US20250109748A1 - Hermetic compressor and refrigeration cycle apparatus - Google Patents

Hermetic compressor and refrigeration cycle apparatus Download PDF

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Publication number
US20250109748A1
US20250109748A1 US18/833,270 US202218833270A US2025109748A1 US 20250109748 A1 US20250109748 A1 US 20250109748A1 US 202218833270 A US202218833270 A US 202218833270A US 2025109748 A1 US2025109748 A1 US 2025109748A1
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United States
Prior art keywords
cylinder
tubular portion
hermetic compressor
outer circumferential
circumferential surface
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US18/833,270
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English (en)
Inventor
Takuma TSUKAMOTO
Tomohiro IYANAGI
Hiroki Nagasawa
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: IYANAGI, Tomohiro, NAGASAWA, HIROKI, TSUKAMOTO, TAKUMA
Publication of US20250109748A1 publication Critical patent/US20250109748A1/en
Pending 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
    • F04C23/008—Hermetic pumps
    • 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
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C2240/806—Pipes for fluids; Fittings therefor
    • 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
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/101—Geometry of the inlet or outlet of the inlet

Definitions

  • the present disclosure relates to a hermetic compressor including a compression mechanism and to a refrigeration cycle apparatus.
  • a compression mechanism and an electric motor that drives the compression mechanism are accommodated in a hermetic container, and the compression mechanism has a cylinder having a suction hole into which a suction pipe is press-fitted (see, for example, Patent Literature 1).
  • the present disclosure is applied to solve the above problem, and relates to a hermetic compressor and a refrigeration cycle apparatus that can reduce the likelihood that a cylinder will be distorted in a circumferential direction as a whole.
  • a hermetic compressor includes a compression mechanism in a hermetic container.
  • the compression mechanism is driven by an electric motor through a rotation shaft, and includes a cylinder including a cylinder chamber having a cylindrical shape.
  • the cylinder has a cylinder suction hole that extends in a radial direction of the cylinder and that allows fluid to be sucked into the cylinder chamber.
  • a cylindrical groove is formed in such a manner as to surround the cylinder suction hole. Between the cylinder suction hole and the cylindrical groove, a cylinder tubular portion is provided.
  • a suction pipe or a connecting pipe provided at one end of the suction pipe is connected, the suction pipe being a pipe through which the fluid is guided from outside of the hermetic container to the cylinder chamber.
  • a refrigeration cycle apparatus includes: the above hermetic compressor; an outdoor-side heat exchanger; a pressure reducing device; and an indoor-side heat exchanger.
  • the cylindrical groove is formed in such a manner as to surround the cylinder suction hole.
  • the cylinder tubular portion is provided between the cylinder suction hole and the cylindrical groove.
  • the suction pipe or the connecting pipe is connected to the outer circumferential surface of the cylinder tubular portion. It is therefore possible to reduce occurrence of distortion of the cylinder in the circumferential direction as a whole, since the cylinder suction hole is not expanded when the suction pipe or the connecting pipe is connected to the cylinder tubular portion.
  • FIG. 1 is a vertical sectional schematic view of a hermetic compressor according to Embodiment 1.
  • FIG. 2 is a cross-sectional schematic view of a compression mechanism as the hermetic compressor as illustrated in FIG. 1 is viewed in a direction indicated by arrows A and A′; that is, a cross-sectional schematic view of the compression mechanism that is taken along line A-A′.
  • FIG. 3 is a cross-sectional schematic view of an electric motor 30 as the hermetic compressor 100 as illustrated in FIG. 1 is viewed in a direction indicated by arrows B and B′, that is, a cross-section schematic view of the electric motor that is taken along line B-B′.
  • FIG. 4 is a schematic configuration diagram of a refrigeration cycle apparatus including the hermetic compressor according to Embodiment 1.
  • FIG. 5 is a cross-sectional schematic diagram illustrating a cylinder suction hole and surroundings thereof in a cylinder of the hermetic compressor according to Embodiment 1.
  • FIG. 6 is a schematic diagram illustrating the cylinder suction hole and surroundings thereof in the cylinder of the hermetic compressor according to Embodiment 1 as viewed from the front.
  • FIG. 7 is a vertical sectional schematic diagram illustrating the cylinder suction hole and surroundings thereof in the cylinder of the hermetic compressor according to Embodiment 1 when viewed side-on.
  • FIG. 8 is a cross-sectional schematic diagram illustrating a cylinder suction hole and surroundings thereof in a cylinder of an existing hermetic compressor.
  • FIG. 9 is a schematic diagram illustrating a cylinder suction hole and surroundings thereof in a cylinder of a hermetic compressor according to Embodiment 2 as viewed from the front.
  • FIG. 10 is a schematic diagram illustrating a cylinder suction hole and surroundings thereof in a cylinder of a hermetic compressor according to Embodiment 3 as viewed from the front.
  • FIG. 11 is a schematic diagram illustrating a cylinder suction hole and surroundings thereof in a cylinder of a hermetic compressor according to Embodiment 4 as viewed from the front.
  • FIG. 12 is a schematic diagram illustrating a cylinder suction hole and surroundings thereof in a cylinder of a hermetic compressor according to Embodiment 5 as viewed from the front.
  • FIG. 13 is a schematic diagram illustrating a cylinder suction hole and surroundings thereof in a cylinder of a hermetic compressor according to Embodiment 6 as viewed from the front.
  • FIG. 14 is a vertical sectional schematic diagram illustrating a cylinder suction hole and surroundings thereof in a cylinder of a hermetic compressor according to Embodiment 7 as viewed side-on.
  • FIG. 1 is a sectional view of a hermetic compressor 100 according to Embodiment 1.
  • FIG. 2 is a cross-sectional schematic view of a compression mechanism 20 as the hermetic compressor 100 as illustrated in FIG. 1 is viewed in a direction indicated by arrows A and A′; that is, a cross-sectional schematic view of the compression mechanism 20 that is taken along line A-A′.
  • the overall configuration of the hermetic compressor 100 according to Embodiment 1 will be described below with reference to FIGS. 1 and 2 .
  • the hermetic compressor 100 for example, a single-cylinder rotary compressor having a single cylinder 23 as illustrated in FIG. 1 , that is, a single rotary compressor, is used.
  • the hermetic compressor 100 is not limited to the single rotary compressor, and may be a rotary compressor having a plurality of cylinders 23 , for example, a twin rotary compressor having two cylinders 23 .
  • the hermetic compressor 100 includes a compression mechanism 20 and an electric motor 30 in a hermetic container 10 .
  • the compression mechanism 20 compresses refrigerant gas, and the electric motor 30 drives the compression mechanism 20 .
  • the hermetic container 10 is made up of an upper container 11 and a lower container 12 .
  • the compression mechanism 20 is located in a lower portion of the hermetic container 10
  • the electric motor 30 is located in an upper portion of the hermetic container 10 .
  • the compression mechanism 20 and the electric motor 30 are connected by a rotation shaft 21 .
  • the rotation shaft 21 transmits rotational motion of the electric motor 30 to the compression mechanism 20 .
  • refrigerant gas is compressed by the transmitted rotational force, and the compressed refrigerant gas is discharged into the hermetic container 10 .
  • the interior of the hermetic container 10 is filled with the compressed refrigerant gas, that is, high-temperature and high-pressure refrigerant gas.
  • refrigerating machine oil is stored as oil for lubricating the compression mechanism 20 .
  • an oil pump (not illustrated) is provided at a lower portion of the rotation shaft 21 .
  • the oil pump pumps up the refrigerating machine oil stored in the bottom portion of the hermetic container 10 as the rotation shaft 21 rotates, and supplies the refrigerating machine oil to sliding parts of the compression mechanism 20 , thereby ensuring a mechanical lubricating action of the compression mechanism 20 .
  • the rotation shaft 21 includes a main shaft portion 21 a, an eccentric shaft portion 21 b, and a sub-shaft portion 21 c.
  • the main shaft portion 21 a, the eccentric shaft portion 21 b, and the sub-shaft portion 21 c are formed in this order from the upper side in the axial direction.
  • the electric motor 30 is fixed to the main shaft portion 21 a by shrink fit or press fit.
  • a cylindrical rolling piston 22 is slidably fitted to the eccentric shaft portion 21 b.
  • the compression mechanism 20 includes a cylinder 23 , the rolling piston 22 , an upper bearing 24 , a lower bearing 25 , and a vane 26 (see FIG. 2 ).
  • a cylindrical space that is, a cylinder chamber 23 a
  • the cylinder chamber 23 a may have a substantially cylindrical space.
  • the cylinder chamber 23 a accommodates the eccentric shaft portion 21 b of the rotation shaft 21 , the rolling piston 22 , and the vane 26 .
  • the eccentric shaft portion 21 b is eccentrically moved in the cylinder chamber 23 a.
  • the rolling piston 22 is fitted to the eccentric shaft portion 21 b.
  • the vane 26 partitions a space formed by an inner circumferential surface of the cylinder chamber 23 a and an outer circumferential surface of the rolling piston 22 .
  • a vane groove 23 c formed to extend in a radial direction of the cylinder 23 extends through the cylinder 23 in the axial direction.
  • One of ends of the vane groove 23 c in the radial direction is opened in the cylinder chamber 23 a and the other end is opened in a back pressure chamber 23 b.
  • the vane 26 is accommodated in the vane groove 23 c.
  • the vane 26 is moved back and forth in the radial direction in the vane groove 23 c.
  • the vane 26 has a flat shape, that is, a substantially cuboid shape such that its thickness in the circumferential direction is smaller than its length in the radial direction and its length in the axial direction.
  • a vane spring (not illustrated) is provided in part of the vane groove 23 c that is located in the back pressure chamber 23 b.
  • a vane spring (not illustrated) is provided in part of the vane groove 23 c that is located in the back pressure chamber 23 b.
  • high-pressure refrigerant gas in the hermetic container 10 flows into the back pressure chamber 23 b, and a differential pressure between a refrigerant-gas pressure in the back pressure chamber 23 b and a refrigerant-gas pressure in the cylinder chamber 23 a produces a force to move the vane 26 in the radial direction toward the center of the cylinder chamber 23 a.
  • the vane 26 is moved in the radial direction toward the center of the cylinder chamber 23 a by both the force produced due to the differential pressure between the back pressure chamber 23 b and the cylinder chamber 23 a and a pressing force of the vane spring in the radial direction.
  • the force to move the vane 26 in the radial direction brings one end of the vane 26 that adjoins the cylinder chamber 23 a into contact with a cylindrical outer circumferential surface of the rolling piston 22 . It is therefore possible to partition the space defined by the inner circumferential surface of the cylinder 23 and the outer circumferential surface of the rolling piston 22 into a suction-side space and a compression-side space.
  • the upper bearing 24 is formed in a substantially inverse T-shape as viewed side-on, and is fitted to the main shaft portion 21 a of the rotation shaft 21 to support the main shaft portion 21 a such that the main shaft portion 21 a is rotatable.
  • the upper bearing 24 is in contact with the cylinder 23 and closes an upper-side opening of the cylinder chamber 23 a in the axial direction.
  • the lower bearing 25 is formed in a substantially T-shape as viewed side-on, and is fitted to the sub-shaft portion 21 c of the rotation shaft 21 to support the sub-shaft portion 21 c such that the sub-shaft portion 21 c is rotatable.
  • the lower bearing 25 is in contact with the cylinder 23 and closes a lower-side opening of the cylinder chamber 23 a in the axial direction.
  • a suction port (not illustrated) is provided that allows refrigerant gas corresponding to low-pressure fluid to be sucked into the cylinder chamber 23 a from the outside of the hermetic container 10 .
  • the upper bearing 24 has a discharge port (not illustrated) that allows compressed refrigerant gas to be discharged to the outside of the cylinder chamber 23 a.
  • a discharge valve (not illustrated) is provided.
  • the discharge valve controls the timing at which high-temperature and high-pressure refrigerant gas is discharged from the cylinder 23 through the discharge port. That is, the discharge valve is kept closed until refrigerant gas compressed in the cylinder chamber 23 a of the cylinder 23 reaches a predetermined pressure. When the refrigerant gas reaches the predetermined pressure or higher, the discharge valve is opened and as a result, the high-temperature and high-pressure refrigerant gas is discharged from the cylinder chamber 23 a to the outside of the cylinder chamber 23 a.
  • the discharge valve also prevents backflow of the refrigerant gas after the refrigerant gas is discharged.
  • a discharge muffler 27 is attached to an outer side of the upper bearing 24 , that is, part of the upper bearing 24 that is closer to the electric motor 30 than other part of the upper bearing 24 , such that the discharge muffler 27 covers the upper bearing 24 .
  • the discharge muffler 27 has a discharge hole (not illustrated) through which a space defined by the discharge muffler 27 and the upper bearing 24 communicates with the interior of the hermetic container 10 . Refrigerant gas discharged from the cylinder 23 through the discharge port is once discharged to the space defined by the discharge muffler 27 and the upper bearing 24 , and is thereafter discharged from the discharge hole into the hermetic container 10 .
  • a suction muffler 101 is provided to reduce the likelihood that liquid refrigerant will be directly sucked into the cylinder chamber 23 a of the cylinder 23 .
  • low-pressure refrigerant gas and liquid refrigerant are mixedly sent to the hermetic compressor 100 . If the liquid refrigerant flows into the cylinder 23 and is compressed in the compression mechanism 20 , a failure occurs in the compression mechanism 20 .
  • the suction muffler 101 the refrigerant gas and the liquid refrigerant are separated from each other, and only the refrigerant gas is sent to the cylinder chamber 23 a.
  • the suction muffler 101 is connected to the suction port of the cylinder 23 by a suction pipe 51 and a connecting pipe 52 provided at one end of the suction pipe 51 .
  • Low-pressure refrigerant gas sent from the suction muffler 101 is sucked into the cylinder chamber 23 a through the suction pipe 51 and the connecting pipe 52 . That is, the suction pipe 51 and the connecting pipe 52 guide the low-pressure refrigerant gas from the outside of the hermetic container 10 to the cylinder chamber 23 a.
  • the compression mechanism 20 has the above configuration, and the eccentric shaft portion 21 b of the rotation shaft 21 is rotated in the cylinder chamber 23 a of the cylinder 23 by the rotational motion of the rotation shaft 21 .
  • An operating chamber is defined by the inner circumferential surface of the cylinder chamber 23 a, the outer circumferential surface of the rolling piston 22 fitted to the eccentric shaft portion 21 b, and the vane 26 , and the volume of the operating chamber increases or decreases as the rotation shaft 21 rotates.
  • the operating chamber communicates with the suction port, and low-pressure refrigerant gas is then sucked into this operating chamber.
  • the operating chamber is blocked so as not to communicate with the suction port, and as the volume of the operating chamber decreases, refrigerant gas in the operating chamber is compressed.
  • the operating chamber communicates with the discharge port, and after the refrigerant gas in the operating chamber reaches a predetermined pressure, the discharge valve provided at the discharge port is opened, whereby the refrigerant gas compressed to a high-pressure and high-temperature state is discharged to the outside of the operating chamber, that is, the high-pressure and high-temperature refrigerant gas is discharged to the outside of the cylinder chamber 23 a.
  • the high-pressure and high-temperature refrigerant gas discharged from the cylinder chamber 23 a into the hermetic container 10 through the discharge muffler 27 passes through the electric motor 30 , then flows up in the hermetic container 10 , and is discharged to the outside of the hermetic container 10 from a discharge pipe 102 provided at the top of the hermetic container 10 .
  • a refrigerant circuit in which refrigerant flows is formed outside the hermetic container 10 .
  • the discharged refrigerant circulates in the refrigerant circuit and flows back to the suction muffler 101 .
  • FIG. 3 is a cross-sectional schematic view of the electric motor 30 as the hermetic compressor 100 as illustrated in FIG. 1 is viewed in a direction indicated by arrows B and B′, that is, a cross-section schematic view of the electric motor 30 that is taken along line B-B′.
  • the electric motor 30 includes a substantially cylindrical stator 41 fixed to the inner circumferential surface of the hermetic container 10 and a substantially columnar rotor 31 located inward of the stator 41 .
  • the rotor 31 includes a rotor iron core 32 formed by laminating iron core sheets obtained by stamping out a thin electromagnetic steel sheet.
  • the rotor 31 is a rotor using permanent magnets as in, for example, a blushless DC motor or a rotor using secondary windings as in an induction motor.
  • magnet insertion holes 33 are provided in the axial direction of the rotor iron core 32 .
  • permanent magnets 34 such as ferrite magnets or rare-earth magnets are inserted.
  • the permanent magnets 34 produces magnetic poles on the rotor 31 . With an action of magnetic fluxes produced by the magnetic poles on the rotor 31 and magnetic fluxes produced by stator windings 44 on the stator 41 , the rotor 31 is rotated.
  • secondary windings are provided at the rotor iron core 32 , instead of the permanent magnets.
  • the stator windings 44 at the stator 41 induce the magnetic fluxes to rotor-side secondary windings provided on a rotor side to produce a rotational force that causes the rotor 31 to rotate.
  • a shaft hole (not illustrated) is provided through which the rotation shaft 21 extends.
  • the main shaft portion 21 a of the rotation shaft 21 is fastened to the rotor iron core 32 by, for example, shrink fit, whereby rotational motion of the rotor 31 is transmitted to the rotation shaft 21 .
  • air holes 35 are provided around the shaft hole. High-pressure and high-temperature refrigerant compressed by the compression mechanism 20 located below the electric motor 30 passes through the air holes 35 . It should be noted that the refrigerant compressed by the compression mechanism 20 also passes through an air gap between the rotor 31 and the stator 41 and gaps between the stator windings 44 , in addition to the air holes 35 .
  • FIG. 4 is a schematic configuration diagram of a refrigeration cycle apparatus 200 including the hermetic compressor 100 .
  • the refrigeration cycle apparatus 200 is, for example, an air-conditioning apparatus.
  • the refrigeration cycle apparatus 200 includes the hermetic compressor 100 including the suction muffler 101 connected to the suction side of the hermetic compressor 100 , a flow switching valve 103 connected to the discharge side of the hermetic compressor 100 , an outdoor-side heat exchanger 104 , a pressure reducing device 105 , and an indoor-side heat exchanger 106 , and these components are sequentially connected by pipes, whereby a refrigerant circuit is formed in which refrigerant circulates.
  • an R407C refrigerant, an R410A refrigerant, an R32 refrigerant, or other kind of refrigerant is used as the refrigerant that circulates in the refrigerant circuit.
  • the indoor-side heat exchanger 106 is mounted in a device provided indoors, while the hermetic compressor 100 , the flow switching valve 103 , the outdoor-side heat exchanger 104 , and the pressure reducing device 105 are mounted in a device located outdoors.
  • the flow switching valve 103 is, for example, a four-way valve, and configured to switch the flow direction of the refrigerant between plural flow directions to switch the operation between a cooling operation and a heating operation. It should be noted that, in place of the four-way valve, for example, a combination of two-way valves or a combination of three-way valves may be used as the flow switching valve 103 .
  • the pressure reducing device 105 is configured to reduce the pressure of refrigerant to expand the refrigerant.
  • the pressure reducing device 105 is, for example, an electronic expansion valve whose opening degree can be adjusted.
  • the pressure reducing device 105 is adjusted in opening degree to control the pressure of refrigerant that flows into the indoor-side heat exchanger 106 in the cooling operation and to control the pressure of refrigerant that flows into the outdoor-side heat exchanger 104 in the heating operation.
  • the outdoor-side heat exchanger 104 serves as an evaporator or a condenser, and causes heat exchange to be performed between air and the refrigerant to evaporate and gasify the refrigerant or condense and liquefy the refrigerant.
  • the outdoor-side heat exchanger 104 serves as an evaporator in the heating operation, and serves as a condenser in the cooling operation.
  • the indoor-side heat exchanger 106 serves as an evaporator or a condenser, and causes heat exchange to be performed between air and the refrigerant to evaporate and gasify the refrigerant or condense and liquefy the refrigerant.
  • the indoor-side heat exchanger 106 serves as a condenser in the heating operation, and serves as an evaporator in the cooling operation.
  • the flow switching valve 103 is connected to the indoor-side heat exchanger 106 as indicated by solid lines in FIG. 4 .
  • High-temperature and high-pressure refrigerant obtained by compression by the hermetic compressor 100 flows to the indoor-side heat exchanger 106 and condenses and liquefies. Thereafter, the refrigerant that has liquefied is reduced in pressure by the pressure reducing device 105 to change into low-temperature and low-pressure two-phase refrigerant, and the low-temperature low-pressure two-phase refrigerant then flows to the outdoor-side heat exchanger 104 and evaporates and gasifies.
  • the refrigerant that has gasified passes through the flow switching valve 103 and flows back to the hermetic compressor 100 .
  • the refrigerant circulates as indicated by solid arrows in FIG. 4 . Because of this circulation of the refrigerant, at the outdoor-side heat exchanger 104 serving as an evaporator, the refrigerant sent to the outdoor-side heat exchanger 104 exchanges heat with outside air to receive heat from the outside air. The refrigerant that has received heat is sent to the indoor-side heat exchanger 106 serving as a condenser, and at the indoor-side heat exchanger 106 , exchanges heat with indoor air to heat the indoor air.
  • the flow switching valve 103 is connected to the outdoor-side heat exchanger 104 as indicated by dashed lines in FIG. 4 .
  • High-temperature and high-pressure refrigerant obtained through compression by the hermetic compressor 100 flows to the outdoor-side heat exchanger 104 and condenses and liquefies. Thereafter, the refrigerant that has liquefied is reduced in pressure by the pressure reducing device 105 to change into low-temperature and low-pressure two-phase refrigerant, and the low-temperature and low-pressure two-phase refrigerant then flows to the indoor-side heat exchanger 106 and evaporates and gasifies.
  • the refrigerant that has gasified passes through the flow switching valve 103 and flows back to the hermetic compressor 100 .
  • the indoor-side heat exchanger 106 serving as a condenser changes to serve as an evaporator
  • the outdoor-side heat exchanger 104 serving as an evaporator changes to serve as a condenser.
  • the refrigerant circulates as indicated by dashed arrows in FIG. 4 .
  • the refrigerant exchanges heat with indoor air to receive heat from the indoor air, that is, cool the indoor air.
  • the refrigerant that has received heat is sent to the outdoor-side heat exchanger 104 serving as a condenser to exchange heat with outside air and transfer heat to the outside air.
  • FIG. 5 is a cross-sectional schematic diagram illustrating a cylinder suction hole 110 and surroundings thereof in in the cylinder 23 of the hermetic compressor 100 according to Embodiment 1.
  • FIG. 6 is a schematic diagram illustrating the cylinder suction hole 110 and the surroundings thereof in the cylinder 23 of the hermetic compressor 100 according to Embodiment 1 as viewed from the front.
  • FIG. 7 is a vertical sectional schematic view illustrating the cylinder suction hole 110 and the surroundings in the cylinder 23 of the hermetic compressor 100 according to Embodiment 1 as viewed side-on.
  • the shape of a suction passage in the hermetic compressor 100 will be described with reference to FIGS. 5 to 7 .
  • the cylinder suction hole 110 is formed.
  • the cylinder suction hole 110 extends through the cylinder 23 from an outer circumferential surface of the cylinder 23 to an inner circumferential surface thereof, that is, extends through the cylinder 23 in the radial direction of the cylinder 23 , but does not extend through the cylinder 23 in the thickness direction of the cylinder 23 .
  • a cylindrical groove 111 that has a circular shape as viewed from the front is provided in such a manner as to surround the cylinder suction hole 110 .
  • a cylinder tubular portion 110 a is provided between the cylindrical groove 111 and the cylinder suction hole 110 .
  • the connecting pipe 52 is connected to an outer circumferential surface of the cylinder tubular portion 110 a by press-fitting, screws, welding, or an adhesive, for example. Therefore, a bonding face between the cylinder tubular portion 110 a and the connecting pipe 52 is that between the outer circumferential surface of the cylinder tubular portion 110 a and an inner circumferential surface of the connecting pipe 52 .
  • the connecting pipe 52 is not directly bonded to the inner circumferential surface of the cylinder suction hole 110 .
  • the cylinder tubular portion 110 a has a circular shape as viewed from the front. However, it is not indispensable that the cylinder tubular portion 110 a has an exactly circular shape. That is, the cylinder tubular portion 110 a may have a substantially circular shape.
  • FIG. 8 is a cross-sectional schematic diagram illustrating a cylinder suction hole 110 A and surroundings thereof in a cylinder 23 A of an existing hermetic compressor.
  • an existing connecting-pipe connection configuration as illustrated in FIG. 8 in which an inner circumferential surface of the cylinder suction hole 110 A of the cylinder 23 A and an outer circumferential surface of the connecting pipe 52 are bonded together, there is a risk that the entire cylinder 23 A will be deformed due to a load that is applied outwardly in the circumferential direction (in directions indicated by arrows in FIG. 8 ) in such a manner to release the load, thereby causing an inner side of the cylinder 23 A to be deformed such that an inside diameter thereof change, and also causing a vane groove (not illustrated) to be deformed.
  • a load is applied to the cylinder 23 inwardly in the circumferential direction (directions indicated by arrows in FIG. 5 ) at the time of connecting the connecting pipe 52 .
  • the cylinder tubular portion 110 a has lower stiffness with reference to the overall stiffness of the cylinder 23 , and the cylinder tubular portion 110 a is thus selectively (locally) distorted, thereby reducing the amount of distortion of the inner side of the cylinder 23 that changes the inner diameter thereof and the amount of distortion of the vane groove 23 c.
  • the cylindrical groove 111 does not extend through the cylinder 23 in the thickness direction of the cylinder 23 (direction indicated by arrow X).
  • the inner circumferential surface of the connecting pipe 52 is press-fitted into the outer circumferential surface of the cylinder tubular portion 110 a that is a thin-walled cylinder having a small thickness and provided on the outer circumferential surface of the cylinder 23 .
  • the cylinder 23 is not distorted as a whole, and that is, only the cylinder tubular portion 110 a is easily deformed, whereby it is possible to reduce deformation of the inner side of the cylinder 23 that results in change in the inside diameter thereof and the deformation of the vane groove 23 c.
  • the hermetic compressor 100 includes the compression mechanism 20 in the hermetic container 10 , and the compression mechanism 20 is driven by the electric motor 30 through the rotation shaft 21 .
  • the compression mechanism 20 includes the cylinder 23 that includes the cylinder chamber 23 a having a cylindrical shape and that has the cylinder suction hole 110 which extends in the radial direction and through which fluid is sucked into the cylinder chamber 23 a.
  • the cylindrical groove 111 is formed in such a manner as to surround the cylinder suction hole 110 .
  • the cylinder tubular portion 110 a is provided between the cylinder suction hole 110 and the cylindrical groove 111 .
  • the refrigeration cycle apparatus 200 includes the hermetic compressor 100 , the outdoor-side heat exchanger 104 , the pressure reducing device 105 , and the indoor-side heat exchanger 106 .
  • the cylindrical groove 111 is formed in such a manner as to surround the cylinder suction hole 110 .
  • the cylinder tubular portion 110 a is provided between the cylinder suction hole 110 and the cylindrical groove 111 .
  • the suction pipe 51 or the connecting pipe 52 is connected to the outer circumferential surface of the cylinder tubular portion 110 a.
  • the cylinder suction hole 110 is not expanded at the time of connecting the suction pipe 51 or the connecting pipe 52 to the cylinder tubular portion 110 a. It is therefore possible to reduce the likelihood that the cylinder 23 will be distorted in the circumferential direction as a whole.
  • Embodiment 2 will be described.
  • components that are the same as or equivalent to those in Embodiment 1 will be denoted by the same reference signs, and their descriptions will thus be omitted and only descriptions that are different from those regarding Embodiment 1 will be made.
  • FIG. 9 is a schematic diagram illustrating a cylinder suction hole 120 and surroundings thereof in the cylinder 23 of the hermetic compressor 100 according to Embodiment 2 as viewed from the front.
  • the cylinder 23 has the cylinder tubular portion 110 a having a circular shape as viewed from the front
  • the cylinder 23 has a cylinder tubular portion 120 a having an elliptical shape as viewed from the front.
  • a cylindrical groove 121 having an elliptical shape is provided in such a manner as to surround the cylinder suction hole 120 .
  • the connecting pipe 52 is connected to an outer circumferential surface of the cylinder tubular portion 120 a by press-fitting, screws, welding, or an adhesive, for example.
  • the major axis of the elliptical shape of the cylinder tubular portion 120 a may extend in the circumferential direction (Y direction) or the thickness direction (X direction) of the cylinder 23 .
  • the major axis of the elliptical shape of the cylinder tubular portion 120 a extends in the circumferential direction, expansion of the cylinder tubular portion 120 a in the thickness direction of the cylinder 23 is constrained, but the cylinder tubular portion 12 a can be expanded in the circumferential direction of the cylinder 23 and its opening area can thus be increased, as compared with the cylinder tubular portion 120 a has a circular shape.
  • the vane groove 23 c of the cylinder 23 is made to communicate with a spring hole 23 d provided in the same phase as the vane groove 23 c, expansion of the cylinder tubular portion 120 a in the circumferential direction of the cylinder 23 is constrained; in contrast, the cylinder tubular portion 120 a can be expanded in the thickness direction of the cylinder 23 , and its opening area can be increased as compared with the case where the cylinder tubular portion 120 a has a circular shape.
  • the cylinder tubular portion 120 a is formed in the shape of an ellipse as viewed from the front.
  • the hermetic compressor 100 it is possible to increase the opening area of the cylinder tubular portion 120 a, as compared with the case where the cylinder tubular portion 120 a has a circular shape. As a result, it is possible to increase the effective diameter of the cylinder suction hole 120 , and thus to reduce the pressure loss in the flow passage through which refrigerant flows, and increase the volumetric efficiency increases. Accordingly, the compressor performance can be improved.
  • Embodiment 3 will be described.
  • components that are the same as or equivalent to those in Embodiment 1 or 2 will be denoted by the same reference signs, and their descriptions will thus be omitted and only descriptions that are different from those regarding Embodiments 1 and 2 will be made.
  • FIG. 10 is a schematic diagram illustrating a cylinder suction hole 130 and surroundings thereof in the cylinder 23 of the hermetic compressor 100 according to Embodiment 3 as viewed from the front.
  • the cylinder 23 has the cylinder tubular portion 120 a formed in the shape of an ellipse as viewed from the front.
  • the cylinder 23 has a cylinder tubular portion 130 a formed in the shape of a rectangle having rounded corners as viewed from the front.
  • the cylinder tubular portion 130 a is made up of a pair of opposite straight portions 130 a 1 and a pair of opposite arc-shaped portions 130 a 2 .
  • a cylindrical groove 131 formed in the shape of a rectangle having rounded corners is provided in such a manner as to surround the cylinder suction hole 130 .
  • the connecting pipe 52 is connected to an outer circumferential surface of the cylinder tubular portion 130 a by press-fitting, screws, welding, or an adhesive, for example.
  • the longitudinal direction of the cylinder tubular portion 130 a may be made to coincide with the circumferential direction (the Y direction) or the thickness direction (the X direction) of the cylinder 23 .
  • the longitudinal direction of the cylinder tubular portion 130 a is the circumferential direction
  • expansion of the cylinder tubular portion 130 a in the thickness direction of the cylinder 23 is constrained, but the cylinder tubular portion 130 a can be expanded in the circumferential direction of the cylinder 23 , whereby the opening area of the cylinder tubular portion 130 a can be increased, as compared with the case where the cylinder tubular portion 130 a has a circular shape.
  • the longitudinal direction of the cylinder tubular portion 130 a is the thickness direction
  • the vane groove 23 c of the cylinder 23 is made to communicate with the spring hole 23 d provided in the same phase as the vane groove 23 c
  • expansion of the cylinder tubular portion 130 a in the circumferential direction of the cylinder 23 is constrained, but the cylinder tubular portion 130 a can be expanded in the thickness direction of the cylinder 23 , whereby the opening area of the cylinder tubular portion 130 a can be increased, as compared with the case where the cylinder tubular portion 130 a has a circular shape.
  • the cylinder tubular portion 130 a is formed in the shape of a rectangle having rounded corners as viewed from the front.
  • the hermetic compressor 100 it is possible to increase the opening area of the cylinder tubular portion 130 a, as compared with the case where the cylinder tubular portion 130 a has a circular shape. As a result, it is possible to increase the effective diameter of the cylinder suction hole 130 , and thus possible to reduce the pressure loss in the flow passage through which refrigerant flows, and increase the volumetric efficiency. Accordingly, it is possible to improve the compressor performance.
  • Embodiment 4 will be described.
  • components that are the same as or equivalent to those in any of Embodiments 1 to 3 will be denoted by the same reference signs, and their descriptions will thus be omitted and only descriptions that are different from those regarding Embodiments 1 to 3 will be made.
  • FIG. 11 is a schematic diagram illustrating a cylinder suction hole 140 and surroundings thereof in the cylinder 23 of the hermetic compressor 100 according to Embodiment 4 as viewed from the front.
  • the cylindrical groove 111 provided in the outer circumferential surface of the cylinder 23 and having a circular shape as viewed from the front does not extend through the cylinder 23 in the thickness direction of the cylinder 23 (the X direction)
  • a cylindrical groove 141 provided in the outer circumferential surface of the cylinder 23 and having a circular shape as viewed from the front extends through the cylinder 23 in the thickness direction of the cylinder 23 (the X direction).
  • the cylindrical groove 141 is formed in the outer circumferential surface of the cylinder 23 , and is made up of a pair of arc-shaped grooves 141 a.
  • the arc-shaped grooves 141 a are opened in upper and lower surfaces of the cylinder 23 .
  • a cylinder tubular portion 140 a is provided between the cylindrical groove 141 and the cylinder suction hole 140 .
  • the connecting pipe 52 is connected to an outer circumferential surface of the cylinder tubular portion 140 a by press-fitting, screws, welding, or an adhesive, for example.
  • connection surfaces between the cylinder tubular portion 140 a and the connecting pipe 52 are the outer circumferential surface of the cylinder tubular portion 140 a and the inner circumferential surface of the connecting pipe 52 .
  • the pair of arc-shaped grooves 141 a provided outward of the outer circumferential surface of the cylinder tubular portion 140 a are opened in the upper and lower surfaces of the cylinder 23 , the refrigerant does not leak from the cylinder suction hole 140 to the outside.
  • it is possible to increase the effective diameter of the cylinder suction hole 140 as compared with Embodiment 1. Accordingly, the compressor performance can be improved, as compared with Embodiment 1.
  • the bonding face between the cylinder tubular portion 140 a and the connecting pipe 52 corresponds to the outer circumferential surface of the cylinder tubular portion 140 a and the inner circumferential surface of the connecting pipe 52 .
  • the outer diameter of the connecting pipe 52 is greater than the height of the cylinder 23 , but the outer circumferential surface of the connecting pipe 52 does not serve as a refrigerant sealing surface.
  • the inner circumferential surface of the connecting pipe 52 serves as a refrigerant sealing surface, refrigerant sealing is unnecessary on the outer circumferential surface of the connecting pipe 52 . For this reason, in a single cylinder rotary compressor that includes the cylinder 23 interposed between the upper bearing 24 and the lower bearing 25 , the upper bearing 24 and the lower bearing 25 do not share the refrigerant sealing surface between them.
  • the outer circumferential surface of the connecting pipe 52 does not serve as a refrigerant sealing surface. It is therefore unnecessary to perform the recess processing.
  • the cylindrical groove 141 extends through the cylinder 23 in the thickness direction of the cylinder 23 .
  • the hermetic compressor 100 it is possible to increase the effective diameter of the cylinder suction hole 140 , as compared with Embodiment 1. Accordingly, the compressor performance can be improved, as compared with Embodiment 1.
  • Embodiment 5 will be described. Regarding Embodiment 5, components that are the same as or equivalent to those in any of Embodiments 1 to 4 will be denoted by the same reference signs, and their descriptions will thus be omitted and only descriptions that are different from those regarding Embodiments 1 to 4 will be made.
  • FIG. 12 is a schematic diagram illustrating a cylinder suction hole 150 and surroundings thereof in the cylinder 23 of the hermetic compressor 100 according to Embodiment 5 as viewed from the front.
  • the cylindrical groove 121 provided in the outer circumferential surface of the cylinder 23 and formed in the shape of an ellipse as viewed in front view does not extend through the cylinder 23 in the thickness direction of the cylinder 23 (the X direction), and in contrast, in Embodiment 5, as illustrated in FIG.
  • a cylindrical groove 151 provided in the outer circumferential surface of the cylinder 23 and formed in the shape of an ellipse as viewed from the front extends through the cylinder 23 in the thickness direction of the cylinder 23 (the X direction). That is, the cylindrical groove 151 is formed in the outer circumferential surface of the cylinder 23 , and is made up of a pair of arc-shaped grooves 151 a. The arc-shaped grooves 151 a are opened in the upper and lower surfaces of the cylinder 23 . Between the cylindrical groove 151 and the cylinder suction hole 150 , a cylinder tubular portion 150 a is provided.
  • the connecting pipe 52 is connected to an outer circumferential surface of the cylinder tubular portion 150 a by press-fitting, screws, welding, or an adhesive, for example.
  • the bonding face between the cylinder tubular portion 150 a and the connecting pipe 52 corresponds to the outer circumferential surface of the cylinder tubular portion 150 a and the inner circumferential surface of the connecting pipe 52 .
  • the pair of arc-shaped grooves 151 a provided outward of the outer circumferential surface of the cylinder tubular portion 150 a are opened in the upper and lower surfaces of the cylinder 23 , refrigerant does not leak from the cylinder suction hole 150 to the outside.
  • it is possible to increase the effective diameter of the cylinder suction hole 150 as compared with Embodiment 2. Accordingly, the compressor performance can be improved, as compared with Embodiment 2.
  • the cylindrical groove 151 extends through the cylinder 23 in the thickness direction of the cylinder 23 .
  • the hermetic compressor 100 it is possible to increase the effective diameter of the cylinder suction hole 150 , as compared with Embodiment 2. Accordingly, the compressor performance can be improved, as compared with Embodiment 2.
  • Embodiment 6 will be described. Regarding Embodiment 6, components that are the same as or equivalent to those in any of Embodiments 1 to 5 will be denoted by the same reference signs, and their descriptions will thus be omitted and only descriptions that are different from those regarding Embodiments 1 to 5 will be made.
  • FIG. 13 is a schematic diagram illustrating a cylinder suction hole 160 and surroundings thereof in the cylinder 23 of the hermetic compressor 100 according to Embodiment 6 as viewed from the front.
  • the cylindrical groove 131 provided in the outer circumferential surface of the cylinder 23 and formed in the shape of a rectangle having rounded corners as viewed from the front does not extend through the cylinder 23 in the thickness direction of the cylinder 23 (the X direction), and in contrast, in Embodiment 6, as illustrated in FIG.
  • a cylindrical groove 161 provided in the outer circumferential surface of the cylinder 23 and formed in the shape of a rectangle having rounded corners as viewed from the front extend through the cylinder 23 in the thickness direction of the cylinder 23 (the X direction). That is, the cylindrical groove 161 is formed in the outer circumferential surface of the cylinder 23 , and made up of a pair of arc-shaped grooves 161 a. The arc-shaped grooves 161 a are opened in the upper and lower surfaces of the cylinder 23 .
  • a cylinder tubular portion 160 a is provided between the cylindrical groove 161 and the cylinder suction hole 160 , and the cylinder tubular portion 160 a is made up of a pair of opposite straight portions 160 a 1 and a pair of opposite arc-shaped portions 160 a 2 .
  • the connecting pipe 52 is connected to an outer circumferential surface of the cylinder tubular portion 160 a by press-fitting, screws, welding, or an adhesive, for example.
  • the bonding face between the cylinder tubular portion 160 a and the connecting pipe 52 corresponds to the outer circumferential surface of the cylinder tubular portion 160 a and the inner circumferential surface of the connecting pipe 52 .
  • the pair of arc-shaped grooves 161 a provided outward of the outer circumferential surface of the cylinder tubular portion 160 a are opened in the upper and lower surfaces of the cylinder 23 , the refrigerant does not leak from the cylinder suction hole 160 to the outside.
  • it is possible to increase the effective diameter of the cylinder suction hole 160 as compared with Embodiment 3. Accordingly, the compressor performance can be improved, as compared with Embodiment 3.
  • the cylindrical groove 161 extends through the cylinder 23 in the thickness direction of the cylinder 23 .
  • the hermetic compressor 100 according to Embodiment 6 it is possible to increase the effective diameter of the cylinder suction hole 160 , as compared with Embodiment 3. Accordingly, the compressor performance can be improved, as compared with Embodiment 3.
  • Embodiment 7 will be described. Regarding Embodiment 7, components that are the same as or equivalent to those in any of Embodiments 1 to 6 will be denoted by the same reference signs, and their descriptions will thus be omitted and only descriptions that are different from those regarding Embodiments 1 to 6 will be made.
  • FIG. 14 is a vertical sectional schematic diagram illustrating a cylinder suction hole 170 and surroundings thereof in the cylinder 23 of the hermetic compressor 100 according to Embodiment 7 as viewed side-on.
  • a cylindrical groove 171 extends through the cylinder 23 in the thickness direction of the cylinder 23 , for example, when an outer circumferential end portion (Z 1 -side end portion) of the upper bearing 24 is located closer to a radially outer side (Z 1 -side) than a radially inner end portion 171 a of the cylindrical groove 171 as illustrated in FIG.
  • a bearing recessed portion 24 a that is recessed toward a radially inner side (Z 2 -side) is provided at an outer circumferential end portion of the upper bearing 24 .
  • the bearing recessed portion 24 a may have any shape as long as the bearing recessed portion 24 a can prevent interference between the upper bearing 24 and the connecting pipe 52 .
  • the cylindrical groove 171 extends through the cylinder 23 in the thickness direction of the cylinder 23 , for example, when the outer circumferential end portion of the upper bearing 24 (Z 1 -side end portion) is located closer to the radially inner side (Z 2 -side) than a radially inner end portion 111 a of the cylindrical groove 111 as illustrated in FIG. 7 , the upper bearing 24 does not interfere with the connecting pipe 52 even if the bearing recessed portion 24 a is not provided.
  • the hermetic compressor 100 includes a bearing that is in contact with the cylinder 23 and that supports the rotation shaft 21 such that the rotation shaft 21 is rotatable, and at the outer circumferential end portion of the bearing, the bearing recessed portion 24 a is provided to prevent interference between the bearing and the suction pipe 51 or the connecting pipe 52 .
  • the hermetic compressor 100 according to Embodiment 7 can prevent interference between the upper bearing 24 and the suction pipe 51 or the connecting pipe 52 .
  • the suction muffler 101 is connected to the suction port of the cylinder 23 by the suction pipe 51 and the connecting pipe 52 provided at one end of this suction pipe 51 , this description is not limiting.
  • the suction muffler 101 may be configured such that the connecting pipe 52 is not provided at one end of the suction pipe 51 and the suction pipe 51 is directly connected to the suction port of the cylinder 23 with no connecting pipe 52 .

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US20120174620A1 (en) * 2009-09-25 2012-07-12 Toshiba Carrier Corporation Hermetic compressor and refrigeration cycle equipment using the same
US20150236574A1 (en) * 2014-02-20 2015-08-20 Mitsubishi Electric Corporation Single-phase induction motor, hermetic compressor, and refrigeration cycle device
US9115715B2 (en) * 2011-09-28 2015-08-25 Daikin Industries, Ltd. Compressor with pressure reduction groove formed in eccentric part
US20170045268A1 (en) * 2014-04-30 2017-02-16 Mitsubishi Electric Corporation Electric motor, hermetic compressor, and refrigeration cycle apparatus
US20190211823A1 (en) * 2016-11-09 2019-07-11 Fujitsu General Limited Rotary compressor

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JP2003214370A (ja) * 2002-01-23 2003-07-30 Mitsubishi Heavy Ind Ltd ロータリ圧縮機
JP6570930B2 (ja) * 2015-09-09 2019-09-04 三菱重工サーマルシステムズ株式会社 ロータリ圧縮機およびその製造方法
CN207437369U (zh) * 2017-10-20 2018-06-01 珠海格力节能环保制冷技术研究中心有限公司 一种泵体组件及压缩机

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Publication number Priority date Publication date Assignee Title
US20120174620A1 (en) * 2009-09-25 2012-07-12 Toshiba Carrier Corporation Hermetic compressor and refrigeration cycle equipment using the same
US9115715B2 (en) * 2011-09-28 2015-08-25 Daikin Industries, Ltd. Compressor with pressure reduction groove formed in eccentric part
US20150236574A1 (en) * 2014-02-20 2015-08-20 Mitsubishi Electric Corporation Single-phase induction motor, hermetic compressor, and refrigeration cycle device
US20170045268A1 (en) * 2014-04-30 2017-02-16 Mitsubishi Electric Corporation Electric motor, hermetic compressor, and refrigeration cycle apparatus
US20190211823A1 (en) * 2016-11-09 2019-07-11 Fujitsu General Limited Rotary compressor

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