JP2011521194A - Filling management in refrigerant vapor compression systems. - Google Patents

Filling management in refrigerant vapor compression systems. Download PDF

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JP2011521194A
JP2011521194A JP2011509646A JP2011509646A JP2011521194A JP 2011521194 A JP2011521194 A JP 2011521194A JP 2011509646 A JP2011509646 A JP 2011509646A JP 2011509646 A JP2011509646 A JP 2011509646A JP 2011521194 A JP2011521194 A JP 2011521194A
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refrigerant
vapor compression
compression system
closed loop
circuit
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タラス，マイケル，エフ．
リフソン，アレキサンダー
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Carrier Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/17—Control issues by controlling the pressure of the condenser

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Conditioning Control Device (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

冷媒蒸気圧縮システムは、閉ループ冷媒回路において直列の冷媒連通関係でそれぞれ配設された、冷媒圧縮装置、冷媒放熱用熱交換器、膨張装置および冷媒吸熱用熱交換器を備える。冷媒貯蔵装置は、少なくとも１つの冷媒ラインにより閉ループ冷媒回路と流体連通して接続され、この冷媒ラインに冷媒流制御装置が配される。冷媒は冷媒回路の高圧側から選択的に取り除かれ、該高圧側へと選択的に戻される。または、冷媒は冷媒回路の低圧側から選択的に取り除かれ、該低圧側へと選択的に戻される。あるいは、冷媒は冷媒回路の高圧側から選択的に取り除かれ、該低圧側へと選択的に戻される。冷媒は、作動中またはオフサイクル時に冷媒回路から選択的に取り除かれ、該回路に選択的に戻される。The refrigerant vapor compression system includes a refrigerant compression device, a refrigerant heat dissipation heat exchanger, an expansion device, and a refrigerant heat absorption heat exchanger, which are arranged in series in a refrigerant communication relationship in a closed loop refrigerant circuit. The refrigerant storage device is connected in fluid communication with a closed loop refrigerant circuit by at least one refrigerant line, and a refrigerant flow control device is disposed in the refrigerant line. Refrigerant is selectively removed from the high pressure side of the refrigerant circuit and selectively returned to the high pressure side. Alternatively, the refrigerant is selectively removed from the low pressure side of the refrigerant circuit and selectively returned to the low pressure side. Alternatively, the refrigerant is selectively removed from the high pressure side of the refrigerant circuit and selectively returned to the low pressure side. Refrigerant is selectively removed from the refrigerant circuit during operation or off-cycle and selectively returned to the circuit.

Description

本発明は、一般に、冷媒蒸気圧縮システムに関し、特に、二酸化炭素冷媒を使用し、遷臨界（トランスクリティカル）サイクルで作動する輸送冷凍用冷媒蒸気圧縮システムを含む冷媒蒸気圧縮システムの効果的な冷媒の充填管理に関する。   The present invention relates generally to refrigerant vapor compression systems, and more particularly to effective refrigerant refrigerant compression systems including transport refrigerant refrigeration vapor compression systems that use carbon dioxide refrigerant and operate in a transcritical cycle. It relates to filling management.

冷媒蒸気圧縮システムは、当技術分野においては周知であり、冷凍製品や生鮮製品を輸送するために、輸送冷凍システムにおいて、トラック、トレーラ、コンテナ等の温度制御された貨物スペースに供給する空気の冷却に広く用いられている。また、冷媒蒸気圧縮システムは、生鮮食品を貯蔵する低温室や冷却展示用陳列棚に冷却空気を供給する、スーパーマーケット、コンビニエンスストア、レストラン、あるいは他の商業施設に関連した商業用冷凍システムにおいても一般に用いられている。さらに、冷媒蒸気圧縮システムは、住宅、オフィスビル、病院、学校、レストラン、あるいは他の施設における温度調整される快適領域に供給する空気の調和のために広く用いられている。一般に、上記のような冷媒蒸気圧縮システムは、圧縮機と、亜臨界運転ではコンデンサとして機能し、遷臨界運転ではガス冷却器として機能する空冷または水冷式の冷媒放熱用熱交換器と、エバポレータとして機能する冷媒吸熱用熱交換器と、一般には感温式膨張弁または電子膨張弁であり、冷媒流に関して冷媒吸熱用熱交換器の上流側でかつ冷媒放熱用熱交換器の下流側に配置される膨張装置と、を備える。これらの基本的な冷媒システムの構成要素は、閉ループの冷媒回路として、冷媒ラインによって互いに接続されるとともに、周知の冷媒蒸気圧縮サイクルに応じて配置されている。   Refrigerant vapor compression systems are well known in the art, and cooling of air supplied to temperature controlled cargo spaces such as trucks, trailers, containers, etc. in transport refrigeration systems for transporting frozen and fresh products. Widely used in Refrigerant vapor compression systems are also commonly used in commercial refrigeration systems associated with supermarkets, convenience stores, restaurants, or other commercial facilities that supply cooling air to cold rooms for storing fresh food or cooling display shelves. It is used. In addition, refrigerant vapor compression systems are widely used for conditioning air supplied to comfort zones that are temperature controlled in homes, office buildings, hospitals, schools, restaurants, or other facilities. In general, the refrigerant vapor compression system as described above functions as a compressor, an air-cooled or water-cooled refrigerant heat dissipation heat exchanger that functions as a condenser in subcritical operation, and functions as a gas cooler in transcritical operation, and an evaporator. A functioning heat exchanger for heat absorption of refrigerant, and generally a temperature-sensitive expansion valve or electronic expansion valve, which is arranged upstream of the heat exchanger for heat absorption of refrigerant and downstream of the heat exchanger for heat dissipation of refrigerant with respect to the refrigerant flow. An expansion device. The components of these basic refrigerant systems are connected to each other by a refrigerant line as a closed-loop refrigerant circuit and arranged according to a known refrigerant vapor compression cycle.

伝統的に、この冷媒蒸気圧縮システムの殆どは、亜臨界（サブクリティカル）冷媒圧力で作動する。亜臨界範囲で作動する冷媒蒸気圧縮システムには、一般に、通常のフロン冷媒、例えば、Ｒ２２などのヒドロクロロフルオロカーボン（ＨＣＦＣ）、さらに一般的にはＲ１３４ａ、Ｒ４１０Ａ、Ｒ４０７Ｃなどのヒドロフルオロカーボン（ＨＦＣ）が充填されるが、これらに限定されるものではない。現在の市場では、空調装置や輸送冷凍システムに使用するため、ＨＦＣ冷媒に代えて二酸化炭素などの「自然」冷媒に注目が集まっている。しかし、冷媒として二酸化炭素が充填された冷媒蒸気圧縮システムの多くは、二酸化炭素の臨界温度が低いため、遷臨界圧力方式で作動するように設計されている。例えば、輸送用冷媒蒸気圧縮システムは、周囲空気の温度が二酸化炭素の臨界温度である３１．１℃（８８°Ｆ）を超過する環境で作動する空冷式の冷媒放熱用熱交換器を備えており、この冷媒蒸気圧縮システムは、圧縮機の吐出圧が二酸化炭素の臨界圧力である７．３８ＭＰａ（１０７０ｐｓｉ）を超過する環境でも作動することが必要とされ、遷臨界サイクルで作動する。遷臨界サイクルで作動する冷媒蒸気圧縮システムでは、エバポレータは亜臨界範囲の冷媒温度および圧力で作動する一方、冷媒放熱用熱交換器は、冷媒の臨界点温度および圧力を超える冷媒温度および圧力下で、コンデンサとしてではなくガス冷却器として作動する。   Traditionally, most of this refrigerant vapor compression system operates at subcritical refrigerant pressure. Refrigerant vapor compression systems that operate in the subcritical range generally include conventional chlorofluorocarbon refrigerants, such as hydrochlorofluorocarbons (HCFCs) such as R22, and more generally hydrofluorocarbons (HFCs) such as R134a, R410A, and R407C. Although it is filled, it is not limited to these. In the current market, attention is focused on “natural” refrigerants such as carbon dioxide instead of HFC refrigerants for use in air conditioners and transport refrigeration systems. However, many refrigerant vapor compression systems filled with carbon dioxide as a refrigerant are designed to operate in a transcritical pressure mode because the critical temperature of carbon dioxide is low. For example, a transport refrigerant vapor compression system includes an air-cooled refrigerant heat dissipation heat exchanger that operates in an environment where the ambient air temperature exceeds 31.1 ° C. (88 ° F.), the critical temperature of carbon dioxide. This refrigerant vapor compression system is required to operate even in an environment where the discharge pressure of the compressor exceeds 7.38 MPa (1070 psi), which is the critical pressure of carbon dioxide, and operates in a transcritical cycle. In refrigerant vapor compression systems operating in a transcritical cycle, the evaporator operates at sub-critical refrigerant temperatures and pressures, while the heat-dissipating heat exchanger operates at refrigerant temperatures and pressures above the refrigerant critical point temperature and pressure. Operates as a gas cooler, not as a condenser.

エバポレータ膨張装置の出口と冷媒吸入口との間に位置する冷媒蒸気圧縮システムの低圧側において、冷媒圧力および冷媒温度は関連付けられている。しかし、遷臨界運転では、圧縮装置の冷媒吐出口とエバポレータ膨張装置の入口との間に位置する冷媒蒸気圧縮システムの高圧側において、冷媒圧力および冷媒温度は互いに独立している。したがって、冷媒圧力は単一の設計作動点に対して最適化され得る。そのため、設計条件外では、冷媒充填が最適な冷媒充填より高いか低くなるため、冷媒蒸気圧縮システムは最適状態に及ばない場合がある。   On the low pressure side of the refrigerant vapor compression system located between the outlet of the evaporator expansion device and the refrigerant inlet, the refrigerant pressure and the refrigerant temperature are associated. However, in transcritical operation, the refrigerant pressure and the refrigerant temperature are independent of each other on the high pressure side of the refrigerant vapor compression system located between the refrigerant discharge port of the compressor and the inlet of the evaporator expansion device. Thus, the refrigerant pressure can be optimized for a single design operating point. For this reason, the refrigerant vapor compression system may not reach the optimum state because the refrigerant charge is higher or lower than the optimum refrigerant charge outside the design conditions.

米国特許出願公開第２００５／０１３２７２９Ａ１号明細書には、冷媒貯蔵容器を有する遷臨界冷媒蒸気圧縮システムが開示されており、この冷媒貯蔵容器は可変の冷媒質量を受容し、これによりシステムの容量が制御される。   US 2005/0132729 A1 discloses a transcritical refrigerant vapor compression system having a refrigerant storage container that receives a variable refrigerant mass, thereby reducing the capacity of the system. Be controlled.

上記明細書の開示では、冷媒貯蔵容器は、流体に対して蒸発膨張装置の上流でかつ冷媒放熱用熱交換器の下流の位置において、単一の冷媒ラインを介して閉ループ冷媒回路と常に開放状態で流体連通している。冷媒貯蔵容器内の冷媒質量は、容器の温度の調節または容器内の貯蔵容積の調節によって制御される。このため、永続的または一時的に冷媒システムに付与される付加的な測定可能な出力が要求されることとなる。   In the disclosure of the above specification, the refrigerant storage container is always open with the closed-loop refrigerant circuit via a single refrigerant line at a position upstream of the evaporation expansion device and downstream of the refrigerant heat dissipation heat exchanger with respect to the fluid. In fluid communication. The mass of the refrigerant in the refrigerant storage container is controlled by adjusting the temperature of the container or adjusting the storage volume in the container. This requires an additional measurable output that is permanently or temporarily applied to the refrigerant system.

本発明の一態様では、冷媒蒸気圧縮システムは、閉ループ冷媒回路において直列の冷媒連通関係でそれぞれ配設された冷媒圧縮装置、冷媒放熱用熱交換器、膨張装置および冷媒吸熱用熱交換器と、少なくとも１つの冷媒ラインにより閉ループ冷媒回路と流体連通関係で接続されるとともに貯蔵容積を画定する冷媒貯蔵装置と、少なくとも１つの冷媒ラインに配される冷媒流制御装置と、を備える。冷媒流制御装置は、少なくとも１つの冷媒ラインを通る冷媒の流れを許容する開位置、および少なくとも１つの冷媒ラインを通る冷媒の流れを遮断する閉位置を有する。一実施例では、コントローラは、冷媒流制御装置と関連して作動し、冷媒流制御装置を開位置および閉位置に選択的に配置する。   In one aspect of the present invention, a refrigerant vapor compression system includes a refrigerant compression device, a refrigerant heat dissipation heat exchanger, an expansion device, and a refrigerant heat absorption heat exchanger that are respectively arranged in a serial refrigerant communication relationship in a closed loop refrigerant circuit; A refrigerant storage device connected in fluid communication with a closed-loop refrigerant circuit by at least one refrigerant line and defining a storage volume; and a refrigerant flow control device arranged in the at least one refrigerant line. The refrigerant flow control device has an open position that allows the flow of refrigerant through at least one refrigerant line, and a closed position that blocks the flow of refrigerant through at least one refrigerant line. In one embodiment, the controller operates in conjunction with the refrigerant flow control device and selectively places the refrigerant flow control device in an open position and a closed position.

一実施例では、冷媒貯蔵装置の貯蔵容積は、閉ループ冷媒回路と流体連通する単一の冷媒ラインによって、冷媒流との関係において膨張装置の上流で冷媒蒸気圧縮システムの高圧側の位置に接続され、膨張装置は、冷媒放熱用熱交換器の下流でかつ冷媒吸熱用熱交換器の上流で閉ループ冷媒回路に配設される。一実施例では、冷媒貯蔵装置の貯蔵容積は、閉ループ冷媒回路と流体連通する単一の冷媒ラインによって、冷媒流に関して膨張装置の下流で冷媒蒸気圧縮システムの低圧側の位置に接続される。   In one embodiment, the storage volume of the refrigerant storage device is connected to a position on the high pressure side of the refrigerant vapor compression system upstream of the expansion device in relation to the refrigerant flow by a single refrigerant line in fluid communication with the closed loop refrigerant circuit. The expansion device is disposed in the closed-loop refrigerant circuit downstream of the refrigerant heat dissipation heat exchanger and upstream of the refrigerant heat absorption heat exchanger. In one embodiment, the storage volume of the refrigerant storage device is connected to a low pressure side location of the refrigerant vapor compression system downstream of the expansion device with respect to the refrigerant flow by a single refrigerant line in fluid communication with the closed loop refrigerant circuit.

本発明の一態様では、冷媒蒸気圧縮システムは、閉ループ冷媒回路において直列の冷媒連通関係でそれぞれ配設された冷媒圧縮装置、冷媒放熱用熱交換器、膨張装置および冷媒吸熱用熱交換器と、上方領域および下方領域を有する貯蔵容積を画定する冷媒貯蔵装置と、を備え、上方領域は、閉ループ冷媒回路と流体連通する第１の冷媒ラインにより、冷媒流との関係において膨張装置の上流の冷媒蒸気圧縮システムの高温側の位置に接続され、下方領域は、閉ループ冷媒回路と流体連通する第２の冷媒ラインにより、冷媒流に関して膨張装置の下流の冷媒蒸気圧縮システムの低圧側の位置に接続される。第１の冷媒流制御装置は第１の冷媒ラインに配され、第２の冷媒流制御装置は第２の冷媒ラインに配される。各冷媒流制御装置は、開位置および閉位置を有する。一実施例では、各冷媒流制御装置は、開位置および閉位置を有するソレノイドバルブを含む。冷媒蒸気圧縮システムは、第１および第２の冷媒流制御装置と関連して作動するコントローラをさらに備え、該コントローラは、第１および第２の冷媒流制御装置の一方を選択的に開位置に配置し、同時に他方の冷媒流制御装置を選択的に閉位置に配置する。   In one aspect of the present invention, a refrigerant vapor compression system includes a refrigerant compression device, a refrigerant heat dissipation heat exchanger, an expansion device, and a refrigerant heat absorption heat exchanger that are respectively arranged in a serial refrigerant communication relationship in a closed loop refrigerant circuit; A refrigerant storage device defining a storage volume having an upper region and a lower region, wherein the upper region is a refrigerant upstream of the expansion device in relation to the refrigerant flow by a first refrigerant line in fluid communication with the closed loop refrigerant circuit. The lower region is connected to the low pressure side position of the refrigerant vapor compression system downstream of the expansion device with respect to the refrigerant flow by a second refrigerant line in fluid communication with the closed loop refrigerant circuit. The The first refrigerant flow control device is arranged in the first refrigerant line, and the second refrigerant flow control device is arranged in the second refrigerant line. Each refrigerant flow control device has an open position and a closed position. In one embodiment, each refrigerant flow control device includes a solenoid valve having an open position and a closed position. The refrigerant vapor compression system further includes a controller that operates in conjunction with the first and second refrigerant flow controllers, wherein the controller selectively places one of the first and second refrigerant flow controllers into the open position. And, at the same time, selectively arrange the other refrigerant flow control device in the closed position.

本発明の一態様では、遷臨界サイクルで作動する冷媒蒸気圧縮システムにおいて冷媒の充填を管理する方法を提供する。冷媒蒸気圧縮システムは、閉ループ冷媒回路において直列の冷媒連通関係でそれぞれ配設された冷媒圧縮装置、冷媒放熱用熱交換器および冷媒吸熱用熱交換器と、冷媒放熱用熱交換器の下流でかつ冷媒吸熱用熱交換器上流で閉ループ冷媒回路に配設された膨張装置と、を備える。前記方法は、冷媒蒸気圧縮システムの閉ループ冷媒回路から冷媒を選択的に取り除くステップと、取り除いた冷媒を冷媒貯蔵装置に貯蔵するステップと、冷媒貯蔵装置から冷媒蒸気圧縮システムの閉ループ冷媒回路へと冷媒を戻すステップと、を含む。   In one aspect of the invention, a method for managing refrigerant charge in a refrigerant vapor compression system operating in a transcritical cycle is provided. The refrigerant vapor compression system includes a refrigerant compression device, a refrigerant heat dissipation heat exchanger, a refrigerant heat absorption heat exchanger, and a refrigerant heat dissipation heat exchanger, which are respectively arranged in series communication relationship in a closed loop refrigerant circuit, and An expansion device disposed in a closed loop refrigerant circuit upstream of the refrigerant heat absorption heat exchanger. The method includes selectively removing refrigerant from a closed loop refrigerant circuit of a refrigerant vapor compression system, storing the removed refrigerant in a refrigerant storage device, and refrigerant from the refrigerant storage device to a closed loop refrigerant circuit of the refrigerant vapor compression system. Returning.

冷媒貯蔵装置が高圧側の位置で閉ループ冷媒回路に接続されている場合、冷媒は、通常、冷媒蒸気圧縮システムの作動サイクル中に閉ループ冷媒回路から取り除かれ、冷媒蒸気圧縮システムのオフサイクル中に閉ループ冷媒回路に戻される。本実施例の方法では、冷媒は、膨張装置の上流に位置する高圧側の位置で閉ループ冷媒回路から取り除かれ、取り除かれた冷媒は、膨張装置の上流の位置で閉ループ冷媒回路に戻される。   When the refrigerant storage device is connected to the closed loop refrigerant circuit at the high pressure side, the refrigerant is typically removed from the closed loop refrigerant circuit during the refrigerant vapor compression system operating cycle and closed loop during the refrigerant vapor compression system off cycle. Returned to the refrigerant circuit. In the method of the present embodiment, the refrigerant is removed from the closed loop refrigerant circuit at a high-pressure side position located upstream of the expansion device, and the removed refrigerant is returned to the closed loop refrigerant circuit at a position upstream of the expansion device.

冷媒貯蔵装置が低圧側の位置で閉ループ冷媒回路に接続されている場合、冷媒は、通常、冷媒蒸気圧縮システムのオフサイクル中に閉ループ冷媒回路から取り除かれ、冷媒蒸気圧縮システムの作動中に閉ループ冷媒回路に戻される。本実施例の方法では、冷媒は、膨張装置の下流に位置する低圧側の位置で閉ループ冷媒回路から取り除かれ、取り除かれた冷媒は、膨張装置の下流の位置で閉ループ冷媒回路に戻される。   When the refrigerant storage device is connected to the closed loop refrigerant circuit at a low pressure position, the refrigerant is typically removed from the closed loop refrigerant circuit during the off cycle of the refrigerant vapor compression system and closed loop refrigerant during operation of the refrigerant vapor compression system. Returned to the circuit. In the method of the present embodiment, the refrigerant is removed from the closed loop refrigerant circuit at a low pressure side position located downstream of the expansion device, and the removed refrigerant is returned to the closed loop refrigerant circuit at a position downstream of the expansion device.

冷媒貯蔵装置が２つの位置（つまり、一方が高圧側、他方が低圧側）において閉ループ冷媒回路に接続されている場合、冷媒は、通常、冷媒蒸気圧縮システムの作動サイクル中に閉ループ冷媒回路から取り除かれ、冷媒蒸気圧縮システムの作動サイクル中に閉ループ冷媒回路に戻される。本実施例の方法では、冷媒は、膨張装置の上流に位置する高圧側の位置で閉ループ冷媒回路から取り除かれ、取り除かれた冷媒は、膨張装置の下流に位置する低圧側の位置で閉ループ冷媒回路に戻される。   If the refrigerant storage device is connected to the closed loop refrigerant circuit in two positions (ie, one on the high pressure side and the other on the low pressure side), the refrigerant is typically removed from the closed loop refrigerant circuit during the operating cycle of the refrigerant vapor compression system. And returned to the closed loop refrigerant circuit during the operating cycle of the refrigerant vapor compression system. In the method of this embodiment, the refrigerant is removed from the closed-loop refrigerant circuit at a high-pressure side position located upstream of the expansion device, and the removed refrigerant is closed-loop refrigerant circuit at a low-pressure side position located downstream of the expansion device. Returned to

本発明をさらに理解するために、以下に記載した発明を実施するための形態を参照されたい。これに付随する図面について以下に簡単に説明する。   For a better understanding of the present invention, reference is made to the following detailed description. The accompanying drawings will be briefly described below.

本発明による冷媒蒸気圧縮システムの第１の例示的な実施例を示す概略図。1 is a schematic diagram illustrating a first exemplary embodiment of a refrigerant vapor compression system according to the present invention. 本発明による冷媒蒸気圧縮システムの第２の例示的な実施例を示す概略図。FIG. 3 is a schematic diagram illustrating a second exemplary embodiment of a refrigerant vapor compression system according to the present invention. 本発明による冷媒蒸気圧縮システムの第３の例示的な実施例を示す概略図。FIG. 3 is a schematic diagram illustrating a third exemplary embodiment of a refrigerant vapor compression system according to the present invention.

図１〜３を参照すると、冷媒蒸気圧縮システム１０は、圧縮装置２０と、冷媒放熱用熱交換器４０と、冷媒吸熱用熱交換器５０（エバポレータとも呼ぶ）と、を備えており、これらの構成要素は、冷媒閉回路において種々の冷媒ライン２，４，６により直列の冷媒流関係で接続されている。さらに、エバポレータ５０と関連して作動する膨張装置５５が、冷媒ライン４において、冷媒流との関係で冷媒放熱用熱交換器４０の下流側でかつ冷媒吸熱用熱交換器５０の上流側に配置されている。図１〜３に示した冷媒蒸気圧縮システム１０の実施例では、膨張装置５５は電子膨張弁である。しかし、膨張装置は、感温式膨張弁、もしくはキャピラリチューブなどの固定オリフィス装置であってもよいことを理解されたい。   Referring to FIGS. 1 to 3, the refrigerant vapor compression system 10 includes a compression device 20, a refrigerant heat dissipation heat exchanger 40, and a refrigerant heat absorption heat exchanger 50 (also referred to as an evaporator). The components are connected in a serial refrigerant flow relationship by various refrigerant lines 2, 4, 6 in a refrigerant closed circuit. Further, an expansion device 55 that operates in association with the evaporator 50 is disposed in the refrigerant line 4 on the downstream side of the refrigerant heat dissipation heat exchanger 40 and the upstream side of the refrigerant heat absorption heat exchanger 50 in relation to the refrigerant flow. Has been. In the embodiment of the refrigerant vapor compression system 10 shown in FIGS. 1 to 3, the expansion device 55 is an electronic expansion valve. However, it should be understood that the expansion device may be a temperature sensitive expansion valve or a fixed orifice device such as a capillary tube.

冷媒蒸気圧縮システム１０が遷臨界（トランスクリティカル）サイクルで作動する場合、例えば、二酸化炭素冷媒が充填されていてコンプレッサの吐出圧が二酸化炭素の臨界圧力を超過した状態で作動するときには、冷媒放熱用熱交換器４０は、超臨界（スーパークリティカル）圧力で作動し、冷媒ガスクーラとして機能するが、二酸化炭素冷媒蒸気を凝縮するように作動しない。冷媒放熱用熱交換器４０のチューブ列４２には、例えば、従来のラウンドチューブ・プレートフィン型熱交換器のチューブ列などのプレートフィン・ラウンドチューブ列やミニチャネルまたはマイクロチャネル熱交換器の波形のフィン・マルチチャネルフラットチューブ列が含まれる。冷媒が冷媒放熱用熱交換器４０を通過するときに、冷媒は、チューブ列４２の熱交換チューブを通流し、通常は周囲空気（一般的に外気）である第２の流体と熱交換し、この第２の流体は、冷媒放熱用熱交換器４０のチューブ列４２と関連して作動する空気移動装置４４（例えば、１つまたは複数のファン）によってチューブ列４２を通して引き込まれる。   When the refrigerant vapor compression system 10 operates in a transcritical cycle, for example, when the refrigerant is compressed with carbon dioxide refrigerant and the discharge pressure of the compressor exceeds the critical pressure of carbon dioxide, The heat exchanger 40 operates at supercritical pressure and functions as a refrigerant gas cooler, but does not operate to condense the carbon dioxide refrigerant vapor. The tube row 42 of the refrigerant heat radiating heat exchanger 40 includes, for example, a plate fin / round tube row such as a tube row of a conventional round tube / plate fin type heat exchanger or a waveform of a mini-channel or micro-channel heat exchanger. A fin multi-channel flat tube row is included. When the refrigerant passes through the heat radiating heat exchanger 40, the refrigerant flows through the heat exchange tubes of the tube row 42 and exchanges heat with the second fluid, which is usually ambient air (generally outside air), This second fluid is drawn through the tube row 42 by an air moving device 44 (eg, one or more fans) that operates in conjunction with the tube row 42 of the refrigerant heat dissipating heat exchanger 40.

冷媒蒸気圧縮システム１０が亜臨界（サブクリティカル）サイクルまたは遷臨界サイクルで作動する場合でも、冷媒回路において冷媒流に関して膨張装置５５の下流側に配置された冷媒吸熱用熱交換器５０は、常に、亜臨界圧力で作動し、エバポレータとして機能する。冷媒が冷媒吸熱用熱交換器５０を通過するときには、冷媒は、チューブ列５２の熱交換チューブを通流し、調和される空気、一般に温度制御環境から引き込まれ該環境に戻される空気と熱交換し、この空気は、冷媒吸熱用熱交換器５０のチューブ列５２と関連して作動する空気移動装置５４（例えば、１つまたは複数のファン）によってチューブ列５２を通して引き込まれる。これにより、空気は冷却され、冷媒は過熱されて気化する。冷媒吸熱用熱交換器５０のチューブ列５２には、例えば、従来のラウンドチューブ・プレートフィン型熱交換器のチューブ列のプレートフィン・ラウンドチューブ列などのフィン付きチューブ型熱交換やミニチャネルまたはマイクロチャネル熱交換器の波形のフィン・マルチチャネルフラットチューブ列が含まれる。   Even when the refrigerant vapor compression system 10 operates in a subcritical or transcritical cycle, the refrigerant endothermic heat exchanger 50 disposed downstream of the expansion device 55 with respect to the refrigerant flow in the refrigerant circuit is always Operates at subcritical pressure and functions as an evaporator. When the refrigerant passes through the refrigerant heat absorption heat exchanger 50, the refrigerant flows through the heat exchange tubes of the tube row 52 and exchanges heat with the conditioned air, generally the air drawn from the temperature controlled environment and returned to the environment. The air is drawn through the tube row 52 by an air moving device 54 (eg, one or more fans) that operates in conjunction with the tube row 52 of the refrigerant heat sink heat exchanger 50. Thereby, air is cooled and the refrigerant is superheated and vaporized. The tube row 52 of the refrigerant heat absorption heat exchanger 50 includes, for example, a tube type heat exchange with fins such as a plate fin / round tube row of a conventional round tube / plate fin type heat exchanger, mini-channel or micro A channel heat exchanger corrugated fin multi-channel flat tube row is included.

圧縮装置２０は、後述するように冷媒を圧縮し、かつ冷媒回路に冷媒を循環させるように機能する。圧縮装置２０は、図示したように、１つの段からなる単一のコンプレッサとすることができ、該コンプレッサは、例えば、スクロールコンプレッサ、往復コンプレッサ、ロータリコンプレッサ、スクリューコンプレッサおよび遠心コンプレッサである。しかし、圧縮装置２０は、少なくとも低圧圧縮段および高圧圧縮段を有し、冷媒流が低圧圧縮段から高圧圧縮段へと通流する多段圧縮装置としてもよいことを理解されたい。上記の実施例では、複数の段からなる圧縮装置は、複数の段からなる単一のコンプレッサ、例えば、スクロールコンプレッサ、あるいは段状の圧縮ポケットを有したスクリューコンプレッサ、あるいは少なくとも第１のシリンダ列および第２のシリンダ列を有した往復コンプレッサ、あるいは冷媒流との関係においてコンプレッサの上流側の吐出口とコンプレッサの下流側の吸入口とを直列に接続する一対の段からなるコンプレッサとすることができる。圧縮装置２０は、並列または直列で作動する２つまたは複数の圧縮機を含んでいてもよい。   The compression device 20 functions to compress the refrigerant and circulate the refrigerant in the refrigerant circuit as will be described later. As shown, the compressor 20 can be a single compressor consisting of a single stage, such as a scroll compressor, a reciprocating compressor, a rotary compressor, a screw compressor and a centrifugal compressor. However, it should be understood that the compression device 20 may be a multi-stage compression device having at least a low pressure compression stage and a high pressure compression stage, with the refrigerant stream flowing from the low pressure compression stage to the high pressure compression stage. In the above embodiment, the multi-stage compression apparatus includes a single multi-stage compressor, such as a scroll compressor, or a screw compressor having a stage-like compression pocket, or at least a first cylinder row and A reciprocating compressor having a second cylinder row, or a compressor composed of a pair of stages in which a discharge port on the upstream side of the compressor and a suction port on the downstream side of the compressor are connected in series in relation to the refrigerant flow. . The compression device 20 may include two or more compressors that operate in parallel or in series.

冷媒蒸気圧縮システム１０は、変動する冷媒が貯蔵される容積を画定する冷媒貯蔵装置（レシーバ）６０を含む。レシーバ６０は、少なくとも１つの冷媒ラインを介して冷媒蒸気圧縮システム１０の閉ループ冷媒回路と流体連通する。冷媒蒸気圧縮システム１０は、冷媒蒸気圧縮システム１０の閉ループ冷媒回路と流体連通するレシーバ６０を接続する少なくとも１つの冷媒ラインに配された冷媒流制御装置と関連して作動するコントローラ１００をさらに備える。少なくとも１つの冷媒ラインを通流する冷媒流は、冷媒流制御装置を選択的に開閉することによって制御される。   The refrigerant vapor compression system 10 includes a refrigerant storage device (receiver) 60 that defines a volume in which fluctuating refrigerant is stored. The receiver 60 is in fluid communication with the closed loop refrigerant circuit of the refrigerant vapor compression system 10 via at least one refrigerant line. The refrigerant vapor compression system 10 further includes a controller 100 that operates in conjunction with a refrigerant flow control device disposed in at least one refrigerant line that connects a receiver 60 in fluid communication with the closed loop refrigerant circuit of the refrigerant vapor compression system 10. The refrigerant flow through the at least one refrigerant line is controlled by selectively opening and closing the refrigerant flow control device.

図１に示す実施例において、レシーバ６０は、液体冷媒が受容される下方領域６３と、冷媒蒸気が存在する下方領域６７と、を有する容積を画定する。特定の環境および作動状態では、レシーバ６０の全内部容積は冷媒蒸気で満たされる場合があることを理解されたい。上方領域６７は、冷媒流との関係において冷媒膨張装置５５の上流側でかつ冷媒放熱用熱交換器４０の下流側の位置において、冷媒蒸気圧縮システム１０の高圧側に配された冷媒ライン４と冷媒ライン１２を介して流体連通する。下方領域６３は、冷媒流に関して冷媒膨張装置５５の下流側でかつ冷媒吸熱用熱交換器５０の上流側の位置において、冷媒蒸気圧縮システム１０の低圧側に配された冷媒ライン４と冷媒ライン１４を介して流体連通する。さらに、開位置および閉位置を有する冷媒流制御装置６５が冷媒ライン１２に配され、開位置および閉位置を有する冷媒流制御装置７５が冷媒ライン１４に配される。レシーバ６０と冷媒流連通関係をなすように冷媒蒸気圧縮システム１０の高圧側および低圧側における他の位置を選択してもよいことを理解されたい。   In the embodiment shown in FIG. 1, the receiver 60 defines a volume having a lower region 63 in which liquid refrigerant is received and a lower region 67 in which refrigerant vapor is present. It should be understood that under certain circumstances and operating conditions, the entire internal volume of the receiver 60 may be filled with refrigerant vapor. The upper region 67 is connected to the refrigerant line 4 disposed on the high pressure side of the refrigerant vapor compression system 10 at a position upstream of the refrigerant expansion device 55 and downstream of the refrigerant heat dissipation heat exchanger 40 in relation to the refrigerant flow. Fluid communication is established via the refrigerant line 12. The lower region 63 has a refrigerant line 4 and a refrigerant line 14 arranged on the low pressure side of the refrigerant vapor compression system 10 at a position downstream of the refrigerant expansion device 55 and upstream of the refrigerant heat absorption heat exchanger 50 with respect to the refrigerant flow. Fluid communication via Further, a refrigerant flow control device 65 having an open position and a closed position is arranged in the refrigerant line 12, and a refrigerant flow control device 75 having an open position and a closed position is arranged in the refrigerant line 14. It should be understood that other locations on the high pressure side and low pressure side of the refrigerant vapor compression system 10 may be selected to be in refrigerant flow communication with the receiver 60.

本実施例では、コントローラ１００は、冷媒ライン１２，１４に配された各冷媒流制御装置６５，７５と作動可能に関連し、各冷媒流制御装置を開位置または閉位置へと選択的に配置する。コントローラ１００は、所定の作動点に対する圧縮装置２０からの所望の冷媒吐出圧を維持するため、冷媒ライン２，４，６によって画定される閉ループ冷媒回路を循環する冷媒の充填量を調節する。この調節は、冷媒流制御装置を開位置または閉位置を選択的に配置することにより、冷媒を閉ループ冷媒回路からレシーバ６０を通して閉ループ冷媒回路を循環する冷媒の充填量を減少させるか、あるいは冷媒をレシーバ６０から閉ループ冷媒回路へと通して閉ループ冷媒回路を循環する冷媒の充填量を増加させることによって行われる。したがって、閉ループ冷媒回路への冷媒の追加は、冷媒蒸気圧縮システム１０の低圧側においてなされ、冷媒の閉ループ冷媒回路からの除去は、冷媒蒸気圧縮システム１０の高圧側においてなされる。   In this embodiment, the controller 100 is operatively associated with each refrigerant flow control device 65, 75 disposed in the refrigerant line 12, 14, and selectively arranges each refrigerant flow control device to an open position or a closed position. To do. The controller 100 adjusts the amount of refrigerant that circulates in the closed loop refrigerant circuit defined by the refrigerant lines 2, 4, 6 in order to maintain the desired refrigerant discharge pressure from the compressor 20 for a given operating point. This adjustment can be accomplished by selectively placing the refrigerant flow control device in the open or closed position, thereby reducing the amount of refrigerant that circulates through the closed loop refrigerant circuit from the closed loop refrigerant circuit through the receiver 60, or This is done by increasing the amount of refrigerant that circulates through the closed-loop refrigerant circuit from the receiver 60 through the closed-loop refrigerant circuit. Therefore, the refrigerant is added to the closed loop refrigerant circuit on the low pressure side of the refrigerant vapor compression system 10, and the refrigerant is removed from the closed loop refrigerant circuit on the high pressure side of the refrigerant vapor compression system 10.

冷媒蒸気圧縮システム１０の閉ループ冷媒回路から冷媒を取り除くため、コントローラ１００は、通常、作動中に冷媒流制御装置６５を開位置に配置し、冷媒流制御装置７５を閉位置に配置する。このように冷媒流制御装置６５，７５を配置することにより、高圧の冷媒蒸気は冷媒ライン４から冷媒ライン１２を通ってレシーバ６０の貯蔵チャンバに流入する。しかし、該冷媒蒸気は、冷媒流制御装置７５が閉位置にあるため冷媒ライン１４を通ってレシーバ６０から流出しない。   To remove refrigerant from the closed loop refrigerant circuit of the refrigerant vapor compression system 10, the controller 100 typically places the refrigerant flow control device 65 in the open position and the refrigerant flow control device 75 in the closed position during operation. By arranging the refrigerant flow control devices 65 and 75 in this way, high-pressure refrigerant vapor flows from the refrigerant line 4 through the refrigerant line 12 into the storage chamber of the receiver 60. However, the refrigerant vapor does not flow out of the receiver 60 through the refrigerant line 14 because the refrigerant flow control device 75 is in the closed position.

冷媒蒸気圧縮システム１０の閉ループ冷媒回路に冷媒を追加するため（作動中またはオフサイクル時になされる）、コントローラ１００は、冷媒流制御装置６５を閉位置に配置し、冷媒流制御装置７５を開位置に配置する。このように冷媒流制御装置６５，７５を配置することにより、冷媒はレシーバ６０の貯蔵チャンバの下方領域６３から冷媒ライン１４を通って冷媒ライン４へと流れる。しかし、冷媒流制御装置６５が閉位置にあり、冷媒ライン１２を通る高圧の冷媒蒸気の流れが遮断されるため、高圧の冷媒蒸気はレシーバ６０に流入しない。特定の環境状態におけるオフサイクルの間に、冷媒は冷媒流制御装置６５，７５を通して冷媒蒸気圧縮システム１０の閉ループ冷媒回路に追加または該回路から除去されてもよいことを理解されたい。   To add refrigerant to the closed-loop refrigerant circuit of the refrigerant vapor compression system 10 (during operation or during off-cycle), the controller 100 places the refrigerant flow control device 65 in the closed position and opens the refrigerant flow control device 75 in the open position. To place. By arranging the refrigerant flow control devices 65 and 75 in this way, the refrigerant flows from the lower region 63 of the storage chamber of the receiver 60 to the refrigerant line 4 through the refrigerant line 14. However, since the refrigerant flow control device 65 is in the closed position and the flow of the high-pressure refrigerant vapor passing through the refrigerant line 12 is blocked, the high-pressure refrigerant vapor does not flow into the receiver 60. It should be understood that during off-cycles in certain environmental conditions, refrigerant may be added to or removed from the closed-loop refrigerant circuit of the refrigerant vapor compression system 10 through the refrigerant flow controllers 65, 75.

レシーバ６０の貯蔵チャンバは、貯蔵される冷媒量ともに変化する平衡圧を有する。この平衡圧は、冷媒蒸気圧縮システム１０の作動中、常に、膨張装置５５の上流に位置する冷媒ライン４における高圧側の冷媒圧力より低く、膨張装置５５の下流に位置する冷媒ライン４における低圧側の冷媒圧力より高い。冷媒蒸気圧縮システム１０の作動中、所定の時間の間、冷媒流制御装置６５を単に開にすることによって冷媒が閉ループ冷媒回路からレシーバ６０へと取り除かれる。冷媒ライン１２が膨張装置５５の上流の冷媒ライン４に接する位置における冷媒圧力と、レシーバ６０の貯蔵チャンバ内の平衡圧との圧力差により冷媒蒸気が冷媒ライン１２を通って流れる。冷媒蒸気圧縮システム１０の作動中、冷媒流制御装置７５を単に開にすることによってレシーバ６０から閉ループ冷媒回路に冷媒が追加される。レシーバ６０の貯蔵チャンバ内の平衡圧と、冷媒ライン１４が膨張装置５５の下流の冷媒ライン４に接する位置における冷媒圧力との圧力差により冷媒蒸気が冷媒ライン１４を通って流れる。   The storage chamber of the receiver 60 has an equilibrium pressure that varies with the amount of refrigerant stored. During the operation of the refrigerant vapor compression system 10, this equilibrium pressure is always lower than the high-pressure side refrigerant pressure in the refrigerant line 4 located upstream of the expansion device 55, and the low-pressure side in the refrigerant line 4 located downstream of the expansion device 55. Higher than the refrigerant pressure. During operation of the refrigerant vapor compression system 10, the refrigerant is removed from the closed loop refrigerant circuit to the receiver 60 by simply opening the refrigerant flow controller 65 for a predetermined time. The refrigerant vapor flows through the refrigerant line 12 due to the pressure difference between the refrigerant pressure at the position where the refrigerant line 12 contacts the refrigerant line 4 upstream of the expansion device 55 and the equilibrium pressure in the storage chamber of the receiver 60. During operation of the refrigerant vapor compression system 10, refrigerant is added from the receiver 60 to the closed loop refrigerant circuit by simply opening the refrigerant flow controller 75. The refrigerant vapor flows through the refrigerant line 14 due to the pressure difference between the equilibrium pressure in the storage chamber of the receiver 60 and the refrigerant pressure at the position where the refrigerant line 14 contacts the refrigerant line 4 downstream of the expansion device 55.

冷媒の温度および圧力は互いに独立しており、最適な高圧側の圧力は環境状態によって異なるため、上記のような冷媒充填管理は、冷媒蒸気圧縮システム１０の遷臨界での作動では特に重要であることを理解されたい。   Since the temperature and pressure of the refrigerant are independent from each other, and the optimum pressure on the high-pressure side varies depending on the environmental conditions, the refrigerant charging management as described above is particularly important in the transcritical operation of the refrigerant vapor compression system 10. Please understand that.

冷媒蒸気圧縮システム１０の例示的な実施例を示す図２を参照すると、レシーバ６０は、冷媒蒸気圧縮システム１０の高圧側および低圧側の双方に接続されるのではなく、単一の冷媒ライン１６を介して高圧側において閉ループ冷媒回路と冷媒流連通関係をなして接続される。冷媒ライン１６は冷媒放熱用熱交換器４０の下流でかつ膨張装置５５の上流で冷媒ライン４に接する。開位置および閉位置を有する冷媒流制御装置８５は、冷媒ライン１６に配される。コントローラ１００は、冷媒流制御装置８５と作動可能に関連して、冷媒流制御装置８５を選択的に開位置または閉位置に配置する。   Referring to FIG. 2 illustrating an exemplary embodiment of the refrigerant vapor compression system 10, the receiver 60 is not connected to both the high pressure side and the low pressure side of the refrigerant vapor compression system 10, but a single refrigerant line 16. And is connected in a refrigerant flow communication relationship with the closed-loop refrigerant circuit on the high-pressure side. The refrigerant line 16 contacts the refrigerant line 4 downstream of the refrigerant heat radiating heat exchanger 40 and upstream of the expansion device 55. A refrigerant flow control device 85 having an open position and a closed position is disposed in the refrigerant line 16. Controller 100 is operatively associated with refrigerant flow control device 85 and selectively places refrigerant flow control device 85 in the open or closed position.

本実施例において、コントローラ１００は、所定の作動点に対する圧縮装置２０からの所望の冷媒吐出圧を維持するため、冷媒ライン２，４，６によって画定される閉ループ冷媒回路を循環する冷媒の充填量を調節する。この調節は、冷媒を閉ループ冷媒回路からレシーバ６０へと通すか、または冷媒をレシーバ６０から閉ループ冷媒回路へと通すように冷媒流制御装置８５を開位置に選択的に配置することによって、あるいは冷媒ライン１６を通る冷媒を遮断するように冷媒流制御装置８５を閉位置に選択的に配置することによって行われる。システム１０の作動中、コントローラ１００が現時点の作動状態において冷媒充填量が過度であると判断した場合、コントローラ１００は、冷媒流制御装置８５を開にして、冷媒蒸気をレシーバ６０へと流す。冷媒充填量が所望のように減少されると、コントローラ１００は冷媒流制御装置８５を閉にし、レシーバ６０内に高圧の冷媒蒸気を閉じこめる。システム１０がオフサイクルの場合、コントローラ１００は、冷媒流制御装置８５を開にすることにより、高圧の冷媒蒸気をレシーバ６０から冷媒ライン１６を通して冷媒ライン４へと流出させ、冷媒蒸気を閉ループ冷媒回路に戻してシステムの冷媒充填量を増加させる。コントローラ１００がシステムの冷媒充填量が十分であると判断した場合、コントローラ１００は、冷媒流制御装置８５を再び閉にし、これにより、冷媒蒸気圧縮システム１０が作動状態に戻ったときに冷媒蒸気がレシーバ６０に流入しないようにする。前述のように、冷媒ライン１６の接続位置は、冷媒蒸気圧縮システム１０の高圧側の任意の位置とすることができる。   In this embodiment, the controller 100 fills the refrigerant that circulates in the closed-loop refrigerant circuit defined by the refrigerant lines 2, 4, 6 in order to maintain a desired refrigerant discharge pressure from the compressor 20 with respect to a predetermined operating point. Adjust. This adjustment can be accomplished by selectively placing the refrigerant flow control device 85 in the open position to pass refrigerant from the closed loop refrigerant circuit to the receiver 60, or to pass refrigerant from the receiver 60 to the closed loop refrigerant circuit, or This is done by selectively placing the refrigerant flow control device 85 in the closed position so as to block the refrigerant passing through the line 16. During operation of the system 10, if the controller 100 determines that the refrigerant charge is excessive in the current operating state, the controller 100 opens the refrigerant flow control device 85 and causes the refrigerant vapor to flow to the receiver 60. When the refrigerant charge is reduced as desired, the controller 100 closes the refrigerant flow control device 85 and traps the high-pressure refrigerant vapor in the receiver 60. When the system 10 is off-cycle, the controller 100 opens the refrigerant flow control device 85 to cause the high-pressure refrigerant vapor to flow out from the receiver 60 through the refrigerant line 16 to the refrigerant line 4, and the refrigerant vapor is closed loop refrigerant circuit. To increase the refrigerant charge of the system. If the controller 100 determines that the system refrigerant charge is sufficient, the controller 100 closes the refrigerant flow control device 85 again, so that the refrigerant vapor is not generated when the refrigerant vapor compression system 10 returns to the operating state. Do not flow into the receiver 60. As described above, the connection position of the refrigerant line 16 can be any position on the high-pressure side of the refrigerant vapor compression system 10.

次に冷媒蒸気圧縮システム１０の例示的な実施例を示す図３を参照すると、レシーバ６０は、冷媒蒸気圧縮システム１０の高圧側および低圧側の双方に接続されるのではなく、単一の冷媒ライン１８を介して低圧側において閉ループ冷媒回路と冷媒流連通関係をなして接続される。冷媒ライン１８は膨張装置５５の下流でかつ冷媒吸熱用熱交換器５０の上流で冷媒ライン４に接する。開位置および閉位置を有する冷媒流制御装置９５は、冷媒ライン１８に配される。コントローラ１００は、冷媒流制御装置９５と作動可能に関連して、冷媒流制御装置９５を選択的に開位置または閉位置に配置する。   Referring now to FIG. 3, which shows an exemplary embodiment of the refrigerant vapor compression system 10, the receiver 60 is not connected to both the high pressure side and the low pressure side of the refrigerant vapor compression system 10, but a single refrigerant. It is connected via a line 18 in a refrigerant flow communication relationship with the closed loop refrigerant circuit on the low pressure side. The refrigerant line 18 contacts the refrigerant line 4 downstream of the expansion device 55 and upstream of the refrigerant heat absorption heat exchanger 50. A refrigerant flow control device 95 having an open position and a closed position is disposed in the refrigerant line 18. Controller 100 is operatively associated with refrigerant flow control device 95 and selectively places refrigerant flow control device 95 in the open or closed position.

本実施例において、コントローラ１００は、所定の作動点に対する圧縮装置２０からの所望の冷媒吐出圧を維持するため、冷媒ライン２，４，６によって画定される閉ループ冷媒回路を循環する冷媒の充填量を調節する。この調節は、液体冷媒を閉ループ冷媒回路からレシーバ６０へと通すか、または液体冷媒をレシーバ６０から閉ループ冷媒回路へと通すように冷媒流制御装置９５を開位置に選択的に配置することによって、および冷媒ライン１８を通る冷媒を遮断するように冷媒流制御装置９５を閉位置に選択的に配置することによって行われる。コントローラ１００が現時点の作動状態において冷媒充填量が過度であると判断した場合、コントローラ１００は、冷媒蒸気圧縮システム１０をシャットダウンし、冷媒蒸気圧縮システム１０がオフサイクルの間は冷媒流制御装置９５を開にして、冷媒ライン１８を通して冷媒をレシーバ６０へと流す。冷媒充填量が所望のように減少されると、コントローラ１００は冷媒流制御装置９５を閉にし、レシーバ６０内に冷媒蒸気を閉じこめ、冷媒蒸気圧縮システム１０の作動が再開される。冷媒蒸気圧縮システム１０の作動中、コントローラ１００は、冷媒流制御装置９５を開にすることにより、冷媒蒸気をレシーバ６０から冷媒ライン１８を通して冷媒ライン４へと流出させ、冷媒を閉ループ冷媒回路に戻してシステムの冷媒充填量を増加させる。コントローラ１００がシステムの冷媒充填量が十分であると判断した場合、コントローラ１００は、冷媒流制御装置９５を再び閉にし、これにより、レシーバ６０からの冷媒の流れが遮断される。前述のように、冷媒ライン１８の接続位置は、冷媒蒸気圧縮システム１０の低圧側の任意の位置としてもよい。   In this embodiment, the controller 100 fills the refrigerant that circulates in the closed-loop refrigerant circuit defined by the refrigerant lines 2, 4, 6 in order to maintain a desired refrigerant discharge pressure from the compressor 20 with respect to a predetermined operating point. Adjust. This adjustment is accomplished by selectively placing the refrigerant flow controller 95 in the open position to pass liquid refrigerant from the closed loop refrigerant circuit to the receiver 60 or to pass liquid refrigerant from the receiver 60 to the closed loop refrigerant circuit. And the refrigerant flow control device 95 is selectively disposed at the closed position so as to block the refrigerant passing through the refrigerant line 18. If the controller 100 determines that the refrigerant charge amount is excessive in the current operating state, the controller 100 shuts down the refrigerant vapor compression system 10 and activates the refrigerant flow control device 95 during the off-cycle of the refrigerant vapor compression system 10. Open and allow the refrigerant to flow through the refrigerant line 18 to the receiver 60. When the refrigerant charge is reduced as desired, the controller 100 closes the refrigerant flow control device 95, traps the refrigerant vapor in the receiver 60, and the operation of the refrigerant vapor compression system 10 is resumed. During operation of the refrigerant vapor compression system 10, the controller 100 opens the refrigerant flow control device 95 to cause refrigerant vapor to flow from the receiver 60 through the refrigerant line 18 to the refrigerant line 4 and return the refrigerant to the closed loop refrigerant circuit. Increase the refrigerant charge in the system. If the controller 100 determines that the refrigerant charge of the system is sufficient, the controller 100 closes the refrigerant flow control device 95 again, thereby blocking the refrigerant flow from the receiver 60. As described above, the connection position of the refrigerant line 18 may be an arbitrary position on the low pressure side of the refrigerant vapor compression system 10.

冷媒流制御装置６５，７５，８５，９５は、少なくとも第１の開位置および第２の閉位置に選択的に位置変更可能である流れ制御装置を含む。第１の開位置では冷媒流制御装置が配設される冷媒ラインを冷媒が通流し、第２の閉位置では冷媒流制御装置が配設される冷媒ラインを冷媒が通流しないように遮断される。例えば、各冷媒流制御装置６５，７５，８５，９５は、２位置ソレノイドバルブを含んでいてもよい。一実施例では、冷媒貯蔵装置（レシーバ）６０においてより正確に冷媒量を制御することができるように、冷媒ライン１２，１４の少なくとも一方は、例えば、付加的なオリフィスやキャピラリーチューブを備えていてもよい。オリフィスやキャピラリーチューブにより、冷媒貯蔵装置６０に対する又は該装置６０からの冷媒の移行プロセスが減速し、これにより、冷媒貯蔵装置においてより正確に冷媒量を制御することが可能となる。オリフィスは、バルブ機構の一部であってもよく、または独立した冷媒流制御装置としてもよい。   The refrigerant flow control devices 65, 75, 85, and 95 include a flow control device that can be selectively repositioned to at least a first open position and a second closed position. In the first open position, the refrigerant flows through the refrigerant line in which the refrigerant flow control device is disposed, and in the second closed position, the refrigerant is blocked from flowing through the refrigerant line in which the refrigerant flow control device is disposed. The For example, each refrigerant flow control device 65, 75, 85, 95 may include a two-position solenoid valve. In one embodiment, at least one of the refrigerant lines 12, 14 includes, for example, an additional orifice or capillary tube so that the refrigerant amount can be controlled more accurately in the refrigerant storage device (receiver) 60. Also good. The orifice or capillary tube slows down the refrigerant transfer process to or from the refrigerant storage device 60, thereby enabling more accurate control of the refrigerant amount in the refrigerant storage device. The orifice may be part of the valve mechanism or may be an independent refrigerant flow control device.

冷媒蒸気圧縮システム１０は、圧縮機２０に蒸気の注入を行うエコノマイザーサイクルを有していてもよい。また、冷媒蒸気圧縮システム１０は、圧縮機２０内の圧縮プロセスを冷却する液体の注入を行うようにしてもよい。第２の流体移動装置４４，５４は、冷媒蒸気圧縮システム１０の閉ループ冷媒回路を循環する冷媒と熱交換関係にある水またはグリコール水溶液などの液体を循環させるポンプを含んでいてもよい。   The refrigerant vapor compression system 10 may have an economizer cycle that injects steam into the compressor 20. Further, the refrigerant vapor compression system 10 may inject a liquid for cooling the compression process in the compressor 20. The second fluid moving devices 44 and 54 may include a pump that circulates a liquid such as water or an aqueous glycol solution that is in a heat exchange relationship with the refrigerant circulating in the closed loop refrigerant circuit of the refrigerant vapor compression system 10.

図を参照しながら発明を実施するための形態について図示、説明したが、当業者であれば、本発明の精神および範囲を逸脱することなく種々の変更がなされることを理解されるであろう。   While the invention has been illustrated and described with reference to the drawings, those skilled in the art will recognize that various modifications can be made without departing from the spirit and scope of the invention. .

Claims (19)

閉ループ冷媒回路において直列の冷媒連通関係をなしてそれぞれ配設された、冷媒圧縮装置と、圧縮装置からの冷媒を冷却媒体と熱交換関係をなして高圧で通過させる冷媒放熱用熱交換器と、冷却される媒体と熱交換関係をなして低圧で冷媒を通過させる冷媒吸熱用熱交換器と、
冷媒放熱用熱交換器の下流でかつ冷媒吸熱用熱交換器の上流で閉ループ冷媒回路に配設された膨張装置と、
少なくとも１つの冷媒ラインによって閉ループ冷媒回路と流体連通して接続されるとともに、貯蔵容積を画定する冷媒貯蔵装置と、
少なくとも１つの冷媒ラインに配された冷媒流制御装置と、
を備え、
冷媒流制御装置は、冷媒が少なくとも１つの冷媒ラインを通流する開位置と、少なくとも１つの冷媒ラインを通る冷媒の流れを遮断する閉位置と、を有することを特徴とする冷媒蒸気圧縮システム。 A refrigerant compressor arranged in series in a closed loop refrigerant circuit, and a refrigerant heat dissipating heat exchanger for passing the refrigerant from the compressor at a high pressure in a heat exchange relationship with the cooling medium; A refrigerant heat absorption heat exchanger that allows the refrigerant to pass at low pressure in a heat exchange relationship with the medium to be cooled;
An expansion device disposed in the closed loop refrigerant circuit downstream of the refrigerant heat dissipating heat exchanger and upstream of the refrigerant heat absorbing heat exchanger;
A refrigerant storage device connected in fluid communication with the closed loop refrigerant circuit by at least one refrigerant line and defining a storage volume;
A refrigerant flow control device arranged in at least one refrigerant line;
With
The refrigerant flow control device has an open position where the refrigerant flows through at least one refrigerant line, and a closed position where the refrigerant flow through the at least one refrigerant line is blocked. 冷媒流制御装置と関連して作動し、冷媒流制御装置を開位置および閉位置に選択的に配置するコントローラをさらに備えることを特徴とする請求項１に記載の冷媒蒸気圧縮システム。   The refrigerant vapor compression system of claim 1, further comprising a controller that operates in conjunction with the refrigerant flow control device and selectively places the refrigerant flow control device in an open position and a closed position. 冷媒貯蔵装置の貯蔵容積を流体連通関係で閉ループ冷媒回路と接続する少なくとも１つの冷媒ラインは、冷媒蒸気圧縮システムの高圧側の位置において閉ループ冷媒回路と流体連通する単一の冷媒ラインからなることを特徴とする請求項１に記載の冷媒蒸気圧縮システム。   The at least one refrigerant line connecting the storage volume of the refrigerant storage device with the closed loop refrigerant circuit in fluid communication is comprised of a single refrigerant line in fluid communication with the closed loop refrigerant circuit at a position on the high pressure side of the refrigerant vapor compression system. The refrigerant vapor compression system according to claim 1. 冷媒貯蔵装置の貯蔵容積を流体連通関係で閉ループ冷媒回路と接続する少なくとも１つの冷媒ラインは、冷媒蒸気圧縮システムの低圧側の位置において閉ループ冷媒回路と流体連通する単一の冷媒ラインからなることを特徴とする請求項１に記載の冷媒蒸気圧縮システム。   The at least one refrigerant line connecting the storage volume of the refrigerant storage device with the closed loop refrigerant circuit in fluid communication is comprised of a single refrigerant line in fluid communication with the closed loop refrigerant circuit at a low pressure side position of the refrigerant vapor compression system. The refrigerant vapor compression system according to claim 1. 冷媒貯蔵装置の貯蔵容積を流体連通関係で閉ループ冷媒回路と接続する少なくとも１つの冷媒ラインは、
冷媒貯蔵装置の貯蔵容積の上方部分を流体連通関係で冷媒蒸気圧縮システムの高圧側の位置において閉ループ冷媒回路と接続する第１の冷媒ラインと、
冷媒貯蔵装置の貯蔵容積の下方部分を流体連通関係で冷媒蒸気圧縮システムの低圧側の位置において閉ループ冷媒回路と接続する第２の冷媒ラインと、
を含むことを特徴とする請求項１に記載の冷媒蒸気圧縮システム。 At least one refrigerant line connecting the storage volume of the refrigerant storage device with the closed loop refrigerant circuit in fluid communication relationship;
A first refrigerant line connecting an upper portion of the storage volume of the refrigerant storage device with a closed loop refrigerant circuit at a high pressure side position of the refrigerant vapor compression system in fluid communication relation;
A second refrigerant line connecting a lower portion of the storage volume of the refrigerant storage device with a closed loop refrigerant circuit at a low pressure side position of the refrigerant vapor compression system in fluid communication relation;
The refrigerant vapor compression system according to claim 1, comprising: 少なくとも１つの冷媒ラインに配された冷媒流制御装置は、
第１の冷媒ラインに配された第１の冷媒流制御装置と、
第２の冷媒ラインに配された第２の冷媒流制御装置と、
を含むことを特徴とする請求項５に記載の冷媒蒸気圧縮システム。 The refrigerant flow control device arranged in at least one refrigerant line is:
A first refrigerant flow control device disposed in the first refrigerant line;
A second refrigerant flow control device disposed in the second refrigerant line;
The refrigerant vapor compression system according to claim 5, comprising: 冷媒蒸気圧縮システムは、少なくとも一定の時間の間、遷臨界サイクルで作動することを特徴とする請求項１に記載の冷媒蒸気圧縮システム。   The refrigerant vapor compression system of claim 1, wherein the refrigerant vapor compression system operates in a transcritical cycle for at least a fixed time. 冷媒蒸気圧縮システムを循環する冷媒は二酸化炭素であることを特徴とする請求項１に記載の冷媒蒸気圧縮システム。   The refrigerant vapor compression system according to claim 1, wherein the refrigerant circulating in the refrigerant vapor compression system is carbon dioxide. 閉ループ冷媒回路において直列の冷媒連通関係をなしてそれぞれ配設された、冷媒吐出口および冷媒吸入口を有する冷媒圧縮装置と、圧縮装置からの冷媒を冷却媒体と熱交換関係をなして高圧で通過させる冷媒放熱用熱交換器と、冷却される媒体と熱交換関係をなして低圧で冷媒を通過させる冷媒吸熱用熱交換器と、
冷媒放熱用熱交換器の下流でかつ冷媒吸熱用熱交換器の上流で閉ループ冷媒回路に配設された膨張装置と、
上方領域および下方領域を有するチャンバを画定する冷媒貯蔵装置と、
を備え、
第１の冷媒ラインによって、上方領域は冷媒流に関して膨張装置の上流位置において流体連通関係で閉ループ冷媒回路の高圧側に接続され、
第２の冷媒ラインによって、下方領域は、冷媒流に関して膨張装置の下流位置において流体連通関係で閉ループ冷媒回路の低圧側に接続されることを特徴とする冷媒蒸気圧縮システム。 A refrigerant compression device having a refrigerant discharge port and a refrigerant suction port, which are respectively arranged in series in a closed-loop refrigerant circuit and having a refrigerant discharge port and a refrigerant suction port, and the refrigerant from the compression device passes through the cooling medium at a high pressure. A refrigerant heat-dissipating heat exchanger, a refrigerant heat-absorbing heat exchanger that allows the refrigerant to pass at low pressure in a heat exchange relationship with the medium to be cooled,
An expansion device disposed in the closed loop refrigerant circuit downstream of the refrigerant heat dissipating heat exchanger and upstream of the refrigerant heat absorbing heat exchanger;
A refrigerant storage device defining a chamber having an upper region and a lower region;
With
By means of the first refrigerant line, the upper region is connected to the high-pressure side of the closed-loop refrigerant circuit in fluid communication at the upstream position of the expansion device with respect to the refrigerant flow,
A refrigerant vapor compression system, characterized in that, by means of a second refrigerant line, the lower region is connected to the low pressure side of the closed loop refrigerant circuit in fluid communication at a downstream position of the expansion device with respect to the refrigerant flow. 第１の冷媒ラインに配された第１の冷媒流制御装置と、
第２の冷媒ラインに配された第２の冷媒流制御装置と、
をさらに備えることを特徴とする請求項９に記載の冷媒蒸気圧縮システム。 A first refrigerant flow control device disposed in the first refrigerant line;
A second refrigerant flow control device disposed in the second refrigerant line;
The refrigerant vapor compression system according to claim 9, further comprising: 第１および第２の冷媒流制御装置は、開位置および閉位置をそれぞれ有することを特徴とする請求項１０に記載の冷媒蒸気圧縮システム。   The refrigerant vapor compression system according to claim 10, wherein the first and second refrigerant flow control devices have an open position and a closed position, respectively. 第１および第２の冷媒流制御装置は、開位置および閉位置を有するソレノイドバルブをそれぞれ含むことを特徴とする請求項１１に記載の冷媒蒸気圧縮システム。   The refrigerant vapor compression system according to claim 11, wherein the first and second refrigerant flow control devices each include a solenoid valve having an open position and a closed position. 第１および第２の冷媒流制御装置と関連して作動するコントローラをさらに備え、該コントローラは、第１および第２の冷媒流制御装置の一方を選択的に開位置に配置し、同時に他方の冷媒流制御装置を選択的に閉位置に配置することを特徴とする請求項１０に記載の冷媒蒸気圧縮システム。   A controller that operates in conjunction with the first and second refrigerant flow control devices, wherein the controller selectively places one of the first and second refrigerant flow control devices in the open position and simultaneously The refrigerant vapor compression system according to claim 10, wherein the refrigerant flow control device is selectively arranged at a closed position. 冷媒蒸気圧縮システムは、少なくとも一定の時間の間、遷臨界サイクルで作動することを特徴とする請求項９に記載の冷媒蒸気圧縮システム。   The refrigerant vapor compression system of claim 9, wherein the refrigerant vapor compression system operates in a transcritical cycle for at least a fixed time. 冷媒蒸気圧縮システムを循環する冷媒は二酸化炭素であることを特徴とする請求項９に記載の冷媒蒸気圧縮システム。   The refrigerant vapor compression system according to claim 9, wherein the refrigerant circulating in the refrigerant vapor compression system is carbon dioxide. 少なくとも一定の時間の間、遷臨界サイクルで作動する冷媒蒸気圧縮システムにおいて冷媒の充填を管理する方法であって、
冷媒蒸気圧縮システムは、閉ループ冷媒回路において直列の冷媒連通関係でそれぞれ配設された冷媒圧縮装置、冷媒放熱用熱交換器および冷媒吸熱用熱交換器を備えるとともに、冷媒放熱用熱交換器の下流でかつ冷媒吸熱用熱交換器の上流で閉ループ冷媒回路に配設された膨張装置を備え、
閉ループ冷媒回路から冷媒を選択的に取り除くステップと、
取り除かれた冷媒を冷媒貯蔵装置に貯蔵するステップと、
取り除かれた冷媒を冷媒貯蔵装置から閉ループ冷媒回路に戻すステップと、
を含むことを特徴とする方法。 A method for managing refrigerant charge in a refrigerant vapor compression system operating in a transcritical cycle for at least a certain period of time, comprising:
The refrigerant vapor compression system includes a refrigerant compression device, a refrigerant heat dissipation heat exchanger, and a refrigerant heat absorption heat exchanger that are respectively arranged in a serial refrigerant communication relationship in a closed loop refrigerant circuit, and downstream of the refrigerant heat dissipation heat exchanger. And an expansion device disposed in a closed loop refrigerant circuit upstream of the refrigerant heat absorption heat exchanger,
Selectively removing refrigerant from the closed loop refrigerant circuit;
Storing the removed refrigerant in a refrigerant storage device;
Returning the removed refrigerant from the refrigerant storage device to the closed loop refrigerant circuit;
A method comprising the steps of: 閉ループ冷媒回路から冷媒を選択的に取り除くステップは、冷媒蒸気圧縮システムの作動サイクル中に行われ、
取り除かれた冷媒を冷媒貯蔵装置から閉ループ冷媒回路に戻すステップは、冷媒蒸気圧縮システムの作動サイクル中に行われることを特徴とする請求項１６に記載の方法。 The step of selectively removing refrigerant from the closed loop refrigerant circuit is performed during the operating cycle of the refrigerant vapor compression system,
17. The method of claim 16, wherein the step of returning removed refrigerant from the refrigerant storage device to the closed loop refrigerant circuit occurs during an operating cycle of the refrigerant vapor compression system. 閉ループ冷媒回路から冷媒を選択的に取り除くステップは、冷媒蒸気圧縮システムの作動サイクル中に実行され、
取り除かれた冷媒を冷媒貯蔵装置から閉ループ冷媒回路に戻すステップは、冷媒蒸気圧縮システムのオフサイクル中に実行されることを特徴とする請求項１６に記載の方法。 The step of selectively removing refrigerant from the closed loop refrigerant circuit is performed during the operating cycle of the refrigerant vapor compression system,
The method of claim 16, wherein returning the removed refrigerant from the refrigerant storage device to the closed loop refrigerant circuit is performed during an off-cycle of the refrigerant vapor compression system. 閉ループ冷媒回路から冷媒を選択的に取り除くステップは、冷媒蒸気圧縮システムのオフサイクル中に実行され、
取り除かれた冷媒を冷媒貯蔵装置から閉ループ冷媒回路に戻すステップは、冷媒蒸気圧縮システムの作動サイクル中に実行されることを特徴とする請求項１６に記載の方法。 The step of selectively removing refrigerant from the closed loop refrigerant circuit is performed during the off-cycle of the refrigerant vapor compression system,
The method of claim 16, wherein returning the removed refrigerant from the refrigerant storage device to the closed loop refrigerant circuit is performed during an operating cycle of the refrigerant vapor compression system.
JP2011509646A 2008-05-14 2009-05-13 Filling management in refrigerant vapor compression systems. Withdrawn JP2011521194A (en)

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