WO2022038922A1 - Dispositif à cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération Download PDF

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Publication number
WO2022038922A1
WO2022038922A1 PCT/JP2021/025952 JP2021025952W WO2022038922A1 WO 2022038922 A1 WO2022038922 A1 WO 2022038922A1 JP 2021025952 W JP2021025952 W JP 2021025952W WO 2022038922 A1 WO2022038922 A1 WO 2022038922A1
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WIPO (PCT)
Prior art keywords
refrigerant
unit
evaporator
opening degree
temperature
Prior art date
Application number
PCT/JP2021/025952
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English (en)
Japanese (ja)
Inventor
徹 岡村
紘明 河野
直也 牧本
吉毅 加藤
Original Assignee
株式会社デンソー
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.)
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Publication date
Priority claimed from JP2021087579A external-priority patent/JP2022035977A/ja
Application filed by 株式会社デンソー filed Critical 株式会社デンソー
Priority to CN202180051002.1A priority Critical patent/CN115885142A/zh
Publication of WO2022038922A1 publication Critical patent/WO2022038922A1/fr

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/22—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • 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
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • 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

Definitions

  • the present disclosure relates to a refrigeration cycle device in which the opening degree of the decompression unit is controlled by a control unit.
  • Patent Document 1 describes a refrigeration cycle device applied to a vehicle air conditioner.
  • the evaporator cools the air blown into the vehicle interior by exchanging heat between the refrigerant flowing out from the expansion valve and the air blown into the vehicle interior.
  • the opening degree of the expansion valve is controlled by the control device so that the degree of superheat of the refrigerant flowing into the compressor approaches the target degree of superheat.
  • the refrigerant flowing into the compressor may not be able to take the degree of superheat, such as when the suction air temperature of the evaporator is low. If there is a large load fluctuation under such conditions, the refrigerant may dry out in the evaporator and the evaporator may not be able to exert its cooling capacity.
  • the dry out means that the evaporation of the refrigerant becomes excessive in the evaporator and the region where only the vapor phase refrigerant exists becomes excessive.
  • the present disclosure aims to suppress the dryout of the refrigerant in the evaporator.
  • the refrigeration cycle device includes a compressor, a heat dissipation unit, a decompression unit, an evaporation unit, a refrigerant state detection unit, and a control unit.
  • the compressor sucks in the refrigerant, compresses it, and discharges it.
  • the heat radiating unit dissipates the refrigerant.
  • the pressure reducing unit can reduce the pressure of the refrigerant and adjust the flow path opening so that the flow rate of the refrigerant is adjusted.
  • the evaporation unit causes the refrigerant decompressed by the decompression unit to absorb heat from the air.
  • the refrigerant state detection unit detects the state of the refrigerant on the downstream side of the refrigerant inlet of the evaporation unit and on the upstream side of the suction port of the compressor.
  • the control unit controls the opening degree of the decompression unit to a normal opening degree at which the degree of superheat of the refrigerant flowing out of the evaporator approaches the target degree of superheat, and the state of the refrigerant detected by the refrigerant state detection unit is set. Based on this, it is determined whether or not the refrigerant is dry out in the evaporating unit, and when it is determined that the refrigerant is dry out in the evaporating unit, the opening degree of the decompression unit is made larger than the normal opening degree.
  • the flow rate of the refrigerant flowing into the evaporation unit can be increased, so that the dry out of the refrigerant in the evaporator can be suppressed.
  • FIG. 1st Embodiment It is an overall block diagram of the refrigeration cycle apparatus in 1st Embodiment. It is a block diagram which shows the electric control part of the refrigeration cycle apparatus in 1st Embodiment. It is a flowchart which shows the control process of the control program in 1st Embodiment. It is a graph which shows the refrigerant temperature and the refrigerant pressure when the dryout does not occur in the evaporator of 1st Embodiment. It is a graph which shows the refrigerant temperature and the refrigerant pressure when the dryout occurs in the evaporator of 1st Embodiment.
  • the vehicle air conditioner 1 shown in FIG. 1 is an air conditioner that adjusts the vehicle interior space (in other words, the air conditioning target space) of an automobile to an appropriate temperature.
  • the vehicle air conditioner 1 has a refrigeration cycle device 10.
  • the refrigerating cycle device 10 is a steam compression type refrigerating machine including a compressor 11, a condenser 12, a receiver 13, an expansion valve 14, and an evaporator 15.
  • the refrigeration cycle apparatus 10 of the present embodiment uses a fluorocarbon-based refrigerant as the refrigerant, and constitutes a subcritical refrigeration cycle in which the pressure of the high-pressure side refrigerant does not exceed the critical pressure of the refrigerant.
  • a refrigerant circulation circuit is formed in the refrigeration cycle device 10.
  • the refrigerant circulates in the order of the compressor 11, the condenser 12, the receiver 13, the expansion valve 14, the evaporator 15, and the compressor 11.
  • the compressor 11 is an electric compressor driven by electric power supplied from a battery, and sucks in the refrigerant of the refrigerating cycle device 10, compresses it, and discharges it.
  • the electric motor of the compressor 11 is controlled by the control device 60 shown in FIG.
  • the compressor 11 may be a variable displacement compressor driven by a belt.
  • the condenser 12 is a high-pressure side heat exchanger that dissipates heat and condenses the high-pressure side refrigerant discharged from the compressor 11.
  • the condenser 12 condenses the high-pressure side refrigerant by exchanging heat between the high-pressure side refrigerant discharged from the compressor 11 and the outside air.
  • the condenser 12 may condense the high-pressure side refrigerant by exchanging heat between the high-pressure side refrigerant discharged from the compressor 11 and the cooling water.
  • the receiver 13 is a gas-liquid separation unit that separates the gas-liquid of the high-pressure refrigerant flowing out from the condenser 12, causes the separated liquid-phase refrigerant to flow out to the downstream side, and stores the excess refrigerant in the cycle.
  • the expansion valve 14 is a decompression unit that depressurizes and expands the liquid phase refrigerant flowing out of the receiver 13.
  • the expansion valve 14 is an electric expansion valve.
  • the electric expansion valve is an electric variable throttle mechanism having a valve body configured to change the throttle opening degree and an electric actuator for changing the throttle opening degree.
  • the expansion valve 14 is a refrigerant flow switching unit that switches between a state in which the refrigerant flows in the evaporator 15 and a state in which the refrigerant does not flow.
  • the operation of the expansion valve 14 is controlled by a control signal output from the control device 60.
  • the evaporator 15 is an evaporator that evaporates the refrigerant by exchanging heat between the refrigerant flowing out from the expansion valve 14 and the air blown into the vehicle interior. In the evaporator 15, the refrigerant absorbs heat from the air blown into the vehicle interior.
  • the evaporator 15 is an air cooler that cools the air blown into the vehicle interior. The vapor phase refrigerant evaporated in the evaporator 15 is sucked into the compressor 11 and compressed.
  • the evaporator 15 is housed in the air conditioning casing 51 of the indoor air conditioning unit 50.
  • the indoor air conditioning unit 50 is arranged inside an instrument panel (not shown) in the front part of the vehicle interior.
  • the air conditioning casing 51 is an air passage forming member that forms an air passage.
  • the inside / outside air switching box 52 is an inside / outside air switching unit that switches between inside and outside air and introduces the inside air into the air passage in the air conditioning casing 51.
  • the indoor blower 53 sucks in and blows the inside air and the outside air introduced into the air passage in the air conditioning casing 51 through the inside / outside air switching box 52.
  • the operation of the indoor blower 53 is controlled by the control device 60.
  • the heater core 54 is arranged on the downstream side of the air flow of the evaporator 15 in the air passage in the air conditioning casing 51.
  • the heater core 54 is an air heater that heats the air blown into the vehicle interior by exchanging heat between the high-temperature cooling water and the air blown into the vehicle interior.
  • the high-temperature cooling water is heated by a heating heat source such as a traveling engine or an electric heater.
  • the high temperature cooling water may be heated by the condenser 12.
  • An air mix door 55 is arranged between the evaporator 15 and the heater core 54 in the air passage in the air conditioning casing 51.
  • the air mix door 55 adjusts the air volume ratio between the cold air flowing into the heater core 54 and the cold air flowing through the cold air bypass passage 56 among the cold air passing through the evaporator 15.
  • the cold air bypass passage 56 is an air passage through which the cold air that has passed through the evaporator 15 flows through the heater core 54.
  • the rotating shaft of the air mix door 55 is driven by the servomotor 57.
  • the operation of the servomotor for the air mix door is controlled by the control device 60.
  • the air mix door 55 may be a slide door that slides and moves in a direction substantially orthogonal to the air flow.
  • the sliding door may be a plate-shaped door formed of a rigid body. It may be a film door made of a flexible film material.
  • the conditioned air whose temperature is adjusted by the air mix door 55 is blown into the vehicle interior from the air outlet 58 formed in the air conditioning casing 51.
  • the control device 60 shown in FIG. 2 is composed of a well-known microcomputer including a CPU, ROM, RAM, and the like, and peripheral circuits thereof.
  • the control device 60 performs various operations and processes based on the control program stored in the ROM.
  • Various controlled devices are connected to the output side of the control device 60.
  • the control device 60 is a control unit that controls the operation of various controlled devices.
  • the controlled devices controlled by the control device 60 are a compressor 11, an expansion valve 14, an indoor blower 53, a servomotor 57 for an air mix door, and the like.
  • the software and hardware for controlling the electric motor of the compressor 11 in the control device 60 is the refrigerant discharge capacity control unit.
  • the software and hardware for controlling the expansion valve 14 in the control device 60 is a throttle control unit.
  • the software and hardware for controlling the indoor blower 53 is an air blower capacity control unit.
  • the software and hardware for controlling the air mix door servomotor 57 among the control devices 60 are air volume ratio control units.
  • control sensor groups are connected to the input side of the control device 60.
  • Various control sensor groups include an inside air temperature sensor 61, an outside air temperature sensor 62, a solar radiation amount sensor 63, an evaporator temperature sensor 64, an intake refrigerant temperature sensor 65, an intake refrigerant pressure sensor 66, a high temperature cooling water temperature sensor 67, and the like. ..
  • the inside air temperature sensor 61 detects the vehicle interior temperature Tr.
  • the outside air temperature sensor 62 detects the outside air temperature Tam.
  • the solar radiation amount sensor 63 detects the solar radiation amount Ts in the vehicle interior.
  • the evaporator temperature sensor 64 is an evaporator temperature detection unit that detects the refrigerant evaporation temperature (evaporator temperature) Tefien in the evaporator 15.
  • the evaporator temperature sensor 64 specifically detects the temperature of the heat exchange fins of the evaporator 15.
  • the evaporator temperature sensor 64 is arranged in the region of the evaporator 15 where the liquid phase refrigerant is present when the dryout does not occur.
  • the evaporator temperature sensor 64 is arranged at a portion of the evaporator 15 on the upstream side of the refrigerant flow.
  • the suction refrigerant temperature sensor 65 is a suction refrigerant temperature detection unit that detects the suction refrigerant temperature Tsuc of the refrigerant sucked into the compressor 11. In other words, the intake refrigerant temperature sensor 65 detects the temperature of the outlet-side refrigerant of the evaporator 15.
  • the suction refrigerant pressure sensor 66 is a suction refrigerant temperature detection unit that detects the suction refrigerant pressure Psuc of the refrigerant sucked into the compressor 11. In other words, the suction refrigerant pressure sensor 66 detects the pressure of the refrigerant on the outlet side of the evaporator 15.
  • the suction refrigerant temperature sensor 65 and the suction refrigerant pressure sensor 66 are arranged in a region where a refrigerant having a degree of superheat exists when dryout does not occur in the evaporator 15.
  • the suction refrigerant temperature sensor 65 and the suction refrigerant pressure sensor 66 are arranged in the refrigerant pipe between the evaporator 15 and the compressor 11.
  • the evaporator temperature sensor 64 and the suction refrigerant pressure sensor 66 are refrigerant state detection units that detect the state of the refrigerant on the downstream side of the refrigerant inlet of the expansion valve 14 and on the upstream side of the suction port of the compressor 11. More preferably, the evaporator temperature sensor 64 and the suction refrigerant pressure sensor 66 detect the state of the refrigerant on the downstream side of the refrigerant inlet of the evaporator 15 and on the upstream side of the suction port of the compressor 11.
  • the suction refrigerant pressure sensor 66 is a first detection unit that detects the state of the refrigerant on the downstream side of the outlet of the evaporator 15 and on the upstream side of the suction port of the compressor 11.
  • the evaporator temperature sensor 64 is a second detection unit that detects the state of the refrigerant on the downstream side of the inlet of the evaporator 15 and on the upstream side of the outlet of the evaporator 15.
  • the high temperature cooling water temperature sensor 67 detects the temperature TW of the high temperature cooling water flowing into the heater core 54. For example, the high temperature cooling water temperature sensor 67 detects the temperature of the cooling water flowing out of the condenser 12.
  • Various operation switches (not shown) are connected to the input side of the control device 60.
  • Various operation switches are provided on the operation panel 70 and are operated by an occupant.
  • the operation panel 70 is arranged near the instrument panel in the front part of the vehicle interior. Operation signals from various operation switches are input to the control device 60.
  • the auto switch is a switch for setting and canceling the automatic control operation of the vehicle air conditioner 1.
  • the air conditioner switch is a switch for setting whether or not to cool the air in the indoor air conditioning unit 50.
  • the temperature setting switch is a switch for setting the set temperature in the vehicle interior.
  • the rotation speed Nc of the compressor 11, the opening SW of the air mix door 55, and the throttle opening EV of the expansion valve 14 are determined.
  • the rotation speed of the compressor 11 is based on the deviation between the target evaporator temperature TEO and the evaporator temperature Tefin detected by the evaporator temperature sensor 64, and the evaporator temperature Tefin is the target evaporator temperature TEO by the feedback control method. It is decided to approach.
  • the target evaporator temperature TEO is determined based on the target blowout temperature TAO with reference to the control map stored in the control device 60. In the control map of the present embodiment, it is determined that the target evaporator temperature TEO increases as the target blowout temperature TAO increases.
  • the target blowing temperature TAO is the target temperature of the blowing air blown into the vehicle interior.
  • the control device 60 calculates the target blowout temperature TAO based on the following mathematical formula F1.
  • TAO Kset x Tset-Kr x Tr-Kam x Tam-Ks x Ts + C ... (F1)
  • Tset is the vehicle interior set temperature set by the temperature setting switch of the operation panel 70
  • Tr is the inside air temperature detected by the inside air temperature sensor 61
  • Tam is the outside air temperature detected by the outside air temperature sensor 62
  • Ts is. It is the amount of solar radiation detected by the solar radiation amount sensor 63.
  • Kset, Kr, Kam, and Ks are control gains
  • C is a correction constant.
  • the opening SW of the air mix door 55 is determined so that the air-conditioned air temperature adjusted by the air mix door 55 becomes the target blowing temperature TAO. Specifically, the opening degree of the air mix door 55 is determined based on the target outlet temperature TAO, the evaporator temperature Tefien, the temperature TW of the high temperature cooling water flowing into the heater core 54, and the like.
  • the throttle opening EV of the expansion valve 14 is determined by the control process shown in the flowchart of FIG. First, in step S100, the throttle opening EVN (hereinafter referred to as the normal opening) of the expansion valve 14 during normal control determines the target superheat degree SHEO of the evaporator 15 outlet side refrigerant and the superheat degree of the evaporator 15 outlet side refrigerant. Based on the deviation from the SHE, the feedback control method determines that the superheat degree SH approaches the target superheat degree SHEO.
  • the target superheat degree SHEO is a predetermined constant (5 ° C. in this embodiment).
  • the degree of superheat SHE is calculated based on the suction refrigerant pressure Psuc detected by the suction refrigerant pressure sensor 66 and the suction refrigerant temperature Tsuc detected by the suction refrigerant temperature sensor 65.
  • next step S110 it is determined whether or not the temperature difference obtained by subtracting the evaporator outlet saturation temperature Tsat from the evaporator temperature Tefien exceeds the threshold value ⁇ 1.
  • the evaporator outlet saturation temperature Tsat is calculated based on the suction refrigerant pressure Psuc detected by the suction refrigerant pressure sensor 66.
  • the threshold value ⁇ 1 is a positive value appropriately determined by the control device 60.
  • the evaporator temperature sensor 64 detects the temperature of the refrigerant having no degree of superheat, and thus the evaporator temperature Tefin.
  • the temperature difference obtained by subtracting the evaporator outlet saturation temperature Tsat from the above is lower than the threshold value ⁇ 1.
  • the evaporator temperature sensor 64 detects the temperature of the refrigerant having a degree of superheat, so that the evaporator temperature Tefin is used as an evaporator.
  • the temperature difference obtained by subtracting the outlet saturation temperature Tsat exceeds the threshold value ⁇ 1.
  • the threshold value ⁇ 1 is determined to be a larger value as the flow rate of the refrigerant flowing into the evaporator 15 is larger. As shown in FIG. 6, when the flow rate of the refrigerant is large, the pressure loss becomes large, so that a pressure difference occurs between the inlet side and the outlet side of the evaporator 15, and this is to suppress erroneous determination due to the pressure difference.
  • step S110 If it is determined in step S110 that the temperature difference obtained by subtracting the evaporator outlet saturation temperature Tsat from the evaporator temperature Tefien does not exceed the threshold value ⁇ 1, the process proceeds to step S120. If it is determined in step S110 that the temperature difference obtained by subtracting the evaporator outlet saturation temperature Tsat from the evaporator temperature Tefien exceeds the threshold value ⁇ 1, the process proceeds to step S130.
  • step S120 since it is considered that dryout has not occurred in the evaporator 15, the normal opening EVN determined in step S100 is determined as the throttle opening EV of the expansion valve 14, and the process proceeds to step S140.
  • step S130 it is considered that dryout has occurred in the evaporator 15, so that the throttle opening EV of the expansion valve 14 is an opening EVD (hereinafter, dry) larger than the normal opening EVN determined in step S100. It is determined to be out opening degree) and proceeds to step S140.
  • the dryout opening degree EVD is the opening degree (100%) when the expansion valve 14 is fully opened.
  • the dry-out opening degree EVD may be an opening degree larger than the normal opening degree EVN by a predetermined amount.
  • step S140 a control signal or a control voltage is output to the expansion valve 14 so that the throttle opening EV of the expansion valve 14 determined in steps S120 and S130 can be obtained, and the process returns to step S100.
  • the state of the refrigerant circulating in the cycle changes as follows. That is, the high-pressure refrigerant discharged from the compressor 11 flows into the condenser 12 and dissipates heat. As a result, the refrigerant is cooled and condensed in the condenser 12.
  • the refrigerant flowing out of the condenser 12 is gas-liquid separated by the receiver 13.
  • the liquid phase refrigerant separated by the receiver 13 flows into the expansion valve 14, and is depressurized and expanded by the expansion valve 14 until it becomes a low-pressure refrigerant.
  • the low-pressure refrigerant decompressed by the expansion valve 14 flows into the evaporator 15 and absorbs heat from the air blown into the vehicle interior to evaporate. As a result, the air blown into the vehicle interior is cooled.
  • the refrigerating cycle device 10 can make the low-pressure refrigerant absorb heat from the air by the evaporator 15 and blow out the cooled air into the vehicle interior. As a result, it is possible to realize cooling in the vehicle interior.
  • the throttle opening EV of the expansion valve 14 is made larger than the normal opening EVN in step S130, so that the flow rate of the refrigerant flowing into the evaporator 15 can be increased. can. As a result, the dry out can be quickly eliminated.
  • the detection values of the evaporator temperature sensor 64 and the suction refrigerant pressure sensor 66 are feedback-controlled, they can be appropriately used up to a low opening without being affected by the tolerance of the expansion valve 14 itself. Further, the degree of superheat is easily controlled at the outlet of the evaporation unit 15, and a gas-liquid separation mechanism (so-called accumulator) is not required between the outlet of the evaporation unit 15 and the suction port of the compressor 11, so that suction pressure loss is reduced. It can be reduced to improve performance and efficiency, and manufacturing costs can be reduced.
  • accumulator gas-liquid separation mechanism
  • Whether or not dryout has occurred in the evaporator 15 is determined based on the temperature difference obtained by subtracting the evaporator outlet saturation temperature Tsat from the evaporator temperature Tefin, so that it flows into the evaporator 15 as shown in FIG. Whether or not dryout has occurred in the evaporator 15 can be appropriately determined even under the condition that the temperature of the air is low.
  • the behavior of the expansion valve 14 is as shown in FIG. Repeat the increase / decrease. In other words, the opening degree of the expansion valve 14 fluctuates. Therefore, even if the temperature of the air flowing into the evaporator 15 is low, the degree of superheat can be appropriately feedback-controlled.
  • the control device 60 in the normal control of the expansion valve 14, the control device 60 has an opening degree of the expansion valve 14 such that the superheat degree SH of the refrigerant flowing out from the evaporator 15 approaches the target superheat degree SHEO. Control to normal opening.
  • the control device 60 determines whether or not the refrigerant is dried out by the evaporator 15 from the refrigerant temperature Tefin detected by the evaporator temperature sensor 64 and the refrigerant pressure Psuc detected by the suction refrigerant pressure sensor 66. When the control device 60 determines that the refrigerant is dry out by the evaporator 15, the opening degree of the expansion valve 14 is made larger than the normal opening degree.
  • the flow rate of the refrigerant flowing into the evaporator 15 can be increased, so that the dry out of the refrigerant in the evaporator 15 can be suppressed.
  • the suction refrigerant pressure sensor 66 is provided as a first detection unit for detecting the state of the refrigerant on the downstream side of the outlet of the evaporator 15 and on the upstream side of the suction port of the compressor 11, and the inlet of the evaporator 15 is provided.
  • An evaporator temperature sensor 64 is provided as a second detection unit for detecting the state of the refrigerant on the downstream side of the refrigerant and on the upstream side of the outlet of the evaporator 15. According to this, whether or not the refrigerant is dry out can be appropriately determined by the evaporator 15.
  • the control device 60 calculates the saturation temperature Tsat of the refrigerant based on the pressure Psuc of the refrigerant detected by the suction refrigerant pressure sensor 66, and the temperature Tefin and the saturation temperature Tsat of the refrigerant detected by the evaporator temperature sensor 64. When the difference from the above value exceeds the threshold value ⁇ 1, it is determined by the evaporator 15 that the refrigerant is dry out.
  • control device 60 increases the threshold value ⁇ 1 as the flow rate of the refrigerant flowing into the evaporator 15 increases. According to this, the dryout can be determined more appropriately in consideration of the pressure loss of the refrigerant in the evaporator 15.
  • the expansion valve 14 since the above-mentioned expansion valve control is applied to the refrigeration cycle device 10 provided with the receiver 13 on the downstream side of the condenser 12 and the upstream side of the expansion valve 14, the expansion valve 14 is slightly closed and easy to use. .. As a result, the phenomenon that the liquid phase refrigerant is sucked into the compressor 11 (so-called liquid back) can be suppressed.
  • the control device 60 expands the expansion valve 14 so as to return it to the normal opening after making the opening of the expansion valve 14 larger than the normal opening. Control the valve 14. As a result, after the dryout is eliminated, the expansion valve 14 can be normally controlled to appropriately control the refrigeration cycle device 10.
  • control device 60 causes the superheat degree SH of the evaporator 15 outlet side refrigerant to approach the target superheat degree SHEO based on the deviation between the target superheat degree SHEO and the superheat degree SHE of the evaporator 15 outlet side refrigerant. To decide. As a result, the degree of superheat SHE can be appropriately controlled during normal control.
  • the temperature difference obtained by subtracting the evaporator outlet saturation temperature Tsat from the evaporator temperature Tefin exceeds the threshold value ⁇ 1.
  • the dryout opening degree EVD is determined as the throttle opening degree EV of the expansion valve 14.
  • the throttle opening EV of the expansion valve 14 is determined by the control process shown in the flowchart of FIG. First, in step S200, similarly to step S100 of the first embodiment, the normal opening EVN of the expansion valve 14 is the target superheat degree SHEO of the evaporator 15 outlet side refrigerant and the superheat degree SH of the evaporator 15 outlet side refrigerant. Based on the deviation of, the feedback control method determines that the superheat degree SH approaches the target superheat degree SHEO.
  • the target superheat degree SHEO is a predetermined constant (5 ° C. in this embodiment).
  • the refrigerant flow rate Gr is calculated based on the suction refrigerant pressure Psuc detected by the suction refrigerant pressure sensor 66, the rotation speed of the compressor 11, and the like.
  • the refrigerant flow rate Gr may be detected by the refrigerant flow rate sensor.
  • the threshold value ⁇ 1 is stored in the control device 60 in advance.
  • step S210 it is determined whether or not the area is shaded in FIG. 10 (hereinafter referred to as a dryout opening degree area).
  • the dryout opening degree region is a part of the region where the dryout occurs (the region above the solid line in FIG. 10).
  • step S210 When it is determined in step S210 that the temperature difference obtained by subtracting the evaporator outlet saturation temperature Tsat from the evaporator temperature Tefin does not exceed the threshold value ⁇ 1 or the refrigerant flow rate does not fall below the threshold value ⁇ 1 (that is, the dryout of FIG. 10). If it is determined that the opening area is not reached), the process proceeds to step S220. When it is determined in step S210 that the temperature difference obtained by subtracting the evaporator outlet saturation temperature Tsat from the evaporator temperature Tefin is above the threshold value ⁇ 1 and the refrigerant flow rate Gr is below the threshold value ⁇ 1 (that is, the dry in FIG. 10). If it is determined to be in the out opening degree region), the process proceeds to step S230.
  • step S220 similarly to step S120 of the first embodiment, the normal opening EVN determined in step S200 is determined as the throttle opening EV of the expansion valve 14, and the process proceeds to step S240.
  • the threshold value ⁇ 1 the amount of heat exchange in the evaporator 15 is small in the first place, so that even if the evaporator 15 causes a dryout, the performance deterioration due to the dryout is considered to be small.
  • the refrigerant flow rate does not fall below the threshold value ⁇ 1, even if a dryout occurs in the evaporator 15, even if the refrigerant flow rate decreases, the performance deterioration does not become a major problem.
  • step S230 it is considered that dryout has occurred in the evaporator 15, so that the normal opening determined in step S200 is set as the throttle opening EV of the expansion valve 14 as in step S130 of the first embodiment. It is determined that the dryout opening degree EVD is larger than the degree EVN, and the process proceeds to step S240.
  • the dryout opening degree EVD is the opening degree (100%) when the expansion valve 14 is fully opened.
  • the dry-out opening degree EVD may be an opening degree larger than the normal opening degree EVN by a predetermined amount.
  • step S240 similarly to step S240 of the first embodiment, a control signal or a control voltage is sent to the expansion valve 14 so that the throttle opening EV of the expansion valve 14 determined in steps S220 and S230 can be obtained. Output and return to step S200.
  • the throttle opening EV of the expansion valve 14 is made larger than the normal opening EVN in step S230, so that the evaporator.
  • the flow rate of the refrigerant flowing into 15 can be increased. As a result, the dry out can be quickly eliminated.
  • the region where the throttle opening EV of the expansion valve 14 is determined to be the dryout opening EVD is limited to the low flow rate region of the refrigerant, so that control can be simplified and the design man-hours can be reduced. can.
  • a fluorocarbon-based refrigerant is used as the refrigerant, but the type of the refrigerant is not limited to this, and a natural refrigerant such as carbon dioxide, a hydrocarbon-based refrigerant, or the like may be used. good.
  • the refrigeration cycle apparatus 10 of the above embodiment constitutes a subcritical refrigeration cycle in which the high pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant, but the supercritical refrigeration cycle in which the high pressure side refrigerant pressure exceeds the critical pressure of the refrigerant. May be configured.
  • the evaporator 15 of the above embodiment exchanges heat between the refrigerant and air (in other words, gas), but is not limited to this, and exchanges heat between the refrigerant and cooling water (in other words, liquid). May be good.
  • An object to be cooled such as a battery may be in contact with the evaporator 15 so as to be thermally conductive, and the object to be cooled may be cooled by the refrigerant flowing through the evaporator 15.
  • the refrigerating cycle device 10 of the above embodiment is applied to an air conditioner for vehicles, but the application target of the refrigerating cycle device 10 is not limited to this, and a battery cooling device, a stationary air conditioner, and a refrigerating / refrigerating device are applied. It may be applied to a device or the like.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

La présente invention comprend : un compresseur (11) pour aspirer, comprimer et décharger un fluide frigorigène; une unité de rayonnement (12) pour dissiper la chaleur provenant du fluide frigorigène; une unité de décompression (14) apte à décompresser le fluide frigorigène et à ajuster un degré d'ouverture de trajet d'écoulement de façon à ajuster le débit du fluide frigorigène; une unité d'évaporation (15) pour permettre au fluide frigorigène décompressé par l'unité de décompression d'absorber la chaleur provenant de l'air; des unités de détection d'état de fluide frigorigène (64, 66) pour détecter l'état du fluide frigorigène en aval d'une entrée de fluide frigorigène de l'unité d'évaporation et en amont d'un orifice d'aspiration du compresseur; et une unité de commande (60) pour commander le degré d'ouverture de l'unité de décompression jusqu'à un degré d'ouverture normal (EVN) qui est un degré d'ouverture où le degré de surchauffe (SHE) du fluide frigorigène s'écoulant hors d'un évaporateur s'approche d'un degré de surchauffe cible (SHEO), l'unité de commande (60) déterminant si l'assèchement du fluide frigorigène s'est produit dans l'unité d'évaporation sur la base de l'état du fluide frigorigène détecté par les unités de détection d'état de fluide frigorigène et, s'il est déterminé que l'assèchement du fluide frigorigène s'est produit dans l'unité d'évaporation, amène le degré d'ouverture de l'unité de décompression à être supérieur au degré d'ouverture normal.
PCT/JP2021/025952 2020-08-21 2021-07-09 Dispositif à cycle de réfrigération WO2022038922A1 (fr)

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JP2020140048 2020-08-21
JP2020-140048 2020-08-21
JP2021-087579 2021-05-25
JP2021087579A JP2022035977A (ja) 2020-08-21 2021-05-25 冷凍サイクル装置

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011075120A (ja) * 2009-09-29 2011-04-14 Toshiba Carrier Corp 空気調和機
JP2015090227A (ja) * 2013-11-05 2015-05-11 ダイキン工業株式会社 冷凍装置及び冷凍装置の制御方法
JP2018151117A (ja) * 2017-03-13 2018-09-27 トヨタ自動車株式会社 電池冷却システム

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011075120A (ja) * 2009-09-29 2011-04-14 Toshiba Carrier Corp 空気調和機
JP2015090227A (ja) * 2013-11-05 2015-05-11 ダイキン工業株式会社 冷凍装置及び冷凍装置の制御方法
JP2018151117A (ja) * 2017-03-13 2018-09-27 トヨタ自動車株式会社 電池冷却システム

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