EP2910870B1 - Dispositif de réfrigération et son procédé de commande - Google Patents

Dispositif de réfrigération et son procédé de commande Download PDF

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Publication number
EP2910870B1
EP2910870B1 EP12884923.9A EP12884923A EP2910870B1 EP 2910870 B1 EP2910870 B1 EP 2910870B1 EP 12884923 A EP12884923 A EP 12884923A EP 2910870 B1 EP2910870 B1 EP 2910870B1
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EP
European Patent Office
Prior art keywords
temperature side
low
compressor
condenser
refrigeration apparatus
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Application number
EP12884923.9A
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German (de)
English (en)
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EP2910870A4 (fr
EP2910870A1 (fr
Inventor
Akinori KURACHI
Tetsuya Yamashita
Takeshi Sugimoto
Takashi Ikeda
Katsunori Horiuchi
Hirofumi HARAIGAWA
Yuji TARUMI
Junichi Miyai
Nobuki Sato
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP2910870A4 publication Critical patent/EP2910870A4/fr
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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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off operation
    • 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
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2104—Temperatures of an indoor room or compartment

Definitions

  • the present invention relates to a refrigeration apparatus including a plurality of refrigeration cycles (refrigerant circuits), and a control method of such a refrigeration apparatus.
  • Some of existing refrigeration apparatuses include a high-temperature side (or higher side, primary side) refrigeration cycle (hereinafter, high-temperature side cycle) and a low-temperature side (or lower side, secondary side) refrigeration cycle (hereinafter, low-temperature side cycle) (for example, see Patent Literature 1).
  • an evaporator in the high-temperature side cycle and a condenser in the low-temperature side cycle constitute a cascade condenser.
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2012-112615 (paragraphs [0013] to [0051], Fig. 1 to Fig. 7 )
  • the controller drives an expansion valve in the low-temperature side cycle so as to narrow the path, thereby reducing the refrigerant supply to a compressor in the low-temperature side cycle.
  • the controller turns off the compressor in the low-temperature side cycle, in other words stops the circulation in the low-temperature side cycle, to thereby prevent the compressor in the low-temperature side cycle from sucking an excessive amount of the refrigerant, thus preventing a pressure drop in the low-temperature side cycle.
  • Such a control is called low-pressure cut-off control.
  • the circulation in the low-temperature side cycle may be stopped as in the low-pressure cut-off control, when the evaporator in the low-temperature side cycle is performing a defrosting operation.
  • a refrigerant of a low critical temperature such as a CO 2 refrigerant is often employed as the refrigerant in the low-temperature side cycle.
  • the present invention has been accomplished in view of the foregoing problem, and provides a refrigeration apparatus that suppresses an increase in pressure in a low-temperature side cycle when circulation in the low-temperature side cycle is stopped, and a control method performed by the refrigeration apparatus.
  • the present invention provides a refrigeration apparatus according to claim 1.
  • the refrigeration apparatus according to the invention includes a first refrigerant circuit in which a refrigerant circulates, the first refrigerant circuit including a first compressor, a first condenser, a first throttle device, and a first evaporator sequentially connected by piping, a second refrigerant circuit in which a refrigerant circulates, the second refrigerant circuit including a second compressor, a second condenser, a receiver, a second throttle device, and a second evaporator sequentially connected by piping, and a cascade condenser including the first evaporator and the second condenser and configured to heat exchange between the refrigerant flowing in the first evaporator and the refrigerant flowing in the second condenser.
  • the receiver is located under the cascade condenser.
  • the refrigeration apparatus further comprises a controller that controls operation of the first compressor and the second compressor and activates the first compressor when the second compressor is of as well as controls at least one of frequency of the first compressor and an opening degree of the first expansion device on the basis of a pressure on a high-pressure side of the second refrigerant circuit, when the second compressor is off and the first compressor is on.
  • the refrigeration apparatus further comprises a flow control value which is provided to a pipe connecting between an outlet side of the second condenser and the receiver and the controller opens the flow control value when the second compressor is off and the first compressor is on.
  • the receiver is located under the cascade condenser. Accordingly, when the circulation in the second refrigerant circuit is stopped, the refrigerant in the second refrigerant circuit, which has been condensed and liquefied by the refrigerant in the first refrigerant circuit, is rapidly collected in the receiver, and therefore an increase in pressure in the second refrigerant circuit can be suppressed.
  • Fig. 1 is a diagram showing the configuration of the refrigeration apparatus according to Embodiment 1.
  • the refrigeration apparatus 1 includes a high-temperature side cycle 11, a low-temperature side cycle 21, a cascade condenser 51, and a controller 61.
  • the high-temperature side cycle 11 corresponds to the "first refrigerant circuit" in the present invention.
  • the low-temperature side cycle 21 corresponds to the "second refrigerant circuit".
  • the high-temperature side cycle 11 includes a high-temperature side compressor 12, a high-temperature side condenser 13, a high-temperature side expansion valve 14, and a high-temperature side evaporator 15.
  • the high-temperature side compressor 12 corresponds to the "first compressor”.
  • the high-temperature side condenser 13 corresponds to the "first condenser”.
  • the high-temperature side expansion valve 14 corresponds to the "first throttle device”.
  • the high-temperature side evaporator 15 corresponds to the "first evaporator”.
  • the high-temperature side compressor 12, the high-temperature side condenser 13, the high-temperature side expansion valve 14, and the high-temperature side evaporator 15 are connected in series.
  • the low-temperature side cycle 21 includes a low-temperature side compressor 22, an intermediate cooler 23, a low-temperature side condenser 24, a receiver 25, a cooling unit 41, and an accumulator 26.
  • the low-temperature side compressor 22 corresponds to the "second compressor”.
  • the low-temperature side condenser 24 corresponds to the "second condenser”.
  • the low-temperature side compressor 22, the intermediate cooler 23, the low-temperature side condenser 24, the receiver 25, the cooling unit 41, and the accumulator 26 are connected in series.
  • a service valve 27 is provided between the outlet side of the receiver 25 and the inlet side of the cooling unit 41.
  • a service valve 28 is provided between the outlet side of the cooling unit 41 and the inlet side of the accumulator 26.
  • the cooling unit 41 can be separated from the refrigeration apparatus 1 by the service valves 27 and 28.
  • the service valves 27 and 28 may be excluded, and the cooling unit 41 may be inseparable.
  • a non-illustrated sight glass for confirming the amount or condition of the refrigerant, and a non-illustrated drier for absorbing moisture in the pipe may be provided in the low-temperature side cycle 21.
  • the high-temperature side evaporator 15 and the low-temperature side condenser 24 constitute a cascade condenser 51.
  • the refrigerant in the high-temperature side cycle 11 and the refrigerant in the low-temperature side cycle 21 exchange heat with each other in the cascade condenser 51.
  • Fig. 2 is a perspective view showing the refrigeration apparatus according to Embodiment 1.
  • the receiver 25 is located under the cascade condenser 51.
  • the receiver 25 and the low-temperature side condenser 24 are connected to each other via a pipe 29 having an outer diameter of, for example, 15.88 mm.
  • Fig. 2 illustrates the case where the cascade condenser 51 is composed of a pair of plate-type heat exchangers connected in series and disposed side by side.
  • Fig. 2 illustrates the case where the cooling unit 41 is separated.
  • the cooling unit 41 includes a low-temperature side first solenoid valve 42, a low-temperature side expansion valve 43, and a low-temperature side evaporator 44.
  • the low-temperature side expansion valve 43 corresponds to the "second throttle device”.
  • the low-temperature side evaporator 44 corresponds to the "second evaporator”.
  • the low-temperature side first solenoid valve 42, the low-temperature side expansion valve 43, and the low-temperature side evaporator 44 are connected in series.
  • the low-temperature side evaporator 44 is located in a refrigerating room.
  • Examples of the refrigerating room include a freezing showcase installed in a super market or the like, and a freezing room of a unit cooler installed in a food processing plant.
  • a cooling unit utilized in an existing refrigerating room may be employed as the cooling unit 41.
  • a HFC refrigerant R410A, R404A, R32, R407C
  • a HFO refrigerant R407C
  • a HC refrigerant a HFC refrigerant
  • a CO 2 refrigerant having a global warming potential (GWP) of 1 may be employed as the refrigerant in the low-temperature side cycle 21.
  • At least the high-temperature side compressor 12, the low-temperature side compressor 22, the low-temperature side expansion valve 43, the temperature sensor 62, the low-temperature side high pressure sensor 63, and the low-temperature side low pressure sensor 64 are connected to the controller 61.
  • the temperature sensor 62 detects the temperature of the object to be cooled, such as the air in the refrigerating room.
  • the low-temperature side high pressure sensor 63 is located, for example, between the outlet side of the intermediate cooler 23 and the inlet side of the low-temperature side condenser 24, and detects the pressure on the high-pressure side of the low-temperature side cycle 21.
  • the low-temperature side high pressure sensor 63 may be located at a desired position, provided that the position is between the outlet side of the low-temperature side compressor 22 and the inlet side of the low-temperature side expansion valve 43.
  • the low-temperature side low pressure sensor 64 is located, for example, between the service valve 28 and the inlet side of the accumulator 26, and detects the pressure on the low-pressure side of the low-temperature side cycle 21.
  • the low-temperature side low pressure sensor 64 may be located at a desired position, provided that the position is between the outlet side of the low-temperature side expansion valve 43 and the inlet side of the low-temperature side compressor 22.
  • the refrigerant which has entered the high-temperature side condenser 13 is condensed and liquefied through heat exchange with outside air, and turns into high-pressure liquid phase refrigerant.
  • the high-pressure liquid phase refrigerant is depressurized in the high-temperature side expansion valve 14, thus to turn into low-temperature/low-pressure gas-liquid two-phase refrigerant.
  • the low-temperature/low-pressure gas-liquid two-phase refrigerant is heated in the cascade condenser 51 by the refrigerant in the low-temperature side cycle 21 (cools the refrigerant in the low-temperature side cycle 21) and evaporated, thus to turn into low-pressure gas phase refrigerant.
  • the low-pressure gas phase refrigerant flows into the high-temperature side compressor 12.
  • High-temperature/high-pressure gas phase refrigerant discharged from the low-temperature side compressor 22 is cooled in the intermediate cooler 23 and flows into the cascade condenser 51.
  • the refrigerant which has entered the cascade condenser 51 is condensed and liquefied by the refrigerant in the high-temperature side cycle 11, and turns into high-pressure liquid phase refrigerant.
  • the high-pressure liquid phase refrigerant flows into the low-temperature side expansion valve 43 through the receiver 25, the service valve 27, and the low-temperature side first solenoid valve 42.
  • the high-pressure liquid phase refrigerant which has entered the low-temperature side expansion valve 43 is depressurized, thus to turn into low-temperature/low-pressure gas-liquid two-phase refrigerant.
  • the low-temperature/low-pressure gas-liquid two-phase refrigerant is heated in the low-temperature side evaporator 44 by the air in the refrigerating room (cools the air in the refrigerating room) and evaporated, thus to turn into low-pressure gas phase refrigerant.
  • the low-pressure gas phase refrigerant flows into the low-temperature side compressor 22 through the service valve 28 and the accumulator 26.
  • controller 61 The operation of the controller 61 will be described hereunder.
  • controller 61 The following is merely an example of the operation of the controller 61, and the present disclosure encompasses other operations of the controller 61.
  • Fig. 3 is a flowchart showing the operation of the controller in the refrigeration apparatus according to Embodiment 1.
  • the controller 61 activates the high-temperature side compressor 12 and the low-temperature side compressor 22, and controls the opening degree of the low-temperature side expansion valve 43, so as to reduce the opening degree the closer the temperature detected by the temperature sensor 62 is to a target temperature.
  • the controller 61 determines whether the pressure detected by the low-temperature side low pressure sensor 64 is equal to or lower than a predetermined lower-limit pressure (hereinafter, first predetermined lower-limit pressure).
  • the first predetermined lower-limit pressure corresponds to the "third reference pressure”.
  • the controller 61 returns to step 31.
  • step 33 the controller 61 proceeds to step 33.
  • the controller 61 turns off the low-temperature side compressor 22, and turns on the high-temperature side compressor 12.
  • the controller 61 determines whether the pressure detected by the low-temperature side low pressure sensor 64 is higher than another predetermined lower-limit pressure (hereinafter, second predetermined lower-limit pressure), and whether the pressure detected by the low-temperature side high pressure sensor 63 is equal to or lower than a predetermined upper-limit pressure (hereinafter, first predetermined upper-limit pressure).
  • second predetermined lower-limit pressure another predetermined lower-limit pressure
  • first predetermined upper-limit pressure hereinafter, first predetermined upper-limit pressure
  • the second predetermined lower-limit pressure corresponds to the "first reference pressure”.
  • the first predetermined upper-limit pressure corresponds to the "second reference pressure”.
  • the controller 61 returns to step 33.
  • step 31 the controller 61 proceeds to step 31.
  • the second predetermined lower-limit pressure of step 34 may be the same as or different from the first predetermined lower-limit pressure of step 32.
  • the first predetermined upper-limit pressure may be, for example, 6.9 MPa.
  • a refrigerant of a low critical temperature such as a CO 2 refrigerant
  • the refrigeration apparatus 1 is installed in an environment where outside air temperature is higher than the critical temperature
  • the refrigerant in the low-temperature side cycle 21 is heated by the outside air and turns into gas phase when the circulation in the low-temperature side cycle 21 is stopped, and therefore the pressure in the low-temperature side cycle 21 increases.
  • the critical temperature of the CO 2 refrigerant is approximately 31 degrees Celsius.
  • the controller 61 turns on the high-temperature side compressor 12 when the circulation in the low-temperature side cycle 21 is stopped, to thereby activate the circulation in the high-temperature side cycle 11.
  • the gas phase refrigerant in the low-temperature side cycle 21 is condensed and liquefied in the cascade condenser 51 by the refrigerant in the high-temperature side cycle 11, and turns into liquid phase refrigerant.
  • the receiver 25 and the cascade condenser 51 have the same pressure, and therefore the liquid phase refrigerant drops onto the receiver 25 located under the cascade condenser 51b through the pipe 29, because of the gravity.
  • the receiver 25 since the receiver 25 is located under the cascade condenser 51, the refrigerant in the low-temperature side cycle 21 condensed and liquefied by the refrigerant in the high-temperature side cycle 11 is promptly collected in the receiver 25 when the circulation in the low-temperature side cycle 21 is stopped, and therefore an increase in pressure in the low-temperature side cycle 21 can be suppressed.
  • the controller 61 simply turns on the high-temperature side compressor 12 when the circulation in the low-temperature side cycle 21 is stopped.
  • the controller 61 may operate the high-temperature side compressor 12 while controlling at least one of the frequency thereof and the opening degree of the high-temperature side expansion valve 14, on the basis of the pressure detected by the low-temperature side high pressure sensor 63.
  • Fig. 4 is a flowchart showing a variation of the operation of the controller in the refrigeration apparatus according to Embodiment 1.
  • controller 61 works as shown in Fig. 4 .
  • Steps 41, 42, and 44 are the same as steps 31, 32, and 34 in Fig. 3 .
  • the controller 61 turns off the low-temperature side compressor 22, and operates the high-temperature side compressor 12 at a higher frequency while reducing the opening degree of the high-temperature side expansion valve 14, the higher the pressure detected by the low-temperature side high pressure sensor 63 is.
  • At least one of the frequency of the high-temperature side compressor 12 and the opening degree of the high-temperature side expansion valve 14 may be controlled either linearly or stepwise, on the basis of the pressure detected by the low-temperature side high pressure sensor 63.
  • the controller 61 may activate the high-temperature side compressor 12 only when the pressure detected by the low-temperature side high pressure sensor 63 is higher than a predetermined upper-limit pressure (hereinafter, second predetermined upper-limit pressure), at step 33 or strep 43.
  • a predetermined upper-limit pressure hereinafter, second predetermined upper-limit pressure
  • the second predetermined upper-limit pressure specified for the mentioned case may be the same as or different from the first predetermined upper-limit pressure of step 34 or step 44.
  • the controller 61 may activate the high-temperature side compressor 12 only when a predetermined time (hereinafter, first predetermined time) has elapsed after the circulation in the low-temperature side cycle 21 is stopped.
  • the controller 61 may operate the high-temperature side compressor 12 either continuously or intermittently, when the first predetermined time has elapsed after the circulation in the low-temperature side cycle 21 is stopped.
  • controller 61 may monitor, based on the pressure detected by the low-temperature side high pressure sensor 63, whether the pressure in the low-temperature side cycle 21 has dropped, in other words whether the refrigerant is falling onto the receiver 25, at step 33 or step 43.
  • the controller 61 determines that the refrigerant is not falling onto the receiver 25 in the mentioned case, the controller 61 outputs an alarm signal.
  • a non-illustrated temperature sensor may be provided in the receiver 25, and the controller 61 may determine whether the refrigerant is falling onto the receiver 25 on the basis of the temperature detected by the temperature sensor.
  • the cascade condenser 51 of the refrigeration apparatus according to Embodiment 1 includes a pair of plate-type heat exchangers connected in series and disposed side by side as shown in Fig. 2
  • the cascade condenser 51 may be configured in a different form.
  • the cascade condenser 51 may be a shell-and-tube heat exchanger, without limitation to the plate-type heat exchanger.
  • the cascade condenser 51 may be constituted of a single heat exchanger, or three or more heat exchangers disposed side by side.
  • the cascade condenser 51 may include a plurality of heat exchangers connected in parallel, or a plurality of heat exchangers aligned in a vertical direction.
  • Fig. 5 is a perspective view showing a variation of the cascade condenser in the refrigeration apparatus according to Embodiment 1.
  • the refrigerant in the low-temperature side cycle 21, which has been condensed and liquefied in the high-temperature side evaporator 15, can smoothly flow downward because of the gravity, thereby more effectively suppressing the increase in pressure in the low-temperature side cycle 21.
  • Fig. 6 is a diagram showing the configuration of the refrigeration apparatus according to Embodiment 2.
  • the refrigeration apparatus 2 includes the high-temperature side cycle 11, a low-temperature side cycle 30, the cascade condenser 51, and a controller 65.
  • the low-temperature side cycle 30 includes a low-temperature side compressor 22, the intermediate cooler 23, the low-temperature side condenser 24, the receiver 25, the cooling unit 41, and the accumulator 26.
  • a flow control valve 31 is provided between the outlet side of the low-temperature side condenser 24 and the inlet side of the receiver 25.
  • At least the high-temperature side compressor 12, the low-temperature side compressor 22, the flow control valve 31, the low-temperature side expansion valve 43, the temperature sensor 62, the low-temperature side high pressure sensor 63, and the low-temperature side low pressure sensor 64 are connected to the controller 65.
  • Fig. 7 is a flowchart showing the operation of the controller in the refrigeration apparatus according to Embodiment 2.
  • the controller 65 works as shown in Fig. 7 .
  • Steps 71, 72, and 74 are the same as steps 31, 32, and 34 in Fig. 3 .
  • the controller 65 turns off the low-temperature side compressor 22 and turns on the high-temperature side compressor 12 while opening the flow control valve 31.
  • the controller 65 may open the flow control valve 31 to a fixed opening degree.
  • the controller 65 may open the flow control valve 31 to the higher opening degree, the higher the pressure detected by the low-temperature side high pressure sensor 63 is, at step 73.
  • the opening degree of the flow control valve 31 may be adjusted either linearly or stepwise, on the basis of the pressure detected by the low-temperature side high pressure sensor 63.
  • the controller 65 may open the flow control valve 31 to the fixed opening degree or to the opening degree based on the pressure detected by the low-temperature side high pressure sensor 63, only when the pressure detected by the low-temperature side high pressure sensor 63 is higher than a predetermined upper-limit pressure (hereinafter, third predetermined upper-limit pressure).
  • a predetermined upper-limit pressure hereinafter, third predetermined upper-limit pressure
  • the third predetermined upper-limit pressure specified for the mentioned case may be the same as or different from the first predetermined upper-limit pressure of step 74.
  • the controller 65 may open the flow control valve 31 only when a predetermined time (hereinafter, second predetermined time) has elapsed after the circulation in the low-temperature side cycle 30 is stopped.
  • the controller 65 may open the flow control valve 31 either continuously or intermittently, when the second predetermined time has elapsed after the circulation in the low-temperature side cycle 30 is stopped.
  • the controller 65 activates the high-temperature side compressor 12 while opening the flow control valve 31, when the circulation of the refrigerant in the low-temperature side cycle 30 is stopped.
  • the refrigerant can more smoothly fall onto the receiver 25 from the low-temperature side condenser 24, and hence the refrigerant condensed and liquefied by the refrigerant in the high-temperature side cycle 11 is more rapidly collected into the receiver 25. Consequently, the increase in pressure in the low-temperature side cycle 30 can be more effectively suppressed.
  • controller 65 controls the opening and closing of the flow control valve 31 in the refrigeration apparatus according to Embodiment 2
  • the flow control valve 31 may be manually opened and closed. This variation does not belong to the invention.
  • the controller 65 simply turns on the high-temperature side compressor 12 when the circulation in the low-temperature side cycle 30 is stopped.
  • the controller 65 may operate the high-temperature side compressor 12 while controlling at least one of the frequency thereof and the opening degree of the high-temperature side expansion valve 14, on the basis of the pressure detected by the low-temperature side high pressure sensor 63, as shown in Fig. 4 .
  • This alternative does not belong to the invention.
  • Fig. 8 is a diagram showing the configuration of the refrigeration apparatus according to Embodiment 3.
  • the refrigeration apparatus 3 includes the high-temperature side cycle 11, a low-temperature side cycle 32, the cascade condenser 51, and a controller 66.
  • the low-temperature side cycle 32 includes the low-temperature side compressor 22, the intermediate cooler 23, the low-temperature side condenser 24, the receiver 25, the cooling unit 41, and the accumulator 26.
  • the top portion of the receiver 25 and the inlet side of the low-temperature side condenser 24 are connected to each other via a bypass pipe 33.
  • the bypass pipe 33 includes a low-temperature side second solenoid valve 34.
  • At least the high-temperature side compressor 12, the low-temperature side compressor 22, the low-temperature side second solenoid valve 34, the low-temperature side expansion valve 43, the temperature sensor 62, the low-temperature side high pressure sensor 63, and the low-temperature side low pressure sensor 64 are connected to the controller 66.
  • Fig. 9 is a flowchart showing the operation of the controller in the refrigeration apparatus according to Embodiment 3.
  • the controller 66 works as shown in Fig. 9 .
  • Steps 91, 92, and 94 are the same as steps 31, 32, and 34 in Fig. 3 .
  • the controller 66 turns off the low-temperature side compressor 22 and turns on the high-temperature side compressor 12 while opening the low-temperature side second solenoid valve 34.
  • the controller 66 may open the low-temperature side second solenoid valve 34, only when the pressure detected by the low-temperature side high pressure sensor 63 is higher than a predetermined upper-limit pressure (hereinafter, fourth predetermined upper-limit pressure).
  • the fourth predetermined upper-limit pressure specified for the mentioned case may be the same as or different from the first predetermined upper-limit pressure of step 94.
  • the controller 66 may open the low-temperature side second solenoid valve 34 only when a predetermined time (hereinafter, third predetermined time) has elapsed after the circulation in the low-temperature side cycle 32 is stopped.
  • a predetermined time hereinafter, third predetermined time
  • the controller 66 may open the low-temperature side second solenoid valve 34 either continuously or intermittently, when the third predetermined time has elapsed after the circulation in the low-temperature side cycle 32 is stopped.
  • the controller 66 activates the high-temperature side compressor 12 while opening the low-temperature side second solenoid valve 34, when the circulation of the refrigerant in the low-temperature side cycle 32 is stopped.
  • the refrigerant turned into gas phase is conducted to the low-temperature side condenser 24 through the bypass pipe 33, and hence the refrigerant condensed and liquefied by the refrigerant in the high-temperature side cycle 11 can more smoothly fall from the low-temperature side condenser 24 onto the receiver 25. Consequently, the increase in pressure in the low-temperature side cycle 32 can be more effectively suppressed.
  • the controller 66 controls the opening and closing of the low-temperature side second solenoid valve 34 in the refrigeration apparatus according to Embodiment 3, the valve may be provided in the bypass pipe 33 and manually opened and closed.
  • the controller 66 simply turns on the high-temperature side compressor 12 when the circulation in the low-temperature side cycle 32 is stopped.
  • controller 66 may operate the high-temperature side compressor 12 while controlling at least one of the frequency thereof and the opening degree of the high-temperature side expansion valve 14, on the basis of the pressure detected by the low-temperature side high pressure sensor 63, as shown in Fig. 4 .
  • the flow control valve 31 may be provided between the outlet side of the low-temperature side condenser 24 and the inlet side of the receiver 25, as in the refrigeration apparatus according to Embodiment 2.
  • a refrigeration apparatus according to this variation belongs to the invention.
  • Fig. 10 is a diagram showing the configuration of the refrigeration apparatus according to Embodiment 4.
  • the refrigeration apparatus 4 includes a high-temperature side cycle 16, the low-temperature side cycle 21, the cascade condenser 51, and a controller 67.
  • the high-temperature side cycle 16 includes the high-temperature side compressor 12, the high-temperature side condenser 13, the high-temperature side expansion valve 14, and the high-temperature side evaporator 15.
  • a service valve 17 is provided between the outlet side of the high-temperature side expansion valve 14 and the inlet side of the high-temperature side evaporator 15.
  • a service valve 18 is provided between the outlet side of the high-temperature side evaporator 15 and the inlet side of the high-temperature side compressor 12.
  • the low-temperature side cycle 21 and the cascade condenser 51 can be separated from the refrigeration apparatus 4, by the service valves 17 and 18.
  • the controller 67 includes a high-temperature side controller 68 and a low-temperature side controller 69.
  • Fig. 11 is a drawing showing an arrangement of the components in the refrigeration apparatus according to Embodiment 4.
  • the components of the refrigeration apparatus 4 are separately located in a high-temperature side casing 81 and a low-temperature side casing 82.
  • Fig. 11 illustrates the case where the cooling unit 41 is separated.
  • the high-temperature side casing 81 includes the high-temperature side compressor 12, the high-temperature side condenser 13, the high-temperature side expansion valve 14, and the high-temperature side controller 68.
  • the low-temperature side casing 82 includes the low-temperature side compressor 22, the intermediate cooler 23, the receiver 25, the accumulator 26, the cascade condenser 51, and the low-temperature side controller 69.
  • the high-temperature side casing 81 and the low-temperature side casing 82 are mounted on a pedestal 83.
  • Forming the high-temperature side casing 81 and the low-temperature side casing 82 in the same shape enables the parts to be used in common, thereby contributing to reducing the cost of the refrigeration apparatus.
  • the service valves 17 and 18 are located in the high-temperature side casing 81.
  • the service valves 27 and 28 are located in the high-temperature side casing 82.
  • the high-temperature side controller 68 includes an operation switch 70.
  • At least the high-temperature side compressor 12, and an air-blowing device 84 that supplies outside air to the high-temperature side condenser 13 are connected to the high-temperature side controller 68.
  • the low-temperature side controller 69 includes an operation switch 71.
  • At least the low-temperature side compressor 22, the low-temperature side expansion valve 43, the temperature sensor 62, the low-temperature side high pressure sensor 63, the low-temperature side low pressure sensor 64, and an air-blowing device 85 that supplies outside air to the intermediate cooler 23 are connected to the low-temperature side controller 69.
  • the components are separately located in the high-temperature side casing 81 and the low-temperature side casing 82.
  • Such a configuration reduces the weight of each of the casings compared with the case where all the components are included in a single casing, thereby facilitating the transport and installment of the refrigeration apparatus 4.
  • cascade condenser 51 is located in the low-temperature side casing 82.
  • the low-temperature side casing 82 can be additionally connected on site to an existing refrigeration apparatus that includes a compressor, a condenser, and an expansion valve like the high-temperature side casing 81, and therefore the existing refrigeration apparatus can be easily converted into a plural refrigeration apparatus.
  • the high-temperature side casing 81 and the low-temperature side casing 82 respectively include the high-temperature side controller 68 and the low-temperature side controller 69.
  • the operator can turn on the operation switch 71 provided in the low-temperature side casing 82 thereby cooling an object to be cooled, such as the air in the refrigerating room.
  • the service valve 17 is provided between the outlet side of the high-temperature side expansion valve 14 and the inlet side of the high-temperature side evaporator 15.
  • the service valve 17 may be provided between the outlet side of the high-temperature side condenser 13 and the inlet side of the high-temperature side expansion valve 14, and the high-temperature side expansion valve 14 may be located in the low-temperature side casing 82.
  • the cascade condenser 51 is located in the low-temperature side casing 82 in the refrigeration apparatus according to Embodiment 4, the service valves 17 and 18 may be provided in the low-temperature side cycle 21 and the cascade condenser 51 may be located in the high-temperature side casing 81.
  • the pipes of the high-temperature side casing 81 and the pipe of the low-temperature side casing 82 are connected via the service valves 17 and 18 in the refrigeration apparatus according to Embodiment 4, the pipes may be connected by a different method, for example by brazing, instead of via the service valves 17 and 18.
  • the present invention is not limited to Embodiment 2.
  • Embodiment 2 and one or more of Embodiments 1, 3 or 4 or variations thereof may be combined as desired as long as the combination falls within the scope of the appended claims.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Claims (5)

  1. Appareil de réfrigération comprenant :
    un premier circuit de fluide frigorigène (11) dans lequel circule un fluide frigorigène, le premier circuit de fluide frigorigène (11) incluant un premier compresseur (12), un premier condenseur (13), un premier dispositif de détente (14) et un premier évaporateur (15) reliés en séquence par tuyauterie ;
    un second circuit de fluide frigorigène (21) dans lequel circule un fluide frigorigène, le second circuit de fluide frigorigène (21) incluant un second compresseur (22), un second condenseur (24), un récepteur (25), un second dispositif de détente (43) et un second évaporateur (44) reliés en séquence par tuyauterie ;
    un condenseur en cascade (51) incluant le premier évaporateur (15) et le second condenseur (24) et configuré pour échanger de la chaleur entre le fluide frigorigène s'écoulant dans le premier évaporateur (15) et le fluide frigorigène s'écoulant dans le second condenseur (24) ; et
    une unité de commande (65) configurée pour commander le fonctionnement du premier compresseur et du second compresseur ;
    dans lequel le récepteur (25) est situé en dessous du condenseur en cascade (51), et
    caractérisé en ce que l'unité de commande (65) est configurée pour activer le premier compresseur lorsque le second compresseur est éteint, et commander au moins l'un de la fréquence du premier compresseur et d'un degré d'ouverture du premier dispositif de détente sur la base d'une pression sur un côté haute-pression du second circuit de fluide frigorigène, lorsque le second compresseur est éteint et que le premier compresseur est allumé,
    dans lequel une vanne de régulation de débit (31) est prévue sur un tuyau assurant la liaison entre un côté de sortie du second condensateur (24) et le récepteur (25), et
    l'unité de commande (65) est configurée pour ouvrir la vanne de régulation de débit (31) lorsque le second compresseur (22) est éteint et que le premier compresseur (12) est allumé.
  2. Appareil de réfrigération selon la revendication 1,
    dans lequel une partie supérieure du récepteur (25) et un côté d'entrée du second condenseur (24) sont reliés l'un à l'autre par le biais d'un tuyau de dérivation (33) et d'une électrovanne (34), et
    dans lequel l'unité de commande ouvre l'électrovanne (34) lorsque le second compresseur (22) est éteint et que le premier compresseur (12) est allumé.
  3. Appareil de réfrigération selon la revendication 1 ou 2,
    dans lequel l'unité de commande active le premier compresseur (12) et le second compresseur (22) lorsqu'une pression sur un côté basse pression du second circuit de fluide frigorigène (21) est plus élevée qu'une première pression de référence prédéterminée et qu'une pression sur le côté haute pression du second circuit de fluide frigorigène (21) est inférieure ou égale à une seconde pression de référence prédéterminée.
  4. Appareil de réfrigération selon l'une quelconque des revendications 1 à 3
    dans lequel l'unité de commande éteint le second compresseur (22) lorsque la pression sur le côté basse pression du second circuit de fluide frigorigène (21) est inférieure ou égale à une troisième pression de référence prédéterminée.
  5. Procédé de commande d'un appareil de réfrigération incluant un premier circuit de fluide frigorigène (11) dans lequel circule un fluide frigorigène, le premier circuit de fluide frigorigène (11) incluant un premier compresseur (12), un premier condenseur (13), un premier dispositif de détente (14) et un premier évaporateur (15) reliés en séquence par tuyauterie ; un second circuit de fluide frigorigène (21) dans lequel circule un fluide frigorigène, le second circuit de fluide frigorigène (21) incluant un second compresseur (22), un second condenseur (24), un récepteur (25), un second dispositif de détente (43) et un second évaporateur (44) reliés en séquence par tuyauterie ; et un condenseur en cascade (51) incluant le premier évaporateur (15) et le second condenseur (24) et configuré pour échanger de la chaleur entre le fluide frigorigène s'écoulant dans le premier évaporateur (15) et le fluide frigorigène s'écoulant dans le second condenseur (24), le récepteur (25) étant situé en dessous du condenseur en cascade (51), le procédé de commande comprenant les étapes suivantes :
    activation du premier compresseur (12) lorsque le second compresseur (22) est éteint, et
    commande d'au moins l'un de la fréquence du premier compresseur et d'un degré d'ouverture du premier dispositif de détente sur la base d'une pression sur un côté haute-pression du second circuit de fluide frigorigène, lorsque le second compresseur est éteint et que le premier compresseur est allumé, dans lequel une vanne de régulation de débit (31) est prévue sur un tuyau assurant la liaison entre un côté de sortie du second condensateur (24) et le récepteur (25), et
    ouverture de la soupape de régulation de débit (31) lorsque le second compresseur (22) est éteint et que le premier compresseur (12) est allumé.
EP12884923.9A 2012-09-21 2012-09-21 Dispositif de réfrigération et son procédé de commande Active EP2910870B1 (fr)

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PCT/JP2012/074214 WO2014045400A1 (fr) 2012-09-21 2012-09-21 Dispositif de réfrigération et son procédé de commande

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JP6937608B2 (ja) * 2017-05-09 2021-09-22 エア・ウォーター株式会社 超電導ケーブル用冷却装置及びそれを用いた超電導ケーブルの冷却方法
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KR101825636B1 (ko) * 2017-07-06 2018-03-22 주식회사 이너지테크놀러지스 냉방, 난방 및 급탕기능을 구비한 히트펌프
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Publication number Publication date
JPWO2014045400A1 (ja) 2016-08-18
EP2910870A4 (fr) 2016-07-20
EP2910870A1 (fr) 2015-08-26
WO2014045400A1 (fr) 2014-03-27
JP5800994B2 (ja) 2015-10-28

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