Heat pump device

Abstract

In the case where the first refrigerant is a compound having carbon-carbon unsaturated bonds, a heat pump device is provided that can suppress the increased risk of disproportionation reactions due to changes in the composition of the non-azeotropic refrigerant mixture. The air conditioner (1) as a heat pump device includes a refrigerant circuit (10), a compressor (11), and a composition regulating mechanism (100). In the refrigerant circuit (10), a non-azeotropic refrigerant mixture including a first refrigerant and a second refrigerant with a boiling point higher than that of the first refrigerant circulates. The compressor (11) compresses the non-azeotropic refrigerant mixture. The first refrigerant is a compound represented by a molecular formula having one or more carbon-carbon unsaturated bonds. The composition regulating mechanism (100) is provided in the refrigerant circuit (10). The composition regulating mechanism (100) suppresses an increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor (11).

Description

Technical Field

[0001] This disclosure relates to a heat pump device using a non-azeotropic refrigerant mixture. Background Technology

[0002] In existing heat pump devices, as described in Patent Document 1 (Japanese Patent No. 6390431), a vapor compression refrigeration cycle is implemented using a non-azeotropic refrigerant mixture. The non-azeotropic refrigerant mixture described in Patent Document 1 is a mixture of 2,3,3,3-tetrafluoropropylene (hereinafter sometimes designated as HFO-1234yf) and difluoromethane (hereinafter sometimes designated as R32). Summary of the Invention The technical problem that the invention aims to solve

[0003] In the non-azeotropic refrigerant mixture of Patent Document 1, the boiling point of HFO-1234yf is -29.5°C, and the boiling point of R32 is -51.7°C. However, the boiling points used in this disclosure are standard boiling points at one atmosphere. Therefore, the boiling point of HFO-1234yf is higher than that of R32.

[0004] If a liquid non-azeotropic refrigerant mixture with a low boiling point (R32) accumulates in the refrigerant circuit of a heat pump unit, the proportion of R32 in the circulating refrigerant will increase. However, since the compound with carbon-carbon unsaturated bonds that easily cause disproportionation reactions is HFO-1234yf, the risk of disproportionation reactions in the circulating refrigerant actually decreases even if the proportion of R32 in the circulating refrigerant increases.

[0005] However, even with the same non-azeotropic refrigerant mixture, if the lower-boiling-point refrigerant is a compound with carbon-carbon unsaturated bonds, and a liquid non-azeotropic refrigerant mixture including a significant amount of higher-boiling-point refrigerant accumulates in the refrigerant loop, the proportion of compounds with carbon-carbon unsaturated bonds in the circulating refrigerant increases. A higher proportion of compounds with carbon-carbon unsaturated bonds in the circulating refrigerant increases the risk of disproportionation reactions.

[0006] Thus, in heat pump devices using non-azeotropic refrigerant mixtures, if the refrigerant with the lowest boiling point among the multiple refrigerants included in the non-azeotropic refrigerant mixture is a compound with carbon-carbon unsaturated bonds, there is a risk of increased disproportionation reactions due to changes in the composition of the non-azeotropic refrigerant mixture. Technical solutions adopted to solve technical problems

[0007] The heat pump device of the first viewpoint includes a refrigerant circuit, a compressor, and a composition regulating mechanism. In the refrigerant circuit, a non-azeotropic refrigerant mixture comprising a first refrigerant and a second refrigerant with a boiling point higher than that of the first refrigerant circulates. The compressor is located in the refrigerant circuit and compresses the non-azeotropic refrigerant mixture. The composition regulating mechanism is connected to the refrigerant circuit and suppresses the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor. The first refrigerant is a compound represented by a molecular formula having one or more carbon-carbon unsaturated bonds.

[0008] In the heat pump device of the first viewpoint, the composition regulating mechanism suppresses the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor. As a result, the increase in compounds represented by molecular formulas having more than one carbon-carbon unsaturated bond in the non-azeotropic refrigerant mixture discharged from the compressor is suppressed, thus reducing the risk of disproportionation reactions.

[0009] The second viewpoint heat pump device is based on the first viewpoint heat pump device and includes a storage tank disposed in the refrigerant circuit. The storage tank has a first flow path connected to the compressor suction port and an outlet connected to the first flow path. The storage tank has a liquid reservoir for storing a liquid non-azeotropic refrigerant mixture. A composition regulating mechanism prevents an increase in the proportion of the first refrigerant entering the suction port compared to the proportion of the first refrigerant contained in the non-azeotropic refrigerant mixture entering the storage tank.

[0010] In the heat pump device of the second perspective, the composition regulating mechanism can suppress an increase in the proportion of the first refrigerant entering the compressor suction port compared to the proportion of the first refrigerant contained in the non-azeotropic refrigerant mixture entering the storage tank. As a result, the increase in compounds represented by molecular formulas having more than one carbon-carbon unsaturated bond in the non-azeotropic refrigerant mixture discharged from the compressor is suppressed, thus reducing the risk of disproportionation reactions.

[0011] The third viewpoint heat pump device is based on the second viewpoint heat pump device, and includes an adjustment mechanism to connect the first flow path with the liquid storage section, and an extraction mechanism to extract the liquid non-azeotropic refrigerant from the liquid storage section and make it flow out of the first flow path.

[0012] The third-view heat pump device, through a take-out mechanism, can remove the liquid non-azeotropic refrigerant mixture from the liquid storage section of the tank and allow it to flow out into the first flow path. As a result, the amount of liquid non-azeotropic refrigerant mixture accumulating in the tank can be reduced, and the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor can be suppressed.

[0013] The fourth viewpoint of the heat pump device is based on the third viewpoint of the heat pump device, and the extraction mechanism includes an expansion mechanism that expands the liquid non-azeotropic refrigerant flowing in the extraction mechanism.

[0014] In the heat pump device of the fourth perspective, the resistance generated by the throttling mechanism prevents excessive flow of liquid non-azeotropic refrigerant mixture to the extraction mechanism. As a result, compressor malfunctions caused by excessive return of liquid non-azeotropic refrigerant mixture to the compressor can be prevented.

[0015] The fifth viewpoint's heat pump device is based on the third or fourth viewpoint's heat pump device, and the extraction mechanism includes a small-diameter section disposed in the first flow path and a narrow-diameter tube connecting the liquid storage section and the small-diameter section. The small-diameter section has an inner diameter smaller than the inner diameter of the first flow path upstream of the small-diameter section and the inner diameter of the first flow path downstream of the small-diameter section. The narrow-diameter tube has an inner diameter smaller than the inner diameter of the small-diameter section.

[0016] In the heat pump device of the fifth viewpoint, in the first flow path, the flow rate of the non-azeotropic refrigerant mixture in the narrow diameter section is faster than that on its upstream and downstream sides, thus generating the Venturi effect. Due to the Venturi effect, the pressure in the narrow diameter section decreases, thereby allowing the liquid non-azeotropic refrigerant mixture accumulated in the liquid storage section of the tank to be stably extracted through the narrow diameter pipe.

[0017] The sixth viewpoint's heat pump device is based on any of the third to fifth viewpoints, wherein the storage tank has an outlet pipe located at the outlet and connected to a first flow path. The outlet pipe has an outlet end connected to the compressor's suction inlet and an inlet end located inside the storage tank. The extraction mechanism is an opening formed at a predetermined location on the outlet pipe within the liquid storage section.

[0018] In the heat pump device of the sixth viewpoint, liquid non-azeotropic refrigerant mixture can be drawn out to the first flow path through the opening of the outlet pipe. As a result, the accumulation of a large amount of liquid non-azeotropic refrigerant mixture in the liquid storage section of the storage tank can be suppressed.

[0019] The heat pump device of the seventh viewpoint is based on any of the heat pump devices in the second to sixth viewpoints, and the regulating mechanism includes a stirring mechanism for the non-azeotropic mixed refrigerant in the stirring tank.

[0020] In the heat pump device of the seventh viewpoint, the stirring mechanism promotes the evaporation of the liquid second refrigerant in the tank by stirring the non-azeotropic refrigerant mixture in the tank. As a result, the liquid second refrigerant becomes less likely to remain in the tank, thereby suppressing the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor.

[0021] The heat pump device of the eighth viewpoint is based on the heat pump device of the seventh viewpoint, wherein the storage tank has an inlet pipe near its inner wall for introducing a non-azeotropic refrigerant mixture into the interior. The stirring mechanism is a structure that sprays the non-azeotropic refrigerant mixture out of the inlet pipe along the inner wall of the storage tank in a direction intersecting with the direction of gravity.

[0022] The heat pump device of the eighth viewpoint ejects a non-azeotropic refrigerant mixture from the inlet pipe structure along the inner wall of the storage tank in a direction intersecting with the direction of gravity. This allows for a swirling flow of the non-azeotropic refrigerant mixture along the inner wall of the tank. This swirling flow promotes the evaporation of the liquid non-azeotropic refrigerant mixture, making it difficult for the liquid second refrigerant to remain in the storage tank.

[0023] The heat pump device of the ninth viewpoint is based on the heat pump device of the seventh or eighth viewpoint. The stirring mechanism includes a refrigerant inlet flow path that connects the nozzle to the storage tank, connects the inlet to a part of the refrigerant circuit with a pressure higher than that in the storage tank, and allows the non-azeotropic refrigerant mixture to flow from the inlet to the nozzle.

[0024] In the heat pump device of the ninth viewpoint, a high-pressure non-azeotropic refrigerant mixture, with a pressure higher than that inside the tank, flows from the inlet of the refrigerant inlet path to the outlet and is ejected from the outlet. Therefore, the non-azeotropic refrigerant mixture in the tank is agitated by the high-pressure refrigerant mixture. As a result, the evaporation of the liquid non-azeotropic refrigerant mixture in the tank is promoted, making it difficult for the liquid refrigerant mixture to remain in the tank.

[0025] The heat pump device of the tenth viewpoint is based on any of the heat pump devices in the second to ninth viewpoints, and the regulating mechanism includes an internal heat exchanger that heats the non-azeotropic refrigerant flowing into the first flow path.

[0026] In the heat pump device of the tenth perspective, the non-azeotropic refrigerant flowing to the first flow path in the internal heat exchanger is heated, thus at least a portion of the liquid non-azeotropic refrigerant flowing in the first flow path is vaporized. Because at least a portion of the liquid non-azeotropic refrigerant is vaporized, the proportion of liquid non-azeotropic refrigerant drawn into the compressor is reduced, thereby lowering the risk of compressor malfunction due to drawing in a large amount of liquid non-azeotropic refrigerant.

[0027] The heat pump device of the eleventh viewpoint is based on any of the heat pump devices in the second to tenth viewpoints, wherein the refrigerant circuit has a second flow path for the flow of a non-azeotropic refrigerant mixture into the storage tank. The regulating mechanism includes a bypass flow path that bypasses the storage tank and is connected to the first and second flow paths, an on / off valve for the bypass flow path, and a control unit for controlling the on / off valve. When operating in the storage tank at a predetermined ratio in which the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture flowing out of the first flow path is increased compared to the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture flowing in from the second flow path, the control unit controls the opening and closing of the on / off valve.

[0028] In the heat pump device of the eleventh perspective, the result of control by the control unit is that, during a predetermined operation in which the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture flowing from the storage tank to the first flow path increases, the non-azeotropic refrigerant mixture passes through the bypass flow path without passing through the storage tank. Therefore, during the predetermined operation, the accumulation of the second refrigerant in the storage tank is prevented, and the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor is suppressed.

[0029] The heat pump device of the twelfth viewpoint is based on any of the heat pump devices in the second to tenth viewpoints, and includes an adjustment mechanism comprising a control unit. This control unit has a predetermined mode for increasing the suction superheat at the compressor inlet by controlling devices related to the non-azeotropic refrigerant mixture in the refrigerant circuit. The control unit switches to the predetermined mode when liquid non-azeotropic refrigerant mixture accumulates in the storage tank.

[0030] In the heat pump device of the twelfth viewpoint, when a liquid non-azeotropic refrigerant mixture accumulates in the storage tank, the control unit switches to a predetermined mode, thereby increasing the suction superheat at the compressor inlet. Due to the increase in suction superheat, the liquid non-azeotropic refrigerant mixture becomes less likely to accumulate in the storage tank, and the heat pump device can suppress the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor.

[0031] The heat pump device of the thirteenth viewpoint is based on the heat pump device of the first viewpoint. The regulating mechanism is a receiver that is arranged in the high-pressure section of the refrigerant circuit where the pressure is higher than that of the compressor suction port, and allows the refrigerant to pass through without changing the ratio of the first refrigerant and the second refrigerant in the non-azeotropic refrigerant mixture.

[0032] In the heat pump device of the thirteenth aspect, a liquid non-azeotropic refrigerant mixture can be stored in the receiver, thus, for example, eliminating the need for a storage tank for storing the liquid non-azeotropic refrigerant mixture. In the receiver, changes in the ratio of the first refrigerant and the second refrigerant in the non-azeotropic refrigerant mixture are suppressed; therefore, the heat pump device can suppress an increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor.

[0033] The heat pump device of the fourteenth viewpoint is based on any of the heat pump devices in the first to thirteenth viewpoints, with a non-azeotropic mixed refrigerant as the first refrigerant, including trans-1,2-difluoroethylene.

[0034] The heat pump device of the fifteenth viewpoint is based on any of the heat pump devices of the first to fourteenth viewpoints, with a non-azeotropic mixed refrigerant as the first refrigerant, including trifluoroethylene.

[0035] The heat pump device of the sixteenth viewpoint is based on any of the heat pump devices in the first to fifteenth viewpoints, and includes an indoor heat exchanger installed in the refrigerant circuit to exchange heat between the non-azeotropic refrigerant discharged from the compressor and the air inside the electric vehicle. Attached Figure Description

[0036] Figure 1 This is a schematic diagram illustrating an example of the structure of an air conditioner according to the first embodiment. Figure 2 This is a block diagram illustrating the control of the controller in the first embodiment. Figure 3 This is a gas-liquid equilibrium diagram of a non-azeotropic refrigerant mixture. Figure 4 It means Figure 1 A schematic diagram of an example of a component adjustment mechanism. Figure 5 It means Figure 1 A schematic diagram of another example of a component adjustment mechanism. Figure 6 This is a schematic diagram illustrating an example of the component adjustment mechanism in the second embodiment. Figure 7 This is a schematic diagram illustrating an example of the component adjustment mechanism in the third embodiment. Figure 8A This is a schematic diagram illustrating another example of the component adjustment mechanism in the third embodiment. Figure 8B This is a schematic diagram illustrating another example of the component adjustment mechanism in the third embodiment. Figure 9A This is a schematic diagram illustrating an example of the component adjustment mechanism in the fourth embodiment. Figure 9B It is used for explanation Figure 9A A schematic diagram showing the relationship between the inner wall of the storage tank and the inlet pipe. Figure 10 This is a schematic diagram illustrating an example of the structure of the air conditioner according to the fifth embodiment. Figure 11 This is a block diagram illustrating the control of the component adjustment mechanism in the fifth embodiment. Figure 12 This is a schematic diagram illustrating an example of the structure of the air conditioner according to the sixth embodiment. Figure 13 This is a block diagram illustrating the control of the component adjustment mechanism in the sixth embodiment. Figure 14 This is a schematic diagram illustrating an example of the structure of the air conditioner according to the seventh embodiment. Figure 15 This is a block diagram illustrating an example of the component adjustment mechanism in the eighth embodiment. Figure 16 This is a schematic diagram illustrating an example of the structure of the air conditioner according to the ninth embodiment. Figure 17 This is a schematic diagram showing another example of the structure of the air conditioner according to the ninth embodiment. Figure 18 This is a schematic diagram showing another example of the structure of the air conditioner according to the ninth embodiment. Figure 19 This is a schematic diagram showing another example of the structure of the air conditioner according to the ninth embodiment. Detailed Implementation

[0037] <First Implementation> (1) Overall structure Figure 1 The diagram shows an air conditioner 1 as a heat pump device according to a first embodiment. The heat pump device disclosed herein uses a non-azeotropic refrigerant mixture and implements a vapor compression refrigeration cycle. In the following description, the non-azeotropic refrigerant mixture is sometimes simply referred to as a mixed refrigerant. The air conditioner 1 is used, for example, in the interior of a building, the interior of a railway vehicle, or the interior of an electric vehicle. The air conditioner 1 is configured to switch between cooling mode, heating mode, and dehumidification / heating mode. Besides air conditioners, heat pump devices are used, for example, in water heaters, refrigerators, washer-dryer combos, and underfloor heating systems.

[0038] (1-1) Regarding non-azeotropic refrigerant mixtures The non-azeotropic refrigerant used in air conditioner 1 is a mixture of a first refrigerant composed of compounds having a molecular formula representing one or more carbon-carbon unsaturated bonds and a second refrigerant with a boiling point higher than that of the first refrigerant. Similarly, in the following description of the second embodiment, the refrigerant composed of compounds having a molecular formula representing one or more carbon-carbon unsaturated bonds is referred to as the first refrigerant, and the refrigerant composed of compounds with a boiling point higher than that of the first refrigerant is referred to as the second refrigerant. Therefore, the non-azeotropic refrigerant of this disclosure is a mixture of a first refrigerant with a relatively low boiling point and a second refrigerant with a relatively high boiling point, composed of the aforementioned compounds. The aforementioned non-azeotropic refrigerant including the first and second refrigerants includes the following first mixed refrigerant, second mixed refrigerant, and third mixed refrigerant. Furthermore, the non-azeotropic refrigerant can also be used with refrigeration oil.

[0039] (First mixed refrigerant) The non-azeotropic refrigerant mixture includes a first refrigerant mixture comprising trans-1,2-difluoroethylene (HFO-1132(E)) and 2,3,3,3-tetrafluoropropylene (HFO-1234yf). Trans-1,2-difluoroethylene (HFO-1132(E)) has a boiling point of -52.5°C, and 2,3,3,3-tetrafluoropropylene (HFO-1234yf) has a boiling point of -29.5°C. Therefore, in the first refrigerant mixture, trans-1,2-difluoroethylene (HFO-1132(E)) is the first refrigerant, while 2,3,3,3-tetrafluoropropylene (HFO-1234yf) is the second refrigerant.

[0040] The proportions of each refrigerant in the first mixed refrigerant, for example, relative to the total mass of trans-1,2-difluoroethylene (HFO-1132(E)) and 2,3,3,3-tetrafluoropropylene (HFO-1234yf), the proportion of trans-1,2-difluoroethylene (HFO-1132(E)) is 12.1–72.0% by mass, and the proportion of 2,3,3,3-tetrafluoropropylene (HFO-1234yf) is 87.9–28.0% by mass. Combining the mass of trans-1,2-difluoroethylene with the mass of 2,3,3,3-tetrafluoropropylene yields the mass of the non-azeotropic mixed refrigerant. For example, if the proportion of trans-1,2-difluoroethylene is 20.0% by mass, then the proportion of 2,3,3,3-tetrafluoropropylene is 80.0% by mass.

[0041] (Second mixed refrigerant) Furthermore, the non-azeotropic refrigerant mixture includes a second refrigerant mixture comprising trifluoroethylene (HFO-1123) and 2,3,3,3-tetrafluoropropylene (HFO-1234yf). Trifluoroethylene (HFO-1123) has a boiling point of -56.0°C; therefore, in the second refrigerant mixture, HFO-1123 is the first refrigerant, and HFO-1234yf is the second refrigerant. Even if the second refrigerant mixture includes compounds other than HFO-1123 and HFO-1234yf, the relationship that HFO-1123 is the first refrigerant and HFO-1234yf is the second refrigerant always holds true. Additionally, the second refrigerant mixture (non-azeotropic refrigerant mixture) can be a mixture of multiple first refrigerants or multiple second refrigerants. The composition of the second refrigerant mixture includes the following first to ninth components.

[0042] (The first component of the second mixed refrigerant) First, the first component of the second mixed refrigerant will be described. In the first component of the second mixed refrigerant, the total amount of trifluoroethylene and 2,3,3,3-tetrafluoropropylene is 70-100% by mass relative to the total amount of the second mixed refrigerant, and the proportion of trifluoroethylene is 35-95% by mass relative to the total amount of trifluoroethylene and 2,3,3,3-tetrafluoropropylene. When the total amount of HFO-1123 and HFO-1234yf relative to the total amount of the second mixed refrigerant is less than 100% by mass, the first component of the second mixed refrigerant also includes components for the thermal cycle system.

[0043] Furthermore, the composition of the first component of the second mixed refrigerant for the thermal cycle system includes 10 to 30% by mass of a refrigerant for the thermal cycle relative to the total amount of the second mixed refrigerant. The refrigerant for the thermal cycle is composed of at least one compound selected from saturated hydrofluorocarbons and hydrofluorocarbons having carbon-carbon double bonds (excluding trifluoroethylene and 2,3,3,3-tetrafluoropropylene).

[0044] Furthermore, the thermal cycle system composition of the first component of the second mixed refrigerant, when the total amount of trifluoroethylene (HFO-1123) and 2,3,3,3-tetrafluoropropylene (HFO-1234yf) and the thermal cycle refrigerant is less than 100% by mass of the total amount of the second mixed refrigerant, includes other compounds. These other compounds are at least one compound from the group consisting of carbon dioxide, hydrocarbons, chlorofluoroolefins (CFO), and hydrochlorofluoroolefins (HCFO).

[0045] (Second component of the second mixed refrigerant) Based on the first component of the second mixed refrigerant described above, the second component of the second mixed refrigerant is a composition in which the total amount of trifluoroethylene and 2,3,3,3-tetrafluoropropylene is in a ratio of 80% to 100% by mass relative to the total amount of the second mixed refrigerant.

[0046] (The third component of the second mixed refrigerant) Based on the first component or the second component of the second mixed refrigerant mentioned above, the third component of the second mixed refrigerant is a composition in which the ratio of trifluoroethylene to the total amount of trifluoroethylene and 2,3,3,3-tetrafluoropropylene is 40% to 95% by mass.

[0047] (The fourth component of the second mixed refrigerant) Based on any one of the first to third components of the second mixed refrigerant, the fourth component of the second mixed refrigerant is a component in which the proportion of trifluoroethylene to the total amount of the second mixed refrigerant is less than 70 mol%.

[0048] (The fifth component of the second mixed refrigerant) Based on any one of the first to fourth components of the second mixed refrigerant described above, the fifth component of the second mixed refrigerant is a hydrofluorocarbon having a carbon-carbon double bond selected from at least one of the following: 1,2-difluoroethylene, 2-fluoropropene, 1,1,2-trifluoropropene, trans-1,2,3,3,3-pentafluoropropene, cis-1,2,3,3,3-pentafluoropropene, trans-1,3,3,3-tetrafluoropropene, cis-1,3,3,3-tetrafluoropropene, and 3,3,3-trifluoropropene.

[0049] (The sixth component of the second mixed refrigerant) Based on any one of the first to fifth components of the second mixed refrigerant, the sixth component of the second mixed refrigerant is a hydrofluorocarbon having a carbon-carbon double bond, which is trans-1,3,3,3-tetrafluoropropylene.

[0050] (The seventh component of the second mixed refrigerant) Based on any one of the first to sixth components of the second mixed refrigerant described above, the seventh component of the second mixed refrigerant is a saturated hydrofluorocarbon selected from at least one of the following groups: difluoromethane, 1,1-difluoroethane, 1,1,1-trifluoroethane, 1,1,2,2-tetrafluoroethane, 1,1,1,2-tetrafluoroethane, and pentafluoroethane.

[0051] (The eighth component of the second mixed refrigerant) Based on any one of the first to seventh components of the second mixed refrigerant, the eighth component of the second mixed refrigerant is a saturated hydrofluorocarbon selected from at least one of the following groups: difluoromethane, 1,1,1,2-tetrafluoroethane, and pentafluoroethane.

[0052] (The ninth component of the second mixed refrigerant) Based on any one of the first to eighth components of the second mixed refrigerant described above, the ninth component of the second mixed refrigerant is a saturated hydrofluorocarbon, namely difluoromethane, wherein the proportion of trifluoroethylene relative to the total amount of trifluoroethylene, 2,3,3,3-tetrafluoropropylene, and difluoromethane is 30 to 80% by mass, the proportion of 2,3,3,3-tetrafluoropropylene is 40% by mass or less, the proportion of difluoromethane is 30% by mass or less, and the proportion of trifluoroethylene relative to the total amount of the working medium is 70 mol% or less.

[0053] (Third mixed refrigerant) In non-azeotropic refrigerant mixtures, a third refrigerant mixture exists, comprising trifluoroethylene (HFO-1123), difluoromethane (R32), and 1,3,3,3-tetrafluoropropylene (HFO-1234ze). Trifluoroethylene (HFO-1123) has a boiling point of -56.0°C, and 1,3,3,3-tetrafluoropropylene (HFO-1234ze) has a boiling point of -19°C. Therefore, in the third refrigerant mixture, HFO-1123 is the first refrigerant, and HFO-1234ze is the second refrigerant. Even when the third refrigerant mixture includes compounds other than HFO-1123 and HFO-1234ze, the relationship that HFO-1123 is the first refrigerant and HFO-1234ze is the second refrigerant always holds true. Furthermore, the third refrigerant mixture (non-azeotropic refrigerant mixture) can be a mixture of multiple first refrigerants or multiple second refrigerants. The third mixed refrigerant contains the following first to fifth components.

[0054] (The first component of the third mixed refrigerant) First, the first composition of the third mixed refrigerant is described. In the first composition of the third mixed refrigerant, the proportion of trifluoroethylene, difluoromethane, and 1,3,3,3-tetrafluoropropylene relative to the total amount of the third refrigerant is greater than 90% by mass and less than or equal to 100% by mass. In the first composition of the third mixed refrigerant, the proportion of trifluoroethylene relative to the total amount of trifluoroethylene, difluoromethane, and 1,3,3,3-tetrafluoropropylene is greater than 0% by mass and less than or equal to 50% by mass, the proportion of difluoromethane is greater than 0% by mass and less than or equal to 40% by mass, and the proportion of 1,3,3,3-tetrafluoropropylene is greater than or equal to 40% by mass and less than or equal to 90% by mass.

[0055] (Second component of the third mixed refrigerant) Based on the first component of the aforementioned third mixed refrigerant, the second component of the third mixed refrigerant is a composition in which the proportion of trifluoroethylene relative to the total amount of trifluoroethylene, difluoromethane, and 1,3,3,3-tetrafluoropropylene is greater than 0% by mass and less than or equal to 20% by mass, the proportion of difluoromethane is greater than 0% by mass and less than or equal to 20% by mass, and the proportion of 1,3,3,3-tetrafluoropropylene is greater than or equal to 65% by mass and less than or equal to 90% by mass.

[0056] (The third component of the third mixed refrigerant) Based on the first component or the second component of the third mixed refrigerant mentioned above, the third component of the third mixed refrigerant is a composition of 1,3,3,3-tetrafluoropropylene containing more than 60% by mass of trans-1,3,3,3-tetrafluoropropylene.

[0057] (The fourth component of the third mixed refrigerant) Based on any one of the first to third components of the third mixed refrigerant, the fourth component of the third mixed refrigerant is a composition including 2,3,3,3-tetrafluoropropylene.

[0058] (The fifth component of the third mixed refrigerant) Based on a refrigerant having any one of the first to fourth components of the third mixed refrigerant, the fifth component of the third mixed refrigerant is a refrigerant composed of trifluoroethylene, difluoromethane, and 1,3,3,3-tetrafluoropropylene.

[0059] (1-2) Overview of the structure of air conditioner 1 like Figure 1 As shown, the air conditioner 1 includes a refrigerant circuit 10 for circulating a non-azeotropic refrigerant mixture and a compressor 11. In the refrigerant circuit 10, the non-azeotropic refrigerant mixture is compressed by the compressor 11. The refrigerant circuit 10 is equipped with a first heat exchanger 12, a first expansion valve 13, a second heat exchanger 14, a three-way valve 15, a second expansion valve 16, a third heat exchanger 17, and a storage tank 20. For the compressor 11, a scroll compressor or a rotary compressor can be used, for example. The first expansion valve 13 and the second expansion valve 16 are, for example, electrically operated valves, whose opening degree can be changed by the control of the controller 90 described later. The three-way valve 15 is, for example, an electrically operated valve, which can switch its internal flow path by the control of the controller 90 described later.

[0060] The air conditioner 1 includes an indoor unit 50 that supplies conditioned air to the target space inside the vehicle. The indoor unit 50 has a housing 51. A first heat exchanger 12, a third heat exchanger 17, a fan 52, a first air path switching device 53, and a second air path switching device 54 are disposed on the housing 51 of the indoor unit 50.

[0061] like Figure 2As shown, the air conditioner 1 includes a controller 90, which uses various sensors 80 to determine the conditions of the refrigerant circuit 10 and the environment, and controls the equipment installed in the refrigerant circuit 10 and the indoor unit 50. The various sensors 80 in the air conditioner 1 may include, for example, temperature sensors, pressure sensors, sensors for detecting refrigerant leaks, and other sensors. Among the temperature sensors, there are, for example, temperature sensors that detect the temperature of the air blown out of the indoor unit 50, temperature sensors that detect the air temperature inside the vehicle, temperature sensors that detect the air temperature outside the vehicle, and temperature sensors that detect the temperature of the mixed refrigerant flowing in various parts of the refrigerant circuit 10. Among the pressure sensors, there are, for example, pressure sensors that detect the pressure of the mixed refrigerant flowing in a designated part of the refrigerant circuit 10. The controller 90 is connected to an input unit 85 that receives information needed to determine the control objective. For example, the set temperature inside the vehicle and the airflow rate blown out of the indoor unit 50 are input from the input unit 85.

[0062] The controller 90 controls the compressor 11, the first expansion valve 13, the three-way valve 15, the second expansion valve 16, the fan 52, the first airflow switching device 53, and the second airflow switching device 54. The devices controlled by the controller 90 are related to a non-azeotropic refrigerant mixture circulating in the refrigerant circuit 10. The controller 90 controls the on / off state of the compressor 11. If the speed of the compressor 11 is variable, the controller 90 is configured to control the speed of the compressor 11. The controller 90 controls the opening degree of the first expansion valve 13 and the second expansion valve 16. The controller 90 switches the on / off state of the three-way valve 15. The controller 90 controls the speed of the fan 52, thereby controlling the airflow from the indoor unit 50. The controller 90 switches between the first airflow switching device 53 and the second airflow switching device 54.

[0063] The controller 90 is implemented by a computer. The controller 90 includes, for example, a control processing unit and a storage unit. The control processing unit may use a processor such as a CPU or a GPU. The control processing unit reads a program stored in the storage unit and performs prescribed image processing or computational processing according to the program. Furthermore, the control processing unit can write computation results to the storage unit according to the program and can read information stored in the storage unit according to the program. The storage unit can be used as a database.

[0064] The refrigerant circuit 10 can switch the circulation path of the mixed refrigerant via a three-way valve 15. The three-way valve 15 switches between a state connecting the second heat exchanger 14 to the storage tank 20 and a state connecting the second heat exchanger 14 to the second expansion valve 16. When the three-way valve 15 is connected to the second heat exchanger 14 and the storage tank 20, the second expansion valve 16 is closed, thus preventing mixed refrigerant from flowing from the three-way valve 15 through the second expansion valve 16 and the third heat exchanger 17 to the storage tank 20. When the three-way valve 15 is connected to the second heat exchanger 14 and the expansion valve 16, mixed refrigerant flows from the three-way valve 15 through the second expansion valve 16 and the third heat exchanger 17 to the storage tank 20.

[0065] (1-3) Operation of Air Conditioner 1 in various modes In the refrigerant circuit 10, there is a first path for the mixed refrigerant to flow in the heating mode and a second path for the mixed refrigerant to flow in the cooling mode and the dehumidification heating mode. Figure 1 In the first path, the mixed refrigerant flows in the direction indicated by the arrow on the dashed line. Figure 1 In the second path, the mixed refrigerant flows in the direction indicated by the solid line and the dashed arrow.

[0066] In the first path of the heating mode, the mixed refrigerant flows sequentially through the compressor 11, the first heat exchanger 12, the first expansion valve 13, the second heat exchanger 14, the three-way valve 15, the storage tank 20, and the compressor 11.

[0067] In the second path of cooling mode and dehumidification and heating mode, the mixed refrigerant flows sequentially through compressor 11, first heat exchanger 12, first expansion valve 13, second heat exchanger 14, three-way valve 15, second expansion valve 16, third heat exchanger 17, storage tank 20 and compressor 11.

[0068] In heating mode, the gaseous refrigerant mixture is drawn into and compressed through the suction port of compressor 11 in the first path. The compressed gaseous refrigerant mixture in compressor 11 is discharged from the discharge port 11b of compressor 11. The refrigerant mixture discharged from the discharge port 11b of compressor 11 is sent to the first heat exchanger 12. In heating mode, the refrigerant mixture exchanges heat with the air blown into the vehicle interior in the first heat exchanger 12. After heat exchange in the first heat exchanger 12, the refrigerant mixture is depressurized in the first expansion valve 13. After depressurization in the expansion valve 13, the refrigerant mixture exchanges heat with the outside air in the second heat exchanger 14. After heat exchange in the second heat exchanger 14, the refrigerant mixture flows into the storage tank 20 via the three-way valve 15. In the storage tank 20, the gas-liquid two-phase refrigerant mixture is separated. The separated refrigerant mixture is then drawn into compressor 11.

[0069] In heating mode, the second airflow switching device 54 is switched so that the air blown from the indoor unit 50 passes through the first heat exchanger 12. In other words, the second airflow switching device 54 directs the airflow towards the indoor unit 50. Figure 1 The solid line indicates the state switching, causing airflow generated by fan 52 to flow into the first heat exchanger 12. In heating mode, the air exchanged for heat in the first heat exchanger 12 is blown into the vehicle interior as warm air. In heating mode, the first heat exchanger 12 functions as a condenser. In heating mode, the second expansion valve 16 is fully closed, and the mixed refrigerant in the third heat exchanger 17 does not flow. Therefore, the air blown into the interior from the third heat exchanger 17 is not exchanged for heat.

[0070] In cooling mode, the gaseous refrigerant mixture is drawn into and compressed through the suction port of compressor 11 in the second path. The compressed gaseous refrigerant mixture in compressor 11 is discharged from the discharge port 11b of compressor 11. The refrigerant mixture discharged from the discharge port 11b of compressor 11 is sent to the first heat exchanger 12. In cooling mode, the refrigerant mixture does not undergo heat exchange in the first heat exchanger 12. After passing through the first heat exchanger 12, the refrigerant mixture passes through the fully open first expansion valve 13. The refrigerant mixture that has not been depressurized in the first expansion valve 13 exchanges heat with outside air in the second heat exchanger 14. After heat exchange in the second heat exchanger 14, the refrigerant mixture is depressurized in the second expansion valve 16 via the three-way valve 15. After depressurization in the second expansion valve 16, the refrigerant mixture exchanges heat with air blown into the vehicle interior in the third heat exchanger 17. The refrigerant mixture that has undergone heat exchange in the third heat exchanger 17 flows into the storage tank 20. In storage tank 20, the gas-liquid two-phase refrigerant mixture is separated into gas and liquid phases. The separated refrigerant mixture is then drawn into compressor 11.

[0071] In cooling mode, the second airflow switching device 54 is switched so that the air blown from the indoor unit 50 does not pass through the first heat exchanger 12. In other words, the second airflow switching device 54 directs the airflow towards the indoor unit 50. Figure 1 The dotted line indicates the state switching, blocking the airflow generated by fan 52 so that it does not flow into the first heat exchanger 12. In cooling mode, the air that has been heat-exchanged in the third heat exchanger 17 is blown into the vehicle interior as cold air. In cooling mode, the third heat exchanger 17 functions as an evaporator. In cooling mode, the first expansion valve 13 is fully open, and no pressure reduction occurs in the first expansion valve 13.

[0072] In dehumidification and heating mode, the mixed refrigerant circulates in the second path in the same way as in cooling mode. The state of the second air path switching device 54 differs between dehumidification and heating modes. In dehumidification and heating mode, the state of the second air path switching device 54 is switched to... Figure 1The solid line indicates the state. In other words, in dehumidification and heating mode, the second air path switching device 54 switches to the state where the air blown from the indoor unit 50 passes through the first heat exchanger 12. In this state, the air cooled in the third heat exchanger 17 is dehumidified by condensation. The dehumidified air is heated by passing through the first heat exchanger 12 and then blown into the vehicle interior.

[0073] In the dehumidification and heating mode, the gaseous refrigerant mixture is drawn in and compressed from the suction port of compressor 11 in the second path. The compressed gaseous refrigerant mixture in compressor 11 is discharged from the discharge port 11b of compressor 11. The refrigerant mixture discharged from the discharge port 11b of compressor 11 is sent to the first heat exchanger 12. In the dehumidification and heating mode, the refrigerant mixture exchanges heat with the air blown into the vehicle interior in heat exchanger 12. After passing through the first heat exchanger 12, the refrigerant mixture is depressurized in the first expansion valve 13. The refrigerant mixture after depressurization in the first expansion valve 13 exchanges heat with the outside air in the second heat exchanger 14. After heat exchange in the second heat exchanger 14, the refrigerant mixture is depressurized in the second expansion valve 16 via the three-way valve 15. After depressurization in the second expansion valve 16, the refrigerant mixture exchanges heat with the air blown into the vehicle interior in the third heat exchanger 17. The refrigerant mixture after heat exchange in the third heat exchanger 17 flows into the storage tank 20. In storage tank 20, the gas-liquid two-phase mixed refrigerant is separated into gas and liquid phases. The separated gas-liquid mixed refrigerant is then drawn into compressor 11. In dehumidification and heating mode, the air cooled and dehumidified in the third heat exchanger 17 is heated in the first heat exchanger 12 and blown into the vehicle interior.

[0074] The interior unit 50 has a first air inlet 58 and a second air inlet 59 for introducing air that has been heat-exchanged in the first heat exchanger 12 or the third heat exchanger 17. The first air inlet 58 leads to the vehicle interior, and the second air inlet 59 leads to the outside of the vehicle. A first airflow switching device 53 can switch the first air inlet 58 to a closed state so that air can be introduced from the outside of the vehicle. Figure 1 (The state shown by the solid line). Furthermore, the first airflow switching device 53 can switch the first air inlet 58 to a closed state in a manner that allows air to be drawn in from outside the vehicle. Figure 1 (The state is shown by the solid line in the middle). Air introduced from the first air inlet 58 or the second air inlet 59 passes through the fan 52 and the third heat exchanger 17. After passing through the third heat exchanger 17, the air passes through the first heat exchanger 12 or is blown out into the vehicle compartment without passing through the first heat exchanger 12, depending on the switching state of the second air path switching device 54.

[0075] (1-4) Composition of adjustment mechanism 100 A composition regulating mechanism 100 is provided in the refrigerant circuit 10. The composition regulating mechanism 100 is a mechanism that suppresses the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor 11. The composition of the non-azeotropic refrigerant mixture is a predetermined composition when the air conditioner 1 is installed. However, during repeated compression and expansion, the composition of the non-azeotropic refrigerant mixture in the refrigerant circuit 10 may sometimes change due to liquefaction or vaporization. Figure 3 This is a gas-liquid equilibrium diagram for a non-azeotropic refrigerant mixture. At constant pressure and refrigerant temperature t1℃, point a contains both gaseous and liquid non-azeotropic refrigerant mixtures, with the first refrigerant comprising 50% of the molar ratio. At the same refrigerant temperature t1℃, at point b, the gaseous non-azeotropic refrigerant mixture contains 70% of the first refrigerant, and at point c, the liquid non-azeotropic refrigerant mixture contains 10% of the first refrigerant. Furthermore, although the molar ratio of the first refrigerant is the same at points d and b, the refrigerant temperature at point d is lower, and the non-azeotropic refrigerant mixture at point d is a two-phase mixture of liquid and gaseous non-azeotropic refrigerant.

[0076] In storage tank 20, when the gaseous and liquid non-azeotropic refrigerant mixtures are separated and reach equilibrium, there will be two states: point b and point c. Due to the inflow and outflow of non-azeotropic refrigerant mixtures into and out of storage tank 20, an ideal gas-liquid equilibrium cannot be achieved. However, there are... Figure 3 As shown, the proportion of the first refrigerant in the liquid non-azeotropic refrigerant mixture accumulated in tank 20 becomes smaller than the proportion of the first refrigerant in the non-azeotropic refrigerant mixture entering tank 20 in a gas-liquid two-phase state. Therefore, if liquid non-azeotropic refrigerant mixture accumulates in tank 20, the proportion of the first refrigerant in the non-azeotropic refrigerant mixture circulating in the refrigerant circuit 10 other than tank 20 becomes larger.

[0077] The composition adjustment mechanism 100 of the first embodiment is a take-out mechanism 100, which suppresses the increase of the proportion of the first refrigerant entering the suction port of the compressor 11 compared with the proportion of the first refrigerant included in the non-azeotropic mixed refrigerant entering the storage tank 20. Figure 1 The extraction mechanism 110 shown is a mechanism that removes liquid non-azeotropic refrigerant mixture from the storage tank 20 and allows it to flow into the compressor 11. The extraction mechanism 110 reduces the amount of liquid non-azeotropic refrigerant mixture accumulated in the storage tank 20 to prevent an increase in the proportion of the first refrigerant entering the suction port of the compressor 11.

[0078] (2) Detailed Structure (2-1) Removal mechanism 110 The extraction mechanism 110 is a mechanism for extracting liquid, non-azeotropic refrigerant mixture from the storage tank 20. For example... Figure 4 As shown, the storage tank 20 has an outlet 20e connected to a first flow path P1 connected to the suction port 11a of the compressor 11, and an inlet 20i for the inflow of non-azeotropic refrigerant mixture. The separated liquid non-azeotropic refrigerant mixture in the storage tank 20 accumulates in a liquid storage section 21 of the storage tank 20. The liquid storage section 21 is located at the bottom of the storage tank 20, below the direction of gravity. The extraction mechanism 110 includes an expansion mechanism 30 and an extraction flow path 31. The extraction flow path 31 connects the liquid storage section 21 of the storage tank 20 to the first flow path P1. The liquid non-azeotropic refrigerant mixture accumulated in the liquid storage section 21 can enter the first flow path P1 through the extraction flow path 31. An expansion mechanism 30 is provided in this extraction flow path 31. If a large amount of liquid refrigerant mixture is returned to the compressor 11, it will cause compressor malfunction. Therefore, the amount of liquid refrigerant mixture extracted by the extraction mechanism 110 is regulated by the expansion mechanism 30. As an expansion mechanism 30, a capillary tube 32 is used, for example. The mixed refrigerant passing through the capillary tube 32 is depressurized and expands. Through this capillary tube 32, a suitable amount of liquid mixed refrigerant can be returned to the compressor 11 in a manner that does not cause the compressor 11 to fail. By returning the liquid non-azeotropic mixed refrigerant accumulated in the storage tank 20 as mixed refrigerant circulating in the refrigerant circuit 10, it is possible to suppress the increase in the proportion of the first refrigerant included in the non-azeotropic mixed refrigerant discharged from the compressor 11.

[0079] (3) Variations (3-1) Variation 1A In the first embodiment described above, the case where a capillary tube 32 is used as the expansion mechanism 30 has been explained. However, the expansion mechanism 30 is not limited to the capillary tube 32. For example... Figure 5 As shown, an electric expansion valve 33 can also be used as the expansion mechanism 30. This electric expansion valve 33 is controlled by a controller 90. The controller 90 can, for example, be configured to open the electric expansion valve 33 when the superheat of the compressor 11's suction inlet 11a exceeds a predetermined value, thereby returning the liquid non-azeotropic refrigerant mixture stored in the storage tank 20 to the first flow path P1. With such control, a large amount of liquid refrigerant mixture will not be drawn into the compressor 11; therefore, the compressor 11 can prevent malfunctions caused by the intake of large amounts of liquid refrigerant mixture. The superheat of the compressor 11's suction inlet 11a can be detected using various currently known sensors 80.

[0080] Alternatively, if a predetermined amount or more of a liquid non-azeotropic refrigerant mixture has accumulated, the controller 90 can be configured to open the electric expansion valve 33. To detect whether a predetermined amount or more of a liquid non-azeotropic refrigerant mixture has accumulated, a liquid refrigerant detection sensor 81 can be provided to detect the liquid mixture accumulated in the liquid reservoir 21. The liquid refrigerant sensor 81 can be, for example, a liquid level sensor or a thermistor.

[0081] (4) Features The air conditioner 1 of the first embodiment and Modification 1A can remove liquid non-azeotropic refrigerant mixture from the liquid storage section 21 of the storage tank 20 and allow it to flow out to the first flow path P1 via the extraction mechanism 110. This reduces the amount of liquid non-azeotropic refrigerant mixture accumulating in the storage tank 20. As a result, it is possible to suppress the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor 11. Thus, by suppressing the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor 11, the risk of increased disproportionation reaction can be prevented. Furthermore, the air conditioner 1 of the first embodiment and Modification 1A is an example of a heat pump device.

[0082] Furthermore, if the first refrigerant is flammable, by suppressing the increase in the proportion of the first refrigerant, the flammability of the mixed refrigerant circulating in the refrigerant circuit 10 can be prevented from increasing. Furthermore, by suppressing the increase in the proportion of the first refrigerant, the efficiency and capacity of the air conditioner 1 can be prevented from decreasing due to an unsuitable composition in the mixed refrigerant circulating in the refrigerant circuit 10 caused by an increased proportion of the first refrigerant. Furthermore, by suppressing the increase in the proportion of the first refrigerant, the ability to precisely control the air conditioner 1 can be prevented from becoming unsuitable due to an unsuitable composition in the mixed refrigerant circulating in the refrigerant circuit 10 caused by an increased proportion of the first refrigerant.

[0083] Furthermore, the air conditioner 1 can be used as an in-vehicle air conditioner for electric vehicles. The refrigerant circuit 10 of the air conditioner 1 includes a first heat exchanger 12, which serves as an indoor heat exchanger for exchanging heat between the non-azeotropic refrigerant mixture discharged from the compressor 11 and the air inside the electric vehicle. Hereinafter, the air conditioner 1 of the second to ninth embodiments, like the first embodiment, can also be applied to electric vehicles. In the case where the first heat exchanger 12 is an indoor heat exchanger for exchanging heat with the air blown into the vehicle interior, the risk of adverse conditions occurring inside the vehicle interior due to an increase in the proportion of the first refrigerant in the indoor heat exchanger can be reduced.

[0084] <Second Implementation> (5) Overall structure The air conditioner 1 of the second embodiment differs from the air conditioner 1 of the first embodiment in the structure of its component adjustment mechanism 100, but the rest of the structure is the same. The air conditioner 1 of the second embodiment includes the component adjustment mechanism 100, such as... Figure 6 As shown, the second embodiment includes an extraction mechanism 120, which differs from the extraction mechanism 110 of the first embodiment. The structure of the air conditioner 1 in the second embodiment is the same as that in the first embodiment, except for the extraction mechanism 120. Therefore, the structure of the air conditioner 1 in the second embodiment, except for the extraction mechanism 120, is the same as described in (1-2) above. Furthermore, the operation of the air conditioner 1 in each mode of the second embodiment is also the same as described in (1-3) above. Additionally, the non-azeotropic refrigerant used in the air conditioner 1 of the second embodiment can also be the same non-azeotropic refrigerant described in (1-1) above.

[0085] (6) Structure and operation of the extraction mechanism 120 The extraction mechanism 120 includes a small-diameter portion P1a disposed in the first flow path P1 and a narrow-diameter tube 34 connected to the small-diameter portion P1a. The narrow-diameter tube 34 is a tube connecting the small-diameter portion P1a and the liquid storage portion 21. In the storage tank 20 of the second embodiment, the liquid storage portion 21 is also disposed at the bottom of the storage tank 20 located below the direction of gravity.

[0086] The smaller diameter section P1a has an inner diameter DL smaller than the inner diameter Du of the upstream first flow path P1 and the inner diameter Dd of the downstream first flow path P1. The narrow-diameter pipe 34 has an inner diameter Dm smaller than the inner diameter DL of the smaller diameter section P1a. Since the inner diameter DL of the smaller diameter section P1a is smaller than the inner diameter Du of the upstream first flow path P1 and the inner diameter Dd of the downstream first flow path P1, the flow velocity of the mixed refrigerant in the smaller diameter section P1a is faster than that of the mixed refrigerant upstream and downstream. Due to the Venturi effect (or ejector effect) caused by this velocity difference, the pressure in the smaller diameter section P1a is lower than the pressure in other parts of the first flow path P1. Through this effect, the liquid non-azeotropic mixed refrigerant accumulated in the liquid storage section 21 of the storage tank 20 is stably extracted through the narrow-diameter pipe 34.

[0087] (7) Variation (7-1) Variation 2A The extraction mechanism 120 of the second embodiment may also include the expansion mechanism 30 of the first embodiment. In the extraction mechanism 120 of the second embodiment, for example, an electrically operated expansion valve 33 may be installed on the narrow-diameter tube 34. Furthermore, in the extraction mechanism 120 of the second embodiment, the capillary tube 32 may also be used as the narrow-diameter tube 34.

[0088] (8) Features In the air conditioner 1 of the second embodiment and Modification 2A, the flow rate of the non-azeotropic refrigerant mixture in the small-diameter section P1a of the first flow path P1 is faster than that on its upstream and downstream sides, thus generating a Venturi effect. Due to this Venturi effect, the pressure in the small-diameter section P1a decreases, thereby stably removing the liquid non-azeotropic refrigerant mixture accumulated in the liquid storage section 21 of the storage tank 20 through the narrow-diameter pipe 34. As a result, it is possible to suppress the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor 11. Thus, by suppressing the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor 11, it is possible to prevent an increase in the risk of disproportionation reaction. In addition, the air conditioner 1 of the second embodiment and Modification 2A is an example of a heat pump device.

[0089] Furthermore, if the first refrigerant is flammable, by suppressing the increase in the proportion of the first refrigerant, the flammability of the mixed refrigerant circulating in the refrigerant circuit 10 can be prevented from increasing. Furthermore, by suppressing the increase in the proportion of the first refrigerant, the efficiency and capacity of the air conditioner 1 can be prevented from decreasing due to an unsuitable composition in the mixed refrigerant circulating in the refrigerant circuit 10 caused by an increased proportion of the first refrigerant. Furthermore, by suppressing the increase in the proportion of the first refrigerant, the ability to precisely control the air conditioner 1 can be prevented from becoming unsuitable due to an unsuitable composition in the mixed refrigerant circulating in the refrigerant circuit 10 caused by an increased proportion of the first refrigerant.

[0090] <Third Implementation Method> (9) Overall structure The air conditioner 1 of the third embodiment differs in structure from the air conditioner 1 of the first embodiment in that the component adjustment mechanism 100 is the same, but otherwise the structure is identical. The air conditioner 1 of the third embodiment includes the component adjustment mechanism 100, such as... Figure 7 As shown, the third embodiment includes an extraction mechanism 130, which differs from the extraction mechanism 110 of the first embodiment. The structure of the air conditioner 1 in the third embodiment, except for the extraction mechanism 130, is the same as that of the air conditioner 1 in the first embodiment. Therefore, the structure of the air conditioner 1 in the third embodiment, except for the extraction mechanism 130, is the same as that described in (1-2) above. Furthermore, the operation of the air conditioner 1 in each mode of the third embodiment is also the same as that described in (1-3) above. Additionally, the non-azeotropic refrigerant used in the air conditioner 1 of the third embodiment can also be the same non-azeotropic refrigerant described in (1-1) above.

[0091] (10) Structure and operation of the extraction mechanism 130 The storage tank 20 of the air conditioner 1 in the third embodiment, such as Figure 7As shown, an outlet pipe 23 is provided at an outlet 20e in the storage tank 20 and connected to a first flow path P1. The outlet pipe 23 has an outlet end 23e connected to the suction port of the compressor 11, an inlet end 23i located inside the storage tank 20, and a U-shaped portion 23u that makes a U-turn below the inlet end 23i in the direction of gravity. The extraction mechanism 130 is an opening 23h formed at a predetermined location in the U-shaped portion 23u located in the liquid storage section 21. The opening 23h is preferably positioned near the lowermost part of the liquid storage section 21. Liquid non-azeotropic refrigerant mixture accumulated in the liquid storage section 21 enters the outlet pipe 23 through the opening 23h. The non-azeotropic refrigerant mixture entering the outlet pipe 23 through the opening 23h is drawn out through the outlet pipe 23 to the first flow path P1 for extraction from the storage tank 20.

[0092] (11) Variation (11-1) Variation 3A The extraction mechanism 130 of the third embodiment can also be combined with the extraction mechanism 110 of the first embodiment or the extraction mechanism 120 of the second embodiment. In the extraction mechanism 130 of the third embodiment, for example, it can be configured such that the height position of the part that makes the extraction mechanism 110 or 120 extract the part along the direction of gravity is different from the height position of the opening 23h of the extraction mechanism 130.

[0093] (11-2) Variation 3B The case where the opening 23h of the outlet pipe 23 is formed in the U-shaped portion 23u in the third embodiment of the extraction mechanism 130 has been described. However, the shape of the outlet pipe 23 is not limited to having a U-shaped portion 23u. For example, as Figure 8A As shown, the outlet pipe 23 can also be I-shaped. The I-shaped outlet pipe 23 is installed on the outlet 20e located on the bottom surface 20b of the storage tank 20. The non-azeotropic refrigerant mixture in the outlet pipe 23 flows downwards from the bottom surface 20b in the direction of gravity. The extraction mechanism 130 is formed in the opening 23h of the I-shaped outlet pipe 23, and the opening 23h is located in the liquid storage section 21. Furthermore, as... Figure 8B As shown, the outlet pipe 23 can also be L-shaped. The L-shaped outlet pipe 23 is installed on the outlet 20e located on the side 20s of the storage tank 20. The non-azeotropic refrigerant mixture in the outlet pipe 23 flows from the side 20s in a horizontal direction orthogonal to the direction of gravity. The extraction mechanism 130 is formed in the opening 23h of the L-shaped outlet pipe 23, which is located in the liquid storage section 21. More specifically, the opening 23h is formed at the corner of the L-shaped outlet pipe 23.

[0094] (12) Features In the air conditioner 1 of the third embodiment and modifications 3A and 3B, an opening 23h is formed at a predetermined location on the outlet pipe 23 located in the liquid storage section 21. The liquid non-azeotropic refrigerant mixture, as a mixed refrigerant circulating in the refrigerant circuit 10, can return to the first flow path P1 through the opening 23h formed at this predetermined location. Specifically, the air conditioner 1 of the third embodiment and modifications 3A and 3B can draw the liquid non-azeotropic refrigerant mixture into the first flow path P1 through the U-shaped portion 23u, the I-shaped outlet pipe 23, or the opening 23h of the L-shaped outlet pipe 23. This suppresses the accumulation of large amounts of liquid non-azeotropic refrigerant mixture in the liquid storage section 21 of the storage tank 20. As a result, it is possible to suppress the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor 11. Thus, by suppressing the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor 11, the risk of disproportionation reaction can be prevented. Furthermore, the air conditioner 1 in the third embodiment and the modified example 3A is an example of a heat pump device.

[0095] Furthermore, if the first refrigerant is flammable, by suppressing the increase in the proportion of the first refrigerant, the flammability of the mixed refrigerant circulating in the refrigerant circuit 10 can be prevented from increasing. Furthermore, by suppressing the increase in the proportion of the first refrigerant, the efficiency and capacity of the air conditioner 1 can be prevented from decreasing due to an unsuitable composition in the mixed refrigerant circulating in the refrigerant circuit 10 caused by an increased proportion of the first refrigerant. Furthermore, by suppressing the increase in the proportion of the first refrigerant, the ability to precisely control the air conditioner 1 can be prevented from becoming unsuitable due to an unsuitable composition in the mixed refrigerant circulating in the refrigerant circuit 10 caused by an increased proportion of the first refrigerant.

[0096] <Fourth Implementation> (13) Overall structure The air conditioner 1 of the fourth embodiment differs in structure from the air conditioner 1 of the first embodiment in that the component adjustment mechanism 100 is the same, but otherwise the structure is identical. The air conditioner 1 of the fourth embodiment includes the component adjustment mechanism 100, as follows: Figure 9A as well as Figure 9B As shown, it includes a stirring mechanism 140, which is different from the extraction mechanism 110 of the first embodiment. The structure of the air conditioner 1 in the fourth embodiment, excluding the stirring mechanism 140, is the same as that in the first embodiment. Therefore, the structure of the air conditioner 1 in the fourth embodiment, excluding the stirring mechanism 140, is the same as that described in (1-2) above. Furthermore, the operation of the air conditioner 1 in each mode of the fourth embodiment, excluding the stirring mechanism 140, is also the same as that described in (1-3) above. Additionally, the non-azeotropic refrigerant used in the air conditioner 1 of the fourth embodiment can also be the same non-azeotropic refrigerant described in (1-1) above.

[0097] (14) Structure and operation of stirring mechanism 140 The composition adjustment mechanism 100 of the fourth embodiment, such as Figure 9A as well as Figure 9B As shown, a stirring mechanism 140 is included in the stirring tank 20 for a non-azeotropic refrigerant mixture. The tank 20 of the fourth embodiment has an inlet pipe 24 for the non-azeotropic refrigerant mixture to flow into its interior. The stirring mechanism 140 is a structure provided near the inner wall 25 of the tank 20, near the inlet pipe 24. The inlet pipe 24 of the stirring mechanism 140 is structured to spray the non-azeotropic refrigerant mixture along the inner wall 25 of the tank 20 in a direction intersecting the direction of gravity. More specifically, the inner wall 25 is annular when viewed from above, and the spray direction of the inlet pipe 24 is tangential to the annular inner wall 25. By spraying the non-azeotropic refrigerant mixture along the inner wall 25 in a direction intersecting the direction of gravity, a swirling flow is generated in the tank 20. This swirling flow promotes the evaporation of the liquid non-azeotropic refrigerant mixture contained in the non-azeotropic refrigerant mixture sprayed from the inlet pipe 24 into the tank 20. Ideally, the mixed refrigerant injected from the inlet pipe 24 should swirl for as long as possible. Therefore, the inlet pipe 24 should, for example, spray out in a direction slightly above horizontal.

[0098] With the stirring mechanism 140, the liquid refrigerant mixture entering from the inlet pipe 24 evaporates and does not accumulate in the storage tank 20. In other words, the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture flowing out from the outlet pipe 23 of the storage tank 20 does not increase.

[0099] (15) Variations (15-1) Variation 4A The stirring mechanism 140 of the fourth embodiment can be combined with the extraction mechanism 110, 120, 130 of the first, second or third embodiment.

[0100] (16) Features In the air conditioner 1 of the fourth embodiment and variation 4A, the stirring mechanism 140 is a structure that sprays the non-azeotropic refrigerant mixture from the inlet pipe 24 along the inner wall 25 of the storage tank 20 in a direction intersecting with the direction of gravity. In the stirring mechanism 140, a swirling flow of the non-azeotropic refrigerant mixture can occur along the inner wall of the storage tank. This swirling flow promotes the evaporation of the liquid non-azeotropic refrigerant mixture, making it difficult for the liquid second refrigerant to remain in the storage tank 20. As a result, the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor 11 can be suppressed. Thus, by suppressing the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor 11, the risk of increased disproportionation reaction can be prevented. Furthermore, the air conditioner 1 of the fourth embodiment and variation 4A is an example of a heat pump device.

[0101] Furthermore, if the first refrigerant is flammable, by suppressing the increase in the proportion of the first refrigerant, the flammability of the mixed refrigerant circulating in the refrigerant circuit 10 can be prevented from increasing. Furthermore, by suppressing the increase in the proportion of the first refrigerant, the efficiency and capacity of the air conditioner 1 can be prevented from decreasing due to an unsuitable composition in the mixed refrigerant circulating in the refrigerant circuit 10 caused by an increased proportion of the first refrigerant. Furthermore, by suppressing the increase in the proportion of the first refrigerant, the ability to precisely control the air conditioner 1 can be prevented from becoming unsuitable due to an unsuitable composition in the mixed refrigerant circulating in the refrigerant circuit 10 caused by an increased proportion of the first refrigerant.

[0102] <Fifth Implementation> (17) Overall structure The air conditioner 1 of the fifth embodiment differs in structure from the air conditioner 1 of the first embodiment in that the component adjustment mechanism 100 is the same, except for the structure itself. The air conditioner 1 of the fifth embodiment includes the component adjustment mechanism 100, as follows: Figure 10 As shown, the fifth embodiment includes a stirring mechanism 150, which differs from the extraction mechanism 110 of the first embodiment. The structure of the air conditioner 1 in the fifth embodiment, excluding the stirring mechanism 150, is the same as that in the first embodiment. Therefore, the structure of the air conditioner 1 in the fifth embodiment, excluding the stirring mechanism 150, is the same as that described in (1-2) above. Furthermore, the operation of the air conditioner 1 in the fifth embodiment under each mode, excluding the stirring mechanism 150, is also the same as that described in (1-3) above. Additionally, the non-azeotropic refrigerant used in the air conditioner 1 of the fifth embodiment can also be the same non-azeotropic refrigerant described in (1-1) above.

[0103] (18) Structure and operation of stirring mechanism 150 The fifth embodiment includes a component adjustment mechanism 100, such as... Figure 10As shown, a stirring mechanism 150 is included in the stirring tank 20 for a non-azeotropic refrigerant mixture. The stirring mechanism 150 includes a refrigerant inlet flow path 35 for supplying the non-azeotropic refrigerant mixture within the tank 20. The refrigerant inlet flow path 35 is connected to a spray outlet 35a within the tank 20. The refrigerant inlet flow path 35 is connected to an inlet 35b at a point in the refrigerant circuit where the pressure is higher than the pressure in the tank 20. Specifically, it is connected to the flow path connecting the first heat exchanger 12 and the first expansion valve 13. In the flow path connecting the first heat exchanger 12 and the first expansion valve 13, the high-pressure non-azeotropic refrigerant mixture compressed by the compressor 11 flows. The spray outlet 35a of the refrigerant inlet flow path 35 is preferably connected to the liquid storage section 21 of the tank 20. Furthermore, the spray outlet 35a is preferably connected to the bottom of the liquid storage section 21. A flow regulating valve 36 is provided in the refrigerant inlet flow path 35. If a non-azeotropic refrigerant mixture is allowed to flow from the refrigerant inlet flow path 35 to the storage tank 20, circulation of the refrigerant mixture, unrelated to heat transfer, will occur, resulting in reduced efficiency. To suppress this efficiency reduction, for example, if liquid non-azeotropic refrigerant mixture accumulates in the storage tank 20, the flow control valve 36 is opened to introduce high-pressure non-azeotropic refrigerant mixture into the storage tank 20. To introduce high-pressure non-azeotropic refrigerant mixture at the appropriate time, such as... Figure 11 As shown, the flow regulating valve 36 is controlled by the controller 90. Alternatively, when the liquid non-azeotropic refrigerant mixture in the storage tank 20 is in a state where it is prone to accumulating, the flow regulating valve 36 is opened to introduce the high-pressure non-azeotropic refrigerant mixture into the storage tank 20. To open the flow regulating valve 36 when the liquid non-azeotropic refrigerant mixture in the storage tank 20 is in a state where it is prone to accumulating, as shown... Figure 11 As shown, the flow regulating valve 36 is controlled by the controller 90. To store the appropriate timing in the controller 90, information related to the appropriate timing can be obtained in advance, for example, through experiments or simulations using actual equipment.

[0104] By introducing the high-pressure mixed refrigerant from refrigerant circuit 10 into storage tank 20, the non-azeotropic mixed refrigerant is stirred within storage tank 20. The stirring of the non-azeotropic mixed refrigerant in storage tank 20 facilitates the evaporation of the liquid non-azeotropic mixed refrigerant. Through this stirring mechanism 150, the liquid non-azeotropic mixed refrigerant in storage tank 20 evaporates without accumulating in storage tank 20. In other words, the proportion of the first refrigerant included in the non-azeotropic mixed refrigerant flowing out of outlet pipe 23 of storage tank 20 does not increase.

[0105] (19) Variation (19-1) Variation 5A The stirring mechanism 150 of the fifth embodiment can be combined with the extraction mechanisms 110, 120, and 130 of the first, second, or third embodiments. Furthermore, the stirring mechanism 150 of the fifth embodiment can also be combined with the stirring mechanism 140 of the fourth embodiment.

[0106] (20) Features In the air conditioner 1 of the fifth embodiment and modification 5A, the high-pressure, non-azeotropic refrigerant mixture sprayed from the refrigerant inlet flow path 35 into the storage tank 20 agitates the non-azeotropic refrigerant mixture in the storage tank 20. This promotes the evaporation of the liquid non-azeotropic refrigerant mixture in the storage tank 20, making it difficult for the liquid second refrigerant to remain in the storage tank 20. As a result, it is possible to suppress the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor 11. Thus, by suppressing the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor 11, the risk of increased disproportionation reaction can be prevented. Furthermore, the air conditioner 1 of the fifth embodiment and modification 5A is an example of a heat pump device.

[0107] Furthermore, if the first refrigerant is flammable, by suppressing the increase in the proportion of the first refrigerant, the flammability of the mixed refrigerant circulating in the refrigerant circuit 10 can be prevented from increasing. Furthermore, by suppressing the increase in the proportion of the first refrigerant, the efficiency and capacity of the air conditioner 1 can be prevented from decreasing due to an unsuitable composition in the mixed refrigerant circulating in the refrigerant circuit 10 caused by an increased proportion of the first refrigerant. Furthermore, by suppressing the increase in the proportion of the first refrigerant, the ability to precisely control the air conditioner 1 can be prevented from becoming unsuitable due to an unsuitable composition in the mixed refrigerant circulating in the refrigerant circuit 10 caused by an increased proportion of the first refrigerant.

[0108] <Sixth Implementation Method> (21) Overall structure The air conditioner 1 of the sixth embodiment differs in structure from the air conditioner 1 of the first embodiment in that the component adjustment mechanism 100 is the same, but otherwise the structure is identical. The air conditioner 1 of the sixth embodiment includes the component adjustment mechanism 100, as follows: Figure 12 as well as Figure 13As shown, it includes a bypass section 160, which is different from the extraction mechanism 110 of the first embodiment. The structure of the air conditioner 1 in the sixth embodiment, except for the bypass section 160, is the same as that in the first embodiment. Therefore, the structure of the air conditioner 1 in the sixth embodiment, except for the bypass section 160, is the same as that described in (1-2) above. Furthermore, the operation of the air conditioner 1 in the sixth embodiment under each mode, except for the bypass section 160, is also the same as that described in (1-3) above. Additionally, the non-azeotropic refrigerant used in the air conditioner 1 of the sixth embodiment can also be the same non-azeotropic refrigerant described in (1-1) above.

[0109] (22) Structure and operation of bypass section 160 The fifth embodiment includes a component adjustment mechanism 100, such as... Figure 12 As shown, the system includes a bypass section 160 that bypasses the storage tank 20. The bypass section 160 consists of a bypass flow path 40 connected to the first flow path P1 and the second flow path P2, bypassing the storage tank 20; an on / off valve 41 that opens and closes the bypass flow path 40; and a controller 90 that controls the on / off valve 41. The on / off valve 41 is an electrically operated valve that opens and closes based on a control signal from the controller 90. The controller 90 controls the opening and closing of the on / off valve 41 when a specified amount of liquid non-azeotropic refrigerant mixture returns to the suction port 11a of the compressor 11, or when the humidity is lower than a specified value. Through this control, the non-azeotropic refrigerant mixture, including the liquid non-azeotropic refrigerant mixture at a level that prevents compressor 11 from malfunctioning, does not return to the suction port 11a of the compressor 11 via the storage tank 20. When the on / off valve 41 is open, the amount of liquid non-azeotropic refrigerant mixture separated in the storage tank 20 is reduced compared to the case where the bypass section 160 is not provided. Through the operation of the bypass section 160, the amount of liquid non-azeotropic refrigerant mixture accumulated in the storage tank 20 is reduced. In other words, the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture flowing out of the storage tank 20 will not increase.

[0110] In addition, the prescribed operation of opening and closing the valve 41 and the timing of opening and closing are determined in advance, for example, by experimentation using actual equipment or by simulation, and stored in the controller 90.

[0111] (23) Variation (23-1) Variation 6A The bypass portion 160 of the sixth embodiment can be combined with the extraction mechanisms 110, 120, and 130 of the first, second, or third embodiments. Furthermore, the bypass portion 160 of the sixth embodiment can also be combined with the stirring mechanisms 140 and 150 of the fourth or fifth embodiments.

[0112] (23-2) Variation 6B In the sixth embodiment, an on / off valve 41 that is electrically operated is used, but as an alternative to the on / off valve 41, an electric valve capable of changing the opening degree can also be used.

[0113] (24) Features In the air conditioner 1 of the sixth embodiment and its modifications 6A and 6B, the result of control by the controller 90, which serves as the control unit, is that during a predetermined operating period, the non-azeotropic refrigerant mixture flows through the bypass flow path 40 instead of the storage tank 20. During this predetermined operating period, if it flows through the storage tank 20 instead of the bypass flow path 40, the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture flowing from the storage tank 20 to the first flow path P1 increases. By allowing the non-azeotropic refrigerant mixture to flow from the second flow path P2 to the first flow path P1 via the bypass flow path 40 during the predetermined operating period, the accumulation of the second refrigerant in the storage tank 20 during the predetermined operating period can be prevented. This suppresses the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor. Consequently, the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor 11 can be suppressed. Thus, by suppressing the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor 11, the risk of an increased disproportionation reaction can be prevented. Furthermore, the air conditioner 1 in the sixth embodiment and variations 6A and 6B is an example of a heat pump device.

[0114] Furthermore, if the first refrigerant is flammable, by suppressing the increase in the proportion of the first refrigerant, the flammability of the mixed refrigerant circulating in the refrigerant circuit 10 can be prevented from increasing. Furthermore, by suppressing the increase in the proportion of the first refrigerant, the efficiency and capacity of the air conditioner 1 can be prevented from decreasing due to an unsuitable composition in the mixed refrigerant circulating in the refrigerant circuit 10 caused by an increased proportion of the first refrigerant. Furthermore, by suppressing the increase in the proportion of the first refrigerant, the ability to precisely control the air conditioner 1 can be prevented from becoming unsuitable due to an unsuitable composition in the mixed refrigerant circulating in the refrigerant circuit 10 caused by an increased proportion of the first refrigerant.

[0115] <Seventh Implementation> (25) Overall structure The air conditioner 1 of the seventh embodiment differs in structure from the air conditioner 1 of the first embodiment in that the component adjustment mechanism 100 is the same, but otherwise the structure is identical. The air conditioner 1 of the seventh embodiment includes the component adjustment mechanism 100, as follows: Figure 14As shown, it includes the extraction mechanism 110 of the first embodiment and the internal heat exchanger 45. The structure of the air conditioner 1 of the seventh embodiment is the same as that of the air conditioner 1 of the first embodiment, except for the internal heat exchanger 45. Therefore, the structure of the air conditioner 1 of the seventh embodiment, except for the internal heat exchanger 45, is the same as that described in (1-2) above. Furthermore, the operation of the air conditioner 1 of the seventh embodiment in each mode, except for the internal heat exchanger 45, is also the same as that described in (1-3) above. In addition, the non-azeotropic refrigerant used in the air conditioner 1 of the seventh embodiment can also be the same non-azeotropic refrigerant described in (1-1) above.

[0116] (26) Structure and operation of internal heat exchanger 45 like Figure 14 As shown, the composition adjustment structure 100 of the seventh embodiment includes an internal heat exchanger 45 that performs heat exchange on the non-azeotropic refrigerant mixture flowing in the first flow path P1 and heats the non-azeotropic refrigerant mixture. Here, the internal heat exchanger 45 performs heat exchange between the non-azeotropic refrigerant mixture flowing from the first heat exchanger to the first expansion valve 13 and the non-azeotropic refrigerant mixture flowing to the first flow path P1. After the liquid non-azeotropic refrigerant mixture in the storage tank 20 is merged in the first flow path P1, the superheat of the mixed refrigerant mixture being drawn into the compressor 11 can be increased by heating the non-azeotropic refrigerant mixture flowing in the first flow path P1. By increasing the superheat after the liquid non-azeotropic refrigerant mixture is merged in the first flow path P1, the liquid non-azeotropic refrigerant mixture is vaporized, thereby preventing a large amount of liquid refrigerant from being drawn into the compressor 11. Through this action, compared to the case where the internal heat exchanger 45 is not provided, a large amount of liquid non-azeotropic refrigerant mixture can be returned from the storage tank 20 to the first flow path P1. By providing such an internal heat exchanger 45, the amount of liquid non-azeotropic refrigerant mixture in the storage tank 20 can be easily reduced. In other words, compared to the air conditioner 1 of the first embodiment, the air conditioner 1 of the second embodiment can more easily suppress the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture flowing out of the outlet 20e of the storage tank 20.

[0117] (27) Variation (27-1) Variation 7A The composition adjustment mechanism 100 of the seventh embodiment has been described with the inclusion of a take-out mechanism 110 and an internal heat exchanger 45. However, the take-out mechanism provided together with the internal heat exchanger 45 is not limited to the take-out mechanism 110 of the first embodiment. The composition adjustment mechanism 100 of the seventh embodiment may also be configured by combining the take-out mechanisms 120, 130 of the second or third embodiment with the internal heat exchanger 45. Furthermore, the composition adjustment mechanism 100 of the seventh embodiment may also combine the stirring mechanisms 140, 150 of the fourth or fifth embodiment with the internal heat exchanger 45. In addition, the composition adjustment mechanism 100 of the seventh embodiment may also be configured by incorporating the internal heat exchanger 45 into the composition adjustment mechanism 100 of the sixth embodiment.

[0118] (28) Features In the air conditioner 1 of the seventh embodiment and variation 7A, since the non-azeotropic refrigerant flowing to the first flow path P1 in the internal heat exchanger 45 is heated, at least a portion of the liquid non-azeotropic refrigerant flowing in the first flow path P1 is vaporized. Because at least a portion of the liquid non-azeotropic refrigerant is vaporized, the proportion of liquid non-azeotropic refrigerant drawn into the compressor 11 is reduced, thus reducing the risk of the compressor 11 malfunctioning due to drawing in a large amount of liquid non-azeotropic refrigerant. Therefore, compared to the case without the internal heat exchanger 45, more liquid non-azeotropic refrigerant can flow from the storage tank 20 to the first flow path P1, and the liquid second refrigerant becomes less likely to remain in the storage tank 20. As a result, the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant discharged from the compressor 11 can be suppressed. Thus, by suppressing the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant discharged from the compressor 11, the risk of an increased disproportionation reaction can be prevented. Furthermore, the air conditioner 1 in the seventh embodiment and the modified example 7A is an example of a heat pump device.

[0119] Furthermore, if the first refrigerant is flammable, by suppressing the increase in the proportion of the first refrigerant, the flammability of the mixed refrigerant circulating in the refrigerant circuit 10 can be prevented from increasing. Furthermore, by suppressing the increase in the proportion of the first refrigerant, the efficiency and capacity of the air conditioner 1 can be prevented from decreasing due to an unsuitable composition in the mixed refrigerant circulating in the refrigerant circuit 10 caused by an increased proportion of the first refrigerant. Furthermore, by suppressing the increase in the proportion of the first refrigerant, the ability to precisely control the air conditioner 1 can be prevented from becoming unsuitable due to an unsuitable composition in the mixed refrigerant circulating in the refrigerant circuit 10 caused by an increased proportion of the first refrigerant.

[0120] <Eighth Implementation Method> (29) Overall structure The air conditioner 1 of the eighth embodiment differs in structure from the air conditioner 1 of the first embodiment in that the adjustment mechanism 100 is structurally different, but otherwise the structures are the same. For example... Figure 15 As shown, the air conditioner 1 of the eighth embodiment includes a composition adjustment mechanism 100 comprising a liquid refrigerant detection sensor 81 for detecting the liquid non-azeotropic refrigerant mixture accumulated in the storage tank 20. Except for the liquid refrigerant detection sensor 81, the structure of the air conditioner 1 of the eighth embodiment is the same as that of the air conditioner 1 of the first embodiment. Therefore, the structure of the air conditioner 1 of the eighth embodiment, except for the structure of the liquid refrigerant detection sensor 81, is the same as that described in (1-2) above. Furthermore, the operation of the air conditioner 1 of the eighth embodiment in each mode, excluding the liquid refrigerant detection sensor 81, is also the same as that described in (1-3) above. Additionally, the non-azeotropic refrigerant mixture used in the air conditioner 1 of the eighth embodiment can also be the same non-azeotropic refrigerant mixture described in (1-1) above.

[0121] (30) Structure and operation of liquid refrigerant detection sensor 81 The composition adjustment mechanism 100 of the eighth embodiment includes a control unit, which has a control function for the refrigerant circuit 10 (see reference). Figure 1 The equipment related to the non-azeotropic refrigerant mixture in the compressor 11 and the improvement at the suction port 11a of the compressor 11 (see reference) Figure 1 The prescribed pattern for the intake superheat at ( ). More specifically, such as Figure 14 As shown, the composition adjustment mechanism 100 of the eighth embodiment consists of a controller 90 as a control unit, a liquid refrigerant detection sensor 81, a first expansion valve 13, and a second expansion valve 16. In the composition adjustment mechanism 100 of the eighth embodiment, if the liquid refrigerant detection sensor 81 detects the accumulation of liquid non-azeotropic refrigerant mixture in the storage tank 20, the controller 90 switches to a predetermined mode. If the controller 90 switches to the predetermined mode, control is performed to increase the suction superheat at the suction port 11a of the compressor 11 compared to before the switch. If the controller 90 switches to the predetermined mode, in the heating mode, the suction superheat at the suction port 11a of the compressor 11 is increased by reducing the opening of the first expansion valve 13 to reduce the flow rate of the mixed refrigerant to the second heat exchanger 14. If the controller 90 switches to the predetermined mode, in the cooling mode and the dehumidification heating mode, the suction superheat at the suction port 11a of the compressor 11 is increased by reducing the opening of the second expansion valve 16 to reduce the flow rate of the mixed refrigerant to the third heat exchanger 17.

[0122] By switching to a predetermined mode and increasing the suction superheat of compressor 11 through controller 90, the amount of liquid non-azeotropic refrigerant entering storage tank 20 can be reduced compared to before switching to the predetermined mode. Alternatively, by switching to a predetermined mode and increasing the suction superheat of compressor 11 through controller 90, the amount of liquid non-azeotropic refrigerant accumulated in storage tank 20 can be reduced compared to before switching to the predetermined mode.

[0123] (31) Variation Example (31-1) Variation 8A The composition adjustment mechanism 100 of the eighth embodiment can also be combined with the extraction mechanisms 110, 120, and 130 of the first, second, or third embodiments. Furthermore, the composition adjustment mechanism 100 of the eighth embodiment can also be combined with the stirring mechanisms 140 and 150 of the fourth or fifth embodiments. Additionally, the composition adjustment mechanism 100 of the eighth embodiment can also be combined with the composition adjustment mechanism 100 of the sixth or seventh embodiment.

[0124] (31-2) Variation 8B In the component adjustment mechanism 100 of the eighth embodiment, the controller 90 determines the time of switching to a predetermined mode using a liquid refrigerant detection sensor 81. However, the time of switching to the predetermined mode can also be determined by using a method other than the liquid refrigerant detection sensor 81. For example, if the controller is configured to determine the time of switching to the predetermined mode by using various sensors 80 used in existing air conditioners other than the liquid refrigerant sensor 81 through prior experimentation with actual equipment, the liquid refrigerant detection sensor 81 can be omitted.

[0125] (32) Features In the air conditioner 1 of the eighth embodiment and modifications 8A and 8B, when liquid non-azeotropic refrigerant mixture accumulates in the storage tank 20, the controller 90, which is a control unit, switches to a predetermined mode. By switching the controller 90 to the predetermined mode, the suction superheat at the suction port 11a of the compressor 11 can be increased. Due to the increase in suction superheat, it becomes difficult for liquid non-azeotropic refrigerant mixture to accumulate in the storage tank 20, and the air conditioner 1 can suppress the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor 11. In this way, by suppressing the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor 11, the risk of disproportionation reaction can be prevented. In addition, the air conditioner 1 of the eighth embodiment and modifications 8A and 8B is an example of a heat pump device.

[0126] Furthermore, if the first refrigerant is flammable, by suppressing the increase in the proportion of the first refrigerant, the flammability of the mixed refrigerant circulating in the refrigerant circuit 10 can be prevented from increasing. Furthermore, by suppressing the increase in the proportion of the first refrigerant, the efficiency and capacity of the air conditioner 1 can be prevented from decreasing due to an unsuitable composition in the mixed refrigerant circulating in the refrigerant circuit 10 caused by an increased proportion of the first refrigerant. Furthermore, by suppressing the increase in the proportion of the first refrigerant, the ability to precisely control the air conditioner 1 can be prevented from becoming unsuitable due to an unsuitable composition in the mixed refrigerant circulating in the refrigerant circuit 10 caused by an increased proportion of the first refrigerant.

[0127] <Ninth Implementation Method> (33) Overall structure Figure 16 The diagram illustrates an example of the structure of the air conditioner 1 according to the ninth embodiment. Figure 1 and Figure 16 A comparison reveals that the air conditioner 1 of the ninth embodiment differs from the air conditioner 1 of the first embodiment in that it includes a receiver 48 as a replacement for the storage tank 20, but otherwise the structures are the same. In other words, the structure of the air conditioner 1 of the ninth embodiment is a structure in which the storage tank 20 is removed and the receiver 48 is installed from the structure of the air conditioner 1 of the first embodiment.

[0128] The structure of the air conditioner 1 in the ninth embodiment, excluding the receiver 48, is the same as that of the air conditioner 1 in the first embodiment, excluding the storage tank 20. Therefore, the structure of the air conditioner 1 in the ninth embodiment, excluding the receiver 48, is the same as that described in (1-2) above, excluding the storage tank 20. For example, the three-way valve 15 switches between a state where the second heat exchanger 14 is connected to the suction port 11a of the compressor 11 and a state where the second heat exchanger 14 is connected to the second expansion valve 16. When the three-way valve 15 is connected to the suction port 11a of the compressor 11, the second expansion valve 16 is closed, so no mixed refrigerant flows from the three-way valve 15 through the second expansion valve 16 and the third heat exchanger 17 to the suction port 11a of the compressor 11. When the three-way valve 15 is connected to the second heat exchanger 14 through the second expansion valve 16, the mixed refrigerant flows from the three-way valve 15 through the second expansion valve 16 and the third heat exchanger 17 to the suction port 11a of the compressor 11. In addition, the mixed refrigerant flowing out of the first heat exchanger 12 flows to the first expansion valve 13 via the receiver 48.

[0129] Furthermore, the operation of the air conditioner 1 in each mode of the ninth embodiment, except for the receiver 48, is the same as the operation described in (1-3) above, except for the storage tank 20. For example, in the first path of the heating mode, the mixed refrigerant flows sequentially through the compressor 11, the first heat exchanger 12, the receiver 48, the first expansion valve 13, the second heat exchanger 14, the three-way valve 15, and the compressor 11.

[0130] In the second path of cooling mode and dehumidification and heating mode, the mixed refrigerant flows sequentially through compressor 11, first heat exchanger 12, receiver 48, first expansion valve 13, second heat exchanger 14, three-way valve 15, second expansion valve 16, third heat exchanger 17 and compressor 11.

[0131] In heating mode, the gaseous refrigerant mixture is drawn into and compressed through the suction port of compressor 11 in the first path. The compressed gaseous refrigerant mixture in compressor 11 is discharged from the discharge port 11b of compressor 11. The refrigerant mixture discharged from the discharge port 11b of compressor 11 is sent to the first heat exchanger 12. In heating mode, the refrigerant mixture exchanges heat with the air blown into the vehicle interior in the first heat exchanger 12. The refrigerant mixture after heat exchange in the first heat exchanger 12 enters the receiver 48, where the remaining refrigerant accumulates. The refrigerant leaving the receiver 48 is depressurized in the first expansion valve 13. The refrigerant mixture after depressurization in the first expansion valve 13 exchanges heat with the outside air in the second heat exchanger 14. The refrigerant mixture after heat exchange in the second heat exchanger 14 is drawn into compressor 11 via three-way valve 15.

[0132] In the cooling mode, the gaseous refrigerant mixture is drawn in and compressed from the suction port of compressor 11 in the second path. The compressed gaseous refrigerant mixture in compressor 11 is discharged from the discharge port 11b of compressor 11. The refrigerant mixture discharged from the discharge port 11b of compressor 11 is sent to the first heat exchanger 12. In the cooling mode, the refrigerant mixture does not undergo heat exchange in the first heat exchanger 12. After passing through the first heat exchanger 12, the refrigerant mixture enters the receiver 48, where the remaining refrigerant accumulates. The refrigerant leaving the receiver 48 passes through the fully open first expansion valve 13. The refrigerant mixture that has not been depressurized in the first expansion valve 13 exchanges heat with outside air in the second heat exchanger 14. After heat exchange in the second heat exchanger 14, the refrigerant mixture is depressurized in the second expansion valve 16 via the three-way valve 15. After depressurization in the second expansion valve 16, the refrigerant mixture that has been depressurized exchanges heat with air blown into the vehicle interior in the third heat exchanger 17. The mixed refrigerant after heat exchange in the third heat exchanger 17 is drawn into the compressor 11.

[0133] In addition, the non-azeotropic refrigerant used in the air conditioner 1 of the ninth embodiment may also be the same non-azeotropic refrigerant described in (1-1) above.

[0134] (34) Structure and operation of receiver 48 The composition adjustment mechanism 100 in the ninth embodiment is a receiver 48. It is located in the high-pressure section of the refrigerant circuit 10, where the pressure is higher than that at the suction port 11a of the compressor 11. In the ninth embodiment, the receiver 48 is positioned between the first heat exchanger 12 and the first expansion valve 13. The receiver 48 has the function of allowing the refrigerant to pass through without changing the ratio of the first and second refrigerants in the non-azeotropic refrigerant mixture. In heating mode or dehumidification heating mode, for example, the ratio of the first and second refrigerants in the liquid non-azeotropic refrigerant mixture entering the receiver 48, the liquid non-azeotropic refrigerant mixture accumulating in the receiver 48, and the liquid non-azeotropic refrigerant mixture leaving the receiver 48 is the same. Furthermore, the air conditioner 1 in the ninth embodiment does not have a storage tank 20. In this case, even if residual liquid non-azeotropic refrigerant accumulates in the receiver 48, the ratio of the first and second refrigerants in the mixed refrigerant circulating in the refrigerant circuit 10 does not change. Furthermore, even if the ratio of the first refrigerant to the second refrigerant in the mixed refrigerant accumulated in the receiver 48 changes somewhat compared to the mixed refrigerant entering and leaving the receiver 48, the impact on the composition of the mixed refrigerant circulating in the refrigerant circuit 10 is very small compared to the case where liquid non-azeotropic mixed refrigerant is accumulated in the storage tank 20.

[0135] (35) Variations (35-1) Variation 9A In the air conditioner 1 of the ninth embodiment, the case where the storage tank 20 is removed has been described. However, in the composition adjustment mechanism 100 of the ninth embodiment, which does not remove the storage tank 20 and includes the receiver 48, it may also be configured in combination with the extraction mechanisms 110, 120, and 130 of the first, second, or third embodiments. The composition adjustment mechanism 100 of the ninth embodiment may also be combined with the stirring mechanisms 140 and 150 of the fourth or fifth embodiments. Furthermore, the composition adjustment mechanism 100 of the ninth embodiment may also be combined with the composition adjustment mechanism 100 of the sixth or seventh embodiment. In addition, the stirring mechanism 100 of the ninth embodiment may also be combined with the composition adjustment mechanism 100 of the eighth embodiment.

[0136] (35-2) Variation 9B In the composition adjustment mechanism 100 of the ninth embodiment, such as Figure 17As shown, it can also be configured to include an internal heat exchanger 45. The composition adjustment mechanism 100 of the variation 9B of the ninth embodiment is as follows: Figure 17 As shown, the internal heat exchanger 45 performs heat exchange and heats the non-azeotropic refrigerant mixture drawn into the compressor 11 through the suction port 11a. Here, the internal heat exchanger 45 exchanges heat between the non-azeotropic refrigerant mixture flowing from the receiver 48 to the first expansion valve 13 and the non-azeotropic refrigerant mixture flowing into the compressor 11 before the suction port 11a. By heating the non-azeotropic refrigerant mixture flowing into the compressor 11 before the suction port 11a, the superheat of the refrigerant mixture drawn into the compressor 11 can be increased. By increasing the superheat, the liquid non-azeotropic refrigerant mixture is vaporized, thereby preventing a large amount of liquid refrigerant from being drawn into the compressor 11.

[0137] (35-3) Variation 9C In the composition adjustment mechanism 100 of the modified example 9C of the ninth embodiment, such as Figure 18 as well as Figure 19 As shown, receiver 49 is located between the second heat exchanger 14 and the second expansion valve 16. Figure 18 as well as Figure 19 As shown, when using two receivers 48 and 49, in heating mode or dehumidification heating mode, the liquid non-azeotropic refrigerant mixture accumulates in receiver 48, and in cooling mode, the liquid non-azeotropic refrigerant mixture accumulates in receiver 49. The regulating mechanism 100 is equipped with a switching mechanism including on / off valves 48a and 49a to perform this operation. In cooling mode, to prevent the non-azeotropic refrigerant mixture from flowing to receiver 48, on / off valve 48a is open. If on / off valve 48a is open, the refrigerant mixture flows around receiver 48. In cooling mode, on / off valve 49a is closed and the flow path around receiver 49 is blocked, and the liquefied refrigerant mixture in the second heat exchanger 14 passes through receiver 49.

[0138] In heating mode or dehumidification heating mode, the on / off valve 48a is closed and the on / off valve 49a is open. In this case, as described in the ninth embodiment, the liquid mixed refrigerant passes through the receiver 48. At this time, the on / off valve 49a is open, so the mixed refrigerant flows around the receiver 49, and the mixed refrigerant does not flow in the receiver 49.

[0139] (36) Features In the air conditioner 1 of the ninth embodiment and its modifications 9A, 9B, and 9C, liquid non-azeotropic refrigerant mixture can be stored in receiver 48, or in both receivers 48 and 49. Since the liquid non-azeotropic refrigerant mixture can be stored in receivers 48 and 49, the storage tank 20, which serves to store the liquid non-azeotropic refrigerant mixture, can be eliminated, for example. Changes in the ratio of the first refrigerant to the second refrigerant in the non-azeotropic refrigerant mixture are suppressed in receivers 48 and 49; therefore, the air conditioner 1 can suppress an increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor 11. Furthermore, even if a storage tank 20 is provided in the air conditioner 1 of the ninth embodiment, since the remaining refrigerant can be stored in receivers 48 and 49, it is unnecessary to store the remaining refrigerant in storage tank 20; therefore, the amount of liquid non-azeotropic refrigerant stored in storage tank 20 can be reduced. As a result, by suppressing the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from compressor 11, the risk of increased disproportionation reaction can be prevented. Furthermore, the air conditioner 1 of the ninth embodiment and its modifications 9A, 9B, and 9C is an example of a heat pump device.

[0140] Furthermore, if the first refrigerant is flammable, by suppressing the increase in the proportion of the first refrigerant, the flammability of the mixed refrigerant circulating in the refrigerant circuit 10 can be prevented from increasing. Furthermore, by suppressing the increase in the proportion of the first refrigerant, the efficiency and capacity of the air conditioner 1 can be prevented from decreasing due to an unsuitable composition in the mixed refrigerant circulating in the refrigerant circuit 10 caused by an increased proportion of the first refrigerant. Furthermore, by suppressing the increase in the proportion of the first refrigerant, the ability to precisely control the air conditioner 1 can be prevented from becoming unsuitable due to an unsuitable composition in the mixed refrigerant circulating in the refrigerant circuit 10 caused by an increased proportion of the first refrigerant.

[0141] The embodiments of this disclosure have been described above. However, it should be understood that various changes in form and detail can be made without departing from the spirit and scope of this disclosure as set forth in the claims. (Symbol Explanation)

[0142] 1. Air conditioner 1 (example of a heat pump unit); 10. Refrigerant circuit; 11 compressors; 12 First heat exchanger (example of an indoor heat exchanger); 20 storage tanks; 21 liquid storage part; 23. Outlet pipe; 23e export end; Opening at 23h; 23i entry point; 24 Inlet pipe; 30. Expansion mechanism; 34mm narrow diameter pipe; 35. Refrigerant inlet flow path; 35a nozzle; 35b inlet; 40 bypass flow paths; 41. On / off valve; 45 Internal heat exchanger; Receivers 48 and 49; 90 Controller (Example of a control unit); 100 components form an adjustment mechanism; 110, 120, 130 Removal Mechanism; 140, 150 mixing mechanism; P1 first flow path; P2 second flow path; P1a minor diameter. Existing technical documents Patent documents

[0143] Patent Document 1: Japanese Patent No. 6390431

Claims

1. A heat pump device (1), characterized in that, include: Refrigerant circuit (10), wherein the refrigerant circuit supplies a non-azeotropic mixed refrigerant for circulation, wherein the non-azeotropic mixed refrigerant includes a first refrigerant and a second refrigerant with a boiling point higher than that of the first refrigerant; Compressor (11), the compressor is disposed in the refrigerant circuit, and compresses the non-azeotropic refrigerant mixture; as well as A composition regulating mechanism (100) is disposed in the refrigerant circuit to suppress the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor. The first refrigerant is a compound represented by a molecular formula having one or more carbon-carbon unsaturated bonds. Includes a storage tank (20), which is disposed in the refrigerant circuit and has a first flow path (P1) connected to the suction port of the compressor and an outlet connected to the first flow path. The composition regulating mechanism prevents the proportion of the first refrigerant entering the compressor's suction inlet from increasing compared to the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture entering the storage tank. The storage tank has a liquid storage section (21) for storing the liquid non-azeotropic refrigerant mixture. The composition adjustment mechanism is a take-out mechanism (110, 120, 130) that connects the first flow path to the liquid storage section, takes out the liquid non-azeotropic refrigerant mixture from the liquid storage section and makes it flow out into the first flow path. The extraction mechanism (110) includes an expansion mechanism (30) for expanding the liquid non-azeotropic refrigerant flowing in the extraction mechanism.

2. A heat pump device (1), characterized in that, include: Refrigerant circuit (10), wherein the refrigerant circuit supplies a non-azeotropic mixed refrigerant for circulation, wherein the non-azeotropic mixed refrigerant includes a first refrigerant and a second refrigerant with a boiling point higher than that of the first refrigerant; Compressor (11), the compressor is disposed in the refrigerant circuit, and compresses the non-azeotropic refrigerant mixture; as well as A composition regulating mechanism (100) is disposed in the refrigerant circuit to suppress the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor. The first refrigerant is a compound represented by a molecular formula having one or more carbon-carbon unsaturated bonds. Includes a storage tank (20), which is disposed in the refrigerant circuit and has a first flow path (P1) connected to the suction port of the compressor and an outlet connected to the first flow path. The composition regulating mechanism prevents the proportion of the first refrigerant entering the compressor's suction inlet from increasing compared to the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture entering the storage tank. The storage tank has a liquid storage section (21) for storing the liquid non-azeotropic refrigerant mixture. The composition adjustment mechanism is a take-out mechanism (110, 120, 130) that connects the first flow path to the liquid storage section, takes out the liquid non-azeotropic refrigerant mixture from the liquid storage section and makes it flow out into the first flow path. The extraction mechanism (120) includes a small-diameter section (P1a) disposed in the first flow path and a narrow-diameter tube (34) connecting the liquid storage section and the small-diameter section. The smaller diameter portion has an inner diameter smaller than the inner diameter of the first flow path upstream of the smaller diameter portion and the inner diameter of the first flow path downstream of the smaller diameter portion. The narrow-diameter tube has an inner diameter smaller than that of the narrow-diameter section.

3. The heat pump device (1) as described in claim 1 or 2, characterized in that, The storage tank has an outlet pipe (23) located at the outlet and connected to the first flow path. The outlet pipe has an outlet end (23e) connected to the suction port of the compressor and an inlet end (23i) located inside the storage tank. The extraction mechanism is an opening (23h) formed at a predetermined location in the outlet pipe within the liquid storage section.

4. The heat pump device (1) as described in claim 1 or 2, characterized in that, The composition adjustment mechanism includes a stirring mechanism (140, 150) for stirring the non-azeotropic mixed refrigerant in the storage tank.

5. The heat pump device (1) as described in claim 4, characterized in that, The storage tank has an inlet pipe (24) near its inner wall to introduce the non-azeotropic refrigerant mixture into the interior. The stirring mechanism (140) is the structure of the inlet pipe that sprays the non-azeotropic refrigerant along the inner wall of the tank in a direction intersecting with the direction of gravity.

6. The heat pump device (1) as described in claim 4, characterized in that, The stirring mechanism (150) includes a refrigerant inlet flow path (35), which connects the spray outlet (35a) to the storage tank and the inlet (35b) to a part of the refrigerant circuit with a pressure higher than that in the storage tank, and allows the non-azeotropic mixed refrigerant to flow from the inlet to the spray outlet.

7. The heat pump device (1) as described in claim 1 or 2, characterized in that, The composition adjustment mechanism includes an internal heat exchanger (45) that performs heat exchange on the non-azeotropic refrigerant flowing into the first flow path and heats the non-azeotropic refrigerant.

8. A heat pump device (1), characterized in that, include: Refrigerant circuit (10), wherein the refrigerant circuit supplies a non-azeotropic mixed refrigerant for circulation, wherein the non-azeotropic mixed refrigerant includes a first refrigerant and a second refrigerant with a boiling point higher than that of the first refrigerant; Compressor (11), the compressor is disposed in the refrigerant circuit, and compresses the non-azeotropic refrigerant mixture; as well as A composition regulating mechanism (100) is disposed in the refrigerant circuit to suppress the increase in the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture discharged from the compressor. The first refrigerant is a compound represented by a molecular formula having one or more carbon-carbon unsaturated bonds. Includes a storage tank (20), which is disposed in the refrigerant circuit and has a first flow path (P1) connected to the suction port of the compressor and an outlet connected to the first flow path. The composition regulating mechanism prevents the proportion of the first refrigerant entering the compressor's suction inlet from increasing compared to the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture entering the storage tank. The refrigerant circuit has a second flow path (P2) for the flow of the non-azeotropic refrigerant mixture into the storage tank. The regulating mechanism includes: a bypass flow path (40) connected to the first flow path and the second flow path and bypassing the storage tank, an on / off valve (41) for opening and closing the bypass flow path, and a control unit (90) for controlling the on / off valve. When the storage tank is operated in a predetermined manner such that the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture flowing in the second flow path is increased compared to the proportion of the first refrigerant included in the non-azeotropic refrigerant mixture flowing in the first flow path, the control unit controls the opening and closing of the on / off valve.

9. The heat pump device (1) as described in claim 1 or 2, characterized in that, The composition adjustment mechanism includes a control unit (90) having devices for controlling the non-azeotropic refrigerant mixture in the refrigerant circuit, thereby increasing the suction superheat at the compressor inlet in a predetermined mode. When the liquid non-azeotropic refrigerant mixture accumulates in the storage tank, the control unit switches to the specified mode.

10. The heat pump device (1) as described in claim 1, 2, or 8, characterized in that, The non-azeotropic mixed refrigerant, as the first refrigerant, includes trans-1,2-difluoroethylene.

11. The heat pump device (1) as described in claim 1, 2, or 8, characterized in that, The non-azeotropic mixed refrigerant, as the first refrigerant, includes trifluoroethylene.

12. The heat pump device (1) as described in claim 1, 2, or 8, characterized in that, Includes an indoor heat exchanger (12), which is disposed in the refrigerant circuit to exchange heat between the non-azeotropic refrigerant discharged from the compressor and the air inside the electric vehicle.

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