Refrigeration Cycle Equipment

Abstract

To provide a refrigeration cycle apparatus capable of improving the lubricity in the refrigeration cycle apparatus in performing a refrigeration cycle using a refrigerant having a sufficiently small GWP.SOLUTION: A refrigeration cycle apparatus (1) includes a refrigerant circuit (10) and a prescribed small-GWP refrigerant enclosed in the refrigerant circuit (10). The refrigerant circuit includes a compressor (21), a condenser (23), a decompressing unit (24), and an evaporator (31).SELECTED DRAWING: Figure 3A

Description

[Technical Field]

[0001] The present disclosure relates to a refrigeration cycle device. [Background technology]

[0002] Conventionally, R410A and R404A have been widely used as refrigerants in heat cycle systems such as air conditioners. R410A is a two-component refrigerant mixture of (CH2F2; HFC-32 or R32) and pentafluoroethane (C2HF5; HFC-125 or R125), and is a pseudo-azeotropic composition. R404A is a three-component refrigerant mixture of R125, R134a, and R143a, and is a pseudo-azeotropic composition. In addition, the single refrigerant R134a is also widely used as a refrigerant.

[0003] However, the global warming potential (GWP) of R410A is 2088, that of R404A is 3920, and that of R134a is 1430. In recent years, due to growing concerns about global warming, there has been a trend toward using refrigerants with lower GWPs.

[0004] For example, Patent Document 1 (WO 2015 / 141678) proposes a low-GWP refrigerant mixture that can replace R410A. Patent Document 2 (JP 2018-184597 A) proposes various low-GWP refrigerant mixtures that can replace R404A. Patent Document 3 (WO 2005 / 105947 A) proposes a low-GWP refrigerant mixture that can replace R134a. Summary of the Invention

[0005] (1) Group 1 When a refrigeration cycle is performed using a refrigerant with a sufficiently small GWP, improving the lubrication within the refrigeration cycle device has not been studied up to now.

[0006] The present disclosure has been made in consideration of the above points, and aims to provide a refrigeration cycle device that can improve lubrication within the refrigeration cycle device when a refrigeration cycle is performed using a refrigerant with a sufficiently low GWP.

[0007] A refrigeration cycle device according to a first aspect of the first group includes a working fluid for a refrigerating machine, the working fluid including a refrigerant composition containing a refrigerant, the refrigerant being a first refrigerant X, a second refrigerant Y, a third refrigerant A, a fourth refrigerant B, a fifth refrigerant C, a sixth refrigerant D, or a seventh refrigerant E, as described below.

[0008] This refrigeration cycle device contains a refrigerant with a sufficiently low GWP and a refrigerating machine oil, which allows for improved lubrication within the refrigeration cycle device when the refrigerant composition is used for the refrigeration cycle. Furthermore, this refrigeration cycle device can also provide improved lubrication within the refrigeration cycle device when using a refrigerant that has the same refrigeration capacity (also referred to as cooling capacity or capacity) and coefficient of performance (COP) as R410A.

[0009] A refrigeration cycle apparatus according to a second aspect of the first group is the refrigeration cycle apparatus according to the first aspect, wherein the kinetic viscosity of the refrigerating machine oil at 40°C is 1 mm 2 / s or more 750mm 2 / s or less.

[0010] A refrigeration cycle apparatus according to a third aspect of the first group is the refrigeration cycle apparatus according to the first aspect or the second aspect of the first group, wherein the kinetic viscosity of the refrigerating machine oil at 100°C is 1 mm 2 / s or more 100mm 2 / s or less.

[0011] A refrigeration cycle apparatus according to a fourth aspect of the first group is the refrigeration cycle apparatus according to any one of the first aspect to the third aspect of the first group, wherein the volume resistivity of the refrigerating machine oil at 25°C is 1.0×10 12 Ω·cm or more.

[0012] A refrigeration cycle apparatus according to a fifth aspect of the first group is the refrigeration cycle apparatus according to any one of the first aspect to the fourth aspect of the first group, in which the acid value of the refrigeration oil is 0.1 mgKOH / g or less.

[0013] A refrigeration cycle apparatus according to a sixth aspect of the first group is the refrigeration cycle apparatus according to any one of the first aspect to the fifth aspect of the first group, wherein the ash content of the refrigeration oil is 100 ppm or less.

[0014] A refrigeration cycle apparatus according to a seventh aspect of the first group is the refrigeration cycle apparatus according to any one of the first aspect to the sixth aspect of the first group, wherein the aniline point of the refrigerating machine oil is −100° C. or higher and 0° C. or lower.

[0015] A refrigeration cycle apparatus according to an eighth aspect of the first group is the refrigeration cycle apparatus according to any one of the first aspect to the seventh aspect of the first group, and includes a refrigerant circuit. The refrigerant circuit is configured by connecting a compressor, a condenser, a pressure reducing section, and an evaporator with refrigerant piping. A working fluid for a refrigerating machine circulates inside the refrigerant circuit.

[0016] A refrigeration cycle device according to a ninth aspect of the first group is a refrigeration cycle device according to any one of the first aspect to the eighth aspect of the first group, in which the blending ratio of refrigerant oil in the working fluid for the refrigeration machine is 5 mass% or more and 60 mass% or less.

[0017] A refrigeration cycle apparatus according to a tenth aspect of the first group is the refrigeration cycle apparatus according to any one of the first aspect to the ninth aspect of the first group, wherein the refrigeration oil contains at least one additive selected from an acid scavenger, an extreme pressure agent, an antioxidant, an antifoaming agent, an oiliness agent, a metal deactivator, an antiwear agent, and a compatibilizer, and the proportion of the additive to the mass of the refrigeration oil containing the additive is 5 mass% or less.

[0018] (2) Group 2 When a refrigeration cycle is performed using a refrigerant with a sufficiently small GWP, improving the lubrication within the refrigeration cycle device has not been studied up to now.

[0019] The present disclosure has been made in consideration of the above-mentioned points, and aims to provide a refrigerating machine oil for a refrigerant or a refrigerant composition that can improve lubrication when a refrigeration cycle is performed using a refrigerant with a sufficiently low GWP, a method for using the refrigerating machine oil, and use of the refrigerating machine oil.

[0020] A refrigerating machine oil for a refrigerant composition according to a first aspect of the second group is a refrigerating machine oil for a refrigerant composition containing a refrigerant, and the refrigerant includes any one of refrigerant X, refrigerant Y, and refrigerants A to E shown in "(26) Details of refrigerants in each of the above groups" described below.

[0021] A refrigerating machine oil for a refrigerant composition according to a second aspect of the second group is the refrigerating machine oil for a refrigerant composition according to the first aspect of the second group, wherein the kinetic viscosity of the refrigerating machine oil at 40°C is 1 mm 2 / s or more 750mm 2 / s or less.

[0022] A refrigerating machine oil for a refrigerant composition according to a third aspect of the second group is a refrigerating machine oil for a refrigerant composition according to the first aspect or the second aspect of the second group, wherein the kinetic viscosity of the refrigerating machine oil at 100°C is 1 mm 2 / s or more 100mm 2 / s or less.

[0023] A refrigerating machine oil for a refrigerant composition according to a fourth aspect of the second group is a refrigerating machine oil for a refrigerant composition according to any one of the first aspect to the third aspect of the second group, wherein the volume resistivity of the refrigerating machine oil at 25°C is 1.0 × 10 12 Ω·cm or more.

[0024] A refrigerating machine oil for a refrigerant composition according to a fifth aspect of the second group is a refrigerating machine oil for a refrigerant composition according to any one of the first aspect to the fourth aspect of the second group, wherein the acid value of the refrigerating machine oil is 0.1 mgKOH / g or less.

[0025] A refrigerating machine oil for a refrigerant composition according to a sixth aspect of the second group is a refrigerating machine oil for a refrigerant composition according to any one of the first aspect to the fifth aspect of the second group, wherein the ash content of the refrigerating machine oil is 100 ppm or less.

[0026] A refrigerating machine oil for a refrigerant composition according to a seventh aspect of the second group is a refrigerating machine oil for a refrigerant composition according to any one of the first aspect to the sixth aspect of the second group, wherein the aniline point of the refrigerating machine oil is −100° C. or higher and 0° C. or lower.

[0027] A method of using a refrigerating machine oil according to an eighth aspect of the second group is a method of using a refrigerating machine oil together with a refrigerant composition containing a refrigerant, wherein the refrigerant includes any of the refrigerants shown in (26) below.

[0028] According to the method for using this refrigeration oil, it is possible to improve the lubrication when a refrigeration cycle is carried out using a refrigerant with a sufficiently low GWP or a refrigerant composition containing such a refrigerant.

[0029] A method of using a refrigerating machine oil according to a ninth aspect of the second group is the method of using a refrigerating machine oil according to the eighth aspect of the second group, wherein the kinetic viscosity of the refrigerating machine oil at 40°C is 1 mm 2 / s or more 750mm 2 / s or less.

[0030] A method of using a refrigerating machine oil according to a tenth aspect of the second group is the method of using a refrigerating machine oil according to the eighth or ninth aspect of the second group, wherein the kinetic viscosity of the refrigerating machine oil at 100°C is 1 mm 2 / s or more 100mm 2 / s or less.

[0031] A method of using a refrigerating machine oil according to an eleventh aspect of the second group is the method of using a refrigerating machine oil according to any one of the eighth aspect to the tenth aspect of the second group, wherein the volume resistivity of the refrigerating machine oil at 25°C is 1.0 × 10 12 Ω·cm or more.

[0032] A method of using a refrigeration oil according to a twelfth aspect of the second group is a method of using a refrigeration oil according to any one of the eighth aspect to the eleventh aspect of the second group, wherein the acid value of the refrigeration oil is 0.1 mgKOH / g or less.

[0033] A method of using a refrigeration oil according to a thirteenth aspect of the second group is the method of using a refrigeration oil according to any one of the eighth aspect to the twelfth aspect of the second group, wherein the ash content of the refrigeration oil is 100 ppm or less.

[0034] A method of using a refrigeration oil according to a fourteenth aspect of the second group is the method of using a refrigeration oil according to any one of the eighth aspect to the thirteenth aspect of the second group, wherein the aniline point of the refrigeration oil is −100° C. or higher and 0° C. or lower.

[0035] The use as a refrigerating machine oil according to a fifteenth aspect of the second group is a use as a refrigerating machine oil used together with a refrigerant composition containing a refrigerant, and the refrigerant includes any of the refrigerants shown in (26) below.

[0036] When used as a refrigerating machine oil, it is possible to improve lubrication when a refrigeration cycle is carried out using a refrigerant with a sufficiently low GWP or a refrigerant composition containing such a refrigerant.

[0037] The use as a refrigeration oil according to a sixteenth aspect of the second group is the use as a refrigeration oil according to the fifteenth aspect of the second group, wherein the kinetic viscosity of the refrigeration oil at 40°C is 1 mm 2 / s or more 750mm 2 / s or less.

[0038] The use as a refrigeration oil according to a seventeenth aspect of the second group is the use as a refrigeration oil according to the fifteenth or sixteenth aspect of the second group, wherein the kinetic viscosity of the refrigeration oil at 100°C is 1 mm 2 / s or more 100mm 2 / s or less.

[0039] The use as a refrigerating machine oil according to an eighteenth aspect of the second group is the use as a refrigerating machine oil according to any one of the fifteenth aspect to the seventeenth aspect of the second group, wherein the volume resistivity of the refrigerating machine oil at 25°C is 1.0 × 10 12 Ω·cm or more.

[0040] The use as a refrigeration oil according to a nineteenth aspect of the second group is the use as a refrigeration oil according to any one of the fifteenth aspect to the eighteenth aspect of the second group, wherein the acid value of the refrigeration oil is 0.1 mgKOH / g or less.

[0041] A use as a refrigeration oil according to a twentieth aspect of the second group is the use as a refrigeration oil according to any one of the fifteenth aspect to the nineteenth aspect of the second group, wherein the ash content of the refrigeration oil is 100 ppm or less.

[0042] Use as a refrigeration oil according to a 21st aspect of the second group is the use as a refrigeration oil according to any one of the 15th aspect to the 20th aspect of the second group, wherein the aniline point of the refrigeration oil is −100° C. or higher and 0° C. or lower.

[0043] (3) Group 3 So far, no specific refrigerant circuits capable of using refrigerants with low GWP have been considered.

[0044] A refrigeration cycle apparatus according to a first aspect of the third group includes a refrigerant circuit and a refrigerant. The refrigerant circuit includes a compressor, a condenser, a pressure reducing section, and an evaporator. The refrigerant is a first refrigerant X, a second refrigerant Y, a third refrigerant A, a fourth refrigerant B, a fifth refrigerant C, a sixth refrigerant D, or a seventh refrigerant E, which will be described later.

[0045] This refrigeration cycle device can perform a refrigeration cycle using a refrigerant of the first aspect described below in a refrigerant circuit having a compressor, a condenser, a pressure reducing section, and an evaporator, making it possible to perform a refrigeration cycle using a refrigerant with a low GWP.

[0046] A refrigeration cycle apparatus according to a second aspect of the third group is the refrigeration cycle apparatus according to the first aspect of the third group, wherein the refrigerant circuit further includes a low-pressure receiver, the low-pressure receiver being provided midway along the refrigerant flow path from the evaporator toward the suction side of the compressor.

[0047] This refrigeration cycle device can operate the refrigeration cycle while storing excess refrigerant in the refrigerant circuit in the low-pressure receiver.

[0048] A refrigeration cycle apparatus according to a third aspect of the third group is the refrigeration cycle apparatus according to the first or second aspect of the third group, wherein the refrigerant circuit further includes a high-pressure receiver, which is provided midway along the refrigerant flow path from the condenser to the evaporator.

[0049] In this refrigeration cycle device, the refrigeration cycle can be performed while excess refrigerant in the refrigerant circuit is stored in the high-pressure receiver.

[0050] A refrigeration cycle apparatus according to a fourth aspect of the third group is the refrigeration cycle apparatus according to any one of the first aspect to the third aspect of the third group, wherein the refrigerant circuit further includes a first pressure reduction section, a second pressure reduction section, and an intermediate pressure receiver. The first pressure reduction section, the second pressure reduction section, and the intermediate pressure receiver are all provided midway along the refrigerant flow path from the condenser to the evaporator. The intermediate pressure receiver is provided between the first pressure reduction section and the second pressure reduction section in the refrigerant flow path from the condenser to the evaporator.

[0051] In this refrigeration cycle device, the refrigeration cycle can be performed while excess refrigerant in the refrigerant circuit is stored in the intermediate pressure receiver.

[0052] A refrigeration cycle apparatus according to a fifth aspect of the third group is the refrigeration cycle apparatus according to any one of the first aspect to the fourth aspect of the third group, further including a control unit. The refrigerant circuit further includes a first pressure reduction unit and a second pressure reduction unit. The first pressure reduction unit and the second pressure reduction unit are provided midway along a refrigerant flow path from the condenser to the evaporator. The control unit adjusts both the degree of pressure reduction of the refrigerant passing through the first pressure reduction unit and the degree of pressure reduction of the refrigerant passing through the second pressure reduction unit.

[0053] In this refrigeration cycle device, by controlling the degree of pressure reduction in the first and second pressure reduction sections provided in the refrigerant flow path from the condenser to the evaporator, it is possible to reduce the density of the refrigerant located between the first and second pressure reduction sections in the refrigerant flow path from the condenser to the evaporator, which makes it easier for the refrigerant sealed in the refrigerant circuit to be present in a larger amount in the condenser and / or evaporator, thereby improving performance.

[0054] A refrigeration cycle apparatus according to a sixth aspect of the third group is the refrigeration cycle apparatus according to any one of the first aspect to the fifth aspect of the third group, wherein the refrigerant circuit further includes a refrigerant heat exchanger that exchanges heat between the refrigerant flowing from the condenser to the evaporator and the refrigerant flowing from the evaporator to the compressor.

[0055] In this refrigeration cycle device, the refrigerant flowing from the evaporator to the compressor is heated by the refrigerant flowing from the condenser to the evaporator in the refrigerant heat exchanger, thereby suppressing liquid compression in the compressor.

[0056] (4) Group 4 Some refrigerants have a low GWP and are flammable. Therefore, even if a flammable refrigerant leaks, it is preferable to adopt an arrangement structure that makes it difficult for the leaked refrigerant to reach the vicinity of electrical components.

[0057] The contents of the present disclosure have been made in consideration of the above points, and aim to provide a heat exchange unit that is less likely to allow the refrigerant to reach the electrical equipment unit, even when a flammable refrigerant of the first aspect described below is used.

[0058] A heat exchange unit according to a first aspect of the fourth group is a heat exchange unit constituting a part of a refrigeration cycle apparatus, and includes a housing, a heat exchanger, a piping connection part, and an electrical equipment unit. The heat exchange unit is either a user-side unit or a heat-source-side unit. The user-side unit and the heat-source-side unit are connected to each other via a communication pipe. The heat exchanger is provided in the housing, and a refrigerant flows therein. The piping connection part is connected to the communication pipe. The electrical equipment unit is provided in the housing. The refrigerant is any of the refrigerants according to the first to forty-second aspects described below, and is a flammable refrigerant. When the heat exchange unit is installed, the lower end of the electrical equipment unit is located at a position higher than the piping connection part.

[0059] Here, the flammable refrigerant refers to a refrigerant that has a flammability of "2L class" or higher according to the flammability classification of the US ANSI / ASHRAE34-2013 standard.

[0060] The piping connection portion is not particularly limited, but may be connected directly to the refrigerant piping extending from the heat exchanger, or indirectly via another element.

[0061] The form of the electrical equipment unit is not particularly limited, and may be an electrical equipment box that houses a plurality of electrical components, or a board on which a plurality of electrical components are provided.

[0062] In the installed state, the lower end of the electrical component unit is positioned higher than the pipe connection, so even if flammable refrigerant leaks from the pipe connection, the refrigerant, which is heavier than air, is unlikely to reach the electrical component unit.

[0063] (5) Group 5 When a refrigerant according to the first aspect described below is used as a refrigerant with a sufficiently small GWP, no study has been conducted to date on improving the operating efficiency of the refrigeration cycle.

[0064] The present disclosure has been made in consideration of the above points, and aims to provide a refrigeration cycle device that can improve the operating efficiency when using a refrigerant according to a first aspect described below.

[0065] A refrigeration cycle apparatus according to a first aspect of the fifth group includes a compressor, a condenser, a pressure reduction unit, an evaporator, and an injection flow path. The compressor draws in low-pressure refrigerant from the suction flow path, compresses the refrigerant, and discharges high-pressure refrigerant. The condenser condenses the high-pressure refrigerant discharged from the compressor. The pressure reduction unit reduces the pressure of the high-pressure refrigerant that has left the condenser. The evaporator evaporates the refrigerant reduced in pressure by the pressure reduction unit. The injection flow path is at least one of an intermediate injection flow path and a suction injection flow path. The intermediate injection flow path merges a portion of the refrigerant flowing from the condenser toward the evaporator with intermediate-pressure refrigerant in the compressor. The suction injection flow path merges a portion of the refrigerant flowing from the condenser toward the evaporator with low-pressure refrigerant that is suctioned into the compressor. The refrigerant is a first refrigerant X, a second refrigerant Y, a third refrigerant A, a fourth refrigerant B, a fifth refrigerant C, a sixth refrigerant D, or a seventh refrigerant E, which will be described later.

[0066] In this refrigeration cycle device, the GWP can be kept sufficiently low by using a refrigerant according to a first aspect described below, and the operating efficiency of the refrigeration cycle can be improved by using an injection flow path.

[0067] A refrigeration cycle apparatus according to a second aspect of the fifth group is the refrigeration cycle apparatus according to the first aspect of the fifth group, further comprising a branch flow path, an opening adjustment valve, and an injection heat exchanger. The branch flow path branches off from a main refrigerant flow path connecting the condenser and the evaporator. The opening adjustment valve is provided in the branch flow path. The injection heat exchanger exchanges heat between refrigerant flowing through the main refrigerant flow path and refrigerant flowing downstream of the opening adjustment valve in the branch flow path. The refrigerant that leaves the injection heat exchanger and flows through the branch flow path flows into the injection flow path.

[0068] In this refrigeration cycle device, it is possible to further improve the operating efficiency of the refrigeration cycle.

[0069] A refrigeration cycle apparatus according to a third aspect of the fifth group is the refrigeration cycle apparatus according to the first or second aspect of the fifth group, further comprising a refrigerant storage tank provided in a main refrigerant flow path connecting the condenser and the evaporator, and a gas component of the refrigerant stored inside the refrigerant storage tank flows through the injection flow path.

[0070] In this refrigeration cycle device, it is possible to improve the efficiency of the refrigeration cycle while storing excess refrigerant in the refrigerant storage tank.

[0071] A refrigeration cycle apparatus according to a fourth aspect of the fifth group is the refrigeration cycle apparatus according to any one of the first aspect to the third aspect of the fifth group, in which the compressor has a fixed scroll and a rotating scroll. The fixed scroll has an end plate and a wrap rising in a spiral shape from the end plate. The rotating scroll meshes with the fixed scroll to form a compression chamber. Refrigerant flowing through the injection flow path merges with the compression chamber.

[0072] In this refrigeration cycle device, it is possible to improve the operating efficiency of the refrigeration cycle while using a scroll compressor.

[0073] (6) Group 6 When a refrigerant according to the first aspect described below is used as a refrigerant with a sufficiently small GWP, no consideration has been given to what pressure resistance strength should be used for the refrigeration cycle device and its constituent devices.

[0074] For example, when updating a refrigeration cycle device that uses refrigerants such as R410A or R32, which have been widely used in the past, to a refrigerant according to the first aspect described below while reusing the existing connecting piping, there is a risk of damage to the existing connecting piping if the equipment that makes up the refrigeration cycle device is operated at a pressure that exceeds the withstand pressure of the existing connecting piping.

[0075] The contents of the present disclosure have been made in consideration of the above points, and aim to provide a heat source unit and a refrigeration cycle device that can suppress damage to connecting piping when using a refrigerant of the first aspect described below.

[0076] A heat source unit according to a first aspect of the sixth group includes a compressor and a heat source side heat exchanger. The heat source unit is connected to the utilization units via a connecting pipe to form a refrigeration cycle device. The utilization units include a utilization side heat exchanger. The heat source unit uses the refrigerant according to the first aspect described below as a refrigerant. The design pressure of the heat source unit is lower than 1.5 times the design pressure of the connecting pipe.

[0077] Note that "design pressure" means gauge pressure (the same applies below).

[0078] Since the design pressure of this heat source unit is less than 1.5 times the design pressure of the connecting pipe, it is operated at a pressure lower than the withstand pressure of the connecting pipe, so even when it is connected to the connecting pipe and used, it is possible to suppress damage to the connecting pipe.

[0079] A refrigeration cycle apparatus according to a second aspect of the sixth group includes utilization units, a connecting pipe, and the heat source unit according to the first aspect. The refrigeration cycle apparatus uses a refrigerant according to the first aspect, which will be described later. The design pressure of the heat source unit is equivalent to the design pressure of the refrigeration cycle apparatus when refrigerant R22 or refrigerant R407C is used.

[0080] Here, "equivalent" preferably means within a range of ±10% of the design pressure of the refrigeration cycle device when refrigerant R22 or refrigerant R407C is used.

[0081] In this refrigeration cycle device, even when a refrigeration cycle device that used refrigerant R22 or refrigerant R407C is updated to a refrigeration cycle device that uses the refrigerant of the first aspect described below while reusing the connecting piping, damage to the connecting piping can be suppressed by using a design pressure for the heat source unit that is equivalent to or the same as that before the update.

[0082] A refrigeration cycle apparatus according to a third aspect of the sixth group is the refrigeration cycle apparatus according to the second aspect of the sixth group, wherein the design pressure of the heat source unit is 3.0 MPa or more and 3.7 MPa or less.

[0083] A refrigeration cycle apparatus according to a fourth aspect of the sixth group includes utilization units, a connecting pipe, and the heat source unit according to the first aspect. The refrigeration cycle apparatus uses a refrigerant according to the first aspect, which will be described later. The design pressure of the heat source unit is equivalent to the design pressure of the refrigeration cycle apparatus when the refrigerant R410A or the refrigerant R32 is used.

[0084] Here, "equivalent" preferably means within a range of ±10% of the design pressure of the refrigeration cycle device when refrigerant R410A or refrigerant R32 is used.

[0085] In this refrigeration cycle device, even when a refrigeration cycle device that used refrigerant R410A or refrigerant R32 is updated to a refrigeration cycle device that uses the refrigerant of the first aspect described below while reusing the connecting piping, damage to the connecting piping can be suppressed by using a design pressure for the heat source unit that is equivalent to or the same as that before the update.

[0086] A refrigeration cycle apparatus according to a fifth aspect of the sixth group is the refrigeration cycle apparatus according to the fourth aspect of the sixth group, wherein the design pressure of the heat source unit is 4.0 MPa or more and 4.8 MPa or less.

[0087] A refrigeration cycle apparatus according to a sixth aspect of the sixth group includes a heat source unit, a utilization unit, and a connecting pipe. The heat source unit has a compressor and a heat source side heat exchanger. The utilization unit has a utilization side heat exchanger. The connecting pipe connects the heat source unit and the utilization unit. The refrigeration cycle apparatus uses a refrigerant according to the first aspect described below. The design pressure of the heat source unit is equivalent to the design pressure of the refrigeration cycle apparatus when refrigerant R22 or refrigerant R407C is used.

[0088] Here, "equivalent" preferably means within a range of ±10% of the design pressure of the refrigeration cycle device when refrigerant R22 or refrigerant R407C is used.

[0089] In this refrigeration cycle device, even when a refrigeration cycle device that used refrigerant R22 or refrigerant R407C is updated to a refrigeration cycle device that uses the refrigerant of the first aspect described below while reusing the connecting piping, damage to the connecting piping can be suppressed by using a design pressure for the heat source unit that is equivalent to or the same as that before the update.

[0090] A refrigeration cycle apparatus according to a seventh aspect of the sixth group is the refrigeration cycle apparatus according to the sixth aspect of the sixth group, wherein the design pressure of the heat source unit is 3.0 MPa or more and 3.7 MPa or less.

[0091] A refrigeration cycle apparatus according to an eighth aspect of the sixth group includes a heat source unit, a utilization unit, and a connecting pipe. The heat source unit has a compressor and a heat source side heat exchanger. The utilization unit has a utilization side heat exchanger. The connecting pipe connects the heat source unit and the utilization unit. The refrigeration cycle apparatus uses a refrigerant according to the first aspect described below. The design pressure of the heat source unit is equivalent to the design pressure of the refrigeration cycle apparatus when refrigerant R410A or refrigerant R32 is used.

[0092] Here, "equivalent" preferably means within a range of ±10% of the design pressure of the refrigeration cycle device when refrigerant R410A or refrigerant R32 is used.

[0093] In this refrigeration cycle device, even when a refrigeration cycle device that used refrigerant R410A or refrigerant R32 is updated to a refrigeration cycle device that uses the refrigerant of the first aspect described below while reusing the connecting piping, damage to the connecting piping can be suppressed by using a design pressure for the heat source unit that is equivalent to or the same as that before the update.

[0094] A refrigeration cycle apparatus according to a ninth aspect of the sixth group is the refrigeration cycle apparatus according to the eighth aspect of the sixth group, wherein the design pressure of the heat source unit is 4.0 MPa or more and 4.8 MPa or less.

[0095] A heat source unit according to a tenth aspect of the sixth group includes a compressor, a heat source-side heat exchanger, and a control device. The heat source unit is connected to a utilization unit via a connecting pipe to form a refrigeration cycle device. The utilization unit has a utilization-side heat exchanger. The heat source unit uses the refrigerant according to the first aspect described below as a refrigerant. The control device is configured so that the upper limit of the control pressure of the refrigerant is set or can be set to be lower than 1.5 times the design pressure of the connecting pipe.

[0096] This heat source unit is configured so that the upper limit of the refrigerant control pressure by the control device is set or can be set to be lower than 1.5 times the design pressure of the connecting pipe. Therefore, even when the heat source unit is connected to the connecting pipe and used, operation control is ensured at a pressure lower than the withstand pressure of the connecting pipe, making it possible to suppress damage to the connecting pipe.

[0097] A refrigeration cycle apparatus according to an eleventh aspect of the sixth group includes a utilization unit, a connecting pipe, and the heat source unit according to the tenth aspect of the sixth group. The refrigeration cycle apparatus uses a refrigerant according to the first aspect described below. The control device is configured to set or be able to set an upper limit value of the control pressure of the refrigerant to be equal to the upper limit value of the control pressure in the refrigeration cycle apparatus when refrigerant R22 or refrigerant R407C is used.

[0098] Here, "equivalent" preferably means within a range of ±10% of the upper limit of the control pressure in the refrigeration cycle device when refrigerant R22 or refrigerant R407C is used.

[0099] In this refrigeration cycle device, even when a refrigeration cycle device that previously used refrigerant R22 or refrigerant R407C is updated to a refrigeration cycle device that uses the refrigerant of the first aspect described below while reusing the connecting piping, the upper limit value of the control pressure of the refrigerant by the control device of the heat source unit is set or can be set to be equivalent to or the same as the upper limit value of the control pressure of the heat source unit of the refrigeration cycle device when refrigerant R22 or refrigerant R407C was used, thereby making it possible to suppress damage to the connecting piping.

[0100] A refrigeration cycle apparatus according to a twelfth aspect of the sixth group is the refrigeration cycle apparatus according to the eleventh aspect of the sixth group, wherein the upper limit of the control pressure is set to 3.0 MPa or more and 3.7 MPa or less.

[0101] A refrigeration cycle apparatus according to a thirteenth aspect of the sixth group includes a utilization unit, a communication pipe, and the heat source unit of the tenth aspect. The refrigeration cycle apparatus uses a refrigerant according to the first aspect described below. The control device is configured to set or be able to set an upper limit value of the control pressure of the refrigerant to be equal to the upper limit value of the control pressure in the refrigeration cycle apparatus when refrigerant R410A or refrigerant R32 is used.

[0102] Here, "equivalent" preferably means within a range of ±10% of the upper limit of the control pressure in the refrigeration cycle device when refrigerant R410A or refrigerant R32 is used.

[0103] In this refrigeration cycle device, even when a refrigeration cycle device that used refrigerant R410A or refrigerant R32 is updated to a refrigeration cycle device that uses the refrigerant of the first aspect described below while reusing the connecting piping, the upper limit value of the control pressure of the refrigerant by the control device of the heat source unit is set or can be set to be equivalent to or the same as the upper limit value of the control pressure of the heat source unit of the refrigeration cycle device when refrigerant R410A or refrigerant R32 was used, thereby making it possible to suppress damage to the connecting piping.

[0104] A refrigeration cycle apparatus according to a fourteenth aspect of the sixth group is the refrigeration cycle apparatus according to the thirteenth aspect of the sixth group, wherein the upper limit of the control pressure is set to 4.0 MPa or more and 4.8 MPa or less.

[0105] A refrigeration cycle apparatus according to a fifteenth aspect of the sixth group includes a heat source unit, utilization units, a communication pipe, and a control device. The heat source unit has a compressor and a heat source side heat exchanger. The utilization units have a communication side heat exchanger. The communication pipe connects the heat source unit and the utilization units. The refrigeration cycle apparatus uses a refrigerant according to the first aspect described below. The control device is configured so that the upper limit of the control pressure of the refrigerant is set or can be set to be equal to the upper limit of the control pressure in the refrigeration cycle apparatus when refrigerant R22 or refrigerant R407C is used.

[0106] Here, "equivalent" preferably means within a range of ±10% of the upper limit of the control pressure in the refrigeration cycle device when refrigerant R22 or refrigerant R407C is used.

[0107] In this refrigeration cycle device, even when a refrigeration cycle device that previously used refrigerant R22 or refrigerant R407C is updated to a refrigeration cycle device that uses the refrigerant of the first aspect described below while reusing the connecting piping, the upper limit value of the control pressure of the refrigerant by the control device of the heat source unit is set or can be set to be equivalent to or the same as the upper limit value of the control pressure of the heat source unit of the refrigeration cycle device when refrigerant R22 or refrigerant R407C was used, thereby making it possible to suppress damage to the connecting piping.

[0108] A refrigeration cycle apparatus according to a sixteenth aspect of the sixth group is the refrigeration cycle apparatus according to the fifteenth aspect of the sixth group, wherein the upper limit of the control pressure is set to 3.0 MPa or more and 3.7 MPa or less.

[0109] A refrigeration cycle apparatus according to a seventeenth aspect of the sixth group includes a heat source unit, a utilization unit, a communication pipe, and a control device. The heat source unit has a compressor and a heat source side heat exchanger. The utilization unit has a communication side heat exchanger. The communication pipe connects the heat source unit and the utilization unit. The refrigeration cycle apparatus uses a refrigerant according to the first aspect described below. The control device is configured so that the upper limit of the control pressure of the refrigerant is set or can be set to be equal to the upper limit of the control pressure in the refrigeration cycle apparatus when refrigerant R410A or refrigerant R32 is used.

[0110] Here, "equivalent" preferably means within a range of ±10% of the upper limit of the control pressure in the refrigeration cycle device when refrigerant R410A or refrigerant R32 is used.

[0111] In this refrigeration cycle device, even when a refrigeration cycle device that used refrigerant R410A or refrigerant R32 is updated to a refrigeration cycle device that uses the refrigerant of the first aspect described below while reusing the connecting piping, the upper limit value of the control pressure of the refrigerant by the control device of the heat source unit is set or can be set to be equivalent to or the same as the upper limit value of the control pressure of the heat source unit of the refrigeration cycle device when refrigerant R410A or refrigerant R32 was used, thereby making it possible to suppress damage to the connecting piping.

[0112] A refrigeration cycle apparatus according to an eighteenth aspect of the sixth group is the refrigeration cycle apparatus according to the seventeenth aspect of the sixth group, wherein the upper limit of the control pressure is set to 4.0 MPa or more and 4.8 MPa or less.

[0113] (7) Group 7 Some refrigerants have low GWP and are flammable. Air conditioning units often use high-power electric heating devices for various purposes. Even if a flammable refrigerant leaks in an air conditioning unit that uses such a high-power electric heating device, it is desirable to prevent the electric heating device from catching fire.

[0114] The present disclosure has been made in consideration of the above points, and aims to provide an air conditioning unit that uses a refrigerant with a low GWP and is capable of suppressing ignition in an electric heating device even in the event of a refrigerant leak.

[0115] An air conditioning unit according to a first aspect of the seventh group includes a housing, a device, and an electric heating device. The device is provided inside the housing. The electric heating device is provided inside the housing. The device is a compressor that compresses a refrigerant according to the first aspect described below, and / or a heat exchanger that exchanges heat between outside air and the refrigerant according to the first aspect described below. The electric heating device consumes 300 W or less power.

[0116] The air conditioning unit is not particularly limited, and may be, for example, a heat source unit or a utilization unit in a refrigeration cycle device such as an air conditioner in which a heat source unit such as an outdoor unit and a utilization unit such as an indoor unit are connected via a refrigerant communication pipe.The heat source unit may have only a heat exchanger, and the compressor may be provided in a separate unit.

[0117] This air conditioning unit accommodates, in a housing, a compressor for compressing a refrigerant of a first aspect described below and / or a heat exchanger for exchanging heat between outside air and the refrigerant of the first aspect described below, together with an electric heating device, but the power consumption of the electric heating device is 300 W or less. Therefore, even if the refrigerant leaks, ignition in the electric heating device is suppressed.

[0118] An air conditioning unit according to a second aspect of the seventh group is the air conditioning unit according to the first aspect of the seventh group, wherein the housing has an outlet formed on a side surface in an installed state for blowing out air that has passed through the heat exchanger, and the power consumption of the electric heating device is 75 W or more.

[0119] This air conditioning unit's electric heating device consumes 75W or more of power, making it easy to utilize the function of the electric heating device.

[0120] An air conditioning unit according to a third aspect of the seventh group is the air conditioning unit according to the second aspect of the seventh group, further comprising a fan for forming an air flow passing through the heat exchanger, and the power consumption of the electric heating device is 75 W or more and 100 W or less.

[0121] The internal volume (volume of fluid that can be filled inside) of a heat exchanger in an air conditioning unit equipped with only one fan is preferably 0.4 L or more and less than 3.5 L. In particular, if the refrigerant circuit in which the air conditioning unit is used does not have a refrigerant container (such as a low-pressure receiver or high-pressure receiver, excluding the accumulator attached to the compressor), the internal volume is preferably 0.4 L or more and less than 2.5 L, and if the refrigerant circuit has a refrigerant container (preferably one with one user unit such as an indoor unit), the internal volume is preferably 1.4 L or more and less than 3.5 L.

[0122] This air conditioning unit has a capacity of only one fan, so even if the power consumption of the electric heating device is 100W or less, the electric heating device can still function satisfactorily.

[0123] An air conditioning unit according to a fourth aspect of the seventh group is the air conditioning unit according to the second aspect of the seventh group, further comprising two fans for forming an air flow passing through the heat exchanger. The power consumption of the electric heating device is 100 W or more.

[0124] The internal volume (volume of fluid that can be filled inside) of a heat exchanger in an air conditioning unit equipped with two fans is preferably 3.5 L or more and 7.0 L or less. In particular, if the refrigerant circuit in which the air conditioning unit is used is equipped with one or more utilization units such as indoor units that do not have an expansion valve, the internal volume is preferably 3.5 L or more and less than 5.0 L, and if the refrigerant circuit is equipped with multiple utilization units such as indoor units that have an expansion valve, the internal volume is preferably 5.0 L or more and 7.0 L or less.

[0125] This air conditioning unit is equipped with two fans, so the capacity of the air conditioning unit is large, and there is a tendency for the electric heating device to also require large capacity. However, in this case, the electric heating device uses a power consumption of 100W or more, so it is possible to fully utilize the function of the electric heating device to match the capacity of the air conditioning unit.

[0126] An air conditioning unit according to a fifth aspect of the seventh group is the air conditioning unit according to the first aspect of the seventh group, wherein the housing has an air outlet for blowing air that has passed through the heat exchanger upward, and the power consumption of the electric heating device is 200 W or more.

[0127] The internal volume (volume of fluid that can be filled inside) of the heat exchanger of an air conditioning unit, in which air that has passed through the heat exchanger is blown upward, is preferably 5.5 L or more and 38 L or less. Heat exchangers with an internal volume of 5.5 L or more and 38 L or less are preferably used in systems in which a plurality of utilization units, such as indoor units with expansion valves, are installed in the refrigerant circuit.

[0128] This air conditioning unit sends air upward after passing through a heat exchanger, so the air conditioning unit has a large capacity, and the electric heating device also tends to require a large capacity.However, in this case, the electric heating device uses a power consumption of 200W or more, so it is possible to fully utilize the function of the electric heating device to match the capacity of the air conditioning unit.

[0129] An air conditioning unit according to a sixth aspect of the seventh group is an air conditioning unit according to any one of the first aspect to the fifth aspect of the seventh group, in which the electric heating device is at least one of a drain pan heater, a crankcase heater, and a refrigerant heater.

[0130] If this air conditioning unit is equipped with a drain pan heater, it can prevent condensation water on the drain pan from freezing in an air conditioning unit equipped with a drain pan; if it is equipped with a crankcase heater, it can prevent the generation of bubbles in the refrigeration oil (oil foaming) when the compressor is started in an air conditioning unit equipped with a compressor; and if it is equipped with a refrigerant heater, it can heat the refrigerant in the refrigerant circuit.

[0131] (8) Group 8 An index used in the prevention of global warming is called LCCP (Life Cycle Climate Performance). LCCP is an index used in the prevention of global warming, and is a numerical value obtained by adding the energy consumption (indirect impact) during the production of greenhouse gases used and leakage into the outside air (direct impact) to TEWI (Total Equivalent Warning Impact), and is expressed in kg-CO2. In other words, TEWI is obtained by adding the direct impact and indirect impact, which are calculated using the required formula. LCCP is calculated using the following relational formula: LCCP=GWPRM×W+GWP×W×(1-R)+N×Q×A

[0132] where GWPRM is the global warming effect associated with refrigerant production, W is the amount of refrigerant charged, R is the amount of refrigerant recovered when the equipment is disposed of, N is the equipment usage period (years), Q is the CO2 emission intensity, and A is the annual power consumption.

[0133] The LCCP of a refrigeration cycle device increases when the refrigerant circuit is filled with too little refrigerant, resulting in a deterioration in cycle efficiency due to a lack of refrigerant.Furthermore, when the refrigerant circuit is filled with too much refrigerant, the influence of GWP increases, resulting in a higher LCCP.Furthermore, refrigerants with a lower GWP than the commonly used R32 tend to have a lower heat transfer capacity, which reduces cycle efficiency and tends to increase LCCP.

[0134] The present disclosure has been made in consideration of the above points, and aims to provide a refrigeration cycle device that can keep LCCP low when a heat cycle is performed using a refrigerant with a sufficiently small GWP, and a method for determining the amount of refrigerant charged in the refrigeration cycle device.

[0135] A refrigeration cycle apparatus according to a first aspect of the eighth group includes a heat source unit, a utilization unit, and a refrigerant piping. The heat source unit has a compressor and a heat source side heat exchanger. The utilization unit has a utilization side heat exchanger. The refrigerant piping connects the heat source unit and the utilization unit. A refrigerant according to the first aspect described below is sealed in a refrigerant circuit formed by connecting the compressor, the heat source side heat exchanger, and the utilization side heat exchanger. The amount of refrigerant sealed in the refrigerant circuit satisfies the condition of 160 g to 560 g per kW of refrigeration capacity of the refrigeration cycle apparatus.

[0136] The refrigeration capacity of the refrigeration cycle device means the rated refrigeration capacity.

[0137] In this refrigeration cycle device, the refrigerant circuit is sealed with 160 g to 560 g of the refrigerant of the first aspect described below per kW of refrigeration capacity, so that it is possible to keep the LCCP low when performing a heat cycle using a refrigerant with a sufficiently small GWP.

[0138] The internal volume (volume of fluid that can be filled inside) of the heat source side heat exchanger is preferably 0.4 L or more and 2.5 L or less if the refrigerant circuit does not include a refrigerant container (such as a low-pressure receiver or a high-pressure receiver, excluding accumulators attached to the compressor), and is preferably 1.4 L or more and less than 5.0 L if the refrigerant circuit includes a refrigerant container.

[0139] Furthermore, the internal volume (volume of fluid that can be filled inside) of the heat source side heat exchanger of a heat source unit having only one fan is preferably 0.4 L or more and less than 3.5 L when the heat source unit has a housing with an outlet formed on the side when installed for blowing out air that has passed through the heat source side heat exchanger (when the heat source unit is a trunk type, etc.), and the internal volume (volume of fluid that can be filled inside) of the heat source side heat exchanger of a heat source unit having two fans is preferably 3.5 L or more and less than 5.0 L when the heat source unit has a housing with an outlet formed on the side when installed for blowing out air that has passed through the heat source side heat exchanger (when the heat source unit is a trunk type, etc.).

[0140] A refrigeration cycle apparatus according to a second aspect of the eighth group includes a heat source unit, a first usage unit, a second usage unit, and refrigerant piping. The heat source unit has a compressor and a heat source side heat exchanger. The first usage unit has the first usage side heat exchanger. The second usage unit has a second usage side heat exchanger. The refrigerant piping connects the heat source unit, the first usage unit, and the second usage unit. A refrigerant according to the first aspect described below is sealed in a refrigerant circuit formed by connecting the first usage side heat exchanger and the second usage side heat exchanger in parallel to the compressor and the heat source side heat exchanger. The amount of refrigerant sealed in the refrigerant circuit per 1 kW of refrigeration capacity satisfies the condition of 190 g to 1660 g.

[0141] This refrigeration cycle device has a refrigerant circuit having a plurality of user-side heat exchangers connected in parallel with each other, and a refrigerant according to the first aspect described below is sealed in an amount of 190 g to 1,660 g per kW of refrigeration capacity. Therefore, when a heat cycle is performed using a refrigerant with a sufficiently small GWP, it is possible to keep the LCCP low.

[0142] The internal volume of the heat source side heat exchanger (volume of fluid that can be filled inside) is preferably 1.4 L or more and less than 5.0 L when the first usage unit does not have an expansion valve on the liquid side of the first usage side heat exchanger and the second usage unit does not have an expansion valve on the liquid side of the second usage side heat exchanger, and is preferably 5.0 L or more and 38 L or less when the first usage unit has an expansion valve on the liquid side of the first usage side heat exchanger and the second usage unit has an expansion valve on the liquid side of the second usage side heat exchanger.

[0143] Furthermore, the internal volume (volume of fluid that can be filled inside) of the heat source side heat exchanger of a heat source unit having only one fan is preferably 0.4 L or more and less than 3.5 L when the heat source unit has a housing with an outlet formed on the side in the installed state for blowing out air that has passed through the heat source side heat exchanger (when the heat source unit is a trunk type, etc.), and the internal volume (volume of fluid that can be filled inside) of the heat source side heat exchanger of a heat source unit having two fans is preferably 3.5 L or more and 7.0 L or less when the heat source unit has a housing with an outlet formed on the side in the installed state for blowing out air that has passed through the heat source side heat exchanger (when the heat source unit is a trunk type, etc.), and the internal volume (volume of fluid that can be filled inside) of the heat source side heat exchanger of a heat source unit from which air that has passed through the heat source side heat exchanger is blown upward is preferably 5.5 L or more and 38 L or less.

[0144] (9) Group 9 For conventional refrigeration cycle devices using R410A or R32, the outer diameters of the liquid-side refrigerant connection pipe and the gas-side refrigerant connection pipe that connect the heat source unit having a heat source-side heat exchanger and the user unit having a user-side heat exchanger have been specifically considered and proposed.

[0145] However, for a refrigeration cycle device using a refrigerant of the first aspect described below as a refrigerant with a sufficiently small GWP, the outer diameters of the liquid side refrigerant connection pipe and the gas side refrigerant connection pipe have not been considered or proposed at all.

[0146] The present disclosure has been made in consideration of the above points, and aims to provide a refrigeration cycle device that can minimize a decrease in performance when using a refrigerant according to a first aspect described below.

[0147] A refrigeration cycle apparatus according to a first aspect of the ninth group has a refrigerant circuit in which a compressor, a heat source side heat exchanger, a pressure reducing section, a liquid side refrigerant connection pipe, a user side heat exchanger, and a gas side refrigerant connection pipe are connected. The refrigeration cycle apparatus uses a refrigerant according to the first aspect described below. The pipe outer diameters of the liquid side refrigerant connection pipe and the gas side refrigerant connection pipe are D0 / 8 inches (here, "D0-1 / 8 inch" is the pipe outer diameter of the refrigerant connection pipe when refrigerant R32 is used), and the range of D0 for the liquid side refrigerant connection pipe is "2≦D0≦4", and the range of D0 for the gas side refrigerant connection pipe is "3≦D0≦8".

[0148] The pressure reducing section is not particularly limited and may be an expansion valve or a capillary tube. It is more preferable that the range of D0 in the liquid side refrigerant communication pipe is "2≦D0≦3", and that the range of D0 in the gas side refrigerant communication pipe is "4≦D0≦7".

[0149] This refrigeration cycle device can minimize the decrease in capacity while keeping the GWP sufficiently low by using a refrigerant according to a first aspect described below.

[0150] The refrigeration cycle apparatus according to the first aspect of the ninth group may be the following refrigeration cycle apparatus, taking into account the difference in physical properties between the refrigerant of the present disclosure and the refrigerant R32.

[0151] In the refrigeration cycle device relating to the first aspect of the ninth group, the rated refrigeration capacity of the refrigeration cycle device is 6.3 kW or more and 10.0 kW or less, and the pipe outer diameter of the liquid side refrigerant connecting pipe is D0 / 8 inches (here, ``D0-1 / 8 inch'' is the pipe outer diameter of the liquid side refrigerant connecting pipe when refrigerant R32 is used), and the liquid side refrigerant connecting pipe may have a D0 of 3.

[0152] In the refrigeration cycle device relating to the first aspect of the ninth group, the rated refrigeration capacity of the refrigeration cycle device is 4.0 kW or less, and the outer diameter of the gas side refrigerant connecting pipe is D0 / 8 inches (here, "D0-1 / 8 inches" is the outer diameter of the gas side refrigerant connecting pipe when refrigerant R32 is used), and the D0 of the gas side refrigerant connecting pipe may be 4.

[0153] In the refrigeration cycle device relating to the first aspect of the ninth group, the rated refrigeration capacity of the refrigeration cycle device is 6.3 kW or more and 10.0 kW or less, and the pipe outer diameter of the gas side refrigerant connection pipe is D0 / 8 inches (here, "D0-1 / 8 inch" is the pipe outer diameter of the gas side refrigerant connection pipe when refrigerant R32 is used), and the gas side refrigerant connection pipe may have a D0 of 5.

[0154] In the refrigeration cycle device relating to the first aspect of the ninth group, the rated refrigeration capacity of the refrigeration cycle device is 15.0 kW or more and 19.0 kW or less, and the pipe outer diameter of the gas side refrigerant connection pipe is D0 / 8 inches (here, "D0-1 / 8 inch" is the pipe outer diameter of the gas side refrigerant connection pipe when refrigerant R32 is used), and the gas side refrigerant connection pipe may have a D0 of 6.

[0155] In the refrigeration cycle device according to the first aspect of the ninth group, the rated refrigeration capacity of the refrigeration cycle device is 25.0 kW or more, and the outer diameter of the gas side refrigerant connecting pipe is D0 / 8 inches (here, "D0-1 / 8 inches" is the outer diameter of the gas side refrigerant connecting pipe when refrigerant R32 is used), and the D0 of the gas side refrigerant connecting pipe may be 7.

[0156] A refrigeration cycle apparatus according to a second aspect of the ninth group is the refrigeration cycle apparatus according to the first aspect of the ninth group, wherein the rated refrigeration capacity of the refrigeration cycle apparatus is greater than 5.6 kW and less than 11.2 kW, and the liquid side refrigerant connection pipe has a D0 of 3 (i.e., a pipe diameter of 3 / 8 inch). It is preferable that the rated refrigeration capacity of the refrigeration cycle apparatus is 6.3 kW or more and 10.0 kW or less, and the liquid side refrigerant connection pipe has a D0 of 3 (i.e., a pipe diameter of 3 / 8 inch).

[0157] The refrigeration cycle device according to the third aspect of the ninth group is the refrigeration cycle device according to the first aspect of the ninth group, wherein the rated refrigeration capacity of the refrigeration cycle device is greater than 22.4 kW and the gas side refrigerant connecting pipe has a D0 of 7 (i.e., a pipe diameter of 7 / 8 inch), the rated refrigeration capacity of the refrigeration cycle device is greater than 14.0 kW and less than 22.4 kW and the gas side refrigerant connecting pipe has a D0 of 6 (i.e., a pipe diameter of 6 / 8 inch), the rated refrigeration capacity of the refrigeration cycle device is greater than 5.6 kW and less than 11.2 kW and the gas side refrigerant connecting pipe has a D0 of 5 (i.e., a pipe diameter of 5 / 8 inch), or the rated refrigeration capacity of the refrigeration cycle device is less than 4.5 kW and the gas side refrigerant connecting pipe has a D0 of 4 (i.e., a pipe diameter of 1 / 2 inch). It is preferable that the rated refrigeration capacity of the refrigeration cycle device is 25.0 kW or more and the gas side refrigerant connection pipe has a D0 of 7 (i.e., a pipe diameter of 7 / 8 inch), or the rated refrigeration capacity of the refrigeration cycle device is 15.0 kW or more and less than 19.0 kW and the gas side refrigerant connection pipe has a D0 of 6 (i.e., a pipe diameter of 6 / 8 inch), or the rated refrigeration capacity of the refrigeration cycle device is 6.3 kW or more and less than 10.0 kW and the gas side refrigerant connection pipe has a D0 of 5 (i.e., a pipe diameter of 5 / 8 inch), or the rated refrigeration capacity of the refrigeration cycle device is less than 4.0 kW and the gas side refrigerant connection pipe has a D0 of 4 (i.e., a pipe diameter of 1 / 2 inch).

[0158] A refrigeration cycle apparatus according to a fourth aspect of the ninth group has a refrigerant circuit in which a compressor, a heat source side heat exchanger, a pressure reducing section, a liquid side refrigerant connection pipe, a user side heat exchanger, and a gas side refrigerant connection pipe are connected. The cycle apparatus uses the refrigerant of the first aspect described below. The pipe outer diameters of the liquid side refrigerant connection pipe and the gas side refrigerant connection pipe are D0 / 8 inches, and the range of D0 for the liquid side refrigerant connection pipe is "2≦D0≦4", and the range of D0 for the gas side refrigerant connection pipe is "3≦D0≦8". The pipe outer diameter of the liquid side refrigerant connection pipe is the same as the pipe outer diameter of the liquid side refrigerant connection pipe when refrigerant R410A is used, and the pipe outer diameter of the gas side refrigerant connection pipe is the same as the pipe outer diameter of the gas side refrigerant connection pipe when refrigerant R410A is used.

[0159] The pressure reducing section is not particularly limited and may be an expansion valve or a capillary tube. It is more preferable that the range of D0 in the liquid side refrigerant communication pipe is "2≦D0≦3", and that the range of D0 in the gas side refrigerant communication pipe is "4≦D0≦7".

[0160] This refrigeration cycle device can minimize the decrease in capacity while keeping the GWP sufficiently low by using a refrigerant including the refrigerant of the first aspect described below.

[0161] A refrigeration cycle apparatus according to a fifth aspect of the ninth group is the refrigeration cycle apparatus according to the fourth aspect of the ninth group, in which D0 of the liquid side refrigerant communication pipe is 2 (that is, the pipe diameter is ¼ inch).

[0162] The refrigeration cycle device according to the sixth aspect of the ninth group is the refrigeration cycle device according to the fourth aspect of the ninth group, wherein the rated refrigeration capacity of the refrigeration cycle device is 6.3 kW or more and the liquid side refrigerant connecting pipe has a D0 of 3 (i.e., a pipe diameter of 3 / 8 inch), or the rated refrigeration capacity of the refrigeration cycle device is less than 6.3 kW and the liquid side refrigerant connecting pipe has a D0 of 2 (i.e., a pipe diameter of 1 / 4 inch).

[0163] The refrigeration cycle device according to the seventh aspect of the ninth group is the refrigeration cycle device according to the fourth aspect of the ninth group, wherein the rated refrigeration capacity of the refrigeration cycle device is 6.0 kW or more and the gas side refrigerant connecting pipe has a D0 of 4 (i.e., a pipe diameter of 1 / 2 inch), or the rated refrigeration capacity of the refrigeration cycle device is less than 6.0 kW and the gas side refrigerant connecting pipe has a D0 of 3 (i.e., a pipe diameter of 3 / 8 inch).

[0164] The refrigeration cycle device according to the eighth aspect of the ninth group is the refrigeration cycle device according to the fourth aspect of the ninth group, wherein the rated refrigeration capacity of the refrigeration cycle device is 25.0 kW or more and the gas side refrigerant connection pipe has a D0 of 7 (i.e., a pipe diameter of 7 / 8 inch), or the rated refrigeration capacity of the refrigeration cycle device is 15.0 kW or more and less than 25.0 kW and the gas side refrigerant connection pipe has a D0 of 6 (i.e., a pipe diameter of 6 / 8 inch), or the rated refrigeration capacity of the refrigeration cycle device is 6.3 kW or more and less than 15.0 kW and the gas side refrigerant connection pipe has a D0 of 5 (i.e., a pipe diameter of 5 / 8 inch), or the rated refrigeration capacity of the refrigeration cycle device is less than 6.3 kW and the gas side refrigerant connection pipe has a D0 of 4 (i.e., a pipe diameter of 1 / 2 inch).

[0165] A refrigeration cycle apparatus according to a ninth aspect of the ninth group has a refrigerant circuit in which a compressor, a heat source side heat exchanger, a pressure reducing section, a liquid side refrigerant connection pipe, a user side heat exchanger, and a gas side refrigerant connection pipe are connected. The refrigeration cycle apparatus uses the refrigerant of the first aspect described below. The pipe outer diameters of the liquid side refrigerant connection pipe and the gas side refrigerant connection pipe are D0 / 8 inches, and the range of D0 for the liquid side refrigerant connection pipe is "2≦D0≦4", and the range of D0 for the gas side refrigerant connection pipe is "3≦D0≦8".

[0166] The pressure reducing section is not particularly limited and may be an expansion valve or a capillary tube. It is more preferable that the range of D0 in the liquid side refrigerant communication pipe is "2≦D0≦3", and that the range of D0 in the gas side refrigerant communication pipe is "4≦D0≦7".

[0167] This refrigeration cycle device can minimize the decrease in capacity while keeping the GWP sufficiently low by using a refrigerant according to a first aspect described below.

[0168] A refrigeration cycle apparatus according to a tenth aspect of the ninth group is the refrigeration cycle apparatus of the ninth aspect of the ninth group, wherein D0 of the liquid side refrigerant communication pipe is 2 (that is, the pipe diameter is ¼ inch).

[0169] The refrigeration cycle device according to the eleventh aspect of the ninth group is a refrigeration cycle device according to the ninth aspect of the ninth group, wherein the rated refrigeration capacity of the refrigeration cycle device is 7.5 kW or more and the liquid side refrigerant connecting pipe has a D0 of 2.5 (i.e., a pipe diameter of 5 / 16 inch), or the rated refrigeration capacity of the refrigeration cycle device is 2.6 kW or more and less than 7.5 kW and the liquid side refrigerant connecting pipe has a D0 of 2 (i.e., a pipe diameter of 1 / 4 inch), or the rated refrigeration capacity of the refrigeration cycle device is less than 2.6 kW and the liquid side refrigerant connecting pipe has a D0 of 1.5 (i.e., a pipe diameter of 3 / 16 inch).

[0170] The refrigeration cycle device according to the twelfth aspect of the ninth group is a refrigeration cycle device according to the ninth aspect of the ninth group, wherein the rated refrigeration capacity of the refrigeration cycle device is 6.3 kW or more and the liquid side refrigerant connecting pipe has a D0 of 3 (i.e., a pipe diameter of 3 / 8 inch), or the rated refrigeration capacity of the refrigeration cycle device is less than 6.3 kW and the liquid side refrigerant connecting pipe has a D0 of 2 (i.e., a pipe diameter of 1 / 4 inch).

[0171] The refrigeration cycle device according to the thirteenth aspect of the ninth group is a refrigeration cycle device according to the ninth aspect of the ninth group, wherein the rated refrigeration capacity of the refrigeration cycle device is 12.5 kW or more and the liquid side refrigerant connecting pipe has a D0 of 3 (i.e., a pipe diameter of 3 / 8 inch), or the rated refrigeration capacity of the refrigeration cycle device is 6.3 kW or more and less than 12.5 kW and the liquid side refrigerant connecting pipe has a D0 of 2.5 (i.e., a pipe diameter of 5 / 16 inch), or the rated refrigeration capacity of the refrigeration cycle device is less than 6.3 kW and the liquid side refrigerant connecting pipe has a D0 of 2 (i.e., a pipe diameter of 1 / 4 inch).

[0172] The refrigeration cycle device according to the fourteenth aspect of the ninth group is a refrigeration cycle device according to the ninth aspect of the ninth group, wherein the rated refrigeration capacity of the refrigeration cycle device is 6.0 kW or more and the gas side refrigerant connecting pipe has a D0 of 4 (i.e., a pipe diameter of 1 / 2 inch), or the rated refrigeration capacity of the refrigeration cycle device is less than 6.0 kW and the gas side refrigerant connecting pipe has a D0 of 3 (i.e., a pipe diameter of 3 / 8 inch).

[0173] The refrigeration cycle device according to the 15th aspect of the 9th group is a refrigeration cycle device according to the 9th aspect of the 9th group, wherein the rated refrigeration capacity of the refrigeration cycle device is 6.0 kW or more and the gas side refrigerant connecting pipe has a D0 of 4 (i.e., a pipe diameter of 1 / 2 inch), or the rated refrigeration capacity of the refrigeration cycle device is 3.2 kW or more and less than 6.0 kW and the gas side refrigerant connecting pipe has a D0 of 3 (i.e., a pipe diameter of 3 / 8 inch), or the rated refrigeration capacity of the refrigeration cycle device is less than 3.2 kW and the gas side refrigerant connecting pipe has a D0 of 2.5 (i.e., a pipe diameter of 5 / 16 inch).

[0174] A refrigeration cycle device according to a sixteenth aspect of the ninth group is a refrigeration cycle device according to the ninth aspect of the ninth group, wherein the rated refrigeration capacity of the refrigeration cycle device is 25.0 kW or more and the gas side refrigerant connection pipe has a D0 of 7 (i.e., a pipe diameter of 7 / 8 inch), or the rated refrigeration capacity of the refrigeration cycle device is 15.0 kW or more and less than 25.0 kW and the gas side refrigerant connection pipe has a D0 of 6 (i.e., a pipe diameter of 6 / 8 inch), or the rated refrigeration capacity of the refrigeration cycle device is 6.3 kW or more and less than 15.0 kW and the gas side refrigerant connection pipe has a D0 of 5 (i.e., a pipe diameter of 5 / 8 inch), or the rated refrigeration capacity of the refrigeration cycle device is less than 6.3 kW and the gas side refrigerant connection pipe has a D0 of 4 (i.e., a pipe diameter of 1 / 2 inch).

[0175] (10) Group 10 In recent years, from the viewpoint of environmental protection, refrigerants with low global warming potential (GWP) (hereinafter referred to as low-GWP refrigerants) have been considered for use in air conditioners. As low-GWP refrigerants, any of the refrigerants according to the first to forty-second aspects described below are promising.

[0176] However, there is little prior art that considers the aspect of increasing the efficiency of air conditioners that use the above refrigerants. When attempting to apply the above refrigerants to air conditioners, there is a problem of how to achieve high compressor efficiency.

[0177] A compressor according to a first aspect of the tenth group includes a compression section and a motor. The compression section compresses the refrigerant according to any one of the first to forty-second aspects described below. The motor has a rotor including a permanent magnet and drives the compression section.

[0178] The compressor is suitable for a variable displacement compressor in which the motor has a rotor including a permanent magnet, and the rotation speed of the motor can be changed. In this case, in an air conditioner using a refrigerant according to any one of the first to forty-second aspects described below, the rotation speed of the motor can be changed in accordance with the air conditioning load, and therefore, the efficiency of the compressor can be improved.

[0179] A compressor according to a second aspect of the tenth group is the compressor according to the first aspect of the tenth group, in which the rotor is an interior permanent magnet rotor. The interior permanent magnet rotor has permanent magnets embedded in the rotor.

[0180] A compressor according to a third aspect of the tenth group is the compressor according to the first or second aspect of the tenth group, wherein the rotor is formed by laminating a plurality of electromagnetic steel plates in a thickness direction, the thickness of the electromagnetic steel plates being 0.05 mm or more and 0.5 mm or less.

[0181] Generally, the thinner the sheet thickness, the more the eddy current loss can be reduced. However, it is difficult to process electrical steel sheets with thicknesses of less than 0.05 mm, and if the sheet thickness exceeds 0.5 mm, it takes time to siliconize the steel sheet surface and to perform a diffusion process to optimize the Si distribution. Considering these factors, a sheet thickness of 0.05 to 0.5 mm is desirable.

[0182] A compressor according to a fourth aspect of the tenth group is the compressor according to the first or second aspect of the tenth group, wherein the rotor is formed by stacking a plurality of plate-shaped amorphous metals in the plate thickness direction.

[0183] In this compressor, a highly efficient motor with little iron loss is realized, making it possible to improve the efficiency of the compressor.

[0184] A compressor according to a fifth aspect of the tenth group is the compressor according to the first or second aspect of the tenth group, wherein the rotor is formed by stacking a plurality of electromagnetic steel plates containing 5 mass % or more of silicon in the plate thickness direction.

[0185] In this compressor, the use of electrical steel sheets containing an appropriate amount of silicon to reduce hysteresis allows for a motor with low iron loss and high efficiency, making it possible to improve the efficiency of the compressor.

[0186] A compressor according to a sixth aspect of the tenth group is the compressor according to any one of the first aspect to the fifth aspect of the tenth group, in which the permanent magnet is an Nd—Fe—B based magnet.

[0187] In this compressor, a motor capable of increasing the magnetic energy product is realized, and therefore the efficiency of the compressor can be increased.

[0188] A compressor according to a seventh aspect of the tenth group is the compressor according to any one of the first aspect to the sixth aspect of the tenth group, wherein the permanent magnet is formed by grain boundary diffusion of a heavy rare earth.

[0189] In this compressor, the demagnetization resistance of the permanent magnet is improved, and the holding force of the permanent magnet can be increased with a small amount of heavy rare earth, making it possible to improve the efficiency of the compressor.

[0190] A compressor according to an eighth aspect of the tenth group is the compressor according to the sixth aspect of the tenth group, wherein the permanent magnet contains 1 mass % or less of dysprosium.

[0191] In this compressor, the holding force of the permanent magnet is improved, so that the efficiency of the compressor can be increased.

[0192] A compressor according to a ninth aspect of a tenth group is the compressor according to any one of the first aspect to the eighth aspect of the tenth group, in which the average crystal grain size of the permanent magnets is 10 μm or less.

[0193] In this compressor, the demagnetization resistance of the permanent magnet is increased, making it possible to increase the efficiency of the compressor.

[0194] A compressor according to a tenth aspect of the tenth group is the compressor according to the first or second aspect of the tenth group, in which the permanent magnets are flat and a plurality of permanent magnets are embedded in the rotor so as to form a V-shape. The holding force of the portion located in the valley of the V-shape is {1 / (4π)}×10 3 It is set higher than [A / m].

[0195] In this compressor, demagnetization of the permanent magnets is suppressed, and therefore the efficiency of the compressor can be increased.

[0196] A compressor according to an eleventh aspect of the tenth group is the compressor according to the first or second aspect of the tenth group, wherein the rotor is formed by stacking a plurality of high-tensile electromagnetic steel plates having a tensile strength of 400 MPa or more in the plate thickness direction.

[0197] In this compressor, the durability of the rotor during high-speed rotation is improved, making it possible to increase the efficiency of the compressor.

[0198] A compressor according to a twelfth aspect of the tenth group is the compressor according to the eleventh aspect of the tenth group, wherein the permanent magnets are flat plates having a predetermined thickness. The rotor has an accommodating hole, a non-magnetic space, and a bridge. A plurality of permanent magnets are embedded in the accommodating hole. The non-magnetic space extends from the end of each permanent magnet accommodated in the accommodating hole to near the surface of the rotor. The bridge is located outside the non-magnetic space and connects the magnetic poles. The thickness of the bridge is 3 mm or more.

[0199] This compressor has improved durability during high-speed rotation, making it possible to increase the efficiency of the compressor.

[0200] A compressor according to a thirteenth aspect of the tenth group is the compressor according to the first aspect of the tenth group, in which the rotor is a surface magnet rotor. In the surface magnet rotor, permanent magnets are attached to the surface of the rotor.

[0201] A refrigeration cycle apparatus according to a fourteenth aspect of the tenth group is a refrigeration cycle apparatus including any one of the compressors according to the first aspect to the thirteenth aspect of the tenth group.

[0202] (11) Group 11 WO 2015 / 141678 proposes various low-GWP refrigerant mixtures that can replace R410A.

[0203] In addition, as for a refrigeration cycle device using R32 as a refrigerant, for example, as described in Japanese Patent Application Laid-Open No. 2002-54888, it has been proposed to set the piping diameter of the heat transfer tubes of the heat exchanger to 7 mm or more and 10 mm or less in order to improve energy efficiency when R32 is used as a refrigerant.

[0204] However, when a refrigerant according to a first aspect described below is used as a refrigerant with a sufficiently small GWP, no consideration has been given to the piping diameter of the heat transfer tubes of the heat exchanger that can reduce the pressure loss and keep the amount of refrigerant to a low level.

[0205] The present disclosure has been made in consideration of the above points, and aims to provide a refrigeration cycle device that can reduce pressure loss while keeping the amount of refrigerant stored low when using a refrigerant of the first aspect described below.

[0206] A refrigeration cycle apparatus according to a first aspect of the eleventh group includes a refrigerant circuit and a refrigerant. The refrigerant circuit includes a compressor, a heat source-side heat exchanger, a pressure reducing section, and a user-side heat exchanger. The refrigerant is sealed in the refrigerant circuit and is the refrigerant according to the first aspect described below. The heat source-side heat exchanger includes a heat transfer tube with a piping diameter of 6.35 mm or more and less than 10.0 mm.

[0207] The pressure reducing section is not particularly limited, and may be an expansion valve or a capillary tube.

[0208] This refrigeration cycle device uses a refrigerant according to a first aspect described below, thereby making it possible to keep the GWP sufficiently low, reduce pressure loss, and keep the amount of refrigerant held low.

[0209] The refrigeration cycle apparatus according to the second aspect of the 11th group is the refrigeration cycle apparatus according to the first aspect of the 11th group, wherein the heat source side heat exchanger has a heat transfer tube having a piping diameter of any of 6.35 mm, 7.0 mm, 8.0 mm, and 9.5 mm.

[0210] A refrigeration cycle apparatus according to a third aspect of the 11th group is the refrigeration cycle apparatus according to the first or second aspect of the 11th group, wherein the heat source side heat exchanger has a heat transfer tube with a piping diameter of 7.0 mm or more.

[0211] A refrigeration cycle apparatus according to a fourth aspect of the eleventh group includes a refrigerant circuit and a refrigerant. The refrigerant circuit includes a compressor, a heat source side heat exchanger, a pressure reducing section, and a user side heat exchanger. The refrigerant is sealed in the refrigerant circuit and is the refrigerant according to the first aspect described below. The user side heat exchanger includes a heat transfer tube having a piping diameter of 4.0 mm or more and less than 10.0 mm.

[0212] This refrigeration cycle device uses a refrigerant according to a first aspect described below, thereby making it possible to keep the GWP sufficiently low, reduce pressure loss, and keep the amount of refrigerant held low.

[0213] A refrigeration cycle apparatus according to a fifth aspect of the eleventh group is the refrigeration cycle apparatus according to the fourth aspect of the eleventh group, wherein the utilization side heat exchanger has heat transfer tubes with a piping diameter of 8.0 mm or less.

[0214] A refrigeration cycle apparatus according to a sixth aspect of the 11th group is a refrigeration cycle apparatus according to the fourth or fifth aspect of the 11th group, in which the user side heat exchanger has a heat transfer tube having a piping diameter of any one of 4.0 mm, 5.0 mm, 6.35 mm, 7.0 mm, and 8.0 mm.

[0215] (12) Group 12 In recent years, from the viewpoint of environmental protection, refrigerants with low global warming potential (GWP) (hereinafter referred to as low-GWP refrigerants) have been considered for use in air conditioners. As low-GWP refrigerants, any of the refrigerants according to the first to forty-second aspects described below are promising.

[0216] However, there is little prior art that considers the aspect of increasing the efficiency of air conditioners that use the above refrigerants. When attempting to apply the above refrigerants to air conditioners, a challenge remains: how to achieve high compressor output.

[0217] A compressor according to a first aspect of the twelfth group includes a compression section that compresses a refrigerant according to any one of the first to forty-second aspects described below, and an induction motor that drives the compression section.

[0218] As described above, by employing an induction motor in a compressor for compressing a refrigerant according to any one of the first to forty-second aspects described below, it is possible to achieve high output at relatively low cost.

[0219] A compressor according to a second aspect of the twelfth group is the compressor according to the first aspect of the twelfth group, wherein the rotor of the induction motor has a plurality of conductor rods that are rod-shaped conductors and arranged in a ring shape, and end rings that connect the plurality of conductor rods at their axial ends, and at least the conductor rods are made of a metal having an electrical resistance lower than that of aluminum.

[0220] In this compressor, heat generation due to the current flowing through the conductor rods of the induction motor is suppressed, making it possible to achieve high output.

[0221] A compressor according to a third aspect of the twelfth group is the compressor according to the first aspect of the twelfth group, wherein the rotor of the induction motor has a heat dissipation structure.

[0222] In this compressor, the temperature rise of the rotor of the induction motor is suppressed, making it possible to achieve high output.

[0223] A compressor according to a fourth aspect of the 12th group is the compressor according to the third aspect of the 12th group, wherein the rotor of the induction motor has a plurality of conductive rods that are rod-shaped conductors arranged in an annular shape, and end rings that connect the plurality of conductive rods at their axial ends, and the heat dissipation structure is formed in the end rings.

[0224] In this compressor, the heat dissipation structure itself rotates, which not only improves heat dissipation but also causes forced convection due to the rotation, suppressing the rise in the surrounding temperature, making it possible to achieve high output.

[0225] A compressor according to a fifth aspect of the twelfth group is the compressor according to the third or fourth aspect of the twelfth group, in which the heat dissipation structure is a heat sink.

[0226] In this compressor, the heat sink can be molded integrally with the end ring of the induction motor, making it possible to achieve high output at a relatively low cost.

[0227] A compressor according to a sixth aspect of the twelfth group is the compressor according to the first aspect of the twelfth group, further comprising a cooling structure that cools the stator of the induction motor with a refrigerant.

[0228] In this compressor, the induction motor is cooled, making it possible to achieve high output.

[0229] A compressor according to a seventh aspect of the twelfth group is the compressor according to the sixth aspect of the twelfth group, wherein the cooling structure cools the stator by cold heat of a refrigerant flowing through a refrigerant circuit to which the compressor is connected.

[0230] A refrigeration cycle apparatus according to an eighth aspect of the twelfth group is a refrigeration cycle apparatus including any one of the compressors according to any one of the first aspect to the seventh aspect of the twelfth group.

[0231] (13) Group 13 In recent years, from the viewpoint of environmental protection, refrigerants with low global warming potential (GWP) (hereinafter referred to as low-GWP refrigerants) have been considered for use in air conditioners. The refrigerants of the first aspect described below are promising as low-GWP refrigerants.

[0232] However, there is little prior art that considers the aspect of increasing the efficiency of air conditioners that use the above refrigerants. For example, when attempting to apply the above refrigerants to air conditioners, there is a problem of how to achieve high efficiency.

[0233] An air conditioner according to a first aspect of the thirteenth group includes a compressor for compressing a refrigerant according to any one of the first to forty-second aspects described below, and a power conversion device. The power conversion device has a motor for driving the compressor, and is connected between an AC power supply and the motor, has a switching element, and controls the switching element so that the output of the motor reaches a target value.

[0234] In an air conditioner using any of the refrigerants of the first to forty-second aspects described below, the motor rotation speed of the compressor can be changed according to the air conditioning load, thereby achieving high annual energy consumption efficiency [Annual Performance Factor (APF)].

[0235] An air conditioner according to a second aspect of the thirteenth group is the air conditioner according to the first aspect of the thirteenth group, wherein the power conversion device includes a rectifier circuit and a capacitor. The rectifier circuit rectifies AC voltage from an AC power supply. The capacitor is connected in parallel to the output side of the rectifier circuit and smoothes voltage fluctuations caused by switching of the power conversion device.

[0236] In this air conditioner, an electrolytic capacitor is not required on the output side of the rectifier circuit, which prevents the circuit from becoming larger and more expensive.

[0237] An air conditioner according to a third aspect of the thirteenth group is the air conditioner according to the first or second aspect of the thirteenth group, in which the AC power supply is a single-phase power supply.

[0238] An air conditioner according to a fourth aspect of the thirteenth group is the air conditioner according to the first or second aspect of the thirteenth group, in which the AC power supply is a three-phase power supply.

[0239] An air conditioner according to a fifth aspect of a thirteenth group is the air conditioner according to the first aspect of the thirteenth group, wherein the power conversion device is an indirect matrix converter including a converter and an inverter. The converter converts AC voltage of an AC power supply into DC voltage. The inverter converts the DC voltage into AC voltage and supplies it to the motor.

[0240] This air conditioner is highly efficient and does not require an electrolytic capacitor on the output side of the rectifier circuit, which prevents the circuit from becoming larger and more expensive.

[0241] An air conditioner according to a sixth aspect of the thirteenth group is the air conditioner according to the first aspect of the thirteenth group, in which the power conversion device is a matrix converter that directly converts the AC voltage of the AC power supply into AC voltage of a predetermined frequency and supplies it to the motor.

[0242] This air conditioner is highly efficient and does not require an electrolytic capacitor on the output side of the rectifier circuit, which prevents the circuit from becoming larger and more expensive.

[0243] An air conditioner according to a seventh aspect of a thirteenth group is the air conditioner according to the first aspect of the thirteenth group, in which the compressor is any one of a scroll compressor, a rotary compressor, a turbo compressor, and a screw compressor.

[0244] An air conditioner according to an eighth aspect of a thirteenth group is the air conditioner according to any one of the first aspect to the seventh aspect of a thirteenth group, in which the motor is a permanent magnet synchronous motor having a rotor including a permanent magnet.

[0245] (14) Group 14 In recent years, from the viewpoint of environmental protection, refrigerants with low global warming potential (GWP) (hereinafter referred to as low-GWP refrigerants) have been considered for use in air conditioners. The refrigerants of the first aspect described below are promising as low-GWP refrigerants.

[0246] However, there is little prior art that considers the aspect of increasing the efficiency of air conditioners that use the above refrigerants. For example, when attempting to apply the above refrigerants to air conditioners, there is a problem of how to achieve high efficiency.

[0247] An air conditioner according to a first aspect of the 14th group includes a compressor that compresses a refrigerant according to any one of the first to 42nd aspects described below, a motor that drives the compressor, and a connection part that supplies power from an AC power source to the motor without frequency conversion.

[0248] In an air conditioner using a refrigerant according to any one of the first to forty-second aspects described below, the compressor can be driven without interposing a power conversion device between the AC power supply and the motor, making it possible to provide an air conditioner with a relatively inexpensive configuration that is environmentally friendly.

[0249] An air conditioner according to a second aspect of the fourteenth group is the air conditioner according to the first aspect of the fourteenth group, wherein the connection section directly applies the AC voltage of the AC power supply between at least two terminals of the motor.

[0250] An air conditioner according to a third aspect of the fourteenth group is the air conditioner according to the first or second aspect of the fourteenth group, in which the AC power supply is a single-phase power supply.

[0251] An air conditioner according to a fourth aspect of the fourteenth group is the air conditioner according to any one of the first aspect to the third aspect of the fourteenth group, in which a starter circuit is connected in series to one terminal of the motor.

[0252] An air conditioner according to a fifth aspect of a fourteenth group is the air conditioner according to the fourth aspect of the fourteenth group, in which the starter circuit is a circuit in which a positive temperature coefficient thermistor and an operating capacitor are connected in parallel.

[0253] In an air conditioner using a refrigerant according to any one of the first to forty-second aspects described below, after the compressor is started, the positive temperature coefficient thermistor heats up by itself, increasing its resistance value, and the operation circuit is essentially switched to one using an operation capacitor, so that the compressor is able to output rated torque at the appropriate time.

[0254] An air conditioner according to a sixth aspect of the fourteenth group is the air conditioner according to the first or second aspect of the fourteenth group, in which the AC power supply is a three-phase power supply.

[0255] This air conditioner does not require a starter circuit and is therefore relatively inexpensive.

[0256] An air conditioner according to a seventh aspect of the fourteenth group is the air conditioner according to any one of the first aspect to the sixth aspect of the fourteenth group, in which the motor is an induction motor.

[0257] In this air conditioner, the motor is capable of high output at a relatively low cost, making it possible to increase the efficiency of the air conditioner.

[0258] (15) Group 15 2. Description of the Related Art Hot water production apparatuses that generate hot water using boilers or electric heaters have been widely used for some time, and there are also hot water production apparatuses that use heat pump units as their heat source.

[0259] Conventional hot water production apparatuses that employ a heat pump unit often use carbon dioxide as a refrigerant in the heat pump unit. However, there is a demand for a system that produces hot water more efficiently than conventional hot water production apparatuses.

[0260] A hot water production apparatus according to a first aspect of the fifteenth group uses the refrigerant according to the first aspect described below as a refrigerant. This hot water production apparatus includes a compressor, a first heat exchanger on the heat source side, an expansion mechanism, and a second heat exchanger on the user side. The second heat exchanger heats the first water by exchanging heat between the mixed refrigerant flowing therethrough and the first water.

[0261] This hot water production device uses the above-mentioned mixed refrigerant as the refrigerant instead of the carbon dioxide that has been commonly used in the past, which allows for efficient production of hot water.

[0262] A hot water producing apparatus according to a second aspect of the fifteenth group is the hot water producing apparatus according to the first aspect of the fifteenth group, further comprising a tank and a circulation flow path. The circulation flow path circulates the first water between the tank and the second heat exchanger.

[0263] A hot water producing apparatus according to a third aspect of the fifteenth group is the hot water producing apparatus of the first aspect of the fifteenth group, further comprising a first circulation flow path, a second circulation flow path, a third heat exchanger, and a tank. The first circulation flow path circulates first water heated by the second heat exchanger. The second circulation flow path is a circulation flow path separate from the first circulation flow path. The third heat exchanger heats the second water flowing through the second circulation flow path by exchanging heat between the first water flowing through the first circulation flow path and the second water flowing through the second circulation flow path. The tank stores the second water heated by the third heat exchanger.

[0264] A hot water producing apparatus according to a fourth aspect of the fifteenth group is the hot water producing apparatus according to the first aspect of the fifteenth group, further comprising a first circulation flow path and a tank. The first circulation flow path circulates the first water heated by the second heat exchanger. A portion of the first circulation flow path is disposed within the tank, and heat is exchanged between the first water flowing through the first circulation flow path and the second water in the tank, thereby heating the second water in the tank.

[0265] A hot water producing apparatus according to a fifth aspect of the fifteenth group is the hot water producing apparatus of the first aspect of the fifteenth group, further comprising a tank, a first circulation flow path, a third heat exchanger, a second circulation flow path, and a third flow path. The first circulation flow path circulates the first water between the second heat exchanger and the tank. The second circulation flow path circulates the first water between the third heat exchanger and the tank. The third flow path is a flow path separate from the first circulation flow path and the second circulation flow path. The third heat exchanger heats the third water flowing through the third flow path by exchanging heat between the first water flowing from the tank and the third water flowing through the third flow path.

[0266] A hot water producing apparatus according to a sixth aspect of the fifteenth group is the hot water producing apparatus according to the first aspect of the fifteenth group, further comprising a tank, a first circulation flow path, and a second flow path. The first circulation flow path circulates the first water between the tank and the second heat exchanger. The second flow path is a flow path separate from the first circulation flow path. A portion of the second flow path is disposed within the tank, and heat is exchanged between the first water in the tank and the second water flowing through the second flow path, thereby heating the second water flowing through the second flow path.

[0267] A hot water producing apparatus according to a seventh aspect of the fifteenth group is the hot water producing apparatus according to the first aspect of the fifteenth group, further comprising a tank for storing first water and a flow path through which second water flows. A portion of the flow path is disposed within the tank. The second heat exchanger heats the first water stored in the tank within the tank. The first water stored in the tank heats the second water flowing through the flow path.

[0268] A hot water producing apparatus according to an eighth aspect of the fifteenth group is the hot water producing apparatus according to the first aspect of the fifteenth group, further comprising a tank and a flow path for flowing first water from a water supply source to the tank. The second heat exchanger heats the first water flowing through the flow path.

[0269] A hot water producing apparatus according to a ninth aspect of the fifteenth group is the hot water producing apparatus according to any one of the first aspect to the eighth aspect of the fifteenth group, further comprising a fourth heat exchanger on the user side and a fourth circulation flow path. The fourth heat exchanger is a heat exchanger separate from the second heat exchanger. Fourth water for cooling or heating flows through the fourth circulation flow path. The fourth heat exchanger cools or heats the fourth water by exchanging heat between the mixed refrigerant flowing therein and the fourth water flowing through the fourth circulation flow path.

[0270] (16) Group 16 Conventionally, there has been a refrigeration cycle apparatus equipped with a heat exchanger, as described in, for example, Japanese Patent Laid-Open Publication No. 11-256358. Like the heat exchanger of this refrigeration cycle apparatus, some use copper pipes for the heat transfer tubes. However, heat exchangers using copper pipes for the heat transfer tubes are expensive.

[0271] As described above, a refrigeration cycle device equipped with a heat exchanger has a problem of reducing material costs.

[0272] A refrigeration cycle device according to a first aspect of the 16th group includes a refrigerant according to the first aspect described below, an evaporator that evaporates the refrigerant, and a condenser that condenses the refrigerant, wherein at least one of the evaporator and the condenser has a plurality of fins made of aluminum or an aluminum alloy and a plurality of heat transfer tubes made of aluminum or an aluminum alloy, and is a heat exchanger that exchanges heat between the refrigerant flowing inside the heat transfer tubes and a fluid flowing along the fins, and the refrigerant is configured to circulate between the evaporator and the condenser to repeat the refrigeration cycle.

[0273] This refrigeration cycle device has multiple fins made of aluminum or aluminum alloy and multiple heat transfer tubes made of aluminum or aluminum alloy, so the material costs of the heat exchanger can be reduced compared to, for example, using copper pipes for the heat transfer tubes.

[0274] A refrigeration cycle apparatus according to a second aspect of the 16th group is a refrigeration cycle apparatus according to a first aspect of the 16th group, wherein each of the plurality of fins has a plurality of holes, a plurality of heat transfer tubes pass through the plurality of holes in the plurality of fins, and the outer peripheries of the plurality of heat transfer tubes are in close contact with the inner peripheries of the plurality of holes.

[0275] A refrigeration cycle device according to a third aspect of the 16th group is a refrigeration cycle device according to a first aspect of the 16th group, wherein the plurality of heat transfer tubes are a plurality of flat tubes, and the flat portions of adjacent flat tubes are arranged facing each other.

[0276] The refrigeration cycle device according to the fourth aspect of the 16th group is a refrigeration cycle device according to the third aspect of the 16th group, in which each of the multiple fins is bent into a wave shape and arranged between the flat surfaces of adjacent flat tubes, and is connected so as to transfer heat to the flat surfaces.

[0277] The refrigeration cycle device according to the fifth aspect of the 16th group is a refrigeration cycle device according to the third aspect of the 16th group, wherein each of the plurality of fins has a plurality of notches, and a plurality of flat tubes are inserted into the plurality of notches of the plurality of fins and connected so as to transfer heat to the plurality of fins.

[0278] (17) Group 17 BACKGROUND ART Conventionally, a multi-type air conditioner has been known as an air conditioner that adjusts the air in multiple rooms within a room with a single unit.

[0279] A multi-type air conditioner has a first indoor unit and a second indoor unit located in different rooms. In this type of air conditioner, a refrigerant is circulated between the first indoor unit and the second indoor unit, so the amount of refrigerant filled in the air conditioner is large.

[0280] 2. Description of the Related Art Air conditioners that condition the air in multiple rooms indoors have a problem of reducing the amount of refrigerant filled in the air conditioner.

[0281] The air conditioning apparatus according to a first aspect of the 17th group includes a compressor, a user-side heat exchanger that exchanges heat with first air, a heat-source-side heat exchanger that exchanges heat with second air, a refrigerant containing a refrigerant according to the first aspect described below and circulating through the compressor, the user-side heat exchanger, and the heat-source-side heat exchanger to repeat a refrigeration cycle, a first duct that supplies the first air to a plurality of rooms in a room, and a casing that is connected to the first duct and has a user-side space that houses the user-side heat exchanger, and is configured to send the first air to the first duct after heat exchange with the refrigerant in the user-side heat exchanger.

[0282] In this air conditioner, the number of indoor heat exchangers is reduced compared to an air conditioner in which multiple indoor units are placed in multiple rooms, so the amount of refrigerant filled in the air conditioner can be reduced.

[0283] An air conditioning apparatus according to a second aspect of the 17th group is the air conditioning apparatus according to the first aspect of the 17th group, comprising: a second duct that takes in the first air from the room; a user-side unit that has the casing and connects the casing to the second duct and is configured to guide the first air taken in from the room to the user-side heat exchanger; and a heat-source-side unit that houses the heat-source-side heat exchanger and is separate from the user-side unit.

[0284] In this air conditioner, the user side unit and the heat source side unit are separate entities, which makes it easy to install the air conditioner.

[0285] An air conditioning apparatus according to a third aspect of the 17th group is the air conditioning apparatus according to the first aspect of the 17th group, comprising: a third duct that takes in the first air from outdoors; a user-side unit that has the casing and connects the casing to the third duct and is configured to guide the first air taken in from outdoors to the user-side heat exchanger; and a heat-source-side unit that houses the heat-source-side heat exchanger and is separate from the user-side unit.

[0286] In this air conditioner, the user side unit and the heat source side unit are separate entities, which makes it easy to install the air conditioner.

[0287] An air conditioning apparatus according to a fourth aspect of the 17th group is the air conditioning apparatus according to the first aspect of the 17th group, and is provided with a second duct connected to a casing for supplying the first air taken in from inside the room to the use-side space, the casing having a partition plate separating the heat source-side space through which the second air taken in from outside passes from the use-side space and blocking the flow of air between the heat source-side space and the use-side space, and the heat source-side heat exchanger is arranged in the heat source-side space.

[0288] In this air conditioning system, the user-side heat exchanger and the heat source-side heat exchanger are housed in a single casing, with the user-side space and the heat source-side space separated by a partition plate, making it easier to install the air conditioning system in a limited space.

[0289] (18) Group 18 In a refrigeration cycle using a non-azeotropic refrigerant mixture, if the refrigerant is evaporated at a constant pressure in the heat source side heat exchanger, the heat exchange capacity is not fully exerted.

[0290] A refrigeration cycle according to a first aspect of the 18th group is a refrigeration cycle using the refrigerant of the first aspect described below, and includes a compressor, a heat source-side heat exchanger, an expansion mechanism, a user-side heat exchanger, and a pressure reduction mechanism. The pressure reduction mechanism reduces the pressure of the mixed refrigerant flowing through the heat source-side heat exchanger functioning as an evaporator, between the inlet and the outlet of the heat source-side heat exchanger.

[0291] In this system, when the refrigerant evaporates in the heat source heat exchanger, the pressure reduction mechanism reduces the refrigerant pressure along the way. This reduces the difference in evaporation temperature between the inlet and outlet of the heat source heat exchanger, which occurs when refrigerant evaporates at a constant pressure. As a result, heat exchange capacity can be secured and the performance of the refrigeration cycle is improved.

[0292] A refrigeration cycle according to a second aspect of the eighteenth group is the refrigeration cycle according to the first aspect of the eighteenth group, in which the pressure reducing mechanism reduces the pressure of the mixed refrigerant flowing through the heat source side heat exchanger in accordance with a temperature gradient of the mixed refrigerant.

[0293] A refrigeration cycle according to a third aspect of the 18th group is the refrigeration cycle according to the first or second aspect of the 18th group, in which the heat source side heat exchanger has a first heat exchange section and a second heat exchange section, and the pressure reducing mechanism is disposed between the first heat exchange section and the second heat exchange section.

[0294] A refrigeration cycle according to a fourth aspect of the 18th group is the refrigeration cycle according to any one of the first to fourth aspects of the 18th group, wherein the utilization side heat exchanger is disposed in a utilization unit. The utilization side heat exchanger has a third heat exchange section located on the front side of the utilization unit and a fourth heat exchange section located on the rear side of the utilization unit. The upper part of the fourth heat exchange section is located near the upper part of the third heat exchange section. The third heat exchange section extends obliquely downward from its upper part toward the front side of the utilization unit. The fourth heat exchange section extends obliquely downward from its upper part toward the rear side of the utilization unit. The volume of the refrigerant flow path of the third heat exchange section is larger than the volume of the refrigerant flow path of the fourth heat exchange section.

[0295] Here, the third heat exchanger located on the front side of the utilization unit has a larger refrigerant flow path volume than the fourth heat exchanger, so that the third heat exchanger, which has a larger refrigerant flow path volume, performs more heat exchange between the mixed refrigerant and the air on the front side of the utilization unit where the speed of air passing through the heat exchanger tends to be faster.

[0296] (19) 19th Group The control circuit of an air conditioner includes an inverter circuit and the like that generates heat. For this reason, as disclosed in Japanese Patent Application Laid-Open No. 62-69066, the control circuit is cooled. When any of the refrigerants described in the first to forty-second aspects below is used as the refrigerant for the air conditioner, some of them are less efficient than the R32 refrigerant. For this reason, in an air conditioner using any of the refrigerants described in the first to forty-second aspects below, the power consumption of the compressor increases, and the amount of heat generated by the control circuit, such as the inverter circuit, increases. Therefore, the control circuit needs to be cooled.

[0297] An air conditioner according to a first aspect of the 19th group includes a printed circuit board and a refrigerant jacket. A power element is attached to the printed circuit board. The power element is thermally connected to the refrigerant jacket. A refrigerant flows through the refrigerant jacket. The power element is cooled by the refrigerant flowing through the refrigerant jacket. The refrigerant is any one of the refrigerants according to the first to 42nd aspects described below.

[0298] An air conditioner according to a second aspect of the nineteenth group is the air conditioner of the first aspect of the nineteenth group, further comprising a refrigerant circuit that performs a refrigeration cycle. The refrigerant flowing through the refrigerant jacket circulates through the refrigerant circuit.

[0299] An air conditioner according to a third aspect of the 19th group is the air conditioner according to the first aspect of the 19th group, further comprising a refrigerant circuit that performs a refrigeration cycle. The refrigerant jacket has pipes that seal in the refrigerant. The pipes do not exchange refrigerant with the refrigerant circuit.

[0300] (20) Group 20 With the recent rise in environmental awareness, there is a demand for air conditioners that use refrigerants with low global warming potential (GWP). In such cases, it is desirable for the air conditioner to be able to perform dehumidification operation while maintaining comfort.

[0301] An air conditioner according to a first aspect of the 20th group includes a refrigerant circuit in which a compressor, an outdoor heat exchanger, a pressure reducer, a first indoor heat exchanger, a dehumidifying pressure reducer, and a second indoor heat exchanger are connected in a ring shape. The air conditioner performs dehumidifying operation with the pressure reducer in an open state using the dehumidifying pressure reducer. The air conditioner uses as its refrigerant any of the refrigerants according to the first to forty-second aspects described below.

[0302] An air conditioner according to a second aspect of the twentieth group is the air conditioner of the first aspect of the twentieth group, wherein the dehumidifying pressure reducing device is disposed between the first indoor heat exchanger and the second indoor heat exchanger.

[0303] An air conditioner according to a third aspect of the twentieth group is the air conditioner according to the first or second aspect of the twentieth group, in which the dehumidifying pressure reducing device is a solenoid valve.

[0304] An air conditioner according to a fourth aspect of the twentieth group is the air conditioner according to the first or second aspect of the twentieth group, in which the dehumidifying pressure reducing device is an expansion valve.

[0305] (21) Group 21 Various air conditioners with dehumidifying functions have been developed. For example, there are air conditioners in which the indoor heat exchanger is divided into two heat exchangers connected in series. During dehumidification, the refrigerant condenses in one of the two indoor heat exchangers and evaporates in the other.

[0306] However, in such an air conditioner, the indoor heat exchanger and the mechanism for controlling the flow of refrigerant in the indoor heat exchanger are complicated.

[0307] An air conditioner having such a dehumidifying function has a problem of simplifying the configuration of the refrigerant circuit.

[0308] The air conditioner according to the first aspect of the 21st group comprises a refrigerant according to the first aspect described below, a compressor that compresses the refrigerant, a first heat exchanger that evaporates the refrigerant in an evaporation region, a pressure reduction section that reduces the pressure of the refrigerant, and a second heat exchanger that condenses the refrigerant, and is configured to be able to switch between a first operation in which air that has been heat exchanged in the first heat exchanger, with the entire first heat exchanger serving as the evaporation region, is blown into the room, and a second operation in which air that has been heat exchanged in the first heat exchanger, with only a portion of the first heat exchanger serving as the evaporation region, is blown into the room.

[0309] This air conditioner is capable of dehumidifying by evaporating the refrigerant in the evaporation zone and has a simplified refrigerant circuit.

[0310] An air conditioner according to a second aspect of the 21st group is an air conditioner according to a first aspect of the 21st group, wherein the first heat exchanger is an auxiliary heat exchanger, a main heat exchanger is provided downwind of the auxiliary heat exchanger, and the air conditioner is configured to be switchable between a first operation in which the entire auxiliary heat exchanger is used as an evaporation area and air that has been heat exchanged between the auxiliary heat exchanger and the main heat exchanger is blown into the room, and a second operation in which only a portion of the first heat exchanger is used as an evaporation area and air that has been heat exchanged between the auxiliary heat exchanger and the main heat exchanger is blown into the room.

[0311] This air conditioner can suppress deterioration of the COP due to dehumidifying operation during cooling operation.

[0312] The air conditioner according to the third aspect of the 21st group is an air conditioner according to the first or second aspect of the 21st group, which is configured to switch from the first operation to the second operation depending on the load in a dehumidification operation mode for dehumidifying the room.

[0313] When this air conditioner selects dehumidification mode and starts operation, if the load is high, sufficient dehumidification is possible even in first operation because the temperature of the first heat exchanger is low, so by starting first operation, it is possible to efficiently perform dehumidification and cooling simultaneously. Then, as the room temperature drops and the load decreases, the evaporation temperature becomes too high in first operation to dehumidify, so at that point it switches to second operation. This reduces the impact of COP deterioration due to dehumidification operation.

[0314] The air conditioner according to the fourth aspect of the 21st group is the air conditioner according to the third aspect of the 21st group, and detects the load based on the difference between the set temperature and the temperature of the indoor air with which the first heat exchanger exchanges heat.

[0315] An air conditioner according to a fifth aspect of the 21st group is the air conditioner according to the third or fourth aspect of the 21st group, in which the load is detected based on the frequency of the compressor.

[0316] An air conditioner according to the sixth aspect of the 21st group is an air conditioner according to any one of the first aspect to the fifth aspect of the 21st group, which is configured to perform the first operation without switching from the first operation to the second operation when the evaporation temperature of the refrigerant in the first heat exchanger is lower than a predetermined temperature in a dehumidification operation mode for dehumidifying the room.

[0317] In this air conditioner, when the load decreases to a predetermined value or less, the evaporation temperature is lower than the predetermined value, so dehumidification is possible without switching from the first operation mode to the second operation mode.

[0318] An air conditioner according to the seventh aspect of the 21st group is an air conditioner according to any one of the first aspect to the sixth aspect of the 21st group, in which, in the second operation, a part other than a part of the first heat exchanger is in a superheated region where the refrigerant is at or above the evaporation temperature.

[0319] (22) Group 22 There have been no satisfactory proposals so far regarding the configuration of a refrigerant circuit that achieves highly efficient operation using a refrigerant with a low global warming potential.

[0320] A refrigeration cycle apparatus according to a first aspect of the 22nd group includes a refrigerant circuit including a compressor, a heat source-side heat exchanger, an expansion mechanism, and a user-side heat exchanger. The refrigerant circuit is filled with a refrigerant according to the first aspect described below. At least during a predetermined operation, the flow of the refrigerant and the flow of a heat medium exchanging heat with the refrigerant are counterflows in at least one of the heat source-side heat exchanger and the user-side heat exchanger.

[0321] In the refrigeration cycle apparatus of the first aspect of the 22nd group, a refrigerant of the first aspect described below, which has a low global warming potential, is used, and a highly efficient operation is realized by effectively utilizing the heat exchanger.

[0322] A refrigeration cycle device according to a second aspect of the 22nd group is a refrigeration cycle device according to a first aspect of the 22nd group, in which, during operation of the refrigeration cycle device using the heat source side heat exchanger as an evaporator, the flow of the refrigerant and the flow of the heat medium exchanging heat with the refrigerant in the heat source side heat exchanger are counterflows.

[0323] A refrigeration cycle apparatus according to a third aspect of the 22nd group is a refrigeration cycle apparatus according to the first or second aspect of the 22nd group, in which, during operation of the refrigeration cycle apparatus using the heat source side heat exchanger as a condenser, the flow of the refrigerant and the flow of the heat medium exchanging heat with the refrigerant in the heat source side heat exchanger are counterflows.

[0324] Here, even when a refrigerant is used that makes it difficult to achieve a temperature difference between the refrigerant and the heat medium at the outlet side of the condenser due to the effect of temperature glide, it is relatively easy to maintain a temperature difference from the inlet to the outlet of the condenser, thereby achieving highly efficient operation of the refrigeration cycle device.

[0325] A refrigeration cycle device according to a fourth aspect of the 22nd group is a refrigeration cycle device according to any one of the first aspect to the third aspect of the 22nd group, in which, during operation of the refrigeration cycle device using the utilization side heat exchanger as an evaporator, the flow of the refrigerant and the flow of the heat medium exchanging heat with the refrigerant in the utilization side heat exchanger are counterflows.

[0326] A refrigeration cycle device according to a fifth aspect of the 22nd group is a refrigeration cycle device according to any one of the first aspect to the fourth aspect of the 22nd group, in which, during operation of the refrigeration cycle device using the utilization side heat exchanger as a condenser, the flow of the refrigerant and the flow of the heat medium exchanging heat with the refrigerant are countercurrents in the utilization side heat exchanger.

[0327] A refrigeration cycle apparatus according to a sixth aspect of the 22nd group is the refrigeration cycle apparatus according to any one of the first aspect to the fifth aspect of the 22nd group, in which the heat medium is air.

[0328] A refrigeration cycle apparatus according to a seventh aspect of the 22nd group is the refrigeration cycle apparatus according to any one of the first aspect to the fifth aspect of the 22nd group, in which the heat medium is liquid.

[0329] (23) Group 23 In a refrigeration cycle device using a refrigerant according to the first aspect described below as a refrigerant with a sufficiently small GWP, the outer diameters of the liquid side refrigerant communication pipe and the gas side refrigerant communication pipe are increased in order to suppress pressure loss, which may result in increased costs.

[0330] The present disclosure has been made in consideration of the above points, and aims to provide a refrigeration cycle device that suppresses increases in cost when using a refrigerant according to a first aspect described below.

[0331] A refrigeration cycle apparatus according to a first aspect of the 23rd group is a refrigeration cycle apparatus having a refrigerant circuit in which a compressor, a heat source side heat exchanger, a pressure reducing section, a liquid side refrigerant connection pipe, a user side heat exchanger, and a gas side refrigerant connection pipe are connected, in which a refrigerant according to the first aspect described below is used, and the liquid side refrigerant connection pipe and the gas side refrigerant connection pipe are made of aluminum or an aluminum alloy.

[0332] In this refrigeration cycle device, when using the refrigerant of the first aspect described below, even if the diameters of the liquid side refrigerant connection pipe and the gas side refrigerant connection pipe are increased to suppress pressure loss, by using pipes made of aluminum or an aluminum alloy, it is possible to suppress cost increases.

[0333] A refrigeration cycle apparatus according to a second aspect of the 23rd group is the refrigeration cycle apparatus according to the first aspect of the 23rd group, wherein the thickness of the liquid side refrigerant communication pipe is equal to or greater than the thickness of a liquid side refrigerant communication pipe made of copper or a copper alloy and used in a refrigeration cycle apparatus having the same rated refrigeration capacity as the refrigeration cycle apparatus, and the thickness of the gas side refrigerant communication pipe is equal to or greater than the thickness of a gas side refrigerant communication pipe made of copper or a copper alloy and used in a refrigeration cycle apparatus having the same rated refrigeration capacity as the refrigeration cycle apparatus.

[0334] A refrigeration cycle apparatus according to a third aspect of the 23rd group is the refrigeration cycle apparatus of the first aspect of the 23rd group, wherein the outer diameter of the liquid side refrigerant communication pipe is equal to or larger than the outer diameter of a liquid side refrigerant communication pipe made of copper or a copper alloy and used in a refrigeration cycle apparatus having the same rated refrigeration capacity as the refrigeration cycle apparatus, and the outer diameter of the gas side refrigerant communication pipe is equal to or larger than the outer diameter of a gas side refrigerant communication pipe made of copper or a copper alloy and used in a refrigeration cycle apparatus having the same rated refrigeration capacity as the refrigeration cycle apparatus.

[0335] A refrigeration cycle apparatus according to a fourth aspect of the 23rd group is a refrigeration cycle apparatus according to the third aspect of the 23rd group, wherein the outer diameter of the liquid side refrigerant connecting pipe is the same as the outer diameter of the liquid side refrigerant connecting pipe made of copper or a copper alloy and used in a refrigeration cycle apparatus having the same rated refrigeration capacity as the refrigeration cycle apparatus.

[0336] A refrigeration cycle apparatus according to a fifth aspect of the 23rd group is the refrigeration cycle apparatus according to the third aspect of the 23rd group, wherein the outer diameter of the liquid side refrigerant communication pipe is in the range of 6.4 mm to 12.7 mm, and the outer diameter of the gas side refrigerant communication pipe is in the range of 12.7 mm to 25.4 mm.

[0337] The refrigeration mining device according to the sixth aspect of the 23rd group is a refrigeration cycle device according to the fifth aspect of the 23rd group, in which the rated refrigeration capacity of the refrigeration cycle device is 8.5 kW or more and 10.0 kW or less, and the outer diameter of the gas side refrigerant connection pipe is 19.1 mm.

[0338] The refrigeration cycle device according to the seventh aspect of the 23rd group is the refrigeration cycle device according to the fifth aspect of the 23rd group, wherein the rated refrigeration capacity of the refrigeration cycle device is 25.0 kW or more and 28 kW or less, and the outer diameter of the gas side refrigerant connection pipe is 25.4 mm.

[0339] A refrigeration cycle apparatus according to an eighth aspect of the 23rd group is the refrigeration cycle apparatus according to the first aspect of the 23rd group, The rated refrigeration capacity of the refrigeration cycle device is 25.0 kW or more, and the outer diameter of the gas side refrigerant connection pipe is 25.4 mm, or The rated refrigeration capacity of the refrigeration cycle device is 19.0 kW or more but less than 25.0 kW, and the outer diameter of the gas side refrigerant connection pipe is 22.2 mm, or The rated refrigeration capacity of the refrigeration cycle device is 8.5kW or more and 19.0kW or less, and the outer diameter of the gas side refrigerant connection pipe is 19.1mm, or The rated refrigeration capacity of the refrigeration cycle device is 5.0 kW or more but less than 8.5 kW, and the outer diameter of the gas side refrigerant connection pipe is 15.9 mm, or The rated refrigeration capacity of the refrigeration cycle device is less than 5.0 kW, and the outer diameter of the gas side refrigerant connection pipe is 12.7 mm. Either:

[0340] A refrigeration cycle apparatus according to a ninth aspect of the 23rd group is the refrigeration cycle apparatus according to the first aspect of the 23rd group, The rated refrigeration capacity of the refrigeration cycle device is 19.0 kW or more, and the outer diameter of the liquid side refrigerant connection pipe is 12.7 mm, or The rated refrigeration capacity of the refrigeration cycle device is 5.0 kW or more but less than 19.0 kW, and the outer diameter of the liquid side refrigerant connection pipe is 9.5 mm, or The rated refrigeration capacity of the refrigeration cycle device is less than 5.0 kW, and the outer diameter of the liquid side refrigerant connection pipe is 6.4 mm. Either:

[0341] A refrigeration cycle device according to the tenth aspect of the 23rd group is a refrigeration cycle device according to any one of the first aspect to the ninth aspect of the 23rd group, in which the material used for the liquid side refrigerant connecting pipe and the gas side refrigerant connecting pipe is any one of A3003TD, A3003TDS-O, A3005TDS-O and A6063TDS-T84 as specified in the Japanese Industrial Standard "JIS H 4080".

[0342] (24) Group 24 In refrigeration cycles using refrigerants with low global warming potential, there have been no sufficient proposals so far on how to achieve power load leveling.

[0343] A heat storage device according to a first aspect of the 24th group includes a heat storage tank and a heat storage heat exchanger. A heat storage medium is stored in the heat storage tank. The heat storage heat exchanger is immersed in the heat storage medium in the heat storage tank. The heat storage heat exchanger is connected to a refrigerant supply device. The heat storage heat exchanger cools the heat storage medium with a refrigerant according to the first aspect, which will be described later, supplied from the refrigerant supply device.

[0344] In the heat storage device of the first aspect of the 24th group, a refrigerant of the first aspect described below, which has a low global warming potential, is supplied from a refrigerant supply device to cool the heat storage medium and store cold energy in the heat storage tank, thereby contributing to the leveling of the power load.

[0345] (25) 25th Group Conventional refrigeration systems include systems equipped with a high-temperature (primary) refrigeration cycle and a low-temperature (secondary) refrigeration cycle. For example, there are cascade refrigeration systems that use an HFC refrigerant (such as R410A or R32) or an HFO refrigerant as the refrigerant in the high-temperature refrigeration cycle and a carbon dioxide refrigerant as the refrigerant in the low-temperature refrigeration cycle. There is a demand for more efficient operation in refrigeration systems that combine two cycles, such as cascade refrigeration systems.

[0346] A refrigeration apparatus according to a first aspect of the 25th group includes a first cycle and a second cycle. The first cycle has a first compressor, a first radiator, a first expansion mechanism, and a first heat absorber connected to it. A first refrigerant circulates in the first cycle. The second cycle has a second radiator and a second heat absorber connected to it. A second refrigerant circulates in the second cycle. The first heat absorber and the second radiator are a heat exchanger. This heat exchanger exchanges heat between the first refrigerant flowing through the first heat absorber and the second refrigerant flowing through the second radiator. At least one of the first refrigerant and the second refrigerant is a refrigerant according to the first aspect described below.

[0347] Here, by employing a refrigerant according to a first aspect described below, it becomes possible to improve the efficiency of heat exchange in the heat exchanger.

[0348] A refrigeration apparatus according to a second aspect of the 25th group includes a first cycle and a second cycle. The first cycle has a first compressor, a first radiator, a first expansion mechanism, and a first heat absorber connected to it. A first refrigerant circulates in the first cycle. The second cycle has a second radiator and a second heat absorber connected to it. A second refrigerant circulates in the second cycle. The first radiator and the second heat absorber are a heat exchanger. This heat exchanger exchanges heat between the first refrigerant flowing through the first radiator and the second refrigerant flowing through the second heat absorber. At least one of the first refrigerant and the second refrigerant is the refrigerant of the first aspect described below.

[0349] Here, by employing a refrigerant according to a first aspect described below, it becomes possible to improve the efficiency of heat exchange in the heat exchanger.

[0350] A refrigeration apparatus according to a third aspect of the 25th group is the refrigeration apparatus according to the first aspect of the 25th group, wherein the second cycle further includes a second compressor and a second expansion mechanism. The first refrigerant flowing through the first radiator of the first cycle releases heat to outside air. The first refrigerant is the above-described mixed refrigerant. The second refrigerant is carbon dioxide.

[0351] A refrigeration apparatus according to a fourth aspect of the 25th group is the refrigeration apparatus according to the first aspect of the 25th group, wherein the second cycle further includes a second compressor and a second expansion mechanism. The first refrigerant flowing through the first radiator of the first cycle releases heat to outside air. The first refrigerant is the mixed refrigerant described above. The second refrigerant is the mixed refrigerant described above.

[0352] A refrigeration apparatus according to a fifth aspect of the 25th group is the refrigeration apparatus according to the first aspect of the 25th group, wherein the second cycle further includes a second compressor and a second expansion mechanism. The first refrigerant flowing through the first radiator of the first cycle releases heat to outside air. The first refrigerant is R32. The second refrigerant is the above-described mixed refrigerant.

[0353] A refrigeration apparatus according to a sixth aspect of the 25th group is the refrigeration apparatus according to the first aspect of the 25th group, wherein the first refrigerant flowing through the first radiator of the first cycle releases heat to outside air. The first refrigerant is the mixed refrigerant described above. The second refrigerant is a liquid medium.

[0354] A refrigeration apparatus according to a seventh aspect of the 25th group is the refrigeration apparatus according to the second aspect of the 25th group, wherein the second cycle further includes a second compressor and a second expansion mechanism. The first refrigerant flowing through the first heat absorber of the first cycle absorbs heat from outside air. The first refrigerant is the mixed refrigerant described above. The second refrigerant has a lower saturation pressure at a predetermined temperature than the mixed refrigerant.

[0355] (26) Details of refrigerants in each of the above groups The refrigerant employed in each of the above groups 1 to 25 is a refrigerant of the first aspect, which is the following first refrigerant X, second refrigerant Y, third refrigerant A, fourth refrigerant B, fifth refrigerant C, sixth refrigerant D, or seventh refrigerant E.

[0356] The first refrigerant X comprises CO2, trans-1,2-difluoroethylene (HFO-1132(E)), difluoromethane (R32), and 2,3,3,3-tetrafluoro-1-propene (R1234yf).

[0357] The second refrigerant Y comprises cis-1,2-difluoroethylene (HFO-1132(Z)) and 2,3,3,3-tetrafluoropropene (HFO-1234yf).

[0358] The third refrigerant A includes trans-1,2-difluoroethylene (HFO-1132(E)), difluoromethane (HFC-32), and 2,3,3,3-tetrafluoropropene (HFO-1234yf).

[0359] The fourth refrigerant B includes HFO-1132(E), HFO-1123, and HFO-1234yf.

[0360] The fifth refrigerant C includes HFO-1132(E) and HFO-1234yf.

[0361] The sixth refrigerant D includes HFC-32, HFO-1234yf, and at least one of 1,1-difluoroethylene (HFO-1132a) and tetrafluoroethylene (FO-1114).

[0362] The seventh refrigerant E includes difluoromethane (R32), carbon dioxide (CO2), pentafluoroethane (R125), 1,1,1,2-tetrafluoroethane (R134a), and 2,3,3,3-tetrafluoropropene (R1234yf).

[0363] Preferably, in each of the above first to twenty-fifth groups, any of the refrigerants according to the following second to forty-second aspects is employed as the refrigerant.

[0364] (26-1) First refrigerant X A refrigerant according to a second aspect is refrigerant X, CO2, as well as trans-1,2-difluoroethylene (HFO-1132(E)), difluoromethane (R32) and 2,3,3,3-tetrafluoro-1-propene (R1234yf), When the mass percentages of CO2, R32, HFO-1132(E), and R1234yf based on their sum are w, x, y, and z, respectively, in a three-component composition diagram where the sum of R32, HFO-1132(E), and R1234yf is (100-w) mass%, the coordinates (x, y, z) are: 0 <w≦1.2のとき、 Point I(0.0, 72.0, 28.0-w) Point J(18.3, 48.5, 33.2-w) Point K(36.8, 35.6, 27.6-w) Point L(51.7, 28.9, 19.4-w) Point B''(-1.5278w2+2.75w+50.5, 0.0, 1.5278w2-3.75w+49.5) Point D(-2.9167w+40.317, 0.0, 1.9167w+59.683) Point C(0.0, -4.9167w+58.317, 3.9167w+41.683) The points are within the range of the figure enclosed by the curves IJ, JK and KL, as well as the lines LB'', B''D, DC and CI, which connect the seven points above, or on the line segments mentioned above (however, points on the lines B''D and CI are excluded). 1.2 <w≦4.0のとき、 Point I(0.0, 72.0, 28.0-w) Point J(18.3, 48.5, 33.2-w) Point K(36.8, 35.6, 27.6-w) Point L(51.7, 28.9, 19.4-w) Point B''(51.6, 0.0, 48.4-w) Point D(-2.8226w+40.211, 0.0, 1.8226w+59.789) Point C(0.0, 0.1081w2-5.169w+58.447, -0.1081w2+4.169w+41.553) The points are within the range of the figure enclosed by the curves IJ, JK and KL, as well as the lines LB'', B''D, DC and CI, which connect the seven points above, or on the line segments mentioned above (however, points on the lines B''D and CI are excluded). 4.0 <w≦7.0のとき、 Point I(0.0, 72.0, 28.0-w) Point J(18.3, 48.5, 33.2-w) Point K(36.8, 35.6, 27.6-w) Point L(51.7, 28.9, 19.4-w) Point B''(51.6, 0.0, 48.4-w) Point D (-2.8w+40.1, 0.0, 1.8w+59.9) Point C(0.0, 0.0667w2-4.9667w+58.3, -0.0667w2+3.9667w+41.7) The points are within the range of the figure bounded by the curves IJ, JK, and KL, as well as the lines LB'', B''D, DC, and CI, which connect the seven points above, or on the line segments mentioned above (however, points on the lines B''D and CI are excluded), and The curve IJ is Coordinates (x, 0.0236x2-1.716x+72, -0.0236x2+0.716x+28-w) It is expressed as Curvy JK is Coordinates (x, 0.0095x2-1.2222x+67.676, -0.0095x2+0.2222x+32.324-w) It is expressed as The curve KL is Coordinates (x, 0.0049x2-0.8842x+61.488, -0.0049x2-0.1158x+38.512) It is expressed as:

[0365] A refrigerant according to a third aspect is refrigerant X, CO2, as well as trans-1,2-difluoroethylene (HFO-1132(E)), difluoromethane (R32) and 2,3,3,3-tetrafluoro-1-propene (R1234yf), When the mass percentages of CO2, R32, HFO-1132(E), and R1234yf based on their sum are w, x, y, and z, respectively, in a three-component composition diagram where the sum of R32, HFO-1132(E), and R1234yf is (100-w) mass%, the coordinates (x, y, z) are: 0 <w≦1.2のとき、 Point I(0.0, 72.0, 28.0-w) Point J(18.3, 48.5, 33.2-w) Point K(36.8, 35.6, 27.6-w) Point F(-0.0833w+36.717, -4.0833w+5.1833, 3.1666w+58.0997) Point C(0.0, -4.9167w+58.317, 3.9167w+41.683) The points are within the range of the figure bounded by the curves IJ and JK connecting the five points above, as well as the lines KF, FC, and CI, or on the line segments mentioned above (excluding points on the line CI), 1.2 <w≦1.3のとき、 Point I(0.0, 72.0, 28.0-w) Point J(18.3, 48.5, 33.2-w) Point K(36.8, 35.6, 27.6-w) Point F(36.6, -3w+3.9, 2w+59.5) Point C(0.0, 0.1081w2-5.169w+58.447, -0.1081w2+4.169w+41.553) The points are within the range of the figure bounded by the curves IJ and JK connecting the five points above, as well as the lines KF, FC, and CI, or on the line segments mentioned above (excluding points on the line CI), 1.3 <w≦4.0のとき、 Point I(0.0, 72.0, 28.0-w) Point J(18.3, 48.5, 33.2-w) Point K(36.8, 35.6, 27.6-w) Point B'(36.6, 0.0, -w+63.4) Point D(-2.8226w+40.211, 0.0, 1.8226w+59.789) Point C(0.0, 0.1081w2-5.169w+58.447, -0.1081w2+4.169w+41.553) The points are within the range of the figure bounded by the curves IJ and JK connecting the six points above, as well as the lines KB', B'D, DC, and CI, or on the line segments mentioned above (excluding points on the line CI). 4.0 <w≦7.0のとき、 Point I(0.0, 72.0, 28.0-w) Point J(18.3, 48.5, 33.2-w) Point K(36.8, 35.6, 27.6-w) Point B'(36.6, 0.0, -w+63.4) Point D (-2.8w+40.1, 0.0, 1.8w+59.9) Point C(0.0, 0.0667w2-4.9667w+58.3, -0.0667w2+3.9667w+41.7) The curves IJ and JK connecting the six points above, as well as the lines KB', B'D, DC and CI, are within the range of the figure bounded by these points or on the line segments (excluding points on the line CI), and the curve IJ is Coordinates (x, 0.0236x2-1.716x+72, -0.0236x2+0.716x+28-w) It is expressed as Curvy JK is Coordinates (x, 0.0095x2-1.2222x+67.676, -0.0095x2+0.2222x+32.324-w) It is expressed as:

[0366] A refrigerant according to a fourth aspect is refrigerant X, CO2, as well as R32, HFO-1132(E) and R1234yf, When the mass percentages of CO2, R32, HFO-1132(E), and R1234yf based on their sum are w, x, y, and z, respectively, in a three-component composition diagram where the sum of R32, HFO-1132(E), and R1234yf is (100-w) mass%, the coordinates (x, y, z) are: 0 <w≦1.2のとき、 Point I(0.0, 72.0, 28.0-w) Point J(18.3, 48.5, 33.2-w) Point E(18.2, -1.1111w2-3.1667w+31.9, 1.1111w2+2.1667w+49.9) Point C(0.0, -4.9167w+58.317, 3.9167w+41.683) The points are within the range of the figure enclosed by the curves IJ and JK connecting the four points above, as well as the lines KF, FC, and CI, or on the line segments mentioned above (excluding points on the line CI), 1.2 <w≦4.0のとき、 Point I(0.0, 72.0, 28.0-w) Point J(18.3, 48.5, 33.2-w) Point E (-0.0365w+18.26, 0.0623w2-4.5381w+31.856, -0.0623w2+3.5746w+49.884) Point C(0.0, 0.1081w2-5.169w+58.447, -0.1081w2+4.169w+41.553) The points are within the range of the figure enclosed by the curves IJ and JK connecting the four points above, as well as the lines KF, FC, and CI, or on the line segments mentioned above (excluding points on the line CI), 4.0 <w≦7.0のとき、 Point I(0.0, 72.0, 28.0-w) Point J(18.3, 48.5, 33.2-w) Point E(18.1, 0.0444w2-4.3556w+31.411, -0.0444w2+3.3556w+50.489) Point C(0.0, 0.0667w2-4.9667w+58.3, -0.0667w2+3.9667w+41.7) The points are within the range of the figure enclosed by the curves IJ and JK connecting the four points above, and the lines KF, FC, and CI, or on the line segments (excluding points on the line CI), and The curve IJ is Coordinates (x, 0.0236x2-1.716x+72, -0.0236x2+0.716x+28-w) It is expressed as:

[0367] A refrigerant according to a fifth aspect is refrigerant X, CO2, as well as R32, HFO-1132(E) and R1234yf, When the mass percentages of CO2, R32, HFO-1132(E), and R1234yf based on their sum are w, x, y, and z, respectively, in a three-component composition diagram where the sum of R32, HFO-1132(E), and R1234yf is (100-w) mass%, the coordinates (x, y, z) are: 0 <w≦0.6のとき、 Point G(-5.8333w2-3.1667w+22.2, 7.0833w2+1.4167w+26.2, -1.25w2+0.75w+51.6) Point O(36.8, 0.8333w2+1.8333w+22.6, -0.8333w2-2.8333w+40.6) Point P(51.7, 1.1111w2+20.5, -1.1111w2-w+27.8) Point B''(-1.5278w2+2.75w+50.5, 0.0, 1.5278w2-3.75w+49.5) Point D(-2.9167w+40.317, 0.0, 1.9167w+59.683) The points are within the range of the figure enclosed by the curves GO and OP connecting the five points above, as well as the lines PB'', B''D and DG, or on the line segments (excluding points on the line B''D). 0.6 <w≦1.2のとき、 Point G(-5.8333w2-3.1667w+22.2, 7.0833w2+1.4167w+26.2, -1.25w2+0.75w+51.6) Point N(18.2, 0.2778w2+3w+27.7, -0.2778w2-4w+54.1) Point O(36.8, 0.8333w2+1.8333w+22.6, -0.8333w2-2.8333w+40.6) Point P(51.7, 1.1111w2+20.5, -1.1111w2-w+27.8) Point B''(-1.5278w2+2.75w+50.5, 0.0, 1.5278w2-3.75w+49.5) Point D(-2.9167w+40.317, 0.0, 1.9167w+59.683) The points are within the range of the figure bounded by the curves GN, NO, and OP, which connect the six points above, as well as the lines PB'', B''D, and DG, or on the line segments mentioned above (excluding points on the line B''D). and The curve GO is 0 <w≦0.6のとき、 Coordinates (x, (0.00487w2-0.0059w+0.0072)x2+(-0.279w2+0.2844w-0.6701)x+3.7639w2-0.2467w+37.512, 100-wxy) It is expressed as The curve GN is 0.6 <w≦1.2のとき、 Coordinates (x, (0.0122w2-0.0113w+0.0313)x2+(-0.3582w2+0.1624w-1.4551)x+2.7889w2+3.7417w+43.824 , 100-wxy) It is expressed as Curve No. 0.6 <w≦1.2のとき、 Coordinates (x, (0.00487w2-0.0059w+0.0072)x2+(-0.279w2+0.2844w-0.6701)x+3.7639w2-0.2467w+37.512, 100-wxy) is expressed as Curve OP is, 0 <w≦1.2のとき、 Coordinates (x, (0.0074w2-0.0133w+0.0064)x2+(-0.5839w2+1.0268w-0.7103)x+11.472w2-17.455w+40.07, 100-wxy) It is expressed as 1.2 <w≦4.0のとき、 Point M(0.0, -0.3004w2+2.419w+55.53, 0.3004w2-3.419w+44.47) Point W(10.0, -0.3645w2+3.5024w+44.422, 0.3645w2-4.5024w+55.578) Point N(18.2, -0.3773w2+3.319w+28.26, 0.3773w2-4.319w+53.54) Point O(36.8, -0.1392w2+1.4381w+24.475, 0.1392w2-2.4381w+38.725) Point P(51.7, -0.2381w2+1.881w+20.186, 0.2381w2-2.881w+28.114) Point B''(51.6, 0.0, -w+48.4) Point D(-2.8226w+40.211, 0.0, 1.8226w+59.789) Point C(0.0, 0.1081w2-5.169w+58.447, -0.1081w2+4.169w+41.553) The points are within the range of the figure enclosed by the curves MW, WN, NO and OP, and the lines PB'', B''D, DC and CM, which connect the above eight points, or on the line segments (however, points on the lines B''D and CM are excluded), and The curve MW is Coordinates (x, (0.0043w2-0.0359w+0.1509)x2+(-0.0493w2+0.4669w-3.6193)x-0.3004w2+2.419w+55.53, 100-wxy) It is expressed as The curve WN is Coordinates (x, (0.0055w2-0.0326w+0.0665)x2+(-0.1571w2+0.8981w-2.6274)x+0.6555w2-2.2153w+54.044, 100-wxy) It is expressed as Curve No. Coordinates (x, (-0.00062w2+0.0036w+0.0037)x2+(0.0375w2-0.239w-0.4977)x-0.8575w2+6.4941w+36.078, 100-wxy) It is expressed as Curve OP is, Coordinates (x, (-0.000463w2+0.0024w-0.0011)x2+(0.0457w2-0.2581w-0.075)x-1.355w2+8. 749w+27.096, 100-wxy) It is expressed as 4.0 <w≦7.0のとき、 Point M(0.0, -0.0667w2+0.8333w+58.133, 0.0667w2-1.8333w+41.867) Point W(10.0, -0.0667w2+1.1w+39.267, 0.0667w2-2.1w+50.733) Point N(18.2, -0.0889w2+1.3778w+31.411, 0.0889w2-2.3778w+50.389) Point O(36.8, -0.0444w2+0.6889w+25.956, 0.0444w2-1.6889w+37.244) Point P(51.7, -0.0667w2+0.8333w+21.633, 0.0667w2-1.8333w+26.667) Point B''(51.6, 0.0, -w+48.4) Point D (-2.8w+40.1, 0.0, 1.8w+59.9) Point C(0.0, 0.0667w2-4.9667w+58.3, -0.0667w2+3.9667w+41.7) The points are within the range of the figure enclosed by the curves MW, WN, NO and OP, and the lines PB'', B''D, DC and CM, which connect the above eight points, or on the line segments (however, points on the lines B''D and CM are excluded), and The curve MW is Coordinates (x, (0.00357w2-0.0391w+0.1756)x2+(-0.0356w2+0.4178w-3.6422)x-0.0667w2+0.8333w+58.103, 100-wxy) It is expressed as The curve WN is Coordinates (x, (-0.002061w2+0.0218w-0.0301)x2+(0.0556w2-0.5821w-0.1108)x-0.4158w2+4.7352w+43.383, 100-wxy) It is expressed as Curve No. Coordinates (x, 0.0082x2+(0.0022w2-0.0345w-0.7521)x-0.1307w2+2.0247w+42.327, 100-wxy) It is expressed as Curve OP is, Coordinates (x, (-0.0006258w2+0.0066w-0.0153)x2+(0.0516w2-0.5478w+0.9894)x-1.074w2+11.651w+10.992, 100-wxy) It is expressed as:

[0368] A refrigerant according to a sixth aspect is refrigerant X, CO2, as well as R32, HFO-1132(E) and R1234yf, When the mass percentages of CO2, R32, HFO-1132(E), and R1234yf based on their sum are w, x, y, and z, respectively, in a three-component composition diagram where the sum of R32, HFO-1132(E), and R1234yf is (100-w) mass%, the coordinates (x, y, z) are: 0 <w≦0.6のとき、 Point G(-5.8333w2-3.1667w+22.2, 7.0833w2-1.4167w+26.2, -1.25w2+3.5834w+51.6) Point O(36.8, 0.8333w2+1.8333w+22.6, -0.8333w2-2.8333w+40.6) Point F(-0.0833w+36.717, -4.0833w+5.1833, 3.1666w+58.0997) The curve GO connecting the three points and the straight lines OF and FG are within the range of the figure enclosed by the curve GO connecting the three points, or are on the line segment. The curve GO is Coordinates (x, (0.00487w2-0.0059w+0.0072)x2+(-0.279w2+0.2844w-0.6701)x+3.7639w2-0.2467w+37.512, 100-wxy) It is expressed as 0.6 <w≦1.2のとき、 Point G(-5.8333w2-3.1667w+22.2, 7.0833w2-1.4167w+26.2, -1.25w2+3.5834w+51.6) Point N(18.2, 0.2778w2+3.0w+27.7, -0.2.778w2-4.0w+54.1) Point O(36.8, 0.8333w2+1.8333w+22.6, -0.8333w2-2.8333w+40.6) Point F(-0.0833w+36.717, -4.0833w+5.1833, 3.1666w+58.0997) The curves GN and NO connecting the four points and the lines OF and FG respectively lie within the range of the figure enclosed by these lines or on the line segments. The curve GN is 0.6 <w≦1.2のとき、 Coordinates (x, (0.0122w2-0.0113w+0.0313)x2+(-0.3582w2+0.1624w-1.4551)x+2.7889w2+3.7417w+43.824 , 100-wxy) It is expressed as Curve No. 0.6 <w≦1.2のとき、 Coordinates (x, (0.00487w2-0.0059w+0.0072)x2+(-0.279w2+0.2844w-0.6701)x+3.7639w2-0.2467w+37.512, 100-wxy) It is expressed as 1.2 <w≦1.3のとき、 Point M(0.0, -0.3004w2+2.419w+55.53, 0.3004w2-3.419w+44.47) Point W(10.0, -0.3645w2+3.5024w34.422, 0.3645w2-4.5024w+55.578) Point N(18.2, -0.3773w2+3.319w+28.26, 0.3773w2-4.319w+53.54) Point O(36.8, -0.1392w2+1.4381w+24.475, 0.1392w2-2.4381w+38.725) Point F(36.6, -3w+3.9, 2w+59.5) Point C(0.1081w2-5.169w+58.447, 0.0, -0.1081w2+4.169w+41.553) The points are within the area of ​​the shape bounded by the curves MW, WN and NO, and the lines OF, FC and CM, which connect the six points above, or on the line segments (however, points on the line CM are excluded), and The curve MW is Coordinates (x, (0.0043w2-0.0359w+0.1509)x2+(-0.0493w2+0.4669w-3.6193)x-0.3004w2+2.419w+55.53, 100-wxy) It is expressed as The curve WN is Coordinates (x, (0.0055w2-0.0326w+0.0665)x2+(-0.1571w2+0.8981w-2.6274)x+0.6555w2-2.2153w+54.044, 100-wxy) It is expressed as Curve No. Coordinates (x, (-0.00062w2+0.0036w+0.0037)x2+(0.0375w2-0.239w-0.4977)x-0.8575w2+6.4941w+36.078, 100-wxy) It is expressed as 1.3 <w≦4.0のとき、 Point M(0.0, -0.3004w2+2.419w+55.53, 0.3004w2-3.419w+44.47) Point W(10.0, -0.3645w2+3.5024w+34.422, 0.3645w2-4.5024w+55.578) Point N(18.2, -0.3773w2+3.319w+28.26, 0.3773w2-4.319w+53.54) Point O(36.8, -0.1392w2+1.4381w+24.475, 0.1392w2-2.4381w+38.725) Point B'( 36.6, 0.0, -w+63.4) Point D(-2.8226w+40.211, 0.0, 1.8226w+59.789) Point C(0.0, 0.1081w2-5.169w+58.447, -0.1081w2+4.169w+41.553) The points are within the range of the figure bounded by the curves MW, WN, and NO, which connect the seven points above, as well as the lines OB', B'D, DC, and CM, or on the line segments mentioned above (excluding points on the line CM), and The curve MW is Coordinates (x, (0.0043w2-0.0359w+0.1509)x2+(-0.0493w2+0.4669w-3.6193)x-0.3004w2+2.419w+55.53, 100-wxy) It is expressed as The curve WN is Coordinates (x, (0.0055w2-0.0326w+0.0665)x2+(-0.1571w2+0.8981w-2.6274)x+0.6555w2-2.2153w+54.044, 100-wxy) Curve No. Coordinates (x, (-0.00062w2+0.0036w+0.0037)x2+(0.0457w2-0.2581w-0.075)x-1.355w2+8.749w+27.096, 100-wxy) It is expressed as 4.0 <w≦7.0のとき、 Point M(0.0, -0.0667w2+0.8333w58.133, 0.0667w2-1.8333w+41.867) Point W(10.0, -0.0667w2+1.1w+39.267, 0.0667w2-2.1w+50.733) Point N(18. 2, -0.0889w2+1.3778w+31.411, 0.0889w2-2.3778w+50.389) Point O(36.8, -0.0444w2+0.6889w+25.956, 0.0444w2-1.6889w+37.244) Point B'(36.6, 0.0, -w+63.4) Point D (-2.8w+40.1, 0.0, 1.8w+59.9) Point C(0.0, 0.0667w2-4.9667w+58.3, -0.0667w2+3.9667w+41.7) The points are within the range of the figure bounded by the curves MW, WN, and NO, which connect the seven points above, as well as the lines OB', B'D, DC, and CM, or on the line segments mentioned above (excluding points on the line CM), and The curve MW is Coordinates (x, (0.00357w2-0.0391w+0.1756)x2+(-0.0356w2+0.4178w-3.6422)x-0.0667w2+0.8333w+58.103, 100-wxy) It is expressed as The curve WN is Coordinates (x, (-0.002061w2+0.0218w-0.0301)x2+(0.0556w2-0.5821w-0.1108)x-0.4158w2+4.7352w+43.383, 100-wxy) Curve No. Coordinates (x, (0.0082x2+(0.0022w2-0.0345w-0.7521)x-0.1307w2+2.0247w+42.327, 100-wxy) It is expressed as:

[0369] A refrigerant according to a seventh aspect is refrigerant X, CO2, as well as R32, HFO-1132(E) and R1234yf, When the mass percentages of CO2, R32, HFO-1132(E), and R1234yf based on their sum are w, x, y, and z, respectively, in a three-component composition diagram where the sum of R32, HFO-1132(E), and R1234yf is (100-w) mass%, the coordinates (x, y, z) are: 1.2 <w≦4.0のとき、 Point M(0.0, -0.3004w2+2.419w+55.53, 0.3004w2-3.419w+44.47) Point W(10.0, -0.3645w2+3.5024w+34.422, 0.3645w2-4.5024w+55.578) Point N(18.2, -0.3773w2+3.319w+28.26, 0.3773w2-4.319w+53.54) Point E (-0.0365w+18.26, 0.0623w2-4.5381w+31.856, -0.0623w2+3.5746w+49.884) Point C(0.0, 0.1081w2-5.169w+58.447, -0.1081w2+4.169w+41.553) The points are within the range of the shape bounded by the curves MW and WN, and the lines NE, EC, and CM, which connect the above five points, or on the line segments (excluding points on the line CM), and The curve MW is Coordinates (x, (0.0043w2-0.0359w+0.1509)x2+(-0.0493w2+0.4669w-3.6193)x-0.3004w2+2.419w+55.53, 100-wxy) It is expressed as The curve WN is Coordinates (x, (0.0055w2-0.0326w+0.0665)x2+(-0.1571w2+0.8981w-2.6274)x+0.6555w2-2.2153w+54.044, 100-wxy) It is expressed as 4.0 <w≦7.0のとき、 Point M(0.0, -0.0667w2+0.8333w+58.133, 0.0667w2-1.8333w+41.867) Point W(10.0, -0.0667w2+1.1w+39.267, 0.0667w2-2.1w+50.733) Point N(18.2, -0.0889w2+1.3778w+31.411, 0.0889w2-2.3778w+50.389) Point E(18.1, 0.0444w2-4.3556w+31.411, -0.0444w2+3.3556w+50.489) Point C(0.0, 0.0667w2-4.9667w+58.3, -0.0667w2+3.9667w+41.7) The points are within the range of the shape bounded by the curves MW and WN, and the lines NE, EC, and CM, which connect the above five points, or on the line segments (excluding points on the line CM), and The curve MW is Coordinates (x, (0.00357w2-0.0391w+0.1756)x2+(-0.0356w2+0.4178w-3.6422)x-0.0667w2+0.8333w+58.103, 100-wxy) It is expressed as The curve WN is Coordinates (x, (-0.002061w2+0.0218w-0.0301)x2+(0.0556w2-0.5821w-0.1108)x-0.4158w2+4.7352w+43.383, 100-wxy) It is expressed as:

[0370] (26-2) Second refrigerant Y A refrigerant according to an eighth aspect is refrigerant Y, Based on the total mass of HFO-1132(Z) and HFO-1234yf, The content of HFO-1132(Z) is 53.0 to 59.5 mass%, The content of HFO-1234yf is 47.0 to 40.5 mass %.

[0371] A refrigerant according to a ninth aspect is refrigerant Y, Based on the total mass of HFO-1132(Z) and HFO-1234yf, The content of HFO-1132(Z) is 41.0 to 49.2 mass%, The content of HFO-1234yf is 59.0 to 50.8 mass %.

[0372] A refrigerant according to a tenth aspect is the refrigerant Y according to the eighth or ninth aspect, and is used to operate a refrigeration cycle having an evaporation temperature of -60 to 20°C.

[0373] A refrigerant according to an eleventh aspect is the refrigerant Y according to any one of the eighth to tenth aspects, It consists only of HFO-1132(Z) and HFO-1234yf.

[0374] A refrigerant according to a twelfth aspect is the refrigerant Y according to any one of the eighth to eleventh aspects, R134a, R22, R12, R404A, R407A, R407C, R407F, R407H, R410A, R413A, R417A, R422A, R422B, R422C, R422D, R423A, R424A, R426A, R427A, R428A, R430A, R434A, R437A, R438A, R448A, R449A, R449B, R449C, R450A, R452A, R452B, R454A, R452B, R454C, R455A, R465A, R502, R507, R513A, R513B, R515A or R515B It is used as an alternative refrigerant.

[0375] A refrigerant according to a thirteenth aspect is the refrigerant Y according to any one of the eighth to twelfth aspects, which contains at least one substance selected from the group consisting of water, a tracer, an ultraviolet fluorescent dye, a stabilizer, and a polymerization inhibitor.

[0376] A refrigerant according to a fourteenth aspect is the refrigerant Y according to any one of the eighth to thirteenth aspects, further containing refrigerating machine oil, and is used as a working fluid for a refrigeration system.

[0377] A refrigerant according to a fifteenth aspect is the refrigerant Y according to the fourteenth aspect, wherein the refrigerating machine oil is at least one polymer selected from the group consisting of polyalkylene glycol (PAG), polyol ester (POE), and polyvinyl ether (PVE); Contains:

[0378] (26-3) Third Refrigerant A A refrigerant according to a sixteenth aspect is a refrigerant A containing trans-1,2-difluoroethylene (HFO-1132(E)), difluoromethane (HFC-32), and 2,3,3,3-tetrafluoropropene (HFO-1234yf), the total concentration of the three components being 99.5% by mass or more based on the total mass of the refrigerant; and In a triangular composition diagram with the three components at each vertex, the mass ratio of the three components is: Point A (HFO-1132(E) / HFC-32 / HFO-1234yf=51.8 / 1.0 / 47.2% by mass), Point B (HFO-1132(E) / HFC-32 / HFO-1234yf=35.3 / 1.0 / 63.7% by mass), Point C (HFO-1132(E) / HFC-32 / HFO-1234yf=10.1 / 18.0 / 71.9% by mass) and Point D (HFO-1132(E) / HFC-32 / HFO-1234yf=27.8 / 18.0 / 54.2% by mass), It is within the area enclosed by the shape passing through the four points.

[0379] A refrigerant according to a seventeenth aspect is the refrigerant A according to the sixteenth aspect, comprising HFO-1132(E), HFC-32, and HFO-1234yf, the total concentration of the three components being 99.5 mass% or more based on the total mass of the refrigerant; and In a triangular composition diagram with the three components at each vertex, the mass ratio of the three components is: Point A (HFO-1132(E) / HFC-32 / HFO-1234yf=51.8 / 1.0 / 47.2% by mass), Point B (HFO-1132(E) / HFC-32 / HFO-1234yf=35.3 / 1.0 / 63.7% by mass), Point E (HFO-1132(E) / HFC-32 / HFO-1234yf=15.2 / 14.3 / 70.5 mass%) and Point F (HFO-1132(E) / HFC-32 / HFO-1234yf=31.1 / 14.3 / 54.6% by mass), It is within the area enclosed by the shape passing through the four points.

[0380] A refrigerant according to an eighteenth aspect is refrigerant A, which contains HFO-1132(E), HFC-32, and HFO-1234yf, and the total concentration of the three components is 99.5% by mass or more based on the total amount of the refrigerant; and In a triangular composition diagram with the three components at each vertex, the mass ratio of the three components is: Point P (HFO-1132(E) / HFC-32 / HFO-1234yf=45.6 / 1.0 / 53.4% ​​by mass), Point B (HFO-1132(E) / HFC-32 / HFO-1234yf=35.3 / 1.0 / 63.7% by mass), Point Q (HFO-1132(E) / HFC-32 / HFO-1234yf=1.0 / 24.8 / 74.2% by mass), Point R (HFO-1132(E) / HFC-32 / HFO-1234yf=1.0 / 29.2 / 69.8 mass%) and Point S (HFO-1132(E) / HFC-32 / HFO-1234yf=6.5 / 29.2 / 64.3 mass%), It is within the area enclosed by a shape passing through the five points.

[0381] A refrigerant according to a nineteenth aspect is the refrigerant A according to any one of the sixteenth to eighteenth aspects, which consists only of HFO-1132(E), HFC-32 and HFO-1234yf.

[0382] (26-4) Fourth Refrigerant B A refrigerant according to a twentieth aspect is refrigerant B, which contains HFO-1132(E), HFO-1123, and HFO-1234yf, and the total concentration of the three components is 99.5% by mass or more based on the total amount of the refrigerant; and In a triangular composition diagram with the three components at each vertex, the mass ratio of the three components is: Point A (HFO-1132(E) / HFO-1123 / HFO-1234yf=42.5 / 1.0 / 56.5% by mass), Point B (HFO-1132(E) / HFO-1123 / HFO-1234yf=27.1 / 1.0 / 71.9 mass%), Point C (HFO-1132(E) / HFO-1123 / HFO-1234yf=1.0 / 30.4 / 68.6% by mass), Point D (HFO-1132(E) / HFO-1123 / HFO-1234yf=1.0 / 57.0 / 42.0 mass%) and Point E (HFO-1132(E) / HFO-1123 / HFO-1234yf=42.5 / 24.1 / 33.4 mass%) It is within the area enclosed by a shape passing through the five points.

[0383] A refrigerant according to a twenty-first aspect is the refrigerant B according to the twentieth aspect, comprising HFO-1132(E), HFO-1123, and HFO-1234yf, the total concentration of the three components being 99.5 mass% or more based on the total mass of the refrigerant; and In a triangular composition diagram with the three components at each vertex, the mass ratio of the three components is: Point A (HFO-1132(E) / HFO-1123 / HFO-1234yf=42.5 / 1.0 / 56.5% by mass), Point B (HFO-1132(E) / HFO-1123 / HFO-1234yf=27.1 / 1.0 / 71.9 mass%), Point C (HFO-1132(E) / HFO-1123 / HFO-1234yf=1.0 / 30.4 / 68.6% by mass), Point F (HFO-1132(E) / HFO-1123 / HFO-1234yf=1.0 / 52.2 / 46.8% by mass) and Point G (HFO-1132(E) / HFO-1123 / HFO-1234yf=42.5 / 18.9 / 38.6 mass%) It is within the area enclosed by a shape passing through the five points.

[0384] A refrigerant according to a twenty-second aspect is refrigerant B according to the twentieth or twenty-first aspect, comprising HFO-1132(E), HFO-1123 and HFO-1234yf, the total concentration of the three components being 99.5 mass% or more based on the total mass of the refrigerant; and In a triangular composition diagram with the three components at each vertex, the mass ratio of the three components is: Point A (HFO-1132(E) / HFO-1123 / HFO-1234yf=42.5 / 1.0 / 56.5 mass%), Point B (HFO-1132(E) / HFO-1123 / HFO-1234yf=27.1 / 1.0 / 71.9 mass%), Point C (HFO-1132(E) / HFO-1123 / HFO-1234yf=1.0 / 30.4 / 68.6% by mass), Point H (HFO-1132(E) / HFO-1123 / HFO-1234yf=1.0 / 35.2 / 63.8% by mass), Point I (HFO-1132(E) / HFO-1123 / HFO-1234yf=27.4 / 29.8 / 42.8% by mass) and Point G (HFO-1132(E) / HFO-1123 / HFO-1234yf=42.5 / 18.9 / 38.6 mass%) It is within the area enclosed by a shape passing through the six points.

[0385] A refrigerant according to a twenty-third aspect is the refrigerant B according to any one of the twentieth to twenty-second aspects, and consists solely of HFO-1132(E), HFO-1123 and HFO-1234yf.

[0386] (26-5) Fifth Refrigerant C A refrigerant in a twenty-fourth aspect is refrigerant C, which contains HFO-1132(E) and HFO-1234yf, and the amount of HFO-1132(E) and HFO-1234yf relative to the total mass of HFO-1132(E) and HFO-1234yf is: The content of HFO-1132(E) is 35.0 to 65.0 mass%; The content of HFO-1234yf is 65.0 to 35.0 mass %.

[0387] A refrigerant according to a twenty-fifth aspect is Refrigerant C according to the twenty-fourth aspect, wherein, relative to the total mass of HFO-1132(E) and HFO-1234yf, The content of HFO-1132(E) is 41.3 to 53.5 mass%, The content of HFO-1234yf is 58.7 to 46.5 mass %.

[0388] A refrigerant according to a twenty-sixth aspect is refrigerant C according to the twenty-fourth or twenty-fifth aspect, which consists of only HFO-1132(E) and HFO-1234yf.

[0389] A refrigerant according to a twenty-seventh aspect is refrigerant C containing HFO-1132(E) and HFO-1234yf, wherein the amount of HFO-1132(E) and HFO-1234yf contained in the refrigerant C is: The content of HFO-1132(E) is 40.5 to 49.2 mass%, The content of HFO-1234yf is 59.5 to 50.8 mass %.

[0390] A refrigerant according to a twenty-eighth aspect is refrigerant C according to the twenty-seventh aspect, which consists of only HFO-1132(E) and HFO-1234yf.

[0391] A refrigerant according to a twenty-ninth aspect is the refrigerant C according to the twenty-seventh or twenty-eighth aspect, which has an evaporation temperature of -75 to -5°C.

[0392] A refrigerant according to a thirtieth aspect is refrigerant C containing HFO-1132(E) and HFO-1234yf, wherein the amount of HFO-1132(E) and HFO-1234yf contained in the refrigerant C is: The content of HFO-1132(E) is 31.1 to 39.8 mass%, The content of HFO-1234yf is 68.9 to 60.2 mass %.

[0393] A refrigerant according to a thirty-first aspect is refrigerant C according to the thirtieth aspect, wherein, relative to the total mass of HFO-1132(E) and HFO-1234yf, The content of HFO-1132(E) is 31.1 to 37.9 mass%, The content of HFO-1234yf is 68.9 to 62.1 mass %.

[0394] A refrigerant according to a thirty-second aspect is refrigerant C according to the thirtieth or thirty-first aspect, which consists of only HFO-1132(E) and HFO-1234yf.

[0395] A refrigerant according to a thirty-third aspect is the refrigerant C according to any one of the thirtieth to thirty-second aspects, and has an evaporation temperature of -75 to -5°C.

[0396] A refrigerant according to a thirty-fourth aspect is refrigerant C containing HFO-1132(E) and HFO-1234yf, wherein the amount of HFO-1132(E) and HFO-1234yf contained in the refrigerant C is: The content of HFO-1132(E) is 21.0 to 28.4 mass%, The content of HFO-1234yf is 79.0 to 71.6 mass %.

[0397] A refrigerant according to a thirty-fifth aspect is refrigerant C according to the thirty-fourth aspect, which consists of only HFO-1132(E) and HFO-1234yf.

[0398] A refrigerant according to a thirty-sixth aspect is refrigerant C containing HFO-1132(E) and HFO-1234yf, wherein the amount of HFO-1132(E) and HFO-1234yf contained in the refrigerant C is: The content of HFO-1132(E) is 12.1 to 72.0 mass%; The content of HFO-1234yf is 87.9 to 28.0 mass %.

[0399] (26-6) 6th Refrigerant D A refrigerant according to a thirty-seventh aspect is refrigerant D, which contains HFO-1132a.

[0400] A refrigerant according to a thirty-eighth aspect is refrigerant D according to the thirty-seventh aspect, which contains 15.0 to 24.0 mass% of HFC-32 and 1.0 to 7.0 mass% of HFO-1132a, relative to 100 mass% of the total amount of HFC-32, HFO-1234yf, and HFO-1132a.

[0401] A refrigerant according to a thirty-ninth aspect is refrigerant D according to the thirty-seventh aspect, which contains 19.5 to 23.5 mass% of HFC-32 and 3.1 to 3.7 mass% of HFO-1132a, relative to 100 mass% of the total amount of HFC-32, HFO-1234yf, and HFO-1132a.

[0402] A refrigerant in a fortieth aspect is refrigerant D comprising HFC-32, HFO-1234yf, and HFO-1132a, wherein, in the refrigerant, when the mass percentages of HFC-32, HFO-1132a, and HFO-1234yf based on the sum of these are x, y, and z, respectively, in a ternary composition diagram in which the sum of HFC-32, HFO-1132a, and HFO-1234yf is 100 mass%, the coordinates (x, y, z) are: Point R(21.80, 3.95, 74.25), Point S(21.80, 3.05, 75.15), and Point T(20.95, 75.30, 3.75), The point is located within the triangle defined by the line segments RS, ST, and TR connecting the three points above, or on the line segments.

[0403] A refrigerant in a forty-first aspect is refrigerant D comprising HFC-32, HFO-1234yf, and HFO-1132a, wherein, in the refrigerant, when the mass percentages of HFC-32, HFO-1132a, and HFO-1234yf based on the sum of these are x, y, and z, respectively, in a ternary composition diagram in which the sum of HFC-32, HFO-1132a, and HFO-1234yf is 100 mass%, the coordinates (x, y, z) are: Point L(74.0, 19.9, 6.1), Point F(49.1, 25.9, 25.0), Point G(0.0, 48.6, 51.4), Point O(0.0, 0.0, 100), and Point B(73.9, 0.0, 26.1), The object is located within the area of ​​the figure enclosed by the line segments LF, FG, GO, OB, and BL connecting the above five points, or on the above line segments (excluding the line segments GO and OB), The line segment LF is Coordinates (y=0.0021x 2 -0.4975x+45.264), The line segment FG is Coordinates (y=0.0031x 2 -0.6144x+48.6), and The line segments GO, OB and BL are straight lines.

[0404] A refrigerant in a forty-second aspect is refrigerant D comprising HFC-32, HFO-1234yf, and HFO-1132a, wherein, in the refrigerant, when the mass percentages of HFC-32, HFO-1132a, and HFO-1234yf based on the sum of these are x, y, and z, respectively, in a ternary composition diagram in which the sum of HFC-32, HFO-1132a, and HFO-1234yf is 100 mass%, the coordinates (x, y, z) are: Point P(59.1, 23.2, 17.7), Point F(49.1, 25.9, 25.0), Point G(0.0, 48.6, 51.4), Point O(0.0, 0.0, 100), and Point B'(59.0, 0.0, 40.2), The object is within the area of ​​the figure enclosed by the line segments PF, FG, GO, OB', and B'P connecting the above five points, or on said line segments (excluding the line segments GO and OB'), The line segment PF is Coordinates (y=0.0021x 2 -0.4975x+45.264), The line segment FG is Coordinates (y=0.0031x 2 -0.6144x+48.6), and The line segments GO, OB' and B'P are straight lines.

[0405] A refrigerant in a forty-third aspect is refrigerant D comprising HFC-32, HFO-1234yf, and HFO-1132a, wherein, in the refrigerant, when the mass percentages of HFC-32, HFO-1132a, and HFO-1234yf based on the sum of these are x, y, and z, respectively, in a ternary composition diagram in which the sum of HFC-32, HFO-1132a, and HFO-1234yf is 100 mass%, the coordinates (x, y, z) are: Point M(74.0, 19.5, 6.5), Point I (62.9, 15.5, 21.6), Point J (33.5, 0.0, 66.5), and Point B(73.9, 0.0, 26.1), The object is located within the area of ​​the figure enclosed by the line segments MI, IJ, JB, and BM connecting the four points above, or on the line segments (excluding the line segment JB), The line segment MI is Coordinates (y=0.006x 2 +1.1837x-35.264), The line segment IJ is Coordinates (y=0.0083x 2 -0.2719x-0.1953), and The line segments JB and BM are straight lines.

[0406] A refrigerant in a forty-fourth aspect is refrigerant D comprising HFC-32, HFO-1234yf, and HFO-1132a, wherein, in the refrigerant, when the mass percentages of HFC-32, HFO-1132a, and HFO-1234yf based on the sum of these are x, y, and z, respectively, in a ternary composition diagram in which the sum of HFC-32, HFO-1132a, and HFO-1234yf is 100 mass%, the coordinates (x, y, z) are: Point Q(59.1, 12.7, 28.2), Point J (33.5, 0.0, 66.5), and Point B'(59.0, 0.0, 40.2), The object is located within the area of ​​the figure enclosed by the line segments QJ, JB', and B'Q connecting the above three points, or on the line segments (excluding the line segment JB'), The line segment QJ is Coordinates (y=0.0083x 2 -0.2719x-0.1953), and The line segments JB' and B'Q are straight lines.

[0407] A refrigerant in a forty-fifth aspect is refrigerant D comprising HFC-32, HFO-1234yf, and HFO-1132a, wherein, in the refrigerant, when the mass percentages of HFC-32, HFO-1132a, and HFO-1234yf based on the sum of these are x, y, and z, respectively, in a ternary composition diagram in which the sum of HFC-32, HFO-1132a, and HFO-1234yf is 100 mass%, the coordinates (x, y, z) are: Point Q(59.1, 12.7, 28.2), Point U(59.0, 5.5, 35.5), and Point V(52.5, 8.4, 39.1), It is within the range of the figure enclosed by the line segments QU, UV, and VQ connecting the three points above, or on said line segments, The line segment VQ is Coordinates (y=0.0083x 2 -0.2719x-0.1953), and The line segment UV is Coordinates (y=0.0026x 2 -0.7385x+39.946), The line segment QU is a straight line.

[0408] (26-7) Seventh Refrigerant E A refrigerant in a forty-sixth aspect is refrigerant E, wherein, in the refrigerant, based on the total of R32, CO2, R125, R134a, and R1234yf, when the mass percentage of R32 is a, the mass percentage of CO2 is b, the mass percentage of R125 is c1, the mass percentage of R134a is c2, the mass percentage of the total of R125 and R134a is c, the mass percentage of R1234yf is x, and c1 / (c1+c2) is r, In a three-component composition diagram with vertices at the points where R32 is (100-x) mass%, CO2 is (100-x) mass%, and the total of R125 and R134a is (100-x) mass%, the coordinates (a, b, c) are: 1-1-1) When 43.8≧x≧41 and 0.5≧r≧0.25, Point A(-0.6902x+43.307, 100-ax, 0.0), point O r=0.25~0.5 ((-2.2857x+87.314)r 2 +(1.7143x-55.886)r+(-0.9643x+55.336), (2.2857x-112.91)r 2 +(-1.7143x+104.69)r+(-0.25x+11.05), 100-abx), point D r=0.25~0.5 (0.0, -28.8r 2 +54.0r+(-x+49.9), 100-bx) and Point Q(0.0, 100-x, 0.0) Is it within the area of ​​the rectangle enclosed by the line segment connecting the lines or on the line segment (however, the line segment D r=0.25~0.5 (excluding points on Q and QA), or 1-1-2) When 43.8≧x≧41 and 1.0≧r≧0.5, Point A(-0.6902x+43.307, 100-ac, 0.0), point O r=0.5~1.0 ((-0.2857x+8.5143)r 2 +(0.5x-10.9)+(-0.8571x+52.543), (-0.2857x+4.5143)r 2 +(0.5x+0.9)r+(-0.7143x+33.586), 100-abx), point Dr=0.5~1.0 (0.0, (-0.5714x+12.229)r 2 +(0.8571x-0.3429)r+(-1.2857x+66.814), 100-bx) and Point Q(0.0, 100-x, 0.0) Is it within the area of ​​the rectangle enclosed by the line segment connecting the lines or on the line segment (however, the line segment D r=0.5~1.0 (excluding points on Q and QA), or 1-2-1) When 46.5≧x≧43.8 and 0.5≧r≧0.25, Point A(-0.6902x+43.307, 100-ax, 0.0), point O r=0.25~0.5 ((1.1852x-64.711)r 2 +(-0.7407x+51.644)r+(-0.5556x+37.433), (-2.3704x+91.022)r 2 +(2.0741x-61.244)r+(-0.963x+42.278), 100-abx), point D r=0.25~0.5 (0.0, -28.8r 2 +54.0r+(-x+49.9), 100-bx) and Point Q(0.0, 100-x, 0.0) Is it within the area of ​​the rectangle enclosed by the line segment connecting the lines or on the line segment (however, the line segment D r=0.25~0.5 (excluding points on Q and QA), or 1-2-2) When 46.5≧x≧43 and 1.0≧r≧0.5, Point A(-0.6902x+43.307, 100-ax, 0.0), point O r=0.5~1.0 ((0.2963x-16.978)r2+(-0.3704x+27.222)r+(-0.5185x+37.711), -8.0r2+22.8r+(-0.5185x+25.011), 100-abx), point D r=0.5~1.0 (0.0, -12.8r 2 +37.2r+(-x+54.3), 100-bx) and Point Q(0.0, 100-x, 0.0) Is it within the area of ​​the rectangle enclosed by the line segment connecting the lines or on the line segment (however, the line segment D r=0.5~1.0 (excluding points on Q and QA) 1-3-1) When 50≧x≧46.5 and 0.5≧r≧0.25, Point A(-0.6902x+43.307, 100-ax, 0.0), point O r=0.25~0.5 (-9.6r 2 +17.2r+(-0.6571x+42.157), -19.2r 2 +(0.2286x+24.571)r+(-0.6286x+26.729), 100-abx), point D r=0.25~0.5 (0.0, (0.9143x-71.314)r 2 +(-0.5714x+80.571)+(-0.9143x+45.914), 100-bx) and Point Q(0.0, 100-x, 0.0) Is it within the area of ​​the rectangle enclosed by the line segment connecting the lines or on the line segment (however, the line segment D r=0.25~0.5 (excluding points on Q and QA), or 1-3-2) When 50≧x≧46.5 and 1.0≧r≧0.5, Point A(-0.6902x+43.307, 100-ax, 0.0), point O r=0.5~1.0 ((-0.2286x+7.4286)r 2 +(0.4x-8.6)r+(-0.8x+50.8), (0.2286x-18.629)r 2 +(-0.2857x+36.086)r+(-0.4286x+20.829), 100-abx), point D r=0.5~1.0 (0.0, (0.2286x-23.429)r 2 +(-0.4x+55.8)r+(-0.8286x+46.329), 100-bx) and Point Q(0.0, 100-x, 0.0) Within the area of ​​the rectangle enclosed by the line segment connectingr=0.5~1.0 (Excluding points on Q and QA).

[0409] A refrigerant in a forty-seventh aspect is refrigerant E, wherein, in the refrigerant, based on the total sum of R32, CO2, R125, R134a, and R1234yf, when the mass percentage of R32 is a, the mass percentage of CO2 is b, the mass percentage of R125 is c1, the mass percentage of R134a is c2, the mass percentage of the total of R125 and R134a is c, the mass percentage of R1234yf is x, and c1 / (c1+c2) is r, In a three-component composition diagram with vertices at the points where R32 is (100-x) mass%, CO2 is (100-x) mass%, and the total of R125 and R134a is (100-x) mass%, the coordinates (a, b, c) are: 2-1-1) When 43.8≧x≧41 and 0.5≧r≧0.25, point F r=0.25~0.5 (0.0, (-1.1429x+37.257)r 2 +(1.2857x-38.714)r-(-1.7143x+106.89), 100-bx), point P r=0.25~0.5 ((-1.1429x+34.057)r 2 +(1.0x-21.0)r+(-0.4643x+27.636), (2.2857x-119.31)r 2 +(-2.0x+122.0)r+(-0.3929x+19.907), 100-abx) and point D r=0.25~0.5 (0.0, -28.8r 2 +54.0r+(-x+49.9), 100-bx) Is it within the triangle enclosed by the line segment connecting the two lines or is it on that line segment? r=0.25~0.5 F r=0.25~0.5 (excluding the above points), or 2-1-2) When 43.8≧x≧41 and 1.0≧r≧0.5, point F r=0.5~1.0 (0.0, (3.7143x-159.49)r 2 +(-5.0714x+222.53)r+(0.25x+25.45), 100-bx), point Pr=0.5~1.0 ((3.4286x-138.17)r 2 +(-5.4286x+203.57)+(1.6071x-41.593), (-2.8571x+106.74)r 2 +(4.5714x-143.63)r+(-2.3929x+96.027), 100-abx) and point D r=0.5~1.0 (0.0, (-0.5714x+12.229)r 2 +(0.8571x-0.3429)r+(-1.2857x+66.814), 100-bx) Is it within the triangle enclosed by the line segment connecting the two lines or is it on that line segment? r=0.5~1.0 F r=0.5~1.0 (excluding the above points), or 2-2-1) When 46.5≧x≧43 and 0.5≧r≧0.25, point F r=0.25~0.5 (0.0, (9.4815x-428.09)r 2 +(-7.1111x+329.07)r+(-0.2593x+43.156), 100-bx), point P r=0.25~0.5 ((-8.2963x+347.38)r 2 +(4.8889x-191.33)r+(-0.963x+49.478), (7.1111x-330.67)r 2 +(-4.1481x+216.09)r+(-0.2593x+14.056), 100-abx) and point D r=0.25~0.5 (0.0, -28.8r 2 +54.0r+(-x+49.9), 100-bx) Is it within the triangle enclosed by the line segment connecting the two lines or is it on that line segment? r=0.25~0.5 F r=0.25~0.5 (excluding the above points), or 2-2-2) When 46.5≧x≧43 and 1.0≧r≧0.5, point F r=0.5~1.0 (0.0, (-4.7407x+210.84)r 2+(6.963x-304.58)r+(-3.7407x+200.24), 100-bx), point P r=0.5~1.0 ((0.2963x-0.9778)r 2 +(0.2222x-43.933)r+(-0.7778x+62.867), (-0.2963x-5.4222)r 2 +(-0.0741x+59.844)r+(-0.4444x+10.867), 100-abx) and point D r=0.5~1.0 (0.0, -12.8r 2 +37.2r+(-x+54.3), 100-bx) Is it within the triangle enclosed by the line segment connecting the two lines or is it on that line segment? r=0.5~1.0 F r=0.5~1.0 (excluding the above points), or 2-3-1) When 50≧x≧46.5 and 0.37≧r≧0.25, point F r=0.25~0.37 (0.0, (-35.714x+1744.0)r 2 +(23.333x-1128.3)r+(-5.144x+276.32), 100-bx), point P r=0.25~0.37 ((11.905x-595.24)r 2 +(-7.6189x+392.61)r+(0.9322x-39.027), (-27.778x+1305.6)r 2 +(17.46x-796.35)r+(-3.5147x+166.48),100-abx) and point D r=0.25~0.37 (0.0, (0.9143x-71.314)r 2 +(-0.5714x+80.571)+(-0.9143x+45.914), 100-bx) Is it within the triangle enclosed by the line segment connecting the two lines or is it on that line segment? r=0.25~0.37 F r=0.25~0.37 (excluding the above points), or 2-3-2) When 50≧x≧46.5 and 1.0≧r≧0.5, point F r=0.5~1.0(0.0, (2.2857x-115.89)r 2 +(-3.0857x+162.69)r+(-0.3714x+43.571), 100-bx), point P r=0.5~1.0 ((-3.2x+161.6)r 2 +(4.4571x-240.86)r+(-2.0857x+123.69), (2.5143x-136.11)r 2 +(-3.3714x+213.17)r+(0.5429x-35.043), 100-abx) and point D r=0.5~1.0 (0.0, (0.2286x-23.429)r 2 +(-0.4x+55.8)r+(-0.8286x+46.329), 100-bx) Within the triangle enclosed by the line segment connecting r=0.5~1.0 F r=0.5~1.0 (Except for the above points).

[0410] A refrigerant according to a forty-eighth aspect is refrigerant E according to the forty-sixth or forty-seventh aspect, wherein the refrigerant contains 99.5 mass % or more of R32, CO2, R125, R134a and R1234yf in total, based on the total mass of the refrigerant.

[0411] (27) Characteristics of the technologies of each group using the above refrigerants According to the first group of techniques using any of the above refrigerants with a sufficiently small GWP, it is possible to improve the lubrication inside the refrigeration cycle device.

[0412] According to the second group of techniques using any of the above refrigerants with a sufficiently small GWP, it is possible to improve lubrication when operating a refrigeration cycle.

[0413] According to the third group of technologies using any of the above refrigerants with a sufficiently small GWP, a refrigeration cycle can be performed.

[0414] According to the fourth group of techniques that use any of the above refrigerants with a sufficiently small GWP, it is possible to make it difficult for the refrigerant to reach the electrical equipment unit even in the event of a refrigerant leak.

[0415] According to the fifth group of technologies using any of the above refrigerants with a sufficiently small GWP, it is possible to improve the operating efficiency of the refrigeration cycle.

[0416] According to the sixth group of techniques using any of the above refrigerants with a sufficiently small GWP, it is possible to suppress damage to the interconnecting pipes.

[0417] According to the technology of the seventh group, which uses any of the above refrigerants with a sufficiently small GWP, even if the refrigerant leaks, it is possible to prevent fires in the electric heating device.

[0418] According to the technology of the eighth group using any of the above refrigerants with a sufficiently small GWP, a refrigeration cycle can be performed.

[0419] According to the technology of the ninth group, which uses any of the above refrigerants with a sufficiently small GWP, it is possible to keep the decrease in capacity to a minimum.

[0420] According to the technology of the 10th group, which uses any of the above refrigerants with a sufficiently small GWP, the motor rotation speed of the compressor can be changed according to the air conditioning load, thereby making it possible to increase the efficiency of the compressor.

[0421] According to the technology of Group 11, which uses any of the above refrigerants with a sufficiently small GWP, it is possible to achieve good energy efficiency.

[0422] According to the technology of the 12th group, which uses any of the above refrigerants with a sufficiently small GWP, by employing an induction motor as the compressor motor, it is possible to achieve high output at relatively low cost.

[0423] According to the technology of the 13th group, which uses any of the above refrigerants with a sufficiently small GWP, the motor rotation speed of the compressor that compresses the refrigerant can be changed depending on the air conditioning load, thereby achieving high annual energy consumption efficiency [Annual Performance Factor (APF)].

[0424] According to the technology of the 14th group, which uses any of the above refrigerants with a sufficiently small GWP, it is possible to provide an air conditioner that is environmentally friendly.

[0425] According to the technology of the 15th group that uses any of the above refrigerants with a sufficiently small GWP, it is possible to efficiently produce hot water.

[0426] According to the technology of Group 16, which uses any of the above refrigerants with a sufficiently small GWP, it is possible to reduce the material costs of the heat exchanger.

[0427] According to the technology of the 17th group, which uses any of the above refrigerants with a sufficiently small GWP, it is possible to reduce the amount of refrigerant charged into the air conditioner.

[0428] According to the technology of the 18th group, which uses any of the above refrigerants with a sufficiently small GWP, it is possible to improve the heat exchange capacity of the heat source side heat exchanger.

[0429] According to the technology of Group 19, which uses any of the above refrigerants with a sufficiently low GWP, it is possible to cool the control circuit.

[0430] According to the technology of the 20th group, which uses any of the above refrigerants with a sufficiently small GWP, it is possible to properly perform the reheat dehumidification operation.

[0431] According to the technology of the 21st group, which uses any of the above refrigerants with a sufficiently small GWP, it is possible to evaporate the refrigerant in the evaporation zone to dehumidify, and it is also possible to simplify the configuration of the refrigerant circuit.

[0432] According to the technology of the 22nd group, which uses any of the above refrigerants with a sufficiently small GWP, highly efficient operation can be achieved.

[0433] According to the technology of the 23rd group, which uses any of the above refrigerants with sufficiently small GWP, even when the diameters of the liquid side refrigerant connecting pipe and the gas side refrigerant connecting pipe are increased to reduce pressure loss, an increase in costs can be reduced by using pipes made of aluminum or an aluminum alloy.

[0434] According to the technology of the 24th group, which uses any of the above refrigerants with a sufficiently small GWP, it is possible to store cold energy in a heat storage tank.

[0435] According to the technology of the 25th group, which uses any of the above refrigerants with a sufficiently small GWP, it is possible to improve the efficiency of heat exchange. [Brief explanation of the drawings]

[0436] [Figure 1A] FIG. 1 is a schematic diagram of an apparatus used to measure the burning rate. [Figure 1B] FIG. 1 is a diagram showing points and lines defining the refrigerants of the present disclosure on a three-component composition diagram in which the sum of R32, HFO-1132(E), and R1234yf is 100% by mass. [Figure 1C] FIG. 1 is a diagram showing points and lines defining the refrigerants of the present disclosure on a three-component composition diagram in which the total of R32, HFO-1132(E), and R1234yf is 99.4% by mass (CO2 content: 0.6% by mass). [Figure 1D] FIG. 1 is a diagram showing points and lines defining the refrigerants of the present disclosure on a three-component composition diagram in which the total of R32, HFO-1132(E), and R1234yf is 98.8% by mass (CO content: 1.2% by mass). [Figure 1E] FIG. 1 is a diagram showing points and lines defining the refrigerants of the present disclosure on a three-component composition diagram in which the total of R32, HFO-1132(E), and R1234yf is 98.7% by mass (CO content: 1.3% by mass). [Figure 1F] FIG. 1 is a diagram showing points and lines defining the refrigerants of the present disclosure on a three-component composition diagram in which the total of R32, HFO-1132(E), and R1234yf is 97.5% by mass (CO content: 2.5% by mass). [Figure 1G] FIG. 1 is a diagram showing points and lines defining the refrigerants of the present disclosure on a three-component composition diagram in which the total of R32, HFO-1132(E), and R1234yf is 96% by mass (CO2 content: 4% by mass). [Figure 1H] FIG. 1 is a diagram showing points and lines defining the refrigerants of the present disclosure on a three-component composition diagram in which the total of R32, HFO-1132(E), and R1234yf is 94.5% by mass (CO content: 5.5% by mass). [Figure 1I] FIG. 1 is a diagram showing points and lines defining the refrigerants of the present disclosure on a three-component composition diagram in which the total of R32, HFO-1132(E), and R1234yf is 93% by mass (CO2 content: 7% by mass). [Figure 1J] FIG. 1 is a schematic diagram of an experimental device for determining flammability (flammable or non-flammable). [Figure 2A] FIG. 1 shows the mass ratios of HFO-1132(E), HFC-32, and HFO-1234yf contained in refrigerant A1 (the area enclosed by a line passing through four points A, B, C, and D, and the area enclosed by a line passing through four points A, B, E, and F) in a triangular composition diagram of trans-1,2-difluoroethylene (HFO-1132(E)), difluoromethane (HFC-32), and 2,3,3,3-tetrafluoropropene (HFO-1234yf). [Figure 2B] FIG. 1 shows the mass ratios of HFO-1132(E), HFC-32, and HFO-1234yf contained in refrigerant A2 (the area enclosed by a figure passing through five points P, B, Q, R, and S) in a triangular composition diagram of HFO-1132(E), HFC-32, and HFO-1234yf. [Figure 2C]FIG. 1 shows the mass ratios of HFO-1132(E), HFO-1123, and HFO-1234yf contained in refrigerant B in a triangular composition diagram of HFO-1132(E), HFO-1123, and HFO-1234yf (the area enclosed by a line passing through five points A, B, C, D, and E, the area enclosed by a line passing through five points A, B, C, F, and G, and the area enclosed by a line passing through six points A, B, C, H, I, and G). [Figure 2D] A three-component composition diagram illustrating the composition of refrigerant D in the first and second embodiments of the present disclosure. In the enlarged view of FIG. 2D , the maximum composition of refrigerant D in the first embodiment is within the rectangle indicated by X or on a line segment of the rectangle. In the enlarged view of FIG. 2D , a preferred composition of the refrigerant in the first embodiment is within the rectangle indicated by Y or on a line segment of the rectangle. Also, in the enlarged view of FIG. 2D , the composition of refrigerant D in the second embodiment is within the triangle surrounded by line segments RS, ST, and TR or on said line segment. [Figure 2E] FIG. 2 is a three-component composition diagram illustrating the composition of refrigerant D according to the third to seventh embodiments of the present disclosure. [Figure 2F] FIG. 1 is a schematic diagram of an apparatus used in a flammability test. [Figure 2G] FIG. 1 is a schematic diagram showing an example of a counterflow heat exchanger. [Figure 2H] 1A and 1B are schematic diagrams showing an example of a counterflow heat exchanger, in which (a) is a plan view and (b) is a perspective view. [Figure 2I1] 1 is a schematic diagram showing one embodiment of a refrigerant circuit in a refrigerator according to the present disclosure. [Figure 2I2] FIG. 2C is a schematic diagram showing a modification of the refrigerant circuit of FIG. 2H. [Figure 2I3] FIG. 2I is a schematic diagram showing a modification of the refrigerant circuit of FIG. [Figure 2I4] FIG. 2I is a schematic diagram showing a modification of the refrigerant circuit of FIG. [Figure 2I5] FIG. 1 is a schematic diagram illustrating off-cycle defrosting. [Figure 2I6] FIG. 1 is a schematic diagram illustrating heating defrosting. [Figure 2I7] FIG. 1 is a schematic diagram illustrating reverse cycle hot gas defrosting. [Figure 2I8] FIG. 1 is a schematic diagram illustrating positive cycle hot gas defrosting. [Figure 2J] This is a diagram showing the straight line Fr=0.25Pr=0.25 connecting the ASHRAE non-flammable limit points shown in Tables 206 to 209, points Fr=0.25, and points Pr=0.25, in a three-component composition diagram for refrigerant E, with vertices at points where R32 is (100-x) mass%, CO2 is (100-x) mass%, and the sum of R125 and R134a is (100-x) mass%. [Figure 2K] This is a diagram showing the straight line Fr=0.375Pr=0.375, which connects the ASHRAE non-flammable limit points shown in Tables 206 to 209, points Fr=0.375, and points Pr=0.375, in a three-component composition diagram for refrigerant E, with vertices at points where R32 is (100-x) mass%, CO2 is (100-x) mass%, and the sum of R125 and R134a is (100-x) mass%. [Figure 2L] This is a diagram showing the straight line Fr=0.5Pr=0.5 connecting the ASHRAE non-flammable limit points shown in Tables 206 to 209, points Fr=0.5, and points Pr=0.5 in a three-component composition diagram for refrigerant E, with vertices at points where R32 is (100-x) mass%, CO2 is (100-x) mass%, and the sum of R125 and R134a is (100-x) mass%. [Figure 2M] This is a diagram showing the straight line Fr=0.75Pr=0.75, which connects the ASHRAE non-flammable limit points shown in Tables 206 to 209, points Fr=0.75, and points Pr=0.75, in a three-component composition diagram for refrigerant E, with vertices at points where R32 is (100-x) mass%, CO2 is (100-x) mass%, and the sum of R125 and R134a is (100-x) mass%. [Figure 2N] This is a diagram showing the straight line Fr=1.0Pr=1.0 that connects the ASHRAE non-flammable limit points shown in Tables 206 to 209, points Fr=1.0, and points Pr=1.0 in a three-component composition diagram for refrigerant E, with vertices at points where R32 is (100-x) mass%, CO2 is (100-x) mass%, and the sum of R125 and R134a is (100-x) mass%. [Figure 2O]FIG. 1 is a ternary diagram showing points A, Or=0.25 to 1, Dr=0.25 to 1, Cr=0.25 to 1, Fr=0.25 to 1, Pr=0.25 to 1, and Q for refrigerant E when the concentration of R1234yf is 41% by mass. [Figure 2P] FIG. 1 is a ternary diagram showing points A, Or=0.25 to 1, Dr=0.25 to 1, Cr=0.25 to 1, Fr=0.25 to 1, Pr=0.25 to 1, and Q for refrigerant E when the concentration of R1234yf is 43.8 mass %. [Figure 2Q] FIG. 1 is a ternary diagram showing points A, Or=0.25 to 1, Dr=0.25 to 1, Cr=0.25 to 1, Fr=0.25 to 1, Pr=0.25 to 1, and Q for refrigerant E when the concentration of R1234yf is 46.5% by mass. [Figure 2R] FIG. 1 is a ternary diagram showing points A, Or=0.25 to 1, Dr=0.25 to 1, Cr=0.25 to 1, Pr=0.25 to 1, and Q for refrigerant E when the concentration of R1234yf is 50.0 mass %. [Figure 2S] This is a ternary diagram showing points Dr=0.25 to 1, Cr=0.25 to 1, Fr=0.25 to 0.37, Fr=0.5 to 1, Pr=0.25 to 0.37, Pr=0.50 to 1, and Q for refrigerant E when the concentration of R1234yf is 46.5 mass%. [Figure 2T] This is a ternary diagram showing points Dr=0.25 to 1, Cr=0.25 to 1, Fr=0.25 to 0.37, Fr=0.37 to 1, Pr=0.25 to 0.37, Pr=0.37 to 1, and Q when the concentration of R1234yf is 50.0 mass% for refrigerant E. [Figure 3A] FIG. 2 is a schematic configuration diagram of a refrigerant circuit according to a first embodiment of a third group of techniques. [Figure 3B] FIG. 2 is a schematic control block diagram of a refrigeration cycle device according to a first embodiment of a third group of techniques. [Figure 3C] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a second embodiment of the third group of techniques. [Figure 3D] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a second embodiment of the third group of techniques. [Figure 3E] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a third embodiment of the third group of techniques. [Figure 3F] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a third embodiment of the third group of techniques. [Figure 3G] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a fourth embodiment of the third group of techniques. [Figure 3H] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a fourth embodiment of the third group of techniques. [Figure 3I] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a fifth embodiment of the third group of techniques. [Figure 3J] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a fifth embodiment of the third group of techniques. [Figure 3K] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a sixth embodiment of the third group of techniques. [Figure 3L] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a sixth embodiment of the third group of techniques. [Figure 3M] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a seventh embodiment of the third group of techniques. [Figure 3N] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a seventh embodiment of the third group of techniques. [Figure 3O] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to an eighth embodiment of the third group of techniques. [Figure 3P] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to an eighth embodiment of the third group of techniques. [Figure 3Q] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a ninth embodiment of the third group of techniques. [Figure 3R] FIG. 13 is a schematic control block diagram of a refrigeration cycle device according to a ninth embodiment of the third group of techniques. [Figure 3S] FIG. 19 is a schematic configuration diagram of a refrigerant circuit according to a tenth embodiment of the third group of techniques. [Figure 3T]FIG. 20 is a schematic control block diagram of a refrigeration cycle device according to a tenth embodiment of the third group of techniques. [Figure 3U] FIG. 16 is a schematic configuration diagram of a refrigerant circuit according to an eleventh embodiment of the third group of techniques. [Figure 3V] FIG. 19 is a schematic control block diagram of a refrigeration cycle device according to an eleventh embodiment of the third group of techniques. [Figure 3W] FIG. 22 is a schematic configuration diagram of a refrigerant circuit according to a twelfth embodiment of the third group of techniques. [Figure 3X] FIG. 22 is a schematic control block diagram of a refrigeration cycle device according to a twelfth embodiment of the third group of techniques. [Figure 4A] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a first embodiment of a fourth group of techniques. [Figure 4B] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a first embodiment of a fourth group of techniques. [Figure 4C] FIG. 10 is a schematic external perspective view of an outdoor unit according to a first embodiment of the fourth group of techniques. [Figure 4D] FIG. 10 is a perspective view showing a schematic internal structure of an outdoor unit according to a first embodiment of the fourth group of techniques. [Figure 4E] FIG. 10 is a schematic external front view of an indoor unit according to a first embodiment of the fourth group of techniques. [Figure 4F] FIG. 10 is a schematic side view of an indoor unit according to a first embodiment of the fourth group of techniques. [Figure 4G] FIG. 10 is a cross-sectional side view showing a schematic structure of the interior of an indoor unit according to a first embodiment of the fourth group of techniques. [Figure 4H] FIG. 10 is a schematic external front view of an indoor unit according to Modification B of the first embodiment of the fourth group of techniques. [Figure 4I] FIG. 10 is a schematic front view showing the internal structure of an indoor unit according to Modification B of the first embodiment of the fourth group of techniques. [Figure 4J] FIG. 10 is a schematic side view showing a schematic structure of the interior of an indoor unit according to Modification B of the first embodiment of the fourth group of techniques. [Figure 4K]FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a second embodiment of the fourth group of techniques. [Figure 4L] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a second embodiment of the fourth group of techniques. [Figure 4M] FIG. 10 is a perspective view showing a schematic configuration of an outdoor unit (with the front panel removed) according to a second embodiment of the fourth group of techniques. [Figure 4N] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a third embodiment of the fourth group of techniques. [Figure 4O] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a third embodiment of the fourth group of techniques. [Figure 4P] FIG. 10 is a schematic external perspective view of an outdoor unit according to a third embodiment of the fourth group of techniques. [Figure 4Q] FIG. 10 is an exploded perspective view showing a schematic internal structure of an outdoor unit according to a third embodiment of the fourth group of techniques. [Figure 4R] FIG. 10 is a plan view showing a schematic internal structure of an outdoor unit according to a third embodiment of the fourth group of techniques. [Figure 4S] FIG. 10 is a front view showing a schematic internal structure of an outdoor unit according to a third embodiment of the fourth group of techniques. [Figure 4T] FIG. 10 is a schematic configuration diagram of a refrigerant circuit and a water circuit according to a fourth embodiment of the fourth group of techniques. [Figure 4U] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a fourth embodiment of the fourth group of techniques. [Figure 4V] FIG. 10 is a schematic structural diagram of a cold and hot water supply unit according to a fourth embodiment of the fourth group of techniques. [Figure 4W] FIG. 10 is a schematic configuration diagram of a refrigerant circuit and a water circuit according to Modification A of the fourth embodiment of the fourth group of techniques. [Figure 4X] FIG. 10 is a schematic diagram of a hot water storage device according to variant A of the fourth embodiment of the fourth group of techniques. [Figure 5A] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a first embodiment of the fifth group of techniques. [Figure 5B]FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a first embodiment of the fifth group of techniques. [Figure 5C] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to Modification B of the first embodiment of the fifth group of techniques. [Figure 5D] FIG. 10 is a cross-sectional side view showing a schematic configuration of a compressor according to Modification B of the first embodiment of the fifth group of techniques. [Figure 5E] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a second embodiment of the fifth group of techniques. [Figure 5F] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a second embodiment of the fifth group of techniques. [Figure 5G] FIG. 10 is a cross-sectional side view showing a schematic configuration of a compressor according to a second embodiment of the fifth group of techniques. [Figure 5H] FIG. 10 is a cross-sectional plan view showing the periphery of a cylinder chamber of a compressor according to a second embodiment of the fifth group of techniques. [Figure 5I] FIG. 10 is a cross-sectional plan view of a piston of a compressor according to a second embodiment of the fifth group of techniques. [Figure 6A] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a first embodiment of a sixth group of techniques. [Figure 6B] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a first embodiment of a sixth group of techniques. [Figure 6C] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a second embodiment of the sixth group of techniques. [Figure 6D] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a second embodiment of the sixth group of techniques. [Figure 6E] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a third embodiment of the sixth group of techniques. [Figure 6F] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a third embodiment of the sixth group of techniques. [Figure 7A] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a first embodiment of the seventh group of techniques. [Figure 7B]FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a first embodiment of the seventh group of techniques. [Figure 7C] FIG. 10 is a schematic external perspective view of an outdoor unit according to a first embodiment of the seventh group of techniques. [Figure 7D] FIG. 12 is a schematic perspective view of a drain pan heater provided on a bottom plate of the seventh group of techniques. [Figure 7E] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a second embodiment of the seventh group of techniques. [Figure 7F] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a second embodiment of the seventh group of techniques. [Figure 7G] FIG. 10 is a schematic external perspective view of an outdoor unit according to a second embodiment of the seventh group of techniques (with the front panel of the machine room removed). [Figure 7H] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a third embodiment of the seventh group of techniques. [Figure 7I] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a third embodiment of the seventh group of techniques. [Figure 7J] FIG. 10 is a schematic external perspective view of an outdoor unit according to a third embodiment of the seventh group of techniques. [Figure 7K] FIG. 10 is a schematic exploded perspective view of an outdoor unit according to a third embodiment of the seventh group of technologies. [Figure 7L] FIG. 12 is a schematic perspective view of the external appearance of an IH heater according to a seventh group of techniques. [Figure 7M] FIG. 10 is a schematic cross-sectional view of an IH heater according to the seventh group of techniques. [Figure 8A] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a first embodiment of an eighth group of techniques. [Figure 8B] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a first embodiment of the eighth group of techniques. [Figure 8C] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a second embodiment of the eighth group of techniques. [Figure 8D] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a second embodiment of the eighth group of techniques. [Figure 8E] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a third embodiment of the eighth group of techniques. [Figure 8F] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a third embodiment of the eighth group of techniques. [Figure 9A] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a first embodiment of the ninth group of techniques. [Figure 9B] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a first embodiment of the ninth group of techniques. [Figure 9C] 10 shows a graph of pressure loss in liquid-side refrigerant connection piping for each pipe outer diameter during heating operation when refrigerants R410A, R32, and refrigerant X are used in an air conditioner according to a first embodiment of the ninth group of techniques. [Figure 9D] 10 shows a graph of pressure loss in gas side refrigerant connection piping during cooling operation for each pipe outer diameter when refrigerants R410A, R32, and refrigerant X are used in an air conditioner according to a first embodiment of the ninth group of techniques. [Figure 9E] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a second embodiment of the ninth group of techniques. [Figure 9F] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a second embodiment of the ninth group of techniques. [Figure 9G] 10 shows a graph of pressure loss in the liquid refrigerant communication pipe for each pipe outer diameter during heating operation when using refrigerants R410A, R32, and refrigerant X in an air conditioner according to a second embodiment of the ninth group of techniques. [Figure 9H] 10 shows a graph of pressure loss in gas side refrigerant connection piping during cooling operation for each pipe outer diameter when refrigerants R410A, R32, and refrigerant X are used in an air conditioner according to a second embodiment of the ninth group of techniques. [Figure 9I] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a third embodiment of the ninth group of techniques. [Figure 9J] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a third embodiment of the ninth group of techniques. [Figure 9K]10 shows a graph of pressure loss in the liquid refrigerant communication pipe for each pipe outer diameter during heating operation when using refrigerants R410A, R32, and refrigerant X in an air conditioner according to a third embodiment of the ninth group of techniques. [Figure 9L] 10 shows a graph of pressure loss in gas side refrigerant connection piping during cooling operation for each pipe outer diameter when refrigerants R410A, R32, and refrigerant X are used in an air conditioner according to a third embodiment of the ninth group of techniques. [Figure 10A] FIG. 10 is a refrigerant circuit diagram of an air conditioner that uses a compressor according to an embodiment of the tenth group of techniques. [Figure 10B] FIG. 10 is a longitudinal sectional view of a compressor according to an embodiment of the technology of the 10th group. [Figure 10C] FIG. 10 is a cross-sectional view of a motor cut along a plane perpendicular to the rotation axis of the 10th group of technologies. [Figure 10D] FIG. 10 is a cross-sectional view of a rotor cut along a plane perpendicular to the rotation axis of the technology of the 10th group. [Figure 10E] FIG. 10 is a perspective view of a rotor according to the tenth group of technologies. [Figure 10F] FIG. 10 is a cross-sectional view of another rotor cut along a plane perpendicular to the rotation axis of the 10th group of technologies. [Figure 10G] FIG. 10 is a longitudinal sectional view of a compressor according to a second embodiment of the technology of the 10th group. [Figure 11A] FIG. 1 is a schematic configuration diagram of a refrigerant circuit according to a first embodiment of the technology of an eleventh group. [Figure 11B] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a first embodiment of the technology of the 11th group. [Figure 11C] FIG. 11 is a schematic external perspective view of an outdoor unit according to a first embodiment of the technology of the 11th group. [Figure 11D] FIG. 11 is a perspective view showing a schematic internal structure of an outdoor unit according to a first embodiment of the technology of the 11th group. [Figure 11E] FIG. 11 is a schematic external front view of an indoor unit according to a first embodiment of the technology of the 11th group. [Figure 11F]FIG. 11 is a cross-sectional side view showing a schematic structure of the interior of an indoor unit according to a first embodiment of the technology of the 11th group. [Figure 11G] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a second embodiment of the technology of the 11th group. [Figure 11H] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a second embodiment of the technology of the 11th group. [Figure 11I] FIG. 11 is a schematic external perspective view of an outdoor unit according to a second embodiment of the technology of the eleventh group. [Figure 11J] FIG. 11 is a perspective view showing a schematic internal structure of an outdoor unit according to a second embodiment of the technology of the 11th group. [Figure 11K] FIG. 11 is a schematic external perspective view of an indoor unit according to a second embodiment of the technology of the eleventh group. [Figure 11L] FIG. 11 is a cross-sectional side view showing a schematic structure of the interior of an indoor unit according to a second embodiment of the technology of the eleventh group. [Figure 11M] FIG. 10 is a schematic configuration diagram of a refrigerant circuit according to a third embodiment of the technology of the 11th group. [Figure 11N] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to a third embodiment of the technology of the 11th group. [Figure 11O] FIG. 11 is a schematic external perspective view of an outdoor unit according to a third embodiment of the technology of the 11th group. [Figure 11P] FIG. 11 is an exploded perspective view showing a schematic internal structure of an outdoor unit according to a third embodiment of the technology of the 11th group. [Figure 12A] FIG. 10 is a refrigerant circuit diagram of an air conditioner that uses a compressor according to an embodiment of the 12th group of techniques. [Figure 12B] FIG. 10 is a longitudinal sectional view of a compressor according to an embodiment of the twelfth group of techniques. [Figure 12C] FIG. 12 is a cross-sectional view of a motor taken along a plane perpendicular to the rotation axis of the 12th group of technology. [Figure 12D] FIG. 12 is a cross-sectional view of a rotor cut along a plane perpendicular to the rotation axis of the 12th group of technologies. [Figure 12E]FIG. 12 is a perspective view of a rotor according to the twelfth group of technologies. [Figure 12F] FIG. 10 is a perspective view of a rotor 71 used in an induction motor of a compressor according to a second modification of the twelfth group of techniques. [Figure 12G] FIG. 10 is a refrigerant circuit diagram of an air conditioner that uses a compressor according to a third modification of the technology of the twelfth group. [Figure 12H] FIG. 10 is a longitudinal sectional view of a compressor according to a second embodiment of the technology of the twelfth group. [Figure 13A] FIG. 10 is a configuration diagram of an air conditioner according to a first embodiment of the technology of the 13th group. [Figure 13B] FIG. 10 is a circuit block diagram of a power conversion device mounted in a first embodiment of the technology of the 13th group. [Figure 13C] FIG. 13 is a circuit block diagram of a power conversion device according to a modified example of the first embodiment of the technology of the 13th group. [Figure 13D] FIG. 10 is a circuit block diagram of a power conversion device mounted on an air conditioner according to a second embodiment of the technology of the thirteenth group. [Figure 13E] FIG. 13 is a circuit block diagram of a power conversion device according to a modified example of the second embodiment of the technology of the thirteenth group. [Figure 13F] FIG. 10 is a circuit block diagram of a power conversion device mounted on an air conditioner according to a third embodiment of the technology of the 13th group. [Figure 13G] FIG. 13 is a circuit diagram conceptually illustrating a bidirectional switch according to the 13th group of techniques. [Figure 13H] FIG. 13 is a circuit diagram showing an example of a current direction in a matrix converter according to the 13th group of techniques. [Figure 13I] FIG. 13 is a circuit diagram showing an example of another current direction in the matrix converter of the 13th group of techniques. [Figure 13J] FIG. 13 is a circuit block diagram of a power conversion device according to a modification of the third embodiment of the technology of the 13th group. [Figure 13K] FIG. 13 is a circuit diagram of a clamp circuit according to the 13th group of techniques. [Figure 14A] FIG. 10 is a configuration diagram of an air conditioner according to an embodiment of the technology of the 14th group. [Figure 14B] FIG. 11 is a circuit diagram showing the operation of the compressor motor in the technology of the 14th group. [Figure 14C] FIG. 11 is an operating circuit diagram of a motor of a compressor in an air conditioner according to a modification of the technology of the 14th group. [Figure 15A] FIG. 10 is an external view of a hot water supply system as a hot water production device according to a first embodiment of the technology of the 15th group. [Figure 15B] FIG. 10 is a diagram showing a water circuit and a refrigerant circuit of a hot water supply system according to a first embodiment of the technology of the 15th group. [Figure 15C] FIG. 10 is a control block diagram of a hot water supply system according to a first embodiment of the technology of the 15th group. [Figure 15D] FIG. 11 is a diagram showing a water circuit and a refrigerant circuit of a hot water supply system according to a first modified example of the first embodiment of the technology of the 15th group. [Figure 15E] FIG. 11 is a diagram showing a water circuit and a refrigerant circuit of a hot water supply system according to a second modified example of the first embodiment of the technology of the 15th group. [Figure 15F] FIG. 10 is a diagram showing a part of the configuration of a hot water circulation heating system as a hot water producing apparatus according to a second embodiment of the technology of the 15th group. [Figure 15G] FIG. 10 is a diagram showing a part of the configuration of a hot water circulation heating system according to a second embodiment of the technology of the 15th group. [Figure 15H] FIG. 10 is a diagram showing a part of the configuration of a hot water circulation heating system according to a second embodiment of the technology of the 15th group. [Figure 15I] FIG. 10 is a control block diagram of a hot water circulation heating system according to a second embodiment of the technology of the 15th group. [Figure 15J] FIG. 10 is a diagram showing a part of the configuration of a hot water circulation heating system according to a first modified example of the second embodiment of the technology of the 15th group. [Figure 15K] FIG. 10 is a diagram showing a part of the configuration of a hot water circulation heating system according to a second modified example of the second embodiment of the technology of the 15th group. [Figure 15L] FIG. 10 is a schematic configuration diagram of a hot water supply system as a hot water production device according to a third embodiment of the technology of the 15th group. [Figure 15M]FIG. 10 is a schematic configuration diagram of a heat source unit of a hot water supply system according to a third embodiment of the technology of the 15th group. [Figure 15N] FIG. 10 is a control block diagram of a hot water supply system according to a third embodiment of the technology of the 15th group. [Figure 16A] FIG. 1 is a schematic configuration diagram of a refrigeration device according to a first embodiment of the technology of the 16th group. [Figure 16B] FIG. 10 is a front view of an outdoor heat exchanger or an indoor heat exchanger according to a first embodiment of the technology of the 16th group. [Figure 16C] FIG. 10 is a cross-sectional view of a flat tube of a heat exchanger according to a first embodiment of the technology of the 16th group. [Figure 16D] FIG. 10 is a schematic perspective view of an outdoor heat exchanger according to a second embodiment of the technology of the 16th group. [Figure 16E] FIG. 11 is a partial enlarged view of a heat exchange tube portion of the outdoor heat exchanger according to the technology of the 16th group cut in the vertical direction. [Figure 16F] FIG. 10 is a cross-sectional view in the pipe axis direction showing the configuration of an inner grooved pipe according to a third embodiment of the technology of the 16th group. [Figure 16G] FIG. 16C is a cross-sectional view of the inner grooved pipe shown in FIG. 16F taken along line II. [Figure 16H] FIG. 16F is a partially enlarged view showing a portion of the inner grooved pipe shown in FIG. 16G. [Figure 16I] FIG. 10 is a plan view showing the configuration of plate fins in the technology of the 16th group. [Figure 17A] FIG. 10 is a schematic diagram showing the arrangement of an air conditioner according to a first embodiment of the technology of the 17th group. [Figure 17B] FIG. 10 is a schematic diagram of an air conditioning device according to the seventeenth group of techniques. [Figure 17C] FIG. 10 is a block diagram showing an electrical connection state of a controller and a thermostat in an air conditioning system according to a first embodiment of the technology of the 17th group. [Figure 17D] FIG. 10 is a perspective view showing an air conditioner according to a second embodiment of the technology of the 17th group installed in a building. [Figure 17E] FIG. 11 is a perspective view showing the appearance of an air conditioner according to the seventeenth group of techniques. [Figure 17F] FIG. 11 is a perspective view showing the appearance of an air conditioner according to the seventeenth group of techniques. [Figure 17G] FIG. 12 is a perspective view illustrating the internal configuration of the air conditioner according to the seventeenth group of techniques. [Figure 17H] FIG. 12 is a perspective view illustrating the internal configuration of the air conditioner according to the seventeenth group of techniques. [Figure 17I] FIG. 12 is a perspective view illustrating the internal configuration of the air conditioner according to the seventeenth group of techniques. [Figure 17J] FIG. 13 is a perspective view illustrating a duct of the air conditioner according to the seventeenth group of techniques. [Figure 17K] FIG. 10 is a diagram illustrating a refrigerant circuit of an air conditioner according to a second embodiment of the technology of the 17th group. [Figure 17L] FIG. 10 is a block diagram illustrating a control system of an air conditioner according to a second embodiment of the technology of the 17th group. [Figure 17M] FIG. 12 is a partially enlarged perspective view showing the periphery of the left side of the user-side heat exchanger of the seventeenth group of technology. [Figure 17N] 13 is a schematic diagram for explaining the positional relationship between the first opening and the second opening and each member in the technology of the 17th group. FIG. [Figure 17O] FIG. 10 is a schematic diagram showing the configuration of an air conditioning apparatus according to a third embodiment of the technology of the 17th group. [Figure 18A] FIG. 10 is a refrigerant circuit diagram showing a refrigeration cycle according to a first embodiment of the technology of the 18th group. [Figure 18B] FIG. 10 is a longitudinal cross-sectional view of a utilization unit of the 18th group technology. [Figure 18C] FIG. 10 is a Mollier diagram showing the operating state of a refrigeration cycle according to a first embodiment of the technology of the 18th group. [Figure 18D] FIG. 10 is a refrigerant circuit diagram showing a refrigeration cycle according to a second embodiment of the technology of the 18th group. [Figure 19A] FIG. 10 is a piping diagram of a refrigerant circuit 10 of an air conditioner 1 according to a first embodiment of the technology of a 19th group. [Figure 19B]FIG. 10 is a diagram showing the mounting structure of the power element 33, the refrigerant jacket 20, and the heat transfer plate 50 in the first embodiment of the technology of the 19th group. [Figure 19C] FIG. 10 is a diagram showing a cross-sectional shape of an outdoor unit 100 in a first embodiment of the technology of the 19th group. [Figure 19D] FIG. 10 is a front view of the outdoor unit 100 according to the first embodiment of the technology of the 19th group. [Figure 19E] FIG. 10 is a schematic side view of a main part of an outdoor unit 100 of an air conditioner 1 according to a second embodiment of the technology of the 19th group. [Figure 20A] FIG. 10 is a circuit diagram of an air conditioner according to an embodiment of the 20th group of techniques. [Figure 20B] FIG. 10 is a cross-sectional view showing the configuration of a dehumidification solenoid valve according to an embodiment of the 20th group of techniques. [Figure 20C] FIG. 10 is a cross-sectional view showing the configuration of a dehumidification solenoid valve according to an embodiment of the 20th group of techniques. [Figure 20D] FIG. 10 is a diagram showing the configuration of a tapered surface of a valve seat of a dehumidification solenoid valve in an embodiment of the technology of the 20th group. [Figure 21A] FIG. 10 is a circuit diagram showing a refrigerant circuit of an air conditioner according to an embodiment of the technology of the 21st group. [Figure 21B] FIG. 10 is a schematic cross-sectional view of an indoor unit of an air conditioner according to an embodiment of the 21st group of techniques. [Figure 21C] FIG. 10 is a diagram illustrating the configuration of an indoor heat exchanger in an embodiment of the technology of the 21st group. [Figure 21D] FIG. 10 is a diagram illustrating a control unit of an air conditioner according to an embodiment of the technology of the 21st group. [Figure 21E] 10 shows an example of a change in flow rate when the opening degree is changed in an expansion valve in an embodiment of the technology of the 21st group. [Figure 21F] FIG. 10 is a diagram illustrating the operation of an air conditioner according to an embodiment of the technology of the 21st group. [Figure 22A] FIG. 10 is a schematic diagram showing an example of a counterflow type heat exchanger according to an embodiment of the technology of the 22nd group. [Figure 22B]10A and 10B are schematic diagrams showing another example of a counterflow type heat exchanger according to an embodiment of the 22nd group of techniques, where (a) is a plan view and (b) is a perspective view. [Figure 22C] FIG. 2 is a schematic diagram showing one aspect of the configuration of a refrigerant circuit in a refrigeration cycle device according to a first embodiment of the technology of the 22nd group. [Figure 22D] FIG. 22D is a schematic diagram showing a modification of the refrigerant circuit of FIG. 22C. [Figure 22E] FIG. 22E is a schematic diagram showing a modification of the refrigerant circuit of FIG. 22D. [Figure 22F] FIG. 22E is a schematic diagram showing a modification of the refrigerant circuit of FIG. 22D. [Figure 22G] FIG. 10 is a schematic diagram showing the configuration of a refrigerant circuit of an air conditioner as an example of a refrigeration cycle device according to a second embodiment of the technology of the 22nd group. [Figure 22H] FIG. 22B is a schematic control block diagram of the air conditioning apparatus of FIG. 22G. [Figure 22I] FIG. 10 is a schematic diagram showing the configuration of a refrigerant circuit of an air conditioner as an example of a refrigeration cycle device according to a third embodiment of the technology of the 22nd group. [Figure 22J] FIG. 22I is a schematic control block diagram of the air conditioning apparatus. [Figure 23A] FIG. 1 is a schematic configuration diagram of a refrigerant circuit according to an embodiment of the 23rd group of techniques. [Figure 23B] FIG. 10 is a schematic control block diagram of a refrigeration cycle device according to an embodiment of the 23rd group of techniques. [Figure 23C] 10 is a comparison table showing, for each rated refrigeration capacity, the outer diameters of copper pipes used for the gas side refrigerant communication pipes and liquid side refrigerant communication pipes of an air conditioning system that uses refrigerant X, and the outer diameters of the gas side refrigerant communication pipes and liquid side refrigerant communication pipes when aluminum pipes are used instead of copper pipes, in one embodiment of the technology of the 23rd group. [Figure 23D] 10 is a comparison table showing the wall thickness of copper pipes and aluminum pipes by "pipe designation" in one embodiment of the technology of the 23rd group. [Figure 24A]FIG. 10 is a circuit diagram showing a heat storage operating state of a heat storage device according to a first embodiment of the technology of the 24th group. [Figure 24B] FIG. 10 is a vertical cross-sectional view of a heat storage tank of a heat storage device according to a first embodiment of the technology of the 24th group. [Figure 24C] 24B is a diagram corresponding to FIG. 24A and illustrating a heat storage recovery cooling operation state of the heat storage device according to the first embodiment of the technology of the 24th group. FIG. [Figure 24D] FIG. 10 is a cross-sectional view showing a state in which ice has adhered to a cooling pipe of a heat storage device according to a first embodiment of the technology of the 24th group. [Figure 24E] FIG. 24C is a diagram showing a modified example of the cooling pipe, corresponding to FIG. 24B. [Figure 24F] FIG. 10 is a circuit diagram showing a heat storage operating state of a heat storage device according to a second embodiment of the technology of the 24th group. [Figure 24G] FIG. 24F is a diagram illustrating a heat storage recovery cooling operation state of the heat storage device according to the second embodiment of the 24th group of techniques. [Figure 24H] FIG. 10 is a vertical cross-sectional view of a heat storage tank of a heat storage device according to a second embodiment of the technology of the 24th group during a heat storage recovery cooling operation. [Figure 24I] FIG. 10 is a cross-sectional view of a heat storage tank of a heat storage device according to a second embodiment of the technology of the 24th group during heat storage recovery cooling operation. [Figure 25A] FIG. 1 is a schematic configuration diagram of a heat load treatment system that is a refrigeration device according to a first embodiment of the technology of the 25th group. [Figure 25B] FIG. 10 is a schematic diagram showing an installation mode of a heat load treatment system according to a first embodiment of the technology of the 25th group. [Figure 25C] FIG. 10 is a control block diagram of a heat load treatment system according to a first embodiment of the technology of the 25th group. [Figure 25D] FIG. 10 is a refrigerant circuit diagram of a cascade refrigeration system, which is a refrigeration system according to a second embodiment of the technology of the 25th group. [Figure 25E] FIG. 10 is a circuit configuration diagram of an air conditioning and hot water supply system that is a refrigeration device according to a second embodiment of the technology of the 25th group. DETAILED DESCRIPTION OF THE INVENTION

[0437] (1) (1-1) Definition of terms As used herein, the term "refrigerant" includes at least compounds assigned a refrigerant number (ASHRAE number) beginning with the letter R, which indicates the type of refrigerant, as defined by ISO 817 (International Organization for Standardization), and also includes compounds that have equivalent refrigerant properties even if they have not yet been assigned a refrigerant number. Refrigerants are broadly classified into "fluorocarbon compounds" and "non-fluorocarbon compounds" based on their chemical structure. "Fluorocarbon compounds" include chlorofluorocarbons (CFCs), hydrochlorofluorocarbons (HCFCs), and hydrofluorocarbons (HFCs). "Non-fluorocarbon compounds" include propane (R290), propylene (R1270), butane (R600), isobutane (R600a), carbon dioxide (R744), and ammonia (R717).

[0438] In this specification, the term "composition containing a refrigerant" includes at least (1) a refrigerant itself (including a mixture of refrigerants), (2) a composition that further contains other components and can be used to obtain a working fluid for a refrigerant by mixing with at least a refrigerating machine oil, and (3) a working fluid for a refrigerant containing a refrigerating machine oil. In this specification, of these three aspects, the composition (2) is referred to as a "refrigerant composition" to distinguish it from the refrigerant itself (including a mixture of refrigerants). Furthermore, the working fluid for a refrigerant (3) is referred to as a "refrigerating machine oil-containing working fluid" to distinguish it from the "refrigerant composition."

[0439] As used herein, the term "substitution," when used in the context of "replacing" a first refrigerant with a second refrigerant, refers to a first type of equipment designed to operate using a first refrigerant, which can be operated under optimal conditions using a second refrigerant with only minor component changes (at least one of refrigeration oil, gaskets, packing, expansion valves, dryers, and other components) and equipment adjustments, as necessary. In other words, this type refers to operating the same equipment with a "substitution" of a refrigerant. This type of "substitution" can be categorized as "drop-in substitution," "nearly drop-in substitution," or "retrofit," in order of decreasing degree of change or adjustment required when replacing with the second refrigerant.

[0440] The second category, where equipment designed to operate with a second refrigerant is installed and used for the same purpose as an existing use of a first refrigerant, is also included in the term "substitution." This category refers to "substituting" a refrigerant to serve the same purpose.

[0441] In this specification, the term "refrigerator" refers to a device that removes heat from an object or space, thereby lowering the temperature below that of the surrounding air, and maintaining that low temperature. In other words, a refrigerator is a conversion device that obtains energy from an external source, performs work, and converts it into energy in order to transfer heat from a low-temperature object to a high-temperature object.

[0442] In this disclosure, a refrigerant being "non-flammable" means that the WCF (Worst Case Formulation for Flammability) composition, which is the most flammable composition among the allowable refrigerant concentrations, is determined to be "Class 1" in the US ANSI / ASHRAE34-2013 standard.

[0443] In this specification, a refrigerant being "weakly flammable" means that the WCF composition is determined to be "Class 2" according to the US ANSI / ASHRAE34-2013 standard.

[0444] In this disclosure, a refrigerant is considered "ASHRAE nonflammable" if its WCF or WCFF composition is determined to be nonflammable using the test equipment and method specified in ASTM E681-2009 (Standard Test Methods for Flammable Concentration Limits of Chemicals (Vapors and Gases)). The WCF or WCFF composition is classified as "Class 1 ASHRAE nonflammable (WCF nonflammable)" or "Class 1 ASHRAE nonflammable (WCFF nonflammable)," respectively. The WCFF composition (worst case of fractionation for flammability) is determined by leak testing during storage, transportation, and use in accordance with ANSI / ASHRAE34-2013.

[0445] In this specification, a refrigerant being "mildly flammable" means that the WCF composition is determined to be "Class 2L" according to the US ANSI / ASHRAE34-2013 standard.

[0446] As used herein, a refrigerant is "WCF mildly flammable" means that its most flammable formulation (WCF) has a burning velocity of 10 cm / s or less according to the U.S. ANSI / ASHRAE 34-2013 standard. Also, as used herein, a refrigerant is "ASHRAE mildly flammable" means that its WCF has a burning velocity of 10 cm / s or less, and its most flammable fraction (WCFF), determined by leak testing during storage, transportation, and use according to ANSI / ASHRAE 34-2013, has a burning velocity of 10 cm / s or less, and its flammability classification according to the U.S. ANSI / ASHRAE 34-2013 standard is determined to be "Class 2L."

[0447] As used herein, the term "temperature glide" can be rephrased as the absolute value of the difference between the start temperature and end temperature of a phase change process of a composition containing the refrigerant of the present disclosure in a component of a thermal cycle system.

[0448] In this specification, the term "vehicle air conditioner" refers to a type of refrigeration device used in automobiles such as gasoline vehicles, hybrid vehicles, electric vehicles, hydrogen vehicles, etc. The term "vehicle air conditioner" refers to a refrigeration device that has a refrigeration cycle in which heat is exchanged with a liquid refrigerant in an evaporator, the evaporated refrigerant gas is sucked into a compressor, the adiabatically compressed refrigerant gas is cooled and liquefied in a condenser, and the refrigerant is further adiabatically expanded by passing through an expansion valve, and then supplied to the evaporator again as a liquid refrigerant.

[0449] In this specification, the term "turbo chiller" refers to a type of large-scale chiller. A turbo chiller refers to a refrigeration device that performs heat exchange with a liquid refrigerant in an evaporator, draws the evaporated refrigerant gas into a centrifugal compressor, cools and liquefies the adiabatically compressed refrigerant gas in a condenser, and then adiabatically expands the refrigerant gas through an expansion valve before supplying it back to the evaporator as a liquid refrigerant. Note that the above "large-scale chiller" refers to a large-scale air conditioner used for air conditioning an entire building.

[0450] In this specification, "saturation pressure" means the pressure of saturated steam.

[0451] In this specification, the term "discharge temperature" refers to the temperature of the mixed refrigerant at the discharge port of the compressor.

[0452] In this specification, "evaporation pressure" means the saturation pressure at the evaporation temperature.

[0453] In this specification, the term "critical temperature" refers to the temperature at the critical point, and refers to the temperature below which a gas cannot be liquefied even if it is compressed.

[0454] In this specification, the evaporation temperature in a refrigeration cycle refers to the temperature at which a refrigerant liquid absorbs heat and turns into vapor during the evaporation process of the refrigeration cycle. The evaporation temperature in a refrigeration cycle can be determined by measuring the temperature at the evaporator inlet and / or outlet. For simple refrigerants and azeotropic refrigerants, the evaporation temperature is constant, but for non-azeotropic refrigerants, the evaporation temperature is the average of the evaporator inlet temperature and the dew point temperature. That is, for non-azeotropic refrigerants, the evaporation temperature can be calculated as "evaporation temperature = (evaporator inlet temperature + dew point temperature) / 2."

[0455] In this specification, GWP refers to a value based on the value in the Fourth Assessment Report of the Intergovernmental Panel on Climate Change (IPCC).

[0456] In this specification, the term "mass ratio" has the same meaning as the term "composition ratio."

[0457] In this specification, a numerical range indicated using "to" indicates a range that includes the numerical values ​​before and after "to" as the minimum and maximum values, respectively.

[0458] In this specification, the terms "contain" and "include" are used to contemplate the concepts of "consisting essentially of" and "consisting only of."

[0459] In this specification, the term "refrigeration system" broadly refers to any device that removes heat from an object or space to lower its temperature below that of the surrounding air and maintains that low temperature. In other words, in a broad sense, a refrigeration system refers to a conversion device that obtains energy from an external source, performs work, and converts it into energy in order to transfer heat from a low-temperature environment to a high-temperature environment. In this disclosure, a refrigeration system is broadly synonymous with a heat pump.

[0460] In addition, in this disclosure, in the narrow sense, refrigeration devices are used to distinguish them from heat pumps due to the difference in the temperature range and operating temperature used. In this case, a refrigeration device is a device that places a low-temperature heat source in a temperature range lower than atmospheric temperature, while a heat pump is a device that uses the heat dissipation effect by placing a low-temperature heat source near atmospheric temperature and driving a refrigeration cycle. Note that there are also devices that combine the functions of both a refrigeration device in the narrow sense and a heat pump in the narrow sense, such as air conditioners that have a "cooling mode" and a "heating mode." In this specification, unless otherwise specified, the terms "refrigeration device" and "heat pump" are all used in the broad sense.

[0461] (1-2) Refrigerant As will be described in detail later, any one of refrigerant X, refrigerant Y, refrigerant A, refrigerant B, refrigerant C, refrigerant D, and refrigerant E of the present disclosure (sometimes referred to as "the refrigerant of the present disclosure") can be used as the refrigerant.

[0462] (1-3) Various refrigerants The refrigerants X, Y, and A to E used in the present disclosure will be described in detail below.

[0463] Note that the following descriptions of refrigerant X, refrigerant Y, refrigerant A, refrigerant B, refrigerant C, refrigerant D, and refrigerant E are independent of each other, and the letters indicating points and lines, the numbers of the examples, and the numbers of the comparative examples are all independent of each other among refrigerant X, refrigerant Y, refrigerant A, refrigerant B, refrigerant C, refrigerant D, and refrigerant E.

[0464] (1-3-1) Refrigerant X 1. Refrigerant 1.1 Refrigerant components The refrigerant of the present disclosure is a mixed refrigerant including CO2, R32, HFO-1132(E), and R1234yf.

[0465] The refrigerant of the present disclosure has desirable properties as an alternative to R410A, such as a cooling capacity equivalent to that of R410A, a sufficiently small GWP, and mild flammability.

[0466] In the refrigerant of the present disclosure, when the mass percentages of CO2, R32, HFO-1132(E), and R1234yf based on the sum of these are w, x, y, and z, respectively, in a ternary composition diagram in which the sum of R32, HFO-1132(E), and R1234yf is (100-w) mass%, the coordinates (x, y, z) are as follows: Point I(0.0, 72.0, 28.0-w) Point J(18.3, 48.5, 33.2-w) Point K(36.8, 35.6, 27.6-w) Point L(51.7, 28.9, 19.4-w) Point B''(-1.5278w 2 +2.75w+50.5, 0.0, 1.5278w 2 -3.75w+49.5) Point D(-2.9167w+40.317, 0.0, 1.9167w+59.683) Point C(0.0, -4.9167w+58.317, 3.9167w+41.683) The points are within the range of the figure enclosed by the curves IJ, JK and KL, as well as the lines LB'', B''D, DC and CI, which connect the seven points above, or on the line segments mentioned above (however, points on the lines B''D and CI are excluded). 1.2 <w≦4.0のとき、 Point I(0.0, 72.0, 28.0-w) Point J(18.3, 48.5, 33.2-w) Point K(36.8, 35.6, 27.6-w) Point L(51.7, 28.9, 19.4-w) Point B''(51.6, 0.0, 48.4-w) Point D(-2.8226w+40.211, 0.0, 1.8226w+59.789) Point C(0.0, 0.1081w 2 -5.169w+58.447, -0.1081w 2 +4.169w+41.553) The points are within the range of the figure enclosed by the curves IJ, JK and KL, as well as the lines LB'', B''D, DC and CI, which connect the seven points above, or on the line segments mentioned above (however, points on the lines B''D and CI are excluded). 4.0 <w≦7.0のとき、 Point I(0.0, 72.0, 28.0-w) Point J(18.3, 48.5, 33.2-w) Point K(36.8, 35.6, 27.6-w) Point L(51.7, 28.9, 19.4-w) Point B''(51.6, 0.0, 48.4-w) Point D (-2.8w+40.1, 0.0, 1.8w+59.9) Point C(0.0, 0.0667w 2 -4.9667w+58.3, -0.0667w 2 +3.9667w+41.7) The points are within the range of the figure bounded by the curves IJ, JK, and KL, as well as the lines LB'', B''D, DC, and CI, which connect the seven points above, or on the line segments mentioned above (however, points on the lines B''D and CI are excluded), and The curve IJ is Coordinate(x, 0.0236x 2 -1.716x+72, -0.0236x 2 +0.716x+28-w) It is expressed as Curvy JK is Coordinates (x, 0.0095x 2 -1.2222x+67.676, -0.0095x 2 +0.2222x+32.324-w) It is expressed as The curve KL is Coordinate(x, 0.0049x 2 -0.8842x+61.488, -0.0049x 2 -0.1158x+38.512) It is expressed as:

[0467] The refrigerant of the present disclosure has a refrigeration capacity ratio of 80% or more based on R410A, a GWP of 350 or less, and is a WCF mildly flammable refrigerant.

[0468] In the refrigerant of the present disclosure, when the mass percentages of CO2, R32, HFO-1132(E), and R1234yf based on the sum of these are w, x, y, and z, respectively, in a ternary composition diagram in which the sum of R32, HFO-1132(E), and R1234yf is (100-w) mass%, the coordinates (x, y, z) are as follows: 0 <w≦1.2のとき、 Point I(0.0, 72.0, 28.0-w) Point J(18.3, 48.5, 33.2-w) Point K(36.8, 35.6, 27.6-w) Point F(-0.0833w+36.717, -4.0833w+5.1833, 3.1666w+58.0997) Point C(0.0, -4.9167w+58.317, 3.9167w+41.683) The points are within the range of the figure bounded by the curves IJ and JK connecting the five points above, as well as the lines KF, FC, and CI, or on the line segments mentioned above (excluding points on the line CI), 1.2 <w≦1.3のとき、 Point I(0.0, 72.0, 28.0-w) Point J(18.3, 48.5, 33.2-w) Point K(36.8, 35.6, 27.6-w) Point F(36.6, -3w+3.9, 2w+59.5) Point C(0.0, 0.1081w 2 -5.169w+58.447, -0.1081w 2 +4.169w+41.553) The points are within the range of the figure bounded by the curves IJ and JK connecting the five points above, as well as the lines KF, FC, and CI, or on the line segments mentioned above (excluding points on the line CI), 1.3 <w≦4.0のとき、 Point I(0.0, 72.0, 28.0-w) Point J(18.3, 48.5, 33.2-w) Point K(36.8, 35.6, 27.6-w) Point B'(36.6, 0.0, -w+63.4) Point D(-2.8226w+40.211, 0.0, 1.8226w+59.789) Point C(0.0, 0.1081w 2 -5.169w+58.447, -0.1081w 2 +4.169w+41.553) The points are within the range of the figure bounded by the curves IJ and JK connecting the six points above, as well as the lines KB', B'D, DC, and CI, or on the line segments mentioned above (excluding points on the line CI). 4.0 <w≦7.0のとき、 Point I(0.0, 72.0, 28.0-w) Point J(18.3, 48.5, 33.2-w) Point K(36.8, 35.6, 27.6-w) Point B'(36.6, 0.0, -w+63.4) Point D (-2.8w+40.1, 0.0, 1.8w+59.9) Point C(0.0, 0.0667w 2 -4.9667w+58.3, -0.0667w 2 +3.9667w+41.7) The curves IJ and JK connecting the six points above, as well as the lines KB', B'D, DC and CI, are within the range of the figure bounded by these points or on the line segments (excluding points on the line CI), and the curve IJ is Coordinate(x, 0.0236x 2 -1.716x+72, -0.0236x 2 +0.716x+28-w) It is expressed as Curvy JK is Coordinates (x, 0.0095x 2 -1.2222x+67.676, -0.0095x 2 +0.2222x+32.324-w) When the refrigerant of the present disclosure satisfies the above requirements, the refrigerant has a refrigeration capacity ratio of 80% or more based on R410A, a GWP of 250 or less, and is a mildly flammable WCF.

[0469] In the refrigerant of the present disclosure, when the mass percentages of CO2, R32, HFO-1132(E), and R1234yf based on the sum of these are w, x, y, and z, respectively, in a ternary composition diagram in which the sum of R32, HFO-1132(E), and R1234yf is (100-w) mass%, the coordinates (x, y, z) are as follows: 0 <w≦1.2のとき、 Point I(0.0, 72.0, 28.0-w) Point J(18.3, 48.5, 33.2-w) Point E(18.2, -1.1111w 2 -3.1667w+31.9, 1.1111w 2 +2.1667w+49.9) Point C(0.0, -4.9167w+58.317, 3.9167w+41.683) The points are within the range of the figure enclosed by the curves IJ and JK connecting the four points above, as well as the lines KF, FC, and CI, or on the line segments mentioned above (excluding points on the line CI), 1.2 <w≦4.0のとき、 Point I(0.0, 72.0, 28.0-w) Point J(18.3, 48.5, 33.2-w) Point E(-0.0365w+18.26, 0.0623w 2 -4.5381w+31.856, -0.0623w 2 +3.5746w+49.884) Point C(0.0, 0.1081w 2 -5.169w+58.447, -0.1081w 2 +4.169w+41.553) The points are within the range of the figure enclosed by the curves IJ and JK connecting the four points above, as well as the lines KF, FC, and CI, or on the line segments mentioned above (excluding points on the line CI), 4.0 <w≦7.0のとき、 Point I(0.0, 72.0, 28.0-w) Point J(18.3, 48.5, 33.2-w) Point E(18.1, 0.0444w 2 -4.3556w+31.411, -0.0444w 2 +3.3556w+50.489) Point C(0.0, 0.0667w 2 -4.9667w+58.3, -0.0667w 2 +3.9667w+41.7) The points are within the range of the figure enclosed by the curves IJ and JK connecting the four points above, and the lines KF, FC, and CI, or on the line segments (excluding points on the line CI), and The curve IJ is Coordinate(x, 0.0236x 2 -1.716x+72, -0.0236x 2 +0.716x+28-w) When the refrigerant of the present disclosure satisfies the above requirements, the refrigerant has a refrigeration capacity ratio of 80% or more based on R410A, a GWP of 125 or less, and is a mildly flammable WCF.

[0470] In the refrigerant of the present disclosure, when the mass percentages of CO2, R32, HFO-1132(E), and R1234yf based on the sum of these are w, x, y, and z, respectively, in a ternary composition diagram in which the sum of R32, HFO-1132(E), and R1234yf is (100-w) mass%, the coordinates (x, y, z) are as follows: 0 <w≦0.6のとき、 Point G(-5.8333w 2 -3.1667w+22.2, 7.0833w 2 +1.4167w+26.2, -1.25w 2 +0.75w+51.6) Point O(36.8, 0.8333w 2 +1.8333w+22.6, -0.8333w 2 -2.8333w+40.6) Point P(51.7, 1.1111w 2 +20.5, -1.1111w 2 -w+27.8) Point B''(-1.5278w 2 +2.75w+50.5, 0.0, 1.5278w 2 -3.75w+49.5) Point D(-2.9167w+40.317, 0.0, 1.9167w+59.683) The points are within the range of the figure enclosed by the curves GO and OP connecting the five points above, as well as the lines PB'', B''D and DG, or on the line segments (excluding points on the line B''D). 0.6 <w≦1.2のとき、 Point G(-5.8333w 2 -3.1667w+22.2, 7.0833w 2 +1.4167w+26.2, -1.25w 2 +0.75w+51.6) Point N(18.2, 0.2778w2+3w+27.7, -0.2778w2-4w+54.1) Point O(36.8, 0.8333w 2 +1.8333w+22.6, -0.8333w 2 -2.8333w+40.6) Point P(51.7, 1.1111w 2 +20.5, -1.1111w 2 -w+27.8) Point B''(-1.5278w 2 +2.75w+50.5, 0.0, 1.5278w 2 -3.75w+49.5) Point D(-2.9167w+40.317, 0.0, 1.9167w+59.683) The points are within the range of the figure bounded by the curves GN, NO, and OP, which connect the six points above, as well as the lines PB'', B''D, and DG, or on the line segments mentioned above (excluding points on the line B''D). and The curve GO is 0 <w≦0.6のとき、 Coordinate(x, (0.00487w 2 -0.0059w+0.0072)x 2 +(-0.279w 2 +0.2844w-0.6701)x+3.7639w 2 -0.2467w+37.512, 100-wxy) It is expressed as The curve GN is 0.6 <w≦1.2のとき、 Coordinates (x, (0.0122w 2 -0.0113w+0.0313)x 2 +(-0.3582w 2 +0.1624w-1.4551)x+2.7889w 2 +3.7417w+43.824 , 100-wxy) It is expressed as Curve No. 0.6 <w≦1.2のとき、 Coordinate(x, (0.00487w 2 -0.0059w+0.0072)x 2 +(-0.279w 2 +0.2844w-0.6701)x+3.7639w 2 -0.2467w+37.512, 100-wxy) is expressed as Curve OP is, 0 <w≦1.2のとき、 Coordinates (x, (0.0074w 2 -0.0133w+0.0064)x 2 +(-0.5839w 2 +1.0268w-0.7103)x+11.472w 2 -17.455w+40.07, 100-wxy) It is expressed as 1.2 <w≦4.0のとき、 Point M(0.0, -0.3004w 2 +2.419w+55.53, 0.3004w 2 -3.419w+44.47) Point W(10.0, -0.3645w 2+3.5024w+44.422, 0.3645w 2 -4.5024w+55.57) Point N(18.2, -0.3773w 2 +3.319w+28.26, 0.3773w 2 -4.319w+53.54) Point O(36.8, -0.1392w 2 +1.4381w+24.475, 0.1392w 2 -2.4381w+38.725) Point P(51.7, -0.2381w 2 +1.881w+20.186, 0.2381w 2 -2.881w+28.114) Point B''(51.6, 0.0, -w+48.4) Point D(-2.8226w+40.211, 0.0, 1.8226w+59.789) Point C(0.0, 0.1081w 2 -5.169w+58.447, -0.1081w 2 +4.169w+41.553) The points are within the range of the figure enclosed by the curves MW, WN, NO and OP, and the lines PB'', B''D, DC and CM, which connect the above eight points, or on the line segments (however, points on the lines B''D and CM are excluded), and The curve MW is Coordinates (x, (0.0043w 2 -0.0359w+0.1509)x 2 +(-0.0493w 2 +0.4669w-3.6193)x-0.3004w 2 +2.419w+55.53, 100-wxy) It is expressed as The curve WN is Coordinates (x, (0.0055w 2 -0.0326w+0.0665)x 2 +(-0.1571w 2 +0.8981w-2.6274)x+0.6555w 2-2.2153w+54.044, 100-wxy) It is expressed as Curve No. Coordinate(x, (-0.00062w 2 +0.0036w+0.0037)x 2 +(0.0375w 2 -0.239w-0.4977)x-0.8575w 2 +6.4941w+36.078, 100-wxy) It is expressed as Curve OP is, Coordinates (x, (-0.000463w 2 +0.0024w-0.0011)x 2 +(0.0457w 2 -0.2581w-0.075)x-1.355w 2 +8.749w+27.096, 100-wxy) It is expressed as 4.0 <w≦7.0のとき、 Point M(0.0, -0.0667w 2 +0.8333w+58.133, 0.0667w 2 -1.8333w+41.867) Point W(10.0, -0.0667w 2 +1.1w+39.267, 0.0667w 2 -2.1w+50.733) Point N(18.2, -0.0889w 2 +1.3778w+31.411, 0.0889w 2 -2.3778w+50.389) Point O(36.8, -0.0444w 2 +0.6889w+25.956, 0.0444w 2 -1.6889w+37.244) Point P(51.7, -0.0667w 2 +0.8333w+21.633, 0.0667w 2 -1.8333w+26.667) Point B''(51.6, 0.0, -w+48.4) Point D (-2.8w+40.1, 0.0, 1.8w+59.9) Point C(0.0, 0.0667w 2 -4.9667w+58.3, -0.0667w 2 +3.9667w+41.7) The points are within the range of the figure enclosed by the curves MW, WN, NO and OP, and the lines PB'', B''D, DC and CM, which connect the above eight points, or on the line segments (however, points on the lines B''D and CM are excluded), and The curve MW is Coordinates (x, (0.00357w 2 -0.0391w+0.1756)x 2 +(-0.0356w 2 +0.4178w-3.6422)x-0.0667w 2 +0.8333w+58.103, 100-wxy) It is expressed as The curve WN is Coordinates (x, (-0.002061w 2 +0.0218w-0.0301)x 2 +(0.0556w 2 -0.5821w-0.1108)x-0.4158w 2 +4.7352w+43.383, 100-wxy) It is expressed as Curve No. Coordinates (x, 0.0082x 2 +(0.0022w 2 -0.0345w-0.7521)x-0.1307w 2 +2.0247w+42.327, 100-wxy) It is expressed as Curve OP is, Coordinate(x, (-0.0006258w 2 +0.0066w-0.0153)x 2 +(0.0516w 2 -0.5478w+0.9894)x-1.074w 2 +11.651w+10.992, 100-wxy) When the refrigerant of the present disclosure satisfies the above requirements, the refrigerant has a refrigeration capacity ratio of 80% or more based on R410A, a GWP of 350 or less, and is ASHRAE mildly flammable.

[0471] In the refrigerant of the present disclosure, when the mass percentages of CO2, R32, HFO-1132(E), and R1234yf based on the sum of these are w, x, y, and z, respectively, in a ternary composition diagram in which the sum of R32, HFO-1132(E), and R1234yf is (100-a) mass%, the coordinates (x, y, z) are as follows: 0 <w≦0.6のとき、 Point G(-5.8333w 2 -3.1667w+22.2, 7.0833w 2 -1.4167w+26.2, -1.25w 2 +3.5834w+51.6) Point O(36.8, 0.8333w 2 +1.8333w+22.6, -0.8333w 2 -2.8333w+40.6) Point F(-0.0833w+36.717, -4.0833w+5.1833, 3.1666w+58.0997) The curve GO connecting the three points and the straight lines OF and FG are within the range of the figure enclosed by the curve GO connecting the three points, or are on the line segment. The curve GO is Coordinate(x, (0.00487w 2 -0.0059w+0.0072) x 2 +(-0.279w 2 +0.2844w-0.6701)x+3.7639w 2 -0.2467w+37.512, 100-wxy) It is expressed as 0.6 <w≦1.2のとき、 Point G(-5.8333w 2 -3.1667w+22.2, 7.0833w 2 -1.4167w+26.2, -1.25w 2 +3.5834w+51.6) Point N(18.2, 0.2778w 2 +3.0w+27.7, -0.2.778w 2 -4.0w+54.1) Point O(36.8, 0.8333w 2 +1.8333w+22.6, -0.8333w 2 -2.8333w+40.6) Point F(-0.0833w+36.717, -4.0833w+5.1833, 3.1666w+58.0997) The curves GN and NO connecting the four points and the lines OF and FG respectively lie within the range of the figure enclosed by these lines or on the line segments. The curve GN is 0.6 <w≦1.2のとき、 Coordinates (x, (0.0122w 2 -0.0113w+0.0313)x 2 +(-0.3582w 2 +0.1624w-1.4551)x+2.7889w 2 +3.7417w+43.824, 100-wxy) It is expressed as Curve No. 0.6 <w≦1.2のとき、 Coordinate(x, (0.00487w 2 -0.0059w+0.0072)x 2 +(-0.279w 2 +0.2844w-0.6701)x+3.7639w 2 -0.2467w+37.512, 100-wxy) It is expressed as 1.2 <w≦1.3のとき、 Point M(0.0, -0.3004w 2 +2.419w+55.53, 0.3004w 2 -3.419w+44.47) Point W(10.0, -0.3645w 2 +3.5024w34.422, 0.3645w 2 -4.5024w+55.578) Point N(18.2, -0.3773w 2+3.319w+28.26, 0.3773w 2 -4.319w+53.54) Point O(36.8, -0.1392w 2 +1.4381w+24.475, 0.1392w 2 -2.4381w+38.725) Point F(36.6, -3w+3.9, 2w+59.5) Point C(0.1081w 2 -5.169w+58.447, 0.0, -0.1081w 2 +4.169w+41.553) The points are within the area of ​​the shape bounded by the curves MW, WN and NO, and the lines OF, FC and CM, which connect the six points above, or on the line segments (however, points on the line CM are excluded), and The curve MW is Coordinates (x, (0.0043w 2 -0.0359w+0.1509)x 2 +(-0.0493w 2 +0.4669w-3.6193)x-0.3004w 2 +2.419w+55.53, 100-wxy) It is expressed as The curve WN is Coordinates (x, (0.0055w 2 -0.0326w+0.0665)x 2 +(-0.1571w 2 +0.8981w-2.6274)x+0.6555w 2 -2.2153w+54.044, 100-wxy) It is expressed as Curve No. Coordinate(x, (-0.00062w 2 +0.0036w+0.0037)x 2 +(0.0375w 2 -0.239w-0.4977)x-0.8575w 2 +6.4941w+36.078, 100-wxy) It is expressed as 1.3 <w≦4.0のとき、 Point M(0.0, -0.3004w 2 +2.419w+55.53, 0.3004w 2 -3.419w+44.47) Point W(10.0, -0.3645w 2 +3.5024w+34.422, 0.3645w 2 -4.5024w+55.578) Point N(18.2, -0.3773w 2 +3.319w+28.26, 0.3773w 2 -4.319w+53.54) Point O(36.8, -0.1392w 2 +1.4381w+24.475, 0.1392w 2 -2.4381w+38.725) Point B'(36.6, 0.0, -w+63.4) Point D(-2.8226w+40.211, 0.0, 1.8226w+59.789) Point C(0.0, 0.1081w 2 -5.169w+58.447, -0.1081w 2 +4.169w+41.553) The points are within the range of the figure bounded by the curves MW, WN, and NO, which connect the seven points above, as well as the lines OB', B'D, DC, and CM, or on the line segments mentioned above (excluding points on the line CM), and The curve MW is Coordinates (x, (0.0043w 2 -0.0359w+0.1509)x 2 +(-0.0493w 2 +0.4669w-3.6193)x-0.3004w 2 +2.419w+55.53, 100-wxy) It is expressed as The curve WN is Coordinates (x, (0.0055w 2 -0.0326w+0.0665)x 2 +(-0.1571w 2 +0.8981w-2.6274)x+0.6555w 2-2.2153w+54.044, 100-wxy) Curve No. Coordinate(x, (-0.00062w 2 +0.0036w+0.0037)x 2 +(0.0457w 2 -0.2581w-0.075)x-1.355w 2 +8.749w+27.096, 100-wxy) It is expressed as 4.0 <w≦7.0のとき、 Point M(0.0, -0.0667w 2 +0.8333w58.133, 0.0667w 2 -1.8333w+41.867) Point W(10.0, -0.0667w 2 +1.1w+39.267, 0.0667w 2 -2.1w+50.733) Point N(18. 2, -0.0889w 2 +1.3778w+31.411, 0.0889w 2 -2.3778w+50.389) Point O(36.8, -0.0444w 2 +0.6889w+25.956, 0.0444w 2 -1.6889w+37.244) Point B'(36.6, 0.0, -w+63.4) Point D (-2.8w+40.1, 0.0, 1.8w+59.9) Point C(0.0, 0.0667w 2 -4.9667w+58.3, -0.0667w 2 +3.9667w+41.7) The points are within the range of the figure bounded by the curves MW, WN, and NO, which connect the seven points above, as well as the lines OB', B'D, DC, and CM, or on the line segments mentioned above (excluding points on the line CM), and The curve MW is Coordinates (x, (0.00357w 2 -0.0391w+0.1756)x 2+(-0.0356w 2 +0.4178w-3.6422)x-0.0667w 2 +0.8333w+58.103, 100-wxy) It is expressed as The curve WN is Coordinates (x, (-0.002061w 2 +0.0218w-0.0301)x 2 +(0.0556w 2 -0.5821w-0.1108)x-0.4158w 2 +4.7352w+43.383, 100-wxy) Curve No. Coordinates (x, (0.0082x 2 +(0.0022w 2 -0.0345w-0.7521)x-0.1307w 2 +2.0247w+42.327, 100-wxy) When the refrigerant of the present disclosure satisfies the above requirements, it has a refrigeration capacity ratio of 80% or more based on R410A, a GWP of 250 or less, and is ASHRAE mildly flammable.

[0472] In the refrigerant of the present disclosure, when the mass percentages of CO2, R32, HFO-1132(E), and R1234yf based on the sum of these are w, x, y, and z, respectively, in a ternary composition diagram in which the sum of R32, HFO-1132(E), and R1234yf is (100-a) mass%, the coordinates (x, y, z) are as follows: 1.2 <w≦4.0のとき、 Point M(0.0, -0.3004w 2 +2.419w+55.53, 0.3004w 2 -3.419w+44.47) Point W(10.0, -0.3645w 2 +3.5024w+34.422, 0.3645w 2 -4.5024w+55.578) Point N(18.2, -0.3773w 2 +3.319w+28.26, 0.3773w2 -4.319w+53.54) Point E(-0.0365w+18.26, 0.0623w 2 -4.5381w+31.856, -0.0623w 2 +3.5746w+49.884) Point C(0.0, 0.1081w 2 -5.169w+58.447, -0.1081w 2 +4.169w+41.553) The points are within the range of the shape bounded by the curves MW and WN, and the lines NE, EC, and CM, which connect the above five points, or on the line segments (excluding points on the line CM), and The curve MW is Coordinates (x, (0.0043w 2 -0.0359w+0.1509)x 2 +(-0.0493w 2 +0.4669w-3.6193)x-0.3004w 2 +2.419w+55.53, 100-wxy) It is expressed as The curve WN is Coordinates (x, (0.0055w 2 -0.0326w+0.0665)x 2 +(-0.1571w 2 +0.8981w-2.6274)x+0.6555w 2 -2.2153w+54.044, 100-wxy) It is expressed as 4.0 <w≦7.0のとき、 Point M(0.0, -0.0667w 2 +0.8333w+58.133, 0.0667w 2 -1.8333w+41.867) Point W(10.0, -0.0667w 2 +1.1w+39.267, 0.0667w 2 -2.1w+50.733) Point N(18.2, -0.0889w 2 +1.3778w+31.411, 0.0889w 2-2.3778w+50.389) Point E(18.1, 0.0444w 2 -4.3556w+31.411, -0.0444w 2 +3.3556w+50.489) Point C(0.0, 0.0667w 2 -4.9667w+58.3, -0.0667w 2 +3.9667w+41.7) The points are within the range of the shape bounded by the curves MW and WN, and the lines NE, EC, and CM, which connect the above five points, or on the line segments (excluding points on the line CM), and The curve MW is Coordinates (x, (0.00357w 2 -0.0391w+0.1756)x 2 +(-0.0356w 2 +0.4178w-3.6422)x-0.0667w 2 +0.8333w+58.103, 100-wxy) It is expressed as The curve WN is Coordinates (x, (-0.002061w 2 +0.0218w-0.0301)x 2 +(0.0556w 2 -0.5821w-0.1108)x-0.4158w 2 +4.7352w+43.383, 100-wxy) When the refrigerant of the present disclosure satisfies the above requirements, the refrigerant has a refrigeration capacity ratio of 80% or more based on R410A, a GWP of 125 or less, and is ASHRAE mildly flammable.

[0473] The refrigerant of the present disclosure may contain, in addition to CO2, R32, HFO-1132(E), and R1234yf, other additional refrigerants, as long as the above-described properties and effects are not impaired. In this regard, the refrigerant of the present disclosure preferably contains 99.5 mass% or more of CO2, R32, HFO-1132(E), and R1234yf in total, based on the total refrigerant, more preferably 99.75 mass% or more, and even more preferably 99.9 mass% or more.

[0474] The additional refrigerant is not particularly limited and can be selected from a wide range. The mixed refrigerant may contain one type of additional refrigerant alone or two or more types of additional refrigerants.

[0475] 1.2 Application The refrigerant of the present disclosure can be preferably used as a working fluid in a refrigerator.

[0476] The compositions of the present disclosure are suitable for use as replacement refrigerants for R410A.

[0477] 2. Refrigerant Composition The refrigerant composition of the present disclosure contains at least the refrigerant of the present disclosure and can be used for the same applications as the refrigerant of the present disclosure. Furthermore, the refrigerant composition of the present disclosure can be further mixed with at least a refrigerating machine oil to obtain a working fluid for a refrigerating machine.

[0478] The refrigerant composition of the present disclosure contains at least one other component in addition to the refrigerant of the present disclosure. The refrigerant composition of the present disclosure may contain at least one of the following other components, as necessary. As described above, when the refrigerant composition of the present disclosure is used as a working fluid in a refrigerator, it is usually mixed with at least a refrigerating machine oil. Therefore, the refrigerant composition of the present disclosure is preferably substantially free of refrigerating machine oil. Specifically, the refrigerant composition of the present disclosure preferably contains 0 to 1 mass %, more preferably 0 to 0.1 mass %, of the refrigerating machine oil relative to the total refrigerant composition.

[0479] 2.1 Water The refrigerant composition of the present disclosure may contain a trace amount of water. The water content in the refrigerant composition is preferably 0.1 mass% or less based on the total refrigerant. When the refrigerant composition contains a trace amount of water, the intramolecular double bonds of unsaturated fluorocarbon compounds that may be contained in the refrigerant are stabilized, and oxidation of the unsaturated fluorocarbon compounds is also made less likely, thereby improving the stability of the refrigerant composition.

[0480] 2.2 Tracer The tracer is added to the refrigerant composition of the present disclosure at a detectable concentration so that if the refrigerant composition of the present disclosure is diluted, contaminated, or otherwise altered, the tracer can be traced.

[0481] The refrigerant composition of the present disclosure may contain one type of tracer alone or two or more types of tracers.

[0482] The tracer is not particularly limited and can be appropriately selected from commonly used tracers. Preferably, the tracer is selected from compounds that cannot be impurities that inevitably become mixed into the refrigerant of the present disclosure.

[0483] Examples of tracers include hydrofluorocarbons, hydrochlorofluorocarbons, chlorofluorocarbons, hydrochlorocarbons, fluorocarbons, deuterated hydrocarbons, deuterated hydrofluorocarbons, perfluorocarbons, fluoroethers, brominated compounds, iodinated compounds, alcohols, aldehydes, ketones, nitrous oxide (NO), etc. Particularly preferred tracers are hydrofluorocarbons, hydrochlorofluorocarbons, chlorofluorocarbons, fluorocarbons, hydrochlorocarbons, fluorocarbons, and fluoroethers.

[0484] Specifically, the following compounds are preferred as the tracer: FC-14 (tetrafluoromethane, CF4) HCC-40 (chloromethane, CH3Cl) HFC-23 (trifluoromethane, CHF3) HFC-41 (fluoromethane, CH3Cl) HFC-125 (pentafluoroethane, CF3CHF2) HFC-134a (1,1,1,2-tetrafluoroethane, CF3CH2F) HFC-134 (1,1,2,2-tetrafluoroethane, CHF2CHF2) HFC-143a (1,1,1-trifluoroethane, CF3CH3) HFC-143 (1,1,2-trifluoroethane, CHF2CH2F) HFC-152a (1,1-difluoroethane, CHF2CH3) HFC-152 (1,2-difluoroethane, CH2FCH2F) HFC-161 (fluoroethane, CH3CH2F) HFC-245fa (1,1,1,3,3-pentafluoropropane, CF3CH2CHF2) HFC-236fa (1,1,1,3,3,3-hexafluoropropane, CF3CH2CF3) HFC-236ea (1,1,1,2,3,3-hexafluoropropane, CF3CHFCHF2) HFC-227ea (1,1,1,2,3,3,3-heptafluoropropane, CF3CHFCF3) HCFC-22 (chlorodifluoromethane, CHClF2) HCFC-31 (chlorofluoromethane, CH2ClF) CFC-1113 (chlorotrifluoroethylene, CF2=CClF) HFE-125 (trifluoromethyl-difluoromethyl ether, CF3OCHF2) HFE-134a (trifluoromethyl-fluoromethyl ether, CF3OCH2F) HFE-143a (trifluoromethyl methyl ether, CF3OCH3) HFE-227ea (trifluoromethyl-tetrafluoroethyl ether, CF3OCHFCF3) HFE-236fa (trifluoromethyl-trifluoroethyl ether, CF3OCH2CF3)

[0485] The tracer compound may be present in the refrigerant composition at a total concentration of from about 10 parts per million (ppm) by weight to about 1000 ppm. Preferably, the tracer compound is present in the refrigerant composition at a total concentration of from about 30 ppm to about 500 ppm, and most preferably, the tracer compound is present in the refrigerant composition at a total concentration of from about 50 ppm to about 300 ppm.

[0486] 2.3 UV fluorescent dyes The refrigerant composition of the present disclosure may contain one type of ultraviolet fluorescent dye alone or two or more types.

[0487] The ultraviolet fluorescent dye is not particularly limited and can be appropriately selected from among commonly used ultraviolet fluorescent dyes.

[0488] Examples of ultraviolet fluorescent dyes include naphthalimide, coumarin, anthracene, phenanthrene, xanthene, thioxanthene, naphthoxanthene, and fluorescein, and derivatives thereof. As the ultraviolet fluorescent dye, either or both of naphthalimide and coumarin are particularly preferred.

[0489] 2.4 Stabilizers The refrigerant composition of the present disclosure may contain one type of stabilizer alone or two or more types.

[0490] The stabilizer is not particularly limited and can be appropriately selected from commonly used stabilizers.

[0491] Examples of stabilizers include nitro compounds, ethers, and amines.

[0492] Examples of nitro compounds include aliphatic nitro compounds such as nitromethane and nitroethane, and aromatic nitro compounds such as nitrobenzene and nitrostyrene.

[0493] An example of the ethers is 1,4-dioxane.

[0494] Examples of amines include 2,2,3,3,3-pentafluoropropylamine and diphenylamine.

[0495] Other examples include butylhydroxyxylene and benzotriazole.

[0496] The content of the stabilizer is not particularly limited, and is usually preferably 0.01 to 5 mass % and more preferably 0.05 to 2 mass % relative to the total mass of the refrigerant.

[0497] 2.5 Polymerization inhibitors The refrigerant composition of the present disclosure may contain one type of polymerization inhibitor alone, or may contain two or more types.

[0498] The polymerization inhibitor is not particularly limited and can be appropriately selected from among commonly used polymerization inhibitors.

[0499] Examples of the polymerization inhibitor include 4-methoxy-1-naphthol, hydroquinone, hydroquinone methyl ether, dimethyl-t-butylphenol, 2,6-di-tert-butyl-p-cresol, and benzotriazole.

[0500] The content of the polymerization inhibitor is not particularly limited, and is usually preferably 0.01 to 5 mass %, more preferably 0.05 to 2 mass %, based on the total mass of the refrigerant.

[0501] 3. Working fluid containing refrigeration oil The refrigerating machine oil-containing working fluid of the present disclosure contains at least the refrigerant or refrigerant composition of the present disclosure and a refrigerating machine oil, and is used as a working fluid in a refrigerator. Specifically, the refrigerating machine oil-containing working fluid of the present disclosure is obtained by mixing the refrigerating machine oil used in the compressor of the refrigerator with the refrigerant or refrigerant composition. The refrigerating machine oil-containing working fluid generally contains 10 to 50 mass% of the refrigerating machine oil.

[0502] 3.1 Refrigeration oil The composition of the present disclosure may contain one type of refrigerating machine oil alone, or may contain two or more types of refrigerating machine oils.

[0503] The refrigerating machine oil is not particularly limited and can be appropriately selected from commonly used refrigerating machine oils. In this case, if necessary, a refrigerating machine oil that is superior in terms of miscibility with the mixture and the effect of improving the stability of the mixture can be appropriately selected.

[0504] The base oil of the refrigerating machine oil is preferably at least one selected from the group consisting of polyalkylene glycol (PAG), polyol ester (POE), and polyvinyl ether (PVE).

[0505] The refrigerating machine oil may further contain, in addition to the base oil, an additive such as at least one selected from the group consisting of an antioxidant, an extreme pressure agent, an acid scavenger, an oxygen scavenger, a copper deactivator, a rust inhibitor, an oiliness agent, and an antifoaming agent.

[0506] From the viewpoint of lubrication, a refrigerating machine oil having a kinematic viscosity at 40°C of 5 to 400 cSt is preferred.

[0507] The refrigerating machine oil-containing working fluid of the present disclosure may further contain at least one additive, if necessary. Examples of the additive include the following compatibilizers.

[0508] 3.2 Compatibilizers The refrigerating machine oil-containing working fluid of the present disclosure may contain one type of compatibilizer alone or two or more types.

[0509] The compatibilizer is not particularly limited and can be appropriately selected from among commonly used compatibilizers.

[0510] Examples of the compatibilizer include polyoxyalkylene glycol ether, amide, nitrile, ketone, chlorocarbon, ester, lactone, aryl ether, fluoroether, and 1,1,1-trifluoroalkane, etc. Polyoxyalkylene glycol ether is particularly preferred as the compatibilizer.

[0511] 4. How to operate the refrigerator The method for operating a refrigerator according to the present disclosure is a method for operating a refrigerator using the refrigerant according to the present disclosure.

[0512] Specifically, a method of operating a refrigerator according to the present disclosure includes circulating a refrigerant according to the present disclosure in the refrigerator.

[0513] Although the embodiments have been described above, it will be understood that various changes in form and details can be made without departing from the spirit and scope of the claims. [Example]

[0514] The present disclosure will be described in more detail below with reference to examples, but is not limited to these examples.

[0515] The burning velocity of CO2 and the refrigerant mixtures R32, HFO-1132(E), and R1234yf was measured according to the ANSI / ASHRAE34-2013 standard. While varying the CO2 concentration, compositions showing a burning velocity of 10 cm / s were identified. The compositions found are shown in Tables 1 to 3.

[0516] The burning rate test was performed using the apparatus shown in Figure 1A as follows. First, the mixed refrigerant used was 99.5% or higher purity and degassed by repeated cycles of freezing, pumping, and thawing until no trace of air was observed on the vacuum gauge. The burning rate was measured using the closed-loop method. The initial temperature was ambient. Ignition was achieved by generating an electric spark between electrodes at the center of the sample cell. The discharge duration was 1.0–9.9 ms, and the ignition energy was typically approximately 0.1–1.0 J. Schlieren photography was used to visualize the flame spread. A cylindrical container (inner diameter: 155 mm, length: 198 mm) with two transparent acrylic windows was used as the sample cell, and a xenon lamp was used as the light source. Schlieren images of the flame were recorded with a high-speed digital video camera at a frame rate of 600 fps and saved on a PC.

[0517] The WCFF concentration was calculated by performing a leakage simulation using the NIST Standard Reference Data Base Refleak Version 4.0 with the WCF concentration as the initial concentration.

[0518] [Table 1]

[0519] [Table 2]

[0520] [Table 3]

[0521] From these results, it can be seen that when the mass percentages of CO2, R32, HFO-1132(E), and R1234yf based on the sum of these are w, and x, y, and z, respectively, in the ternary composition diagrams of Figures 1B to 1I, where the sum of R32, HFO-1132(E), and R1234yf is (100-w) mass%, when the coordinates (x, y, z) are on or below the line connecting points I, J, K, and L, respectively, WCF mild flammability is achieved.

[0522] In addition, in the three-component composition diagram of FIG. 1B, when the coordinates (x, y, z) are on or below the line segment connecting points M, N, O, and P, respectively, it is understood that the composition is ASHRAE mildly combustible.

[0523] Mixed refrigerants were prepared by mixing R32, HFO-1132(E), and R1234yf in the mass percentages shown in Tables 4 to 14, based on the sum of these refrigerants. The coefficient of performance (COP) ratio and refrigeration capacity ratio, based on R410, were determined for each of the mixed refrigerants in Tables 4 to 11.

[0524] The GWP of compositions containing a mixture of R1234yf and R410A (50% R32 / 50% R125) was evaluated based on the values ​​in the Fourth Assessment Report of the Intergovernmental Panel on Climate Change (IPCC). Although the GWP of HFO-1132(E) is not disclosed, its GWP was assumed to be 1 based on HFO-1132a (GWP = 1 or less) and HFO-1123 (GWP = 0.3, as described in Patent Document 1). The refrigeration capacity of compositions containing mixtures of R410A and HFO-1132(E), HFO-1123, and R1234yf was calculated by theoretical calculations of the refrigeration cycle of the mixed refrigerant under the following conditions using the National Institute of Science and Technology (NIST) Reference Fluid Thermodynamic and Transport Properties Database (Refprop 9.0). Evaporation temperature: 5℃ Condensation temperature: 45℃ Superheat degree: 5K Supercooling degree; 5K E comp (Compression work): 0.7 kWh

[0525] These values, along with the GWP for each refrigerant mixture, are shown in Tables 4 to 11. Tables 4 to 11 show the results for CO2 concentrations of 0 mass%, 0.6 mass%, 1.2 mass%, 1.3 mass%, 2.5 mass%, 4 mass%, 5.5 mass%, and 7 mass%, respectively.

[0526] [Table 4]

[0527] [Table 5]

[0528] [Table 6]

[0529] [Table 7]

[0530] [Table 8]

[0531] [Table 9]

[0532] [Table 10]

[0533] [Table 11]

[0534]

Table 12

[0535]

Table 13

[0536]

Table 14

[0537]

Table 15

[0538] Table 16

[0539]

Table 17

[0540]

Table 18

[0541]

Table 19

[0542] Table 20

[0543] These results indicate that in the ternary composition diagrams of Figures 1B to 1I, where the mass percentages of CO2, R32, HFO-1132(E), and R1234yf, based on their sum, are w, x, y, and z, respectively, the total mass percentage of R32, HFO-1132(E), and R1234yf is (100-w) mass%, when the coordinates (x, y, z) are on the line A''B'', the GWP of the mixed refrigerant is 350, and when the coordinates are to the right of the line, the GWP of the mixed refrigerant is less than 350. Furthermore, in the ternary composition diagrams of Figures 1B to 1I, when the coordinates (x, y, z) are on the line A'B', the GWP of the mixed refrigerant is 250, and when the coordinates are to the right of the line, the GWP of the mixed refrigerant is less than 250. Furthermore, in the three-component composition diagrams of Figures 1B to 1I, when the coordinates (x, y, z) are on the line AB, the GWP of the mixed refrigerant is 125, and when they are located to the right of the line, the GWP of the mixed refrigerant is less than 125.

[0544] It can be seen that the straight line connecting points D and C is located slightly to the left of the curve connecting the points where the refrigeration capacity ratio based on R410A is 80%. Therefore, when the coordinates (x, y, z) are to the left of the line connecting points D and C, it can be seen that the refrigeration capacity ratio of the mixed refrigerant based on R410A is 80% or more.

[0545] The coordinates of points A and B, A' and B', and A'' and B'' were determined by calculating approximate formulas based on the points listed in the above tables. Specifically, calculations were performed as shown in Table 21 (points A and B), Table 22 (points A' and B'), and Table 23 (points A'' and B'').

[0546] [Table 21]

[0547] [Table 22]

[0548]

Table 23

[0549] The coordinates of points C to G were determined by obtaining an approximate expression based on each point described in the above table. Specifically, calculations were performed as shown in Tables 24 and 25.

[0550]

Table 24

[0551]

Table 25

[0552] The coordinates of the points on curve IJ, curve JK, and curve KL were determined by obtaining an approximate expression based on each point described in the above table. Specifically, calculations were performed as shown in Table 26.

[0553]

Table 26

[0554] The coordinates of the points on curve MW and curve WM were determined by obtaining an approximate expression based on each point described in the above table. Specifically, calculations were performed as shown in Table 27 (when 0 mass% < CO2 concentration ≤ 1.2 mass%), Table 28 (when 1.2 mass% < CO2 concentration ≤ 4.0 mass%), and Table 29 (when 4.0 mass% < CO2 concentration ≤ 7.0 mass%).

[0555]

Table 27

[0556]

Table 28

[0557]

Table 29

[0558] The coordinates of the points on curve NO and curve OP were determined by obtaining an approximate formula based on each point described in the above table. Specifically, calculations were performed as shown in Table 30 (when 0 mass% < CO2 concentration ≤ 1.2 mass%), Table 31 (when 1.2 mass% < CO2 concentration ≤ 4.0 mass%), and Table 32 (when 4.0 mass% < CO2 concentration ≤ 7.0 mass%).

[0559]

Table 30

[0560]

Table 31

[0561]

Table 32

[0562] (1-3-2) Refrigerant Y 1. Composition The composition of the present disclosure contains a refrigerant, and examples of the refrigerant include "Refrigerant 1" and "Refrigerant 2". Hereinafter, Refrigerant 1 and Refrigerant 2 will be described respectively. In this specification, "the refrigerant of the present disclosure" means Refrigerant 1 and Refrigerant 2.

[0563] 1.1 Refrigerant 1 In one aspect, the refrigerant contained in the composition of the present disclosure contains HFO-1132(Z) and HFO-1234yf. This refrigerant may be referred to as "Refrigerant 1".

[0564] For Refrigerant 1, the content ratio of HFO-1132(Z) is 53.0 to 59.5 mass%, and the content ratio of HFO-1234yf is 47.0 to 40.5 mass% with respect to the total mass of HFO-1132(Z) and HFO-1234yf.

[0565] With this configuration, Refrigerant 1 has desirable properties as an alternative to R134a: (1) a sufficiently low GWP (100 or less), (2) a COP equal to or greater than that of R134a, (3) a refrigeration capacity equal to or greater than that of R134a, and (4) mild flammability (Class 2L) according to ASHRAE standards.

[0566] In this item, a sufficiently small GWP means that the GWP is usually 100 or less, preferably 75 or less, more preferably 50 or less, and even more preferably 25 or less.

[0567] If the content of HFO-1132(Z) in Refrigerant 1 exceeds 59.5 mass % relative to the total mass of HFO-1132(Z) and HFO-1234yf, the problem of Refrigerant 1 becoming weakly flammable will arise.

[0568] From the viewpoint of reducing power consumption during operation compared to commercially available refrigeration equipment for R134a, Refrigerant 1 has a refrigeration capacity of typically 95% or more, preferably 98% or more, more preferably 99% or more, even more preferably 100% or more, and particularly preferably 100.5% or more relative to R134a.

[0569] Refrigerant 1 has a GWP of 100 or less, and therefore can significantly reduce the environmental impact from the perspective of global warming compared to other general-purpose refrigerants.

[0570] Refrigerant 1 has a ratio of the power consumed in the refrigeration cycle to the refrigeration capacity (coefficient of performance (COP)) of 100% or more compared to R134a, so it can be applied to commercially available refrigeration equipment for R134a without major design changes.

[0571] From the viewpoint of energy consumption efficiency, it is preferable that Refrigerant 1 has a high coefficient of performance (COP) relative to R134a, which is the ratio of the power consumed in the refrigeration cycle to the refrigeration capacity. Specifically, the COP relative to R134a is preferably 98% or more, more preferably 99% or more, even more preferably 100% or more, and particularly preferably 101% or more.

[0572] Refrigerant 1 preferably contains 53.0 to 59.0 mass% of HFO-1132(Z) and 47.0 to 41.0 mass% of HFO-1234yf relative to the total mass of HFO-1132(Z) and HFO-1234yf.

[0573] Refrigerant 1 more preferably contains 54.0 to 59.0 mass% of HFO-1132(Z) and 46.0 to 41.0 mass% of HFO-1234yf relative to the total mass of HFO-1132(Z) and HFO-1234yf.

[0574] Refrigerant 1 more preferably contains 55.0 to 59.0 mass% of HFO-1132(Z) and 45.0 to 41.0 mass% of HFO-1234yf relative to the total mass of HFO-1132(Z) and HFO-1234yf.

[0575] It is particularly preferable that Refrigerant 1 contains 56.0 to 59.0 mass% of HFO-1132(Z) and 44.0 to 41.0 mass% of HFO-1234yf relative to the total mass of HFO-1132(Z) and HFO-1234yf.

[0576] Refrigerant 1 may contain HFO-1132(Z) and HFO-1234yf in a total concentration of typically 99.5% by mass or more. In the present disclosure, the total amount of HFO-1132(Z) and HFO-1234yf in Refrigerant 1 as a whole is preferably 99.7% by mass or more, more preferably 99.8% by mass or more, and even more preferably 99.9% by mass or more.

[0577] Refrigerant 1 can contain other refrigerants in addition to HFO-1132(Z) and HFO-1234yf, as long as the above-mentioned properties are not impaired. In this case, the content of the other refrigerants in the total refrigerant 1 is preferably 0.5 mass% or less, more preferably 0.3 mass% or less, even more preferably 0.2 mass% or less, and particularly preferably 0.1 mass% or less. The other refrigerants are not particularly limited and can be selected from a wide range of known refrigerants widely used in this field. Refrigerant 1 may contain a single other refrigerant or two or more other refrigerants.

[0578] In the present disclosure, the refrigerant 1 is preferably used to operate a refrigeration cycle with an evaporation temperature of -60 to 20°C, from the viewpoint of sufficiently cooling the room and the object to be cooled.

[0579] In a refrigeration cycle in which refrigerant 1 is used, from the viewpoint of sufficiently cooling the room and the object to be cooled, it is more preferable that the evaporation temperature is 15°C or less, even more preferably 10°C or less, even more preferably 5°C or less, and particularly preferably less than 0°C.

[0580] In a refrigeration cycle using refrigerant 1, in order to achieve an evaporation pressure of 0.02 MPa or higher, the evaporation temperature is preferably -55°C or higher, more preferably -50°C or higher, even more preferably -45°C or higher, and particularly preferably -40°C or higher.

[0581] In a refrigeration cycle in which refrigerant 1 is used, the evaporation temperature is more preferably -55°C or higher and 15°C or lower, even more preferably -50°C or higher and 10°C or lower, even more preferably -45°C or higher and 5°C or lower, and particularly preferably -40°C or higher and lower than 0°C.

[0582] It is particularly preferred that Refrigerant 1 consists solely of HFO-1132(Z) and HFO-1234yf. In other words, it is particularly preferred that the total concentration of HFO-1132(Z) and HFO-1234yf in Refrigerant 1 as a whole is 100 mass%.

[0583] When refrigerant 1 consists only of HFO-1132(Z) and HFO-1234yf, it is preferable that the content of HFO-1132(Z) is 53.0 to 59.5 mass% and the content of HFO-1234yf is 47.0 to 40.5 mass% based on the total mass of HFO-1132(Z) and HFO-1234yf.

[0584] When refrigerant 1 consists only of HFO-1132(Z) and HFO-1234yf, it is even more preferable that the content of HFO-1132(Z) is 54.0 to 59.0 mass% and the content of HFO-1234yf is 46.0 to 41.0 mass%, based on the total mass of HFO-1132(Z) and HFO-1234yf.

[0585] When refrigerant 1 consists only of HFO-1132(Z) and HFO-1234yf, it is more preferable that the content of HFO-1132(Z) is 55.0 to 59.0 mass% and the content of HFO-1234yf is 45.0 to 41.0 mass% based on the total mass of HFO-1132(Z) and HFO-1234yf.

[0586] When refrigerant 1 consists only of HFO-1132(Z) and HFO-1234yf, it is particularly preferable that the content of HFO-1132(Z) is 56.0 to 59.0 mass% and the content of HFO-1234yf is 44.0 to 41.0 mass%, based on the total mass of HFO-1132(Z) and HFO-1234yf.

[0587] When refrigerant 1 consists only of HFO-1132(Z) and HFO-1234yf, it is preferred that the content of HFO-1132(Z) is 53.0 to 59.5 mass% and the content of HFO-1234yf is 47.0 to 40.5 mass% relative to the total mass of HFO-1132(Z) and HFO-1234yf, and that refrigerant 1 be used to operate a refrigeration cycle with an evaporation temperature of -55°C to 15°C.

[0588] When refrigerant 1 consists only of HFO-1132(Z) and HFO-1234yf, it is more preferable that the content of HFO-1132(Z) is 54.0 to 59.0 mass% and the content of HFO-1234yf is 46.0 to 41.0 mass% relative to the total mass of HFO-1132(Z) and HFO-1234yf, and refrigerant 1 is used to operate a refrigeration cycle with an evaporation temperature of -50°C to 10°C.

[0589] When refrigerant 1 consists only of HFO-1132(Z) and HFO-1234yf, it is more preferable that the content of HFO-1132(Z) is 55.0 to 59.0 mass% and the content of HFO-1234yf is 45.0 to 41.0 mass% relative to the total mass of HFO-1132(Z) and HFO-1234yf, and that refrigerant 1 is used to operate a refrigeration cycle with an evaporation temperature of -45°C to 5°C.

[0590] When refrigerant 1 consists only of HFO-1132(Z) and HFO-1234yf, it is particularly preferred that the content of HFO-1132(Z) is 56.0 to 59.0 mass% and the content of HFO-1234yf is 44.0 to 41.0 mass% relative to the total mass of HFO-1132(Z) and HFO-1234yf, and that refrigerant 1 be used to operate a refrigeration cycle having an evaporation temperature of -40°C or higher and lower than 0°C.

[0591] 1.2 Refrigerant 2 In one embodiment, the refrigerant contained in the composition of the present disclosure contains HFO-1132(Z) and HFO-1234yf, with the content of HFO-1132(Z) being 41.0 to 49.2 mass% and the content of HFO-1234yf being 59.0 to 50.8 mass% based on the total mass of HFO-1132(Z) and HFO-1234yf. This refrigerant may be referred to as "Refrigerant 2."

[0592] With this configuration, Refrigerant 2 has desirable properties as an alternative to R134a: (1) a sufficiently small GWP (100 or less), (2) a COP equal to or greater than that of R134a, (3) a refrigeration capacity equal to or greater than that of R134a, and (4) mildly flammable (Class 2L) according to ASHRAE standards.

[0593] In this item, a sufficiently small GWP means that the GWP is usually 100 or less, preferably 75 or less, more preferably 50 or less, and even more preferably 25 or less.

[0594] Refrigerant 2 has a GWP of 100 or less, and therefore can significantly reduce the environmental impact from the perspective of global warming compared to other general-purpose refrigerants.

[0595] From the viewpoint of reducing power consumption during operation compared to commercially available refrigeration equipment for R134a, refrigerant 2 typically has a refrigeration capacity of 95% or more, preferably 98% or more, more preferably 99% or more, even more preferably 100% or more, and particularly preferably 101% or more of that of R134a.

[0596] Refrigerant 2 has a ratio of the power consumed in the refrigeration cycle to the refrigeration capacity (coefficient of performance (COP)) of 100% or more compared to R134a, so it can be applied to commercially available refrigeration equipment for R134a without major design changes.

[0597] From the viewpoint of energy consumption efficiency, it is preferable that the refrigerant 2 has a high coefficient of performance (COP) relative to R134a, which is the ratio of the power consumed in the refrigeration cycle to the refrigeration capacity. Specifically, the COP relative to R134a is preferably 98% or more, more preferably 99% or more, even more preferably 100% or more, and particularly preferably 101% or more.

[0598] Refrigerant 2 preferably contains 42.0 to 49.2 mass% of HFO-1132(Z) and 58.0 to 50.8 mass% of HFO-1234yf relative to the total mass of HFO-1132(Z) and HFO-1234yf.

[0599] Refrigerant 2 more preferably contains 43.0 to 49.2 mass% of HFO-1132(Z) and 57.0 to 50.8 mass% of HFO-1234yf relative to the total mass of HFO-1132(Z) and HFO-1234yf.

[0600] Refrigerant 2 more preferably contains 44.0 to 49.0 mass% of HFO-1132(Z) and 56.0 to 51.0 mass% of HFO-1234yf relative to the total mass of HFO-1132(Z) and HFO-1234yf.

[0601] Refrigerant 2 may contain HFO-1132(Z) and HFO-1234yf in a total concentration of typically 99.5% by mass or more. In the present disclosure, the total amount of HFO-1132(Z) and HFO-1234yf in Refrigerant 2 as a whole is preferably 99.7% by mass or more, more preferably 99.8% by mass or more, and even more preferably 99.9% by mass or more.

[0602] Refrigerant 2 can contain other refrigerants in addition to HFO-1132(Z) and HFO-1234yf, as long as the above-mentioned properties are not impaired. In this case, the content of the other refrigerants in the total refrigerant 2 is preferably 0.5 mass% or less, more preferably 0.3 mass% or less, even more preferably 0.2 mass% or less, and particularly preferably 0.1 mass% or less. The other refrigerants are not particularly limited and can be selected from a wide range of known refrigerants widely used in this field. Refrigerant 2 may contain a single other refrigerant or two or more other refrigerants.

[0603] In the present disclosure, the refrigerant 2 is preferably used to operate a refrigeration cycle with an evaporation temperature of -60 to 20°C, from the viewpoint of sufficiently cooling the room and the object to be cooled.

[0604] In a refrigeration cycle in which refrigerant 2 is used, from the viewpoint of sufficiently cooling the room and the object to be cooled, it is more preferable that the evaporation temperature is 15°C or less, even more preferably 10°C or less, even more preferably 5°C or less, and particularly preferably less than 0°C.

[0605] In a refrigeration cycle using refrigerant 2, in order to achieve an evaporation pressure of 0.02 MPa or higher, the evaporation temperature is preferably -55°C or higher, more preferably -50°C or higher, even more preferably -45°C or higher, and particularly preferably -40°C or higher.

[0606] In a refrigeration cycle in which refrigerant 2 is used,...

Claims

1. A hot water production device using a mixed refrigerant, A compressor (21, 211, 335), A first heat exchanger (24, 214, 337) on the heat source side; An expansion mechanism (23, 213, 336); A second heat exchanger (22, 212, 333) on the utilization side; Equipped with The second heat exchanger (22, 212, 333) exchanges heat between the mixed refrigerant flowing therethrough and first water to heat the first water, The refrigerants include HFO-1132(E) and HFO-1234yf, The refrigerant contains HFO-1132(E) and HFO-1234yf in a total concentration of 99.7% by mass or more, and based on the total mass of HFO-1132(E) and HFO-1234yf, The content of HFO-1132(E) is 35.0 to 65.0 mass%; The content of HFO-1234yf is 65.0 to 35.0 mass%. Hot water production equipment.

2. A hot water production device using a mixed refrigerant, A compressor (21, 211, 335), A first heat exchanger (24, 214, 337) on the heat source side; An expansion mechanism (23, 213, 336); A second heat exchanger (22, 212, 333) on the utilization side; Equipped with The second heat exchanger (22, 212, 333) exchanges heat between the mixed refrigerant flowing therethrough and first water to heat the first water, The refrigerants include HFO-1132(E) and HFO-1234yf, The refrigerant contains HFO-1132(E) and HFO-1234yf in a total concentration of 99.7% by mass or more, and based on the total mass of HFO-1132(E) and HFO-1234yf, The content of HFO-1132(E) is 12.1 to 72.0 mass%; The content of HFO-1234yf is 87.9 to 28.0 mass%. Hot water production equipment.

3. A hot water production device using a mixed refrigerant, A compressor (21, 211, 335), A first heat exchanger (24, 214, 337) on the heat source side; An expansion mechanism (23, 213, 336); A second heat exchanger (22, 212, 333) on the utilization side; Equipped with The second heat exchanger (22, 212, 333) exchanges heat between the mixed refrigerant flowing therethrough and first water to heat the first water, The refrigerants include HFO-1132(E) and HFO-1234yf, The refrigerant contains HFO-1132(E) and HFO-1234yf in a total concentration of 99.5% by mass or more, and based on the total mass of HFO-1132(E) and HFO-1234yf, The content of HFO-1132(E) is 40.5 to 49.2 mass%; The content of HFO-1234yf is 59.5 to 50.8 mass%. Hot water production equipment.

4. A hot water production device using a mixed refrigerant, A compressor (21, 211, 335), A first heat exchanger (24, 214, 337) on the heat source side; An expansion mechanism (23, 213, 336); A second heat exchanger (22, 212, 333) on the utilization side; Equipped with The second heat exchanger (22, 212, 333) exchanges heat between the mixed refrigerant flowing therethrough and first water to heat the first water, The refrigerants include HFO-1132(E) and HFO-1234yf, The refrigerant contains HFO-1132(E) and HFO-1234yf in a total concentration of 99.5% by mass or more, and based on the total mass of HFO-1132(E) and HFO-1234yf, The content of HFO-1132(E) is 31.1 to 39.8% by mass, The content of HFO-1234yf is 68.9 to 60.2 mass%. Hot water production equipment.

5. A hot water production device using a mixed refrigerant, A compressor (21, 211, 335), A first heat exchanger (24, 214, 337) on the heat source side; An expansion mechanism (23, 213, 336); A second heat exchanger (22, 212, 333) on the utilization side; Equipped with The second heat exchanger (22, 212, 333) exchanges heat between the mixed refrigerant flowing therethrough and first water to heat the first water, The refrigerants include HFO-1132(E) and HFO-1234yf, The refrigerant contains HFO-1132(E) and HFO-1234yf in a total concentration of 99.5% by mass or more, and based on the total mass of HFO-1132(E) and HFO-1234yf, The content of HFO-1132(E) is 21.0 to 28.4 mass%; The content of HFO-1234yf is 79.0 to 71.6 mass%. Hot water production equipment.

6. The refrigerant is, based on the total mass of HFO-1132(E) and HFO-1234yf, The content of HFO-1132(E) is 41.3 to 53.5 mass%; The content of HFO-1234yf is 58.7 to 46.5 mass%. The hot water producing apparatus according to claim 1.

7. The refrigerant consists of only HFO-1132(E) and HFO-1234yf, The hot water producing apparatus according to claim 1 or 2.

8. The refrigerant consists of only HFO-1132(E) and HFO-1234yf, The hot water producing apparatus according to claim 3.

9. The evaporation temperature is -75 to -5°C. The hot water producing apparatus according to claim 3 or 8.

10. The refrigerant is, based on the total mass of HFO-1132(E) and HFO-1234yf, The content of HFO-1132(E) is 31.1 to 37.9% by mass, The content of HFO-1234yf is 68.9 to 62.1 mass%. The hot water producing apparatus according to claim 4.

11. The refrigerant consists of only HFO-1132(E) and HFO-1234yf, The hot water producing apparatus according to claim 4 or 10.

12. The evaporation temperature is -75 to -5°C. The hot water producing apparatus according to any one of claims 4, 10 and 11.

13. The refrigerant consists of only HFO-1132(E) and HFO-1234yf, The hot water producing apparatus according to claim 5.

14. A tank (35); a circulation flow path (30) for circulating the first water between the tank (35) and the second heat exchanger (22); The hot water producing device (1) according to any one of claims 1 to 13, further comprising:

15. a first circulation flow path (60) for circulating the first water heated by the second heat exchanger (22); a second circulation flow path (30) separate from the first circulation flow path (60); a third heat exchanger (62) that exchanges heat between the first water flowing through the first circulation flow path (60) and the second water flowing through the second circulation flow path (30) to heat the second water flowing through the second circulation flow path (30); and a tank (35) for storing the second water heated by the third heat exchanger (62); The hot water producing apparatus (1a) according to any one of claims 1 to 11, further comprising:

16. a first circulation flow path (30b) for circulating the first water heated by the second heat exchanger (22); A tank (35); Further equipped with a portion (38) of the first circulation flow path (30b) is disposed in the tank (35), and heat is exchanged between the first water flowing through the first circulation flow path (30b) and the second water in the tank (35) to heat the second water in the tank (35). A hot water producing apparatus (1b) according to any one of claims 1 to 13.

17. A tank (240); a first circulation flow path (231) for circulating the first water between the second heat exchanger (212) and the tank (240); A third heat exchanger (112); a second circulation flow path (110) for circulating the first water between the third heat exchanger (112) and the tank (240); a third flow path (118) separate from the first circulation flow path (231) and the second circulation flow path (110); Further equipped with The third heat exchanger (112) exchanges heat between the first water flowing from the tank and third water flowing through the third flow path (118) to heat the third water flowing through the third flow path (118). The hot water producing apparatus according to any one of claims 1 to 13.

18. A tank (240); a first circulation flow path (231) for circulating the first water between the tank (240) and the second heat exchanger (212); a second flow path (241) separate from the first circulation flow path (231); Further equipped with A portion (241a) of the second flow path (241) is disposed in the tank (240), and heat is exchanged between the first water in the tank (240) and the second water flowing through the second flow path (241) to heat the second water flowing through the second flow path (241). The hot water producing apparatus according to any one of claims 1 to 13.

19. A tank (240) for storing the first water; a second water flow passage (241), a portion (241a) of which is disposed in the tank (240); Further equipped with The second heat exchanger (216) heats the first water stored in the tank (240), The first water stored in the tank (240) heats the second water flowing through the flow path (241). The hot water producing apparatus according to any one of claims 1 to 13.

20. A tank (340); a flow path (312, 331, 314) for flowing the first water from a water supply source (320) to the tank (340); Further equipped with The second heat exchanger (333) heats the first water flowing through the flow path (331). The hot water producing apparatus according to any one of claims 1 to 13.

21. a fourth heat exchanger (22a) on the utilization side, separate from the second heat exchanger (212); a fourth circulation flow path (190) through which a fourth water for cooling or heating flows; Further equipped with The fourth heat exchanger (22a) performs heat exchange between the mixed refrigerant flowing therein and the fourth water flowing through the fourth circulation flow path (190) to cool or heat the fourth water. A hot water producing apparatus (1b) according to any one of claims 1 to 20.

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