JP6528077B2 - Refrigeration cycle device - Google Patents

Description

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

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

  As refrigerants in these refrigeration cycle apparatuses, it is specified by the US ASHRAE 34 standard that fluorocarbons (fluorocarbons are described as R ○○ or R ○○○. Hereinafter, they are shown as R ○○ or R ○○○ Halogenated hydrocarbons derived from methane or ethane are known.

  R410A is often used as a refrigerant for a refrigeration cycle apparatus as described above, but the global warming potential (GWP) of the R410A refrigerant is as large as 1730, and there is a problem from the viewpoint of global warming prevention.

  Therefore, 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, a patent) Document 1 or Patent Document 2).

International Publication No. 2012/157764 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 risk of conversion to another compound by reaction. The disproportionation reaction involves large heat release, which may reduce the reliability of the compressor and the refrigeration cycle apparatus. For this reason, when R1123 and R1132 are used for a compressor or a refrigeration cycle apparatus, it is necessary to suppress this disproportionation reaction.

  In view of the above-mentioned conventional problems, the present invention, for example, specifies a compressor form 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, a lubricating oil more suitable to use a working fluid containing R1123 is specified. Further, the present invention provides a refrigeration cycle apparatus more suitable for using a working fluid containing R1123.

In order to solve the above-mentioned 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 wraps spirally from a mirror plate Is provided with a compression chamber in which the fixed scroll and the orbiting scroll are engaged to form a bi-directionally, and the suction volume of the first compression chamber formed on the wrap outer wall side of the orbiting scroll is the wrap inner wall side of the orbiting scroll The suction volume of the second compression chamber formed in

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

Sectional view of a scroll compressor according to a first embodiment of the present invention The principal part enlarged sectional view of the compression mechanism part of the scroll compressor according to Embodiment 1 of the present invention Sectional view of fixed scroll and orbiting scroll engaged with each other in the scroll compressor according to Embodiment 1 of the present invention The figure which shows the pressure rise curve of the 1st compression chamber in Embodiment 1 of this invention, and a 2nd compression chamber. Sectional view of fixed scroll and orbiting scroll engaged with each other in the scroll compressor according to Embodiment 1 of the present invention The schematic block diagram of the refrigerating-cycle apparatus of Embodiment 1 of this invention Principal part enlarged transverse cross-sectional view of the feed terminal vicinity of the compressor of Embodiment 1 of this invention The schematic block diagram of the refrigerating-cycle apparatus based on Embodiment 2 of this invention Mollier diagram for explaining the operation of the refrigeration cycle apparatus according to the second embodiment of the present invention Mollier diagram for explaining the operation of the refrigeration cycle apparatus according to the second embodiment of the present invention Mollier diagram for explaining the operation of the refrigeration cycle apparatus according to the second embodiment of the present invention The schematic block diagram of the refrigerant | coolant piping joint which comprises the refrigerating-cycle apparatus which concerns on Embodiment 2 of this invention The schematic block diagram of the refrigerating-cycle apparatus based on Embodiment 3 of this invention The schematic block diagram of the refrigerating-cycle apparatus based on Embodiment 4 of this invention Mollier diagram for explaining the operation of the refrigeration cycle apparatus according to the fourth embodiment of the present invention Sectional view of a scroll compressor according to Embodiment 5 of the present invention

  The first invention uses a refrigerant containing 1,1,2-trifluoroethylene as a working fluid, a polyvinyl ether oil as a lubricant for a compressor, and fixed scroll and orbiting scroll in which a spiral wrap rises from an end plate. A compression chamber formed in mesh in both directions, wherein a suction volume of a first compression chamber formed on the wrap outer wall side of the orbiting scroll is formed on a wrap inner wall side of the orbiting scroll It is larger than the suction volume of the chamber. According to this, since it is possible to suppress the heating of the refrigerant in the path to the closed position of the first compression chamber 15a, it is possible to suppress the disproportionation reaction of R1123. In addition, polyvinyl ether oil is relatively low in polarity, and the effect of improving the slidability by the additive is easily exhibited. Therefore, it is possible to suppress local heat generation in the sliding portion and to suppress the autolysis reaction of R1123.

In a second aspect based on the first aspect, the working fluid is a mixed working fluid containing difluoromethane, and the difluoromethane is 30% by weight or more and 60% by weight or less, or contains tetrafluoroethane. A mixed working fluid, wherein the tetrafluoroethane is 30 wt% or more and 60 wt% or less, or a mixed working fluid comprising difluoromethane and tetrafluoroethane, wherein the difluoromethane and tetrafluoroethane are mixed And
The mixing ratio of 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, refrigeration 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 antiwear agent. According to this, the anti-wear agent adsorbs to the surface of the sliding portion to reduce friction, thereby suppressing heat generation, thereby suppressing the autolysis reaction of the R1123 refrigerant.

  According to a fourth invention, in the first or second invention, the polyvinyl ether oil contains a phenolic antioxidant. According to this, since the phenolic antioxidant rapidly captures the radicals generated in 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 prepared by mixing 1% to less than 50% of terpenes or terpenoids with a lubricating oil having a viscosity higher than that of a base oil, or terpenes or It is a lubricating oil in which an additive oil prepared by mixing in advance a lubricating oil of an ultra high viscosity equal to or more than the terpenoids and adjusting the viscosity to the same level as the base oil 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 a wire obtained by applying and baking a thermosetting insulating material 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 can be kept high even when the coil is immersed in the liquid refrigerant, and the discharge can be suppressed. As a result, decomposition of the R1123 refrigerant can be suppressed.

  A seventh invention is according to the first or second invention, wherein the sealed container has a feeding terminal installed at an opening through an insulating member, and a connection terminal for connecting the feeding terminal to a lead. And the doughnut-shaped insulating member is disposed on the power supply terminal inside the sealed container in close contact with the insulating member. According to this, since the insulator is added to the feeding terminal inside the metal casing, the insulation failure of the feeding terminal can be suppressed by extending the shortest distance between the conductors, and the ignition by the discharge energy of R1123 is prevented. . In addition, hydrogen fluoride generated when R1123 is decomposed is prevented from coming into contact with the glass insulator, thereby preventing corrosion and breakage of the glass insulator.

  An eighth invention is a compressor according to any one of the first to seventh inventions, a condenser for cooling a refrigerant gas compressed to a high pressure by the compressor, and a high pressure refrigerant liquefied by the condenser. The refrigeration cycle apparatus is configured by connecting a throttling mechanism that decompresses the pressure and an evaporator that gasifies the refrigerant that has been decompressed by the throttling mechanism by piping. According to this, while suppressing the disproportionation reaction of R1123, refrigeration capacity and COP can be improved.

  A ninth aspect of the invention relates to the eighth aspect, wherein the condensation temperature detection means provided in the condenser is provided, and a 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 throttling 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 5 K or more considering the safety margin from the critical pressure, By controlling the degree of opening of the throttling mechanism, it is possible to prevent the condensation pressure from being increased excessively, so a disproportionation that may occur as a result of an excessive pressure rise (as a result of close intermolecular distances). The reaction can be suppressed, and the reliability of the device can be secured.

  A tenth invention according to the eighth invention comprises a high pressure side pressure detection means provided between the discharge portion of the compressor and the inlet of the throttling mechanism, wherein the critical pressure of the working fluid and the high pressure side pressure detection The opening degree of the throttling mechanism is controlled so that the difference between the pressure detected by the means and the pressure is 0.4 MPa or more. According to this, with respect to the working fluid including R1123, in particular, when using a non-azeotropic refrigerant having a large temperature gradient, the refrigerant pressure can be detected more accurately, and further, using the detection result, Since the degree of opening control can be performed and the high-pressure side pressure (condensing pressure) in the refrigeration cycle apparatus can be lowered, disproportionation reaction can be suppressed, and the reliability of the apparatus can be improved.

  According to an eleventh aspect of the present invention, in the eighth aspect, the condenser outlet temperature detection means provided between the condenser and the throttling mechanism, the condensation temperature detected by the condensation temperature detection means and the condenser outlet The opening degree of the throttling mechanism is controlled so that the difference between the condenser outlet temperature detected by the temperature detecting means is 15 K or less.

  According to this, the opening degree control of the throttling 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. Since an excessive pressure rise can be prevented, disproportionation reaction can be suppressed and the reliability of the device can be improved.

  A twelfth invention is according to the eighth invention, a first conveying means for conveying the first medium heat-exchanged by the condenser, and a second conveying means for conveying the second medium heat-exchanged by the evaporator. Condensing temperature detecting means provided in the condenser, first medium temperature detecting means for detecting the temperature of the first medium before flowing into the condenser, and second medium before flowing into the evaporator A second medium temperature detection means for detecting the temperature of the first transfer means, the change amount per unit time of the input of the compressor, the change amount per unit time of the input of the first transfer means, the input of the second transfer means The first medium temperature detection means detects the change amount per unit time of the condensation temperature detected by the condensation temperature detection means when the change amount per unit time is smaller than a predetermined value determined in advance. 1 change in temperature of medium per unit time and Wherein when the is larger than any of the amount of change per unit time of the temperature of the second medium detecting a second medium temperature detecting means, and controls the throttle mechanism in the opening direction. According to this, it is considered that the pressure increase due to the disproportionation reaction is caused when a sudden change occurs in the condensation temperature when the appearance of the surrounding medium does not change, so that the opening direction of the throttling mechanism is opened. Control. By doing so, it becomes possible to improve the reliability of the device.

  In a thirteenth invention according to any one of the eighth to twelfth inventions, the outer periphery of the joint of the 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 sealing agent and the working fluid containing R1123 react with each other to generate a polymerization product, so that the product is visually recognized. While it becomes easy to confirm a leak, the polymerization product acts as a hindrance of the refrigerant flow discharged | emitted outside, and refrigerant | coolant leak suppression becomes possible.

  In a fourteenth invention according to any one of the first to seventh inventions, the discharge chamber always communicates with the compression chamber through the discharge hole. According to this, even if the compression mechanism supplies the electric power to the motor without performing the compression operation, and the electric motor heats the refrigerant inside the closed container as a heating element and the refrigerant pressure rises, the compression chamber is discharged via the discharge hole. The pressure acts to reversely rotate the compression mechanism to release the pressure in the closed container toward the low pressure side of the refrigeration cycle, thereby making it possible to avoid an abnormal pressure rise which is a condition for generating disproportionation reaction.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The present invention is not limited by the embodiment.

Embodiment 1
FIG. 6 shows a system configuration diagram of a refrigeration cycle apparatus using a compressor according to the first embodiment of the present invention.

  As shown in FIG. 6, when the refrigeration cycle apparatus of the present embodiment is described as, for example, a cycle dedicated to cooling, it is mainly composed of a compressor 61, a condenser 62, a throttling mechanism 63, and an evaporator 64. These devices are connected by pipes so as to circulate the working fluid (refrigerant).

  In the refrigeration cycle apparatus configured as described above, the refrigerant changes to a liquid by pressurization and cooling, and changes to a gas by depressurization and heating. The compressor 61 is driven by a motor, pressurizes the low-temperature low-pressure gaseous refrigerant to the high-temperature high-pressure gaseous refrigerant, and is conveyed to the condenser 62. The condenser 62 is cooled and condensed by air blown by a fan or the like to become a low temperature / high pressure liquid refrigerant. The liquid refrigerant is decompressed by the throttling mechanism 63 and is partially transported to a low temperature / low pressure gaseous refrigerant, and the rest is transported to the evaporator 64 as a low temperature / low pressure liquid refrigerant. The evaporator 64 is heated and evaporated by the air blown by a fan or the like, and turns into a low-temperature low-pressure gaseous refrigerant, and this cycle is again sucked and pressurized by the compressor 61.

  Moreover, although the said embodiment demonstrated as a refrigerating-cycle apparatus only for air_conditioning | cooling, it is possible to operate as a heating-cycle apparatus via a four-way valve etc. of course, and to implement.

  The heat transfer pipe forming the refrigerant flow path of the heat exchanger of at least one of the condenser 62 and the evaporator 64 is preferably an aluminum refrigerant pipe containing aluminum or an aluminum alloy, and in particular, a plurality of refrigerants A flat tube with flow holes is desirable to lower the condensation temperature or to increase the evaporation temperature.

  The working fluid (refrigerant) sealed in the refrigeration cycle apparatus according to the present embodiment is a mixture of two-component systems consisting of (1) R1123 (1,1,2-trifluoroethylene) and (2) R32 (difluoromethane). It is a working fluid, in particular, a mixed working fluid in which R 32 is 30% by weight or more and 60% by weight or less.

  In the application to the compressor described later, the disproportionation reaction of R1123 can be suppressed by mixing 30% by weight or more of R32 with R1123. In addition, the disproportionation reaction can be further suppressed as the concentration of R32 is higher. This means that the action of alleviating the disproportionation reaction due to the small polarization to the fluorine atom of R32 and the behavior at the time of phase change such as condensation and evaporation become unity because R1123 and R32 have similar physical properties. The disproportionation reaction of R 1123 can be suppressed by the action of reducing the reaction opportunity of disproportionation due to

  Further, the mixed refrigerant of R1123 and R32 has an azeotropic point at 30% by weight of R32 and 70% of R1123 and there is no temperature slip, so that the same handling as a single refrigerant is possible. That is, since mixing of 60% by weight or more of R32 may increase temperature slippage and may make it difficult to handle the same as a single refrigerant, it is desirable to mix R32 of 60% by weight or less. In particular, it is desirable to mix R32 at 40 wt% or more and 50 wt% or less in order to prevent disproportionation and to make the temperature slip smaller because it approaches the azeotropic point, and to facilitate the design of the device.

Tables 1 and 2 show that the pressure and temperature of the refrigeration cycle and the displacement of the compressor are the same at the mixing ratio where R32 is 30% by weight or more and 60% by weight or less among the mixed working fluids of R1123 and R32 The refrigeration capacity and cycle efficiency (COP) were calculated and compared to R410A and R1123.

  First, the calculation conditions of 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 advanced, 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, in consideration of actual operating conditions, the cooling calculation conditions in Table 1 correspond to the cooling operation of the air conditioner (room dry bulb temperature 27 ° C., wet bulb temperature 19 ° C., outdoor dry bulb temperature 35 ° C.) The evaporation temperature was 15 ° C., the condensation temperature was 45 ° C., the degree of superheat of the refrigerant sucked into the compressor was 5 ° C., and the degree of subcooling of 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 degree of superheat of the refrigerant sucked into the compressor was 2 ° C., and the degree of subcooling of the condenser outlet was 12 ° C.

  From Table 1 and Table 2, by mixing R32 at 30 wt% or more and 60 wt% or less, the refrigeration capacity is increased by about 20% during cooling and heating operation as compared to R410A, 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, in view of prevention of disproportionation, magnitude of temperature slip, capacity during cooling operation / heating operation, and COP (that is, compression described later) Mixture containing 30% by weight or more and 60% by weight or less of R 32 is desirable, and more preferably 40% by weight or more and 50% by weight or less of R 32 Is desirable.

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

  In the application to the compressor to be described later, the disproportionation reaction of R1123 can be suppressed by mixing 30% by weight or more of R125. In addition, the disproportionation reaction can be further suppressed as the concentration of R125 is higher. This means that the action of alleviating the disproportionation reaction due to the small polarization of R125 to the fluorine atom and the behavior at the time of phase change such as condensation and evaporation become unity because R1123 and R125 have similar physical properties. The disproportionation reaction of R 1123 can be suppressed by the action of reducing the reaction opportunity of disproportionation due to In addition, since R125 is a nonflammable refrigerant, R125 can reduce the flammability of R1123.

  Tables 3 and 4 show that the pressure and temperature of the refrigeration cycle and the displacement of the compressor are the same at the mixing ratio where R125 is 30% by weight or more and 60% by weight or less among the mixed working fluids of R1123 and R125. The refrigeration capacity and cycle efficiency (COP) were calculated and compared to R410A and R1123. The calculation conditions are the same as in Tables 1 and 2.

  According to 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%, as compared to R410A. .

  In particular, by mixing R125 at 40% by weight or more and 50% by weight or less, disproportionation of R1123 can be prevented and the discharge temperature can be reduced. Becomes easy. Furthermore, the global warming potential can be reduced to 50 to 100% of R410A.

As described above, in the two-component system of R1123 and R125, in view of prevention of disproportionation, reduction of combustibility, ability during cooling operation / heating operation, COP, discharge temperature (that is, it will be described later) Mixing ratio suitable for air conditioning equipment using a compressor), a mixture containing 30% by weight or more and 60% by weight or less of R125 is desirable, and more preferably 40% by weight or more and 50% by weight or less of R125 A mixture containing is 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). A mixed working fluid comprising a mixture of R32 and R125 in a mixing ratio of 30 to less than 60% by weight, and a mixing ratio of R1123 in a range of 40 to 70% by weight. It may be

  In the application to the compressor described later, the disproportionation reaction of R1123 can be suppressed when the mixing ratio of R32 and R125 is 30% by weight or more. In addition, the disproportionation reaction can be further suppressed as the mixing ratio of R32 and R125 combined increases. Also, R125 reduces the flammability of R1123.

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

  According to Tables 5 and 6, when the mixing ratio of R32 and R125 is 30 wt% or more and 60 wt% or less, the refrigerating capacity is 107 to 116% and the cycle efficiency (COP) is 93 to 96 as compared with R410A. It becomes%.

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

  In the second modification of the working fluid, 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 0% to 100% by weight. Well, if you want to increase the refrigeration capacity, increase the mixing ratio of R32, conversely decrease the mixing ratio of R32, increase the mixing ratio of R125, reduce the discharge temperature, and reduce the flammability be able to.

  As described above, in the three-component system of R1123, R32, and R125, in view of prevention of disproportionation, reduction of combustibility, ability during cooling operation / heating operation, COP, discharge temperature (that is, And a mixture of R32 and R125, and the sum of R32 and R125 is preferably 30% by weight or more and 60% by weight or less. Desirably, a mixture containing 40% by weight or more and 50% by weight or less of the sum of R 32 and R 125 is desirable.

  FIG. 1 is a longitudinal sectional view of a scroll compressor according to a first embodiment of the present invention, and FIG. 2 is an enlarged sectional view of an essential part of a compression mechanism portion of FIG. Hereinafter, the operation and action of the scroll compressor will be described.

  As shown in FIG. 1, the scroll compressor according to the first embodiment is configured to include a closed container 1 and a compression mechanism 2, a motor unit 3, and an oil storage unit 20 inside thereof. The details of the compression mechanism will be described with reference to FIG. 2. The main bearing member 11 of the shaft 4 fixed by welding or shrink fitting in the closed container 1 and the fixed scroll 12 bolted on the main bearing member 11. And a scroll-type compression mechanism 2 is configured by sandwiching the orbiting scroll 13 engaged with the fixed scroll 12. The fixed scroll 12 and the orbiting scroll 13 each have a structure in which a spiral wrap rises (projects) from a mirror plate.

  Between the orbiting scroll 13 and the main bearing member 11, a rotation restraint mechanism 14 such as an Oldham ring or the like for guiding the orbiting scroll 13 so as to perform circular orbit motion while preventing rotation of the orbiting scroll 13 is provided. The eccentrically driving the orbiting scroll 13 by the portion 4a causes the orbiting scroll 13 to make a circular orbit motion. As a result, the compression chamber 15 formed between the fixed scroll 12 and the orbiting scroll 13 moves from the outer peripheral side toward the central portion while reducing the volume, whereby the suction communicated with the outside of the sealed container 1 The working fluid is sucked from the suction port 17 on the outer peripheral portion of the pipe 16 and the fixed scroll 12 and is closed in the compression chamber 15 and then compressed. The working fluid having reached a predetermined pressure pushes the reed valve 19 from the discharge hole 18 at the central portion of the fixed scroll 12 and is discharged into the discharge chamber 22. The discharge chamber 22 is a space formed by the muffler 24 provided on the end plate surface of the fixed scroll 12 so as to cover the discharge hole 18. The working refrigerant discharged to the discharge chamber 22 is discharged into the closed container 1 through the communication passage provided in the compression mechanism. The working refrigerant discharged into the closed container 1 is discharged from the closed container 1 to the refrigeration cycle through the discharge pipe 23.

  In addition, in order to avoid damage due to excessive deformation of the reed valve 19, a valve stop 21 for regulating the lift amount is provided. The reed valve 19 is provided, for example, on the end surface of the fixed scroll 12 at the position where the bypass hole 68 of the end plate of the fixed scroll 12 is formed.

FIG. 3 is a view in which the orbiting scroll 13 is engaged with the fixed scroll 12. As shown in FIG. 3, in the compression chamber 15 formed by the fixed scroll 12 and the orbiting scroll 13, the first compression chamber 15 a formed on the wrap outer wall side of the orbiting scroll 13 is formed on the lap inner wall side. There is a second compression chamber 15b, and the suction volume of the first compression chamber 15a is larger than the suction volume of the second compression chamber 15b. That is, since the timings for confining the working fluid are different, the pressures of the first compression chamber 15a and the second compression chamber 15b as a pair are also different.

  FIG. 4 shows pressure rise curves of the first compression chamber 15a and the second compression chamber 15b. Since the first compression chamber 15a and the second compression chamber 15b originally have different timings of confinement, the start points of the pressure curves do not match, but here the timing of confinement is matched to clarify the difference. This will be described using a graph. It can be seen from FIG. 4 that the pressure change rate is larger in the second compression chamber 15b having a smaller suction volume than in the first compression chamber 15a. That is, the pressure difference .DELTA.Pb between the second compression chamber 15b-1 formed one before and the second compression chamber 15b-0 formed next is also larger than the pressure difference .DELTA.Pa of the first compression chamber. In the second compression chamber 15b, the working fluid is likely to leak through the radial contact of the wrap.

  Further, a pump 25 is provided at one end of the shaft 4 and disposed so that the suction port of the pump 25 exists in the oil reservoir 20. Since the pump 25 is driven at the same time as the scroll compressor, the pressure of the oil (compressor lubricating oil, refrigerator oil) 6 in the oil storage unit 20 provided at the bottom of the closed vessel 1 to pressure conditions and operating speed Regardless of it, it can be sucked up reliably and the worry of running out of oil is eliminated. The oil 6 sucked up by the pump 25 is supplied to the compression mechanism 2 through an oil supply hole 26 extending in the shaft 4. Before or after the oil 6 is sucked by the pump 25, if foreign matter is removed from the oil 6 with an oil filter or the like, the foreign matter can be prevented from mixing into the compression mechanism 2, and the reliability can be further improved.

  The oil 6 introduced to the compression mechanism 2 is substantially equivalent to the discharge pressure of the scroll compressor, and also serves as a back pressure source for the orbiting scroll 13. As a result, the orbiting scroll 13 does not separate from or collide with the fixed scroll 12, and stably exerts a predetermined compression function. Further, a part of the oil 6 enters the fitting portion between the eccentric shaft portion 4a and the orbiting scroll 13 and the bearing portion 66 between the shaft 4 and the main bearing member 11 so as to obtain a relief by the supply pressure and own weight. After lubricating each part, it falls and returns to the oil storage unit 20.

  Further, with regard to the position where the working fluid of the first compression chamber 15a and the second compression chamber 15b is confined, in the general symmetrical scroll, as shown by the broken line in FIG. It is formed so as not to have contact with the orbiting scroll 13. In this case, the closed position of the first compression chamber 15a is at point T in FIG. 3, and the working fluid is heated along the path to point T, and R1123 is more stable than conventional refrigerants such as R410A. It is low and may cause disproportionation reaction accompanied by polymerization reaction and large heat release.

  Therefore, the spiral wrap is configured such that the positions where the working fluid is confined in the first compression chamber 15a and the second compression chamber 15b are shifted by approximately 180 degrees. Specifically, with the fixed scroll 12 and the orbiting scroll 13 engaged, the spiral wrap of the fixed scroll 12 is extended to the same extent as the spiral wrap of the orbiting scroll 13. In this case, the position where the first compression chamber 15a encloses the working fluid is point S in FIG. 3, and after the first compression chamber 15a is enclosed, the rotation of the shaft 4 advances by about 180 degrees before the second compression chamber I will confine 15b. Thereby, the influence of the refrigerant temperature rise due to the suction heating can be minimized with respect to the first compression chamber 15a, and the maximum suction volume can be further secured. That is, since the wrap height can be set low, and as a result, the leak clearance (= leakage cross-sectional area) of the radial contact portion of the wrap can be reduced, the leakage loss can be further reduced.

Further, a high pressure region 30 and a back pressure chamber 29 set to an intermediate pressure of high pressure and low pressure are formed on the back surface 13 e of the orbiting scroll 13, a plurality of oil feeding paths 50 are provided, Configure to go through. By applying pressure from the back surface 13e, the orbiting scroll 13 is stably pressed against the fixed scroll 12, and leakage from the back pressure chamber 29 to the compression chamber 15 can be reduced and stable operation can be performed. Further, by providing a plurality of fueling paths 50, it is possible to carry out fueling only to the necessary location. For example, although a certain amount of seal oil is required in the suction stroke before the compression chamber 15 is confined, if a large amount of oil is supplied, suction overheating of the working fluid may occur to cause a reduction in volumetric efficiency. Also, even during compression, if a large amount is supplied, an increase in input due to viscosity loss is caused. Therefore, it is ideal to refuel only the necessary amount to each location, and in order to realize it, a plurality of refueling paths 50 are formed. Moreover, the pressure difference with the compression chamber 15 supplied can be made small by passing the back pressure chamber 29. For example, it is necessary to supply oil from the back pressure chamber 29 set to an intermediate pressure rather than directly supplying oil from the high pressure region 30 to the suction stroke or during compression because the pressure difference is smaller. It is possible to refuel for a limited time. That is, excessive refueling can be prevented, and performance reduction due to suction heating and input increase due to viscosity loss can be suppressed.

  Further, a seal member 78 is disposed on the back surface 13e of the orbiting scroll 13. The inner side of the seal member 78 is divided into a high pressure region 30, the outer side of the seal member 78 is divided into a back pressure chamber 29, and at least one of the oil supply paths 50 is a high pressure region. A back pressure chamber oil supply path 51 from 30 to the back pressure chamber 29 and a compression chamber oil supply path 52 from the back pressure chamber 29 to the second compression chamber 15 b are formed. By using the seal member 78, the pressure in the high pressure region 30 and the back pressure chamber 29 can be completely separated, so that the pressure application from the back surface 13e of the orbiting scroll 13 can be stably controlled. Further, by providing the back pressure chamber oil supply path 51 from the high pressure region 30 to the back pressure chamber 29, the oil 6 is supplied to the sliding portion of the rotation restraint mechanism 14 and the thrust sliding portions of the fixed scroll 12 and the orbiting scroll 13. be able to. Further, by providing the compression chamber oil supply path 52 from the back pressure chamber 29 to the second compression chamber 15b, the amount of oil supply to the second compression chamber 15b can be positively increased, and in the second compression chamber 15b. Leakage loss can be suppressed.

  Further, one open end 51 b of the back pressure chamber oil supply path 51 is formed on the back surface 13 e of the orbiting scroll 13, and the seal member 78 is made to come in and the other open end 51 a is always opened in the high pressure region 30. Thus, intermittent refueling can be realized.

  FIG. 5 shows a state in which the orbiting scroll 13 is engaged with the fixed scroll 12 and viewed from the back of the orbiting scroll 13, and the phase is shifted by 90 degrees. As shown in FIG. 5, the rear surface area of the orbiting scroll 13 is partitioned by the seal member 78 into an inner high pressure area 30 and an outer back pressure chamber 29. Since the open end 51 b is open to the back pressure chamber 29 outside the seal member 78 in the state of (II), oil is supplied. On the other hand, in (I) (III) (IV), the open end 51b is opened to the inside of the seal member 78, so oil is not supplied.

  That is, although one open end 51b of the back pressure chamber oil supply passage 51 passes between the high pressure region 30 and the back pressure chamber 29, only when a pressure difference occurs at both open ends 51a and 51b of the back pressure chamber oil supply passage 51. The oil 6 is supplied to the back pressure chamber 29. With this configuration, the amount of oil supply can be adjusted at a rate at which the open end 51b passes the seal member 78, so that the passage diameter of the back pressure chamber oil supply passage 51 can be 10 times or more the size of the oil filter Become.

  As a result, there is no risk of foreign matter biting into the passage and clogging, stable application of back pressure and simultaneously lubrication of the thrust sliding portion and the rotation restraint mechanism 14 can be maintained in a good condition, resulting in high efficiency and high reliability. A scroll compressor can be provided to realize the In the present embodiment, the case where the open end 51a is always in the high pressure region 30 and the open end 51b passes between the high pressure region 30 and the back pressure chamber 29 has been described as an example. Even when the pressure chamber 29 is returned and the open end 51b is always in the back pressure chamber 29, a pressure difference is generated between the both open ends 51a and 51b, so intermittent fueling can be realized and the same effect can be obtained.

  In the case where the pressure application from the back surface 13 e of the orbiting scroll 13 is insufficient, there is a possibility of causing a tilting phenomenon in which the orbiting scroll 13 separates from the fixed scroll 12. In the tilting state, the working fluid leaks from the back pressure chamber 29 to the compression chamber 15 before the closing, so the volumetric efficiency is deteriorated. In order not to generate this, the back pressure chamber 29 needs to maintain a predetermined pressure. Therefore, the compression chamber oil supply path 52 is configured such that the second compression chamber 15b after closing the working fluid and the back pressure chamber 29 communicate with each other. As a result, the pressure in the back pressure chamber 29 becomes a predetermined pressure higher than the suction pressure, so that the tilting phenomenon can be prevented, and high efficiency can be realized. Further, even if tilting occurs, the pressure of the second compression chamber 15b can be introduced to the back pressure chamber 29, so early return to normal operation is possible.

  In the present embodiment, the suction volume of the first compression chamber 15a formed on the wrap outer wall side of the orbiting scroll 13 is larger than the suction volume of the second compression chamber 15b formed on the lap inner wall side of the orbiting scroll 13. doing. As a result, the path to the closed position of the first compression chamber 15a can be shortened, and heating of the refrigerant before the start of compression can be suppressed, so that disproportionation reaction of R1123 can be suppressed. .

  Further, in the compressor of the present embodiment, polyvinyl ether oil is used as a lubricant for the compressor. Moreover, as an additive added to lubricating oil for compressors, it contains at least 1 sort (s) of additive of a phosphoric acid ester type anti-wear agent and a phenolic antioxidant.

  Specifically, tributyl phosphate, tripentyl phosphate, trihexyl phosphate, triheptyl phosphate, trioctyl phosphate, trinyl phosphate, tridecyl phosphate, triundecyl phosphate, triundecyl phosphate, tridodecyl phosphate as phosphate antiwear agents. Phosphate, tritetradecyl phosphate, tripentadecyl phosphate, trihexadecyl phosphate, triheptadecyl phosphate, trioctadecyl phosphate, trioleyl phosphate, triphenyl phosphate, tricresyl phosphate, trixylenyl phosphate, cresyl diphenyl phosphate, xylose Renyl diphenyl phosphate etc. are mentioned. Usually, by adding 0.1 to 3 wt% of phosphate ester type anti-wear agent to refrigerator oil, it is efficiently adsorbed on the surface of the sliding part to create a film with small shear force on the sliding surface. The wear prevention effect is obtained.

  According to this, it is possible to obtain the effect of suppressing the self decomposition reaction of the R1123 refrigerant by suppressing the local heat generation of the sliding portion by 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, butyl hydroxytoluene, dodecyl gallate and the like can be used. These antioxidants can capture a radical efficiently and can prevent reaction by adding 0.1 to 1 wt% with respect to a base oil. In addition, the coloring of the base oil itself by the antioxidant can be minimized.

  According to this, the phenol-based antioxidant effectively captures the radicals generated in the closed container 1 to obtain the effect of suppressing the decomposition reaction of R1123.

Further, in order to prevent reaction of highly reactive molecules containing a double bond and a fluorine atom such as R1123, about 5% of limonene may be added to the amount of the R1123 refrigerant. The compressor of the present invention and the refrigeration cycle apparatus using the compressor are a closed system, and as described above, the lubricating oil is enclosed as a base oil. Generally, the viscosity of the lubricating oil used as the base oil to be enclosed in such a compressor is generally from about 32 mm2 / s to 68 mm2 / s, while the viscosity of limonene is as low as about 0.8 mm2 / s. The viscosity drops sharply to 60 mm 2 / s when mixed about 5%, 48 mm 2 / s when mixed 15%, and 32 mm 2 / s when mixed 35%. Therefore, mixing a large amount of limonene to prevent the reaction of R1123 affects the reliability of the compressor and refrigeration cycle device, such as the decrease in viscosity of the lubricating oil, wear due to poor lubrication, and metal soap contact due to metal contact on the sliding surface. Do.

  The lubricating oil of the compressor according to the present embodiment may be based on a high viscosity lubricating oil in advance or may be mixed with limonene in order to compensate for the decrease in viscosity of the base oil caused by the mixing of a suitable amount of limonene to prevent the reaction. The proper viscosity of the lubricating oil is secured by mixing an amount of the ultra-high viscosity lubricating oil equal to or more 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 68 mm2 / s can be secured by selecting one having a viscosity of about 230 mm2 / s. . In addition, in order to maximize the effect of preventing the reaction of R1123 by limonene, the extreme example may be considered such as increasing the mixing amount of limonene to 70% or 80%, but the viscosity of the high viscosity lubricating oil as the base is 8500 mm2 / It is considered that s or 25000 mm2 / s exceeds 3200 mm2 / s which is the maximum value of ISO standard, and uniform mixing with limonene is also difficult, and practical application is difficult.

  Further, when mixing ultra-high viscosity lubricating oil with limonene in an equal amount, 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. In addition, when mixing limonene and an ultra-high viscosity oil which differ in a viscosity difference, if it mixes, adding ultra-high viscosity oil little by little to limonene, the lubricating oil of a comparatively uniform composition viscosity will be obtained.

  Although limonene is taken as an example in this embodiment, the same effect can be obtained with terpenes or terpenoids, for example, isoprene of hemiterpenes, prenol, geranyl diphosphate of 3-methylbutanoic acid or monoterpenes, cineole , Pinene and sesquiterpenes farnesyl diphosphate, artemisinin, bisabolol, diterpenes geranylgeranyl diphosphate, retinol, retinal, phytol, paclitaxel, forskolin, aphidicoline and triterpenes such as squalene, lanosterol, etc. Compressors and refrigeration cycle devices It can be selected according to the operating temperature and the required lubricating oil viscosity.

  In addition, the illustrated viscosity is a specific example of a compressor having a high pressure vessel, and the same operation can be carried out also with a low pressure vessel compressor used with a lubricating oil viscosity as low as 5 mm2 / s to 32 mm2 / s. Needless to say, similar effects can be obtained.

  It should be noted that although terpenes such as limonene and terpenoids have solubility in plastics, if the mixture is less than about 30%, the effect is small, and the electrical insulation required for the plastic in the compressor is a problem. Not at the same level. However, it is desirable to use polyimide, polyimideamide or polyphenylene sulfide having chemical resistance when there is a problem, such as when long-term reliability is required or when the constant use temperature is high.

Further, in the winding of the motor unit 3 of the compressor of the present embodiment, varnish (a thermosetting insulating material) is applied and baked on a conductor via an insulating film. The thermosetting insulating material may, for example, be a polyimide resin, an epoxy resin, or an unsaturated polyester resin. Among them, the polyimide resin can be polyimidized by applying it in the state of a polyamic acid which is a precursor and baking it at around 300.degree. It is known that the imidization reaction occurs by the reaction of an amine and a carboxylic acid anhydride. Since R1123 refrigerant may react even at short circuit between electrodes, a polyimide acid varnish mainly composed of a polyimide precursor formed by reacting an aromatic diamine and an aromatic tetracarboxylic acid dianhydride on a motor winding is used. The application can prevent a short circuit between the electrodes.

  For this reason, even when the coil of the motor unit 3 is immersed in the liquid refrigerant, the resistance between the windings can be kept high, and the discharge between the windings can be suppressed, as a result, the autolysis reaction of the R1123 refrigerant can be suppressed. Effect is obtained.

  FIG. 4 is a partial cross-sectional view showing the structure in the vicinity of the feeding terminal of the compressor according to the present embodiment. In FIG. 4, 71 is a feeding terminal, 72 is a glass insulator, 73 is a metallic lid for holding a feeding terminal, 74 is a flag type terminal connected to the feeding terminal, and 75 is a lead wire. In the compressor according to the present embodiment, a doughnut-shaped insulating member 76 in close contact with the insulating member is disposed on the feed terminal inside the hermetic container 1 of the compressor. The doughnut-shaped insulating member is the one that maintains insulation and is most suitable for being resistant to hydrofluoric acid. For example, a ceramic gasket or HNBR rubber donut type spacer may be mentioned. It is essential for the doughnut-shaped insulating member to be in intimate contact with the glass insulator, but it is preferable that the insulating member be in intimate contact with the connection terminal as well.

  In the feed terminal configured in this way, the creeping distance between the feed terminal and the inner surface of the cover of the cover is longer by the doughnut-shaped insulating member, and terminal tracking is prevented and ignition by the discharge energy of R1123 is prevented. Can. It also prevents the hydrofluoric acid generated by the decomposition of R1123 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 hole 18 is opened in the closed container 1 and the inside of the closed container 1 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 hole 18 is opened in the closed container 1 and the inside of the closed container 1 is filled with the refrigerant before being compressed in the compression chamber 15, heating is performed in the closed container 1. In the configuration in which temperature rise easily occurs before it is introduced into the compression chamber 15, the temperature lowering by the introduction of low temperature refrigerant in the compression chamber 15 becomes more remarkable, which is desirable in order to suppress the disproportionation reaction of R1123.

  In the high pressure shell type compressor, the refrigerant discharged from the discharge hole 18 is allowed to pass around the motor unit 3 and heated by the motor unit 3 in the closed container 1. You may comprise so that it may be discharged outside. According to this, since the refrigerant temperature in the compression chamber 15 can be lowered even if the temperature of the refrigerant discharged from the discharge pipe 23 is equal, it is desirable for suppressing the disproportionation reaction of R1123.

Second Embodiment
FIG. 8 shows a refrigeration cycle apparatus 101 according to a second embodiment of the present invention. The refrigeration cycle apparatus 101 of the present embodiment is connected by the refrigerant pipe 106 in the order of the compressor 102, the condenser 103, the expansion valve 104 which is a throttling mechanism, and the evaporator 105 to constitute a refrigeration cycle circuit. A working fluid (refrigerant) is enclosed in the refrigeration cycle circuit.

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

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

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

  For the expansion valve 104, for example, a pulse motor drive type electronic expansion valve or the like is used.

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

  As the ambient medium, air in the atmosphere may be used, water, or brine such as ethyl glycol may be used, and when the refrigeration cycle apparatus 101 is a binary refrigeration cycle, refrigeration may be performed. Preferred refrigerants for the cycle and operating temperature range are, for example, hydrofluorocarbons (HFCs), hydrocarbons (HCs), carbon dioxide and the like.

  When the surrounding medium is air, an axial-flow fan such as a propeller fan, a cross-flow fan, or a centrifugal fan such as a turbo fan is used as the fluid machine 107a and b for driving the surrounding medium. A centrifugal pump or the like is used.

  When the refrigeration cycle apparatus 101 is a binary refrigeration cycle, the compressor plays the role of fluid machines 107a and 107b for conveying the surrounding medium.

  In the condenser 103, a condensation temperature detection means is provided at a point where the refrigerant flowing inside thereof flows in two phases (a state in which gas and liquid are mixed) (hereinafter referred to as "two-phase pipe of condenser" in the present specification). 110a is installed, and the refrigerant temperature can be measured.

  Further, between the outlet of the condenser 103 and the inlet of the expansion valve 104, a condenser outlet temperature detection means 110b is installed. The condenser outlet temperature detection means 110b can detect the degree of supercooling at the inlet of the expansion valve 104 (the value obtained by subtracting the condenser temperature from the expansion valve inlet temperature).

  In the evaporator 105, an evaporation temperature detecting means 110c is provided at a point where the refrigerant flowing inside thereof flows in two phases (hereinafter referred to as "two-phase pipe of the evaporator" in the present specification). It is possible to measure the temperature of the refrigerant.

  A suction temperature detection unit 110 d is provided at the suction portion of the compressor 102 (between the outlet of the evaporator 105 and the inlet of the compressor 102). Thereby, measurement of the temperature (intake temperature) of the refrigerant drawn into the compressor 102 is possible.

  The temperature detection means 110a to 110d may use, for example, an electronic thermostat connected in contact with a pipe through which a refrigerant flows or an outer pipe of a heat transfer pipe. Electronic thermostats may be used.

  High pressure side pressure detection means for detecting the pressure on the high pressure side of the refrigeration cycle (the area where the refrigerant from the outlet of the compressor 102 to the inlet of the expansion valve 104 exists at high pressure) between the condenser 103 outlet and the inlet of the expansion valve 104 115a is installed.

  At the outlet of the expansion valve 104, a low pressure side pressure detection means 115b is provided which detects the pressure on the low pressure side of the refrigeration cycle (the area where the refrigerant from the expansion valve 104 outlet to the inlet of the compressor 102 exists at low pressure).

As the pressure detection means 115a, 115b, for example, one that converts the displacement of the diaphragm into an electrical signal is used. In place of the high pressure side pressure detection means 115a and the low pressure side pressure detection means 115b, a differential pressure gauge (a measurement means for measuring the pressure difference between the expansion valve 104 and the inlet and outlet) may be used.

  In the above description, the temperature detectors 110a to 110d and the pressure detectors 115a and 115b are all described, but in the control described later, it is possible to omit the detector that does not use the detection value. 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 superheat 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 expansion valve 104 is controlled such that the degree of superheat becomes a predetermined target degree of superheat (for example, 5 K).

  Alternatively, discharge temperature detection means (not shown) may be further provided in the discharge portion of the compressor 102, and control may be performed 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 expansion valve 104 is controlled such that the degree of superheat becomes a predetermined target degree of superheat.

  Next, control in the case of a unique operating state in which the possibility of disproportionation reaction increases is described.

  In the present embodiment, when the temperature detection value of the condensation temperature detection means 110 a becomes excessive, the expansion valve 104 is opened to perform control to lower the high pressure side working fluid pressure / temperature in the refrigeration cycle apparatus 101.

Generally, in a refrigerant other than carbon dioxide, it is necessary to prevent the supercritical condition from exceeding the critical point (a point described as T _cri in FIG. 9 described later). In the supercritical state, the substance is neither gas nor 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 standard, and from this temperature, the expansion temperature is kept within a predetermined value (5 K) so that the condensation temperature does not approach. The opening degree of the valve 104 is controlled. In addition, when using the working fluid (mixed refrigerant) containing R1123, it controls so that the temperature of a working fluid does not become (critical temperature -5) ° C or more using the critical temperature of the mixed refrigerant.

  Specifically, this will be described using the Mollier diagram of FIG. In FIG. 9, a refrigeration cycle under an excessive pressure condition which causes disproportionation reaction is shown by a solid line (EP) and a refrigeration cycle under normal operation is shown by a broken line (NP).

  If the temperature value at the condensation temperature detection means 110a provided in the two-phase pipe of the condenser 103 is within 5 K with respect to the critical temperature stored in advance in the controller (EP in FIG. 9), expansion occurs The valve 104 is controlled to open. As a result, as shown in NP of FIG. 9, the condensation pressure on the high pressure side of the refrigeration cycle apparatus 101 is reduced, so it is possible to suppress the disproportionation reaction caused by the excessive increase of the refrigerant pressure. When the leveling reaction occurs, it is possible to suppress the pressure rise.

  In the above 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 opening degree of the expansion valve 104, the working fluid including R1123 is azeotropically Alternatively, if there is no temperature difference (temperature gradient) between the dew point and the boiling point of the working fluid containing R 1123 in the condenser 103 or the temperature is pseudo-azeotropic, use the condensation temperature as an index instead of the condensation pressure It is particularly preferable because it can.

<Modification 1 of control method>
Alternatively, as described above, by comparing the critical temperature and the condensation temperature, the high pressure (refrigerant refrigerant pressure in the condenser) state of the refrigeration cycle apparatus 101 is indirectly detected, and the appropriate operation is performed by the expansion valve 104 or the like. Instead of the control method instructed to the above, the expansion valve 104 opening degree control may be performed based on the directly measured pressure.

  FIG. 10 is a diagram showing this control operation in a Mollier diagram. In FIG. 10, a refrigeration cycle in which an excessive pressure rise is occurring from the compressor discharge portion to the condenser and the expansion valve inlet is indicated by a solid line (EP), and a broken line (NP) indicates the above-described excessive pressure state. The refrigeration cycle in the detached state is shown.

During operation, for example, a pressure difference obtained by subtracting the condenser outlet pressure P _cond detected by the high-pressure side pressure detection means 115 a from the pressure (critical pressure) P _cri at the critical point stored in advance in the control device is predetermined. If it becomes smaller than the value (Δp = 0.4MPa) (EP in FIG. 10), whether disproportionation reaction occurred in the working fluid including R1123 from the discharge of the compressor 102 to the inlet of the expansion valve 104, Alternatively, it is determined that there is a high possibility of the occurrence, and the expansion valve 104 is controlled to be opened to avoid continuation of the high pressure condition.

  As a result, the refrigeration cycle in FIG. 10 acts on the side where the high pressure (condensing pressure) decreases as in the 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 in the case of a non-azeotropic state in the working fluid containing R1123, 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. 11 is a diagram showing this control operation in a Mollier diagram. In FIG. 11, a refrigeration cycle under an excessive pressure condition causing the disproportionation reaction is denoted by EP, indicated by a solid line, and a refrigeration cycle under normal operation is denoted by NP, by a broken line.

  Generally, in the refrigeration cycle apparatus, the temperature of the refrigerant in the condenser is a certain degree with respect to the surrounding medium by appropriate control of the refrigeration cycle such as the expansion valve and the compressor, heat exchanger size and refrigerant charge optimization. To be high. The degree of supercooling is generally about 5K. Similar measures are taken with working fluids containing 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 expansion valve 104 tends to increase as shown by EP in FIG. Therefore, in the present embodiment, the degree of opening of the expansion valve 104 is controlled based on the degree of supercooling of the refrigerant at the inlet of the expansion valve 104.

In the present embodiment, the degree of supercooling of the refrigerant at the inlet of the expansion valve 104 during normal operation is considered to be 5 K, and the opening degree of the expansion valve 104 is controlled by using 15 K three times that value as a standard. There is. The reason why the threshold degree of supercooling is tripled is that the degree of supercooling may change in that 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. Then, when the degree of supercooling at the inlet of the expansion valve 104 reaches a predetermined value (15 K), the expansion valve 104 operates in the direction of opening to decrease the condensation pressure which is the high pressure portion of the refrigeration cycle apparatus 101 Control (solid line to broken line in FIG. 11). Since the decrease in the condensation pressure is the same as the decrease in the condensation temperature, the condensation temperature decreases from Tcond1 to Tcond2, and the degree of supercooling at the inlet of the expansion valve 104 changes from Tcond1-Texin to Tcond2-Texin And the degree of supercooling decreases (here, the working fluid temperature at the inlet of the expansion valve 104 does not change and is assumed to be Texin). As described above, since the degree of supercooling also decreases with the decrease in the condensation pressure in the refrigeration cycle apparatus, it is understood that the control of the condensation pressure in the refrigeration cycle apparatus is possible even when the degree of supercooling is used as a reference.

  FIG. 12 shows a pipe joint 117 which constitutes 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 example, in a split-type air conditioner (air conditioner) for home use, it is composed of 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 can not be integrated due to their construction, they are connected at the installation site 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 work failure, the refrigerant leaks from the joint portion, which adversely affects the performance of the device. In addition, since the working fluid itself including R1123 is a greenhouse gas having a warming effect, it may adversely affect the global environment. Therefore, it is required to quickly detect and correct the refrigerant leak.

  There are methods of detecting a refrigerant leak by applying a detection agent to the site and detecting if bubbles are generated, a method of using a detection sensor, and the like, all of which require a large amount of work.

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

  Specifically, in the working fluid containing R1123, generation of polytetrafluoroethylene, which is one of fluorinated carbon resins, is utilized when a polymerization reaction occurs. The working fluid containing R1123 and the polymerization accelerator are intentionally brought into contact at the leakage point so that polytetrafluoroethylene is precipitated and solidified at the leakage point. As a result, it becomes easy to visually detect a leak easily, so it is possible to reduce the time taken to detect and repair the leak.

  Furthermore, since the generation site of polytetrafluoroethylene is a leak site of the working fluid containing R1123, a polymerization product is generated and attached to the site that prevents the leak by itself, so it is also possible to suppress the leak amount. It becomes.

Third Embodiment
FIG. 13 shows a refrigeration cycle apparatus 130 according to a third embodiment of the present invention. The difference between the configurations of the refrigeration cycle apparatus 130 shown in FIG. 13 and the refrigeration cycle apparatus 101 of the second embodiment resides in that a bypass pipe 113 having an on-off valve connected to the inlet and outlet of the expansion valve 104 is newly installed. A point is that a purge line having a relief valve 114 is provided between the outlet of the condenser 103 and the inlet of the expansion valve 104. The opening side of the relief valve 114 is disposed outside the room. In FIG. 13, the descriptions of the temperature detection units 110 a to 110 d and the pressure detection units 115 a and 115 b described with reference to FIG. 8 are omitted.

  The control method described in the second embodiment (for example, the expansion valve 104 so that the value obtained by subtracting the working fluid temperature measured in the two-phase pipe of the condenser 103 from the critical temperature of the working fluid containing R1123 becomes 5 K or more). The expansion valve 104 performs a control method of controlling the opening degree or a control method of controlling the difference between the critical pressure of the working fluid and the pressure detected by the high pressure side pressure detection means 115a to be 0.4 MPa or more. Even when the opening degree is opened, there is a possibility that the pressure drop can not be improved or a situation where it is desired to increase the pressure drop rate.

  Therefore, when the above situation occurs, open the on-off valve provided in the bypass pipe 113 of the present embodiment and allow the refrigerant to flow through the bypass pipe 113, thereby rapidly working fluid pressure on the high pressure side. It is possible to lower the refrigeration cycle apparatus 130 and prevent the refrigeration cycle apparatus 130 from being damaged.

  Furthermore, in addition to the control to increase the opening degree of the expansion valve 104 and the control of the on-off valve provided in the bypass pipe 113, if the compressor 102 is emergency stopped, the refrigeration cycle device 130 is prevented from being damaged. preferable. When the compressor 102 is stopped in an emergency, it is desirable not to stop the first transfer means 117a or the second transfer means 117b in order to rapidly lower the working fluid pressure on the high pressure side.

  Even when the above measures are taken, if the disproportionation reaction is not further 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 5 K. 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 detection means 115a is less than 0.4 MPa, the refrigerant pressure in the refrigeration cycle apparatus 130 is further increased. Because of the fear, there is a need to release the high-pressure refrigerant to the outside to prevent the refrigeration cycle apparatus 130 from being damaged. Then, the relief valve 114 which purges the working fluid containing R1123 in the refrigerating cycle device 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, from the condenser outlet shown in this embodiment to the expansion valve inlet (at this position, the working fluid is in the supercooled liquid state of high pressure, (Due to the water hammer effect that may occur as a result of the sharp pressure increase accompanying disproportionation reaction) or from the compressor discharge part to the condenser inlet (in this position, the working fluid is a high temperature high pressure gas, molecular It is particularly preferable that the exercise be activated and the disproportionation reaction itself is likely to occur.

  The relief valve 114 is provided on the outdoor unit side. In the case of this configuration, in the case of an air conditioner, there is no discharge of the working fluid to the indoor space, and in the case of the refrigeration unit, the working fluid is not discharged to the display side such as a showcase. As human beings and products are not considered to have direct influence.

  Note that 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. 14 shows a refrigeration cycle apparatus 140 according to a fourth embodiment of the present invention. The difference between the configurations of the refrigeration cycle apparatus 140 shown in FIG. 14 and the refrigeration cycle apparatus 101 of the first embodiment is the first medium temperature detection means 110e for detecting the temperature of the first medium before flowing into the condenser 103. And second medium temperature detection means 110f for detecting the temperature of the second medium before flowing into the evaporator 105, detection values of the temperature detection means 110a to 110f, and pressure detection means 115a, 115b, , The input powers of the compressor 102 and the fluid machines 107a and 107b are recorded in an electronic recording device (not shown) for a certain period of time.

  FIG. 15 is a diagram showing the operation of the refrigeration cycle apparatus 140 of the present embodiment on a Mollier chart. In FIG. 15, the refrigeration cycle indicated by EP indicates the condensation pressure at the time of occurrence of disproportionation reaction, and the refrigeration cycle indicated by NP indicates the refrigeration cycle during normal operation. In FIG. 15, the cycle change (e.g., the difference between the evaporation pressure of NP and EP, etc.) when the condensation pressure rises is not shown for the sake of simplicity.

  The reasons for the rapid rise in the condensation temperature of the working fluid containing R1123 measured in the two-phase pipe in the condenser 103 are: (1) ambient medium temperature Tmcon, a sharp rise in Tmeva, (2) the compressor 102 A pressure increase action due to a rise in power, and (3) a change in flow of the surrounding medium (a rise in power of any one of the fluid machines 107a and 107b for driving the surrounding medium) are considered. Aside from these factors, events specific to the working fluid including R1123 include (4) pressure increase action by disproportionation reaction. Therefore, in order to specify that the disproportionation reaction has occurred, it is a feature of the present embodiment to determine and control that the events (1) to (3) have not occurred.

  Therefore, as the control method of the present embodiment, the expansion valve opens when the amount of change in the condensation temperature of the working fluid including R1123 is larger than the amount of change in the temperature or input power of (1) to (3). Control on the side.

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

  For example, the amount of temperature change is measured at certain time intervals, for example, 10 seconds to 1 minute. Prior to this measurement, for example, the input electric energy of the compressor 102 and the fluid machines 107a and 7b is maintained at a constant value from about 10 seconds to about 1 minute ago. 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, it is assumed that, in the compressor 102, the change in the compressor suction state due to the refrigerant bias or that in the fluid machines 107a and 107b, if the first and second media are the ambient air, the compressor 102 sets almost zero. This is because the input power is slightly fluctuated by the influence of blowing and the like. That is, this approximately zero means that it is smaller than a predetermined value including a slight fluctuation.

  Under the above conditions, the change amount per unit time of the condensation temperature measured by the condensation temperature detection means 110a is the change per unit time of the temperature of the first medium detected by the first medium temperature detection means 110e. If the amount is larger than one of the unit time of the temperature of the second medium detected by the second medium temperature detection means 110f, the expansion valve 104 is opened in the opening direction, assuming that the disproportionation reaction has occurred. Control.

  Note that the bypass pipe 113 is arranged in parallel with the expansion valve 104 as described in the second embodiment, in preparation for the case where the pressure increase generated with the disproportionation reaction can not be controlled only by the expansion valve 104 opening degree control. It is also possible to provide means such as an emergency stop of the compressor 102 and a relief valve 114 for reducing the pressure by releasing the refrigerant to the outside.

  Further, in the present embodiment, an example of control of the expansion valve 104 implemented based on the amount of change of the temperature detection means installed in the two-phase pipe of the condenser 103 has been shown. In this case, the change in pressure at any point may be used as a reference, or the change in degree of supercooling at the inlet of the expansion valve 104 may be used as a reference.

  In addition, it is possible to further improve the reliability by using the present embodiment in combination with any of the above-described second and third embodiments of the present invention, which is preferable.

Fifth Embodiment
FIG. 16 is a cross-sectional view of a scroll compressor according to a fifth embodiment of the present invention. The configuration is the same as that of the first embodiment except for the presence or absence of the reed valve 19 provided in the discharge hole 18, and therefore the description of the other configuration is omitted.

  Although the reed valve 19 (check valve) is provided in the discharge hole 18 in the first embodiment, the reed valve 19 is not provided in the discharge hole 18 in the fifth embodiment. Therefore, the discharge chamber 22 is always in communication with the nearby compression chamber 15 through the discharge hole 18, and the discharge chamber 22 and the compression chamber 15 are in substantially the same pressure state. In the fifth embodiment, the discharge valve 18 is not provided in the discharge hole 18, so the valve stop 21 is not provided.

  Conditions under which disproportionation reaction is particularly likely to occur are conditions under excessive high temperature and pressure, so conditions not under predetermined operating conditions, for example, clogging of refrigerant piping in the refrigeration cycle or stop of air flow in the condenser, two-way The compression mechanism boosts the refrigerant pressure due to the discharge pressure (high pressure side of the refrigeration cycle) rising excessively due to forgetting to open the valve or three-way valve, or the torque of the motor (motor unit 3) of the compressor is insufficient It may happen that there is no condition.

  Under this condition, when power is continuously supplied to the compressor, current is excessively supplied to the motor constituting the compressor, and the motor generates heat. As a result, the motor in the compressor acts on the refrigerant as a heating element, and the internal refrigerant pressure and temperature rise excessively. As a result, the insulators of the windings constituting the stator of the motor melt and core wires (electrically conductive wires) of the windings come in contact with each other to cause a phenomenon called layer short. The layer short instantaneously propagates high energy to the surrounding refrigerant, and can be a source of disproportionation reaction.

  Therefore, in the present embodiment, even when power supply to the motor is continued while the compression mechanism does not perform the boosting operation, the pressure increase on the high pressure side of the refrigeration cycle, that is, the closed container 1 accommodating the motor is suppressed. The pressure is used to avoid the generation conditions of the disproportionation reaction. Specifically, the discharge chamber 22 is always in communication with the nearby compression chamber 15 through the discharge hole 18.

  According to the present invention, when power is supplied to the motor without performing the compression operation, the motor heats the refrigerant inside the sealed container 1 as a heating element, but even if the pressure of the refrigerant is increased due to the heating, the discharge is performed. The pressure acts on the compression chamber 15 through the hole 18, and the compression mechanism is reversely rotated to release the pressure in the closed container 1 to the low pressure side of the refrigeration cycle. It becomes possible to avoid the rise.

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

DESCRIPTION OF SYMBOLS 1 airtight container 2 compression mechanism 3 motor part 4 shaft 6 oil 12 fixed scroll 13 revolving scroll 14 rotation restraint mechanism 15 compression chamber 15a 1st compression chamber 15b 2nd compression chamber 18 discharge hole 19 reed valve 20 oil reservoir 21 valve stop Reference Signs List 22 discharge chamber 23 discharge pipe 24 muffler 25 pump 29 back pressure chamber 30 high pressure region 50 oil supply path 51 back pressure chamber oil supply path 51a, 51b open end 52 compression chamber oil supply path 52a, 52b open end 61 compressor 62 condenser 63 throttle mechanism 64 Evaporator 71 Feeding Terminal 72 Glass Insulating Material 73 Metal Lid Holding a Terminal for Feeding 74 Flag Type Terminal 75 Lead Wire 76 Donut-shaped Insulating Member 78 Sealing Member 101, 130, 140 Refrigerating Cycle Device 102 Compressor 103 Condensing 104 expansion valve 105 evaporator 106 Refrigerant pipes 107a, 107b Fluid machinery 108 Isotherm line 109 Saturated liquid line, saturated vapor line 110a Condensation temperature detection means 110b Condenser outlet temperature detection means 110c Evaporation temperature detection means 110d Intake temperature detection means 110e First medium temperature detection means 110f Second Medium temperature detection means 111 Union flare 112 Seal containing 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 Piping joint EP Under excessive pressure conditions State change of refrigeration cycle State change of refrigeration cycle at normal operation of NP

Claims (12)

Using a refrigerant containing 1,1,2-trifluoroethylene as a working fluid, using polyvinyl ether oil as a lubricant for a compressor, engaging a fixed scroll and a swirling scroll in which a spiral wrap rises from an end plate The suction volume of the first compression chamber formed on the wrap outer wall side of the orbiting scroll is larger than the suction volume of the second compression chamber formed on the lap inner wall side of the orbiting scroll. A compressor, a condenser for cooling a refrigerant gas compressed to a high pressure by the compressor, a throttle mechanism for decompressing the high pressure refrigerant liquefied by the condenser, and a refrigerant for decompressing the refrigerant decompressed by the throttle mechanism A first conveying means for connecting a first medium to be heat exchanged with the condenser, and a second medium to exchange heat with the evaporator. A second medium conveying means for feeding, a condensing temperature detecting means provided in the condenser, a first medium temperature detecting means for detecting the temperature of the first medium before flowing into the condenser, and the evaporator And second medium temperature detection means for detecting the temperature of the second medium before the inflow, wherein the amount of change in input power of the compressor per unit time, the amount of input power of the first transport means per unit time When the amount of change and the amount of change per unit time of the input power of the second transport means are smaller than a predetermined value determined in advance, the amount of change per unit time of condensation temperature detected by the condensation temperature detection means is From the amount of change per unit time of the temperature of the first medium detected by the first medium temperature detection means and the amount of change per unit time of the temperature of the second medium detected by the second medium temperature detection means If the Refrigerating cycle apparatus characterized by controlling the mechanism in the opening direction. The working fluid is a mixed working fluid containing difluoromethane, and the difluoromethane is 30% by weight or more and 60% by weight or less, or a mixed working fluid containing tetrafluoroethane, wherein the tetrafluoroethane is A mixed working fluid containing 30% by weight or more and 60% by weight or containing difluoromethane and tetrafluoroethane, wherein the difluoromethane and tetrafluoroethane are mixed, and the difluoromethane and tetrafluoroethane are combined. The refrigeration cycle apparatus according to claim 1, wherein the mixing ratio is 30% by weight or more and 60% by weight or less. The refrigeration cycle apparatus according to claim 1, wherein the polyvinyl ether oil contains a phosphate ester type antiwear agent. The refrigeration cycle apparatus according to claim 1, wherein the polyvinyl ether oil contains a phenolic antioxidant. The polyvinyl ether oil is prepared by mixing 1% to less than 50% of terpenes or terpenoids with a lubricating oil having a viscosity higher than that of the base oil, or lubricating oil having an ultrahigh viscosity equal to or larger than terpenes or terpenoids in advance. The refrigeration cycle apparatus according to claim 1 or 2, which is a lubricating oil in which an additive oil mixed and adjusted to have the same viscosity as the base oil is mixed with the base oil. The electric motor according to claim 1, further comprising: a motor unit for driving the orbiting scroll, wherein the motor unit uses a wire obtained by applying and baking a thermosetting insulating material on a conductor through an insulating film. The refrigeration cycle apparatus according to 2. A sealed container for containing the compression chamber and the motor unit is provided, and the sealed container includes a feed terminal installed at the mouth through an insulating member, and a connection terminal for connecting the feed terminal to a lead wire. The refrigeration cycle apparatus according to claim 6, further comprising: a doughnut-shaped insulating member disposed in close contact with the insulating member on a power supply terminal inside the sealed container. The opening degree of the throttling mechanism is set so that the difference between the critical temperature of the working fluid and the condensation temperature detected by the condensation temperature detection means is 5 K or more. The refrigeration cycle apparatus according to claim 1, wherein the control is performed. The high pressure side pressure detection means provided between the discharge part of the compressor and the inlet of the throttling mechanism is provided, and the difference between the critical pressure of the working fluid and the pressure detected by the high pressure side pressure detection means is The refrigeration cycle apparatus according to claim 1, wherein the opening degree of the throttling mechanism is controlled to be 0.4 MPa or more. Condenser outlet temperature detection means provided between the condenser and the throttling mechanism, the condensation temperature detected by the condensation temperature detection means, and the condenser outlet temperature detected by the condenser outlet temperature detection means The refrigeration cycle apparatus according to claim 1, wherein the opening degree of the throttling mechanism is controlled such that the difference between the values is 15 K or less. The refrigeration cycle apparatus according to claim 1, wherein an outer periphery of a joint of a pipe constituting the refrigeration cycle is covered with a sealing agent containing a polymerization accelerator. The refrigeration cycle apparatus according to claim 1, wherein a discharge chamber is provided on an end plate of the fixed scroll, and the discharge chamber is always in communication with the compression chamber through a discharge hole.