WO2018079242A1 - 冷凍装置、冷凍システム - Google Patents
冷凍装置、冷凍システム Download PDFInfo
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- WO2018079242A1 WO2018079242A1 PCT/JP2017/036626 JP2017036626W WO2018079242A1 WO 2018079242 A1 WO2018079242 A1 WO 2018079242A1 JP 2017036626 W JP2017036626 W JP 2017036626W WO 2018079242 A1 WO2018079242 A1 WO 2018079242A1
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- WIPO (PCT)
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- refrigerant
- expansion valve
- high pressure
- opening degree
- pressure value
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
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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
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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
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
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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
- F25B6/00—Compression machines, plants or systems, with several condenser circuits
- F25B6/02—Compression machines, plants or systems, with several condenser circuits arranged in parallel
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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
- 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
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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
- 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
- F25B2400/16—Receivers
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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
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
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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
- F25B2700/21—Temperatures
- F25B2700/2106—Temperatures of fresh outdoor air
Definitions
- the present invention relates to a refrigeration apparatus and a refrigeration system.
- This application claims priority on Japanese Patent Application No. 2016-213257 filed in Japan on October 31, 2016, the contents of which are incorporated herein by reference.
- a plurality of refrigeration equipment such as refrigerators, freezers, and showcases that store or display products such as foods and beverages in a refrigerated state or a frozen state are used.
- the plurality of refrigeration equipment receives supply of low-temperature and low-pressure liquid refrigerant from a condensing unit provided separately.
- Refrigeration equipment cools goods by supplying liquid refrigerant to an internal heat exchanger.
- the condensing unit is a so-called refrigeration device.
- the condensing unit includes a compressor, a cooler (gas cooler), an expansion valve, and a receiver (gas-liquid separator).
- the condensing unit compresses the refrigerant heated by the external refrigeration equipment with a compressor.
- the compressed refrigerant is cooled by a cooler and then expanded by an expansion valve to be a low-pressure and low-temperature refrigerant.
- the refrigerant that has entered the gas-liquid two-phase state through the expansion valve is separated into a gas phase (gas refrigerant) and a liquid phase (liquid refrigerant) by the receiver.
- the separated liquid refrigerant is supplied to an external refrigeration equipment.
- the separated gas refrigerant is sent to the compressor and compressed again.
- Refrigeration and refrigeration equipment to which liquid refrigerant is supplied from the condensing unit individually controls the cooling temperature for actually cooling the product according to the set temperature.
- refrigeration equipment is provided with the adjustment valve which adjusts the amount of refrigerant supplied to each heat exchanger, and the controller which controls the opening of an adjustment valve.
- the controller which controls the opening of an adjustment valve.
- the regulator is closed by the controller to reduce the amount of refrigerant supplied to the heat exchanger.
- Patent Document 1 discloses that a heat source side (condensing unit side) throttle mechanism (expansion valve) and a use side (refrigeration / refrigeration equipment side) so as to expand the refrigerant in two stages.
- a throttling mechanism (expansion valve) is described.
- a target value of high-pressure refrigerant pressure discharged from the compressor hereinafter referred to as a target high-pressure value
- the throttle amount (expansion valve opening) of each throttle mechanism is adjusted so that the high-pressure refrigerant pressure becomes the target high-pressure value.
- the target high pressure value varies according to the outside air temperature. Specifically, the target high pressure value becomes low when the outside air temperature is low, and conversely becomes high when the outside air temperature is high.
- the high pressure refrigerant pressure may exceed the target high pressure if the refrigeration capacity load from the refrigeration equipment side is large.
- the opening degree of the expansion valve on the condensing unit side is increased, and the pressure on the downstream side of the expansion valve is increased.
- a member provided on the downstream side of the expansion valve for example, an injection circuit that sends gas refrigerant from the receiver to the compressor, or a refrigeration unit is connected.
- a pressure resistant design is required for piping and the like, leading to an increase in cost.
- the high-pressure refrigerant pressure may be lower than the target high-pressure when the refrigeration capacity load from the refrigeration equipment side is low.
- the opening degree of the expansion valve on the condensing unit side is reduced, and the liquid refrigerant supplied from the condensing unit to the refrigeration equipment side is reduced.
- the present invention provides a refrigeration apparatus and a refrigeration system that can make it difficult for an expansion valve to be fully opened or fully closed.
- the refrigeration apparatus includes a compressor that compresses a refrigerant, a heat exchanger that condenses the refrigerant compressed by the compressor, and an expansion that expands the refrigerant condensed by the heat exchanger.
- the opening of the expansion valve is adjusted so that the pressure of the refrigerant compressed by the compressor approaches the target high pressure value set based on the valve and the outside air temperature,
- a controller that corrects the target high-pressure value when a preset opening upper limit value or opening lower limit value is exceeded.
- the opening degree of the expansion valve changes to an opening degree corresponding to the corrected target high pressure value.
- the adjustment amount of the opening degree of the expansion valve is changed by reducing the difference between the target high pressure value and the pressure of the refrigerant compressed by the compressor. Therefore, by correcting the target high pressure value, when the opening degree of the expansion valve exceeds the opening degree upper limit value or the opening degree lower limit value, it is possible to suppress the opening degree of the expansion valve from changing greatly.
- the controller corrects the target high pressure value to increase when the opening degree of the expansion valve exceeds the opening degree upper limit value. May be.
- the opening of the expansion valve when the opening of the expansion valve is large, the target high pressure value can be increased to approach the pressure of the refrigerant compressed by the compressor. As a result, the difference between the target high pressure value and the pressure of the refrigerant compressed by the compressor becomes relatively small, and the adjustment amount of the opening degree of the expansion valve becomes small. Thereby, the opening degree of the expansion valve is less likely to be fully opened after exceeding the opening degree upper limit value.
- the controller sets the target high pressure value when the opening degree of the expansion valve exceeds the opening degree lower limit value. You may correct
- the target high pressure value can be reduced to approach the pressure of the refrigerant compressed by the compressor.
- the difference between the target high pressure value and the pressure of the refrigerant compressed by the compressor becomes relatively small, and the adjustment amount of the opening degree of the expansion valve becomes small.
- the opening degree of the expansion valve is less likely to be fully closed after the opening degree is lower than the lower limit value.
- the controller performs the plurality of times so as to increase or decrease the target high pressure value at a predetermined ratio. You may correct
- the difference between the target high pressure value and the pressure of the refrigerant compressed by the compressor is gradually reduced by repeatedly correcting and increasing the target high pressure value.
- the opening degree of the expansion valve is gradually adjusted, and the amount of adjustment once becomes small. This can prevent the opening degree of the expansion valve from being fully opened or fully closed with high accuracy.
- the compressor in any one of the first aspect to the fourth aspect, includes a first-stage compression unit and a second-stage compression unit, and A receiver that gas-liquid separates the refrigerant condensed by the expansion valve into a gas refrigerant and a liquid refrigerant; and an injection circuit that sends the gas refrigerant separated by the receiver to the second-stage compression unit of the compressor; You may make it provide.
- the pressure of the medium-pressure gas refrigerant sent to the compressor through the injection circuit can be suppressed by making it difficult for the opening degree of the expansion valve to be fully opened. Therefore, the pressure resistance performance required for the member through which the refrigerant flows can be suppressed, and an increase in cost can be suppressed.
- the refrigerant in any one of the first aspect to the fifth aspect, may be carbon dioxide.
- the refrigeration system according to the seventh aspect of the present invention exchanges heat with the refrigeration apparatus of any one of the first aspect to the sixth aspect and the refrigerant supplied from the refrigeration apparatus, connected to the refrigeration apparatus.
- a loader having a load-side heat exchanger having a load-side heat exchanger.
- the loader may further include a load side expansion valve for expanding the refrigerant supplied from the refrigeration apparatus.
- Such a configuration makes it difficult for the expansion valve on the refrigeration apparatus side to be in a fully open state or a fully closed state, and the expansion process is reliably performed even on the load side expansion valve. Therefore, the refrigerant can be expanded in two stages by the expansion valve on the refrigeration apparatus side and the load side expansion valve, thereby realizing an efficient refrigeration cycle.
- a plurality of the loaders may be connected to the refrigeration apparatus.
- the expansion valve by making the expansion valve less likely to be in a fully open state or a fully closed state, it is possible to suppress an increase in cost and an insufficient supply amount of liquid refrigerant, and to improve the refrigeration cycle efficiency.
- the refrigeration system 1 of the present embodiment includes a plurality of (three in the present embodiment) loaders 2 and a condensing unit (refrigeration apparatus) 3.
- the refrigeration system 1 uses CO 2 (carbon dioxide) as a refrigerant.
- the loader 2 is a refrigerator or a freezer that cools or refrigerates and stores the product, and a refrigeration device such as a showcase that cools or refrigerates and displays the product.
- the loader 2 receives the supply of the liquid refrigerant RL from the condensing unit 3.
- the loader 2 includes a load-side heat exchanger 21, a control valve (load-side expansion valve) 22, a loader controller 23, and a temperature sensor 24.
- the load side heat exchanger 21 cools the product by exchanging heat with the liquid refrigerant RL supplied from the condensing unit 3.
- the load-side heat exchanger 21 returns the heat-exchanged refrigerant to the condensing unit 3.
- the control valve 22 adjusts the cooling temperature of the product by adjusting the flow rate of the liquid refrigerant RL supplied from the condensing unit 3.
- the loader controller 23 controls the control valve 22 so that the internal cooling temperature approaches the set temperature based on the set temperature set from the outside and the cooling temperature at which the product is actually cooled detected by the temperature sensor 24. Adjust the opening.
- the condensing unit 3 includes a compressor 31, a gas cooler (heat exchanger) 32, an electronic expansion valve (expansion valve) 33, a receiver 34, an injection circuit 38, and an oil separator 39.
- the low pressure sensor 40, the high pressure sensor 41, the outside air temperature sensor 43, and the controller 100 are mainly provided.
- the compressor 31, gas cooler 32, electronic expansion valve 33, receiver 34, and oil separator 39 are connected by a refrigerant pipe 300.
- the compressor 31 compresses the refrigerant supplied from the loader 2 through the accumulator 35 by the suction pipe 302.
- the compressor 31 discharges a high-pressure and high-temperature refrigerant.
- CO 2 having a larger compression ratio than that of Freon or the like is used as the refrigerant.
- the compressor 31 is a two-stage compressor having a first-stage first-stage compression section 31a and a second-stage second-stage compression section 31b.
- the compressor 31 has a temperature sensor 37 that detects the temperature of the refrigerant liquid and oil in the first stage compression unit 31 a of the compressor 31.
- the gas cooler 32 is supplied with a high-pressure and high-temperature refrigerant via an oil separator 39 after being discharged from the compressor 31.
- the gas cooler 32 exchanges heat between the supplied high-pressure and high-temperature refrigerant and air sent by a blower (not shown) to condense the refrigerant.
- a plurality of gas coolers 32 are provided in parallel.
- Each of the oil separators 39 collects lubricating oil contained in the refrigerant and returns it to the compressor 31.
- the electronic expansion valve 33 expands the refrigerant condensed by the gas cooler 32 to obtain a low-pressure and low-temperature refrigerant.
- the refrigerant expanded by the electronic expansion valve 33 is in a gas-liquid two-phase state.
- the receiver 34 gas-liquid separates the gas-liquid two-phase refrigerant expanded by the electronic expansion valve 33 into a gas refrigerant RG that is a gas-phase refrigerant and a liquid refrigerant RL that is a liquid-phase refrigerant.
- a plurality of receivers 34 are provided in parallel.
- the receiver 34 includes a tank 341 that stores a refrigerant in a gas-liquid phase state.
- a liquid supply pipe 301 and an injection circuit 38 are connected to the tank 341.
- the liquid refrigerant RL separated in the tank 341 is supplied to each external loader 2 through the liquid feeding pipe 301.
- the gas refrigerant RG separated in the tank 341 of the receiver 34 is sucked into the compressor 31 via the injection circuit 38.
- the injection circuit 38 is connected to the second-stage second compression unit 31 b of the compressor 31.
- the injection circuit 38 supplies the gas refrigerant RG in the tank 341 to the second-stage second compression unit 31b.
- the injection circuit 38 is provided with a solenoid valve 36.
- the opening degree of the solenoid valve 36 is adjusted according to the temperature of the refrigerant liquid and oil detected by the temperature sensor 37 under the control of the controller 100.
- the flow rate of the gas refrigerant RG from the receiver 34 is adjusted by opening and closing the electromagnetic valve 36.
- the low pressure sensor 40 measures the pressure value (low pressure value) of the low pressure refrigerant supplied to the compressor 31 via the loader 2.
- the low pressure sensor 40 outputs the measurement result to the controller.
- the high pressure sensor 41 measures the pressure value (high pressure value) of the high pressure refrigerant discharged from the compressor 31.
- the high-pressure sensor 41 outputs the measurement result to the controller.
- the outside air temperature sensor 43 measures the outside air temperature around the condensing unit 3. The outside air temperature sensor 43 outputs the measurement result to the controller.
- the controller 100 controls ON / OFF of the operation of the compressor 31 and the rotation speed, and the opening degree of the electronic expansion valve 33.
- the controller 100 of this embodiment controls the opening degree of the electronic expansion valve 33 based on the outside air temperature, the low pressure value, and the high pressure value.
- the controller 100 activates the compressor 31.
- the controller 100 operates the compressor 31 between a predetermined upper limit rotation speed and a lower limit rotation speed.
- the controller 100 sets a target high pressure value HP as a target value of the pressure of the high pressure refrigerant discharged from the compressor 31 based on the outside air temperature detected by the outside air temperature sensor 43.
- the controller 100 adjusts the opening degree of the electronic expansion valve 33 based on the set target high pressure value HP and the high pressure refrigerant pressure P that is the actual pressure value of the high pressure refrigerant detected by the high pressure sensor 41.
- the controller 100 adjusts and controls the opening degree of the electronic expansion valve 33 so that the high-pressure refrigerant pressure P approaches the target high-pressure value HP.
- the controller 100 corrects the target high pressure value HP when a preset opening upper limit value or opening lower limit value is exceeded.
- the controller 100 corrects the target high pressure value HP repeatedly several times while increasing / decreasing the target high pressure value HP at a predetermined ratio.
- the target high pressure value HP is a value determined by the outside air temperature of the condensing unit 3.
- the target high pressure value HP increases as the outside air temperature increases, and decreases as the outside air temperature decreases.
- the target high pressure value HP is in the range of 4 (Mpa ⁇ G) to 6 (Mpa ⁇ G) when the outside air temperature is 0 ° C. or lower.
- the target high pressure value HP is in the range of 6 (Mpa ⁇ G) to 8 (Mpa ⁇ G) when the outside air temperature is 0 ° C. or higher and 30 ° C. or lower.
- the target high pressure value HP is in the range of 8 (Mpa ⁇ G) to 12 (Mpa ⁇ G) when the outside air temperature is 30 ° C. or higher.
- the controller 100 of this embodiment adjusts the opening degree of the electronic expansion valve 33 by PI control based on the deviation between the target high pressure value HP and the high pressure refrigerant pressure P.
- the controller 100 preferably performs PI control via a first-order delay of 3 seconds in order to reduce the influence of noise on the input of the high-voltage sensor 41.
- the opening range of the electronic expansion valve 33 is set in a preset range.
- the opening range of the electronic expansion valve 33 is, for example, Maximum opening (fully open state): 470 pulses Minimum opening (fully closed state): 10 pulses.
- the controller 100 opens the electronic expansion valve 33 as described above after a certain period of time has elapsed from the start of the operation of the compressor 31 and the operating speed of the compressor 31 reaches the rated operating speed. Perform degree adjustment control.
- the controller 100 executes correction control of the target high pressure value HP according to the opening degree of the electronic expansion valve 33 as shown in FIG. 3 at predetermined time intervals.
- the controller 100 determines whether the opening degree of the electronic expansion valve 33 is fully open or fully closed based on the target high pressure value HP and the high pressure refrigerant pressure P of the refrigerant detected by the high pressure sensor 41. Control so as not to become. For this reason, the controller 100 is preset with an opening degree upper limit value and an opening degree lower limit value of the electronic expansion valve 33.
- the upper limit of the opening degree of the electronic expansion valve 33 is set to 70% to 90% of the maximum opening degree.
- the lower limit of the opening of the electronic expansion valve 33 is set to 5% to 20% of the maximum opening.
- the opening degree upper limit value of the electronic expansion valve 33 of this embodiment is set to 400 pulses, for example, and the opening degree lower limit value is set to 80 pulses, for example.
- the controller 100 sets the target high pressure value HP based on the outside air temperature detected by the outside air temperature sensor 43 (step S101).
- the controller 100 determines whether or not the opening degree of the electronic expansion valve 33 is equal to or larger than the opening degree upper limit value (step S102). When the controller 100 determines that the opening degree of the electronic expansion valve 33 is not more than the upper limit value of the opening degree, the controller 100 determines whether the opening degree of the electronic expansion valve 33 is not more than the lower limit value of the opening degree (step S106). ). When the controller 100 determines that the opening degree of the electronic expansion valve 33 is not less than or equal to the opening lower limit value, the controller 100 repeats the processes of step S101, step S102, and step S106 every predetermined time.
- the controller 100 determines in step S102 that the opening degree of the electronic expansion valve 33 is equal to or greater than the opening degree upper limit value, the controller 100 maintains the opening degree of the electronic expansion valve 33 until a preset standby time elapses.
- the standby time is a time required until the value of the high-pressure refrigerant pressure P is stabilized after the opening degree of the electronic expansion valve 33 is maintained.
- the waiting time may be about 1 to 10 minutes, preferably about 5 minutes.
- the controller 100 corrects the target high pressure value HP set in step S101 to increase (step S104). Specifically, a pressure addition value that is a predetermined ratio is added to the target high pressure value HP set in step S101.
- the pressure addition value is an increase rate at the time of correction determined in accordance with the target high pressure value HP.
- the pressure addition value of this embodiment is, for example, 0.1 (MPa ⁇ G).
- the target high pressure value HP is corrected so as to increase by the pressure addition value.
- the controller 100 determines whether or not the target high pressure value HP before correction has changed due to a change in the outside air temperature detected by the outside air temperature sensor 43. . Specifically, the controller 100 determines whether or not the measurement value input from the outside air temperature sensor 43 has changed (step S105).
- step S105 If it is determined in step S105 that the outside air temperature has changed, the controller 100 ends a series of correction processes.
- the controller 100 continues the normal opening control of the electronic expansion valve 33 that brings the high-pressure refrigerant pressure P close to the target high-pressure value HP.
- step S105 If it is determined in step S105 that the outside air temperature has not changed, the controller 100 returns to step S103 and maintains the opening degree of the electronic expansion valve 33 until a preset standby time elapses. To do.
- the controller 100 repeats Step S103 to Step S105 a plurality of times, thereby gradually increasing the target high pressure value (HP) by the pressure addition value over a plurality of times.
- the correction process for increasing the target high pressure value HP as in step S103 and step S104 can be repeated up to a predetermined number of times, for example, up to five times.
- the controller 100 ends the correction process for increasing the target high pressure value HP regardless of the change state of the outside air temperature. Thereafter, the controller 100 continues the normal opening control of the electronic expansion valve 33 that brings the high-pressure refrigerant pressure P close to the target high-pressure value HP.
- step S106 determines in step S106 that the opening degree of the electronic expansion valve 33 is equal to or smaller than the opening degree lower limit value
- the controller 100 maintains the opening degree of the electronic expansion valve 33 until a preset standby time elapses. Leave as is (step S107).
- the controller 100 corrects the target high pressure value HP set in step S101 to be lowered (step S108). For this purpose, a pressure subtraction value which is a predetermined ratio is subtracted from the target high pressure value HP set in step S101. Note that the pressure subtraction value is a rate of decrease when correction is determined according to the target high pressure value HP.
- the pressure subtraction value of this embodiment is, for example, 0.1 (MPa ⁇ G). Thus, the target high pressure value HP is corrected so as to decrease by the pressure subtraction value.
- the controller 100 determines whether or not the target high pressure value HP before correction has changed due to a change in the outside air temperature detected by the outside air temperature sensor 43. . Specifically, the controller 100 determines whether or not the measurement value input from the outside air temperature sensor 43 has changed (step S109).
- step S109 If it is determined in step S109 that the outside air temperature has changed, the controller 100 ends a series of correction processes.
- the controller 100 continues the normal opening control of the electronic expansion valve 33 that brings the high-pressure refrigerant pressure P close to the target high-pressure value HP.
- step S109 If it is determined in step S109 that the outside air temperature has not changed, the controller 100 returns to step S107 and maintains the opening degree of the electronic expansion valve 33 until a preset standby time elapses. To do.
- the controller 100 repeatedly decreases the target high pressure value (HP) by the pressure subtraction value by a plurality of times by repeating the steps S107 to S109 a plurality of times.
- the correction process for reducing the target high pressure value HP as in step S107 and step S108 can be repeated up to a predetermined number of times, for example, up to five times.
- the controller 100 ends the correction process for reducing the target high pressure value HP regardless of the change in the outside air temperature. Thereafter, the controller 100 continues the normal opening control of the electronic expansion valve 33 that brings the high-pressure refrigerant pressure P close to the target high-pressure value HP.
- the controller 100 When the controller 100 repeatedly executes the processing of steps S101 to S109 at predetermined time intervals while the compressor 31 is operating, the following operation is obtained. For example, when the outside air temperature is low, the target high pressure value HP is low. On the other hand, when the refrigeration capacity load on the loader 2 side is large, the high-pressure refrigerant pressure P that is the pressure of the refrigerant discharged from the compressor 31 increases. Therefore, when the outside air temperature is low, the high-pressure refrigerant pressure P may exceed the target high-pressure value HP. In such a state, when the opening degree of the electronic expansion valve 33 is adjusted by the controller 100, the opening degree of the electronic expansion valve 33 may exceed the opening degree upper limit value to be fully opened.
- the controller 100 executes the correction process for increasing the target high pressure value HP as described above and the opening degree of the electronic expansion valve 33 exceeds the opening degree upper limit value, the target high pressure value HP is nearly fully opened. The value HP is increased. Therefore, the target high pressure value HP is corrected so as to approach the high pressure refrigerant pressure P. If the difference between the target high-pressure value HP and the high-pressure refrigerant pressure P is reduced by such correction, the ratio of the opening degree of the electronic expansion valve 33 that is increased by the controller 100 is reduced, and the fully open state is difficult to be achieved.
- the target high pressure value HP becomes high.
- the high-pressure refrigerant pressure P is low. Therefore, when the outside air temperature is high, the high-pressure refrigerant pressure P may be lower than the target high-pressure value HP. In such a state, when the opening degree of the electronic expansion valve 33 is adjusted by the controller 100, the opening degree of the electronic expansion valve 33 may be less than the opening degree lower limit value and may be in a fully closed state.
- the controller 100 executes the correction process for reducing the target high pressure value HP, so that when the opening degree of the electronic expansion valve 33 falls below the opening lower limit value and becomes close to the fully closed state, The high pressure value HP is reduced. Therefore, the target high pressure value HP is corrected so as to approach the high pressure refrigerant pressure P. By such correction, the opening degree of the electronic expansion valve 33 is increased. Thereby, if the difference between the target high pressure value HP and the high pressure refrigerant pressure P becomes small, the ratio of the opening degree of the electronic expansion valve 33 that is made small by the controller 100 becomes small, and it becomes difficult to be in the fully closed state.
- FIG. 4 shows changes in the target high pressure value HP when the correction control of the target high pressure value HP by the controller 100 as described above is executed and when the correction control is not executed in the actual condensing unit 3. It is a figure which shows an example of the change of the opening degree of an expansion valve.
- FIG. 4 shows a change in a state in which the high-pressure refrigerant pressure P exceeds the target high-pressure value HP because the outside air temperature is low and the refrigeration load capacity from the loader 2 side is large.
- a two-dot chain line L2 indicates the target high pressure value HP when correction is not performed.
- a solid line L12 indicates the target high pressure value HP when the correction of the present embodiment is performed.
- a two-dot chain line L3 indicates the opening degree of the electronic expansion valve 33 when the target high pressure value HP is not corrected.
- a solid line L13 indicates the opening of the electronic expansion valve 33 when the target high pressure value HP is corrected.
- the target high pressure value HP that is not corrected is initially set to the outside temperature as indicated by a two-dot chain line L2 in FIG. It remains constant as set accordingly.
- the electronic expansion valve 33 has an opening degree so that the refrigerant pressure approaches the target high pressure value HP when the refrigeration load capacity from the loader 2 side is large. As a result of performing control to increase, the opening degree is in a fully open state.
- the target high pressure value HP is initially set according to the outside air temperature as shown by a solid line L12 in FIG. After being set, as a result of the opening degree of the electronic expansion valve 33 reaching the opening degree upper limit value, it increases stepwise. Further, as indicated by a solid line L13 in FIG. 4, the electronic expansion valve 33 has its opening degree fully opened as a result of the target high pressure value HP increasing stepwise in a state where the refrigeration load capacity from the loader 2 side is large. It reaches a certain state before reaching the state.
- the opening degree of the electronic expansion valve 33 exceeds a preset opening degree upper limit value or opening degree lower limit value, the high pressure refrigerant pressure P is approached.
- the target high pressure value HP is corrected.
- the opening degree of the electronic expansion valve 33 changes to an opening degree corresponding to the corrected target high pressure value HP. Specifically, when the difference between the target high pressure value HP and the high pressure refrigerant pressure P becomes small, the adjustment amount of the opening degree of the electronic expansion valve 33 becomes small.
- the electronic expansion valve 33 is prevented from changing greatly. It becomes difficult to be in the fully open state or the fully closed state.
- the electronic expansion valve 33 by making the electronic expansion valve 33 less likely to be fully opened, the degree of opening of the electronic expansion valve 33 is fully opened and the refrigerant cannot be sufficiently expanded, and only the control valve 22 that is the expansion valve on the loader 2 side is used. It can prevent becoming the structure of the 1 stage aperture_diaphragm
- the controller 100 corrects the target high pressure value HP to increase when the opening degree of the electronic expansion valve 33 exceeds the opening degree upper limit value. Therefore, when the opening degree of the electronic expansion valve 33 is large, the target high pressure value HP can be increased to approach the high pressure refrigerant pressure P. As a result, the difference between the target high pressure value HP and the high pressure refrigerant pressure P becomes relatively small, and the adjustment amount of the opening degree of the electronic expansion valve 33 becomes small. Thereby, the opening degree of the electronic expansion valve 33 is less likely to be fully opened after the opening degree upper limit value is exceeded.
- the controller 100 corrects the target high pressure value HP to be lowered when the opening degree of the electronic expansion valve 33 exceeds the opening degree lower limit value. Therefore, when the opening degree of the electronic expansion valve 33 is small, the target high pressure value HP can be reduced to approach the high pressure refrigerant pressure P. As a result, the difference between the target high pressure value HP and the high pressure refrigerant pressure P becomes relatively small, and the adjustment amount of the opening degree of the electronic expansion valve 33 becomes small. As a result, the opening degree of the electronic expansion valve 33 is less likely to be fully closed after the opening degree is lower than the lower limit value.
- the difference between the target high pressure value HP and the high pressure refrigerant pressure P is gradually reduced by repeatedly correcting and increasing the target high pressure value HP.
- the opening degree of the electronic expansion valve 33 is gradually adjusted, and the adjustment amount at one time becomes small. Thereby, it is possible to prevent the opening degree of the electronic expansion valve 33 from being fully opened or fully closed with high accuracy.
- the opening of the electronic expansion valve 33 is not easily opened, the pressure of the medium-pressure gas refrigerant RG sent to the compressor 31 through the injection circuit 38 is suppressed. Therefore, the pressure resistance required for the member through which the refrigerant such as the injection circuit 38 circulates can be suppressed, and the cost increase can be suppressed.
- the electronic expansion valve 33 on the condensing unit 3 side is less likely to be fully opened or fully closed, the expansion process is reliably performed in both the electronic expansion valve 33 and the control valve 22. Therefore, the refrigerant can be expanded in two stages by the electronic expansion valve 33 and the control valve 22 on the condensing unit 3 side, thereby realizing an efficient refrigeration cycle.
- the refrigeration system 1 is provided with the two-stage expansion process including the electronic expansion valve 33 and the load-side expansion valve 22, but the present invention can be applied to a configuration including only one expansion process. Can be applied.
- the compressor 31 includes the first-stage compression unit 31a and the second-stage compression unit 31b and is configured to compress the refrigerant in two stages. However, the compressor 31 may perform compression in only one stage.
- the electronic expansion valve 33 in the configuration of one-stage expansion and one-stage compression, if the electronic expansion valve 33 is fully opened when the outside air temperature is low and the high-pressure refrigerant pressure P is low or the pipe length is long, the electronic expansion is performed. The control by the valve 33 does not function, and the liquid refrigerant RL easily returns to the compressor 31.
- the one-stage expansion and one-stage compression configuration when the outside air temperature is high and the differential pressure between the high-pressure refrigerant pressure and the load side is high, if the electronic expansion valve 33 is fully closed, the refrigerant circulation rate decreases. , Lack of ability.
- control by the controller 100 is not limited to the above-described example, and the processing order can be changed or a part of the processing can be omitted.
- the refrigeration system 1 includes the plurality of loaders 2 and the condensing unit 3, but the number of loaders 2 is not limited at all.
- the plurality of loaders 2 do not have to be the same type, and a plurality of types of loaders 2 may be provided in a mixed manner.
- the refrigeration system 1 can be a unit having a loader 2 and a condensing unit 3 integrally.
- An example of such a unit is a vending machine for beverages.
- the refrigeration apparatus and the refrigeration system it is possible to prevent the expansion valve from being fully opened or fully closed, thereby suppressing an increase in cost and a shortage of supply amount of liquid refrigerant and increasing the refrigeration cycle efficiency.
- Refrigeration system 2 Loader 3 Condensing unit (refrigeration equipment) 21 Load-side heat exchanger 22 Load-side expansion valve 23 Load controller 24 Temperature sensor 31 Compressor 31a First stage compression section 31b Second stage compression section 32 Gas cooler (heat exchanger) 33 Electronic expansion valve (expansion valve) 34 Receiver 35 Accumulator 36 Solenoid valve 37 Temperature sensor 38 Injection circuit 39 Oil separator 40 Low pressure sensor 41 High pressure sensor 43 Outside air temperature sensor 100 Controller 300 Refrigerant pipe 301 Liquid feed pipe 302 Suction pipe 341 Tank HP Target high pressure value P High pressure refrigerant pressure RG Gas Refrigerant RL Liquid refrigerant
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Abstract
Description
本願は、2016年10月31日に、日本に出願された特願2016-213257号について優先権を主張し、その内容をここに援用する。
最大開度(全開状態):470パルス
最小開度(全閉状態):10パルス
とする。
以上、本発明の実施形態について図面を参照して詳述したが、各実施形態における各構成及びそれらの組み合わせ等は一例であり、本発明の趣旨から逸脱しない範囲内で、構成の付加、省略、置換、及びその他の変更が可能である。また、本発明は実施形態によって限定されることはなく、特許請求の範囲によってのみ限定される。
2 負荷器
3 コンデンシングユニット(冷凍装置)
21 負荷側熱交換器
22 負荷側膨張弁
23 負荷器コントローラ
24 温度センサ
31 圧縮機
31a 第一段圧縮部
31b 第二段圧縮部
32 ガスクーラ(熱交換器)
33 電子膨張弁(膨張弁)
34 レシーバ
35 アキュムレータ
36 電磁弁
37 温度センサ
38 インジェクション回路
39 オイルセパレータ
40 低圧センサ
41 高圧センサ
43 外気温センサ
100 コントローラ
300 冷媒配管
301 送液管
302 吸入管
341 タンク
HP 目標高圧値
P 高圧冷媒圧力
RG ガス冷媒
RL 液冷媒
Claims (9)
- 冷媒を圧縮する圧縮機と、
前記圧縮機で圧縮された前記冷媒を凝縮させる熱交換器と、
前記熱交換器で凝縮された冷媒を膨張させる膨張弁と、
外気温に基づいて設定される目標高圧値に対し、前記圧縮機で圧縮された前記冷媒の圧力が近づくよう前記膨張弁の開度を調整するとともに、前記膨張弁の開度が、予め設定された開度上限値又は開度下限値を越えた場合に、前記目標高圧値を補正するコントローラと、
を備える冷凍装置。 - 前記コントローラは、前記膨張弁の開度が前記開度上限値を超えた場合に、前記目標高圧値を増加させるよう補正する請求項1に記載の冷凍装置。
- 前記コントローラは、前記膨張弁の開度が前記開度下限値を超えた場合に、前記目標高圧値を低下させるよう補正する請求項1又は2に記載の冷凍装置。
- 前記コントローラは、予め定めた所定の割合で前記目標高圧値を増減させるように複数回繰り返して補正する請求項1から3の何れか一項に記載の冷凍装置。
- 前記圧縮機は、第一段圧縮部と第二段圧縮部とを備えるとともに、
前記膨張弁で凝縮された前記冷媒をガス冷媒と液冷媒とに気液分離するレシーバと、
前記レシーバで分離された前記ガス冷媒を、前記圧縮機の前記第二段圧縮部に送り込むインジェクション回路と、
を備える請求項1から4の何れか一項に記載の冷凍装置。 - 前記冷媒は、二酸化炭素である、請求項1から5の何れか一項に記載の冷凍装置。
- 請求項1から6の何れか一項に記載の冷凍装置と、
前記冷凍装置に接続され、前記冷凍装置から供給される前記冷媒と熱交換する負荷側熱交換器を有する負荷器と、
を備える冷凍システム。 - 前記負荷器は、前記冷凍装置から供給される前記冷媒を膨張させる負荷側膨張弁をさらに備える請求項7に記載の冷凍システム。
- 前記冷凍装置に対し、複数の前記負荷器が接続される、請求項7又は8に記載の冷凍システム。
Priority Applications (2)
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EP17866017.1A EP3499148A4 (en) | 2016-10-31 | 2017-10-10 | REFRIGERATION DEVICE, REFRIGERATION SYSTEM |
AU2017350238A AU2017350238B2 (en) | 2016-10-31 | 2017-10-10 | Refrigeration device, refrigeration system |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2016-213257 | 2016-10-31 | ||
JP2016213257A JP2018071909A (ja) | 2016-10-31 | 2016-10-31 | 冷凍装置、冷凍システム |
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WO2018079242A1 true WO2018079242A1 (ja) | 2018-05-03 |
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PCT/JP2017/036626 WO2018079242A1 (ja) | 2016-10-31 | 2017-10-10 | 冷凍装置、冷凍システム |
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EP (1) | EP3499148A4 (ja) |
JP (1) | JP2018071909A (ja) |
AU (1) | AU2017350238B2 (ja) |
WO (1) | WO2018079242A1 (ja) |
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JP2021139542A (ja) * | 2020-03-04 | 2021-09-16 | 株式会社富士通ゼネラル | 空気調和装置 |
DE102021125446A1 (de) * | 2021-09-30 | 2023-03-30 | Thermo Electron Led Gmbh | Kühlsystem und Laborgerät mit Kühlsystem |
EP4361531A1 (en) * | 2022-10-26 | 2024-05-01 | Ariston S.P.A. | Heat pump with expanded modulation of the expansion device |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2007263383A (ja) * | 2006-03-27 | 2007-10-11 | Daikin Ind Ltd | 冷凍装置 |
JP2010156507A (ja) * | 2008-12-26 | 2010-07-15 | Daikin Ind Ltd | 空気調和機 |
JP2011252622A (ja) * | 2010-05-31 | 2011-12-15 | Mitsubishi Heavy Ind Ltd | ヒートポンプ式給湯・空調装置 |
JP2014089006A (ja) * | 2012-10-31 | 2014-05-15 | Daikin Ind Ltd | 空気調和機 |
Family Cites Families (1)
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JP6193555B2 (ja) * | 2012-11-09 | 2017-09-06 | 株式会社Soken | 冷凍サイクル装置 |
-
2016
- 2016-10-31 JP JP2016213257A patent/JP2018071909A/ja active Pending
-
2017
- 2017-10-10 AU AU2017350238A patent/AU2017350238B2/en active Active
- 2017-10-10 EP EP17866017.1A patent/EP3499148A4/en not_active Withdrawn
- 2017-10-10 WO PCT/JP2017/036626 patent/WO2018079242A1/ja unknown
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2007263383A (ja) * | 2006-03-27 | 2007-10-11 | Daikin Ind Ltd | 冷凍装置 |
JP2010156507A (ja) * | 2008-12-26 | 2010-07-15 | Daikin Ind Ltd | 空気調和機 |
JP2011252622A (ja) * | 2010-05-31 | 2011-12-15 | Mitsubishi Heavy Ind Ltd | ヒートポンプ式給湯・空調装置 |
JP2014089006A (ja) * | 2012-10-31 | 2014-05-15 | Daikin Ind Ltd | 空気調和機 |
Non-Patent Citations (1)
Title |
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See also references of EP3499148A4 * |
Also Published As
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AU2017350238B2 (en) | 2020-07-16 |
EP3499148A4 (en) | 2019-09-11 |
EP3499148A1 (en) | 2019-06-19 |
AU2017350238A1 (en) | 2019-04-04 |
JP2018071909A (ja) | 2018-05-10 |
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