WO2017047354A1 - 複数段圧縮式冷凍サイクル装置 - Google Patents
複数段圧縮式冷凍サイクル装置 Download PDFInfo
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- WO2017047354A1 WO2017047354A1 PCT/JP2016/074962 JP2016074962W WO2017047354A1 WO 2017047354 A1 WO2017047354 A1 WO 2017047354A1 JP 2016074962 W JP2016074962 W JP 2016074962W WO 2017047354 A1 WO2017047354 A1 WO 2017047354A1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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- 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
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- 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
- F25B2400/13—Economisers
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- 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
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- 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
- F25B2500/29—High ambient temperatures
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- 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
- F25B2600/021—Inverters therefor
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- 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
- F25B2600/022—Compressor control for multi-stage operation
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- 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
- F25B2600/0253—Compressor control by controlling speed with variable speed
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- 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
- F25B2600/11—Fan speed control
- F25B2600/111—Fan speed control of condenser fans
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- 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
- F25B2600/11—Fan speed control
- F25B2600/112—Fan speed control of evaporator fans
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- 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
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- 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
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- 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
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- 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
- F25B2700/2106—Temperatures of fresh outdoor air
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- 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
- F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
- F25B2700/21172—Temperatures of an evaporator of the fluid cooled by the evaporator at the inlet
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Definitions
- the present disclosure relates to a multi-stage compression refrigeration cycle apparatus including a multi-stage compression mechanism.
- the multistage compression refrigeration cycle apparatus of Patent Document 1 is configured as a so-called economizer refrigeration cycle.
- the economizer refrigeration cycle includes a radiator that radiates high-pressure refrigerant discharged from the high-stage compression mechanism, and an intermediate-pressure expansion valve that decompresses and expands part of the high-pressure refrigerant flowing out of the radiator until it becomes intermediate-pressure refrigerant. Yes.
- the intermediate-pressure refrigerant decompressed by the intermediate-pressure expansion valve is guided to the suction side of the high-stage compression mechanism.
- the high-stage compression mechanism can suck a mixed refrigerant of the intermediate-pressure refrigerant decompressed by the intermediate-pressure expansion valve and the intermediate-pressure refrigerant discharged from the low-stage compression mechanism. it can.
- the mixed refrigerant having a lower temperature can be sucked into the high stage side compression mechanism than when the intermediate pressure refrigerant discharged from the low stage side compression mechanism is sucked. Efficiency can be improved.
- the conventional apparatus is configured such that the rotation speeds of the low-stage compressor and the high-stage compressor are controlled so that the rotation speed ratio between the low-stage compression mechanism and the high-stage compression mechanism is constant.
- such a device protects the motor provided in the high stage compressor when the temperature in the warehouse is high, so that the rotational speed of the high stage compressor is less than a predetermined protection control value. Limited. For this reason, the rotation speeds of the low-stage compressor and the high-stage compressor cannot be sufficiently increased, and it takes a long time to cool the interior when the apparatus is started.
- This disclosure aims to shorten the cool-down time when starting up the apparatus without increasing the size of each compressor.
- a multi-stage compression refrigeration cycle apparatus includes a low-stage compression mechanism that compresses and discharges low-pressure refrigerant until it becomes intermediate-pressure refrigerant, and an intermediate medium that is discharged from the low-stage compression mechanism.
- a high-stage compression refrigeration cycle apparatus comprising a high-stage compression mechanism that compresses and discharges pressurized refrigerant until it becomes high-pressure refrigerant, wherein the high-pressure refrigerant discharged from the high-stage compression mechanism is heated with outdoor air and heat.
- a heat radiator that radiates heat by exchanging, an intermediate pressure expansion valve that decompresses and expands the high-pressure refrigerant that flows out of the heat radiator until it becomes an intermediate-pressure refrigerant, and flows out to the suction side of the high-stage compression mechanism, and a high pressure that flows out of the radiator
- a low-pressure expansion valve that decompresses and expands the refrigerant until it becomes a low-pressure refrigerant
- the low-pressure refrigerant decompressed and expanded by the low-pressure expansion valve exchanges heat with the blown air that blows air to the space to be cooled, evaporates, and sucks the low-stage compression mechanism With the evaporator flowing out to the side
- a control device for controlling the rotational speed of the low-stage compression mechanism and a higher stage compression mechanism, and a physical quantity sensor for detecting a physical quantity correlating to the pressure of the low pressure refrigerant, a.
- the control device is configured to increase the rotation speed ratio of the low
- control device is configured to increase the rotation speed ratio of the low-stage compression mechanism with respect to the rotation speed of the high-stage compression mechanism as the pressure of the low-pressure refrigerant increases, based on the physical quantity detected by the physical quantity sensor. ing. For this reason, even if the rotation speed of the high stage compressor is limited, the rotation speed of the low stage compression mechanism can be increased to improve the refrigerating capacity of the evaporator. Therefore, the cool-down time when starting up the apparatus can be shortened without increasing the size of each compressor.
- FIG. 1 is an overall configuration diagram of a multistage compression refrigeration cycle apparatus according to an embodiment. It is a flowchart which shows the control processing of the control apparatus of the multistage compression refrigeration cycle apparatus which concerns on embodiment. It is a figure showing the relationship between the optimal rotation speed ratio of a low stage side compressor and a high stage side compressor, and a low pressure refrigerant pressure. It is the figure which showed the relationship of the time characteristic of the rotation speed ratio of the high stage side compression mechanism after implementing cool down, and the low stage side compression mechanism. It is the figure which showed the relationship between internal temperature and cool down time. It is the figure which showed the result of having calculated
- FIG. 1 is an overall configuration diagram of a multiple-stage compression refrigeration cycle apparatus according to the present embodiment.
- This multi-stage compression refrigeration cycle apparatus is applied to a refrigerator and has a function of cooling the blown air blown into a freezer as a cooling target space to an extremely low temperature of about ⁇ 30 ° C. to ⁇ 10 ° C. Fulfill.
- the multistage compression refrigeration cycle apparatus includes two compressors, a high-stage compressor 11 and a low-stage compressor 12, so that the refrigerant circulating in the cycle is multistage.
- the pressure is increased.
- coolant a normal freon-type refrigerant
- coolant for example, R404A
- the refrigerant is mixed with refrigerating machine oil (that is, oil) for lubricating the sliding parts in the low-stage compressor 12 and the high-stage compressor 11, and a part of the refrigerating machine oil is cycled together with the refrigerant. Is circulating.
- the low-stage compressor 12 includes a low-stage compression mechanism 12a that compresses and discharges the low-pressure refrigerant until it becomes an intermediate-pressure refrigerant, and a low-stage electric motor 12b that rotationally drives the low-stage compression mechanism 12a. It is an electric compressor having.
- the low-stage electric motor 12b is an AC motor whose operation (for example, the number of rotations) is controlled by an alternating current output from the low-stage inverter 22. Moreover, the low stage side inverter 22 outputs the alternating current of the frequency according to the control signal output from the refrigerator control apparatus 20 mentioned later. And by this frequency control, the refrigerant
- the low-stage electric motor 12b constitutes the discharge capacity changing unit of the low-stage compressor 12.
- a DC motor may be employed as the low-stage electric motor 12b, and the rotation speed may be controlled by a control voltage output from the refrigerator control device 20.
- the suction port side of the high-stage compressor 11 is connected to the discharge port of the low-stage compression mechanism 12a.
- the basic configuration of the high stage compressor 11 is the same as that of the low stage compressor 12. Accordingly, the high-stage compressor 11 includes a high-stage compression mechanism 11a that compresses and discharges the intermediate-pressure refrigerant discharged from the low-stage compressor 12 until it becomes a high-pressure refrigerant, and a high-stage electric motor 11b. It is an electric compressor having.
- the rotation speed of the high stage side electric motor 11 b is controlled by the alternating current output from the high stage side inverter 21. Further, the compression ratio of the high-stage compression mechanism 11a and the compression ratio of the low-stage compression mechanism 12a of the present embodiment are substantially the same.
- the refrigerant inlet side of the radiator 13 is connected to the discharge port of the high stage side compression mechanism 11a.
- the heat radiator 13 performs heat exchange between the high-pressure refrigerant discharged from the high-stage compressor 11 and the outside air blown by the cooling fan 13a (that is, outdoor air) to dissipate the high-pressure refrigerant and cool it. Heat exchanger.
- the refrigerator control device 20 constitutes a control device that controls the rotational speeds of the low-stage compression mechanism 12a and the high-stage compression mechanism 11a. More specifically, the refrigerator control device 20 controls the number of rotations of the low-stage electric motor 12b that rotates the low-stage compression mechanism 12a and the high-stage electric motor 11b that rotates the high-stage compression mechanism 11a. Configure the device.
- the cooling fan 13a is an electric blower whose rotation speed is controlled by a control voltage output from the refrigerator control device 20. The amount of blown air is determined according to this rotational speed.
- a chlorofluorocarbon refrigerant is employed as the refrigerant, and a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant is configured. Functions as a condenser to condense the refrigerant.
- a branching portion 14 for branching the flow of the refrigerant flowing out of the radiator 13 is connected to the refrigerant outlet of the radiator 13.
- the branch part 14 has a three-way joint structure having three inflow / outlets.
- One of the inflow / outflow ports is a refrigerant inflow port, and two are refrigerant outflow ports.
- Such a branch part 14 may be configured by joining pipes, or may be configured by providing a plurality of refrigerant passages in a metal block or a resin block.
- the inlet side of the intermediate pressure expansion valve 15 is connected to one refrigerant outlet of the branch part 14, and the inlet side of the high-pressure refrigerant flow path 16 a of the intermediate heat exchanger 16 is connected to the other refrigerant outlet of the branch part 14.
- the intermediate pressure expansion valve 15 is a temperature type expansion valve that expands the high pressure refrigerant flowing out of the radiator 13 under reduced pressure until it becomes intermediate pressure refrigerant and flows out to the suction side of the high-stage compression mechanism 11a.
- the intermediate pressure expansion valve 15 has a temperature sensing portion disposed on the outlet side of the intermediate pressure refrigerant channel 16b of the intermediate heat exchanger 16, and the temperature of the refrigerant on the outlet side of the intermediate pressure refrigerant channel 16b. Based on the pressure, the degree of superheat of the refrigerant on the outlet side of the intermediate pressure refrigerant flow path 16b is detected.
- the intermediate pressure expansion valve 15 adjusts the valve opening degree by a mechanical mechanism so that the degree of superheat becomes a predetermined value set in advance.
- the intermediate pressure expansion valve 15 refrigerant flow rate is determined according to the valve opening. Further, the outlet side of the intermediate pressure expansion valve 15 is connected to the inlet side of the intermediate pressure refrigerant flow path 16b.
- the intermediate heat exchanger 16 is decompressed and expanded by the intermediate pressure expansion valve 15 and circulates through the intermediate pressure refrigerant flow path 16b, and the other is branched at the branch portion 14 and circulated through the high pressure refrigerant flow path 16a. Exchanges heat with high-pressure refrigerant. Since the temperature of the high-pressure refrigerant is reduced by reducing the pressure, in the intermediate heat exchanger 16, the intermediate-pressure refrigerant flowing through the intermediate-pressure refrigerant channel 16b is heated, and the high-pressure refrigerant flowing through the high-pressure refrigerant channel 16a is cooled. Will be.
- the intermediate heat exchanger 16 a double-pipe heat exchanger configuration in which an inner tube forming the intermediate pressure refrigerant flow channel 16b is arranged inside the outer tube forming the high pressure refrigerant flow channel 16a.
- the high-pressure refrigerant channel 16a may be an inner tube
- the intermediate-pressure refrigerant channel 16b may be an outer tube.
- coolant piping which forms the high pressure refrigerant flow path 16a and the intermediate pressure refrigerant flow path 16b, and heat-exchange may be employ
- the flow direction of the high-pressure refrigerant flowing through the high-pressure refrigerant flow path 16a and the flow direction of the intermediate pressure refrigerant flowing through the intermediate-pressure refrigerant flow path 16b are the same.
- a heat exchanger is used.
- an AC type heat exchanger in which the flow direction of the high-pressure refrigerant flowing through the high-pressure refrigerant flow path 16a and the flow direction of the intermediate-pressure refrigerant flowing through the intermediate pressure refrigerant flow path 16b are opposite may be employed.
- the inlet side of the above-described high-stage compression mechanism 11a is connected to the outlet side of the intermediate pressure refrigerant flow path 16b of the intermediate heat exchanger 16 through a check valve (not shown). Therefore, the high-stage compression mechanism 11a of the present embodiment sucks the mixed refrigerant of the intermediate-pressure refrigerant that has flowed out from the intermediate-pressure refrigerant flow path 16b and the intermediate-pressure refrigerant that is discharged from the low-stage compressor 12.
- the inlet side of the low-pressure expansion valve 17 is connected to the outlet side of the high-pressure refrigerant channel 16a of the intermediate heat exchanger 16.
- the low-pressure expansion valve 17 is a temperature type expansion valve that decompresses and expands the high-pressure refrigerant flowing out of the radiator 13 until it becomes a low-pressure refrigerant.
- the basic configuration of the low pressure expansion valve 17 is the same as that of the intermediate pressure expansion valve 15.
- the low-pressure expansion valve 17 has a temperature sensing portion arranged on the refrigerant outlet side of the evaporator 18 described later, and the evaporator 18 is based on the temperature and pressure of the refrigerant on the outlet side of the evaporator 18. The degree of superheat of the outlet side refrigerant is detected.
- the low pressure expansion valve 17 adjusts the valve opening degree by a mechanical mechanism so that the degree of superheat becomes a predetermined value set in advance.
- the flow rate of the refrigerant flowing through the low pressure expansion valve 17 is determined according to the valve opening.
- the refrigerant inlet side of the evaporator 18 is connected to the outlet side of the low pressure expansion valve 17.
- the evaporator 18 evaporates the low-pressure refrigerant and exhibits an endothermic effect by exchanging heat between the low-pressure refrigerant decompressed and expanded by the low-pressure expansion valve 17 and the blown air circulated through the freezer by the blower fan 18a.
- This is an endothermic heat exchanger.
- the blower fan 18 a is an electric blower whose rotation speed is controlled by a control voltage output from the refrigerator control device 20. The amount of air blown from the blower fan 18a is determined according to the rotational speed.
- the refrigerant outlet of the evaporator 18 is connected to the suction port side of the low-stage compression mechanism 12a.
- the refrigerator control device 20 includes a well-known microcomputer including a CPU and a storage circuit, an output circuit that outputs control signals or control voltages to various control target devices, an input circuit that receives detection signals of various sensors, and a power source It consists of a circuit and the like.
- the CPU performs control processing and arithmetic processing.
- the storage circuit is a ROM, a RAM, or the like that stores programs, data, and the like.
- the storage circuit is a non-transitional tangible storage medium.
- the above-described low-stage inverter 22, high-stage inverter 21, cooling fan 13a, blower fan 18a, and the like are connected to the output side of the refrigerator control device 20 as control target devices.
- the refrigerator control device 20 controls the operation of these control target devices.
- the refrigerator control device 20 is configured such that a control unit that controls the operation of these control target devices is integrally configured.
- the configuration (that is, hardware and software) that controls the operation of each control target device in the refrigerator control device 20 constitutes a control unit of each control target device.
- the configuration (that is, hardware and software) that controls the refrigerant discharge capacity of the low-stage side compression mechanism 12a by controlling the operation of the low-stage side inverter 22 is the first discharge capacity control unit 20a.
- a configuration (that is, hardware and software) that controls the refrigerant discharge capacity of the high-stage compression mechanism 11a by controlling the operation of the side inverter 21 is referred to as a second discharge capacity control unit 20b.
- the rotation speed of the low-stage side electric motor 12b and the rotation speed of the high-stage side electric motor 11b can be controlled independently of each other by the first discharge capacity control unit 20a and the second discharge capacity control unit 20b, respectively.
- the outside air temperature sensor 23, the internal temperature sensor 24, the low pressure sensor 25, the intermediate pressure sensor 26, the high pressure sensor 27, and the like are connected to the input side of the refrigerator control device 20. Detection signals from these sensors are input to the refrigerator control device 20.
- the outside air temperature sensor 23 detects the outside air temperature Tam of the outside air (that is, the outside air) that exchanges heat with the high-pressure refrigerant in the radiator 13.
- the internal temperature sensor 24 detects the air temperature Tfr of the blown air that exchanges heat with the low-pressure refrigerant in the evaporator 18.
- the low-pressure sensor 25 detects the pressure of the low-pressure refrigerant that flows out of the evaporator 18 and is sucked into the low-stage compressor 12.
- the intermediate pressure sensor 26 detects the pressure of the intermediate pressure refrigerant discharged from the low stage compressor 12.
- the high pressure sensor 27 detects the pressure of the high pressure refrigerant discharged from the high stage compressor 11.
- the low-pressure sensor 25 is a physical quantity sensor that detects a physical quantity correlated with the pressure of the low-pressure refrigerant.
- an operation panel 30 is connected to the input side of the refrigerator control device 20.
- the operation panel 30 is provided with an operation / stop switch, a temperature setting switch, and the like. Operation signals of these switches are input to the refrigerator control device 20.
- the operation / stop switch is a request signal output unit that outputs an operation request signal or a stop request signal of the refrigerator.
- the temperature setting switch is a target temperature setting unit that sets a target cooling temperature Tset in the warehouse.
- FIG. 2 is a flowchart showing a control process executed by the refrigerator control device 20.
- each control step in the flowchart shown in FIG. 2 constitutes various function realization units that the refrigerator control device 20 has.
- step S100 detection signals detected by the outside air temperature sensor 23, the internal temperature sensor 24, the low pressure sensor 25, the intermediate pressure sensor 26, the high pressure sensor 27, and the like, and operation signals such as the temperature setting switch of the operation panel 30 are read. .
- the refrigerator control device 20 specifies the outside air temperature based on the detection signal from the outside air temperature sensor 23 and specifies the target cooling temperature in the refrigerator based on the operation signal from the temperature setting switch.
- the refrigerator control device 20 determines that the cool-down is being performed, and the temperature difference between the outside air temperature and the target cooling temperature is less than the predetermined temperature. It is determined that the cool-down is not in progress.
- the refrigerator control device 20 specifies the optimum rotation speed ratio in step S104. To do.
- a map representing the relationship between the optimum rotational speed ratio of the low stage compressor 12 and the high stage compressor 11 and the low pressure refrigerant pressure is stored in the ROM of the refrigerator control device 20 as shown in FIG.
- the rotation speed ratio is defined as the ratio of the rotation speed of the low-stage compression mechanism 12a to the rotation speed of the high-stage compression mechanism 11a.
- the optimum rotation speed ratio is a rotation speed ratio that maximizes the refrigerating capacity of the evaporator 18. As shown in the figure, it is specified that the optimum rotational speed ratio increases as the pressure of the low-pressure refrigerant increases.
- the relationship between the pressure of the low-pressure refrigerant and the optimum rotational speed ratio obtained experimentally is stored in the ROM of the refrigerator control device 20.
- the optimum speed ratio is specified with reference to the map shown in FIG. Specifically, the pressure of the low-pressure refrigerant is specified based on the detection signal detected by the low-pressure sensor 25, and the optimum rotational speed ratio corresponding to the pressure of the low-pressure refrigerant is specified with reference to the map shown in FIG. .
- the internal temperature is high and the low-pressure refrigerant pressure is high, so the optimum rotation speed ratio is a relatively large value.
- the optimum rotational speed ratio gradually decreases.
- the refrigerator control device 20 specifies the rotational speed of the low stage compressor 12 and the rotational speed of the high stage compressor 11 in the next step S106.
- the rotational speed of the high stage compressor 11 is limited to less than a predetermined protection control value in order to protect the motor provided in the high stage compressor. For this reason, first, the rotational speed of the high-stage compressor 11 is specified to a value lower than the limit value by a predetermined rotational speed, and then the rotational speed of the high-stage compressor 11 and the optimum rotational speed ratio specified in step S104. Based on the above, the rotational speed of the low-stage compressor 12 is specified.
- step S108 the rotational speeds of the low-stage compressor 12 and the high-stage compressor 11 are controlled so as to be the rotational speeds specified in step S106. Specifically, the low stage compressor 12 and the high stage compressor 11 are instructed to rotate at the respective rotational speeds specified in step S106.
- the low-stage inverter 22 outputs an alternating current having a frequency corresponding to the control signal output from the refrigerator control device 20. And by this frequency control, the refrigerant
- the high-stage inverter 21 outputs an alternating current having a frequency corresponding to the control signal output from the refrigerator control device 20. And by this frequency control, the refrigerant
- the rotation speeds of the high-stage compression mechanism 11a and the low-stage compression mechanism 12a are controlled so as to have an optimum rotation ratio. Therefore, the rotation speed of the low-stage compressor 12 is specified to be larger than that in the case where the rotation speed ratio of the low-stage compression mechanism 12a to the rotation speed of the high-stage compression mechanism 11a is constant. The refrigeration capacity of 18 is maximized.
- the refrigerator control device 20 determines whether or not the refrigeration cycle device 10 stops operating. Specifically, it is determined whether or not the refrigeration cycle apparatus 10 stops operating based on whether or not a stop request signal is output from the operation panel 30.
- step S110 determines whether the stop request signal is not output. If YES is determined in the step S102, the processes in the steps S104 to S110 are performed again.
- step S200 when the temperature difference between the outside air temperature and the target cooling temperature becomes less than the predetermined temperature, it is determined that the cool-down is not being performed, the process proceeds to step S200, and a transition is made to normal control.
- the rotation speeds of the low-stage compressor and the high-stage compressor are controlled so that the rotation speed ratio between the high-stage compression mechanism 11a and the low-stage compression mechanism 12a is constant.
- FIG. 4 shows the time characteristics of the rotation speed ratio of the high stage compression mechanism 11a and the low stage compression mechanism 12a after the cool down.
- the rotation speed ratio between the high-stage compression mechanism 11a and the low-stage compression mechanism 12a of the multi-stage compression refrigeration cycle apparatus of the present embodiment is indicated by a solid line.
- the rotational speed ratio of the comparative example in which the rotational speed ratio of the high stage compression mechanism 11a and the low stage compression mechanism 12a is constant is indicated by a dotted line.
- the internal temperature is high and the low-pressure refrigerant pressure is high, and the rotation speed ratio of the high-stage compression mechanism 11a and the low-stage compression mechanism 12a is controlled to be a relatively large value. .
- the optimum rotational speed ratio gradually decreases.
- the rotation speed ratio of the high-stage compression mechanism 11a and the low-stage compression mechanism 12a becomes the same constant value as in the comparative example.
- Fig. 5 shows the time characteristics of the internal temperature after the cool-down.
- the internal temperature of the multistage compression refrigeration cycle apparatus of the present embodiment is indicated by a solid line.
- the internal temperature of the comparative example which made the rotation speed ratio of the high stage side compression mechanism 11a and the low stage side compression mechanism 12a constant is shown by the dotted line.
- the internal temperature is rapidly reduced immediately after the cool-down is performed as compared with the comparative example.
- the cool-down time until the internal temperature reaches the target cooling temperature is significantly shortened as compared with the comparative example.
- the refrigerator control device 20 reduces the low-stage compression with respect to the rotation speed of the high-stage compression mechanism 11a as the pressure of the low-pressure refrigerant specified based on the pressure of the low-pressure refrigerant detected by the low-pressure sensor 25 increases.
- the rotation speed ratio of the mechanism 12a is increased. For this reason, even if the rotation speed of the high-stage compressor is limited, the rotation speed of the low-stage compression mechanism can be increased to improve the refrigerating capacity of the evaporator 18. Therefore, the cool-down time when starting up the apparatus can be shortened without increasing the size of each compressor.
- the refrigerator control device 20 may determine whether or not to perform cool-down for rapidly cooling the cooling target space based on the temperature of the cooling target space.
- the refrigerator control device 20 may increase the rotation speed ratio of the low-stage compression mechanism with respect to the rotation speed of the high-stage compression mechanism as the pressure of the low-pressure refrigerant increases.
- the higher the pressure of the low-pressure refrigerant the larger the rotation speed ratio of the low-stage compression mechanism with respect to the rotation speed of the high-stage compression mechanism, thereby rapidly Can be cooled.
- the refrigeration cycle apparatus 10 includes a high-pressure sensor 27 that detects the pressure of the high-pressure refrigerant.
- a high-pressure sensor 27 that detects the pressure of the high-pressure refrigerant.
- the refrigerator control apparatus 20 specifies optimal rotation speed ratio based on the relationship between the pressure of the low-pressure refrigerant
- the relationship between the pressure of the low-pressure refrigerant and the optimum rotational speed ratio can also be specified.
- FIG. 6 shows the result of theoretical determination of the relationship between the pressure of the low-pressure refrigerant that maximizes the refrigerating capacity of the evaporator 18 and the optimum intermediate pressure ratio.
- the intermediate pressure ratio is expressed as intermediate pressure refrigerant pressure Pm / ⁇ (high pressure refrigerant pressure Pd ⁇ low pressure refrigerant pressure Ps).
- the rotation speed ratio of the low-stage compression mechanism 12a to the rotation speed of the high-stage compression mechanism 11a can be specified so that the intermediate pressure ratio as shown in FIG. 6 is obtained.
- the refrigerator control device 20 detects the internal temperature correlated with the pressure of the low-pressure refrigerant by the internal temperature sensor 24, and the higher the internal temperature detected by the internal temperature sensor 24, the larger the rotation speed ratio. May be.
- the internal temperature sensor 24 is a physical quantity sensor that detects a physical quantity that correlates with the pressure of the low-pressure refrigerant.
- the refrigerator control device 20 may specify the pressure of the low-pressure refrigerant based on the physical quantity detected by the internal temperature sensor 24. And the refrigerator control apparatus 20 may enlarge the rotation speed ratio of the low stage compression mechanism 12a with respect to the rotation speed of the high stage compression mechanism 11a, so that the pressure of the specified low pressure refrigerant
- the refrigerator control device 20 specifies the rotation speed ratio that is the ratio of the rotation speed of the low-stage compression mechanism 12a to the rotation speed of the high-stage compression mechanism 11a based on the pressure of the low-pressure refrigerant. did.
- the refrigerating machine control device 20 uses, for example, a rotation speed ratio that is a ratio of the rotation speed of the low-stage compression mechanism 12a to the rotation speed of the high-stage compression mechanism 11a based on the pressure of the low-pressure refrigerant and the pressure of the intermediate-pressure refrigerant. May be specified.
- the refrigerator control device 20 is the ratio of the rotation speed of the low-stage compression mechanism 12a to the rotation speed of the high-stage compression mechanism 11a based on the pressure of the low-pressure refrigerant, the pressure of the intermediate-pressure refrigerant, and the pressure of the high-pressure refrigerant.
- the rotation speed ratio may be specified. As described above, by using not only the pressure of the low-pressure refrigerant but also the pressure of the intermediate-pressure refrigerant or the pressure of the high-pressure refrigerant, the optimum rotation speed ratio can be specified with higher accuracy.
- the refrigerator control device 20 specifies a rotation speed ratio that is a ratio of the rotation speed of the low-stage compression mechanism 12a to the rotation speed of the high-stage compression mechanism 11a based on the pressure of the low-pressure refrigerant. did.
- the refrigerator control device 20 is, for example, a rotational speed that is a ratio of the rotational speed of the low-stage compression mechanism 12a to the rotational speed of the high-stage compression mechanism 11a based on the temperature of the low-pressure refrigerant that correlates with the pressure of the low-pressure refrigerant. The ratio may be specified.
- the refrigerator control device 20 may detect the temperature of the pipe through which the low-pressure refrigerant flows without detecting the temperature of the low-pressure refrigerant directly. Further, the refrigerator control device 20 specifies a rotation speed ratio that is a ratio of the rotation speed of the low-stage compression mechanism 12a to the rotation speed of the high-stage compression mechanism 11a based on the temperature of the low-pressure refrigerant and the temperature of the intermediate-pressure refrigerant. May be.
- the refrigerator control device 20 is the ratio of the rotation speed of the low-stage compression mechanism 12a to the rotation speed of the high-stage compression mechanism 11a based on the temperature of the low-pressure refrigerant, the temperature of the intermediate-pressure refrigerant, and the temperature of the high-pressure refrigerant.
- the rotation speed ratio may be specified.
- the refrigerator control device 20 specifies the rotation speed ratio that is the ratio of the rotation speed of the low-stage compression mechanism 12a to the rotation speed of the high-stage compression mechanism 11a based on the pressure of the low-pressure refrigerant. did. However, the refrigerator control device 20 specifies, for example, a rotation speed ratio that is a ratio of the rotation speed of the low-stage compression mechanism 12a to the rotation speed of the high-stage compression mechanism 11a based on the outside air temperature and the internal temperature. Also good. In this case, if a map that defines the optimum rotational speed corresponding to the outside air temperature and the internal temperature is stored in the ROM of the refrigerator control device 20, the refrigerator control device 20 uses the map to perform the high-stage compression. A rotation speed ratio that is a ratio of the rotation speed of the low-stage compression mechanism 12a to the rotation speed of the mechanism 11a can be specified.
- the refrigerator control device 20 determines that the cool-down is being performed when the temperature difference between the outside air temperature and the target cooling temperature is equal to or higher than a predetermined temperature.
- the refrigerator control device 20 may determine that the cool-down is being performed, for example, when the pressure of the high-pressure refrigerant is equal to or higher than the protection control value.
- the refrigerator control device 20 is in a cool-down state when the temperature difference between the outside air temperature and the target cooling temperature is equal to or higher than a predetermined temperature, and when the pressure of the high-pressure refrigerant is equal to or higher than the protection control value. You may judge.
- various features of the present disclosure are applied to a multi-stage compression refrigeration cycle apparatus having a two-stage compression mechanism on the high stage side and the low stage side.
- the various features of the present disclosure can also be applied to a multistage compression refrigeration cycle apparatus having a compression mechanism of three or more stages.
- the refrigerator control device 20 may determine whether or not the pressure of the high-pressure refrigerant exceeds a threshold value. When the refrigerator control device 20 determines that the pressure of the high-pressure refrigerant exceeds the threshold value, the refrigerator control device 20 reduces the rotation speed of the high-stage compression mechanism 11a and the rotation speed of the low-stage compression mechanism 12a for protection. May be.
- a chlorofluorocarbon refrigerant for example, R404A
- the refrigerant is not limited to the fluorocarbon refrigerant, and for example, a refrigerant mainly composed of carbon dioxide may be employed.
- the refrigerator control device 20 corresponds to the determination unit by executing the process of step S102.
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Abstract
Description
図1~3により、第1実施形態を説明する。図1は、本実施形態の複数段圧縮式冷凍サイクル装置の全体構成図である。この複数段圧縮式冷凍サイクル装置は、冷凍機に適用されており、冷却対象空間である冷凍庫内へ送風される送風空気を-30℃以上-10℃以下程度の極低温となるまで冷却する機能を果たす。
(1)上記実施形態では、冷凍機制御装置20は、実験的に求められた低圧冷媒の圧力と最適回転数比の関係に基づいて最適回転数比を特定する。しかし、理論的に低圧冷媒の圧力と最適回転数比の関係を特定することもできる。図6は、蒸発器18の冷凍能力が最大となる低圧冷媒の圧力と最適な中間圧比の関係を理論的に求めた結果を示している。なお、中間圧比は、中間圧冷媒圧力Pm/√(高圧冷媒圧力Pd×低圧冷媒圧力Ps)として表される。図6に示すような中間圧比となるよう高段側圧縮機構11aの回転数に対する低段側圧縮機構12aの回転数比を特定することができる。
Claims (4)
- 低圧冷媒を中間圧冷媒となるまで圧縮して吐出する低段側圧縮機構(12a)と、
前記低段側圧縮機構から吐出された中間圧冷媒を高圧冷媒となるまで圧縮して吐出する高段側圧縮機構(11a)と、を備えた複数段圧縮式冷凍サイクル装置であって、
前記高段側圧縮機構から吐出された高圧冷媒を室外空気と熱交換させて放熱させる放熱器(13)と、
前記放熱器から流出した高圧冷媒を中間圧冷媒となるまで減圧膨張させて前記高段側圧縮機構の吸入側へ流出させる中間圧膨張弁(15)と、
前記放熱器から流出した高圧冷媒を低圧冷媒となるまで減圧膨張させる低圧膨張弁(17)と、
前記低圧膨張弁にて減圧膨張された低圧冷媒を冷却対象空間に送風させる送風空気と熱交換させて蒸発させ、前記低段側圧縮機構の吸入側へ流出させる蒸発器(18)と、
前記低段側圧縮機構及び前記高段側圧縮機構の回転数を制御する制御装置(20)と、
前記低圧冷媒の圧力に相関する物理量を検出する物理量センサ(24、25)と、を備え、
前記制御装置は、前記物理量センサにより検出された物理量に基づいて、前記低圧冷媒の圧力が高いほど前記高段側圧縮機構の回転数に対する前記低段側圧縮機構の回転数比を大きくするよう構成されている複数段圧縮式冷凍サイクル装置。 - 前記物理量センサは、前記冷却対象空間の温度を検出する庫内温度センサ(24)であり、
前記制御装置は、前記庫内温度センサにより検出された前記冷却対象空間の温度が高いほど前記回転数比を大きくするよう構成されている請求項1に記載の複数段圧縮式冷凍サイクル装置。 - 前記冷却対象空間の温度に基づいて前記冷却対象空間を急速に冷却するクールダウンを実施するか否かを判定する判定部を備え、
前記制御装置は、前記判定部により前記クールダウンを実施すると判定された場合、前記低圧冷媒の圧力が高いほど前記高段側圧縮機構の回転数に対する前記低段側圧縮機構の回転数比を大きくするよう構成されている請求項1または2に記載の複数段圧縮式冷凍サイクル装置。 - 前記高圧冷媒の圧力を検出する高圧センサ(27)を備え、
前記判定部は、前記高圧センサにより検出された前記高圧冷媒の圧力が予め定められた基準値以上となっている場合、前記クールダウンを実施すると判定する請求項3に記載の複数段圧縮式冷凍サイクル装置。
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CN201680053105.0A CN108027176B (zh) | 2015-09-15 | 2016-08-26 | 多级压缩式制冷循环装置 |
US15/744,638 US20180202689A1 (en) | 2015-09-15 | 2016-08-26 | Multi-stage compression refrigeration cycle device |
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JP2009014210A (ja) * | 2007-06-29 | 2009-01-22 | Daikin Ind Ltd | 冷凍装置 |
JP5208275B2 (ja) * | 2009-06-12 | 2013-06-12 | パナソニック株式会社 | 冷凍サイクル装置 |
JP5287831B2 (ja) * | 2010-10-29 | 2013-09-11 | 株式会社デンソー | 二段昇圧式冷凍サイクル |
JP5510393B2 (ja) * | 2011-05-30 | 2014-06-04 | 株式会社デンソー | 複数段圧縮式冷凍サイクル装置 |
KR101873597B1 (ko) * | 2012-02-23 | 2018-07-31 | 엘지전자 주식회사 | 공기 조화기 |
CN104534713B (zh) * | 2014-12-31 | 2017-04-19 | 华南理工大学 | 一种双机快速降温低温制冷系统及方法 |
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CN108027176A (zh) | 2018-05-11 |
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