US20110023535A1 - Refrigeration apparatus - Google Patents

Refrigeration apparatus Download PDF

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Publication number
US20110023535A1
US20110023535A1 US12/921,545 US92154509A US2011023535A1 US 20110023535 A1 US20110023535 A1 US 20110023535A1 US 92154509 A US92154509 A US 92154509A US 2011023535 A1 US2011023535 A1 US 2011023535A1
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Prior art keywords
refrigerant
compression mechanism
compressor
refrigeration apparatus
pressure
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US12/921,545
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English (en)
Inventor
Kouki Morimoto
Masanori Yanagisawa
Kazuhiro Furusho
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Daikin Industries Ltd
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Daikin Industries Ltd
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Assigned to DAIKIN INDUSTRIES, LTD. reassignment DAIKIN INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MORIMOTO, KOUKI, YANAGISAWA, MASANORI, FURUSHO, KAZUHIRO
Publication of US20110023535A1 publication Critical patent/US20110023535A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
    • F04C18/322—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the outer member
    • 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
    • C09K5/041—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa for compression-type refrigeration systems
    • C09K5/044—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa for compression-type refrigeration systems comprising halogenated compounds
    • C09K5/045—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa for compression-type refrigeration systems comprising halogenated compounds containing only fluorine as halogen
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • 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
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • 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
    • C09K2205/00—Aspects relating to compounds used in compression type refrigeration systems
    • C09K2205/10—Components
    • C09K2205/12—Hydrocarbons
    • C09K2205/126—Unsaturated fluorinated hydrocarbons
    • 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
    • C09K2205/00—Aspects relating to compounds used in compression type refrigeration systems
    • C09K2205/22—All components of a mixture being fluoro compounds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/10—Fluid working
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/10—Fluid working
    • F04C2210/1022—C3HmFn
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F04C2210/263—HFO1234YF
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/19—Temperature
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/12—Inflammable refrigerants
    • F25B2400/121—Inflammable refrigerants using R1234

Definitions

  • the present invention relates to a refrigeration apparatus, and particularly relates to a refrigeration apparatus for which refrigerant containing a compound represented by a molecular formula of C 3 H m F n is used.
  • Patent Document 1 discloses that refrigerant containing a compound represented by a molecular formula of C 3 H m F n is used as refrigerant of a refrigerant circuit.
  • refrigerant has excellent properties as the refrigerant of the refrigerant circuit, and attempts have been made to improve a coefficient of performance (COP) of a refrigeration apparatus.
  • COP coefficient of performance
  • refrigerant does not contain chlorine and bromine atoms, and has a small influence on destruction of the ozone layer.
  • the refrigerant (C 3 H m F n ) disclosed in Patent Document 1 has properties such as a relatively-high theoretical COP and low global warming potential (GWP).
  • GWP global warming potential
  • Patent Document 1 Japanese Patent Application No. 04-110388
  • the refrigerant are likely to be decomposed at high temperature, and therefore the refrigerant is desirably used under a condition where an increase in temperature is not likely to be caused.
  • a conventional single-stage single-cylinder compressor if a cylinder volume or a compression ratio is increased, then a discharge flow rate is increased in response to an increase in so-called “over-compression” of refrigerant, and a refrigerant temperature tends to increase.
  • refrigerant is decomposed depending on conditions.
  • the present invention has been made in view of the foregoing, and it is an object of the present invention to reduce or prevent decomposition of refrigerant due to an increase in discharge temperature of a compressor in a refrigeration apparatus for which refrigerant containing a compound represented by a molecular formula of C 3 H m F n is used.
  • the refrigeration apparatus includes a compressor ( 10 ) for performing a compression phase of refrigerant, and the compressor ( 10 ) includes a first compression mechanism ( 20 A) and a second compression mechanism ( 20 B) inside a casing ( 11 ).
  • a so-called “two-cylinder” or “two-stage” compressor ( 10 ) can be used.
  • a discharge flow rate of each cylinder can be decreased as compared to that of a single-cylinder compressor ( 10 ), thereby reducing over-compression.
  • an increase in refrigerant temperature can be reduced.
  • a second aspect of the invention specifies the configuration of the compressor ( 10 ) in the first aspect of the invention as a two-stage compressor.
  • the second aspect of the invention is intended for the refrigeration apparatus of the first aspect of the invention, in which the first compression mechanism ( 20 A) of the compressor ( 10 ) is a lower-stage compression mechanism ( 20 L), and the second compression mechanism ( 20 B) is a higher-stage compression mechanism ( 20 H); and both of the compression mechanisms ( 20 A, 20 B) serve as a two-stage compression mechanism ( 20 L, 20 H) for compressing refrigerant at two stages.
  • refrigerant is compressed at two stages to reduce the over-compression of refrigerant on a higher-stage side as compared to a single-stage compression, thereby decreasing a discharge temperature.
  • an increase in refrigerant temperature can be reduced.
  • a third aspect of the invention is intended for the refrigeration apparatus of the first or second aspect of the invention, in which the compression mechanism ( 20 A, 20 B) is a swing piston type compression mechanism which includes a cylinder ( 21 L, 21 H) having a cylinder chamber ( 25 ), and a swing piston ( 28 ) orbiting along an inner circumferential surface of the cylinder ( 21 L, 21 H); in which a blade ( 28 b ) outwardly protruding in a radial direction is formed in the swing piston ( 28 ); and in which support members ( 29 ) for holding the blade ( 28 b ) so as to move the blade ( 28 b ) back and forth are rotatably held by the cylinder ( 21 L, 21 H).
  • the compression mechanism ( 20 A, 20 B) is a swing piston type compression mechanism which includes a cylinder ( 21 L, 21 H) having a cylinder chamber ( 25 ), and a swing piston ( 28 ) orbiting along an inner circumferential surface of the cylinder ( 21 L, 21 H); in which
  • the compression mechanisms ( 20 A, 20 B) are the swing piston type compression mechanisms.
  • a rolling piston type compressor ( 10 ) includes a cylinder having a cylinder chamber; and a rolling piston orbiting along an inner circumferential surface of the cylinder.
  • the cylinder holds a blade, one end (tip end) of which is pressed against, and is brought contact with, an outer circumferential surface of the rolling piston.
  • the outer circumferential surface of the rolling piston and the tip end surface of the blade slide against each other to generate heat, and therefore an inside of the compressor is likely to have a high temperature.
  • the refrigerant is used, the refrigerant is decomposed.
  • the swing piston type compressor ( 10 ) since the swing piston type compressor ( 10 ) is used considering refrigerant which is likely to be decomposed at high temperature, the swing piston ( 28 ) and the blade ( 28 b ) do not slide against each other, thereby not generating heat in such a section. Thus, refrigerant is less susceptible to heat.
  • a fifth aspect of the invention is intended for the refrigeration apparatus of any one of the first to fourth aspects of the invention, in which the refrigerant of the refrigerant circuit ( 2 ) is refrigerant mixture further containing difluoromethane.
  • a sixth aspect of the invention is intended for the refrigeration apparatus of any one of the first to fifth aspects of the invention, in which the refrigerant of the refrigerant circuit ( 2 ) is refrigerant mixture further containing pentafluoroethane.
  • the compressor ( 10 ) including the two compression mechanisms ( 20 A, 20 B) is used considering refrigerant which is likely to be decomposed at high temperature as in the first aspect of the invention, and therefore refrigerant is less susceptible to heat.
  • the so-called “two-cylinder” or “two-stage” compressor ( 10 ) can be used.
  • the two-cylinder compressor of such compressors the over-compression of refrigerant of each cylinder is reduced as compared to the single-cylinder compressor ( 10 ), thereby decreasing the discharge flow rate.
  • the increase in refrigerant temperature can be reduced, thereby reducing or preventing the decomposition of refrigerant.
  • refrigerant is compressed at the two stages, thereby decreasing the discharge temperature as compared to that of the single-stage compression.
  • the decomposition of refrigerant can be reduced or prevented as in the first aspect of the invention.
  • the compression mechanisms ( 20 A, 20 B) are the swing piston type compression mechanisms, thereby easily reducing the increase in refrigerant temperature.
  • the decomposition of refrigerant can be more effectively reduced or prevented.
  • the compressor ( 10 ) including the two compression mechanisms ( 20 A, 20 B) is used considering refrigerant which is likely to be decomposed at high temperature, thereby reducing the increase in refrigerant temperature.
  • the decomposition of refrigerant can be reduced.
  • FIG. 1 is a refrigerant circuit diagram of a refrigeration apparatus of a first embodiment of the present invention.
  • FIG. 2 is a longitudinal sectional view of a compressor.
  • FIG. 3 is a cross sectional view of a compression mechanism.
  • FIG. 4 is a Mollier diagram showing a change in refrigerant properties in the refrigerant circuit.
  • FIG. 5 is a longitudinal sectional view of a compressor of a second embodiment.
  • the first embodiment relates to an air conditioning system.
  • an air conditioning system ( 1 ) is a heat pump type air conditioning system, and is switchable between a cooling operation and a heating operation.
  • a refrigerant circuit ( 2 ) of the air conditioning system ( 1 ) includes a compressor ( 10 ) for performing a compression phase of refrigerant in a refrigeration cycle; a four-way switching valve ( 3 ) which is a flow direction switching mechanism for switching a flow direction of refrigerant; an outdoor heat exchanger ( 4 ) which is a heat-source-side heat exchanger; a first expansion valve ( 5 A) which is a first expansion mechanism; a gas-liquid separator ( 6 ); a second expansion valve ( 5 B) which is a second expansion mechanism; an indoor heat exchanger ( 7 ) which is a utilization-side heat exchanger; and an accumulator ( 8 ).
  • the refrigerant circuit ( 2 ) is formed as a closed circuit by connecting such components with pipes.
  • the refrigerant circuit ( 2 ) of the present embodiment is filled with single component refrigerant containing HFO-1234yf (2,3,3,3-tetrafluoro-1-propene) as refrigerant.
  • a discharge port of the compressor ( 10 ) is connected to a first port (P 1 ) of the four-way switching valve ( 3 ), and a second port (P 2 ) of the four-way switching valve ( 3 ) is connected to a gas-side end of the outdoor heat exchanger ( 4 ).
  • a liquid-side end of the outdoor heat exchanger ( 4 ) is connected to a liquid-side end of the indoor heat exchanger ( 7 ) through the first expansion valve ( 5 A), the gas-liquid separator ( 6 ), and the second expansion valve ( 5 B).
  • a gas-side end of the indoor heat exchanger ( 7 ) is connected to a third port (P 3 ) of the four-way switching valve ( 3 ), and a fourth port (P 4 ) of the four-way switching valve ( 3 ) is connected to a suction port of the compressor ( 10 ) through the accumulator ( 8 ).
  • the four-way switching valve ( 3 ) is switchable between a first state during the cooling operation, in which the first port (P 1 ) communicates with the second port (P 2 ), and the third port (P 3 ) communicates with the fourth port (P 4 ) (state indicated by a solid line in FIG. 1 ); and a second state during the heating operation, in which the first port (P 1 ) communicates with the third port (P 3 ), and the second port (P 2 ) communicates with the fourth port (P 4 ) (state indicated by a dashed line in FIG. 1 ).
  • An injection pipe ( 2 A) is provided in the refrigerant circuit ( 2 ).
  • the injection pipe ( 2 A) is an injection pipe for injecting intermediate-pressure gaseous refrigerant which is intermediate-pressure fluid, to the compressor ( 10 ).
  • One end of the injection pipe ( 2 A) communicates with the gas-liquid separator ( 6 ), and the other end communicates with the compressor ( 10 ).
  • intermediate-pressure refrigerant is stored, which has intermediate pressure between condensing pressure of refrigerant which is high-pressure fluid, and evaporating pressure of refrigerant which is low-pressure fluid.
  • the injection pipe ( 2 A) is used for injecting intermediate-pressure gas-phase refrigerant of the intermediate-pressure refrigerant stored in the gas-liquid separator ( 6 ), to the compressor ( 10 ).
  • the first expansion valve ( 5 A) and the second expansion valve ( 5 B) are motorized valves with adjustable opening. Intermediate-pressure refrigerant made by reducing its pressure by the first expansion valve ( 5 A) or the second expansion valve ( 5 B) is stored in the gas-liquid separator ( 6 ).
  • the compressor ( 10 ) controls an operational capacity in a single-step or multiple-step manner.
  • an electric motor ( 30 ) for driving a compression mechanism ( 20 ) is accommodated in the compressor ( 10 ).
  • the electric motor ( 30 ) is connected to a power source ( 35 ) through an inverter (rotational speed control mechanism) ( 34 ), and a drive frequency is changed to adjust the rotational speed.
  • the compressor ( 10 ) is a two-stage compressor. As illustrated in FIG. 2 , a lower-stage compression mechanism ( 20 L) which is a first compression mechanism ( 20 A); a higher-stage compression mechanism ( 20 H) which is a second compression mechanism ( 20 B); and the electric motor ( 30 ) for driving both of the compression mechanisms ( 20 L, 20 H) are accommodated in a hermetic casing ( 11 ).
  • the casing ( 11 ) includes a cylindrical body section ( 12 ) having upper and lower openings; and end plate sections ( 13 , 14 ) fixed to upper and lower end sections of the body section ( 12 ) by welding.
  • the electric motor ( 30 ) includes a stator ( 31 ) fixed to an inner circumferential surface of the casing ( 11 ); and a rotor ( 32 ) arranged in a center section of the stator ( 31 ).
  • a drive shaft ( 33 ) is connected to a center section of the rotor ( 32 ).
  • the drive shaft ( 33 ) downwardly extends from the rotor ( 32 ), and is connected to the lower-stage compression mechanism ( 20 L) and the higher-stage compression mechanism ( 20 H).
  • a bottom section inside the casing ( 11 ) serves as an oil storage section ( 17 ) of lubricant, and a lower end section of the drive shaft ( 33 ) is dipped in the lubricant of the oil storage section ( 17 ).
  • a centrifugal oil pump ( 36 ) is provided in the lower end section of the drive shaft ( 33 ), and the lubricant is supplied to sliding sections and bearing sections of the lower-stage compression mechanism ( 20 L) and the higher-stage compression mechanism ( 20 H) through an oil supply path ( 33 c ) inside the drive shaft ( 33 ).
  • the lower-stage compression mechanism ( 20 L) and the higher-stage compression mechanism ( 20 H) are positioned below the electric motor ( 30 ), and are stacked in two tiers. Both of the lower-stage compression mechanism ( 20 L) and the higher-stage compression mechanism ( 20 H) are so-called “swing piston type” compression mechanisms.
  • the lower-stage compression mechanism ( 20 L) and the higher-stage compression mechanism ( 20 H) have approximately the same configuration, and the higher-stage compression mechanism ( 20 H) is arranged above the lower-stage compression mechanism ( 20 L).
  • a swing piston ( 28 ) is accommodated in a cylinder chamber ( 25 ) formed in a cylinder ( 21 H, 21 L).
  • a middle plate ( 22 ) is provided between the cylinders ( 21 H, 21 L) of the compression mechanisms ( 20 L, 20 H).
  • a lower plate (rear head) ( 24 ) is provided on a lower surface of the lower-stage cylinder ( 21 L) to close the lower-stage cylinder ( 21 L), and an upper plate (front head) ( 23 ) is provided on an upper surface of the higher-stage cylinder ( 21 H) to close the higher-stage cylinder ( 21 H).
  • the whole of the swing piston ( 28 ) of the compression mechanism ( 20 L, 20 H) is formed in an annular form, and an eccentric section ( 33 a, 33 b ) of the drive shaft ( 33 ) is rotatably fitted into the swing piston ( 28 ).
  • the eccentric section ( 33 a, 33 b ) is formed so as to be eccentric to the center of rotation of the drive shaft ( 33 ).
  • a suction path ( 21 a, 21 b ) is formed in the cylinder ( 21 H, 21 L), and one end of the suction path ( 21 a, 21 b ) opens to the cylinder chamber ( 25 ) to serve as a suction port.
  • a discharge path ( 24 a ) of the lower-stage compression mechanism ( 20 L) is formed in the lower plate ( 24 ), whereas a discharge path ( 23 a ) of the higher-stage compression mechanism ( 20 H) is formed in the upper plate ( 23 ).
  • One end of the discharge path ( 23 a, 24 a ) opens to the cylinder chamber ( 25 ) to serve as a discharge port.
  • a discharge valve for opening the discharge port when reaching a predetermined discharge pressure is provided in the discharge path ( 23 a, 24 a ).
  • a cylindrical bush hole ( 21 c ) which extends in an axial direction, and which is positioned between the suction port and the discharge port is formed so as to open to the cylinder chamber ( 25 ).
  • an annular body section ( 28 a ) is integrally formed with a blade ( 28 b ) protruding from the body section ( 28 a ) in a radial direction.
  • a tip end side of the blade ( 28 b ) is inserted into the bush hole ( 21 c ) through swing bushes ( 29 ) which is a pair of support members.
  • the blade ( 28 b ) divides the cylinder chamber ( 25 ) into a low-pressure chamber ( 25 a ) communicating with the suction path ( 21 a, 21 b ), and a high-pressure chamber ( 25 b ) communicating with the discharge path ( 23 a, 24 a ).
  • the swing piston ( 28 ) compresses refrigerant by orbiting the body section ( 28 a ) along an inner circumferential surface of the cylinder chamber ( 25 ) while swinging the blade ( 28 b ) about the swing bushes ( 29 ) as a pivot point.
  • a suction pipe ( 15 ) for supplying low-pressure gaseous refrigerant to the lower-stage compression mechanism ( 20 L) is connected to the suction path ( 21 a ) of the lower-stage compression mechanism ( 20 L).
  • a suction-side refrigerant pipe ( 2 B) (see FIG. 1 ) of the refrigerant circuit ( 2 ) is connected to the suction pipe ( 15 ).
  • a lower muffler ( 26 ) is provided in the lower plate ( 24 ).
  • a middle path ( 20 M) is formed in the compression mechanism ( 20 ).
  • the middle path ( 20 M) penetrates the middle plate ( 22 ) through the lower plate ( 24 ) and the lower-stage cylinder ( 21 L), and communicates with the suction path ( 21 b ) of the higher-stage compression mechanism ( 20 H).
  • the injection pipe ( 2 A) is connected to the middle plate ( 22 ) to communicate with the middle path ( 20 M). That is, the middle path ( 20 M) is configured to be in an intermediate-pressure atmosphere by supplying intermediate-pressure gaseous refrigerant thereto. Such configuration supplies intermediate-pressure refrigerant to the higher-stage compression mechanism ( 20 H).
  • An upper muffler ( 27 ) covering the discharge path ( 23 a ) of the higher-stage compression mechanism ( 20 H) is provided in the upper plate ( 23 ).
  • the discharge path ( 23 a ) of the higher-stage compression mechanism ( 20 H) opens to the casing ( 11 ) through the upper muffler ( 27 ), and is configured such that an inside of the casing ( 11 ) is in a high-pressure atmosphere.
  • a discharge pipe ( 16 ) for discharging high-pressure gaseous refrigerant to the refrigerant circuit ( 2 ) is fixed to an upper section of the casing ( 11 ).
  • a discharge-side refrigerant pipe ( 2 C) of the refrigerant circuit ( 2 ) is connected to the discharge pipe ( 16 ) (see FIG. 1 ).
  • the four-way switching valve ( 3 ) is switched to the state indicated by the solid line in FIG. 1 .
  • Refrigerant discharged from the compressor ( 10 ) is condensed by exchanging heat with outdoor air in the outdoor heat exchanger ( 4 ).
  • the pressure of the liquid refrigerant is reduced by the first expansion valve ( 5 A), and then such refrigerant is stored in the gas-liquid separator ( 6 ) as intermediate-pressure refrigerant having intermediate pressure between the condensing pressure and the evaporating pressure.
  • intermediate-pressure liquid refrigerant of the intermediate-pressure refrigerant in the gas-liquid separator ( 6 ) is reduced by the second expansion valve ( 5 B). Subsequently, such refrigerant is evaporated by exchanging heat with room air in the indoor heat exchanger ( 7 ), thereby cooling the room air. Then, the gaseous refrigerant returns to the compressor ( 10 ) through the accumulator ( 8 ), thereby performing a refrigeration circulating operation.
  • the four-way switching valve ( 3 ) is switched to the state indicated by the dashed line in FIG. 1 .
  • Refrigerant discharged from the compressor ( 10 ) exchanges heat with room air in the indoor heat exchanger ( 7 ), and then is condensed while heating the room air.
  • the pressure of the liquid refrigerant is reduced by the second expansion valve ( 5 B), and such refrigerant is stored in the gas-liquid separator ( 6 ) as intermediate-pressure refrigerant.
  • the pressure of intermediate-pressure liquid refrigerant of the intermediate-pressure refrigerant in the gas-liquid separator ( 6 ) is reduced by the first expansion valve ( 5 A), and then such refrigerant is evaporated by exchanging heat with outdoor air in the outdoor heat exchanger ( 4 ). Subsequently, the gaseous refrigerant returns to the compressor ( 10 ) through the accumulator ( 8 ), thereby performing the refrigerant circulating operation.
  • injection pipe ( 2 A) Since the injection pipe ( 2 A) is provided, intermediate-pressure gaseous refrigerant in the gas-liquid separator ( 6 ) is injected to the compressor ( 10 ) in the air conditioning operation.
  • a change in refrigerant properties in the refrigerant circuit ( 2 ) will be described with reference to FIG. 4 .
  • refrigerant in the compressor ( 10 ) is compressed so as to transition from a low-pressure state at a point A to a high-condensing-pressure state at a point B through the injection of intermediate-pressure refrigerant.
  • the high-pressure gaseous refrigerant is condensed in the outdoor heat exchanger ( 4 ) or the indoor heat exchanger ( 7 ), and then changes into high-pressure liquid refrigerant at a point C.
  • the pressure of the high-pressure liquid refrigerant is reduced to a point D by the first expansion valve ( 5 A) or the second expansion valve ( 5 B), thereby changing into intermediate-pressure refrigerant.
  • the intermediate-pressure refrigerant is stored in the gas-liquid separator ( 6 ), and is separated into intermediate-pressure liquid refrigerant and intermediate-pressure gaseous refrigerant in the gas-liquid separator ( 6 ).
  • the separated intermediate-pressure gaseous refrigerant is injected into the compressor ( 10 ) through the injection pipe ( 2 A) at a point E (refrigerant at the point D has a lower temperature than that of gaseous refrigerant discharged from the lower-stage compression mechanism ( 20 L), and both of them are mixed together to start a second stage of the compression at the point E). Meanwhile, the pressure of the intermediate-pressure liquid refrigerant is reduced from a point F to a point G by the second expansion valve ( 5 B) or the first expansion valve ( 5 A), and thus, the refrigerant becomes low-pressure two-phase refrigerant.
  • the low-pressure two-phase refrigerant is evaporated in the indoor heat exchanger ( 7 ) or the outdoor heat exchanger ( 4 ). Subsequently, such refrigerant transitions to the state at the point A, and then returns to the compressor ( 10 ).
  • the low-pressure two-phase refrigerant at the point G has an enthalpy difference increasing from the point D to the point F, thereby increasing a heat amount of refrigerant to be evaporated in the indoor heat exchanger ( 7 ).
  • cooling capability is improved.
  • the two-stage compression is employed in the present embodiment, and therefore a discharge temperature of refrigerant is lower than that in a single-stage compression refrigeration cycle shown by a virtual line.
  • intermediate-pressure refrigerant is supplied from the gas-liquid separator ( 6 ) to the middle path ( 20 M), and therefore the discharge valve of the lower-stage compression mechanism ( 20 L) is opened when the pressure of refrigerant in the cylinder chamber ( 25 ) reaches an intermediate pressure level.
  • Refrigerant discharged from the lower-stage compression mechanism ( 20 L) passes from the discharge path ( 24 a ) through the lower muffler ( 26 ), and flows into the suction path ( 21 b ) of the higher-stage compression mechanism ( 20 H) through the middle path ( 20 M).
  • Such refrigerant joins intermediate-pressure refrigerant of the injection pipe ( 2 A) at the middle path ( 20 M), and flows into the cylinder chamber ( 25 ) of the higher-stage compression mechanism ( 20 H).
  • intermediate-pressure refrigerant is compressed, and high-pressure refrigerant is discharged into the casing ( 11 ).
  • the high-pressure refrigerant passes between the stator ( 31 ) and the rotor ( 32 ) of the electric motor ( 30 ), and is discharged to the refrigerant circuit ( 2 ).
  • the high-pressure refrigerant circulates in the refrigerant circuit ( 2 ) as described above.
  • the single component refrigerant containing the HFO-1234yf (2,3,3,3-tetrafluoro-1-propene) is used as the refrigerant of the refrigerant circuit ( 2 ).
  • the HFO-1234yf has properties such as a relatively-high theoretical COP.
  • the single component refrigerant of such refrigerant is used, thereby performing a refrigerant cycle with excellent operational efficiency. Consequently, operational efficiency of the refrigeration apparatus ( 1 ) can be improved.
  • the HFO-1234yf has properties such as relatively-low global warming potential (GWP).
  • GWP global warming potential
  • the single component refrigerant of such refrigerant is used as the refrigerant, thereby providing the environment-friendly refrigeration apparatus ( 1 ).
  • the two-stage compressor including the lower-stage compression mechanism ( 20 L) and the higher-stage compression mechanism ( 20 H) is used, resulting in the lower discharge temperature of refrigerant than that of a single-stage single-cylinder compressor.
  • the decomposition of refrigerant is not caused.
  • the swing piston type compressor ( 10 ) is used, thereby not causing the sliding of the outer circumferential surface of the piston and the tip end surface of the blade, which is caused in the rolling piston type compressor.
  • heat due to the sliding of such members is not generated, thereby not causing the decomposition of refrigerant even in the HFO-1234yf refrigerant which is likely to be decomposed at high temperature.
  • the HFO-1234yf is refrigerant suitable for using under low-pressure condition, and a sufficient circulating amount thereof is hard to be ensured.
  • intermediate-pressure gaseous refrigerant is injected into the compressor ( 10 ) in the present embodiment. Consequently, an apparent operational capacity increases to increase the refrigerant circulating amount, thereby enhancing the refrigeration capability even with the HFO-1234yf with which the sufficient refrigeration capability is hard to be ensured.
  • the inverter control is performed, and therefore an increase in rotational speed results in an increase in suction amount.
  • such configuration also increases the operational capacity to increase the refrigerant circulating amount, thereby enhancing the refrigeration capability even with the HFO-1234yf with which the sufficient refrigeration capability is hard to be ensured.
  • a system in which intermediate-pressure gaseous refrigerant is injected to the compressor ( 10 ) in the two-stage compression refrigeration cycle.
  • the two-compression refrigeration cycle is the system in which, after low-pressure refrigerant gas is compressed to an intermediate pressure level in the lower-stage compression mechanism ( 20 L), the intermediate-pressure gaseous refrigerant is cooled to a temperature near a saturated vapor temperature, and then such refrigerant is further compressed in the higher-stage compression mechanism ( 20 H).
  • the gas injection system is employed, in which the gas-liquid separator ( 6 ) is used as an intermediate cooler (intermediate cooling unit) for cooling intermediate-pressure gaseous refrigerant.
  • intermediate cooler other systems including units such as a refrigerant heat exchanger for exchanging heat between high-pressure liquid refrigerant and two-phase refrigerant made by reducing the pressure of the high-pressure liquid refrigerant to an intermediate pressure level may be used.
  • refrigerant heat exchanger for exchanging heat between high-pressure liquid refrigerant and two-phase refrigerant made by reducing the pressure of the high-pressure liquid refrigerant to an intermediate pressure level
  • a two-cylinder compressor 10
  • a two-cylinder compressor 10
  • a first compression mechanism ( 20 A) and a second compression mechanism ( 20 B) are two compression mechanisms which are not on lower and higher stages, but are in a parallel relationship.
  • a suction path ( 21 a, 21 b ) is provided in each of the compression mechanisms ( 20 A, 20 B), and the suction paths ( 21 a, 21 b ) are connected to a suction-side refrigerant pipe ( 2 B) of a refrigerant circuit ( 2 ) in parallel.
  • the first compression mechanism ( 20 A) and the second compression mechanism ( 20 B) are on the lower and higher stages, and both of the compression mechanisms ( 20 A, 20 B) are connected together by the middle path ( 20 M).
  • the middle path ( 20 M) is not employed in the second embodiment.
  • a lower muffler ( 26 ) fixed to a lower plate ( 24 ) opens to an internal space of a casing ( 11 ), and refrigerant discharged from the first compression mechanism ( 20 A) and the second compression mechanism ( 20 B) is separately discharged into the casing ( 11 ).
  • the configuration is not employed, in which intermediate-pressure gaseous refrigerant is injected to the compression mechanisms.
  • the second embodiment has the same configurations as those of the first embodiment.
  • An operation is the same as that of the first embodiment, except that the two-stage compression is not performed.
  • the second embodiment has the same advantages as those of the first embodiment.
  • the foregoing embodiments may have the following configurations.
  • the compressor including the swing piston type compression mechanisms ( 20 A, 20 B) is used.
  • the swing piston type compression mechanism e.g., a rolling piston type or scroll type compression mechanism may be used.
  • a two-cylinder or two-stage compression mechanism 20 A, 20 B is employed, thereby reducing or preventing an increase in discharge temperature of refrigerant. Consequently, decomposition of HFO-1234yf which is refrigerant can be reduced or prevented.
  • the single component refrigerant includes, e.g., 1,2,3,3,3-pentafluoro-1-propene (referred to as “HFO-1225ye,” and a chemical formula thereof is represented by an expression CF 3 —CF ⁇ CHF); 1,3,3,3-tetrafluoro-1-propene (referred to as “HFO-1234ze,” and a chemical formula thereof is represented by an expression CF 3 —CH ⁇ CHF); 1,2,3,3-tetrafluoro-1-propene (referred to as “HFO-1234ye,” and a chemical formula thereof is represented by an expression CHF 2 —CF ⁇ CHF); 3,3,3-trifluoro-1-propene (referred to as “HFO-1243zf,” and a chemical formula thereof is represented by an expression CF 3 —CH ⁇ CH 2 ); 1,2,2-trifluoro-1-propene (a chemical formula thereof is represented by an expression CH 3 —CF ⁇ CF 2 ); and 2-fluoro-1-propene (
  • refrigerant mixture may be used, which is made by adding at least one of HFC-32 (difluoromethane), HFC-125 (pentafluoroethane), HFC-134 (1,1,2,2-tetrafluoroethane), HFC-134a (1,1,1,2-tetrafluoroethane), HFC-143a (1,1,1-trifluoroethane), HFC-152a (1,1-difluoroethane), HFC-161, HFC-227ea, HFC-236ea, HFC-236fa, HFC-365mfc, methane, ethane, propane, propene, butane, isobutane, pentane, 2-methylbutane, cyclopentane, dimethyl ether, bis-trifluoromethyl-sulfide, carbon dioxide, and helium; to the refrigerant represented by the molecular formula and having the single double bond in the molecular
  • Refrigerant mixture of, e.g., the HFO-1234yf and the HFC-32 may be used.
  • the refrigerant mixture may be used, in which the proportion of the HFO-1234yf is 78.2% by mass, and the proportion of the HFC-32 is 21.8% by mass.
  • the refrigerant mixture may be used, in which the proportion of the HFO-1234yf is 77.6% by mass, and the proportion of the HFC-32 is 22.4% by mass.
  • the proportion of the HFO-1234yf may be equal to or greater than 70% by mass and equal to or less than 94% by mass, and the proportion of the HFC-32 may be equal to or greater than 6% by mass and equal to or less than 30% by mass.
  • the proportion of the HFO-1234yf is preferably equal to or greater than 77% by mass and equal to or less than 87% by mass, and the proportion of the HFC-32 may be equal to or greater than 13% by mass and equal to or less than 23% by mass.
  • the proportion of the HFO-1234yf is equal to or greater than 77% by mass and equal to or less than 79% by mass, and the proportion of the HFC-32 is equal to or greater than 21% by mass and equal to or less than 23% by mass.
  • Refrigerant mixture of the HFO-1234yf and the HFC-125 may be used.
  • the proportion of the HFC-125 is preferably equal to or greater than 10% by mass, and more preferably equal to or greater than 10% by mass and equal to or less than 20% by mass.
  • Refrigerant mixture of the HFO-1234yf, the HFC-32, and the HFC-125 may be used.
  • refrigerant mixture may be used, which contains the HFO-1234yf of 52% by mass, the HFC-32 of 23% by mass, and the HFC-125 of 25% by mass.
  • the present invention is useful for the refrigeration apparatus for which the refrigerant containing the compound represented by the molecular formula of C 3 H m F n is used.

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  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
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Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110150683A1 (en) * 2009-12-22 2011-06-23 Lee Yunhi Rotary compressor
US20110179822A1 (en) * 2008-09-30 2011-07-28 Daikin Industries, Ltd. Refrigerating apparatus
US20110219815A1 (en) * 2009-05-08 2011-09-15 Honeywell International Inc. Heat transfer compositions and methods
US8992793B2 (en) 2009-02-04 2015-03-31 Panasonic Intellectual Property Management Co., Ltd. Refrigeration apparatus
US20160225959A1 (en) * 2015-02-04 2016-08-04 Everlight Electronics Co., Ltd. LED Packaging Structure And Method For Manufacturing The Same
US9803897B2 (en) 2011-09-01 2017-10-31 Daikin Industries, Ltd. Refrigeration apparatus which injects an intermediate-gas liquid refrigerant from multi-stage expansion cycle into the compressor
US20180017057A1 (en) * 2016-07-14 2018-01-18 Fujitsu General Limited Rotary compressor
US20180156215A1 (en) * 2015-08-24 2018-06-07 Guangdong Meizhi Compressor Co., Ltd. Rotary compressor and refrigeration cycle device having same
US10443912B2 (en) 2013-10-25 2019-10-15 Mitsubishi Heavy Industries Thermal Systems, Ltd. Refrigerant circulation device, method for circulating refrigerant and acid suppression method
US10465959B2 (en) 2013-10-25 2019-11-05 Mitsubishi Heavy Industries Thermal Systems, Ltd. Refrigerant circulation device, method for circulating refrigerant and method for suppressing isomerization
US10487832B2 (en) * 2016-12-22 2019-11-26 Lennox Industries Inc. Method and apparatus for pressure equalization in rotary compressors
US10508848B2 (en) * 2014-03-14 2019-12-17 Mitsubishi Electric Corporation Refrigeration cycle apparatus
US10801510B2 (en) 2017-04-24 2020-10-13 Lennox Industries Inc. Method and apparatus for pressure equalization in rotary compressors
US20220372983A1 (en) * 2020-02-10 2022-11-24 Daikin Industries, Ltd. Compressor

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011092881A2 (en) * 2010-02-01 2011-08-04 Panasonic Corporation Refrigeration apparatus
JP2011094841A (ja) * 2009-10-28 2011-05-12 Daikin Industries Ltd 冷凍装置
JPWO2011155176A1 (ja) * 2010-06-07 2013-08-01 パナソニック株式会社 圧縮機
CN102691660B (zh) * 2011-12-15 2014-12-24 珠海凌达压缩机有限公司 一种高制冷性能的二级双缸压缩机
JP2013134040A (ja) * 2011-12-27 2013-07-08 Daikin Industries Ltd 冷凍装置
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EP3012557A4 (en) * 2013-06-19 2017-02-22 Mitsubishi Electric Corporation Refrigeration cycle device
US10724525B2 (en) * 2015-07-15 2020-07-28 Daikin Industries, Ltd. Compression mechanism for a compressor
CN105783305A (zh) * 2016-04-29 2016-07-20 广东美的制冷设备有限公司 单冷型空调器及其控制方法
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JP2018123974A (ja) * 2017-01-30 2018-08-09 ダイキン工業株式会社 冷凍装置
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CN115769030A (zh) 2020-07-03 2023-03-07 大金工业株式会社 在压缩机中作为制冷剂的用途、压缩机和制冷循环装置
JP7260804B2 (ja) * 2021-03-26 2023-04-19 ダイキン工業株式会社 冷媒導入管を有する圧縮機

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4571157A (en) * 1981-10-02 1986-02-18 Karl Eickmann Propeller with an interior arrangement to variate the pitch
US5170636A (en) * 1990-04-24 1992-12-15 Kabushiki Kaisha Toshiba Heat exchanger
US20050008519A1 (en) * 2002-03-18 2005-01-13 Masanori Masuda Rotary compressor
US20060153723A1 (en) * 2003-06-10 2006-07-13 Dalkin Industries, Ltd Rotary fluid machinery
US20070224073A1 (en) * 2004-04-23 2007-09-27 Daikin Industries, Ltd. Rotary Fluid Machine
US20080240958A1 (en) * 2004-05-11 2008-10-02 Masanori Masuda Rotary Fluid Machine
US20080307797A1 (en) * 2004-08-05 2008-12-18 Daikin Industries, Ltd Positive Displacement Expander and Fluid Machinery
US20090068046A1 (en) * 2006-03-03 2009-03-12 Daikin Industries, Ltd. Compressor and manufacturing method thereof
US7789634B2 (en) * 2003-12-11 2010-09-07 Daikin Industries, Ltd. Compressor
US7837449B2 (en) * 2001-09-27 2010-11-23 Sanyo Electric Co., Ltd. Compressor, method for manufacturing the compressor, defroster of refrigerant circuit, and refrigerant unit
US7896627B2 (en) * 2003-09-08 2011-03-01 Daikin Industries, Ltd. Rotary type expander and fluid machinery

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2513700B2 (ja) * 1987-06-30 1996-07-03 株式会社東芝 空気調和装置
JPH04110388A (ja) 1990-08-31 1992-04-10 Daikin Ind Ltd 熱伝達用流体
KR20010014817A (ko) * 1999-07-06 2001-02-26 다카노 야스아키 냉매압축기 및 이것을 이용한 냉동냉방장치
CA2591130A1 (en) * 2004-12-21 2006-06-29 Honeywell International Inc. Stabilized iodocarbon compositions
US20060243944A1 (en) * 2005-03-04 2006-11-02 Minor Barbara H Compositions comprising a fluoroolefin
JP2007023993A (ja) * 2005-07-21 2007-02-01 Daikin Ind Ltd 二段圧縮機
US7335804B2 (en) * 2005-11-03 2008-02-26 Honeywell International Inc. Direct conversion of HCFC 225ca/cb mixture
JP2007263109A (ja) * 2006-03-03 2007-10-11 Daikin Ind Ltd 回転式圧縮機
JP4797715B2 (ja) * 2006-03-09 2011-10-19 ダイキン工業株式会社 冷凍装置

Patent Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4571157A (en) * 1981-10-02 1986-02-18 Karl Eickmann Propeller with an interior arrangement to variate the pitch
US5170636A (en) * 1990-04-24 1992-12-15 Kabushiki Kaisha Toshiba Heat exchanger
US7837449B2 (en) * 2001-09-27 2010-11-23 Sanyo Electric Co., Ltd. Compressor, method for manufacturing the compressor, defroster of refrigerant circuit, and refrigerant unit
US20050008519A1 (en) * 2002-03-18 2005-01-13 Masanori Masuda Rotary compressor
US7029252B2 (en) * 2002-03-18 2006-04-18 Dakin Industries, Ltd Rotary compressor
US7563084B2 (en) * 2003-06-10 2009-07-21 Daikin Industries, Ltd. Rotary fluid machine
US20060153723A1 (en) * 2003-06-10 2006-07-13 Dalkin Industries, Ltd Rotary fluid machinery
US7896627B2 (en) * 2003-09-08 2011-03-01 Daikin Industries, Ltd. Rotary type expander and fluid machinery
US7789634B2 (en) * 2003-12-11 2010-09-07 Daikin Industries, Ltd. Compressor
US7435065B2 (en) * 2004-04-23 2008-10-14 Daikin Industries, Ltd. Rotary fluid machine having a swinging bushing with a swing center disposed radially inwardly of an annular midline of an annular piston
US20070224073A1 (en) * 2004-04-23 2007-09-27 Daikin Industries, Ltd. Rotary Fluid Machine
US7549851B2 (en) * 2004-05-11 2009-06-23 Daikin Industries, Ltd. Rotary fluid machine having a pair of rotation mechanisms and a partition plate disposed between the rotation mechanisms
US20080240958A1 (en) * 2004-05-11 2008-10-02 Masanori Masuda Rotary Fluid Machine
US20080307797A1 (en) * 2004-08-05 2008-12-18 Daikin Industries, Ltd Positive Displacement Expander and Fluid Machinery
US20090068046A1 (en) * 2006-03-03 2009-03-12 Daikin Industries, Ltd. Compressor and manufacturing method thereof
US8167596B2 (en) * 2006-03-03 2012-05-01 Daikin Industries, Ltd. Compressor and manufacturing method thereof

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110179822A1 (en) * 2008-09-30 2011-07-28 Daikin Industries, Ltd. Refrigerating apparatus
US8992793B2 (en) 2009-02-04 2015-03-31 Panasonic Intellectual Property Management Co., Ltd. Refrigeration apparatus
US20110219815A1 (en) * 2009-05-08 2011-09-15 Honeywell International Inc. Heat transfer compositions and methods
US20110150683A1 (en) * 2009-12-22 2011-06-23 Lee Yunhi Rotary compressor
US8967984B2 (en) * 2009-12-22 2015-03-03 Lg Electronics Inc. Rotary compressor
US9803897B2 (en) 2011-09-01 2017-10-31 Daikin Industries, Ltd. Refrigeration apparatus which injects an intermediate-gas liquid refrigerant from multi-stage expansion cycle into the compressor
US10465959B2 (en) 2013-10-25 2019-11-05 Mitsubishi Heavy Industries Thermal Systems, Ltd. Refrigerant circulation device, method for circulating refrigerant and method for suppressing isomerization
US10443912B2 (en) 2013-10-25 2019-10-15 Mitsubishi Heavy Industries Thermal Systems, Ltd. Refrigerant circulation device, method for circulating refrigerant and acid suppression method
US10508848B2 (en) * 2014-03-14 2019-12-17 Mitsubishi Electric Corporation Refrigeration cycle apparatus
US20160225959A1 (en) * 2015-02-04 2016-08-04 Everlight Electronics Co., Ltd. LED Packaging Structure And Method For Manufacturing The Same
US10465682B2 (en) * 2015-08-24 2019-11-05 Guangdong Meizhi Compressor Co., Ltd. Rotary compressor and refrigeration cycle device having same
US20180156215A1 (en) * 2015-08-24 2018-06-07 Guangdong Meizhi Compressor Co., Ltd. Rotary compressor and refrigeration cycle device having same
US20180017057A1 (en) * 2016-07-14 2018-01-18 Fujitsu General Limited Rotary compressor
US10738779B2 (en) * 2016-07-14 2020-08-11 Fujitsu General Limited Rotary compressor
US10487832B2 (en) * 2016-12-22 2019-11-26 Lennox Industries Inc. Method and apparatus for pressure equalization in rotary compressors
US11015604B2 (en) * 2016-12-22 2021-05-25 Lennox Industries Inc. Method and apparatus for pressure equalization in rotary compressors
US10801510B2 (en) 2017-04-24 2020-10-13 Lennox Industries Inc. Method and apparatus for pressure equalization in rotary compressors
US11460027B2 (en) 2017-04-24 2022-10-04 Lennox Industries Inc. Method and apparatus for pressure equalization in rotary compressors
US20220372983A1 (en) * 2020-02-10 2022-11-24 Daikin Industries, Ltd. Compressor
US11698072B2 (en) * 2020-02-10 2023-07-11 Daikin Industries, Ltd. Compressor

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