WO2016181529A1 - 冷凍サイクル装置 - Google Patents
冷凍サイクル装置 Download PDFInfo
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- WO2016181529A1 WO2016181529A1 PCT/JP2015/063803 JP2015063803W WO2016181529A1 WO 2016181529 A1 WO2016181529 A1 WO 2016181529A1 JP 2015063803 W JP2015063803 W JP 2015063803W WO 2016181529 A1 WO2016181529 A1 WO 2016181529A1
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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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/029—Control issues
- F25B2313/0293—Control issues related to the indoor fan, e.g. controlling speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/029—Control issues
- F25B2313/0294—Control issues related to the outdoor fan, e.g. controlling speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
- F25B2313/0314—Temperature sensors near the indoor heat exchanger
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/031—Sensor arrangements
- F25B2313/0315—Temperature sensors near the outdoor heat exchanger
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
- F25B2600/025—Compressor control by controlling speed
- F25B2600/0253—Compressor control by controlling speed with variable speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/11—Fan speed control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/11—Fan speed control
- F25B2600/111—Fan speed control of condenser fans
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/11—Fan speed control
- F25B2600/112—Fan speed control of evaporator fans
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/21—Refrigerant outlet evaporator temperature
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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
- F25B2700/21—Temperatures
- F25B2700/2106—Temperatures of fresh outdoor air
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
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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
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Definitions
- the present invention relates to a refrigeration cycle apparatus using a low GWP refrigerant.
- a specific saturated fluorinated hydrocarbon refrigerant such as R32 has a lower GWP (global warming potential) and a lower pressure loss of the refrigerant than current refrigerants, and is thus being applied to a refrigeration cycle apparatus.
- R32 has a characteristic that the discharge temperature of the compressor is higher than the conventional R410A and the like, and a technique for suppressing the discharge temperature has been developed.
- a refrigerant containing 70 wt% of R32 is used, and a refrigeration cycle in which a compressor, a four-way valve, an outdoor heat exchanger, an expansion valve, a valve, an indoor heat exchanger, a gas-liquid separator, and an accumulator are connected in this order.
- a refrigeration cycle apparatus provided with (for example, refer to Patent Document 1).
- this refrigeration cycle apparatus by controlling the compressor or the expansion valve so that the dryness of the R32 refrigerant sucked into the compressor is 0.65 or more and 0.85 or less, the refrigerant discharged from the compressor is controlled. The discharge temperature is lowered.
- the discharge temperature of the refrigerant containing 70% or more of the R32 refrigerant is about 10 to 20 ° C. higher than that of R410A. .
- the discharge temperature of the refrigerant containing 70% or more of the R32 refrigerant is about 10 to 20 ° C. higher than that of R410A. .
- due to the high discharge temperature there is a problem that the refrigeration oil, the compressor material, the coating, and the substrate are deteriorated and the long-term reliability is lowered.
- the present invention has been made to solve the above-described problems.
- an ethylene-based fluorinated hydrocarbon refrigerant By using an ethylene-based fluorinated hydrocarbon refrigerant, it is possible to suppress an increase in discharge temperature while preventing liquid back, and to realize a low GWP.
- An object of the present invention is to provide a simple refrigeration cycle apparatus.
- a refrigeration cycle apparatus includes a refrigerant circuit including a compressor, a condenser, a decompression device, and an evaporator, a first fan that blows air to the condenser, a second fan that blows air to the evaporator, and a compressor
- a control unit that controls at least one of the frequency of the compressor, the opening of the pressure reducing device, the rotational speed of the first fan, and the rotational speed of the second fan so that the dryness at the time of refrigerant suction is 1.0 or more;
- the refrigerant circuit is configured such that a mixed refrigerant containing 30 wt% or more and 50% wt or less of the ethylene-based fluorinated hydrocarbon refrigerant circulates.
- the refrigeration cycle apparatus includes a refrigerant circuit including a compressor, a condenser, a decompression device, and an evaporator, a first fan that blows air to the condenser, a second fan that blows air to the evaporator, and outside air.
- the outside air temperature detecting means for detecting the temperature, the compressor frequency, the opening of the decompression device, the first so that the suction superheat degree at the time of refrigerant suction of the compressor is equal to or less than the outside air temperature detected by the outside air temperature detecting means.
- a control unit that controls at least one of the rotational speed of the fan and the rotational speed of the second fan, and the refrigerant circuit circulates 30 to 70% by weight of the ethylene-based fluorinated hydrocarbon refrigerant and circulates the mixed refrigerant It is comprised so that it may do.
- a refrigeration cycle apparatus capable of realizing a low GWP by using an ethylene-based fluorinated hydrocarbon refrigerant and suppressing an increase in discharge temperature while preventing liquid back.
- FIG. 1 is a PH diagram of an air conditioner according to Embodiment 1 of the present invention. It is a figure which shows the relationship between the mixing ratio of R1123 refrigerant
- FIG. 2 is a diagram showing a discharge temperature when the air conditioner of FIG.
- FIG. 2 is a diagram showing a discharge SH when the air conditioner of FIG. 1 is operated with a dryness at the time of suction of the compressor being 1 and changing the mixing ratio under heating high compression conditions.
- FIG. 2 is a diagram showing a discharge SH when the air conditioner of FIG. 1 is operated with a dryness of 1 when the compressor is sucked and changing the mixing ratio under heating low compression conditions.
- FIG. 2 is a diagram showing a discharge SH when the air conditioner of FIG. 1 is operated with a dryness at the time of suction of the compressor being 1, and changing a mixing ratio under heating standard conditions.
- FIG. 2 is a diagram showing a discharge SH when the air conditioner of FIG. 1 is operated with a dryness at the time of suction of the compressor being 1, and changing a mixing ratio under a heating overload condition.
- FIG. 2 is a diagram showing a discharge temperature when the air conditioner of FIG. 1 is operated with a dryness at the time of suction of the compressor being 1 and changing a mixing ratio under a cooling high compression condition.
- FIG. 2 is a diagram illustrating a discharge temperature when the air conditioner of FIG. 1 is operated with a dryness at the time of suction of the compressor being 1, and changing a mixing ratio under a cooling low compression condition.
- FIG. 2 is a diagram illustrating a discharge temperature when the air conditioner of FIG.
- FIG. 2 is a diagram illustrating a discharge temperature when the air conditioner of FIG. 1 is operated with a dryness at the time of suction of the compressor being 1 and changing a mixing ratio under a cooling overload condition.
- FIG. 2 is a diagram showing the discharge SH when the air conditioner of FIG. 1 is operated with a dryness at the time of suction of the compressor being 1, and changing the mixing ratio under the cooling high compression condition.
- FIG. 2 is a diagram illustrating a discharge SH when the air conditioner of FIG. 1 is operated with a dryness of 1 when sucking a compressor being changed and a mixing ratio is changed under a cooling low compression condition.
- FIG. 2 is a diagram showing a discharge SH when the air conditioner of FIG. 1 is operated with a dryness of 1 when the compressor is sucked and a mixture ratio changed under a cooling standard condition.
- FIG. 2 is a diagram showing the discharge SH when the air conditioner of FIG. 1 is operated with a dryness at the time of suction of the compressor being 1, and changing the mixing ratio under cooling overload conditions. It is a flowchart which shows operation
- FIG. 1 is a diagram illustrating a refrigerant circuit of an air-conditioning apparatus according to Embodiment 1 of the present invention.
- the air conditioner includes an outdoor unit 10 and an indoor unit 20.
- the outdoor unit 10 includes a compressor 11, a four-way valve 12, an outdoor heat exchanger 13, and an outdoor fan 14 that blows air to the outdoor heat exchanger 13.
- the outdoor unit 10 further includes a temperature detection unit 15 and a temperature detection unit 16.
- the indoor unit 20 includes an expansion valve 21, an indoor heat exchanger 22, an indoor fan 23 that blows air to the indoor heat exchanger 22, and temperature detection means 24.
- the expansion valve 21 is used as the pressure reducing device, but other pressure reducing devices such as a capillary tube may be used.
- the compressor 11, the four-way valve 12, the indoor heat exchanger 22, the expansion valve 21, and the outdoor heat exchanger 13 are connected by a refrigerant pipe to constitute a refrigerant circuit in which the refrigerant circulates.
- the air conditioner equipped with this refrigerant circuit cools and heats the room by switching the four-way valve 12.
- the indoor heat exchanger 22 functions as a condenser and the outdoor heat exchanger 13 functions as an evaporator
- the indoor heat exchanger 22 functions as an evaporator
- the outdoor heat exchanger 13 functions as a condenser.
- the air conditioner shown in FIG. 1 is the smallest component that can be operated for cooling and heating. Even if devices such as a pressure gauge, a gas-liquid branching device, a receiver, and an accumulator are further connected, the air conditioner is formed. Good.
- FIG. 2 is a schematic perspective view of the outdoor heat exchanger of the air-conditioning apparatus according to Embodiment 1 of the present invention.
- the outdoor heat exchanger 13 is configured by a heat exchanger having a heat transfer tube 13a formed of a circular tube or a flat multi-hole tube mainly composed of copper or aluminum.
- the indoor heat exchanger 22 is also composed of a heat exchanger having a heat transfer tube composed of a circular tube or a flat multi-hole tube mainly composed of copper or aluminum.
- the temperature detection means 15 is attached to the outer periphery of the pipe between the suction side of the compressor 11 and the four-way valve 12 and detects the suction temperature of the compressor 11.
- the temperature detection means 16 is attached in the vicinity of the middle position of all the pipe lengths in the outdoor heat exchanger 13, and detects the evaporating temperature during the heating operation and the condensing temperature during the cooling operation.
- the temperature detection means 24 is attached to the pipe outer periphery near the middle position of all the pipe lengths in the indoor heat exchanger 22, and detects the condensation temperature during the heating operation and the evaporation temperature during the cooling operation.
- the attachment positions of the temperature detection means 16 and the temperature detection means 24 are not limited to the above positions, and the temperature detection means 16 can detect the evaporation temperature during the heating operation and the condensation temperature during the cooling operation.
- the means 24 should just be provided in the position which can detect a condensing temperature at the time of heating operation, and evaporation temperature at the time of air_conditionaing
- a plurality of temperature detection means may be provided in the attachment section.
- the temperature detection means 15 is attached immediately before the suction portion of the compressor 11 from the viewpoint of accurately detecting the suction temperature of the compressor 11. It is preferable that the temperature detection means 16 is attached to the inlet side by heating operation rather than an intermediate position of all the pipe lengths of the outdoor heat exchanger 13. This is because the evaporator inlet side temperature (evaporation temperature in a two-phase state) can be reliably detected by attaching to the inlet side, and the suction SH can be accurately calculated.
- the temperature detection means 24 is preferably attached to the outlet side in the heating operation rather than an intermediate position of all the pipe lengths of the indoor heat exchanger 22. This is because by attaching to the outlet side, the evaporator inlet side temperature can be reliably detected during cooling operation, and the suction SH can be accurately calculated.
- the temperature detection means 15 is attached to a pipe between the evaporator outlet and the suction portion of the compressor 11 to detect the suction temperature
- the temperature detection means 16 includes the outlet of the expansion valve 21 and the outlet of the evaporator. What is necessary is just to detect evaporation temperature by being attached to piping between.
- the temperature detection means (first temperature detection means) 15 and the temperature detection means (second temperature detection means) 16 constitute the suction superheat degree detection means of the present invention.
- the air conditioner is further provided with a control unit 100 that controls the entire air conditioner.
- the control unit 100 is configured by a microcomputer or the like, and includes a CPU, a RAM, a ROM, and the like.
- the ROM stores a control program and a program corresponding to the flowchart of FIG.
- the control unit 100 is connected to these temperature detection means so as to receive detection signals from the temperature detection means 15, the temperature detection means 16, and the temperature detection means 24.
- the control unit 100 is connected to the compressor 11, the four-way valve 12, the expansion valve 21, and the indoor fan 23.
- the control unit 100 controls at least one of the frequency of the compressor 11, the opening degree of the expansion valve 21, the rotational speed of the outdoor fan 14, and the rotational speed of the indoor fan 23 based on the detection signal of each temperature detection means. To do.
- control unit 100 also detects the outside air temperature detected by the outside air temperature detecting means 17 configured by, for example, a temperature sensor so that the indoor temperature detected by the indoor temperature detecting means (not shown) becomes the target set temperature.
- the control unit 100 also detects the outside air temperature detected by the outside air temperature detecting means 17 configured by, for example, a temperature sensor so that the indoor temperature detected by the indoor temperature detecting means (not shown) becomes the target set temperature.
- the frequency of the compressor 11, the opening degree of the expansion valve 21, and the rotational speeds of the outdoor fan 14 and the indoor fan 23 is controlled.
- FIG. 1 shows a configuration in which one control unit 100 is provided, the functions of the control unit 100 are divided so that each of the outdoor unit 10 and the indoor unit 20 has a control unit, and the mutual processing is performed. You may make it the structure which performs.
- the compressor 11 is operated such that the discharge temperature of the compressor 11 is equal to or lower than the upper limit temperature for the purpose of avoiding material deterioration and oil deterioration of the compressor 11.
- the upper limit temperature is set to 120 ° C., which is the heat resistance reference temperature of the electric product defined by the Electric Safety Act. In order to secure long-term reliability, it is better to set the temperature at a lower 90 ° C.
- the refrigerant state becomes a superheated gas state when the dryness is 1.0 or more.
- the operation is performed so that the dryness of the refrigerant sucked in the compressor 11 is at least 1.0 or more.
- the target value of the suction superheat degree (hereinafter referred to as suction SH) is set to 0 or more so that the refrigerant state at the time of refrigerant suction of the compressor 11 is 1.0 or more, and the suction SH is Drive to 0 or more.
- suction SH the target value of the suction superheat degree
- the operation is performed so that the intake SH becomes 0 or more in a range where the discharge temperature during the operation does not exceed the upper limit temperature of 120 ° C.
- the suction SH at the time of heating is obtained by the difference between the detection temperature of the temperature detection means 15 and the detection temperature of the temperature detection means 16. Further, the suction SH during cooling is obtained from the difference between the temperature detected by the temperature detector 15 and the temperature detected by the temperature detector 24.
- the upper limit temperature of the discharge temperature is 120 ° C. as described above, but the lower limit temperature is determined as follows.
- discharge SH the discharge superheat degree (calculated by subtracting the saturated gas temperature of the pressure at the time of discharge from the discharge temperature)
- the discharge SH is ensured to be 10 ° C. or more, and the discharge temperature calculated using the discharge SH is set as the lower limit temperature.
- the discharge temperature calculated using the discharge SH is the temperature obtained by adding the discharge SH to the temperature detected by the temperature detection unit 24 during heating, and the discharge SH is added to the temperature detected by the temperature detection unit 16 during cooling. Temperature.
- the first embodiment uses a mixed refrigerant containing 30 wt% or more and 50 wt% or less of an ethylene-based fluorinated hydrocarbon refrigerant. The reason for the mixing ratio will be described in detail again.
- FIG. 3 is a schematic configuration diagram showing a PH diagram of the air-conditioning apparatus according to Embodiment 1 of the present invention.
- 3A to 3D show refrigerant states at the respective positions A to D in FIG.
- the refrigerant temperature is highest on the discharge side (point B) of the compressor 11 in the air conditioner.
- the suction temperature (temperature at point A) detected by the temperature detection means 15 is equal to or lower than the saturated gas temperature (temperature at point a)
- the liquid back state is established.
- the four-way valve 12 is switched to the state shown by the solid line in FIG.
- the refrigerant compressed by the compressor 11 becomes a high-temperature and high-pressure gas refrigerant, which is sent to the indoor heat exchanger 22 through the four-way valve 12.
- the refrigerant flowing into the indoor heat exchanger 22 is liquefied by exchanging heat with the indoor air conveyed by the indoor fan 23 and radiating heat.
- the liquefied refrigerant is decompressed by the expansion valve 21 to be in a gas-liquid two-phase state and flows into the outdoor heat exchanger 13.
- the refrigerant flowing into the outdoor heat exchanger 13 exchanges heat with the outdoor air conveyed by the outdoor fan 14, gasifies by absorbing heat, and is returned to the compressor 11.
- the heating operation is performed by circulating the refrigerant through the refrigerant circuit.
- the four-way valve 12 is switched to the state indicated by the dotted line in FIG.
- the refrigerant compressed by the compressor 11 becomes a high-temperature and high-pressure gas refrigerant, which is sent to the outdoor heat exchanger 13 through the four-way valve 12.
- the refrigerant flowing into the outdoor heat exchanger 13 is liquefied by exchanging heat with the outdoor air conveyed by the outdoor fan 14 and dissipating heat.
- the liquefied refrigerant is decompressed by the expansion valve 21 to become a gas-liquid two-phase state, and flows into the indoor heat exchanger 22.
- the refrigerant that has flowed into the indoor heat exchanger 22 exchanges heat with the indoor air conveyed by the indoor fan 23, gasifies by absorbing heat, and is returned to the compressor 11. As described above, the refrigerant circulates through the refrigerant circuit to perform the cooling operation.
- R1123 is preferable because the ethylene-based fluorohydrocarbon refrigerant has a low standard boiling point, and it is preferable to use R32 refrigerant having a boiling point close to that of R1123 as the refrigerant to be mixed with R1123.
- refrigerants generally used for air conditioning equipment for example, R410A, R407C, etc. may be used as the remaining refrigerant constituting the refrigerant.
- the remaining 70 wt% of the refrigerant may be a mixed refrigerant of a plurality of refrigerants, such as 50 wt% of R32 refrigerant and 20 wt% of R410A.
- R1123 ethylene-based fluorinated hydrocarbon refrigerants
- R1123 from the following points.
- R1123 and R32 are mixed, the boiling points are close, so that even if they are mixed, a pseudo azeotropic refrigerant can be obtained.
- GWP is 0. (GWP can be reduced by mixing)
- ⁇ GWP decreases even when mixed with HFO1234yf, but becomes a non-azeotropic refrigerant when mixed with R32 and HFO1234yf.
- the discharge temperature can be reduced by mixing with R1123 as compared with R32 alone.
- R1123 is not toxic or carcinogenic.
- FIG. 4 is a diagram showing the relationship between the mixing ratio of the R1123 refrigerant and the discharge temperature in the air conditioner of FIG. 4 shows a graph during heating operation at a high compression ratio.
- FIG. 5 is a diagram showing the relationship between the mixing ratio of the R1123 refrigerant and the discharge SH in the air conditioner of FIG. 4 and 5, the refrigerant mixed with the R1123 refrigerant is R32 refrigerant. 4 and 5 are graphs when the dryness of the compressor 11 when the refrigerant is sucked is 1.0.
- the mixing ratio is R1123 30 wt% or more, It is desirable to mix R32 at 70 wt% or less.
- the graph when the dryness is 1.0 is shown here, the graph of FIG. 4 moves upward as the dryness increases, and the graph of FIG. 4 moves downward as the dryness decreases. Will be moved to.
- the mixing ratio of the ethylene-based fluorohydrocarbon refrigerant is such that the discharge temperature of the compressor 11 is 120 ° C. or less and the discharge SH is 10 ° C. or more when the dryness of the suction refrigerant of the compressor 11 is at least 1.0. Mixing ratio.
- the reason why the mixed concentration of the ethylene-based fluorinated hydrocarbon refrigerant is set to 30 wt% or more and 50 wt% or less will be described based on more detailed data.
- FIG. 6A is a diagram showing the discharge temperature when the air-conditioning apparatus of FIG. 1 is operated with the dryness at the time of suction of the compressor being 1, and the mixing ratio is changed under heating high compression conditions.
- FIG. 6B is a diagram showing the discharge temperature when the air conditioner of FIG. 1 is operated with the dryness at the time of suction of the compressor being 1, and changing the mixing ratio under the heating low compression condition.
- FIG. 6C is a diagram showing the discharge temperature when the air conditioner of FIG. 1 is operated with the dryness at the time of suction of the compressor being 1, and changing the mixing ratio under the heating standard condition.
- 6D is a diagram illustrating a discharge temperature when the air conditioner of FIG. 1 is operated with a dryness of 1 when the compressor is sucked and a mixing ratio changed under a heating overload condition.
- the horizontal axis represents the mixing ratio [wt% / wt%] of R1123 and R32
- the vertical axis represents the discharge temperature [° C.].
- the discharge temperature when the suction SH is 0 is indicated by a black portion
- the discharge temperature when the suction SH is maximum is indicated by a hatched portion.
- the maximum value of the intake SH varies depending on the outside air temperature.
- the maximum value of the intake SH is 12 ° C. in the heating high compression condition of FIG. 6A, 6 ° C. in the heating low compression condition of FIG. 6B, and 15 ° C. in the heating standard condition of FIG. It has become.
- the discharge temperature can be made 120 ° C. or lower under any operating condition when the mixing ratio of R1123 is 30 wt% or more. That is, the minimum mixing ratio of R1123 capable of setting the discharge temperature to 120 ° C. or lower is 30 wt%, and if it is higher than this, the discharge temperature can be set to 120 ° C. or lower.
- the mixing ratio is 0/100, that is, when the refrigerant is a conventional R32 single refrigerant, the discharge temperature exceeds 120 ° C. even if the suction SH is 0 as shown in FIG. 6A.
- FIG. 7A is a diagram showing the discharge SH when the air-conditioning apparatus of FIG. 1 is operated with the dryness at the time of suction of the compressor being 1, and changing the mixing ratio under heating high compression conditions.
- FIG. 7B is a diagram showing the discharge SH when the air conditioner of FIG. 1 is operated with the dryness at the time of suction of the compressor being 1, and changing the mixing ratio under the heating low compression condition.
- FIG. 7C is a diagram showing the discharge SH when the air conditioner of FIG. 1 is operated with the dryness at the time of suction of the compressor being 1, and changing the mixing ratio under the heating standard condition.
- FIG. 7D is a diagram showing the discharge SH when the air conditioner of FIG. 1 is operated with the dryness at the time of suction of the compressor being 1, and changing the mixing ratio under the heating overload condition.
- the horizontal axis represents the mixing ratio [wt% / wt%] of R1123 and R32, and the vertical axis represents the discharge SH [° C.].
- the discharge SH when the suction SH is 0 is indicated by a black portion
- the discharge SH when the suction SH is maximum is indicated by a hatched portion.
- the discharge SH becomes 10 ° C. or higher when the mixing ratio of R1123 is 70 wt% or less under any operating condition.
- the maximum mixing ratio of R1123 that allows the discharge SH to be 10 ° C. or higher under any operating condition is 70 wt%.
- the discharge SH cannot be secured at 10 ° C. or more when the suction SH is 0 (dryness 1.0).
- FIG. 8A is a diagram showing the discharge temperature when the air-conditioning apparatus of FIG. 1 is operated with the dryness at the time of suction of the compressor being 1, and changing the mixing ratio under the cooling high compression condition.
- FIG. 8B is a diagram showing the discharge temperature when the air-conditioning apparatus of FIG. 1 is operated with the dryness at the time of suction of the compressor being 1 and changing the mixing ratio under the cooling low compression condition.
- FIG. 8C is a diagram showing the discharge temperature when the air-conditioning apparatus of FIG. 1 is operated with the dryness at the time of suction of the compressor being 1, and changing the mixing ratio under the cooling standard conditions.
- FIG. 8D is a diagram showing the discharge temperature when the air conditioner of FIG. 1 is operated with the dryness at the time of suction of the compressor being 1 and changing the mixing ratio under the cooling overload condition.
- the horizontal axis represents the mixing ratio [wt% / wt%] of R1123 and R32, and the vertical axis represents the discharge temperature [° C.].
- the discharge temperature when the suction SH is 0 is indicated by a black portion
- the discharge temperature when the suction SH is the maximum is indicated by a hatched portion.
- the maximum value of the intake SH varies depending on the outside air temperature.
- the maximum value of the intake SH is 24 ° C. in the cooling high compression condition of FIG. 8A, 4 ° C. in the cooling low compression condition of FIG. 8B, and 32 ° C. in the cooling standard condition of FIG.
- the cooling overload condition in FIG. 8D is 18 ° C.
- the cooling operation generally tends to have a lower discharge temperature than the heating operation, and the discharge temperature is 120 ° C. or lower in any cooling operation condition.
- the mixing ratio of R1123 is 0 wt%, that is, the conventional R32 single refrigerant
- the discharge temperature is 120 ° C. or less in the cooling operation.
- the mixing ratio of R1123 is less than 30 wt%, as described above, the dryness is 1.0 or more and the discharge temperature exceeds 120 ° C. in the heating condition, so the minimum mixing ratio of R1123 needs to be 30 wt%. There is.
- FIG. 9A is a diagram showing the discharge SH when the air-conditioning apparatus of FIG. 1 is operated with the dryness at the time of suction of the compressor being 1 and changing the mixing ratio under the cooling high compression condition.
- FIG. 9B is a diagram showing the discharge SH when the air conditioner of FIG. 1 is operated with the dryness at the time of suction of the compressor being 1, and changing the mixing ratio under the cooling low compression condition.
- FIG. 9C is a diagram showing the discharge SH when the air conditioner of FIG. 1 is operated with the dryness at the time of suction of the compressor set to 1 and the mixing ratio changed under the cooling standard conditions.
- FIG. 9D is a diagram showing the discharge SH when the air conditioner of FIG. 1 is operated with the dryness at the time of suction of the compressor being 1 and changing the mixing ratio under the cooling overload condition.
- the horizontal axis indicates the mixing ratio [wt% / wt%] of R1123 and R32, and the vertical axis indicates the discharge SH [° C.].
- the discharge SH when the suction SH is 0 is indicated by a black portion
- the discharge SH when the suction SH is the maximum is indicated by a hatched portion.
- the discharge SH in the cooling operation, the discharge SH generally tends to be lower than that in the heating operation, and among the cooling operation conditions, the cooling low compression ratio condition shown in FIG. 9B has the lowest discharge SH. .
- the discharge SH even under the cooling low compression ratio condition in which the discharge SH is low, by setting the mixing ratio of R1123 to 50% or less, even if the suction SH is 0, the discharge SH is 10 ° C. or higher.
- the mixing ratio of R1123 is set to 50% or less, the discharge SH can be set to 10 ° C. or higher not only in the heating operation but also in the cooling operation.
- the discharge SH when the intake SH is maximized (equal to the outside air), the discharge SH is 10 ° C. or more when the mixing ratio of R1123 is 70% or less.
- R1123 is set to 30 wt% or more and 50 wt% or less in order to establish the cooling / heating condition in which the dryness of the refrigerant when sucking the compressor is set to 1.0 or more and the upper limit temperature of the discharge temperature is set to 120 ° C. It is necessary to use a mixed refrigerant contained in
- the intake SH is maximized (equivalent to the outside air), in other words, if the intake SH is set to the outside air temperature or less, the ratio of the mixed refrigerant of R1123 is 30 wt% or more and 70 wt% or less. Can be raised to 10 ° C. or higher.
- the control unit 100 of the air conditioner is configured such that the frequency of the compressor 11, the opening degree of the expansion valve 21, the outdoor fan 14, and the temperature are detected based on the temperature detection unit 15, the temperature detection unit 16, and the temperature detection unit 24.
- the rotation speed of the indoor fan 23 is controlled.
- control unit 100 controls the frequency of the compressor 11, the opening degree of the expansion valve 21, the rotational speed of the outdoor fan 14, and the indoor fan 23 so that the discharge temperature of the refrigerant discharged from the compressor 11 is 120 ° C. or less. Control at least one of the rotational speeds.
- control unit 100 compresses the compressor so that the room temperature becomes the target set temperature based on the discharge temperature and each temperature detected by the room temperature detection means and the outside air temperature detection means not shown in FIG. 11 is also performed to control at least one of the frequency 11, the opening degree of the expansion valve 21, and the rotational speed of the outdoor fan 14 and the indoor fan 23.
- FIG. 10 is a flowchart showing the operation of the air-conditioning apparatus according to Embodiment 1 of the present invention.
- the heat exchangers are not distinguished as the outdoor heat exchanger 13 and the indoor heat exchanger 22, but are described as an evaporator or a condenser showing the function.
- control unit 100 determines whether the refrigeration cycle is a cooling operation or a heating operation based on information input to the control unit 100 from the outside (S1).
- the control unit 100 switches the four-way valve 12 to be a heating circuit when it is determined to be a heating operation (S2), and determines that the four-way valve 12 is to be a cooling circuit when it is determined to be a cooling operation (S3). And the control part 100 acquires the temperature detected by each of the temperature detection means 15, the temperature detection means 16, and the temperature detection means 24 (S4). Then, the control unit 100 calculates the pressure (intake pressure, low pressure, high pressure) of each part from a preset relational expression of the temperature and pressure of the refrigerant based on each acquired temperature (S5).
- control unit 100 determines whether the suction SH is 0 ° C. or higher (S6).
- the calculation method of inhalation SH is as described above.
- the control unit 100 proceeds to S7 if the inhalation SH is less than 0 ° C, and proceeds to S8 if it is 0 ° C or more.
- the control part 100 changes at least one among the frequency of the compressor 11, the opening degree of the expansion valve 21, the rotation speed of the outdoor fan 14, and the rotation speed of the indoor fan 23 (S7). Specifically, the control unit 100 increases the frequency of the compressor 11 and raises the opening of the expansion valve 21 in order to increase the suction SH.
- the evaporator fan (the outdoor fan 14 during heating and the indoor fan during cooling). The control of increasing the rotational speed of 23) is performed.
- control unit 100 returns to S6 and determines again whether the inhalation SH is 0 or more. If the suction SH is less than 0, the liquid back state has not yet been resolved, and the control unit 100 performs the process of S7 again. On the other hand, when determining that the suction SH is 0 or more, the control unit 100 determines that the liquid back state has been eliminated, and performs the next process of S8.
- control unit 100 calculates the suction entropy from the refrigerant temperature and pressure before the compressor suction.
- the intake entropy is calculated based on the intake temperature detected by the temperature detection means 15 and the intake pressure calculated based on the intake temperature both during heating and during cooling.
- the control unit 100 calculates the discharge temperature (S9).
- the discharge temperature is calculated as follows. First, the control unit 100 calculates an ideal discharge temperature on the assumption that the change of the refrigerant in the compressor 11 is an isentropic change, corrects the discharge temperature with the compressor efficiency, and sets the corrected discharge temperature. obtain.
- the ideal discharge temperature is calculated.
- an ideal discharge is obtained from the high pressure obtained by converting the temperature detected by the temperature detection means 16 into saturation, the suction pressure converted from the suction temperature detected by the temperature detection means 15, and the suction temperature. Calculate the temperature.
- the ideal discharge temperature is corrected on the assumption that the compressor efficiency is 0.7, and the corrected discharge temperature is obtained.
- the control unit 100 determines whether or not the discharge temperature obtained in S9 is within a preset range (hereinafter referred to as a threshold range) (S10).
- the upper limit temperature of the threshold range is 120 ° C., which is the heat resistant temperature of the motor component
- the lower limit temperature is a temperature at which the discharge SH becomes 10 ° C. or higher. That is, the lower limit temperature at the time of heating is a temperature obtained by adding the discharge SH to the detected temperature detected by the temperature detecting unit 16, and a temperature obtained by adding the discharge SH to the detected temperature detected by the temperature detecting unit 24 during cooling. .
- the controller 100 determines that the discharge temperature obtained in S7 is outside the threshold range, the frequency of the compressor 11, the opening of the expansion valve 21, and the rotation of the outdoor fan 14 are set so that the discharge temperature is within the threshold range. At least one of the number and the number of rotations of the indoor fan 23 is changed (S11). On the other hand, if the discharge temperature is within the threshold range, the control unit 100 continues the operation as it is.
- the air-conditioning apparatus uses a mixed refrigerant containing 30 wt% or more and 50 wt% or less of an ethylene-based fluorinated hydrocarbon refrigerant (for example, R1123), so that the dryness at the time of refrigerant suction is 1.0 or more. Also, by controlling at least one of the frequency of the compressor 11, the opening degree of the expansion valve 21, the rotational speed of the outdoor fan 14, and the rotational speed of the indoor fan 23, the discharge temperature is set within a preset threshold range. can do. Therefore, while using a low GWP refrigerant, it is possible to prevent liquid back, improve the reliability of the compressor material by preventing excessive heating of the discharge temperature, and prevent wear and heat generation of the compressor sliding part by avoiding insufficient discharge SH. Can be planned.
- an ethylene-based fluorinated hydrocarbon refrigerant for example, R1123
- the air conditioner according to Embodiment 1 uses the mixed refrigerant containing 30 wt% or more and 70 wt% or less of an ethylene-based fluorinated hydrocarbon refrigerant (for example, R1123), thereby maximizing the intake SH when the refrigerant is sucked (outside air
- the discharge temperature is set in advance by controlling at least one of the frequency of the compressor 11, the opening degree of the expansion valve 21, the rotational speed of the outdoor fan 14, and the rotational speed of the indoor fan 23. Can be within range. Therefore, while using a low GWP refrigerant, it is possible to prevent liquid back, improve the reliability of the compressor material by preventing excessive heating of the discharge temperature, and prevent wear and heat generation of the compressor sliding part by avoiding insufficient discharge SH. Can be planned.
- the air conditioning apparatus according to Embodiment 1 sets the dryness at the time of refrigerant suction to 1.0 or more, liquid back can be prevented.
- the air conditioner according to Embodiment 1 by preventing the liquid back and allowing the gas state refrigerant to flow into the compressor 11 reliably, the viscosity of the refrigeration oil decreases, the compressor sliding part wears, Deterioration and failure due to heat generation can be prevented.
- the refrigerant state in the compressor 11 flows into the compressor 11 in a two-phase state by reliably flowing the refrigerant in the gas state into the compressor 11. As a result, the control stability can be improved.
- the air conditioner according to Embodiment 1 by using a mixed refrigerant containing 30 wt% or more and 50 wt% or less of an ethylene-based fluorinated hydrocarbon refrigerant, even when the dryness at the time of refrigerant suction is 1.0 or more, The discharge temperature can be reduced as compared with the case where the R32 single refrigerant is operated at the same saturation temperature.
- the air conditioner according to Embodiment 1 by setting the upper limit temperature of the discharge temperature threshold range to 120 ° C., deterioration of the refrigeration oil, the compressor material, the coating, and the substrate can be prevented, and the reliability Can be improved.
- the lower limit temperature of the discharge temperature threshold range is determined in consideration of ensuring the viscosity of the refrigerating machine oil. As a result, wear and heat generation of the compressor sliding portion can be prevented.
- the air-conditioning apparatus can form a refrigeration cycle capable of reducing GWP by using a refrigerant containing an ethylene-based fluorinated hydrocarbon refrigerant (for example, R1123 refrigerant).
- a refrigerant containing an ethylene-based fluorinated hydrocarbon refrigerant for example, R1123 refrigerant.
- the air-conditioning apparatus according to Embodiment 1 becomes a pseudo-azeotropic mixed refrigerant by using a mixed refrigerant of R1123 and R32, it is possible to eliminate a temperature change accompanying a phase change.
- the cross-sectional area of the circular pipe in the pipe is 5.3 mm 2.
- tube can be reduced.
- discharge temperature can be reduced.
- the cross-sectional area of the circular pipe to 65.3 mm 2 or less, it is possible to prevent the size of the heat exchanger from becoming excessive and to prevent an increase in the amount of enclosed refrigerant.
- the cross-sectional area of the flat multi-hole tube is 0.
- the thickness is 0.8 mm 2 or more
- the pressure loss in the pipe can be reduced.
- discharge temperature can be reduced.
- the cross-sectional area of the flat multi-hole tube to 4.8 mm 2 or less, it is possible to prevent the size of the heat exchanger from becoming excessive and to prevent an increase in the amount of enclosed refrigerant.
- tube is a cross-sectional area considered when the use as a heat exchanger for an air conditioning is assumed.
- the cost for forming the air conditioner can be reduced.
- Embodiment 2 the detection means for detecting the state of the refrigerant is different from that in the first embodiment, and the other configuration of the refrigeration cycle is the same as that in the first embodiment. In the following, the second embodiment will be described focusing on the differences from the first embodiment.
- FIG. 11 is a diagram illustrating a refrigerant circuit of the air-conditioning apparatus according to Embodiment 2 of the present invention.
- the air conditioner of the second embodiment has a configuration in which the air conditioner of the first embodiment shown in FIG. 1 is further provided with a temperature detecting means 30, a temperature detecting means 31, and a temperature detecting means 32.
- the temperature detection means 30 is provided between the discharge side of the compressor 11 and the four-way valve 12, particularly on the pipe outer periphery near the outlet of the compressor 11, and detects the discharge temperature of the compressor 11.
- the temperature detection means 31 is provided between the discharge side of the compressor 11 and the four-way valve 12, particularly in the vicinity of the outlet of the compressor 11, and detects the discharge pressure of the compressor 11.
- the temperature detection means 32 is attached between the suction side of the compressor 11 and the four-way valve 12, particularly in the vicinity of the inlet of the compressor 11, and detects the suction pressure of the compressor 11.
- the control unit 100 is connected to these detection means so as to receive detection signals from the temperature detection means 30, the temperature detection means 31, and the temperature detection means 32. And the control part 100 is based on the calculation result obtained from the detection result of the temperature detection means 15, the temperature detection means 16, the temperature detection means 24, the temperature detection means 30, the temperature detection means 31, and the temperature detection means 32, and it is a compressor. 11, the opening degree of the expansion valve 21, the rotational speed of the outdoor fan 14, and the rotational speed of the indoor fan 23 are controlled.
- the air-conditioning apparatus includes the temperature detection unit 31 and the temperature detection unit 32, and thus directly measures the high pressure and the low pressure from the detection temperature as in the first embodiment. It becomes possible. Further, the discharge temperature can be directly measured by the temperature detection means 30. As a result, the steps S5, S8, and S9 are omitted in the flowchart of FIG.
- the air conditioner according to the second embodiment can obtain the same effects as those of the first embodiment, and can accurately detect the discharge temperature of the compressor 11 by providing the temperature detection means 30. For this reason, the control which discharge temperature does not exceed upper limit temperature more reliably can be implement
- the temperature detecting means 31 and the temperature detecting means 32 it is possible to detect high and low pressure with high accuracy. For this reason, the discharge temperature of S9 in FIG. 10 can be accurately calculated. If the actuator is controlled so that both the calculated discharge temperature and the discharge temperature detected by the temperature detecting means 30 are equal to or lower than the preset upper limit temperature of the discharge temperature, the discharge can be performed more reliably. Control that the temperature does not exceed the upper limit temperature can be realized.
- the refrigeration cycle apparatus is described as an air conditioner.
- a cooling apparatus or a hot water supply apparatus that cools a refrigerated warehouse or the like may be used.
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Abstract
Description
図1は、本発明の実施の形態1に係る空気調和装置の冷媒回路を示す図である。
空気調和装置は、室外機10と、室内機20とを有している。室外機10は、圧縮機11と、四方弁12と、室外熱交換器13と、室外熱交換器13に送風する室外ファン14とを備えている。室外機10は更に、温度検知手段15と温度検知手段16とを備えている。
室外熱交換器13は、銅又はアルミを主成分とした円管又は扁平多穴管で構成された伝熱管13aを有する熱交換器で構成される。室内熱交換器22も室外熱交換器13と同様に銅又はアルミを主成分とした円管又は扁平多穴管で構成された伝熱管を有する熱交換器で構成される。
温度検知手段15は、圧縮機11の吸入側と四方弁12との間の配管外周部に取り付けられ、圧縮機11の吸入温度を検知する。温度検知手段16は、図2に示すように室外熱交換器13内の全配管長の中間位置付近に取り付けられ、暖房運転時に蒸発温度、冷房運転時に凝縮温度を検知する。温度検知手段24は、室内熱交換器22内の全配管長の中間位置付近の配管外周部に取り付けられ、暖房運転時に凝縮温度、冷房運転時に蒸発温度を検知する。なお、温度検知手段16及び温度検知手段24の取り付け位置は上記の位置に限られたものではなく、温度検知手段16は暖房運転時に蒸発温度、冷房運転時に凝縮温度を検知でき、また、温度検知手段24は、暖房運転時に凝縮温度、冷房運転時に蒸発温度を検知できる位置に設けられていればよい。また、前記取り付け区間に複数の温度検知手段を設けてもよい。
本実施の形態1では、圧縮機11の材料劣化及び油劣化等を避けることを目的に圧縮機11の吐出温度が上限温度以下となるように運転する。この上限温度は、ここでは、電安法により定められた電気品の耐熱基準温度である120℃とする。なお、長期信頼性確保のため更に低い90℃に設定すると更によい。
図3から明らかなように、空気調和装置おいて最も冷媒の温度が高くなるのは圧縮機11の吐出側(B点)である。また、温度検知手段15で検知される吸入温度(A点の温度)が飽和ガス温度(点aの温度)以下となると、液バック状態となる。
暖房運転では、四方弁12が図1の実線で示される状態に切り換えられる。空気調和装置において、暖房運転時は、圧縮機11で圧縮された冷媒は高温高圧のガス冷媒となり、四方弁12を通り室内熱交換器22に送り込まれる。室内熱交換器22に流入した冷媒は、室内ファン23で搬送される室内空気と熱交換し、放熱することにより液化する。液化した冷媒は膨張弁21で減圧されて気液二相状態となり、室外熱交換器13に流入する。室外熱交換器13に流入した冷媒は、室外ファン14で搬送される室外空気と熱交換し、吸熱することによりガス化し、圧縮機11へ戻される。以上のように冷媒が冷媒回路を循環することにより暖房運転を行う。
冷房運転では、四方弁12が図1の点線で示される状態に切り換えられる。空気調和装置において、冷房運転時は、圧縮機11で圧縮された冷媒は高温高圧のガス冷媒となり、四方弁12を通り室外熱交換器13に送り込まれる。室外熱交換器13に流入した冷媒は、室外ファン14で搬送される室外空気と熱交換し、放熱することにより液化する。液化した冷媒は膨張弁21で減圧されて気液二相状態となり、室内熱交換器22に流入する。室内熱交換器22に流入した冷媒は、室内ファン23で搬送される室内空気と熱交換し、吸熱することによりガス化し、圧縮機11へ戻される。以上のように冷媒が冷媒回路を循環することにより冷房運転を行う。
(1)R32に近い沸点(-57℃)でR32同等程度の高圧冷媒であること。
(2)R1123とR32との混合の場合沸点が近いため、混合しても擬似共沸冷媒とできること。
(3)GWPが0であること。(混合によりGWPが低減可能)
→HFO1234yfとの混合でもGWPは低下するが、R32とHFO1234yfとの混合では非共沸冷媒となること。
(4)R1123との混合により、R32単体よりも吐出温度を低減可能であること。
(5)R1123には毒性及び発がん性がないこと。
実施の形態2は、冷媒の状態を検知するための検知手段が実施の形態1と異なるものであり、それ以外の冷凍サイクルの構成は実施の形態1と同様である。以下、実施の形態2が実施の形態1と異なる部分を中心に説明する。
実施の形態2の空気調和装置は、図1に示した実施の形態1の空気調和装置に更に、温度検知手段30、温度検知手段31及び温度検知手段32を備えた構成である。温度検知手段30は、圧縮機11の吐出側と四方弁12との間、特に圧縮機11の出口近傍の配管外周部に設けられ、圧縮機11の吐出温度を検知する。温度検知手段31は、圧縮機11の吐出側と四方弁12との間、特に圧縮機11の出口近傍に設けられ、圧縮機11の吐出圧力を検知する。温度検知手段32は、圧縮機11の吸入側と四方弁12との間、特に圧縮機11の入口近傍に取り付けられ、圧縮機11の吸入圧力を検知する。
Claims (9)
- 圧縮機、凝縮器、減圧装置及び蒸発器を備えた冷媒回路と、
前記凝縮器に送風する第1ファンと、
前記蒸発器に送風する第2ファンと、
前記圧縮機の冷媒吸入時の乾き度が1.0以上となるように、前記圧縮機の周波数、前記減圧装置の開度、前記第1ファンの回転数及び前記第2ファンの回転数の少なくとも一つを制御する制御部とを備え、
前記冷媒回路は、エチレン系フッ化炭化水素冷媒を30wt%以上50%wt以下、含有する混合冷媒が循環するように構成されている冷凍サイクル装置。 - 圧縮機、凝縮器、減圧装置及び蒸発器を備えた冷媒回路と、
前記凝縮器に送風する第1ファンと、
前記蒸発器に送風する第2ファンと、
外気温度を検知する外気温度検知手段と、
前記圧縮機の冷媒吸入時の吸入過熱度が前記外気温度検知手段で検知された外気温度以下となるように、前記圧縮機の周波数、前記減圧装置の開度、前記第1ファンの回転数及び前記第2ファンの回転数の少なくとも一つを制御する制御部とを備え、
前記冷媒回路は、エチレン系フッ化炭化水素冷媒を30wt%以上70%wt以下、含有する混合冷媒が循環するように構成されている冷凍サイクル装置。 - 前記制御部は、前記圧縮機の吐出温度を予め設定された範囲内にする制御を行う請求項1又は請求項2記載の冷凍サイクル装置。
- 前記予め設定された範囲の上限温度は120℃、下限温度は前記圧縮機の吐出過熱度が10℃となる吐出温度である請求項3記載の冷凍サイクル装置。
- 前記圧縮機に吸入される冷媒の吸入過熱度を検知する吸入過熱度検知手段を備え、
前記制御部は、前記吸入過熱度が0℃以上となるように、前記圧縮機の周波数、前記減圧装置の開度、前記第1ファンの回転数及び第2ファンの回転数の少なくとも一つを制御することで、前記圧縮機の冷媒吸入時の乾き度を1.0以上とする請求項1記載の冷凍サイクル装置。 - 前記吸入過熱度検知手段は、
前記蒸発器出口と前記圧縮機の吸入部との間の配管に取り付けられ、吸入温度を検知する第1温度検知手段と、前記減圧装置の出口と前記蒸発器の出口との間の配管に取り付けられ、蒸発温度を検知する第2温度検知手段とを備え、これらの検知温度の温度差から吸入過熱度を検知する請求項5記載の冷凍サイクル装置。 - 前記第2温度検知手段は前記蒸発器を構成する配管の全長の中間位置よりも冷媒出口側に設けられている請求項6記載の冷凍サイクル装置。
- 前記冷媒回路における冷媒の流れを切り替えて冷房運転と暖房運転とを可能とする四方弁を備えた請求項1~請求項7の何れか一項に記載の冷凍サイクル装置。
- 前記混合冷媒は、前記エチレン系フッ化炭化水素冷媒とR32冷媒とを混合した冷媒である請求項1~請求項8の何れか一項に記載の冷凍サイクル装置。
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