JP2018087665A - Refrigerant circuit device - Google Patents

Refrigerant circuit device Download PDF

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JP2018087665A
JP2018087665A JP2016231540A JP2016231540A JP2018087665A JP 2018087665 A JP2018087665 A JP 2018087665A JP 2016231540 A JP2016231540 A JP 2016231540A JP 2016231540 A JP2016231540 A JP 2016231540A JP 2018087665 A JP2018087665 A JP 2018087665A
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refrigerant
heat exchanger
path
expansion mechanism
compressor
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JP6805759B2 (en
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彬 中野
Akira Nakano
彬 中野
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Fuji Electric Co Ltd
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Fuji Electric Co Ltd
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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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/37—Capillary tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • G—PHYSICS
    • G07—CHECKING-DEVICES
    • G07F—COIN-FREED OR LIKE APPARATUS
    • G07F9/00—Details other than those peculiar to special kinds or types of apparatus
    • G07F9/10—Casings or parts thereof, e.g. with means for heating or cooling
    • G07F9/105—Heating or cooling means, for temperature and humidity control, for the conditioning of articles and their storage
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • F25B2313/02331—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements during cooling
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02731—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one three-way valve
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02732—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two three-way valves
    • 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
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • 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
    • F25B2600/25—Control of valves
    • F25B2600/2519—On-off valves

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • General Physics & Mathematics (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

PROBLEM TO BE SOLVED: To prevent deterioration of operation efficiency together with reduction of a circulation refrigerant amount in cooling/heating operations.SOLUTION: The device comprises: a main path 30 for connecting plural interior heat exchangers 34, a compressor 31, an exterior heat exchanger 32 and a first expansion mechanism 33 by a refrigerant pipeline 35; an introduction path 40 for feeding the refrigerant compressed by the compressor 31 to a left interior heat exchanger 34c; and a feedback path 50 for feeding the refrigerant passing through the left interior heat exchanger 34c to the main path 30. The main path 30 includes a low-voltage side electromagnetic valve 36d and the like provided between the exterior heat exchanger 32 and the first expansion mechanism 33. The feedback path 50 joins between the exterior heat exchanger 32 and the low-voltage side electromagnetic valve 36d and the like, and comprises a control part 20b for circulating a refrigerant circuit 20a so that the refrigerant compressed by the compressor 31 is adiabatic-expanded by the first expansion mechanism 33 and passes through the interior heat exchanger 34 after the refrigerant exchanges heat by the left interior heat exchanger 34c and then adiabatic-expanded by an electronic expansion valve 52 provided in the feedback path 50.SELECTED DRAWING: Figure 3

Description

本発明は、冷媒回路装置に関し、より詳細には、例えば自動販売機等に適用され、かつヒートポンプ機能を有する冷媒回路を備えた冷媒回路装置に関するものである。   The present invention relates to a refrigerant circuit device, and more particularly to a refrigerant circuit device that is applied to, for example, a vending machine and includes a refrigerant circuit having a heat pump function.

従来、例えば自動販売機等に適用され、かつヒートポンプ機能を有する冷媒回路を備えた冷媒回路装置として、主経路と、導入経路と、帰還経路とを備えたものが知られている。   2. Description of the Related Art Conventionally, as a refrigerant circuit device that is applied to, for example, a vending machine and includes a refrigerant circuit having a heat pump function, a refrigerant circuit device that includes a main path, an introduction path, and a return path is known.

主経路は、庫内熱交換器、圧縮機、庫外熱交換器及び膨張機構が冷媒管路で接続されて構成されている。庫内熱交換器は、室である商品収容庫の内部に設置されている。圧縮機は、庫内熱交換器を通過した冷媒を吸引し、吸引した冷媒を圧縮して高温高圧の状態にして吐出するものである。庫外熱交換器は、通過させる冷媒を周囲空気と熱交換させるものである。膨張機構は、通過する冷媒を減圧して断熱膨張させるものである。   The main path is configured by connecting an internal heat exchanger, a compressor, an external heat exchanger, and an expansion mechanism through a refrigerant pipe. The in-compartment heat exchanger is installed inside a commodity storage that is a room. The compressor sucks the refrigerant that has passed through the internal heat exchanger, compresses the sucked refrigerant, and discharges it in a high-temperature and high-pressure state. The external heat exchanger exchanges heat between the refrigerant to be passed and ambient air. The expansion mechanism depressurizes the passing refrigerant and adiabatically expands it.

このような主経路では、圧縮機で圧縮された冷媒が庫外熱交換器で凝縮し、凝縮した冷媒が膨張機構で断熱膨張され、庫内熱交換器で蒸発する。この庫内熱交換器で蒸発した冷媒は、圧縮機により吸引されて再び圧縮されて循環することになる。これにより商品収容庫の内部空気は冷却される。   In such a main path, the refrigerant compressed by the compressor is condensed by the external heat exchanger, and the condensed refrigerant is adiabatically expanded by the expansion mechanism and evaporated by the internal heat exchanger. The refrigerant evaporated in the internal heat exchanger is sucked by the compressor, compressed again, and circulated. Thereby, the internal air of a goods storage is cooled.

導入経路は、圧縮機で圧縮した冷媒を導入し、主経路を構成する庫内熱交換器のうち加熱対象となる商品収容庫に設置された加熱兼用庫内熱交換器に供給することにより該庫内熱交換器で冷媒を放熱させるものである。これにより加熱兼用庫内熱交換器が設置された商品収容庫の内部空気は加熱される。   The introduction path introduces the refrigerant compressed by the compressor, and supplies the refrigerant to the heating / compartment heat exchanger installed in the commodity storage to be heated among the internal heat exchangers constituting the main path. The refrigerant is radiated by the internal heat exchanger. Thereby, the internal air of the commodity storage in which the heating / compartment internal heat exchanger is installed is heated.

帰還経路は、加熱兼用庫内熱交換器で凝縮した冷媒を導入して庫外熱交換器に供給することで該冷媒を主経路に送出するものである。   A return path | route sends out the refrigerant | coolant to a main path | route by introduce | transducing the refrigerant | coolant condensed with the heating combined heat exchanger and supplying it to an external heat exchanger.

このような構成を有する冷媒回路装置においては、該当する商品収容庫の内部空気の冷却のみを行う場合（冷却単独運転を行う場合）には、冷媒が主経路のみを通過するよう循環させている。その一方、一の商品収容庫の内部空気を冷却して他の商品収容庫の内部空気を加熱する場合（冷却加熱運転を行う場合）には、圧縮機で圧縮した冷媒が導入経路を通過した後に加熱兼用庫内熱交換器で凝縮し、その後に帰還経路の通過途中に該帰還経路に設けられた膨張機構で断熱膨張している。かかる膨張機構で断熱膨張した冷媒が庫外熱交換器を経由して主経路の一部を通過するよう循環させている。   In the refrigerant circuit device having such a configuration, when only the cooling of the internal air of the corresponding product storage is performed (when the cooling single operation is performed), the refrigerant is circulated so as to pass only the main path. . On the other hand, when the internal air of one product storage is cooled to heat the internal air of another product storage (when cooling heating operation is performed), the refrigerant compressed by the compressor has passed through the introduction path. Later, it is condensed by a heat exchanger in the heating / compartment chamber, and then adiabatically expanded by an expansion mechanism provided in the return path in the middle of passing through the return path. The refrigerant adiabatically expanded by such an expansion mechanism is circulated so as to pass through a part of the main path via the external heat exchanger.

そして、冷却加熱運転における運転効率を向上させるために、該冷却加熱運転において冷却対象となる商品収容庫に設置された庫内熱交換器同士を冷媒管路にて直列に接続し、一方の庫内熱交換器を通過した冷媒が他方の庫内熱交換器を通過するようにした冷媒回路装置が提案されている（例えば、特許文献１参照）。   Then, in order to improve the operation efficiency in the cooling and heating operation, the internal heat exchangers installed in the product storage to be cooled in the cooling and heating operation are connected in series through a refrigerant pipe, A refrigerant circuit device has been proposed in which the refrigerant that has passed through the internal heat exchanger passes through the other internal heat exchanger (see, for example, Patent Document 1).

特開２０１６−９９０１５号公報Japanese Patent Laid-Open No. 2006-99015

ところで、上述した冷媒回路装置においては、冷却加熱運転を行う場合、加熱兼用庫内熱交換器を通過した冷媒は、密度が高い液相冷媒を多量に含んだ気液混合状態であるのが一般的である。このような冷媒の気液混合状態は、主経路における庫内熱交換器の通過途中まで維持される。   By the way, in the above-described refrigerant circuit device, when performing the cooling and heating operation, the refrigerant that has passed through the heating / compartment heat exchanger is generally in a gas-liquid mixed state containing a large amount of high-density liquid-phase refrigerant. Is. Such a gas-liquid mixed state of the refrigerant is maintained until it passes through the internal heat exchanger in the main path.

そのため、上述したように帰還経路が庫外熱交換器に冷媒を供給する構成では、冷媒回路の全容積において比較的大きい割合を占める庫外熱交換器でも冷媒が気液混合状態となり、見かけ上、庫外熱交換器に液相冷媒が滞留して寝込んでいるのと等価である。そのため、冷媒回路で循環する冷媒量が少なくなってしまい、冷却加熱運転の運転効率が低下する虞れがあった。   Therefore, in the configuration in which the return path supplies the refrigerant to the external heat exchanger as described above, even in the external heat exchanger that occupies a relatively large proportion of the total capacity of the refrigerant circuit, the refrigerant is in a gas-liquid mixed state, and apparently This is equivalent to the liquid phase refrigerant staying in the external heat exchanger. For this reason, the amount of refrigerant circulating in the refrigerant circuit is reduced, and the operation efficiency of the cooling and heating operation may be reduced.

本発明は、上記実情に鑑みて、冷却加熱運転を行う場合において循環冷媒量の低減に伴う運転効率の低下を防止することができる冷媒回路装置を提供することを目的とする。   In view of the above circumstances, an object of the present invention is to provide a refrigerant circuit device capable of preventing a decrease in operation efficiency associated with a reduction in the amount of circulating refrigerant when performing a cooling and heating operation.

上記目的を達成するために、本発明に係る冷媒回路装置は、各室に設置された複数の室内熱交換器と、前記室の外部に設置された圧縮機及び室外熱交換器と、通過する冷媒を断熱膨張させる第１膨張機構とを冷媒管路で順次接続して構成された主経路と、前記圧縮機で圧縮された冷媒を、前記室内熱交換器のうち加熱対象となる室に設置された加熱兼用室内熱交換器に送出する導入経路と、通過する冷媒を断熱膨張させる第２膨張機構を有し、かつ前記導入経路を通じて前記加熱兼用室内熱交換器に送出された冷媒を前記主経路に送出する帰還経路とを備えた冷媒回路を有する冷媒回路装置において、前記主経路は、前記室外熱交換器と前記第１膨張機構との間の冷媒管路に開閉可能に設置され、かつ開成する場合には冷媒が通過することを許容する一方、閉成する場合には冷媒の通過を規制する電磁弁を備え、前記帰還経路は、前記室外熱交換器と前記電磁弁との間の冷媒管路に合流し、かつ前記加熱兼用室内熱交換器で熱交換を行った冷媒を送出するものであり、加熱対象となる室の内部空気を加熱して他の室の内部空気を冷却する冷却加熱運転を行う場合、圧縮機で圧縮された冷媒が前記導入経路を介して前記加熱兼用室内熱交換器で熱交換した後に前記帰還経路を通過中に前記第２膨張機構で断熱膨張してから前記第１膨張機構で断熱膨張して前記室内熱交換器を通過するよう前記冷媒回路を循環させる制御手段を備えたことを特徴とする。   In order to achieve the above object, a refrigerant circuit device according to the present invention passes through a plurality of indoor heat exchangers installed in each chamber, a compressor and an outdoor heat exchanger installed outside the chamber. A main path configured by sequentially connecting a first expansion mechanism for adiabatic expansion of the refrigerant through a refrigerant pipe, and a refrigerant compressed by the compressor are installed in a room to be heated in the indoor heat exchanger. And a second expansion mechanism for adiabatically expanding the refrigerant passing therethrough, and the refrigerant sent to the heating combined indoor heat exchanger through the introduction path. In the refrigerant circuit device having a refrigerant circuit having a return path for sending out to the path, the main path is installed in a refrigerant conduit between the outdoor heat exchanger and the first expansion mechanism so as to be opened and closed, and When opening, make sure that the refrigerant passes. On the other hand, it is equipped with an electromagnetic valve that restricts the passage of the refrigerant when it is closed, and the return path merges with a refrigerant pipe line between the outdoor heat exchanger and the electromagnetic valve, and is also used for the heating The refrigerant that has exchanged heat with the indoor heat exchanger is sent out. When performing the cooling heating operation that heats the internal air of the chamber to be heated and cools the internal air of the other chambers, it is compressed by the compressor. The refrigerant is subjected to heat exchange by the second expansion mechanism while passing through the return path after heat exchange is performed by the heating / combined indoor heat exchanger via the introduction path, and then adiabatic expansion by the first expansion mechanism. Control means for circulating the refrigerant circuit so as to pass through the indoor heat exchanger is provided.

また本発明は、上記冷媒回路装置において、前記主経路は、前記室外熱交換器と前記第１膨張機構との間の冷媒管路に設置され、かつ通過する冷媒を断熱膨張させる第３膨張機構を備え、前記帰還経路は、前記第３膨張機構と前記電磁弁との間の冷媒管路に合流し、かつ前記加熱兼用室内熱交換器で熱交換を行った冷媒を送出することを特徴とする。   In the refrigerant circuit device according to the present invention, the main path is installed in a refrigerant pipe line between the outdoor heat exchanger and the first expansion mechanism, and a third expansion mechanism that adiabatically expands the refrigerant passing therethrough. The return path joins a refrigerant pipe line between the third expansion mechanism and the solenoid valve, and sends out the refrigerant that has exchanged heat with the heating / combined indoor heat exchanger. To do.

また本発明は、上記冷媒回路装置において、前記圧縮機と前記室外熱交換器との間の冷媒管路から分岐するとともに、前記室内熱交換器と前記圧縮機との間の冷媒管路に合流する態様で配設されたバイパス経路と、前記バイパス経路に開閉可能に設置され、かつ開成する場合には冷媒が通過することを許容する一方、閉成する場合には冷媒の通過を規制するバイパスバルブとを備えたことを特徴とする。   In the refrigerant circuit device according to the present invention, the refrigerant circuit device may branch from a refrigerant pipe line between the compressor and the outdoor heat exchanger, and may join a refrigerant pipe line between the indoor heat exchanger and the compressor. A bypass path arranged in such a manner as to be openable and closable in the bypass path and permitting passage of the refrigerant when opened, and restricting passage of the refrigerant when closed And a valve.

また本発明は、上記冷媒回路装置において、前記第２膨張機構は、電子膨張弁により構成されたことを特徴とする。   In the refrigerant circuit device according to the present invention, the second expansion mechanism is constituted by an electronic expansion valve.

また本発明は、上記冷媒回路装置において、前記室外熱交換器と前記第３膨張機構との間の冷媒管路に開閉可能に設置され、かつ開成する場合には冷媒が通過することを許容する一方、閉成する場合には冷媒の通過を規制する規制電磁弁を備え、前記制御手段が、前記冷却加熱運転を行う場合、前記規制電磁弁を閉成させることを特徴とする。   Further, the present invention provides the refrigerant circuit device, wherein the refrigerant circuit device is openably and closably installed in a refrigerant pipe line between the outdoor heat exchanger and the third expansion mechanism, and allows the refrigerant to pass through when opened. On the other hand, a restriction electromagnetic valve for restricting the passage of the refrigerant when closed is provided, and the control means closes the restriction electromagnetic valve when performing the cooling and heating operation.

本発明によれば、帰還経路が、主経路における室外熱交換器と電磁弁との間の冷媒管路に合流し、かつ加熱兼用室内熱交換器で熱交換を行った冷媒を送出するものであり、制御手段が、加熱対象となる室の内部空気を加熱して他の室の内部空気を冷却する冷却加熱運転を行う場合、圧縮機で圧縮された冷媒が導入経路を介して加熱兼用室内熱交換器で熱交換した後に帰還経路を通過中に第２膨張機構で断熱膨張してから第１膨張機構で断熱膨張して室内熱交換器を通過するよう冷媒回路を循環させるので、冷媒が室外熱交換器を積極的に通過することなく冷媒回路を循環させることができる。これにより、加熱兼用室内熱交換器を通過後に気液混合状態となる冷媒の多くが第２膨張機構で減圧された後に第１膨張機構で減圧されて室内熱交換器で蒸発するので、室外熱交換器に滞留して寝込んでしまうことを抑制することができる。そのため、冷媒回路を循環する冷媒量が少なくなってしまうことがない。従って、冷却加熱運転を行う場合において循環冷媒量の低減に伴う運転効率の低下を防止することができるという効果を奏する。   According to the present invention, the return path joins the refrigerant pipe line between the outdoor heat exchanger and the solenoid valve in the main path, and sends out the refrigerant that has exchanged heat with the heating and indoor heat exchanger. Yes, when the control means performs a cooling heating operation in which the internal air of the chamber to be heated is heated to cool the internal air of the other chamber, the refrigerant compressed by the compressor is heated through the introduction path. After the heat exchange with the heat exchanger, the refrigerant circuit is circulated so that the second expansion mechanism adiabatically expands while passing through the return path and then the first expansion mechanism adiabatically expands and passes through the indoor heat exchanger. The refrigerant circuit can be circulated without actively passing through the outdoor heat exchanger. As a result, most of the refrigerant that is in the gas-liquid mixed state after passing through the heating and indoor heat exchanger is depressurized by the second expansion mechanism and then depressurized by the first expansion mechanism and is evaporated by the indoor heat exchanger. It can suppress staying in the exchanger and falling asleep. Therefore, the amount of refrigerant circulating through the refrigerant circuit does not decrease. Therefore, in the case of performing the cooling and heating operation, there is an effect that it is possible to prevent the operation efficiency from being lowered due to the reduction of the circulating refrigerant amount.

図１は、本発明の実施の形態１である冷媒回路装置が適用された自動販売機の内部構造を正面から見た場合を示す断面図である。FIG. 1 is a cross-sectional view showing a case where an internal structure of a vending machine to which the refrigerant circuit device according to Embodiment 1 of the present invention is applied is viewed from the front. 図２は、図１に示した自動販売機の内部構造を示すものであり、右側の商品収容庫の断面側面図である。FIG. 2 shows the internal structure of the vending machine shown in FIG. 1, and is a cross-sectional side view of the right commodity storage. 図３は、本発明の実施の形態１である冷媒回路装置を概念的に示す概念図である。FIG. 3 is a conceptual diagram conceptually showing the refrigerant circuit device according to the first embodiment of the present invention. 図４は、図３に示した冷媒回路装置において冷却単独運転（ＣＣＣ運転）を行う場合の冷媒の流れを示す概念図である。FIG. 4 is a conceptual diagram showing the flow of the refrigerant when performing a single cooling operation (CCC operation) in the refrigerant circuit device shown in FIG. 3. 図５は、図３に示した冷媒回路装置において冷却加熱運転（ＨＣＣ運転）を行う場合の冷媒の流れを示す概念図である。FIG. 5 is a conceptual diagram showing the flow of the refrigerant when performing the cooling heating operation (HCC operation) in the refrigerant circuit device shown in FIG. 3. 図６は、図３に示した冷媒回路装置において加熱単独運転を行う場合の冷媒の流れを示す概念図である。FIG. 6 is a conceptual diagram illustrating the flow of the refrigerant when the single heating operation is performed in the refrigerant circuit device illustrated in FIG. 3. 図７は、本発明の実施の形態２である冷媒回路装置を概念的に示す概念図である。FIG. 7 is a conceptual diagram conceptually showing the refrigerant circuit device according to the second embodiment of the present invention. 図８は、図７に示した冷媒回路装置において冷却加熱運転（ＨＣＣ運転）を行う場合の冷媒の流れを示す概念図である。FIG. 8 is a conceptual diagram showing the flow of refrigerant when performing the cooling heating operation (HCC operation) in the refrigerant circuit device shown in FIG. 図９は、本発明の実施の形態３である冷媒回路装置を概念的に示す概念図である。FIG. 9 is a conceptual diagram conceptually showing the refrigerant circuit device according to the third embodiment of the present invention. 図１０は、図９に示した冷媒回路装置において冷却単独運転（ＣＣＣ運転）を行う場合の冷媒の流れを示す概念図である。FIG. 10 is a conceptual diagram showing a refrigerant flow when the cooling single operation (CCC operation) is performed in the refrigerant circuit device shown in FIG. 9. 図１１は、図９に示した冷媒回路装置において冷却加熱運転（ＨＣＣ運転）を行う場合の冷媒の流れを示す概念図である。FIG. 11 is a conceptual diagram showing the flow of the refrigerant when performing the cooling heating operation (HCC operation) in the refrigerant circuit device shown in FIG. 9. 図１２は、図９に示した冷媒回路装置において加熱単独運転を行う場合の冷媒の流れを示す概念図である。FIG. 12 is a conceptual diagram illustrating the flow of the refrigerant when the single heating operation is performed in the refrigerant circuit device illustrated in FIG. 9.

以下に添付図面を参照して、本発明に係る冷媒回路装置の好適な実施の形態について詳細に説明する。   Exemplary embodiments of a refrigerant circuit device according to the present invention will be explained below in detail with reference to the accompanying drawings.

＜実施の形態１＞
図１は、本発明の実施の形態１である冷媒回路装置が適用された自動販売機の内部構造を正面から見た場合を示す断面図である。ここで例示する自動販売機は、本体キャビネット１を備えている。 <Embodiment 1>
FIG. 1 is a cross-sectional view showing a case where an internal structure of a vending machine to which the refrigerant circuit device according to Embodiment 1 of the present invention is applied is viewed from the front. The vending machine illustrated here includes a main body cabinet 1.

本体キャビネット１は、前面に開口（以下、前面開口１ａ（図２参照）ともいう）が形成された直方状の形態を成すものである。この本体キャビネット１には、その内部に例えば２つの断熱仕切板２によって仕切られた３つの独立した商品収容庫３が左右に並んだ態様で設けられている。この商品収容庫３は、缶入り飲料やペットボトル入り飲料等の商品を所望の温度に維持した状態で収容する室で、断熱構造を有している。   The main body cabinet 1 has a rectangular shape in which an opening (hereinafter also referred to as a front opening 1a (see FIG. 2)) is formed on the front surface. The main body cabinet 1 is provided with three independent commodity storage boxes 3 partitioned by two heat insulating partition plates 2 in the left and right sides, for example. The commodity storage 3 is a room for storing commodities such as canned beverages and plastic bottled beverages while being maintained at a desired temperature, and has a heat insulating structure.

図２は、図１に示した自動販売機の内部構造を示すものであり、右側の商品収容庫３の断面側面図である。尚、ここでは右側の商品収容庫３（以下、適宜右庫３ａとも称する）の内部構造について示すが、中央の商品収容庫３（以下、適宜中庫３ｂとも称する）及び左側の商品収容庫３（以下、適宜左庫３ｃとも称する）の内部構造も右庫３ａと略同じような構成である。尚、本明細書における右側とは、自動販売機を正面から見た場合の右方を示し、左側とは、自動販売機を正面から見た場合の左方を示す。   FIG. 2 shows the internal structure of the vending machine shown in FIG. 1 and is a cross-sectional side view of the right product storage case 3. Here, the internal structure of the right product storage 3 (hereinafter also referred to as the right storage 3a) is shown, but the central product storage 3 (hereinafter also referred to as the intermediate storage 3b) and the left product storage 3 are shown. The internal structure (hereinafter also referred to as the left warehouse 3c as appropriate) has substantially the same configuration as the right warehouse 3a. In the present specification, the right side indicates the right side when the vending machine is viewed from the front, and the left side indicates the left side when the vending machine is viewed from the front.

かかる図２に示すように、本体キャビネット１の前面には、外扉４及び内扉５が設けられている。外扉４は、本体キャビネット１の前面開口１ａを開閉するためのものであり、内扉５は、商品収容庫３の前面を開閉するためのものである。この内扉５は、上下に分割されており、上側の扉５ａは商品を補充する際に開閉するものである。   As shown in FIG. 2, an outer door 4 and an inner door 5 are provided on the front surface of the main body cabinet 1. The outer door 4 is for opening and closing the front opening 1 a of the main body cabinet 1, and the inner door 5 is for opening and closing the front surface of the commodity storage 3. The inner door 5 is divided into upper and lower parts, and the upper door 5a opens and closes when a product is replenished.

上記商品収容庫３には、商品収納ラック６、払出機構７及び商品シュータ８が設けられている。商品収納ラック６は、商品を上下方向に沿って並ぶ態様で収納するためのものである。払出機構７は、商品収納ラック６の下部に設けられており、この商品収納ラック６に収納された商品群の最下位にある商品を１つずつ払い出すためのものである。商品シュータ８は、払出機構７から払い出された商品を外扉４に設けられた商品取出口４ａに導くためのものである。   The product storage 3 is provided with a product storage rack 6, a payout mechanism 7 and a product shooter 8. The commodity storage rack 6 is for storing commodities in a manner arranged in the vertical direction. The payout mechanism 7 is provided at the lower part of the product storage rack 6 and is used to pay out the products at the lowest level of the product group stored in the product storage rack 6 one by one. The product shooter 8 is for guiding the product delivered from the delivery mechanism 7 to the product outlet 4 a provided in the outer door 4.

図３は、本発明の実施の形態１である冷媒回路装置を概念的に示す概念図である。ここで例示する冷媒回路装置は、冷媒が封入された冷媒回路２０ａと、この冷媒回路２０ａに設けられた各部を適宜制御する制御部（制御手段）２０ｂとを備えて構成されている。   FIG. 3 is a conceptual diagram conceptually showing the refrigerant circuit device according to the first embodiment of the present invention. The refrigerant circuit device illustrated here includes a refrigerant circuit 20a in which a refrigerant is sealed, and a control unit (control means) 20b that appropriately controls each unit provided in the refrigerant circuit 20a.

冷媒回路２０ａは、主経路３０、導入経路４０、帰還経路５０及びバイパス経路６０を有している。主経路３０は、圧縮機３１、庫外熱交換器３２、第１膨張機構３３及び庫内熱交換器３４を冷媒管路３５にて適宜接続して構成されている。   The refrigerant circuit 20a has a main path 30, an introduction path 40, a return path 50, and a bypass path 60. The main path 30 is configured by appropriately connecting a compressor 31, an external heat exchanger 32, a first expansion mechanism 33, and an internal heat exchanger 34 through a refrigerant pipe 35.

圧縮機３１は、図２にも示すように、機械室９に設置されている。機械室９は、本体キャビネット１の内部であって商品収容庫３と区画され、かつ商品収容庫３の下方側の室である。この圧縮機３１は、吸引口を通じて冷媒を吸引し、吸引した冷媒を圧縮して高温高圧の状態（高温高圧冷媒）にして吐出口より吐出するものである。   As shown in FIG. 2, the compressor 31 is installed in the machine room 9. The machine room 9 is a room inside the main body cabinet 1, partitioned from the product storage 3 and below the product storage 3. The compressor 31 sucks the refrigerant through the suction port, compresses the sucked refrigerant to be in a high-temperature and high-pressure state (high-temperature and high-pressure refrigerant), and discharges it from the discharge port.

庫外熱交換器３２は、図２にも示すように、圧縮機３１と同様に機械室９に設置されている。この庫外熱交換器３２は、通過する冷媒と周囲空気とを熱交換させるものである。かかる庫外熱交換器３２の近傍には庫外送風ファン１０が設けられている。   As shown in FIG. 2, the external heat exchanger 32 is installed in the machine room 9 similarly to the compressor 31. The external heat exchanger 32 exchanges heat between the refrigerant passing through and the ambient air. An outside fan 10 is provided in the vicinity of the outside heat exchanger 32.

この庫外熱交換器３２と圧縮機３１とを接続する冷媒管路３５には、三方弁３６ａが設けられている。かかる三方弁３６ａについては後述する。   A three-way valve 36 a is provided in the refrigerant pipe 35 that connects the external heat exchanger 32 and the compressor 31. The three-way valve 36a will be described later.

第１膨張機構３３は、図２にも示すように、圧縮機３１及び庫外熱交換器３２と同様に機械室９に設置されている。この第１膨張機構３３は、通過する冷媒を減圧して断熱膨張させるものである。より詳細には、第１膨張機構３３は、右庫用キャピラリーチューブ３３ａ、中庫用キャピラリーチューブ３３ｂ及び左庫用キャピラリーチューブ３３ｃを備えて構成されている。これら右庫用キャピラリーチューブ３３ａ、中庫用キャピラリーチューブ３３ｂ及び左庫用キャピラリーチューブ３３ｃは、庫外熱交換器３２に接続する冷媒管路３５に連結された分配器３６ｂにより３つに分岐された冷媒管路３５にそれぞれ設けられている。尚、庫外熱交換器３２と分配器３６ｂとの間の冷媒管路３５には、出口側キャピラリーチューブ（第３膨張機構）３６ｃが設けられている。出口側キャピラリーチューブ３６ｃは、通過する冷媒を減圧して断熱膨張させるものである。   As shown in FIG. 2, the first expansion mechanism 33 is installed in the machine room 9 similarly to the compressor 31 and the external heat exchanger 32. This 1st expansion mechanism 33 decompresses the refrigerant | coolant to pass, and carries out adiabatic expansion. More specifically, the first expansion mechanism 33 includes a right-handed capillary tube 33a, a middle-housed capillary tube 33b, and a left-handed capillary tube 33c. These right-handed capillary tube 33a, middle-housed capillary tube 33b, and left-handed capillary tube 33c were branched into three by a distributor 36b connected to a refrigerant pipe 35 connected to the external heat exchanger 32. The refrigerant pipes 35 are provided respectively. An outlet side capillary tube (third expansion mechanism) 36c is provided in the refrigerant line 35 between the external heat exchanger 32 and the distributor 36b. The outlet side capillary tube 36c is for adiabatic expansion by depressurizing the refrigerant passing therethrough.

ここで第１膨張機構３３を構成する右庫用キャピラリーチューブ３３ａ、中庫用キャピラリーチューブ３３ｂ及び左庫用キャピラリーチューブ３３ｃの絞り量であるが、最も冷媒流量が大きくなる冷却加熱運転（後述するＨＣＣ運転）を行う場合に最適となるように調整されている。そして、図１からも明らかなように、中庫３ｂの容積が最も小さいので、中庫用キャピラリーチューブ３３ｂの絞り量が最も大きく調整されている。   Here, it is the amount of squeezing of the right-side capillary tube 33a, the middle-use capillary tube 33b, and the left-side capillary tube 33c constituting the first expansion mechanism 33. It is adjusted so as to be optimal when driving. As apparent from FIG. 1, the volume of the storage 3 b is the smallest, so that the amount of restriction of the storage capillary tube 33 b is adjusted to be the largest.

また、分配器３６ｂから右庫用キャピラリーチューブ３３ａ、中庫用キャピラリーチューブ３３ｂ及び左庫用キャピラリーチューブ３３ｃのそれぞれに至る途中に低圧側電磁弁３６ｄ，３６ｅ，３６ｆが設けられている。低圧側電磁弁３６ｄ，３６ｅ，３６ｆは、それぞれ開閉可能な弁体であり、制御部２０ｂから開指令が与えられた場合には開成して冷媒の通過を許容する一方、閉指令が与えられた場合には閉成して冷媒の通過を規制するものである。尚、図３中の符号３６ｇは、低圧側逆止弁である。   Further, low-pressure side solenoid valves 36d, 36e, and 36f are provided on the way from the distributor 36b to the right-side capillary tube 33a, the middle-side capillary tube 33b, and the left-side capillary tube 33c. The low-pressure side solenoid valves 36d, 36e, and 36f are valve bodies that can be opened and closed, respectively. In such a case, it is closed to restrict the passage of the refrigerant. In addition, the code | symbol 36g in FIG. 3 is a low voltage | pressure side check valve.

庫内熱交換器３４は、複数（図示の例では３つ）設けられており、各商品収容庫３の内部低域であって、背面ダクト１１（図２参照）の前面側に設置されている。   A plurality of (3 in the illustrated example) internal heat exchangers 34 are provided, and are installed in front of the rear duct 11 (see FIG. 2), which is an internal low region of each commodity storage 3. Yes.

右庫３ａに設置された庫内熱交換器３４（以下、右庫内熱交換器３４ａとも称する）は、右庫用キャピラリーチューブ３３ａの下流側に位置する態様で冷媒管路３５に接続されている。この右庫内熱交換器３４ａの出口部分に接続された冷媒管路３５は、圧縮機３１の吸引口部分に接続されている。   The internal heat exchanger 34 installed in the right warehouse 3a (hereinafter also referred to as the right internal heat exchanger 34a) is connected to the refrigerant pipe 35 in a manner located downstream of the right warehouse capillary tube 33a. Yes. The refrigerant pipe 35 connected to the outlet portion of the right-side heat exchanger 34 a is connected to the suction port portion of the compressor 31.

中庫３ｂに設置された庫内熱交換器３４（以下、中庫内熱交換器３４ｂとも称する）は、中庫用キャピラリーチューブ３３ｂの下流側に位置する態様で冷媒管路３５に接続されている。この中庫内熱交換器３４ｂの出口部分に接続された冷媒管路３５は、右庫内熱交換器３４ａの出口部分に接続された冷媒管路３５の途中の第１合流点Ｐ１で該冷媒管路３５に合流している。   The internal heat exchanger 34 (hereinafter also referred to as the internal heat exchanger 34b) installed in the internal warehouse 3b is connected to the refrigerant pipe 35 in a manner located on the downstream side of the internal capillary tube 33b. Yes. The refrigerant pipe 35 connected to the outlet part of the inner-compartment heat exchanger 34b is connected to the refrigerant at a first junction P1 in the middle of the refrigerant pipe 35 connected to the outlet part of the right-hand inner heat exchanger 34a. It joins the pipeline 35.

左庫３ｃに設置された庫内熱交換器３４（以下、左庫内熱交換器３４ｃとも称する）は、左庫用キャピラリーチューブ３３ｃの下流側に位置する態様で冷媒管路３５に接続されている。この左庫内熱交換器３４ｃの出口部分に接続された冷媒管路３５は、中庫内熱交換器３４ｂの出口部分に接続された冷媒管路３５の途中の左庫３ｃ内熱交換器第２合流点Ｐ２で該冷媒管路３５に合流している。   The internal heat exchanger 34 (hereinafter also referred to as the left internal heat exchanger 34c) installed in the left warehouse 3c is connected to the refrigerant pipe 35 in a manner located on the downstream side of the left capillary tube 33c. Yes. The refrigerant line 35 connected to the outlet portion of the left-side internal heat exchanger 34c is the left-side chamber 3c internal heat exchanger No. 3 in the middle of the refrigerant line 35 connected to the outlet portion of the intermediate-side heat exchanger 34b. The refrigerant pipe 35 merges at the two junction P2.

また左庫内熱交換器３４ｃの出口部分に接続された冷媒管路３５の途中には出口側電磁弁３６ｈが設けられている。出口側電磁弁３６ｈは、開閉可能な弁体であり、制御部２０ｂから開指令が与えられた場合には開成して冷媒の通過を許容する一方、閉指令が与えられた場合には閉成して冷媒の通過を規制するものである。   In addition, an outlet-side electromagnetic valve 36h is provided in the middle of the refrigerant pipe 35 connected to the outlet portion of the left-side heat exchanger 34c. The outlet side solenoid valve 36h is a valve body that can be opened and closed. When the opening command is given from the control unit 20b, the outlet side solenoid valve 36h opens and allows the refrigerant to pass therethrough, but when the closing command is given, the outlet side solenoid valve 36h is closed. Thus, the passage of the refrigerant is restricted.

尚、図３中の符号１３及びＳは、ヒータ及びストレーナである。ヒータ１３は、中庫３ｂ及び左庫３ｃに設置されている。ストレーナＳは、通過する冷媒に含まれる固形物等の異物を除去するためのものである。   In addition, the code | symbol 13 and S in FIG. 3 are a heater and a strainer. The heater 13 is installed in the middle store 3b and the left store 3c. The strainer S is for removing foreign substances such as solids contained in the passing refrigerant.

導入経路４０は、上記三方弁３６ａに接続され、かつ左庫内熱交換器３４ｃの入口側の冷媒管路３５の第３合流点Ｐ３に合流する導入管路４１とにより構成された経路である。三方弁３６ａは、圧縮機３１で圧縮した冷媒を庫外熱交換器３２へ送出する第１送出状態と、圧縮機３１で圧縮した冷媒を導入経路４０へ送出する第２送出状態との間で択一的に切換可能な切換バルブである。かかる三方弁３６ａの切換動作は、制御部２０ｂから与えられる指令に応じて行われる。つまり、導入経路４０においては、三方弁３６ａが第２送出状態となる場合に開成されており、三方弁３６ａが第１送出状態となる場合に閉成されている。   The introduction path 40 is a path that is connected to the three-way valve 36a and is constituted by an introduction pipe 41 that joins the third junction P3 of the refrigerant pipe 35 on the inlet side of the left-side heat exchanger 34c. . The three-way valve 36 a is between a first sending state in which the refrigerant compressed by the compressor 31 is sent to the external heat exchanger 32 and a second sending state in which the refrigerant compressed by the compressor 31 is sent to the introduction path 40. This is a switching valve that can be switched alternatively. The switching operation of the three-way valve 36a is performed according to a command given from the control unit 20b. That is, the introduction path 40 is opened when the three-way valve 36a is in the second delivery state, and is closed when the three-way valve 36a is in the first delivery state.

帰還経路５０は、左庫内熱交換器３４ｃの出口側に接続された冷媒管路３５の途中の第１分岐点Ｑ１で分岐し、庫外熱交換器３２から分配器３６ｂに至る冷媒管路３５における出口側キャピラリーチューブ３６ｃと分配器３６ｂとの間の第４合流点Ｐ４で合流する態様で該冷媒管路３５に接続された帰還管路５１により構成された経路である。   The return path 50 branches off at the first branch point Q1 in the middle of the refrigerant line 35 connected to the outlet side of the left-side heat exchanger 34c, and reaches the distributor 36b from the external heat exchanger 32. 35 is a path constituted by a return line 51 connected to the refrigerant line 35 in a mode of merging at a fourth merging point P4 between the outlet side capillary tube 36c and the distributor 36b.

この帰還経路５０は、左庫内熱交換器３４ｃで凝縮した冷媒を主経路３０に帰還させるためのものである。該帰還経路５０を構成する帰還管路５１の途中には、電子膨張弁（第２膨張機構）５２及び帰還逆止弁５３が設けられている。電子膨張弁５２は、制御部２０ｂから与えられる指令に応じてその開度が調整されるものであり、通過する冷媒を断熱膨張させるものである。   This return path 50 is for returning the refrigerant condensed in the left-side heat exchanger 34 c to the main path 30. An electronic expansion valve (second expansion mechanism) 52 and a feedback check valve 53 are provided in the middle of the feedback pipe 51 constituting the feedback path 50. The opening degree of the electronic expansion valve 52 is adjusted in accordance with a command given from the control unit 20b, and adiabatic expansion of the passing refrigerant is performed.

バイパス経路６０は、圧縮機３１（三方弁３６ａ）から庫外熱交換器３２に至る冷媒管路３５の途中の第２分岐点Ｑ２から分岐し、第１合流点Ｐ１から圧縮機３１に至る冷媒管路３５の途中の第５合流点Ｐ５で合流する態様で設けたバイパス管路６１により構成されている。このバイパス管路６１には、バイパスバルブ６２が設けられている。バイパスバルブ６２は、開閉可能な弁体であり、制御部２０ｂから開指令が与えられた場合には開成して冷媒がバイパス管路６１を通過することを許容する一方、制御部２０ｂから閉指令が与えられた場合には閉成して冷媒がバイパス管路６１を通過することを規制するものである。   The bypass path 60 branches from a second branch point Q2 in the middle of the refrigerant pipe 35 extending from the compressor 31 (three-way valve 36a) to the external heat exchanger 32, and reaches the compressor 31 from the first junction P1. It is comprised by the bypass line 61 provided in the aspect which merges in the 5th confluence | merging point P5 in the middle of the pipe line 35. FIG. The bypass pipe 61 is provided with a bypass valve 62. The bypass valve 62 is a valve body that can be opened and closed. When the opening command is given from the control unit 20b, the bypass valve 62 opens and allows the refrigerant to pass through the bypass conduit 61, while the control unit 20b closes the closing command. Is closed to restrict the refrigerant from passing through the bypass line 61.

以上のような構成を有する冷媒回路装置は、次のようにして商品収容庫３に収容された商品を冷却、あるいは加熱する。   The refrigerant circuit device having the above-described configuration cools or heats the product stored in the product storage 3 as follows.

まず冷却単独運転の一例として、ＣＣＣ運転（全ての商品収容庫３の内部空気を冷却する運転）を行う場合について説明する。   First, as an example of a single cooling operation, a case where a CCC operation (an operation for cooling the internal air of all the commodity containers 3) is performed will be described.

この場合、制御部２０ｂは三方弁３６ａを第１送出状態にし、低圧側電磁弁３６ｄ，３６ｅ，３６ｆ及び出口側電磁弁３６ｈを開成させる一方、バイパスバルブ６２を閉成させる。これにより圧縮機３１で圧縮された冷媒は、図４に示すように循環する。   In this case, the control unit 20b brings the three-way valve 36a into the first delivery state, opens the low-pressure side solenoid valves 36d, 36e, 36f, and the outlet side solenoid valve 36h, and closes the bypass valve 62. As a result, the refrigerant compressed by the compressor 31 circulates as shown in FIG.

すなわち、圧縮機３１で圧縮された冷媒は、三方弁３６ａを通過して冷媒管路３５を経由して庫外熱交換器３２に至る。庫外熱交換器３２に至った冷媒は、該庫外熱交換器３２を通過中に、周囲空気（外気）に放熱して凝縮する。庫外熱交換器３２で凝縮した冷媒は、出口側キャピラリーチューブ３６ｃを通過することで減圧されて断熱膨張し、その後に分配器３６ｂで分岐され、右庫用キャピラリーチューブ３３ａ、中庫用キャピラリーチューブ３３ｂ及び左庫用キャピラリーチューブ３３ｃにより減圧されて断熱膨張し、右庫内熱交換器３４ａ、中庫内熱交換器３４ｂ及び左庫内熱交換器３４ｃに至る。このように各庫内熱交換器３４に至った冷媒は、各庫内熱交換器３４で蒸発して商品収容庫３の内部空気から熱を奪い、該内部空気を冷却する。冷却された内部空気は、各庫内熱交換器３４の近傍に配設された庫内送風ファン１２の駆動により内部を循環し、これにより各商品収容庫３に収容された商品は、循環する内部空気に冷却される。   That is, the refrigerant compressed by the compressor 31 passes through the three-way valve 36 a and reaches the external heat exchanger 32 via the refrigerant pipe 35. The refrigerant that reaches the external heat exchanger 32 dissipates heat to ambient air (outside air) and condenses while passing through the external heat exchanger 32. The refrigerant condensed in the external heat exchanger 32 is depressurized and adiabatically expanded by passing through the outlet side capillary tube 36c, and then branched by the distributor 36b, and the right side capillary tube 33a and the inner side capillary tube. 33b and the left-side capillary tube 33c are depressurized and adiabatically expanded, and reach the right-side internal heat exchanger 34a, the central internal heat exchanger 34b, and the left-side internal heat exchanger 34c. Thus, the refrigerant | coolant which reached each internal heat exchanger 34 evaporates in each internal heat exchanger 34, takes heat from the internal air of the goods storage 3, and cools this internal air. The cooled internal air circulates in the interior by driving the internal blower fan 12 disposed in the vicinity of each internal heat exchanger 34, whereby the products accommodated in each commodity storage 3 circulate. Cooled to internal air.

各庫内熱交換器３４で蒸発した冷媒は、第１合流点Ｐ１及び第２合流点Ｐ２で合流した後に圧縮機３１に吸引され、その後に圧縮されて上述した循環を繰り返す。   The refrigerant evaporated in each internal heat exchanger 34 joins at the first joining point P1 and the second joining point P2, and then is sucked into the compressor 31 and then compressed and repeats the circulation described above.

次に冷却加熱運転の一例として、ＨＣＣ運転（左庫３ｃの内部空気を加熱し、かつ中庫３ｂ及び右庫３ａの内部空気を冷却する運転）を行う場合について説明する。   Next, as an example of the cooling and heating operation, a case where the HCC operation (operation for heating the internal air of the left warehouse 3c and cooling the internal air of the middle warehouse 3b and the right warehouse 3a) will be described.

この場合、制御部２０ｂは三方弁３６ａを第２送出状態にし、低圧側電磁弁３６ｄ，３６ｅを開成させる一方、低圧側電磁弁３６ｆ、出口側電磁弁３６ｈ及びバイパスバルブ６２を閉成させる。これにより圧縮機３１で圧縮された冷媒は、図５に示すように循環する。尚、制御部２０ｂは、帰還管路５１に設けた電子膨張弁５２については、冷媒の蒸発温度に応じて開度を調整する。   In this case, the control unit 20b puts the three-way valve 36a in the second delivery state and opens the low pressure side solenoid valves 36d and 36e, while closing the low pressure side solenoid valve 36f, the outlet side solenoid valve 36h, and the bypass valve 62. As a result, the refrigerant compressed by the compressor 31 circulates as shown in FIG. In addition, the control part 20b adjusts the opening degree of the electronic expansion valve 52 provided in the return line 51 according to the evaporation temperature of the refrigerant.

圧縮機３１で圧縮された冷媒は、導入管路４１を通過して左庫内熱交換器３４ｃに至る。左庫内熱交換器３４ｃに至った冷媒は、該左庫内熱交換器３４ｃを通過中に、左庫３ｃの内部空気とそれぞれ熱交換し、該内部空気に放熱して凝縮する。これにより、左庫３ｃの内部空気を加熱する。加熱された内部空気は、庫内送風ファン１２の駆動により、左庫３ｃの内部を循環し、これにより左庫３ｃに収容された商品は、循環する内部空気に加熱される。つまり、左庫内熱交換器３４ｃは、本発明における室内熱交換器のうち加熱対象となる室に設置された加熱兼用室内熱交換器に相当する。   The refrigerant compressed by the compressor 31 passes through the introduction pipe 41 and reaches the left-inside heat exchanger 34c. The refrigerant that has reached the left-side internal heat exchanger 34c exchanges heat with the internal air of the left-side 3c while passing through the left-side internal heat exchanger 34c, and dissipates heat to the internal air to condense. Thereby, the internal air of the left warehouse 3c is heated. The heated internal air circulates inside the left warehouse 3c by driving the internal blower fan 12, whereby the product stored in the left warehouse 3c is heated to the circulating internal air. That is, the left-side heat exchanger 34c corresponds to a heating / combined indoor heat exchanger installed in a room to be heated among the indoor heat exchangers in the present invention.

左庫内熱交換器３４ｃで凝縮した冷媒は、帰還経路５０を構成する帰還管路５１を通過して電子膨張弁５２で減圧されて断熱膨張し、その後に第４合流点Ｐ４を通過して主経路３０に至る。このように主経路３０に至った冷媒は、分配器３６ｂを経由して右庫用キャピラリーチューブ３３ａ及び中庫用キャピラリーチューブ３３ｂで減圧されて断熱膨張する。   The refrigerant condensed in the left-side heat exchanger 34c passes through the return pipe 51 constituting the return path 50, is depressurized by the electronic expansion valve 52 and adiabatically expands, and then passes through the fourth junction P4. The main route 30 is reached. Thus, the refrigerant that has reached the main path 30 is decompressed and adiabatically expanded by the right-side capillary tube 33a and the middle-use capillary tube 33b via the distributor 36b.

中庫用キャピラリーチューブ３３ｂで断熱膨張した冷媒は、中庫内熱交換器３４ｂに至り、この中庫内熱交換器３４ｂで蒸発して中庫３ｂの内部空気から熱を奪い、該内部空気を冷却する。冷却された内部空気は、庫内送風ファン１２の駆動により中庫３ｂの内部を循環し、これにより中庫３ｂに収容された商品は冷却される。   The refrigerant adiabatically expanded by the internal capillary tube 33b reaches the internal heat exchanger 34b, evaporates in the internal heat exchanger 34b, takes heat from the internal air of the internal chamber 3b, and removes the internal air. Cooling. The cooled internal air circulates through the interior of the intermediate store 3b by driving the internal blower fan 12, whereby the product stored in the intermediate store 3b is cooled.

一方、右庫用キャピラリーチューブ３３ａで断熱膨張した冷媒は、右庫内熱交換器３４ａに至り、この右庫内熱交換器３４ａで蒸発して右庫３ａの内部空気から熱を奪い、該内部空気を冷却する。冷却された内部空気は、庫内送風ファン１２の駆動により右庫３ａの内部を循環し、これにより右庫３ａに収容された商品は冷却される。   On the other hand, the refrigerant adiabatically expanded in the right-hand capillary tube 33a reaches the right-hand heat exchanger 34a, evaporates in the right-hand heat exchanger 34a, and takes heat from the internal air of the right-hand warehouse 3a. Cool the air. The cooled internal air circulates through the inside of the right warehouse 3a by driving the internal blower fan 12, whereby the product stored in the right warehouse 3a is cooled.

右庫内熱交換器３４ａ及び中庫内熱交換器３４ｂで蒸発した冷媒は、第１合流点Ｐ１で合流した後に圧縮機３１に吸引され、その後に圧縮されて上述した循環を繰り返す。   The refrigerant evaporated in the right internal heat exchanger 34a and the internal internal heat exchanger 34b joins at the first junction P1, and then is sucked into the compressor 31 and then compressed and repeats the circulation described above.

更に加熱単独運転の一例として、左庫３ｃの内部空気のみを加熱する運転を行う場合について説明する。   Furthermore, the case where the operation | movement which heats only the internal air of the left store | warehouse | chamber 3c is performed is demonstrated as an example of heating independent operation.

この場合、制御部２０ｂは、三方弁３６ａを第２送出状態にし、バイパスバルブ６２を開成させる一方、低圧側電磁弁３６ｄ，３６ｅ，３６ｆ及び出口側電磁弁３６ｈを閉成させる。これにより圧縮機３１で圧縮された冷媒は、図６に示すように循環する。尚、制御部２０ｂは、帰還管路５１に設けた電子膨張弁５２についても通過する冷媒を断熱膨張するべく、所望の絞り量となるよう開度を調整する。   In this case, the control unit 20b sets the three-way valve 36a to the second delivery state, opens the bypass valve 62, and closes the low-pressure side solenoid valves 36d, 36e, 36f and the outlet side solenoid valve 36h. As a result, the refrigerant compressed by the compressor 31 circulates as shown in FIG. Note that the control unit 20b adjusts the opening degree so as to obtain a desired throttle amount so that the refrigerant passing through the electronic expansion valve 52 provided in the return pipe 51 is adiabatically expanded.

圧縮機３１で圧縮された冷媒は、導入管路４１を通過して左庫内熱交換器３４ｃに至る。左庫内熱交換器３４ｃに至った冷媒は、該左庫内熱交換器３４ｃを通過中に、左庫３ｃの内部空気とそれぞれ熱交換し、該内部空気に放熱して凝縮する。これにより、左庫３ｃの内部空気を加熱する。加熱された内部空気は、庫内送風ファン１２の駆動により、左庫３ｃの内部を循環し、これにより左庫３ｃに収容された商品は、循環する内部空気に加熱される。   The refrigerant compressed by the compressor 31 passes through the introduction pipe 41 and reaches the left-inside heat exchanger 34c. The refrigerant that has reached the left-side internal heat exchanger 34c exchanges heat with the internal air of the left-side 3c while passing through the left-side internal heat exchanger 34c, and dissipates heat to the internal air to condense. Thereby, the internal air of the left warehouse 3c is heated. The heated internal air circulates inside the left warehouse 3c by driving the internal blower fan 12, whereby the product stored in the left warehouse 3c is heated to the circulating internal air.

左庫内熱交換器３４ｃで凝縮した冷媒は、帰還経路５０を構成する帰還管路５１を通過して電子膨張弁５２で減圧されて断熱膨張し、その後に第４合流点Ｐ４を通過して主経路３０に至る。このように主経路３０に至った冷媒は、出口側キャピラリーチューブ３６ｃを通過することで減圧されて断熱膨張し、その後に庫外熱交換器３２に至り、該庫外熱交換器３２で周囲空気と熱交換を行って蒸発する。庫外熱交換器３２で蒸発した冷媒は、バイパス管路６１を通過した後に圧縮機３１に吸引され、その後に圧縮されて上述した循環を繰り返す。   The refrigerant condensed in the left-side heat exchanger 34c passes through the return pipe 51 constituting the return path 50, is depressurized by the electronic expansion valve 52 and adiabatically expands, and then passes through the fourth junction P4. The main route 30 is reached. Thus, the refrigerant that has reached the main path 30 is decompressed and adiabatically expanded by passing through the outlet side capillary tube 36 c, and then reaches the external heat exchanger 32, and the ambient air is exchanged by the external heat exchanger 32. Evaporate with heat exchange. The refrigerant evaporated in the external heat exchanger 32 is sucked into the compressor 31 after passing through the bypass pipe 61, and then compressed and repeated as described above.

以上説明したように、本実施の形態１である冷媒回路装置によれば、帰還経路５０が、主経路３０における庫外熱交換器３２と低圧側電磁弁３６ｄ，３６ｅ，３６ｆとの間の冷媒管路３５に合流し、かつ左庫内熱交換器３４ｃで熱交換を行った冷媒を送出するものであり、制御部２０ｂが、左庫３ｃの内部空気を加熱して右庫３ａ及び中庫３ｂの少なくとも一方の内部空気を冷却する冷却加熱運転を行う場合、圧縮機３１で圧縮された冷媒が導入経路４０（導入管路４１）を介して左庫内熱交換器３４ｃで熱交換した後に帰還管路５１（帰還経路５０）を通過中に電子膨張弁５２で断熱膨張してから第１膨張機構３３（右庫用キャピラリーチューブ３３ａ及び中庫用キャピラリーチューブ３３ｂ）で断熱膨張して右庫内熱交換器３４ａ及び中庫内熱交換器３４ｂを通過するよう冷媒回路２０ａを循環させるので、冷媒が庫外熱交換器３２を積極的に通過することなく冷媒回路２０ａを循環させることができる。これにより、左庫内熱交換器３４ｃを通過後に気液混合状態となる冷媒の多くが電子膨張弁５２で減圧された後に第１膨張機構３３で減圧されて庫内熱交換器３４で蒸発するので、庫外熱交換器３２に滞留して寝込んでしまうことを抑制することができる。そのため、冷媒回路２０ａを循環する冷媒量が少なくなってしまうことがない。従って、冷却加熱運転を行う場合において循環冷媒量の低減に伴う運転効率の低下を防止することができる。   As described above, according to the refrigerant circuit device of the first embodiment, the return path 50 is a refrigerant between the external heat exchanger 32 and the low pressure side solenoid valves 36d, 36e, 36f in the main path 30. The refrigerant that merges with the pipe line 35 and exchanges heat with the left-side heat exchanger 34c is sent out, and the control unit 20b heats the internal air of the left-side warehouse 3c to heat the right-side warehouse 3a and the middle warehouse. When performing the cooling and heating operation for cooling at least one of the internal air of 3b, after the refrigerant compressed by the compressor 31 performs heat exchange in the left-side internal heat exchanger 34c via the introduction path 40 (introduction pipe line 41) Adiabatic expansion is performed by the electronic expansion valve 52 while passing through the return pipe 51 (return path 50), and then adiabatic expansion is performed by the first expansion mechanism 33 (the right-side capillary tube 33a and the middle-use capillary tube 33b). Inner heat exchanger 34a and inside Since circulating refrigerant circuit 20a to pass through the inner heat exchanger 34b, it is possible to circulate the refrigerant circuit 20a without refrigerant actively passing through the compartment outside heat exchanger 32. As a result, most of the refrigerant that enters the gas-liquid mixed state after passing through the left internal heat exchanger 34c is decompressed by the electronic expansion valve 52, then decompressed by the first expansion mechanism 33, and evaporated by the internal heat exchanger 34. Therefore, it can suppress staying in the external heat exchanger 32 and falling asleep. Therefore, the amount of refrigerant circulating through the refrigerant circuit 20a does not decrease. Therefore, in the case of performing the cooling and heating operation, it is possible to prevent a decrease in operation efficiency due to a reduction in the circulating refrigerant amount.

このように冷却加熱運転を行う場合において循環冷媒量の低減に伴う運転効率の低下を防止することができるので、冷媒回路２０ａに対する冷媒の封入量を低減することができ、コストの低減化を図ることができるとともに、冷却加熱運転での加熱能力の向上により省エネルギー化を図ることができる。   In this way, when performing the cooling and heating operation, it is possible to prevent a decrease in operation efficiency due to a reduction in the amount of circulating refrigerant, so that the amount of refrigerant enclosed in the refrigerant circuit 20a can be reduced, and the cost can be reduced. In addition, energy saving can be achieved by improving the heating capacity in the cooling and heating operation.

上記冷媒回路装置によれば、通過する冷媒を断熱膨張させる出口側キャピラリーチューブ３６ｃが、庫外熱交換器３２と第１膨張機構３３との間の冷媒管路３５に設置され、帰還経路５０が、出口側キャピラリーチューブ３６ｃと低圧側電磁弁３６ｄ，３６ｅ，３６ｆとの間の第４合流点Ｐ４で冷媒管路３５に合流し、かつ左庫内熱交換器３４ｃで熱交換を行った冷媒を送出するので、冷却加熱運転を行う場合に、帰還経路５０を通過した冷媒の一部が庫外熱交換器３２に向かったとしても、該冷媒は出口側キャピラリーチューブ３６ｃで減圧された後に庫外熱交換器３２を通過することとなり、該庫外熱交換器３２で周囲空気と熱交換を行って蒸発する。そのため、冷媒が気液混合状態で庫外熱交換器３２に滞留してしまうことを抑制できる。   According to the refrigerant circuit device, the outlet side capillary tube 36c that adiabatically expands the refrigerant passing therethrough is installed in the refrigerant pipe 35 between the external heat exchanger 32 and the first expansion mechanism 33, and the return path 50 is The refrigerant that has joined the refrigerant pipe 35 at the fourth junction P4 between the outlet side capillary tube 36c and the low pressure side solenoid valves 36d, 36e, 36f and that has exchanged heat with the left-side internal heat exchanger 34c Therefore, even when a part of the refrigerant that has passed through the return path 50 is directed to the external heat exchanger 32 when cooling and heating operation is performed, the refrigerant is decompressed by the outlet side capillary tube 36c and then outside the refrigerator. It passes through the heat exchanger 32 and is evaporated by exchanging heat with ambient air in the external heat exchanger 32. Therefore, it can suppress that a refrigerant | coolant retains in the external heat exchanger 32 in a gas-liquid mixed state.

＜実施の形態２＞
図７は、本発明の実施の形態２である冷媒回路装置を概念的に示す概念図である。尚、上述した実施の形態１である冷媒回路装置と同様の構成を有するものには同一の符号を付してその説明を適宜省略する。 <Embodiment 2>
FIG. 7 is a conceptual diagram conceptually showing the refrigerant circuit device according to the second embodiment of the present invention. In addition, the same code | symbol is attached | subjected to what has the structure similar to the refrigerant circuit apparatus which is Embodiment 1 mentioned above, and the description is abbreviate | omitted suitably.

ここで例示する冷媒回路装置は、冷媒が封入された冷媒回路２１ａと、この冷媒回路２１ａに設けられた各部を適宜制御する制御部（制御手段）２１ｂとを備えて構成されている。   The refrigerant circuit device illustrated here includes a refrigerant circuit 21a in which a refrigerant is sealed, and a control unit (control means) 21b that appropriately controls each unit provided in the refrigerant circuit 21a.

冷媒回路２１ａは、主経路３０ａ、導入経路４０、帰還経路５０及びバイパス経路６０を有している。主経路３０ａは、圧縮機３１、庫外熱交換器３２、第１膨張機構３３及び庫内熱交換器３４を冷媒管路３５にて適宜接続して構成されている。この主経路３０ａでは、庫外熱交換器３２と出口側キャピラリーチューブ３６ｃとの間の冷媒管路３５に規制電磁弁３７が設けられている。   The refrigerant circuit 21a has a main path 30a, an introduction path 40, a return path 50, and a bypass path 60. The main path 30 a is configured by appropriately connecting a compressor 31, an external heat exchanger 32, a first expansion mechanism 33, and an internal heat exchanger 34 through a refrigerant pipe 35. In the main path 30a, a regulating electromagnetic valve 37 is provided in the refrigerant line 35 between the external heat exchanger 32 and the outlet side capillary tube 36c.

規制電磁弁３７は、開閉可能な弁体であり、制御部２１ｂから開指令が与えられた場合には開成して冷媒の通過を許容する一方、閉指令が与えられた場合には閉成して冷媒の通過を規制するものである。   The regulating electromagnetic valve 37 is a valve body that can be opened and closed. When the opening command is given from the control unit 21b, the regulating solenoid valve 37 opens and allows the refrigerant to pass therethrough, but when the closing command is given, the regulating solenoid valve 37 closes. This restricts the passage of refrigerant.

以上のような構成を有する冷媒回路装置は、次のような冷却加熱運転を行う。ここで、冷却加熱運転の一例として、ＨＣＣ運転を行う場合について説明する。   The refrigerant circuit device having the above configuration performs the following cooling and heating operation. Here, a case where the HCC operation is performed will be described as an example of the cooling and heating operation.

この場合、制御部２１ｂは三方弁３６ａを第２送出状態にし、低圧側電磁弁３６ｄ，３６ｅ及びを開成させる一方、低圧側電磁弁３６ｆ、出口側電磁弁３６ｈ、バイパスバルブ６２及び規制電磁弁３７を閉成させる。これにより圧縮機３１で圧縮された冷媒は、図８に示すように循環する。尚、制御部２１ｂは、帰還管路５１に設けた電子膨張弁５２については、冷媒の蒸発温度に応じて開度を調整する。   In this case, the control unit 21b sets the three-way valve 36a to the second delivery state and opens the low pressure side solenoid valves 36d and 36e, while the low pressure side solenoid valve 36f, the outlet side solenoid valve 36h, the bypass valve 62, and the regulating solenoid valve 37. Is closed. Thus, the refrigerant compressed by the compressor 31 circulates as shown in FIG. Note that the control unit 21b adjusts the opening degree of the electronic expansion valve 52 provided in the return line 51 according to the evaporation temperature of the refrigerant.

圧縮機３１で圧縮された冷媒は、導入管路４１を通過して左庫内熱交換器３４ｃに至る。左庫内熱交換器３４ｃに至った冷媒は、該左庫内熱交換器３４ｃを通過中に、左庫３ｃの内部空気とそれぞれ熱交換し、該内部空気に放熱して凝縮する。これにより、左庫３ｃの内部空気を加熱する。加熱された内部空気は、庫内送風ファン１２の駆動により、左庫３ｃの内部を循環し、これにより左庫３ｃに収容された商品は、循環する内部空気に加熱される。   The refrigerant compressed by the compressor 31 passes through the introduction pipe 41 and reaches the left-inside heat exchanger 34c. The refrigerant that has reached the left-side internal heat exchanger 34c exchanges heat with the internal air of the left-side 3c while passing through the left-side internal heat exchanger 34c, and dissipates heat to the internal air to condense. Thereby, the internal air of the left warehouse 3c is heated. The heated internal air circulates inside the left warehouse 3c by driving the internal blower fan 12, whereby the product stored in the left warehouse 3c is heated to the circulating internal air.

左庫内熱交換器３４ｃで凝縮した冷媒は、帰還経路５０を構成する帰還管路５１を通過して電子膨張弁５２で減圧されて断熱膨張し、その後に第４合流点Ｐ４を通過して主経路３０ａに至る。このように主経路３０ａに至った冷媒は、分配器３６ｂを経由して右庫用キャピラリーチューブ３３ａ及び中庫用キャピラリーチューブ３３ｂで減圧されて断熱膨張する。   The refrigerant condensed in the left-side heat exchanger 34c passes through the return pipe 51 constituting the return path 50, is depressurized by the electronic expansion valve 52 and adiabatically expands, and then passes through the fourth junction P4. It reaches the main path 30a. Thus, the refrigerant that has reached the main path 30a is adiabatically expanded by being depressurized by the right-side capillary tube 33a and the middle-use capillary tube 33b via the distributor 36b.

中庫用キャピラリーチューブ３３ｂで断熱膨張した冷媒は、中庫内熱交換器３４ｂに至り、この中庫内熱交換器３４ｂで蒸発して中庫３ｂの内部空気から熱を奪い、該内部空気を冷却する。冷却された内部空気は、庫内送風ファン１２の駆動により中庫３ｂの内部を循環し、これにより中庫３ｂに収容された商品は冷却される。   The refrigerant adiabatically expanded in the internal capillary tube 33b reaches the internal heat exchanger 34b, evaporates in the internal heat exchanger 34b, takes heat from the internal air of the internal chamber 3b, and removes the internal air. Cooling. The cooled internal air circulates through the interior of the intermediate store 3b by driving the internal blower fan 12, whereby the product stored in the intermediate store 3b is cooled.

一方、右庫用キャピラリーチューブ３３ａで断熱膨張した冷媒は、右庫内熱交換器３４ａに至り、この右庫内熱交換器３４ａで蒸発して右庫３ａの内部空気から熱を奪い、該内部空気を冷却する。冷却された内部空気は、庫内送風ファン１２の駆動により右庫３ａの内部を循環し、これにより右庫３ａに収容された商品は冷却される。   On the other hand, the refrigerant adiabatically expanded in the right-hand capillary tube 33a reaches the right-hand heat exchanger 34a, evaporates in the right-hand heat exchanger 34a, and takes heat from the internal air of the right-hand warehouse 3a. Cool the air. The cooled internal air circulates through the inside of the right warehouse 3a by driving the internal blower fan 12, whereby the product stored in the right warehouse 3a is cooled.

右庫内熱交換器３４ａ及び中庫内熱交換器３４ｂで蒸発した冷媒は、第１合流点Ｐ１で合流した後に圧縮機３１に吸引され、その後に圧縮されて上述した循環を繰り返す。   The refrigerant evaporated in the right internal heat exchanger 34a and the internal internal heat exchanger 34b joins at the first junction P1, and then is sucked into the compressor 31 and then compressed and repeats the circulation described above.

以上説明したように、本実施の形態２である冷媒回路装置によれば、主経路３０ａにおける庫外熱交換器３２と出口側キャピラリーチューブ３６ｃとの間の冷媒管路３５に規制電磁弁３７が設けられており、帰還経路５０が、出口側キャピラリーチューブ３６ｃと低圧側電磁弁３６ｄ，３６ｅ，３６ｆとの間の冷媒管路３５に合流し、制御部２１ｂが、左庫３ｃの内部空気を加熱して右庫３ａ及び中庫３ｂの少なくとも一方の内部空気を冷却する冷却加熱運転を行う場合、規制電磁弁３７を閉成させて、圧縮機３１で圧縮された冷媒が導入経路４０（導入管路４１）を介して左庫内熱交換器３４ｃで熱交換した後に帰還管路５１（帰還経路５０）を通過中に電子膨張弁５２で断熱膨張してから第１膨張機構３３（右庫用キャピラリーチューブ３３ａ及び中庫用キャピラリーチューブ３３ｂ）で断熱膨張して右庫内熱交換器３４ａ及び中庫内熱交換器３４ｂを通過するよう冷媒回路２１ａを循環させるので、冷媒が庫外熱交換器３２を通過することなく冷媒回路２１ａを循環させることができる。これにより、左庫内熱交換器３４ｃを通過後に気液混合状態となる冷媒の多くが電子膨張弁５２で減圧された後に第１膨張機構３３で減圧されて庫内熱交換器３４で蒸発するので、庫外熱交換器３２に滞留して寝込んでしまうことを抑制することができる。そのため、冷媒回路２１ａを循環する冷媒量が少なくなってしまうことがない。従って、冷却加熱運転を行う場合において循環冷媒量の低減に伴う運転効率の低下を防止することができる。   As described above, according to the refrigerant circuit device of the second embodiment, the regulating electromagnetic valve 37 is provided in the refrigerant pipe 35 between the external heat exchanger 32 and the outlet side capillary tube 36c in the main path 30a. The return path 50 joins the refrigerant pipe 35 between the outlet side capillary tube 36c and the low pressure side solenoid valves 36d, 36e, and 36f, and the control unit 21b heats the internal air of the left chamber 3c. When the cooling and heating operation for cooling the internal air of at least one of the right warehouse 3a and the middle warehouse 3b is performed, the regulating electromagnetic valve 37 is closed, and the refrigerant compressed by the compressor 31 is introduced into the introduction path 40 (introduction pipe 40). The first expansion mechanism 33 (for the right warehouse is used after adiabatic expansion by the electronic expansion valve 52 while passing through the return pipe 51 (return path 50) after heat exchange by the left-side heat exchanger 34c via the path 41). Capillary tube 3a and the internal capillary tube 33b), and the refrigerant circuit 21a is circulated so as to pass through the right internal heat exchanger 34a and the internal heat exchanger 34b, so that the refrigerant passes through the external heat exchanger 32. The refrigerant circuit 21a can be circulated without passing. As a result, most of the refrigerant that enters the gas-liquid mixed state after passing through the left internal heat exchanger 34c is decompressed by the electronic expansion valve 52, then decompressed by the first expansion mechanism 33, and evaporated by the internal heat exchanger 34. Therefore, it can suppress staying in the external heat exchanger 32 and falling asleep. Therefore, the amount of refrigerant circulating through the refrigerant circuit 21a does not decrease. Therefore, in the case of performing the cooling and heating operation, it is possible to prevent a decrease in operation efficiency due to a reduction in the circulating refrigerant amount.

このように冷却加熱運転を行う場合において循環冷媒量の低減に伴う運転効率の低下を防止することができるので、冷媒回路２１ａに対する冷媒の封入量を低減することができ、コストの低減化を図ることができるとともに、冷却加熱運転での加熱能力の向上により省エネルギー化を図ることができる。   In this way, when performing the cooling and heating operation, it is possible to prevent a decrease in operation efficiency due to a reduction in the amount of circulating refrigerant, so that the amount of refrigerant enclosed in the refrigerant circuit 21a can be reduced, and the cost can be reduced. In addition, energy saving can be achieved by improving the heating capacity in the cooling and heating operation.

＜実施の形態３＞
図９は、本発明の実施の形態３である冷媒回路装置を概念的に示す概念図である。尚、上述した実施の形態１である冷媒回路装置と同様の構成を有するものには同一の符号を付してその説明を適宜省略する。 <Embodiment 3>
FIG. 9 is a conceptual diagram conceptually showing the refrigerant circuit device according to the third embodiment of the present invention. In addition, the same code | symbol is attached | subjected to what has the structure similar to the refrigerant circuit apparatus which is Embodiment 1 mentioned above, and the description is abbreviate | omitted suitably.

ここで例示する冷媒回路装置は、冷媒が封入された冷媒回路２２ａと、この冷媒回路２２ａに設けられた各部を適宜制御する制御部（制御手段）２２ｂとを備えて構成されている。   The refrigerant circuit device illustrated here includes a refrigerant circuit 22a in which a refrigerant is sealed, and a control unit (control means) 22b that appropriately controls each unit provided in the refrigerant circuit 22a.

冷媒回路２２ａは、主経路３０ｂ、導入経路４０、帰還経路５０ａ及びバイパス経路６０ａを有している。主経路３０ｂは、圧縮機３１、庫外熱交換器３２、第１膨張機構３３及び庫内熱交換器３４を冷媒管路３５にて適宜接続して構成されており、庫外熱交換器３２と分配器３６ｂとの間の冷媒管路３５には出口側逆止弁３８が設けられている。   The refrigerant circuit 22a has a main path 30b, an introduction path 40, a return path 50a, and a bypass path 60a. The main path 30 b is configured by appropriately connecting a compressor 31, an external heat exchanger 32, a first expansion mechanism 33, and an internal heat exchanger 34 through a refrigerant pipe 35. An outlet-side check valve 38 is provided in the refrigerant pipe 35 between the outlet 36b and the distributor 36b.

帰還経路５０ａは、左庫内熱交換器３４ｃの出口側に接続された冷媒管路３５の途中の第１分岐点Ｑ１で分岐し、庫外熱交換器３２から分配器３６ｂに至る冷媒管路３５における出口側逆止弁３８と分配器３６ｂとの間の第４合流点Ｐ４で合流する態様で該冷媒管路３５に接続された帰還管路５１ａにより構成された経路である。   The return path 50a branches at a first branch point Q1 in the middle of the refrigerant line 35 connected to the outlet side of the left-side heat exchanger 34c, and reaches the distributor 36b from the external heat exchanger 32. 35 is a path constituted by a return pipe 51a connected to the refrigerant pipe 35 in a mode of joining at a fourth junction P4 between the outlet side check valve 38 and the distributor 36b.

この帰還経路５０ａは、左庫内熱交換器３４ｃで凝縮した冷媒を主経路３０ｂに帰還させるためのものである。該帰還経路５０ａを構成する帰還管路５１ａの途中には、電子膨張弁５２、帰還キャピラリーチューブ５４、帰還三方弁５５及び帰還逆止弁５６が設けられている。   This return path 50a is for returning the refrigerant condensed in the left-side heat exchanger 34c to the main path 30b. An electronic expansion valve 52, a feedback capillary tube 54, a feedback three-way valve 55, and a feedback check valve 56 are provided in the middle of the feedback pipe 51a constituting the feedback path 50a.

帰還キャピラリーチューブ５４は、帰還管路５１ａにおける電子膨張弁５２の下流側に設置されており、通過する冷媒を減圧して断熱膨張させるものである。   The return capillary tube 54 is installed on the downstream side of the electronic expansion valve 52 in the return line 51a, and decompresses the refrigerant passing therethrough to adiabatically expand.

帰還三方弁５５は、電子膨張弁５２及び帰還キャピラリーチューブ５４で断熱膨張した冷媒を帰還管路５１ａを通じて主経路３０ｂに送出する第１送出状態と、電子膨張弁５２及び帰還キャピラリーチューブ５４で断熱膨張した冷媒を第２帰還管路５１ｂを通じて主経路３０ｂに送出する第２送出状態との間で択一的に切換可能な切換バルブである。ここで、第２帰還管路５１ｂは、一端が帰還三方弁５５の一の出口に接続されるとともに、他端が圧縮機３１と庫外熱交換器３２との間の冷媒管路３５の第６合流点Ｐ６で合流する態様で設けられている。上記帰還三方弁５５の切換動作は、制御部２２ｂから与えられる指令に応じて行われる。帰還逆止弁５６は、帰還三方弁５５の下流側となる帰還管路５１ａに設けられている。   The return three-way valve 55 includes a first delivery state in which the refrigerant adiabatically expanded by the electronic expansion valve 52 and the return capillary tube 54 is sent to the main path 30b through the return conduit 51a, and adiabatic expansion by the electronic expansion valve 52 and the return capillary tube 54. This is a switching valve that can be switched selectively between the second delivery state in which the refrigerant is delivered to the main route 30b through the second return pipeline 51b. Here, one end of the second return pipe 51b is connected to one outlet of the return three-way valve 55, and the other end of the second return pipe 51b is the first of the refrigerant pipe 35 between the compressor 31 and the external heat exchanger 32. It is provided in such a manner that it merges at 6 junction points P6. The switching operation of the feedback three-way valve 55 is performed according to a command given from the control unit 22b. The return check valve 56 is provided in the return line 51 a on the downstream side of the return three-way valve 55.

バイパス経路６０ａは、庫外熱交換器３２から出口側逆止弁３８に至る冷媒管路３５の途中の第３分岐点Ｑ３から分岐し、第１合流点Ｐ１から圧縮機３１に至る冷媒管路３５の途中の第５合流点Ｐ５で合流する態様で設けたバイパス管路６１ａにより構成されている。このバイパス管路６１ａには、バイパスバルブ６２が設けられている。バイパスバルブ６２は、開閉可能な弁体であり、制御部２２ｂから開指令が与えられた場合には開成して冷媒がバイパス管路６１ａを通過することを許容する一方、制御部２２ｂから閉指令が与えられた場合には閉成して冷媒がバイパス管路６１ａを通過することを規制するものである。   The bypass path 60a branches from the third branch point Q3 in the middle of the refrigerant pipe 35 extending from the external heat exchanger 32 to the outlet check valve 38, and is connected to the compressor 31 from the first junction P1. 35 is constituted by a bypass pipeline 61a provided in such a manner that it merges at a fifth junction P5 in the middle of 35. A bypass valve 62 is provided in the bypass conduit 61a. The bypass valve 62 is a valve body that can be opened and closed. When the opening command is given from the control unit 22b, the bypass valve 62 opens and allows the refrigerant to pass through the bypass pipe 61a, while the control unit 22b closes the closing command. Is closed to restrict the refrigerant from passing through the bypass pipe 61a.

以上のような構成を有する冷媒回路装置は、次のようにして商品収容庫３に収容された商品を冷却、あるいは加熱する。   The refrigerant circuit device having the above-described configuration cools or heats the product stored in the product storage 3 as follows.

まず冷却単独運転の一例として、ＣＣＣ運転を行う場合について説明する。この場合、制御部２２ｂは三方弁３６ａ及び帰還三方弁５５を第１送出状態にし、低圧側電磁弁３６ｄ，３６ｅ，３６ｆ及び出口側電磁弁３６ｈを開成させる一方、バイパスバルブ６２を閉成させる。これにより圧縮機３１で圧縮された冷媒は、図１０に示すように循環する。   First, a case where a CCC operation is performed will be described as an example of a single cooling operation. In this case, the controller 22b sets the three-way valve 36a and the feedback three-way valve 55 to the first delivery state, opens the low-pressure side solenoid valves 36d, 36e, 36f, and the outlet-side solenoid valve 36h, and closes the bypass valve 62. As a result, the refrigerant compressed by the compressor 31 circulates as shown in FIG.

すなわち、圧縮機３１で圧縮された冷媒は、三方弁３６ａを通過して冷媒管路３５を経由して庫外熱交換器３２に至る。庫外熱交換器３２に至った冷媒は、該庫外熱交換器３２を通過中に、周囲空気（外気）に放熱して凝縮する。庫外熱交換器３２で凝縮した冷媒は、分配器３６ｂで分岐され、右庫用キャピラリーチューブ３３ａ、中庫用キャピラリーチューブ３３ｂ及び左庫用キャピラリーチューブ３３ｃにより減圧されて断熱膨張し、右庫内熱交換器３４ａ、中庫内熱交換器３４ｂ及び左庫内熱交換器３４ｃに至る。このように各庫内熱交換器３４に至った冷媒は、各庫内熱交換器３４で蒸発して商品収容庫３の内部空気から熱を奪い、該内部空気を冷却する。冷却された内部空気は、各庫内熱交換器３４の近傍に配設された庫内送風ファン１２の駆動により内部を循環し、これにより各商品収容庫３に収容された商品は、循環する内部空気に冷却される。   That is, the refrigerant compressed by the compressor 31 passes through the three-way valve 36 a and reaches the external heat exchanger 32 via the refrigerant pipe 35. The refrigerant that reaches the external heat exchanger 32 dissipates heat to ambient air (outside air) and condenses while passing through the external heat exchanger 32. The refrigerant condensed in the external heat exchanger 32 is branched by the distributor 36b, depressurized by the right-side capillary tube 33a, the middle-use capillary tube 33b, and the left-side capillary tube 33c, and is adiabatically expanded. It reaches the heat exchanger 34a, the internal heat exchanger 34b, and the left internal heat exchanger 34c. Thus, the refrigerant | coolant which reached each internal heat exchanger 34 evaporates in each internal heat exchanger 34, takes heat from the internal air of the goods storage 3, and cools this internal air. The cooled internal air circulates in the interior by driving the internal blower fan 12 disposed in the vicinity of each internal heat exchanger 34, whereby the products accommodated in each commodity storage 3 circulate. Cooled to internal air.

各庫内熱交換器３４で蒸発した冷媒は、第１合流点Ｐ１及び第２合流点Ｐ２で合流した後に圧縮機３１に吸引され、その後に圧縮されて上述した循環を繰り返す。   The refrigerant evaporated in each internal heat exchanger 34 joins at the first joining point P1 and the second joining point P2, and then is sucked into the compressor 31 and then compressed and repeats the circulation described above.

次に冷却加熱運転の一例として、ＨＣＣ運転を行う場合について説明する。この場合、制御部２２ｂは三方弁３６ａを第２送出状態にするとともに帰還三方弁５５を第１送出状態にし、低圧側電磁弁３６ｄ，３６ｅを開成させる一方、低圧側電磁弁３６ｆ、出口側電磁弁３６ｈ及びバイパスバルブ６２を閉成させる。これにより圧縮機３１で圧縮された冷媒は、図１１に示すように循環する。尚、制御部２２ｂは、帰還管路５１ａに設けた電子膨張弁５２については、冷媒の蒸発温度に応じて開度を調整する。   Next, a case where the HCC operation is performed will be described as an example of the cooling and heating operation. In this case, the control unit 22b sets the three-way valve 36a to the second sending state and the feedback three-way valve 55 to the first sending state to open the low-pressure side solenoid valves 36d and 36e, while the low-pressure side solenoid valve 36f and the outlet-side solenoid The valve 36h and the bypass valve 62 are closed. Thus, the refrigerant compressed by the compressor 31 circulates as shown in FIG. The control unit 22b adjusts the opening degree of the electronic expansion valve 52 provided in the return pipe 51a according to the evaporation temperature of the refrigerant.

圧縮機３１で圧縮された冷媒は、導入管路４１を通過して左庫内熱交換器３４ｃに至る。左庫内熱交換器３４ｃに至った冷媒は、該左庫内熱交換器３４ｃを通過中に、左庫３ｃの内部空気とそれぞれ熱交換し、該内部空気に放熱して凝縮する。これにより、左庫３ｃの内部空気を加熱する。加熱された内部空気は、庫内送風ファン１２の駆動により、左庫３ｃの内部を循環し、これにより左庫３ｃに収容された商品は、循環する内部空気に加熱される。   The refrigerant compressed by the compressor 31 passes through the introduction pipe 41 and reaches the left-inside heat exchanger 34c. The refrigerant that has reached the left-side internal heat exchanger 34c exchanges heat with the internal air of the left-side 3c while passing through the left-side internal heat exchanger 34c, and dissipates heat to the internal air to condense. Thereby, the internal air of the left warehouse 3c is heated. The heated internal air circulates inside the left warehouse 3c by driving the internal blower fan 12, whereby the product stored in the left warehouse 3c is heated to the circulating internal air.

左庫内熱交換器３４ｃで凝縮した冷媒は、帰還経路５０ａを構成する帰還管路５１ａを通過して電子膨張弁５２及び帰還キャピラリーチューブ５４で減圧されて断熱膨張し、その後に第４合流点Ｐ４を通過して主経路３０ｂに至る。このように主経路３０ｂに至った冷媒は、分配器３６ｂを経由して右庫用キャピラリーチューブ３３ａ及び中庫用キャピラリーチューブ３３ｂで減圧されて断熱膨張する。   The refrigerant condensed in the left-side internal heat exchanger 34c passes through the return line 51a constituting the return path 50a, is decompressed by the electronic expansion valve 52 and the return capillary tube 54, and is adiabatically expanded. Thereafter, the fourth confluence It passes through P4 and reaches the main route 30b. The refrigerant that has reached the main path 30b is decompressed and adiabatically expanded by the right-side capillary tube 33a and the middle-use capillary tube 33b via the distributor 36b.

中庫用キャピラリーチューブ３３ｂで断熱膨張した冷媒は、中庫内熱交換器３４ｂに至り、この中庫内熱交換器３４ｂで蒸発して中庫３ｂの内部空気から熱を奪い、該内部空気を冷却する。冷却された内部空気は、庫内送風ファン１２の駆動により中庫３ｂの内部を循環し、これにより中庫３ｂに収容された商品は冷却される。   The refrigerant adiabatically expanded by the internal capillary tube 33b reaches the internal heat exchanger 34b, evaporates in the internal heat exchanger 34b, takes heat from the internal air of the internal chamber 3b, and removes the internal air. Cooling. The cooled internal air circulates through the interior of the intermediate store 3b by driving the internal blower fan 12, whereby the product stored in the intermediate store 3b is cooled.

一方、右庫用キャピラリーチューブ３３ａで断熱膨張した冷媒は、右庫内熱交換器３４ａに至り、この右庫内熱交換器３４ａで蒸発して右庫３ａの内部空気から熱を奪い、該内部空気を冷却する。冷却された内部空気は、庫内送風ファン１２の駆動により右庫３ａの内部を循環し、これにより右庫３ａに収容された商品は冷却される。   On the other hand, the refrigerant adiabatically expanded in the right-hand capillary tube 33a reaches the right-hand heat exchanger 34a, evaporates in the right-hand heat exchanger 34a, and takes heat from the internal air of the right-hand warehouse 3a. Cool the air. The cooled internal air circulates through the inside of the right warehouse 3a by driving the internal blower fan 12, whereby the product stored in the right warehouse 3a is cooled.

右庫内熱交換器３４ａ及び中庫内熱交換器３４ｂで蒸発した冷媒は、第１合流点Ｐ１で合流した後に圧縮機３１に吸引され、その後に圧縮されて上述した循環を繰り返す。   The refrigerant evaporated in the right internal heat exchanger 34a and the internal internal heat exchanger 34b joins at the first junction P1, and then is sucked into the compressor 31 and then compressed and repeats the circulation described above.

更に加熱単独運転の一例として、左庫３ｃの内部空気のみを加熱する運転を行う場合について説明する。   Furthermore, the case where the operation | movement which heats only the internal air of the left store | warehouse | chamber 3c is performed is demonstrated as an example of heating independent operation.

この場合、制御部２２ｂは、三方弁３６ａ及び帰還三方弁５５を第２送出状態にし、バイパスバルブ６２を開成させる一方、低圧側電磁弁３６ｄ，３６ｅ，３６ｆ及び出口側電磁弁３６ｈを閉成させる。これにより圧縮機３１で圧縮された冷媒は、図１２に示すように循環する。尚、制御部２２ｂは、帰還管路５１ａに設けた電子膨張弁５２についても通過する冷媒を断熱膨張するべく、所望の絞り量となるよう開度を調整する。   In this case, the control unit 22b sets the three-way valve 36a and the feedback three-way valve 55 to the second delivery state, opens the bypass valve 62, and closes the low-pressure side solenoid valves 36d, 36e, 36f and the outlet-side solenoid valve 36h. . As a result, the refrigerant compressed by the compressor 31 circulates as shown in FIG. In addition, the control part 22b adjusts an opening degree so that it may become a desired throttle amount so that the refrigerant | coolant which passes also about the electronic expansion valve 52 provided in the return pipeline 51a may be adiabatically expanded.

圧縮機３１で圧縮された冷媒は、導入管路４１を通過して左庫内熱交換器３４ｃに至る。左庫内熱交換器３４ｃに至った冷媒は、該左庫内熱交換器３４ｃを通過中に、左庫３ｃの内部空気とそれぞれ熱交換し、該内部空気に放熱して凝縮する。これにより、左庫３ｃの内部空気を加熱する。加熱された内部空気は、庫内送風ファン１２の駆動により、左庫３ｃの内部を循環し、これにより左庫３ｃに収容された商品は、循環する内部空気に加熱される。   The refrigerant compressed by the compressor 31 passes through the introduction pipe 41 and reaches the left-inside heat exchanger 34c. The refrigerant that has reached the left-side internal heat exchanger 34c exchanges heat with the internal air of the left-side 3c while passing through the left-side internal heat exchanger 34c, and dissipates heat to the internal air to condense. Thereby, the internal air of the left warehouse 3c is heated. The heated internal air circulates inside the left warehouse 3c by driving the internal blower fan 12, whereby the product stored in the left warehouse 3c is heated to the circulating internal air.

左庫内熱交換器３４ｃで凝縮した冷媒は、帰還経路５０ａを構成する帰還管路５１ａを通過して電子膨張弁５２及び帰還キャピラリーチューブ５４で減圧されて断熱膨張し、その後に第６合流点Ｐ６を通過して庫外熱交換器３２に至り、該庫外熱交換器３２で周囲空気と熱交換を行って蒸発する。庫外熱交換器３２で蒸発した冷媒は、バイパス管路６１ａを通過した後に圧縮機３１に吸引され、その後に圧縮されて上述した循環を繰り返す。   The refrigerant condensed in the left internal heat exchanger 34c passes through the return pipe 51a constituting the return path 50a, is decompressed by the electronic expansion valve 52 and the return capillary tube 54, and is adiabatically expanded. It passes through P6 and reaches the external heat exchanger 32, and heat is exchanged with ambient air in the external heat exchanger 32 to evaporate. The refrigerant evaporated in the external heat exchanger 32 is sucked into the compressor 31 after passing through the bypass pipe 61a, and then compressed and repeated as described above.

以上説明したように、本実施の形態３である冷媒回路装置によれば、帰還経路５０ａが、帰還三方弁５５が第１送出状態となる場合には、主経路３０ｂにおける庫外熱交換器３２と低圧側電磁弁３６ｄ，３６ｅ，３６ｆとの間の冷媒管路３５に合流し、かつ左庫内熱交換器３４ｃで熱交換を行った冷媒を送出するものであり、制御部２２ｂが、左庫３ｃの内部空気を加熱して右庫３ａ及び中庫３ｂの少なくとも一方の内部空気を冷却する冷却加熱運転を行うとき、圧縮機３１で圧縮された冷媒が導入経路４０（導入管路４１）を介して左庫内熱交換器３４ｃで熱交換した後に帰還管路５１ａ（帰還経路５０ａ）を通過中に電子膨張弁５２で断熱膨張してから第１膨張機構３３（右庫用キャピラリーチューブ３３ａ及び中庫用キャピラリーチューブ３３ｂ）で断熱膨張して右庫内熱交換器３４ａ及び中庫内熱交換器３４ｂを通過するよう冷媒回路２２ａを循環させるので、冷媒が庫外熱交換器３２を通過することなく冷媒回路２２ａを循環させることができる。これにより、左庫内熱交換器３４ｃを通過後に気液混合状態となる冷媒の多くが電子膨張弁５２で減圧された後に第１膨張機構３３で減圧されて庫内熱交換器３４で蒸発するので、庫外熱交換器３２に滞留して寝込んでしまうことを抑制することができる。そのため、冷媒回路２２ａを循環する冷媒量が少なくなってしまうことがない。従って、冷却加熱運転を行う場合において循環冷媒量の低減に伴う運転効率の低下を防止することができる。   As described above, according to the refrigerant circuit device of the third embodiment, when the return path 50a is in the first delivery state of the return three-way valve 55, the external heat exchanger 32 in the main path 30b. And the low-pressure side solenoid valves 36d, 36e, and 36f join the refrigerant pipe 35 and send out the refrigerant that has exchanged heat with the left-side heat exchanger 34c. When performing a cooling and heating operation in which the internal air of the warehouse 3c is heated to cool at least one of the internal air of the right warehouse 3a and the middle warehouse 3b, the refrigerant compressed by the compressor 31 is introduced into the introduction path 40 (introduction pipe 41). The first expansion mechanism 33 (the right-side capillary tube 33a is adiabatically expanded by the electronic expansion valve 52 while passing through the return line 51a (the return path 50a) after heat exchange by the left-side heat exchanger 34c via And capillary cup for storage The refrigerant circuit 22a is circulated so that the refrigerant circuit 22a passes through the right internal heat exchanger 34a and the internal heat exchanger 34b after being adiabatically expanded in step 33b), so that the refrigerant does not pass through the external heat exchanger 32. 22a can be circulated. As a result, most of the refrigerant that enters the gas-liquid mixed state after passing through the left internal heat exchanger 34c is decompressed by the electronic expansion valve 52, then decompressed by the first expansion mechanism 33, and evaporated by the internal heat exchanger 34. Therefore, it can suppress staying in the external heat exchanger 32 and falling asleep. Therefore, the amount of refrigerant circulating through the refrigerant circuit 22a does not decrease. Therefore, in the case of performing the cooling and heating operation, it is possible to prevent a decrease in operation efficiency due to a reduction in the circulating refrigerant amount.

このように冷却加熱運転を行う場合において循環冷媒量の低減に伴う運転効率の低下を防止することができるので、冷媒回路２２ａに対する冷媒の封入量を低減することができ、コストの低減化を図ることができるとともに、冷却加熱運転での加熱能力の向上により省エネルギー化を図ることができる。   In this way, when performing the cooling and heating operation, it is possible to prevent a decrease in operation efficiency due to a reduction in the amount of circulating refrigerant, so that it is possible to reduce the amount of refrigerant enclosed in the refrigerant circuit 22a and to reduce costs. In addition, energy saving can be achieved by improving the heating capacity in the cooling and heating operation.

以上、本発明の好適な実施の形態１〜３について説明したが、本発明はこれに限定されるものではなく、種々の変更を行うことができる。   As mentioned above, although preferred Embodiment 1-3 of this invention was demonstrated, this invention is not limited to this, A various change can be performed.

上述した実施の形態１〜３では、３つの庫内熱交換器３４を有する冷媒回路装置について説明したが、本発明においては、２つ以上の室内熱交換器を有しているものであっても良い。   Although Embodiment 1-3 mentioned above demonstrated the refrigerant circuit apparatus which has the three heat exchangers 34 in a warehouse, in this invention, it has two or more indoor heat exchangers, Also good.

３ 商品収容庫
２０ａ 冷媒回路
２０ｂ 制御部（制御手段）
３０ 主経路
３１ 圧縮機
３２ 庫外熱交換器
３３ 第１膨張機構
３４ 庫内熱交換器
３５ 冷媒管路
３６ａ 三方弁
３６ｂ 分配器
３６ｃ 出口側キャピラリーチューブ
３６ｄ 低圧側電磁弁
３６ｅ 低圧側電磁弁
３６ｆ 低圧側電磁弁
３６ｈ 出口側電磁弁
４０ 導入経路
４１ 導入管路
５０ 帰還経路
５１ 帰還管路
５２ 電子膨張弁
６０ バイパス経路
６１ バイパス管路
６２ バイパスバルブ 3 goods storage 20a refrigerant circuit 20b control part (control means)
30 Main path 31 Compressor 32 External heat exchanger 33 First expansion mechanism 34 Internal heat exchanger 35 Refrigerant conduit 36a Three-way valve 36b Distributor 36c Outlet side capillary tube 36d Low pressure side solenoid valve 36e Low pressure side solenoid valve 36f Low pressure Side solenoid valve 36h outlet side solenoid valve 40 introduction path 41 introduction pipe line 50 return path 51 return pipe line 52 electronic expansion valve 60 bypass path 61 bypass pipe line 62 bypass valve

Claims (5)

各室に設置された複数の室内熱交換器と、前記室の外部に設置された圧縮機及び室外熱交換器と、通過する冷媒を断熱膨張させる第１膨張機構とを冷媒管路で順次接続して構成された主経路と、
前記圧縮機で圧縮された冷媒を、前記室内熱交換器のうち加熱対象となる室に設置された加熱兼用室内熱交換器に送出する導入経路と、
通過する冷媒を断熱膨張させる第２膨張機構を有し、かつ前記導入経路を通じて前記加熱兼用室内熱交換器に送出された冷媒を前記主経路に送出する帰還経路と
を備えた冷媒回路を有する冷媒回路装置において、
前記主経路は、前記室外熱交換器と前記第１膨張機構との間の冷媒管路に開閉可能に設置され、かつ開成する場合には冷媒が通過することを許容する一方、閉成する場合には冷媒の通過を規制する電磁弁を備え、前記帰還経路は、前記室外熱交換器と前記電磁弁との間の冷媒管路に合流し、かつ前記加熱兼用室内熱交換器で熱交換を行った冷媒を送出するものであり、
加熱対象となる室の内部空気を加熱して他の室の内部空気を冷却する冷却加熱運転を行う場合、圧縮機で圧縮された冷媒が前記導入経路を介して前記加熱兼用室内熱交換器で熱交換した後に前記帰還経路を通過中に前記第２膨張機構で断熱膨張してから前記第１膨張機構で断熱膨張して前記室内熱交換器を通過するよう前記冷媒回路を循環させる制御手段を備えたことを特徴とする冷媒回路装置。 A plurality of indoor heat exchangers installed in each chamber, a compressor and an outdoor heat exchanger installed outside the chamber, and a first expansion mechanism for adiabatically expanding the refrigerant passing therethrough are sequentially connected by a refrigerant pipe. A main route configured as
An introduction path for sending the refrigerant compressed by the compressor to a heating combined indoor heat exchanger installed in a room to be heated in the indoor heat exchanger;
A refrigerant having a second expansion mechanism for adiabatically expanding the refrigerant passing therethrough, and having a refrigerant circuit having a return path for sending the refrigerant sent to the heating / combustion indoor heat exchanger through the introduction path to the main path In the circuit device,
The main path is installed in a refrigerant conduit between the outdoor heat exchanger and the first expansion mechanism so as to be openable and closable, and allows the refrigerant to pass when opening, while closing the main path. Includes a solenoid valve for restricting passage of the refrigerant, and the return path joins a refrigerant pipe line between the outdoor heat exchanger and the solenoid valve, and heat is exchanged by the heating combined indoor heat exchanger. To deliver the refrigerant that has been performed,
When performing a cooling and heating operation in which the internal air of a chamber to be heated is heated to cool the internal air of another chamber, the refrigerant compressed by the compressor is transferred to the heating combined indoor heat exchanger via the introduction path. Control means for circulating the refrigerant circuit so as to pass through the indoor heat exchanger after adiabatic expansion by the second expansion mechanism and adiabatic expansion by the first expansion mechanism while passing through the return path after heat exchange. A refrigerant circuit device comprising: 前記主経路は、前記室外熱交換器と前記第１膨張機構との間の冷媒管路に設置され、かつ通過する冷媒を断熱膨張させる第３膨張機構を備え、
前記帰還経路は、前記第３膨張機構と前記電磁弁との間の冷媒管路に合流し、かつ前記加熱兼用室内熱交換器で熱交換を行った冷媒を送出することを特徴とする請求項１に記載の冷媒回路装置。 The main path includes a third expansion mechanism that is installed in a refrigerant pipe line between the outdoor heat exchanger and the first expansion mechanism and adiabatically expands the refrigerant that passes therethrough,
The return path joins a refrigerant pipe line between the third expansion mechanism and the solenoid valve, and sends out the refrigerant that has been heat-exchanged by the heating and indoor heat exchanger. 2. The refrigerant circuit device according to 1. 前記圧縮機と前記室外熱交換器との間の冷媒管路から分岐するとともに、前記室内熱交換器と前記圧縮機との間の冷媒管路に合流する態様で配設されたバイパス経路と、
前記バイパス経路に開閉可能に設置され、かつ開成する場合には冷媒が通過することを許容する一方、閉成する場合には冷媒の通過を規制するバイパスバルブと
を備えたことを特徴とする請求項１又は請求項２に記載の冷媒回路装置。 A bypass path arranged in a manner to branch from a refrigerant pipe line between the compressor and the outdoor heat exchanger and merge with a refrigerant pipe line between the indoor heat exchanger and the compressor;
A bypass valve that is installed in the bypass path so as to be openable and closable and allows passage of the refrigerant when opened, and restricts passage of the refrigerant when closed. The refrigerant circuit device according to claim 1 or 2. 前記第２膨張機構は、電子膨張弁により構成されたことを特徴とする請求項１〜３のいずれか１つに記載の冷媒回路装置。   The refrigerant circuit device according to claim 1, wherein the second expansion mechanism is configured by an electronic expansion valve. 前記室外熱交換器と前記第３膨張機構との間の冷媒管路に開閉可能に設置され、かつ開成する場合には冷媒が通過することを許容する一方、閉成する場合には冷媒の通過を規制する規制電磁弁を備え、
前記制御手段が、前記冷却加熱運転を行う場合、前記規制電磁弁を閉成させることを特徴とする請求項２〜４のいずれか１つに記載の冷媒回路装置。 The refrigerant pipe between the outdoor heat exchanger and the third expansion mechanism is installed to be openable and closable, and allows the refrigerant to pass when opening, while passing the refrigerant when closing. Equipped with a regulating solenoid valve to regulate
The refrigerant circuit device according to any one of claims 2 to 4, wherein when the control means performs the cooling and heating operation, the regulating electromagnetic valve is closed.
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