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WO2018163346A1 - Climatiseur - Google Patents

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Publication number
WO2018163346A1
WO2018163346A1 PCT/JP2017/009419 JP2017009419W WO2018163346A1 WO 2018163346 A1 WO2018163346 A1 WO 2018163346A1 JP 2017009419 W JP2017009419 W JP 2017009419W WO 2018163346 A1 WO2018163346 A1 WO 2018163346A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
compressor
air conditioner
flow rate
heat exchanger
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2017/009419
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English (en)
Japanese (ja)
Inventor
孝史 福井
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to JP2019504217A priority Critical patent/JP6779361B2/ja
Priority to PCT/JP2017/009419 priority patent/WO2018163346A1/fr
Publication of WO2018163346A1 publication Critical patent/WO2018163346A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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

Definitions

  • the present invention relates to an air conditioner having a refrigerant circuit for circulating a refrigerant.
  • a control means that can vary the time for which the compressor can be held at a constant frequency for a predetermined time according to the length of the installation pipe after the compressor is started, and lubrication discharged from the compressor.
  • an air conditioner that operates to increase the operating frequency of the compressor after the oil returns to the compressor through the refrigeration cycle (see, for example, Patent Document 3).
  • JP 2009-103449 A JP 2001-201191 A Japanese Unexamined Patent Publication No. 1-6653 JP-A-6-101925
  • Patent Document 4 it is possible to ensure oil repellency corresponding to differences in operation modes of cooling and heating, and changes in outside air temperature and indoor set temperature. There was a problem that the oil-repellent property corresponding to could not be secured.
  • the present invention has been made in order to solve the above-described problems, and does not require an additional element that causes an increase in cost such as an oil separator, and the length of the refrigerant pipe that connects the outdoor unit and the indoor unit.
  • an additional element that causes an increase in cost such as an oil separator, and the length of the refrigerant pipe that connects the outdoor unit and the indoor unit.
  • the installation conditions, operating conditions, and operating conditions of the air conditioning equipment such as the height of the unit installation location and the refrigerant charge amount, ensuring the oil-repellent property to maintain a certain amount of refrigeration oil in the compressor, and improving the reliability of the air conditioning equipment It aims at obtaining the air conditioning apparatus which implement
  • the air conditioner according to the present invention is At least one room having a compressor, a four-way valve, an outdoor heat exchanger, an outdoor air blower, an outdoor air blower, an opening degree variable pressure reducing device, an indoor heat exchanger, and an indoor air blower, each of which has a variable driving frequency.
  • Air conditioning operation of the air conditioner in the air conditioner in which the unit is connected by a refrigerant pipe and the refrigerant circuit for circulating the refrigerant to the compressor, four-way valve, outdoor heat exchanger, decompression device, and indoor heat exchanger is configured.
  • a control device that controls the operation state detecting means for detecting the operation state, and the flow rate of refrigerant circulating in the refrigerant circuit based on the operation state detected by the operation state detection means, and based on a preset threshold value
  • the refrigerant flow rate determining means for determining whether or not the operating condition has a high refrigerant flow rate, and the maximum operation of the compressor when the refrigerant flow rate determining means determines that the operating condition has a refrigerant flow rate greater than a predetermined amount
  • control means for controlling so as to lower the frequency, but with a.
  • the air conditioner of the present invention estimates the refrigerant flow rate circulating through the refrigerant circuit based on the operating condition detecting means for detecting the operating condition of the air conditioner and the operating condition detected by the operating condition detecting means.
  • the refrigerant flow rate determining means for determining whether or not there are many operating conditions, and when the refrigerant flow rate determining means determines that the refrigerant flow rate is higher than a predetermined amount, the compressor flow rate Control means to control the maximum operating frequency to be low, so no additional elements such as oil separators that increase costs are required, and a certain amount or more in the compressor regardless of operating conditions and operating conditions Since it is possible to ensure the oil-repellent property of maintaining the refrigerating machine oil, it is possible to realize a highly reliable air conditioner.
  • FIG. 3 is a Ph diagram illustrating a state transition of a refrigerant in the air-conditioning apparatus according to Embodiment 1 of the present invention. It is a flowchart which shows the control action of the air conditioning apparatus which concerns on Embodiment 1 of this invention. It is a flowchart which shows the control action of the air conditioning apparatus which concerns on Embodiment 2 of this invention. It is a flowchart which shows the control action of the air conditioning apparatus which concerns on Embodiment 3 of this invention.
  • FIG. 1 is a refrigerant circuit diagram schematically showing an air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • the air conditioner 100 is an apparatus used for indoor air conditioning by performing a vapor compression refrigeration cycle operation.
  • the air conditioner 100 includes a heat source unit A, a liquid connection pipe 6 and a gas connection pipe 9 serving as a refrigerant communication pipe. And a plurality of use units B (one in the present embodiment) connected in parallel.
  • refrigerant used in the air conditioner examples include HFC refrigerants such as R410A, R407C, R404A, and R32, HFO refrigerants such as R1234yf / ze, HCFC refrigerants such as R22 and R134a, carbon dioxide (CO 2 ), and carbonized carbon.
  • HFC refrigerants such as R410A, R407C, R404A, and R32
  • HFO refrigerants such as R1234yf / ze
  • HCFC refrigerants such as R22 and R134a
  • CO 2 carbonized carbon
  • natural refrigerants such as hydrogen, helium and propane.
  • the use unit B is installed in the indoor ceiling by embedding or hanging, or wall-mounted on the indoor wall surface, and is connected to the heat source unit A via the liquid connection pipe 6 and the gas connection pipe 9 as described above. It constitutes a part of the refrigerant circuit.
  • the usage unit B constitutes an indoor side refrigerant circuit that is a part of the refrigerant circuit, and includes an indoor air blower 8 and an indoor heat exchanger 7 that is a usage side heat exchanger.
  • the indoor heat exchanger 7 is composed of a cross fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins, and functions as a refrigerant evaporator during cooling operation. In the heating operation, it functions as a refrigerant condenser and heats indoor air.
  • the indoor air blower 8 is a fan capable of changing the flow rate of air supplied to the indoor heat exchanger 7, and is composed of, for example, a centrifugal fan or a multiblade fan driven by a DC motor (not shown).
  • a centrifugal fan or a multiblade fan driven by a DC motor not shown.
  • various sensors are installed in the use unit B. That is, on the liquid side of the indoor heat exchanger 7, the temperature of the refrigerant in the liquid state or the gas-liquid two-phase state (the supercooled liquid temperature Tco during the heating operation or the refrigerant temperature corresponding to the evaporation temperature Te during the cooling operation).
  • a liquid side temperature sensor 205 for detection is provided.
  • the indoor heat exchanger 7 has a gas-side temperature sensor 207 that detects the temperature of the refrigerant in the gas-liquid two-phase state (condensation temperature Tc during heating operation or refrigerant temperature corresponding to the evaporation temperature Te during cooling operation). Is provided.
  • an indoor temperature sensor 206 for detecting the temperature of the indoor air flowing into the unit is provided on the indoor air inlet side of the utilization unit B.
  • all of the liquid side temperature sensor 205, the gas side temperature sensor 207, and the room temperature sensor 206 are composed of thermistors. Operation
  • movement of the indoor air blower 8 is controlled by the operation control means (control part 30).
  • the heat source unit A is installed outdoors and is connected to the utilization unit B through the liquid connection pipe 6 and the gas connection pipe 9 and constitutes a part of the refrigerant circuit.
  • the heat source unit A includes a compressor 1, a four-way valve 2, an outdoor heat exchanger 3 as a heat source side heat exchanger, an outdoor air blower 4, a decompressor 5a, a decompressor 5b, and a receiver 11. ing.
  • the decompression devices 5a and 5b are connected to the liquid side of the heat source unit A in order to adjust the flow rate of the refrigerant flowing in the refrigerant circuit.
  • the compressor 1 is a compressor capable of varying the operating capacity (frequency), and here, a positive displacement compressor driven by a motor (not shown) controlled by an inverter is used.
  • a positive displacement compressor driven by a motor (not shown) controlled by an inverter is used.
  • the compressor 1 is only one here, it is not limited to this, According to the number of use units etc., two or more compressors may be connected in parallel. .
  • the four-way valve 2 is a valve having a function of switching the direction of refrigerant flow.
  • compression is performed so that the outdoor heat exchanger 3 functions as a refrigerant condenser compressed in the compressor 1 and the indoor heat exchanger 7 functions as a refrigerant evaporator condensed in the outdoor heat exchanger 3.
  • the discharge side of the machine 1 and the gas side of the outdoor heat exchanger 3 are connected, and the refrigerant flow path is switched so as to connect the suction side of the compressor 1 and the gas connection pipe 9 side (four-way valve 2 in FIG. 1). Dashed line).
  • the indoor heat exchanger 7 functions as a refrigerant condenser compressed in the compressor 1 and the outdoor heat exchanger 3 functions as a refrigerant evaporator condensed in the indoor heat exchanger 7.
  • 1 is connected to the discharge side of the compressor 1 and the gas connection pipe 9 side, and the refrigerant flow path is switched to connect the suction side of the compressor 1 and the gas side of the outdoor heat exchanger 3 (four-way valve 2 in FIG. 1). Solid line).
  • the outdoor heat exchanger 3 is a cross-fin type fin-and-tube type composed of a heat transfer tube whose gas side is connected to the four-way valve 2 and whose liquid side is connected to the liquid connection pipe 6 and a large number of fins. It consists of a heat exchanger and functions as a refrigerant condenser during cooling operation and as a refrigerant evaporator during heating operation.
  • the outdoor blower 4 is a fan capable of changing the flow rate of air supplied to the outdoor heat exchanger 3, and is composed of, for example, a propeller fan driven by a DC motor (not shown). Accordingly, the outdoor air is sucked into the heat source unit A, and the air heat-exchanged with the refrigerant by the outdoor heat exchanger 3 is discharged to the outside.
  • the receiver 11 is a refrigerant container that stores liquid refrigerant.
  • the receiver 11 stores liquid refrigerant that has become excessive during operation and has a gas-liquid separation function.
  • the internal heat exchanger 12 is built in the receiver 11 and heats the refrigerant circulating in the gas connection pipe 9 that connects the four-way valve 2 and the suction portion of the compressor 1 and the liquid refrigerant stored in the receiver 11.
  • Refrigerant piping is connected and configured to be replaced.
  • various sensors are installed in the heat source unit A. That is, the compressor 1 is provided with a discharge temperature sensor 201 for detecting the discharge temperature Td, and the outdoor heat exchanger 3 has a gas-liquid two-phase refrigerant temperature (condensation temperature Tc during cooling operation or A gas side temperature sensor 202 for detecting a refrigerant temperature corresponding to the evaporation temperature Te during heating operation is provided. Further, on the liquid side of the outdoor heat exchanger 3, a liquid side temperature sensor 204 for detecting the temperature of the refrigerant in the liquid state or the gas-liquid two-phase state is provided.
  • An outdoor temperature sensor 203 for detecting the temperature of the outdoor air flowing into the unit, that is, the outdoor air temperature Ta, is provided on the outdoor air inlet side of the heat source unit A.
  • the discharge temperature sensor 201, the gas side temperature sensor 202, the outdoor temperature sensor 203, and the liquid side temperature sensor 204 are all composed of a thermistor.
  • operation of the compressor 1, the four-way valve 2, the outdoor air blower 4, and the pressure reduction apparatus 5a, 5b is controlled by the operation control means (control part 30).
  • the heat source unit A and the utilization unit B are connected via the liquid connection pipe 6 and the gas connection pipe 9 to constitute the refrigerant circuit of the air conditioner.
  • the liquid connection pipe 6 and the gas connection pipe 9 are constituted by long (for example, a total length of 100 m or more) refrigerant pipe.
  • the longer the refrigerant pipe length the greater the required amount of refrigerant and the greater the amount of oil discharged from the compressor. Therefore, the oil return until the discharged refrigeration oil returns to the compressor also deteriorates. For this reason, it has an effect that the reliability can be maintained under conditions exceeding the total length of 100 m currently permitted as installation conditions.
  • the refrigerant of the air conditioner according to the length in order to perform an appropriate refrigeration cycle operation in the refrigerant circuit It is necessary to increase the filling amount.
  • the refrigerant flow rate circulating in the refrigerant circuit is relatively increased according to the refrigerant charge amount.
  • the oil circulation rate of the refrigerating machine oil which is defined by the ratio of the mass flow rate of the refrigerating machine oil to the total mass flow rate of the refrigerant and the refrigerating machine oil, is increased.
  • the configuration in the case where there is one heat source unit A will be described as an example.
  • the present invention is not limited to this, and there may be a plurality of heat source units A that are two or more. good.
  • the respective capacities may vary from large to small, or all may have the same capacity.
  • the configuration in which the heat source unit A and the utilization unit B are installed at the same height (the height difference is 0 m) will be described as an example.
  • the present invention is not limited to this, and the heat source You may be comprised by the installation conditions (for example, 30 m or more of height differences) with a large height difference of the installation place height of the unit A and the utilization unit B.
  • the greater the difference in height of the unit installation location the more the refrigeration oil in the compressor mounted on the heat source unit A is discharged together with the refrigerant into the refrigerant circuit, and the effect of the head difference as hydrodynamic energy.
  • the refrigeration oil circulates through the refrigerant circuit and becomes difficult to return to the compressor, so that the oil return property is deteriorated.
  • the height difference of 30 m currently accepted as the installation height condition is used as a guide, and the reliability can be maintained even under conditions exceeding this.
  • FIG. 2 is a control block diagram according to Embodiment 1 of the present invention.
  • FIG. 2 shows a connection configuration of the control unit 30 that performs measurement control of the air-conditioning apparatus 100 of the first embodiment, operation information connected thereto, and actuators.
  • the control unit 30 is built in the air conditioner 100, and includes a measurement unit 30a, a calculation unit 30b, a drive unit 30c, a storage unit 30d, and a determination unit 30e.
  • Operation information detected by various sensors or the like is input to the measurement unit 30a, and operation state quantities such as pressure, temperature, and frequency are measured.
  • the operation state quantity measured by the measurement unit 30a is input to the calculation unit 30b.
  • the calculation unit 30b calculates, for example, a refrigerant physical property value (saturation pressure, saturation temperature, density, etc.) using a formula given in advance based on the operation state quantity measured by the measurement unit 30a. Moreover, the calculating part 30b performs a calculation process based on the driving
  • a refrigerant physical property value saturated pressure, saturation temperature, density, etc.
  • the driving unit 30c drives a compressor, a decompression device, a blower, and the like based on the calculation result of the calculation unit 30b.
  • the storage unit 30d is a function formula or function for calculating the results obtained by the calculation unit 30b, predetermined constants, specification values of the device and its constituent elements, and physical property values (saturation pressure, saturation temperature, density, etc.) of the refrigerant.
  • a table (table) or the like is stored. These stored contents in the storage unit 30d can be referred to and rewritten as necessary.
  • the storage unit 30d further stores a control program, and the control unit 30 controls the air conditioner 100 according to the program in the storage unit 30d.
  • the determination unit 30e performs processing such as large / small comparison and determination based on the result obtained by the calculation unit 30b.
  • the measurement unit 30a, the calculation unit 30b, the drive unit 30c, and the determination unit 30e are configured by, for example, a microcomputer, and the storage unit 30d is configured by a semiconductor memory or the like.
  • control unit 30 is built in the air conditioner, but the present invention is not limited to this.
  • the main control unit is provided in the heat source unit A, and the sub-control unit having a part of the function of the control unit is provided in the use unit B, and data communication is performed between the main control unit and the sub-control unit to perform the cooperation processing.
  • a configuration, a configuration in which a control unit having all functions is installed in the use unit B, or a configuration in which the control unit is separately provided outside these units may be employed.
  • the four-way valve 2 is in a state indicated by a broken line in FIG. 1, that is, the discharge side of the compressor 1 is connected to the gas side of the outdoor heat exchanger 3, and the suction side of the compressor 1 is the indoor heat exchanger 7. It is connected to the gas side.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 reaches the outdoor heat exchanger 3 that is a condenser via the four-way valve 2, and the refrigerant is condensed and liquefied by the blowing action of the outdoor air blower 4, and the high-pressure and low-temperature refrigerant. It becomes.
  • the condensed and liquefied high-temperature and low-pressure refrigerant is decompressed by the decompression device 5 a to become a medium-pressure two-phase refrigerant, further decompressed by the decompression device 5 b via the receiver 11, and supplied to the usage unit B via the liquid connection pipe 6. Sent to the indoor heat exchanger 7.
  • the decompressed two-phase refrigerant evaporates by the blowing action of the indoor blower 8 in the indoor heat exchanger 7 that is an evaporator, and becomes a low-pressure gas refrigerant.
  • the low-pressure gas refrigerant exchanges heat with the medium-pressure two-phase refrigerant between the decompression devices 5a and 5b in the internal heat exchanger 12 via the four-way valve 2, and then is sucked into the compressor 1 again.
  • the high-temperature medium-pressure two-phase refrigerant decompressed by the decompression device 5a is saturated with the low-temperature low-pressure refrigerant circulating between the four-way valve 2 and the compressor 1 suction side. Cooled to the refrigerant (change from point D to point E in FIG. 3). At the same time, the low-pressure refrigerant is heated to become a low-pressure superheated gas refrigerant and flows into the compressor 1 (change from point G to point A in FIG. 3).
  • the enthalpy of the refrigerant flowing into the indoor heat exchanger 7 is reduced, and the enthalpy difference at the entrance and exit of the indoor heat exchanger 7 is increased.
  • the refrigerant circulation amount necessary for obtaining the predetermined capacity is reduced, and the pressure loss is reduced, thereby improving the operation efficiency COP of the refrigeration cycle.
  • the low-pressure refrigerant flowing into the compressor 1 is in a superheated gas state, a liquid back state due to an excessive inflow of liquid refrigerant into the compressor 1 is avoided.
  • the decompression device 5a controls the flow rate of the refrigerant by adjusting the opening degree so that the refrigerant subcooling degree at the outlet of the outdoor heat exchanger 3 becomes a predetermined value, it is condensed in the outdoor heat exchanger 3.
  • the liquid refrigerant is in a state having a predetermined degree of supercooling.
  • the refrigerant subcooling degree at the outlet of the outdoor heat exchanger 3 is detected by a value obtained by subtracting the gas side temperature sensor 202 (equivalent to the refrigerant condensation temperature Tc) from the detection value of the liquid side temperature sensor 204.
  • the decompression device 5b controls the flow rate of the refrigerant circulating through the indoor heat exchanger 7 by adjusting the opening degree so that the discharge refrigerant temperature of the compressor 1 becomes a predetermined value
  • the pressure reduction apparatus 5b is discharged from the compressor 1.
  • the discharged gas refrigerant is in a predetermined temperature state.
  • the discharge refrigerant temperature of the compressor 1 is detected by the compressor discharge temperature sensor 201 or the compressor shell temperature sensor 208.
  • required in the air-conditioning space in which the utilization unit B was installed flows into the indoor heat exchanger 7.
  • the four-way valve 2 is in the state indicated by the solid line in FIG. 1, that is, the discharge side of the compressor 1 is connected to the gas side of the indoor heat exchanger 7 and the suction side of the compressor 1 is connected to the outdoor heat exchanger 3. It is connected to the gas side.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 is sent to the utilization unit B via the four-way valve 2 and the gas connection pipe 9, reaches the indoor heat exchanger 7 that is a condenser, and is blown by the indoor blower 8.
  • the refrigerant condenses and becomes a high-pressure and low-temperature refrigerant.
  • the condensed and liquefied high-temperature and low-pressure refrigerant is sent to the heat source unit A via the liquid connection pipe 6 and is depressurized by the decompression device 5b to become an intermediate-pressure two-phase refrigerant, passes through the receiver 11, and is decompressed by the decompression device 5a.
  • the pressure is further reduced and sent to the outdoor heat exchanger 3.
  • the decompressed two-phase refrigerant is evaporated by the blowing action of the outdoor blower 4 in the outdoor heat exchanger 3 that is an evaporator, and becomes a low-pressure gas refrigerant.
  • the low-pressure gas refrigerant exchanges heat with the medium-pressure two-phase refrigerant between the decompression devices 5a and 5b in the internal heat exchanger 12 via the four-way valve 2, and then is sucked into the compressor 1 again.
  • the high-temperature medium-pressure two-phase refrigerant decompressed by the decompression device 5b is cooled to the saturated liquid refrigerant by the low-temperature low-pressure refrigerant circulating between the four-way valve 2 and the compressor 1 suction side (see FIG. 3 point D ⁇ change of point E).
  • the low-pressure refrigerant is heated to become a low-pressure superheated gas refrigerant and flows into the compressor 1 (change from point G to point A in FIG. 3).
  • the enthalpy of the refrigerant flowing into the indoor heat exchanger 7 is reduced, and the enthalpy difference at the entrance and exit of the indoor heat exchanger 7 is increased. Thereby, the refrigerant circulation amount necessary for obtaining a predetermined capacity is reduced, and the COP of the refrigeration cycle is improved by reducing the pressure loss.
  • the low-pressure refrigerant flowing into the compressor 1 is in a superheated gas state, a liquid back state due to an excessive inflow of liquid refrigerant into the compressor 1 is avoided.
  • the decompression device 5b controls the flow rate of the refrigerant flowing through the indoor heat exchanger 7 by adjusting the opening degree so that the degree of refrigerant supercooling at the outlet of the indoor heat exchanger 7 becomes a predetermined value
  • the liquid refrigerant condensed in the heat exchanger 7 is in a state having a predetermined degree of supercooling.
  • the refrigerant subcooling degree at the outlet of the indoor heat exchanger 7 is detected by a value obtained by subtracting the gas side temperature sensor 207 (equivalent to the refrigerant condensation temperature Tc) from the detection value of the liquid side temperature sensor 205.
  • the decompression device 5a controls the flow rate of the refrigerant circulating in the outdoor heat exchanger 3 by adjusting the opening degree so that the discharge refrigerant temperature of the compressor 1 becomes a predetermined value, it is discharged from the compressor 1.
  • the discharged gas refrigerant is in a predetermined temperature state.
  • the discharge refrigerant temperature of the compressor 1 is detected by the compressor discharge temperature sensor 201 or the compressor shell temperature sensor 208.
  • required in the air-conditioning space in which the utilization unit B was installed flows into the indoor heat exchanger 7.
  • a pressure sensor is installed on the discharge side of the compressor 1 to detect the refrigerant discharge pressure, and the discharge pressure The detected value may be converted into the saturation temperature and used as the refrigerant condensing temperature.
  • FIG. 4 is a flowchart showing a flow of activation control of the air-conditioning apparatus 100 according to Embodiment 1 of the present invention.
  • the drive unit 30c starts the compressor 1, and the measurement unit 30a starts time t measurement (STEP 11).
  • the control value of the maximum operating frequency Fmax of the compressor 1 is set to the initial value Fmax0.
  • the operating state of the air conditioner 100 is detected by the measuring unit 30a (STEP 12).
  • an operation state detection means for example, a temperature sensor that is installed in the heat source unit A or the utilization unit B of the air conditioner 100 and measures the refrigerant temperature and the air temperature, and a sensor that detects the operation frequency of the compressor 1 (not shown). Z). Based on these sensor detection values, it is detected as an operating state quantity.
  • the refrigerant flow rate Gr circulating through the refrigerant circuit of the air conditioner 100 is detected by calculating the refrigerant flow rate Gr by the calculation unit 30b based on the detected operating state quantity (STEP 13).
  • the refrigerant flow rate Gr is calculated using, for example, the following equation.
  • Vst is the compressor stroke volume [m 3 ]
  • F is the compressor operating frequency [Hz]
  • ⁇ s is the compressor suction refrigerant density [kg / m 3 ]
  • ⁇ v is the volumetric efficiency [ ⁇ ].
  • the compressor stroke volume Vst is a specification value of the compressor that is a component of the refrigerant circuit, is stored in advance in the storage unit 30d as device information, and is used as calculation information (constant) when calculating by the calculation unit 30b.
  • the compressor suction refrigerant density ⁇ s is a refrigerant physical property value, and is a value corresponding to the operation state based on the information on the refrigerant physical property value stored in advance in the storage unit 30d and the operation state amount detected by the measurement unit 30a. Is used as calculation information when the calculation unit 30b calculates.
  • the amount of operating state required at this time can be obtained from the intake refrigerant pressure Ps and the intake refrigerant temperature Ts of the compressor.
  • a method for detecting the suction refrigerant pressure Ps for example, first, the refrigerant evaporating temperature Te is detected, and the detected pressure value is obtained by converting to a saturated pressure.
  • the refrigerant evaporating temperature Te is a detection value of the gas side temperature sensor 207 provided in the indoor heat exchanger 7 (during cooling operation) or a detection value of the gas side temperature sensor 202 provided in the outdoor heat exchanger 3 (heating operation). Time).
  • the suction refrigerant temperature Ts is a low pressure Ps (equivalent to the suction pressure of the compressor) obtained by converting the evaporation temperature Te of the refrigerant into a saturation pressure, and a high pressure Pd (equivalent to the discharge pressure of the compressor) obtained by converting the condensation temperature Tc of the refrigerant into a saturation pressure.
  • the refrigerant discharge temperature Td, the compression step of the compressor 1 can be calculated from the following equation assuming that the polytropic index n is a polytropic change.
  • Ts and Td are temperature [K]
  • Ps and Pd are pressure [MPa]
  • n is a polytropic index [-].
  • the high pressure and low pressure of the refrigerant are calculated from the condensation temperature and the evaporation temperature of the refrigerant.
  • the pressure sensors are directly installed on the suction side and the discharge side of the compressor 1 to obtain the pressure. It may be.
  • a temperature sensor may be installed on the suction side of the compressor 1 to directly detect the suction refrigerant temperature Ts.
  • the volumetric efficiency ⁇ v is calculated when the calculation unit 30b calculates a value corresponding to the operation state based on the performance characteristics of the compressor previously stored in the storage unit 30d and the operation state quantity detected by the measurement unit 30a. Used as calculation information. Since the volumetric efficiency ⁇ v mainly changes depending on the compressor frequency F and the compression ratio (ratio of the high pressure Pd and the low pressure Ps), the volumetric efficiency value corresponding to these state quantities is stored in the storage unit 30d. .
  • the determination unit 30e it is determined whether or not the refrigerant flow rate Gr detected by the calculation unit 30b is equal to or greater than a predetermined determination threshold value (predetermined value Gr0) for the refrigerant flow rate Gr (STEP 14). If the detected refrigerant flow rate Gr is equal to or greater than the predetermined value Gr0, it is determined that the refrigerant flow rate is high (STEP 14; YES), and the control value of the maximum operating frequency Fmax of the compressor 1 is lower than the current value by the drive unit 30c. Change to Fmax1 (STEP 15). If the conditions are not satisfied, it is determined that the refrigerant flow rate is not high (STEP 14; NO), and the drive unit 30c continues the operation while maintaining the current maximum operating frequency Fmax of the compressor 1 (STEP 16).
  • predetermined value Gr0 a predetermined determination threshold value for the refrigerant flow rate Gr
  • the determination threshold value (predetermined value Gr0) of the refrigerant flow rate Gr and the maximum operating frequency Fmax are set to a level at which the refrigerating machine oil is not excessively discharged from the compressor 1 into the refrigerant circuit with respect to the refrigerant flow rate Gr. Set to.
  • the determination threshold Gr0 defined by the ratio of the mass flow rate of the refrigerating machine oil to the total mass flow rate of the refrigerant and the refrigerating machine oil so that the oil circulation rate of the refrigerating machine oil is 1.5% or less, and the maximum operating frequency Set Fmax.
  • the determination unit 30e determines whether or not the predetermined time t0 has elapsed after the start of the compressor 1 (STEP 17). If the predetermined time t0 has not elapsed (STEP 17; NO), the process returns to STEP 12 and is repeated. If the predetermined time t0 has elapsed (STEP 17; YES), the start-up control ends, the maximum operating frequency Fmax of the compressor 1 is changed to the control value Fmax2 during normal operation (STEP 18), and the control flow ends.
  • control value of the maximum operating frequency Fmax of the compressor 1 is set to satisfy Fmax2> Fmax0> Fmax1.
  • Embodiment 2 The structure of the air conditioning apparatus 200 according to Embodiment 2 of the present invention will be described. In the second embodiment, the description will focus on the differences from the first embodiment, and the description of similar parts will be omitted.
  • the refrigerant circuit, the configuration of the control unit, and the basic operation of the air conditioner 200 are the same as those in the first embodiment.
  • FIG. 5 is a flowchart showing a flow of control operation at start-up in the air-conditioning apparatus 200 according to Embodiment 2 of the present invention.
  • the operation mode (cooling operation / heating operation) of the air conditioner 200 is detected by the measurement unit 30a (STEP 21), and it is determined whether or not the operation mode is the cooling operation mode (STEP 22). If the operation mode is the cooling operation mode (STEP 22; YES), the drive unit 30c sets the maximum operation frequency Fmax of the compressor 1 to the control value Fmax_c during the cooling operation (STEP 23). If it is not the cooling operation mode, that is, if it is the heating operation mode (STEP 22; NO), the drive unit 30c sets the maximum operation frequency Fmax of the compressor 1 to the control value Fmax_h during the heating operation (STEP 24). Thereafter, the compressor 1 is activated by the drive unit 30c, and the time t measurement is started by the measurement unit 30a (STEP 25).
  • the refrigerant flow rate is higher in the cooling operation in which the operation is performed in the high outside air temperature condition than in the heating operation in which the operation is performed in the low outside air temperature condition.
  • the control value of the maximum operation frequency Fmax is set so that Fmax_c during cooling operation ⁇ Fmax_h during heating operation.
  • the determination unit 30e determines whether or not the predetermined time t0 has elapsed after the start of the compressor 1 (STEP 26). If the predetermined time t0 has not elapsed (STEP 26; NO), the process returns to STEP 26 and is repeated. If the predetermined time t0 has elapsed (STEP 26; YES), the start-up control is ended, the maximum operating frequency Fmax of the compressor 1 is changed to the control value Fmax2 for normal operation (STEP 27), and the control flow is ended.
  • control value of the maximum operating frequency Fmax of the compressor 1 is set to satisfy Fmax2> Fmax_h> Fmax_c.
  • Embodiment 3 The structure of the air conditioning apparatus 300 according to Embodiment 3 of the present invention will be described. In the second embodiment, the difference from the first and second embodiments will be mainly described, and the description of the same portions will be omitted.
  • the refrigerant circuit, the configuration of the control unit, and the basic operation of the air conditioning apparatus 300 are the same as those in the first and second embodiments.
  • FIG. 6 is a flowchart showing a flow of control operation at start-up in the air-conditioning apparatus 300 according to Embodiment 3 of the present invention.
  • STEP 31 to STEP 34 are the same operations as STEP 21 to STEP 24 shown in FIG. 5, and the control value of the maximum operating frequency Fmax of the compressor 1 at the initial start-up is set to Fmax_c during the cooling operation depending on whether the operation mode is the cooling operation or the heating operation. / Set to one of Fmax_h during heating operation.
  • the control value of the maximum operating frequency Fmax of the compressor 1 set here is set as the initial value Fmax0, and the compressor 1 is started by the drive unit 30c similarly to STEP 25, and the time t measurement is started by the measurement unit 30a. (STEP 35).
  • Subsequent STEP36 to STEP42 operate in the same manner as STEP12 to STEP18 shown in FIG.
  • an additional element that causes a cost increase such as an oil separator is not required, and a certain amount or more of refrigerating machine oil is supplied into the compressor regardless of operating conditions and operating conditions. Since it becomes possible to ensure the oil-repellency to maintain, a highly reliable air conditioner can be realized.
  • the air conditioner according to the present embodiment it is possible to suppress the discharge amount of the refrigeration oil that flows out of the compressor together with the refrigerant into the refrigerant circuit by the operation operation. Refrigeration cycle performance degradation associated with storage of water can be avoided, and high performance of the air conditioner can be realized.
  • the air conditioner installation conditions such as the length of the refrigerant pipe connecting the outdoor unit and the indoor unit, the height difference of the unit installation location, and the refrigerant charging amount are not included in the compressor. Since it is possible to ensure oil-repellency that maintains a certain amount or more of refrigerating machine oil, it is possible to achieve an increase in the upper limit of the allowable range of installation conditions (such as refrigerant pipe length and height difference of equipment installation location) in the use of air conditioning equipment.

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

Abstract

L'invention concerne un climatiseur comprenant: un moyen de détection d'état de fonctionnement qui détecte l'état de fonctionnement du climatiseur; un moyen d'évaluation d'écoulement de fluide frigorigène qui estime l'écoulement de fluide frigorigène circulant à travers un circuit de fluide frigorigène sur la base de l'état de fonctionnement détecté par le moyen de détection d'état de fonctionnement et évalue si le fonctionnement est en train d'effectuer un écoulement de fluide frigorigène élevé; et un moyen de commande qui, dans le cas où le moyen d'évaluation d'écoulement de fluide frigorigène évalue que le fonctionnement est effectué à un débit de fluide frigorigène dépassant une quantité prédéterminée, effectue une commande de façon à réduire la fréquence de fonctionnement maximale d'un compresseur jusqu'à ce qu'une période de temps prédéterminée soit écoulée après que le compresseur ait démarré.
PCT/JP2017/009419 2017-03-09 2017-03-09 Climatiseur Ceased WO2018163346A1 (fr)

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JP2019504217A JP6779361B2 (ja) 2017-03-09 2017-03-09 空気調和装置
PCT/JP2017/009419 WO2018163346A1 (fr) 2017-03-09 2017-03-09 Climatiseur

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PCT/JP2017/009419 WO2018163346A1 (fr) 2017-03-09 2017-03-09 Climatiseur

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116643602A (zh) * 2023-04-07 2023-08-25 武汉汉立制冷科技股份有限公司 一种激光制冷系统控制温差自适应修正方法
JPWO2023228323A1 (fr) * 2022-05-25 2023-11-30

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5812938A (ja) * 1981-07-17 1983-01-25 Hitachi Ltd 空気調和装置の制御方法
JP2007248001A (ja) * 2006-03-17 2007-09-27 Mitsubishi Electric Corp 冷凍空調装置

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4063023B2 (ja) * 2002-09-12 2008-03-19 株式会社デンソー 蒸気圧縮式冷凍機
JP4946840B2 (ja) * 2006-12-08 2012-06-06 ダイキン工業株式会社 冷凍装置

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5812938A (ja) * 1981-07-17 1983-01-25 Hitachi Ltd 空気調和装置の制御方法
JP2007248001A (ja) * 2006-03-17 2007-09-27 Mitsubishi Electric Corp 冷凍空調装置

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPWO2023228323A1 (fr) * 2022-05-25 2023-11-30
JP7683823B2 (ja) 2022-05-25 2025-05-27 三菱電機株式会社 冷凍サイクル装置
CN116643602A (zh) * 2023-04-07 2023-08-25 武汉汉立制冷科技股份有限公司 一种激光制冷系统控制温差自适应修正方法

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