WO2023140249A1 - Dispositif à cycle frigorifique - Google Patents

Dispositif à cycle frigorifique Download PDF

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Publication number
WO2023140249A1
WO2023140249A1 PCT/JP2023/001177 JP2023001177W WO2023140249A1 WO 2023140249 A1 WO2023140249 A1 WO 2023140249A1 JP 2023001177 W JP2023001177 W JP 2023001177W WO 2023140249 A1 WO2023140249 A1 WO 2023140249A1
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Prior art keywords
temperature
refrigerant
heat exchanger
variable throttle
compressor
Prior art date
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PCT/JP2023/001177
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English (en)
Japanese (ja)
Inventor
達博 鈴木
康太 萩原
良寛 後藤
幸男 上村
拓郎 古越
Original Assignee
株式会社デンソー
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Publication of WO2023140249A1 publication Critical patent/WO2023140249A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/04—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for reversible pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
    • F25B41/335—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant via diaphragms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • 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

Definitions

  • the present disclosure relates to a refrigeration cycle device.
  • the refrigeration cycle apparatus described in Patent Document 1 includes a four-way valve provided midway along a pipe connecting a compressor and an indoor heat exchanger and midway along a pipe connecting a compressor and an outdoor heat exchanger.
  • this refrigeration cycle device can perform cooling operation and heating operation by switching the flow of the refrigerant with the four-way valve.
  • cooling operation the refrigerant discharged from the compressor flows through the four-way valve, the outdoor heat exchanger, the first throttle valve, the receiver, the second throttle valve, the indoor heat exchanger, the four-way valve, and the compressor in that order.
  • heating operation the refrigerant discharged from the compressor flows through the 4-way valve, the indoor heat exchanger, the second throttle valve, the receiver, the first throttle valve, the outdoor heat exchanger, the 4-way valve, and the compressor in that order.
  • the refrigeration cycle apparatus of Patent Document 1 has two throttle valves and a receiver installed between the outdoor heat exchanger and the indoor heat exchanger, and on the other hand, has a configuration in which no accumulator is installed on the suction port side of the compressor.
  • Patent Document 1 describes that a temperature sensor is provided in the middle of each heat exchanger and that a temperature sensor is provided only on the discharge side of the compressor.
  • Patent Document 1 when a temperature sensor is provided in the middle of each heat exchanger as in Patent Document 1, or when a temperature sensor is provided only on the discharge side of the compressor, it is difficult to operate the throttle valve so as to improve the cooling capacity, heating capacity, and coefficient of performance (hereinafter referred to as "COP"). That is, Patent Document 1 does not describe a throttle valve operation method for improving the cooling capacity, the heating capacity, and the COP during the cooling operation and the heating operation, and the configuration necessary for executing the operation method. Note that COP is an abbreviation for Coefficient Of Performance.
  • An object of the present disclosure is to provide a refrigeration cycle device that is capable of simplifying the configuration, reducing the size, and improving the cooling capacity, heating capacity, and COP.
  • a refrigeration cycle device includes a compressor, an outdoor heat exchanger, an indoor heat exchanger, a receiver, a first variable throttle, a second variable throttle, a first temperature/pressure sensor, and a second temperature/pressure sensor.
  • the compressor has a first opening and a second opening for sucking and discharging refrigerant, and is capable of performing a heating operation in which the refrigerant sucked through the first opening is compressed and discharged through the second opening, and a cooling operation in which the refrigerant sucked through the second opening is compressed and discharged through the first opening.
  • the outdoor heat exchanger is provided on the side of the first opening of the compressor, and performs heat exchange between the air discharged to the outside of the room and the refrigerant.
  • the indoor heat exchanger is provided on the second opening side of the compressor, and performs heat exchange between the air blown into the room and the refrigerant.
  • a receiver is a reservoir provided between the outdoor heat exchanger and the indoor heat exchanger.
  • the first variable throttle is provided between the outdoor heat exchanger and the receiver and adjusts the flow rate of refrigerant.
  • a second variable throttle is provided between the indoor heat exchanger and the receiver to adjust the flow rate of the refrigerant.
  • a first temperature-pressure sensor is provided between the first opening of the compressor and the outdoor heat exchanger and detects at least one of the temperature and pressure of the refrigerant.
  • a second temperature-pressure sensor is provided between the second opening of the compressor and the indoor heat exchanger and detects at least one of the temperature and pressure of the refrigerant.
  • the refrigeration cycle apparatus is configured such that, during heating operation, the valve opening of the first variable throttle is controlled according to the temperature and pressure detected by the first temperature and pressure sensor so that the refrigerant sucked into the first opening of the compressor becomes a gas refrigerant having a predetermined degree of superheat, and the valve opening of the second variable throttle is controlled according to the temperature and pressure detected by the second temperature and pressure sensor so that the refrigerant flowing out of the indoor heat exchanger becomes a liquid refrigerant having a predetermined degree of subcooling.
  • the refrigeration cycle apparatus is configured such that, during cooling operation, the valve opening degree of the second variable throttle is controlled according to the temperature and pressure detected by the second temperature and pressure sensor so that the refrigerant sucked into the second opening of the compressor becomes a gas refrigerant having a predetermined degree of superheat, and the valve opening degree of the first variable throttle is controlled according to the temperature and pressure detected by the first temperature and pressure sensor so that the refrigerant flowing out from the outdoor heat exchanger becomes a liquid refrigerant having a predetermined degree of subcooling.
  • the refrigerating cycle apparatus uses two temperature/pressure sensors to control the opening of two variable throttles in both heating operation and cooling operation. Specifically, while adjusting the degree of superheat of the refrigerant sucked into the compressor and the degree of superheat of the refrigerant discharged from the compressor, it is possible to adjust the degree of subcooling of the refrigerant flowing out of the heat exchanger that functions as a condenser among the indoor heat exchanger and the outdoor heat exchanger. Therefore, this refrigeration cycle apparatus can simplify the configuration by reducing the number of parts, such as one receiver, two temperature pressure sensors, and two variable throttles, and can reduce the size.
  • this refrigeration cycle apparatus uses a so-called dual-rotation compressor capable of performing both heating operation and cooling operation, so compared to a configuration in which a compressor and a four-way valve are combined as in Patent Document 1, the number of parts can be reduced and the size can be reduced.
  • the predetermined degree of superheating and the predetermined degree of supercooling are appropriately set according to various requirements for the refrigeration cycle device, such as a scene in which priority is given to cooling capacity or heating capacity, a scene in which COP is given priority, or a scene in which both cooling capacity or heating capacity and COP are given priority.
  • a refrigeration cycle device includes a compressor, an outdoor heat exchanger, an indoor heat exchanger, a receiver, a first variable throttle, a second variable throttle, a flow path switching valve, a first temperature/pressure sensor, a second temperature/pressure sensor, and an electronic control device.
  • the compressor sucks refrigerant through the first opening, compresses it, and discharges it through the second opening.
  • the outdoor heat exchanger exchanges heat between the air discharged outdoors and the refrigerant.
  • the indoor heat exchanger exchanges heat between the air blown indoors and the refrigerant.
  • a receiver is a reservoir provided between the outdoor heat exchanger and the indoor heat exchanger.
  • the first variable throttle is provided between the outdoor heat exchanger and the receiver and adjusts the flow rate of refrigerant.
  • a second variable throttle is provided between the indoor heat exchanger and the receiver to adjust the flow rate of the refrigerant.
  • the flow path switching valve is provided in the middle of the flow path that connects the compressor and the indoor heat exchanger and in the middle of the flow path that connects the compressor and the outdoor heat exchanger, and switches between the heating operation and the cooling operation. In the heating operation operation, the refrigerant discharged from the second opening of the compressor flows through the flow path switching valve, the indoor heat exchanger, the second variable throttle, the receiver, the first variable throttle, the outdoor heat exchanger, and the flow path switching valve in this order, and is sucked into the first opening of the compressor.
  • the refrigerant discharged from the second opening of the compressor flows through the flow switching valve, the outdoor heat exchanger, the first variable throttle, the receiver, the second variable throttle, the indoor heat exchanger, and the flow switching valve in that order, and is drawn into the first opening of the compressor.
  • the first temperature-pressure sensor is provided between the first opening of the compressor and the flow path switching valve or between the flow path switching valve and the outdoor heat exchanger, and detects at least one of the temperature and pressure of the refrigerant.
  • the second temperature-pressure sensor is provided between the second opening of the compressor and the flow path switching valve or between the flow path switching valve and the indoor heat exchanger, and detects at least one of the temperature and pressure of the refrigerant.
  • the electronic control device controls the valve opening of the first variable throttle according to the temperature and pressure detected by the sensor downstream of the outdoor heat exchanger among the first and second temperature and pressure sensors so that the refrigerant drawn into the first opening of the compressor becomes gas refrigerant with a predetermined degree of superheat, and the temperature and pressure detected by the first temperature and pressure sensor and the second temperature and pressure sensor downstream of the indoor heat exchanger so that the refrigerant flowing out of the indoor heat exchanger becomes liquid refrigerant with a predetermined degree of supercooling.
  • the valve opening degree of the second variable throttle is controlled according to the pressure.
  • the electronic control unit controls the valve opening degree of the second variable throttle according to the temperature and pressure detected by the sensor downstream of the indoor heat exchanger among the first temperature-pressure sensor and the second temperature-pressure sensor so that the refrigerant sucked into the first opening of the compressor becomes a gas refrigerant with a predetermined degree of superheat during the cooling operation, and the sensor upstream of the outdoor heat exchanger among the first temperature-pressure sensor and the second temperature-pressure sensor so that the refrigerant flowing out of the outdoor heat exchanger becomes liquid refrigerant with a predetermined degree of supercooling.
  • the valve opening degree of the first variable throttle is controlled according to the detected temperature and pressure.
  • the refrigeration cycle device can achieve the same effects as the refrigeration cycle device according to one aspect of the present disclosure, except that the channel switching valve is provided.
  • FIG. 1 is a circuit diagram of a refrigeration cycle apparatus according to a first embodiment
  • FIG. FIG. 4 is a Mollier diagram showing the behavior of refrigerant during heating operation.
  • FIG. 3 is a Mollier diagram showing the behavior of a refrigerant during cooling operation.
  • 4 is a flow chart of control processing executed by an electronic control device included in the refrigeration cycle apparatus;
  • FIG. 4 is a Mollier diagram showing the behavior of the refrigerant under control of the lower stage throttle and the upper stage throttle.
  • 1 is a plan view of a refrigeration cycle apparatus according to a first embodiment
  • FIG. FIG. 7 is a front view of the refrigeration cycle apparatus viewed from the VII direction of FIG. 6
  • FIG. 8 is a side view of the refrigeration cycle apparatus viewed from the VIII direction of FIGS.
  • FIG. 6 and 7 1 is a schematic configuration diagram of a refrigeration cycle apparatus according to a first embodiment, showing the flow of refrigerant during heating operation;
  • FIG. 1 is a schematic configuration diagram of a refrigeration cycle apparatus according to a first embodiment, showing the flow of refrigerant during cooling operation;
  • FIG. It is a schematic block diagram of the refrigerating-cycle apparatus which concerns on 2nd Embodiment. It is sectional drawing of the 1st mechanical expansion valve and the 1st temperature-sensing part with which the refrigerating-cycle apparatus which concerns on 2nd Embodiment is provided. It is sectional drawing of the 2nd mechanical expansion valve and the 2nd temperature-sensing part with which the refrigerating-cycle apparatus which concerns on 2nd Embodiment is provided.
  • FIG. 12 is a diagram showing the flow of refrigerant during cooling operation in the circuit diagram of the refrigeration cycle apparatus according to the sixth embodiment.
  • FIG. 12 is a diagram showing the flow of refrigerant during heating operation in the circuit diagram of the refrigeration cycle apparatus according to the sixth embodiment.
  • the refrigeration cycle apparatus of the present embodiment is installed in, for example, a compact car or compact mobility vehicle (hereinafter referred to as "vehicle or the like"), and is applied to a heat pump system that performs air conditioning including cooling and heating in the vehicle interior.
  • vehicle or the like a compact car or compact mobility vehicle
  • the refrigeration cycle device includes a compressor 10, an outdoor heat exchanger 13, an indoor heat exchanger 23, a receiver 30, a first variable throttle 14, a second variable throttle 24, a first temperature/pressure sensor 12, a second temperature/pressure sensor 22, an electronic control unit 40, and the like.
  • the electronic control unit 40 is hereinafter referred to as "ECU”.
  • ECU is an abbreviation for Electronic Control Unit.
  • the compressor 10, the outdoor heat exchanger 13, the indoor heat exchanger 23, the receiver 30, the first variable throttle 14, the second variable throttle 24, etc. are connected by refrigerant passages or pipes (hereinafter referred to as "piping etc.") to form a vapor compression refrigeration cycle.
  • refrigerant passages or pipes hereinafter referred to as "piping etc."
  • refrigerant that circulates in the refrigeration cycle device for example, an HFC-based refrigerant (eg, R134a) or an HFO-based refrigerant (eg, R1234yf) is used.
  • a natural refrigerant for example, carbon dioxide
  • the refrigerant for example, carbon dioxide
  • the compressor 10 has a first opening 11 and a second opening 21 for sucking and discharging refrigerant.
  • the compressor 10 can perform an operation of compressing the refrigerant sucked from the first opening 11 and discharging it from the second opening 21 (hereinafter referred to as "heating operation") and an operation of compressing the refrigerant sucked from the second opening 21 and discharging it from the first opening 11 (hereinafter referred to as "cooling operation").
  • the compressor 10 is a so-called bi-rotating compressor.
  • the direction of refrigerant flow when the compressor 10 performs the heating operation is indicated by a dashed arrow
  • the direction of refrigerant flow when the compressor 10 performs the cooling operation is indicated by a solid arrow. That is, in FIG. 1, the refrigerant circulates counterclockwise during heating operation, and circulates clockwise during cooling operation.
  • the compressor 10 As a specific configuration of the compressor 10, for example, it is possible to use a rolling piston type electric compressor as described in Japanese Patent Application No. 2021-86462 filed by the same applicant as the present disclosure. Note that the type of the compressor 10 is not limited thereto, and any type, such as a rotary vane electric compressor, may be used as long as the direction of sucking and discharging the refrigerant can be switched between the first opening 11 and the second opening 21 .
  • the outdoor heat exchanger 13 is connected to the first opening 11 side of the compressor 10 via piping or the like.
  • the outdoor heat exchanger 13 is a heat exchanger that exchanges heat between the refrigerant flowing in the tubes of the outdoor heat exchanger 13 and the air discharged to the outside (hereinafter referred to as "outdoor discharged air").
  • the outdoor exhaust air is supplied from outside the vehicle to the outdoor heat exchanger 13 by driving the outdoor fan 15 and is discharged outside the vehicle after passing through the outdoor heat exchanger 13 .
  • the low-pressure refrigerant flowing through the tubes of the outdoor heat exchanger 13 absorbs heat from the outdoor exhaust air passing through the outdoor heat exchanger 13 and evaporates.
  • the outdoor heat exchanger 13 functions as an evaporator that evaporates the low-pressure refrigerant by exchanging heat with the air discharged to the outside.
  • the high-pressure refrigerant flowing through the tubes of the outdoor heat exchanger 13 releases heat to the outdoor exhaust air passing through the outdoor heat exchanger 13 and condenses. Therefore, during the cooling operation, the outdoor heat exchanger 13 functions as a condenser that condenses the high-pressure refrigerant by exchanging heat with the outdoor exhaust air.
  • the indoor heat exchanger 23 is connected to the second opening 21 side of the compressor 10 via piping or the like.
  • the indoor heat exchanger 23 is a heat exchanger that exchanges heat between the refrigerant flowing through the tubes of the indoor heat exchanger 23 and the air blown into the room (hereinafter referred to as "indoor blown air").
  • the indoor blowing air is supplied to the indoor heat exchanger 23 from inside or outside the vehicle by the driving of the indoor fan 25, and is blown out into the vehicle after passing through the indoor heat exchanger 23.
  • the high-pressure refrigerant flowing through the tubes of the indoor heat exchanger 23 radiates heat to the indoor blown air passing through the indoor heat exchanger 23 and condenses.
  • the indoor heat exchanger 23 functions as a condenser that exchanges heat between the high-pressure refrigerant and the air blown into the room to condense the refrigerant.
  • the low-pressure refrigerant flowing through the tubes of the indoor heat exchanger 23 absorbs heat from the indoor blown air passing through the indoor heat exchanger 23 and evaporates. Therefore, during the cooling operation, the indoor heat exchanger 23 functions as an evaporator that evaporates the low-pressure refrigerant by exchanging heat with the air blown into the room.
  • a ventilation passage in which the indoor heat exchanger 23 is provided is provided with a blowout temperature sensor 26 that detects the blowout temperature of the air blown into the vehicle interior after passing through the indoor heat exchanger 23 .
  • the blowout temperature of the air detected by the blowout temperature sensor 26 is transmitted to the ECU.
  • the receiver 30 is a liquid storage unit that stores surplus refrigerant in order to cope with load fluctuations in the refrigeration cycle.
  • the receiver 30 separates and stores gas refrigerant and liquid refrigerant.
  • the receiver 30 is provided between the outdoor heat exchanger 13 and the indoor heat exchanger 23, and is connected to the outdoor heat exchanger 13 and the indoor heat exchanger 23 via pipes or the like.
  • the pipes and the like are connected to a lower part of the receiver 30 in the gravitational direction where the liquid refrigerant is stored.
  • the first variable throttle 14 is an electronic expansion valve provided between the outdoor heat exchanger 13 and the receiver 30, and is configured such that the degree of valve opening is controlled by the control of the ECU.
  • the first variable throttle 14 decompresses and expands the refrigerant supplied from the receiver 30 to the outdoor heat exchanger 13, supplies the refrigerant to the outdoor heat exchanger 13 as a low-temperature, low-pressure gas-liquid two-phase state, and adjusts the flow rate of the refrigerant.
  • the first variable throttle 14 adjusts the flow rate of high-pressure refrigerant flowing from the outdoor heat exchanger 13 into the receiver 30 .
  • the second variable throttle 24 is an electronic expansion valve provided between the indoor heat exchanger 23 and the receiver 30, and is configured such that the degree of opening of the valve is controlled by the control of the ECU. During heating operation, the second variable throttle 24 adjusts the flow rate of high-pressure refrigerant flowing from the indoor heat exchanger 23 to the receiver 30 . On the other hand, during cooling operation, the second variable throttle 24 decompresses and expands the refrigerant supplied from the receiver 30 to the indoor heat exchanger 23, and supplies it to the indoor heat exchanger 23 as a low-temperature, low-pressure gas-liquid two-phase state, and adjusts the flow rate of the refrigerant.
  • the first temperature-pressure sensor 12 is a sensor that is provided between the first opening 11 of the compressor 10 and the outdoor heat exchanger 13 and detects at least one of the temperature and pressure of the refrigerant flowing therethrough. The temperature and pressure of the refrigerant detected by the first temperature/pressure sensor 12 are transmitted to the ECU.
  • the second temperature/pressure sensor 22 is provided between the second opening 21 of the compressor 10 and the indoor heat exchanger 23 and detects at least one of the temperature and pressure of the refrigerant flowing therethrough. The temperature and pressure of the refrigerant detected by the second temperature/pressure sensor 22 are also transmitted to the ECU. Note that the refrigeration cycle apparatus of the first embodiment includes only the first temperature/pressure sensor 12 and the second temperature/pressure sensor 22 as functional units that detect at least one of the temperature and pressure of the refrigerant.
  • the ECU has a processor that performs control processing and arithmetic processing, a microcomputer with a memory that stores programs and data, and its peripheral circuits.
  • a processor is composed of a CPU and an MPU.
  • the memory includes various non-transitional physical storage media such as ROM, RAM, and non-volatile rewritable memory.
  • the processor executes a program stored in the memory to sense and control the valve opening degrees of the first variable throttle 14 and the second variable throttle 24, the rotation speed and refrigerant discharge direction of the compressor 10, the rotation speed of the outdoor fan 15 and the indoor fan 25, the amount of electricity, and the like.
  • the ECU controls the valve opening of the first variable throttle 14 based on the temperature and pressure of the refrigerant detected by the first temperature/pressure sensor 12, and controls the valve opening of the second variable throttle 24 based on the temperature and pressure of the refrigerant detected by the second temperature/pressure sensor 22.
  • a method of controlling the first variable aperture 14 and the second variable aperture 24 by this ECU will be described later.
  • information from sensors such as an intake air temperature sensor, an intake humidity sensor, a vehicle interior temperature sensor, an outside air temperature sensor, and a solar radiation sensor is input to the ECU as needed. Further, the ECU is connected to a servomotor for controlling a door that switches the flow of air flowing through the indoor heat exchanger 23 as required.
  • FIG. 2 is a Mollier diagram showing an example of the behavior of the refrigerant when the refrigeration cycle device performs heating operation.
  • the positions of A1 to A4 vary depending on various conditions such as the rotation speed of the compressor 10, the opening degrees of the first variable throttle 14 and the second variable throttle 24, the rotation speeds of the outdoor fan 15 and the indoor fan 25, the outside air temperature, and the vehicle interior temperature.
  • Line SL indicates the saturated liquid line
  • point CP indicates the critical point
  • line SV indicates the saturated vapor line.
  • A1 indicates the state of the refrigerant that flows out from the outdoor heat exchanger 13 that functions as an evaporator during heating operation and that is sucked into the first opening 11 of the compressor 10 .
  • A2 indicates the state of the refrigerant discharged from the second opening 21 of the compressor 10 and flowing into the indoor heat exchanger 23 functioning as a condenser during heating operation.
  • A3 indicates the state of the refrigerant flowing out of the indoor heat exchanger 23 functioning as its condenser and flowing into the second variable throttle 24 .
  • A4 indicates the state of the refrigerant that flows out from the first variable throttle 14 and flows into the outdoor heat exchanger 13 that functions as an evaporator.
  • the first temperature/pressure sensor 12 detects the temperature and pressure of the refrigerant sucked into the compressor 10, indicated by A1.
  • the second temperature/pressure sensor 22 detects the temperature and pressure of the refrigerant discharged from the compressor 10, indicated by A2.
  • the first variable throttle 14 is the downstream side throttle with respect to the receiver 30
  • the second variable throttle 24 is the upstream side throttle with respect to the receiver 30 .
  • the diaphragm on the downstream side with respect to the receiver 30 will be referred to as the "lower stage diaphragm”
  • the diaphragm on the upstream side with respect to the receiver 30 will be referred to as the "upper stage diaphragm”.
  • FIG. 3 is a Mollier diagram showing an example of the behavior of the refrigerant when the refrigeration cycle device performs cooling operation.
  • the positions of B1 to B4 also change depending on various conditions such as the rotation speed of the compressor 10, the opening degrees of the first variable throttle 14 and the second variable throttle 24, the rotation speeds of the outdoor fan 15 and the indoor fan 25, the outside air temperature, and the vehicle interior temperature.
  • B1 indicates the state of the refrigerant that flows out from the indoor heat exchanger 23 that functions as an evaporator during cooling operation and is sucked into the second opening 21 of the compressor 10 .
  • B2 indicates the state of the refrigerant discharged from the first opening 11 of the compressor 10 and flowing into the outdoor heat exchanger 13 functioning as a condenser during cooling operation.
  • B3 indicates the state of the refrigerant that flows out from the outdoor heat exchanger 13 functioning as its condenser and flows into the first variable throttle 14 .
  • B4 indicates the state of the refrigerant that flows out from the second variable throttle 24 and flows into the indoor heat exchanger 23 that functions as an evaporator.
  • the second temperature/pressure sensor 22 detects the temperature and pressure of the refrigerant sucked into the compressor 10, indicated by B1
  • the first temperature/pressure sensor 12 detects the temperature and pressure of the refrigerant discharged from the compressor 10, indicated by B2.
  • the second variable throttle 24 becomes the lower stage throttle
  • the first variable throttle 14 becomes the upper stage throttle.
  • first temperature/pressure sensor 12, outdoor heat exchanger 13, first variable throttle 14 will be referred to as the first set
  • second temperature/pressure sensor 22, indoor heat exchanger 23, second variable throttle 24 will be referred to as the second set.
  • first set and the second set switch between the high pressure side and the low pressure side with the receiver 30 and the compressor 10 as the axes in the refrigerant behavior on the Mollier diagram. Therefore, this refrigeration cycle apparatus can be controlled by the same logic when switching between the heating operation and the cooling operation, so that the control capacity of the ECU can be reduced, and the control circuit can be miniaturized.
  • the refrigeration cycle apparatus of this embodiment includes only the first temperature/pressure sensor 12 and the second temperature/pressure sensor 22 as functional units that detect at least one of the temperature and pressure of the refrigerant.
  • This refrigeration cycle apparatus can control the opening degrees of the two variable throttles 14, 24 using a small number of two temperature pressure sensors 12, 22 in both the heating operation and the cooling operation.
  • the ability to control with a minimum sensor configuration is based on the following idea, and is effective in reducing the size of the system.
  • the direction of refrigerant flow is reversed, so even if only the temperature and pressure of the refrigerant sucked into the compressor 10 are to be detected, temperature and pressure sensors are required on the suction and discharge sides of the compressor 10, respectively.
  • the temperature-pressure sensor that detects the temperature and pressure of the refrigerant sucked into the compressor 10 during cooling operation detects the temperature and pressure of the refrigerant that is discharged from the compressor 10 (hereinafter referred to as "discharged refrigerant") during heating operation.
  • the ECU controls the first variable throttle 14 and the second variable throttle 24 using the two temperature/pressure sensors 12 and 22 .
  • This control process starts when the refrigeration cycle device starts operating.
  • the ECU determines the operation mode targeted by the refrigeration cycle apparatus according to the user's operation or the output of various sensors mounted on the vehicle (ie, temperature conditions, etc.).
  • the operation modes include a mode for maximizing COP for the purpose of reducing power consumption, a mode for maximizing heating performance or cooling performance, and a mode for securing a heating blowout temperature especially when outside air is low.
  • the heating performance may be referred to as heating capacity
  • the cooling performance may be referred to as cooling capacity.
  • step S20 the ECU sets a target degree of supercooling of the liquid refrigerant at the condenser outlet (hereinafter referred to as "target condenser outlet SC" or " TSC ") according to the operation mode determined in step S10.
  • SC is an abbreviation for subcool or supercooling.
  • the condenser is the indoor heat exchanger 23 during heating operation and the outdoor heat exchanger 13 during cooling operation.
  • step S30 the ECU controls the valve opening of the upper throttle.
  • the upper throttle is the second variable throttle 24 during heating operation, and the first variable throttle 14 during cooling operation.
  • the opening of the upper throttle is fully opened. That is, at the start of control, the upper stage throttle is in a state where it does not function as a throttle, and after the valve opening degree of the lower stage throttle is once set, the valve opening degree of the upper stage throttle is set.
  • the lower throttle is the first variable throttle 14 during heating operation, and the second variable throttle 24 during cooling operation.
  • step S40 to S90 the ECU feedback-controls the valve opening of the lower throttle.
  • step S40 the ECU sets a target degree of superheat of the gas refrigerant sucked into the compressor 10 (hereinafter referred to as “target suction SH” or “T SH ").
  • SH is an abbreviation for superheat.
  • step S50 the ECU controls the valve opening of the lower throttle.
  • the valve opening degree of the lower throttle is set to a preset opening degree.
  • step S60 the ECU acquires the temperature and pressure of the refrigerant sucked into the compressor 10 based on the information transmitted from the first temperature-pressure sensor 12 and the second temperature-pressure sensor 22 located on the suction side of the compressor 10.
  • the sensor arranged on the suction side of the compressor 10 is referred to as the "suction-side sensor".
  • the suction side sensor is the first temperature/pressure sensor 12 during heating operation, and the second temperature/pressure sensor 22 during cooling operation.
  • step S70 the ECU calculates the degree of superheat of the refrigerant sucked into the compressor 10 (hereinafter referred to as "suction SH" or " T1 ”) from the information acquired in step S60.
  • step S80 the ECU determines whether or not the difference between the target suction SH (T SH ) and the suction SH (T 1 ) is within the error range regarding the degree of superheat of the refrigerant sucked into the compressor 10 .
  • the error related to the degree of superheat of the refrigerant sucked into the compressor 10 is referred to as "SH error reference value”. If the absolute value of the difference between the target inhalation SH (T SH ) and the inhalation SH (T 1 ) is greater than or equal to the SH error reference value, the process proceeds to step S90.
  • step S90 the ECU calculates the control amount related to the opening degree of the lower throttle, and returns the process to step S50.
  • step S50 the ECU controls the valve opening of the lower throttle. In this manner, the ECU feedback-controls the valve opening of the lower throttle.
  • step S80 if the absolute value of the difference between the target inhalation SH (T SH ) and the inhalation SH (T 1 ) is smaller than the SH error reference value in step S80, the process proceeds to step S100.
  • step S100 to S150 and S30 the ECU feedback-controls the valve opening of the upper throttle.
  • step S100 the ECU acquires the temperature and pressure of the refrigerant discharged from the compressor 10 based on the information transmitted from the first temperature-pressure sensor 12 and the second temperature-pressure sensor 22 located on the discharge side of the compressor 10.
  • the sensor arranged on the discharge side of the compressor 10 is called the "discharge-side sensor".
  • the discharge side sensor is the second temperature/pressure sensor 22 during heating operation, and the first temperature/pressure sensor 12 during cooling operation.
  • step S110 the ECU calculates the degree of superheat of the refrigerant discharged from the compressor 10 (hereinafter referred to as "discharge SH" or " T3 ”) from the information obtained in step S100.
  • the ECU obtains information on the flow rate of the air supplied to the condenser, the temperature of the intake air, and the flow rate of the refrigerant discharged from the compressor 10.
  • the ECU calculates the amount of air supplied to the condenser from, for example, the number of rotations of the motor that drives the fan that blows air to the condenser (that is, the indoor fan 25 during heating operation and the outdoor fan 15 during cooling operation).
  • the ECU acquires the intake air temperature supplied to the condenser from, for example, vehicle interior temperature information obtained from a vehicle interior temperature sensor (not shown) or outside air temperature information obtained from an outside air temperature sensor (not shown).
  • the ECU calculates the flow rate of the refrigerant discharged from the compressor 10 from the temperature and pressure of the refrigerant obtained from the suction side sensor and the rotation speed of the compressor 10, for example.
  • step S130 the ECU calculates the degree of subcooling of the liquid refrigerant at the condenser outlet (hereinafter referred to as "condenser outlet SC" or " T2 ”) based on the information acquired in steps S110 and S120.
  • step S140 the ECU determines whether the difference between the target condenser outlet SC (T SC ) set in step S20 and the condenser outlet SC (T 2 ) calculated in step S130 is within the error range regarding the degree of supercooling of the refrigerant at the condenser outlet.
  • the error regarding the degree of subcooling of the refrigerant at the outlet of the condenser is referred to as "SC error reference value”. If the absolute value of the difference between the target condenser outlet SC (T SC ) and the condenser outlet SC (T 2 ) is greater than or equal to the SC error reference value, the process proceeds to step S150.
  • step S150 the ECU calculates the control amount related to the opening degree of the upper throttle, and returns the process to step S30.
  • step S30 the ECU controls the valve opening of the upper throttle.
  • steps S40 to S90 the valve opening degree of the lower throttle is controlled again. In this manner, the ECU feedback-controls the valve opening of the upper throttle and the valve opening of the lower throttle.
  • step S140 if it is determined in step S140 that the absolute value of the difference between the target condenser outlet SC (T SC ) and the condenser outlet SC (T 2 ) is smaller than the SC error reference value, the ECU once terminates the process, and starts the above control process again after a predetermined control time has elapsed.
  • the SH amount of the refrigerant sucked into the compressor 10 and the SC amount of the refrigerant at the outlet of the condenser are described as the controlled variables as they are, but correlated variables and physical property values may be used instead.
  • the specific enthalpy may be calculated from the temperature and pressure and used for control.
  • the cooling capacity or heating capacity can be increased and the cycle COP can be maximized.
  • the above control method is based on the following concept. That is, in the refrigeration cycle apparatus, when the lower throttle is considered as the main throttle valve in a predetermined operating state, the valve opening degree of this lower throttle is controlled according to the SH of the refrigerant sucked into the compressor 10 . At this time, if the upper stage throttle is fully open, the refrigerant at the outlet of the condenser becomes a saturated liquid state by the receiver 30 . On the other hand, the SC can be removed by the condenser by narrowing the upper stage throttle from the fully open state (that is, reducing the valve opening degree).
  • the enthalpy of the refrigerant at the outlet of the condenser (that is, the enthalpy of the refrigerant at the inlet of the evaporator) can be lowered, so the performance of the heat pump cycle (that is, cooling capacity or heating capacity) is improved.
  • the upper stage throttle acts in the direction of increasing the SC at the outlet of the condenser, but at the same time, the pressure of the high-pressure refrigerant rises and the compression power of the compressor 10 increases. Therefore, when maximizing the cycle COP, there is an optimum value, and by performing control as a variable throttle, the cooling capacity or heating capacity can be increased and the cycle COP can be maximized.
  • FIG. 5 is a Mollier diagram showing an example of the behavior of the refrigerant according to the control method described above.
  • C1 to C4 show the behavior of the refrigerant when the valve opening of the lower throttle is controlled so that the suction SH of the refrigerant sucked into the compressor 10 (that is, C1 in FIG. 5) becomes the target suction SH with the upper throttle fully open.
  • D1 to D5 show the behavior of the refrigerant when the valve opening degree of the lower throttle is controlled so that the suction SH of the refrigerant sucked into the compressor 10 (that is, D1 in FIG. 5) becomes the target suction SH, and the upper throttle is controlled to be throttled from the fully open state.
  • the condenser By narrowing the upper throttle (that is, reducing the valve opening degree), the condenser can be made to take the SC, so the enthalpy of the refrigerant at the condenser outlet indicated by D3 in FIG. 5 and the enthalpy of the refrigerant at the evaporator inlet indicated by D5 can be lowered. This improves the cooling capacity and heating capacity.
  • D4 indicates the state of the refrigerant in the receiver 30 (that is, saturated liquid).
  • Equation 1 the cooling capacity is represented by Equation 1 below.
  • Qer is the cooling capacity
  • Gr is the refrigerant flow rate
  • ⁇ ie is the amount of change in refrigerant enthalpy in the evaporator.
  • Equation 2 The heating capacity is represented by Equation 2 below.
  • Qhe Gr ⁇ ic (Formula 2)
  • Qhe is the heating capacity
  • Gr is the refrigerant flow rate
  • ⁇ ic is the amount of change in enthalpy of the refrigerant in the condenser.
  • Equation 3 The COP during cooling is expressed by Equation 3 below, and the COP during heating is expressed by Equation 4 below.
  • COP during cooling Qer/L (Formula 3)
  • COP during heating Qhe/L (Formula 4)
  • L is the power of the compressor 10.
  • the cooling capacity and the heating capacity are improved by controlling the opening degree of the upper throttle, increasing the SC of the refrigerant at the condenser outlet, and lowering the enthalpy of the refrigerant at the condenser outlet (that is, the enthalpy of the refrigerant at the evaporator inlet).
  • the COP of the cycle can be improved by controlling the valve opening of the lower stage throttle to suppress an increase in the degree of superheat of the refrigerant sucked into the compressor 10, and controlling the valve opening of the upper stage throttle to suppress the pressure rise of the high-pressure refrigerant discharged from the compressor 10.
  • FIG. 6 to 8 an example of a ventilation passage 80 for flowing air to the outdoor heat exchanger 13 and the indoor heat exchanger 23 is shown by a broken line, and in FIG. 8, the direction of the wind flowing through the ventilation passage 80 is indicated by arrows AF1 and AF2.
  • FIGS. 7 and 8 the direction in which the refrigeration cycle device is mounted on a vehicle or the like is indicated by a double-headed arrow in the direction of gravity. 9 indicate the flow of the refrigerant during heating operation, and the arrows drawn along the pipes etc. in FIG. 10 indicate the flow of refrigerant during cooling operation.
  • the refrigeration cycle apparatus of the present embodiment has a compressor 10 and a receiver 30 integrally configured.
  • the first temperature/pressure sensor 12 and the first variable throttle 14 are configured integrally.
  • the second temperature pressure sensor 22 and the second variable throttle 24 are integrally constructed.
  • the outdoor heat exchanger 13 and the indoor heat exchanger 23 are constructed integrally.
  • the phrase “a plurality of members are integrally configured” means that the plurality of members are accommodated in the same housing, or that some or all of the plurality of members are connected directly or via a spacer or the like.
  • the integral configuration of the compressor 10 and the receiver 30 is referred to as a "compressor/receiver structure 300".
  • the first temperature/pressure sensor 12 and the first variable throttle 14 are integrally constructed as a "first throttle valve structure 100”
  • the second temperature/pressure sensor 22 and the second variable throttle 24 are integrally constructed as a "second throttle valve structure 200”.
  • the first throttle valve structure 100 and the second throttle valve structure 200 have the same configuration. By adopting a system configuration using two identical parts in this way, the number of new parts can be reduced, and the cost can be reduced.
  • first throttle valve structure 100, the second throttle valve structure 200, and the comp receiver structure 300 are arranged adjacent to each other. As a result, it is possible to simplify the configuration of the piping connecting the first throttle valve structure 100 and the second throttle valve structure 200 and the compressor receiver structure 300 .
  • the outdoor heat exchanger 13 is arranged below the indoor heat exchanger 23 in the direction of gravity. Condensed water obtained by condensing water vapor in the air passing through the indoor heat exchanger 23 is supplied to the outer wall surface of the tubes or fins of the outdoor heat exchanger 13 by gravity. Therefore, during the cooling operation, the condensed water generated in the indoor heat exchanger 23 cools the tubes or fins of the outdoor heat exchanger 13, thereby enhancing the heat radiation effect of the outdoor heat exchanger 13 and improving the cooling performance.
  • the refrigeration cycle apparatus of the first embodiment described above has the following effects.
  • the valve opening degree of the first variable throttle 14 is controlled according to the temperature and pressure detected by the first temperature and pressure sensor 12 so that the refrigerant sucked into the first opening 11 of the compressor 10 becomes a gas refrigerant having a predetermined degree of superheat during the heating operation.
  • the valve opening degree of the second variable throttle 24 is controlled according to the temperature and pressure detected by the second temperature and pressure sensor 22 so that the refrigerant flowing out of the indoor heat exchanger 23 becomes liquid refrigerant with a predetermined degree of supercooling.
  • valve opening degree of the second variable throttle 24 is controlled according to the temperature and pressure detected by the second temperature and pressure sensor 22 so that the refrigerant sucked into the second opening 21 of the compressor 10 becomes a gas refrigerant with a predetermined degree of superheat during cooling operation.
  • valve opening of the first variable throttle 14 is controlled according to the temperature and pressure detected by the first temperature and pressure sensor 12 so that the refrigerant flowing out of the outdoor heat exchanger 13 becomes liquid refrigerant with a predetermined degree of supercooling.
  • this refrigeration cycle apparatus uses two temperature pressure sensors 12, 22 to adjust the opening of two variable throttles 14, 24 in both heating operation and cooling operation. Specifically, while adjusting the intake SH of the refrigerant sucked into the compressor 10 and the discharge SH of the refrigerant discharged from the compressor 10, it is possible to adjust the condenser outlet SC of the refrigerant flowing out of the heat exchanger functioning as a condenser among the indoor heat exchanger 23 and the outdoor heat exchanger 13. Therefore, this refrigeration cycle apparatus can simplify the configuration by reducing the number of parts such as one receiver 30, two temperature pressure sensors 12, 22, and two variable throttles 14, 24, and can be downsized. In addition, the cooling capacity and the heating capacity can be improved, and the COP can be improved.
  • this refrigeration cycle apparatus uses a bi-rotating compressor that can perform both heating operation and cooling operation, thereby reducing the number of parts and downsizing compared to a configuration in which a compressor and a four-way valve are combined as in Patent Document 1 described above.
  • both the first variable throttle 14 and the second variable throttle 24 are electronic expansion valves. Then, the ECU controls the valve opening degree of the first variable throttle 14 according to the temperature and pressure detected by the first temperature/pressure sensor 12, and controls the valve opening degree of the second variable throttle 24 according to the temperature and pressure detected by the second temperature/pressure sensor 22.
  • the refrigerating cycle device has a structure in which the first set and the second set are arranged symmetrically with respect to the axis of the compressor 10 and the receiver 30 in terms of the behavior of the refrigerant represented on the Mollier diagram. Therefore, this refrigeration cycle apparatus can be controlled by the same logic when switching between the cooling operation and the heating operation, so that the control capacity of the ECU can be reduced and the control circuit can be downsized.
  • this refrigeration cycle apparatus can perform operations corresponding to various demands of the refrigeration cycle apparatus.
  • operations corresponding to various requests for the refrigeration cycle apparatus include a scene in which priority is given to cooling capacity or heating capacity, a scene in which priority is given to COP, or a scene in which both cooling capacity or heating capacity and COP are given priority.
  • the ECU calculates the degree of subcooling of the refrigerant flowing out of the indoor heat exchanger 23 based on various information during the heating operation.
  • Various information at this time includes the temperature and pressure detected by the second temperature and pressure sensor 22, the refrigerant flow rate discharged from the compressor 10, the air flow rate supplied to the indoor heat exchanger 23, and the intake air temperature.
  • the ECU controls the valve opening degree of the second variable throttle 24 so that the refrigerant flowing out of the indoor heat exchanger 23 becomes liquid refrigerant with a predetermined target degree of supercooling.
  • the ECU calculates the degree of supercooling of the refrigerant flowing out of the outdoor heat exchanger 13 based on various information during the cooling operation.
  • Various information at this time includes the temperature and pressure detected by the first temperature and pressure sensor 12, the refrigerant flow rate discharged from the compressor 10, the air flow rate supplied to the outdoor heat exchanger 13, and the intake air temperature. Then, the ECU controls the valve opening degree of the first variable throttle 14 so that the refrigerant flowing out of the outdoor heat exchanger 13 becomes liquid refrigerant with a predetermined target degree of supercooling. According to this, the ECU can control the opening degrees of the two variable throttles 14, 24 using a small number of temperature pressure sensors 12, 22 in both the heating operation and the cooling operation.
  • the ECU controls the valve opening of the first variable throttle 14 while increasing the valve opening of the second variable throttle 24, and then controls the valve opening of the first variable throttle 14 while controlling the valve opening of the second variable throttle 24. Further, at the start of cooling operation, the ECU controls the valve opening degree of the second variable throttle 24 with the valve opening degree of the first variable throttle 14 increased, and then controls the valve opening degree of the second variable throttle 24 while controlling the valve opening degree of the first variable throttle 14.
  • the ECU adjusts the degree of superheat of the refrigerant sucked into the compressor 10 by controlling the valve opening of the first variable throttle 14, and then controls the valve opening of the second variable throttle 24 to adjust the degree of subcooling of the refrigerant flowing out from the indoor heat exchanger 23 functioning as a condenser. Therefore, by controlling the second variable throttle 24, the ECU can increase the degree of supercooling of the refrigerant flowing out of the indoor heat exchanger 23 to increase the heating capacity. In addition, the ECU prevents liquid refrigerant from being sucked into the compressor 10 by controlling the first variable throttle 14 and prevents the refrigerant sucked into the compressor 10 from becoming too superheated.
  • the ECU also controls the second variable throttle 24 to suppress the pressure rise of the high-pressure refrigerant discharged from the compressor 10 . Thereby, the COP of the cycle can be improved. Further, when the cooling operation is started, the ECU adjusts the degree of superheat of the refrigerant sucked into the compressor 10 by controlling the opening degree of the second variable throttle 24, and then controls the opening degree of the first variable throttle 14 to adjust the degree of subcooling of the refrigerant flowing out from the outdoor heat exchanger 13 functioning as a condenser. Therefore, by controlling the first variable throttle 14, the ECU can increase the degree of subcooling of the refrigerant flowing out of the outdoor heat exchanger 13 to increase the cooling capacity.
  • the ECU prevents the liquid refrigerant from being sucked into the compressor 10 by controlling the second variable throttle 24 and prevents the refrigerant sucked into the compressor 10 from becoming too superheated. Further, the ECU controls the pressure increase of the high-pressure refrigerant discharged from the compressor 10 by controlling the first variable throttle 14 . Thereby, the COP of the cycle can be improved. Therefore, this refrigeration cycle device can perform operations corresponding to various requests to the refrigeration cycle device, such as a scene in which priority is given to cooling capacity or heating capacity, a scene in which COP is given priority, or a scene in which both cooling capacity or heating capacity and COP are given priority.
  • this refrigerating cycle apparatus can adjust the opening degrees of the two variable throttles 14, 24 using a small number of two temperature pressure sensors 12, 22 in both the heating operation and the cooling operation.
  • a plurality of members integrally configured means that the plurality of members are accommodated in the same housing, or that some or all of the plurality of members are connected directly or via a spacer or the like.
  • the first temperature/pressure sensor 12 and the first variable throttle 14 are integrated into the first throttle valve structure 100, and the second temperature/pressure sensor 22 and the second variable throttle 24 are also integrated into the second throttle valve structure 200. According to this, by using two units in which the temperature pressure sensor and the variable throttle are integrated, the configuration of the refrigeration cycle apparatus can be simplified and the size thereof can be reduced.
  • the first throttle valve structure 100 and the second throttle valve structure 200 have the same configuration, and the system configuration using two of the same structure can reduce the number of new parts, thereby reducing the cost.
  • the outdoor heat exchanger 13 is arranged below the indoor heat exchanger 23 in the direction of gravity. Condensed water obtained by condensing water vapor in the air passing through the indoor heat exchanger 23 is supplied to the outer wall surface of the tubes or fins of the outdoor heat exchanger 13 by gravity. According to this, the tubes or fins of the outdoor heat exchanger 13 are cooled by the condensed water obtained by condensing the water vapor in the air passing through the indoor heat exchanger 23 during the cooling operation, so that the heat dissipation effect of the outdoor heat exchanger 13 can be enhanced and the cooling performance can be improved.
  • the second embodiment differs from the first embodiment in the configuration of the temperature pressure sensor and the variable throttle, and is otherwise the same as the first embodiment. Therefore, only the differences from the first embodiment will be described.
  • the first temperature/pressure sensor 12 and the first variable throttle 14 are integrated to constitute the first throttle valve structure 100.
  • the second temperature/pressure sensor 22 and the second variable throttle 24 are integrated to form a second throttle valve structure 200 .
  • FIG. 12 shows a specific example of the first throttle valve structure 100
  • FIG. 13 shows a specific example of the second throttle valve structure 200.
  • both the first variable throttle 14 and the second variable throttle 24 are mechanical expansion valves.
  • the temperature and pressure sensors 12, 22 are temperature sensing parts that control the operation of the mechanical expansion valves.
  • the first variable throttle 14 is called “first mechanical expansion valve 140", and the first temperature pressure sensor 12 is called “first temperature sensing part 120".
  • the first mechanical expansion valve 140 is configured such that the degree of valve opening is mechanically controlled according to the temperature and pressure detected by the first temperature sensing portion 120 .
  • the second variable throttle 24 is called “second mechanical expansion valve 240”, and the second temperature pressure sensor 22 is called “second temperature sensing part 220”.
  • the second mechanical expansion valve 240 is configured such that the degree of valve opening is mechanically controlled according to the temperature and pressure detected by the second temperature sensing portion 220 .
  • the configuration of the first throttle valve structure 100 will be described with reference to FIG. 12 .
  • the first throttle valve structure 100 is provided with a first mechanical expansion valve 140 and a first temperature sensing section 120 in a body section 50 as a housing.
  • the body portion 50 is formed with a temperature sensing portion side refrigerant passage 51 provided on the first temperature sensing portion 120 side and a valve portion side refrigerant passage 52 provided on the first mechanical expansion valve 140 side.
  • One end 511 of the temperature sensing part side refrigerant passage 51 communicates with the first opening 11 of the compressor 10
  • the other end 512 of the temperature sensing part side refrigerant passage 51 communicates with the outdoor heat exchanger 13 .
  • a first temperature sensing portion 120 is provided in the middle of the temperature sensing portion side refrigerant passage 51 .
  • valve-side refrigerant passage 52 communicates with the receiver 30
  • the other end 522 of the valve-side refrigerant passage 52 communicates with the outdoor heat exchanger 13
  • a first valve seat 141 , a first valve body 142 , and the like, which constitute the first mechanical expansion valve 140 are provided in a valve chamber 520 provided in the middle of the valve section side refrigerant passage 52 .
  • the first temperature sensing section 120 includes a diaphragm 121, a cover 122, an operating member 125, an operating rod 126, and the like. Diaphragm 121 and cover 122 form an enclosed space 123 in which a temperature-sensitive medium is enclosed. As the temperature-sensitive medium, for example, the same refrigerant as in the refrigeration cycle is sealed in a gas-liquid mixture state. An introduction space 124 is formed on the side of the diaphragm 121 opposite to the sealed space 123 , into which the refrigerant is introduced from the temperature-sensing-side refrigerant passage 51 through a hole 127 .
  • An actuating member 125 is arranged in the introduction space 124 and an actuating rod 126 is fixed to the actuating member 125 .
  • the actuating rod 126 has one end fixed to the actuating member 125 , a central portion inserted through the hole 53 provided in the body portion 50 , and the other end abutting against the first valve body 142 constituting the first mechanical expansion valve 140 .
  • the pressure of the temperature-sensitive medium in the enclosed space 123 changes due to heat transfer from the coolant in the introduction space 124 . Therefore, the diaphragm 121 is displaced according to the differential pressure between the temperature-sensitive medium in the enclosure space 123 and the coolant in the introduction space 124 .
  • the operating member 125 and operating rod 126 are displaced together with the diaphragm 121 to operate the first valve body 142 .
  • the first mechanical expansion valve 140 includes a first valve seat 141, a first valve body 142, a spring 143 and the like.
  • the first valve seat 141 , the first valve body 142 , and the spring 143 are provided in a valve chamber 520 provided in the middle of the valve section side refrigerant passage 52 .
  • the first valve seat 141 is formed on part of the inner wall surface of the valve chamber 520 .
  • the first valve body 142 is provided in a passage on the side of the receiver 30 with respect to the first valve seat 141 and can be seated on and separated from the first valve seat 141 .
  • a spring 143 biases the first valve body 142 toward the first valve seat 141 .
  • the biasing force of spring 143 can be adjusted by adjusting screw 144 .
  • the actuating rod 126 of the first temperature sensing part 120 moves the first valve body 142 against the biasing force of the spring 143 , and the first valve body 142 is separated from the first valve seat 141 .
  • the first mechanical expansion valve 140 is mechanically controlled in valve opening according to the temperature and pressure detected by the first temperature sensing section 120 .
  • the configuration of the second throttle valve structure 200 is substantially the same as the configuration of the first throttle valve structure 100 described above.
  • a second mechanical expansion valve 240 and a second temperature sensing section 220 are provided in a body section 60 as a housing.
  • the body portion 60 is formed with a temperature sensing portion side refrigerant passage 61 provided on the second temperature sensing portion 220 side and a valve portion side refrigerant passage 62 provided on the second mechanical expansion valve 240 side.
  • One end 611 of the temperature sensing part side refrigerant passage 61 communicates with the second opening 21 of the compressor 10
  • the other end 612 of the temperature sensing part side refrigerant passage 61 communicates with the indoor heat exchanger 23 .
  • a second temperature sensing portion 220 is provided in the middle of the temperature sensing portion side refrigerant passage 61 .
  • valve-side refrigerant passage 62 communicates with the receiver 30
  • the other end 622 of the valve-side refrigerant passage 62 communicates with the indoor heat exchanger 23 .
  • a second valve seat 241 , a second valve body 242 , and the like, which constitute a second mechanical expansion valve 240 are provided in a valve chamber 620 provided in the middle of the valve section side refrigerant passage 62 .
  • the second temperature sensing section 220 includes a diaphragm 221, a cover 222, an operating member 225, an operating rod 226, and the like. Diaphragm 221 and cover 222 form an enclosed space 223 in which a temperature-sensitive medium is enclosed. As the temperature-sensitive medium, for example, the same refrigerant as in the refrigeration cycle is sealed in a gas-liquid mixture state. On the opposite side of the diaphragm 221 to the sealed space 223 , an introduction space 224 is formed into which the refrigerant is introduced from the temperature sensing section side refrigerant passage 61 through a hole 227 .
  • An actuating member 225 is arranged in the introduction space 224 and an actuating rod 226 is fixed to the actuating member 225 .
  • the actuating rod 226 has one end fixed to the actuating member 225 , a central portion inserted through a hole 63 provided in the body portion 60 , and the other end abutting a second valve body 242 that constitutes the second mechanical expansion valve 240 .
  • the pressure of the temperature-sensitive medium in the enclosed space 223 changes due to heat transfer from the coolant in the introduction space 224 . Therefore, the diaphragm 221 is displaced according to the differential pressure between the temperature-sensitive medium in the enclosure space 223 and the coolant in the introduction space 224 .
  • the operating member 225 and the operating rod 226 are displaced together with the diaphragm 221 to operate the second valve body 242 .
  • the second mechanical expansion valve 240 includes a second valve seat 241, a second valve body 242, a spring 243 and the like.
  • the second valve seat 241 , the second valve body 242 and the spring 243 are provided in a valve chamber 620 provided in the middle of the valve section side refrigerant passage 62 .
  • the second valve seat 241 is formed on part of the inner wall surface of the valve chamber 620 .
  • the second valve body 242 is provided in the passage on the side of the receiver 30 with respect to the second valve seat 241 and can be seated on and separated from the second valve seat 241 .
  • a spring 243 biases the second valve body 242 toward the second valve seat 241 side.
  • the biasing force of spring 243 can be adjusted by adjusting screw 244 .
  • the actuating rod 226 of the second temperature sensing part 220 moves the second valve body 242 against the biasing force of the spring 243 , and the second valve body 242 is separated from the second valve seat 241 .
  • the opening degree of the second mechanical expansion valve 240 is mechanically controlled according to the temperature and pressure detected by the second temperature sensing section 220 .
  • the first throttle valve structure 100 and the second throttle valve structure 200 have substantially the same configuration.
  • the first throttle valve structure 100 becomes the lower stage throttle
  • the second throttle valve structure 200 becomes the upper stage throttle.
  • the first throttle valve structure 100 serves as an upper throttle
  • the second throttle valve structure 200 serves as a lower throttle.
  • the characteristics of the temperature-sensitive medium enclosed in the enclosed spaces 123, 223 of the temperature-sensitive portions 120, 220 and the biasing forces of the springs 143, 243 of the mechanical expansion valves are appropriately adjusted.
  • the operation of the first throttle valve structure 100 and the second throttle valve structure 200 allows the refrigerant at the condenser outlet to have a desired condenser outlet SC and the refrigerant sucked into the compressor 10 to have a desired intake SH.
  • the pressure difference between the high-pressure refrigerant discharged from the compressor 10 and the refrigerant downstream of the upper throttle may become excessive. Therefore, if the valve seat of the mechanical expansion valve forming the upper throttle is arranged on the receiver 30 side with respect to the valve body, the upper throttle may be closed unintentionally due to the pressure difference.
  • both the first mechanical expansion valve 140 and the second mechanical expansion valve 240 have the valve bodies 142 and 242 arranged on the receiver 30 side with respect to the valve seats 141 and 241 .
  • the first variable throttle 14 is the first mechanical expansion valve 140
  • the first temperature/pressure sensor 12 is the first temperature sensing section 120 that controls the operation of the first mechanical expansion valve 140.
  • the second variable throttle 24 is a second mechanical expansion valve 240
  • the second temperature/pressure sensor 22 is a second temperature sensing section 220 that controls the operation of the second mechanical expansion valve 240 .
  • the configuration in which the first valve body 142 is arranged on the receiver 30 side with respect to the first valve seat 141 described in the second embodiment may be applied to the first variable throttle 14 (that is, the electronic expansion valve) described in the first embodiment.
  • the arrangement of disposing the second valve body 242 on the receiver 30 side with respect to the second valve seat 241 described in the second embodiment may be applied to the second variable throttle 24 (that is, the electronic expansion valve) described in the first embodiment.
  • the compressor 10 included in the refrigeration cycle apparatus of the third embodiment has a plurality of compression mechanism units 101 and 102 that compress refrigerant.
  • the plurality of compression mechanisms 101 and 102 are rotationally driven by an electric motor 103 .
  • the electric motor 103 is rotatable in both forward and reverse directions.
  • Compressor 10 is therefore an electric, bi-rotating compressor.
  • As the compression mechanisms 101 and 102 various types such as a rotary vane type and a rolling piston type can be used.
  • One of the plurality of compression mechanism units 101 and 102 of the compressor 10 is called a first compression mechanism unit 101 and the other compression mechanism unit is called a second compression mechanism unit 102 .
  • the rotation phases of the first compression mechanism portion 101 and the second compression mechanism portion 102 are out of phase by 180°. It should be noted that the phase shift of 180 degrees of rotation may be substantially 180 degrees, and includes manufacturing tolerances and the like.
  • the first compression mechanism section 101 and the second compression mechanism section 102 are connected in parallel by a refrigerant passage or the like inside the compressor 10 .
  • the compressor 10 can perform heating operation and cooling operation by switching between forward rotation and reverse rotation.
  • dashed arrows indicate the direction of refrigerant flow when compressor 10 performs the heating operation
  • solid arrows indicate the direction of refrigerant flow when compressor 10 performs the cooling operation.
  • FIG. 15 is a Mollier diagram showing an example of the behavior of the refrigerant when the refrigeration cycle apparatus of the third embodiment performs cooling operation.
  • the positions of E1 to E4 vary depending on various conditions such as the number of rotations of the compressor 10, the opening degrees of the first variable throttle 14 and the second variable throttle 24, the number of rotations of the outdoor fan 15 and the indoor fan 25, the outside air temperature, and the vehicle interior temperature.
  • E1 indicates the state of the refrigerant that flows out from the indoor heat exchanger 23 that functions as an evaporator during cooling operation and is sucked into the first compression mechanism section 101 and the second compression mechanism section 102 of the compressor 10 .
  • E2 indicates the state of refrigerant discharged from the first compression mechanism portion 101 and the second compression mechanism portion 102 of the compressor 10 and flowing into the outdoor heat exchanger 13 functioning as a condenser during cooling operation.
  • E3 indicates the state of the refrigerant that flows out from the outdoor heat exchanger 13 functioning as its condenser and flows into the first variable throttle 14 .
  • E4 indicates the state of the refrigerant that flows out from the second variable throttle 24 and flows into the indoor heat exchanger 23 that functions as an evaporator.
  • the behavior of the refrigerant in the refrigeration cycle device of the third embodiment is substantially the same as that described in the first embodiment.
  • the behavior of the refrigerant when the refrigeration cycle apparatus of the third embodiment performs the heating operation also changes between the first set and the second set on the high pressure side and the low pressure side with the receiver 30 and the compressor 10 as the axes, so illustration is omitted. Therefore, the refrigerating cycle device of the third embodiment can also achieve the same effects as the refrigerating cycle device of the first embodiment.
  • the compressor 10 has a plurality of compression mechanism units 101 and 102 for compressing the refrigerant.
  • the rotation phases of the first compression mechanism portion 101 and the second compression mechanism portion 102 are shifted by 180°.
  • the phase shift of 180 degrees of rotation may be substantially 180 degrees, and includes manufacturing tolerances and the like. According to this, the vibration and noise of the compressor 10 can be reduced.
  • 4th Embodiment also changes the structure of the compressor 10 with respect to 1st Embodiment etc., and since it is the same as that of 1st Embodiment etc. about others, only a different part from 1st Embodiment etc. is demonstrated.
  • the compressor 10 included in the refrigeration cycle apparatus of the fourth embodiment is also a dual rotary compressor having a first compression mechanism section 101 and a second compression mechanism section 102, like the third embodiment. Therefore, this refrigeration cycle apparatus can also perform heating operation and cooling operation by switching the forward rotation and reverse rotation of the compressor 10 .
  • the direction of refrigerant flow when the compressor 10 performs the heating operation is indicated by the dashed arrow
  • the direction of the refrigerant flow when the compressor 10 performs the cooling operation is indicated by the solid arrow.
  • the first compression mechanism section 101 and the second compression mechanism section 102 are connected in series by a refrigerant passage or the like inside the compressor 10 .
  • the compressor 10 is configured such that refrigerant sucked, compressed, and discharged by the first compression mechanism portion 101 is sucked, compressed, and discharged by the second compression mechanism portion 102 in the cooling operation.
  • the compressor 10 is configured such that the refrigerant sucked, compressed, and discharged to the second compression mechanism portion 102 is sucked, compressed, and discharged to the first compression mechanism portion 101 during the heating operation.
  • the compressor 10 and the receiver 30 are integrally configured as a "compressor/receiver structure 300". Therefore, the configuration of the piping connecting the compressor 10 and the receiver 30 can be simplified, and the size can be reduced.
  • FIG. 17 is a Mollier diagram showing an example of the behavior of the refrigerant when the refrigeration cycle apparatus of the fourth embodiment performs cooling operation.
  • the positions of F1 to F7 vary depending on various conditions such as the rotation speed of the compressor 10, the valve opening degrees of the first variable throttle 14 and the second variable throttle 24, the rotation speeds of the outdoor fan 15 and the indoor fan 25, the outside air temperature, and the vehicle interior temperature.
  • F1 indicates the state of the refrigerant that flows out from the indoor heat exchanger 23 that functions as an evaporator during cooling operation and is drawn into the first compression mechanism section 101 of the compressor 10 .
  • F2 indicates the state of the refrigerant discharged from the first compression mechanism section 101 .
  • F3 indicates the state of refrigerant sucked into the second compression mechanism portion 102 .
  • the gas refrigerant in the receiver 30 is supplied to the intermediate stages 104 and 105 of the first compression mechanism section 101 and the second compression mechanism section 102, so the specific enthalpy is lower than in F2.
  • F4 indicates the state of the refrigerant discharged from the second compression mechanism section 102 and flowing into the outdoor heat exchanger 13 functioning as a condenser during cooling operation.
  • F5 indicates the state of the refrigerant flowing out of the outdoor heat exchanger 13 functioning as its condenser and flowing into the first variable throttle 14 .
  • F6 indicates the state of the refrigerant in the receiver 30;
  • F7 indicates the state of the refrigerant that flows out from the second variable throttle 24 and flows into the indoor heat exchanger 23 that functions as an evaporator.
  • the refrigeration cycle apparatus of the fourth embodiment described above by supplying the gas refrigerant of the receiver 30 to the intermediate stages 104 and 105 of the two-stage compression compressor 10, it is possible to lower the specific enthalpy of the refrigerant compressed by the compression mechanism section on the high pressure side among the plurality of compression mechanism sections. Therefore, by reducing the power of the compressor 10 and lowering the specific enthalpy of the refrigerant discharged from the compressor 10, the cooling performance and the heating performance can be improved, and the COP can be improved.
  • the compressor 10 and the receiver 30 by integrally configuring the compressor 10 and the receiver 30, it is possible to omit the piping or the like connecting the compressor 10 and the receiver 30 or to shorten the piping or the like. Therefore, it is possible to simplify the configuration of the refrigeration cycle apparatus and reduce its size.
  • the fifth embodiment is different from the first embodiment, etc. in the configuration of the temperature pressure sensor, and is otherwise the same as the first embodiment, so only the parts different from the first embodiment, etc. will be described.
  • the refrigeration cycle apparatus of the fifth embodiment includes a third temperature/pressure sensor 17 and a fourth temperature/pressure sensor 27 in addition to the first temperature/pressure sensor 12 and the second temperature/pressure sensor 22 described in the first embodiment.
  • the third temperature/pressure sensor 17 is a sensor that is provided between the outdoor heat exchanger 13 and the first variable throttle 14 and detects at least one of the temperature and pressure of the refrigerant flowing therethrough.
  • a fourth temperature/pressure sensor 27 is provided between the indoor heat exchanger 23 and the second variable throttle 24 and detects at least one of the temperature and pressure of the refrigerant flowing therethrough.
  • the temperature and pressure of the refrigerant detected by the third temperature/pressure sensor 17 and the fourth temperature/pressure sensor 27 are respectively transmitted to the ECU.
  • the ECU can directly detect the degree of supercooling of the refrigerant flowing out of the condenser in both the heating operation and the cooling operation by the output from the third temperature/pressure sensor 17 and the fourth temperature/pressure sensor 27 .
  • the ECU controls the valve opening of the second variable throttle 24 according to the temperature and pressure detected by the fourth temperature and pressure sensor 27 instead of the second temperature and pressure sensor 22 described in the first to fourth embodiments.
  • the ECU controls the opening degree of the first variable throttle 14 according to the temperature and pressure detected by the first temperature/pressure sensor 12 during the heating operation.
  • the ECU controls the valve opening of the first variable throttle 14 according to the temperature and pressure detected by the third temperature and pressure sensor 17 instead of the first temperature and pressure sensor 12 described in the first to fourth embodiments.
  • the ECU controls the valve opening degree of the second variable throttle 24 according to the temperature and pressure detected by the second temperature/pressure sensor 22 during cooling operation.
  • the refrigeration cycle apparatus of the fifth embodiment described above has four temperature/pressure sensors 12, 17, 22, and 27 as functional units that detect at least one of the temperature and pressure of the refrigerant. Thereby, the calculation load of the ECU can be reduced.
  • the compressor 10 only performs the operation of sucking the refrigerant through the first opening 11, compressing it, and discharging it through the second opening 21.
  • the flow path switching valve 70 is a four-way valve provided midway along the flow path that connects the compressor 10 and the indoor heat exchanger 23 and over the middle of the flow path that connects the compressor 10 and the outdoor heat exchanger 13 .
  • the passage switching valve 70 is driven and controlled by the ECU.
  • the ECU drives and controls the flow path switching valve 70 to switch the refrigerant flow between the compressor 10 and the heat exchangers 13 and 23, thereby performing the heating operation and the cooling operation.
  • the refrigerant discharged from the second opening 21 of the compressor 10 flows through the flow path switching valve 70, the indoor heat exchanger 23, the second variable throttle 24, the receiver 30, the first variable throttle 14, the outdoor heat exchanger 13, and the flow path switching valve 70 in this order and is sucked into the first opening 11 of the compressor 10.
  • the refrigerant discharged from the second opening 21 of the compressor 10 flows through the flow path switching valve 70, the outdoor heat exchanger 13, the first variable throttle 14, the receiver 30, the second variable throttle 24, the indoor heat exchanger 23, and the flow path switching valve 70 in this order and is sucked into the first opening 11 of the compressor 10.
  • the first temperature-pressure sensor 12 is provided between the first opening 11 of the compressor 10 and the flow path switching valve 70 .
  • the second temperature/pressure sensor 22 is provided between the second opening 21 of the compressor 10 and the flow path switching valve 70 .
  • the temperature and pressure of the refrigerant detected by the first temperature-pressure sensor 12 and the second temperature-pressure sensor 22 are respectively transmitted to the ECU.
  • the ECU controls the valve opening of the first variable throttle 14 according to the temperature and pressure detected by the first temperature and pressure sensor 12 so that the refrigerant sucked into the first opening 11 of the compressor 10 has a predetermined SH.
  • the ECU controls the valve opening degree of the second variable throttle 24 according to the temperature and pressure detected by the second temperature/pressure sensor 22 so that the refrigerant flowing out of the indoor heat exchanger 23 has a predetermined SC.
  • the ECU controls the valve opening of the second variable throttle 24 according to the temperature and pressure detected by the first temperature and pressure sensor 12 so that the refrigerant sucked into the first opening 11 of the compressor 10 has a predetermined SH.
  • the ECU controls the opening degree of the first variable throttle 14 according to the temperature and pressure detected by the second temperature/pressure sensor 22 so that the refrigerant flowing out of the outdoor heat exchanger 13 has a predetermined SC.
  • the first temperature/pressure sensor 12 may be provided between the flow path switching valve 70 and the outdoor heat exchanger 13 .
  • the second temperature/pressure sensor 22 may be provided between the flow path switching valve 70 and the indoor heat exchanger 23 .
  • the ECU controls the valve opening degree of the first variable throttle 14 according to the temperature and pressure detected by the first temperature and pressure sensor 12 so that the refrigerant sucked into the first opening 11 of the compressor 10 has a predetermined SH.
  • the ECU controls the valve opening degree of the second variable throttle 24 according to the temperature and pressure detected by the second temperature/pressure sensor 22 so that the refrigerant flowing out of the indoor heat exchanger 23 has a predetermined SC.
  • the ECU controls the valve opening degree of the second variable throttle 24 according to the temperature and pressure detected by the second temperature and pressure sensor 22 so that the refrigerant sucked into the first opening 11 of the compressor 10 has a predetermined SH.
  • the ECU controls the opening degree of the first variable throttle 14 according to the temperature and pressure detected by the first temperature/pressure sensor 12 so that the refrigerant flowing out of the outdoor heat exchanger 13 has a predetermined SC.
  • first opening 11 of the compressor 10 and the first temperature/pressure sensor 12 may be integrated, or the second opening 21 and the second temperature/pressure sensor 22 of the compressor may be integrated. As a result, the number of assembling man-hours can be reduced.
  • the first variable throttle 14 configured as an electronic expansion valve and the first temperature/pressure sensor 12 may be integrated into one module.
  • the second variable throttle 24 configured as an electronic expansion valve and the second temperature/pressure sensor 22 may be integrated into one module.
  • the present disclosure is not limited to the above-described embodiments, and can be modified as appropriate. Moreover, the above-described embodiments are not unrelated to each other, and can be appropriately combined unless the combination is clearly impossible. Further, in each of the above-described embodiments, it goes without saying that the elements constituting the embodiment are not necessarily essential unless explicitly stated as essential or clearly considered essential in principle. In addition, in each of the above-described embodiments, when numerical values such as the number, numerical value, amount, range, etc. of the constituent elements of the embodiment are mentioned, they are not limited to the specific numbers, except when explicitly stated as essential or when they are clearly limited to a specific number in principle. In addition, in each of the above-described embodiments, when referring to the shape, positional relationship, etc.
  • the shape, positional relationship, etc. are not limited, except in cases where it is particularly specified and in principle limited to a specific shape, positional relationship, etc.
  • the sensor when it is described that the external environment information of the vehicle (for example, the humidity outside the vehicle) is obtained from a sensor, the sensor can be eliminated and the external environment information can be received from a server or cloud outside the vehicle.
  • the sensor it is also possible to eliminate the sensor, acquire related information related to the external environment information from a server or cloud outside the vehicle, and estimate the external environment information from the acquired related information.
  • the controller and method described in the present disclosure may be implemented by a dedicated computer provided by configuring a processor and memory programmed to perform one or more functions embodied by a computer program.
  • the controls and techniques described in this disclosure may be implemented by a dedicated computer provided by configuring the processor with one or more dedicated hardware logic circuits.
  • the controls and techniques described in this disclosure may be implemented by one or more dedicated computers configured with a processor and memory programmed to perform one or more functions in combination with the processor configured by one or more hardware logic circuits.
  • the computer program may also be stored as computer-executable instructions on a computer-readable non-transitional tangible recording medium.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Dans la présente invention, un compresseur (10) est capable de chauffer l'opération de fonctionnement et de refroidissement. Un récepteur (30) est disposé entre un échangeur de chaleur externe (13) et un échangeur de chaleur interne (23). Un premier étranglement variable (14) est disposé entre l'échangeur de chaleur externe (13) et le récepteur (30). Un second étranglement variable (24) est disposé entre l'échangeur de chaleur interne (23) et le récepteur (30). Un premier capteur de pression-température (12) est disposé entre une première ouverture (11) du compresseur (10) et l'échangeur de chaleur externe (13). Un second capteur de pression-température (22) est disposé entre une seconde ouverture (21) du compresseur (10) et l'échangeur de chaleur interne (23). Pendant l'opération de chauffage et l'opération de refroidissement, l'ouverture de soupape du premier étranglement variable (14) est commandée en fonction de la température et de la pression détectées par le premier capteur de pression-température (12), et l'ouverture de soupape du second étranglement variable (24) est commandée en fonction de la température et de la pression détectées par le second capteur de pression-température (22).
PCT/JP2023/001177 2022-01-24 2023-01-17 Dispositif à cycle frigorifique WO2023140249A1 (fr)

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JP2022008846A JP2023107582A (ja) 2022-01-24 2022-01-24 冷凍サイクル装置
JP2022-008846 2022-01-24

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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61171606A (ja) * 1985-01-24 1986-08-02 Matsushita Electric Ind Co Ltd カ−エアコン冷凍装置
JPS6213940A (ja) * 1985-07-11 1987-01-22 Matsushita Seiko Co Ltd 個別形空気調和機
JP2001174091A (ja) * 1999-12-15 2001-06-29 Mitsubishi Electric Corp 冷凍サイクル
JP2002195700A (ja) * 2000-12-26 2002-07-10 Mitsubishi Electric Corp 冷凍サイクル装置
JP2009270822A (ja) * 2009-08-21 2009-11-19 Mitsubishi Electric Corp ヒートポンプ装置及びヒートポンプ装置の室外機
JP2010085001A (ja) * 2008-09-30 2010-04-15 Daikin Ind Ltd 冷凍装置
JP2011503504A (ja) * 2007-11-09 2011-01-27 キャリア コーポレイション 輸送用冷凍システムおよびその作動方法

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61171606A (ja) * 1985-01-24 1986-08-02 Matsushita Electric Ind Co Ltd カ−エアコン冷凍装置
JPS6213940A (ja) * 1985-07-11 1987-01-22 Matsushita Seiko Co Ltd 個別形空気調和機
JP2001174091A (ja) * 1999-12-15 2001-06-29 Mitsubishi Electric Corp 冷凍サイクル
JP2002195700A (ja) * 2000-12-26 2002-07-10 Mitsubishi Electric Corp 冷凍サイクル装置
JP2011503504A (ja) * 2007-11-09 2011-01-27 キャリア コーポレイション 輸送用冷凍システムおよびその作動方法
JP2010085001A (ja) * 2008-09-30 2010-04-15 Daikin Ind Ltd 冷凍装置
JP2009270822A (ja) * 2009-08-21 2009-11-19 Mitsubishi Electric Corp ヒートポンプ装置及びヒートポンプ装置の室外機

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