JP2017015299A

JP2017015299A - Cooling device

Info

Publication number: JP2017015299A
Application number: JP2015131050A
Authority: JP
Inventors: 中村　新吾; Shingo Nakamura; 新吾中村; 賢河村; Masaru Kawamura; 博志加藤; Hiroshi Kato
Original assignee: Fuji Electric Co Ltd
Current assignee: Fuji Electric Co Ltd
Priority date: 2015-06-30
Filing date: 2015-06-30
Publication date: 2017-01-19

Abstract

PROBLEM TO BE SOLVED: To provide a cooling device capable of properly adjusting a flow rate and a temperature of a refrigerant flowing from a bypass flow channel to an evaporator in each evaporator, in the cooling device including the plurality of evaporators connected in parallel with each other.SOLUTION: A cooling device 100 includes a hot gas bypass flow channel 6 connecting a discharge side of a compressor 10 and each of refrigerant inflow sides of a plurality of evaporators 30a-30c, a plurality of solenoid valves 52a-52c disposed on the hot gas bypass flow channel 6, a plurality of solenoid valves 53a-53c disposed at the refrigerant outflow sides of the evaporators 30a-30c, and a control portion controlling opening degrees of the plurality of solenoid valves 52a-52c and controlling opening degrees of the plurality of solenoid valves 53a-53c.SELECTED DRAWING: Figure 1

Description

この発明は、冷却装置に関し、特に、圧縮機の吐出側と蒸発器の冷媒流入側とを接続するバイパス流路を備える冷却装置に関する。 The present invention relates to a cooling device, and more particularly, to a cooling device including a bypass channel that connects a discharge side of a compressor and a refrigerant inflow side of an evaporator.

従来、圧縮機の吐出側と蒸発器の冷媒流入側とを接続するバイパス流路を備える冷却装置が知られている（たとえば、特許文献１参照）。 2. Description of the Related Art Conventionally, a cooling device including a bypass channel that connects a discharge side of a compressor and a refrigerant inflow side of an evaporator is known (see, for example, Patent Document 1).

上記特許文献１には、１台の圧縮機と、凝縮器と、主膨張弁と、蒸発器とを備えるコンテナ用冷凍装置が開示されている。このコンテナ用冷凍装置には、圧縮機からの圧縮冷媒を、凝縮器および主膨張弁をバイパスして蒸発器に送るためのホットガスバイパス回路が設けられている。また、ホットガスバイパス回路には、蒸発器に流入する冷媒の流量を調整するための弁が設けられている。そして、このコンテナ用冷凍装置では、蒸発器の霜を除霜する除霜動作時に、ホットガスバイパス回路から蒸発器に流入する冷媒の流量が弁で調整されるとともに、圧縮機の圧縮冷媒の圧力（温度）が目標値になるように、１台の圧縮機の運転回転数が制御される。 Patent Document 1 discloses a container refrigeration apparatus including one compressor, a condenser, a main expansion valve, and an evaporator. The container refrigeration apparatus is provided with a hot gas bypass circuit for sending the compressed refrigerant from the compressor to the evaporator by bypassing the condenser and the main expansion valve. The hot gas bypass circuit is provided with a valve for adjusting the flow rate of the refrigerant flowing into the evaporator. In this container refrigeration apparatus, the flow rate of the refrigerant flowing into the evaporator from the hot gas bypass circuit is adjusted by the valve during the defrosting operation for defrosting the evaporator frost, and the pressure of the compressed refrigerant of the compressor The operating rotational speed of one compressor is controlled so that (temperature) becomes a target value.

特開２０１１−２５２７０２号公報JP 2011-252702 A

しかしながら、上記特許文献１に記載されたコンテナ用冷凍装置では、ホットガスバイパス回路から蒸発器に流入する冷媒の流量が弁で調整されるとともに、圧縮機の圧縮冷媒の圧力（温度）が目標値になるように、１台の圧縮機の運転回転数が制御されるように構成されている一方、圧縮機が１台であるため、蒸発器が複数並列して設けられる場合には、複数の蒸発器の圧縮冷媒の圧力（温度）を、蒸発器毎に適切に調整するのが困難であるという問題点がある。 However, in the container refrigeration apparatus described in Patent Document 1, the flow rate of the refrigerant flowing into the evaporator from the hot gas bypass circuit is adjusted by a valve, and the pressure (temperature) of the compressed refrigerant in the compressor is a target value. On the other hand, since the number of operating revolutions of one compressor is controlled, the compressor is one, so when a plurality of evaporators are provided in parallel, There is a problem that it is difficult to appropriately adjust the pressure (temperature) of the compressed refrigerant in the evaporator for each evaporator.

この発明は、上記のような課題を解決するためになされたものであり、この発明の１つの目的は、互いに並列に接続された複数の蒸発器を備える冷却装置において、バイパス流路から蒸発器に流入する冷媒の流量および温度を蒸発器毎に適切に調整することが可能な冷却装置を提供することである。 The present invention has been made to solve the above-described problems, and one object of the present invention is to provide an evaporator from a bypass flow path in a cooling device including a plurality of evaporators connected in parallel to each other. It is an object of the present invention to provide a cooling device capable of appropriately adjusting the flow rate and temperature of the refrigerant flowing into each of the evaporators.

上記目的を達成するために、この発明の一の局面による冷却装置は、冷媒を圧縮する圧縮機と、冷媒を凝縮する凝縮器と、互いに並列に接続され、冷媒を蒸発させる複数の蒸発器と、複数の蒸発器毎に設けられ、凝縮器によって凝縮された冷媒を膨張させる複数の膨張弁と、圧縮機、凝縮器、複数の膨張弁、および、複数の蒸発器を接続する主流路と、圧縮機の吐出側と、複数の蒸発器の各々の冷媒流入側とを接続するバイパス流路と、バイパス流路上に、複数の蒸発器毎に設けられる開き具合の制御が可能な複数の第１弁と、蒸発器の冷媒流出側に、複数の蒸発器毎に設けられる開き具合の制御が可能な複数の第２弁と、複数の蒸発器毎に設けられる複数の第１弁の開き具合を制御するとともに、複数の蒸発器毎に設けられる複数の第２弁の開き具合を制御する制御部とを備える。 In order to achieve the above object, a cooling device according to one aspect of the present invention includes a compressor that compresses a refrigerant, a condenser that condenses the refrigerant, and a plurality of evaporators that are connected in parallel to each other and evaporate the refrigerant. A plurality of expansion valves that are provided for each of the plurality of evaporators and expand the refrigerant condensed by the condenser; a compressor, a condenser, a plurality of expansion valves, and a main flow path that connects the plurality of evaporators; A bypass channel connecting the discharge side of the compressor and the refrigerant inflow side of each of the plurality of evaporators, and a plurality of firsts capable of controlling the degree of opening provided for each of the plurality of evaporators on the bypass channel. On the refrigerant outflow side of the evaporator, a plurality of second valves capable of controlling the degree of opening provided for each of the plurality of evaporators, and a degree of opening of the plurality of first valves provided for each of the plurality of evaporators. A plurality of second valves provided for each of a plurality of evaporators while controlling Open and a control unit for controlling the condition.

この発明の一の局面による冷却装置では、上記のように、複数の蒸発器毎に設けられる複数の第１弁の開き具合を制御するとともに、複数の蒸発器毎に設けられる複数の第２弁の開き具合を制御する制御部を備えることによって、第１弁および第２弁が、それぞれ、複数の蒸発器毎に設けられているので、第１弁の開き具合を調整することによるバイパス流路からの冷媒の圧力（温度）の調整と、第２弁の開き具合を調整することによるバイパス流路からの冷媒の流量の調整とを、蒸発器毎に適切に行うことができる。その結果、互いに並列に接続された複数の蒸発器を備える冷却装置において、バイパス流路から蒸発器に流入する冷媒の流量および温度を蒸発器毎に適切に調整することができる。 In the cooling device according to one aspect of the present invention, as described above, the degree of opening of the plurality of first valves provided for each of the plurality of evaporators is controlled, and the plurality of second valves provided for each of the plurality of evaporators. Since the first valve and the second valve are provided for each of the plurality of evaporators by including a control unit that controls the degree of opening of the first bypass valve, the bypass flow path by adjusting the degree of opening of the first valve The adjustment of the refrigerant pressure (temperature) from the refrigerant and the adjustment of the flow rate of the refrigerant from the bypass flow path by adjusting the opening degree of the second valve can be appropriately performed for each evaporator. As a result, in the cooling device including a plurality of evaporators connected in parallel to each other, the flow rate and temperature of the refrigerant flowing into the evaporator from the bypass channel can be appropriately adjusted for each evaporator.

上記一の局面による冷却装置において、好ましくは、複数の蒸発器の冷媒流出側と、複数の膨張弁の冷媒流入側とをそれぞれ接続する複数の過冷却促進流路をさらに備え、複数の第２弁は、それぞれ、複数の過冷却促進流路上に設けられている。このように構成すれば、蒸発器から流出する比較的温度の低い冷媒が、第２弁を介して、圧縮機から吐出され膨張弁に流入される比較的温度の高い冷媒に混合されるので、膨張弁から蒸発器に流入する冷媒の温度を低下させることができる。すなわち、膨張弁から蒸発器に流入する冷媒の過冷却を促進することができる。 In the cooling device according to the above aspect, it is preferable that the cooling device further includes a plurality of subcooling promotion flow paths respectively connecting the refrigerant outflow sides of the plurality of evaporators and the refrigerant inflow sides of the plurality of expansion valves. Each of the valves is provided on a plurality of supercooling promotion flow paths. If comprised in this way, since the comparatively low temperature refrigerant | coolant which flows out from an evaporator is mixed with the comparatively high temperature refrigerant | coolant discharged from a compressor and flowing in into an expansion valve via a 2nd valve, The temperature of the refrigerant flowing into the evaporator from the expansion valve can be lowered. That is, it is possible to promote supercooling of the refrigerant flowing from the expansion valve into the evaporator.

この場合、好ましくは、複数の蒸発器毎に設けられ、蒸発器の入口近傍の流路の温度を検出する第１流路温度検出部と、複数の蒸発器毎に設けられ、蒸発器の近傍の空気の温度を検出する空気温度検出部とをさらに備え、制御部は、暖房運転時には、第１流路温度検出部によって検出された流路の温度に基づいて、暖房運転をする蒸発器に対応する第１弁の開き具合を制御するとともに、空気温度検出部によって検出された蒸発器の近傍の空気の温度に基づいて、暖房運転をする蒸発器に対応する第２弁の開き具合を制御するように構成されている。このように構成すれば、暖房運転をする蒸発器に流入する冷媒の温度、および、暖房運転をする蒸発器近傍の空気（蒸発器から送風される空気）の温度を、所望の温度に調整することができるので、暖房運転をする蒸発器の暖房能力を適切（適正）に制御することができる。 In this case, it is preferable that the first flow path temperature detection unit that is provided for each of the plurality of evaporators and detects the temperature of the flow path in the vicinity of the evaporator inlet, and the vicinity of the evaporator that is provided for each of the plurality of evaporators. And an air temperature detection unit for detecting the temperature of the air, and the control unit, in the heating operation, is based on the temperature of the flow path detected by the first flow path temperature detection unit in the evaporator that performs the heating operation. The opening degree of the corresponding first valve is controlled, and the opening degree of the second valve corresponding to the evaporator performing the heating operation is controlled based on the temperature of the air in the vicinity of the evaporator detected by the air temperature detection unit. Is configured to do. If comprised in this way, the temperature of the refrigerant | coolant which flows into the evaporator which performs heating operation, and the temperature of the air (air blown from an evaporator) near the evaporator which performs heating operation are adjusted to desired temperature. Therefore, the heating capacity of the evaporator that performs the heating operation can be appropriately controlled.

上記第２弁が過冷却促進流路上に設けられている冷却装置において、好ましくは、暖房運転時には、暖房運転をする蒸発器から流出した冷媒が、過冷却促進流路を介して、冷房運転をする蒸発器に流入されるように構成されている。このように構成すれば、暖房後の蒸発器から流出する比較的温度の低い冷媒が、冷房運転をする蒸発器に流入する比較的温度の高い冷媒に混合されるので、冷房運転をする蒸発器に流入する冷媒の過冷却を促進することができる。その結果、冷房運転の効率を向上させることができる。 In the cooling device in which the second valve is provided on the supercooling promotion flow path, preferably, during the heating operation, the refrigerant flowing out of the evaporator that performs the heating operation performs the cooling operation via the supercooling promotion flow path. It is configured to flow into the evaporator. If comprised in this way, since the comparatively low temperature refrigerant | coolant which flows out from the evaporator after heating is mixed with the comparatively high temperature refrigerant | coolant which flows into the evaporator which carries out air_conditionaing | cooling operation, the evaporator which carries out air_conditionaing | cooling operation It is possible to promote supercooling of the refrigerant flowing into the refrigerant. As a result, the efficiency of the cooling operation can be improved.

上記一の局面による冷却装置において、好ましくは、複数の蒸発器毎に設けられ、蒸発器の出口近傍の流路の温度を検出する第２流路温度検出部をさらに備え、制御部は、除霜運転時には、第２流路温度検出部によって検出された流路の温度に基づいて、除霜運転をする蒸発器に対応する第１弁の開き具合を制御するように構成されている。このように構成すれば、除霜運転をする蒸発器に流入する冷媒の温度が調整されるので、除霜運転を適切に行うことができる。また、除霜運転をする蒸発器から流出する冷媒の温度を調整することができるので、除霜運転をする蒸発器から流出する冷媒の温度が高すぎることに起因する悪影響を抑制することができる。 In the cooling device according to the above aspect, it is preferable that the cooling device further includes a second flow path temperature detection unit that is provided for each of the plurality of evaporators and detects the temperature of the flow path near the outlet of the evaporator. During the frost operation, the opening degree of the first valve corresponding to the evaporator that performs the defrosting operation is controlled based on the temperature of the flow path detected by the second flow path temperature detection unit. If comprised in this way, since the temperature of the refrigerant | coolant which flows in into the evaporator which performs a defrost operation is adjusted, a defrost operation can be performed appropriately. Moreover, since the temperature of the refrigerant flowing out from the evaporator performing the defrosting operation can be adjusted, it is possible to suppress an adverse effect caused by the temperature of the refrigerant flowing out from the evaporator performing the defrosting operation being too high. .

上記一の局面による冷却装置において、好ましくは、主流路に設けられ、冷媒が収容される冷媒タンクと、冷媒タンクの近傍の主流路に設けられ、冷媒タンクの近傍の流路の温度を検出する第３流路温度検出部と、冷媒タンクの近傍の主流路に設けられ、冷媒タンクの近傍の冷媒の圧力を検出する圧力検出部とをさらに備え、制御部は、バイパス流路に冷媒が流れることにより、冷却装置の冷凍回路内の冷媒の密度が変化した場合、第３流路温度検出部によって検出された温度と、圧力検出部によって検出された圧力とに基づいて、冷媒タンクから冷凍回路内に冷媒を放出するか、または、冷凍回路から冷媒タンクに冷媒を回収するように制御するように構成されている。このように構成すれば、バイパス流路に冷媒が流れることにより冷却装置の冷凍回路内の冷媒の密度が変化することに起因して、冷凍回路内の冷媒の圧力が変化した場合でも、冷媒タンクからの冷媒の放出または回収により、冷凍回路内の冷媒の圧力を、適切な圧力に調整（維持）することができる。 In the cooling device according to the above aspect, it is preferable that the temperature of the refrigerant tank provided in the main flow path, the refrigerant tank in which the refrigerant is accommodated, and the main flow path in the vicinity of the refrigerant tank be detected. A third flow path temperature detection section; and a pressure detection section that is provided in the main flow path near the refrigerant tank and detects the pressure of the refrigerant in the vicinity of the refrigerant tank, and the control section flows the refrigerant into the bypass flow path. Thus, when the density of the refrigerant in the refrigeration circuit of the cooling device changes, the refrigeration circuit from the refrigerant tank is based on the temperature detected by the third flow path temperature detection unit and the pressure detected by the pressure detection unit. It is configured to discharge the refrigerant into the inside or to recover the refrigerant from the refrigeration circuit to the refrigerant tank. With this configuration, even when the refrigerant pressure in the refrigeration circuit changes due to the change in the density of the refrigerant in the refrigeration circuit of the cooling device due to the refrigerant flowing in the bypass flow path, the refrigerant tank By releasing or collecting the refrigerant from the refrigerant, the pressure of the refrigerant in the refrigeration circuit can be adjusted (maintained) to an appropriate pressure.

本発明によれば、上記のように、互いに並列に接続された複数の蒸発器を備える冷却装置において、バイパス流路から蒸発器に流入する冷媒の流量および温度を蒸発器毎に適切に調整することができる。 According to the present invention, as described above, in the cooling device including a plurality of evaporators connected in parallel to each other, the flow rate and temperature of the refrigerant flowing into the evaporator from the bypass channel are appropriately adjusted for each evaporator. be able to.

本発明の一実施形態による冷却装置の概略的な構成を示した図である。It is the figure which showed schematic structure of the cooling device by one Embodiment of this invention. 本発明の一実施形態による冷却装置の制御構成を示したブロック図である。It is the block diagram which showed the control structure of the cooling device by one Embodiment of this invention. 冷却装置の通常運転時の動作を説明するための図である。It is a figure for demonstrating the operation | movement at the time of the normal driving | operation of a cooling device. 冷却装置の冷房および暖房の併用時の動作を説明するための図である。It is a figure for demonstrating the operation | movement at the time of combined use of air_conditioning | cooling of a cooling device and heating. 冷却装置の冷房、暖房および除霜の併用時の動作を説明するための図である。It is a figure for demonstrating the operation | movement at the time of combined use of air_conditioning | cooling of a cooling device, heating, and a defrost. 冷却装置の圧力調整時の動作を説明するための図である。It is a figure for demonstrating the operation | movement at the time of pressure adjustment of a cooling device.

以下、本発明を具体化した実施形態を図面に基づいて説明する。 DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments embodying the present invention will be described below with reference to the drawings.

図１を参照して、本実施形態による冷却装置１００の構成について説明する。 With reference to FIG. 1, the structure of the cooling device 100 by this embodiment is demonstrated.

（冷却装置の構成）
本実施形態による冷却装置１００は、図１に示すように、ＣＯ_２冷媒を用いて所定の冷凍サイクルを形成可能に構成されている。具体的には、冷却装置１００は、冷媒を圧縮する圧縮機１０、冷媒を凝縮する凝縮器２０、互いに並列に接続され、冷媒を蒸発させる蒸発器３０ａ〜３０ｃとを備えている。また、冷却装置１００は、複数の蒸発器３０ａ〜３０ｃ毎に設けられ、凝縮器２０によって凝縮された冷媒を膨張させる複数の膨張弁４０ａ〜４０ｃを備えている。また、冷却装置１００は、圧縮機１０、凝縮器２０、複数の膨張弁４０ａ〜４０ｃ、および、複数の蒸発器３０ａ〜３０ｃを接続する主流路１（主に吐出管２、液管３、冷媒配管４ａ〜４ｃ、吸入管（ガス管）５）を備えている。また、蒸発器３０ａ〜３０ｃは、それぞれ、冷蔵室Ａ〜Ｃに配置されている。 (Configuration of cooling device)
As shown in FIG. 1, the cooling device 100 according to the present embodiment is configured to be able to form a predetermined refrigeration cycle using a CO ₂ refrigerant. Specifically, the cooling device 100 includes a compressor 10 that compresses a refrigerant, a condenser 20 that condenses the refrigerant, and evaporators 30a to 30c that are connected in parallel to evaporate the refrigerant. In addition, the cooling device 100 includes a plurality of expansion valves 40 a to 40 c that are provided for each of the plurality of evaporators 30 a to 30 c and expand the refrigerant condensed by the condenser 20. The cooling device 100 includes a compressor 10, a condenser 20, a plurality of expansion valves 40a to 40c, and a main flow path 1 (mainly a discharge pipe 2, a liquid pipe 3, and a refrigerant) connecting the plurality of evaporators 30a to 30c. Pipes 4a to 4c and a suction pipe (gas pipe) 5) are provided. Moreover, the evaporators 30a-30c are each arrange | positioned at refrigerator compartment AC.

また、蒸発器３０ａ〜３０ｃは、１つの冷凍サイクル（冷却装置１００を構成する冷媒回路）の低圧側に互いに並列接続されている。すなわち、高圧側となる液管３は、液管３ａ〜３ｃの３系統に分岐されている。液管３ａには、膨張弁４０ａと蒸発器３０ａとが直列接続され、液管３ｂには、膨張弁４０ｂと蒸発器３０ｂとが直列接続されている。また、液管３ｃには、膨張弁４０ｃと蒸発器３０ｃとが直列接続されている。そして、低圧側となる蒸発器３０ａ〜３０ｃの各々の下流側に接続された冷媒配管４ａ〜４ｃは、１つに合流して吸入管５となり、吸入管５が圧縮機１０に接続されている。 Further, the evaporators 30a to 30c are connected in parallel to each other on the low pressure side of one refrigeration cycle (a refrigerant circuit constituting the cooling device 100). That is, the liquid pipe 3 on the high pressure side is branched into three systems of liquid pipes 3a to 3c. An expansion valve 40a and an evaporator 30a are connected in series to the liquid pipe 3a, and an expansion valve 40b and an evaporator 30b are connected in series to the liquid pipe 3b. An expansion valve 40c and an evaporator 30c are connected in series to the liquid pipe 3c. And the refrigerant | coolant piping 4a-4c connected to each downstream of the evaporators 30a-30c used as a low voltage | pressure side merges, and becomes the suction pipe 5, and the suction pipe 5 is connected to the compressor 10. FIG. .

（冷却装置を構成する各機能部品）
冷却装置１００を構成する各機能部品について簡潔に説明する。圧縮機１０は、吸入されたガス冷媒を圧縮して高圧側（吐出管２）に吐出する役割を有する。また、圧縮機１０には、回転数制御に基づき冷媒吐出量が制御可能なインバータ制御式圧縮機が用いられる。凝縮器２０は、内部を流通する過熱ガス状態の冷媒を送風機（図示せず）により送風される外気（空気）を用いて冷却する機能を有する。また、凝縮器２０内で凝縮（液化）された冷媒は、液管３ａ〜３ｃを流通して、膨張弁４０ａ〜４０ｃに流入される。その後、蒸発器３０ａ〜３０ｃに流入する。なお、以下では、液管３ａ、膨張弁４０ａ、および、蒸発器３０ａについて説明する。 (Functional parts that make up the cooling system)
Each functional component constituting the cooling device 100 will be briefly described. The compressor 10 has a role of compressing the sucked gas refrigerant and discharging it to the high-pressure side (discharge pipe 2). The compressor 10 is an inverter-controlled compressor that can control the refrigerant discharge amount based on the rotational speed control. The condenser 20 has a function of cooling the refrigerant in the superheated gas state circulating inside using outside air (air) blown by a blower (not shown). The refrigerant condensed (liquefied) in the condenser 20 flows through the liquid pipes 3a to 3c and flows into the expansion valves 40a to 40c. Then, it flows into the evaporators 30a-30c. Hereinafter, the liquid pipe 3a, the expansion valve 40a, and the evaporator 30a will be described.

膨張弁４０ａは、凝縮器２０で冷却（液化）された冷媒を絞り膨張させて蒸発器３０ａに供給する役割を有する。また、膨張弁４０ａは、パルス制御により駆動されるステッピングモータの駆動力を利用して弁機構を開閉駆動する。また、膨張弁４０ａの開度または開閉のデューティ（開閉時間の割合）に応じて蒸発器３０ａに流入する冷媒流量が制御される。また、膨張弁４０ａにより絞り膨張された液冷媒は、気液二相状態のまま液管３ａを介して蒸発器３０ａに流入される。 The expansion valve 40a has a role of expanding the refrigerant cooled (liquefied) by the condenser 20 and supplying it to the evaporator 30a. The expansion valve 40a opens and closes the valve mechanism using the driving force of a stepping motor driven by pulse control. Further, the flow rate of the refrigerant flowing into the evaporator 30a is controlled according to the opening degree of the expansion valve 40a or the duty of opening / closing (ratio of opening / closing time). Further, the liquid refrigerant expanded and contracted by the expansion valve 40a flows into the evaporator 30a through the liquid pipe 3a while being in a gas-liquid two-phase state.

蒸発器３０ａは、膨張弁４０ａから供給された気液二相冷媒を蒸発させる機能を有する。冷媒は、蒸発器３０ａを流通する際に蒸発潜熱を得ながら蒸発し、この際、冷蔵室Ａを流通する空気から熱が奪われる。詳細な図示は省略するが、蒸発器３０ａは、伝熱管内部を冷媒が流通するフィンアンドチューブ型の空気熱交換器である。すなわち、蒸発器３０ａは、一対の端板（エンドプレート）間を往復蛇行する伝熱管群と、並行配置された伝熱管群の外周壁に固定されるとともに等ピッチ間隔に配置された複数のフィン部材とを備えている。また、蒸発器３０ａにおける蒸発後の冷媒は、気相を多く含んだガス状態となって冷媒配管４ａおよび吸入管５の順に流通されて圧縮機１０に戻される。 The evaporator 30a has a function of evaporating the gas-liquid two-phase refrigerant supplied from the expansion valve 40a. The refrigerant evaporates while obtaining latent heat of vaporization when flowing through the evaporator 30a, and at this time, heat is taken away from the air flowing through the refrigerator compartment A. Although detailed illustration is omitted, the evaporator 30a is a fin-and-tube type air heat exchanger in which a refrigerant flows through the heat transfer tube. That is, the evaporator 30a includes a plurality of fins that are fixed to the outer peripheral wall of the heat transfer tube group that reciprocates between a pair of end plates (end plates) and the heat transfer tube groups that are arranged in parallel and are arranged at equal pitch intervals. And a member. In addition, the refrigerant after evaporation in the evaporator 30 a becomes a gas state containing a large amount of gas phase, and is circulated in the order of the refrigerant pipe 4 a and the suction pipe 5 and returned to the compressor 10.

また、蒸発器３０ａ〜３０ｃの冷媒流出側（下流側）の冷媒配管４ａ〜４ｃに電磁弁５１ａ〜５１ｃが設けている。また、電磁弁５１ａ〜５１ｃは、蒸発器３０ａ〜３０ｃと圧縮機１０との間に配置されている。電磁弁５１ａ〜５１ｃは、パルス制御により駆動されるステッピングモータの駆動力を利用して弁機構を開閉駆動する。また、電磁弁５１ａ〜５１ｃの開き具合（開度または開閉のデューティ）に応じて蒸発器３０ａ〜３０ｃから流出する冷媒流量が制御されるように構成されている。 In addition, solenoid valves 51a to 51c are provided in the refrigerant pipes 4a to 4c on the refrigerant outflow side (downstream side) of the evaporators 30a to 30c. The electromagnetic valves 51 a to 51 c are disposed between the evaporators 30 a to 30 c and the compressor 10. The electromagnetic valves 51a to 51c open and close the valve mechanism using the driving force of the stepping motor driven by pulse control. Further, the flow rate of the refrigerant flowing out of the evaporators 30a to 30c is controlled in accordance with the degree of opening (opening or opening / closing duty) of the electromagnetic valves 51a to 51c.

ここで、本実施形態では、冷却装置１００は、圧縮機１０の吐出側と、複数の蒸発器３０ａ〜３０ｃの各々の冷媒流入側とを接続するホットガスバイパス流路６を備えている。また、ホットガスバイパス流路６上には、複数の蒸発器３０ａ〜３０ｃ毎に設けられる開き具合（開度または開閉のデューティ）の制御が可能な複数の電磁弁５２ａ〜５２ｃが設けられている。具体的には、ホットガスバイパス流路６は、圧縮機１０の吐出側の主流路１の吐出管２から分岐するとともに、電磁弁５２ａ〜５２ｃの冷媒流入側で３つに分岐している。そして、３つに分岐したホットガスバイパス流路６は、電磁弁５２ａ〜５２ｃを介して、蒸発器３０ａ〜３０ｃに接続されている。なお、ホットガスバイパス流路６は、特許請求の範囲の「バイパス流路」の一例である。また、電磁弁５２ａ〜５２ｃは、特許請求の範囲の「第１弁」の一例である。 Here, in the present embodiment, the cooling device 100 includes the hot gas bypass channel 6 that connects the discharge side of the compressor 10 and the refrigerant inflow side of each of the plurality of evaporators 30a to 30c. In addition, on the hot gas bypass flow path 6, a plurality of electromagnetic valves 52 a to 52 c capable of controlling the degree of opening (opening or opening / closing duty) provided for each of the plurality of evaporators 30 a to 30 c are provided. . Specifically, the hot gas bypass flow path 6 branches from the discharge pipe 2 of the main flow path 1 on the discharge side of the compressor 10 and branches into three on the refrigerant inflow side of the electromagnetic valves 52a to 52c. And the hot gas bypass flow path 6 branched into three is connected to the evaporators 30a-30c via the solenoid valves 52a-52c. The hot gas bypass channel 6 is an example of the “bypass channel” in the claims. The solenoid valves 52a to 52c are examples of the “first valve” in the claims.

また、本実施形態では、蒸発器３０ａ〜３０ｃの冷媒流出側に、それぞれ、複数の蒸発器３０ａ〜３０ｃ毎に設けられる開き具合の制御が可能な複数の電磁弁５３ａ〜５３ｃが設けられている。具体的には、冷却装置１００には、複数の蒸発器３０ａ〜３０ｃの冷媒流出側と、膨張弁４０ａ〜４０ｃの冷媒流入側とを、それぞれ接続する複数の過冷却促進流路７ａ〜７ｃが設けられている。そして、複数の電磁弁５３ａ〜５３ｃは、それぞれ、過冷却促進流路７ａ〜７ｃ上に設けられている。なお、電磁弁５３ａ〜５３ｃは、特許請求の範囲の「第２弁」の一例である。 Moreover, in this embodiment, the several solenoid valves 53a-53c which can control the opening condition provided for every several evaporator 30a-30c are provided in the refrigerant | coolant outflow side of the evaporators 30a-30c, respectively. . Specifically, the cooling device 100 includes a plurality of supercooling promotion channels 7a to 7c that connect the refrigerant outflow sides of the plurality of evaporators 30a to 30c and the refrigerant inflow sides of the expansion valves 40a to 40c, respectively. Is provided. The plurality of solenoid valves 53a to 53c are provided on the supercooling promotion flow paths 7a to 7c, respectively. The solenoid valves 53a to 53c are examples of the “second valve” in the claims.

また、本実施形態では、図２に示すように、冷却装置１００は、複数の蒸発器３０ａ〜３０ｃ毎に設けられる複数の電磁弁５２ａ〜５２ｃの開き具合（開度または開閉のデューティ）を制御するとともに、複数の蒸発器３０ａ〜３０ｃ毎に設けられる複数の電磁弁５３ａ〜５３ｃの開き具合を制御する制御部６１を備えている。また、制御部６１は、膨張弁４０ａ〜４０ｃの開き具合の調整、電磁弁５１ａ〜５１ｃの開き具合の調整、および、後述する冷媒タンク８１からの冷媒の放出および冷媒タンク８１への冷媒の回収を制御するように構成されている。また、制御部６１には、ＲＯＭ６２と、ＲＡＭ６３とが接続されている。 In this embodiment, as shown in FIG. 2, the cooling device 100 controls the degree of opening (opening or opening / closing duty) of the plurality of electromagnetic valves 52a to 52c provided for each of the plurality of evaporators 30a to 30c. In addition, a control unit 61 that controls the degree of opening of the plurality of electromagnetic valves 53a to 53c provided for each of the plurality of evaporators 30a to 30c is provided. Further, the control unit 61 adjusts the degree of opening of the expansion valves 40a to 40c, adjusts the degree of opening of the electromagnetic valves 51a to 51c, and discharges the refrigerant from the refrigerant tank 81 and collects the refrigerant into the refrigerant tank 81, which will be described later. Is configured to control. In addition, a ROM 62 and a RAM 63 are connected to the control unit 61.

また、図１に示すように、複数の蒸発器３０ａ〜３０ｃ毎に、蒸発器３０ａ〜３０ｃの入口近傍の流路（配管、冷媒）の温度を検出する流路温度センサ７１ａ〜７１ｃが設けられている。また、複数の蒸発器３０ａ〜３０ｃ毎に、蒸発器３０ａ〜３０ｃの近傍の空気の温度を検出する空気温度センサ７２ａ〜７２ｃが設けられている。また、複数の蒸発器３０ａ〜３０ｃ毎に、蒸発器３０ａ〜３０ｃの出口近傍の流路の温度を検出する流路温度センサ７３ａ〜７３ｃが設けられている。なお、流路温度センサ７１ａ〜７１ｃは、特許請求の範囲の「第１流路温度検出部」の一例である。また、空気温度センサ７２ａ〜７２ｃは、特許請求の範囲の「空気温度検出部」の一例である。また、流路温度センサ７３ａ〜７３ｃは、特許請求の範囲の「第２流路温度検出部」の一例である。 Moreover, as shown in FIG. 1, the flow path temperature sensors 71a-71c which detect the temperature of the flow path (pipe, refrigerant | coolant) near the inlet_port | entrance of evaporator 30a-30c are provided for every some evaporator 30a-30c. ing. In addition, air temperature sensors 72a to 72c that detect the temperature of air near the evaporators 30a to 30c are provided for each of the plurality of evaporators 30a to 30c. Moreover, the flow path temperature sensors 73a-73c which detect the temperature of the flow path in the vicinity of the exit of the evaporators 30a-30c are provided for each of the plurality of evaporators 30a-30c. The flow path temperature sensors 71a to 71c are examples of the “first flow path temperature detection unit” in the claims. Air temperature sensors 72a-72c are examples of an "air temperature detection part" of a claim. The flow path temperature sensors 73a to 73c are examples of the “second flow path temperature detection unit” in the claims.

また、主流路１には、冷媒が収容される冷媒タンク８１が設けられている。具体的には、冷媒タンク８１は、凝縮器２０の冷媒流出側と、膨張弁４０ａ〜４０ｃとの間の主流路１の液管３に設けられている（接続されている）。また、冷媒タンク８１の近傍の主流路１の液管３（冷媒タンク８１の下流側）には、冷媒タンク８１の近傍の流路の温度を検出する流路温度センサ８２が設けられている。また、冷媒タンク８１の近傍の主流路１の液管３（凝縮器２０の下流側）には、冷媒タンク８１の近傍の冷媒の圧力を検出する圧力センサ８３が設けられている。なお、流路温度センサ８２は、特許請求の範囲の「第３流路温度検出部」の一例である。また、圧力センサ８３は、特許請求の範囲の「圧力検出部」の一例である。 The main channel 1 is provided with a refrigerant tank 81 in which a refrigerant is accommodated. Specifically, the refrigerant tank 81 is provided (connected) to the liquid pipe 3 of the main flow path 1 between the refrigerant outflow side of the condenser 20 and the expansion valves 40a to 40c. A flow path temperature sensor 82 that detects the temperature of the flow path in the vicinity of the refrigerant tank 81 is provided in the liquid pipe 3 of the main flow path 1 in the vicinity of the refrigerant tank 81 (on the downstream side of the refrigerant tank 81). Further, a pressure sensor 83 that detects the pressure of the refrigerant in the vicinity of the refrigerant tank 81 is provided in the liquid pipe 3 of the main channel 1 in the vicinity of the refrigerant tank 81 (on the downstream side of the condenser 20). The flow path temperature sensor 82 is an example of the “third flow path temperature detection unit” in the claims. The pressure sensor 83 is an example of the “pressure detection unit” in the claims.

（動作説明）
次に、図３〜図６を参照して、冷却装置１００の通常運転時（冷房運転時）と、冷房および暖房の併用時と、冷房、暖房および除霜の併用時と、圧力調整時との動作について説明する。 (Description of operation)
Next, referring to FIG. 3 to FIG. 6, during normal operation (cooling operation) of cooling device 100, combined use of cooling and heating, combined use of cooling, heating and defrosting, and pressure adjustment Will be described.

〈通常運転時（冷房運転時）〉
図３に示すように、通常運転時では、膨張弁４０ａ〜４０ｃ、および、蒸発器３０ａ〜３０ｃの冷媒流出側の電磁弁５１ａ〜５１ｃが、開状態にされる。なお、電磁弁５１ａ〜５１ｃの開き具合（開度、開閉デューティ）は、制御部６１により調整される。また、ホットガスバイパス流路６上の電磁弁５２ａ〜５２ｃ、および、過冷却促進流路７ａ〜７ｃ上の電磁弁５３ａ〜５３ｃは、閉状態にされる。すなわち、ホットガスバイパス流路６、および、過冷却促進流路７ａ〜７ｃには、冷媒は流れない。これにより、図３の太線で表される流路（冷媒の流れ）に示すように、圧縮機１０から吐出された冷媒（たとえば、６０℃）が、凝縮器２０を介することにより、圧力が３ＭＰａになるとともに、温度が３０℃になり、液管３ａ〜３ｃを介して、膨張弁４０ａ〜４０ｃに流入する。また、冷媒は、膨張弁４０ａ〜４０ｃを流出した後、温度が−４０℃になり、蒸発器３０ａ〜３０ｃに流入する。これにより、冷蔵室Ａ〜Ｃが冷房される。そして、冷媒は、蒸発器３０ａ〜３０ｃを流出した後、電磁弁５１ａ〜５１ｃを介して、再び圧縮機１０に帰還される。 <During normal operation (cooling operation)>
As shown in FIG. 3, during normal operation, the expansion valves 40a to 40c and the solenoid valves 51a to 51c on the refrigerant outflow side of the evaporators 30a to 30c are opened. The opening degree (opening and opening / closing duty) of the electromagnetic valves 51 a to 51 c is adjusted by the control unit 61. Further, the electromagnetic valves 52a to 52c on the hot gas bypass flow path 6 and the electromagnetic valves 53a to 53c on the supercooling promotion flow paths 7a to 7c are closed. That is, the refrigerant does not flow through the hot gas bypass channel 6 and the supercooling promotion channels 7a to 7c. Thereby, as shown in the flow path (refrigerant flow) represented by the thick line in FIG. 3, the refrigerant discharged from the compressor 10 (for example, 60 ° C.) passes through the condenser 20, and thus the pressure becomes 3 MPa. At the same time, the temperature becomes 30 ° C. and flows into the expansion valves 40a to 40c via the liquid pipes 3a to 3c. In addition, after the refrigerant flows out of the expansion valves 40a to 40c, the temperature becomes −40 ° C. and flows into the evaporators 30a to 30c. Thereby, the refrigerator compartments A to C are cooled. Then, after the refrigerant flows out of the evaporators 30a to 30c, the refrigerant is returned to the compressor 10 again through the electromagnetic valves 51a to 51c.

〈冷房および暖房の併用時〉
図４を参照して、冷房および暖房の併用時の運転について説明する。ここでは、蒸発器３０ａにより、暖房運転が行われ、蒸発器３０ｂおよび３０ｃにより、冷房運転が行われるとする。 <When combined with cooling and heating>
With reference to FIG. 4, the operation | movement at the time of combined use of air_conditioning | cooling and heating is demonstrated. Here, it is assumed that the heating operation is performed by the evaporator 30a and the cooling operation is performed by the evaporators 30b and 30c.

冷房および暖房の併用時では、膨張弁４０ｂおよび４０ｃ、ホットガスバイパス流路６上の電磁弁５２ａ、および、過冷却促進流路７ａ上の電磁弁５３ａ、および、蒸発器３０ｂおよび３０ｃの冷媒流出側の電磁弁５１ｂおよび５１ｃが、開状態にされる。また、膨張弁４０ａ、ホットガスバイパス流路６上の電磁弁５２ｂおよび５２ｃ、過冷却促進流路７ｂおよび７ｃ上の電磁弁５３ｂおよび５３ｃ、および、蒸発器３０ａの冷媒流出側の電磁弁５１ａは、閉状態にされる。 At the time of combined use of cooling and heating, the refrigerant flows out of the expansion valves 40b and 40c, the electromagnetic valve 52a on the hot gas bypass channel 6, the electromagnetic valve 53a on the supercooling promotion channel 7a, and the evaporators 30b and 30c. The electromagnetic valves 51b and 51c on the side are opened. The expansion valve 40a, the electromagnetic valves 52b and 52c on the hot gas bypass flow path 6, the electromagnetic valves 53b and 53c on the supercooling promotion flow paths 7b and 7c, and the electromagnetic valve 51a on the refrigerant outflow side of the evaporator 30a are And closed.

これにより、ホットガスバイパス流路６から暖房運転をする蒸発器３０ａに冷媒が流れるとともに、蒸発器３０ａから流出した冷媒が、過冷却促進流路７ａに流入する。なお、蒸発器３０ｂおよび３０ｃには、上記した通常運転時と同様に、圧縮機１０から吐出した冷媒が、凝縮器２０と、膨張弁４０ｂおよび４０ｃとを介して流入する。また、蒸発器３０ｂおよび３０ｃから流出した冷媒は、電磁弁５１ｂおよび５１ｃを介して、再び圧縮機１０に帰還される。 Thereby, while a refrigerant | coolant flows into the evaporator 30a which performs heating operation from the hot gas bypass flow path 6, the refrigerant | coolant which flowed out from the evaporator 30a flows in into the supercooling promotion flow path 7a. Note that the refrigerant discharged from the compressor 10 flows into the evaporators 30b and 30c through the condenser 20 and the expansion valves 40b and 40c, as in the normal operation described above. In addition, the refrigerant that has flowed out of the evaporators 30b and 30c is returned to the compressor 10 again through the electromagnetic valves 51b and 51c.

ここで、本実施形態では、制御部６１は、暖房運転時には、流路温度センサ７１ａによって検出された流路の温度に基づいて、暖房運転をする蒸発器３０ａに対応する電磁弁５２ａの開き具合を制御するとともに、空気温度センサ７２ａによって検出された蒸発器３０ａの近傍の空気の温度に基づいて、暖房運転をする蒸発器３０ａに対応する電磁弁５３ａの開き具合を制御する。具体的には、圧縮機１０から吐出された冷媒（６０℃）を直接蒸発器３０ａに流入させると、蒸発器３０ａの暖房能力が過大になるので、蒸発器３０ａに流入する冷媒の温度が所望の冷媒温度（たとえば、３０℃）になるように、流路温度センサ７１ａによって検出された流路（冷媒）の温度に基づいて、電磁弁５２ａの開き具合が制御される。また、蒸発器３０ａに流入する冷媒の流量が所望の冷媒流量になるように、空気温度センサ７２ａによって検出された空気の温度に基づいて、電磁弁５３ａの開き具合が制御される。また、過冷却促進流路７ａ上の電磁弁５３ａを流出した冷媒は、温度がたとえば０℃になる。 Here, in the present embodiment, during the heating operation, the controller 61 opens the electromagnetic valve 52a corresponding to the evaporator 30a that performs the heating operation based on the temperature of the flow path detected by the flow path temperature sensor 71a. And the degree of opening of the electromagnetic valve 53a corresponding to the evaporator 30a performing the heating operation is controlled based on the temperature of the air in the vicinity of the evaporator 30a detected by the air temperature sensor 72a. Specifically, when the refrigerant (60 ° C.) discharged from the compressor 10 is directly flowed into the evaporator 30a, the heating capacity of the evaporator 30a becomes excessive, so the temperature of the refrigerant flowing into the evaporator 30a is desired. The degree of opening of the solenoid valve 52a is controlled based on the temperature of the flow path (refrigerant) detected by the flow path temperature sensor 71a so that the refrigerant temperature becomes 30 ° C. (for example, 30 ° C.). Further, the degree of opening of the electromagnetic valve 53a is controlled based on the temperature of the air detected by the air temperature sensor 72a so that the flow rate of the refrigerant flowing into the evaporator 30a becomes a desired refrigerant flow rate. In addition, the temperature of the refrigerant that has flowed out of the electromagnetic valve 53a on the supercooling promotion flow path 7a becomes, for example, 0 ° C.

また、本実施形態では、暖房運転時には、暖房運転をする蒸発器３０ａから流出した冷媒が、過冷却促進流路７ａを介して、冷房運転をする蒸発器３０ｂおよび３０ｃに流入される。すなわち、凝縮器２０を介して蒸発器３０ｂおよび３０ｃに流入する冷媒（３０℃）と、過冷却促進流路７ａを介して膨張弁４０ｂおよび４０ｃ（蒸発器３０ｂおよび３０ｃ）に流入する冷媒（０℃）とが混合される。その結果、膨張弁４０ｂおよび４０ｃに流入する冷媒の温度は、通常運転時（図３参照）の温度（３０℃）よりも、小さく（たとえば、２５℃）なる。すなわち、冷媒の過冷却が促進される。その後、冷媒は、膨張弁４０ｂおよび４０ｃ、蒸発器３０ｂおよび３０ｃ、電磁弁５１ｂおよび５１ｃを介して、再び圧縮機１０に帰還される。 In the present embodiment, during the heating operation, the refrigerant that has flowed out of the evaporator 30a that performs the heating operation flows into the evaporators 30b and 30c that perform the cooling operation via the supercooling promotion flow path 7a. That is, the refrigerant (30 ° C.) that flows into the evaporators 30b and 30c via the condenser 20 and the refrigerant (0 that flows into the expansion valves 40b and 40c (evaporators 30b and 30c) via the supercooling promotion flow path 7a). ° C). As a result, the temperature of the refrigerant flowing into the expansion valves 40b and 40c becomes smaller (for example, 25 ° C.) than the temperature (30 ° C.) during normal operation (see FIG. 3). That is, the supercooling of the refrigerant is promoted. Thereafter, the refrigerant is returned to the compressor 10 again via the expansion valves 40b and 40c, the evaporators 30b and 30c, and the electromagnetic valves 51b and 51c.

なお、主流路１に加えて、ホットガスバイパス流路６に冷媒が流れることにより、冷却装置１００の冷凍回路内の冷媒の密度が変化する（小さくなる）。これにより、凝縮器２０の冷媒流出側では、冷媒の圧力が、通常運転時の３ＭＰａから２．５ＭＰａに低下する。 In addition, when the refrigerant flows in the hot gas bypass flow path 6 in addition to the main flow path 1, the density of the refrigerant in the refrigeration circuit of the cooling device 100 changes (decreases). Thereby, on the refrigerant | coolant outflow side of the condenser 20, the pressure of a refrigerant | coolant falls from 3 MPa at the time of normal operation to 2.5 MPa.

〈冷房、暖房および除霜の併用時〉
図５を参照して、冷房、暖房および除霜の併用時の運転について説明する。ここでは、蒸発器３０ａにより、暖房運転が行われ、蒸発器３０ｂにより、冷房運転が行われ、蒸発器３０ｃにより、除霜運転が行われるとする。 <When combined with cooling, heating and defrosting>
With reference to FIG. 5, the operation | movement at the time of combined use of air_conditioning | cooling, heating, and a defrost is demonstrated. Here, it is assumed that the heating operation is performed by the evaporator 30a, the cooling operation is performed by the evaporator 30b, and the defrosting operation is performed by the evaporator 30c.

冷房、暖房および除霜の併用時では、膨張弁４０ｂ、ホットガスバイパス流路６上の電磁弁５２ａおよび５２ｃ、過冷却促進流路７ａおよび７ｃ上の電磁弁５３ａおよび５３ｃ、蒸発器３０ｂの冷媒流出側の電磁弁５１ｂが、開状態にされる。また、膨張弁４０ａおよび４０ｃ、ホットガスバイパス流路６上の電磁弁５２ｂ、過冷却促進流路７ｂ上の電磁弁５３ｂ、蒸発器３０ａおよび３０ｃの冷媒流出側の電磁弁５１ａおよび５１ｃは、閉状態にされる。 In the combined use of cooling, heating and defrosting, the expansion valve 40b, the electromagnetic valves 52a and 52c on the hot gas bypass channel 6, the electromagnetic valves 53a and 53c on the supercooling promotion channels 7a and 7c, and the refrigerant of the evaporator 30b The electromagnetic valve 51b on the outflow side is opened. The expansion valves 40a and 40c, the electromagnetic valve 52b on the hot gas bypass flow path 6, the electromagnetic valve 53b on the supercooling promotion flow path 7b, and the electromagnetic valves 51a and 51c on the refrigerant outflow side of the evaporators 30a and 30c are closed. Put into state.

すなわち、ホットガスバイパス流路６から暖房運転をする蒸発器３０ａ、および、除霜運転をする蒸発器３０ｃに冷媒が流れる。また、蒸発器３０ａおよび３０ｃから流出した冷媒が、それぞれ、過冷却促進流路７ａおよび７ｃに流入する。 That is, the refrigerant flows from the hot gas bypass passage 6 to the evaporator 30a that performs the heating operation and the evaporator 30c that performs the defrosting operation. Moreover, the refrigerant | coolant which flowed out from the evaporators 30a and 30c flows in into the supercooling promotion flow path 7a and 7c, respectively.

ここで、本実施形態では、制御部６１は、除霜運転時には、流路温度センサ７３ｃによって検出された流路の温度に基づいて、除霜運転をする蒸発器３０ｃに対応する電磁弁５２ｃの開き具合を制御する。具体的には、圧縮機１０から吐出された冷媒（６０℃）が、ホットガスバイパス流路６上の電磁弁５２ｃを介して、蒸発器３０ｃに流入する。これにより、除霜が行われる。ここで、比較的温度が高いとともに流量が大きい冷媒を、過冷却促進流路７ｃを介して蒸発器３０ｂに流入させると、蒸発器３０ｂによる冷房効率が低下する。そこで、制御部６１は、除霜運転時には、流路温度センサ７３ｃによって検出された流路の温度に基づいて、除霜運転をする蒸発器３０ｃに対応する電磁弁５２ｃの開き具合を制御することによって、蒸発器３０ｃから流出する冷媒の温度を調整（たとえば、０℃）する。 Here, in the present embodiment, during the defrosting operation, the control unit 61 sets the solenoid valve 52c corresponding to the evaporator 30c that performs the defrosting operation based on the temperature of the flow path detected by the flow path temperature sensor 73c. Controls the degree of opening. Specifically, the refrigerant (60 ° C.) discharged from the compressor 10 flows into the evaporator 30 c via the electromagnetic valve 52 c on the hot gas bypass channel 6. Thereby, defrosting is performed. Here, if a refrigerant having a relatively high temperature and a large flow rate is caused to flow into the evaporator 30b via the supercooling promotion flow path 7c, the cooling efficiency by the evaporator 30b is reduced. Therefore, during the defrosting operation, the control unit 61 controls the opening degree of the electromagnetic valve 52c corresponding to the evaporator 30c performing the defrosting operation based on the temperature of the flow channel detected by the flow channel temperature sensor 73c. To adjust the temperature of the refrigerant flowing out of the evaporator 30c (for example, 0 ° C.).

また、蒸発器３０ａについては、上記冷房および暖房の併用時の運転と同様に、暖房運転が行われている。そして、除霜運転している蒸発器３０ｃから流出した温度が調整（０℃）された冷媒と、暖房運転している蒸発器３０ａから流出した温度が調整（０℃）された冷媒とが、膨張弁４０ｂ（冷房運転する蒸発器３０ｂ）に流入する冷媒と混合される。これにより、膨張弁４０ｂに流入する冷媒の温度は、たとえば２０℃になる。すなわち、膨張弁４０ｂに流入する冷媒の温度は、上記冷房および暖房の併用時の運転における膨張弁４０ｂに流入する冷媒の温度（２５℃）よりも、さらに低くなる。つまり、冷媒の過冷却がさらに促進される。その後、冷媒は、膨張弁４０ｂ、蒸発器３０ｂ、および、電磁弁５１ｂを介して、再び圧縮機１０に帰還される。 Moreover, about the evaporator 30a, the heating operation is performed similarly to the driving | operation at the time of combined use of the said cooling and heating. And the refrigerant | coolant by which the temperature which flowed out from the evaporator 30c which is defrosting-operated was adjusted (0 degreeC), and the refrigerant | coolant by which the temperature which flowed out from the evaporator 30a which is heating-operation was adjusted (0 degreeC), The refrigerant is mixed with the refrigerant flowing into the expansion valve 40b (evaporator 30b for cooling operation). Thereby, the temperature of the refrigerant | coolant which flows in into the expansion valve 40b will be 20 degreeC, for example. That is, the temperature of the refrigerant flowing into the expansion valve 40b is further lower than the temperature (25 ° C.) of the refrigerant flowing into the expansion valve 40b in the operation when the cooling and heating are combined. That is, the supercooling of the refrigerant is further promoted. Thereafter, the refrigerant is returned to the compressor 10 again via the expansion valve 40b, the evaporator 30b, and the electromagnetic valve 51b.

なお、主流路１に加えて、ホットガスバイパス流路６（蒸発器４０ａと４０ｂとへの２つの流路）に冷媒が流れることにより、冷却装置１００の冷凍回路内の冷媒の密度が変化する（小さくなる）。これにより、凝縮器２０の冷媒流出側では、冷媒の圧力が、上記冷房および暖房の併用時の２．５ＭＰａから２ＭＰａに低下する。 In addition to the main flow path 1, the refrigerant flows in the hot gas bypass flow path 6 (two flow paths to the evaporators 40 a and 40 b), thereby changing the density of the refrigerant in the refrigeration circuit of the cooling device 100. (Smaller). Thereby, on the refrigerant | coolant outflow side of the condenser 20, the pressure of a refrigerant | coolant falls from 2.5 MPa at the time of combined use of the said cooling and heating to 2 MPa.

〈圧力調整時〉
図６を参照して、圧力調整時の運転について説明する。 <Pressure adjustment>
With reference to FIG. 6, the operation at the time of pressure adjustment will be described.

上記冷房、暖房および除霜の併用時（図５参照）では、ホットガスバイパス流路６に冷媒が流れることにより、冷媒の圧力が低下（２ＭＰａ）する。そこで、本実施形態では、制御部６１は、ホットガスバイパス流路６に冷媒が流れることにより、冷却装置１００の冷凍回路内の冷媒の密度が変化した場合、流路温度センサ８２によって検出された温度と、圧力センサ８３によって検出された圧力とに基づいて、冷媒タンク８１から冷凍回路内に冷媒を放出するか、または、冷凍回路から冷媒タンク８１に冷媒を回収する。たとえば、冷媒の圧力が低下している場合には、冷媒タンク８１から冷凍回路内に冷媒を放出することにより、冷凍回路内の冷媒の密度が大きくなる。その結果、冷媒の圧力が適切な圧力（たとえば、２．５ＭＰａ）に調整される。 When the cooling, heating, and defrosting are used together (see FIG. 5), the refrigerant flows through the hot gas bypass channel 6 to reduce the refrigerant pressure (2 MPa). Therefore, in the present embodiment, the controller 61 detects the flow rate temperature sensor 82 when the density of the refrigerant in the refrigeration circuit of the cooling device 100 changes due to the flow of the refrigerant to the hot gas bypass flow path 6. Based on the temperature and the pressure detected by the pressure sensor 83, the refrigerant is discharged from the refrigerant tank 81 into the refrigeration circuit, or the refrigerant is recovered from the refrigeration circuit to the refrigerant tank 81. For example, when the refrigerant pressure is reduced, the refrigerant is discharged from the refrigerant tank 81 into the refrigeration circuit, so that the density of the refrigerant in the refrigeration circuit increases. As a result, the pressure of the refrigerant is adjusted to an appropriate pressure (for example, 2.5 MPa).

（本実施形態の効果）
本実施形態では、以下のような効果を得ることができる。なお、以下では、暖房運転時には、蒸発器３０ａが暖房運転するものとし、除霜時には、蒸発器３０ｃが除霜運転するものとして効果を記載している。 (Effect of this embodiment)
In the present embodiment, the following effects can be obtained. In the following description, the effect is described assuming that the evaporator 30a performs the heating operation during the heating operation, and the evaporator 30c performs the defrosting operation during the defrosting.

本実施形態では、上記のように、複数の蒸発器３０ａ〜３０ｃ毎に設けられる複数の電磁弁５２ａ〜５２ｃの開き具合を制御するとともに、複数の蒸発器３０ａ〜３０ｃ毎に設けられる複数の電磁弁５３ａ〜５３ｃの開き具合を制御する制御部６１を設ける。これにより、電磁弁５２ａ〜５２ｃおよび電磁弁５３ａ〜５３ｃが、それぞれ、複数の蒸発器３０ａ〜３０ｃ毎に設けられているので、電磁弁５２ａ〜５２ｃの開き具合を調整することによるホットガスバイパス流路６からの冷媒の圧力（温度）の調整と、電磁弁５３ａ〜５３ｃの開き具合を調整することによるホットガスバイパス流路６からの冷媒の流量の調整とを、蒸発器３０ａ〜３０ｃ毎に適切に行うことができる。その結果、互いに並列に接続された複数の蒸発器３０ａ〜３０ｃを備える冷却装置１００において、ホットガスバイパス流路６から蒸発器３０ａ〜３０ｃに流入する冷媒の流量および温度を蒸発器３０ａ〜３０ｃ毎に適切に調整することができる。 In the present embodiment, as described above, the degree of opening of the plurality of electromagnetic valves 52a to 52c provided for each of the plurality of evaporators 30a to 30c is controlled, and the plurality of electromagnetics provided for each of the plurality of evaporators 30a to 30c. A control unit 61 for controlling the opening degree of the valves 53a to 53c is provided. Thereby, since the solenoid valves 52a to 52c and the solenoid valves 53a to 53c are respectively provided for the plurality of evaporators 30a to 30c, the hot gas bypass flow by adjusting the degree of opening of the solenoid valves 52a to 52c. Adjustment of the refrigerant pressure (temperature) from the passage 6 and adjustment of the refrigerant flow rate from the hot gas bypass flow path 6 by adjusting the degree of opening of the solenoid valves 53a to 53c are performed for each of the evaporators 30a to 30c. Can be done appropriately. As a result, in the cooling device 100 including a plurality of evaporators 30a to 30c connected in parallel to each other, the flow rate and temperature of the refrigerant flowing into the evaporators 30a to 30c from the hot gas bypass flow path 6 are set for each of the evaporators 30a to 30c. Can be adjusted appropriately.

また、本実施形態では、上記のように、複数の蒸発器３０ａ〜３０ｃの冷媒流出側と、複数の膨張弁４０ａ〜４０ｃの冷媒流入側とを接続する過冷却促進流路７ａ〜７ｃを設けて、複数の電磁弁５３ａ〜５３ｃを、それぞれ、過冷却促進流路７ａ〜７ｃ上に設ける。これにより、蒸発器３０ａ〜３０ｃから流出する比較的温度の低い冷媒が、電磁弁５３ａ〜５３ｃを介して、圧縮機１０から吐出され膨張弁４０ａ〜４０ｃに流入される比較的温度の高い冷媒に混合されるので、膨張弁４０ａ〜４０ｃから蒸発器３０ａ〜３０ｃに流入する冷媒の温度を低下させることができる。すなわち、膨張弁４０ａ〜４０ｃから蒸発器３０ａ〜３０ｃに流入する冷媒の過冷却を促進することができる。 In the present embodiment, as described above, the supercooling promotion flow paths 7a to 7c that connect the refrigerant outflow sides of the plurality of evaporators 30a to 30c and the refrigerant inflow sides of the plurality of expansion valves 40a to 40c are provided. The plurality of solenoid valves 53a to 53c are provided on the supercooling promotion flow paths 7a to 7c, respectively. Thereby, the relatively low temperature refrigerant flowing out of the evaporators 30a to 30c becomes the relatively high temperature refrigerant discharged from the compressor 10 and flowing into the expansion valves 40a to 40c via the electromagnetic valves 53a to 53c. Since they are mixed, the temperature of the refrigerant flowing into the evaporators 30a to 30c from the expansion valves 40a to 40c can be lowered. That is, the supercooling of the refrigerant flowing into the evaporators 30a to 30c from the expansion valves 40a to 40c can be promoted.

また、本実施形態では、上記のように、複数の蒸発器３０ａ〜３０ｃ毎に設けられ、蒸発器３０ａ〜３０ｃの入口近傍の流路の温度を検出する流路温度センサ７１ａ〜７１ｃと、複数の蒸発器３０ａ〜３０ｃ毎に設けられ、蒸発器３０ａ〜３０ｃの近傍の空気の温度を検出する空気温度センサ７２ａ〜７２ｃとを備える。そして、制御部６１を、暖房運転時には、流路温度センサ７１ａによって検出された流路の温度に基づいて、暖房運転をする蒸発器３０ａに対応する電磁弁５２ａの開き具合を制御するとともに、空気温度センサ７２ａによって検出された蒸発器３０ａの近傍の空気の温度に基づいて、暖房運転をする蒸発器３０ａに対応する電磁弁５３ａの開き具合を制御するように構成する。これにより、暖房運転をする蒸発器３０ａに流入する冷媒の温度、および、暖房運転をする蒸発器３０ａ近傍の空気（蒸発器３０ａから送風される空気）の温度を、所望の温度に調整することができるので、暖房運転をする蒸発器３０ａの暖房能力を適切（適正）に制御することができる。 In the present embodiment, as described above, a plurality of flow path temperature sensors 71a to 71c that are provided for each of the plurality of evaporators 30a to 30c and detect the temperature of the flow path in the vicinity of the inlets of the evaporators 30a to 30c, Air temperature sensors 72a to 72c that are provided for each of the evaporators 30a to 30c and detect the temperature of the air in the vicinity of the evaporators 30a to 30c. Then, during the heating operation, the controller 61 controls the degree of opening of the electromagnetic valve 52a corresponding to the evaporator 30a that performs the heating operation based on the temperature of the flow path detected by the flow path temperature sensor 71a, and the air Based on the temperature of the air in the vicinity of the evaporator 30a detected by the temperature sensor 72a, the opening degree of the electromagnetic valve 53a corresponding to the evaporator 30a that performs the heating operation is controlled. Thereby, the temperature of the refrigerant flowing into the evaporator 30a performing the heating operation and the temperature of the air in the vicinity of the evaporator 30a performing the heating operation (air blown from the evaporator 30a) are adjusted to desired temperatures. Therefore, the heating capacity of the evaporator 30a that performs the heating operation can be appropriately controlled.

また、本実施形態では、上記のように、暖房運転時には、暖房運転をする蒸発器３０ａから流出した冷媒を、過冷却促進流路７ａを介して、冷房運転をする蒸発器３０ｂおよび３０ｃに流入させる。これにより、暖房後の蒸発器３０ａから流出する比較的温度の低い冷媒が、冷房運転をする蒸発器３０ｂおよび３０ｃに流入する比較的温度の高い冷媒に混合されるので、冷房運転をする蒸発器３０ｂおよび３０ｃに流入する冷媒の過冷却を促進することができる。その結果、冷房運転の効率を向上させることができる。 In the present embodiment, as described above, during the heating operation, the refrigerant that has flowed out of the evaporator 30a that performs the heating operation flows into the evaporators 30b and 30c that perform the cooling operation via the supercooling promotion flow path 7a. Let Accordingly, the refrigerant having a relatively low temperature flowing out from the evaporator 30a after the heating is mixed with the refrigerant having a relatively high temperature flowing into the evaporators 30b and 30c performing the cooling operation, and thus the evaporator performing the cooling operation. Supercooling of the refrigerant flowing into 30b and 30c can be promoted. As a result, the efficiency of the cooling operation can be improved.

また、本実施形態では、上記のように、複数の蒸発器３０ａ〜３０ｃ毎に設けられ、蒸発器３０ａ〜３０ｃの出口近傍の流路の温度を検出する流路温度センサ７３ａ〜７３ｃを設ける。そして、制御部６１を、除霜運転時には、流路温度センサ７３ｃによって検出された流路の温度に基づいて、除霜運転をする蒸発器３０ｃに対応する電磁弁５２ｃの開き具合を制御するように構成する。これにより、除霜運転をする蒸発器３０ｃに流入する冷媒の温度が調整されるので、除霜運転を適切に行うことができる。また、除霜運転をする蒸発器３０ｃから流出する冷媒の温度を調整することができるので、除霜運転をする蒸発器３０ｃから流出する冷媒の温度が高すぎることに起因する悪影響を抑制することができる。 In the present embodiment, as described above, the channel temperature sensors 73a to 73c are provided for each of the plurality of evaporators 30a to 30c and detect the temperature of the channel near the outlets of the evaporators 30a to 30c. And the control part 61 controls the opening degree of the solenoid valve 52c corresponding to the evaporator 30c which performs a defrost operation based on the temperature of the flow path detected by the flow path temperature sensor 73c at the time of a defrost operation. Configure. Thereby, since the temperature of the refrigerant | coolant which flows into the evaporator 30c which performs a defrost operation is adjusted, a defrost operation can be performed appropriately. Moreover, since the temperature of the refrigerant | coolant which flows out from the evaporator 30c which performs a defrost operation can be adjusted, the bad influence resulting from the temperature of the refrigerant | coolant which flows out from the evaporator 30c which performs a defrost operation is too high is suppressed. Can do.

また、本実施形態では、上記のように、主流路１に設けられ、冷媒が収容される冷媒タンク８１と、冷媒タンク８１の近傍の主流路１に設けられ、冷媒タンク８１の近傍の流路の温度を検出する流路温度センサ８２と、冷媒タンク８１の近傍の主流路１に設けられ、冷媒タンク８１の近傍の冷媒の圧力を検出する圧力センサ８３とを備える。そして、制御部６１を、ホットガスバイパス流路６に冷媒が流れることにより、冷却装置１００の冷凍回路内の冷媒の密度が変化した場合、流路温度センサ８２によって検出された温度と、圧力センサ８３によって検出された圧力とに基づいて、冷媒タンク８１から冷凍回路内に冷媒を放出するか、または、冷凍回路から冷媒タンク８１に冷媒を回収するように制御するように構成する。これにより、ホットガスバイパス流路６に冷媒が流れることにより冷却装置１００の冷凍回路内の冷媒の密度が変化することに起因して、冷凍回路内の冷媒の圧力が変化した場合でも、冷媒タンク８１からの冷媒の放出または回収により、冷凍回路内の冷媒の圧力を、適切な圧力に調整（維持）することができる。 In the present embodiment, as described above, the main tank 1 is provided with the refrigerant tank 81 in which the refrigerant is accommodated, the main tank 1 in the vicinity of the refrigerant tank 81, and the flow path in the vicinity of the refrigerant tank 81. And a pressure sensor 83 that is provided in the main flow path 1 in the vicinity of the refrigerant tank 81 and detects the pressure of the refrigerant in the vicinity of the refrigerant tank 81. And when the density of the refrigerant | coolant in the freezing circuit of the cooling device 100 changes by the refrigerant | coolant flowing into the hot gas bypass flow path 6 in the control part 61, the temperature detected by the flow path temperature sensor 82, and a pressure sensor Based on the pressure detected by 83, the refrigerant is discharged from the refrigerant tank 81 into the refrigeration circuit, or the refrigerant is recovered from the refrigeration circuit into the refrigerant tank 81. Thus, even when the refrigerant pressure in the refrigeration circuit changes due to the refrigerant density in the refrigeration circuit of the cooling device 100 changing due to the refrigerant flowing in the hot gas bypass channel 6, the refrigerant tank By releasing or collecting the refrigerant from 81, the pressure of the refrigerant in the refrigeration circuit can be adjusted (maintained) to an appropriate pressure.

[変形例]
なお、今回開示された実施形態は、すべての点で例示であって制限的なものではないと考えられるべきである。本発明の範囲は、上記した実施形態の説明ではなく特許請求の範囲によって示され、さらに特許請求の範囲と均等の意味および範囲内でのすべての変更（変形例）が含まれる。 [Modification]
The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is shown not by the above description of the embodiment but by the scope of claims for patent, and further includes all modifications (modifications) within the meaning and scope equivalent to the scope of claims for patent.

たとえば、上記実施形態では、冷却装置１００に３つの蒸発器３０ａ〜３０ｃが設けられる例について示したが、本発明はこれに限られない。本発明では、冷却装置１００に、３つ以外の数の複数の蒸発器が設けられていてもよい。 For example, in the above-described embodiment, the example in which the three evaporators 30a to 30c are provided in the cooling device 100 has been described, but the present invention is not limited thereto. In the present invention, the cooling device 100 may be provided with a plurality of evaporators other than three.

また、上記実施形態では、過冷却促進流路７ａ〜７ｃ上に、蒸発器３０ａ〜３０ｃの冷媒の流量を調整するための電磁弁５３ａ〜５３ｃが設けられている例について示したが、本発明はこれに限られない。本発明では、蒸発器３０ａ〜３０ｃの冷媒の流量を調整するための電磁弁５３ａ〜５３ｃが、過冷却促進流路７ａ〜７ｃ以外の流路上に設けられていてもよい。 Moreover, although the said embodiment showed about the example in which the solenoid valves 53a-53c for adjusting the flow volume of the refrigerant | coolant of the evaporators 30a-30c were provided on the supercooling promotion flow paths 7a-7c, this invention was shown. Is not limited to this. In the present invention, the electromagnetic valves 53a to 53c for adjusting the flow rate of the refrigerant in the evaporators 30a to 30c may be provided on channels other than the supercooling promotion channels 7a to 7c.

また、上記実施形態では、冷房および暖房の併用時に、蒸発器３０ａが暖房運転をするとともに、蒸発器３０ｂおよび３０ｃが冷房運転をする例について示したが、本発明はこれに限られない。たとえば、冷房および暖房の併用時に、蒸発器３０ａ〜３０ｃのうちの１つまたは２つの蒸発器が暖房運転をし、残りの蒸発器が冷房運転をするようにしてもよい。 In the above-described embodiment, the example in which the evaporator 30a performs the heating operation and the evaporators 30b and 30c perform the cooling operation at the time of the combined use of the cooling and heating has been described, but the present invention is not limited thereto. For example, when the cooling and heating are used together, one or two of the evaporators 30a to 30c may perform the heating operation, and the remaining evaporators may perform the cooling operation.

また、上記実施形態では、冷房、暖房および除霜の併用時に、蒸発器３０ａが暖房運転をして、蒸発器３０ｂが冷房運転して、蒸発器３０ｃが除霜運転をする例について示したが、本発明はこれに限られない。たとえば、暖房運転、冷房運転および除霜運転をする蒸発器が入れ替わってもよい。また、暖房は行わずに、冷房と除霜とを併用する運転を行ってもよい。 In the above-described embodiment, the example in which the evaporator 30a performs the heating operation, the evaporator 30b performs the cooling operation, and the evaporator 30c performs the defrosting operation when the cooling, heating, and defrosting are used together. The present invention is not limited to this. For example, the evaporator that performs the heating operation, the cooling operation, and the defrosting operation may be replaced. Moreover, you may perform the driving | operation which uses cooling and defrost together, without heating.

また、上記実施形態では、圧力調整時に、冷媒の圧力を大きくするように、冷媒タンク８１から冷凍回路内に冷媒が放出される例について示したが、本発明はこれに限られない。本発明では、何らかの要因により冷媒の圧力が適切な圧力よりも大きくなった場合には、冷凍回路から冷媒タンク８１に冷媒を回収することにより、冷媒の圧力が適切な圧力に調整される。 In the above embodiment, the example in which the refrigerant is discharged from the refrigerant tank 81 into the refrigeration circuit so as to increase the pressure of the refrigerant at the time of pressure adjustment has been described, but the present invention is not limited to this. In the present invention, when the refrigerant pressure becomes larger than an appropriate pressure due to some factor, the refrigerant pressure is adjusted to an appropriate pressure by collecting the refrigerant from the refrigeration circuit to the refrigerant tank 81.

また、上記実施形態では、圧縮機１０に回転数の変更により冷媒吐出量が制御可能なインバータ制御式圧縮機を用いた例について示したが、本発明はこれに限られない。たとえば、インバータ制御を用いない一定速型（非可変容量型）の圧縮機１０を用いて冷却装置１００を構成してもよい。また、圧縮機１０としては、制御方式（インバータ制御式または一定速型）に関係なく、レシプロ式圧縮機、ロータリ式圧縮機、スクロール式圧縮機およびスクリュ式圧縮機などのいずれを用いてもよい。 Moreover, although the said embodiment showed about the example using the inverter control type compressor which can control refrigerant | coolant discharge amount by the rotation speed change to the compressor 10, this invention is not limited to this. For example, the cooling device 100 may be configured using a constant speed (non-variable capacity) compressor 10 that does not use inverter control. Further, as the compressor 10, any of a reciprocating compressor, a rotary compressor, a scroll compressor, a screw compressor, and the like may be used regardless of the control method (inverter control type or constant speed type). .

また、上記実施形態では、蒸発器３０ａ〜３０ｃを、冷蔵室Ａ〜Ｃに配置する例について示したが、本発明はこれに限られない。たとえば、蒸発器３０ａ〜３０ｃを、冷蔵室以外のショーケース、業務用冷蔵庫、家庭用冷蔵庫、空調機器などに配置してもよい。 Moreover, in the said embodiment, although the evaporator 30a-30c was shown about the example arrange | positioned in the refrigerator compartment AC, this invention is not limited to this. For example, the evaporators 30a to 30c may be arranged in a showcase other than the refrigerator compartment, a commercial refrigerator, a household refrigerator, an air conditioner, or the like.

また、上記実施形態では、フィンアンドチューブ型の空気熱交換器が蒸発器３０ａ〜３０ｃに用いられた冷却装置に対して本発明を適用したが、この限りではない。すなわち、冷媒が所定の蒸発温度で蒸発可能な圧力容器を介して他の熱交換流体（水、ブラインなど）との熱交換が可能な蒸発器を備えた冷却装置に対して本発明を適用してもよい。 Moreover, in the said embodiment, although this invention was applied with respect to the cooling device with which the fin and tube type air heat exchanger was used for evaporator 30a-30c, it is not this limitation. That is, the present invention is applied to a cooling device including an evaporator capable of exchanging heat with another heat exchange fluid (water, brine, etc.) via a pressure vessel in which the refrigerant can evaporate at a predetermined evaporation temperature. May be.

また、上記実施形態では、二酸化炭素（ＣＯ_２）冷媒を用いて冷却装置１００を動作させる例について示したが、本発明はこれに限られない。二酸化炭素冷媒以外の他の自然冷媒を使用してもよいし、オゾン層破壊係数がゼロの代替フロン冷媒を使用してもよい。 In the above embodiment, carbon dioxide (CO ₂₎ is shown an example of operating a cooling device 100 using a refrigerant, the present invention is not limited thereto. A natural refrigerant other than the carbon dioxide refrigerant may be used, or an alternative chlorofluorocarbon refrigerant having an ozone layer depletion coefficient of zero may be used.

１主流路
６ホットガスバイパス流路（バイパス流路）
７ａ、７ｂ、７ｃ過冷却促進流路
１０圧縮機
２０凝縮器
３０ａ、３０ｂ、３０ｃ蒸発器
４０ａ、４０ｂ、４０ｃ膨張弁
５２ａ、５２ｂ、５２ｃ電磁弁（第１弁）
５３ａ、５３ｂ、５３ｃ電磁弁（第２弁）
６１制御部
７１ａ、７１ｂ、７１ｃ流路温度センサ（第１流路温度検出部）
７２ａ、７２ｂ、７２ｃ空気温度センサ（空気温度検出部）
７３ａ、７３ｂ、７３ｃ流路温度センサ（第２流路温度検出部）
８１冷媒タンク
８２流路温度センサ（第３流路温度検出部）
８３圧力センサ（圧力検出部）
１００冷却装置 1 Main channel 6 Hot gas bypass channel (bypass channel)
7a, 7b, 7c Supercooling promotion flow path 10 Compressor 20 Condenser 30a, 30b, 30c Evaporator 40a, 40b, 40c Expansion valve 52a, 52b, 52c Solenoid valve (first valve)
53a, 53b, 53c Solenoid valve (second valve)
61 Control part 71a, 71b, 71c Channel temperature sensor (1st channel temperature detection part)
72a, 72b, 72c Air temperature sensor (air temperature detector)
73a, 73b, 73c Channel temperature sensor (second channel temperature detector)
81 Refrigerant tank 82 Channel temperature sensor (third channel temperature detector)
83 Pressure sensor (pressure detector)
100 Cooling device

Claims

A compressor for compressing the refrigerant;
A condenser that condenses the refrigerant;
A plurality of evaporators connected in parallel to evaporate the refrigerant;
A plurality of expansion valves that are provided for each of the plurality of evaporators and expand the refrigerant condensed by the condenser;
A main flow path connecting the compressor, the condenser, the plurality of expansion valves, and the plurality of evaporators;
A bypass flow path connecting a discharge side of the compressor and a refrigerant inflow side of each of the plurality of evaporators;
A plurality of first valves capable of controlling the degree of opening provided for each of the plurality of evaporators on the bypass flow path;
A plurality of second valves capable of controlling the degree of opening provided for each of the plurality of evaporators on the refrigerant outflow side of the evaporator;
A controller for controlling the degree of opening of the plurality of first valves provided for each of the plurality of evaporators, and for controlling the degree of opening of the plurality of second valves provided for each of the plurality of evaporators. Cooling system.

A plurality of supercooling promotion flow paths that respectively connect the refrigerant outflow side of the plurality of evaporators and the refrigerant inflow side of the plurality of expansion valves;
The cooling device according to claim 1, wherein each of the plurality of second valves is provided on the plurality of supercooling promotion flow paths.

A first flow path temperature detection unit that is provided for each of the plurality of evaporators and detects a temperature of a flow path near the inlet of the evaporator;
An air temperature detection unit that is provided for each of the plurality of evaporators and detects the temperature of air in the vicinity of the evaporator;
The controller controls the degree of opening of the first valve corresponding to the evaporator that performs the heating operation based on the temperature of the flow path detected by the first flow path temperature detection unit during the heating operation. The opening degree of the second valve corresponding to the evaporator that performs the heating operation is controlled based on the temperature of the air in the vicinity of the evaporator detected by the air temperature detector. The cooling device according to claim 2.

The refrigerant that flows out of the evaporator that performs the heating operation is configured to flow into the evaporator that performs the cooling operation through the supercooling promotion flow path during the heating operation. The cooling device according to 1.

A second flow path temperature detection unit that is provided for each of the plurality of evaporators and detects the temperature of the flow path in the vicinity of the outlet of the evaporator;
In the defrosting operation, the control unit controls the degree of opening of the first valve corresponding to the evaporator performing the defrosting operation based on the temperature of the flow channel detected by the second flow channel temperature detection unit. The cooling device according to any one of claims 1 to 4, wherein the cooling device is configured to.

A refrigerant tank provided in the main flow path and containing a refrigerant;
A third flow path temperature detector provided in the main flow path in the vicinity of the refrigerant tank and detecting the temperature of the flow path in the vicinity of the refrigerant tank;
A pressure detector provided in the main flow path in the vicinity of the refrigerant tank and detecting the pressure of the refrigerant in the vicinity of the refrigerant tank;
The control unit detects the temperature detected by the third channel temperature detection unit and the pressure detection when the density of the refrigerant in the refrigeration circuit of the cooling device changes due to the refrigerant flowing in the bypass channel. The refrigerant is discharged from the refrigerant tank into the refrigeration circuit or controlled to collect the refrigerant from the refrigeration circuit to the refrigerant tank based on the pressure detected by the unit. The cooling device according to any one of claims 1 to 5.