JP2018025371A - Refrigeration cycle apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enhance the reliability of a refrigeration cycle apparatus using a working fluid including HFO 1123.SOLUTION: The refrigerant cycle apparatus is provided that is constituted by encapsulating a working fluid including 1,1,2-trifluoroethylene and difluoromethane in a refrigerant cycle circuit constituted by annularly connecting a compressor, a condenser, an expansion valve and an evaporator. The compressor 102 is provided with a pressure fragile portion 200 at a part of the outer shell thereof, and the pressure fragile portion 200 is configured to be broken by pressure generated when the working fluid causes a disproportionation reaction by an external energy source to discharge the working fluid in the compressor to the outside. As a result, when the working fluid causes a disproportionation reaction by the external energy source, the pressure fragile portion is instantaneously broken by the pressure generated by the disproportionation reaction and discharges the working fluid in the inside to the outside to reduce the pressure therein, so that it is possible to prevent the pressure from rising as it is to cause breakage or the like of the compressor, and the safety of the refrigeration cycle apparatus can be secured.SELECTED DRAWING: Figure 6

Description

  The present invention relates to a refrigeration cycle apparatus using a working fluid containing HFO1123.

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

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

  R410A is often used as the refrigerant for the refrigeration cycle apparatus as described above, but the global warming potential (GWP) of the R410A refrigerant is as large as 2090, which is problematic from the viewpoint of preventing global warming.

  Thus, from the viewpoint of preventing global warming, for example, HFO1123 (1,1,2-trifluoroethylene) and HFO1132 (1,2-difluoroethylene) have been proposed as refrigerants having a small GWP (for example, patents). Document 1 or Patent document 2).

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

  However, HFO1123 (1,1,2-trifluoroethylene) and HFO1132 (1,2-difluoroethylene) are less stable than conventional refrigerants such as R410A and disproportionate when they generate radicals. There is a possibility of changing to another compound by the reaction. Since the disproportionation reaction increases in pressure with a large heat release, the reliability of the compressor and the refrigeration cycle apparatus may be reduced. For this reason, when using HFO1123 and HFO1132 for a compressor and a refrigerating cycle device, it is necessary to suppress this disproportionation reaction.

  Such a disproportionation reaction occurs when high energy is added in a refrigerant atmosphere that has become excessively high in temperature and pressure.

  For example, the discharge pressure (high-pressure side of the refrigeration cycle) increases excessively due to a state that is not under normal operating conditions, that is, due to the stop of the blower fan on the condenser side, blockage of the refrigeration cycle circuit, or the like.

  Under such a condition, a compressor lock abnormality occurs, and even under this lock abnormality, if power supply to the compressor is continued, excessive power is supplied to the motor of the compressor, and the motor generates heat abnormally. As a result, a phenomenon called a layer short is caused between the conductors of the stator windings constituting the stator of the electric motor, which becomes a high energy source and induces a disproportionation reaction.

  And when disproportionation reaction generate | occur | produces, the pressure in a compressor rises abnormally and there exists a possibility that a compressor may be damaged.

  The present invention has been made in view of these points, and an object thereof is to improve the safety of a refrigeration cycle apparatus using a working fluid containing HFO 1123 by preventing a compressor from being damaged when a disproportionation reaction occurs. It is what.

  In order to achieve the above object, the present invention provides a refrigeration cycle apparatus configured by enclosing a working fluid containing 1,1,2-trifluoroethylene and difluoromethane in a refrigeration cycle circuit. A pressure fragile portion is provided in a part of the pressure fragile portion, and the pressure fragile portion is broken by the pressure when the working fluid causes a disproportionation reaction by an external energy source and discharges the working fluid in the compressor to the outside.

  According to the above configuration, when the working fluid undergoes a disproportionation reaction due to an external energy source, the pressure fragile portion is instantaneously destroyed by the pressure at that time, and the internal working fluid is discharged to the outside to reduce the pressure. As a result, the compressor can be prevented from being damaged, and the reliability of the refrigeration cycle apparatus can be ensured.

  The present invention can provide a safe and highly reliable refrigeration cycle apparatus using a working fluid containing HFO 1123 with the above configuration.

1 is a schematic configuration diagram of a refrigeration cycle apparatus according to Embodiment 1 of the present invention. 1 is a schematic configuration diagram showing an enlarged main part of an internal high-pressure compressor constituting the refrigeration cycle apparatus according to Embodiment 1 of the present invention. Schematic configuration diagram of an internal low-pressure compressor shown as a compressor constituting the refrigeration cycle apparatus according to Embodiment 1 of the present invention. Schematic configuration diagram of a concentrated winding motor of an internal high-pressure compressor constituting the refrigeration cycle apparatus according to Embodiment 1 of the present invention. Schematic configuration diagram of a distributed winding motor of an internal high-pressure compressor constituting the refrigeration cycle apparatus according to Embodiment 1 of the present invention. 1 is a schematic configuration diagram showing an enlarged main part of an internal high-pressure compressor constituting the refrigeration cycle apparatus according to Embodiment 1 of the present invention. Sectional drawing which shows the electric power feeding terminal junction part of the compressor which comprises the refrigeration cycle apparatus which concerns on Embodiment 1 of this invention. Sectional drawing which shows the discharge pipe junction part of the compressor which comprises the refrigeration cycle apparatus which concerns on Embodiment 1 of this invention. Schematic configuration diagram of main part expansion shown as another example of the pressure weakened part of the compressor constituting the refrigeration cycle apparatus according to Embodiment 1 of the present invention. FIG. 3 is a relationship diagram of pressure and time showing disproportionation reaction characteristics of a working fluid used in the refrigeration cycle apparatus according to Embodiment 1 of the present invention. FIG. 3 is a relationship diagram of pressure and temperature showing disproportionation reaction characteristics of a working fluid used in the refrigeration cycle apparatus according to Embodiment 1 of the present invention. The figure which shows the buffer member (heat exchanger) provided in the refrigerating-cycle apparatus which concerns on Embodiment 2 of this invention. The figure which shows the buffer member (electric motor drive device) provided in the refrigerating-cycle apparatus which concerns on Embodiment 3 of this invention.

  A first invention includes a refrigeration cycle circuit configured by annularly connecting a compressor, a condenser, an expansion valve, and an evaporator, and the refrigeration cycle circuit includes 1,1,2-trifluoroethylene. And a working fluid containing difluoromethane, wherein the compressor is provided with a pressure fragile portion in a part of its outer shell, and the pressure fragile portion is provided by an external energy source. The working fluid in the compressor is discharged to the outside by being destroyed by the pressure when the disproportionation reaction occurs.

  According to the above configuration, when the working fluid undergoes a disproportionation reaction due to an external energy source, the pressure fragile portion is instantaneously destroyed by the pressure at that time, and the internal working fluid is discharged to the outside to reduce the pressure. It is possible to prevent the compressor from being damaged due to the rise, and to ensure the reliability of the refrigeration cycle apparatus.

  In a second aspect based on the first aspect, the pressure weakened portion has a working fluid flow path diameter of 1.5 mm or more.

  As a result, the pressure-fragile part can instantaneously release the working fluid in the compressor at the time of breakdown to prevent an abnormal pressure rise of the compressor, and prevent the compressor from being damaged and ensure the reliability of the refrigeration cycle apparatus. Can do.

  According to a third aspect, in the first or second aspect, the pressure weakened portion is a joint portion of a power feeding terminal for energizing the electric motor of the compressor.

  Thereby, a pressure weak part can be added using an electric power feeding terminal, damage to a compressor etc. can be prevented without giving a special structure, and simplification of a structure can also be achieved.

  According to a fourth aspect of the present invention, in the first or second aspect, the compressor is an internal high-pressure compressor in which a portion including an electric motor is filled with a high-pressure working fluid, and the pressure fragile portion is removed from the compressor. As a joint part of the discharge pipe that discharges water.

  This makes it possible to add a pressure-fragile portion using the discharge pipe, simplifying the structure by eliminating the need for a special configuration, and increasing the pressure in the internal high-pressure compressor. Since it is the site that appears the most, it is quickly destroyed, and the working fluid can be efficiently discharged to the outside to prevent the compressor from being damaged.

  According to a fifth aspect of the present invention, in the first or second aspect, the compressor is an internal low-pressure compressor in which a portion including an electric motor is filled with a low-pressure working fluid, and the pressure fragile portion is provided in the working fluid in the compressor. It is as a joint part of the suction pipe which sends in.

  As a result, it is possible to add a pressure-fragile portion using the suction pipe, which eliminates the need for a special configuration and simplifies the configuration. In addition, the suction pipe causes a disproportionation reaction due to a layer short circuit or the like. In this case, since the pressure exceeds the discharge pressure and becomes higher than the other parts, it is quickly destroyed, and the working fluid can be efficiently discharged to the outside to prevent the compressor from being damaged.

  According to a sixth invention, in the first to fifth inventions, the compressor includes an oil storage portion at a bottom portion, and a pressure weakening portion is provided above the oil storage portion.

  Thereby, when the working fluid is released, the oil in the oil storage section can be prevented from being discharged together with the working fluid, and the reliability of the refrigeration cycle apparatus can be ensured without causing the user to feel uneasy.

  According to a seventh invention, in the first to sixth inventions, a buffer member that suppresses scattering of the discharged refrigerant or the fragile member is provided at a location where the pressure fragile portion around the compressor faces. The discharged refrigerant or the fragile member can be received, and it can be prevented from being scattered more than necessary around the surroundings, and abnormal noise when the fragile member is opened can be reduced.

  According to an eighth invention, in the first to seventh inventions, the buffer member is a heat exchanger constituting the refrigeration cycle, and the flexible heat exchanger receives the impact of the refrigerant or the fragile member, Scattering more than necessary can be prevented.

  According to a ninth invention, in the first to seventh inventions, the buffer member is an electric motor driving device that controls the electric motor. The scattered weak member destroys the electric motor driving device, and the electric motor driving device controls the driving. Since the movable parts (compressor motor and blower motor) are stopped, the operation of the air conditioner can be stopped more quickly and safely.

  A tenth aspect of the invention is the first to seventh aspects of the invention, wherein the buffer member is a casing for storing the refrigeration cycle, and the scattered refrigerant or the fragile member is not taken out of the casing and used. Can maintain a safe state.

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

(Embodiment 1)
FIG. 1 shows a refrigeration cycle apparatus 100 according to a first embodiment of the present invention. The refrigeration cycle apparatus 100 of the present embodiment is a so-called separate type air conditioner in which an indoor unit 101a and an indoor unit 101a are connected to each other by a refrigerant pipe, a control wiring, and the like.

  The indoor unit 101a blows air to the indoor heat exchanger 103 and the indoor heat exchanger 103, and the indoor fan 107a which is a cross-flow fan (cross flow fan) that blows out the air heat-exchanged by the indoor heat exchanger 103 into the room. It has. The outdoor unit 101 b includes a compressor 102, an expansion valve 104 that is a decompression unit, an outdoor heat exchanger 105, a four-way valve 106, and an outdoor fan 107 b that is a propeller fan that blows air to the outdoor heat exchanger 105.

  The indoor unit 101a includes a pipe connection portion 112 so that the indoor unit 101a and the outdoor unit 101b can be separated. The outdoor unit 101b includes a pipe connection part 112, a three-way valve 108 provided between the pipe connection part 112 and the four-way valve 106, and a two-way valve 109 provided between the pipe connection part 112 and the expansion valve 104. I have. The indoor unit 101 a includes an electric motor driving device 115 that drives an electric motor provided in the compressor 102.

  And one pipe connection part 112 of the indoor unit 101a and the pipe connection part 112 on the side where the two-way valve 109 of the outdoor unit 101b is provided are connected by a liquid pipe 111a which is one of refrigerant pipes. Yes. Further, the other pipe connecting portion 112 of the indoor unit 101a and the pipe connecting portion 112 on the side where the three-way valve 108 of the outdoor unit 101b is provided are connected by a gas pipe 111b which is one of refrigerant pipes. .

As described above, the refrigeration cycle apparatus 100 of the present embodiment is mainly configured by connecting the refrigerant 102 in the order of the compressor 102, the indoor heat exchanger 103, the expansion valve 104, and the outdoor heat exchanger 105 to configure a refrigeration cycle circuit. doing. In the refrigeration cycle circuit, the flow direction of the refrigerant discharged from the compressor 102 is changed between the compressor 102 and the indoor heat exchanger 103 or the outdoor heat exchanger 105, either the indoor heat exchanger 103 or the outdoor heat exchanger 105. A four-way valve 106 for switching between the two is provided.

  By providing the four-way valve 106, the refrigeration cycle apparatus 100 of the present embodiment can switch between the cooling operation and the heating operation. That is, during the cooling operation, the four-way valve 106 is switched so that the discharge side of the compressor 102 communicates with the outdoor heat exchanger 105 and the indoor heat exchanger 103 communicates with the suction side of the compressor 102. As a result, the indoor heat exchanger 103 acts as an evaporator, absorbs heat from the ambient atmosphere (indoor air), and the outdoor heat exchanger 105 acts as a condenser, and the heat absorbed in the room is converted into the ambient atmosphere (outdoor air). ). On the other hand, during the heating operation, the four-way valve 106 is switched so that the discharge side of the compressor 102 and the indoor heat exchanger 103 communicate with each other, and the outdoor heat exchanger 105 and the suction side of the compressor 102 communicate with each other. Thus, the outdoor heat exchanger 105 acts as an evaporator, absorbs heat from (outdoor air), the indoor heat exchanger 103 acts as a condenser, and the heat absorbed outside is radiated to the indoor air.

  The four-way valve 106 is an electromagnetic valve type that switches between cooling and heating by an electrical signal from a control device (not shown).

  The refrigeration cycle circuit includes a bypass unit 113 that bypasses the four-way valve 106 and communicates the suction side and the discharge side of the compressor 102, and an on-off valve 113a that opens and closes the refrigerant flow in the bypass unit 113. Yes.

  A relief valve 114 that is an electronically controlled on-off valve is provided on the discharge side of the compressor 102. The relief valve 114 may be provided between the discharge portion of the compressor 102 and the expansion valve 104, or between the discharge portion of the compressor 102 and the three-way valve 108. In order to quickly escape, it is desirable to be provided between the discharge part of the compressor 102 and the four-way valve 106.

  The refrigeration cycle circuit includes a high pressure side pressure detection means 116 provided between the discharge side of the compressor 102 and the inlet of the expansion valve 104. The high pressure side pressure detecting means 116 may be configured to electrically detect and measure the strain of the diaphragm to be pressurized with a strain gauge or the like. Furthermore, you may comprise with the metal bellows and metal diaphragm which detect a pressure mechanically.

  The refrigeration cycle circuit includes a discharge temperature detecting means 117 provided between the discharge side of the compressor 102 and the inlet of the condenser. In this embodiment, since either the indoor heat exchanger 103 or the outdoor heat exchanger 105 becomes a condenser by switching the four-way valve 106, the discharge temperature detecting means 117 is connected to the discharge side of the compressor 102 and the four-way valve. It is provided between the entrances of 106. The discharge temperature detection means 117 is composed of a thermistor, a thermocouple, or the like, and electrically detects the temperature.

  The detection values of the high pressure side pressure detection means 116 and the discharge temperature detection means 117 are electrically transmitted to the control device.

  A working fluid (refrigerant) is enclosed in the refrigeration cycle circuit. The working fluid will be described. The working fluid sealed in the refrigeration cycle apparatus 100 of the present embodiment is a two-component mixed working fluid composed of (1) HFO1123 (1,1,2-trifluoroethylene) and (2) R32 (difluoromethane). In particular, it is a mixed working fluid having R32 of 30 wt% or more and 60 wt% or less.

  By mixing 30 wt% or more of R32 with HFO1123, the disproportionation reaction of HFO1123 can be suppressed. Further, the higher the concentration of R32, the more the disproportionation reaction can be suppressed. This is because the action of mitigating the disproportionation reaction due to the small polarization of R32 to the fluorine atom and the behavior at the time of phase change such as condensation and evaporation are integrated because HFO1123 and R32 have similar physical characteristics. The disproportionation reaction of HFO1123 can be suppressed by the action of reducing the disproportionation reaction opportunity due to.

  Further, the mixed refrigerant of HFO1123 and R32 has an azeotropic boiling point with R32 being 30% by weight and HFO1123 being 70%, and there is no temperature slip, so that it can be handled in the same manner as a single refrigerant. That is, if R32 is mixed by 60% by weight or more, temperature slip increases, and handling similar to that of a single refrigerant may be difficult. Therefore, it is desirable to mix R32 at 60% by weight or less. In particular, it is desirable to mix R32 in an amount of 40 wt% to 50 wt% in order to prevent disproportionation and to make the temperature slip smaller because it approaches the azeotropic point and to facilitate device design.

  Tables 1 and 2 show that the pressure, temperature of the refrigeration cycle, and the displacement of the compressor are the same when the mixing ratio of R32 is 30 wt% to 60 wt% of the mixed working fluid of HFO1123 and R32 Refrigeration capacity and cycle efficiency (COP) are calculated and compared with R410A and HFO1123.

  First, calculation conditions in Tables 1 and 2 will be described. In recent years, in order to improve the cycle efficiency of equipment, the performance of heat exchangers has increased, and in actual operating conditions, the condensation temperature tends to decrease, the evaporation temperature tends to increase, and the discharge temperature also tends to decrease . Therefore, considering the actual operating conditions, the cooling calculation conditions in Table 1 correspond to the cooling operation of the refrigeration cycle apparatus 100 (indoor 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 superheated degree of the refrigerant sucked in the compressor was 5 ° C., and the supercooling degree at the condenser outlet was 8 ° C.

  The heating calculation conditions in Table 2 are the calculation conditions corresponding to the heating operation of the refrigeration cycle apparatus 100 (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 superheated degree of the refrigerant sucked into the compressor was 2 ° C, and the supercooling degree at the outlet of the condenser was 12 ° C.

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

  As described above, in the two-component system of HFO 1123 and R32, taking into consideration the prevention of disproportionation, the magnitude of temperature slip, the capacity during cooling operation / heating operation, and COP (that is, compression described later) When a mixing ratio suitable for an air-conditioning apparatus using an air conditioner is specified, a mixture containing 30% by weight or more and 60% by weight or less R32 is desirable, and a mixture containing 40% by weight or more and 50% by weight or less R32 is more desirable. Is desirable.

  Next, each component constituting the refrigeration cycle circuit will be described.

  As the indoor heat exchanger 103 and the outdoor heat exchanger 105, a fin-and-tube heat exchanger, a parallel flow type (microtube type) heat exchanger, or the like is used. In addition, it is not a separate type air conditioner as shown in FIG. 1, for example, when using a brine (brine is used for air conditioning of a living space) as a surrounding medium of the indoor heat exchanger 103, or a two-way type When using the refrigerant of a refrigerating cycle, you may use a double tube heat exchanger, a plate type heat exchanger, and a shell and tube heat exchanger (not shown) as a form of a heat exchanger. In this case, the indoor heat exchanger 103 does not necessarily cool and heat the object to be cooled and heated (in the case of a separate type air conditioner, directly), and thus is not necessarily arranged indoors. As the expansion valve 104, for example, a pulse motor drive type electronic expansion valve is used.

  Details of the compressor 102 will be described with reference to FIG. The compressor 102 is a so-called hermetic rotary compressor, and is an internal high-pressure compressor in which a portion including an electric motor is filled with a high-pressure working fluid. The compressor may be an internal low-pressure compressor in which a portion including the electric motor shown in FIG. 3 is filled with a low-pressure working fluid, and the internal configuration is the same. Therefore, the internal high-pressure compressor shown in FIG. 2 is used. In the configuration of the internal low-pressure compressor in FIG. 3, the same parts as those in FIG.

  The compressor 102 contains an electric motor 102e and a compression mechanism 102c inside a sealed container 102g as an outer shell, and the inside is filled with high-temperature and high-pressure discharged refrigerant and refrigerating machine oil, and the bottom part is an oil storage part 102f that stores refrigerating machine oil. It has become. The electric motor (motor) 102e is a so-called brushless motor. The electric motor 102e includes a rotor 1021e connected to the compression mechanism 102c, and a stator 1022e provided around the rotor 1021e.

  The stator 1022e is provided with a three-phase stator winding, and a coil end 1023e is formed at the end of the stator 1022e in the vertical direction. The ends of the three-phase stator windings are lead wires 102i. In other words, the stator 1022e includes three lead wires 102i extending from each of the three-phase stator windings. The other ends of the three lead wires 102i are connected to the power supply terminal 102h. The power supply terminal 102 h includes three terminals, and each terminal is connected to the motor driving device 115. The three-phase stator winding is insulated by an insulator (not shown).

  As shown in FIG. 2, each of the three lead wires 102i extends from a position away from the coil end 1023e in the horizontal cross section of the electric motor 102e. More specifically, in each of the three lead wires 102i, the interval between adjacent lead wires 102i on the stator 1022e side (coil end 1023e side described later) is equal to the interval between adjacent lead wires on the power supply terminal 102h side. It is getting bigger. Further, the three lead wires 102i may be arranged at about 120 degrees around the rotation center of the rotor 1021e in the horizontal section of the electric motor 102e.

  FIG. 4 is a cross-sectional view of the electric motor 102e. The electric motor 102e is a so-called concentrated winding electric motor. The stator 1022e is composed of one tooth 31 and an annular yoke 32 connecting the teeth 31, and is disposed on the substantially cylindrical rotor core 33 and the outer peripheral portion thereof, facing the inner peripheral portion of the stator 1022e. A rotor 1021e made of a permanent magnet 34 is held rotatably about the crankshaft 102m. The permanent magnet 34 is fixed by inserting a ring 35 of non-magnetic material such as stainless steel into the outer periphery.

  Note that the permanent magnet may be fixed using an adhesive such as an epoxy resin.

  In the above description, the permanent magnets 34 are arranged as a structure in which the permanent magnets 34 are arranged on the outer periphery of the rotor core 33. However, the permanent magnets are arranged in the rotor core (not shown). Also good.

  On the other hand, the stator 1022e is fixed inside the sealed container 102g by being shrink-fitted into the shell of the compressor. The fixing method of the stator 1022e is not limited to this, and may be fixed by a method such as welding.

  The teeth 31 are provided with a three-phase stator winding, and a current is passed through the winding so that a rotating magnetic field is generated in the rotor 1021e by the switching element of the inverter type electric motor driving device 115. The rotating magnetic field can be generated at a variable speed by an inverter, and is operated at a high speed immediately after the start of operation of the compressor 102 and at a low speed during a stable operation.

  By providing a notch or groove or hole 37 in the outer periphery of the stator 1022e, there is a portion that penetrates the entire length of the stator 1022e between the pressure-sealed container 102g and the stator 1022e or in the stator 1022e itself, Refrigeration is performed by passing through the refrigeration oil.

  When the electric motor 102e is a concentrated winding electric motor, the winding resistance can be reduced, the copper loss can be greatly reduced, and the total motor length can be reduced.

The electric motor 102e has been described as a concentrated winding electric motor, but may be a distributed winding electric motor. FIG. 5 is a cross-sectional view of the distributed winding motor 102e. The stator 1022e is composed of a plurality of teeth 61 and an annular yoke 62 connecting the teeth 61, and is disposed on the substantially cylindrical rotor core 63 and the outer peripheral portion thereof so as to face the inner peripheral portion of the stator 1022e. A rotor 1021e made of a permanent magnet 64 is held rotatably about the crankshaft 102m. The permanent magnet 64 is fixed by inserting a ring 66 made of non-magnetic material such as stainless steel into the outer periphery. The stator 1022e is fixed inside the sealed container 102g by being shrink-fitted into the shell of the compressor.

  By providing a notch 67, a groove, or a hole in the outer peripheral portion of the stator 1022e, the refrigerating machine oil passes therethrough to perform a refrigeration action.

  The rotor 1021e has four poles, and the number of teeth of the stator 1022e is 12 or 24, which is equal to the number of slots. Each slot is provided with a three-phase winding.

  The number of rotor poles and the number of stator slots may be 6 poles 9 slots, 6 poles 18 slots, 4 poles 6 slots, 8 poles 12 slots, 10 poles 12 slots.

  In the compressor 102 configured as described above, the low-pressure refrigerant flowing out of the evaporator is sucked from the suction pipe 102a through the four-way valve 106 and is pressurized by the compression mechanism 102c. The discharged refrigerant that has been pressurized and becomes high temperature and pressure is discharged from the discharge muffler 102l, passes through gaps (between the rotor 1021e and the stator 1022e, between the stator 1022e and the sealed container 102g) formed around the electric motor 102e, It flows into the discharge space 102d. Then, it discharges out of the compressor 102 from the discharge pipe 102b, and goes to a condenser via the four-way valve 106.

  The compression mechanism 102c is connected to the electric motor 102e via the crankshaft 102m. In the electric motor 102e, electric power received from an external power source is converted from electrical energy to mechanical (rotational) energy. In the compression mechanism 102c, the compression work which pressurizes a refrigerant | coolant is performed using the mechanical energy transmitted via the crankshaft 102m from the electric motor 102e.

  Here, as described above, when the operation condition is not normal, that is, when the blower fan on the condenser side is stopped, the refrigeration cycle circuit is blocked, etc., the discharge pressure of the working fluid (high pressure side of the refrigeration cycle) is excessive. To rise.

  In this state, if the power supply to the compressor 102 is continued, the power is excessively supplied to the electric motor 102e constituting the compressor 102, the electric motor 102e generates abnormal heat, and the stator winding 40 of the electric motor 102e is heated. The insulation of the wire is damaged, and the conductors of the windings are in direct contact with each other, causing a layer short circuit. As a result, the working fluid generates a disproportionation reaction starting from the above-mentioned layer short, and the pressure in the compressor 102 increases rapidly in about 0.2 sec as shown in FIG. That is, as shown in the present embodiment, a working fluid in which a disproportionation reaction hardly occurs, for example, a working fluid in which the mixing ratio of R32 to HFO1123 is 30 wt% or more and 60 wt% or less is used. Becomes excessively high temperature and high pressure, and when a high energy source is added in the refrigerant atmosphere under such high temperature and high pressure, a disproportionation reaction occurs and the pressure in the compressor 102 rapidly increases. there is a possibility.

  Therefore, the compressor 102 of this refrigeration cycle apparatus is provided with a pressure weakened portion 200 that is destroyed by the pressure when the working fluid undergoes a disproportionation reaction at an appropriate position of the sealed container 102g that is the outer shell thereof. In this example, as shown in FIG. 6, the joint portion of the power supply terminal 102 h is a pressure weakened portion 200.

Thus, in this compressor 102, when the working fluid causes a disproportionation reaction and the pressure rises, the pressure weakened portion 200 provided in the sealed container 102g of the compressor 102 by the pressure at the time when the disproportionation reaction occurs. Is broken, and the working fluid in the compressor 102 is discharged to the outside. As a result, the pressure in the compressor 102 rapidly decreases, and damage to the compressor 102 can be prevented.

  Here, the pressure at which the pressure fragile portion 200 breaks, that is, the pressure when the disproportionation reaction occurs will be considered.

  As described above, this disproportionation reaction occurs when high energy is applied to the working fluid in an atmosphere in which the working fluid is excessively hot and high in pressure.

  Therefore, first, the pressure when high energy is applied is one condition. This high energy is a high energy source having the highest probability of occurrence of a layer short circuit that occurs when the insulator of the stator winding of the electric motor 102e serving as the drive source of the compressor 102 is melted and broken. The disproportionation reaction generation pressure at the temperature at which the insulator melts becomes the breaking pressure of the pressure fragile portion 200.

  Here, as for the insulator used for the stator winding of the electric motor serving as the drive source of the compressor, the one having a low melting temperature is usually 150 ° C. ± 10%.

  On the other hand, the relationship between the pressure and temperature at which the working fluid causes a disproportionation reaction is as shown in FIG. That is, FIG. 11 shows the disproportionation reaction occurrence region in the working fluid in which the ratio of HFO1123 and R32 is 60:40 (HFO1123 / R32 = 60/40), and the upper side of the broken line in the drawing is the region where disproportionation reaction occurs. Temperature and pressure have an inversely proportional relationship.

  Under such a correlation between pressure and temperature, the pressure causing the disproportionation reaction when the insulator of the stator winding of the motor 102e is melted at 150 ° C. ± 10% is 9 MPa, as shown in FIG. And 9 MPa ± 10%.

  Therefore, the pressure at which the pressure fragile portion 200 breaks may be 9 MPa ± 10% or more. As a result, when a disproportionation reaction occurs starting from the layer short-circuit with the highest probability of occurrence, the pressure becomes 9 MPa or more, the pressure weakened portion 200 is instantaneously destroyed, the working fluid is released, and the pressure is rapidly reduced. . Therefore, damage to the compressor 102 can be prevented.

  Further, as described above, when the working fluid causes a disproportionation reaction, the pressure suddenly rises in about 0.2 seconds as described above. Therefore, it is necessary to release the working fluid in a time shorter than 0.2 seconds. . Therefore, it is preferable that the working fluid flow path diameter of the pressure weakening part 200 shall be 1.5 mm or more.

  In this way, by setting the working fluid flow path diameter of the pressure weakened portion 200 to 1.5 mm or more, even if a disproportionation reaction occurs, the pressure becomes such that the sealed container 102g which is the outer shell of the compressor 102 is damaged. The working fluid can be discharged to the outside before 2 seconds, and the compressor 102 can be prevented from being damaged.

  Further, the pressure weakened portion 200 may be provided in any place as long as it is a sealed container 102g that is an outer shell of the compressor 102, but it is effective to provide it in the following form.

  For example, as described above, the joint portion of the power supply terminal 102h for energizing the electric motor 102e of the compressor 102 is the pressure weakened portion 200 as described above. FIG. 7 shows a joint portion of the power supply terminal 102 h, and a joint portion of the power supply terminal 102 h provided in the sealed container 102 g that is an outline of the compressor 102 is a pressure weakened portion 200.

  As a result, when the working fluid undergoes a disproportionation reaction and the pressure rises abnormally, the joint of the power supply terminal is destroyed, the power supply terminal 102h is separated, and the working fluid in the compressor 102 is discharged to the outside. 102 is prevented from being damaged. Therefore, the compressor 102 can be prevented from being damaged with a simple configuration without providing a special pressure fragile portion.

  Moreover, you may provide a weak part between the terminal pin 102j extended from the power supply terminal 102h instead of the junction part of the power supply terminal 102h, and its peripheral part.

  Moreover, the pressure weak part 200 can also be provided as follows.

  That is, in the case of the internal high-pressure compressor 102 shown in FIG. 2, the joint portion of the discharge pipe 102 b is the pressure weakened portion 200. FIG. 8 shows a joint portion of the discharge pipe 102 b, and a joint portion of the discharge pipe 102 b provided in the sealed container 102 g that is an outline of the compressor 102 is a pressure weakened portion 200.

  Since the discharge pipe part of such an internal high-pressure compressor is a part where the pressure is higher than other parts, the increase in pressure caused by the disproportionation reaction of the working fluid appears as the largest value, and as a result, the pressure Since it breaks quickly as it rises, the working fluid can be quickly discharged to the outside. Therefore, damage to the compressor 102 can be prevented more reliably.

  Further, in the case of the internal low-pressure compressor shown in FIG.

  The suction pipe part of such an internal low-pressure compressor is a part that exceeds the discharge pressure when the disproportionation reaction occurs due to a layer short or the like, and the pressure becomes higher than other parts. The increase in pressure caused by the disproportionation reaction appears as the largest value, and as a result, the working fluid can be quickly discharged to the outside because it is quickly destroyed as the pressure increases. Therefore, damage to the compressor 102 can be prevented more reliably.

  Further, the pressure weakening portion 200 may be separately provided as shown in 200a in FIG.

  In this way, it is possible to make it most easily destroyed at a predetermined pressure by providing it separately, and it is also possible to secure a working fluid flow path shape of 1.5 mm or more that discharges the working fluid within 0.2 sec. Easy to do.

  Note that, under each of the above configurations, the pressure weakening portion 200 is preferably provided above the oil storage portion 102 f provided at the bottom of the compressor 102. With such a configuration, when the working fluid is discharged, the oil in the oil storage portion 102f can be prevented from being released to the outside together with the working fluid, and the working fluid is unevenly distributed without causing distrust to the user. The reliability of the refrigeration cycle apparatus can be ensured by preventing the reaction.

  As described above, in the present embodiment, the rotary compressor has been described as an example. However, this may be any other type, for example, a scroll type, a reciprocating type positive displacement compressor, a centrifugal compressor, or the like. It may be a compressor.

(Embodiment 2)
FIG. 12 shows an outdoor unit 101b of the refrigeration cycle apparatus according to Embodiment 2 of the present invention.

The figure is a perspective view of the outdoor unit as seen from above. A compressor 102 and an outdoor heat exchanger 105 connected to the compressor 102 by piping in a refrigeration cycle are provided inside the casing of the outdoor unit 101b. (Other components are not shown).

  If the working fluid causes a disproportionation reaction due to an external energy source, the pressure weakened portion 300 provided in the compressor 102 is opened, and the refrigerant is discharged to the outside of the compressor and a part of the pressure weakened portion. Is scattered.

  At this time, since the outdoor heat exchanger 105 which is a buffer member is provided in the direction in which the refrigerant and the pressure weak part 300 are scattered, the scattered refrigerant and the pressure weak part collide with the outdoor heat exchanger 105.

  The outdoor heat exchanger 105 is made of relatively soft metal such as aluminum and copper, or only aluminum, so that it can flexibly receive the colliding object and prevent unnecessary scattering to the surroundings. It is also possible to reduce abnormal noise when opened.

(Embodiment 3)
FIG. 13 shows an outdoor unit 101b of the refrigeration cycle apparatus according to Embodiment 3 of the present invention.

  The figure is a perspective view of the outdoor unit as seen from the front in front, and an electric motor drive device that drives and controls the compressor 102 and the compressor motor in the compressor 102 inside the casing of the outdoor unit 101b. 115 is disposed (other components are not shown).

  If the working fluid causes a disproportionation reaction by an external energy source, the pressure weakened portion 301 provided in the compressor 102 is opened, the refrigerant is discharged above the compressor, and a part of the pressure weakened portion. Is scattered.

  At this time, since the motor driving device 115 which is a buffer member is provided in the direction in which the refrigerant and the pressure fragile portion 301 scatter, the scattered refrigerant and the pressure fragile portion collide with the motor driving device 115.

  The electric motor drive device is provided with an electric circuit, and the electric circuit is disconnected when the scattered refrigerant and the pressure fragile portion 301 collide with each other.

  By doing in this way, when the pressure weak part 301 is open | released, an electric circuit is disconnected almost simultaneously, drive control, such as a motor for compressors, stops, and it can stop operation quickly.

  It should be noted that the embodiment 2 and the embodiment 3 may be combined to each other without distinguishing between the embodiment 2 and the embodiment 3. That is, a heat exchanger as a buffer member and an electric motor drive device as a buffer member are provided in the outdoor unit, and when the pressure fragile portion is released, it is received by one of the above or the casing of the outdoor unit. The scattered refrigerant and the pressure-fragile part can be kept inside the outdoor unit.

  As described above, the present invention can improve the safety of a refrigeration cycle apparatus using a working fluid containing HFO 1123, and is used for residential and commercial air conditioners, car air conditioners, water heaters, refrigerators and refrigerators, showcases, dehumidification It can be widely applied to applications such as machines.

DESCRIPTION OF SYMBOLS 100 Refrigeration cycle apparatus 101a Indoor unit 101b Outdoor unit 102 Compressor 102a Intake pipe 102b Discharge pipe 102c Compression mechanism 102e Electric motor 102f Oil storage part 102g Sealed container 102h Feed terminal 102i Lead wire 1021e Rotor 1022e Stator 1023e Coil end Coil end Exchanger 104 Expansion valve 105 Outdoor heat exchanger 106 Four-way valve 107a Indoor fan 107b Outdoor fan 108 Three-way valve 109 Two-way valve 111a Liquid pipe 111b Gas pipe 112 Pipe connection 113 Bypass means 113a On-off valve 114 Relief valve 115 Motor drive Device 200 Pressure vulnerable part 200a Soluble plug 300 Pressure vulnerable part 301 Pressure vulnerable part

Claims (10)

A refrigeration cycle circuit configured by annularly connecting a compressor, a condenser, an expansion valve, and an evaporator is provided, and the refrigeration cycle circuit includes 1,1,2-trifluoroethylene and difluoromethane. A refrigeration cycle apparatus configured by enclosing a working fluid, wherein the compressor is provided with a pressure fragile portion in a part of an outer shell thereof, and the pressure fragile portion causes a disproportionation reaction of the working fluid by an external energy source. A refrigeration cycle apparatus configured to be released by the working fluid in the compressor when it is broken by the pressure of The refrigeration cycle apparatus according to claim 1, wherein the pressure-fragile portion has a working fluid channel diameter of 1.5 mm or more. The refrigeration cycle apparatus according to claim 1 or 2, wherein the pressure weakened portion is a joint portion of a power supply terminal for energizing an electric motor of the compressor. The compressor is an internal high-pressure compressor in which a portion including an electric motor is filled with a high-pressure working fluid, and the pressure weakened portion is a joint portion of a discharge pipe that discharges the working fluid from the compressor. Refrigeration cycle equipment. The compressor according to claim 1 or 2, wherein the compressor is an internal low-pressure compressor in which a portion including an electric motor is filled with a low-pressure working fluid, and the pressure weakened portion is a joint portion of a suction pipe that feeds the working fluid to the compressor. Refrigeration cycle equipment. The refrigeration cycle apparatus according to any one of claims 1 to 5, wherein the compressor includes an oil storage portion at a bottom portion, and a pressure weakening portion is provided above the oil storage portion. The said refrigeration cycle apparatus WHEREIN: The buffer member which suppresses dispersion | distribution of the discharge | released refrigerant | coolant or a weak member is provided in the location where the said pressure weak part around the said compressor faces. The refrigeration cycle apparatus according to any one of the above. The said buffer member is a heat exchanger which comprises the said refrigerating cycle, The refrigerating cycle apparatus in any one of Claims 1-7 characterized by the above-mentioned. The refrigeration cycle apparatus according to any one of claims 1 to 7, wherein the buffer member is an electric motor drive device that controls the electric motor. The refrigeration cycle apparatus according to claim 1, wherein the buffer member is a housing that stores the refrigeration cycle.

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