技术领域technical field
本发明涉及例如用于制冷、冷藏等用途的制冷循环装置。The present invention relates to a refrigeration cycle device used for refrigeration, refrigeration, and the like, for example.
背景技术Background technique
以往，已知由多个连通配管将具有压缩机和冷凝器的热源单元和具有膨胀阀和蒸发器的冷却单元连接，并使制冷剂通过连通配管在热源单元和冷却单元之间循环那样的制冷机。在这样的以往的制冷机中，尝试使用作为高压制冷剂的CO2。Conventionally, there is known a refrigeration unit in which a heat source unit having a compressor and a condenser and a cooling unit having an expansion valve and an evaporator are connected by a plurality of communication pipes, and a refrigerant is circulated between the heat source unit and the cooling unit through the communication pipes. machine. In such conventional refrigerators, attempts have been made to use CO2 as a high-pressure refrigerant.
在这样的使用了高压制冷剂的以往的制冷机中，由于工作压力高，所以，不仅连通配管的壁厚变厚，连通配管本身的成本增大，连通配管的弯曲加工、连接加工也变难，现场的连通配管的设置作业的劳力和时间变大。另外，在向例如便利店、超级市场等店铺设置的陈列柜等使用所述那样的以往的制冷机的情况下，因为将冷却单元设置在远离热源单元的场所的情况多，所以，连通配管的长度变长(例如，连通配管的全长为100m左右)的情况多。若连通配管的长度变长，则用于在现场进行连通配管的施工的材料成本增大。由于这样的情况，用于设置制冷机的作业时间、施工费增加。In such a conventional refrigerator using a high-pressure refrigerant, the high operating pressure not only increases the thickness of the communication pipe, but also increases the cost of the communication pipe itself, and also makes it difficult to bend and connect the communication pipe. , The labor and time required for setting up the connecting piping on site increase. In addition, when the above-mentioned conventional refrigerators are used in showcases installed in stores such as convenience stores and supermarkets, since the cooling unit is often installed in a place far from the heat source unit, the length of the communication piping The length becomes longer (for example, the total length of the communication pipe is about 100 m) in many cases. If the length of the communication pipe becomes longer, the material cost for constructing the communication pipe on site increases. Due to such a situation, the work time and construction cost for installing the refrigerator increase.
以往，为了谋求连通配管的薄壁化，提出了下述的制冷机，该制冷机在热源单元配置主减压机构，使由主减压机构减压了的制冷剂在连通配管中流动，使连通配管内的压力降低(例如，参见专利文献1)。Conventionally, in order to reduce the thickness of communication pipes, there has been proposed a refrigerator in which a main decompression mechanism is arranged in a heat source unit, and the refrigerant decompressed by the main decompression mechanism flows through the communication pipes so that The pressure in the communication pipe decreases (for example, see Patent Document 1).
在先技术文献prior art literature
专利文献patent documents
专利文献1：日本特开2003-139422号公报Patent Document 1: Japanese Patent Laid-Open No. 2003-139422
发明内容Contents of the invention
发明所要解决的课题The problem to be solved by the invention
但是，在专利文献1所示的以往的制冷机中，若连通配管内的制冷剂的压力损失变大，则由主减压机构减压了的制冷剂的压力会进一步大幅降低，因此，蒸发器中的制冷剂的饱和温度容易低于在蒸发器中利用的蒸发温度，难以确保制冷机的恰当的运转。However, in the conventional refrigerating machine shown in Patent Document 1, if the pressure loss of the refrigerant in the communication pipe increases, the pressure of the refrigerant decompressed by the main decompression mechanism will further decrease significantly, so the evaporation The saturation temperature of the refrigerant in the evaporator is likely to be lower than the evaporation temperature used in the evaporator, making it difficult to ensure proper operation of the refrigerator.
本发明是为解决所述那样的课题做出的发明，其目的是得到一种能够谋求减轻现场的设置作业的劳力和时间，且能够避免缩小恰当运转范围的制冷循环装置。The present invention was made to solve the above-mentioned problems, and an object of the present invention is to obtain a refrigeration cycle apparatus capable of reducing the labor and time of on-site installation work and avoiding narrowing of the proper operating range.
用于解决课题的手段means to solve the problem
基于本发明的制冷循环装置具备热源单元、冷却单元、第1连通管以及第2连通管，所述热源单元具有压缩制冷剂的压缩机、冷却来自压缩机的制冷剂的高压侧热交换器、将来自高压侧热交换器的制冷剂减压的主减压装置，所述冷却单元具有使制冷剂蒸发的低压侧热交换器，所述第1连通管在热源单元和冷却单元之间导通从主减压装置向低压侧热交换器输送的制冷剂，所述第2连通管在热源单元和冷却单元之间导通从低压侧热交换器向压缩机输送的制冷剂，第1连通管是在低压侧热交换器中的制冷剂的饱和温度不低于低压侧热交换器的利用蒸发温度的范围产生制冷剂的压力损失的连通管。A refrigeration cycle device according to the present invention includes a heat source unit including a compressor for compressing refrigerant, a high-pressure side heat exchanger for cooling refrigerant from the compressor, a cooling unit, a first communication pipe, and a second communication pipe. A main decompression device for depressurizing the refrigerant from the high-pressure side heat exchanger, the cooling unit has a low-pressure side heat exchanger for evaporating the refrigerant, and the first communication pipe leads between the heat source unit and the cooling unit The refrigerant sent from the main decompression device to the low-pressure side heat exchanger, the second communication pipe conducts the refrigerant sent from the low-pressure side heat exchanger to the compressor between the heat source unit and the cooling unit, and the first communication pipe It is a communicating pipe through which the refrigerant's saturation temperature in the low-pressure side heat exchanger is not lower than the range of the evaporation temperature of the low-pressure side heat exchanger to cause a pressure loss of the refrigerant.
发明效果Invention effect
根据基于本发明的制冷循环装置，因为能够通过主减压装置将制冷剂减压，使第1连通管中的制冷剂的压力变低，所以，能够谋求第1连通管的薄壁化，能够减轻现场的制冷循环装置的设置作业的劳力和时间。另外，因为第1连通管中的制冷剂的压力损失被抑制在低压侧热交换器的制冷剂的饱和温度不低于低压侧热交换器的利用蒸发温度的范围，所以，能够避免缩小制冷循环装置的恰当运转范围。According to the refrigeration cycle device based on the present invention, since the refrigerant can be decompressed by the main decompression device, the pressure of the refrigerant in the first communication pipe can be reduced, so the thickness of the first communication pipe can be reduced, and the pressure of the refrigerant in the first communication pipe can be reduced. I reduce labor and time for setting work of the on-site refrigeration cycle device. In addition, since the pressure loss of the refrigerant in the first communication pipe is suppressed so that the saturation temperature of the refrigerant in the low-pressure side heat exchanger is not lower than the range of the evaporation temperature used by the low-pressure side heat exchanger, it is possible to avoid shrinking the refrigeration cycle. The proper operating range of the device.
附图说明Description of drawings
图1是表示基于本发明的实施方式1的制冷循环装置的结构图。FIG. 1 is a configuration diagram showing a refrigeration cycle apparatus according to Embodiment 1 of the present invention.
图2是表示使用R410A制冷剂的既有的制冷循环装置的结构图。FIG. 2 is a configuration diagram showing a conventional refrigeration cycle apparatus using R410A refrigerant.
图3是表示图1的第1连通管中的制冷剂的压力损失和第1连通管的内径的关系的图表。Fig. 3 is a graph showing the relationship between the pressure loss of the refrigerant in the first communication pipe of Fig. 1 and the inner diameter of the first communication pipe.
图4是表示图1的第1连通管中的制冷剂的压力损失和第1连通管的长度的关系的图表。Fig. 4 is a graph showing the relationship between the pressure loss of the refrigerant in the first communication pipe in Fig. 1 and the length of the first communication pipe.
图5是表示基于本发明的实施方式2的制冷循环装置的结构图。Fig. 5 is a configuration diagram showing a refrigeration cycle apparatus according to Embodiment 2 of the present invention.
图6是表示基于本发明的实施方式3的制冷循环装置的结构图。Fig. 6 is a configuration diagram showing a refrigeration cycle apparatus according to Embodiment 3 of the present invention.
图7是表示基于本发明的实施方式4的制冷循环装置的结构图。Fig. 7 is a configuration diagram showing a refrigeration cycle apparatus according to Embodiment 4 of the present invention.
图8是表示基于本发明的实施方式5的制冷循环装置的结构图。Fig. 8 is a configuration diagram showing a refrigeration cycle apparatus according to Embodiment 5 of the present invention.
图9是表示应用了使用R404A制冷剂的制冷循环装置中的设计压力的第1连通管中的制冷剂的压力损失和第1连通管的内径的关系的图表。Fig. 9 is a graph showing the relationship between the pressure loss of the refrigerant in the first communication pipe and the inner diameter of the first communication pipe to which the design pressure in the refrigeration cycle apparatus using R404A refrigerant is applied.
图10是表示应用了使用R404A制冷剂的制冷循环装置中的设计压力的第1连通管中的制冷剂的压力损失和第1连通管的长度的关系的图表。Fig. 10 is a graph showing the relationship between the pressure loss of the refrigerant in the first communication pipe and the length of the first communication pipe to which the design pressure in the refrigeration cycle apparatus using R404A refrigerant is applied.
具体实施方式detailed description
下面，参照附图，对本发明的优选的实施方式进行说明。Next, preferred embodiments of the present invention will be described with reference to the drawings.
实施方式1.Implementation mode 1.
图1是表示基于本发明的实施方式1的制冷循环装置的结构图。在图中，制冷循环装置具有热源单元1、离开热源单元1被配置的冷却单元2、和分别被连接在热源单元1和冷却单元2之间并使制冷剂在热源单元1和冷却单元2之间循环的第1连通管3以及第2连通管4。在该例中，作为制冷循环装置的制冷剂使用作为高压制冷剂的CO2，制冷循环的高压侧的压力在制冷剂的临界压力以下。FIG. 1 is a configuration diagram showing a refrigeration cycle apparatus according to Embodiment 1 of the present invention. In the figure, the refrigeration cycle device has a heat source unit 1, a cooling unit 2 configured away from the heat source unit 1, and is respectively connected between the heat source unit 1 and the cooling unit 2 and makes refrigerant flow between the heat source unit 1 and the cooling unit 2 The first communication pipe 3 and the second communication pipe 4 for inter-circulation. In this example, CO2 , which is a high-pressure refrigerant, is used as the refrigerant of the refrigeration cycle device, and the pressure on the high-pressure side of the refrigeration cycle is not higher than the critical pressure of the refrigerant.
热源单元1具有压缩机11、冷凝器(高压侧热交换器)12和主减压装置(膨胀阀)13。在热源单元1设置按顺序连接第2连通管4、压缩机11、冷凝器12、主减压装置13和第1连通管3的多个连接管。另一方面，冷却单元2具有蒸发器(低压侧热交换器)14。在冷却单元2设置按顺序连接第1连通管3、蒸发器14和第2连通管4的多个连接管。The heat source unit 1 has a compressor 11 , a condenser (high pressure side heat exchanger) 12 and a main decompression device (expansion valve) 13 . The heat source unit 1 is provided with a plurality of connection pipes that sequentially connect the second communication pipe 4 , the compressor 11 , the condenser 12 , the main decompression device 13 , and the first communication pipe 3 . On the other hand, the cooling unit 2 has an evaporator (low-pressure side heat exchanger) 14 . The cooling unit 2 is provided with a plurality of connection pipes that sequentially connect the first communication pipe 3 , the evaporator 14 , and the second communication pipe 4 .
据此，在制冷循环装置中，若压缩机11被驱动，则制冷剂按照压缩机11、冷凝器12、主减压装置13、第1连通管3、蒸发器14、第2连通管4的顺序被输送，并返回压缩机11。Accordingly, in the refrigeration cycle device, when the compressor 11 is driven, the refrigerant flows through the compressor 11, the condenser 12, the main decompression device 13, the first communication pipe 3, the evaporator 14, and the second communication pipe 4. The sequence is conveyed and returned to compressor 11.
压缩机11压缩气体状的制冷剂。由压缩机11压缩了的制冷剂向冷凝器12输送。The compressor 11 compresses a gaseous refrigerant. The refrigerant compressed by the compressor 11 is sent to the condenser 12 .
冷凝器12冷却来自压缩机11的气体状的制冷剂，使之成为液体状的制冷剂。冷凝器12通过从气体状的制冷剂向冷却材料(例如，空气或水等)释放热来冷却并冷凝制冷剂。由冷凝器12冷凝了的制冷剂向主减压装置13输送。The condenser 12 cools the gaseous refrigerant from the compressor 11 into a liquid refrigerant. The condenser 12 cools and condenses the refrigerant by releasing heat from the gaseous refrigerant to a cooling material (for example, air or water). The refrigerant condensed by the condenser 12 is sent to the main decompression device 13 .
主减压装置13使来自冷凝器12的液体状的制冷剂膨胀并减压。在该例中，主减压装置13为可调整制冷剂的流量的电动膨胀阀。主减压装置13由未图示出的控制部控制。The main decompression device 13 expands and decompresses the liquid refrigerant from the condenser 12 . In this example, the main decompression device 13 is an electric expansion valve capable of adjusting the flow rate of the refrigerant. The main decompression device 13 is controlled by a control unit not shown.
第1连通管3在热源单元1和冷却单元2之间导通从主减压装置13向蒸发器14输送的制冷剂。The first communication pipe 3 conducts the refrigerant sent from the main decompression device 13 to the evaporator 14 between the heat source unit 1 and the cooling unit 2 .
蒸发器14使来自第1连通管3的制冷剂蒸发。蒸发器14被设置在例如设于便利店、超级市场等店铺的冷却用容器(例如，冷却用陈列柜等)。冷却用容器通过由蒸发器14使制冷剂蒸发而被冷却。The evaporator 14 evaporates the refrigerant from the first communication pipe 3 . The evaporator 14 is installed in, for example, a cooling container (for example, a cooling showcase, etc.) provided in a convenience store, a supermarket, or the like. The cooling container is cooled by evaporating the refrigerant in the evaporator 14 .
第2连通管4在热源单元1和冷却单元2之间导通从蒸发器14向压缩机11输送的制冷剂。在第2连通管4内，气体状的制冷剂被导通。The second communication pipe 4 communicates the refrigerant sent from the evaporator 14 to the compressor 11 between the heat source unit 1 and the cooling unit 2 . A gaseous refrigerant is conducted in the second communication pipe 4 .
第1以及第2连通管3、4被设置在与主减压装置13相比的下游、与压缩机11相比的上游。因此，第1以及第2连通管3、4被设置在制冷循环中的低压侧。The first and second communication pipes 3 and 4 are provided downstream of the main decompression device 13 and upstream of the compressor 11 . Therefore, the first and second communication pipes 3 and 4 are provided on the low-pressure side in the refrigeration cycle.
主减压装置13将制冷剂减压到第1以及第2连通管3、4的设计压力以下的压力。在该例中，第1以及第2连通管3、4的设计压力为4.15MPa，主减压装置13将制冷剂减压到4.15MPa以下。The main decompression device 13 decompresses the refrigerant to a pressure equal to or lower than the design pressure of the first and second communication pipes 3 and 4 . In this example, the design pressure of the first and second communication pipes 3 and 4 is 4.15 MPa, and the main decompression device 13 decompresses the refrigerant to 4.15 MPa or less.
例如，在使用了R410A制冷剂的既有的制冷循环装置中，如图2所示，主减压装置13不是被设置在热源单元1，而是被设置在冷却单元2，来自冷凝器12的制冷剂在穿过第1连通管3后，向主减压装置13输送。即，在使用了R410A制冷剂的既有的制冷循环装置中，第1连通管3被设置在制冷循环中的高压侧。使用了R410A制冷剂的图2所示的既有的制冷循环装置的第1连通管3的设计压力为4.15MPa。For example, in an existing refrigeration cycle device using R410A refrigerant, as shown in FIG. The refrigerant is sent to the main decompression device 13 after passing through the first communication pipe 3 . That is, in the conventional refrigeration cycle apparatus using R410A refrigerant, the first communication pipe 3 is provided on the high-pressure side in the refrigeration cycle. The design pressure of the first communication pipe 3 of the conventional refrigeration cycle apparatus shown in FIG. 2 using R410A refrigerant is 4.15 MPa.
在使用了高压制冷剂(CO2)的基于本实施方式的制冷循环装置中，因为主减压装置13被设置在热源单元1，所以，通过由主减压装置13使制冷剂减压，能够使第1以及第2连通管3、4内的制冷剂的压力在既有的制冷循环装置的第1连通管3的设计压力以下(即，4.15MPa以下)。因此，能够将使用R410A制冷剂的既有的制冷循环装置的第1以及第2连通管3、4作为使用高压制冷剂(CO2)的基于本实施方式的制冷循环装置的第1以及第3连通管3、4来再利用。In the refrigeration cycle apparatus according to this embodiment using a high-pressure refrigerant (CO2 ), since the main decompression device 13 is provided in the heat source unit 1, by decompressing the refrigerant with the main decompression device 13, it is possible to The pressure of the refrigerant in the first and second communication pipes 3 and 4 is kept below the design pressure of the first communication pipe 3 of the conventional refrigeration cycle device (ie, 4.15 MPa or less). Therefore, the first and second communication pipes 3 and 4 of the existing refrigeration cycle device using R410A refrigerant can be used as the first and third communication pipes of the refrigeration cycle device according to this embodiment using high-pressure refrigerant (CO2 ). The connecting pipes 3 and 4 are reused.
另外，在从主减压装置13出来的制冷剂穿过第1连通管3时，产生制冷剂的压力损失。第1连通管3的长度越长，第1连通管3中的制冷剂的压力损失越大，第1连通管3的内径越小，第1连通管3中的制冷剂的压力损失越大。在第1连通管3中的制冷剂的压力损失大的情况下，由于制冷剂在第1连通管3穿过，使得制冷剂的压力大幅降低，存在蒸发器14中的制冷剂的饱和温度低于用户欲在蒸发器14利用的蒸发温度(蒸发器14的利用蒸发温度)的担心(即，不可进行制冷循环装置的恰当的运转的担心)。In addition, when the refrigerant coming out of the main decompression device 13 passes through the first communication pipe 3, a pressure loss of the refrigerant occurs. The longer the length of the first communication pipe 3 , the greater the pressure loss of the refrigerant in the first communication pipe 3 , and the smaller the inner diameter of the first communication pipe 3 , the greater the pressure loss of the refrigerant in the first communication pipe 3 . When the pressure loss of the refrigerant in the first communication pipe 3 is large, since the refrigerant passes through the first communication pipe 3, the pressure of the refrigerant is greatly reduced, and the saturation temperature of the refrigerant in the evaporator 14 is low. The user is concerned about the evaporation temperature that the user intends to use in the evaporator 14 (the utilization evaporation temperature of the evaporator 14) (that is, the concern that the refrigeration cycle device cannot be properly operated).
为了防止这种情况，在基于本实施方式的制冷循环装置中，在蒸发器14中的制冷剂的饱和温度不低于蒸发器14的利用蒸发温度的范围，设定第1连通管3中的制冷剂的压力损失的大小。即，第1连通管3成为在蒸发器14中的制冷剂的饱和温度不低于蒸发器14的利用蒸发温度的范围产生制冷剂的压力损失的连通管。第1连通管3中的制冷剂的压力损失的大小通过调整第1连通管3的长度以及内径来设定。In order to prevent this situation, in the refrigeration cycle device based on this embodiment, the saturation temperature of the refrigerant in the evaporator 14 is not lower than the range of the evaporation temperature of the evaporator 14, and the temperature in the first communication pipe 3 is set The size of the pressure loss of the refrigerant. That is, the first communication pipe 3 serves as a communication pipe through which pressure loss of the refrigerant occurs in a range where the saturated temperature of the refrigerant in the evaporator 14 is not lower than the evaporation temperature of the evaporator 14 . The magnitude of the pressure loss of the refrigerant in the first communication pipe 3 is set by adjusting the length and inner diameter of the first communication pipe 3 .
通常，在蒸发器14利用的蒸发温度是-40℃～0℃。因此，若将蒸发器14中的制冷剂的压力保持为蒸发器14中的制冷剂的饱和温度不低于-40℃(利用蒸发温度)，则可进行制冷循环装置的恰当的运转。Usually, the evaporation temperature used in the evaporator 14 is -40°C to 0°C. Therefore, if the pressure of the refrigerant in the evaporator 14 is maintained so that the saturation temperature of the refrigerant in the evaporator 14 is not lower than -40° C. (using the evaporation temperature), proper operation of the refrigeration cycle apparatus can be performed.
图3是表示图1的第1连通管3中的制冷剂的压力损失和第1连通管3的内径的关系的图表。若设想例如被设置在超级市场等店铺的制冷循环装置，则第1连通管3的最大长度为100m左右。在图3中，表示第1连通管3的长度为100m时的第1连通管3的入口压力以及出口压力中的每一个。FIG. 3 is a graph showing the relationship between the pressure loss of the refrigerant in the first communication pipe 3 in FIG. 1 and the inner diameter of the first communication pipe 3 . Assuming, for example, a refrigeration cycle device installed in a store such as a supermarket, the maximum length of the first communication pipe 3 is about 100 m. In FIG. 3 , each of the inlet pressure and the outlet pressure of the first communication pipe 3 when the length of the first communication pipe 3 is 100 m is shown.
如图3所示，了解到第1连通管3的内径越小，第1连通管3的入口压力和出口压力的差越大，第1连通管3中的制冷剂的压力损失越大。在基于本实施方式的制冷循环装置中，若设想例如由主减压装置13将制冷剂的压力减压到4.15MPa(第1连通管3的设计压力)，则根据图3，用于将长度为100m的第1连通管3的出口压力保持在0.90MPa(相当于蒸气温度-40℃的制冷剂的压力)以上的第1连通管3的内径为10.3mm以上。As shown in FIG. 3 , it is understood that the smaller the inner diameter of the first communication pipe 3 is, the larger the difference between the inlet pressure and the outlet pressure of the first communication pipe 3 is, and the pressure loss of the refrigerant in the first communication pipe 3 is larger. In the refrigeration cycle device based on this embodiment, assuming, for example, that the pressure of the refrigerant is decompressed to 4.15 MPa (the design pressure of the first communication pipe 3 ) by the main decompression device 13 , according to FIG. 3 , the length The outlet pressure of the 100m-long first communication pipe 3 is maintained at 0.90 MPa (corresponding to the pressure of the refrigerant at vapor temperature -40°C) or higher. The inner diameter of the first communication pipe 3 is 10.3 mm or more.
图4是表示图1的第1连通管3中的制冷剂的压力损失和第1连通管3的长度的关系的图表。例如，若设想被设置在超级市场等店铺的图2所示那样的制冷循环装置，则第1连通管3的内径为12.7mm。在图4中，表示第1连通管3的内径为12.7mm时的第1连通管3的入口压力以及出口压力中的每一个。FIG. 4 is a graph showing the relationship between the pressure loss of the refrigerant in the first communication pipe 3 in FIG. 1 and the length of the first communication pipe 3 . For example, assuming a refrigeration cycle apparatus as shown in FIG. 2 installed in a store such as a supermarket, the inner diameter of the first communication pipe 3 is 12.7 mm. In FIG. 4 , each of the inlet pressure and the outlet pressure of the first communication pipe 3 when the inner diameter of the first communication pipe 3 is 12.7 mm is shown.
如图4所示，了解到第1连通管3的长度越长，第1连通管3的入口压力和出口压力的差越大，第1连通管3中的制冷剂的压力损失越大。在基于本实施方式的制冷循环装置中，例如，若设想由主减压装置13将制冷剂的压力减压到4.15MPa(第1连通管3的设计压力)，则根据图4，用于将内径为12.7mm的第1连通管3的出口压力保持在0.90MPa(相当于蒸发温度-40℃的制冷剂的压力)以上的第1连通管3的长度为142m以下。As shown in FIG. 4 , it is understood that the longer the length of the first communication pipe 3 is, the larger the difference between the inlet pressure and the outlet pressure of the first communication pipe 3 is, and the pressure loss of the refrigerant in the first communication pipe 3 is larger. In the refrigeration cycle device according to this embodiment, for example, assuming that the pressure of the refrigerant is decompressed to 4.15 MPa (the design pressure of the first communication pipe 3) by the main decompression device 13, according to FIG. The length of the first communication pipe 3 with an inner diameter of 12.7 mm to keep the outlet pressure at 0.90 MPa (corresponding to the pressure of refrigerant at an evaporation temperature of −40° C.) is 142 m or less.
在基于本实施方式的制冷循环装置中，第1连通管3的内径为10.3mm以上或第1连通管3的长度为142m以下。据此，抑制第1连通管3中的制冷剂的压力损失，可进行制冷循环装置的恰当的运转。第1连通管3的长度由于抑制了制冷剂的压力损失，所以，只要在0m以上即可。另外，第1连通管3的内径的上限是被收纳入配管设置空间的大小，或达到非相容的制冷机油可流动的程度的制冷剂流速的大小。In the refrigeration cycle apparatus according to this embodiment, the inner diameter of the first communication pipe 3 is 10.3 mm or more or the length of the first communication pipe 3 is 142 m or less. Thereby, the pressure loss of the refrigerant in the first communication pipe 3 is suppressed, and proper operation of the refrigeration cycle apparatus can be performed. The length of the first communication pipe 3 may be at least 0 m in order to suppress the pressure loss of the refrigerant. In addition, the upper limit of the inner diameter of the first communication pipe 3 is the size accommodated in the piping installation space, or the size of the flow rate of the refrigerant to such an extent that incompatible refrigerating machine oil can flow.
另外，在基于本实施方式的制冷循环装置中，因为由主减压装置13减压了的制冷剂在第1连通管3穿过，所以，第1连通管3中的制冷剂成为气液二相状态。在第1连通管3中，由于气液二相制冷剂的干度越低，制冷剂越接近液体单相，所以，制冷剂的压力损失变小。另一方面，在第1连通管3中，气液二相制冷剂的压力越降低，制冷剂的干度越增加。由于这样的情况，在该例中，为了使第1连通管3中的制冷剂的压力损失小，由主减压装置13调整制冷剂的减压幅度，以便在第1连通管3的设计压力以下的范围，尽量使第1连通管3中的制冷剂的压力高。即，在该例中，由主减压装置13将制冷剂减压，以便第1连通管3的入口压力成为第1连通管3的设计压力。In addition, in the refrigeration cycle device according to this embodiment, since the refrigerant decompressed by the main decompression device 13 passes through the first communication pipe 3, the refrigerant in the first communication pipe 3 becomes gas-liquid. phase state. In the first communication pipe 3, the lower the dryness of the gas-liquid two-phase refrigerant is, the closer the refrigerant is to the single-phase liquid, so the pressure loss of the refrigerant becomes smaller. On the other hand, in the first communication pipe 3 , the lower the pressure of the gas-liquid two-phase refrigerant, the higher the dryness of the refrigerant. Due to such a situation, in this example, in order to reduce the pressure loss of the refrigerant in the first communication pipe 3, the main decompression device 13 adjusts the decompression range of the refrigerant so that the design pressure of the first communication pipe 3 In the range below, the pressure of the refrigerant in the first communication pipe 3 is made as high as possible. That is, in this example, the refrigerant is decompressed by the main decompression device 13 so that the inlet pressure of the first communication pipe 3 becomes the design pressure of the first communication pipe 3 .
在这样的制冷循环装置中，因为通过主减压装置13对制冷剂的减压，能够使第1连通管3中的制冷剂的压力变低，所以，能够将第1连通管3的耐压性能设计得低。据此，能够将使用通常的制冷剂(例如，R410A等)的制冷循环装置的连通管作为使用高压制冷剂(例如，CO2等)的制冷循环装置的第1连通管3来应用。例如，在将使用通常的制冷剂的既有的制冷循环装置的连通管修改为使用高压制冷剂的制冷循环装置的情况下，能够不加改变地再次利用既有的制冷循环装置的连通管，能够谋求减轻制冷循环装置修改工程的劳力和时间。另外，即使在新设置使用高压制冷剂的制冷循环装置的情况下，因为通过第1连通管3内的压力的降低，能够使第1连通管3的壁厚变薄，所以，能够使第1连通管3的弯曲加工以及连接作业变得容易，能够减轻现场的制冷循环装置的设置作业的劳力和时间。In such a refrigeration cycle device, since the pressure of the refrigerant in the first communication pipe 3 can be lowered by decompression of the refrigerant by the main decompression device 13, the withstand pressure of the first communication pipe 3 can be lowered. Performance is designed to be low. Accordingly, the communication pipe of a refrigeration cycle device using a normal refrigerant (eg, R410A, etc.) can be applied as the first communication pipe 3 of a refrigeration cycle device using a high-pressure refrigerant (eg, CO2 , etc.). For example, when the communication pipe of the existing refrigerating cycle device using a normal refrigerant is changed to a refrigerating cycle device using a high-pressure refrigerant, the communication pipe of the existing refrigerating cycle device can be reused without change, It is possible to reduce labor and time required for modification work of the refrigeration cycle device. In addition, even in the case of newly installing a refrigeration cycle device using a high-pressure refrigerant, since the pressure in the first communication pipe 3 is reduced, the wall thickness of the first communication pipe 3 can be reduced, so the first communication pipe 3 can be made thinner. Bending and connecting operations of the communication pipe 3 are facilitated, and labor and time for installation operations of the refrigeration cycle device on site can be reduced.
另外，因为在蒸发器14中的制冷剂的饱和温度不低于蒸发器14的利用蒸发温度的范围内，抑制了第1连通管3中的制冷剂的压力损失，所以，能够防止在蒸发器14的利用蒸发温度没有恰当地进行制冷剂的蒸发的情况，能够避免制冷循环装置的恰当运转范围的缩小。In addition, since the saturation temperature of the refrigerant in the evaporator 14 is not lower than the utilization evaporation temperature of the evaporator 14, the pressure loss of the refrigerant in the first communication pipe 3 is suppressed, so that the evaporator can be prevented from When the utilization evaporation temperature of 14 does not properly evaporate the refrigerant, it is possible to avoid narrowing of the proper operating range of the refrigeration cycle apparatus.
即，在基于本实施方式的制冷循环装置中，能够同时满足减轻设置作业或修改作业的劳力和时间以及避免恰当运转范围的缩小。That is, in the refrigeration cycle apparatus according to the present embodiment, it is possible to simultaneously reduce labor and time of installation work or modification work and avoid narrowing of the proper operating range.
另外，因为第1连通管3的内径在10.3mm以上或第1连通管3的长度在142m以下，所以，能够以简单的结构容易地抑制第1连通管3中的制冷剂的压力损失。In addition, since the inner diameter of the first communication pipe 3 is 10.3 mm or more or the length of the first communication pipe 3 is 142 m or less, the pressure loss of the refrigerant in the first communication pipe 3 can be easily suppressed with a simple structure.
另外，在所述的例子中，制冷循环的高压侧的压力在制冷剂的临界压力以下，但也可以在制冷循环的高压侧的压力比制冷剂的临界压力高的超临界区域进行运转。Also, in the above example, the pressure on the high pressure side of the refrigeration cycle is below the critical pressure of the refrigerant, but operation may be performed in a supercritical region where the pressure on the high pressure side of the refrigeration cycle is higher than the critical pressure of the refrigerant.
实施方式2.Implementation mode 2.
在实施方式1中，不加改变地将来自第1连通管3的制冷剂向蒸发器14输送，但是，也可以在第1连通管3和蒸发器14之间设置流量控制部21，由流量控制部21调整了来自第1连通管3的制冷剂的流量后，将制冷剂向蒸发器14输送，据此，控制从蒸发器14的出口出来的制冷剂的过热度。In Embodiment 1, the refrigerant from the first communication pipe 3 is sent to the evaporator 14 without any change, however, a flow rate control unit 21 may be provided between the first communication pipe 3 and the evaporator 14 to determine the flow rate The controller 21 sends the refrigerant to the evaporator 14 after adjusting the flow rate of the refrigerant from the first communication pipe 3 , thereby controlling the degree of superheat of the refrigerant exiting the outlet of the evaporator 14 .
即，图5是表示基于本发明的实施方式2的制冷循环装置的结构图。冷却单元2还具有流量控制部(冷却单元侧减压装置)21。流量控制部21被设置于连接第1连通管3和蒸发器14的连接管。另外，流量控制部21将来自第1连通管3的制冷剂减压，并向蒸发器14输送。在该例中，流量控制部21为可调整制冷剂的流量的电动膨胀阀。流量控制部21由未图示出的控制部控制。蒸发器14使由流量控制部21减压了的制冷剂蒸发。That is, FIG. 5 is a configuration diagram showing a refrigeration cycle apparatus according to Embodiment 2 of the present invention. The cooling unit 2 further includes a flow rate control unit (cooling unit side decompression device) 21 . The flow control unit 21 is provided in a connection pipe connecting the first communication pipe 3 and the evaporator 14 . In addition, the flow rate control unit 21 decompresses the refrigerant from the first communication pipe 3 and sends it to the evaporator 14 . In this example, the flow rate control unit 21 is an electric expansion valve capable of adjusting the flow rate of the refrigerant. The flow control unit 21 is controlled by a control unit not shown. The evaporator 14 evaporates the refrigerant depressurized by the flow rate control unit 21 .
通过由流量控制部21对制冷剂的流量的调整来控制蒸发器14的出口的制冷剂的过热度。例如，在制冷剂由主减压装置13减压，第1连通管3中的制冷剂的压力成为4.15MPa(第1连通管3的设计压力)后，由流量控制部21调整制冷剂的流量，从蒸发器14的出口出来的制冷剂的过热度为5℃～10℃。其它的结构与实施方式1相同。The degree of superheat of the refrigerant at the outlet of the evaporator 14 is controlled by adjusting the flow rate of the refrigerant by the flow control unit 21 . For example, after the refrigerant is decompressed by the main decompression device 13 and the pressure of the refrigerant in the first communication pipe 3 reaches 4.15 MPa (the design pressure of the first communication pipe 3 ), the flow rate of the refrigerant is adjusted by the flow control unit 21 , the degree of superheat of the refrigerant coming out of the outlet of the evaporator 14 is 5° C. to 10° C. Other configurations are the same as those in Embodiment 1.
在这样的制冷循环装置中，因为使冷却单元2包括将来自第1连通管3的制冷剂减压并向蒸发器14输送的流量控制部21，所以，能够更可靠地控制第1连通管3中的制冷剂的压力以及蒸发器14中的蒸发温度中的每一个。据此，能够一面更可靠地抑制第1连通管3中的制冷剂的压力损失的增大，一面在蒸发器14中使制冷剂充分地蒸发，能够谋求提高蒸发器14中的冷却性能。因此，能够更可靠地进行从蒸发器14返回压缩机11的制冷剂的气体化，能够避免因液体状的制冷剂返回压缩机11造成的压缩机11的故障等。In such a refrigeration cycle device, since the cooling unit 2 includes the flow control unit 21 that depressurizes the refrigerant from the first communication pipe 3 and sends it to the evaporator 14, the first communication pipe 3 can be more reliably controlled. Each of the pressure of the refrigerant in and the evaporation temperature in the evaporator 14. This makes it possible to sufficiently evaporate the refrigerant in the evaporator 14 while more reliably suppressing an increase in the pressure loss of the refrigerant in the first communication pipe 3 , thereby improving the cooling performance in the evaporator 14 . Therefore, the gasification of the refrigerant returned from the evaporator 14 to the compressor 11 can be performed more reliably, and failure of the compressor 11 due to the liquid refrigerant returning to the compressor 11 can be avoided.
这里，由冷却单元2的流量控制部21对制冷剂的减压调整幅度在约0.3MPa以下。因此，能够使第1连通管3中的制冷剂的压力的最大值成为比蒸发压力高0.3MPa的压力。因此，能够在设计压力的范围内提高第1连通管3中的制冷剂的压力，能够一面谋求第1连通管3的薄壁化，一面抑制第1连通管3的压力损失的增大。另外，若第1连通管3中的制冷剂的压力的上限为设计压力4.15MPa，则蒸发压力的上限成为3.85MPa，与3.85MPa的蒸发压力对应的蒸发温度成为5℃。通常，因为制冷循环装置的蒸发温度是-40℃～0℃，所以，能够将蒸发器14中的制冷剂的饱和温度确保在利用蒸发温度以上，能够避免制冷循环装置的恰当运转范围的缩小。Here, the adjustment range of depressurization of the refrigerant by the flow control unit 21 of the cooling unit 2 is about 0.3 MPa or less. Therefore, the maximum value of the pressure of the refrigerant in the first communication pipe 3 can be set to a pressure 0.3 MPa higher than the evaporation pressure. Therefore, the pressure of the refrigerant in the first communication pipe 3 can be increased within the design pressure range, and the increase in the pressure loss of the first communication pipe 3 can be suppressed while reducing the thickness of the first communication pipe 3 . Also, if the upper limit of the pressure of the refrigerant in the first communication pipe 3 is the design pressure of 4.15 MPa, the upper limit of the evaporation pressure is 3.85 MPa, and the evaporation temperature corresponding to the evaporation pressure of 3.85 MPa is 5°C. Usually, since the evaporation temperature of the refrigeration cycle device is -40°C to 0°C, the saturation temperature of the refrigerant in the evaporator 14 can be ensured to be above the utilization evaporation temperature, and the reduction of the proper operating range of the refrigeration cycle device can be avoided.
另外，在实施方式2中，也可以在共用的第1连通管3并联连接多个冷却单元2，从共用的第1连通管3向各冷却单元2输送制冷剂。在这种情况下，由热源单元1的主减压装置13进行制冷剂的主要的减压，使第1连通管3中的制冷剂的压力成为设计压力(4.15MPa)以下。另外，在这种情况下，制冷剂流量的向各蒸发器14的分配与各冷却单元2的制冷能力相应地由各流量控制部21进行。即，制冷剂的去向各蒸发器14的流量的调整由各流量控制部21进行，以便使各蒸发器14中的蒸发温度成为利用温度。这样一来，能够一面更可靠地抑制第1连通管3中的制冷剂的压力损失的增大，一面在各冷却单元2中，使制冷剂充分地蒸发，能够谋求提高各冷却单元中的冷却性能。In addition, in Embodiment 2, a plurality of cooling units 2 may be connected in parallel to the common first communication pipe 3 , and the refrigerant may be sent from the common first communication pipe 3 to each cooling unit 2 . In this case, the main decompression of the refrigerant is performed by the main decompression device 13 of the heat source unit 1, so that the pressure of the refrigerant in the first communication pipe 3 becomes lower than the design pressure (4.15 MPa). In addition, in this case, distribution of the refrigerant flow rate to each evaporator 14 is performed by each flow rate control unit 21 according to the cooling capacity of each cooling unit 2 . That is, the flow rate of the refrigerant to each evaporator 14 is adjusted by each flow rate control unit 21 so that the evaporation temperature in each evaporator 14 becomes the utilization temperature. In this way, the increase in the pressure loss of the refrigerant in the first communication pipe 3 can be more reliably suppressed, and at the same time, the refrigerant can be sufficiently evaporated in each cooling unit 2, and the cooling performance in each cooling unit can be improved. performance.
实施方式3.Implementation mode 3.
图6是表示基于本发明的实施方式3的制冷循环装置的结构图。热源单元1还具有内部热交换器31。内部热交换器31在从第2连通管4向压缩机11输送的制冷剂和从冷凝器12向主减压装置13输送的制冷剂之间进行热交换。即，内部热交换器31在向压缩机11吸入的气体状的制冷剂和从冷凝器12的出口出来的液体状的制冷剂之间进行热交换。在内部热交换器31中，由从冷凝器12向主减压装置13输送的制冷剂向从第2连通管4向压缩机11输送的制冷剂释放热。其它的结构与实施方式2相同。Fig. 6 is a configuration diagram showing a refrigeration cycle apparatus according to Embodiment 3 of the present invention. The heat source unit 1 also has an internal heat exchanger 31 . The internal heat exchanger 31 performs heat exchange between the refrigerant sent from the second communication pipe 4 to the compressor 11 and the refrigerant sent from the condenser 12 to the main decompression device 13 . That is, the internal heat exchanger 31 performs heat exchange between the gaseous refrigerant sucked into the compressor 11 and the liquid refrigerant discharged from the outlet of the condenser 12 . In the internal heat exchanger 31 , heat is released from the refrigerant sent from the condenser 12 to the main decompression device 13 to the refrigerant sent from the second communication pipe 4 to the compressor 11 . Other structures are the same as those in Embodiment 2.
在这样的制冷循环装置中，因为热源单元1包括在从第2连通管4向压缩机11输送的制冷剂和从冷凝器12向主减压装置13输送的制冷剂之间进行热交换的内部热交换器31，所以，能够使进入主减压装置13的液体状的制冷剂的过冷却度增大，能够使第1连通管3中的制冷剂的干度降低。据此，能够抑制第1连通管3中的制冷剂的压力损失，能够确保第1连通管3的出口压力，以使蒸发器14中的制冷剂的饱和温度不低于蒸发器14的利用蒸发温度。据此，能够更可靠地进行制冷循环装置的恰当的运转。In such a refrigeration cycle device, since the heat source unit 1 includes an interior for exchanging heat between the refrigerant sent from the second communication pipe 4 to the compressor 11 and the refrigerant sent from the condenser 12 to the main decompression device 13 Therefore, the heat exchanger 31 can increase the subcooling degree of the liquid refrigerant entering the main decompression device 13, and can reduce the dryness of the refrigerant in the first communication pipe 3. Accordingly, the pressure loss of the refrigerant in the first communication pipe 3 can be suppressed, and the outlet pressure of the first communication pipe 3 can be ensured so that the saturation temperature of the refrigerant in the evaporator 14 is not lower than that of the evaporator 14 using evaporation. temperature. Accordingly, proper operation of the refrigeration cycle apparatus can be performed more reliably.
另外，在实施方式3中，内部热交换器31被应用于实施方式2的热源单元1，但是，也可以将内部热交换器31应用于实施方式1的热源单元1。In addition, in the third embodiment, the internal heat exchanger 31 is applied to the heat source unit 1 of the second embodiment, but the internal heat exchanger 31 may be applied to the heat source unit 1 of the first embodiment.
实施方式4.Implementation mode 4.
图7是表示基于本发明的实施方式4的制冷循环装置的结构图。热源单元1还具有旁通回路41和旁通热交换器42。Fig. 7 is a configuration diagram showing a refrigeration cycle apparatus according to Embodiment 4 of the present invention. The heat source unit 1 also has a bypass circuit 41 and a bypass heat exchanger 42 .
旁通回路41具有将从冷凝器12去向主减压装置13的制冷剂的一部分减压的旁通减压装置43和将由旁通减压装置43减压了的制冷剂向压缩机11的吸入口输送的旁通管44。在该例中，旁通减压装置43为可调整制冷剂的流量的电动膨胀阀。The bypass circuit 41 has a bypass depressurization device 43 for decompressing a part of the refrigerant going from the condenser 12 to the main decompression device 13 , and suction of the refrigerant decompressed by the bypass decompression device 43 to the compressor 11 . Port delivery bypass pipe 44. In this example, the bypass decompression device 43 is an electric expansion valve capable of adjusting the flow rate of the refrigerant.
旁通热交换器42在从冷凝器12向主减压装置13输送的制冷剂和由旁通减压装置43减压了的制冷剂之间进行热交换。即，旁通热交换器42在从冷凝器12的出口出来的液体状的制冷剂和从旁通减压装置43出来的气液二相状态的制冷剂之间进行热交换。在旁通热交换器42中，由从冷凝器12向主减压装置13输送的制冷剂向由旁通减压装置43减压了的制冷剂释放热。其它的结构与实施方式2相同。The bypass heat exchanger 42 exchanges heat between the refrigerant sent from the condenser 12 to the main decompression device 13 and the refrigerant depressurized by the bypass decompression device 43 . That is, the bypass heat exchanger 42 performs heat exchange between the liquid refrigerant discharged from the outlet of the condenser 12 and the gas-liquid two-phase refrigerant discharged from the bypass decompression device 43 . In the bypass heat exchanger 42 , heat is released from the refrigerant sent from the condenser 12 to the main decompression device 13 to the refrigerant depressurized by the bypass decompression device 43 . Other structures are the same as those in Embodiment 2.
在这样的制冷循环装置中，因为热源单元1包括在从冷凝器12向主减压装置13输送的制冷剂和由旁通减压装置43减压了的制冷剂之间进行热交换的旁通热交换器42，所以，能够使进入主减压装置13的液体状的制冷剂的过冷却度增大，能够使第1连通管3中的制冷剂的干度降低。据此，与实施方式3同样，能够抑制第1连通管3中的制冷剂的压力损失。另外，因为通过由旁通回路41将从冷凝器12出来的制冷剂的一部分向压缩机11输送，第1连通管3中的制冷剂的流量降低，所以，能够进一步抑制第1连通管3中的制冷剂的压力损失。因此，能够更可靠地进行制冷循环装置的恰当的运转。In such a refrigeration cycle device, since the heat source unit 1 includes a bypass for heat exchange between the refrigerant sent from the condenser 12 to the main decompression device 13 and the refrigerant decompressed by the bypass decompression device 43 Therefore, the heat exchanger 42 can increase the subcooling degree of the liquid refrigerant entering the main decompression device 13, and can reduce the dryness of the refrigerant in the first communication pipe 3. Accordingly, similarly to Embodiment 3, the pressure loss of the refrigerant in the first communication pipe 3 can be suppressed. In addition, since the flow rate of the refrigerant in the first communication pipe 3 is reduced by sending a part of the refrigerant coming out of the condenser 12 to the compressor 11 through the bypass circuit 41, the flow rate of the refrigerant in the first communication pipe 3 can be further suppressed. pressure loss of the refrigerant. Therefore, proper operation of the refrigeration cycle apparatus can be performed more reliably.
另外，在实施方式4中，旁通回路41以及旁通热交换器42被应用于实施方式2的热源单元1，但是，也可以将旁通回路41以及旁通热交换器42应用于实施方式1的热源单元1。In addition, in Embodiment 4, the bypass circuit 41 and the bypass heat exchanger 42 are applied to the heat source unit 1 of Embodiment 2, but the bypass circuit 41 and the bypass heat exchanger 42 may be applied to the embodiment. 1 heat source unit 1.
另外，也可以将基于实施方式3的内部热交换器31应用于基于实施方式4的热源单元1。即，可以将基于实施方式3的内部热交换器31和基于实施方式4的旁通回路41以及旁通热交换器42均应用于基于实施方式1或2的热源单元1。In addition, the internal heat exchanger 31 according to the third embodiment may also be applied to the heat source unit 1 according to the fourth embodiment. That is, both the internal heat exchanger 31 in Embodiment 3 and the bypass circuit 41 and bypass heat exchanger 42 in Embodiment 4 can be applied to the heat source unit 1 in Embodiment 1 or 2.
实施方式5.Implementation mode 5.
图8是表示基于本发明的实施方式5的制冷循环装置的结构图。热源单元1还具有受液器51。受液器51储存从冷凝器12出来的液体状的制冷剂。据此，受液器51的出口成为制冷剂的饱和液体状态。向主减压装置13输送储存于受液器51的液体状的制冷剂。其它的结构与实施方式2相同。Fig. 8 is a configuration diagram showing a refrigeration cycle apparatus according to Embodiment 5 of the present invention. The heat source unit 1 also has a liquid receiver 51 . The liquid receiver 51 stores the liquid refrigerant discharged from the condenser 12 . Accordingly, the outlet of the liquid receiver 51 becomes a saturated liquid state of the refrigerant. The liquid refrigerant stored in the liquid receiver 51 is sent to the main decompression device 13 . Other structures are the same as those in Embodiment 2.
在这样的制冷循环装置中，因为从冷凝器12出来的液体状的制冷剂被储存于受液器51，被储存于受液器51的液体状的制冷剂向主减压装置13输送，所以，能够防止向主减压装置13输送的制冷剂成为气液二相状态。据此，能够使第1连通管3中的制冷剂的干度降低，能够抑制第1连通管3中的制冷剂的压力损失的增大。据此，能够确保第1连通管3的出口压力，以使蒸发器14中的制冷剂的饱和温度不低于蒸发器14的利用蒸发温度，能够更可靠地进行制冷循环装置的恰当的运转。In such a refrigeration cycle device, since the liquid refrigerant coming out of the condenser 12 is stored in the liquid receiver 51, and the liquid refrigerant stored in the liquid receiver 51 is sent to the main decompression device 13, so Therefore, it is possible to prevent the refrigerant sent to the main decompression device 13 from being in a gas-liquid two-phase state. Accordingly, the dryness of the refrigerant in the first communication pipe 3 can be reduced, and an increase in the pressure loss of the refrigerant in the first communication pipe 3 can be suppressed. Accordingly, the outlet pressure of the first communication pipe 3 can be ensured so that the saturation temperature of the refrigerant in the evaporator 14 does not fall below the utilization evaporation temperature of the evaporator 14, and proper operation of the refrigeration cycle apparatus can be performed more reliably.
另外，例如在设置多个冷却单元2的情况下，因各冷却单元2的运转台数的切换而产生大的负荷变动。此时，若没有受液器51，则冷凝器12的制冷剂不足，冷凝器12的出口的制冷剂成为气液二相状态，制冷循环装置的运转效率会降低。在实施方式5中，因为从冷凝器12出来的液体状的制冷剂被储存于受液器51，所以，能够避免冷凝器12的制冷剂不足，能够避免制冷循环装置的运转效率的降低。In addition, for example, when a plurality of cooling units 2 are installed, a large load fluctuation occurs due to switching of the number of operating units of each cooling unit 2 . At this time, if there is no liquid receiver 51, the refrigerant in the condenser 12 will be insufficient, and the refrigerant at the outlet of the condenser 12 will be in a gas-liquid two-phase state, thereby reducing the operating efficiency of the refrigeration cycle device. In Embodiment 5, since the liquid refrigerant coming out of the condenser 12 is stored in the liquid receiver 51 , it is possible to avoid shortage of refrigerant in the condenser 12 and to avoid a decrease in the operating efficiency of the refrigeration cycle apparatus.
上面，对本发明的具体的实施方式进行了说明，但是，本发明并不限定于各所述实施方式，能够在本发明的范围内进行各种变更来实施。例如，作为第1连通管3的设计压力并不限于4.15MPa，也可以将使用了R404A制冷剂的制冷循环装置的高压侧的设计压力(即，2.94MPa)作为第1连通管3的设计压力。在这种情况下，如图9以及图10所示，通过使第1连通管3的内径在11.0mm以下或使第1连通管3的长度在275m以下，在蒸发器14中的制冷剂的饱和温度不低于蒸发器14的利用蒸发温度的范围，设定第1连通管3中的制冷剂的压力损失的大小。As mentioned above, although the specific embodiment of this invention was demonstrated, this invention is not limited to each said embodiment, Various modifications can be implemented within the scope of this invention. For example, the design pressure of the first communication pipe 3 is not limited to 4.15 MPa, and the design pressure of the high-pressure side of a refrigeration cycle device using R404A refrigerant (ie, 2.94 MPa) may be used as the design pressure of the first communication pipe 3 . In this case, as shown in FIGS. 9 and 10 , by setting the inner diameter of the first communication pipe 3 to 11.0 mm or less or the length of the first communication pipe 3 to 275 m or less, the refrigerant in the evaporator 14 The saturation temperature is not lower than the range in which the evaporation temperature of the evaporator 14 is used, and the magnitude of the pressure loss of the refrigerant in the first communication pipe 3 is set.
另外，在各所述实施方式中，也可以将检测制冷剂的温度或压力的第1检测器设置在第1连通管3或蒸发器14，由控制部根据从第1检测器的检测结果求出的第1连通管3中的制冷剂的压力，控制主减压装置13。在这种情况下，例如，能够将检测制冷剂的压力的压力传感器(第1检测器)设置在第1连通管3，根据来自压力传感器的信息，求出第1连通管3中的制冷剂的压力，或将检测制冷剂的温度的温度传感器(第1检测器)设置在蒸发器14，从蒸发器14的基于温度传感器的温度信息，求出第1连通管3中的制冷剂的压力。另外，例如，还能够将检测制冷剂的温度的温度传感器(第1检测器)设置在第1连通管3，从第1连通管3的基于温度传感器的温度信息，求出第1连通管3中的制冷剂的压力。这样一来，能够更正确地进行第1连通管3中的制冷剂的压力的调整。In addition, in each of the above-described embodiments, a first detector for detecting the temperature or pressure of the refrigerant may be installed on the first communication pipe 3 or the evaporator 14, and the control unit may calculate The pressure of the refrigerant in the first communicating pipe 3 is controlled to control the main decompression device 13 . In this case, for example, a pressure sensor (first detector) that detects the pressure of the refrigerant can be installed on the first communication pipe 3, and the pressure of the refrigerant in the first communication pipe 3 can be obtained based on information from the pressure sensor. or install a temperature sensor (first detector) for detecting the temperature of the refrigerant in the evaporator 14, and obtain the pressure of the refrigerant in the first communication pipe 3 from the temperature information of the evaporator 14 based on the temperature sensor . In addition, for example, it is also possible to install a temperature sensor (first detector) for detecting the temperature of the refrigerant on the first communication pipe 3, and obtain the temperature information of the first communication pipe 3 from the temperature information of the temperature sensor of the first communication pipe 3. The pressure of the refrigerant in it. In this way, it is possible to more accurately adjust the pressure of the refrigerant in the first communication pipe 3 .
另外，在实施方式2～5中，也可以将检测制冷剂的温度或压力的第2检测器(压力传感器或温度传感器)设置在蒸发器14，根据从第2检测器的检测结果求出的蒸发器14的出口处的制冷剂的压力，由控制部控制流量控制部21。这样一来，能够更正确地进行蒸发器14的出口处的制冷剂的过热度的调整。In addition, in Embodiments 2 to 5, a second detector (a pressure sensor or a temperature sensor) for detecting the temperature or pressure of the refrigerant may be installed in the evaporator 14, and the value obtained from the detection result of the second detector may be The pressure of the refrigerant at the outlet of the evaporator 14 is controlled by the flow control unit 21 by the control unit. In this way, it is possible to more accurately adjust the degree of superheat of the refrigerant at the outlet of the evaporator 14 .
另外，在各所述实施方式中，冷却单元2的数量并非限于1个，也可以使冷却单元2的数量为多个。再有，也可以使热源单元1的数量为多个。在使热源单元1的数量为多个的情况下，来自各热源单元1的主减压装置13的每一个的制冷剂由共用的第1连通管3导通，向冷却单元2输送。In addition, in each of the above-described embodiments, the number of cooling units 2 is not limited to one, and the number of cooling units 2 may be plural. In addition, the number of heat source units 1 may be plural. When the number of heat source units 1 is multiple, the refrigerant from each main decompression device 13 of each heat source unit 1 is conducted through the common first communication pipe 3 and sent to the cooling unit 2 .
另外，在各所述实施方式中，作为制冷循环装置的制冷剂，使用作为高压制冷剂的CO2，但是，也可以将制冷循环的高压侧在超临界区域运转的CO2以外的制冷剂(例如，R32等的氟利昂制冷剂、含有CO2以及R32的任意一种的混合制冷剂、乙烯、乙烷、氧化氮等)作为制冷循环装置的制冷剂来使用。In addition, in each of the above-described embodiments, CO2 , which is a high-pressure refrigerant, is used as the refrigerant of the refrigeration cycle apparatus. However, a refrigerant other than CO2 ( For example, Freon refrigerants such as R32, mixed refrigerants containing either of CO2 and R32, ethylene, ethane, nitrogen oxide, etc.) are used as refrigerants of refrigeration cycle devices.
另外，基于各所述实施方式的制冷循环装置除应用于被设置在店铺的冷却用陈列柜以外，能够应用于各种冷却装置、冷藏装置等。In addition, the refrigeration cycle apparatus based on each said embodiment can be applied to various cooling apparatuses, refrigerators, etc. besides the cooling showcase installed in a shop.
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2013/079147WO2015063838A1 (en) | 2013-10-28 | 2013-10-28 | Refrigeration cycle device |
| Publication Number | Publication Date |
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| CN105683681Atrue CN105683681A (en) | 2016-06-15 |
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380080566.3APendingCN105683681A (en) | 2013-10-28 | 2013-10-28 | Refrigeration cycle device |
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| JP (1) | JPWO2015063838A1 (en) |
| CN (1) | CN105683681A (en) |
| GB (1) | GB2534510B (en) |
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