JP5571429B2 - Gas-liquid heat exchange type refrigeration equipment - Google Patents

Gas-liquid heat exchange type refrigeration equipment Download PDF

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JP5571429B2
JP5571429B2 JP2010077377A JP2010077377A JP5571429B2 JP 5571429 B2 JP5571429 B2 JP 5571429B2 JP 2010077377 A JP2010077377 A JP 2010077377A JP 2010077377 A JP2010077377 A JP 2010077377A JP 5571429 B2 JP5571429 B2 JP 5571429B2
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refrigerant
heat exchange
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control valve
compressor
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健太郎 渡邊
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Topre Corp
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Description

本発明は、凝縮器にて凝縮した冷媒と蒸発器にて蒸発した冷媒と気液熱交換器において互いに熱交換させて各冷媒をそれぞれ過冷却及び過熱することによって冷凍能力を高めるようにした気液熱交換型冷凍装置に関するものである。   In the present invention, the refrigerant condensed in the condenser, the refrigerant evaporated in the evaporator and the gas-liquid heat exchanger are mutually heat-exchanged to supercool and superheat each refrigerant, thereby increasing the refrigeration capacity. The present invention relates to a liquid heat exchange type refrigeration apparatus.

一般に冷凍装置は、圧縮機、凝縮器、膨張弁及び蒸発器を冷媒配管によって直列に接続して閉ループの冷媒循環回路を構成するものであって、圧縮機によって圧縮された高圧のガス冷媒を凝縮器での放熱によって液化させて高圧の液冷媒とし、この液冷媒を膨張弁によって膨張（等エンタルピ膨張）させて減圧した後、沸点の下がった低圧の液冷媒を蒸発器において蒸発させ、蒸発に必要な蒸発潜熱を庫内等から奪うことによって庫内等を冷却するものである。   In general, a refrigeration system connects a compressor, a condenser, an expansion valve, and an evaporator in series by a refrigerant pipe to form a closed-loop refrigerant circulation circuit, and condenses high-pressure gas refrigerant compressed by the compressor. The refrigerant is liquefied by heat dissipation in the evaporator to form a high-pressure liquid refrigerant, and this liquid refrigerant is expanded by the expansion valve (isenthalpy expansion) and depressurized. By taking necessary latent heat of vaporization from the inside of the cabinet, the inside of the cabinet is cooled.

斯かる冷凍装置の冷凍能力或いは成績係数（ＣＯＰ）を向上させる方法として、冷媒循環回路の凝縮器と膨張弁との間に気液熱交換器を設け、凝縮器にて凝縮した冷媒と蒸発器にて蒸発した冷媒とを気液熱交換器において互いに熱交換させて各冷媒をそれぞれ過冷却及び過熱する方法が知られている。   As a method for improving the refrigeration capacity or coefficient of performance (COP) of such a refrigeration apparatus, a gas-liquid heat exchanger is provided between the condenser and the expansion valve of the refrigerant circulation circuit, and the refrigerant and evaporator condensed in the condenser There is known a method in which the refrigerant evaporated in step 1 is heat-exchanged with each other in a gas-liquid heat exchanger to supercool and superheat each refrigerant.

ところで、特許文献１には、気液熱交換器を備えた冷凍空調装置において、冷媒循環回路の凝縮器と気液熱交換器の間及び気液熱交換器と蒸発器の間に膨張弁をそれぞれ設け、凝縮器出口の冷媒温度と圧縮機入口の冷媒温度に基づいて膨張弁の開度を制御し、蒸発器出口での冷媒の乾き度を所定の目標値に保つことによって高効率な運転を実現するとともに、蒸発器が乾くことに起因する露飛び等の不具合を解消する提案がなされている。   By the way, in patent document 1, in the refrigeration air conditioner provided with the gas-liquid heat exchanger, an expansion valve is provided between the condenser and the gas-liquid heat exchanger of the refrigerant circulation circuit and between the gas-liquid heat exchanger and the evaporator. Efficient operation by installing each, controlling the opening of the expansion valve based on the refrigerant temperature at the condenser outlet and the refrigerant temperature at the compressor inlet, and keeping the refrigerant dryness at the evaporator outlet at a predetermined target value In addition, a proposal has been made to solve problems such as dew splattering due to drying of the evaporator.

特開２００９−１６２３８８号公報JP 2009-162388 A

ところで、特許文献１において提案された冷凍空調装置を冷凍車のように圧縮機の回転数が大きく変動する環境下で運転した場合、気液熱交換器の熱交換性能が圧縮機の回転数の変動に伴って大きく変化する。例えば、圧縮機の回転数が低下すると冷媒循環量が減少し、気液熱交換器での熱交換量不足による冷却不良が発生し、逆に圧縮機の回転数が増加すると冷媒循環量が増大し、熱交換量過多による圧縮機出口での冷媒の吐出温度の上昇を招き、冷凍機油が劣化する等の問題が発生する。   By the way, when the refrigerating and air-conditioning apparatus proposed in Patent Document 1 is operated in an environment where the rotation speed of the compressor greatly varies like a refrigeration vehicle, the heat exchange performance of the gas-liquid heat exchanger is equal to the rotation speed of the compressor. It changes greatly with fluctuation. For example, if the rotation speed of the compressor decreases, the refrigerant circulation rate decreases, causing a cooling failure due to insufficient heat exchange in the gas-liquid heat exchanger. Conversely, if the compressor rotation rate increases, the refrigerant circulation rate increases. However, the refrigerant discharge temperature rises at the compressor outlet due to the excessive heat exchange amount, causing problems such as deterioration of the refrigeration oil.

本発明は上記問題に鑑みてなされたもので、その目的とする処は、圧縮機の回転数の変動に伴う冷凍能力の変動を抑えるとともに、圧縮機出口での冷媒の吐出温度の上昇を抑えて冷凍機油の劣化を防ぐことができる気液熱交換型冷凍装置を提供することにある。   The present invention has been made in view of the above-described problems, and its intended process is to suppress fluctuations in the refrigeration capacity accompanying fluctuations in the rotational speed of the compressor and to suppress an increase in the refrigerant discharge temperature at the compressor outlet. Another object of the present invention is to provide a gas-liquid heat exchange type refrigerating apparatus that can prevent deterioration of refrigerating machine oil.

上記目的を達成するため、請求項１記載の発明は、少なくとも圧縮機、凝縮器、熱交制御弁、気液熱交換器、膨張弁及び蒸発器を冷媒配管によって直列に接続して閉ループの冷媒循環回路を構成し、前記凝縮器にて凝縮した後に前記熱交制御弁によって減圧された冷媒と前記蒸発器にて蒸発した冷媒とを前記気液熱交換器において熱交換させて各冷媒をそれぞれ過冷却及び過熱するようにした気液熱交換型冷凍装置において、前記冷媒循環回路の前記圧縮機と前記凝縮器の間に吐出温度センサを設けるとともに、前記熱交制御弁と前記気液熱交換器との間に圧力センサを設け、前記吐出温度センサによって検出される圧縮機出口の冷媒温度と前記圧力センサによって検出される熱交制御弁出口の冷媒圧力に基づいて前記熱交制御弁の開度を制御して、前記熱交制御弁を通過して前記気液熱交換器を流れる冷媒の流速を制御する制御手段を設けたことを特徴とする。 In order to achieve the above object, a first aspect of the present invention is a closed-loop refrigerant in which at least a compressor, a condenser, a heat exchange control valve, a gas-liquid heat exchanger, an expansion valve, and an evaporator are connected in series by a refrigerant pipe. A circulation circuit is configured, and after the refrigerant is condensed in the condenser, the refrigerant decompressed by the heat exchange control valve and the refrigerant evaporated in the evaporator are subjected to heat exchange in the gas-liquid heat exchanger, and each refrigerant is In the gas-liquid heat exchange type refrigeration apparatus that is supercooled and overheated, a discharge temperature sensor is provided between the compressor and the condenser of the refrigerant circulation circuit, and the heat exchange control valve and the gas-liquid heat exchange are provided. A pressure sensor is provided between the compressor and the heat exchanger control valve to open based on the refrigerant temperature at the compressor outlet detected by the discharge temperature sensor and the refrigerant pressure at the heat exchanger valve outlet detected by the pressure sensor. Control the degree To, characterized in that a control means for controlling the flow rate of refrigerant flowing through the gas-liquid heat exchanger through the heat exchange control valve.

請求項２記載の発明は、請求項１記載の発明において、前記制御手段は、前記圧縮機の回転数が低下すると前記熱交制御弁の開度を絞り、前記圧縮機の回転数が増加すると前記熱交制御弁の開度を大きくすることを特徴とする。   According to a second aspect of the present invention, in the first aspect of the present invention, when the rotation speed of the compressor decreases, the control means throttles the opening degree of the heat exchanger control valve and increases the rotation speed of the compressor. The opening degree of the heat exchange control valve is increased.

請求項３記載の発明は、請求項１記載の発明において、前記制御手段は、前記吐出温度センサによって検出される圧縮機出口の冷媒温度が設定値を超えると、前記熱交制御弁の開度を、該熱交制御弁で減圧された後に前記気液熱交換器を通過した冷媒が気液混合状態を維持する値まで絞ることを特徴とする。   According to a third aspect of the present invention, in the first aspect of the present invention, when the refrigerant temperature at the compressor outlet detected by the discharge temperature sensor exceeds a set value, the control means opens the opening of the heat exchanger control valve. Is reduced to a value at which the refrigerant that has passed through the gas-liquid heat exchanger after being depressurized by the heat exchange control valve maintains a gas-liquid mixed state.

請求項１及び２記載の発明によれば、圧縮機の回転数が低下すると熱交制御弁の開度を絞るようにしたため、気液熱交換器を流れる冷媒の流速が上がって熱交換量が増え、この熱交換量の増加によって、回転数低下による冷媒循環量の減少に伴う気液熱交換器での熱交換量の減少を補償することができ、熱交換量不足による冷却不良を抑制することができる。   According to the first and second aspects of the present invention, since the opening degree of the heat exchange control valve is reduced when the rotational speed of the compressor is reduced, the flow rate of the refrigerant flowing through the gas-liquid heat exchanger is increased and the heat exchange amount is reduced. By increasing this heat exchange amount, it is possible to compensate for the decrease in heat exchange amount in the gas-liquid heat exchanger due to the decrease in the refrigerant circulation amount due to the decrease in the rotational speed, and suppress the cooling failure due to insufficient heat exchange amount be able to.

又、圧縮機の回転数が増加すると熱交制御弁の開度を大きくするようにしたため、気液熱交換器を流れる冷媒の流速が下がって熱交換量が減少し、この熱交換量の減少によって、回転数増大による冷媒循環量の増加に伴う気液熱交換器での熱交換量の増加を補償することができ、熱交換量過多による圧縮機出口での冷媒の吐出温度の上昇を抑制することができる。   In addition, since the opening degree of the heat exchange control valve is increased as the number of rotations of the compressor increases, the flow rate of the refrigerant flowing through the gas-liquid heat exchanger decreases, the heat exchange amount decreases, and this heat exchange amount decreases. Can compensate for the increase in the heat exchange amount in the gas-liquid heat exchanger due to the increase in the refrigerant circulation rate due to the increase in the rotational speed, and suppress the increase in the refrigerant discharge temperature at the compressor outlet due to the excessive heat exchange amount can do.

請求項３記載の発明によれば、圧縮機出口の冷媒温度が設定値を超えると、熱交制御弁で減圧された後に気液熱交換器を通過した冷媒が気液混合状態を維持する値まで熱交制御弁の開度を大きく絞るようにしたため、気液熱交換器を気液二相流として通過する冷媒と蒸発器からのガス冷媒との温度差が小さくなり、気液熱交換器での両冷媒の熱交換量が低く抑えられる。このため、圧縮機入口での冷媒の過熱度が低く抑えられ、圧縮機出口での冷媒の吐出温度の上昇が抑制されて冷凍機油の劣化が防がれる。 According to the invention of claim 3, when the refrigerant temperature at the compressor outlet exceeds a set value, the value at which the refrigerant that has passed through the gas-liquid heat exchanger after being depressurized by the heat exchanger control valve maintains a gas-liquid mixed state. Since the opening degree of the heat exchanger control valve is greatly reduced until the temperature difference between the refrigerant passing through the gas-liquid heat exchanger as a gas-liquid two- phase flow and the gas refrigerant from the evaporator becomes smaller, the gas-liquid heat exchanger The amount of heat exchange between the two refrigerants can be kept low. For this reason, the degree of superheating of the refrigerant at the compressor inlet is suppressed to a low level, the rise in the refrigerant discharge temperature at the compressor outlet is suppressed, and deterioration of the refrigerating machine oil is prevented.

本発明に係る気液熱交換型冷凍装置の冷媒回路図である。It is a refrigerant circuit figure of the gas-liquid heat exchange type refrigerating device concerning the present invention. 本発明に係る気液熱交換型冷凍装置において圧縮機回転数の変動に応じて熱交制御弁の開度を制御した場合の冷媒の状態変化を示すモリエル線図である。It is a Mollier diagram which shows the state change of a refrigerant | coolant at the time of controlling the opening degree of a heat exchanger control valve according to the fluctuation | variation of compressor rotation speed in the gas-liquid heat exchange type | mold refrigerating apparatus which concerns on this invention. 気液熱交換器における凝縮液冷媒の流速と伝熱性能との関係を示す図である。It is a figure which shows the relationship between the flow rate of the condensate refrigerant | coolant in a gas-liquid heat exchanger, and heat-transfer performance. 本発明に係る気液熱交換型冷凍装置において圧縮機出口での冷媒の吐出温度が設定値を超えたときに熱交制御弁の開度を制御した場合の冷媒の状態変化を示すモリエル線図である。In the gas-liquid heat exchange type refrigeration apparatus according to the present invention, a Mollier diagram showing a change in state of the refrigerant when the opening degree of the heat exchange control valve is controlled when the refrigerant discharge temperature at the compressor outlet exceeds a set value . It is.

以下に本発明の実施の形態を添付図面に基づいて説明する。   Embodiments of the present invention will be described below with reference to the accompanying drawings.

図１は本発明に係る気液熱交換型冷凍装置の冷媒回路図であり、図示の気液熱交換型冷凍装置においては、圧縮機１、凝縮器２、熱交制御弁３、気液熱交換器４、膨張弁５及び蒸発器６が冷媒配管Ｌ１，Ｌ２，Ｌ３，Ｌ４,Ｌ５によって直列に接続されて閉ループの冷媒循環回路が形成されている。ここで、熱交制御弁３は、凝縮器２と気液熱交換器４とを接続する冷媒配管Ｌ２に設けられ、膨張弁５は、気液熱交換器４と蒸発器６とを接続する冷媒配管Ｌ３に設けられている。尚、熱交制御弁３は、開度が無段階に制御される電子制御弁で構成されている。   FIG. 1 is a refrigerant circuit diagram of a gas-liquid heat exchange type refrigeration apparatus according to the present invention. In the illustrated gas-liquid heat exchange type refrigeration apparatus, a compressor 1, a condenser 2, a heat exchange control valve 3, a gas-liquid heat are shown. The exchanger 4, the expansion valve 5 and the evaporator 6 are connected in series by refrigerant pipes L1, L2, L3, L4, and L5 to form a closed loop refrigerant circulation circuit. Here, the heat exchange control valve 3 is provided in the refrigerant pipe L2 that connects the condenser 2 and the gas-liquid heat exchanger 4, and the expansion valve 5 connects the gas-liquid heat exchanger 4 and the evaporator 6. It is provided in the refrigerant pipe L3. The heat exchange control valve 3 is an electronic control valve whose opening degree is controlled steplessly.

又、本発明に係る気液熱交換型冷凍装置においては、圧縮機１と凝縮器２を接続する冷媒配管Ｌ１には吐出温度センサ７が設けられ、冷媒配管Ｌ２の熱交制御弁３と気液熱交換器４の間には圧力センサ８が設けられ、蒸発器６と気液熱交換器４とを接続する冷媒配管Ｌ４には蒸発温度センサ９が設けられており、これらの吐出温度センサ７と圧力センサ８及び蒸発温度センサ９は制御手段であるコントローラ１０に電気的に接続されている。更に、電子制御弁で構成された熱交制御弁３はコントローラ１０に電気的に接続されており、後述のように熱交制御弁３はコントローラ１０からの制御信号によってその開度が制御される。   In the gas-liquid heat exchange type refrigeration apparatus according to the present invention, the refrigerant pipe L1 connecting the compressor 1 and the condenser 2 is provided with the discharge temperature sensor 7, and the heat exchange control valve 3 of the refrigerant pipe L2 and the air exchange control valve 3 are connected. A pressure sensor 8 is provided between the liquid heat exchangers 4, and an evaporation temperature sensor 9 is provided in the refrigerant pipe L4 connecting the evaporator 6 and the gas-liquid heat exchanger 4, and these discharge temperature sensors are provided. 7, the pressure sensor 8 and the evaporation temperature sensor 9 are electrically connected to a controller 10 which is a control means. Further, the heat exchange control valve 3 constituted by an electronic control valve is electrically connected to the controller 10, and the opening degree of the heat exchange control valve 3 is controlled by a control signal from the controller 10 as will be described later. .

次に、本発明に係る気液熱交換型冷凍装置の作用を図２に示すモリエル線図（Ｐ−ｉ線図）を用いて以下に説明する。 Next, the operation of the gas-liquid heat exchange type refrigeration apparatus according to the present invention will be described below with reference to the Mollier diagram (Pi diagram) shown in FIG.

圧縮機１が駆動源である不図示のエンジンによって回転駆動されると、図２にａにて示す状態（圧力Ｐ１、エンタルピｉ１）にあるガス冷媒が圧縮機１によって圧縮されて図２にｂにて示す状態（圧力Ｐ２、エンタルピｉ２）の高温高圧のガス冷媒となり（圧縮行程）、このガス冷媒は冷媒配管Ｌ１を通って凝縮器２へと導入される。尚、このときの圧縮機１の圧縮動力Ｗ（熱量換算）は（ｉ２−ｉ１）で表わされる。 When the compressor 1 is rotationally driven by an engine (not shown) as a drive source, the gas refrigerant in the state (pressure P 1 , enthalpy i 1 ) shown in FIG. B becomes a high-temperature and high-pressure gas refrigerant in the state (pressure P 2 , enthalpy i 2 ) (compression stroke), and this gas refrigerant is introduced into the condenser 2 through the refrigerant pipe L1. In addition, the compression power W (heat amount conversion) of the compressor 1 at this time is represented by (i 2 −i 1 ).

凝縮器２では、高温高圧のガス冷媒が外気に凝縮熱Ｑ２を放出して図２のｂ→ｃへと状態変化（相変化）して液化し（凝縮行程）、図２にｃにて示す状態（圧力Ｐ２、エンタルピｉ３）の高圧液冷媒となる。尚、このときの放熱量（凝縮熱）Ｑ２は（ｉ２−ｉ３）で表わされる。 In the condenser 2, high-temperature high-pressure gas refrigerant by releasing heat of condensation Q 2 to the outside air and liquefied by the state change (phase change) to the b → c 2 (condensation stroke) at c in FIG. 2 state (pressure P 2, enthalpy i3) showing a high-pressure liquid refrigerant. Incidentally, the heat radiation amount of time (condensation heat) Q 2 is represented by (i 2 -i 3).

そして、上述のように凝縮器２において液化した高圧液冷媒は、図２において例えばＢにて示す経路（条件）を経て状態変化する。即ち、凝縮器２において液化した高圧液冷媒は、冷媒配管Ｌ２を通って熱交制御弁３に至り、該熱交制御弁３によって圧力Ｐ３まで減圧されて断熱膨張（等エンタルピ膨張）し（膨張行程）、図２にｄにて示す状態（圧力Ｐ３、エンタルピｉ３）となって、その一部がガス化する。 Then, the high-pressure liquid refrigerant liquefied in the condenser 2 as described above changes its state through a path (condition) indicated by B in FIG. That is, high-pressure liquid refrigerant that has liquefied in the condenser 2 reaches the heat exchange control valve 3 through the refrigerant pipe L2, it is depressurized by the heat exchange control valve 3 to a pressure P 3 adiabatic expansion (isentropic expansion) and ( 2 (expansion stroke), a state indicated by d in FIG. 2 (pressure P 3 , enthalpy i 3 ), and a part thereof is gasified.

上述のように一部がガス化した冷媒は、冷媒配管Ｌ２を通って気液熱交換器４に導入されるが、この気液熱交換器４には後述のように蒸発器６において蒸発して気化したガス冷媒が冷媒配管Ｌ４を経て導入されているため、冷媒配管Ｌ２から気液熱交換器４へと導入された冷媒（一部がガス化した冷媒）は蒸発器６にて蒸発して冷媒配管Ｌ４から導入される温度の低いガス冷媒との熱交換によって過冷却され、図２にｅにて示す状態（圧力Ｐ３、エンタルピｉ４）の液冷媒となる。尚、この場合の過冷却熱量ΔＱ２は（ｉ３−ｉ４）で表わされる。 The refrigerant partially gasified as described above is introduced into the gas-liquid heat exchanger 4 through the refrigerant pipe L2, and is evaporated in the evaporator 6 as described later. Since the vaporized gas refrigerant is introduced through the refrigerant pipe L4, the refrigerant (partially gasified refrigerant) introduced from the refrigerant pipe L2 to the gas-liquid heat exchanger 4 is evaporated in the evaporator 6. Then, it is supercooled by heat exchange with the low-temperature gas refrigerant introduced from the refrigerant pipe L4, and becomes a liquid refrigerant in a state indicated by e in FIG. 2 (pressure P 3 , enthalpy i 4 ). In this case, the supercooling heat quantity ΔQ 2 is represented by (i 3 −i 4 ).

そして、上述のように気液熱交換器４において過冷却された液冷媒は、膨張弁５を通過することによって再度減圧されて断熱膨張（等エンタルピ膨張）し（膨張行程）、図２のｆにて示す状態（圧力Ｐ１、エンタルピｉ４）へと状態変化してその一部がガス化し、減圧されることによって沸点が下がる。このように膨張弁５によって減圧されて沸点が下がった冷媒は、冷媒配管Ｌ３から蒸発器６へと導入され、該蒸発器６を流れる過程で周囲から蒸発熱Ｑ１を奪って蒸発してｆ→ｇ（圧力Ｐ１、エンタルピｉ５）へと状態変化してガス化する（蒸発行程）。このときの蒸発熱量Ｑ１は（ｉ５−ｉ４）で表わされるが、前述のように膨張弁５で減圧される前の冷媒は気液熱交換器４においてΔＱ２（＝ｉ３−ｉ４）だけ過冷却されているため、この過冷却分の熱量ΔＱ２だけ蒸発熱量が増加し、その増加分ΔＱ２だけ冷凍能力が高められる。 Then, the liquid refrigerant supercooled in the gas-liquid heat exchanger 4 as described above is decompressed again by passing through the expansion valve 5 and undergoes adiabatic expansion (equal enthalpy expansion) (expansion stroke). The state changes to the state indicated by (pressure P 1 , enthalpy i 4 ), part of which is gasified and reduced in pressure to lower the boiling point. Thus the refrigerant that is depressurized dropped boiling point by the expansion valve 5 is introduced from the refrigerant pipe L3 to the evaporator 6, and evaporated depriving heat of evaporation Q 1 from the surroundings in the process of flowing through the evaporator 6 f → The gas changes into the gas state (pressure P 1 , enthalpy i 5 ) and gasifies (evaporation process). The amount of heat of vaporization Q1 at this time is represented by (i 5 -i 4 ), but the refrigerant before being depressurized by the expansion valve 5 is ΔQ 2 (= i 3 -i 4 ) in the gas-liquid heat exchanger 4 as described above. ), The amount of heat of evaporation is increased by the amount of heat ΔQ 2 for the amount of subcooling, and the refrigeration capacity is increased by the amount of increase ΔQ 2 .

その後、蒸発器６にて蒸発した低圧ガス冷媒は、前述のように冷媒配管Ｌ４から気液熱交換器４を流れる過程で冷媒配管Ｌ２から気液熱交換器４へと導入される高圧冷媒の過冷却に供されるために温度が上昇し、圧縮機１に吸入される段階では図２に示すｇ→ａ（圧力Ｐ１、エンタルピｉ１）へと変化して図示の熱量ΔＱ１（＝ｉ１−ｉ５）だけ過熱される。そして、この過熱されたガス冷媒は、圧縮機１によって再度圧縮され、以後は冷媒の上記と同様の状態変化が繰り返される。 Thereafter, the low-pressure gas refrigerant evaporated in the evaporator 6 is the high-pressure refrigerant introduced from the refrigerant pipe L2 to the gas-liquid heat exchanger 4 in the process of flowing through the gas-liquid heat exchanger 4 from the refrigerant pipe L4 as described above. At the stage where the temperature rises to be used for supercooling and is sucked into the compressor 1 , it changes from g → a (pressure P 1 , enthalpy i 1 ) shown in FIG. 2 and the amount of heat ΔQ 1 (= i 1 -i 5 ) is overheated. The overheated gas refrigerant is compressed again by the compressor 1, and thereafter, the state change of the refrigerant is repeated as described above.

而して、本発明に係る気液熱交換型冷凍装置においては、以上説明した冷凍サイクルが繰り返され、蒸発器６での低温液冷媒の蒸発に伴う吸熱によって所要の冷凍が行われるが、圧縮機１から吐出されるガス冷媒の温度は吐出温度センサ７によって検出され、凝縮器２によって凝縮された後に熱交制御弁３によって減圧された冷媒の圧力は圧力センサ８によって検出され、これらの検出値はコントローラ１０へと送信される。すると、コントローラ１０は、吐出温度センサ７によって検出される圧縮機１の出口における冷媒温度と圧力センサ８によって検出される熱交制御弁３の出口における冷媒圧力に基づいて熱交制御弁３の開度を制御する。   Thus, in the gas-liquid heat exchange type refrigeration apparatus according to the present invention, the refrigeration cycle described above is repeated, and the required refrigeration is performed by the heat absorption accompanying the evaporation of the low-temperature liquid refrigerant in the evaporator 6, but the compression is performed. The temperature of the gas refrigerant discharged from the machine 1 is detected by the discharge temperature sensor 7, and the pressure of the refrigerant decompressed by the heat exchanger control valve 3 after being condensed by the condenser 2 is detected by the pressure sensor 8, and these are detected. The value is transmitted to the controller 10. Then, the controller 10 opens the heat exchange control valve 3 based on the refrigerant temperature at the outlet of the compressor 1 detected by the discharge temperature sensor 7 and the refrigerant pressure at the outlet of the heat exchange control valve 3 detected by the pressure sensor 8. Control the degree.

具体的には、圧縮機１の回転数が低下すると熱交制御弁３の開度を絞り、逆に圧縮機１の回転数が増加すると熱交制御弁３の開度を大きくする。又、吐出温度センサ７によって検出される圧縮機１の出口における冷媒温度が設定値を超えると、前記熱交制御弁３の開度を、該熱交制御弁３で減圧された後に気液熱交換器４を通過した冷媒が気液混合状態を維持する値まで絞る（図４参照）。   Specifically, when the rotational speed of the compressor 1 decreases, the opening degree of the heat exchange control valve 3 is reduced, and conversely, when the rotational speed of the compressor 1 increases, the opening degree of the heat exchange control valve 3 is increased. When the refrigerant temperature at the outlet of the compressor 1 detected by the discharge temperature sensor 7 exceeds a set value, the opening degree of the heat exchange control valve 3 is reduced by the heat exchange control valve 3 and then the gas-liquid heat. The refrigerant that has passed through the exchanger 4 is throttled to a value that maintains the gas-liquid mixed state (see FIG. 4).

本発明に係る気液熱交換型冷凍装置を例えば冷凍車に搭載した場合、エンジンによって駆動される圧縮機１の回転数は冷凍車の走行状態によって変動する。 If the gas-liquid heat exchanger replaceable refrigeration apparatus according to the present invention is mounted, for example, refrigerated vehicle, the rotational speed of the compressor 1 which is driven by the engine varies by the running condition of the refrigerated vehicle.

例えば、圧縮機１の回転数が低下すると冷媒循環回路における冷媒の循環量が減少するために冷凍能力が低下するが、この場合は前述のようにコントローラ１０は熱交制御弁３の開度を絞るようにしたため、気液熱交換器４を流れる冷媒の流速が上がって熱交換量が増え、この熱交換量の増加によって、回転数低下による冷媒循環量の減少に伴う気液熱交換器４での熱交換量の減少が補償され、熱交換量不足による冷却不良が抑制される。   For example, when the rotational speed of the compressor 1 is reduced, the refrigerant circulation amount in the refrigerant circulation circuit is reduced, so that the refrigeration capacity is lowered. In this case, the controller 10 increases the opening degree of the heat exchanger control valve 3 as described above. Since the flow is reduced, the flow rate of the refrigerant flowing through the gas-liquid heat exchanger 4 is increased and the heat exchange amount is increased. By the increase in the heat exchange amount, the gas-liquid heat exchanger 4 is associated with a decrease in the refrigerant circulation amount due to a decrease in the rotational speed. The decrease in the heat exchange amount at is compensated, and poor cooling due to insufficient heat exchange amount is suppressed.

ここで、凝縮器２において液化した高圧液冷媒が熱交制御弁３から気液熱交換器４を経て膨張弁５へと流れるときの状態変化を例えば図２にＢ，Ｃ，Ｄにて示す。Ｂにて示す状態で運転している場合には熱交制御弁３によって圧力がＰ２からＰ３へと減圧されるが、圧縮機１の回転数が低下すると、その回転数の低下の度合いに応じて熱交制御弁３を絞って図２のＣ，Ｄにて示すように圧力Ｐ３’，Ｐ３”（Ｐ３＞Ｐ３’＞Ｐ３”）まで減圧すれば、気液熱交換器４を流れる冷媒の流速が上がって図示のように熱交換量が増えるため、前述のように熱交換量不足による冷却不良を抑制することができる。 Here, the state change when the high-pressure liquid refrigerant liquefied in the condenser 2 flows from the heat exchanger control valve 3 through the gas-liquid heat exchanger 4 to the expansion valve 5 is shown by B, C, and D in FIG. . When operating in the state indicated by B, the pressure is reduced from P 2 to P 3 by the heat exchanger control valve 3, but when the rotation speed of the compressor 1 decreases, the degree of decrease in the rotation speed If the heat exchange control valve 3 is throttled to reduce the pressure to pressures P 3 ′ and P 3 ″ (P 3 > P 3 ′> P 3 ″) as shown by C and D in FIG. Since the flow rate of the refrigerant flowing through the exchanger 4 increases and the amount of heat exchange increases as shown in the figure, it is possible to suppress the cooling failure due to insufficient heat exchange amount as described above.

図３に気液熱交換器４における冷媒の流速（ｍ／ｓ）と伝熱性能ＫＡ（Ｗ／Ｋ）との関係を示すが、伝熱性能（熱交換量）ＫＡは冷媒の流速の増加と共に増大することが分かる。   FIG. 3 shows the relationship between the refrigerant flow rate (m / s) and the heat transfer performance KA (W / K) in the gas-liquid heat exchanger 4, and the heat transfer performance (heat exchange amount) KA is an increase in the refrigerant flow rate. It turns out that it increases with.

ここで、熱交制御弁３を用いないで気液熱交換器４において冷媒を過冷却した後に膨張弁５によって膨張させた場合の過程（条件）を図２にＡにて示すが、この過程Ａを経て冷媒を状態変化させた場合を基準として各過程Ｂ，Ｃ，Ｄを経て冷媒を状態変化させたときの冷媒の流速と気液熱交換器４での熱交換量及び性能アップ率をシミュレーションによって求めると表１に示すような結果が得られた。   Here, a process (condition) when the refrigerant is supercooled in the gas-liquid heat exchanger 4 without using the heat exchanger control valve 3 and then expanded by the expansion valve 5 is shown by A in FIG. The flow rate of the refrigerant, the amount of heat exchange in the gas-liquid heat exchanger 4 and the performance increase rate when the refrigerant is changed through the processes B, C, D with reference to the case where the refrigerant is changed through A. When obtained by simulation, the results shown in Table 1 were obtained.

Figure 0005571429
表１の結果から明らかなように、圧縮機１の回転数が低下した場合に熱交制御弁３を絞ると流速が増大して気液熱交換器４での交換熱量が増え、結果的に性能がアップして冷凍能力が高められることが分かる。
Figure 0005571429
 As is clear from the results in Table 1, when the heat exchange control valve 3 is throttled when the rotation speed of the compressor 1 is reduced, the flow rate increases and the amount of heat exchanged in the gas-liquid heat exchanger 4 increases. It can be seen that the performance is improved and the refrigeration capacity is increased.

逆に、圧縮機１の回転数が増加すると冷媒循環量が増大し、気液熱交換器４での交換熱量過多による圧縮機１の出口における冷媒の吐出温度が上昇し、冷凍機油が劣化する等の問題が発生するため、前述のようにコントローラ１０は熱交制御弁３を開いてその開度が大きくなるよう制御する。   Conversely, when the rotation speed of the compressor 1 increases, the refrigerant circulation amount increases, the refrigerant discharge temperature rises at the outlet of the compressor 1 due to excessive heat exchange in the gas-liquid heat exchanger 4, and the refrigeration oil deteriorates. As described above, the controller 10 opens the heat exchange control valve 3 and controls the opening degree to increase.

例えば、図２のＤにて示す状態で運転している場合には熱交制御弁３によって圧力がＰ２からＰ３”へと減圧されるが、圧縮機１の回転数が増加すると、その回転数の増加の度合いに応じて熱交制御弁３を開いて図２のＣ，Ｂにて示すように圧力Ｐ３’，Ｐ３（Ｐ３”＜Ｐ３’＜Ｐ３）まで減圧すれば、気液熱交換器４を流れる冷媒の流速が下がって図示のように熱交換量が減少するため、熱交換量過多による圧縮機１の出口での冷媒の吐出温度の上昇が抑えられて冷凍機油の劣化が防がれる。 For example, when operating in the state indicated by D in FIG. 2, the pressure is reduced from P2 to P3 ″ by the heat exchange control valve 3, but when the rotation speed of the compressor 1 increases, the rotation speed If the heat exchanger control valve 3 is opened according to the degree of increase of the pressure and the pressure is reduced to the pressures P3 ′ and P3 (P3 ″ <P3 ′ <P3) as shown by C and B in FIG. 2, the gas-liquid heat exchanger since the amount of heat exchange as shown down the flow velocity of the refrigerant flowing in the 4 decreases, the refrigerating machine oil degradation increase in the discharge temperature of the refrigerant at the outlet of the compressor 1 by heat exchange amount excessive is suppressed and it is proof Can be removed.

表１の結果から明らかなように、圧縮機１の回転数が増加した場合に熱交制御弁３を開くと流速が減少して気液熱交換器４での交換熱量が減少し、結果的に性能がダウンして冷凍能力が下がることが分かる。   As is apparent from the results in Table 1, when the heat exchange control valve 3 is opened when the number of rotations of the compressor 1 is increased, the flow rate is decreased and the amount of heat exchanged in the gas-liquid heat exchanger 4 is decreased. It can be seen that the performance decreases and the refrigeration capacity decreases.

そして、本発明に係る気液熱交換型冷凍装置においては、吐出温度センサ７によって検出される圧縮機１の出口での冷媒温度が設定値を超えると、前述のようにコントローラ１０は熱交制御弁３の開度を、該熱交制御弁３で減圧された後に気液熱交換器４を通過した冷媒が気液混合状態を維持する値まで絞るようにしている。   In the gas-liquid heat exchange type refrigeration apparatus according to the present invention, when the refrigerant temperature at the outlet of the compressor 1 detected by the discharge temperature sensor 7 exceeds the set value, the controller 10 controls the heat exchange as described above. The opening degree of the valve 3 is reduced to a value at which the refrigerant that has passed through the gas-liquid heat exchanger 4 after being depressurized by the heat exchange control valve 3 maintains a gas-liquid mixed state.

例えば、凝縮器２において液化した高圧液冷媒が熱交制御弁３から気液熱交換器４を経て膨張弁５へと流れるときの状態変化を例えば図４にＢ，Ｃ，Ｄにて示すが、凝縮器２において液化した高圧液冷媒を熱交制御弁３を絞ることによって圧力Ｐ２からＰ３’，Ｐ３”へと大きく減圧させれば、Ｂにて示す状態で運転している場合には熱交制御弁３によって圧力がＰ２からＰ３へと減圧されるが、圧縮機１の回転数が低下すると、その回転数の低下の度合いに応じて熱交制御弁３を絞って図２のＣ，Ｄにて示すように圧力Ｐ３’，Ｐ３”（Ｐ３”＜Ｐ３’＜Ｐ３）まで減圧すれば、熱交制御弁３で減圧された後に気液熱交換器４を通過した冷媒が気液混合状態を維持する。 For example, the state change when high-pressure liquid refrigerant liquefied in the condenser 2 flows from the heat exchange control valve 3 through the gas-liquid heat exchanger 4 to the expansion valve 5 is shown by B, C, and D in FIG. If the high pressure liquid refrigerant liquefied in the condenser 2 is greatly reduced from the pressure P 2 to P 3 ′, P 3 ″ by restricting the heat exchange control valve 3, the vehicle is operating in the state indicated by B the Although pressure by heat exchange control valve 3 is reduced from P 2 to P 3, when the rotational speed of the compressor 1 decreases, concentrates heat exchange control valve 3 according to the degree of reduction of the rotational speed C of FIG. 2, the pressure as indicated by D P3 ', P3 "(P 3"<P3'<P 3) if reduced to, gas-liquid heat exchanger 4 is reduced by the heat exchange control valve 3 The refrigerant that passed through maintains a gas-liquid mixed state.

上述のように熱交制御弁３で減圧された後に気液熱交換器４を通過した冷媒が気液混合状態を維持すると、気液熱交換器４を気液二相流として通過する冷媒と蒸発器６から冷媒配管Ｌ４を経て気液熱交換器４へと導入されるガス冷媒との温度差が小さくなり、気液熱交換器４での両冷媒の熱交換量が低く抑えられる。このため、圧縮機１の入口での冷媒の過熱度が低く抑えられ、圧縮機１の出口での冷媒の吐出温度の上昇が抑制されて冷凍機油の劣化が防がれる。 When the refrigerant that has passed through the gas-liquid heat exchanger 4 after being depressurized by the heat exchange control valve 3 as described above maintains a gas-liquid mixed state, the refrigerant that passes through the gas-liquid heat exchanger 4 as a gas-liquid two- phase flow The temperature difference from the gas refrigerant introduced from the evaporator 6 to the gas-liquid heat exchanger 4 via the refrigerant pipe L4 is reduced, and the heat exchange amount of both refrigerants in the gas-liquid heat exchanger 4 is kept low. For this reason, the degree of superheating of the refrigerant at the inlet of the compressor 1 is suppressed to a low level, and an increase in the discharge temperature of the refrigerant at the outlet of the compressor 1 is suppressed, thereby preventing deterioration of the refrigerator oil.

ここで、熱交制御弁を用いないで気液熱交換器４において冷媒を過冷却した後に膨張弁５によって膨張させた場合の過程を図４にＡにて示すが、この過程Ａを経て冷媒を状態変化させた場合を基準として各過程Ｂ，Ｃ，Ｄを経て冷媒を状態変化させたときの冷媒の流速と気液熱交換器４での熱交換量及び性能アップ率をシミュレーションによって求めると表２に示すような結果が得られた。   Here, the process when the refrigerant is supercooled in the gas-liquid heat exchanger 4 without using the heat exchanger control valve and then expanded by the expansion valve 5 is shown by A in FIG. When the state of the refrigerant is changed, the flow rate of the refrigerant, the heat exchange amount in the gas-liquid heat exchanger 4 and the performance increase rate when the state of the refrigerant is changed through the processes B, C, and D are obtained by simulation. Results as shown in Table 2 were obtained.

Figure 0005571429

表２の結果から明らかなように、吐出温度センサ７によって検出される圧縮機１の出口での冷媒温度が設定値を超えた場合に熱交制御弁３を大きく絞ると、冷媒の流速が増大する反面、気液熱交換器４を気液二相流として通過する冷媒と蒸発器６から冷媒配管Ｌ４を経て気液熱交換器４へと導入されるガス冷媒との温度差が小さくなるため、結果的に気液熱交換器４での両冷媒の熱交換量が低く抑えられ、冷凍能力が低下することが分かる。
Figure 0005571429
As is apparent from the results in Table 2, when the refrigerant temperature at the outlet of the compressor 1 detected by the discharge temperature sensor 7 exceeds the set value, the flow rate of the refrigerant increases when the heat exchange control valve 3 is greatly throttled. However, the temperature difference between the refrigerant passing through the gas-liquid heat exchanger 4 as a gas-liquid two- phase flow and the gas refrigerant introduced from the evaporator 6 to the gas-liquid heat exchanger 4 via the refrigerant pipe L4 is reduced. As a result, it can be seen that the heat exchange amount of both refrigerants in the gas-liquid heat exchanger 4 is kept low, and the refrigerating capacity is lowered.

以上のように、本発明によれば、圧縮機１の回転数の変動に伴う冷凍能力の変動を抑えるとともに、圧縮機１の出口での冷媒の吐出温度の上昇を抑えて冷凍機油の劣化を防ぐことができるという効果が得られる。   As described above, according to the present invention, it is possible to suppress refrigeration oil deterioration by suppressing fluctuations in the refrigerating capacity associated with fluctuations in the rotational speed of the compressor 1 and suppressing an increase in refrigerant discharge temperature at the outlet of the compressor 1. The effect that it can prevent is acquired.

１ 圧縮機
２ 凝縮器
３ 熱交制御弁
４ 気液熱交換器
５ 膨張弁
６ 蒸発器
７ 吐出温度センサ
８ 圧力センサ
９ 蒸発温度センサ
１０ コントローラ（制御手段）
Ｌ１〜Ｌ５ 冷媒配管
DESCRIPTION OF SYMBOLS 1 Compressor 2 Condenser 3 Heat exchange control valve 4 Gas-liquid heat exchanger 5 Expansion valve 6 Evaporator 7 Discharge temperature sensor 8 Pressure sensor 9 Evaporation temperature sensor 10 Controller (control means)
L1-L5 Refrigerant piping

Claims (3)

少なくとも圧縮機、凝縮器、熱交制御弁、気液熱交換器、膨張弁及び蒸発器を冷媒配管によって直列に接続して閉ループの冷媒循環回路を構成し、前記凝縮器にて凝縮した後に前記熱交制御弁によって減圧された冷媒と前記蒸発器にて蒸発した冷媒とを前記気液熱交換器において熱交換させて各冷媒をそれぞれ過冷却及び過熱するようにした気液熱交換型冷凍装置において、
前記冷媒循環回路の前記圧縮機と前記凝縮器の間に吐出温度センサを設けるとともに、前記熱交制御弁と前記気液熱交換器との間に圧力センサを設け、前記吐出温度センサによって検出される圧縮機出口の冷媒温度と前記圧力センサによって検出される熱交制御弁出口の冷媒圧力に基づいて前記熱交制御弁の開度を制御して、前記熱交制御弁を通過して前記気液熱交換器を流れる冷媒の流速を制御する制御手段を設けたことを特徴とする気液熱交換型冷凍装置。 At least a compressor, a condenser, a heat exchange control valve, a gas-liquid heat exchanger, an expansion valve, and an evaporator are connected in series by a refrigerant pipe to form a closed-loop refrigerant circulation circuit, and after being condensed in the condenser A gas-liquid heat exchange type refrigerating apparatus in which the refrigerant decompressed by the heat exchange control valve and the refrigerant evaporated in the evaporator are subjected to heat exchange in the gas-liquid heat exchanger to supercool and superheat each refrigerant. In
A discharge temperature sensor is provided between the compressor and the condenser in the refrigerant circulation circuit, and a pressure sensor is provided between the heat exchange control valve and the gas-liquid heat exchanger, and is detected by the discharge temperature sensor. The opening degree of the heat exchange control valve is controlled based on the refrigerant temperature at the compressor outlet and the refrigerant pressure at the heat exchange control valve outlet detected by the pressure sensor, and passes through the heat exchange control valve. A gas-liquid heat exchange type refrigeration apparatus comprising a control means for controlling the flow rate of the refrigerant flowing through the liquid heat exchanger. 前記制御手段は、前記圧縮機の回転数が低下すると前記熱交制御弁の開度を絞り、前記圧縮機の回転数が増加すると前記熱交制御弁の開度を大きくすることを特徴とする請求項１記載の気液熱交換型冷凍装置。   The control means throttles the opening degree of the heat exchange control valve when the rotation speed of the compressor decreases, and increases the opening degree of the heat exchange control valve when the rotation speed of the compressor increases. The gas-liquid heat exchange type refrigeration apparatus according to claim 1. 前記制御手段は、前記吐出温度センサによって検出される圧縮機出口の冷媒温度が設定値を超えると、前記熱交制御弁の開度を、該熱交制御弁で減圧された後に前記気液熱交換器を通過した冷媒が気液混合状態を維持する値まで絞ることを特徴とする請求項１記載の気液熱交換型冷凍装置。
When the refrigerant temperature at the compressor outlet detected by the discharge temperature sensor exceeds a set value, the control means reduces the opening degree of the heat exchange control valve after the pressure is reduced by the heat exchange control valve. The gas-liquid heat exchange type refrigeration apparatus according to claim 1, wherein the refrigerant that has passed through the exchanger is throttled to a value that maintains a gas-liquid mixed state.
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