WO2020031248A1 - ロータリー圧縮機及び冷凍サイクル装置 - Google Patents

ロータリー圧縮機及び冷凍サイクル装置 Download PDF

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Publication number
WO2020031248A1
WO2020031248A1 PCT/JP2018/029523 JP2018029523W WO2020031248A1 WO 2020031248 A1 WO2020031248 A1 WO 2020031248A1 JP 2018029523 W JP2018029523 W JP 2018029523W WO 2020031248 A1 WO2020031248 A1 WO 2020031248A1
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WIPO (PCT)
Prior art keywords
injection
hole
rotary compressor
refrigerant
cylinder
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2018/029523
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English (en)
French (fr)
Japanese (ja)
Inventor
亮 濱田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to CZ202140A priority Critical patent/CZ309303B6/cs
Priority to JP2020535360A priority patent/JP7003272B2/ja
Priority to PCT/JP2018/029523 priority patent/WO2020031248A1/ja
Priority to KR1020217002894A priority patent/KR102449302B1/ko
Priority to CN201880095841.1A priority patent/CN112513466B/zh
Publication of WO2020031248A1 publication Critical patent/WO2020031248A1/ja
Anticipated expiration legal-status Critical
Ceased 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
    • F04C18/34—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 the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—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 the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • 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
    • F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/0085—Prime movers
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • 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
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • F25B31/008—Cooling of compressor or motor by injecting a liquid
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F25B31/026—Compressor arrangements of motor-compressor units with compressor of rotary type
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • 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
    • F04C2240/00—Components
    • F04C2240/10—Stators
    • 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
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • 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
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a

Definitions

  • the present invention relates to a rotary compressor and a refrigeration cycle device having a partition for closing a through hole in a cylinder.
  • an electric motor including a rotor and a stator is mounted on an upper part in a closed container. Then, the rotation of the electric motor is transmitted downward by the crankshaft fixed to the rotor.
  • a compression mechanism is provided below the crankshaft.
  • the compression mechanism mainly includes a cylinder, a main bearing, an auxiliary bearing, an intermediate plate, and a piston. In the compression mechanism, the eccentric crankshaft rotates to move the piston eccentrically, and the volume of the compression chamber is reduced, so that the refrigerant is compressed.
  • one or more of the main bearing, the sub-bearing, and the intermediate plate are formed with an injection hole for introducing an injection refrigerant so as to communicate with the compression chamber.
  • An intermediate-pressure liquid or gaseous refrigerant is injected into the compression chamber as an injection refrigerant by an injection flow path introduced from the middle of the refrigeration cycle circuit.
  • the injection refrigerant from the injection flow path is injected into the compression chamber, thereby increasing the amount of discharged refrigerant and increasing the refrigerant flow rate on the condenser side of the refrigeration cycle circuit. And the heating capacity is improved.
  • the sliding components forming the compression mechanism are cooled by the injection refrigerant, and the gap between the sliding components is appropriately maintained, so that the reliability of the rotary compressor can be improved.
  • the present invention has been made to solve the above problems, and the injection refrigerant always flows into the compression chamber regardless of the eccentric movement of the piston, the amount of the discharged refrigerant is increased, the injection effect is obtained, and the sliding parts are obtained. It is an object of the present invention to provide a rotary compressor and a refrigeration cycle device that can be constantly cooled and have improved reliability.
  • a rotary compressor includes an electric motor having a stator and a rotor, an eccentric portion provided on a main shaft fixed to the rotor, a crankshaft rotated by the electric motor,
  • a rotary compressor including a piston provided in a core portion, a cylinder in which a cylindrical through hole is formed, and a cylinder in which the eccentric portion and the piston are arranged in the through hole and a compression chamber is formed.
  • a refrigeration cycle device includes the rotary compressor described above.
  • the injection flow path is formed in the partition and the plurality of injection holes for injecting the injection refrigerant into the compression chamber from the inside of the partition, and communicates with the plurality of injection holes. And a common hole.
  • the opening area of the injection refrigerant to be injected into the compression chamber is increased with a simple configuration.
  • the injection channel can always communicate with the compression chamber. Therefore, the injection refrigerant always flows into the compression chamber irrespective of the eccentric movement of the piston, the amount of the discharged refrigerant increases, the injection effect is obtained, and the sliding parts are always cooled, so that the reliability can be improved.
  • FIG. 2 is a refrigerant circuit diagram illustrating a refrigeration cycle device to which the twin rotary compressor according to Embodiment 1 of the present invention is applied. It is an explanatory view showing a longitudinal section of a twin rotary compressor according to Embodiment 1 of the present invention. It is a side view which shows the upper bearing in which the common hole which concerns on Embodiment 1 of this invention was formed.
  • FIG. 3 is an explanatory diagram showing a cross section in which an injection hole opened to a compression chamber according to Embodiment 1 of the present invention can be seen.
  • FIG. 5 is an explanatory diagram showing a cross section taken along line AA of FIG. 4 of the upper bearing in which the common hole and the injection hole according to Embodiment 1 of the present invention are formed.
  • FIG. 2 is an explanatory diagram illustrating a vertical cross section of the piston according to Embodiment 1 of the present invention.
  • FIG. 3 is an explanatory diagram showing an opening state of an injection hole according to an eccentric movement of a piston according to Embodiment 1 of the present invention in a range of 0 ° to 360 °.
  • FIG. 4 is an explanatory diagram showing a cross section in which an injection hole opened in a compression chamber according to a first modification of the first embodiment of the present invention is visible. It is an explanatory view showing a longitudinal section of a compression mechanism part of a twin rotary compressor according to Embodiment 2 of the present invention.
  • FIG. 13 is an explanatory diagram showing a cross section of an intermediate plate in which a common hole and an injection hole according to a second modification of the second embodiment of the present invention are formed. It is an explanatory view showing a transverse section in which an injection hole opened to a compression chamber according to Embodiment 3 of the present invention can be seen. It is an explanatory view showing a transverse section in which an injection hole opened to a compression chamber according to Embodiment 4 of the present invention can be seen.
  • FIG. 1 is a refrigerant circuit diagram showing a refrigeration cycle apparatus 200 to which the twin rotary compressor 100 according to Embodiment 1 of the present invention is applied.
  • the refrigeration cycle apparatus 200 includes a twin rotary compressor 100, a condenser 201, an expansion valve 202, and an evaporator 203.
  • the twin rotary compressor 100, condenser 201, expansion valve 202, and evaporator 203 are connected by a refrigerant pipe 204 to form a refrigeration cycle circuit. Then, the refrigerant flowing out of the evaporator 203 is sucked into the twin rotary compressor 100 via the accumulator 206 and becomes high temperature and high pressure. The high-temperature and high-pressure refrigerant is condensed in the condenser 201 to become a liquid.
  • the liquid refrigerant is decompressed and expanded by the expansion valve 202 to become a low-temperature low-pressure gas-liquid two-phase, and the gas-liquid two-phase refrigerant is subjected to heat exchange in the evaporator 203.
  • the refrigeration cycle apparatus 200 includes an injection flow path 205 for injecting a refrigerant into a compression chamber from a separator 207 disposed in a refrigerant pipe 204 before the evaporator 203 in the refrigerant flow direction of the refrigeration cycle circuit and further before the expansion valve 202.
  • a control valve 208 for controlling the flow rate of the injection refrigerant is provided in the middle of the injection flow path 205.
  • the control valve 208 is disposed in the injection flow path 205 on the upstream side of the twin rotary compressor 100 in the injection refrigerant flow direction.
  • the control valve 208 is constituted by, for example, an on-off valve, a check valve, or a flow control valve, and adjusts the flow rate of the injection refrigerant so as to obtain an optimal injection effect.
  • the details of the injection channel 205 will be described later.
  • the twin rotary compressor 100 described below can be applied to such a refrigeration cycle apparatus 200.
  • a refrigeration cycle apparatus 200 for example, an air conditioner, a refrigerating device, a water heater, or the like can be given.
  • FIG. 2 is an explanatory diagram illustrating a vertical cross section of the twin rotary compressor 100 according to Embodiment 1 of the present invention.
  • FIG. 3 is a side view showing upper bearing 109a in which first common hole 205f1 according to Embodiment 1 of the present invention is formed.
  • FIG. 4 is an explanatory diagram showing a visible cross section of the first injection hole 205a1 and the second injection hole 205a2 opened in the first compression chamber 106a according to Embodiment 1 of the present invention.
  • FIG. 5 is a cross-sectional view of the upper bearing 109a in which the first common hole 205f1, the first injection hole 205a1, and the second injection hole 205a2 according to Embodiment 1 of the present invention are formed, taken along the line AA in FIG.
  • FIG. 6 is an explanatory diagram showing a vertical cross section of the first piston 105a according to Embodiment 1 of the present invention.
  • the twin rotary compressor 100 includes a cylindrical hermetic container 101 whose upper and lower ends are closed.
  • the airtight container 101 has a cylindrical member 101a, a bowl-shaped upper end closing member 101b for closing the upper end of the cylindrical member 101a, and a bowl-shaped lower end closing member 101c for closing the lower end of the cylindrical member 101a.
  • the closed container 101 is fixedly mounted on a base 102.
  • An electric motor 103 is arranged in the upper part of the sealed container 101.
  • the electric motor 103 has a stator 103a and a rotor 103b.
  • the stator 103 a of the electric motor 103 has a cylindrical shape and is fixed to the inner peripheral wall of the closed casing 101.
  • the rotor 103b has a columnar shape, and is disposed in a hollow portion formed at the center of the stator 103a so as to be rotatable in the horizontal and circumferential directions.
  • crankshaft 104 rotated by an electric motor 103 is disposed in the sealed container 101 so as to extend in a vertical direction.
  • the crankshaft 104 has a main shaft 104a, a first eccentric portion 104b, a second eccentric portion 104c, and a sub shaft 104d.
  • the main shaft 104a is fixed to the rotor 103b.
  • the main shaft 104a transmits the rotational driving force from the rotor 103b to the first eccentric portion 104b and the second eccentric portion 104c.
  • the first eccentric portion 104b is provided on the main shaft 104a on the main shaft 104a side above the second eccentric portion 104c, is eccentric from the main shaft 104a and the center line, and is larger than the main shaft 104a.
  • the second eccentric portion 104c is provided on the main shaft 104a below the first eccentric portion 104b on the sub-shaft 104d side, and eccentricizes the center line with the main shaft 104a and the first eccentric portion 104b, and is larger than the main shaft 104a. .
  • the first eccentric part 104b is provided with a first piston 105a.
  • the first piston 105a has a vane 105a1 that partitions the first compression chamber 106a.
  • the first piston 105a is also called a rolling piston.
  • the first eccentric part 104b and the first piston 105a are arranged in the first cylinder 107a in which the cylindrical through hole 107a1 is formed.
  • the first eccentric portion 104b and the first piston 105a are arranged in the through hole 107a1 to form a first compression chamber 106a.
  • An upper bearing 109a and an intermediate plate 110 that partition the vertical direction of the first compression chamber 106a in the first cylinder 107a are arranged.
  • the upper bearing 109a and the intermediate plate 110 cover a through hole in the first cylinder 107a.
  • the first compression chamber 106a is a closed cylindrical space.
  • the first inflow refrigerant pipe 108a is connected to the first cylinder 107a through the through hole 107a1.
  • the second eccentric portion 104c is provided with a second piston (not shown).
  • the second piston has a vane that partitions the second compression chamber.
  • the second piston is also called a rolling piston.
  • the second eccentric part 104c and the second piston are disposed below the first cylinder 107a in the second cylinder 107b having a cylindrical through hole.
  • a second compression chamber is formed by disposing the second eccentric portion 104c and the second piston in the through hole.
  • An intermediate plate 110 and a lower bearing 109b which partition the vertical direction of the second compression chamber in the second cylinder 107b are arranged.
  • the intermediate plate 110 and the lower bearing 109b cover a through hole in the second cylinder 107b.
  • the second compression chamber is a closed cylindrical space.
  • a second inflow refrigerant pipe 108b is connected to the second cylinder 107b via a through hole.
  • the upper bearing 109a covering the upper end surface of the first cylinder 107a forms the upper wall of the first compression chamber 106a while slidably holding the crankshaft 104.
  • the lower bearing 109b which covers the lower end surface of the second cylinder 107b constitutes the lower wall of the second compression chamber while slidably holding the crankshaft 104.
  • the intermediate plate 110 disposed between the first cylinder 107a and the second cylinder 107b forms a lower wall of the first compression chamber 106a and an upper wall of the second compression chamber, and the first compression chamber 106a and the second It separates two compression chambers.
  • the first inflow refrigerant pipe 108a and the second inflow refrigerant pipe 108b have both inflow ports inserted upward in the suction muffler 113.
  • the suction muffler 113 is connected by inserting the refrigerant pipe 204 of the refrigeration cycle circuit downward, and allows the refrigerant to flow.
  • the suction muffler 113 is fixed to the outer periphery of the closed container 101.
  • Refrigeration oil is stored at the bottom of the sealed container 101.
  • the refrigerating machine oil accumulated at the bottom is sucked up from the hollow hole provided in the crankshaft 104 by the rotation of the crankshaft 104 in the manner of a centrifugal pump using the rotation of the crankshaft 104.
  • the pumped-up refrigerating machine oil is circulated to each sliding portion through an oil supply hole opened from a hollow hole of the crankshaft 104 to an outer peripheral portion. Thereby, the machine part is sealed by the refrigerating machine oil.
  • crankshaft 104, the first piston 105a, the second piston, the first cylinder 107a, the second cylinder 107b, the upper bearing 109a, the lower bearing 109b, and the intermediate plate 110, which are sliding parts, do not directly contact each other. Damage is prevented and refrigerant leakage is prevented.
  • An oil separator (not shown) is fitted on the upper part of the crankshaft 104.
  • the oil separator prevents the refrigerating machine oil from flowing out of the discharge pipe 112 together with the discharged refrigerant.
  • the oil separator blocks the flow path of the mixed fluid of the refrigerant and the refrigerating machine oil flowing toward the discharge pipe 112, causes the refrigerant and the refrigerating machine oil to collide and separate, and suppresses the outflow of the refrigerating machine oil outside the machine.
  • the crankshaft 104 fixed to the rotor 103b of the motor part is rotated by the electric motor 103.
  • the first eccentric portion 104b and the second eccentric portion 104c, and the first piston 105a and the second piston attached to the outer peripheral portions of the first eccentric portion 104b and the second eccentric portion 104c, respectively.
  • Eccentric rotation the volumes of the first compression chamber 106a and the second compression chamber separated by the vane 105a1 are reduced, and the refrigerant is compressed to change to a high pressure.
  • the first compression chamber 106a and the second compression chamber are provided with a discharge valve that is released when the pressure exceeds a predetermined pressure.
  • the discharge valve When the discharge valve is opened, a high-temperature and high-pressure gas refrigerant is discharged into the closed vessel 101.
  • the compressed gas refrigerant passes through the discharge pipe 112 and is discharged into the refrigeration cycle circuit outside the twin rotary compressor.
  • the working refrigerant is, for example, R410A refrigerant.
  • the injection flow path 205 is connected to the first compression chamber 106 a by a separator 207 provided in the refrigerant pipe 204 before the evaporator 203 and further before the expansion valve 202 in the refrigerant flow direction of the refrigeration cycle circuit. And a refrigerant is injected into each of the second compression chambers.
  • the injection flow path 205 includes a first injection hole 205a1, a second injection hole 205a2, a third injection hole 205a3, a fourth injection hole 205a4, a first common hole 205f1, and a second common hole 205f1. It has a hole 205f2, a bypass pipe 205b, a first injection pipe 205c, a second injection pipe 205d, and an injection muffler 205e.
  • the first injection hole 205a1 and the second injection hole 205a2 are formed in the first compression chamber 106a by opening a part of the upper bearing 109a as a partition.
  • the first injection hole 205a1 and the second injection hole 205a2 inject an injection refrigerant from inside the upper bearing 109a to the first compression chamber 106a.
  • the first injection hole 205a1 and the second injection hole 205a2 are formed at positions equidistant from the center of the first cylinder 107a. More specifically, the first injection hole 205a1 and the second injection hole 205a2 are formed adjacent to the inner diameter boundary of the first cylinder 107a. More preferably, the first injection hole 205a1 and the second injection hole 205a2 are formed in contact with the inner diameter boundary of the first cylinder 107a. Thus, as described later, at least one of the first injection hole 205a1 and the second injection hole 205a2 always opens to the first compression chamber 106a.
  • the third injection hole 205a3 and the fourth injection hole 205a4 are formed in the second compression chamber by opening a part of the lower bearing 109b as a partition.
  • the third injection hole 205a3 and the fourth injection hole 205a4 inject the injection refrigerant into the second compression chamber from inside the lower bearing 109b.
  • the third injection hole 205a3 and the fourth injection hole 205a4 are formed at positions equidistant from the center of the second cylinder 107b. More specifically, the third injection hole 205a3 and the fourth injection hole 205a4 are formed adjacent to the inner diameter boundary of the second cylinder 107b. More preferably, the third injection hole 205a3 and the fourth injection hole 205a4 are formed in contact with the inner diameter boundary of the second cylinder 107b. As a result, at least one of the third injection hole 205a3 and the fourth injection hole 205a4 always opens to the second compression chamber, similarly to the first injection hole 205a1 and the second injection hole 205a2.
  • the positions of the first injection hole 205a1 and the second injection hole 205a2, the hole diameter of the first injection hole 205a1 and the second injection hole 205a2, the outer diameter of the first piston 105a, and the position of the first cylinder 107a By appropriately setting the relation of the inner diameter, at least one of the first injection hole 205a1 and the second injection hole 205a2 can always be opened.
  • description will be made using the configuration inside the first cylinder. The same applies to the configuration inside the second cylinder.
  • the inner diameter of the first cylinder 107a is 50 mm.
  • the outer diameter of the first piston 105a is 32 mm.
  • Two of the first injection hole 205a1 and the second injection hole 205a2 are provided.
  • the diameter of each of the first injection hole 205a1 and the second injection hole 205a2 is 4 mm.
  • the distance from the center of the cylinder to the center of each of the first injection hole 205a1 and the second injection hole 205a2 is 22.9 mm.
  • the phases of the first injection hole 205a1 and the second injection hole 205a2 are located at 270 ° and 180 ° counterclockwise with respect to the reference that the position of the vane 105a1 is 0 °.
  • a chamfered R-process 105a3 is applied to the inner side of the inner diameter boundary of the first piston 105a on the sliding surface 105a2 with respect to the upper bearing 109a of the first piston 105a. All of the first injection hole 205a1 and the second injection hole 205a2 are formed on the outer diameter side of the inner surface boundary of the first piston 105a on the sliding surface 105a2 with respect to the upper bearing 109a of the first piston 105a. Thereby, injection of the injection refrigerant from the first injection hole 205a1 and the second injection hole 205a2 into the center hole of the first piston 105a is prevented.
  • the first common hole 205f1 is formed by penetrating a part of the upper bearing 109a as a partition part into a straight horizontal hole.
  • a first injection pipe 205c is connected to the first common hole 205f1 at an opening on the side surface of the upper bearing 109a.
  • the back end of the first common hole 205f1 is closed and closed.
  • the first common hole 205f1 communicates with the first injection hole 205a1 and the second injection hole 205a2.
  • One first common hole 205f1 is provided for the first injection hole 205a1 and the second injection hole 205a2.
  • the first common hole 205f1 is formed so as to enter the center side of the first cylinder 107a with respect to a tangent to the inner diameter of the first cylinder 107a.
  • the second common hole 205f2 is formed by penetrating a part of the lower bearing 109b as a partition into a linear lateral hole.
  • a second injection tube 205d is connected to the second common hole 205f2 at an opening on the side surface of the lower bearing 109b.
  • the back end of the second common hole 205f2 is closed and closed.
  • the second common hole 205f2 communicates with the third injection hole 205a3 and the fourth injection hole 205a4.
  • the second common hole 205f2 is formed so as to enter the center side of the second cylinder 107b with respect to the tangent to the inner diameter of the second cylinder 107b.
  • the bypass pipe 205b is connected to the refrigerant pipe 204 of the refrigeration cycle circuit, and is connected to the injection muffler 205e with its tip inserted downward.
  • the first injection pipe 205c has an inflow port inserted upward into the injection muffler 205e, is connected to the first common hole 205f1, and supplies the refrigerant to the first injection hole 205a1 and the second injection hole 205a2.
  • the second injection pipe 205d has an inflow port inserted upward into the injection muffler 205e, is connected to the second common hole 205f2, and supplies refrigerant to the third injection hole 205a3 and the third injection hole 205a3.
  • the second injection pipe 205d is connected to a lower part of the closed vessel 101 than the first injection pipe 205c, and thus is longer than the first injection pipe 205c.
  • the injection muffler 205e is disposed between the bypass pipe 205b and the first injection pipe 205c and the second injection pipe 205d.
  • the inner diameter of the injection muffler 205e is larger than the inner diameters of the first injection pipe 205c and the second injection pipe 205d.
  • the first injection pipe 205c and the second injection pipe 205d are inserted into the circular bottom of the injection muffler 205e at two places.
  • the injection muffler 205e is fixed to the outer peripheral portion of the sealed container 101, like the suction muffler 113.
  • the volume of the injection muffler 205e is based on the relationship between the suction refrigerant and the injection refrigerant.
  • FIG. 7 is an explanatory diagram showing an opening state of the first injection hole 205a1 and the second injection hole 205a2 according to the eccentric movement of the first piston 105a according to Embodiment 1 of the present invention in a range of 0 ° to 360 °. It is. Here, the state during the operation of the first piston 105a will be described. The same applies to the second piston.
  • both the first injection hole 205a1 and the second injection hole 205a2 It is also opened. For this reason, the injection refrigerant flows into the first compression chamber 106a from both the first injection hole 205a1 and the second injection hole 205a2.
  • the first injection hole 205a1 slides on the first piston 105a. It is covered and closed by the surface 105a2.
  • the second injection hole 205a2 maintains an opened state. Therefore, the injection refrigerant flows into the first compression chamber 106a only from the second injection hole 205a2.
  • the second injection hole 205a2 is placed on the sliding surface of the first piston 105a. It is covered and closed by 105a2.
  • the closed first compression chamber 106a gradually narrows and, when the pressure exceeds a predetermined pressure, is discharged from the discharge hole 107a3 as a high-temperature and high-pressure gas refrigerant.
  • the first injection hole 205a1 is opened to the next first compression chamber 106a, and the injection refrigerant flows therein.
  • one of the first injection hole 205a1 and the second injection hole 205a2 opens in the first cylinder 107a.
  • the refrigerant flowing from the refrigeration cycle circuit through the injection flow path 205 flows into the injection muffler 205e through the bypass pipe 205b.
  • the refrigerant flowing into the injection muffler 205e is supplied to the first injection pipe 205c and the second injection pipe 205d in the injection muffler 205e.
  • the refrigerant supplied to the first injection pipe 205c passes through the first common hole 205f1 of the twin rotary compressor 100 and flows from the first injection hole 205a1 and the second injection hole 205a2 into the first compression chamber 106a into a liquid or gaseous refrigerant.
  • the pressure in the injection muffler 205e is determined by the injection pressure from the refrigeration cycle circuit and the pressure of the first injection pipe 205c and the second injection pipe 205d supplied to the first compression chamber 106a and the second compression chamber. Intermediate pressure. For this reason, it is in a state where leakage of the refrigerant due to the differential pressure between the first compression chamber 106a and the second compression chamber hardly occurs.
  • the pressure in the first injection pipe 205c and the pressure in the second injection pipe 205d fluctuate depending on the phases of the first piston 105a and the second piston.
  • the first injection pipe 205c and the second injection pipe 205d are connected to the bypass pipe 205b via an injection muffler 205e that maintains the internal pressure at an intermediate pressure. For this reason, the pressure of the bypass pipe 205b is kept constant, so that the refrigerant injected from the injection flow path 205 is stable and loss is small.
  • one of the two first injection holes 205a1 and the second injection hole 205a2 is always open to the first compression chamber 106a. Thereby, the flow of the injection refrigerant is not hindered, and the injection effect is enhanced.
  • the openings of the first injection hole 205a1 and the second injection hole 205a2 are preferably completely open. Since the first injection hole 205a1 or the second injection hole 205a2 is always completely opened, the injection effect is further enhanced. The same applies to the relationship between the third injection hole 205a3 and the fourth injection hole 205a4.
  • the pulsation of the refrigerant flowing backward from the first injection holes 205a1 and the second injection holes 205a2 is reflected by the first piston 105a.
  • refrigerant leakage from the first compression chamber 106a to the suction chamber can be suppressed.
  • the injection hole 205a1 the second injection hole 205a2, the third injection hole 205a3, and the fourth injection hole 205a4
  • the opening section of one injection hole is long, the flow rate of the injection refrigerant increases, and the injection effect increases.
  • the injection hole should be as far away from the center of the cylinder as possible.
  • the injection channel 205 is disposed outside the inner diameter of the cylinder, the injection flow path 205 is closed by the inner wall surface of the cylinder, and the injection effect is reduced.
  • the position where the outer periphery of the injection hole is most inscribed from the inner diameter of the cylinder is about 0.1 mm to 3 mm inside.
  • the distance between each injection hole and the center of the cylinder is substantially the same.
  • the common hole through which the two injection holes are communicated is formed in a linear shape displaced from the tangent to the inner diameter of the cylinder toward the center of the cylinder.
  • Both the first common hole 205f1 and the second common hole 205f2 in the first embodiment are linearly arranged to be shifted from the inner diameter of the cylinder toward the center of the cylinder, and the distance from the center of the cylinder is 16. 2 mm.
  • the injection hole and the center hole in the piston always have a non-communication relationship. This suppresses the flow of the high-pressure refrigerant from the injection flow path 205 into the central hole in the piston, and enhances the injection effect.
  • the inner diameter of the piston is 22 mm with respect to the outer diameter of 32 mm.
  • the inner diameter chamfer amount of the piston is 0.5 mm in the radial direction and 0.2 mm in the height direction.
  • the total area where the injection refrigerant opens to the compression chamber increases.
  • a larger flow rate of the injection refrigerant can flow into the compression chamber.
  • only one injection pipe is inserted into the compression chamber from the outside of the closed vessel 101 for one compression chamber.
  • a plurality of injection holes are provided in one compression chamber, but it is not necessary to provide a plurality of injection pipes. Thereby, the degree of freedom in designing the outside of the sealed container and the periphery of the compression mechanism can be improved.
  • the intersection of the injection hole and the common hole such as the first injection hole 205a1, the second injection hole 205a2, the third injection hole 205a3, and the fourth injection hole 205a4, is arranged inside the inner diameter of the cylinder.
  • one injection hole and one common hole intersect in a T-shape.
  • the hole corresponding to the vertical side of the T-shape may be either an injection hole or a common hole.
  • the one closer to the entrance of the common hole corresponds to the T-shaped vertical hole.
  • all the injection holes are arranged as T-shaped vertical holes.
  • the injection holes such as the first injection hole 205a1, the second injection hole 205a2, the third injection hole 205a3, and the fourth injection hole 205a4 may be circular or non-circular, for example, oval.
  • the injection hole is oval, it is desirable to arrange the long diameter side in the tangential direction of the inner diameter of the cylinder in order to secure the communication section.
  • the injection hole is circular.
  • the diameter of the plurality of injection holes may not be the same.
  • the distribution of the injection refrigerant in the compression chamber can be selectively changed. For example, since the diameter of the injection hole arranged in a phase closer to the vane 105a1 is large, the amount of the injection refrigerant for cooling the vane 105a1 increases, the thermal expansion of the vane 105a1 is suppressed, and the highly reliable twin rotary compressor 100 is provided. it can.
  • FIG. 8 is an explanatory diagram showing a visible cross section of the first injection hole 205a1 and the second injection hole 205a2 opened to the first compression chamber 106a according to the first modification of the first embodiment of the present invention.
  • the description of the same items as those in the above embodiment will be omitted, and only the characteristic portions will be described.
  • the injection refrigerant flows into the upper bearing 109a through the first injection pipe 205c.
  • the injection refrigerant pressure Pinj is an intermediate pressure between the suction pressure Ps and the discharge pressure Pd.
  • Ps 0.5 MPaG.
  • Pd 4.0 MPaG.
  • Pinj 1.5 MPaG.
  • the injection refrigerant flowing into the first cylinder 107a passes through the first common hole 205f1, and is injected into the first compression chamber 106a from the first injection hole 205a1 and the second injection hole 205a2.
  • the first injection hole 205a1 and the second injection hole 205a2 are arranged inside the inner diameter of the first cylinder 107a.
  • the inner diameter of the first cylinder 107a is 50 mm.
  • the hole diameter of the first common hole 205f1 is 3 mm.
  • the distance from the center of the first cylinder 107a to the center of the first injection hole 205a1 and the second injection hole 205a2 is 22.5 mm.
  • the outer diameter of the first piston 105a is 42 mm.
  • the inner diameter of the first piston 105a is 35 mm.
  • the diameter of the first injection hole 205a1 is 2 mm, and the first injection hole 205a1 is arranged at a phase of 270 °, which is the revolving direction of the first piston 105a in the counterclockwise direction, with the vane 105a1 as a reference of 0 °.
  • the second injection hole 205a2 has a hole diameter of 3 mm and is arranged in a phase of 280 °.
  • the mass of the refrigerant discharged from the twin rotary compressor 100 by the injection refrigerant increases, and the heating capacity of the refrigeration cycle device 200 improves. Further, since the injection refrigerant is lower in temperature than the discharged refrigerant, the sliding parts, for example, the vanes 105a1, are cooled to suppress thermal expansion, and the reliability of the twin rotary compressor 100 can be improved.
  • twin rotary compressor 100 includes electric motor 103 having stator 103a and rotor 103b.
  • the twin rotary compressor 100 has a first eccentric portion 104b and a second eccentric portion 104c provided on a main shaft 104a fixed to a rotor 103b, and includes a crankshaft 104 rotated by an electric motor 103.
  • the twin rotary compressor 100 includes a first piston 105a and a second piston provided on the first eccentric portion 104b and the second eccentric portion 104c.
  • a cylindrical through-hole 107a1 is formed, and the first eccentric portion 104b or the second eccentric portion 104c and the first piston 105a or the second piston are arranged in the through-hole 107a1 to form a first through-hole. It has a first cylinder 107a and a second cylinder 107b in which a compression chamber 106a or a second compression chamber is formed.
  • the twin rotary compressor 100 includes an injection flow path 205 for injecting an injection refrigerant into the first compression chamber 106a and the second compression chamber from the refrigerant pipe 204 in front of the evaporator 203 in the refrigerant flow direction of the refrigeration cycle circuit.
  • the twin rotary compressor 100 includes an upper bearing 109a, a lower bearing 109b, and an intermediate plate 110 as a partition for closing a through hole in the first cylinder 107a or the second cylinder.
  • the injection flow path 205 includes a plurality of first injection holes 205a1, a second injection hole 205a2, and a plurality of first injection holes 205 that inject an injection refrigerant from the upper bearing 109a, the lower bearing 109b, or the intermediate plate 110 into the first compression chamber 106a or the second compression chamber.
  • the third injection hole 205a3 and the fourth injection hole 205a4, and the first injection hole 205a1, the second injection hole 205a2, the third injection hole 205a3, and the fourth injection hole 205a2 are formed in the upper bearing 109a, the lower bearing 109b, or the intermediate plate 110. It has a first common hole 205f1 and a second common hole 205f2 communicating with the injection hole 205a4.
  • the opening area in which the injection refrigerant is injected into the first compression chamber 106a and the second compression chamber with a simple configuration increases.
  • the injection flow path 205 can always communicate with the first compression chamber 106a and the second compression chamber. Therefore, the injection refrigerant always flows into the first compression chamber 106a and the second compression chamber irrespective of the eccentric movement of the first piston 105a and the second piston.
  • the parts are constantly cooled and reliability can be improved.
  • At least one of the plurality of first injection holes 205a1, the second injection holes 205a2, the third injection holes 205a3, and the fourth injection holes 205a4 always has the first compression chamber 106a and the second injection holes 205a4. 2. Open the compression chamber.
  • the injection flow path 205 can always communicate with the first compression chamber 106a and the second compression chamber regardless of the eccentric movement of the first piston 105a and the second piston.
  • the plurality of first injection holes 205a1, the second injection holes 205a2, the third injection holes 205a3, and the fourth injection holes 205a4 are equidistant from the centers of the first cylinder 107a and the second cylinder 107b. Formed at the location.
  • the opening section of one injection hole becomes longer, the injection flow rate increases, and the injection effect further increases.
  • the plurality of first injection holes 205a1, the second injection holes 205a2, the third injection holes 205a3, and the fourth injection holes 205a4 are adjacent to the inner diameter boundaries of the first cylinder 107a and the second cylinder 107b. It is formed.
  • the opening section of one injection hole becomes longer, the injection flow rate increases, and the injection effect increases.
  • the plurality of first injection holes 205a1, the second injection holes 205a2, the third injection holes 205a3, and the fourth injection holes 205a4 are inscribed in inner diameter boundaries of the first cylinder 107a and the second cylinder 107b. It is formed.
  • the opening section of one injection hole is the longest, the injection flow rate is increased, and the injection effect is further enhanced.
  • the first common hole 205f1 and the second common hole 205f2 enter the center of the first cylinder 107a and the second cylinder 107b with respect to the tangent of the inner diameter of the first cylinder 107a and the second cylinder 107b. It is formed with.
  • the first common hole 205f1 and the second common hole 205f2 can communicate the plurality of injection holes with a simple structure.
  • all of the plurality of first injection holes 205a1, the second injection holes 205a2, the third injection holes 205a3, and the fourth injection holes 205a4 are the upper bearings 109a of the first piston 105a and the second piston,
  • the sliding surface 105a2 for the lower bearing 109b and the intermediate plate 110 is formed on the outer diameter side of the inner diameter boundary of the first piston 105a and the second piston.
  • the injection refrigerant does not leak into the center holes of the first piston 105a and the second piston, and the injection refrigerant is not wasted.
  • the first common hole 205f1 and the second common hole 205f2 are linear.
  • the processing is easy, and the injection channel 205 can be formed with a simple structure.
  • the first common hole 205f1 and the second common hole 205f2 need not be linear.
  • the first common hole 205f1 and the second common hole 205f2 may have a curved shape, a linear shape having a bent portion in the middle, or a meandering line shape.
  • one first common hole 205f1 and one second common hole 205f2 are provided for the upper bearing 109a, the lower bearing 109b, and the intermediate plate 110.
  • the number of processing steps is small, processing is easier, and the injection channel 205 can be formed with a simple structure.
  • the partition in which the common hole and the plurality of injection holes are formed is the upper bearing 109a or the lower bearing 109b that covers the end surface of the first cylinder 107a or the second cylinder 107b.
  • the opening area in which the injection refrigerant is injected into the first compression chamber 106a and the second compression chamber with a simple configuration increases. Further, the injection flow path 205 can always communicate with the first compression chamber 106a and the second compression chamber.
  • the refrigeration cycle apparatus 200 includes the twin rotary compressor 100 described above.
  • the injection refrigerant always flows into the first compression chamber 106a and the second compression chamber regardless of the eccentric motion of the first piston 105a and the second piston.
  • the amount of refrigerant discharged is increased to obtain an injection effect, and the sliding parts are constantly cooled, so that the reliability can be improved.
  • the refrigeration cycle apparatus 200 has the control valve 208 that controls the flow rate of the injection refrigerant in the injection flow path 205 on the upstream side of the twin rotary compressor 100 in the injection refrigerant flow direction.
  • control valve 208 adjusts the flow rate of the injection refrigerant, and an optimal injection effect can be obtained.
  • FIG. 9 is an explanatory diagram showing a vertical cross section of a compression mechanism of the twin rotary compressor 100 according to Embodiment 2 of the present invention.
  • FIG. 10 shows an intermediate plate 110 having a first common hole 205f1, a first injection hole 205a1, a second injection hole 205a2, a third injection hole 205a3, and a fourth injection hole 205a4 according to Embodiment 2 of the present invention. It is explanatory drawing which shows the cross section of FIG. In the second embodiment, the description of the same items as those in the above embodiment will be omitted, and only the characteristic portions will be described.
  • the injection channel 205 may be provided in the intermediate plate 110. That is, one first common hole 205f1, the first injection hole 205a1, the second injection hole 205a2, the third injection hole 205a3, and the fourth injection hole 205a4 are formed in the intermediate plate 110 as a partition. Since the intermediate plate 110 is disposed between the first cylinder 107a and the second cylinder 107b, a pair of the first injection hole 205a1 and the second injection hole 205a2 and the third injection hole 205a3 and the fourth injection hole 205a4 The pair is communicated with one first common hole 205f1. In addition, by configuring the intersection of the first common hole 205f1 and each injection hole in a cross shape, the injection flow path 205 can be formed with a simpler configuration. In the second embodiment, all intersections are formed in a cross shape.
  • FIG. 11 shows a first common hole 205f1, a second common hole 205f2, a first injection hole 205a1, a second injection hole 205a2, a third injection hole 205a3, and a fourth injection according to Modification 2 of Embodiment 2 of the present invention. It is explanatory drawing which shows the cross section of the intermediate
  • the intermediate plate 110 is disposed between the first cylinder 107a and the second cylinder 107b, the intermediate plate 110 is located between the first injection hole 205a1, the second injection hole 205a2, and the first common hole 205f1.
  • Each of the set and the set of the third injection hole 205a3, the fourth injection hole 205a4, and the second common hole 205f2 is formed in one intermediate plate 110. Since each injection hole and each common hole are formed in one intermediate plate 110, the injection flow path 205 can be formed with a simpler configuration.
  • Embodiment 2 the first eccentric portion 104b and the second eccentric portion 104c, the first piston 105a and the second piston, and the two first cylinders 107a and the second cylinder 107b are provided. ing.
  • the partition having the common hole and the injection hole formed therein is the intermediate plate 110 disposed between the two first cylinders 107a and the second cylinder 107b.
  • the injection channel 205 can be formed with a simpler configuration.
  • the common hole formed in intermediate plate 110 has a plurality of injection holes that inject injection refrigerant into first compression chamber 106a and second compression chamber in two first cylinder 107a and second cylinder 107b.
  • the first injection hole 205a1, the second injection hole 205a2, the third injection hole 205a3, and the fourth injection hole 205a4 are commonly connected.
  • the number of processing steps is smaller, and the injection flow path 205 can be formed with a simpler configuration.
  • FIG. 12 is an explanatory diagram showing a visible cross section of the first injection hole 205a1 and the second injection hole 205a2 opened in the first compression chamber 106a according to Embodiment 3 of the present invention.
  • the description of the same items as those in the above embodiment will be omitted, and only the characteristic portions will be described.
  • the inner diameter of the first cylinder 107a is 60 mm.
  • the outer diameter of the first piston 105a is 44 mm.
  • Two first injection holes 205a1 and second injection holes 205a2 are provided.
  • the diameter of each of the first injection hole 205a1 and the second injection hole 205a2 is 2 mm.
  • the distance from the center of the first cylinder 107a to the center of each of the first injection hole 205a1 and the second injection hole 205a2 is 26 mm.
  • the phase of the first injection hole 205a1 is 30 ° counterclockwise on the basis that the vane 105a1 is 0 °.
  • the phase of the second injection hole 205a2 is 330 ° counterclockwise on the basis that the vane 105a1 is 0 °.
  • the angle of the suction hole 107a2 into which the non-injection refrigerant flows is 30 °.
  • the diameter of the suction hole 107a2 is 10 mm.
  • the length of the suction hole 107a2 penetrating the first cylinder 107a is 20 mm.
  • the injection refrigerant pressure Pinj is an intermediate pressure between the suction pressure Ps and the discharge pressure Pd.
  • Ps 0.5 MPaG.
  • Pd 4.0 MPaG.
  • Pinj 1.5 MPaG.
  • the opening section of the first injection hole 205a1 is -345 ° to -75 °. That is, the first injection hole 205a1 is opened before 15 ° which is the phase in which the first piston 105a passes through the suction hole 107a2 to form the first compression chamber 106a. Also, the phase at which the internal pressure of the first compression chamber 106a becomes higher than the injection refrigerant pressure differs depending on the operating conditions, but the ratio of the absolute pressure between the discharged refrigerant and the suction refrigerant, which is the general heating operation condition of the twin rotary compressor, is used.
  • the internal pressure of the first compression chamber 106a becomes higher than the injection refrigerant pressure in a region where the rotation axis phase is 130 ° or more.
  • the first injection hole 205a1 of the third embodiment does not open in a region where the internal pressure of the first compression chamber 106a is higher than the injection refrigerant pressure and the rotation axis phase is 130 ° or more.
  • the first injection hole 205a1 communicates with the suction hole 107a2 in a part of the section.
  • the opening section of the second injection hole 205a2 is 75 ° to 345 °. That is, the second injection hole 205a2 opens after 15 °, which is the phase in which the first piston 105a passes through the suction hole 107a2, to form the first compression chamber 106a. Further, it is open in a region where the internal pressure of the first compression chamber 106a is higher than the injection refrigerant pressure.
  • the second injection hole 205a2 does not always communicate with the suction hole 107a2 for introducing the refrigerant from the refrigeration cycle circuit of the first cylinder 107a into the first compression chamber 106a.
  • the injection refrigerant hinders the suction of the suction refrigerant from the main circuit of the refrigeration cycle circuit, and the discharge refrigerant amount decreases. I do. Thereby, the heating capacity is reduced, and the injection effect is reduced. For this reason, it is desirable to avoid such a state. This is called constraint A.
  • the position of the injection hole needs to be close to the center of the first cylinder 107a, and the diameter of the injection hole needs to be small. In that case, the injection flow path 205 becomes narrow, and the injection effect is reduced.
  • all the first injection holes 205a1 and the second injection holes 205a2 do not satisfy the restrictions A and B, and one injection hole satisfies only one restriction.
  • the opening section of the first injection hole 205a1 satisfies the constraint A but does not satisfy the constraint B.
  • the opening section of the second injection hole 205a2 satisfies the constraint B but does not satisfy the constraint A.
  • the number of injection holes to be opened is selectively reduced in the section where the injection effect is reduced.
  • maximizing the opening section length of the injection hole means making the injection hole as close as possible to the inner wall surface of the first cylinder.
  • the opening sections of the two injection holes are not common.
  • the opening sections of the two injection holes may be shared. That is, the rotation angle at which the first piston 105a closes the suction hole 107a2 is ⁇ .
  • the rotation angle at which the internal pressure of the first compression chamber 106a becomes higher than the injection refrigerant pressure is denoted by ⁇ .
  • the opening section of the first injection hole 205a1 is defined as ⁇ As to ⁇ Ae.
  • the opening section of the second injection hole 205a2 is defined as ⁇ Bs to ⁇ Be. At this time, the relationship may be such that ⁇ As ⁇ ⁇ Bs ⁇ Ae ⁇ ⁇ Be.
  • the numerical aperture of the two injection holes becomes one at a phase less than ⁇ or greater than ⁇ at which the injection effect is reduced. Further, the numerical apertures of the two injection holes are two in a phase not less than ⁇ and not more than ⁇ in which the injection effect is not reduced. Therefore, the injection effect is further enhanced.
  • At least one of the plurality of first injection holes 205a1, second injection holes 205a2, third injection holes 205a3, and fourth injection holes 205a4 is connected to the first compression chamber 106a and the second compression holes 106a. It always closes in a section where the internal pressure of the compression chamber is higher than the injection pressure of the injection flow path 205. At least one of the plurality of first injection holes 205a1, second injection holes 205a2, third injection holes 205a3, and fourth injection holes 205a4 has an internal pressure of the first compression chamber 106a and the second compression chamber that is injected. It opens in a part of the section of the flow path 205 higher than the injection pressure.
  • the injection refrigerant hinders the suction of the suction refrigerant from the main circuit of the refrigeration cycle circuit, The amount of refrigerant discharged decreases. Thereby, the heating capacity is reduced, and the injection effect is reduced. For this reason, it is desirable that the first injection hole 205a1 be prevented from opening before the phase forming the first compression chamber 106a. This is called constraint A.
  • the opening section of one first injection hole 205a1 satisfies the constraint A, but does not satisfy the constraint B.
  • the opening section of the other second injection hole 205a2 satisfies the constraint B, but does not satisfy the constraint A. Thereby, in the section where the injection effect is reduced, the number of opened injection holes can be selectively reduced. Therefore, a decrease in the injection effect can be suppressed.
  • the relationship between the first injection hole 205a1 and the second injection hole 205a2 is the same as the relationship between the third injection hole 205a3 and the fourth injection hole 205a4.
  • At least one of the plurality of first injection holes 205a1, the second injection holes 205a2, the third injection holes 205a3, and the fourth injection holes 205a4 includes the first cylinder 107a and the second cylinder
  • the refrigerant from the refrigerating cycle circuit 107b does not always communicate with the suction hole 107a2 for introducing the refrigerant into the first compression chamber 106a and the second compression chamber.
  • At least one other of the plurality of first injection holes 205a1, second injection holes 205a2, third injection holes 205a3, and fourth injection holes 205a4 communicates with the suction hole 107a2 in some sections.
  • FIG. 13 is an explanatory diagram showing a cross section in which an injection hole 205a opened to the first compression chamber 106a according to Embodiment 4 of the present invention can be seen.
  • the description of the same items as those in the above embodiment will be omitted, and only the characteristic portions will be described.
  • three or more injection holes 205a may be provided.
  • n injection holes 205a may be provided, and n-1 or less common holes 205f may be provided to communicate the n injection holes 205a.
  • the phases of the three injection holes 205a are at respective positions of 270 °, 225 °, and 180 ° in a counterclockwise direction with the vane 105a1 set to 0 °.
  • the two common holes 205f intersect.
  • One end of one common hole 205f communicates upstream in the injection refrigerant flow direction of the injection flow path 205, and the other end of one common hole 205f is closed.
  • Both ends of the other common hole 205f are closed.
  • the other end of the other common hole 205f is open on the side surface of the upper bearing 109a during processing, and thus is covered with the lid member 109a1.
  • One of the three injection holes 205a is formed at a position where two common holes 205f intersect.
  • two injection holes 205a are respectively formed in the two common holes 205f.
  • One injection hole 205a formed at a position where the two common holes 205f intersect is near the connection portion with the upstream side of the injection flow path 205, and more injection is performed in a section requiring the most injection refrigerant amount. Refrigerant can be injected.
  • a plurality of first common holes 205f1 and second common holes 205f2 are provided for upper bearing 109a, lower bearing 109b, and intermediate plate 110. There are three or more injection holes for one compression chamber. The plurality of first common holes 205f1 and second common holes 205f2 intersect.
  • the injection flow path 205 can always communicate with the first compression chamber 106a and the second compression chamber.
  • one end of one common hole among the plurality of common holes communicates upstream in the injection refrigerant flow direction of the injection flow path 205 and the other end of one common hole is It is closed. Both ends of another common hole among the plurality of common holes are closed.
  • the injection flow path 205 can be simplified, and the injection flow path 205 can be formed with a simple structure.
  • At least one of the plurality of injection holes is formed at a position where the plurality of common holes intersect.
  • Embodiments 1 to 4 of the present invention may be combined or applied to other parts.
  • the twin rotary compressor has been described as an example.
  • the present invention may be applied to other rotary compressors such as a single rotary compressor.
  • 100 twin rotary compressor 101 closed container, 101a cylindrical member, 101b101 upper end closing member, 101c lower end closing member, 102 pedestal, 103 motor, 103a stator, 103b rotor, 104 crankshaft, 104a main shaft, 104b first bias Core part, 104c ⁇ second eccentric part, 104d ⁇ countershaft, 105a ⁇ first piston, 105a1 ⁇ vane, 105a2 ⁇ sliding surface, 105a3 ⁇ R processing, 106a ⁇ first compression chamber, 107a ⁇ first cylinder, 107a1 ⁇ through hole, 107a2 ⁇ suction hole, 107a3 discharge hole, 107b second cylinder, 108a first inflow refrigerant pipe, 108b second inflow refrigerant pipe, 109a upper bearing, 109a1 cover member, 109b lower bearing, 110 intermediate plate, 112 discharge pipe, 113 intake muffler, 20 Refrigeration cycle device, 201 condenser, 202 expansion valve, 203 evaporator

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  • Applications Or Details Of Rotary Compressors (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
PCT/JP2018/029523 2018-08-07 2018-08-07 ロータリー圧縮機及び冷凍サイクル装置 Ceased WO2020031248A1 (ja)

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CZ202140A CZ309303B6 (cs) 2018-08-07 2018-08-07 Rotační kompresor a zařízení chladicího cyklu
JP2020535360A JP7003272B2 (ja) 2018-08-07 2018-08-07 ロータリー圧縮機及び冷凍サイクル装置
PCT/JP2018/029523 WO2020031248A1 (ja) 2018-08-07 2018-08-07 ロータリー圧縮機及び冷凍サイクル装置
KR1020217002894A KR102449302B1 (ko) 2018-08-07 2018-08-07 로터리 압축기 및 냉동 사이클 장치
CN201880095841.1A CN112513466B (zh) 2018-08-07 2018-08-07 旋转式压缩机和制冷循环装置

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CN113530821A (zh) * 2021-08-04 2021-10-22 珠海凌达压缩机有限公司 一种单级补气结构及包含其的双缸压缩机
CN115917154A (zh) * 2020-07-06 2023-04-04 三菱电机株式会社 旋转式压缩机
WO2024029566A1 (ja) 2022-08-04 2024-02-08 三菱重工サーマルシステムズ株式会社 ロータリー圧縮機
US11971038B2 (en) * 2020-03-31 2024-04-30 Gree Electric Appliances, Inc. Of Zhuhai Single-stage enthalpy enhancing rotary compressor and air conditioner having same

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KR102103362B1 (ko) * 2013-11-11 2020-04-22 엘지전자 주식회사 스크롤 압축기 및 이를 포함하는 공기조화기
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JPS63150096U (cs) * 1987-03-24 1988-10-03
JP2018076796A (ja) * 2016-11-08 2018-05-17 株式会社富士通ゼネラル ロータリ圧縮機

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11971038B2 (en) * 2020-03-31 2024-04-30 Gree Electric Appliances, Inc. Of Zhuhai Single-stage enthalpy enhancing rotary compressor and air conditioner having same
CN115917154A (zh) * 2020-07-06 2023-04-04 三菱电机株式会社 旋转式压缩机
CN113530821A (zh) * 2021-08-04 2021-10-22 珠海凌达压缩机有限公司 一种单级补气结构及包含其的双缸压缩机
WO2024029566A1 (ja) 2022-08-04 2024-02-08 三菱重工サーマルシステムズ株式会社 ロータリー圧縮機

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CZ202140A3 (cs) 2021-03-03
CZ309303B6 (cs) 2022-08-10
KR20210024153A (ko) 2021-03-04
CN112513466B (zh) 2022-11-04
JPWO2020031248A1 (ja) 2021-05-13
CN112513466A (zh) 2021-03-16
JP7003272B2 (ja) 2022-01-20

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