WO2018110185A1 - Refrigerant circuit system and method for controlling refrigerant circuit system - Google Patents

Refrigerant circuit system and method for controlling refrigerant circuit system Download PDF

Info

Publication number
WO2018110185A1
WO2018110185A1 PCT/JP2017/040965 JP2017040965W WO2018110185A1 WO 2018110185 A1 WO2018110185 A1 WO 2018110185A1 JP 2017040965 W JP2017040965 W JP 2017040965W WO 2018110185 A1 WO2018110185 A1 WO 2018110185A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
enthalpy
temperature
heat exchanger
gas
Prior art date
Application number
PCT/JP2017/040965
Other languages
French (fr)
Japanese (ja)
Inventor
道明 中西
Original Assignee
三菱重工サーマルシステムズ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to JP2016242022A priority Critical patent/JP6781034B2/en
Priority to JP2016-242022 priority
Application filed by 三菱重工サーマルシステムズ株式会社 filed Critical 三菱重工サーマルシステムズ株式会社
Publication of WO2018110185A1 publication Critical patent/WO2018110185A1/en

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00Subcoolers, desuperheaters or superheaters
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24HEATING; RANGES; VENTILATING
    • F24FAIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00Control or safety arrangements
    • F24F11/70Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00Compression machines, plants or systems, with reversible cycle
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031Sensor arrangements
    • F25B2313/0314Temperature sensors near the indoor heat exchanger
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031Sensor arrangements
    • F25B2313/0315Temperature sensors near the outdoor heat exchanger
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00Problems to be solved
    • F25B2500/08Exceeding a certain temperature value in a refrigeration component or cycle
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00Control issues
    • F25B2600/25Control of valves
    • F25B2600/2501Bypass valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21Temperatures
    • F25B2700/2103Temperatures near a heat exchanger
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21Temperatures
    • F25B2700/2115Temperatures of a compressor or the drive means therefor
    • F25B2700/21152Temperatures of a compressor or the drive means therefor at the discharge side of the compressor

Abstract

Provided is a refrigerant circuit system with which it is possible to promote overcooling while adequately controlling the compressor temperature. The refrigerant circuit system (1) is provided with: a gas-liquid heat exchanger (20) for exchanging heat between a high-pressure refrigerant and a low-pressure refrigerant; a bypass path (21) for diverting the high-pressure refrigerant upstream of a decompression unit (151); a bypass valve (22) capable of adjusting the flow rate; and a control unit (25) for issuing a command corresponding to the flow rate to the bypass valve (22). The control unit (25) determines the ratio of increase/decrease from the current point in time of the flow rate of the high-pressure refrigerant to be channeled into the bypass path (21) on the basis of Δh'/Δh, when: h1 is the discharge enthalpy, which is enthalpy corresponding to the sensed temperature of the discharged refrigerant; Δh is the enthalpy difference, which is the difference in enthalpy corresponding to the sensed refrigerant temperature at the inlet and outlet of the gas-liquid heat exchanger (20); hv is the target discharge enthalpy corresponding to the target temperature Tv allowable for the compressor (14); and Δh' is the compatible enthalpy difference compatible with the target discharge enthalpy hv on the basis of h1 and Δh.

Description

冷媒回路システムおよび冷媒回路システムの制御方法Refrigerant circuit system and method for controlling refrigerant circuit system
 本発明は、気液熱交換器を備えた冷媒回路システムおよび冷媒回路システムの制御方法に関する。 The present invention relates to a refrigerant circuit system including a gas-liquid heat exchanger and a method for controlling the refrigerant circuit system.
 空気調和機等の冷媒回路システムの性能を上げるためには、冷媒の熱をいかに放熱させ、液化できるかが重要であり、その役割を凝縮器が担う。圧縮機により圧縮された高温高圧の冷媒ガスは、凝縮器にて空気との熱交換により、熱を放出してエンタルピを下げる。ここで、過冷却を促進してエンタルピを下げるほど、性能を高められるが、技術の進歩により、冷媒ガスの温度を空気温度に近い温度にまで放熱させている現状においては、さらなる過冷却の促進が困難になってきている。 In order to improve the performance of refrigerant circuit systems such as air conditioners, it is important how the heat of the refrigerant can be dissipated and liquefied, and the condenser plays the role. The high-temperature and high-pressure refrigerant gas compressed by the compressor releases heat and lowers enthalpy by heat exchange with air in the condenser. Here, the performance can be improved as the enthalpy is reduced by promoting supercooling. However, in the current situation where the temperature of the refrigerant gas is dissipated to a temperature close to the air temperature due to technological advances, further promotion of supercooling is achieved. Has become difficult.
 そこで、凝縮器により液化された高圧冷媒と、蒸発器を通過した後の低圧冷媒ガスとの間で熱交換する気液熱交換器(内部熱交換器、インタークーラとも)を使用すると、高圧冷媒をさらに液化してエンタルピを下げることができる。
 しかし、気液熱交換器における高圧冷媒から低圧冷媒への放熱により、圧縮機に吸入される低圧冷媒の温度が高くなるので、圧縮機の温度が上昇する。圧縮機の温度を許容される温度に抑えるため、蒸発器を通過した低圧冷媒の一部だけを気液熱交換器に流し、残りをバイパスさせている例がある(特許文献1)。つまり、バイパスにより、高圧冷媒から放熱される低圧冷媒の流量を調整している。特許文献1では、蒸発器の出口側に、バイパス経路とバイパス用の弁が設けられおり、バイパス経路から圧縮機へと低圧冷媒を吸入させている。
Therefore, if a gas-liquid heat exchanger (both internal heat exchanger and intercooler) that exchanges heat between the high-pressure refrigerant liquefied by the condenser and the low-pressure refrigerant gas after passing through the evaporator is used, Can be further liquefied to lower enthalpy.
However, since the temperature of the low-pressure refrigerant sucked into the compressor increases due to heat radiation from the high-pressure refrigerant to the low-pressure refrigerant in the gas-liquid heat exchanger, the temperature of the compressor rises. In order to suppress the temperature of the compressor to an allowable temperature, there is an example in which only a part of the low-pressure refrigerant that has passed through the evaporator is passed through the gas-liquid heat exchanger and the rest is bypassed (Patent Document 1). That is, the flow rate of the low-pressure refrigerant radiated from the high-pressure refrigerant is adjusted by bypass. In Patent Document 1, a bypass path and a bypass valve are provided on the outlet side of the evaporator, and low-pressure refrigerant is sucked into the compressor from the bypass path.
特開2000-346466号公報JP 2000-346466 A
 特許文献1のように、蒸発器を通過して気液熱交換器を流れる低圧冷媒の流量を調整しようとすると、その冷媒が低圧のガスであるために流量調整が難しい。しかも、バイパスさせた冷媒を圧縮機へと吸入させているため、バイパスさせる冷媒の流量を変化させると、その影響が圧縮機に直接的に作用し、圧縮機の温度が目標の温度に対してオーバーシュートしたりハンチングが生じ易い。 As in Patent Document 1, when trying to adjust the flow rate of the low-pressure refrigerant that passes through the evaporator and flows through the gas-liquid heat exchanger, it is difficult to adjust the flow rate because the refrigerant is a low-pressure gas. In addition, since the bypassed refrigerant is sucked into the compressor, if the flow rate of the bypassed refrigerant is changed, the effect directly acts on the compressor, and the compressor temperature becomes lower than the target temperature. Overshoot and hunting are likely to occur.
 以上より、本発明は、圧縮機の温度を適切に制御しつつ、過冷却も促進できる冷媒回路システムおよび冷媒回路システムの制御方法を提供することを目的とする。 Accordingly, an object of the present invention is to provide a refrigerant circuit system and a refrigerant circuit system control method that can promote supercooling while appropriately controlling the temperature of the compressor.
 本発明は、圧縮機、凝縮器、減圧部、および蒸発器を備える冷媒回路システムであって、冷媒回路システムは、さらに、凝縮器を通過した高圧冷媒と、蒸発器を通過した低圧冷媒とを熱交換させる気液熱交換器と、凝縮器から気液熱交換器へと向かう高圧冷媒の少なくとも一部を受け入れて減圧部よりも上流へと迂回させるバイパス経路と、バイパス経路へと流入する高圧冷媒の流量を調整可能な流量調整部と、流量調整部に流量に応じた指令を与える制御部と、を備え、制御部は、圧縮機から吐出される吐出冷媒の検知された温度に対応するエンタルピである吐出エンタルピがh1、気液熱交換器の入口の冷媒の検知された温度に対応するエンタルピと気液熱交換器の出口の冷媒の検知された温度に対応するエンタルピとの差であるエンタルピ差がΔh、圧縮機に許容される目標温度Tvに対応する目標吐出エンタルピがhv、h1およびΔhに基づいて、目標吐出エンタルピhvに適合する気液熱交換器の入口と出口とのエンタルピの差である適合エンタルピ差がΔh´であるとして、(Δh´/Δh)に基づいて、バイパス経路に流入させる高圧冷媒の流量の現在からの増減比率を決定することを特徴とする。 The present invention is a refrigerant circuit system including a compressor, a condenser, a decompression unit, and an evaporator. The refrigerant circuit system further includes a high-pressure refrigerant that has passed through the condenser and a low-pressure refrigerant that has passed through the evaporator. A gas-liquid heat exchanger that exchanges heat, a bypass path that accepts at least a portion of the high-pressure refrigerant that goes from the condenser to the gas-liquid heat exchanger, and bypasses it upstream from the decompression section, and a high pressure that flows into the bypass path A flow rate adjustment unit capable of adjusting the flow rate of the refrigerant, and a control unit that gives a command according to the flow rate to the flow rate adjustment unit, the control unit corresponding to the detected temperature of the discharged refrigerant discharged from the compressor The discharge enthalpy, which is the enthalpy, is h1, the difference between the enthalpy corresponding to the detected temperature of the refrigerant at the inlet of the gas-liquid heat exchanger and the enthalpy corresponding to the detected temperature of the refrigerant at the outlet of the gas-liquid heat exchanger En Based on hv, h1 and Δh, the target discharge enthalpy corresponding to the target discharge enthalpy hv is based on the enthalpy of the inlet and outlet of the gas-liquid heat exchanger corresponding to the target discharge enthalpy hv. Based on (Δh ′ / Δh), the increase / decrease ratio from the current flow rate of the high-pressure refrigerant flowing into the bypass path is determined on the assumption that the difference in compatible enthalpy, which is the difference, is Δh ′.
 本発明の冷媒回路システムでは、目標温度Tvを含み、上限温度および下限温度を有する目標温度範囲が設定されており、制御部は、下限温度に対応する下限吐出エンタルピから上限温度に対応する上限吐出エンタルピまでに目標吐出エンタルピhvを収めることが可能な適合エンタルピ差Δh´を取得することが好ましい。 In the refrigerant circuit system of the present invention, the target temperature range including the target temperature Tv and having the upper limit temperature and the lower limit temperature is set, and the control unit sets the upper limit discharge corresponding to the upper limit temperature from the lower limit discharge enthalpy corresponding to the lower limit temperature. It is preferable to obtain a suitable enthalpy difference Δh ′ that can accommodate the target discharge enthalpy hv by the enthalpy.
 本発明の冷媒回路システムは、冷媒の流れの向きを変更することで冷房運転と暖房運転とに切り替え可能な切替部と、冷房運転時に凝縮器として機能し、暖房運転時に蒸発器として機能する室外熱交換器と、冷房運転時に蒸発器として機能し、暖房運転時に凝縮器として機能する室内熱交換器と、冷房運転時に気液熱交換器と蒸発器との間に位置し、減圧部として機能する冷房時減圧部と、暖房運転時に気液熱交換器と蒸発器との間に位置し、減圧部として機能する暖房時減圧部と、を備えた空気調和機であることが好ましい。 The refrigerant circuit system of the present invention is an outdoor unit that functions as a condenser during cooling operation and functions as an evaporator during heating operation, by switching between cooling operation and heating operation by changing the direction of refrigerant flow. Positioned between the heat exchanger, the indoor heat exchanger that functions as an evaporator during cooling operation, and functions as a condenser during heating operation, and the gas-liquid heat exchanger and evaporator during cooling operation, and functions as a decompression unit Preferably, the air conditioner includes a cooling decompression unit, and a heating decompression unit that is located between the gas-liquid heat exchanger and the evaporator during heating operation and functions as a decompression unit.
 また、本発明は、圧縮機、凝縮器、減圧部、および蒸発器を備える冷媒回路システムの制御方法であって、冷媒回路システムは、さらに、凝縮器を通過した高圧冷媒と、蒸発器を通過した低圧冷媒とを熱交換させる気液熱交換器と、凝縮器から気液熱交換器へと向かう高圧冷媒の少なくとも一部を受け入れて減圧部よりも上流へと迂回させるバイパス経路と、バイパス経路へと流入する高圧冷媒の流量を調整可能な流量調整部と、を備えており、圧縮機から吐出される吐出冷媒の温度を検知するステップと、気液熱交換器の入口の冷媒の温度を検知するステップ、および気液熱交換器の出口の冷媒の温度を検知するステップと、吐出冷媒の検知された温度に対応するエンタルピである吐出エンタルピがh1、入口の冷媒の検知された温度に対応するエンタルピと出口の冷媒の検知された温度に対応するエンタルピとの差であるエンタルピ差がΔh、圧縮機に許容される目標温度Tvに対応する目標吐出エンタルピがhvであるとして、h1およびΔhに基づいて、目標吐出エンタルピhvに適合する気液熱交換器の入口と出口とのエンタルピの差である適合エンタルピ差Δh´を取得するステップと、(Δh´/Δh)に基づいて、バイパス経路に流入させる高圧冷媒の流量の現在からの増減比率を決定するステップと、を備えることを特徴とする。 The present invention is also a control method for a refrigerant circuit system including a compressor, a condenser, a decompression unit, and an evaporator, wherein the refrigerant circuit system further passes through the high-pressure refrigerant that has passed through the condenser and the evaporator. A gas-liquid heat exchanger for exchanging heat with the low-pressure refrigerant, a bypass path for accepting at least a part of the high-pressure refrigerant from the condenser to the gas-liquid heat exchanger, and bypassing upstream of the decompression unit, and a bypass path A flow rate adjustment unit capable of adjusting the flow rate of the high-pressure refrigerant flowing into the compressor, and detecting the temperature of the refrigerant discharged from the compressor; and the temperature of the refrigerant at the inlet of the gas-liquid heat exchanger The step of detecting, the step of detecting the temperature of the refrigerant at the outlet of the gas-liquid heat exchanger, and the discharge enthalpy corresponding to the detected temperature of the discharged refrigerant is h1, the detected temperature of the refrigerant at the inlet Assuming that the enthalpy difference that is the difference between the corresponding enthalpy and the enthalpy corresponding to the detected temperature of the refrigerant at the outlet is Δh, and the target discharge enthalpy corresponding to the target temperature Tv allowed for the compressor is hv, h1 and Δh Obtaining a matching enthalpy difference Δh ′, which is a difference in enthalpy between the inlet and the outlet of the gas-liquid heat exchanger that matches the target discharge enthalpy hv, and a bypass path based on (Δh ′ / Δh) And a step of determining an increase / decrease ratio from the present of the flow rate of the high-pressure refrigerant to be introduced into the vehicle.
 本発明の冷媒回路システムの制御方法では、目標温度Tvを含み、上限温度および下限温度を有する目標温度範囲が設定されており、Δh´を取得するステップでは、下限温度に対応する下限吐出エンタルピから上限温度に対応する上限吐出エンタルピまでに目標吐出エンタルピhvを収めることが可能な適合エンタルピ差Δh´を取得することが好ましい。 In the control method of the refrigerant circuit system of the present invention, the target temperature range including the target temperature Tv and having the upper limit temperature and the lower limit temperature is set, and in the step of obtaining Δh ′, from the lower limit discharge enthalpy corresponding to the lower limit temperature It is preferable to obtain a suitable enthalpy difference Δh ′ that can accommodate the target discharge enthalpy hv by the upper limit discharge enthalpy corresponding to the upper limit temperature.
 気液熱交換器による過冷却の効果に相当するエンタルピ差Δhと、吐出冷媒の温度に対応する吐出エンタルピh1との関係から、吐出冷媒の温度が目標温度Tvに収まるように導いた(Δh´/Δh)に基づいて流量調整部によりバイパスさせる流量を変更する制御を行うことにより、吐出冷媒の温度を抑えつつ、過冷却を促進して性能向上を図ることができる。
 本発明によれば、気液熱交換器による熱交換量の効果の大きさの現在と将来の比(Δh´/Δh)に基づいて、気液熱交換器を流れる冷媒とバイパス経路を流れる冷媒との流量の比を変更することにより、圧縮機の適度な応答を得て、吐出冷媒の温度を目標温度Tvに早期に安定させることができる。
From the relationship between the enthalpy difference Δh corresponding to the effect of supercooling by the gas-liquid heat exchanger and the discharge enthalpy h1 corresponding to the temperature of the discharged refrigerant, the temperature of the discharged refrigerant is derived so as to be within the target temperature Tv (Δh ′ By controlling the flow rate to be bypassed by the flow rate adjustment unit based on / Δh), it is possible to promote supercooling and improve performance while suppressing the temperature of the discharged refrigerant.
According to the present invention, the refrigerant flowing through the gas-liquid heat exchanger and the refrigerant flowing through the bypass path based on the present and future ratio (Δh ′ / Δh) of the magnitude of the effect of the heat exchange amount by the gas-liquid heat exchanger. By changing the flow rate ratio, an appropriate response of the compressor can be obtained, and the temperature of the discharged refrigerant can be quickly stabilized at the target temperature Tv.
本発明の実施形態に係る冷媒回路システムの構成を示す図である。It is a figure which shows the structure of the refrigerant circuit system which concerns on embodiment of this invention. 気液熱交換器による過冷却の作用を示すp-h線図である。It is a ph diagram which shows the effect | action of the supercooling by a gas-liquid heat exchanger. バイパスさせる高圧冷媒の流量制御量を得るための制御のフローを示す図である。It is a figure which shows the flow of control for obtaining the flow control amount of the high-pressure refrigerant to bypass. 吐出冷媒の温度に対する制御のイメージを表す図である。It is a figure showing the image of control with respect to the temperature of a discharge refrigerant | coolant. 本発明の変形例に係る冷媒回路システムの構成を示す図である。It is a figure which shows the structure of the refrigerant circuit system which concerns on the modification of this invention.
 以下、添付図面を参照しながら、本発明の実施形態について説明する。
〔第1実施形態〕
 図1に示す冷媒回路システム1は、冷媒が循環する冷媒回路を備えている。冷媒回路システム1は、冷凍サイクルを利用する空気調和機であり、室外の空気と冷媒とを熱交換させる室外熱交換器11を有する図示しない室外ユニットと、室内の空気と冷媒とを熱交換させる室内熱交換器12を有する図示しない室内ユニットとを備えている。
Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.
[First Embodiment]
A refrigerant circuit system 1 shown in FIG. 1 includes a refrigerant circuit through which refrigerant circulates. The refrigerant circuit system 1 is an air conditioner that uses a refrigeration cycle, and exchanges heat between an outdoor unit (not shown) having an outdoor heat exchanger 11 that exchanges heat between outdoor air and refrigerant, and indoor air and refrigerant. And an indoor unit (not shown) having the indoor heat exchanger 12.
 冷媒回路システム1は、循環する冷媒の流れの向きを切り替え可能な四方弁13を備えており、四方弁13を操作することで冷房運転と暖房運転とに切り替え可能に構成されている。図1には、冷房時の冷媒の流れを実線の矢印で示している。暖房時には、四方弁13に示したAの経路が閉じる代わりに、破線で示したBの経路が開くことで、冷房時とは逆の向きに冷媒が流れる(図1の破線の矢印)。 The refrigerant circuit system 1 includes a four-way valve 13 capable of switching the direction of the circulating refrigerant flow, and is configured to be switched between a cooling operation and a heating operation by operating the four-way valve 13. In FIG. 1, the refrigerant flow during cooling is indicated by solid arrows. At the time of heating, instead of closing the path A shown in the four-way valve 13, the path B shown by a broken line is opened, so that the refrigerant flows in the direction opposite to that during cooling (broken arrow in FIG. 1).
 室外熱交換器11は、冷房運転時には凝縮器として機能し、暖房運転時には蒸発器として機能する。室内熱交換器12は、冷房運転時には蒸発器として機能し、暖房運転時には凝縮器として機能する。室外熱交換器11に送風するファン11Fと、室内熱交換器12に向けて送風するファン12Fが、冷媒回路システム1に備わっている。
 図1に示した室外熱交換器11および室内熱交換器12には、冷房運転時の機能として、それぞれ、凝縮器、蒸発器と付記している。
 以下、冷房時を基準として、室外熱交換器11のことを凝縮器11と称し、室内熱交換器12のことを蒸発器12と称する。
The outdoor heat exchanger 11 functions as a condenser during the cooling operation, and functions as an evaporator during the heating operation. The indoor heat exchanger 12 functions as an evaporator during cooling operation, and functions as a condenser during heating operation. The refrigerant circuit system 1 includes a fan 11 </ b> F that blows air to the outdoor heat exchanger 11 and a fan 12 </ b> F that blows air toward the indoor heat exchanger 12.
The outdoor heat exchanger 11 and the indoor heat exchanger 12 shown in FIG. 1 are denoted as a condenser and an evaporator, respectively, as functions during cooling operation.
Hereinafter, the outdoor heat exchanger 11 is referred to as a condenser 11 and the indoor heat exchanger 12 is referred to as an evaporator 12 on the basis of cooling.
 冷媒回路システム1は、基本的な要素として、圧縮機14と、凝縮器11と、減圧部15(151,152)と、蒸発器12とを備えている。減圧部15として、冷房運転用の減圧部151と、暖房運転用の減圧部152との2つが用意されている。冷房運転用の減圧部151は暖房運転時には機能しない。同様に、暖房運転用の減圧部152は冷房運転時には機能しない。 The refrigerant circuit system 1 includes a compressor 14, a condenser 11, a decompression unit 15 (151, 152), and an evaporator 12 as basic elements. As the decompression unit 15, two decompression units 151 for cooling operation and decompression unit 152 for heating operation are prepared. The decompression unit 151 for cooling operation does not function during heating operation. Similarly, the decompression unit 152 for heating operation does not function during the cooling operation.
 冷媒回路システム1は、上記の基本的な要素に加えて、蒸発器12を通過した低圧冷媒と、凝縮器11を通過した高圧冷媒とを熱交換させる気液熱交換器20と、気液熱交換器20へと向かう高圧冷媒の一部を減圧部151よりも上流へと迂回させるバイパス経路21と、バイパス経路21へと流入する高圧冷媒の流量を調整可能なバイパス弁22と、バイパス弁22に開度を与える制御部25とを備えている。 In addition to the above basic elements, the refrigerant circuit system 1 includes a gas-liquid heat exchanger 20 that exchanges heat between the low-pressure refrigerant that has passed through the evaporator 12 and the high-pressure refrigerant that has passed through the condenser 11, and gas-liquid heat. A bypass path 21 that bypasses part of the high-pressure refrigerant that goes to the exchanger 20 to the upstream side of the decompression unit 151, a bypass valve 22 that can adjust the flow rate of the high-pressure refrigerant that flows into the bypass path 21, and the bypass valve 22 And a control unit 25 for giving an opening degree.
 気液熱交換器20は、高圧冷媒が流れる高圧経路201と、低圧冷媒が流れる低圧経路202とを備え、高圧経路201を流れる高圧冷媒と低圧経路202を流れる低圧冷媒とが熱交換可能に構成されている。
 バイパス経路21は、高圧経路201よりも上流から高圧冷媒の一部を受け入れ、高圧経路201よりも下流でかつ減圧部151よりも上流へと迂回させる。
The gas-liquid heat exchanger 20 includes a high-pressure path 201 through which a high-pressure refrigerant flows and a low-pressure path 202 through which a low-pressure refrigerant flows. The high-pressure refrigerant flowing through the high-pressure path 201 and the low-pressure refrigerant flowing through the low-pressure path 202 can exchange heat. Has been.
The bypass path 21 receives a part of the high-pressure refrigerant from the upstream side of the high-pressure path 201 and makes a bypass downstream of the high-pressure path 201 and upstream of the decompression unit 151.
 凝縮器11を通過して気液熱交換器20内へと流入した高圧冷媒は、図2に100で示すように、低圧冷媒へと放熱されることで過冷却され、エンタルピが下がる。その後、減圧部151により減圧され、蒸発器12へと流れる。
 気液熱交換器20により高圧冷媒が過冷却される一方で、図2に101で示すように、蒸発器12を経た低温低圧の冷媒が高圧冷媒から吸熱して過熱される。そうすると、圧縮機14へと吸入される冷媒の温度が上昇することとなる。
The high-pressure refrigerant that has flowed into the gas-liquid heat exchanger 20 through the condenser 11 is supercooled by radiating heat to the low-pressure refrigerant, as indicated by 100 in FIG. 2, and the enthalpy is lowered. Thereafter, the pressure is reduced by the pressure reducing unit 151 and flows to the evaporator 12.
While the high-pressure refrigerant is supercooled by the gas-liquid heat exchanger 20, the low-temperature and low-pressure refrigerant that has passed through the evaporator 12 absorbs heat from the high-pressure refrigerant and is overheated as indicated by 101 in FIG. If it does so, the temperature of the refrigerant | coolant suck | inhaled by the compressor 14 will rise.
 圧縮機14の摺動部に用いられる潤滑油の性能や、圧縮機14に電動機が内蔵されている場合は電動機の性能も考慮して、圧縮機14に許容される所定の目標温度Tvを定めることができる。
 本実施形態では、圧縮機14により圧縮された冷媒を圧縮機14の外部へと吐出する吐出管を流れている冷媒の温度である目標温度Tvを定めている。この目標温度Tvを含み、上限温度Xおよび下限温度X-αを含む目標温度範囲が設定されている。
The predetermined target temperature Tv allowed for the compressor 14 is determined in consideration of the performance of the lubricating oil used for the sliding portion of the compressor 14 and the performance of the motor when the motor is built in the compressor 14. be able to.
In the present embodiment, a target temperature Tv that is the temperature of the refrigerant flowing through the discharge pipe that discharges the refrigerant compressed by the compressor 14 to the outside of the compressor 14 is determined. A target temperature range including the target temperature Tv and including the upper limit temperature X and the lower limit temperature X-α is set.
 本実施形態は、気液熱交換器20により、可能な限り過冷却の効果を得つつ、圧縮機14の温度を下限温度X-αから上限温度Xまでに収めるため、バイパス経路21およびバイパス弁22を使用し、バイパス経路21を流れる高圧冷媒の流量を調整する。制御部25からバイパス弁22へと流量に応じた開度指令を与えると、開度指令に応じてバイパス弁22の開度量が変更されることで、バイパス経路21を流れる冷媒の流量が調整される。
 凝縮器11を経た高圧冷媒は、液相が優位であるため、冷媒ガスの流量を調整する場合に比べて容易にかつ確実に流量を調整できる。
In this embodiment, the temperature of the compressor 14 is kept from the lower limit temperature X-α to the upper limit temperature X while obtaining the supercooling effect as much as possible by the gas-liquid heat exchanger 20. 22 is used to adjust the flow rate of the high-pressure refrigerant flowing through the bypass path 21. When an opening degree command according to the flow rate is given from the control unit 25 to the bypass valve 22, the opening amount of the bypass valve 22 is changed according to the opening degree command, so that the flow rate of the refrigerant flowing through the bypass path 21 is adjusted. The
Since the high-pressure refrigerant that has passed through the condenser 11 has a superior liquid phase, the flow rate can be easily and reliably adjusted as compared with the case where the flow rate of the refrigerant gas is adjusted.
 バイパス経路21へと流入する冷媒流量を調整するため、高圧冷媒の圧力および温度と、気液熱交換器20の入口の冷媒温度と、気液熱交換器20の出口の冷媒温度とを用いてそれぞれ導いたエンタルピについて、制御部25は演算を行う。 In order to adjust the flow rate of the refrigerant flowing into the bypass path 21, the pressure and temperature of the high-pressure refrigerant, the refrigerant temperature at the inlet of the gas-liquid heat exchanger 20, and the refrigerant temperature at the outlet of the gas-liquid heat exchanger 20 are used. For each enthalpy derived, the control unit 25 performs a calculation.
 エンタルピを導くため、本実施形態の冷媒回路システム1には、凝縮器温度センサ11Aと、吐出温度センサ14Aと、入口温度センサ20Aと、出口温度センサ20Bとが備えられている。 In order to guide enthalpy, the refrigerant circuit system 1 of the present embodiment includes a condenser temperature sensor 11A, a discharge temperature sensor 14A, an inlet temperature sensor 20A, and an outlet temperature sensor 20B.
 凝縮器温度センサ11Aは、凝縮器11を流れる気液二相の冷媒の温度を検知する。この凝縮器温度センサ11Aにより検知された温度を飽和蒸気の温度とみなし、それに対応する飽和蒸気圧として、高圧冷媒の圧力を得ることができる。
 室外ユニットに、高圧冷媒の圧力を示す圧力計が備えられている場合は、その圧力計により計測された値を高圧冷媒の圧力として用いることができる。
 なお、冷媒回路システム1には、暖房運転時における制御のため、暖房運転時に凝縮器として機能する室内熱交換器12を流れる気液二相の冷媒の温度を検知する温度センサ12Aも備えられている。暖房運転時には、この温度センサ12Aにより検知された温度を用いて、高圧冷媒の圧力を得ることができる。
The condenser temperature sensor 11 </ b> A detects the temperature of the gas-liquid two-phase refrigerant flowing through the condenser 11. The temperature detected by the condenser temperature sensor 11A is regarded as the temperature of the saturated vapor, and the pressure of the high-pressure refrigerant can be obtained as the corresponding saturated vapor pressure.
When the outdoor unit is provided with a pressure gauge indicating the pressure of the high-pressure refrigerant, the value measured by the pressure gauge can be used as the pressure of the high-pressure refrigerant.
The refrigerant circuit system 1 is also provided with a temperature sensor 12A for detecting the temperature of the gas-liquid two-phase refrigerant flowing through the indoor heat exchanger 12 that functions as a condenser during the heating operation for control during the heating operation. Yes. During the heating operation, the pressure of the high-pressure refrigerant can be obtained using the temperature detected by the temperature sensor 12A.
 吐出温度センサ14Aは、圧縮機14の吐出管を流れる冷媒(以下、吐出冷媒)の温度を検知する。
 入口温度センサ20Aは、気液熱交換器20の入口に流入する高圧冷媒の温度を検知する。
 出口温度センサ20Bは、気液熱交換器20の出口から流出する高圧冷媒の温度を検知する。
The discharge temperature sensor 14 </ b> A detects the temperature of refrigerant (hereinafter referred to as discharge refrigerant) flowing through the discharge pipe of the compressor 14.
The inlet temperature sensor 20 </ b> A detects the temperature of the high-pressure refrigerant that flows into the inlet of the gas-liquid heat exchanger 20.
The outlet temperature sensor 20 </ b> B detects the temperature of the high-pressure refrigerant that flows out from the outlet of the gas-liquid heat exchanger 20.
 制御部25による処理の一例を説明する。
 制御部25は、凝縮器温度センサ11Aによる計測値に基づく、あるいは圧力計により得られた高圧冷媒の圧力と、吐出温度センサ14Aにより検知された吐出冷媒の温度Tdとを用いて、吐出冷媒のエンタルピであるh1を取得する。
 また、入口温度センサ20Aにより検知された温度と高圧冷媒の圧力を用いて、気液熱交換器20の入口における冷媒のエンタルピh2を取得し、さらに、出口温度センサ20Bにより検知された温度と高圧冷媒の圧力を用いて、気液熱交換器20の出口における冷媒のエンタルピh3を取得する。
 こうして取得した入口のエンタルピh2と出口のエンタルピh3を用いて、h2-h3の演算より、エンタルピ差Δhを取得する。これは、気液熱交換器20による高圧冷媒の過冷却の効果に相当し、換言すれば、低圧冷媒の過熱の効果に相当する。
An example of processing by the control unit 25 will be described.
The control unit 25 uses the pressure of the high-pressure refrigerant based on the measurement value by the condenser temperature sensor 11A or obtained by the pressure gauge and the temperature Td of the discharge refrigerant detected by the discharge temperature sensor 14A to Get h1 which is enthalpy.
Further, the enthalpy h2 of the refrigerant at the inlet of the gas-liquid heat exchanger 20 is obtained using the temperature detected by the inlet temperature sensor 20A and the pressure of the high-pressure refrigerant, and further, the temperature and high pressure detected by the outlet temperature sensor 20B. The refrigerant enthalpy h3 at the outlet of the gas-liquid heat exchanger 20 is acquired using the refrigerant pressure.
Using the enthalpy h2 at the entrance and the enthalpy h3 at the exit obtained in this way, the enthalpy difference Δh is obtained by the calculation of h2−h3. This corresponds to the effect of supercooling of the high-pressure refrigerant by the gas-liquid heat exchanger 20, in other words, the effect of overheating of the low-pressure refrigerant.
 バイパス経路21へと高圧冷媒を迂回させると、迂回させた流量の比の分だけ、気液熱交換器20による過冷却および過熱の効果が減少するので、気液熱交換器20において高圧冷媒から放熱されることに伴う低圧冷媒の温度上昇が抑制される。すると、圧縮機14へと吸入される低圧冷媒の温度が低下するので、圧縮機14の内部の温度を抑えることが可能となる。 When the high-pressure refrigerant is diverted to the bypass path 21, the effect of supercooling and overheating by the gas-liquid heat exchanger 20 is reduced by the ratio of the diverted flow rate. An increase in the temperature of the low-pressure refrigerant accompanying heat dissipation is suppressed. Then, since the temperature of the low-pressure refrigerant sucked into the compressor 14 is lowered, it becomes possible to suppress the temperature inside the compressor 14.
 検知されたエンタルピ差Δhは、現在、気液熱交換器20が低圧冷媒の温度を上昇させている効果を示している。そうすると、気液熱交換器20を高圧冷媒が流れない場合に検知されるであろう吐出冷媒の温度と高圧冷媒の圧力に対応する吐出エンタルピをh1´と置くと、現在の吐出エンタルピh1は、下記の式(1)で表せる。
 h1=h1´+Δh  ・・・(1)
 なお、気液熱交換器20を高圧冷媒が流れない場合というのは、本実施形態では、バイパス弁22の開度を全開にした場合に相当する。
The detected enthalpy difference Δh indicates the effect that the gas-liquid heat exchanger 20 is currently increasing the temperature of the low-pressure refrigerant. Then, when the discharge enthalpy corresponding to the temperature of the discharge refrigerant and the pressure of the high-pressure refrigerant that will be detected when the high-pressure refrigerant does not flow through the gas-liquid heat exchanger 20 is set as h1 ′, the current discharge enthalpy h1 is It can be expressed by the following formula (1).
h1 = h1 ′ + Δh (1)
The case where the high-pressure refrigerant does not flow through the gas-liquid heat exchanger 20 corresponds to the case where the opening degree of the bypass valve 22 is fully opened in the present embodiment.
 高圧冷媒の圧力が安定していると、エンタルピ差ΔhがΔh´へと変更されたならば、それに倣って吐出エンタルピh1が変化する。
 したがって、圧縮機14に許容される吐出冷媒の目標温度Tvに対応する目標吐出エンタルピhvは、気液熱交換によるエンタルピ差をΔh´と置いて、下記の式(2)で表せる。
 hv=h1´+Δh´  ・・・(2)
When the pressure of the high-pressure refrigerant is stable, if the enthalpy difference Δh is changed to Δh ′, the discharge enthalpy h1 changes accordingly.
Therefore, the target discharge enthalpy hv corresponding to the target temperature Tv of the discharge refrigerant allowed for the compressor 14 can be expressed by the following equation (2), where the enthalpy difference due to gas-liquid heat exchange is set as Δh ′.
hv = h1 ′ + Δh ′ (2)
 上記の式(2)より、Δh´は、目標吐出エンタルピhvに適合する適合エンタルピ差である。制御部25により、hv-h1´を演算してΔh´を割り出すことができる。
 このΔh´と、検知された温度に基づく現在のエンタルピ差Δhとの比から、制御部25は、バイパス経路21を通じてバイパスさせる冷媒流量の制御量を得て、バイパス弁22に開度として与える。
 つまり、目標吐出エンタルピhvに適合する適合エンタルピ差Δh´を実現するため、制御部25は、現在の(Δh´/Δh)の比に基づいて、バイパス経路21に流入させる高圧冷媒の流量の現在からの増減比率を決定し、増減比率を乗じた流量に対応する開度指令をバイパス弁22に与える。
From the above equation (2), Δh ′ is a suitable enthalpy difference that matches the target discharge enthalpy hv. The control unit 25 can calculate Δh ′ by calculating hv−h1 ′.
From the ratio between this Δh ′ and the current enthalpy difference Δh based on the detected temperature, the control unit 25 obtains a control amount of the refrigerant flow rate to be bypassed through the bypass path 21 and gives it to the bypass valve 22 as an opening degree.
That is, in order to realize the suitable enthalpy difference Δh ′ that matches the target discharge enthalpy hv, the control unit 25 presents the current flow rate of the high-pressure refrigerant that flows into the bypass path 21 based on the current ratio (Δh ′ / Δh). An opening / closing command corresponding to the flow rate multiplied by the increasing / decreasing ratio is given to the bypass valve 22.
 後述するように、目標温度Tvを含む所定温度範囲内に吐出冷媒の温度が収まるように、目標吐出エンタルピhvに幅を持たせ、そのエンタルピの上限から下限までに適合するようにΔh´を割り出すことが好ましい。 As will be described later, the target discharge enthalpy hv is widened so that the temperature of the discharged refrigerant falls within a predetermined temperature range including the target temperature Tv, and Δh ′ is calculated so as to fit from the upper limit to the lower limit of the enthalpy. It is preferable.
 制御部25による作用について、冷房運転時を例にとり説明したが、暖房運転時も同様である。
 暖房運転時には、四方弁13の切り替え操作により、圧縮機14、凝縮器としての室内熱交換器12、減圧部152、気液熱交換器20、蒸発器としての室外熱交換器11の順に冷媒が循環する。
 気液熱交換器20の入口と出口は冷房運転時とは逆になるため、気液熱交換器20における熱交換によるエンタルピ差Δhは、温度センサ20Bによる検知温度に対応するエンタルピh3から、温度センサ20Aによる検知温度に対応するエンタルピh2を引いた、h3-h2に相当する。
 エンタルピ差Δhがh3-h2に相当すること、そして、室内熱交換器12の温度センサ12Aにより検知された凝縮器温度に対応する高圧冷媒の圧力を用いて吐出エンタルピh1を取得することを除いて、冷房運転時と同様の処理を行うことができる。
The operation by the control unit 25 has been described by taking the cooling operation as an example, but the same applies to the heating operation.
During the heating operation, the switching operation of the four-way valve 13 causes the refrigerant to flow in the order of the compressor 14, the indoor heat exchanger 12 as a condenser, the decompression unit 152, the gas-liquid heat exchanger 20, and the outdoor heat exchanger 11 as an evaporator. Circulate.
Since the inlet and outlet of the gas-liquid heat exchanger 20 are opposite to those during cooling operation, the enthalpy difference Δh due to heat exchange in the gas-liquid heat exchanger 20 is determined from the enthalpy h3 corresponding to the temperature detected by the temperature sensor 20B. This corresponds to h3-h2 obtained by subtracting enthalpy h2 corresponding to the temperature detected by sensor 20A.
Except that the enthalpy difference Δh corresponds to h3−h2, and the discharge enthalpy h1 is obtained using the pressure of the high-pressure refrigerant corresponding to the condenser temperature detected by the temperature sensor 12A of the indoor heat exchanger 12. The same processing as in the cooling operation can be performed.
 以下、図3を参照し、制御部25により行われる制御の手順の例について説明する。以下では、(Δh´/Δh)のことをΔGrと称する。ΔGrは、気液熱交換器20による熱交換量の増減倍率に相当する。 Hereinafter, an example of a control procedure performed by the control unit 25 will be described with reference to FIG. Hereinafter, (Δh ′ / Δh) is referred to as ΔGr. ΔGr corresponds to an increase / decrease magnification of the heat exchange amount by the gas-liquid heat exchanger 20.
 冷媒回路システム1の冷房運転あるいは暖房運転が行われる間に亘り、制御部25は、図3に示す手順で演算し、算出したΔGrに基づいてバイパス弁22の開度を変更する。
 圧縮機14の温度の制約の下、可能な限り気液熱交換器20に高圧冷媒を流して過冷却を促進させることが好ましい。本実施形態では、バイパス弁22を全閉にした状態で運転を開始する。
 冷房運転時には、まず、上述したように、凝縮器温度センサ11Aを使用しあるいは圧力計により得られた高圧冷媒の圧力と、吐出温度センサ14Aにより検知された吐出冷媒の温度Tdとを用いて、吐出エンタルピh1を取得する(ステップS1)。
While the cooling operation or the heating operation of the refrigerant circuit system 1 is performed, the control unit 25 calculates according to the procedure shown in FIG. 3 and changes the opening degree of the bypass valve 22 based on the calculated ΔGr.
Under the restriction of the temperature of the compressor 14, it is preferable to promote supercooling by flowing a high-pressure refrigerant through the gas-liquid heat exchanger 20 as much as possible. In the present embodiment, the operation is started with the bypass valve 22 fully closed.
During the cooling operation, first, as described above, the pressure of the high-pressure refrigerant obtained by using the condenser temperature sensor 11A or the pressure gauge and the temperature Td of the discharged refrigerant detected by the discharge temperature sensor 14A are used. A discharge enthalpy h1 is acquired (step S1).
 次に、温度センサ20A,20Bによりそれぞれ検知される温度を用いて、気液熱交換器20の入口の冷媒のエンタルピh2と、出口の冷媒のエンタルピh3とを取得し、気液熱交換によるエンタルピ差Δhを算出する(ステップS2)。 Next, using the temperatures detected by the temperature sensors 20A and 20B, the enthalpy h2 of the refrigerant at the inlet of the gas-liquid heat exchanger 20 and the enthalpy h3 of the refrigerant at the outlet are acquired, and enthalpy by gas-liquid heat exchange is obtained. The difference Δh is calculated (step S2).
 次に、吐出冷媒の温度を目標温度Tvに収めるために必要な気液熱交換器20の熱交換量に相当するエンタルピ差Δh´を算出する(ステップS3)。
 ここでは、閾値を使用して目標温度範囲を設定する。この目標温度範囲は、目標温度Tvを含み、上限温度Xと、下限温度(X-α)とを有している。上限温度Xに対応する上限吐出エンタルピと、下限温度(X-α)に対応する下限吐出エンタルピとにより、目標吐出エンタルピhvを含むエンタルピ範囲も設定される。
Next, an enthalpy difference Δh ′ corresponding to the heat exchange amount of the gas-liquid heat exchanger 20 necessary for keeping the temperature of the discharged refrigerant at the target temperature Tv is calculated (step S3).
Here, the target temperature range is set using a threshold value. This target temperature range includes the target temperature Tv, and has an upper limit temperature X and a lower limit temperature (X−α). An enthalpy range including the target discharge enthalpy hv is set by the upper limit discharge enthalpy corresponding to the upper limit temperature X and the lower limit discharge enthalpy corresponding to the lower limit temperature (X−α).
 制御部25は、温度(X-α)に対応する下限エンタルピ以上、温度Xに対応する上限エンタルピ以下に目標吐出エンタルピhvが収まるように、気液熱交換器20を高圧冷媒が流れない場合の吐出エンタルピh1´に加えることが許容されるΔh´を算出する。 When the high pressure refrigerant does not flow through the gas-liquid heat exchanger 20, the control unit 25 makes the target discharge enthalpy hv fall within the upper limit enthalpy corresponding to the temperature (X−α) and lower than the upper limit enthalpy corresponding to the temperature X. Δh ′ allowed to be added to the discharge enthalpy h1 ′ is calculated.
 Δh´を算出したならば、Δh´と、Δhとの比(Δh´/Δh)を気液熱交換量の増減倍率ΔGrとして算出する(ステップS4)。
 ΔGrが1よりも小さければ、吐出冷媒の温度を抑制するため、気液熱交換器20を流れる高圧冷媒の流量を現在よりも減らす必要がある。逆に、ΔGrが1よりも大きければ、圧縮機14の許容温度に対して吐出冷媒の温度が下回っているため、気液熱交換器20を流れる高圧冷媒の流量を現在よりも増やし、高圧冷媒の液化を促進する余地がある。
When Δh ′ is calculated, the ratio (Δh ′ / Δh) between Δh ′ and Δh is calculated as the increase / decrease magnification ΔGr of the gas-liquid heat exchange amount (step S4).
If ΔGr is smaller than 1, it is necessary to reduce the flow rate of the high-pressure refrigerant flowing through the gas-liquid heat exchanger 20 in order to suppress the temperature of the discharged refrigerant. On the other hand, if ΔGr is greater than 1, the temperature of the discharged refrigerant is lower than the allowable temperature of the compressor 14, so the flow rate of the high-pressure refrigerant flowing through the gas-liquid heat exchanger 20 is increased from the current level. There is room to promote liquefaction of
 したがって、算出されたΔGrに応じて、下記の手順によりバイパス弁22の開度を変更することができる。
 例えば、ΔGrが1よりも小さい場合は(ステップS5でY)、バイパス弁22の開度が全開でない限りは(ステップS6でN)、気液熱交換器20を流れる高圧冷媒の流量を減らすため、バイパス弁22に開度を大きくする開度指令を与える(ステップS7)。すると、開度指令に基づいて、現在の(1/ΔGr)倍に相当する開度量にバイパス弁22が駆動される。例えば、単位時間あたりのパルス数が現在の約(1/ΔGr)倍である駆動パルスによりバイパス弁22が駆動される。
 なお、現在バイパス弁22が全閉されているため現在のパルス数が0であってもバイパス弁22を開くことができるように、例えば、最小のパルス数を0.01等と定めておく。
Therefore, the opening degree of the bypass valve 22 can be changed according to the following procedure according to the calculated ΔGr.
For example, when ΔGr is smaller than 1 (Y in step S5), the flow rate of the high-pressure refrigerant flowing through the gas-liquid heat exchanger 20 is reduced unless the opening degree of the bypass valve 22 is fully open (N in step S6). Then, an opening degree command for increasing the opening degree is given to the bypass valve 22 (step S7). Then, the bypass valve 22 is driven to an opening amount corresponding to the current (1 / ΔGr) times based on the opening command. For example, the bypass valve 22 is driven by a driving pulse whose number of pulses per unit time is about (1 / ΔGr) times the current time.
For example, the minimum pulse number is set to 0.01 or the like so that the bypass valve 22 can be opened even if the current pulse number is 0 because the bypass valve 22 is fully closed.
 また、ΔGrが1よりも大きい場合は(ステップS8でY)、バイパス弁22の開度が全閉でない限りは(ステップS9でN)、気液熱交換器20を流れる高圧冷媒の流量を増やすため、バイパス弁22に開度を小さくする開度指令を与える(ステップS10)。 When ΔGr is greater than 1 (Y in step S8), the flow rate of the high-pressure refrigerant flowing through the gas-liquid heat exchanger 20 is increased unless the opening degree of the bypass valve 22 is fully closed (N in step S9). Therefore, an opening degree command for reducing the opening degree is given to the bypass valve 22 (step S10).
 そして、ΔGr=1である場合は(ステップS11)、気液熱交換器20による熱交換量が目標温度Tvに適合しているため、バイパス弁22の開度を現在のまま維持する。 If ΔGr = 1 (step S11), the heat exchange amount by the gas-liquid heat exchanger 20 is adapted to the target temperature Tv, so the opening degree of the bypass valve 22 is maintained as it is.
 以上で説明した本実施形態によれば、気液熱交換器20による過冷却の効果に相当するエンタルピ差Δhと、吐出冷媒の温度Tdに対応する吐出エンタルピh1との関係から、吐出冷媒の温度が目標温度Tvに収まるように導いたΔGrに基づいて、バイパス弁22の開度を変更させる制御を行うことにより、吐出冷媒の温度を抑えつつ、過冷却を促進して空気調和機の性能向上を図ることができる。 According to the present embodiment described above, the temperature of the discharged refrigerant is determined from the relationship between the enthalpy difference Δh corresponding to the effect of supercooling by the gas-liquid heat exchanger 20 and the discharge enthalpy h1 corresponding to the temperature Td of the discharged refrigerant. Is controlled to change the opening degree of the bypass valve 22 based on ΔGr derived so as to be within the target temperature Tv, thereby suppressing the temperature of the discharged refrigerant and promoting supercooling to improve the performance of the air conditioner Can be achieved.
 加えて、バイパス経路21へと迂回した高圧冷媒を減圧部151よりも上流へと流入させているため、バイパスさせた高圧冷媒を圧縮機14の前へと流入させる場合とは違って蒸発器12への冷媒循環量が減少することもなく、蒸発器12の熱交換性能を維持することができる。 In addition, since the high-pressure refrigerant that has bypassed the bypass path 21 is caused to flow upstream from the decompression unit 151, unlike the case where the bypassed high-pressure refrigerant is caused to flow before the compressor 14, the evaporator 12. The heat exchange performance of the evaporator 12 can be maintained without reducing the amount of refrigerant circulating to the evaporator.
 本実施形態では、気液熱交換器20による熱交換量の効果の大きさの現在と将来の比(Δh´/Δh)に基づいて、気液熱交換器20を流れる冷媒とバイパス経路21を流れる冷媒との流量の比を変更することにより、圧縮機14の適度な応答を得て、吐出冷媒の温度を目標温度Tvに早期に安定させることができる。 In the present embodiment, based on the current and future ratio (Δh ′ / Δh) of the magnitude of the effect of the heat exchange amount by the gas-liquid heat exchanger 20, the refrigerant flowing through the gas-liquid heat exchanger 20 and the bypass path 21 are changed. By changing the ratio of the flow rate to the flowing refrigerant, an appropriate response of the compressor 14 can be obtained, and the temperature of the discharged refrigerant can be stabilized at the target temperature Tv at an early stage.
 図4に示す一点鎖線は、吐出冷媒の温度が圧縮機に許容される温度Tvを超過したためバイパス弁22によりバイパス流量を一度に下げた場合を示している。この場合、吐出冷媒の温度が過度に応答してオーバーシュートやハンチングが生じ易い。
 図4に示す破線は、吐出冷媒の温度が圧縮機14に許容される温度Tvを超過した際に、バイパス弁22によりバイパス流量を徐々に下げた場合を示している。この場合、バイパス流量が不足して吐出温度を許容温度Tvに下げることができない可能性がある。
 本実施形態の制御によれば、図4に太い実線で示すように、ΔGrの変更に伴う気液熱交換の効果の大きさの変化に対して吐出冷媒の温度が適度に追従するので、吐出冷媒の温度が目標温度Tvに早期に安定する。バイパスさせた冷媒を圧縮機14から離れている減圧部151の上流へと流入させているため、吐出冷媒の温度が過敏に応答するのを避けられることも、吐出温度の安定に寄与する。
The alternate long and short dash line in FIG. 4 shows a case where the bypass flow rate is reduced by the bypass valve 22 at a time because the temperature of the discharged refrigerant exceeds the temperature Tv allowed for the compressor. In this case, overshoot and hunting are likely to occur due to excessive response of the temperature of the discharged refrigerant.
The broken line shown in FIG. 4 shows the case where the bypass flow rate is gradually reduced by the bypass valve 22 when the temperature of the discharged refrigerant exceeds the temperature Tv allowed for the compressor 14. In this case, there is a possibility that the bypass flow rate is insufficient and the discharge temperature cannot be lowered to the allowable temperature Tv.
According to the control of the present embodiment, as shown by the thick solid line in FIG. 4, the temperature of the discharged refrigerant appropriately follows the change in the magnitude of the effect of gas-liquid heat exchange accompanying the change in ΔGr. The temperature of the refrigerant is quickly stabilized at the target temperature Tv. Since the bypassed refrigerant is allowed to flow upstream of the decompression unit 151 that is away from the compressor 14, it can be avoided that the temperature of the discharged refrigerant responds sensitively, which also contributes to the stability of the discharged temperature.
 本実施形態のバイパス弁22に代えて、図5に示すように、バイパス経路21へと流入する冷媒の流量を調整可能な流量調整部23を用いることもできる。
 冷房運転時に機能する図5の右側の流量調整部23および制御部25と、暖房運転時に機能する図5の左側の流量調整部23および制御部25とが切り替えて用いられる。
 流量調整部23は、必要によっては、凝縮器11を通過して気液熱交換器20へと向かう高圧冷媒の全量をバイパス経路21へと流入させることが可能である。高圧冷媒の全量がバイパス経路21へ流入すれば、高圧冷媒が気液熱交換器20を全く流れないため、高圧冷媒から低圧冷媒へと放熱させないで、低圧冷媒が吸入される圧縮機14の温度を抑えることができる。
 流量調整部23を用いる場合であっても、上記実施形態と同様の方法でエンタルピ差Δh´を制御部25により算出し、現在のΔh´/Δh倍のバイパス流量に対応する指令を流量調整部23に与えることにより、上記実施形態と同様の効果を得ることができる。
Instead of the bypass valve 22 of the present embodiment, as shown in FIG. 5, a flow rate adjusting unit 23 that can adjust the flow rate of the refrigerant flowing into the bypass path 21 can be used.
The flow rate adjustment unit 23 and the control unit 25 on the right side in FIG. 5 that function during the cooling operation and the left flow rate adjustment unit 23 and the control unit 25 in FIG. 5 that function during the heating operation are switched and used.
The flow rate adjusting unit 23 can cause the entire amount of the high-pressure refrigerant that passes through the condenser 11 and goes to the gas-liquid heat exchanger 20 to flow into the bypass path 21 as necessary. If the entire amount of the high-pressure refrigerant flows into the bypass path 21, the high-pressure refrigerant does not flow through the gas-liquid heat exchanger 20, so the heat of the compressor 14 into which the low-pressure refrigerant is sucked without radiating heat from the high-pressure refrigerant to the low-pressure refrigerant. Can be suppressed.
Even when the flow rate adjusting unit 23 is used, the control unit 25 calculates the enthalpy difference Δh ′ by the same method as in the above embodiment, and sends a command corresponding to the current Δh ′ / Δh times bypass flow rate to the flow rate adjusting unit. 23, the same effect as the above embodiment can be obtained.
 上記以外にも、本発明の主旨を逸脱しない限り、上記実施形態で挙げた構成を取捨選択したり、他の構成に適宜変更したりすることが可能である。 In addition to the above, the configurations described in the above embodiments can be selected or changed to other configurations as appropriate without departing from the gist of the present invention.
 本発明の冷媒回路システムは、冷房運転専用あるいは暖房運転専用のシステムとして構成することもできる。その場合は、四方弁13が必要なく、減圧部15は一つで足りる。また、凝縮器温度センサも、2つの熱交換器11,12のうち凝縮器として機能する一方にのみ用意すれば足りる。 The refrigerant circuit system of the present invention can be configured as a system exclusively for cooling operation or heating operation. In that case, the four-way valve 13 is not necessary and only one decompression unit 15 is sufficient. In addition, it is sufficient to prepare a condenser temperature sensor only for one of the two heat exchangers 11 and 12 that functions as a condenser.
 本発明の冷媒回路システムは、空気調和機の他、冷凍庫や給湯器等、冷凍サイクルを利用する適宜な機器に適用することができる。 The refrigerant circuit system of the present invention can be applied not only to an air conditioner but also to an appropriate device using a refrigeration cycle such as a freezer or a water heater.
1    冷媒回路システム
11   室外熱交換器(凝縮器/蒸発器)
11A  凝縮器温度センサ
12   室内熱交換器(蒸発器/凝縮器)
12A  温度センサ
13   四方弁
14   圧縮機
14A  吐出温度センサ
15   減圧部
151  減圧部(冷房時減圧部)
152  減圧部(暖房時減圧部)
20   気液熱交換器
20A,20B   温度センサ
21   バイパス経路
22   バイパス弁(流量調整部)
23   流量調整部
25   制御部
201  高圧経路
202  低圧経路
Td   温度
ΔGr  増減倍率
1 Refrigerant circuit system 11 Outdoor heat exchanger (condenser / evaporator)
11A Condenser temperature sensor 12 Indoor heat exchanger (evaporator / condenser)
12A Temperature sensor 13 Four-way valve 14 Compressor 14A Discharge temperature sensor 15 Decompression unit 151 Decompression unit (cooling decompression unit)
152 Pressure reducing part (Heating pressure reducing part)
20 Gas-liquid heat exchangers 20A and 20B Temperature sensor 21 Bypass path 22 Bypass valve (flow rate adjusting unit)
23 Flow control unit 25 Control unit 201 High pressure path 202 Low pressure path Td Temperature ΔGr Increase / decrease magnification

Claims (5)

  1.  圧縮機、凝縮器、減圧部、および蒸発器を備える冷媒回路システムであって、
     前記冷媒回路システムは、さらに、
     前記凝縮器を通過した高圧冷媒と、前記蒸発器を通過した低圧冷媒とを熱交換させる気液熱交換器と、
     前記凝縮器から前記気液熱交換器へと向かう前記高圧冷媒の少なくとも一部を受け入れて前記減圧部よりも上流へと迂回させるバイパス経路と、
     前記バイパス経路へと流入する前記高圧冷媒の流量を調整可能な流量調整部と、
     前記流量調整部に流量に応じた指令を与える制御部と、を備え、
     前記制御部は、
     前記圧縮機から吐出される吐出冷媒の検知された温度に対応するエンタルピである吐出エンタルピがh1、
     前記気液熱交換器の入口の冷媒の検知された温度に対応するエンタルピと前記気液熱交換器の出口の冷媒の検知された温度に対応するエンタルピとの差であるエンタルピ差がΔh、
     前記圧縮機に許容される目標温度Tvに対応する目標吐出エンタルピがhv、
     h1およびΔhに基づいて、前記目標吐出エンタルピhvに適合する前記気液熱交換器の入口と出口とのエンタルピの差である適合エンタルピ差がΔh´であるとして、
     (Δh´/Δh)に基づいて、前記バイパス経路に流入させる前記高圧冷媒の流量の現在からの増減比率を決定する、
    ことを特徴とする冷媒回路システム。
    A refrigerant circuit system comprising a compressor, a condenser, a decompression unit, and an evaporator,
    The refrigerant circuit system further includes:
    A gas-liquid heat exchanger that exchanges heat between the high-pressure refrigerant that has passed through the condenser and the low-pressure refrigerant that has passed through the evaporator;
    A bypass path that accepts at least a portion of the high-pressure refrigerant from the condenser toward the gas-liquid heat exchanger and bypasses the upstream of the decompression unit;
    A flow rate adjustment unit capable of adjusting the flow rate of the high-pressure refrigerant flowing into the bypass path;
    A control unit that gives a command according to the flow rate to the flow rate adjustment unit,
    The controller is
    A discharge enthalpy that is an enthalpy corresponding to the detected temperature of the refrigerant discharged from the compressor is h1,
    An enthalpy difference that is a difference between an enthalpy corresponding to the detected temperature of the refrigerant at the inlet of the gas-liquid heat exchanger and an enthalpy corresponding to the detected temperature of the refrigerant at the outlet of the gas-liquid heat exchanger is Δh,
    The target discharge enthalpy corresponding to the target temperature Tv allowed for the compressor is hv,
    Based on h1 and Δh, a matching enthalpy difference that is a difference in enthalpy between the inlet and outlet of the gas-liquid heat exchanger that matches the target discharge enthalpy hv is Δh ′,
    Based on (Δh ′ / Δh), a rate of increase / decrease from the current flow rate of the high-pressure refrigerant flowing into the bypass path is determined.
    A refrigerant circuit system characterized by that.
  2.  前記目標温度Tvを含み、上限温度および下限温度を有する目標温度範囲が設定されており、
     前記制御部は、前記下限温度に対応する下限吐出エンタルピから前記上限温度に対応する上限吐出エンタルピまでに前記目標吐出エンタルピhvを収めることが可能な前記適合エンタルピ差Δh´を取得する、
    請求項1に記載の冷媒回路システム。
    A target temperature range including the target temperature Tv and having an upper limit temperature and a lower limit temperature is set,
    The control unit obtains the adaptive enthalpy difference Δh ′ that can accommodate the target discharge enthalpy hv from a lower limit discharge enthalpy corresponding to the lower limit temperature to an upper limit discharge enthalpy corresponding to the upper limit temperature.
    The refrigerant circuit system according to claim 1.
  3.  冷媒の流れの向きを変更することで冷房運転と暖房運転とに切り替え可能な切替部と、
     前記冷房運転時に前記凝縮器として機能し、前記暖房運転時に前記蒸発器として機能する室外熱交換器と、
     前記冷房運転時に前記蒸発器として機能し、前記暖房運転時に前記凝縮器として機能する室内熱交換器と、
     前記冷房運転時に前記気液熱交換器と前記蒸発器との間に位置し、前記減圧部として機能する冷房時減圧部と、
     前記暖房運転時に前記気液熱交換器と前記蒸発器との間に位置し、前記減圧部として機能する暖房時減圧部と、を備えた空気調和機である、
    請求項1または2に記載の冷媒回路システム。
    A switching unit capable of switching between cooling operation and heating operation by changing the direction of the flow of the refrigerant;
    An outdoor heat exchanger that functions as the condenser during the cooling operation and functions as the evaporator during the heating operation;
    An indoor heat exchanger that functions as the evaporator during the cooling operation and functions as the condenser during the heating operation;
    A cooling decompression unit that is located between the gas-liquid heat exchanger and the evaporator during the cooling operation and functions as the decompression unit;
    An air conditioner including a heating decompression unit located between the gas-liquid heat exchanger and the evaporator during the heating operation and functioning as the decompression unit,
    The refrigerant circuit system according to claim 1 or 2.
  4.  圧縮機、凝縮器、減圧部、および蒸発器を備える冷媒回路システムの制御方法であって、
     前記冷媒回路システムは、さらに、
     前記凝縮器を通過した高圧冷媒と、前記蒸発器を通過した低圧冷媒とを熱交換させる気液熱交換器と、
     前記凝縮器から前記気液熱交換器へと向かう前記高圧冷媒の少なくとも一部を受け入れて前記減圧部よりも上流へと迂回させるバイパス経路と、
     前記バイパス経路へと流入する前記高圧冷媒の流量を調整可能な流量調整部と、を備えており、
     前記圧縮機から吐出される吐出冷媒の温度を検知するステップと、
     前記気液熱交換器の入口の冷媒の温度を検知するステップ、および前記気液熱交換器の出口の冷媒の温度を検知するステップと、
     前記吐出冷媒の検知された温度に対応するエンタルピである吐出エンタルピがh1、前記入口の冷媒の検知された温度に対応するエンタルピと前記出口の冷媒の検知された温度に対応するエンタルピとの差であるエンタルピ差がΔh、前記圧縮機に許容される目標温度Tvに対応する目標吐出エンタルピがhvであるとして、h1およびΔhに基づいて、前記目標吐出エンタルピhvに適合する前記気液熱交換器の入口と出口とのエンタルピの差である適合エンタルピ差Δh´を取得するステップと、
     (Δh´/Δh)に基づいて、前記バイパス経路に流入させる前記高圧冷媒の流量の現在からの増減比率を決定するステップと、を備える、
        ことを特徴とする冷媒回路システムの制御方法。
    A method for controlling a refrigerant circuit system including a compressor, a condenser, a decompression unit, and an evaporator,
    The refrigerant circuit system further includes:
    A gas-liquid heat exchanger that exchanges heat between the high-pressure refrigerant that has passed through the condenser and the low-pressure refrigerant that has passed through the evaporator;
    A bypass path that accepts at least a portion of the high-pressure refrigerant from the condenser toward the gas-liquid heat exchanger and bypasses the upstream of the decompression unit;
    A flow rate adjustment unit capable of adjusting the flow rate of the high-pressure refrigerant flowing into the bypass path,
    Detecting the temperature of the refrigerant discharged from the compressor;
    Detecting the temperature of the refrigerant at the inlet of the gas-liquid heat exchanger; and detecting the temperature of the refrigerant at the outlet of the gas-liquid heat exchanger;
    The discharge enthalpy that is the enthalpy corresponding to the detected temperature of the discharged refrigerant is h1, the difference between the enthalpy corresponding to the detected temperature of the refrigerant at the inlet and the enthalpy corresponding to the detected temperature of the refrigerant at the outlet Assuming that a certain enthalpy difference is Δh and a target discharge enthalpy corresponding to a target temperature Tv allowed for the compressor is hv, based on h1 and Δh, the gas-liquid heat exchanger that matches the target discharge enthalpy hv Obtaining a matching enthalpy difference Δh ′, which is the difference in enthalpy between the inlet and the outlet;
    Determining, based on (Δh ′ / Δh), an increase / decrease ratio from the current flow rate of the high-pressure refrigerant flowing into the bypass path,
    A control method for a refrigerant circuit system.
  5.  前記目標温度Tvを含み、上限温度および下限温度を有する目標温度範囲が設定されており、
     Δh´を取得する前記ステップでは、
     前記下限温度に対応する下限吐出エンタルピから前記上限温度に対応する上限吐出エンタルピまでに前記目標吐出エンタルピhvを収めることが可能な前記適合エンタルピ差Δh´を取得する、
    請求項4に記載の冷媒回路システムの制御方法。
    A target temperature range including the target temperature Tv and having an upper limit temperature and a lower limit temperature is set,
    In the step of obtaining Δh ′,
    Obtaining the adapted enthalpy difference Δh ′ capable of accommodating the target discharge enthalpy hv from the lower limit discharge enthalpy corresponding to the lower limit temperature to the upper limit discharge enthalpy corresponding to the upper limit temperature;
    The control method of the refrigerant circuit system of Claim 4.
PCT/JP2017/040965 2016-12-14 2017-11-14 Refrigerant circuit system and method for controlling refrigerant circuit system WO2018110185A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2016242022A JP6781034B2 (en) 2016-12-14 2016-12-14 Refrigerant circuit system and control method of refrigerant circuit system
JP2016-242022 2016-12-14

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP17881376.2A EP3460357A4 (en) 2016-12-14 2017-11-14 Refrigerant circuit system and method for controlling refrigerant circuit system

Publications (1)

Publication Number Publication Date
WO2018110185A1 true WO2018110185A1 (en) 2018-06-21

Family

ID=62558523

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2017/040965 WO2018110185A1 (en) 2016-12-14 2017-11-14 Refrigerant circuit system and method for controlling refrigerant circuit system

Country Status (3)

Country Link
EP (1) EP3460357A4 (en)
JP (1) JP6781034B2 (en)
WO (1) WO2018110185A1 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6929318B2 (en) * 2019-03-28 2021-09-01 東プレ株式会社 Refrigeration equipment and operation method of refrigeration equipment
CN110195925A (en) * 2019-05-31 2019-09-03 宁波奥克斯电气股份有限公司 A kind of control method and air conditioner of low-temperature air source heat pump spray enthalpy valve
CN110486917B (en) * 2019-08-23 2021-06-22 广东美的暖通设备有限公司 Operation control device and method, air conditioner and computer readable storage medium
CN113091205B (en) * 2020-08-19 2022-03-08 广州松下空调器有限公司 Air conditioner abnormity detection method and device

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09105560A (en) * 1995-08-04 1997-04-22 Mitsubishi Electric Corp Freezer
JPH1068553A (en) * 1996-08-27 1998-03-10 Daikin Ind Ltd Air conditioner
JP2002349977A (en) * 2001-05-24 2002-12-04 Denso Corp Heat pump cycle
JP2003214713A (en) * 2002-01-23 2003-07-30 Matsushita Electric Ind Co Ltd Refrigeration cycle device
JP2008121977A (en) * 2006-11-13 2008-05-29 Mitsubishi Electric Corp Heat pump water heater
JP2010002109A (en) * 2008-06-19 2010-01-07 Mitsubishi Electric Corp Refrigeration air conditioner
JP2011043273A (en) * 2009-08-20 2011-03-03 Panasonic Corp Heat pump type heating liquid system
JP2015152262A (en) * 2014-02-17 2015-08-24 東芝キヤリア株式会社 Refrigeration cycle device
DE102014222849A1 (en) * 2014-11-10 2016-05-12 BSH Hausgeräte GmbH Domestic refrigerator and chiller for it

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003130481A (en) * 2001-10-24 2003-05-08 Mitsubishi Heavy Ind Ltd Vapor compression type refrigerating cycle of air conditioner for automobile
CN105074351B (en) * 2013-03-12 2017-03-22 三菱电机株式会社 Air conditioner

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09105560A (en) * 1995-08-04 1997-04-22 Mitsubishi Electric Corp Freezer
JPH1068553A (en) * 1996-08-27 1998-03-10 Daikin Ind Ltd Air conditioner
JP2002349977A (en) * 2001-05-24 2002-12-04 Denso Corp Heat pump cycle
JP2003214713A (en) * 2002-01-23 2003-07-30 Matsushita Electric Ind Co Ltd Refrigeration cycle device
JP2008121977A (en) * 2006-11-13 2008-05-29 Mitsubishi Electric Corp Heat pump water heater
JP2010002109A (en) * 2008-06-19 2010-01-07 Mitsubishi Electric Corp Refrigeration air conditioner
JP2011043273A (en) * 2009-08-20 2011-03-03 Panasonic Corp Heat pump type heating liquid system
JP2015152262A (en) * 2014-02-17 2015-08-24 東芝キヤリア株式会社 Refrigeration cycle device
DE102014222849A1 (en) * 2014-11-10 2016-05-12 BSH Hausgeräte GmbH Domestic refrigerator and chiller for it

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3460357A4 *

Also Published As

Publication number Publication date
JP2018096621A (en) 2018-06-21
EP3460357A1 (en) 2019-03-27
JP6781034B2 (en) 2020-11-04
EP3460357A4 (en) 2019-07-03

Similar Documents

Publication Publication Date Title
WO2018110185A1 (en) Refrigerant circuit system and method for controlling refrigerant circuit system
JP3864980B2 (en) Air conditioner
CN108139120B (en) Air conditioner
EP2122276B1 (en) Free-cooling limitation control for air conditioning systems
US20150338135A1 (en) Refrigeration device for container
CN106662364A (en) Refrigerant cooling for variable speed drive
CN109341125B (en) A kind of refrigeration system and control method
JP4859480B2 (en) Turbo chiller, control device thereof, and control method of turbo chiller
JP2017044454A (en) Refrigeration cycle device and control method for the same
JP6545252B2 (en) Refrigeration cycle device
WO2017086343A1 (en) Refrigeration cycle for vehicular air-conditioning device, and vehicle equipped therewith
WO2017183588A1 (en) Vehicle air-conditioning device and vehicle provided with same
JP4298388B2 (en) Air conditioner and control method of air conditioner
CN109869941B (en) Heat pump system, air suction superheat degree and vapor-liquid separator accumulated liquid evaporation control method
JP2006300371A (en) Air conditioner
JP2006284034A (en) Air conditioner and its expansion valve control method
JP2017062065A (en) Heat exchange system
EP2672205A2 (en) Heat exchanger system
US20200318880A1 (en) Refrigeration cycle apparatus
WO2017135223A1 (en) Vehicle air conditioning device, vehicle provided with same, and method for controlling vehicle grill device
CN112513542B (en) Method for controlling a vapor compression system based on a predicted flow
JP2017137012A (en) Vehicular air conditioner, vehicle including the same and control method for vehicular air conditioner
JP7055239B2 (en) Air conditioner
JP2008032285A (en) Refrigerating machine, temperature adjusting device or its control method
JP2020133998A (en) Freezing device

Legal Events

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

Ref document number: 17881376

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2017881376

Country of ref document: EP

Effective date: 20181218

NENP Non-entry into the national phase

Ref country code: DE