WO2021024380A1 - Dispositif à cycle frigorifique - Google Patents

Dispositif à cycle frigorifique Download PDF

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Publication number
WO2021024380A1
WO2021024380A1 PCT/JP2019/030907 JP2019030907W WO2021024380A1 WO 2021024380 A1 WO2021024380 A1 WO 2021024380A1 JP 2019030907 W JP2019030907 W JP 2019030907W WO 2021024380 A1 WO2021024380 A1 WO 2021024380A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
compressor
refrigerating machine
machine oil
refrigeration cycle
Prior art date
Application number
PCT/JP2019/030907
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English (en)
Japanese (ja)
Inventor
修平 小山
卓美 森下
矢野　賢司
Original Assignee
三菱電機株式会社
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2019/030907 priority Critical patent/WO2021024380A1/fr
Publication of WO2021024380A1 publication Critical patent/WO2021024380A1/fr

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    • C—CHEMISTRY; METALLURGY
    • C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
    • C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
    • C09K5/00—Heat-transfer, heat-exchange or heat-storage materials, e.g. refrigerants; Materials for the production of heat or cold by chemical reactions other than by combustion
    • C09K5/02—Materials undergoing a change of physical state when used
    • C09K5/04—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
    • C10M105/00—Lubricating compositions characterised by the base-material being a non-macromolecular organic compound
    • C10M105/08—Lubricating compositions characterised by the base-material being a non-macromolecular organic compound containing oxygen
    • C10M105/32—Esters
    • C10M105/38—Esters of polyhydroxy compounds
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
    • C10M107/00—Lubricating compositions characterised by the base-material being a macromolecular compound
    • C10M107/20—Lubricating compositions characterised by the base-material being a macromolecular compound containing oxygen
    • C10M107/22—Macromolecular compounds obtained by reactions only involving carbon-to-carbon unsaturated bonds
    • C10M107/24—Macromolecular compounds obtained by reactions only involving carbon-to-carbon unsaturated bonds containing monomers having an unsaturated radical bound to an alcohol, aldehyde, ketonic, ether, ketal or acetal radical
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
    • C10M137/00—Lubricating compositions characterised by the additive being an organic non-macromolecular compound containing phosphorus
    • C10M137/02—Lubricating compositions characterised by the additive being an organic non-macromolecular compound containing phosphorus having no phosphorus-to-carbon bond
    • C10M137/04—Phosphate esters
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
    • C10M169/00—Lubricating compositions characterised by containing as components a mixture of at least two types of ingredient selected from base-materials, thickeners or additives, covered by the preceding groups, each of these compounds being essential
    • C10M169/04—Mixtures of base-materials and additives
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type

Definitions

  • the present invention relates to a refrigeration cycle device including a refrigerant circuit, in which the refrigerant sealed in the refrigerant circuit is carbon dioxide or a mixed refrigerant containing carbon dioxide.
  • a refrigeration cycle device that circulates carbon dioxide as a refrigerant in a refrigerant circuit having a compressor, a condenser, an expansion device, and an evaporator
  • the refrigerating machine oil used in the compressor is 5 ⁇ 300 cSt at viscosity 40 ° C., and a volume resistivity 10 8 ⁇ ⁇ cm or more and, when the carbon dioxide is saturated dissolved
  • a polyalkylene glycol refrigerating machine oil having a pour point of ⁇ 30 ° C. or lower was used.
  • the organic material used in the refrigeration cycle apparatus was a material that was not physically or chemically modified by high-temperature and high-pressure carbon dioxide.
  • the present invention solves the above problems, and an object of the present invention is to provide a refrigerating cycle apparatus capable of preventing damage to the compressor without solidifying the refrigerating machine oil contained in the refrigerant in a low temperature environment in the refrigerant circuit. Is.
  • the refrigerating cycle device includes a refrigerant circuit in which a compressor, a condenser, an expansion device, and an evaporator are connected in a ring shape, and the refrigerant sealed in the refrigerant circuit is a mixture containing carbon dioxide or carbon dioxide.
  • the refrigerating machine oil which is a refrigerant and is used in the compressor is saturated and melted with the refrigerant, and the main component of the refrigerating machine oil is at least one of polyol ester and polyvinyl ether, and the refrigerating machine oil.
  • the flow point in the atmosphere is -35 ° C or lower and -57 ° C or higher, and the extreme pressure agent contained in the refrigerating machine oil is at least one of tricresyl phosphate and trifinyl fluoride. is there.
  • the refrigerant sealed in the refrigerant circuit is carbon dioxide or a mixed refrigerant containing carbon dioxide.
  • the refrigerating machine oil used in the compressor is saturated and melted with the refrigerant.
  • the main component in the refrigerating machine oil is at least one of polyol ester and polyvinyl ether.
  • the pour point of refrigerating machine oil in the atmosphere is ⁇ 35 ° C. or lower and ⁇ 57 ° C. or higher.
  • the extreme pressure agent contained in the refrigerating machine oil is at least one of tricresyl phosphate and trifinyl phosphate. Therefore, the refrigerating machine oil contained in the refrigerant does not solidify in a low temperature environment in the refrigerant circuit, and damage to the compressor can be prevented.
  • FIG. 5 is a relationship diagram showing a correlation between the discharge temperature and time of the refrigerant discharged from the compressor according to the first embodiment in comparison with a comparative example in which the arrangement of the expansion valve and the solenoid valve is reversed.
  • FIG. It is explanatory drawing which shows the compression process according to the presence or absence of a subport which concerns on Embodiment 1.
  • FIG. It is a flowchart which shows the control of the refrigeration cycle apparatus which concerns on Embodiment 1.
  • FIG. It is explanatory drawing which shows the compressor which concerns on Embodiment 2 in the vertical section.
  • It is a relational figure which shows the correlation between the rotation speed of a compressor and volumetric efficiency according to the presence or absence of a check valve which concerns on Embodiment 2.
  • FIG. It is a relational figure which shows the correlation between the rotation speed of a compressor and the compressor efficiency depending on the presence or absence of a check valve which concerns on Embodiment 2.
  • FIG. 1 is a schematic view showing a refrigeration cycle device 100 according to the first embodiment.
  • the refrigeration cycle device 100 includes a refrigerant circuit 60 in which a compressor 50, a condenser 51, an expansion device 52, and an evaporator 53 are connected in a ring shape.
  • the refrigeration cycle device 100 includes a control device 70 that controls the refrigerant circuit 60.
  • the condenser 51 is a user-side heat exchanger is described.
  • a four-way valve or the like may be provided so that the condenser 51 is switched to the heat source side heat exchanger.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 50 is cooled by the condenser 51 to become a liquid refrigerant.
  • the liquid refrigerant cooled by the condenser 51 is expanded to a low pressure by the expansion device 52. After that, the refrigerant becomes a gas refrigerant again in the evaporator 53 and is sucked into the compressor 50.
  • the refrigerant circuit 60 is provided with an injection flow path 57 that returns a part of the refrigerant before flowing out of the condenser 51 and flowing into the expansion device 52 to the compressor 50.
  • the injection flow path 57 branches from between the condenser 51 and the expansion device 52, and is connected to the compressor 50.
  • the expansion valve 56 and the solenoid valve 55 are arranged in this order from the side closest to the compressor 50.
  • the expansion valve 56 is a flow rate adjusting valve for the refrigerant flowing in the injection flow path 57.
  • the solenoid valve 55 is an on-off valve that opens and closes the injection flow path 57.
  • the expansion valve 56 and the solenoid valve 55 are controlled by the control device 70.
  • the control device 70 can control the expansion valve 56 to adjust the flow rate of injection into the compressor 50.
  • Carbon dioxide (CO 2 ) is sealed as a refrigerant in the refrigerant circuit 60 of the refrigeration cycle device 100.
  • the refrigerant sealed in the refrigerant circuit 60 may be carbon dioxide or a mixed refrigerant containing carbon dioxide.
  • the cold resistance temperature of the compressor 50, the expansion device 52, the evaporator 53, and the accumulator 54, which have a low pressure in the component group of the refrigerant circuit 60, is set to ⁇ 50 ° C. or lower and ⁇ 57 ° C. or higher.
  • the cold resistance temperature of the refrigerant circuit 60 is -50 ° C or lower, for example, when the low pressure cut lower limit value is set to -50 ° C, the compressor 50 is delayed in stopping due to a detection delay, and the pressure or temperature rises to -50 ° C or lower. Even if it goes down, it will not break down and reliability can be ensured.
  • the cold resistance temperature of the refrigerant circuit 60 is ⁇ 57 ° C.
  • the component group of the refrigerant circuit 60 can be sufficiently used up to the triple point of carbon dioxide as a refrigerant of ⁇ 57 ° C., and the function of the refrigeration cycle device 100 is up to ⁇ 57 ° C. Can be secured. Carbon dioxide liquefies when it falls below the triple point. Therefore, carbon dioxide below the triple point cannot be vaporized by the evaporator 53, and cannot be established as the refrigeration cycle device 100.
  • FIG. 2 is a hardware configuration diagram showing the control device 70 according to the first embodiment.
  • the control device 70 is responsible for controlling the compressor 50, the expansion device 52, the expansion valve 56, the solenoid valve 55, and the like.
  • the control device 70 is a processing circuit including a microcomputer including a memory such as a CPU, ROM and RAM, and an input / output device such as an I / O port.
  • the control device 70 stores the pour point Tp of the refrigerating machine oil in the atmosphere in the memory in advance.
  • the control device 70 constitutes a control circuit for performing control in which the pour point Tp of the refrigerating machine oil and the lower limit value Tv of the evaporation temperature used in the refrigerant circuit 60 satisfy (Tp-15) ⁇ Tv. The reason for providing the control circuit will be described later.
  • FIG. 3 is an explanatory view showing the compressor 50 according to the first embodiment in a vertical cross section.
  • the compressor 50 is a scroll compressor used in the refrigeration cycle device 100.
  • the compressor 50 has a function of sucking a fluid containing a refrigerant, compressing it into a high temperature and high pressure state, and discharging it.
  • a carbon dioxide refrigerant is used.
  • the refrigerating machine oil used in the compressor 50 is saturated and melted with the refrigerant.
  • the main component in the refrigerating machine oil is at least one of polyol ester and polyvinyl ether.
  • the pour point of refrigerating machine oil in the atmosphere is ⁇ 35 ° C. or lower and ⁇ 57 ° C. or higher.
  • the extreme pressure agent contained in the refrigerating machine oil is at least one of tricresyl phosphate and trifinyl phosphate.
  • the compressor 50 includes a semi-closed container whose outer shell is composed of an upper shell 18, a middle shell 19, and a lower shell 20.
  • the compressor 50 has a compression unit 35 that compresses the refrigerant in a semi-closed container.
  • the compressor 50 has a drive mechanism unit 36 and other components in a semi-sealed container.
  • the lower part in the lower shell 20 is an oil sump 16 for storing refrigerating machine oil.
  • the upper shell 18, the middle shell 19, and the lower shell 20 are detachably fastened with bolts or the like, and the internal components thereof are interchangeably configured.
  • the sealing member between the compressor 50 and the outside air is made of a metal packing that does not allow carbon dioxide to permeate between the upper shell 18, the middle shell 19, and the lower shell 20, a PTFE resin alone, or a rubber whose surface is covered with PTFE. O-ring etc. are used.
  • the compression unit 35 has a function of compressing the refrigerant sucked from the suction pipe 5 and discharging it from the discharge pipe 6 to the outside of the compressor 50.
  • the drive mechanism unit 36 exerts a function of driving the swing scroll 2 constituting the compression unit 35 in order to compress the refrigerant. That is, the drive mechanism unit 36 drives the swing scroll 2 via the crankshaft 4, and the compression unit 35 compresses the refrigerant.
  • the drive mechanism unit 36 is arranged below the compression unit 35.
  • the compression unit 35 has a fixed scroll 1 and a swing scroll 2.
  • the compression unit 35 is configured by combining a fixed scroll 1 in which the fixed spiral body 1b is projected from the fixed base plate 1c and a swing scroll 2 in which the swing spiral body 2b is projected from the rocking base plate 2c. There is.
  • the swing scroll 2 is arranged on the lower side, and the fixed scroll 1 is arranged on the upper side of the swing scroll 2.
  • the fixed scroll 1 has a fixed base plate 1c and a fixed spiral body 1b which is a spiral protrusion provided on the lower surface of the fixed base plate 1c.
  • the oscillating scroll 2 has a oscillating base plate 2c and a oscillating spiral body 2b which is a spiral projection provided on the upper surface of the oscillating base plate 2c.
  • the fixed scroll 1 and the swinging scroll 2 are mounted in the central shell 19 by engaging the fixed spiral body 1b and the swinging spiral body 2b with each other.
  • a compression chamber 12 is formed between the fixed spiral body 1b and the rocking spiral body 2b, whose volume is reduced inward in the radial direction.
  • the fixed scroll 1 is detachably fastened to the frame 3 with bolts or the like.
  • the frame 3 is fixed in the central shell 19 by bolts, shrink fitting, press fitting, or the like.
  • a discharge port 1a for discharging the refrigerant from the compression chamber 12 formed by both the fixed spiral body 1b and the rocking spiral body 2b is provided.
  • the outlet opening of the discharge port 1a is provided with a leaf spring valve 9 that covers the outlet opening to prevent backflow of the refrigerant.
  • a valve retainer 8 for limiting the lift amount of the valve 9 is provided on one end side of the valve 9.
  • the fixed scroll 1 is provided with an injection port 1e that guides an intermediate pressure refrigerant from the injection pipe 7 connected to the injection flow path 57 to the compression chamber 12.
  • the injection port 1e is arranged at a position that does not communicate with the low pressure space in the compressor 50.
  • a sub port 1d for discharging the refrigerant is provided before the compression chamber 12 communicates with the discharge port 1a in the compression process of the compressor 50.
  • the subport 1d relieves the intermediate pressure refrigerant when the intermediate pressure in the compression process exceeds the discharge pressure.
  • the outlet opening of the subport 1d is provided with a leaf spring subport valve 11 that covers the outlet opening to prevent backflow of the refrigerant.
  • a subport valve retainer 10 for limiting the lift amount of the subport valve 11 is provided on one end side of the subport valve 11.
  • the swing scroll 2 performs an eccentric turning motion with respect to the fixed scroll 1 by the old dam ring 15 without rotating.
  • a swing bearing portion 2d that receives a driving force from an eccentric portion 4a of the crankshaft 4 is formed at the center of the swing scroll 2.
  • the eccentric portion 4a of the crankshaft 4 is fitted to the swing bearing portion 2d of the swing scroll 2 with a slight gap.
  • the surface of the oscillating scroll 2 opposite to the forming surface of the oscillating spiral body 2b is axially supported by a thrust bearing portion provided on the frame 3.
  • the drive mechanism unit 36 has a stator 14, a rotor 13, and a crankshaft 4.
  • the stator 14 is fixed to the inside of the central shell 19 by bolts, shrink fitting, press fitting, or the like.
  • the rotor 13 is rotatably arranged on the inner peripheral surface side of the stator 14 and fixed to the crankshaft 4.
  • the crankshaft 4 is a rotating shaft that is vertically extended and housed in the central shell 19 in a rod shape.
  • the stator 14 has a function of rotationally driving the rotor 13 when energized.
  • the rotor 13 has a function of rotating by energizing the stator 14 and rotating the crankshaft 4.
  • the rotor 13 is fixed to the outer periphery of the crankshaft 4 and has a permanent magnet inside. The rotor 13 is held with a slight gap from the stator 14.
  • the crankshaft 4 rotates with the rotation of the rotor 13 to rotate and drive the swing scroll 2.
  • the upper side of the crankshaft 4 is rotatably supported by a bearing portion 3a located at the center of the frame 3.
  • the lower side of the crankshaft 4 is rotatably supported by a bearing portion 21a located at the center of the subframe 21 fixedly arranged below the central shell 19.
  • An eccentric portion 4a that fits with the swing bearing portion 2d is provided at the upper end portion of the crankshaft 4 so that the swing scroll 2 can rotate while being eccentric.
  • a suction pipe 5 for sucking the refrigerant is connected to the central shell 19.
  • a discharge pipe 6 for discharging the refrigerant is connected to the upper shell 18.
  • An injection pipe 7 for guiding an intermediate pressure refrigerant is connected to the upper shell 18.
  • the frame 3 and the subframe 21 are fixed to the inner peripheral surface of the central shell 19.
  • the frame 3 has a through hole formed in the center thereof for axially supporting the crankshaft 4.
  • the frame 3 rotatably supports the crankshaft 4 via the bearing portion 3a.
  • the bearing portion 3a is formed of a slide bearing or the like.
  • the subframe 21 is formed with a through hole in the center thereof that pivotally supports the crankshaft 4.
  • the subframe 21 rotatably supports the crankshaft 4 via the bearing portion 21a.
  • the subframe 21 may be fixed to the inner peripheral surface of the central shell 19 by bolts, shrink fitting, press fitting, or the like.
  • An oil pump 17 is provided at the lower end of the crankshaft 4.
  • the oil pump 17 is a positive displacement pump.
  • the rotational force of the crankshaft 4 can be transmitted to the oil pump 17.
  • the oil pump 17 supplies the refrigerating machine oil stored in the oil sump 16 according to the rotation of the crankshaft 4 to the swing bearing portion 2d, the bearing portion 3a, and the bearing portion 21a through an oil circuit provided inside the crankshaft 4. Demonstrate function.
  • a part of the refrigerating machine oil is also taken into the compression chamber 12, discharged from the discharge pipe 6, and circulates in the refrigerant circuit 60.
  • An old dam ring 15 is arranged between the swing scroll 2 and the frame 3 to prevent the swing scroll 2 from rotating during the eccentric turning motion.
  • the old dam ring 15 exhibits a function of blocking the rotation motion of the swing scroll 2 and enabling the revolution motion.
  • the compression chamber 12 that has taken in the gas refrigerant from the suction pipe 5 reduces the volume while moving from the outer peripheral portion toward the center along with the eccentric turning motion of the rocking scroll 2, and compresses the gas refrigerant.
  • the gas refrigerant compressed in the compression chamber 12 is discharged by opening the valve 9 from the discharge port 1a provided in the fixed scroll 1. Deformation of the valve 9 is regulated by the valve retainer 8 so as not to be deformed more than necessary, and damage to the valve 9 is prevented.
  • the solenoid valve 55 arranged in the injection flow path 57 opens, and the intermediate pressure refrigerant whose flow rate is adjusted by adjusting the opening degree of the expansion valve 56 is injected into the injection pipe. 7 flows into the compression chamber 12 through the injection port 1e, and the temperature inside the compression chamber 12 is adjusted.
  • the intermediate pressure refrigerant flows into the compression chamber 12 through the injection port 1e, the flow rate of the refrigerant discharged from the compressor 50 increases, and the condensing capacity can be increased.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 50 is cooled to about the outside air temperature by the condenser 51 to reach a medium-temperature and high-pressure state, and is expanded to a low-temperature and low-pressure state by the expansion device 52 and then evaporated. It becomes a gas refrigerant again in the vessel 53, passes through the accumulator 54, and is sucked from the suction pipe 5 of the compressor 50.
  • the refrigerant is not sufficiently vaporized, such as when frost is attached to the evaporator 53, the gas-liquid of the refrigerant is separated by the accumulator 54, and only the gas refrigerant returns to the compressor 50.
  • the solenoid valve 55 arranged in the injection flow path 57 is opened, and a part of the refrigerant after passing through the condenser 51 is discharged from the expansion valve 56. Is decompressed and guided to the compressor 50 via the injection flow path 57.
  • Refrigerating machine oil is required to lubricate sliding portions such as the swing bearing portion 2d, the bearing portion 3a, and the bearing portion 21a in the compressor 50 to prevent wear or seizure.
  • a part of the refrigerating machine oil is discharged from the discharge pipe 6 of the compressor 50 to the refrigerant circuit 60 and circulates in the refrigerant circuit 60. Therefore, the refrigerating machine oil circulating in the refrigerant circuit 60 is exposed to the low temperature environment by the evaporator 53, so that the low temperature characteristic of the refrigerating machine oil becomes an important factor.
  • Refrigerating machine oil is usually a liquid. However, even if the refrigerating machine oil solidifies in the refrigerant circuit 60, it does not return to the compressor 50, so that the sliding portion is worn or seized.
  • the pour point As an index of the fluidity of refrigerating machine oil, there is an index called the pour point specified by JIS K2269 (Japanese Industrial Standards).
  • the pour point is measured in the atmosphere, and it is generally desirable that the pour point in the atmosphere is ⁇ 30 ° C. or lower.
  • the refrigerant dissolves in the refrigerating machine oil and the dissolution viscosity of the refrigerating machine oil decreases, so that the pour point in the refrigerant atmosphere in the actual refrigerant circuit 60 is considered to be lower than the pour point in the atmosphere.
  • FIG. 4 is a relationship diagram showing the correlation between the pour point of the refrigerating machine oil according to the first embodiment in the atmosphere and the freezing point in the refrigerant atmosphere.
  • FIG. 4 is data obtained by the inventors through experiments or verifications. As shown in FIG. 4, based on the pour point measured in the atmosphere, it can be seen that the temperature of the freezing point where the refrigerating machine oil solidifies in the refrigerant atmosphere is lower. Therefore, in the refrigerant circuit 60, the pour point Tp of the refrigerating machine oil and the lower limit value Tv of the operating evaporation temperature, which is the lower limit of the temperature of the refrigerant flowing through the evaporator 53 in the refrigerant circuit 60, satisfy (Tp-15) ⁇ Tv. , The refrigerating machine oil is prevented from coagulating, and a highly reliable refrigerating cycle apparatus 100 can be provided. That is, the refrigerant circuit 60 can operate even at ⁇ 50 ° C. or lower.
  • the inventors have found the relationship between the freezing point of the refrigerating machine oil and the pour point of the refrigerating machine oil in the atmosphere when the refrigerating machine oil and the refrigerant are saturated and melted.
  • the pour point of the refrigerating machine oil in the atmosphere is stored in advance in the control device 70, and the stored pour point of the refrigerating machine oil in the atmosphere is reflected in the control of the refrigerant circuit 60 of the control device 70.
  • the refrigerating cycle device 100 can be operated within a range in which the temperature lower limit of the refrigerant circuit 60 does not fall below the freezing point of the refrigerating machine oil when the refrigerating machine oil and the refrigerant are saturated and melted.
  • the viscosity of the refrigerating machine oil in the atmosphere at 40 ° C. is 32 cSt or more in order to secure an oil film on the sliding portion. Further, if the viscosity of the refrigerating machine oil in the atmosphere exceeds 220 cSt, the fluidity of the refrigerating machine oil deteriorates, and it becomes difficult to distribute the refrigerating machine oil in the refrigerant circuit 60. Therefore, it is desirable that the viscosity of the refrigerating machine oil in the atmosphere is in the range of 32 cSt or more and 220 cSt or less.
  • Refrigerating machine oil needs to be chemically stable such as having hydrolysis resistance in a refrigerant atmosphere. Refrigerant oil must not have a detrimental effect on the materials used to configure the refrigerant circuit 60.
  • the compressor 50 has a drive mechanism unit 36.
  • the drive mechanism unit 36 needs to ensure insulation. Therefore, the volume resistivity of the refrigerating machine oil is preferably 10 8 ⁇ ⁇ cm or more, preferably when is 10 11 ⁇ ⁇ cm or more.
  • the lower limit of the evaporation temperature of the refrigeration cycle device 100 is required to be ⁇ 40 ° C. or lower. Therefore, the two-layer separation temperature between the refrigerant and the refrigerating machine oil is preferably ⁇ 40 ° C. or lower.
  • care must be taken because the oil concentration in the accumulator 54 decreases and the two layers are easily separated.
  • ether-based synthetic oil or ester-based synthetic oil is used as the base oil (base oil) of the refrigerating machine oil that satisfies the above conditions.
  • base oil base oil
  • ether-based synthetic oil or ester-based synthetic oil is used among ether-based synthetic oils.
  • polyalkylene glycol (PAG) oil tends to separate into two layers from carbon dioxide when the oil concentration decreases.
  • PVE polyvinyl ether
  • ester-based synthetic oil a polyol ester (POE) oil synthesized from a polyhydric alcohol such as pentaerythritol and a fatty acid is preferable as a base oil for refrigerating machine oil.
  • Refrigerating machine oils that satisfy the above conditions include additives such as antifoaming agents, antioxidants, acid scavengers (moisture scavengers) and extreme pressure agents (wear inhibitors) from the viewpoint of preventing denaturation of the refrigerating machine oil.
  • additives such as antifoaming agents, antioxidants, acid scavengers (moisture scavengers) and extreme pressure agents (wear inhibitors) from the viewpoint of preventing denaturation of the refrigerating machine oil.
  • the additive adds a function to the refrigerating machine oil that cannot be supplemented by the base oil alone, and exerts an effect that cannot be supplemented by the base oil alone.
  • phosphate ester phosphate ester, phosphite ester, thiophosphate, sulfide ester, sulfide, thiobisphenol, etc.
  • TCP tricredyl phosphate
  • TPP trifinyl phosphate
  • the amount of the extreme pressure agent added is preferably 5% by weight or less from the viewpoint of preventing the formation of deteriorated substances such as sludge.
  • Carbon dioxide has a higher temperature rise when compressed than HFC refrigerant or HFO refrigerant. Therefore, when the solenoid valve 55 of the injection flow path 57 is suddenly closed due to a malfunction or failure while the compressor 50 is injecting at a high compression ratio, the temperature inside the compression chamber 12 suddenly rises and the swing scroll There is a problem that 2 or the fixed scroll 1 is burnt. Therefore, the volume of the injection flow path 57 from the solenoid valve 55 to the injection port 1e is designed in a space where the amount of the refrigerant to be injected can be additionally secured at a certain ratio with respect to the amount of push-out of the compressor 50.
  • the refrigerant stored in the space flows into the compression chamber 12 to delay the rise in the temperature inside the compression chamber 12, and the compressor 50 is stopped before the temperature inside the compression chamber 12 rises. ..
  • seizure of the swing scroll 2 or the fixed scroll 1 can be avoided.
  • the expansion valve 56 and the solenoid valve 55 are arranged in this order in the injection flow path 57 from the side closest to the compressor 50. However, even if both the expansion valve 56 and the solenoid valve 55 are closed due to a malfunction or failure, a slight gap is formed in the expansion valve 56 close to the compressor 50. Therefore, the injection refrigerant flows into the compression chamber 12, and the temperature rise in the compression chamber 12 is suppressed.
  • FIG. 5 is a relationship diagram showing the correlation between the discharge temperature and time of the refrigerant discharged from the compressor 50 according to the first embodiment in comparison with a comparative example in which the arrangement of the expansion valve 56 and the solenoid valve 55 is reversed. is there.
  • FIG. 5 shows the discharge temperature of the expansion valve 56 and the solenoid valve 55 in the injection flow path 57 in the case of the first embodiment and the case of the comparative example in which the positional relationship of the solenoid valve 55 is reversed from that of the first embodiment.
  • the correlation between and time is shown.
  • the case of the first embodiment is a solid line.
  • the case of the comparative example is a broken line.
  • the compressor 50 is controlled so that the discharge temperature at a high pressure of 12.5 MPa and a low pressure of 1.5 MPa is 120 ° C. as an operating condition.
  • the discharge temperature rose to 250 ° C. in the case of the comparative example.
  • the temperature was suppressed to 205 ° C.
  • the temperature of a resin component changes by 10 ° C., deterioration is accelerated twice as fast. Therefore, in the first embodiment, it is estimated that the product life is extended by about 8 times as compared with the case of the comparative example.
  • the solenoid valve 55 By providing the solenoid valve 55 on the upstream side of the injection flow path 57, when the solenoid valve 55 and the expansion valve 56 are closed, only the amount of the refrigerant accumulated between the solenoid valve 55 and the expansion valve 56 is injected. The amount of refrigerant increases. Therefore, the solenoid valve 55 should be provided on the upstream side in the injection flow path 57 as much as possible, that is, on the side closer to the condenser 51.
  • the pressure vessel of the compressor 50 is a semi-closed vessel divided into an upper shell 18, a middle shell 19, and a lower shell 20.
  • the reason for this is that the operating pressure of carbon dioxide as a refrigerant is about four times higher than that of the HFC-based R410A refrigerant, and the components are dedicated to carbon dioxide, increasing the cost of the components. Therefore, the compressor 50 is configured to be disassembled, the compressor 50 is regularly maintained, and only the components that need to be replaced can be replaced, and the product cost is suppressed as the product life of the compressor 50.
  • the shell is divided into three parts. However, if the shell can be disassembled, it may be divided into two or more parts.
  • FIG. 6 is an explanatory diagram showing a compression process according to the presence / absence of the sub port 1d according to the first embodiment.
  • FIG. 6 shows the transition of the compression process depending on the presence or absence of the subport 1d.
  • the solid line is the case of the first embodiment having the subport 1d.
  • the broken line is the case where there is no subport 1d.
  • the subport 1d When the sub port 1d is not provided in the fixed scroll 1, the pressure rise with respect to the volume change of carbon dioxide is large with respect to the HFC refrigerant. Therefore, overcompression occurs in the compressor chamber 12, the amount of refrigerant flowing into the compressor 50 is limited, and the compressor performance deteriorates. That is, when there is no subport 1d, the pressure in the compression process overshoots the target pressure and an overcompression loss occurs. Therefore, the subport 1d is provided, the refrigerant overcompressed in the compression chamber 12 escapes from the subport 1d, the overcompression of the compression chamber 12 is prevented, the amount of the refrigerant flowing into the compressor 50 does not decrease, and the compressor performance. Is improved.
  • FIG. 7 is a flowchart showing the control of the refrigeration cycle device 100 according to the first embodiment.
  • the control shown in FIG. 7 is carried out by the control device 70 so that the pour point Tp of the refrigerating machine oil in the atmosphere and the lower limit value Tv of the evaporation temperature used by the refrigerant circuit 60 satisfy (Tp-15) ⁇ Tv. ..
  • the control device 70 starts controlling the operation of the refrigeration cycle device 100 shown in FIG. 7, and detects the lower limit value Tv of the working evaporation temperature of the refrigerant circuit 60 in step S101.
  • the lower limit value Tv of the working evaporation temperature is detected by a temperature sensor provided in the evaporator 53.
  • step S101 the process shifts to step S102.
  • the operation of the refrigeration cycle device 100 itself is carried out by separate control. This control is started at the same time when the operation of the refrigeration cycle device 100 itself is started separately.
  • step S102 the control device 70 has a pour point Tp of refrigerating machine oil stored in advance in the control device 70 in the atmosphere and a lower limit value Tv of the evaporation temperature of the refrigerant circuit 60 detected in step S101 (Tp-). 15) It is determined whether or not ⁇ Tv is satisfied. If (Tp-15) ⁇ Tv is satisfied, the process proceeds to step S103. If (Tp-15) ⁇ Tv is not satisfied, the process proceeds to step S104.
  • the control device 70 continues to control the operation of the refrigeration cycle device 100 in step S103. After the process of step S103, the process shifts to step S105.
  • step S105 the control device 70 determines whether or not to stop the operation of the refrigeration cycle device 100, which is being carried out by another control. When the operation of the refrigeration cycle device 100 is stopped, this control is terminated. If the operation of the refrigeration cycle apparatus 100 is not stopped, the process proceeds to step S101.
  • step S104 the control device 70 stops the operation of the refrigeration cycle device 100 as a low-pressure cut. After the process of step S104, this control is terminated.
  • the refrigeration cycle device 100 includes a refrigerant circuit 60 in which a compressor 50, a condenser 51, an expansion device 52, and an evaporator 53 are connected in a ring shape.
  • the refrigerant sealed in the refrigerant circuit 60 is carbon dioxide or a mixed refrigerant containing carbon dioxide.
  • the refrigerating machine oil used in the compressor 50 is saturated and melted with the refrigerant.
  • the main component in the refrigerating machine oil is at least one of a polyol ester and a polyvinyl ether.
  • the pour point of refrigerating machine oil in the atmosphere is ⁇ 35 ° C. or lower and ⁇ 57 ° C. or higher.
  • the extreme pressure agent contained in the refrigerating machine oil is at least one of tricresyl phosphate and trifinyl phosphate.
  • the refrigerating machine oil has a refrigerant atmosphere. Do not lose the liquidity inside. Therefore, the refrigerating machine oil contained in the refrigerant does not solidify in the refrigerant circuit 60 in a low temperature environment, and damage to the compressor 50 can be prevented. In addition, the additives contained in the refrigerating machine oil do not precipitate, and the lubrication failure does not occur, so that damage to the sliding portion of the compressor 50 can be prevented.
  • the refrigeration cycle device 100 includes a control device 70 that controls the refrigerant circuit 60.
  • the control device 70 stores in advance the pour point Tp of the refrigerating machine oil in the atmosphere.
  • the control device 70 performs control in which the pour point Tp of the refrigerating machine oil and the lower limit value Tv of the used evaporation temperature, which is the lower limit of the temperature of the refrigerant flowing through the evaporator 53 in the refrigerant circuit 60, satisfy (Tp-15) ⁇ Tv.
  • the control circuit is configured.
  • the pour point Tp of the refrigerating machine oil and the lower limit of the operating evaporation temperature Tv which is the lower limit of the temperature of the refrigerant flowing through the evaporator 53 in the refrigerant circuit 60, are (Tp-15). Control that satisfies ⁇ Tv can be performed. As a result, the freezing point of the refrigerant atmosphere of the refrigerant circuit 60 becomes ⁇ 50 ° C. or lower. Even so, the refrigerating machine oil contained in the refrigerant does not solidify in a low temperature environment in the refrigerant circuit 60, and damage to the compressor 50 can be prevented.
  • the cold resistance temperature of the refrigerant circuit 60 is configured to be ⁇ 50 ° C. or lower and ⁇ 57 ° C. or higher.
  • the cold resistance temperature of the refrigerant circuit 60 is set to ⁇ 50 ° C. or lower and ⁇ 57 ° C., so that even if the freezing point of the refrigerant atmosphere of the refrigerant circuit 60 is ⁇ 50 ° C. or lower, the temperature is higher than that under the environment. Failure of the refrigeration cycle device 100 having the refrigerant circuit 60 having a low cold resistance temperature can be prevented.
  • the compressor 50 has a compression unit 35 that compresses the refrigerant in a semi-closed container.
  • the refrigerant can be compressed in the semi-closed container by the compression unit 35 of the compressor 50.
  • the compression unit 35 has a fixed scroll 1 and a swinging scroll 2 in which both fixed spiral bodies 1b and the swinging spiral body 2b are projected from both the fixed base plate 1c and the swing base plate 2c. And are combined with each other.
  • a discharge port 1a for discharging a refrigerant from a compression chamber 12 formed by both fixed spiral bodies 1b and a swinging spiral body 2b is provided.
  • the compressor 50 constitutes a scroll compressor, and the refrigerant can be compressed by the compression unit 35.
  • the sub port 1d for discharging the refrigerant is provided before the compression chamber 12 communicates with the discharge port 1a in the compression process of the compressor 50 in the compressor 50.
  • the subport 1d discharges the refrigerant before the compression chamber 12 communicates with the discharge port 1a, and the refrigerant discharged from the discharge port 1a is not excessively compressed and is overcompressed. Loss can be reduced.
  • the refrigerant circuit 60 is provided with an injection flow path 57 that returns a part of the refrigerant before flowing out of the condenser 51 and flowing into the expansion device 52 to the compressor 50.
  • the gas refrigerant or the liquid refrigerant can be injected in the compression process. Then, in a certain type of refrigerating cycle device 100, the temperature in the compression chamber 12 does not rise abnormally, and damage to the internal parts of the compressor 50 can be prevented.
  • the expansion valve 56 and the solenoid valve 55 are arranged in this order in the injection flow path 57 from the side closest to the compressor 50.
  • the peak of the discharge temperature of the compressor 50 is reduced as compared with the case of the injection flow path 57 in which the solenoid valve 55 and the expansion valve 56 are arranged in this order from the side closer to the compressor 50. it can. Therefore, the deterioration rate of the resin parts is slowed down, and the product life is extended. Further, when the solenoid valve 55 and the expansion valve 56 are closed, the amount of the refrigerant injected is increased by the amount of the refrigerant accumulated between the solenoid valve 55 and the expansion valve 56.
  • the refrigerant accumulated between the solenoid valve 55 and the expansion valve 56 in the injection flow path 57 flows into the compression chamber 12 to delay the rise in the temperature inside the compression chamber 12, and the temperature inside the compression chamber 12 rises. Control is performed to stop the compressor 50 before the operation. As a result, seizure of the swing scroll 2 or the fixed scroll 1 can be avoided.
  • FIG. 8 is an explanatory view showing the compressor 50 according to the second embodiment in a vertical cross section.
  • the description of the same items as in the first embodiment is omitted, and only the characteristic portion thereof is described.
  • a check valve 22 is provided at the downstream end of the injection pipe 7, which is the downstream end of the injection flow path 57, to prevent the backflow of the refrigerant from the compression portion 35 when the injection is off.
  • the check valve 22 is one size larger than the opening area of the injection pipe 7, and presses the valve member 23 housed in the fixed base plate 1c of the fixed scroll 1 and the valve member 23 against the downstream end of the injection pipe 7. It has a spring 24 and.
  • the check valve 22 is closed by pushing up the valve member 23 by the spring 24 under the injection off condition to prevent the refrigerant from leaking from the compression chamber 12, and the compressor performance can be improved.
  • the valve member 23 is pushed down against the repulsive force of the spring 24 by the pressure of the refrigerant to be injected, and the injected refrigerant flows into the compression chamber 12.
  • FIG. 9 is a relationship diagram showing the correlation between the rotation speed of the compressor 50 and the volumetric efficiency according to the presence / absence of the check valve 22 according to the second embodiment.
  • FIG. 10 is a relationship diagram showing the correlation between the rotation speed of the compressor 50 and the compressor efficiency according to the presence or absence of the check valve 22 according to the second embodiment.
  • the thin solid line connecting the circle dots of FIGS. 9 and 10 is the case of the second embodiment having the check valve 22.
  • the dark solid line connecting the triangular dots is the case where there is no check valve 22.
  • the test conditions are high pressure (Pd) of 6.3 MPaG and low pressure (Ps) of 2.5 MPaG.
  • the volumetric efficiency of the second embodiment having the check valve 22 is higher than that without the check valve 22. ..
  • the compressor efficiency of the second embodiment having the check valve 22 is higher than that without the check valve 22.
  • the compressor performance can be improved as compared with the case where the check valve 22 is not provided.
  • the spring 24 repeats expansion and contraction according to switching between the injection on state and the injection off state. Therefore, if the number of repetitions of expansion and contraction is large, the spring 24 that has exceeded the fatigue limit of the material may be damaged. If the spring 24 is damaged, it is assumed that the compressor performance is significantly reduced under the condition of injection off. However, in the second embodiment, since the compressor 50 includes the semi-closed container, the shell of the semi-closed container can be disassembled and the spring 24 can be replaced.
  • the injection flow path 57 is provided with a check valve 22 for preventing the backflow of the refrigerant from the compression unit 35 when the injection is off.
  • the volumetric efficiency and the compressor efficiency when the rotation speed of the compressor 50 is low can be reduced as compared with the case where the check valve 22 is not provided.
  • first embodiment and the second embodiment may be combined or applied to other parts.

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Abstract

Le dispositif à cycle frigorifique de la présente invention comprend un circuit de fluide frigorigène dans lequel un compresseur, un condenseur, un dispositif d'expansion et un évaporateur sont connectés en cercle, dans lequel : un fluide frigorigène scellé dans le circuit de fluide frigorigène est du dioxyde de carbone ou un fluide frigorigène mixte contenant du dioxyde de carbone ; une huile de réfrigérateur utilisée dans le compresseur fusionne avec le fluide frigorigène jusqu'au point de saturation ; le constituant principal de l'huile de réfrigérateur est au moins l'un parmi l'ester de polyol et l'éther de polyvinyle ; le point d'écoulement de l'huile de réfrigérateur dans l'atmosphère est de -35°C à -57°C ; et un agent de pression extrême contenu dans l'huile de réfrigérateur est au moins l'un parmi le phosphate de tricrésyle et le phosphate de triphényle.
PCT/JP2019/030907 2019-08-06 2019-08-06 Dispositif à cycle frigorifique WO2021024380A1 (fr)

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JPH07269475A (ja) * 1994-03-31 1995-10-17 Sanyo Electric Co Ltd スクロール圧縮機
JPH10259962A (ja) * 1997-03-19 1998-09-29 Hitachi Ltd 冷凍装置、冷凍機、冷凍装置用空冷式凝縮機ユニット及び圧縮機ユニット
JPH10267437A (ja) * 1997-03-27 1998-10-09 Daikin Ind Ltd 冷凍装置
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JP2002155290A (ja) * 2000-11-21 2002-05-28 Nippon Mitsubishi Oil Corp 二酸化炭素冷媒用冷凍機油及び冷凍機用流体組成物
WO2007029746A1 (fr) * 2005-09-07 2007-03-15 Idemitsu Kosan Co., Ltd. Lubrifiant pour dispositif refrigerant de type a compression et dispositif refrigerant utilisant ledit lubrifiant
JP2007169396A (ja) * 2005-12-20 2007-07-05 Idemitsu Kosan Co Ltd 冷凍機油組成物、これを用いた冷凍機用圧縮機及び冷凍装置
JP2009138037A (ja) * 2007-12-04 2009-06-25 Hitachi Appliances Inc 冷媒圧縮機およびヒートポンプ式給湯機
JP2009222358A (ja) * 2008-03-18 2009-10-01 Daikin Ind Ltd 冷凍装置
JP2011075178A (ja) * 2009-09-30 2011-04-14 Fujitsu General Ltd ヒートポンプサイクル装置
JP2012052135A (ja) * 2003-11-21 2012-03-15 Nof Corp 冷凍機用潤滑油組成物
JP2014129900A (ja) * 2012-12-28 2014-07-10 Mitsubishi Electric Corp 冷凍装置
WO2014156743A1 (fr) * 2013-03-28 2014-10-02 三菱電機株式会社 Compresseur à spirale et dispositif de cycle de réfrigération le comprenant
US20150226464A1 (en) * 2012-08-01 2015-08-13 Ei Du Pont De Nemours And Company Producing heating in cascade heat pumps using working fluids comprising z 1,1,1,4,4,4-hexafluoro-2-butene in the final cascade stage

Patent Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07269475A (ja) * 1994-03-31 1995-10-17 Sanyo Electric Co Ltd スクロール圧縮機
JPH10259962A (ja) * 1997-03-19 1998-09-29 Hitachi Ltd 冷凍装置、冷凍機、冷凍装置用空冷式凝縮機ユニット及び圧縮機ユニット
JPH10267437A (ja) * 1997-03-27 1998-10-09 Daikin Ind Ltd 冷凍装置
JP2001294886A (ja) * 2000-04-10 2001-10-23 Japan Energy Corp 炭酸ガス冷媒を用いる冷凍装置用潤滑油組成物、作動流体、冷凍サイクルまたはヒートポンプサイクル及び冷凍装置
JP2001304153A (ja) * 2000-04-18 2001-10-31 Hitachi Ltd スクロール圧縮機および空気調和機
JP2002155290A (ja) * 2000-11-21 2002-05-28 Nippon Mitsubishi Oil Corp 二酸化炭素冷媒用冷凍機油及び冷凍機用流体組成物
JP2012052135A (ja) * 2003-11-21 2012-03-15 Nof Corp 冷凍機用潤滑油組成物
WO2007029746A1 (fr) * 2005-09-07 2007-03-15 Idemitsu Kosan Co., Ltd. Lubrifiant pour dispositif refrigerant de type a compression et dispositif refrigerant utilisant ledit lubrifiant
JP2007169396A (ja) * 2005-12-20 2007-07-05 Idemitsu Kosan Co Ltd 冷凍機油組成物、これを用いた冷凍機用圧縮機及び冷凍装置
JP2009138037A (ja) * 2007-12-04 2009-06-25 Hitachi Appliances Inc 冷媒圧縮機およびヒートポンプ式給湯機
JP2009222358A (ja) * 2008-03-18 2009-10-01 Daikin Ind Ltd 冷凍装置
JP2011075178A (ja) * 2009-09-30 2011-04-14 Fujitsu General Ltd ヒートポンプサイクル装置
US20150226464A1 (en) * 2012-08-01 2015-08-13 Ei Du Pont De Nemours And Company Producing heating in cascade heat pumps using working fluids comprising z 1,1,1,4,4,4-hexafluoro-2-butene in the final cascade stage
JP2014129900A (ja) * 2012-12-28 2014-07-10 Mitsubishi Electric Corp 冷凍装置
WO2014156743A1 (fr) * 2013-03-28 2014-10-02 三菱電機株式会社 Compresseur à spirale et dispositif de cycle de réfrigération le comprenant

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