JP2015214927A - Compressor, and refrigeration cycle device using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a required compressor which is more suitable for using working fluid including R1123.SOLUTION: The compressor which uses refrigerant including R1123 (1, 1, 2-trifluoroethylene), as working fluid, and uses polyvinyl ether oil as compressor lubricating oil 21 includes a compression chamber 15 bi-directionally formed by engaging a fixed scroll 12 having a spiral lap rising from an end plate and a turning scroll 11 with each other, the compression chamber having an injection hole for suppressing the disproportionation reaction of the R1123.

Description

  The present invention relates to a compressor using a working fluid containing R1123 and a refrigeration cycle apparatus using the compressor.

  In general, the refrigeration cycle apparatus comprises a compressor, a four-way valve if necessary, a radiator (or a condenser), a decompressor such as a capillary tube or an expansion valve, an evaporator, etc., and constitutes a refrigeration cycle. Cooling or heating action is performed by circulating a refrigerant inside.

  As refrigerants in these refrigeration cycle apparatuses, chlorofluorocarbons (fluorocarbons are described as ROO or ROOXX are defined by the US ASHRAE 34 standard. Hereinafter, they are indicated as ROO or RXX. ) Or halogenated hydrocarbons derived from methane or ethane are known.

  R410A is often used as the refrigerant for the refrigeration cycle apparatus as described above, but the global warming potential (GWP) of the R410A refrigerant is as large as 1730, which is problematic from the viewpoint of preventing global warming.

  Thus, from the viewpoint of preventing global warming, for example, R1123 (1,1,2-trifluoroethylene) and R1132 (1,2-difluoroethylene) have been proposed as refrigerants having a small GWP (for example, patents). Document 1 or Patent document 2).

International Publication No. 2012/157774 International Publication No. 2012/157765

  However, R1123 (1,1,2-trifluoroethylene) and R1132 (1,2-difluoroethylene) are less stable than conventional refrigerants such as R410A and disproportionate when they generate radicals. There is a possibility of changing to another compound by the reaction. Since the disproportionation reaction involves a large heat release, the reliability of the compressor and the refrigeration cycle apparatus may be reduced. For this reason, when using R1123 and R1132 for a compressor and a refrigerating cycle device, it is necessary to suppress this disproportionation reaction.

  In consideration of the above-described conventional problems, the present invention specifies, for example, a compressor that is more suitable for using a working fluid including R1123 in a compressor used for an application such as an air conditioner. is there. In addition, the lubricating oil more suitable for using the working fluid containing R1123 is specified. In addition, the present invention provides a refrigeration cycle apparatus more suitable for using a working fluid containing R1123.

  In order to solve the above-described conventional problems, the present invention uses a refrigerant containing 1,1,2-trifluoroethylene as a working fluid, uses polyvinyl ether oil as a lubricating oil for a compressor, and forms a spiral wrap from the end plate. A compression chamber formed in both directions by meshing the fixed scroll and the orbiting scroll, and the injection hole is provided in the compression chamber.

  The present invention can provide a compressor and a refrigeration cycle apparatus more suitable for using a working fluid containing R1123.

1 is a schematic configuration diagram of a refrigeration cycle apparatus according to Embodiment 1 of the present invention. The longitudinal cross-sectional view of the compressor of Embodiment 1 of this invention FIG. 2 is an enlarged cross-sectional view of a main part near the power supply terminal of the compressor according to the first embodiment of the present invention. Schematic configuration diagram of a refrigeration cycle apparatus according to Embodiment 2 of the present invention. Mollier diagram for explaining the operation of the refrigeration cycle apparatus according to Embodiment 2 of the present invention. Mollier diagram for explaining the operation of the refrigeration cycle apparatus according to Embodiment 2 of the present invention. Mollier diagram for explaining the operation of the refrigeration cycle apparatus according to Embodiment 2 of the present invention. Schematic configuration diagram of a refrigerant pipe joint constituting the refrigeration cycle apparatus according to Embodiment 2 of the present invention. Schematic configuration diagram of a refrigeration cycle apparatus according to Embodiment 3 of the present invention. Schematic configuration diagram of a refrigeration cycle apparatus according to Embodiment 4 of the present invention. Mollier diagram for explaining the operation of the refrigeration cycle apparatus according to Embodiment 4 of the present invention.

  The first invention uses a refrigerant including 1,1,2-trifluoroethylene as a working fluid, polyvinyl ether oil as a lubricant for a compressor, and a fixed scroll and an orbiting scroll in which a spiral wrap rises from an end plate A compression chamber formed in both directions by meshing is provided, and an injection hole is provided in the compression chamber. According to this, the refrigerant temperature of the compression chamber as a whole decreases as a result of the low-temperature refrigerant joining from the injection hole to the refrigerant whose temperature has increased in the middle of compression, and as a result, the refrigerant temperature rises immediately before being ejected from the discharge port. Therefore, the disproportionation reaction of R1123 can be suppressed. Moreover, since polyvinyl ether oil has relatively low polarity and easily exhibits the effect of improving the slidability by the additive, local heat generation at the sliding portion can be suppressed, and the self-decomposing reaction of R1123 can be suppressed.

  According to a second invention, in the first invention, the working fluid is a mixed working fluid containing difluoromethane, and the difluoromethane is 30% by weight to 60% by weight, or contains tetrafluoroethane. A mixed working fluid, wherein the tetrafluoroethane is 30 wt% to 60 wt%, or a mixed working fluid containing difluoromethane and tetrafluoroethane, wherein the difluoromethane and tetrafluoroethane are mixed. The mixing ratio of the difluoromethane and tetrafluoroethane is 30% by weight or more and 60% by weight or less. According to this, while suppressing the disproportionation reaction of R1123, a refrigerating capacity and COP can be improved.

  According to a third invention, in the first or second invention, the polyvinyl ether oil contains a phosphate ester-based antiwear agent. According to this, the anti-decomposition reaction of the R1123 refrigerant is suppressed by suppressing the heat generation by adsorbing the antiwear agent on the surface of the sliding portion and reducing friction.

According to a fourth invention, in the first or second invention, the polyvinyl ether oil contains a phenolic antioxidant. According to this, since the phenol-based antioxidant quickly captures radicals generated at the sliding portion, the radicals are prevented from reacting with the refrigerant R1123.

  According to a fifth invention, in the first or second invention, the polyvinyl ether oil is mixed with a terpene or terpenoid having a viscosity of 1% to less than 50% with a lubricating oil having a viscosity higher than that of the base oil, or a terpene or It is a lubricating oil in which an additive oil adjusted to a viscosity equivalent to that of a base oil by mixing an ultrahigh viscosity lubricating oil equivalent to or more than that of a terpenoid is mixed with the base oil. According to this, the disproportionation reaction of R1123 can be suppressed.

  According to a sixth invention, in the first or second invention, the motor uses, as a coil, an electric wire in which a thermosetting insulating material is applied and baked on a conductor via an insulating film. According to this, by applying a thermosetting insulating material to the winding of the motor coil in the compressor, the resistance between the windings remains high even when the coil is immersed in liquid refrigerant, and the discharge is suppressed. As a result, the decomposition of the R1123 refrigerant can be suppressed.

  According to a seventh invention, in the first or second invention, the hermetic container has a power supply terminal installed at an opening portion via an insulating member, and a connection terminal for connecting the power supply terminal to a lead wire. The doughnut-shaped insulating member is arranged on the power supply terminal inside the closed container in close contact with the insulating member. According to this, since the insulator is added to the power supply terminal inside the metal casing, it is possible to suppress insulation failure of the power supply terminal by extending the shortest distance between the conductors, and to prevent ignition due to the discharge energy of R1123. . Further, hydrogen fluoride generated when R1123 is decomposed is prevented from coming into contact with the glass insulator, and the glass insulator is prevented from being corroded and broken.

  An eighth invention is the compressor according to any one of the first to seventh inventions, a condenser for cooling the refrigerant gas compressed by the compressor to a high pressure, and the high-pressure refrigerant liquefied by the condenser. A first throttle mechanism for decompressing the gas, a gas-liquid separator for separating the refrigerant decompressed by the first throttle mechanism into a gas phase and a liquid phase, and a liquid-phase refrigerant separated by the gas-liquid separator. A second throttle mechanism for reducing pressure and an evaporator for gasifying the refrigerant further reduced in pressure by the second throttle mechanism are connected by a pipe, and the gas-liquid separator and the injection hole are provided. An injection circuit to be connected is provided. According to this, since the discharge temperature can be suppressed by combining the low-temperature refrigerant with the refrigerant in the middle of compression, the disproportionation reaction of R1123 can be suppressed.

  A ninth invention comprises the condensation temperature detection means provided in the condenser according to the eighth invention, wherein the difference between the critical temperature of the working fluid and the condensation temperature detected by the condensation temperature detection means is 5K or more. Thus, the opening degree of the first throttle mechanism and the second throttle mechanism is controlled. According to this, assuming that the working fluid temperature measured by the temperature detecting means corresponds to the pressure, the high pressure side working fluid temperature (pressure) is limited to 5K or more considering safety margin from the critical pressure. By controlling the opening degree of the first throttle mechanism and the second throttle mechanism, it is possible to prevent excessively high condensing pressure from being excessively increased. As a result of excessive pressure rise (result of close intermolecular distance) The disproportionation reaction that may occur can be suppressed, and the reliability of the apparatus can be ensured.

A tenth aspect of the invention is the eighth aspect of the invention, comprising high-pressure side pressure detection means provided between a discharge portion of the compressor and an inlet of the first throttle mechanism, and the critical pressure of the working fluid and the high-pressure side The opening degree of the first throttle mechanism and the second throttle mechanism is controlled so that the difference from the pressure detected by the pressure detection means is 0.4 MPa or more. According to this, with respect to the working fluid including R1123, particularly when a non-azeotropic refrigerant having a large temperature gradient is used, the refrigerant pressure can be detected more accurately, and further, the first result can be obtained using the detection result. The valve opening control of the second throttle mechanism and the second throttle mechanism can be performed to reduce the high-pressure side pressure (condensation pressure) in the refrigeration cycle apparatus, so that the disproportionation reaction can be suppressed and the reliability of the apparatus can be improved. It becomes possible to improve.

  An eleventh invention is the eighth invention, comprising a condenser outlet temperature detection means provided between the condenser and the first throttling mechanism, wherein the condensation temperature detected by the condensation temperature detection means and the The opening degree of the first throttling mechanism and the second throttling mechanism is controlled so that the difference in the condenser outlet temperature detected by the condenser outlet temperature detecting means is 15K or less.

  According to this, the opening degree control of the first throttle mechanism and the second throttle mechanism is performed using the detection result of the degree of supercooling indicated by the difference between the condensation temperature detection means and the condenser outlet temperature detection means. As a result, an excessive increase in the pressure of the working fluid in the refrigeration cycle apparatus can be prevented, so that the disproportionation reaction can be suppressed and the reliability of the apparatus can be improved.

  In a twelfth aspect based on the eighth aspect, the first conveying means for conveying the first medium to be heat-exchanged by the condenser, the second conveying means for conveying the second medium to be heat-exchanged by the evaporator, Condensation temperature detection means provided in the condenser, first medium temperature detection means for detecting the temperature of the first medium before flowing into the condenser, and second medium before flowing into the evaporator Second medium temperature detecting means for detecting the temperature of the compressor, a change amount per unit time of the input of the compressor, a change amount per unit time of the input of the first transport means, and an input of the second transport means When the amount of change per unit time is smaller than a predetermined value, the amount of change per unit time of the condensation temperature detected by the condensation temperature detection means is detected by the first medium temperature detection means. The amount of change per unit time of the temperature of one medium When the amount of change per unit time in the temperature of the second medium detected by the second medium temperature detecting means is larger than the amount of change, the valves of the first throttle mechanism and the second throttle mechanism are opened in the opening direction. It is something to control. According to this, when the appearance of the surrounding medium does not change, and when the condensing temperature changes suddenly, it is considered that the pressure increase due to the disproportionation reaction has occurred. To control. By doing so, it becomes possible to improve the reliability of the apparatus.

  In a thirteenth invention according to any one of the eighth to twelfth inventions, the outer periphery of a joint of a pipe constituting the refrigeration cycle is covered with a sealing agent containing a polymerization accelerator. According to this, when the working fluid leaks from the joint, the polymerization accelerator contained in the sealant and the working fluid containing R1123 undergo a polymerization reaction to generate a polymerization product. Leakage can be easily confirmed, and the polymerization product acts as a hindrance to the refrigerant flow released to the outside, and refrigerant leakage can be suppressed.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.

(Embodiment 1)
FIG. 2 shows a system configuration diagram of a refrigeration cycle apparatus using the compressor according to the first embodiment of the present invention.

  As shown in FIG. 2, the refrigeration cycle apparatus according to the present embodiment is mainly composed of a compressor 61, a condenser 62, a first throttling mechanism 63, a gas-liquid separator 64, A second throttle mechanism 65 and an evaporator 66 are included, and these devices are connected by piping so that a working fluid (refrigerant) circulates. In addition, an injection circuit 67 that connects the gas-liquid separator 64 and the compressor 61 is provided.

In the refrigeration cycle apparatus configured as described above, the refrigerant changes to liquid by pressurization and cooling, and changes to gas by depressurization and heating. The compressor 61 is driven by a motor, pressurizes the low-temperature and low-pressure gas refrigerant into a high-temperature and high-pressure gas refrigerant, and is conveyed to the condenser 62. The condenser 62 is cooled and condensed by air blown by a fan or the like, and becomes a low-temperature and high-pressure liquid refrigerant. This liquid refrigerant is depressurized by the first throttle mechanism 63 and partly becomes low-temperature and low-pressure gas refrigerant (gas phase) and the rest becomes low-temperature and low-pressure liquid refrigerant (liquid phase) and is conveyed to the gas-liquid separator 64. Is done. In the gas-liquid separator 64, the refrigerant is separated into a gas phase and a liquid phase. The liquid refrigerant (liquid phase) separated by the gas-liquid separator 64 is further depressurized by the second throttling mechanism 65 and conveyed to the evaporator 66. The evaporator 66 is heated and evaporated by air blown by a fan or the like, and becomes a low-temperature and low-pressure gaseous refrigerant, and is repeatedly sucked into the compressor 61 and pressurized. The gas refrigerant (gas phase) separated by the gas-liquid separator 64 is introduced through the injection circuit 67 during the pressurization process (compression process) of the compressor 61.

  In the above embodiment, the refrigeration cycle apparatus dedicated to cooling has been described. However, it is of course possible to operate the apparatus as a heating cycle apparatus via a four-way valve or the like.

  The heat transfer tube constituting the refrigerant flow path of at least one of the condenser 62 and the evaporator 66 is preferably an aluminum refrigerant tube containing aluminum or an aluminum alloy. A flat tube having a flow hole is desirable for reducing the condensation temperature or raising the evaporation temperature.

  The working fluid (refrigerant) sealed in the refrigeration cycle apparatus according to the present embodiment is a two-component mixture composed of (1) R1123 (1,1,2-trifluoroethylene) and (2) R32 (difluoromethane). In particular, it is a mixed working fluid having R32 of 30 wt% or more and 60 wt% or less.

  In application to a compressor described later, the disproportionation reaction of R1123 can be suppressed by mixing R32 with 30 wt% or more of R1123. Further, the higher the concentration of R32, the more the disproportionation reaction can be suppressed. This is because the action of mitigating the disproportionation reaction due to the small polarization of R32 to the fluorine atom and the behavior at the time of phase change such as condensation and evaporation are integrated because R1123 and R32 have similar physical characteristics. The disproportionation reaction of R1123 can be suppressed by the action of reducing the disproportionation reaction opportunity due to.

  Further, the mixed refrigerant of R1123 and R32 has an azeotropic boiling point with R32 being 30% by weight and R1123 being 70%, and there is no temperature slip, so that it can be handled in the same manner as a single refrigerant. That is, if R32 is mixed by 60% by weight or more, temperature slip increases, and handling similar to that of a single refrigerant may be difficult. Therefore, it is desirable to mix R32 at 60% by weight or less. In particular, it is desirable to mix R32 in an amount of 40 wt% to 50 wt% in order to prevent disproportionation and to make the temperature slip smaller because it approaches the azeotropic point and to facilitate device design.

  Tables 1 and 2 show that in the mixed working fluid of R1123 and R32, the pressure, temperature, and compressor displacement of the refrigeration cycle are the same when R32 is 30 wt% to 60 wt%. Refrigeration capacity and cycle efficiency (COP) are calculated and compared with R410A and R1123.

First, calculation conditions in Tables 1 and 2 will be described. In recent years, in order to improve the cycle efficiency of equipment, the performance of heat exchangers has increased, and in actual operating conditions, the condensation temperature tends to decrease, the evaporation temperature tends to increase, and the discharge temperature also tends to decrease . Therefore, considering the actual operating conditions, the cooling calculation conditions in Table 1 correspond to the cooling operation of the air conditioner (indoor dry bulb temperature 27 ° C, wet bulb temperature 19 ° C, outdoor dry bulb temperature 35 ° C). The evaporation temperature is 15 ° C, the condensation temperature is 45 ° C,
The superheat degree of the refrigerant sucked into the compressor was 5 ° C., and the supercool degree at the condenser outlet was 8 ° C. The heating calculation conditions in Table 2 are the calculation conditions corresponding to the heating operation of the air conditioner (indoor dry bulb temperature 20 ° C, outdoor dry bulb temperature 7 ° C, wet bulb temperature 6 ° C), and the evaporation temperature is 2 ° C. The condensation temperature was 38 ° C., the superheat degree of the refrigerant sucked into the compressor was 2 ° C., and the supercool degree at the condenser outlet was 12 ° C.

From Table 1 and Table 2, mixing R32 at 30 wt% or more and 60 wt% or less increases the refrigeration capacity by about 20% compared to R410A during cooling and heating operation, and the cycle efficiency (COP) is It becomes 94 to 97%, and the global warming potential can be reduced to 10 to 20% of R410A.

  As described above, in the two-component system of R1123 and R32, taking into consideration the prevention of disproportionation, the magnitude of temperature slip, the capacity during cooling operation / heating operation, and COP (that is, compression described later) When a mixing ratio suitable for an air-conditioning apparatus using an air conditioner is specified, a mixture containing 30% by weight or more and 60% by weight or less R32 is desirable, and a mixture containing 40% by weight or more and 50% by weight or less R32 is more desirable. Is desirable.

<Modification 1 of working fluid>
The working fluid sealed in the refrigeration cycle apparatus of the present embodiment is a two-component mixing operation consisting of (1) R1123 (1,1,2-trifluoroethylene) and (2) R125 (tetrafluoroethane). In particular, it may be a mixed working fluid in which R125 is 30 wt% or more and 60 wt% or less.

In application to a compressor described later, the disproportionation reaction of R1123 can be suppressed by mixing R125 in an amount of 30% by weight or more. Further, the higher the concentration of R125, the more the disproportionation reaction can be suppressed. This is because the disproportionation reaction due to the small polarization of R125 to fluorine atoms and the behavior during phase change such as condensation and evaporation are integrated because R1123 and R125 have similar physical characteristics. The disproportionation reaction of R1123 can be suppressed by the action of reducing the disproportionation reaction opportunity due to. Moreover, since R125 is a nonflammable refrigerant, R1
25 can reduce the combustibility of R1123.

  Tables 3 and 4 show that, in the mixed working fluid of R1123 and R125, the pressure, temperature of the refrigeration cycle, and the displacement of the compressor are the same at a mixing ratio where R125 is 30 wt% or more and 60 wt% or less. Refrigeration capacity and cycle efficiency (COP) are calculated and compared with R410A and R1123. The calculation conditions are the same as those in Tables 1 and 2.

From Tables 3 and 4, by mixing R125 at 30 wt% or more and 60 wt% or less, the refrigerating capacity is 96 to 110% and the cycle efficiency (COP) is 94 to 97% compared to R410A. .

  In particular, by mixing R125 at 40 wt% or more and 50 wt% or less, it is possible to prevent disproportionation of R1123 and to reduce the discharge temperature. Becomes easy. Furthermore, the warming potential can be reduced to 50-100% of R410A.

  As described above, in the two-component system of R1123 and R125, when considering disproportionation, reduction in combustibility, ability during cooling operation / heating operation, COP, and discharge temperature (that is, described later) When a mixing ratio suitable for an air-conditioning apparatus using a compressor is specified, a mixture containing 30 wt% or more and 60 wt% or less of R125 is desirable, and more desirably 40 wt% or more and 50 wt% or less of R125. Mixtures containing are desirable.

<Modification 2 of working fluid>
The working fluid sealed in the refrigeration cycle apparatus of the present embodiment includes (1) R1123 (1,1,2-trifluoroethylene), (2) R32 (difluoromethane), and (3) R125 (tetrafluoroethane). In particular, a mixed working fluid in which the mixing ratio of R32 and R125 is 30 or more and less than 60% by weight and the mixing ratio of R1123 is 40% or more and less than 70% by weight. It may be.

  In application to a compressor, which will be described later, the mixing ratio of R32 and R125 is 30% by weight or more, and the disproportionation reaction of R1123 can be suppressed. Further, the higher the mixing ratio of R32 and R125, the more the disproportionation reaction can be suppressed. R125 also reduces the combustibility of R1123.

  Tables 5 and 6 show that refrigeration capacity and cycle efficiency when the mixing ratio of R32 and R125 is fixed to 50% by weight and the pressure, temperature, and displacement of the compressor when the mixture is mixed with R1123 are the same ( COP) is calculated and compared with R410A and R1123. The calculation conditions are the same as those in Tables 1 and 2.

From Tables 5 and 6, the mixing ratio of R32 and R125 is 30% by weight or more and 60% by weight or less. Compared with R410A, the refrigerating capacity is 107 to 116%, and the cycle efficiency (COP) is 93 to 96. %.

  In particular, when the mixing ratio of R32 and R125 is 40% by weight or more and 50% by weight or less, disproportionation can be prevented, discharge temperature can be reduced, and combustibility can also be reduced. Furthermore, the warming potential can be reduced to 60-30% of R410A.

  In <Working fluid modification 2>, the mixing ratio of R32 and R125 of the three-component working fluid is described as 50% by weight, but the mixing ratio of R32 is set to 0% by weight to 100% by weight. If it is desired to increase the refrigerating capacity, increasing the mixing ratio of R32, conversely decreasing the mixing ratio of R32, and increasing the mixing ratio of R125 will reduce the discharge temperature and reduce the combustibility. be able to.

  As described above, in the three-component system of R1123, R32, and R125, when taking into consideration comprehensively the prevention of disproportionation, reduction of combustibility, ability during cooling operation / heating operation, COP, and discharge temperature (that is, When a mixing ratio suitable for an air conditioner using a compressor described later is specified), a mixture in which R32 and R125 are mixed and the sum of R32 and R125 is 30 wt% or more and 60 wt% or less is desirable. Desirably, a mixture containing 40 wt% or more and 50 wt% or less of the sum of R32 and R125 is desirable.

  FIG. 1 is a longitudinal sectional view of a scroll compressor according to the first embodiment of the present invention. Hereinafter, operation | movement and an effect | action are demonstrated about a scroll compressor.

  As shown in FIG. 1, the scroll compressor according to the first embodiment of the present invention includes a hermetic container 7, a motor unit (electric motor) 8 inside, and a compression mechanism 9. The compression mechanism 9 is supported so that the crankshaft 10 driven by the electric motor (motor unit) 8, the orbiting scroll 11, the fixed scroll 12, and the orbiting scroll 11 do not rotate with respect to the fixed scroll 12. The Oldham ring 13 and a frame 14 which supports the Oldham ring 13 so that the Oldham ring 13 can be moved for the support.

  The crankshaft 10 is supported by bearings 16 and 17 of the frame 14. A shaft 11 a of the orbiting scroll 11 is supported by a bearing 10 c provided on the crank portion 10 a of the crankshaft 10, and is engaged with the fixed scroll 12 to form a compression chamber 15. In addition, 18 is a suction inlet and 19 is a discharge outlet.

  Reference numeral 16 of the sealed container 7 is a suction pipe connected to the evaporator 66, and 23 is a discharge pipe connected to the condenser 62. An injection tube 24 connects the gas-liquid separator 64 and the compression chamber 15 of the compression mechanism 9 via the sealed container 7.

  An oil sump 20 is provided in the lowermost part of the sealed container 7, and the compressor lubricating oil (lubricating oil) 21 in the oil sump 20 is supplied to the lubrication target portion through the oil supply passage 10 b of the crankshaft 10. The bearing 16 is supplied from the oil supply hole 10d.

  About the scroll compressor comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

  When the crankshaft 10 is rotated by being driven by the electric motor (motor unit) 8, the orbiting scroll 11 is orbited through the Oldham ring 13 and sucks the gas refrigerant from the suction pipe 22 to the suction port 18. In the compression chamber 15, the gas refrigerant is compressed by reducing its volume while being moved from the outer peripheral side leading to the suction port 18 to the inner peripheral side leading to the discharge port 19, and discharged from the discharge port 19 into the sealed container 7. The high-temperature and high-pressure gas refrigerant is supplied to the refrigeration cycle from the discharge pipe 23, but is liquefied by the condenser 62, depressurized by the first throttle mechanism 63 to become two-phase, and reaches the gas-liquid separator 64. Here, the refrigerant is separated, and the liquid refrigerant is further decompressed by the second throttle mechanism 65, gasified by the evaporator 66, and reaches the suction pipe 22 of the scroll compressor 1. On the other hand, the gas refrigerant separated by the gas-liquid separator is introduced into the compression chamber 15 of the compression mechanism 9 through the injection circuit 67 and the injection pipe 24, and is compressed together with the suction gas refrigerant.

  In the present embodiment, an injection hole is provided in the compression chamber 15, and the gas refrigerant is introduced into the compression process via the injection pipe 24. As a result, the refrigerant temperature in the compression chamber is combined with the low-temperature refrigerant from the injection hole, so that the refrigerant temperature in the entire compression chamber is lowered, and as a result, the refrigerant temperature rise immediately before being ejected from the discharge port 19 is suppressed. Therefore, the disproportionation reaction of R1123 can be suppressed.

In the compressor of the present embodiment, polyvinyl ether oil is used as the lubricating oil for the compressor. Moreover, as an additive added to the lubricating oil for compressors, at least 1 type of additive is contained among a phosphate ester type | system | group antiwear agent and a phenolic antioxidant.

  Specific phosphate ester antiwear agents include tributyl phosphate, tripentyl phosphate, trihexyl phosphate, triheptyl phosphate, trioctyl phosphate, trinonyl phosphate, tridecyl phosphate, triundecyl phosphate, tridodecyl phosphate, tritridecyl Phosphate, tritetradecyl phosphate, tripentadecyl phosphate, trihexadecyl phosphate, triheptadecyl phosphate, trioctadecyl phosphate, trioleyl phosphate, triphenyl phosphate, tricresyl phosphate, trixylenyl phosphate, cresyl diphenyl phosphate, xyl Examples include lenyl diphenyl phosphate. Normally, phosphate ester antiwear agent is added to the refrigerating machine oil in an amount of 0.1 to 3 wt%, so that it can be effectively adsorbed on the surface of the sliding part to create a film with small shearing force on the sliding surface. Abrasion prevention effect is obtained.

  According to this, the effect of suppressing the self-decomposition reaction of the R1123 refrigerant can be obtained by suppressing the local heat generation of the sliding portion due to the sliding property improving effect by the antiwear agent.

  Specific examples of phenolic antioxidants include propyl gallate, 2,4,5-trihydroxybutyrophenone, t-butylhydroquinone, nordihydroguaiaretic acid, butylhydroxyanisole, 4-hydroxymethyl-2,6. -Di-t-butylphenol, octyl gallate, butylhydroxytoluene, dodecyl gallate and the like can be used. By adding 0.1 to 1 wt% of these antioxidants with respect to the base oil, radicals can be efficiently captured and reaction can be prevented. Further, coloring of the base oil itself by the antioxidant can be minimized.

  According to this, the phenolic antioxidant efficiently captures radicals generated in the sealed container 7, thereby obtaining an effect of suppressing the decomposition reaction of R1123.

  In order to prevent a reaction of a highly reactive molecule containing a double bond and a fluorine atom such as R1123, about 5% of limonene may be added to the refrigerant amount of R1123. The compressor of the present invention and the refrigeration cycle apparatus using the compressor are closed systems, and as described above, lubricating oil is enclosed as a base oil. Generally, the viscosity of the lubricating oil which is the base oil enclosed in such a compressor is generally about 32 mm2 / s to 68 mm2 / s, while the viscosity of limonene is about 0.8 mm2 / s, which is a considerably low viscosity. When about 5% is mixed, the viscosity is drastically reduced to 60 mm2 / s, when 15% is mixed, 48 mm2 / s, and when 35% is mixed, 32 mm2 / s. Therefore, mixing a large amount of limonene to prevent the reaction of R1123 will affect the reliability of compressors and refrigeration cycle equipment, such as wear due to poor lubrication due to lowering of the viscosity of the lubricating oil and generation of metal soap due to metal contact with the sliding surface. To do.

  The lubricating oil of the compressor according to the present embodiment is preliminarily based on a high-viscosity lubricating oil or a mixture of limonene in order to compensate for a decrease in the viscosity of the base oil caused by the mixing of an amount of limonene suitable for preventing reaction. An appropriate lubricating oil viscosity is ensured by mixing an ultra-high viscosity lubricating oil in an amount equal to or greater than the amount.

Specifically, the viscosity of the lubricating oil when mixing 5% limonene is 78 mm2 / s, and the viscosity of the lubricating oil when mixing 35% limonene is about 230 mm2 / s, so that 68 mm2 / s can be secured. . In order to maximize the effect of preventing the reaction of R1123 by limonene, extreme examples such as increasing the mixing amount of limonene to 70% or 80% are conceivable, but the viscosity of the base high-viscosity lubricating oil is 8500 mm 2/2 respectively. s and 25000mm2 / s and I
It exceeds 3200 mm2 / s, which is the maximum value of the SO standard, and it is difficult to achieve uniform application with limonene, making practical application difficult.

  In addition, when mixing an equal amount of ultrahigh viscosity lubricating oil with limonene, a viscosity of 32 mm2 / s to 68 mm2 / s can be obtained by mixing a lubricating oil of 800 mm2 / s to 1000 mm2 / s. When mixing limonene and an ultra-high viscosity oil having different viscosity differences, a lubricating oil having a relatively uniform composition viscosity can be obtained by mixing the limonene while adding the ultra-high viscosity oil little by little.

  In this embodiment, limonene is used as an example. However, similar effects can be obtained if terpenes or terpenoids are used. Compressors and refrigeration cycle equipment such as farnesyl diphosphate of pinene and sesquiterpenes, artemisinin, bisabolol, geranylgeranyl diphosphate of diterpenes, retinol, retinal, phytol, paclitaxel, forskolin, squalene and lanosterol of aphidicolin and triterpenes It can be selected according to the operating temperature and the required lubricating oil viscosity.

  In addition, the illustrated viscosity is a specific example in a compressor having a high-pressure vessel, and the same implementation is possible with a compressor in a low-pressure vessel that is used at a low lubricating oil viscosity of 5 mm2 / s to 32 mm2 / s. Needless to say, the same effect can be obtained.

  Note that terpenes such as limonene and terpenoids have solubility in plastics, but if they are mixed at about 30% or less, the effect is slight, and the electrical insulation required for the plastics in the compressor is a problem. It is not a level. However, it is desirable to use polyimide, polyimide amide, or polyphenylene sulfide having chemical resistance when there is a problem such as when long-term reliability is required or when the use temperature is constantly high.

  Moreover, as for the winding of the motor 2 of the compressor of this Embodiment, the varnish (thermosetting insulating material) is apply | coated and baked through the insulating film on the conductor. Examples of the thermosetting insulating material include a polyimide resin, an epoxy resin, and an unsaturated polyester resin. Among these, the polyimide resin can be converted into a polyimide by coating in the state of polyamic acid as a precursor and baking at around 300 ° C. It is known that the imidization reaction occurs by a reaction between an amine and a carboxylic anhydride. Since the R1123 refrigerant may react even in a short circuit between electrodes, a polyimide acid varnish mainly composed of a polyimide precursor formed by reacting an aromatic diamine and an aromatic tetracarboxylic dianhydride on a motor winding is used. By applying, a short circuit between electrodes can be prevented.

  For this reason, even when the coil of the motor 2 is immersed in the liquid refrigerant, it becomes possible to keep the resistance between the windings high, thereby suppressing the discharge between the windings and consequently suppressing the self-decomposition reaction of the R1123 refrigerant. An effect is obtained.

  FIG. 3 is a partial cross-sectional view showing the structure near the power supply terminal of the compressor according to the present embodiment. In FIG. 3, 71 is a power supply terminal, 72 is a glass insulator, 73 is a metal lid for holding a power supply terminal, 74 is a flag terminal connected to the power supply terminal, and 75 is a lead wire. In the compressor according to the present embodiment, a donut-shaped insulating member 76 that is in close contact with the insulating member is disposed on a power supply terminal inside the sealed container 7 of the compressor. The most suitable donut-shaped insulating member is an insulating member that is resistant to hydrofluoric acid. Examples thereof include ceramic insulators and HNBR rubber donut spacers. Although it is essential that the doughnut-shaped insulating member is in close contact with the glass insulator, it is preferable that the donut-like insulating member is also in close contact with the connection terminal.

The power supply terminal configured in this manner has a long creepage distance between the power supply terminal and the inner surface of the compressor due to the donut-shaped insulating member, thereby preventing terminal tracking and preventing ignition due to the discharge energy of R1123. Can do. Further, hydrofluoric acid generated by the decomposition of R1123 is prevented from corroding the glass insulator.

  The compressor of the present embodiment may be a so-called high-pressure shell type compressor in which the discharge port 19 is opened in the sealed container 7 and the inside of the sealed container 7 is filled with the refrigerant compressed in the compression chamber 15. In the case of a so-called low pressure shell type compressor in which the suction port 18 is opened in the hermetic container 7 and the inside of the hermetic container 7 is filled with the refrigerant before being compressed in the compression chamber 15, it is heated in the hermetic container 7. In the configuration in which the temperature is likely to rise before being introduced into the compression chamber 15, the temperature reduction due to the introduction of the low-temperature refrigerant in the compression chamber 15 becomes more remarkable, which is desirable for suppressing the disproportionation reaction of R1123.

  Further, even in a high-pressure shell type compressor, the refrigerant discharged from the discharge port 19 passes through the periphery of the motor unit 8 and is heated by the motor unit 8 in the sealed container 7. You may comprise so that it may discharge outside. According to this, even if the temperature of the refrigerant discharged from the discharge pipe 23 is equal, the refrigerant temperature in the compression chamber 15 can be lowered, which is desirable in suppressing the disproportionation reaction of R1123.

(Embodiment 2)
FIG. 4 shows a refrigeration cycle apparatus 101 according to the second embodiment of the present invention. In the refrigeration cycle apparatus 101 of the present embodiment, a compressor 102, a condenser 103, a first throttle mechanism 104a, a gas-liquid separator 64, a second throttle mechanism 104b, and an evaporator 105 are connected in this order through a refrigerant pipe 106, A cycle circuit is configured. The gas refrigerant separated by the gas-liquid separator 64 is introduced into the compression chamber of the compressor 102 through the injection circuit 67 and compressed together with the suction gas refrigerant. Naturally, working fluid (refrigerant) is enclosed in the refrigeration cycle circuit.

  Next, the configuration of the refrigeration cycle apparatus will be described.

  For the condenser 103 and the evaporator 105, when the surrounding medium is air, a fin and tube heat exchanger, a parallel flow type (microtube type) heat exchanger, or the like is used.

  On the other hand, when the surrounding medium is brine or a refrigerant of a binary refrigeration cycle, the condenser 103 and the evaporator 105 are a double tube heat exchanger, a plate heat exchanger, or a shell and tube heat exchanger. It is done.

  For example, a pulse motor drive type electronic expansion valve is used for the first diaphragm mechanism 104a and the second diaphragm mechanism 104b, which are the diaphragm mechanisms.

  The refrigeration cycle apparatus 101 includes a fluid machine (first conveying means) 107 a that drives (flows) an ambient medium (first medium) that exchanges heat with refrigerant in the condenser 103 to a heat exchange surface of the condenser 103. Is installed. Further, the refrigeration cycle apparatus 101 includes a fluid machine (second transport means) that drives (flows) an ambient medium (second medium) that exchanges heat with the refrigerant in the evaporator 105 to a heat exchange surface of the evaporator 105. 107b is installed.

  As the surrounding medium, air in the atmosphere may be used, or water or brine such as ethyl glycol may be used. In the case where the refrigeration cycle apparatus 101 is a two-way refrigeration cycle, refrigeration is performed. Preferred refrigerants for the cycle and operating temperature range, such as hydrofluorocarbon (HFC), hydrocarbon (HC), carbon dioxide, etc. are used.

  In the fluid machines 107a and 107b for driving the surrounding medium, when the surrounding medium is air, an axial flow fan such as a propeller fan, a cross flow fan, a centrifugal blower such as a turbo blower is used, and when the surrounding medium is brine, A centrifugal pump or the like is used.

  When the refrigeration cycle apparatus 101 is a two-way refrigeration cycle, the compressor is responsible for the fluid machines 107a and 107b for transporting the surrounding medium.

  In the condenser 103, a condensing temperature detecting means is provided at a location where the refrigerant flowing in the condenser 103 flows in two phases (a state where gas and liquid are mixed) (hereinafter referred to as “two-phase tube of the condenser”). 110a is installed, and the refrigerant temperature can be measured.

  A condenser outlet temperature detection means 110b is installed between the outlet of the condenser 103 and the inlet of the first throttle mechanism 104a. The condenser outlet temperature detection means 110b can detect the degree of supercooling at the inlet of the first throttle mechanism 104a (a value obtained by subtracting the condenser temperature from the first throttle mechanism inlet temperature).

  In the evaporator 105, an evaporation temperature detecting means 110 c is provided at a location where the refrigerant flowing in the two-phase flows (hereinafter referred to as “two-phase pipe of the evaporator” in this specification). The temperature of the refrigerant can be measured.

  A suction temperature detecting means 110d is provided in the compressor 102 suction section (between the evaporator 105 outlet and the compressor 102 inlet). Thereby, the temperature (intake temperature) of the refrigerant sucked into the compressor 102 can be measured.

  For the temperature detection means 110a to 110d, for example, an electronic thermostat that is contact-connected with a pipe through which a refrigerant flows or an outer pipe of a heat transfer pipe may be used, or a sheath pipe type that directly contacts the working fluid. In some cases, an electronic thermostat is used.

  Between the outlet of the condenser 103 and the inlet of the first throttle mechanism 104a, a high pressure for detecting the pressure on the high pressure side of the refrigeration cycle (the region where the refrigerant from the compressor 102 outlet to the inlet of the first throttle mechanism 104a exists at a high pressure). Side pressure detecting means 115a is installed.

  At the outlet of the first throttle mechanism 104a, a low pressure side pressure detecting means 115b for detecting the pressure on the low pressure side of the refrigeration cycle (the region where the refrigerant from the expansion valve 104 outlet to the compressor 102 inlet exists at a low pressure) is installed. .

  As the pressure detection means 115a and 115b, for example, a device that converts the displacement of the diaphragm into an electrical signal is used. A differential pressure gauge (measuring means for measuring the pressure difference at the inlet / outlet of the expansion valve 104) may be used instead of the high pressure side pressure detecting means 115a and the low pressure side pressure detecting means 115b.

  In the above description of the configuration, the temperature detection units 110a to 110d and the pressure detection units 115a and 115b are described as being all provided. However, in the control described later, the detection unit that does not use the detection value can be omitted. Needless to say.

  A control method of the refrigeration cycle apparatus 101 will be described. First, control during normal operation will be described. During normal operation, the degree of superheating of the working fluid at the suction portion of the compressor 102, which is the temperature difference between the suction temperature detection means 110d and the evaporation temperature detection means 110c, is calculated. Then, the first throttle mechanism 104a and the second throttle mechanism 104b are controlled so that the superheat degree becomes a predetermined target superheat degree (for example, 5K).

  Alternatively, it is also possible to further provide a discharge temperature detecting means (not shown) in the discharge portion of the compressor 102 and perform control using the detected value. In this case, the degree of superheat of the working fluid at the discharge portion of the compressor 102, which is the temperature difference between the discharge temperature detection means and the condensation temperature detection means 110a, is calculated. Then, the first throttle mechanism 104a and the second throttle mechanism 104b are controlled so that this superheat degree becomes a predetermined target superheat degree.

  The intermediate pressure of the refrigerant in the gas-liquid separator 64 (takes a value between the condensation pressure and the evaporation pressure) and the amount of injection gas separated from the gas-liquid separator 64 and introduced into the compression chamber of the compressor 102 are: It can be determined by controlling the valve openings of both the first throttle mechanism 104a and the second throttle mechanism 104b.

  Next, the control in the case of a unique operating state in which the possibility of the disproportionation reaction occurring will be described.

  In the present embodiment, when the temperature detection value of the condensation temperature detection means 110a becomes excessive, both the first diaphragm mechanism 104a and the second diaphragm mechanism 104b or one of them (in particular, the first diaphragm mechanism). The valve 104a is more preferable because it greatly affects the condensing pressure, and control is performed to lower the high-pressure working fluid pressure and temperature in the refrigeration cycle apparatus 101. In the following description, when it is simply described as “control (open) the valve opening degree of the first throttling mechanism 104a and the second throttling mechanism 104b”, the above description (both throttling mechanisms, or In the case of one valve, it is particularly preferable to control the first throttle mechanism 104a).

  In general, in a refrigerant excluding carbon dioxide, it is necessary to prevent a supercritical condition from exceeding a critical point (a point described as Tcri in FIG. 5 described later). In the supercritical state, the substance is neither a gas nor a liquid, and its behavior is unstable and active.

  Here, in the present embodiment, the temperature at the critical point (critical temperature) is taken as one guideline, and expansion is performed so that the condensation temperature does not approach within a predetermined value (5 K) from this temperature. The opening degree of the valve 104 is controlled. When a working fluid (mixed refrigerant) including R1123 is used, the temperature of the working fluid is controlled so as not to exceed (critical temperature−5) ° C. using the critical temperature of the mixed refrigerant.

  Specifically, this will be described with reference to the Mollier diagram of FIG. In FIG. 5, a refrigeration cycle under an excessive pressure condition that causes a disproportionation reaction is indicated by a solid line (EP), and a refrigeration cycle under normal operation is indicated by a broken line (NP). As described above, the intermediate pressures of EP and NP are determined by controlling the valve opening degrees of both the first throttle mechanism 104a and the second throttle mechanism 104b, and are not limited to those shown in FIG. The same applies to the Mollier diagrams of FIGS. 6 and 7).

  If the temperature value in the condensing temperature detecting means 110a provided in the two-phase tube of the condenser 103 is within 5K with respect to the critical temperature stored in the control device in advance (EP in FIG. 5), The first throttle mechanism 104a and the second throttle mechanism 104b are controlled to open the valve openings. As a result, the condensing pressure on the high-pressure side of the refrigeration cycle apparatus 101 decreases as shown by NP in FIG. 5, so that it becomes possible to suppress the disproportionation reaction caused by excessive increase in the refrigerant pressure. In the case where the leveling reaction occurs, it is possible to suppress the pressure increase.

Note that the above-described control method for indirectly grasping the pressure in the condenser 103 from the condensation temperature measured by the condensation temperature detection means 110a and controlling the valve openings of the first throttle mechanism 104a and the second throttle mechanism 104b is as follows. , R1123 containing working fluid is azeotropic or pseudo-azeotropic, and the condenser 1
In the case where there is no or small temperature difference (temperature gradient) between the dew point and boiling point of the working fluid containing R1123 in 03, it is particularly preferable because the condensation temperature can be used as an index instead of the condensation pressure.

<Modification 1 of Control Method>
Alternatively, as described above, by comparing the critical temperature and the condensation temperature, the high-pressure (refrigerant pressure in the condenser) state of the refrigeration cycle apparatus 101 is indirectly detected, and appropriate operation is performed by the first throttle mechanism. Instead of the control method instructing the 104a, the second throttle mechanism 104b, etc., the valve opening degree control of the first throttle mechanism 104a and the second throttle mechanism 104b may be performed based on the directly measured pressure. .

  FIG. 6 is a Mollier diagram showing this control operation. In FIG. 6, the refrigeration cycle in which an excessive pressure rise is occurring from the compressor discharge section to the condenser and the expansion valve inlet is indicated by a solid line (EP), and the above-described excessive pressure state is removed by a broken line (NP). The refrigeration cycle in the state is shown.

  During operation, a pressure difference obtained by subtracting, for example, a condenser outlet pressure Pcond detected by the high-pressure side pressure detecting means 115a from a pressure (critical pressure) Pcri at a critical point stored in the control device in advance is a predetermined value. If it is smaller than (Δp = 0.4 MPa) (EP in FIG. 6), whether a disproportionation reaction has occurred in the working fluid containing R1123 from the compressor 102 discharge to the inlet of the first throttle mechanism 104a, Alternatively, it is determined that there is a high possibility that it will occur, and the valve opening degree of the first and second throttle mechanisms 104a and 104b is controlled to open so as to avoid sustaining under this high pressure condition.

  As a result, the refrigeration cycle in FIG. 6 acts on the side where the high pressure (condensation pressure) decreases like NP in the figure, causing the disproportionation reaction to occur, or the pressure increase that occurs after the disproportionation reaction. Suppress.

This control method is preferably used when the working fluid including R1123 is non-azeotropic, particularly when the temperature gradient is large at the condensation pressure.
<Modification 2 of control method>
Alternatively, instead of the control method based on the critical temperature or the critical pressure, a control method based on the degree of supercooling may be used. FIG. 7 is a Mollier diagram showing this control operation. In FIG. 7, a refrigeration cycle under an excessive pressure condition that causes a disproportionation reaction is denoted by EP and indicated by a solid line, and a broken line is denoted by NP and a refrigeration cycle under normal operation is denoted by a broken line.

  In general, in the refrigeration cycle apparatus, the temperature of the refrigerant in the condenser is about a certain level with respect to the surrounding medium by appropriate control of the refrigeration cycle such as a throttle mechanism and a compressor, heat exchanger size, and refrigerant charge optimization. Is installed to be higher. The degree of supercooling generally takes a value of about 5K. Similar measures are taken in working fluids including R1123 using similar refrigeration cycle equipment.

In the refrigeration cycle apparatus in which the above measures are taken, if the refrigerant pressure becomes excessively high, the degree of supercooling at the inlet of the first throttle mechanism 104a tends to increase as shown in EP of FIG. Therefore, in the present embodiment, the opening degree of the first throttle mechanism 104a and the second throttle mechanism 104b is controlled on the basis of the degree of supercooling of the refrigerant at the inlet of the first throttle mechanism 104a. The degree of supercooling of the refrigerant at the inlet of the first throttle mechanism 104a during normal operation is assumed to be 5K, and the valve openings of the first throttle mechanism 104a and the second throttle mechanism 104b are set to 15K which is three times the value as a guide. I am going to control it. The reason why the supercooling degree as the threshold is tripled is that the supercooling degree may change within the range depending on the operating conditions.

  Specifically, first, the degree of supercooling is calculated from the detection values of the condensation temperature detection means 110a and the condenser outlet temperature detection means 110b. The degree of supercooling is a value obtained by subtracting the detection value of the condenser outlet temperature detection means 110b from the detection value of the condensation temperature detection means 110a. When the degree of supercooling at the inlet of the first throttle mechanism 104a reaches a predetermined value (15K), the first throttle mechanism 104a and the second throttle mechanism 104b operate to open the valve openings, and the refrigeration cycle The condensing pressure, which is the high pressure portion of the apparatus 101, is controlled to decrease (the broken line from the solid line in FIG. 7). Since the decrease in the condensation pressure is the same as the decrease in the condensation temperature, it decreases from the condensation temperature Tcond1 to Tcond2, and the degree of supercooling at the inlet of the first throttle mechanism 104a is changed from Tcond1-Texin to Tcond2-. The degree of supercooling decreases to Texin (here, it is assumed that the working fluid temperature at the inlet of the first throttle mechanism 104a remains Texin). As described above, since the degree of supercooling decreases as the condensation pressure in the refrigeration cycle apparatus decreases, it can be seen that the condensation pressure in the refrigeration cycle apparatus can be controlled even when the degree of supercooling is used as a reference.

  FIG. 8 shows a pipe joint 117 constituting a part of the pipe of the refrigeration cycle of the present embodiment. When the refrigeration cycle apparatus 101 of the present invention is used for, for example, a home-use split type air conditioner (air conditioner), the refrigeration cycle apparatus 101 includes an outdoor unit having an outdoor heat exchanger and an indoor unit having an indoor heat exchanger. . Since the outdoor unit and the indoor unit cannot be integrated due to their configuration, they are connected at the installation location using a mechanical joint such as the union flare 111 shown in FIG.

  If the connection state of the mechanical joint is deteriorated due to a cause such as inadequate work, the refrigerant leaks from the joint part, which adversely affects the device performance. Moreover, since the working fluid itself containing R1123 is a greenhouse gas having a warming effect, there is a risk of adversely affecting the global environment. Therefore, it is required to quickly detect and repair the refrigerant leakage.

  The detection of refrigerant leakage includes a method of applying a detection agent to the site and detecting when a bubble is generated, a method of using a detection sensor, and the like, all of which require a lot of work.

  Therefore, in the present embodiment, a seal 112 containing a polymerization accelerator is wound around the outer periphery of the union flare 111 to facilitate refrigerant leak detection and reduce the amount of leakage.

  Specifically, the fact that polytetrafluoroethylene, which is one of the fluorinated carbon resins, is generated when a polymerization reaction occurs in the working fluid containing R1123 is utilized. The working fluid containing R1123 and the polymerization accelerator are intentionally brought into contact with each other at the leaked location, so that polytetrafluoroethylene precipitates and solidifies at the leaked location. As a result, it becomes easier to detect leaks visually, so the time taken to find and repair leaks can be reduced.

  Furthermore, since the generation site of polytetrafluoroethylene is the leakage site of the working fluid containing R1123, the polymerization product is naturally generated and adhered to the site that prevents the leakage, so it is also possible to suppress the amount of leakage. It becomes.

(Embodiment 3)
FIG. 9 shows a refrigeration cycle apparatus 130 according to a third embodiment of the present invention. The difference in configuration between the refrigeration cycle apparatus 130 shown in FIG. 9 and the refrigeration cycle apparatus 101 of the second embodiment is newly provided with an on-off valve connected to the first throttle mechanism 104a inlet and the second throttle mechanism 104b outlet. In addition, a purge line having a relief valve 114 is provided between the point where the bypass pipe 113 is installed and the outlet of the condenser 103 and the inlet of the first throttle mechanism 104a. The opening side of the relief valve 114 is disposed outside the room. In FIG. 9, the description of the temperature detection means 110a to 110d, the pressure detection means 115a, 115b, etc. described with reference to FIG. 4 is omitted.

  The control method described in the second embodiment (for example, the first throttling so that the value obtained by subtracting the working fluid temperature measured by the two-phase pipe of the condenser 103 from the critical temperature of the working fluid including R1123 becomes 5K or more. Control method for controlling the valve opening degree of the mechanism 104a and the second throttle mechanism 104b, and control so that the difference between the critical pressure of the working fluid and the pressure detected by the high pressure side pressure detecting means 115a is 0.4 MPa or more. Even when the valve opening of both the first throttling mechanism 104a and the second throttling mechanism 104b is opened, there is a case where no improvement in pressure drop is observed or there is a situation where the pressure drop speed is desired to be increased. there is a possibility.

  Therefore, if the above situation occurs, the on-off valve provided in the bypass pipe 113 of the present embodiment is opened and the refrigerant is allowed to flow through the bypass pipe 113, so that the working fluid pressure on the high pressure side can be rapidly increased. The breakage of the refrigeration cycle apparatus 130 can be suppressed.

  Furthermore, in addition to the control to increase the valve opening degree of both the first throttle mechanism 104a and the second throttle mechanism 10b and the control of the on-off valve provided in the bypass pipe 113, if the compressor 102 is emergency stopped, It is further preferable in preventing the refrigeration cycle apparatus 130 from being damaged. In the case of emergency stop of the compressor 102, it is desirable not to stop the first transport unit 117a and the second transport unit 117b in order to rapidly reduce the working fluid pressure on the high pressure side.

  Even when the above measures are taken, if the disproportionation reaction is not suppressed, specifically, the difference between the critical temperature of the working fluid and the condensation temperature detected by the condensation temperature detection means 110a is less than 5K. Or, in the case where the difference between the critical pressure of the working fluid and the pressure detected by the high-pressure side pressure detecting means 115a is less than 0.4 MPa, the refrigerant pressure in the refrigeration cycle apparatus 130 further increases. Therefore, there is a need to escape the high-pressure refrigerant to the outside and prevent the refrigeration cycle apparatus 130 from being damaged. Therefore, the relief valve 114 that purges the working fluid including R1123 in the refrigeration cycle apparatus 130 to the external space is opened.

  The installation position of the relief valve 114 in the refrigeration cycle apparatus is preferably on the high pressure side, and further, the intermolecular distance of R1123 is small or the molecular motion becomes active, from the condenser outlet shown in this embodiment to the first throttle mechanism inlet ( At this position, since the working fluid is in a high pressure supercooled liquid state, it is likely to be installed over a water hammer effect resulting from a sudden pressure increase associated with the disproportionation reaction) or from the compressor discharge section to the condenser Installation at the inlet (at this position, the working fluid is in a high-temperature and high-pressure gas state, the molecular motion becomes active, and the disproportionation reaction itself easily occurs) is particularly preferable.

  The relief valve 114 is provided on the outdoor unit side. In the case of this form, if it is an air conditioner, the working fluid is not discharged to the indoor living space, and if it is a refrigeration unit, the working fluid is not discharged to the product display side such as a showcase. As such, it is considered not to have a direct influence on humans, merchandise, etc.

  It is desirable for safety to open the relief valve 114 and stop the refrigeration cycle apparatus 130, for example, to turn off the power.

(Embodiment 4)
FIG. 10 shows a refrigeration cycle apparatus 140 according to a fourth embodiment of the present invention. The difference in configuration between the refrigeration cycle apparatus 140 shown in FIG. 10 and the refrigeration cycle apparatus 101 of the first embodiment is that the first medium temperature detection means 110e that detects the temperature of the first medium before flowing into the condenser 103. A second medium temperature detecting means 110f for detecting the temperature of the second medium before flowing into the evaporator 105, detection values of the temperature detecting means 110a to 110f, and the pressure detecting means 115a and 115b, The input power of the compressor 102 and the fluid machines 107a and 107b is recorded in an electronic recording device (not shown) for a certain period of time.

  FIG. 11 is a diagram showing the operation of the refrigeration cycle apparatus 140 of the present embodiment on a Mollier diagram. In FIG. 11, the refrigeration cycle indicated by EP indicates the condensation pressure when the disproportionation reaction occurs, and the refrigeration cycle indicated by NP indicates the refrigeration cycle during normal operation. In FIG. 11, the cycle change (for example, the difference between the evaporation pressure of NP and EP, the difference in intermediate pressure, etc.) when the condensing pressure rises is not described for the sake of simplicity.

  The causes for the rapid increase in the condensation temperature of the working fluid including R1123 measured by the two-phase tube in the condenser 103 are (1) a rapid increase in the ambient medium temperatures Tmcon and Tmeva, and (2) the compressor 102 A pressurizing action due to a power increase, and (3) a change in the flow of the surrounding medium (an increase in power of one of the fluid machines 107a and 107b that drives the surrounding medium) can be considered. In addition to these factors, the action fluid-specific events including R1123 include (4) pressurization by disproportionation reaction. Therefore, in order to specify that the disproportionation reaction has occurred, it is a feature of the present embodiment that control is performed by determining that the events (1) to (3) have not occurred.

  Therefore, as a control method of the present embodiment, when the change amount of the condensation temperature of the working fluid including R1123 is large with respect to the change amount of the temperature or input power of (1) to (3), the first throttle mechanism. 104a and the second throttle mechanism 104b are controlled to open the valve.

  A specific control method will be described below. First, since it is difficult to compare the amount of change in temperature and the amount of change in input power value under the same standard, when measuring the amount of change in temperature, control is performed so that the input power does not change. That is, when measuring the amount of temperature change, the motor speed of the compressor 102 and the fluid machines 107a and 107b is kept constant.

  For example, the temperature change amount is measured at a certain time interval, for example, for 10 seconds to 1 minute. Prior to this measurement, for example, about 10 seconds to 1 minute before, the input electric energy of the compressor 102 and the fluid machines 107a and 7b is kept at a constant value. At this time, the amount of change per unit time of the input electric energy of the compressor 102 and the fluid machines 107a and 107b is substantially zero. Here, the zero is generally set to zero in the compressor 102, and in the fluid machines 107a and 107b, when the first and second media are ambient air, This is because the input power slightly fluctuates due to the influence of blowing or the like. That is, this substantially zero means that it is smaller than a predetermined value including some fluctuations.

  Under the above conditions, the change amount per unit time of the condensation temperature measured by the condensation temperature detection unit 110a is the change per unit time of the temperature of the first medium detected by the first medium temperature detection unit 110e. If the amount is greater than either the unit time of the temperature of the second medium detected by the second medium temperature detecting means 110f, it is considered that a disproportionation reaction has occurred, and the first throttle mechanism 104a, The valve of the two-throttle mechanism 104b is controlled in the opening direction.

  In addition, as shown in the second embodiment, in case the pressure increase generated with the disproportionation reaction cannot be controlled only by the valve opening control of the first throttle mechanism 104a and the second throttle mechanism 104b, A bypass pipe 113 may be provided in parallel with the first throttle mechanism 104a and the second throttle mechanism 104b, or an emergency stop of the compressor 102, and a relief valve 114 for reducing the pressure by discharging refrigerant to the outside may be provided. Good.

Further, in the present embodiment, the control example of the first throttle mechanism 104a and the second throttle mechanism 104b performed based on the change amount of the temperature detection unit installed in the two-phase tube of the condenser 103 is shown. The amount of change in pressure at some point from the 102 discharge section to the inlet of the first throttle mechanism 104a may be used as a reference, or the amount of change in the degree of supercooling at the inlet of the first throttle mechanism 104a may be used as a reference.

  Note that it is preferable to use this embodiment in combination with any of Embodiments 2 and 3 of the present invention described above because further reliability can be improved.

  As described above, since the compressor and the refrigeration cycle apparatus according to the present invention are suitable for using a working fluid containing R1123, the compressor and the refrigeration cycle apparatus can be applied to uses such as a water heater, a car air conditioner, a refrigerator-freezer, and a dehumidifier.

DESCRIPTION OF SYMBOLS 7 Sealed container 8 Motor part 9 Compression mechanism 10 Crankshaft 11 Orbiting scroll 12 Fixed scroll 13 Oldham ring 14 Frame 15 Compression chamber 16, 17 Bearing 18 Suction port 19 Discharge port 21 Lubricating oil 61 Compressor 62 Condenser 63 First throttle Mechanism 64 Gas-liquid separator 65 Second throttle mechanism 66 Evaporator 67 Injection circuit 71 Power supply terminal 72 Glass insulator 73 Metal lid holding power supply terminal 74 Flag-type terminal 75 Lead wire 76 Donut-shaped insulating member 101 , 130, 140 Refrigeration cycle apparatus 102 Compressor 103 Condenser 104a First throttle mechanism 104b Second throttle mechanism 105 Evaporator 106 Refrigerant piping 107a, 107b Fluid machine 108 Isotherm 109 Saturated liquid line, saturated vapor line 110a Condensation temperature detection means 110b Condenser out Temperature detection means 110c Evaporation temperature detection means 110d Suction temperature detection means 110e First medium temperature detection means 110f Second medium temperature detection means 111 Union flare 112 Seal including a polymerization accelerator 113 Bypass pipe 114 Relief valve 115a High pressure side pressure detection means 115b Low pressure side pressure detection means 116 Flow path of surrounding medium 117 Pipe joint EP State change of refrigeration cycle under excessive pressure condition NP State change of refrigeration cycle during normal operation

Claims (13)

A refrigerant containing 1,1,2-trifluoroethylene is used as the working fluid, polyvinyl ether oil is used as the lubricating oil for the compressor, and the fixed scroll and the orbiting scroll where the spiral wrap rises from the end plate are engaged in both directions. A compressor comprising a compression chamber formed, and an injection hole provided in the compression chamber. The working fluid is a mixed working fluid containing difluoromethane, and the difluoromethane is 30 wt% to 60 wt%, or a mixed working fluid containing tetrafluoroethane, wherein the tetrafluoroethane is 30 wt% or more and 60 wt% or less, or a mixed working fluid containing difluoromethane and tetrafluoroethane, wherein the difluoromethane and tetrafluoroethane are mixed and the difluoromethane and tetrafluoroethane are combined. The compressor according to claim 1, wherein the mixing ratio is 30 wt% or more and 60 wt% or less. The compressor according to claim 1 or 2, wherein the polyvinyl ether oil contains a phosphate ester antiwear agent. The compressor according to claim 1 or 2, wherein the polyvinyl ether oil contains a phenolic antioxidant. The polyvinyl ether oil is mixed with a terpene or terpenoid of 1% to less than 50% with a lubricating oil having a viscosity higher than that of the base oil, or an ultrahigh viscosity lubricating oil equal to or more than the terpene or terpenoid is preliminarily added. The compressor according to any one of claims 1 to 3, which is a lubricating oil obtained by mixing an additive oil mixed and adjusted to a viscosity equivalent to that of the base oil with the base oil. 2. A motor unit for driving the orbiting scroll, wherein the motor unit uses an electric wire formed by applying and baking a thermosetting insulating material on a conductor via an insulating film as a coil. 2. The compressor according to 2. The airtight container which contains the compression chamber and the motor part is provided, and the airtight container has a power supply terminal installed in the mouth part via an insulating member, and a connection terminal for connecting the power supply terminal to the lead wire. The compressor according to claim 1, wherein a donut-shaped insulating member is disposed in close contact with the insulating member on a power supply terminal inside the sealed container. A compressor according to any one of claims 1 to 7, a condenser for cooling the refrigerant gas compressed by the compressor to a high pressure, and a high pressure refrigerant liquefied by the condenser. 1 throttle mechanism, a gas-liquid separator that separates the refrigerant depressurized by the first throttling mechanism into a gas phase and a liquid phase, and a second that depressurizes the liquid-phase refrigerant separated by the gas-liquid separator. And an evaporator that gasifies the refrigerant further reduced in pressure by the second throttle mechanism by a pipe and an injection circuit that connects the gas-liquid separator and the injection hole. A refrigeration cycle apparatus comprising: A condenser temperature detecting means provided in the condenser, the first throttle mechanism and the difference between the critical temperature of the working fluid and the condensation temperature detected by the condensation temperature detecting means being 5K or more; The refrigeration cycle apparatus according to claim 8, wherein the opening degree of the second throttle mechanism is controlled. A high-pressure side pressure detecting means provided between a discharge portion of the compressor and an inlet of the first throttle mechanism, wherein a critical pressure of the working fluid and a pressure detected by the high-pressure side pressure detecting means The refrigeration cycle apparatus according to claim 8, wherein the opening degree of the first throttle mechanism and the second throttle mechanism is controlled so that the difference is 0.4 MPa or more. Condenser outlet temperature detection means provided between the condenser and the first throttling mechanism is provided, and the condensation temperature detected by the condensation temperature detection means and the condensation detected by the condenser outlet temperature detection means The refrigeration cycle apparatus according to claim 8, wherein the opening degree of the first throttle mechanism and the second throttle mechanism is controlled so that the difference in the outlet temperature of the container is 15K or less. First transport means for transporting a first medium for heat exchange with the condenser;
Second transport means for transporting a second medium for heat exchange in the evaporator;
Condensing temperature detection means provided in the condenser;
First medium temperature detecting means for detecting the temperature of the first medium before flowing into the condenser;
Second medium temperature detecting means for detecting the temperature of the second medium before flowing into the evaporator, the amount of change per unit time of the input of the compressor, and the unit time of input of the first transport means When the amount of change per unit time and the amount of change per unit time of the input of the second transport means are smaller than a predetermined value,
The amount of change per unit time of the condensation temperature detected by the condensation temperature detection means is
The amount of change per unit time of the temperature of the first medium detected by the first medium temperature detecting means,
When the change amount per unit time of the temperature of the second medium detected by the second medium temperature detecting means is larger than the first medium mechanism, the first diaphragm mechanism and the second diaphragm mechanism are controlled in the opening direction. The refrigeration cycle apparatus according to claim 8. The refrigeration cycle apparatus according to any one of claims 8 to 12, wherein an outer periphery of a joint of a pipe constituting the refrigeration cycle is covered with a sealing agent containing a polymerization accelerator.