WO2023195042A1 - 冷凍サイクル装置 - Google Patents

冷凍サイクル装置 Download PDF

Info

Publication number
WO2023195042A1
WO2023195042A1 PCT/JP2022/017031 JP2022017031W WO2023195042A1 WO 2023195042 A1 WO2023195042 A1 WO 2023195042A1 JP 2022017031 W JP2022017031 W JP 2022017031W WO 2023195042 A1 WO2023195042 A1 WO 2023195042A1
Authority
WO
WIPO (PCT)
Prior art keywords
compressors
pressure
oil
refrigeration cycle
compressor
Prior art date
Application number
PCT/JP2022/017031
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
智隆 石川
洋貴 佐藤
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2024513573A priority Critical patent/JPWO2023195042A1/ja
Priority to PCT/JP2022/017031 priority patent/WO2023195042A1/ja
Publication of WO2023195042A1 publication Critical patent/WO2023195042A1/ja

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle

Definitions

  • the present disclosure relates to a refrigeration cycle device including a plurality of low-pressure shell type compressors.
  • refrigeration cycle devices include an accumulator that stores surplus refrigerant and refrigeration oil, and an oil regulator that adjusts the amount of refrigeration oil stored in a low-pressure shell compressor.
  • the refrigeration cycle device described in Patent Document 1 has a configuration in which an appropriate amount of refrigeration oil is supplied from an accumulator to a compressor via an oil regulator.
  • an oil regulator is installed in each of the plurality of compressors.
  • Each oil regulator has a built-in float that floats on the oil surface of the refrigerating machine oil and a valve that is linked to the float. It is installed so that it is equal to the surface height.
  • the float position lowers and the valve opens, and the refrigerating machine oil from the accumulator is supplied to the compressor via the oil regulator. be done.
  • the refrigeration cycle device described in Patent Document 1 uses an oil regulator to adjust the amount of refrigeration oil stored in the compressor, but as the number of compressors increases, the number of oil regulators for the number of compressors increases. It becomes necessary. Since oil regulators with built-in float valves are expensive, providing as many oil regulators as the number of compressors causes a problem in that the manufacturing cost of the refrigeration cycle device increases.
  • the present disclosure has been made against the background of the above-mentioned problems, and is intended to provide a refrigeration cycle device that can realize adjustment of the amount of refrigeration oil stored in a plurality of compressors while suppressing an increase in cost. be.
  • a refrigeration cycle device includes a plurality of low-pressure shell compressors connected in parallel, and is connected to each of the plurality of compressors, and adjusts the amount of refrigeration oil supplied to the plurality of compressors.
  • the compressor is equipped with one oil regulator and a pressure equalizing mechanism that equalizes the pressure in the internal spaces of the plurality of compressors.
  • one oil regulator connected to each of the plurality of compressors, and a pressure equalization mechanism that equalizes the pressure in the internal spaces of the plurality of compressors. Therefore, the number of oil regulators can be reduced compared to the conventional method. Therefore, the amount of refrigerating machine oil stored in a plurality of compressors can be adjusted while suppressing an increase in cost.
  • FIG. 1 is a schematic configuration diagram of a refrigeration cycle device according to Embodiment 1.
  • FIG. FIG. 2 is a schematic configuration diagram of a refrigeration cycle device according to a modification of the first embodiment.
  • FIG. 2 is a schematic configuration diagram of a refrigeration cycle device according to a second embodiment. It is a schematic block diagram of the refrigeration cycle apparatus based on Embodiment 3. It is a schematic block diagram of the refrigeration cycle apparatus based on Embodiment 4.
  • FIG. 1 is a schematic configuration diagram of a refrigeration cycle device 100 according to the first embodiment.
  • the refrigeration cycle device 100 of this embodiment is a refrigeration device that cools a freezer compartment such as a warehouse, a showcase, or a refrigerator.
  • the refrigeration cycle device 100 of this embodiment includes a plurality of compressors 1a and 1b, a condenser 2, an expansion valve 3, an evaporator 4, an accumulator 5, and one oil regulator. 6.
  • Compressors 1a and 1b, condenser 2, expansion valve 3, evaporator 4, and accumulator 5 constitute a refrigerant circuit in which refrigerant circulates.
  • the refrigeration cycle device 100 also includes a control device 20.
  • the refrigerant used in the refrigeration cycle device 100 is, for example, an HFC refrigerant such as R410A, R407C, R404A, or R32, an HFO refrigerant such as HFO-1234yf, or a natural refrigerant such as hydrocarbon, helium, or propane.
  • the compressor 1a and the compressor 1b are each a low-pressure shell type inverter compressor in which the internal space of the shell is filled with a low-pressure gas refrigerant.
  • the shells of the compressors 1a, 1b are represented by rectangles labeled 1, 1b.
  • the internal space of the shell filled with low-pressure gas refrigerant may be simply referred to as the internal space of the compressors 1a and 1b.
  • the compressors 1a and 1b have a suction port for sucking refrigerant and a discharge port for discharging compressed refrigerant.
  • the suction ports of the compressors 1a and 1b are connected to the accumulator 5 through suction pipes 11a and 11b, respectively.
  • Discharge pipes 12a and 12b are connected to the discharge ports of the compressors 1a and 1b, respectively.
  • the discharge pipes 12a and 12b are connected to a high pressure pipe 13.
  • Compressors 1a, 1b and condenser 2 are connected by discharge pipes 12a, 12b and high pressure piping 13.
  • a compressor 1a and a compressor 1b are connected in parallel to the condenser 2.
  • Refrigerating machine oil for lubricating sliding parts is stored inside the compressors 1a and 1b.
  • the refrigerating machine oil is, for example, polyalkylene glycol, polyol ester, polyvinyl ether, alkylbenzene, mineral oil, etc., and those having high compatibility with the refrigerant and stability are used.
  • the condenser 2 is, for example, a fin-tube heat exchanger.
  • the condenser 2 exchanges heat between the refrigerant flowing inside the heat transfer tube and air blown by a fan (not shown), and condenses and liquefies the refrigerant.
  • the condenser 2 may be, for example, a plate heat exchanger that exchanges heat between water or brine and a refrigerant.
  • the expansion valve 3 is, for example, an electronic expansion valve whose opening degree can be controlled.
  • the expansion valve 3 reduces the pressure of the refrigerant flowing out from the condenser 2 and expands it.
  • the expansion valve 3 may be a temperature-sensitive expansion valve, or a capillary tube may be provided instead of the expansion valve 3.
  • the evaporator 4 is, for example, a fin-tube heat exchanger.
  • the evaporator 4 exchanges heat between the refrigerant flowing inside the heat transfer tube and air blown by a fan (not shown), and evaporates and gasifies the refrigerant.
  • the evaporator 4 may be, for example, a plate heat exchanger that exchanges heat between water or brine and a refrigerant.
  • the accumulator 5 is a container that stores surplus refrigerant and refrigerating machine oil.
  • the accumulator 5 is connected to the evaporator 4 by a low-pressure pipe 14, separates the refrigerant flowing from the evaporator 4 into a gas refrigerant and a liquid refrigerant, stores the liquid refrigerant, and causes the gas refrigerant to flow out from the suction pipes 11a and 11b. . Further, the refrigerating machine oil contained in the refrigerant flowing from the evaporator 4 is also separated, and the separated refrigerating machine oil is stored at the bottom of the accumulator 5.
  • the accumulator 5 is connected to the oil regulator 6 by an oil return pipe 16. One end of the oil return pipe 16 is connected to the bottom of the accumulator 5, and the refrigerating machine oil accumulated at the bottom of the accumulator 5 flows into the oil regulator 6 through the oil return pipe 16.
  • the oil regulator 6 is a device that has a container for storing surplus refrigerating machine oil in the compressors 1a and 1b, and also supplies refrigerating machine oil to the compressors 1a and 1b. Refrigerating machine oil supplied from the accumulator 5 via the oil return pipe 16 is stored inside the oil regulator 6. Inside the oil regulator 6, there is provided a float that floats on the surface of the refrigerating machine oil and a valve that operates in conjunction with the float. A valve provided in the oil regulator 6 opens and closes the end of the oil return pipe 16 on the oil regulator 6 side.
  • the oil regulator 6 is connected to each of the compressors 1a and 1b via an oil pipe 15 and a pressure equalization pipe 17.
  • the oil pipe 15 is a pipe that supplies refrigerating machine oil from the oil regulator 6 to the compressors 1a and 1b.
  • the oil pipe 15 has an inlet 151, an outlet 152a, and an outlet 152b.
  • the oil pipe 15 has a pipe shape that extends from the inlet 151 and branches, and the branched portions reach the respective outlets 152a and 152b.
  • the inlet 151 is connected to a region in the oil regulator 6 where refrigerating machine oil is stored, that is, to the bottom or lower part of the oil regulator 6.
  • the outlets 152a and 152b are respectively connected to regions where refrigerating machine oil is stored in the compressors 1a and 1b, that is, to the bottoms or lower portions of the shells of the compressors 1a and 1b.
  • the pressure equalization pipe 17 is an example of a pressure equalization mechanism that equalizes the pressure in the internal spaces of the plurality of compressors 1a and 1b.
  • the pressure equalizing pipe 17 of this embodiment is a pipe that connects the internal space of the oil regulator 6 and each of the internal spaces of the plurality of compressors 1a and 1b.
  • the internal space of the compressors 1a, 1b is an internal space of the shell of the compressor 1a, 1b, and is a space that is the same as or communicates with a region where refrigerating machine oil is stored.
  • the pressure equalization pipe 17 has an oil regulator connection port 171, a compressor connection port 172a, and a compressor connection port 172b.
  • the pressure equalizing pipe 17 has a piping shape that extends from the oil regulator connection port 171 and branches, and the branched portions reach compressor connection ports 172a and 172b, respectively.
  • the oil regulator connection port 171 is connected to a space above the oil level when the maximum amount of refrigerating machine oil is stored in the oil regulator 6.
  • the compressor connection ports 172a, 172b are connected to spaces above the oil level when the maximum amount of refrigerating machine oil is stored in the shells of the compressors 1a, 1b.
  • the internal spaces of the compressors 1a, 1b and the internal space of the oil regulator 6 are connected to each other by the pressure equalizing pipe 17, so that the pressures in the internal spaces of the compressors 1a, 1b and the oil regulator 6 are made uniform. As a result, the oil levels of the refrigerating machine oil stored in the compressors 1a, 1b and the oil regulator 6 become the same.
  • the control device 20 controls the overall operation of the refrigeration cycle device 100.
  • the control device 20 is a processing device, such as an ASIC (Application Specific Integrated Circuit) or an FPGA (Field Programmable Gate Array), which includes a memory that stores data and programs necessary for control and a CPU (Central Processing Unit) that executes the programs. Consists of specialized hardware or both.
  • the control device 20 controls the operating frequencies of the compressors 1a and 1b and the operating frequency of the expansion valve 3 based on detection signals from various sensors (not shown) included in the refrigeration cycle device 100, setting information input from the remote controller, elapsed time, etc. Controls the opening degree and fan rotation speed.
  • the various sensors included in the refrigeration cycle device 100 include an indoor temperature sensor that detects the temperature of the space to be cooled, an outside temperature sensor that detects the outside air temperature, and a sensor that detects the temperature or pressure of the refrigerant flowing through each heat exchanger. .
  • the operation of the refrigeration cycle device 100 of this embodiment will be explained based on the flow of refrigerant circulating in the refrigerant circuit.
  • the compressors 1a and 1b compress the refrigerant, convert it into a high-temperature, high-pressure gas state, and discharge it.
  • the gas refrigerant discharged by the compressors 1a and 1b flows into the condenser 2 through the discharge pipes 12a and 12b and the high pressure pipe 13.
  • the condenser 2 exchanges heat between the air supplied from the fan and the refrigerant, and condenses and liquefies the refrigerant.
  • the refrigerant condensed and liquefied in the condenser 2 passes through the expansion valve 3.
  • the expansion valve 3 reduces the pressure of the refrigerant.
  • the refrigerant whose pressure has been reduced by the expansion valve 3 flows into the evaporator 4 .
  • the evaporator 4 exchanges heat between the air supplied from the fan and the refrigerant, and evaporates the refrigerant into gas.
  • the freezer compartment is cooled by the refrigerant absorbing heat from the air.
  • the refrigerant evaporated and gasified in the evaporator 4 flows into the accumulator 5 through the low-pressure pipe 14, and is again sucked into the compressors 1a and 1b from the accumulator 5 through suction pipes 11a and 11b.
  • Adjustment of the amount of refrigerating machine oil in the refrigeration cycle device 100 of this embodiment will be explained.
  • the refrigerating machine oil flows into the accumulator 5 together with the refrigerant that has been evaporated and gasified in the evaporator 4, and is accumulated in the accumulator 5.
  • the accumulator 5 and the oil regulator 6 are in constant communication through an oil return pipe 16, and the refrigerating machine oil accumulated in the accumulator 5 can flow into the oil regulator 6 through the oil return pipe 16 connected to the bottom of the accumulator 5. It is.
  • the internal space of the compressor 1a and the internal space of the compressor 1b are connected by a pressure equalizing pipe 17, and the pressure in each internal space is the same.
  • the pressure equalizing pipe 17 is connected to the internal space of the oil regulator 6, and the oil levels of the refrigerating machine oil in the oil regulator 6 and the compressors 1a and 1b are the same.
  • the oil regulator 6 has a float that floats on the oil surface and a valve that operates in conjunction with the float.
  • Refrigerating machine oil flows out from the oil regulator 6 to the oil pipe 15. Refrigerating machine oil that has flowed out into the oil pipe 15 flows into the compressor 1a from the outlet 152a, and flows into the compressor 1b from the outlet 152b. Refrigerating machine oil is supplied to the oil regulator 6 from the accumulator 5 via an oil return pipe 16. That is, the refrigerating machine oil stored in the accumulator 5 is supplied to the compressor 1a and the compressor 1b via the oil regulator 6.
  • the refrigerating machine oil supplied to the compressors 1a, 1b is discharged from the compressors 1a, 1b together with the refrigerant, passes through the condenser 2, the expansion valve 3, and the evaporator 4, and then flows into the accumulator 5 again.
  • the refrigeration cycle device 100 of the present embodiment includes a plurality of low-pressure shell type compressors 1a and 1b connected in parallel, and one oil regulator 6 connected to each of the compressors 1a and 1b. Equipped with Furthermore, the refrigeration cycle device 100 includes a pressure equalization mechanism that equalizes the pressure between the internal space of the compressor 1a and the internal space of the compressor 1b. Since the pressure of the plurality of compressors 1a, 1b is equalized by the pressure equalization mechanism, the oil level of the refrigerating machine oil of the plurality of compressors 1a, 1b can be controlled by one oil regulator 6. Therefore, the number of oil regulators 6 can be reduced compared to the conventional one. Therefore, the amount of refrigerating machine oil stored in the plurality of compressors 1a and 1b can be adjusted while suppressing an increase in cost.
  • the pressure equalization mechanism of this embodiment has a pressure equalization pipe 17 that connects the internal space of the oil regulator 6 and each of the shells of the compressors 1a and 1b. Since the pressure equalization pipe 17 is connected to each of the shells having internal spaces of the compressors 1a and 1b to be pressure equalized, the pressure equalization state can be maintained with higher accuracy.
  • FIG. 2 is a schematic configuration diagram of a refrigeration cycle apparatus 100A according to a modification of the first embodiment.
  • the pressure equalizing pipe 17 is connected to the oil regulator 6 and the suction pipes 11a and 11b.
  • the oil regulator connection port 171 of the pressure equalization pipe 17 is connected to the space above the oil level when the maximum amount of refrigerating machine oil is stored in the oil regulator 6, as in FIG. 1.
  • Compressor connection ports 172a and 172b are connected to suction pipes 11a and 11b, respectively, unlike in FIG. 1.
  • the configuration shown in FIG. 2 allows one oil regulator 6 to control the level of refrigerating machine oil in the plurality of compressors 1a and 1b. Therefore, the number of oil regulators 6 can be reduced compared to the conventional one. Therefore, the amount of refrigerating machine oil stored in the plurality of compressors 1a and 1b can be adjusted while suppressing an increase in cost.
  • the compressor connection ports 172a, 172b of the pressure equalization pipe 17 are connected to the suction pipes 11a, 11b, so the compressor connection ports 172a, 172b are connected to the shells of the compressors 1a, 1b as shown in FIG.
  • the connection process of the pressure equalizing pipe 17 is easier than when connecting the pressure equalizing pipe 17.
  • FIG. 3 is a schematic configuration diagram of a refrigeration cycle device 100B according to the second embodiment.
  • the refrigeration cycle apparatus 100B of this embodiment differs from the first embodiment in the configuration of a pressure equalization mechanism that equalizes the pressures of the compressors 1a and 1b.
  • Refrigeration cycle device 100B of this embodiment differs from Embodiment 1 in that it does not include pressure equalizing pipe 17 and in the configuration of suction pipes 11a and 11b.
  • the structure and function of compressors 1a, 1b, condenser 2, expansion valve 3, evaporator 4, and accumulator 5 in refrigeration cycle device 100B are the same as in the first embodiment.
  • Suction pipes 11a and 11b for sucking refrigerant are connected to the compressors 1a and 1b, respectively.
  • the same number of suction pipes 11a and 11b as the compressors 1a and 1b are provided.
  • the suction pipe 11a and the suction pipe 11b have the same inner diameter and length. Therefore, the pressure loss value of the refrigerant flowing from the accumulator 5 to the compressor 1a in the suction pipe 11a and the pressure loss value of the refrigerant flowing from the accumulator 5 to the compressor 1b in the suction pipe 11b are the same. Therefore, the pressures in the internal spaces of the compressors 1a and 1b connected in parallel are the same.
  • the compressor 1a and the compressor 1b have the same specifications and are controlled by the control device 20 so that their drive frequencies are the same. That is, in this embodiment, the suction pipes 11a and 11b, which connect each of the compressors 1a and 1b and the accumulator 5 and have the same inner diameter and length, act as a pressure equalizing mechanism for the compressors 1a and 1b. Function.
  • the oil regulator 6 is connected to the compressor 1b by a pressure equalizing pipe 18.
  • the pressure equalizing pipe 18 is a pipe that connects the internal space of the oil regulator 6 and the internal space of the compressor 1b.
  • the internal space of the compressor 1b is an internal space of the shell of the compressor 1b, and is a space that is the same as or communicates with a region where refrigerating machine oil is stored.
  • the pressure equalization pipe 18 of this embodiment connects the oil regulator 6 and the compressor 1b, but the pressure equalization pipe 18 can be used to connect the oil regulator 6 to any one of the plurality of compressors 1a and 1b. good.
  • the pressure equalizing pipe 18 may connect the oil regulator 6 and the suction pipe 11a or the suction pipe 11b.
  • the oil level of the refrigerating machine oil in the plurality of compressors 1a and 1b can be controlled by one oil regulator 6, as in the first embodiment. Therefore, the number of oil regulators 6 can be reduced compared to the conventional one. Therefore, the amount of refrigerating machine oil stored in the plurality of compressors 1a and 1b can be adjusted while suppressing an increase in cost.
  • a plurality of suction pipes 11a, 11b are provided as a pressure equalization mechanism that equalizes the pressure between the internal space of the compressor 1a and the internal space of the compressor 1b.
  • These plurality of suction pipes 11a and 11b have the same inner diameter and length.
  • the inner diameter and length of the suction pipes 11a and 11b are made the same, the pressure in the internal space of the compressor 1a and the internal space of the compressor 1b is equalized, and the structure for equalizing the pressure is Not added. Therefore, the internal space of the compressor 1a and the internal space of the compressor 1b can be equalized in pressure without increasing manufacturing costs due to the addition of structures.
  • FIG. 4 is a schematic configuration diagram of a refrigeration cycle apparatus 100C according to the third embodiment.
  • the refrigeration cycle apparatus 100C of this embodiment is different from the first and second embodiments in the configuration of a pressure equalization mechanism that equalizes the pressure between the internal spaces of the compressors 1a and 1b.
  • the configurations and functions of compressors 1a, 1b, condenser 2, expansion valve 3, evaporator 4, and accumulator 5 in refrigeration cycle device 100C are the same as in the first and second embodiments.
  • the structure and function of the pressure equalizing pipe 18 are the same as in the second embodiment.
  • the first control device 21 controls the overall operation of the refrigeration cycle device 100, similar to the control device 20 of the first embodiment. Further, the first control device 21 controls the displacement amount of the compressors 1a and 1b so that the pressure loss value ⁇ P in the suction pipe 11a of the compressor 1a and the pressure loss value ⁇ P in the suction pipe 11b of the compressor 1b are the same. control. Specifically, the first control device 21 stores in advance parameter values used to calculate the pressure loss value ⁇ P of the suction pipes 11a and 11b.
  • the parameter values used to calculate the pressure loss value ⁇ P of the suction pipes 11a, 11b are the inner diameter D and length L of the suction pipes 11a, 11b when the suction pipes 11a, 11b are straight pipes with a circular cross-sectional shape.
  • the first control device 21 controls the displacement amount of the compressors 1a, 1b based on the ratio of parameter values used to calculate the pressure loss value ⁇ P of the suction pipes 11a, 11b. Since the displacement amount of the compressors 1a, 1b is proportional to the driving frequency of the compressors 1a, 1b, in this embodiment, the displacement amount of the compressors 1a, 1b is controlled by controlling the driving frequency.
  • the pressure loss value ⁇ P of each of the suction pipes 11a and 11b depends on the length L of each.
  • the first control device 21 stores in advance the length L or the ratio of the lengths L of each of the suction pipes 11a and 11b.
  • the driving frequency of the compressor 1a is 60Hz
  • the driving frequency of the compressor 1b is ⁇ (2m/1m ) ⁇ 60Hz.
  • the driving frequency of the compressors 1a, 1b is controlled by the capacity required of the refrigeration cycle device 100C, but the driving frequency of the compressors 1a, 1b, which is controlled by the capacity, is dependent on the length L of each of the suction pipes 11a, 11b.
  • the drive frequency is controlled by multiplying by a correction value according to the ratio.
  • the first control device 21 controls the displacement amount of the compressors 1a and 1b so that the pressure loss value ⁇ P in the suction pipe 11a and the pressure loss value ⁇ P in the suction pipe 11b are the same, so that the compression
  • the internal space of the compressor 1a and the internal space of the compressor 1b can be equalized in pressure. That is, in the present embodiment, the first control device 21 functions as a pressure equalization mechanism that equalizes the pressure between the internal space of the compressor 1a and the internal space of the compressor 1b.
  • the oil level of the refrigerating machine oil in the plurality of compressors 1a and 1b can be controlled by one oil regulator 6, as in the first embodiment. Therefore, the number of oil regulators 6 can be reduced compared to the conventional one. Therefore, the amount of refrigerating machine oil stored in the plurality of compressors 1a and 1b can be adjusted while suppressing an increase in cost.
  • the first control device 21 functions as a pressure equalization mechanism that equalizes the pressure between the internal space of the compressor 1a and the internal space of the compressor 1b.
  • no structure is added for equalizing the pressure between the internal space of the compressor 1a and the internal space of the compressor 1b. Therefore, the internal space of the compressor 1a and the internal space of the compressor 1b can be equalized in pressure without increasing manufacturing costs due to the addition of structures.
  • FIG. 5 is a schematic configuration diagram of a refrigeration cycle device 100D according to the fourth embodiment.
  • the refrigeration cycle device 100D of this embodiment is different from the first to third embodiments in the configuration of a pressure equalization mechanism that equalizes the pressure between the internal spaces of the compressors 1a and 1b.
  • the configurations and functions of compressors 1a, 1b, condenser 2, expansion valve 3, evaporator 4, and accumulator 5 in refrigeration cycle device 100D are the same as in the first to third embodiments.
  • the structure and function of the pressure equalizing pipe 18 are the same as in the second and third embodiments.
  • the refrigeration cycle device 100D includes a pressure sensor 22a that detects the pressure in the internal space of the shell of the compressor 1a, and a pressure sensor 22b that detects the pressure in the internal space of the shell of the compressor 1b.
  • the pressure values detected by the pressure sensor 22a and the pressure sensor 22b are periodically input to the second control device 23.
  • the pressure sensors 22a and 22b may be installed in the suction pipes 11a and 11b so as to detect the internal pressures of the suction pipes 11a and 11b, respectively.
  • the second control device 23 controls the overall operation of the refrigeration cycle device 100, similar to the control device 20 of the first embodiment. Further, the second control device 23 controls the displacement of the compressors 1a and 1b based on the pressure values detected by the pressure sensors 22a and 22b so that the pressures of the compressors 1a and 1b are equalized. Control. Specifically, when the displacement amount of the compressors 1a and 1b is increased, the pressure value detected by the pressure sensors 22a and 22b decreases, and when the displacement amount is decreased, the pressure value increases. Using this relationship, the second control device 23 controls the displacement of the compressors 1a and 1b so that the pressure value detected by the pressure sensor 22a and the pressure value detected by the pressure sensor 22b are equal. , that is, control the driving frequency.
  • the internal space of the compressor 1a and the internal space of the compressor 1b are equalized in pressure.
  • the pressure sensors 22a, 22b and the second control device 23 function as a pressure equalization mechanism that equalizes the pressure between the internal space of the compressor 1a and the internal space of the compressor 1b.
  • the oil level of the refrigerating machine oil in the plurality of compressors 1a and 1b can be controlled by one oil regulator 6, as in the first embodiment. Therefore, the number of oil regulators 6 can be reduced compared to the conventional one. Therefore, the amount of refrigerating machine oil stored in the plurality of compressors 1a and 1b can be adjusted while suppressing an increase in cost.
  • the present embodiment includes pressure sensors 22a and 22b that detect the pressure values in the internal spaces of the plurality of compressors 1a and 1b, and a second control device 23.
  • the second control device 23 controls the displacement amount of the compressors 1a, 1b so that the pressure values detected by the pressure sensors 22a, 22b are equal, so that the pressure in the internal space of the compressors 1a, 1b is can be maintained more precisely and uniformly.
  • Embodiments 1 to 3 can be combined with each of Embodiments 1 to 3, and by combining them, it is possible to more accurately equalize the pressure in the internal spaces of the compressors 1a and 1b.
  • the pressure equalization mechanism described in Embodiments 1 to 3 manufacturing variations in the members constituting the pressure equalization mechanism or the suction pipes 11a and 11b, or variations in pressure loss in the piping of refrigerant mixed with refrigerating machine oil, etc. Disturbances may occur. Such disturbances may lead to a decrease in the accuracy with which the pressure in the internal spaces of the shells of the compressors 1a and 1b is made uniform.
  • the pressure in the internal spaces of the compressors 1a and 1b is feedback-controlled, so that the pressure in the internal spaces of the compressors 1a and 1b is Pressure can be made more accurate and uniform.
  • a refrigeration system has been described as an example of a refrigeration cycle system, but the refrigeration cycle system may be an air conditioner or a water heater that performs cooling and heating operations.
  • the refrigeration cycle apparatus is configured to include two low-pressure shell compressors, but it may also include three or more low-pressure shell compressors connected in parallel.
  • a refrigeration cycle device is shown in which one set consisting of a plurality of compressors and one oil regulator is provided, but in contrast to the refrigeration cycle device, a plurality of compressors and one oil regulator are provided. A plurality of sets of regulators may be provided.
  • valve linked to the float built in the oil regulator 6 opens and closes the inlet 151 of the oil pipe 15.
  • the valve of the oil regulator 6 may open and close the end of the oil return pipe 16 inside the oil regulator 6, or may open and close the flow path from the oil return pipe 16 inside the oil regulator 6 to the inlet 151.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
PCT/JP2022/017031 2022-04-04 2022-04-04 冷凍サイクル装置 WO2023195042A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2024513573A JPWO2023195042A1 (enrdf_load_stackoverflow) 2022-04-04 2022-04-04
PCT/JP2022/017031 WO2023195042A1 (ja) 2022-04-04 2022-04-04 冷凍サイクル装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2022/017031 WO2023195042A1 (ja) 2022-04-04 2022-04-04 冷凍サイクル装置

Publications (1)

Publication Number Publication Date
WO2023195042A1 true WO2023195042A1 (ja) 2023-10-12

Family

ID=88242614

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2022/017031 WO2023195042A1 (ja) 2022-04-04 2022-04-04 冷凍サイクル装置

Country Status (2)

Country Link
JP (1) JPWO2023195042A1 (enrdf_load_stackoverflow)
WO (1) WO2023195042A1 (enrdf_load_stackoverflow)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60178377U (ja) * 1984-05-04 1985-11-27 三菱重工業株式会社 圧縮機の潤滑装置
JPS6287772A (ja) * 1985-10-11 1987-04-22 ダイキン工業株式会社 冷凍装置
JPH0484073A (ja) * 1990-07-26 1992-03-17 Sanyo Electric Co Ltd 冷凍装置
US5634345A (en) * 1995-06-06 1997-06-03 Alsenz; Richard H. Oil monitoring system
JP2014196874A (ja) * 2013-03-29 2014-10-16 三菱電機株式会社 冷凍サイクル装置及びそれを備えた空気調和機
JP2018109451A (ja) * 2016-12-28 2018-07-12 三菱重工サーマルシステムズ株式会社 冷媒回路システム及び均油制御方法

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60178377U (ja) * 1984-05-04 1985-11-27 三菱重工業株式会社 圧縮機の潤滑装置
JPS6287772A (ja) * 1985-10-11 1987-04-22 ダイキン工業株式会社 冷凍装置
JPH0484073A (ja) * 1990-07-26 1992-03-17 Sanyo Electric Co Ltd 冷凍装置
US5634345A (en) * 1995-06-06 1997-06-03 Alsenz; Richard H. Oil monitoring system
JP2014196874A (ja) * 2013-03-29 2014-10-16 三菱電機株式会社 冷凍サイクル装置及びそれを備えた空気調和機
JP2018109451A (ja) * 2016-12-28 2018-07-12 三菱重工サーマルシステムズ株式会社 冷媒回路システム及び均油制御方法

Also Published As

Publication number Publication date
JPWO2023195042A1 (enrdf_load_stackoverflow) 2023-10-12

Similar Documents

Publication Publication Date Title
US10401047B2 (en) Refrigeration cycle apparatus
JP6366742B2 (ja) 空気調和装置
EP1974171B1 (en) Refrigerant vapor compression system with flash tank receiver
US20110041523A1 (en) Charge management in refrigerant vapor compression systems
CN1982808A (zh) 冷冻装置
CN104755858A (zh) 制冷装置
US12044444B2 (en) Refrigeration cycle apparatus
CN102725596B (zh) 热泵系统
CN102147141B (zh) 空调及其控制方法
KR20110129417A (ko) 히트 펌프 시스템
US20190301778A1 (en) Refrigeration cycle apparatus
JP5971548B2 (ja) 冷凍装置
WO2017199382A1 (ja) 冷凍装置
CN111379698A (zh) 可变容积比螺杆压缩机
CN103851817B (zh) 制冷装置
JP6695447B2 (ja) 流路切替装置、冷凍サイクル回路及び冷蔵庫
CN108603697B (zh) 冷冻装置
WO2023195042A1 (ja) 冷凍サイクル装置
EP3517859B1 (en) Refrigeration cycle apparatus
CN106524545A (zh) 冷冻装置
JPWO2017094172A1 (ja) 空気調和装置
JP4599190B2 (ja) 流量調整装置及び空気調和装置
WO2018079226A1 (ja) 冷凍装置、冷凍システム
WO2023073989A1 (ja) 冷凍サイクル装置
WO2023190486A1 (ja) 空気調和機

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 22936445

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 2024513573

Country of ref document: JP

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 22936445

Country of ref document: EP

Kind code of ref document: A1