置並びにその制御方法
US20160047595A1 (en) * 2014-08-18 2016-02-18 Paul Mueller Company Systems and Methods for Operating a Refrigeration System
ES2926137T3 (es) 2015-03-09 2022-10-24 Carrier Corp Control de válvula de expansión
US10113553B2 (en) 2016-01-12 2018-10-30 Daikin Applied Americas Inc. Centrifugal compressor with hot gas injection
CN106338167B (zh) * 2016-09-30 2019-03-22 杭州先途电子有限公司 电子膨胀阀过热度的调节方法
JP6890021B2 (ja) * 2017-02-28 2021-06-18 三菱重工サーマルシステムズ株式会社 ターボ冷凍機、及びターボ冷凍機の運転方法
US11268523B2 (en) 2017-10-10 2022-03-08 Daikin Industries, Ltd. Centrifugal compressor with recirculation structure
JP6987598B2 (ja) * 2017-10-20 2022-01-05 三菱重工サーマルシステムズ株式会社 冷凍サイクルの制御装置、熱源装置、及びその制御方法
CN107933872B (zh) * 2017-11-07 2020-04-24 珠海格力电器股份有限公司 舰船用冷水机组的电子膨胀阀控制方法及装置
US20190178545A1 (en) * 2017-12-07 2019-06-13 Dunan Microstaq, Inc. Heating, ventilating, air conditioning, and refrigeration system with mass flow stabilization
IT201900021534A1 (it) * 2019-11-19 2021-05-19 Carel Ind Spa Apparato frigorifero monovalvola a co2 e metodo di regolazione dello stesso
JP7436980B2 (ja) * 2020-01-22 2024-02-22 日本エア・リキード合同会社 液化装置
CN111595047A (zh) * 2020-06-19 2020-08-28 深圳市英维克科技股份有限公司 一种冷藏车的制冷系统及其控制方法
CN113291128B (zh) * 2021-04-29 2022-05-03 东风柳州汽车有限公司 一种集成式动力电池冷却系统、冷却控制方法及电动汽车
CN113569186B (zh) * 2021-07-28 2023-09-29 东方电气集团东方电机有限公司 一种冷却水阀开度计算方法
CN113858910B (zh) * 2021-08-26 2023-08-29 浙江智马达智能科技有限公司 一种电池板式换热器的电子膨胀阀开度控制方法和系统

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03271656A (ja) * 1990-03-20 1991-12-03 Zexel Corp 冷房・冷凍サイクルの過熱度制御装置
JP2001248919A (ja) * 2000-03-03 2001-09-14 Daikin Ind Ltd 空気調和装置
JP3742864B2 (ja) * 2004-03-31 2006-02-08 ダイキン工業株式会社 空気調和システム
US7886556B2 (en) * 2004-03-31 2011-02-15 Daikin Industries, Ltd. Air conditioning system
JP2007248001A (ja) * 2006-03-17 2007-09-27 Mitsubishi Electric Corp 冷凍空調装置
JP2010054094A (ja) * 2008-08-27 2010-03-11 Mitsubishi Heavy Ind Ltd 空気調和装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2012132944A1 *

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KR20130037730A (ko) 2013-04-16
CN103443563A (zh) 2013-12-11
JP2012202672A (ja) 2012-10-22
US20130180272A1 (en) 2013-07-18
WO2012132944A1 (fr) 2012-10-04

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