COOLING CIRCUIT DEVICE

Abstract

A refrigeration circuit device includes a refrigerant circuit containing a compressor (101). The refrigerant circuit is enclosed with refrigerant, and the refrigerant circuit includes a component in contact with the refrigerant. A surface of the component in contact with the refrigerant contains a crystalline resin material. When the temperature of the crystalline resin material is raised at a rate of 10 °C / min using a differential pressure calorimeter, a value obtained by differentiating a quantity of heat measured by the differential pressure calorimeter with respect to time shows no exothermic peak of 20 µW / mg / min or more over a temperature range from the glass transition temperature of the crystalline resin material to its melting point.

Description

TECHNICAL FIELD

[0001] The present disclosure relates to a refrigeration cycle device. STATE OF THE ART

[0002] To ensure the reliability of a refrigeration cycle device, not only the refrigerant and refrigeration oil, which are essential to the refrigeration cycle device, but also the components used in the refrigeration cycle device must be properly designed. In particular, components such as an insulating film, an insulator, and various valves, which are generally made of resin materials that are more susceptible to wear than metal materials, must be properly designed, including the service life of the materials. The reliability and productivity of the refrigeration cycle device can be ensured by using components made of materials designed to suit the wear modes that may occur in the refrigeration cycle device.

[0003] For example, PTL 1 (Japanese Patent Laid-Open No. 2004-52730) discloses a method for improving the reliability of a sealed electric compressor by using a liquid crystal polymer resin as the material of an insulator used as an insulating member in an electric motor to improve the properties of the insulator, such as low oligomer formation and heat resistance. PTL 2 (Japanese Patent Laid-Open No. 2004-208446) discloses a method for improving productivity while ensuring reliability by using a liquid crystal polymer that has a lower latent heat of crystallization and generates a smaller amount of gas upon melting. LIST OF CITIONSPATENT LITERATURE PTL 1: Japanese Patent Application Laid-Open No. 2004-52730 PTL 2: Japanese Patent Application Laid-Open No. 2004-208446 SUMMARY OF THE INVENTION TECHNICAL PROBLEM

[0004] Conventional considerations regarding the reliability of a refrigeration cycle device have focused on using a component made of a resin material in a refrigeration cycle device. For example, by using a resin material with low oligomer formation, the generation of sludge that can clog the refrigeration cycle can be suppressed, and the component can be used for a longer period of time by improving the heat resistance and damp heat resistance of the resin material.

[0005] However, the components are used in locations where the refrigerant in the refrigeration cycle device can be in either a liquid or a gaseous state. When the liquid refrigerant absorbed into a component expands as it becomes gaseous, this causes the resin material to expand. This leads to the component's deformation, which can reduce the reliability of the refrigeration cycle device.

[0006] The present disclosure has been made in view of the above problem, and an object of the present disclosure is to provide a refrigeration cycle device whose reliability is improved by using a crystalline resin material that suppresses the occurrence of expansion in a component in contact with a refrigerant. SOLUTION TO THE PROBLEM

[0007] A refrigeration cycle device includes a refrigerant cycle including a compressor, wherein the refrigerant cycle is enclosed with refrigerant, the refrigerant cycle includes a component in contact with the refrigerant, and a surface of the component in contact with the refrigerant includes a crystalline resin material, and when a temperature of the crystalline resin material is raised at a temperature rise rate of 10 °C / min using a differential scanning calorimeter, a value obtained by differentiating a heat amount measured by the differential scanning calorimeter with respect to time does not have an exothermic peak of 20 µW / mg / min or more in a temperature range from a glass transition temperature of the crystalline resin material to a melting point thereof. ADVANTAGEOUS EFFECTS OF THE INVENTION

[0008] The reliability of the refrigeration cycle device can be improved by using a crystalline resin material that suppresses the occurrence of expansion in a component in contact with a refrigerant. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a schematic configuration diagram of an air conditioner serving as an example of a refrigeration cycle device according to an embodiment of the present disclosure; Fig. 2 is a schematic cross-sectional view illustrating an example of a compressor according to an embodiment of the present disclosure; Fig. 3 is a graph of differential scanning calorimetry values ​​on sample No. 1; Fig. 4 is a graph of time difference values ​​of differential scanning calorimetry values ​​on sample No. 1; Fig.5 is a graph of differential scanning calorimetry values ​​on sample No. 2; and Fig. Figure 6 is a graph of time difference values ​​of differential scanning calorimetry data on sample No. 2. DESCRIPTION OF EMBODIMENTS

[0009] Embodiments of the present disclosure will be described below with reference to the drawings. In the drawings, dimensions such as length, width, thickness, and depth may be appropriately modified for clarity and simplification of the drawings and may not represent actual dimensions. First embodiment

[0010] First, a sketch of a refrigeration cycle device is briefly described. Fig.1 is a schematic configuration diagram of an air conditioner serving as an example of a refrigeration cycle device according to a first embodiment. The air conditioner 100 is configured, for example, to perform air conditioning in a room of a building. The air conditioner 100 includes a compressor 101, an outdoor heat exchanger 102, a decompressor 103, an indoor heat exchanger 104, a flow path switching device 105, a refrigerant line 106, and the like. The compressor 101, the outdoor heat exchanger 102, the decompressor 103, the indoor heat exchanger 104, and the flow path switching device 105 are connected in a circular manner by the refrigerant line 106. Therefore, a refrigerant cycle is formed in which refrigerant is circulated sequentially through the compressor 101, the outdoor heat exchanger 102, the decompressor 103, the indoor heat exchanger 104 and the flow path switching device 105.

[0011] The compressor 101 is provided with a discharge port 101a and a suction port 101b and is configured to compress the refrigerant drawn from the suction port 101b into a high-temperature and high-pressure gas state and discharge it from the discharge port 101a. The decompressor 103 is configured to reduce the pressure of the refrigerant flowing through it. An electronic expansion valve, a capillary tube, or the like can be used as the decompressor 103.

[0012] Thus, a refrigerant circuit 100 is formed in the refrigeration cycle device, and the refrigerant is circulated in the refrigerant circuit 100 through liquid lines and gas lines.

[0013] A flow path connecting a first connection port 102a and a second connection port 102b is formed in the outdoor heat exchanger 102, whereby heat is exchanged between the refrigerant flowing through the flow path and the air outside the building.

[0014] A flow path connecting a first connection port 104a and a second connection port 104b is formed in the indoor heat exchanger 104, whereby heat is exchanged between the refrigerant flowing through the flow path and the air inside the building.

[0015] The flow path switching device 105 switches the flow direction of the refrigerant flowing through the refrigerant circuit. Specifically, the flow path switching device 105 is a four-way valve having four ports: a port a, a port b, a port c, and a port d.

[0016] The refrigerant line 106 is formed by a first refrigerant line 106a, a second refrigerant line 106b, a third refrigerant line 106c, a fourth refrigerant line 106d, a fifth refrigerant line 106e and a sixth refrigerant line 106f. The first refrigerant line 106a connects the outlet port 101a of the compressor 101 and the port a of the flow path switching device 105. The second refrigerant line 106b connects the port b of the flow path switching device 105 and the first connection port 102a of the outdoor heat exchanger 102. The third refrigerant line 106c connects the second connection port 102b of the outdoor heat exchanger 102 and the decompressor 103. The fourth refrigerant line 106d connects the decompressor 103 and the first connection port 104a of the indoor heat exchanger 104.The fifth refrigerant line 106e connects the second connection port 104b of the indoor heat exchanger 104 and the port c of the flow path switching device 105. The sixth refrigerant line 106f connects the port d of the flow path switching device 105 and the suction port 101b of the compressor 101.

[0017] Next, the flow of refrigerant flowing through the refrigerant circuit in the air conditioner 100 will be described. The air conditioner 100 includes two refrigerant circuits that are switched by the flow path switching device 105, that is, a refrigerant circuit during the cooling operation and a refrigerant circuit during the heating operation.

[0018] The flow of refrigerant flowing through the refrigerant circuit during cooling operation is described. Fig.Fig. 2 is a schematic cross-sectional view illustrating an example of a compressor according to the present embodiment. In the refrigerant cycle, during the cooling operation, as shown by a solid line in Fig.2, the flow path switching device 105 is in a state such that the port a and the port b are connected to each other, and the port c and the port d are connected to each other. The high-temperature and high-pressure gas refrigerant discharged from the outlet port 101a of the compressor 101 flows through the first refrigerant line 106a, the flow path switching device 105, and the second refrigerant line 106b, and then flows into the flow path inside the outdoor heat exchanger 102 from the first connection port 102a. The refrigerant flowing through the flow path inside the outdoor heat exchanger 102 is cooled by the outside air. In other words, the outdoor heat exchanger 102 functions as a condenser in the refrigerant cycle during the cooling operation.

[0019] The refrigerant cooled in the outdoor heat exchanger 102 flows out of the outdoor heat exchanger 102 from the second connection port 102b in the form of a low-temperature, high-pressure liquid. The refrigerant flowing out of the outdoor heat exchanger 102 flows into the decompressor 103 via the third refrigerant line 106c. The low-temperature, high-pressure liquid refrigerant flowing into the decompressor 103 is decompressed into a two-phase gas-liquid low-temperature, low-pressure refrigerant and flows out of the decompressor 103. The refrigerant flowing out of the decompressor 103 flows from the first connection port 104a through the fourth refrigerant pipe 106d into the flow path inside the indoor heat exchanger 104. The refrigerant flowing through the flow path inside the indoor heat exchanger 104 is heated by the indoor air.In other words, the indoor air is cooled by the refrigerant flowing through the flow path inside the indoor heat exchanger 104. In other words, the indoor heat exchanger 104 functions as an evaporator in the refrigerant cycle during cooling operation.

[0020] The refrigerant heated in the indoor heat exchanger 104 flows out of the indoor heat exchanger 104 from the second connection port 104b in the form of a high-temperature, low-pressure gas. The refrigerant flowing out of the indoor heat exchanger 104 is sucked into the compressor 101 from the suction port 101b of the compressor 101 via the fifth refrigerant line 106e, the flow path switching device 105, and the sixth refrigerant line 106f. The refrigerant sucked into the compressor 101 is again discharged from the discharge port 101a in the form of a high-temperature, high-pressure gas. As described above, as the refrigerant flows through the refrigerant cycle, the indoor air is cooled, thereby air-conditioning the room.

[0021] The flow of the refrigerant flowing through the refrigerant circuit during heating operation is described. In the refrigerant circuit, as shown by a dashed line in Fig.2, the flow path switching device 105 is in a state such that the port a and the port c are connected to each other, and the port b and the port d are connected to each other. The high-temperature and high-pressure gas refrigerant discharged from the outlet port 101a of the compressor 101 flows through the first refrigerant line 106a, the flow path switching device 105, and the fifth refrigerant line 106e, and then flows into the flow path inside the indoor heat exchanger 104 from the second connection port 104b. The refrigerant flowing through the flow path inside the indoor heat exchanger 104 is cooled by the indoor air. In other words, the indoor air is heated by the refrigerant flowing through the flow path inside the indoor heat exchanger 104. In other words, the indoor heat exchanger 104 functions as a condenser in the refrigerant cycle during the heating operation.

[0022] The refrigerant cooled in the indoor heat exchanger 104 flows out of the indoor heat exchanger 104 from the first connection port 104a in the form of a low-temperature, high-pressure liquid. The refrigerant flowing out of the indoor heat exchanger 104 flows into the decompressor 103 via the fourth refrigerant line 106d. The low-temperature, high-pressure liquid refrigerant flowing into the decompressor 103 is decompressed into a two-phase gas-liquid low-temperature, low-pressure refrigerant and flows out of the decompressor 103. The refrigerant flowing out of the decompressor 103 flows from the second connection port 102b through the third refrigerant pipe 106c into the flow path inside the outdoor heat exchanger 102. The refrigerant flowing through the flow path inside the outdoor heat exchanger 102 is heated by the outside air.In other words, the outdoor heat exchanger 102 in the refrigerant circuit acts as an evaporator during heating operation.

[0023] The refrigerant heated in the outdoor heat exchanger 102 flows out of the outdoor heat exchanger 102 from the first connection port 102a in the form of a high-temperature, low-pressure gas. The refrigerant flowing out of the outdoor heat exchanger 102 is sucked into the compressor 101 from the suction port 101b of the compressor 101 via the second refrigerant line 106b, the flow path switching device 105, and the sixth refrigerant line 106f. The refrigerant sucked into the compressor 101 is again discharged from the discharge port 101a in the form of a high-temperature, high-pressure gas. As described above, as the refrigerant flows through the refrigerant cycle, the indoor air is heated, thereby air-conditioning the room. <Kältemittel>

[0024] Next, the refrigerant enclosed in the refrigerant cycle according to the present embodiment will be described. Although the refrigerant used in the present embodiment is not particularly limited, it is preferable that the global warming potential (THP) of the refrigerant be, for example, 750 or less. This is because when the THP is 750 or less, the refrigerant has excellent environmental performance and highly complies with regulatory requirements. When the THP of the refrigerant is 750 or less, the refrigerant can be used not only in a refrigerator but also in an air conditioner as a refrigeration cycle device. The values ​​(100-year values) listed in the Fifth Assessment Report (AR5) of the Intergovernmental Panel on Climate Change (IPCC) are used as the THP.For the THP of a refrigerant not listed in AR5, a value described in any other known literature or a value calculated or measured using a known method may be used.

[0025] Examples of the refrigerant with a THP of 750 or less include R32, R454A, R454B, R454C, R466A, R513A, R290, R1234yf and the like.

[0026] The refrigerant used in the present embodiment is preferably a refrigerant classified as non-flammable, for example, in ISO 817:2014. This is because using a refrigerant classified as non-flammable eliminates the need to provide a means, equipment, or structure for diffusing the refrigerant leaking from the refrigeration cycle device, a sensor for detecting refrigerant leakage, or an alarm device for sounding an alarm when the sensor detects a refrigerant leakage. Furthermore, a refrigerant classified as non-flammable can be used in a region where the use of a flammable refrigerant is prohibited by law.

[0027] Examples of refrigerants classified as non-flammable in ISO 817:2014 include R134a, R407H, R410A, R448A, R449A, R463A, R466A, R513A, R744 and the like. <verdichter>

[0028] In the present embodiment, the refrigeration cycle device includes a compressor. The refrigerant flows through the compressor.

[0029] Fig. 2 is a schematic cross-sectional view illustrating an example of a compressor according to the present embodiment, and more specifically, a cross-sectional view of a scroll compressor cut along a cross section parallel to an axial direction of a main shaft of an engine. However, in the present embodiment, the compressor is not limited to a scroll compressor and may be a rotary compressor, a screw compressor, or the like.

[0030] The compressor 101 includes a housing 11. A compression mechanism 12 and an electric motor 13 configured to drive the compression mechanism 12 are housed in a lower space 16 within the housing 11. Furthermore, the housing 11 is connected to a suction pipe 14 for sucking the refrigerant inside the housing and a discharge pipe 15 for discharging the refrigerant from the housing.

[0031] The refrigerant sucked inward from the suction line 14 flows into the lower space 16 of the casing 11, in which the electric motor 13 and the like are housed. The refrigerant flowing into the lower space 16 flows through a gap or the like around the electric motor 13 to cool the electric motor 13, and is then sucked into the compression mechanism 12. Then, the refrigerant flows through the outlet port 12a of the compression mechanism 12 and an upper space 18 of the casing 11 and is discharged from the outlet line 15 connected to the upper space. In other words, the compression mechanism 12 is configured to compress the refrigerant flowing into the casing 11 from the suction line 14 and discharge the refrigerant from the outlet line 15.

[0032] The compression mechanism 12 is a scroll-type compression mechanism composed of teeth of a fixed scroll and teeth of an oscillating scroll. As the oscillating scroll oscillates, the refrigerant drawn through gaps between the teeth of the surrounding fixed scroll is compressed toward the center and discharged into the upper space 18 from the discharge port 12a located at the center of a fixed scroll base plate 12b. The upper space 18 and the lower space 16 are divided by the fixed scroll base plate 12b. The upper space 18 has a smaller volume than the lower space 16, and the pressure of most of the casing 11 is equal to the pressure of the drawn-in refrigerant gas. In other words, the compressor 101 is a low-pressure casing compressor.

[0033] The electric motor 13 transmits compression power to the compression mechanism 12 via a drive shaft 19. For example, a crank is arranged in the compressor 101, and the crank is configured to convert the rotation of the drive shaft 19 into an oscillating movement of the oscillating scroll.

[0034] The compressor 101 includes a main frame 20 including a bearing configured to rotatably support the drive shaft 19 in the housing 11, and a sub-frame 21 disposed below the main frame 20.

[0035] The compressor 101 includes a sliding element in the compression mechanism 12 and in the drive shaft bearing 19. To lubricate the sliding element, refrigerant oil is stored in an oil reservoir 22 located below the compressor 101. The refrigerant oil stored in the oil reservoir 22 is supplied to the sliding element in the drive shaft bearing 19 and the sliding element inside the compression mechanism 12 through an oil supply port 19a provided inside the drive shaft 19. The low-pressure casing compressor 101 is provided with an oil pump 17 installed below the drive shaft 19 to supply lubricating oil to the interior of the compression mechanism 12 through the oil supply port 19a.

[0036] The refrigeration oil used in the present embodiment is not particularly limited and may include polyol ester oil, polyvinyl ether oil, polyalkylene glycol oil, alkylbenzene oil, mineral oil, poly-α-olefin or a mixture thereof.

[0037] The refrigeration oil may contain an antioxidant, an acid scavenger, or an extreme pressure agent (an anti-wear agent) as an oil additive.

[0038] The antioxidant may include phenols such as 2,6-di-tert-butyl-4-methylphenol, 2,6-di-tert-butyl-4-ethylphenol and 2,2'-methylenebis(4-methyl-6-tert-butylphenol), or amines such as phenyl-α-naphthylamine and N,N'-diphenyl-p-phenylenediamine.

[0039] The acid scavenger may preferably include epoxy compounds such as phenyl glycidyl ether, alkyl glycidyl ether, alkylene glycol glycidyl ether, cyclohexene oxide, α-olefin oxide, epoxidized soybean oil, glycidyl ester, glycidyl ether or α-olefin oxide.

[0040] The extreme pressure agent (the antiwear agent) may include phosphorus-containing extreme pressure agents such as phosphate esters, acid phosphate esters, phosphite esters, acid phosphite esters or amine salts thereof, and may preferably include tricresyl phosphate, trithiophenyl phosphate, tri(nonylphenyl) phosphite, dioleyl hydrogen phosphite or 2-ethylhexyldiphenyl phosphite.

[0041] Since moisture in the refrigeration oil can accelerate the wear of the refrigerant, the refrigeration oil and the materials in the compressor, it is necessary to regulate the moisture content in the refrigeration oil to 100 ppm by weight or less. <komponente>

[0042] In the present embodiment, the refrigerant circuit includes a component in contact with the refrigerant. The surface of the component in contact with the refrigerant contains a crystalline resin material, which will be described later.

[0043] The component may be any resin-made component such as an insulator or an insulating film disposed in the electric motor 13, the four-way valve 105, or a check valve disposed in the refrigerant line 106.

[0044] The resin-made component may be made such that only the surface thereof in contact with the refrigerant is made of the crystalline resin material of the present embodiment, or the entire component is made of the crystalline resin material of the present embodiment. <Kristallines Harzmaterial>

[0045] In the present embodiment, the surface of a component in contact with the refrigerant contains a crystalline resin material. The crystalline resin material may include polyphenylene sulfide (PPS), polyethylene terephthalate (PET), polybutylene terephthalate (PBT), or liquid crystal polymer (LCP). According to the present embodiment, when the temperature of the crystalline resin material is raised at a temperature rise rate of 10 °C / min using a differential scanning calorimeter (DSC), a value (DDSC) obtained by differentiating a heat quantity measured by the differential scanning calorimeter with respect to time does not exhibit an exothermic peak of 20 µW / mg / min or more in a temperature range from a glass transition temperature of the crystalline resin material to a melting point thereof. The following describes the reason for using such a crystalline resin material.

[0046] The refrigerant is circulated by the compressor 101. In the refrigerant cycle, the refrigerant is in the form of a liquid or a gas. The refrigerant undergoes a phase transition from a liquid state to a gaseous state or from a gaseous state to a liquid state when the refrigeration cycle equipment is started, stopped, or switched between operating states.

[0047] The component described above is used in locations where the refrigerant may be in a liquid or gaseous state. When the refrigerant is in a liquid state, the refrigerant may be absorbed into a component made of a conventional resin material. When the absorbed liquid refrigerant undergoes a phase transition to a gaseous refrigerant, its volume increases. Accordingly, the resin material also expands, resulting in deformation of the component, which may reduce the reliability of the refrigeration cycle device.

[0048] In view of the above problem, the inventors of the present invention have extensively studied resin materials which are not expanded by the refrigerant and have consequently proposed the above-described crystalline resin material.

[0049] The crystalline resin material of the present embodiment is a resin material that has a crystalline structure but may contain an amorphous portion that does not have a crystalline structure. The crystalline state of a crystalline resin material is usually analyzed using DSC. DSC is a device capable of measuring the amount of heat released when the temperature is raised at a predefined rate. If the state of the test sample changes with increasing temperature, the sample may absorb or release heat from the surrounding environment. Therefore, a change in the state of the sample can be confirmed using DSC.

[0050] When a crystalline resin material contains an amorphous portion, crystallization of the amorphous portion occurs in a temperature range from the glass transition temperature of the crystalline resin material to its melting point during the temperature raising process (at a temperature rise rate of 10 °C / min) using DSC, and heat is generated. Therefore, if the crystalline resin material exhibits an exothermic peak during the temperature raising process by DSC, it can be confirmed that the crystalline resin material does not have a sufficient crystalline portion.

[0051] However, during the temperature rise process by DSC, although it can be confirmed that an amorphous component is present due to the presence of an exothermic peak, the absolute value of the exothermic peak varies depending on the type of crystalline resin material or the inclusion of an ingredient other than the crystalline resin material. For example, if a filler such as glass fiber is included in addition to the crystalline resin material, the exothermic peak becomes small, and it may be difficult to confirm whether the crystalline resin material contains an amorphous component.

[0052] Therefore, the inventors of the present invention have succeeded in eliminating the above-described factors using the DDSC, i.e., the value obtained by differentiating the amount of heat measured by the DSC with respect to time. A high DDSC indicates a rapid change from the initial value, which makes it possible to confirm the presence or absence of an exothermic peak.

[0053] However, in consideration of measurement noise, the crystalline resin material was used in the present embodiment when the DDSC did not exhibit an exothermic peak of 20 μW / mg / min or more in a temperature range from the glass transition temperature of the crystalline resin material to its melting point. In the present embodiment, if the DDSC exhibits an exothermic peak, as mentioned above, it means that crystallization is occurring in the amorphous portion, and thus, it can be numerically confirmed that the crystalline resin material does not have a sufficient crystalline portion. [Examples]

[0054] Hereinafter, the present disclosure will be described in more detail with reference to the examples, but the present disclosure is not limited thereto. <Bewertungstest 1>

[0055] PPS (Sample No. 1 and Sample No. 2) were prepared as test samples of the crystalline resin material. These test samples were subjected to differential scanning calorimetry using a differential scanning calorimeter (DSC6220, manufactured by Hitachi High-Tech Science Corporation) under the following conditions. The DDSC was obtained by differentiating the measured heat quantity with respect to time. The results are shown in the Fig. 3 to 6. The Fig. 3 and Fig. 5 are diagrams of differential scanning calorimetry values ​​on sample No. 1 and sample No. 2 and the Fig. 4 and Fig. Figure 6 shows the DDSC diagrams of Sample No. 1 and Sample No. 2. The glass transition temperature of PPS is 85 °C and its melting point is 280 °C. Measurement conditions Sample amount: 2 to 10 mg Atmospheric gas: nitrogen Temperature range: 50 to 300 °C Temperature rise rate: 10 °C / min

[0056] The tip that is in Fig. 3 is framed by a dashed line, represents an exothermic peak that occurred due to the crystallization of the test sample, and the upwardly convex peak that appeared in Fig. 4 is indicated by a dashed line, which corresponds to the exothermic peak. Fig. 4, it was confirmed that the DDSC of Sample No. 1 exhibited an exothermic peak of about 1050 µW / mg / min in a temperature range from the glass transition temperature to the melting point.

[0057] On the other hand, in the area that is Fig. 5 is framed by the dashed line, no exothermic peak and there is no exothermic peak in the area shown in Fig. 6 is framed by the dashed line, no upwardly convex tip. In other words, Fig. 6 confirms that the DDSC of Sample No. 2 does not exhibit an exothermic peak of 20 µW / mg / min or more in the temperature range from the glass transition temperature to the melting point.

[0058] As described above, since Sample No. 1 has an exothermic peak of 20 µW / mg / min or more in the temperature range from the glass transition temperature to the melting point thereof and Sample No. 2 does not have an exothermic peak of 20 µW / mg / min or more in the temperature range from the glass transition temperature to the melting point thereof, it was confirmed that Sample No. 1 is a PPS that does not have a sufficient crystalline content and Sample No. 2 is a PPS that has a sufficient crystalline content. <Bewertungstest 2>

[0059] Test pieces (thickness: 3 mm) were prepared from Sample No. 1 and Sample No. 2, respectively. Each test piece was impregnated with a liquid refrigerant and then subjected to a phase transition by heating, converting the liquid refrigerant into a gaseous refrigerant. This process was repeated for the number of times shown in Table 1 to measure a change in the thickness (expansion coefficient) of each test piece. The results are shown in Table 1.

[0062] [Table 1] Sample No. Number of repetitions Coefficient of expansion (%) 1 1 4 2 7 3 8 4 9 5 10 2 1 0 2 0 3 0 4 0 5 0

[0060] As shown in Table 1, the test piece of Sample No. 1 was expanded by performing the above-mentioned process once, and the expansion coefficient increased with increasing number of repetitions. In contrast, the test piece of Sample No. 2 did not expand even after performing the above-mentioned process once, and the expansion coefficient did not change even as the number of repetitions increased. <Bewertungstest 3>

[0061] In addition to the test pieces of Sample No. 1 and Sample No. 2 used in Evaluation Test 2, a test piece (Sample No. 3) with the same thickness was made of PPS. The same test as Evaluation Test 2 was repeated 5 times on the test piece of Sample No. 3 to measure its expansion coefficient. The result is shown in Table 2. The same test was repeated 5 times on the test piece of Sample No. 1 and the test piece of Sample No. 2 to measure their expansion coefficients. The DDSC of Sample No. 3, which was made of PPS, was determined under the same conditions as in Evaluation Test 1, and it was confirmed that the DDSC had an exothermic peak of about 640 µW / mg / min in the temperature range from the glass transition temperature to the melting point thereof.

[0065] [Table 2] Sample No. Coefficient of expansion (%) 1 10 2 0 3 8

[0062] Table 2 shows that the expansion coefficients of the test pieces were in the order of Sample No. 2 < Sample No. 3 < Sample No. 1. This is consistent with the magnitude of the exothermic peak in the temperature range from the glass transition temperature to the melting point for the DDSC of the PPS from which each test piece is formed. In other words, it was confirmed that there is a correlation between the magnitude of the exothermic peak and the expansion coefficient.

[0063] Based on the results of evaluation tests 1 to 3, it was confirmed that when the temperature was raised at a temperature rise rate of 10 °C / min using DSC, if the DSC did not exhibit an exothermic peak of 20 µW / mg / min or more in the temperature range from the glass transition temperature to the melting point of PPS, the test piece did not expand. Therefore, it is considered that the reliability of the entire refrigeration cycle device can be ensured by using such a crystalline resin material for a component that comes into contact with the refrigerant in the refrigeration cycle device.

[0064] It is to be understood that the embodiments and examples disclosed herein are illustrative and not restrictive in all respects. The scope of the present invention is defined by the content of the claims rather than by the above description, and is intended to include all modifications within the scope of the claims and the meaning equivalent thereto. LIST OF REFERENCE SYMBOLS

[0065] 100 Air conditioner; 101 Compressor; 101a Outlet port; 101b Suction port; 102 Outdoor heat exchanger; 102a First connection port; 102b Second connection port; 103 Decompressor; 104 Indoor heat exchanger; 104a First connection port; 104b Second connection port; 105 Flow path switching device; 106 Refrigerant pipe; 106a First refrigerant pipe; 106b Second refrigerant pipe; 106c Third refrigerant pipe; 106d Fourth refrigerant pipe; 106e Fifth refrigerant pipe; 106f Sixth refrigerant pipe; 11 Casing; 12 Compression mechanism; 12a Outlet port; 12b Base plate; 13 Electric motor; 14 Suction pipe; 15 Discharge pipe; 16 Lower space; 17 Oil pump; 18 Upper space; 19 Drive shaft; 19A Oil supply opening; 20 Main frame; 20a Bearing; 21 Subframe; 21a Subbearing; 22 Oil tank. QUOTES CONTAINED IN THE DESCRIPTION

[0000] This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions. Cited patent literature

[0000] JP 2004-52730

[0003] JP 2004-208446

[0003] < / komponente> < / verdichter>

Claims

[1] Refrigeration cycle device comprising: a refrigerant circuit containing a compressor, where the refrigerant circuit is enclosed with refrigerant, the refrigerant circuit includes a component in contact with the refrigerant, a surface of the component in contact with the refrigerant contains a crystalline resin material and, when a temperature of the crystalline resin material is raised at a temperature rise rate of 10 °C / min using a differential scanning calorimeter, a value obtained by differentiating a heat quantity measured by the differential scanning calorimeter with respect to time does not have an exothermic peak of 20 µW / mg / min or more in a temperature range from a glass transition temperature of the crystalline resin material to a melting point thereof. [2] The refrigeration cycle device according to claim 1, wherein the component is at least one selected from the group consisting of an insulator, an insulating film, a four-way valve, and a check valve. [3] The refrigeration cycle device according to claim 1 or 2, wherein the crystalline resin material is at least one selected from the group consisting of polyphenylene sulfide, polyethylene terephthalate, polybutylene terephthalate and a liquid crystal polymer.

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