WO2006112157A1 - Dispositif de cycle de refrigeration et procede d’actionnement de celui-ci - Google Patents

Dispositif de cycle de refrigeration et procede d’actionnement de celui-ci Download PDF

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Publication number
WO2006112157A1
WO2006112157A1 PCT/JP2006/303870 JP2006303870W WO2006112157A1 WO 2006112157 A1 WO2006112157 A1 WO 2006112157A1 JP 2006303870 W JP2006303870 W JP 2006303870W WO 2006112157 A1 WO2006112157 A1 WO 2006112157A1
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WO
WIPO (PCT)
Prior art keywords
refrigeration cycle
compressor
radiator
cycle apparatus
expander
Prior art date
Application number
PCT/JP2006/303870
Other languages
English (en)
Japanese (ja)
Inventor
Tetsuya Saito
Yuuichi Yakumaru
Tomoichiro Tamura
Masaya Honma
Original Assignee
Matsushita Electric Industrial Co., Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Matsushita Electric Industrial Co., Ltd. filed Critical Matsushita Electric Industrial Co., Ltd.
Publication of WO2006112157A1 publication Critical patent/WO2006112157A1/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
    • F25B11/00—Compression machines, plants or systems, using turbines, e.g. gas turbines
    • F25B11/02—Compression machines, plants or systems, using turbines, e.g. gas turbines as expanders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/14—Power generation using energy from the expansion of the refrigerant
    • F25B2400/141—Power generation using energy from the expansion of the refrigerant the extracted power is not recycled back in the refrigerant 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
    • F25B2500/00—Problems to be solved
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator

Definitions

  • the present invention relates to a refrigeration cycle apparatus using an expander and an operation method thereof.
  • FIG. 17 shows a conventional refrigeration cycle apparatus described in Patent Document 1.
  • Compressors 1 are those driven by driving means (not shown) such as a traveling engine for sucking and compressing the refrigerant, the refrigerant discharged by the compressor 1 is cooled by the radiator 2.
  • the refrigerant flowing out of the radiator 2 flows into the expander 3 to convert and recover the expansion energy of the refrigerant into mechanical energy (rotational energy), and supplies the recovered mechanical energy (rotational energy) to the generator 4. Power is generated.
  • the refrigerant expanded under reduced pressure in the expander 3 evaporates and evaporates in the evaporator 5 and then sucked into the compressor 1 again.
  • the present invention has been made in view of the above-described problems of the prior art, and when starting up the compressor, the capacity of the expander can be quickly increased by controlling the capacity of the radiator or the evaporator.
  • An object of the present invention is to provide a refrigeration cycle apparatus that secures a differential pressure necessary for driving, minimizes power recovery loss at the start of the compressor, and improves the reliability of the compressor, and an operation method thereof. .
  • the present invention provides a method for operating a refrigeration cycle apparatus in which a compressor, a radiator, an expander, and an evaporator are sequentially connected to circulate a refrigerant, and the radiator is a chamber.
  • the evaporator is provided in one of the outdoor unit and the indoor unit, and the evaporator is provided in the other of the outdoor unit and the indoor unit.
  • the present invention circulates refrigerant by sequentially connecting a compressor, a radiator, an expander, and an evaporator.
  • the radiator is provided in one of the outdoor unit and the indoor unit
  • the evaporator is provided in the other of the outdoor unit and the indoor unit
  • the refrigeration cycle device is provided in the outdoor unit.
  • a controller for controlling the capacity of the fan is further provided, and when the compressor is started, the controller controls the capacity of the outdoor fan to be reduced for a predetermined time from that during normal operation.
  • the controller may control the outdoor fan to operate at a set speed during normal operation.
  • the refrigeration cycle apparatus includes a bypass circuit having an expansion valve that bypasses the expander.
  • the compressor When the compressor is started, the refrigerant flows into the nopass circuit side, and the radiator capacity and the evaporator capacity are At least one of them is controlled so as to reduce the capacity for a predetermined time from the normal operation.
  • the differential pressure necessary for promptly driving the expander by controlling the capabilities of the radiator and the evaporator when the compressor is started up. it is possible to secure a can shorten the time until the expander is driven to minimize the power recovery loss of the compressor startup, and it is possible to improve the reliability of the compressor.
  • FIG. 1 is a configuration diagram of a refrigeration cycle apparatus according to Embodiment 1 of the present invention.
  • FIG. 2 is a configuration diagram of another refrigeration cycle apparatus according to Embodiment 1 of the present invention.
  • FIG. 3 is a Mollier diagram of the refrigeration cycle apparatus in Embodiment 1 of the present invention.
  • FIG. 4 is a flowchart of the refrigeration cycle apparatus in Embodiment 1 of the present invention.
  • FIG. 5 is a pressure change diagram of the refrigeration cycle apparatus in Embodiment 1 of the present invention.
  • FIG. 6 is a configuration diagram of another refrigeration cycle apparatus according to Embodiment 1 of the present invention.
  • FIG. 7 is a configuration diagram of a refrigeration cycle apparatus according to Embodiment 2 of the present invention.
  • FIG. 8 is a flowchart of the refrigeration cycle apparatus according to Embodiment 2 of the present invention.
  • FIG. 9 is a configuration diagram of a refrigeration cycle apparatus according to a modification of the second embodiment of the present invention.
  • FIG. 10 is a flowchart of a refrigeration cycle apparatus in a modification of the second embodiment of the present invention.
  • FIG. 11 is a configuration diagram of a refrigeration cycle apparatus according to another modification of the second embodiment of the present invention.
  • FIG. 12 is a configuration diagram of a refrigeration cycle apparatus according to Embodiment 3 of the present invention.
  • FIG. 13 is a flowchart of the refrigeration cycle apparatus in Embodiment 3 of the present invention.
  • FIG. 14 is a configuration diagram of a refrigeration cycle apparatus according to Embodiment 4 of the present invention.
  • FIG. 15 is a flowchart of the refrigeration cycle apparatus in Embodiment 4 of the present invention.
  • FIG. 16 is a pressure change diagram of the refrigeration cycle apparatus in Embodiment 4 of the present invention.
  • FIG. 17 is a configuration diagram of a conventional refrigeration cycle apparatus.
  • Figure 18 shows the Mollier diagram of a conventional refrigeration cycle system.
  • the refrigeration cycle apparatus of the first embodiment includes a refrigeration cycle in which a compressor 1, a radiator 2, an expander 3, and an evaporator 5 are sequentially connected to circulate refrigerant.
  • a radiator capacity controller 8 that controls the capacity of the radiator 2 or an evaporator capacity controller 10 that controls the capacity of the evaporator 5 is provided.
  • the refrigeration cycle apparatus preferably also includes a generator 4 connected to the expander 3.
  • the expander 3 recovers power by converting the expansion energy of the refrigerant into mechanical energy.
  • the expansion machine 3 converts the expansion energy of the refrigerant into mechanical energy (rotational energy) and recovers it, and supplies the recovered mechanical energy (rotational energy) to the generator 4 to generate electric power.
  • the generated electric power is used, for example, as a drive source for the compressor 1.
  • the generator 4 that generates electric power by supplying the expansion energy recovered by the expander 3, Since it is possible to reduce the load on the compressor at startup, it is possible to reduce power consumption.
  • the radiator 2 includes an air cooling type and a water cooling type.
  • the radiator capacity controller 8 is for controlling the radiator capacity, that is, the heat radiation amount of the radiator 2, and includes a cooling means for the radiator 2. Cooling means include those that exchange heat by sending air to the radiator using a radiator fan (air-cooled), and those that exchange heat using water or other fluids (such as water-cooled).
  • the radiator 2 is an air-cooled heat exchanger
  • the radiator capacity controller 8 is a radiator fan control that supplies voltage to the electric radiator fan 9 and the radiator fan 9. It consists of part 31.
  • One of the features of the first embodiment is that the ability of the radiator fan 9 provided in the outdoor unit during the cooling operation is reduced by the radiator fan control unit 31. By reducing the capacity of the radiator fan 9 at startup, the temperature of the radiator 2 rises quickly. Thereby, the high pressure at the inlet of the expander 3 can be increased, and the expander 3 can be driven quickly.
  • the problem can be solved by quickly increasing the high-low pressure difference between the inlet and the outlet of the expander 3. This can be achieved by increasing the high pressure at the expander inlet or decreasing the low pressure at the expander outlet.
  • the temperature of the radiator 2 may be increased due to the physical properties of the refrigerant. In other words, if you operate the refrigeration cycle to increase AT (K) from (Equation 1), you should decrease K (W / m 2 K) or A (m 2 )!
  • the evaporator capacity controller 10 is for controlling the amount of heat absorbed by the evaporator 5, and includes heating means for the evaporator 5.
  • the evaporator 5 is also an air-cooled heat exchanger.
  • the evaporator capacity controller 10 includes an electric evaporator fan 11 and an evaporator fan controller 32 that supplies voltage to the evaporator fan 11. Heat exchange with air and evaporator 5.
  • Another feature of the first embodiment is that the ability of the evaporator fan 11 provided in the outdoor unit during the heating operation is reduced by the evaporator fan control unit 32. In order to shorten the time until the tension machine 3 is driven, it is necessary to quickly ensure the high-low pressure difference at the inlet / outlet of the expander 3.
  • One method for this is to quickly reduce the low pressure at the outlet of the expander 3, that is, to quickly reduce the temperature of the evaporator 5.
  • the temperature of the evaporator 5 quickly decreases. Thereby, the low pressure at the outlet of the expander 3 can be reduced, and the expander 3 can be driven quickly.
  • the refrigeration cycle apparatus of Embodiment 1 desirably further includes a bypass circuit 6 that bypasses the expander 3, and an expansion valve 7 as a decompression means in the bypass circuit 6.
  • a bypass circuit 6 that bypasses the expander 3, and an expansion valve 7 as a decompression means in the bypass circuit 6.
  • the compressor 1 When the compressor 1 is started, the refrigerant flows into the bypass circuit 6 side, and at least one of the heat sink fan 9 and the evaporator fan 11 has a capacity for a predetermined time (for example, 3 minutes or more) during normal operation. It is desirable to control to reduce. This prevents the refrigeration cycle from being blocked when the compressor 1 is started, so it is possible to avoid an abnormal drop in the low pressure of the refrigeration cycle, improving the reliability of the compressor 1 and starting the compressor 1. At the same time, the power recovery loss of the expander 3 can be reduced.
  • the refrigeration cycle apparatus of the first embodiment includes a controller (control) that controls the start and stop of the compressor 1, the opening of the expansion valve 7, the radiator capacity controller 8, and the evaporator capacity controller 10.
  • Instrument) 211 The controller 211 includes a timer 221.
  • the timer 221 may be provided in connection with the controller 211 outside the force controller 211 provided in the controller 211 in FIG. As will be described later, it is possible to construct a simple and low-cost system by shifting from the control of the refrigeration cycle apparatus when the compressor 1 is started to the control during normal operation by the timer 222.
  • the low-temperature and low-pressure refrigerant is compressed by the operation of the compressor 1, becomes a high-temperature and high-pressure refrigerant, and is discharged (A ⁇ B).
  • the discharged refrigerant exchanges heat with the outdoor air during the cooling operation and indoor air during the heating operation and flows into the expander 3 by the action of the radiator fan 9 in the radiator 2 (B ⁇ C).
  • the coefficient of performance COP (IB -iC) / ((iB-iA)-(iE— iD)), reducing the required power of the compressor 1 compared to a refrigeration cycle system that is enthalpy-expanded with a conventional expansion valve, a capillary tube, etc. Can improve efficiency.
  • the electric power generated by the generator 4 is used as a drive source for the compressor 1.
  • the coefficient of performance COP ((iA—iE) + (iE-iD)) / ((iB-iA) one (iE— iD)), and so on with conventional expansion valves, cylindrical tubes, etc.
  • the required power of the compressor 1 is reduced and the refrigeration effect is increased, so that the efficiency is further improved.
  • controller 211 starts the compressor 1 and starts the accumulated power S of the timer 221 and starts it. Go to step 100.
  • controller 211 sends a signal to radiator capacity controller 8 and evaporator capacity controller 10 to stop radiator fan 9 and evaporator fan 11 (or keep it stopped). Then, control the throttle opening of the expansion valve 7 appropriately, and proceed to Step 110.
  • the expansion energy is not recovered by the expander 3 (the expander 3 is in a stopped state), and the refrigerating cycle operation in which the expansion valve 7 performs isenthalpy expansion is performed.
  • step 110 the integrated value TA of the timer 221 is compared with a preset set time TX1. If the accumulated value TA of timer 221 is smaller than the set time TX1, return to start step 100 to avoid blockage of the freezing cycle, and start step 100 until the accumulated value TA of timer 221 reaches the set time TX1 or more. Maintain the operating state of.
  • the operation proceeds to normal operation step 120, and a signal is sent from the controller 211 to the radiator capacity controller 8 and the evaporator capacity controller 10, and the fan for the radiator 9
  • the evaporator fan 11 is operated at a set speed suitable for normal operation, the expansion valve 7 is fully closed, the capacity of the radiator 2 and the evaporator 5 is maximized, and the refrigerant is applied only to the expander 3 side. To recover the expansion energy.
  • the integrated value TA of the timer 221 is reset.
  • step 120 When the normal operation step 120 is continued, for example, when an indoor temperature detection means (not shown) detects a set temperature or higher, the routine proceeds to step 130, where the controller 211 controls the compressor 1, the radiator fan 9, and the evaporator fan. 11 stops.
  • FIG. 5 the pressure change at the inlet / outlet of the expander 3 is shown by a solid line, and the differential pressure at the inlet / outlet of the expander 3 is shown by a broken line when the compressor 1 is activated.
  • the pressure at the inlet / outlet of the expander 3 is in a balanced state, so the differential pressure is almost OMPa.
  • the refrigeration cycle apparatus of the first embodiment is configured to include the bypass circuit 6 that bypasses the expander 3, but as shown in FIG. 6, the bypass circuit 6 that bypasses the expander 3. Even when the compressor 1 is started, the radiator fan 9 or the evaporator fan 11 1 is stopped when the compressor 1 is started, so that the expander can be operated more quickly than when the radiator fan 9 or the evaporator fan 11 is normally operated. 3 can be driven.
  • the radiator fan 9 and the evaporator fan 11 are stopped.
  • the applied voltage to each fan is smaller than that during normal operation, and the radiator 2 and
  • the radiator fan 9 and the evaporator fan 11 are stopped or decelerated when the compressor 1 is started.
  • the gist of the present invention is that when the compressor is started in the air conditioner or the like.
  • the radiator fan provided in the outdoor unit is stopped or decelerated, or the evaporator fan provided in the outdoor unit is stopped or decelerated when starting the compressor in a heater or the like.
  • the outdoor fan is particularly stopped or decelerated.
  • the refrigeration cycle apparatus of Embodiment 2 includes a first pressure gauge 12 that detects the inlet pressure of the expander 3 in addition to the refrigeration cycle apparatus shown in FIG.
  • a second pressure gauge 13 for detecting the outlet pressure of the expander 3 is arranged in the outlet pipe of the expander 3 on the side pipe, and the signals from the first pressure gauge 12 and the second pressure gauge 13 are And a controller (controller) 212 for controlling the opening degree of the expansion valve 7, the radiator capacity controller 8, and the evaporator capacity controller 10.
  • the operation method of the refrigeration cycle apparatus of the second embodiment is performed by the timer in the first embodiment! /, And the start step force also shifts to the normal operation step.
  • This is a control method in which the difference between the pressure detected by the second pressure gauge 13 and the second pressure gauge 13 exceeds a set value.
  • the arrangement position of the first pressure gauge 12 is most suitable on the inlet side of the expander 3, but from the discharge side of the compressor 1 of the refrigeration cycle to the outlet of the radiator 2.
  • the same role can be played everywhere.
  • the piping on the outlet side of the expander 3 is most appropriate as the position of the second pressure gauge 13, but from the outlet side of the expander 3 of the refrigeration cycle, the compressor 1 If the suction side, can play the same role
  • the compressor 212 is started by the controller 212, and the start step 200 is performed.
  • a signal is sent from the controller 212 to the radiator capacity controller 8 and the evaporator capacity controller 10 to stop the heat radiator fan 9 and the evaporator fan 11 (or continue the stopped state).
  • the throttle opening degree of the expansion valve 7 is appropriately controlled, and the routine proceeds to step 210.
  • expansion energy is not collected by the expander 3 (the expander 3 is in a stopped state), and the refrigeration cycle operation in which the expansion valve 7 performs isenthalpy expansion is performed.
  • step 210 the controller 212 calculates a difference A (PG-PE) between the detected value PG (inlet pressure) of the first pressure gauge 12 and the detected value PE (outlet pressure) of the second pressure gauge 13. While calculating, the difference ⁇ (PG-PE) is compared with the preset differential pressure value ⁇ . If the difference ⁇ (PG-PE) is smaller than the differential pressure value ⁇ , the operation returns to the start step 200, and the operation state of the start step 200 is maintained until the difference A (PG-PE) exceeds the differential pressure value ⁇ PX. .
  • the operation proceeds to the normal operation step 220, and the controller 212 sends a signal to the radiator capacity controller 8 and the evaporator capacity controller 10, and the radiator fan 9 And the evaporator fan 11 and the expansion valve 7 are fully closed, the capacity of the radiator 2 and the evaporator 5 is increased, and the refrigerant is supplied only to the expander 3 side to recover the expansion energy. It becomes a state.
  • step 230 is performed.
  • the controller 212 stops the compressor 1, the radiator fan 9, and the evaporator fan 11 by the controller 212.
  • FIG. 9 shows a refrigeration cycle apparatus as a modified example of the above-described second embodiment.
  • a first thermometer 14 that detects the temperature of the evaporator 5 is shown. (For example, a thermistor).
  • a thermistor By moving from the startup step of the compressor 1 to the normal operation step based on the pressure value detected by the first pressure gauge 12 and the temperature detected by the first thermometer 14, accurate and low-cost The step transition can be realized.
  • the first thermometer 14 is in a position where the temperature of the evaporator 5 can be detected.
  • the outlet force of the expander 3 may be installed in a pipe leading to the outlet of the evaporator 5.
  • the refrigeration cycle apparatus includes a controller (controller) 213 for controlling the opening degree of the radiator capacity controller 8, the evaporator capacity controller 10, and the expansion valve 7, as shown in FIG. It has.
  • the controller 213 is provided with expander outlet pressure calculating means for calculating the physical force saturation pressure of the refrigerant used, that is, the pressure on the outlet side of the expander 3, based on the temperature detected by the first thermometer 14. Speak.
  • the controller (controller) 213 starts up the compressor 1 and proceeds to the start step 300.
  • signals are sent from the controller 213 to the radiator capacity controller 8 and the evaporator capacity controller 10 to stop the radiator fan 9 and the evaporator fan 11 and to stop the expansion valve 7 Adjust the opening appropriately, and go to Step 310.
  • the controller 213 is equipped with The detected value force of the first thermometer 14 and the outlet pressure PE ′ of the expander 3 are always calculated by the expanded expander outlet pressure calculation means. At this time, the expansion energy is not recovered by the expander 3 (the expander 3 is in a stopped state), and the refrigerating cycle operation in which the expansion valve 7 performs isenthalpy expansion is performed.
  • step 310 the controller 213 determines the difference A between the detected value PG (inlet pressure) of the first pressure gauge 12 and the outlet pressure PE 'of the expander 3 that also estimates the detected value force of the first thermometer 14.
  • PG ⁇ PE ′ is calculated and the difference ⁇ (PG ⁇ PE ′) is compared with a preset differential pressure value ⁇ . If the difference A (PG— ⁇ ′) is smaller than the differential pressure value ⁇ , the process returns to the start step 300, and the operating state of the start step 300 is changed until the differential ⁇ (PG—PE ′) becomes greater than the differential pressure value ⁇ . maintain.
  • the operation proceeds to the normal operation step 320, and the controller 213 sends a signal to the radiator capacity controller 8 and the evaporator capacity controller 10 for the radiator. Operate fan 9 and evaporator fan 11 and fully expand expansion valve 7 to increase the capacity of radiator 2 and evaporator 5 and supply refrigerant only to expander 3 side to recover expansion energy. It becomes a driving state.
  • step 330 the controller 1, the compressor 1, the radiator fan 9, and the evaporator fan 11 are stopped by the controller 213.
  • FIG. 11 shows a refrigeration cycle apparatus as another modification of the above-described second embodiment, and a pipe extending from the discharge side of the compressor 1 to the inlet of the radiator 2 without using a pressure gauge.
  • This is a configuration using a second thermometer 15 that detects the temperature.
  • Inlet machine 3 inlet pressure and compressor 1
  • the discharge side force of the radiator has a correlation with the temperature of the pipe leading to the inlet of the radiator 2, so by measuring the discharge temperature of the compressor 1, the inlet pressure of the expander 3 is estimated, and based on this inlet pressure Therefore, the differential pressure across the expander 3 can be estimated.
  • thermometer 15 when the second thermometer 15 detects a set temperature or higher, a signal is sent from the controller (controller) 214 to the radiator capacity controller 8 and the evaporator capacity controller 10 to dissipate heat.
  • controller controller
  • the fan 9 and the evaporator fan 11 are operated and the expansion valve 7 is fully closed, the capacity of the radiator 2 and the evaporator 5 is increased, and the refrigerant is supplied only to the expander 3 side to recover the expansion energy.
  • the transition to the normal operation state can be realized at a lower cost.
  • FIG. 12 shows a schematic diagram of the refrigeration cycle apparatus in the third embodiment.
  • the same components as those in the first embodiment are given the same reference numerals.
  • the refrigeration cycle apparatus of the third embodiment is provided with an ammeter 16 for detecting the current flowing through the generator 4, and the opening of the expansion valve 7, the heat dissipation by the signal of the ammeter 16.
  • a controller (controller) 215 for controlling the vessel capacity controller 8 and the evaporator capacity controller 10 is provided.
  • the compressor 1 is activated by the controller 215, and the activation step 400 is performed.
  • a signal is sent from the controller 215 to the radiator capacity controller 8 and the evaporator capacity controller 10 to stop the heat radiator fan 9 and the evaporator fan 11 and to open the throttle valve 7 Is appropriately controlled, and the process proceeds to Step 410.
  • the expansion energy is not recovered by the expander 3 (the expander 3 is in a stopped state), and the refrigeration cycle operation in which the expansion valve 7 performs isenthalpy expansion.
  • step 410 the controller 215 detects the current value A 1 flowing through the generator 4 from the ammeter 16, and proceeds to step 420.
  • step 420 the current value A1 flowing through the generator 4 is compared with a preset current value AX (eg, 0 amperes). The current value A1 flowing through the generator 4 is If it is smaller than the preset current value AX, it is determined that the generator 4 has not started generating power, that is, the expander 3 is not driven, and the current value A1 flowing through the generator 4 is preset.
  • the start step 400 is maintained until the current value exceeds AX.
  • the generator 4 When the current value A1 flowing through the generator 4 is greater than or equal to the preset current value AX, it is determined that the generator 4 has started generating power, that is, the expander 3 is operating, and the normal operation step 430 Then, a signal is sent from the controller 215 to the radiator capacity controller 8 and the evaporator capacity controller 10 to operate the radiator fan 9 and the evaporator fan 11, and the expansion valve 7 is fully closed. In addition, the capacity of the evaporator 5 is increased, and the refrigerant is supplied only to the expander 3 side to recover the expansion energy.
  • step 440 when an indoor temperature detection means (not shown) detects a set temperature or higher, the process proceeds to step 440, and the compressor 1, the radiator fan 9, and the evaporator fan 11 are stopped by the controller 215.
  • FIG. 14 shows a schematic diagram of the refrigeration cycle apparatus in the fourth embodiment.
  • the same components as those in Embodiments 1 to 3 are denoted by the same reference numerals.
  • the refrigeration cycle apparatus of the fourth embodiment includes a primary side refrigerant circuit 17 and a secondary side refrigerant circuit 18.
  • the primary refrigerant circuit 17 includes a compressor 1, a water-cooled radiator 2 having, for example, a double pipe specification, an expander 3 that recovers power by converting expansion energy of the refrigerant into mechanical energy, and an evaporator 5 Are sequentially connected in series, and a bypass circuit 6 for bypassing the expander 3 is provided, and an expansion valve 7 is provided in the bypass circuit 6 as a pressure reducing means.
  • the secondary refrigerant circuit 18 includes a hot water storage tank 19, a radiator 2, and a circulation pump 20 for circulating water.
  • the radiator capacity controller 8 includes a circulation pump 20 and a circulation pump control unit 33 that supplies voltage to the circulation pump 20.
  • the amount of water flowing through the secondary refrigerant circuit 18 is variable by the action of the circulation pump 20. Especially This makes it possible to control the capacity of radiator 2.
  • the radiator 2 is configured such that the refrigerant flows in the primary side refrigerant circuit 17 and the secondary side refrigerant circuit 18 are opposed to each other.
  • the hot water storage tank 19 is configured to supply tap water from the lower part and supply hot water that has become hot due to the action of the radiator 2 from the upper part to the use side circuit 21. Is supplied to the bath tub 23 through the hot-water tap 22 for use.
  • the hot water storage tank 19 is provided with a hot water storage tank water temperature thermometer 24 (for example, a thermistor) that detects the water temperature in the hot water storage tank 19.
  • a controller (controller) 216 having a built-in timer 226 for controlling the start and stop, as well as the opening degree of the expansion valve 7, the radiator capacity controller 8, and the evaporator capacity controller 10 is provided.
  • step 500 when the hot water tank water temperature TB (° C) detected by the hot water tank water temperature thermometer 24 detects that the temperature is lower than the set temperature TL (° C), the process proceeds to step 510, and the controller 216 At the same time, timer 226 integration starts.
  • start-up step 520 a signal is sent from the controller 216 to the radiator capacity controller 8 and the evaporator capacity controller 10, and the circulation pump 20 and the evaporator fan 11 are stopped (or kept stopped), and the expansion valve Adjust the throttle opening of 7 as appropriate, and go to Step 530.
  • the expansion energy is not recovered by the expander 3 (the expander 3 is in a stopped state), and the refrigeration cycle operation in which the expansion valve 7 performs isenthalpy expansion is performed.
  • step 530 the integrated value TA of timer 226 is compared with preset time TX2. In step 530, until the accumulated value TA of the timer 226 exceeds the set time TX2, the process returns to the start step 520, and the operation state of the start step 520 is maintained until the accumulated value TA of the timer 226 becomes larger than the set time TX2.
  • the routine proceeds to normal operation step 540, and a signal is sent from the controller 216 to the radiator capacity controller 8 and the evaporator capacity controller 10, and the circulation pump 20 and Normal operation in which the evaporator fan 11 is operated and the expansion valve 7 is fully closed to increase the capacity of the radiator 2 and the evaporator 5 and the refrigerant is supplied only to the expander 3 side to recover the expansion energy. It becomes a state. At this time, the integrated value TA of the timer 226 is reset.
  • step 550 when the hot water storage tank water temperature TB (° C) detected by the hot water storage tank water temperature thermometer 24 in step 550 detects the set temperature TH (° C) or more, the process proceeds to step 560 and the controller 216 The compressor 1, the circulation pump 20, and the evaporator fan 11 are stopped.
  • the pressure change at the inlet / outlet of the expander 3 when the compressor 1 is activated is indicated by a solid line
  • the differential pressure at the inlet / outlet of the expander 3 is indicated by a broken line.
  • the operation proceeds from step 530 to the normal operation step 540, and at the same time the expander 3 is driven, the controller 216 operates the circulation pump 20 and the evaporator fan 11 and the expansion valve 7 is fully closed, and the radiator 2 And the capacity of the evaporator 5 can be increased.
  • the configuration includes the bypass circuit 6 that bypasses the expander 3.
  • the compressor 1 can be started even when the bypass circuit 6 that bypasses the expander 3 is not provided.
  • the expander 3 can be driven quickly.
  • the force that is supposed to stop the circulation pump 20 when the compressor 1 is started is made smaller than that during normal operation, and the secondary refrigerant flows into the radiator 2 more than during normal operation.
  • the applied voltage to the circulation pump 20 is made smaller than that during normal operation, and the secondary refrigerant flows into the radiator 2 more than during normal operation.
  • a freezing cycle using hot water such as a water heater. Since the high pressure in the refrigeration cycle can also be quickly increased in the air flow device, the differential pressure necessary for driving the expander 3 can be quickly secured, and the time until the expander 3 is driven. Therefore, the power recovery port of the expander 3 when the compressor 1 is started can be reduced.
  • Embodiments 1 to 4 it is desirable to use carbon dioxide as the refrigerant.
  • At the time of starting up the compressor at least one of the cooling means of the radiator 2 and the heating means of the evaporator 5 is maintained for a predetermined time during normal operation.
  • By controlling to reduce the capacity it is possible to reduce the power recovery loss of the expander at the time of starting the compressor, so hot water heaters, air conditioning and air conditioning equipment, vending machines, household refrigerators, commercial use It can be applied to a wide range of equipment such as refrigerators and ice makers.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

La présente invention concerne un procédé d’actionnement d’un dispositif de cycle de réfrigération dans lequel un compresseur (1), un radiateur (2), un dispositif d’expansion (3) et un évaporateur (5) sont reliés de manière séquentielle pour faire circuler un réfrigérant. Le radiateur (2) est prévu au niveau d'une unité intérieure ou d’une unité extérieure et l'évaporateur (5) au niveau de l'autre de ces unités. La capacité d’un ventilateur extérieur est réglée de manière à être plus faible au moment du démarrage du compresseur (1) que celle du fonctionnement normal, et ce pendant une période prédéterminée au-delà de laquelle le ventilateur extérieur est actionné à une vitesse pré-établie pour le fonctionnement normal.
PCT/JP2006/303870 2005-04-14 2006-03-01 Dispositif de cycle de refrigeration et procede d’actionnement de celui-ci WO2006112157A1 (fr)

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JP2005-116840 2005-04-14
JP2005116840A JP2008175402A (ja) 2005-04-14 2005-04-14 冷凍サイクル装置の運転方法

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WO2006112157A1 true WO2006112157A1 (fr) 2006-10-26

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012092274A1 (fr) * 2010-12-30 2012-07-05 Scherer John S Système frigorifique régulé par la qualité de l'agent frigorigène à l'intérieur de l'évaporateur
WO2012107959A1 (fr) * 2011-02-09 2012-08-16 三菱電機株式会社 Dispositif de réfrigération et de conditionnement d'air
US9791188B2 (en) 2014-02-07 2017-10-17 Pdx Technologies Llc Refrigeration system with separate feedstreams to multiple evaporator zones
WO2018010708A1 (fr) * 2016-07-15 2018-01-18 Zefira Consulting, SE Circuit de refroidissement pour circulation de milieu de refroidissement

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140075941A1 (en) 2012-09-14 2014-03-20 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Power generating apparatus and operation method thereof
WO2016147291A1 (fr) * 2015-03-16 2016-09-22 三菱電機株式会社 Dispositif de réfrigération

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JP2001116371A (ja) * 1999-10-20 2001-04-27 Daikin Ind Ltd 空気調和装置
JP2003042574A (ja) * 2001-08-01 2003-02-13 Denso Corp 蒸気圧縮式冷凍機
JP2004060989A (ja) * 2002-07-29 2004-02-26 Denso Corp 蒸気圧縮式冷凍機及び膨脹機一体型圧縮機
JP2004144399A (ja) * 2002-10-25 2004-05-20 Matsushita Electric Ind Co Ltd 冷凍サイクル装置

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Publication number Priority date Publication date Assignee Title
JP2001116371A (ja) * 1999-10-20 2001-04-27 Daikin Ind Ltd 空気調和装置
JP2003042574A (ja) * 2001-08-01 2003-02-13 Denso Corp 蒸気圧縮式冷凍機
JP2004060989A (ja) * 2002-07-29 2004-02-26 Denso Corp 蒸気圧縮式冷凍機及び膨脹機一体型圧縮機
JP2004144399A (ja) * 2002-10-25 2004-05-20 Matsushita Electric Ind Co Ltd 冷凍サイクル装置

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012092274A1 (fr) * 2010-12-30 2012-07-05 Scherer John S Système frigorifique régulé par la qualité de l'agent frigorigène à l'intérieur de l'évaporateur
US8646286B2 (en) 2010-12-30 2014-02-11 Pdx Technologies Llc Refrigeration system controlled by refrigerant quality within evaporator
US10365018B2 (en) 2010-12-30 2019-07-30 Pdx Technologies Llc Refrigeration system controlled by refrigerant quality within evaporator
WO2012107959A1 (fr) * 2011-02-09 2012-08-16 三菱電機株式会社 Dispositif de réfrigération et de conditionnement d'air
JP5484604B2 (ja) * 2011-02-09 2014-05-07 三菱電機株式会社 冷凍空調装置
US9791188B2 (en) 2014-02-07 2017-10-17 Pdx Technologies Llc Refrigeration system with separate feedstreams to multiple evaporator zones
US11306951B2 (en) 2014-02-07 2022-04-19 Pdx Technologies Llc Refrigeration system with separate feedstreams to multiple evaporator zones
WO2018010708A1 (fr) * 2016-07-15 2018-01-18 Zefira Consulting, SE Circuit de refroidissement pour circulation de milieu de refroidissement

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