CN106104169A - Refrigerating circulatory device - Google Patents

Abstract

Possess and utilize refrigerant piping to connect compressor (10), heat source side heat exchanger (12), throttling arrangement (16) and load side heat exchanger (15) the kind of refrigeration cycle for refrigerant circulation, cold-producing medium is by 1,1,2 trifluoro-ethylenes constitute unitary system cryogen or contain 1,1, the mix refrigerant of 2 trifluoro-ethylenes, compressor (10) has discharge chambe (47) and motor (44) at compressor housing (45), and the insulating materials of motor (44) uses resin material.

Description

Refrigeration cycle device

technical field

The present invention relates to a refrigeration cycle device such as an air conditioner used for, for example, a multi-type air conditioner for a building.

Background technique

In a refrigeration cycle device such as a multi-connected air conditioner for a building, which constitutes a refrigerant circuit that circulates a refrigerant to perform air conditioning, etc., as a refrigerant, generally use non-flammable R410A, weakly flammable R32, and strong Substances containing hydrogen and carbon such as flammable propane. When these substances are released into the atmosphere, they have different lives until they are decomposed in the atmosphere and become different substances, but they have high stability in refrigeration cycle devices and can be used as refrigerants for decades.

On the other hand, some substances containing hydrogen and carbon have poor stability even in refrigeration cycle devices and are difficult to use as refrigerants. Such substances having poor stability include, for example, substances having a property of causing a disproportionation reaction. Disproportionation refers to the property of substances of the same kind reacting with each other to change into different substances. For example, if some strong energy is applied to the refrigerant in a state where adjacent substances are very close to each other, such as in a liquid state, a disproportionation reaction occurs due to the energy, and adjacent substances react with each other to change into different substances. When the disproportionation reaction occurs, heat is generated and a rapid temperature rise occurs, so the pressure may rise rapidly. For example, if a substance capable of undergoing disproportionation reaction is used as a refrigerant in a refrigeration cycle device and enclosed in a pipe such as copper, the pipe cannot withstand the increase in the pressure of the refrigerant inside, and accidents such as pipe rupture may occur. As a substance having the property of causing the disproportionation reaction, for example, 1,1,2-trifluoroethylene (HFO-1123), acetylene, and the like are known.

In addition, there is a thermal cycle system (refrigeration cycle device) that uses 1,1,2-trifluoroethylene (HFO-1123) as a working medium for thermal cycle (for example, Patent Document 1).

prior art literature

patent documents

Patent Document 1: WO12/157764 (page 3, page 12, FIG. 1, etc.)

Contents of the invention

The problem to be solved by the invention

In a refrigeration cycle device such as a thermal cycle system described in Patent Document 1, it is described that 1,1,2-trifluoroethylene (HFO-1123) is used as a working medium for a thermal cycle. 1,1,2-Trifluoroethylene (HFO-1123) is a substance that undergoes a disproportionation reaction. If it is used directly as a refrigerant, adjacent substances will react with each other due to certain energy and change into different substances, not only will it no longer function as a refrigerant, but there may also be a possibility of pipe rupture due to a sharp rise in pressure. ACCIDENT. Therefore, there is a problem that it is necessary to prevent the disproportionation reaction from occurring in order to be used as a refrigerant. Therefore, it is necessary to find a way to prevent the disproportionation reaction from occurring, but in Patent Document 1 and the like, there is no description of a method for realizing a device or the like in which the disproportionation reaction does not occur.

The present invention was made to solve the above-mentioned problems, and provides a refrigeration cycle device capable of reducing external energy received by a refrigerant and safely using a substance having a disproportionation reaction property as a refrigerant.

Solution to the problem

The refrigerating cycle device of the present invention is equipped with a refrigerating cycle in which a compressor, a first heat exchanger, a throttling device, and a second heat exchanger are connected through refrigerant piping, and the refrigerant is circulated. The refrigerant is a substance having a disproportionation reaction. Composed of a single refrigerant or a mixed refrigerant in which other substances are mixed with a substance that undergoes a disproportionation reaction, the compressor has a compression chamber and a motor in an airtight container, and resin materials are used for the insulating material of the motor.

Invention effect

The refrigeration cycle device of the present invention can prevent the disproportionation reaction of substances such as 1,1,2-trifluoroethylene (HFO-1123) from being unable to be used as refrigerants due to disproportionation reactions or accidents such as pipe ruptures, and can be used safely. as a refrigerant.

Description of drawings

FIG. 1 is a schematic diagram showing an installation example of a refrigeration cycle apparatus according to Embodiment 1 of the present invention.

Fig. 2 is a circuit configuration diagram of a refrigeration cycle apparatus according to Embodiment 1 of the present invention.

3 is a circuit configuration diagram during cooling operation of the refrigeration cycle apparatus according to Embodiment 1 of the present invention.

4 is a circuit configuration diagram during a heating operation of the refrigeration cycle apparatus according to Embodiment 1 of the present invention.

5 is a schematic diagram showing the configuration of a compressor of the refrigeration cycle apparatus according to Embodiment 1 of the present invention.

6 is a schematic diagram showing the configuration of an accumulator of the refrigeration cycle apparatus according to Embodiment 1 of the present invention.

detailed description

Hereinafter, a refrigeration cycle apparatus according to an embodiment of the invention will be described with reference to the drawings and the like. Here, in the following drawings including FIG. 1 , members assigned the same reference numerals represent the same or corresponding members, and this applies throughout the entirety of the embodiments described below. Furthermore, the forms of the constituent elements described throughout the specification are merely examples, and are not limited to the forms described in the specification. In particular, the combination of components is not limited to the combinations in the respective embodiments, and components described in other embodiments can be applied to other embodiments. In addition, when there is no need to distinguish or identify a plurality of devices of the same type that are distinguished by subscripts, etc., the subscripts may be omitted and described. In addition, the relationship between the sizes of the constituent members in the drawings may differ from the actual one. Furthermore, regarding the level of temperature, pressure, etc., the level is not particularly determined by the relationship between absolute values, but relatively determined by the state, operation, etc. of a system, device, or the like.

Embodiment 1

Embodiment 1 of the present invention will be described with reference to the drawings. FIG. 1 is a schematic diagram showing an installation example of a refrigeration cycle apparatus according to Embodiment 1 of the present invention. The refrigeration cycle device shown in FIG. 1 constitutes a refrigerant circuit that circulates a refrigerant and utilizes the refrigeration cycle of the refrigerant, so that either a cooling mode or a heating mode can be selected as an operation mode. Here, the refrigeration cycle apparatus of this embodiment is demonstrated as an example which performs air-conditioning of the air-conditioning target space (indoor space 7).

In FIG. 1 , the refrigeration cycle apparatus according to this embodiment has one outdoor unit 1 and a plurality of indoor units 2 as heat source units. The outdoor unit 1 and the indoor unit 2 are connected by an extension pipe (refrigerant pipe) 4 through which a refrigerant is conducted, and cooling energy or heat energy generated by the outdoor unit 1 is sent to the indoor unit 2 .

The outdoor unit 1 is generally arranged in an outdoor space 6 which is a space outside a building 9 such as a building (for example, a roof, etc.), and supplies cooling or heating energy to the indoor unit 2 . The indoor unit 2 is arranged at a position capable of supplying temperature-conditioned air to the indoor space 7, which is a space inside the building 9 (such as a living room, etc.), and supplies cooling air or heating air to the indoor space 7, which is a space to be air-conditioned. with air.

As shown in FIG. 1 , in the refrigeration cycle apparatus according to this embodiment, the outdoor unit 1 and each indoor unit 2 are respectively connected by two extension pipes 4 .

In addition, although the case where the indoor unit 2 is a ceiling unit type was shown as an example in FIG. 1, it is not limited to this. It can also be ceiling-embedded or ceiling-suspended, etc., as long as it can blow heating air or cooling air to the indoor space 7 directly or through pipes, etc., it can be any type of indoor unit.

In FIG. 1, although the case where the outdoor unit 1 was installed in the outdoor space 6 was shown by example, it is not limited to this. For example, the outdoor unit 1 may be installed in an enclosed space such as a machine room with ventilation openings. In addition, as long as waste heat can be exhausted to the outside of the building 9 through the exhaust duct, it may be installed inside the building 9 . In addition, a water-cooled outdoor unit 1 may be used and installed inside the building 9 . No particular problem occurs no matter where the outdoor unit 1 is installed.

In addition, the number of connected outdoor units 1 and indoor units 2 is not limited to the number shown in FIG. 1 , and the number can be determined according to the building 9 in which the refrigeration cycle apparatus of this embodiment is installed.

FIG. 2 is a circuit configuration diagram showing an example of a circuit configuration of a refrigeration cycle device (hereinafter referred to as refrigeration cycle device 100 ) according to Embodiment 1. FIG. The detailed structure of the refrigeration cycle apparatus 100 is demonstrated based on FIG. 2. FIG. As shown in FIG. 2 , the outdoor unit 1 and the indoor unit 2 are connected by an extension pipe (refrigerant pipe) 4 through which a refrigerant flows.

[Outdoor unit 1]

In the outdoor unit 1 , a compressor 10 , a first refrigerant flow switching device 11 such as a four-way valve, a heat source side heat exchanger 12 , and an accumulator 19 are mounted in series through refrigerant piping.

The compressor 10 sucks the refrigerant and compresses the refrigerant into a high-temperature and high-pressure state, and may be, for example, a capacity-controllable inverter compressor or the like. The first refrigerant flow switching device 11 is used to switch the flow of the refrigerant during the heating operation and the flow of the refrigerant during the cooling operation. The heat source side heat exchanger 12 functions as an evaporator during heating operation, and functions as a condenser (or radiator) during cooling operation. And the heat source side heat exchanger 12 as a 1st heat exchanger performs heat exchange between the air supplied from the blower not shown in figure, and a refrigerant|coolant, and evaporates and vaporizes or condenses and liquefies this refrigerant|coolant. The heat source side heat exchanger 12 functions as a condenser during the operation of cooling the indoor space 7 . In addition, the evaporator functions as an evaporator during the operation of heating the indoor space 7 . The accumulator 19 is provided on the suction side of the compressor 10 and stores refrigerant remaining in the refrigerant circuit due to a change in operation mode or the like.

The outdoor unit 1 includes a compressor 10 , a first refrigerant flow switching device 11 , a heat source side heat exchanger 12 , an accumulator 19 , a high pressure detection device 37 , a low pressure detection device 38 , and a control device 60 . In addition, the compressor 10, for example, has a compression chamber in an airtight container, and uses a low-pressure refrigerant pressure environment in the airtight container, a compressor with a low-pressure shell structure that sucks and compresses the low-pressure refrigerant in the airtight container, or uses an airtight container A compressor with a high-pressure shell structure that discharges the high-pressure refrigerant compressed in the compression chamber into a closed container in a high-pressure refrigerant pressure environment. In addition, the outdoor unit 1 is provided with a control device 60, and controls the equipment based on detection information from various detection devices, commands from a remote controller, and the like. For example, the driving frequency of the compressor 10 , the rotation speed (including ON/OFF) of the blower, switching of the first refrigerant flow switching device 11 , etc. are controlled to execute various operation modes described later. Here, the control device 60 of the present embodiment is constituted by, for example, a microcomputer or the like having a control arithmetic processing mechanism such as a CPU (Central Processing Unit). In addition, a storage means (not shown) is provided, and data including processing procedures related to control and the like are provided as programs. Furthermore, the control arithmetic processing means executes processing based on the data of the program, thereby realizing control.

[Indoor unit 2]

Each indoor unit 2 is equipped with a load-side heat exchanger 15 as a second heat exchanger. The load side heat exchanger 15 is connected to the outdoor unit 1 through the extension pipe 4 . The load-side heat exchanger 15 performs heat exchange between air supplied from a blower (not shown) and refrigerant, and generates heating air or cooling air to be supplied to the indoor space 7 . The load-side heat exchanger 15 functions as a condenser during operation for heating the indoor space 7 . In addition, the evaporator functions as an evaporator during operation for cooling the indoor space 7 .

In this FIG. 2 , the case where four indoor units 2 are connected is shown as an example, and an indoor unit 2 a , an indoor unit 2 b , an indoor unit 2 c , and an indoor unit 2 d are shown from the lower side of the drawing. In addition, corresponding to the indoor units 2a to 2d, the load side heat exchangers 15 also show a load side heat exchanger 15a, a load side heat exchanger 15b, a load side heat exchanger 15c, Load side heat exchanger 15d. In addition, as in FIG. 1 , the number of connected indoor units 2 is not limited to four as shown in FIG. 2 .

Each operation mode executed by the refrigeration cycle apparatus 100 will be described. This refrigeration cycle apparatus 100 determines the operation mode of the outdoor unit 1 to be either a cooling operation mode or a heating operation mode in accordance with a command from each indoor unit 2 . That is, the refrigeration cycle apparatus 100 can make all the indoor units 2 perform the same operation (cooling operation or heating operation) to adjust the indoor temperature. In addition, in any mode of the cooling operation mode and the heating operation mode, the operation/stop of each indoor unit 2 can be freely performed.

The operation modes performed by the refrigeration cycle device 100 include a cooling operation mode in which all the driven indoor units 2 perform a cooling operation (including stopping) and a heating operation in which all the driven indoor units 2 perform a heating operation (including stopping). model. Next, each operation mode will be described with reference to the flow of refrigerant.

[Cooling operation mode]

FIG. 3 is a refrigerant circuit diagram showing the flow of refrigerant in a cooling operation mode when the discharge temperature of the refrigeration cycle apparatus 100 is low. In FIG. 3 , the cooling operation mode will be described by taking a case where all the load-side heat exchangers 15 generate a cooling load as an example. In addition, in FIG. 3 , the piping indicated by the thick line indicates the piping through which the refrigerant flows, and the solid arrow indicates the flow direction of the refrigerant.

In the cooling operation mode shown in FIG. 3 , in the outdoor unit 1 , the first refrigerant flow switching device 11 is switched so that the refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 12 . The low-temperature and low-pressure refrigerant is compressed by the compressor 10 to be discharged as a high-temperature and high-pressure gas refrigerant. The high-temperature and high-pressure gas refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 12 via the first refrigerant flow switching device 11 . Then, the refrigerant is condensed and liquefied while radiating heat from the heat source side heat exchanger 12 to the outdoor air, and becomes a high-pressure liquid refrigerant, which flows out from the outdoor unit 1 .

The high-pressure liquid refrigerant flowing out of the outdoor unit 1 flows into the respective indoor units 2 ( 2 a to 2 d ) through the extension pipe 4 . The high-pressure liquid refrigerant flowing into the indoor units 2 (2a to 2d) flows into the expansion device 16 (16a to 16d), is throttled by the expansion device 16 (16a to 16d) and decompressed, and becomes a low-temperature and low-pressure two-phase The refrigerant. Then, it flows into each load-side heat exchanger 15 (15a to 15d) functioning as an evaporator, absorbs heat from the air flowing around the load-side heat exchanger 15, and becomes a low-temperature and low-pressure gas refrigerant. Then, the low-temperature and low-pressure gas refrigerant flows out from the indoor units 2 (2a to 2d), flows into the outdoor unit 1 again through the extension pipe 4, passes through the first refrigerant flow switching device 11, and is sucked again through the accumulator 19. compressor 10.

At this time, the opening degrees (opening areas) of the expansion devices 16a to 16d are controlled so that the temperature detected by the gas refrigerant temperature detection device 28 of the load side heat exchanger and the control device 60 of the outdoor unit 1 are transmitted to each other through communication. The temperature difference (degree of superheat) between the evaporation temperatures of the control device (not shown) of the indoor unit 2 approaches the target value.

In addition, when the cooling operation mode is executed, the refrigerant does not need to flow through the load-side heat exchanger 15 (including the temperature sensor off) with no heat load, so the operation of the indoor unit 2 is stopped. At this time, the throttle device 16 corresponding to the stopped indoor unit 2 is completely closed or opened so small that the refrigerant does not flow.

[Heating operation mode]

FIG. 4 is a refrigerant circuit diagram showing the flow of refrigerant in the heating operation mode of the refrigeration cycle apparatus 100 . In FIG. 4 , the heating operation mode will be described by taking, as an example, a case where all load-side heat exchangers 15 generate thermal energy loads. In addition, in FIG. 4 , the piping indicated by the thick line indicates the piping through which the refrigerant flows, and the solid arrow indicates the flow direction of the refrigerant.

In the heating operation mode shown in FIG. 4 , in the outdoor unit 1 , the first refrigerant flow switching device 11 is switched so that the refrigerant discharged from the compressor 10 does not pass through the heat source side heat exchanger 12 . Flow to indoor unit 2. The low-temperature and low-pressure refrigerant is compressed by the compressor 10 to be discharged as a high-temperature and high-pressure gas refrigerant, passes through the first refrigerant flow switching device 11 , and flows out of the outdoor unit 1 . The high-temperature and high-pressure gas refrigerant flowing out of the outdoor unit 1 flows into the respective indoor units 2 ( 2 a to 2 d ) through the extension pipe 4 . The high-temperature and high-pressure gas refrigerant flowing into the indoor units 2 (2a to 2d) flows into each of the load side heat exchangers 15 (15a to 15d), and radiates heat to the air flowing around the load side heat exchangers 15 (15a to 15d). At the same time, it condenses and liquefies to become a high-temperature and high-pressure liquid refrigerant. The high-temperature and high-pressure liquid refrigerant flowing out of the load-side heat exchanger 15 (15a-15d) flows into the expansion device 16 (16a-16d), and is throttled by the expansion device 16 (16a-16d) to depressurize and become a low temperature. The low-pressure two-phase refrigerant flows out from the indoor units 2 (2a to 2d). The low-temperature and low-pressure two-phase refrigerant flowing out of the indoor unit 2 flows into the outdoor unit 1 again through the extension pipe 4 .

At this time, the opening degrees (opening areas) of the expansion devices 16a to 16d are controlled so that the condensation temperature and The temperature difference (degree of subcooling) between the detection temperatures of the load-side heat exchanger liquid refrigerant temperature detection means 27 approaches the target value.

The low-temperature and low-pressure two-phase refrigerant flowing into the outdoor unit 1 flows into the heat source side heat exchanger 12, absorbs heat from the air flowing around the heat source side heat exchanger 12, and evaporates to become a low-temperature and low-pressure gas refrigerant or a low-temperature and low-pressure gas refrigerant. Two-phase refrigerant with high dryness. The low-temperature and low-pressure gas refrigerant or two-phase refrigerant is sucked into the compressor 10 again through the first refrigerant flow switching device 11 and the accumulator 19 .

When the heating operation mode is executed, the refrigerant does not need to flow through the load-side heat exchanger 15 (including the temperature sensor off) that has no heat load. However, in the heating operation mode, if the throttle device 16 corresponding to the load-side heat exchanger 15 with no heating load is completely closed or set to a small opening so that no refrigerant flows, Inside the side heat exchanger 15 , the refrigerant is cooled by the surrounding air and condenses, and the refrigerant is accumulated, which may lead to insufficient refrigerant in the entire refrigerant circuit. Therefore, during the heating operation, the opening degree (opening area) of the expansion device 16 corresponding to the load-side heat exchanger 15 with no heat load is set to a large opening degree such as fully opened to prevent accumulation of refrigerant.

In addition, the first refrigerant flow switching device 11 generally uses a four-way valve, but is not limited thereto. A two-way switching valve or a three-way switching valve may be used, and the refrigerant may flow in the same manner.

[type of refrigerant]

In the case of using a substance commonly used as a refrigerant such as R32, R410A, etc. as the refrigerant used in the refrigeration cycle device 100, there is no need to try to improve the stability of the refrigerant in the refrigerant circuit, and it can be used normally. However, here, as the refrigerant, a substance that undergoes a disproportionation reaction such as 1,1,2-trifluoroethylene (HFO-1123) having one double bond in the molecular structure represented by C ₂ H ₁ F ₃ is used. A single refrigerant or a mixed refrigerant in which other substances are mixed in a substance that undergoes a disproportionation reaction.

In order to generate a mixed refrigerant, as a substance to be mixed with a substance having a disproportionation reaction, for example, _{tetrafluoropropene} represented by C ₃ H ₂ F _{4 (} 2,3,3, 3-tetrafluoropropene (HFO-1234yf, 1,3,3,3-tetrafluoro-1-propene represented by CF ₃ CF=CHF (HFO-1234ze, etc.) or difluoromethane represented by CH ₂ F ₂ (HFC-32) etc. However, the substance to be mixed with the substance having the property of disproportionation reaction is not limited to this, and HC-290 (propane) or the like may be mixed, as long as it is a substance having thermal properties that can be used as a refrigerant of the refrigeration cycle device 100. can use. In addition, the mixing ratio may be any mixing ratio.

If a substance that undergoes disproportionation reaction is directly used as a refrigerant, it is possible that due to some strong energy from the outside, adjacent substances may react with each other and change into different substances. Therefore, if in the refrigerant circuit, if no measures are taken to use a substance that undergoes disproportionation reaction as a refrigerant, not only may it become a different substance and no longer play the role of refrigerant, but it may also be caused by heat generation. The resulting sudden pressure rise may cause accidents such as pipe rupture. This disproportionation reaction is particularly likely to occur where there is a liquid state substance such as a liquid or a two-phase state where adjacent substances are very close to each other. However, in a gas state, when strong energy is applied, the disproportionation reaction occurs. Therefore, in order to be used as a refrigerant, it is necessary to find a way to prevent the disproportionation reaction from occurring. The disproportionation reaction of the refrigerant is caused by external energy such as causing the refrigerant to collide with a structure or passing an electric current through the refrigerant.

[Compressor 10]

The compressor 10 uses a hermetic compressor. For example, a high-pressure shell type or a low-pressure shell type, a rotary compressor or a scroll compressor is used. FIG. 5 is a schematic diagram of the configuration of compressor 10 according to Embodiment 1 of the present invention. FIG. 5 is a side view of the compressor 10 viewed from the side. The compressor 10 shown in FIG. 5 is a high-pressure shell type rotary compressor. The compressor 10 includes: an inflow pipe 41 through which the refrigerant flows into the compressor 10 , an outflow pipe 42 through which the refrigerant flows out from the compressor 10 , a compression unit 43 which compresses the refrigerant, a motor 44 as a drive source of the compressor 10 , And the compressor casing 45 which is a closed container covering the compression part 43 and the motor 44 . The motor 44 is arranged above the compression unit 43 .

The motor 44 includes a stator 48 and a rotor 49 . The stator 48 is fixed to the compressor housing 45 . The rotor 49 is arranged inside the stator 48 and connected to the shaft 50 . The compression unit 43 includes a rotary plunger 51 . The rotary plunger 51 is fixed to the shaft 50 like the rotor 49 , and the rotation of the rotor 49 is transmitted to the rotary plunger 51 . The rotary plunger 51 is eccentrically attached to the shaft 50 .

In Figure 5. Solid arrows indicate the direction of refrigerant flow. The refrigerant flows into the compressor 10 from the inflow pipe 41 , and flows into the compression chamber 47 of the compression unit 43 through the suction port 46 . The compression chamber 47 changes in volume according to the rotation of the rotary plunger 51 by the rotary plunger 51 eccentrically attached to the shaft 50, and compresses the inflowing refrigerant. The compressed high-temperature and high-pressure gas refrigerant is ejected from the compression chamber 47 into the compressor casing 45 , flows around the motor 44 , and flows out of the compressor 10 through the outflow pipe 42 .

Here, types of hermetic compressors include the above-mentioned high-pressure shell type and low-pressure shell type. The low-pressure shell compressor 10 has a compression unit 43 and a motor 44 in a compressor shell 45 that is an airtight container. The refrigerant sucked into the low-pressure shell compressor 10 flows into the compressor shell 45, and the inside of the compressor shell 45 becomes a low-pressure refrigerant environment. The compression chamber 47 of the compression part 43 is used for sucking and compressing the refrigerant in the compressor housing 45 , and after the compression is completed, the refrigerant is discharged from the compression part 43 to the outside of the compressor housing 45 . In the low-pressure shell compressor 10, for example, the compression unit 43 is arranged at the upper part, and the motor 44 is arranged at the lower part. In this low-pressure shell-type compressor 10 , when the two-phase refrigerant flows into the compressor 10 , the liquid component in the two-phase refrigerant is drawn into the compressor housing 45 before being drawn into the compression chamber 47 . It separates, flows around the motor 44 arranged at the lower part of the compression part 43 , and falls to the lower part of the compressor 10 . Since the liquid refrigerant with a short intermolecular distance flows around the motor 44 , disproportionation reaction easily occurs, and the disproportionation reaction of the refrigerant easily occurs in the compressor housing 45 of the low-pressure shell compressor 10 .

In addition, the high-pressure shell-type compressor 10 is comprised as mentioned above. Therefore, the high-temperature gas refrigerant compressed in the compression chamber 47 is discharged into the compressor housing 45 , which is a space where the motor 44 is exposed. The disproportionation reaction of the refrigerant is easy to occur in a liquid and two-phase state where the distance between molecules is short, but the disproportionation reaction is a chemical reaction, and it is well known that the higher the temperature, the easier the chemical reaction is (the reaction speed is increased). Therefore, even if the refrigerant is in a gaseous state, as long as the temperature is higher, the disproportionation reaction is more likely to occur, and the compressor housing 45 of the high-pressure shell compressor 10 is in a state (though not to the extent of the low-pressure shell compressor). The state of the disproportionation reaction of the agent.

As described above, in the compressor housing 45 of the low-pressure housing compressor 10 , liquid refrigerant having a short intermolecular distance flows around the motor 44 . In addition, the compressor casing 45 of the high-pressure casing compressor 10 is filled with a high-temperature gas refrigerant. Therefore, regardless of the compressor 10 , the disproportionation reaction of the refrigerant is likely to occur in the compressor housing 45 .

In the compressor 10, which is a hermetic compressor, the motor 44 is exposed to a low-pressure refrigerant environment or a high-pressure refrigerant environment. The stator 48 and the rotor 49 of the motor 44 need to be insulated because current flows. If the motor 44 is not insulated, the current will also flow through the surrounding refrigerant, not only the risk of leakage, but also the disproportionation reaction of the refrigerant due to the energy of the current.

As the insulating material of the motor 44, it is preferable to use a substance that is not physically or chemically denatured by the refrigerant, and it is particularly preferable to use a substance having solvent resistance, extraction resistance, thermal and chemical stability, and foaming resistance. As the insulating material of the motor 44, there are insulating coating materials for the windings of the stator 48, insulating films, insulators holding the windings, insulating pipes, etc., and resin materials can be used.

Specifically, polyvinyl formal, polyester, THEIC modified polyester, polyamide, polyamideimide, polyesterimide, polyesteramideimide one or more of the substances. In addition, paint leather with a glass transition temperature above 120°C can also be used.

In addition, the insulating film of the stator 48 uses polyethylene terephthalate (PET), polyethylene naphthalate, polyphenylene sulfide (PPS), polybutylene terephthalate (PBT) one or more of the substances. One or more materials selected from polyetheretherketone (PEEK) and liquid crystal polymer (LCP) are used as insulating materials for holding windings such as insulators. The paint uses epoxy resin. Also, one or more materials selected from polytetrafluoroethylene (PTFE) and tetrafluoroethylene-hexafluoropropylene copolymer resin (FEP) are used for the insulating tube of the stator 48 .

In addition, as described above, even if the refrigerant is in a gaseous state, as long as the temperature rises, the disproportionation reaction easily occurs in the compressor housing 45 . The disproportionation reaction is that the higher the temperature, the easier the reaction is to proceed (the reaction speed is increased). Especially at a temperature above 50° C., the disproportionation reaction as a chemical reaction tends to occur. In a refrigeration cycle device having a high-pressure shell compressor 10, the temperature of the refrigerant in the compressor shell 45 of the compressor 10 is above 50°C in most cases except for the transient state at startup. temperature. However, even in this state, the disproportionation reaction of the refrigerant can be suppressed as long as the motor 44 of the compressor 10 is insulated as described above. In addition, in the state of 80°C, the disproportionation reaction is more likely to occur.

Here, it is considered to use refrigerating machine oil showing compatibility with refrigerants in the refrigerating cycle. The solubility of the refrigerant relative to the miscible refrigerating machine oil is under the same pressure condition, the lower the temperature, the greater the solubility, and under the same temperature condition, the higher the pressure, the greater the solubility. When the refrigerant dissolves in the refrigerating machine oil, the molecules of the refrigerating machine oil dissolve and exist between the molecules of the refrigerant. That is, if the solubility of the refrigerant with respect to the refrigerating machine oil is high, the refrigerating machine oil will exist between many molecules of the refrigerant. The disproportionation reaction of the refrigerant is a phenomenon in which the molecules of adjacent refrigerants react with each other. If a refrigerator oil that is miscible with the refrigerant is used, there are molecules of the refrigerator oil between the molecules of the refrigerant. Therefore, the disproportionation of the refrigerant The reaction becomes more difficult to occur.

In order to suppress the disproportionation reaction of the refrigerant, the greater the solubility of the refrigerant relative to the refrigerating machine oil, the better the effect. In practical terms, when the refrigerant is in a liquid state or a two-phase state, if the solubility of the refrigerant with respect to the refrigerating machine oil is 50% by weight (weight %) or more, then a large amount of the refrigerant is dissolved in the refrigerating machine oil, so it is possible to Inhibition of disproportionation reactions. Therefore, when the low-pressure shell compressor 10 is used as the compressor 10, for example, the temperature of the refrigerant in the compressor shell 45 is 0° C. and the pressure is the saturated pressure when the temperature of the refrigerant is 0° C. If the solubility of the refrigerant with respect to the refrigerating machine oil is 50% by weight (weight %) or more, even if a two-phase refrigerant flows in, the disproportionation reaction of the refrigerant can be sufficiently suppressed.

In addition, as described above, the disproportionation reaction occurs most easily in the case where the refrigerant is in a liquid state or a two-phase state. In addition, even if the refrigerant is in a gaseous state, a disproportionation reaction as a chemical reaction is likely to occur at a high temperature, especially at a temperature above 50°C, and even above 80°C. However, when the refrigerant is in a liquid state or a two-phase state In the case of , the disproportionation reaction is more likely to occur. Although a refrigerant in a gaseous state is soluble in miscible refrigerating machine oil, the solubility required for suppressing disproportionation reaction in a high-temperature gaseous state may be smaller than that in a liquid state or a two-phase state. Practically, when the refrigerant is in a gaseous state, disproportionation reaction of the high-temperature gaseous refrigerant can be sufficiently suppressed if the solubility is at least 10 wt % (weight %). Therefore, when the high-pressure shell compressor 10 is used as the compressor 10, for example, the temperature of the refrigerant in the compressor shell 45 is 80° C. and the pressure is the saturated pressure when the temperature of the refrigerant is 50° C. If the solubility of the refrigerant with respect to the refrigerating machine oil is 10% by weight (weight %) or more, the disproportionation reaction of the refrigerant can be sufficiently suppressed.

In addition, as the refrigerating machine oil of the present embodiment, refrigerating machine oil having a relatively high volume resistivity is used. For example, the volume resistivity of refrigerating machine oil is 2×10 ¹⁰ Ω·m or more at 20°C. Therefore, if miscible oil is used as the refrigerating machine oil, the volume resistivity of the mixed fluid of the refrigerant and refrigerating machine oil in the compressor housing 45 of the compressor 10 will be a relatively high value. Therefore, in the compressor 10, the leakage current from the motor 44 is relatively small, and the disproportionation reaction of the refrigerant is less likely to occur.

In addition, as the refrigerating machine oil, a refrigerating machine oil mainly composed of polyol ester and polyvinyl ether is used. Both polyol esters and polyvinyl ethers are refrigerating machine oils that have a relatively high volume resistivity and are miscible with refrigerants having one double bond in their molecular structure.

In addition, in the present embodiment, the case where the compression unit 43 is located below and the motor 44 is located above in the compressor housing 45 of the compressor 10 has been described as an example, but the present invention is not limited thereto. Alternatively, the compression unit 43 may be located above and the motor 44 may be located below. This is the same whether it is a high pressure shell compressor or a low pressure shell compressor.

In addition, the case where the compressor 10 is a rotary compressor has been described as an example, but it is not limited to this, and any type of compressor such as a scroll compressor or a screw compressor can also be used, and the same compressor can be obtained. Effect.

[Reservoir 19]

FIG. 6 is a schematic diagram of the structure of the accumulator 19 according to Embodiment 1 of the present invention. FIG. 6 is a side view of the accumulator 19 viewed from the side. The accumulator 19 is composed of an inflow pipe 52, an outflow pipe 53, an oil return hole 54 provided on the outflow pipe 53, and an accumulator housing 55 of the liquid accumulator 19, and the inflow pipe 52 and the outflow pipe 53 are inserted into the liquid reservoir. The structure of the device housing 55. In FIG. 6 , solid arrows indicate the direction in which the refrigerant flows. The refrigerant flows in from the inflow pipe 52 , is released into the accumulator case 55 to increase its volume, and then flows out through the outflow pipe 53 . At this time, the inlet of the outflow pipe 53 is positioned higher than the outlet of the inflow pipe 52 , and the refrigerant flowing in from the inflow pipe 52 does not directly flow into the outflow pipe 53 due to inertial force and gravity.

The inflow pipe 52 is inserted from the top of the accumulator case 55, and bends laterally in the accumulator case 55. The position where the inner wall surface of the body 55 contacts is provided toward the inner wall surface of the accumulator case 55 . By directing the inflow pipe 52 toward the inner wall of the accumulator case 55, the refrigerant flowing in from the inflow pipe 52 collides with the inner wall of the accumulator case 55, and the liquid of the two-phase refrigerant The components and refrigerator oil are separated within the accumulator housing 55 and are stored below the accumulator housing 55 under the force of gravity.

The oil return hole 54 provided in the outflow pipe 53 plays the role of allowing the refrigerant liquid in which the refrigerating machine oil is dissolved and stored under the accumulator housing 55 to flow into the outflow pipe 53 to return the refrigerating machine oil to the compressor. 10. At this time, since the refrigerant dissolves in the refrigerating machine oil, the refrigerant also flows out from the oil return hole 54 together with the refrigerating machine oil, and is sucked into the compressor. Therefore, the refrigerant in the two-phase state whose dryness is greater than 0 and less than 1 is sucked into the compressor 10 . Therefore, when a low-pressure shell compressor is used and excess refrigerant is generated in the refrigerating cycle, refrigerant in a two-phase state with a dryness greater than 0 and less than 1 flows into the compressor housing 45 , and the refrigerant flows in the motor 44 flow around. That is, if the oil return hole 54 is provided inside the accumulator 19 , the refrigerant in the two-phase state whose dryness is greater than 0 and less than 1 flows into the compressor 10 .

During cooling operation, low-temperature and low-pressure gas refrigerant flows into the accumulator 19, and during heating operation, since excess refrigerant is generated in the refrigerant circuit, two-phase refrigerant mixed with gas and liquid flows into the accumulator 19. Device 19. In addition, in a refrigeration cycle device such as a multi-type air conditioner having a plurality of indoor units 2, due to changes in the operating number of the indoor units 2, etc., surplus refrigerant may be generated even during cooling operation, and two-phase refrigerant may flow into the air. to reservoir 19.

Here, in this embodiment, the accumulator 19 having the accumulator case 55 elongated in the vertical direction (vertical direction) is illustrated, but any shape such as a elongated structure in the lateral direction may be used. .

In addition, in this embodiment, the case where the accumulator 19 for storing excess refrigerant is provided in the refrigerant circuit has been described, but for example, when the extension pipe 4 is short, or when the number of indoor units 2 is one, etc. In this case, when the remaining refrigerant is small, the accumulator 19 may not be arranged. In addition, when the accumulator 19 is not disposed, the two-phase refrigerant flows directly into the compressor 10 depending on the operating state.

[Extension piping 4]

As described above, the refrigeration cycle apparatus 100 of this embodiment has several operation modes. In these operation modes, the refrigerant flows through the extension pipe 4 connecting the outdoor unit 1 and the indoor unit 2 .

In addition, a high-pressure detection device 37 and a low-pressure detection device 38 are provided to control the high pressure and low pressure of the refrigeration cycle to target values, but a temperature detection device for detecting saturation temperature may also be provided.

In addition, although it seems that the first refrigerant flow switching device 11 is shown as a four-way valve, it is not limited to this, and several two-way switching valves or three-way switching valves may be used to form a The refrigerant flows in the same way.

In addition, generally, blowers are often attached to the heat source side heat exchanger 12 and the load side heat exchangers 15a to 15d to promote condensation or evaporation by blowing air, but the present invention is not limited thereto. For example, as the load side heat exchangers 15a to 15d, heat exchangers such as plate heaters using radiation can be used, and as the heat source side heat exchanger 12, a water-cooled type heat exchanger that moves heat through water or antifreeze can be used. switch. Any heat exchanger can be used as long as it can dissipate heat or absorb heat.

In addition, although the case where there are four load side heat exchangers 15a-15d was demonstrated as an example here, any number may be connected. Also, a plurality of outdoor units 1 may be connected to form one refrigeration cycle.

In addition, the cooling and heating switching type refrigeration cycle apparatus 100 in which the indoor unit 2 performs only the cooling operation or any operation of the heating operation has been described as an example, but the present invention is not limited thereto. For example, it can also be applied to a refrigeration cycle device in which the indoor unit 2 can arbitrarily select any one of the cooling operation and the heating operation, and the entire system can perform a mixed operation of the indoor unit 2 performing the cooling operation and the indoor unit 2 performing the heating operation. , the same effect can be obtained.

In addition, it can also be applied to air-conditioning devices such as indoor air conditioners to which only one indoor unit 2 can be connected, refrigeration equipment connected to showcases or direct expansion coolers, etc., as long as it is a refrigeration cycle device that uses a refrigeration cycle, the same Effect.

In addition, it may be a refrigeration cycle device configured to use a plate heat exchanger or the like for heat exchange with water or antifreeze as the load-side heat exchanger 15, and to circulate the heat-exchanged water or antifreeze into the room. The unit 2 supplies temperature-regulated air to the space to be air-conditioned.

Explanation of reference signs

1 heat source unit (outdoor unit), 2a, 2b, 2c, 2d indoor unit, 4 extension piping (refrigerant piping), 6 outdoor space, 7 indoor space, 8 other than outdoor space and indoor space such as the back of the ceiling Space, 9 buildings and other buildings, 10 compressor, 11 first refrigerant flow switching device (four-way valve), 12 heat source side heat exchanger, 15, 15a, 15b, 15c, 15d load side heat exchanger, 16 , 16a, 16b, 16c, 16d throttling device, 19 liquid receiver, 27 load side heat exchanger liquid refrigerant temperature detection device, 28 load side heat exchanger gas refrigerant temperature detection device, 37 high pressure detection device, 38 low pressure Detection device, 41 inflow pipe, 42 outflow pipe, 43 compression part, 44 motor, 45 compressor casing, 46 suction port, 47 compression chamber, 48 stator, 49 rotor, 50 shaft, 51 rotary plunger, 52 inflow pipe, 53 outflow pipe, 54 oil return hole, 55 reservoir shell, 60 control device, 100 refrigeration cycle device.

Claims (10)

1. a refrigerating circulatory device, described refrigerating circulatory device possess utilize refrigerant piping connect compressor, first heat hand over Parallel operation, throttling arrangement and the second heat exchanger the kind of refrigeration cycle for refrigerant circulation,

Described cold-producing medium is the unitary system cryogen being made up of the material of the character that disproportionated reaction occurs or disproportionated reaction is occurring The material of character is mixed with the mix refrigerant of other materials,

Described compressor has discharge chambe and motor in closed container,

The insulating materials of described motor uses resin material.

2. refrigerating circulatory device according to claim 1, it is characterised in that

The material that the character of described disproportionated reaction occurs is 1,1,2-trifluoro-ethylene.

3. refrigerating circulatory device according to claim 1 and 2, it is characterised in that

The insulating materials of described motor uses from polyvinyl formal, polyester, THEIC modified poly ester, polyamide, polyamide acyl Imines, polyesterimide, imide, polyethylene terephthalate, PEN, polyphenylene sulfide Ether, polybutylene terephthalate (PBT), polyether-ether-ketone, liquid crystal polymer, epoxy resin, polytetrafluoroethylene (PTFE), tetrafluoroethene-hexafluoro The one or more materials selecting in the group of propylene copolymer resin.

4. refrigerating circulatory device according to any one of claim 1 to 3, it is characterised in that

Described compressor is to make described cold-producing medium be flowed in described closed container, at described discharge chambe in described closed container Cold-producing medium be compressed and the described cold-producing medium through overcompression discharged outside described closed container low-pressure shell formula compression Machine,

Have make mass dryness fraction be more than 0 and the described cold-producing medium of two-phase state less than 1 be flowed into the described airtight appearance of described compressor Operating condition in device.

5. refrigerating circulatory device according to any one of claim 1 to 3, it is characterised in that

Described compressor makes described cold-producing medium be flowed into described discharge chambe, at described discharge chambe to being flowed into described discharge chambe Described cold-producing medium is compressed, makes discharge in described closed container through the described cold-producing medium of overcompression and make described airtight appearance The High Pressure Shell formula compressor that described cold-producing medium in device is discharged outside described closed container,

The fortune of the described cold-producing medium of more than 50 DEG C is discharged in having from the described discharge chambe of described compressor to described closed container Turn state.

6. refrigerating circulatory device according to any one of claim 1 to 5, it is characterised in that

It is filled with the refrigerator oil with described cold-producing medium with intersolubility in described kind of refrigeration cycle.

7. refrigerating circulatory device according to claim 6, it is characterised in that

Described refrigerator oil is with polyol ester or polyvinylether as main component.

8. the refrigerating circulatory device according to claim 6 or 7, it is characterised in that

The specific insulation of described refrigerator oil is 2 × 10 when 20 DEG C¹⁰More than Ω m.

9. the 6th, the claim the 4th, being subordinated to claim 4 according to claim is subordinated to appoint in the claim 7 of claim 4 Refrigerating circulatory device described in one, it is characterised in that

Described refrigerator oil in the temperature that the pressure that the temperature of described cold-producing medium is 0 DEG C and described cold-producing medium is described cold-producing medium is It in the state of saturation pressure when 0 DEG C, is more than 50 weight % relative to the solubility of described cold-producing medium.

10. the 6th, the claim the 5th, being subordinated to claim 5 according to claim is subordinated in the claim 7 of claim 5 Refrigerating circulatory device described in any one, it is characterised in that

Described refrigerator oil is in the temperature that the pressure that the temperature of described cold-producing medium is 80 DEG C and described cold-producing medium is described cold-producing medium It in the state of being saturation pressure when 50 DEG C, is more than 10 weight % relative to the solubility of described cold-producing medium.