WO2017141309A1 - ロータリ圧縮機 - Google Patents

ロータリ圧縮機 Download PDF

Info

Publication number
WO2017141309A1
WO2017141309A1 PCT/JP2016/054266 JP2016054266W WO2017141309A1 WO 2017141309 A1 WO2017141309 A1 WO 2017141309A1 JP 2016054266 W JP2016054266 W JP 2016054266W WO 2017141309 A1 WO2017141309 A1 WO 2017141309A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
vane
vane groove
pair
rotary compressor
Prior art date
Application number
PCT/JP2016/054266
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
洋昭 坂東
雄介 小河
隆太郎 水野
中村　英之
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to CN201680081206.9A priority Critical patent/CN108603505B/zh
Priority to CZ2018394A priority patent/CZ308843B6/cs
Priority to JP2017567578A priority patent/JP6607971B2/ja
Priority to PCT/JP2016/054266 priority patent/WO2017141309A1/ja
Priority to KR1020187018808A priority patent/KR102089805B1/ko
Publication of WO2017141309A1 publication Critical patent/WO2017141309A1/ja

Links

Images

Classifications

    • 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
    • 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
    • F04C18/3562—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/18—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber
    • F04C28/22—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • 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
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • 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
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • 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

Definitions

  • the present invention relates to a rotary compressor having a vane groove.
  • a ring-shaped cylinder includes a vane groove that accommodates a vane, and a pressure introduction path that communicates with a terminal portion on the outer peripheral surface side of the vane groove. What is provided is disclosed.
  • the pressure introduction path has a circular opening and penetrates the cylinder in the vertical direction.
  • the present invention is for solving the above-described problems, and provides a rotary compressor that can prevent deterioration of vane slidability and ensure the durability and reliability of the rotary compressor. With the goal.
  • the rotary compressor of the present invention includes a piston that rotates eccentrically by rotation of a crankshaft, a pair of hollow disk surfaces, an inner surface that extends between inner edges of the pair of hollow disk surfaces, and the pair of pairs And a cylinder in which the piston is accommodated in a space surrounded by the inner surface, and the cylinder extends from the inner surface to the outer surface.
  • a vane groove that extends in a radial direction toward the side surface and accommodates a vane that reciprocates by eccentric rotation of the piston; and a vane groove opening that passes through the pair of hollow disk surfaces and communicates with the vane groove; And the vane groove opening is disposed on the outer surface side of the cylinder from the pair of first convex bent portions having a first radius of curvature, and the pair of first convex bent portions, Extending between the pair of first convex bent portions and the second It is formed in a space surrounded by the wall portion and a second convex bent portion having a radius of curvature, the second radius of curvature of the first curvature smaller than the radius.
  • the opening area of the vane groove opening can be configured to be smaller than that of the prior art vane groove opening, the occurrence of distortion of the vane groove can be avoided.
  • the durability of the cylinder can be improved by avoiding the occurrence of distortion in the vane groove.
  • FIG. 4 is a partially enlarged view showing an example of a schematic structure of a vane groove opening 318 of a cylinder 31 in the compression mechanism 30 of the rotary compressor 1 according to Embodiment 1 of the present invention.
  • FIG. 3 is a schematic diagram showing an external force applied to a vane groove 316 when the cylinder 31 is fixed to the sealed container 2 in the rotary compressor 1 according to Embodiment 1 of the present invention. It is the schematic which shows the structure of the vane groove opening part 318a in the rotary compressor 1 of a prior art. It is the schematic which compared the shape of the vane groove opening part 318 in the rotary compressor 1 which concerns on Embodiment 1 of this invention, and the vane groove opening part 318a of the prior art of circular shape.
  • FIG. 1 is a longitudinal sectional view schematically showing an example of a rotary compressor 1 according to the first embodiment.
  • the rotary compressor 1 is used in a refrigeration cycle apparatus such as an air conditioner, and is an element constituting a refrigerant circuit of the refrigeration cycle apparatus.
  • the refrigerant circuit and other components constituting the refrigerant circuit such as a radiator, an evaporator, a decompression device, and an oil separator are not illustrated.
  • the dimensional relationship and shape of each component may be different from the actual one.
  • symbol is attached
  • the positional relationship between the constituent members of the rotary compressor 1 in the following description for example, the positional relationship such as the vertical relationship, is basically the positional relationship when the rotary compressor 1 is installed in a usable state. .
  • the rotary compressor 1 is a rolling piston type compressor, and is a fluid machine that discharges low-pressure gas refrigerant sucked into the rotary compressor 1 as high-pressure gas refrigerant.
  • the casing of the rotary compressor 1 is configured as a cylinder-shaped sealed container 2.
  • the hermetic container 2 includes a main body 2a having a U-shaped longitudinal section and a lid 2b having an inverted U-shaped longitudinal section, and the outer surface of the opening of the lid 2b is an opening of the main body 2a. It is fixed to the inner surface of the.
  • the fixed portion between the main body 2a and the lid 2b is joined by welding or the like, for example.
  • mold is provided in the outer surface of the bottom face of the main-body part 2a.
  • the rotary compressor 1 is configured as a vertical compressor, but may be configured as a horizontal compressor.
  • the casing 4a of the suction muffler 4 is fixed to a support member 5 disposed on the outer surface of the sealed container 2 on the outer surface of the main body 2a of the sealed container 2.
  • the support member 5 can be configured to include, for example, an annular band portion 5a that fixes the outer surface of the suction muffler 4 and a holder portion 5b that is fixed to the outer surface of the sealed container 2 and supports the band portion 5a.
  • An inflow pipe 4b is fixed to the top of the housing 4a of the suction muffler 4 through the housing 4a.
  • the inflow pipe 4b is, for example, a refrigerant pipe through which a low-pressure gas refrigerant or a two-phase refrigerant having a high dryness flowing out from the evaporator of the refrigeration cycle apparatus flows into the housing 4a of the suction muffler 4.
  • one end of the suction pipe 6 passes through and is fixed to the bottom of the housing 4 a of the suction muffler 4, and the other end of the suction pipe 6 passes through the side surface of the main body 2 a of the sealed container 2. Is fixed.
  • the suction muffler 4 is a silencer that reduces or eliminates noise generated by the refrigerant flowing from the inflow pipe 4b.
  • the suction muffler 4 also has an accumulator function, and has a refrigerant storage function for storing surplus refrigerant and a gas-liquid separation function for retaining liquid refrigerant that is temporarily generated when the operating state changes. Have. Due to the gas-liquid separation function of the suction muffler 4, it is possible to prevent a large amount of liquid refrigerant from flowing into the sealed container 2 and liquid compression in the rotary compressor 1.
  • the suction pipe 6 is a refrigerant pipe that sucks low-pressure gas refrigerant into the sealed container 2.
  • the fixed portion between the suction pipe 6 and the main body 2a is joined, for example, by brazing.
  • the suction pipe 6 is provided with an oil return hole in the side surface portion, and sucks the lubricating oil component contained in the high-pressure gas refrigerant separated in the oil separator of the refrigeration cycle apparatus. You may comprise so that it may return to the inside of the airtight container 2 via the pipe
  • the discharge pipe 7 is fixed through the upper surface of the lid 2b of the sealed container 2.
  • the discharge pipe 7 is a refrigerant pipe that discharges high-pressure gas refrigerant to the outside of the sealed container 2.
  • the fixed portion between the discharge pipe 7 and the lid 2b is joined, for example, by brazing.
  • a charge pipe 8 is fixed through the upper surface of the lid 2b of the sealed container 2.
  • the charge pipe 8 can be configured such that the inside of the sealed container 2 is evacuated and a gas refrigerant can be sealed inside the sealed container 2. Further, the charge pipe 8 may be configured such that lubricating oil can be sealed inside the sealed container 2.
  • a glass terminal 9 is disposed on the upper surface of the lid 2b of the sealed container 2.
  • the glass terminal 9 provides an interface for connecting an external power source.
  • the external power supply is a power supply device that supplies power to the rotary compressor 1, and a general commercial AC power supply with an AC frequency of 50 Hz or 60 Hz, or an inverter power supply that can change the AC frequency is used.
  • the frequency variable inverter power supply is used, the rotational speed of the rotary compressor 1 can be changed. Therefore, the rotary compressor 1 can control the discharge amount of the high-pressure gas refrigerant from the discharge pipe 7.
  • the external power source connected to the glass terminal 9 is not shown in the following drawings including FIG.
  • an electric motor unit 10 In the sealed container 2, an electric motor unit 10, a crankshaft 20, and a compression mechanism unit 30 are accommodated.
  • the electric motor unit 10 is disposed above a fixed portion between the main body 2a and the suction pipe 6.
  • the crankshaft 20 is disposed so as to extend in the vertical direction between the electric motor unit 10 and the compression mechanism unit 30 at the center of the sealed container 2.
  • the compression mechanism portion 30 is configured such that the side surface portion of the compression mechanism portion 30 covers a fixed portion between the main body portion 2 a and the suction pipe 6, and the inside of the compression mechanism portion 30 communicates with the suction pipe 6. That is, the electric motor unit 10 is disposed above the compression mechanism unit 30 inside the sealed container 2. Further, the hollow space inside the sealed container 2 above the compression mechanism unit 30 is filled with a high-pressure gas refrigerant compressed by the compression mechanism unit 30.
  • the electric motor unit 10 is configured as a motor that generates a rotational driving force using electric power supplied from an external power source and transmits the rotational driving force to the compression mechanism unit 30 via the crankshaft 20.
  • the electric motor unit 10 includes a stator 12 having a hollow cylindrical appearance in a top view, and a cylindrical rotor 14 that is rotatably arranged inside the inner surface of the stator 12.
  • the stator 12 is fixed to the inner surface of the main body 2 a of the sealed container 2, and is connected to the glass terminal 9 through a conducting wire 16.
  • the electric motor unit 10 can rotate the rotor 14 inside the inner surface of the stator 12 by supplying electric power from an external power source to the coil wound around the stator 12 via the conductive wire 16.
  • a DC brushless motor or the like is used as the electric motor unit 10.
  • a crankshaft 20 is fixed through the rotor 14 at the center of the rotor 14.
  • the crankshaft 20 is a rotating shaft that fixes the rotor 14 with a fixed surface 20 a that is a part of the outer surface of the crankshaft 20 and transmits the rotational driving force of the rotor 14 to the compression mechanism 30.
  • the crankshaft 20 extends from the fixed surface 20a in the vertical direction, that is, in the direction of the lid 2b of the sealed container 2 and the direction of the bottom of the main body 2a of the sealed container 2.
  • An oil separation plate 22 is provided above the fixed surface 20a.
  • the oil separation plate 22 separates the lubricating oil contained in the high-pressure gas refrigerant discharged from the compression mechanism 30 by the centrifugal force generated by the rotation of the crankshaft 20, and drops it to the bottom of the main body 2a by the action of gravity. It is configured.
  • crankshaft 20 has a cylindrical eccentric portion 24 that is located below the fixed surface 20 a and is disposed inside the compression mechanism portion 30.
  • a piston 26 attached rotatably along the outer side surface of the eccentric part 24 is disposed.
  • an oil hole extending upward from the lower end of the crankshaft 20 and flowing through the lubricating oil that is the refrigerating machine oil 40 sucked up from the lower end of the crankshaft 20 is provided at the center of the crankshaft 20.
  • the outer surface of the crankshaft 20 is provided with a plurality of oil supply ports that communicate with the aforementioned oil holes and supply lubricating oil to the compression mechanism 30.
  • a centrifugal pump can be arranged at the lower end of the oil hole of the crankshaft 20.
  • the above-described centrifugal pump is configured as, for example, a spiral centrifugal pump so that the refrigerating machine oil 40 stored at the bottom of the main body 2a of the sealed container 2 can be sucked up.
  • refrigerating machine oil 40 for example, mineral oil-based, alkylbenzene-based, polyalkylene glycol-based, polyvinyl ether-based, polyol ester-based lubricating oil, or the like is used. Further, the oil hole and the oil supply port provided in the crankshaft 20 and the centrifugal pump disposed at the lower end of the oil hole are not shown in the following drawings including FIG.
  • FIG. 2 is a schematic diagram illustrating an example of an internal structure in a side view of the compression mechanism unit 30 of the rotary compressor 1 according to the first embodiment.
  • FIG. 3 is a schematic diagram illustrating an example of an internal structure in a top view of the compression mechanism unit 30 of the rotary compressor 1 according to the first embodiment.
  • the compression mechanism unit 30 compresses the low-pressure gas refrigerant sucked into the low-pressure space of the sealed container 2 from the suction pipe 6 into the high-pressure gas refrigerant by the rotational driving force supplied from the electric motor unit 10 and compresses the compressed high-pressure gas.
  • the refrigerant is discharged above the compression mechanism unit 30.
  • the compression mechanism portion 30 extends between a pair of hollow disk surfaces 31a, an inner side surface 31b extending between the inner edge portions of the pair of hollow disk surfaces 31a, and an outer edge portion of the pair of hollow disk surfaces 31a.
  • a hollow cylindrical cylinder 31 having an outer side surface 31c is provided.
  • the outer surface 31 c of the cylinder 31 is fixed to the inner surface of the main body 2 a of the sealed container 2.
  • the hollow portion 310 of the cylinder 31 is formed in a space surrounded by the inner surface 31b of the cylinder 31, and accommodates the eccentric portion 24 and the piston 26 of the crankshaft 20. That is, the cylinder 31 is configured so that the eccentric portion 24 of the crankshaft 20 and the piston 26 can rotate eccentrically by the rotation of the crankshaft 20 in the hollow portion 310 of the cylinder 31.
  • the cylinder 31 is provided with a suction port 312 that communicates between the suction pipe 6 and the hollow portion 310 of the cylinder 31 and allows low-pressure gas refrigerant to flow into the hollow portion 310 of the cylinder 31 from the suction pipe 6.
  • a semicircular discharge passage 314 extending in the vertical direction is provided on the inner surface of the cylinder 31.
  • the cylinder 31 is provided with a vane groove 316 extending in the radial direction from the inner side surface 31b of the cylinder 31 toward the outer side surface 31c of the cylinder 31 in a top view.
  • the vane groove 316 is formed between two parallel flat side walls 317 in a top view.
  • the vane 32 is accommodated in the vane groove 316 of the cylinder 31.
  • the vane 32 is a sliding member configured to reciprocate in the radial direction inside the vane groove 316 by the eccentric movement of the piston 26.
  • the tip 32 a of the vane 32 disposed in the hollow portion 310 of the cylinder 31 is caused by the restoring force of the elastic body 33 such as a spring provided in the vane groove 316 or the pressure from the high-pressure portion above the compression mechanism 30.
  • the piston 26 is pressed against the outer surface. As shown in FIG.
  • the hollow portion 310 of the cylinder 31 has a low-pressure space portion 310 a that communicates with the suction port 312 and a high-pressure space that communicates with the discharge passage 314 by the vane 32 and the piston 26. It is divided into a part 310b.
  • the low pressure space portion 310a and the high pressure space portion 310b are spaces that constitute a compression chamber of the compression mechanism portion 30 described later.
  • the cylinder 31 is provided with a vane groove opening 318 that communicates with the vane groove 316 and penetrates the pair of hollow disk surfaces 31 a of the cylinder 31.
  • the pressure from the high pressure portion above the compression mechanism portion 30 can be applied to the end portion 32 b of the vane 32 through the vane groove opening 318.
  • the movement of the vane 32 toward the outer surface of the cylinder 31 can be restricted by the vane groove opening 318.
  • the lubricating oil separated from the high-pressure gas refrigerant can be supplied between the vane groove 316 and the vane 32 through the vane groove opening 318, and the vane 32 can be smoothly reciprocated.
  • the detailed structure of the vane groove opening 318 will be described later.
  • a clearance is provided between the vane groove 316 and the vane 32, and the friction is not generated between the vane groove 316 and the vane 32. ing.
  • the clearance between the vane groove 316 and the vane 32 is increased, the refrigerant gas compressed in the hollow portion 310 of the cylinder 31 passes through the clearance and the vane groove opening 318 to the outside of the compression mechanism unit 30. Leakage, and compression efficiency may be reduced. Therefore, the clearance is configured to be small enough that no friction occurs between the vane groove 316 and the vane 32. By configuring the clearance to be small, leakage of the compressed refrigerant gas can be suppressed, leakage loss can be reduced, and compression efficiency can be improved.
  • a main bearing 34 is disposed on the hollow disk surface 31 a on the upper side of the cylinder 31, that is, on the hollow disk surface 31 a on the lid 2 b side of the sealed container 2.
  • a sub-bearing 35 is disposed on the hollow disk surface 31 a on the lower side of the cylinder 31, that is, on the hollow disk surface 31 a on the bottom surface side of the main body 2 a of the sealed container 2.
  • the main bearing 34 and the auxiliary bearing 35 are sliding bearings that slidably support the crankshaft 20.
  • the main bearing 34 has a hollow disk shape when viewed from above.
  • the main bearing 34 has a fixed portion 34a fixed to the upper hollow disk surface 31a of the cylinder 31 and a bearing portion 34b that slidably supports the outer surface of the crankshaft 20.
  • the main bearing 34 is shown as two L-shaped members in the longitudinal sectional view of FIG. Moreover, the main bearing 34 is being fixed to the hollow disc surface 31a above the cylinder 31 with the volt
  • the auxiliary bearing 35 has a hollow disk shape when viewed from below.
  • the sub bearing 35 has a fixed portion 35a fixed to the hollow disk surface 31a on the lower side of the cylinder 31, and a bearing portion 35b that slidably supports the outer surface of the crankshaft 20.
  • the sub bearing 35 is displayed as two L-shaped members in the longitudinal sectional view of FIG.
  • the auxiliary bearing 35 is fixed to the hollow disc surface 31a on the lower side of the cylinder 31 by, for example, a bolt or the like.
  • a sealable space surrounded by the piston 26, the cylinder 31, the vane 32, the fixing portion 34 a of the main bearing 34, and the fixing portion 35 a of the auxiliary bearing 35 is a low pressure sucked from the suction pipe 6.
  • the high-pressure gas refrigerant compressed in the compression chamber is discharged from a discharge port provided in the main bearing 34.
  • the discharge port provided in the main bearing 34 is not shown in the following drawings including FIG.
  • a silencer 36 is disposed on the upper surface side of the fixed portion 34a of the main bearing 34.
  • the silencer 36 covers the fixed part 34a of the main bearing 34 and a part of the bearing part 34b, and is configured to remove or reduce noise generated when the refrigerant is compressed in the compression mechanism 30.
  • the silencer 36 is provided with a plurality of openings for discharging high-pressure gas refrigerant flowing from the discharge port provided in the main bearing 34 into the closed container 2.
  • the muffler 36 is fixed to the hollow disk surface 31a on the upper side of the cylinder 31 via the main bearing 34, for example, with bolts or the like.
  • FIG. 4 is a partially enlarged view showing an example of a schematic structure of the vane groove opening 318 of the cylinder 31 in the compression mechanism 30 of the rotary compressor 1 according to the first embodiment.
  • the cylinder 31 is provided with the vane groove opening 318 that communicates with the vane groove 316 and penetrates the pair of hollow disk surfaces 31 a of the cylinder 31.
  • the vane groove opening 318 is formed in a space surrounded by a wall surface portion 319 having a pair of first convex bent portions 319 a and second convex bent portions 319 b.
  • the pair of first convex bent portions 319a are disposed on the inner surface 31b side of the cylinder 31 and have a first radius of curvature R1.
  • the second convex bent portion 319b is disposed closer to the outer surface 31c of the cylinder 31 than the pair of first convex bent portions 319a, extends between the pair of first convex bent portions 319a, and has a second curvature. It has a radius R2. Further, as shown in FIG. 4, in the first convex bent portion 319a, the center of the first radius of curvature R1 is located on the vane groove opening 318 side, and also in the second convex bent portion 319b. The center of the second radius of curvature R2 is located on the vane groove opening 318 side.
  • the vane groove opening 318 is formed by, for example, drilling a hole having a first radius of curvature R1 that penetrates the hollow disk surface 31a with a drilling tool such as a drill, and then the first radius of curvature R1 that penetrates the hollow disk surface 31a. It is formed by drilling holes. Therefore, since the vane groove opening 318 can be formed by a simple drilling operation, the manufacturing cost of the rotary compressor 1 can be reduced.
  • the vane groove opening 318 is not limited to the example of FIG. 4 and can be formed in a space surrounded by a wall surface 319 having a plurality of convex bent portions.
  • the vane groove opening 318 may have an oval shape, a spindle shape such as a rugby ball shape, or an oval shape such as a capsule shape. There may be.
  • the wall surface portion 319 is configured to be disposed inside a virtual circle whose diameter is the maximum width of the vane groove opening 318 in the radial direction of the cylinder 31.
  • the maximum width of the vane groove opening 318 described above is the vane groove opening in the radial direction of the cylinder 31 formed by a drilling tool such as a drill, assuming that the vane groove 316 is not formed in the cylinder 31.
  • the maximum width is 318.
  • the plurality of convex bent portions described above may have different radii of curvature.
  • the eccentric part 24 and the piston 26 housed in the cylinder 31 together with the crankshaft 20 are eccentrically rotated at high speed.
  • the vane 32 provided in the vane groove 316 of the cylinder 31 performs a piston motion.
  • the low-pressure gas refrigerant that has flowed into the compression mechanism portion 30 from the suction pipe 6 through the suction port 312 is surrounded by the piston 26, the cylinder 31, the vane 32, the fixed portion 34a of the main bearing 34, and the fixed portion 35a of the auxiliary bearing 35. Flows into the compression chamber, which is a sealed space.
  • the low-pressure gas refrigerant flowing into the compression chamber is compressed into the high-pressure gas refrigerant as the compression chamber volume decreases due to the eccentric rotation of the piston 26.
  • the refrigerating machine oil 40 stored at the bottom of the main body 2 a in the sealed container 2 is sucked up from the lower end of the crankshaft 20.
  • the sucked refrigeration oil 40 flows as a lubricating oil between the bearing portion 34 b of the main bearing 34 and the crankshaft 20 and between the bearing portion 35 b of the auxiliary bearing 35 and the crankshaft 20.
  • the lubricating oil flows into the sliding portion between the crankshaft 20 and the bearing portion 34b of the main bearing 34 or the bearing portion 35b of the auxiliary bearing 35, whereby the crankshaft 20 smoothly transmits the rotational driving force to the piston 26. be able to.
  • the lubricating oil also flows between the fixed portion 34 a of the main bearing 34 and the upper surface of the piston 26 and between the fixed portion 35 a of the auxiliary bearing 35 and the lower surface of the piston 26.
  • Lubricating oil is used to smoothly rotate the piston 26, but part of the lubricating oil is compressed together with the low-pressure gas refrigerant and discharged in a state of being contained in the high-pressure gas refrigerant.
  • High-pressure gas refrigerant containing lubricating oil flows from the cylinder 31 into the silencer 36 through the discharge passage 314 and the discharge port provided in the main bearing 34.
  • the high-pressure gas refrigerant inside the silencer 36 is discharged from a plurality of openings provided in the silencer 36 to a high-pressure portion inside the sealed container 2 positioned between the electric motor unit 10 and the compression mechanism unit 30. .
  • the high-pressure gas refrigerant discharged to the high-pressure portion flows through the gap provided in the stator 12 and the rotor 14 and flows upward in the crankshaft 20.
  • the lubricating oil component is separated from the high-pressure gas refrigerant by the centrifugal force generated by the rotation of the oil separation plate 22.
  • the lubricating oil separated by the oil separation plate 22 adheres to the inner surface of the sealed container 2 and falls downward by gravity through an outer groove provided in the stator 12.
  • the lubricating oil that has dropped downward is collected, for example, at the bottom of the main body 2a of the sealed container 2 through the vane groove opening 318, but a part of the lubricating oil 316 is used to smoothly reciprocate the vane 32.
  • the vane 32 is supplied to the clearance.
  • the high-pressure gas refrigerant from which the lubricating oil component has been separated by the oil separation plate 22 reaches the lid portion 2 b of the sealed container 2 and is discharged out of the sealed container 2 through the discharge pipe 7.
  • the rotary compressor 1 includes the piston 26 that rotates eccentrically with the rotation of the crankshaft 20, the pair of hollow disk surfaces 31a, and the inner edges of the pair of hollow disk surfaces 31a.
  • the piston 26 is accommodated in a space surrounded by the inner side surface 31b.
  • the inner side surface 31b extends between the inner side surfaces 31b and the outer side surface 31c extends between the outer edge portions of the pair of hollow disk surfaces 31a.
  • the cylinder 31 extends in the radial direction from the inner side surface 31b to the outer side surface 31c, and includes a vane groove 316 that houses a vane 32 that reciprocates by eccentric rotation of the piston 26, and a pair of hollow There is a vane groove opening 318 that penetrates the disk surface 31a and communicates with the vane groove 316.
  • the vane groove opening 318 has a pair of first convex bent portions 319 having a first radius of curvature R1.
  • a second protrusion having a second radius of curvature R2 that is disposed on the outer surface 31c side of the cylinder 31 from the pair of first convex bent portions 319a, extends between the pair of first convex bent portions 319a. Formed in a space surrounded by a wall surface 319 having a bent portion 319b, and the second radius of curvature R2 is configured to be smaller than the first radius of curvature R1.
  • FIG. 5 is a schematic view showing a method of fixing the cylinder 31 to the sealed container 2 at the time of manufacturing the rotary compressor 1 according to the first embodiment.
  • the outer surface 31 c of the cylinder 31 is struck by hitting the pressing jig 55 from the outside of the closed container 2 with three caulking load mechanisms 50 to form three caulking portions, thereby forming the closed container 2.
  • the inner surface Fixed to the inner surface.
  • pressure is applied to the cylinder 31 in the radial direction from the outer surface 31c toward the inner surface 31b.
  • FIG. 6 is a schematic diagram showing an external force applied to the vane groove 316 when the cylinder 31 is fixed to the sealed container 2 in the rotary compressor 1 according to the first embodiment.
  • the vane groove 316 is perpendicular to the radial direction of the cylinder 31 as shown by the black block arrows in FIG.
  • the external force acts in the direction and the direction of narrowing the width of the vane groove 316.
  • FIG. 7 is a schematic diagram showing the structure of the vane groove opening 318a in the rotary compressor 1 of the prior art.
  • the vane groove opening 318 a is formed in a space surrounded by a circular wall surface 319.
  • the inner diameter of the cylinder 31 is increased from 44 mm to 46 mm, for example. Think about it.
  • the rigidity of the cylinder 31 with respect to the pressure by the caulking load mechanism 50 decreases, so that the external force acting in the direction of narrowing the width of the vane groove 316 increases.
  • the vane groove 316 may be distorted. When distortion occurs in the vane groove 316, friction is generated between the vane groove 316 and the vane 32, and the slidability of the vane 32 is deteriorated.
  • FIG. 8 is a schematic diagram comparing the shape of the vane groove opening 318 in the rotary compressor 1 according to the first embodiment with the conventional vane groove opening 318a having a circular shape. As shown in the hatched area A of FIG. 8, the opening area of the vane groove opening 318 can be configured to be smaller than that of the vane groove opening 318a of the prior art. It is possible to avoid a decrease in the rigidity of 31.
  • the vane groove opening 318 is formed by, for example, drilling a hole having the first curvature radius R1 that penetrates the hollow disk surface 31a with a drilling tool such as a drill, and then the hollow disk surface 31a. Can be formed by perforating a hole having a first radius of curvature R1 that passes through. Therefore, since the vane groove opening 318 can be formed by a simple drilling operation, the manufacturing cost of the rotary compressor 1 can be reduced.
  • the rotary compressor 1 is configured as a rolling piston type compressor, but may be configured as a swing vane type swing compressor.
  • a piston part in which a rolling piston part corresponding to the piston 26 of the first embodiment and a vane part corresponding to the vane 32 of the first embodiment are integrated is provided inside the cylinder 31.
  • the swing vane type swing compressor includes a bush for swinging the piston portion.
  • the bushes are a pair of semi-cylindrical rocking members that are disposed in the cylinder 31 and are supported with the vane portion of the piston portion interposed therebetween.
  • the opening area of the vane groove opening 318 can be configured to be smaller than that of the conventional vane groove opening 318a. Therefore, even when the rotary compressor 1 is configured as a swing compressor, a reduction in the rigidity of the cylinder 31 can be avoided, so that deterioration of the slidability of the vane 32 can be avoided, and durability and reliability can be avoided. Can be provided.
  • the rotary compressor 1 is configured as a hermetic compressor, but may be configured as a semi-hermetic or open compressor.
  • the rotary compressor 1 is configured as a one-cylinder compressor, but may be configured as a compressor having two or more cylinders 31.
PCT/JP2016/054266 2016-02-15 2016-02-15 ロータリ圧縮機 WO2017141309A1 (ja)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CN201680081206.9A CN108603505B (zh) 2016-02-15 2016-02-15 旋转式压缩机的制造方法
CZ2018394A CZ308843B6 (cs) 2016-02-15 2016-02-15 Způsob výroby rotačního kompresoru
JP2017567578A JP6607971B2 (ja) 2016-02-15 2016-02-15 ロータリ圧縮機の製造方法
PCT/JP2016/054266 WO2017141309A1 (ja) 2016-02-15 2016-02-15 ロータリ圧縮機
KR1020187018808A KR102089805B1 (ko) 2016-02-15 2016-02-15 로터리 압축기 및 로터리 압축기의 제조 방법

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2016/054266 WO2017141309A1 (ja) 2016-02-15 2016-02-15 ロータリ圧縮機

Publications (1)

Publication Number Publication Date
WO2017141309A1 true WO2017141309A1 (ja) 2017-08-24

Family

ID=59625635

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2016/054266 WO2017141309A1 (ja) 2016-02-15 2016-02-15 ロータリ圧縮機

Country Status (5)

Country Link
JP (1) JP6607971B2 (cs)
KR (1) KR102089805B1 (cs)
CN (1) CN108603505B (cs)
CZ (1) CZ308843B6 (cs)
WO (1) WO2017141309A1 (cs)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7285953B2 (ja) * 2019-11-21 2023-06-02 三菱電機株式会社 回転式圧縮機および冷凍サイクル装置

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011127475A (ja) * 2009-12-16 2011-06-30 Toshiba Carrier Corp 多気筒ロータリ式圧縮機と冷凍サイクル装置

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6421286U (cs) * 1987-07-28 1989-02-02
KR930008486B1 (ko) * 1991-07-03 1993-09-07 주식회사 금성사 밀폐형 왕복동식 압축기의 압축구조
JP3511680B2 (ja) * 1994-08-02 2004-03-29 株式会社日立製作所 ロータリ圧縮機
CZ285286B6 (cs) * 1996-04-09 1999-06-16 Jaroslav B. Ing. Struha Kompresor nebo spalovací motor s oběžnými písty
CN2570500Y (zh) * 2002-04-29 2003-09-03 上海日立电器有限公司 叶片槽带润滑油孔的旋转式压缩机气缸
KR20100034914A (ko) * 2008-09-25 2010-04-02 삼성전자주식회사 로터리 압축기용 실린더 및 이를 구비한 로터리 압축기
JP5631398B2 (ja) * 2010-07-08 2014-11-26 パナソニック株式会社 ロータリ圧縮機及び冷凍サイクル装置
CN103946554B (zh) * 2011-11-16 2016-06-22 松下电器产业株式会社 旋转压缩机
CN103629115B (zh) * 2012-08-22 2016-09-28 上海日立电器有限公司 滚动转子式压缩机斜置式叶片槽结构
JP2014040815A (ja) * 2012-08-23 2014-03-06 Daikin Ind Ltd ロータリー圧縮機
JP2014070596A (ja) 2012-09-28 2014-04-21 Fujitsu General Ltd ロータリ圧縮機
JP6070069B2 (ja) * 2012-10-30 2017-02-01 株式会社富士通ゼネラル ロータリ圧縮機

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011127475A (ja) * 2009-12-16 2011-06-30 Toshiba Carrier Corp 多気筒ロータリ式圧縮機と冷凍サイクル装置

Also Published As

Publication number Publication date
KR20180090324A (ko) 2018-08-10
CN108603505A (zh) 2018-09-28
CZ308843B6 (cs) 2021-07-07
JPWO2017141309A1 (ja) 2018-09-13
JP6607971B2 (ja) 2019-11-20
CZ2018394A3 (cs) 2018-09-26
KR102089805B1 (ko) 2020-03-17
CN108603505B (zh) 2020-09-15

Similar Documents

Publication Publication Date Title
US8419394B2 (en) Hermetic compressor including a backflow preventing portion and refrigeration cycle device having the same
US8043079B2 (en) Hermetic compressor and refrigeration cycle device having the same
JP6787480B2 (ja) ロータリ圧縮機
KR20060051788A (ko) 압축기
JP6479206B2 (ja) ロータリ圧縮機
JP2012219654A (ja) 回転式流体機械
JP6134903B2 (ja) 容積型圧縮機
JP6607971B2 (ja) ロータリ圧縮機の製造方法
CN109153063B (zh) 压缩机、压缩机的制造方法以及扩管器具
WO2020170886A1 (ja) 密閉型圧縮機
JP2014136985A (ja) スクロール型圧縮機
JP5781355B2 (ja) 密閉型ロータリ圧縮機
JP2017172346A (ja) スクロール圧縮機、及び、空気調和機
JP5355361B2 (ja) 密閉型回転圧縮機
JP2009127517A (ja) 密閉型圧縮機
JP2014234785A (ja) スクロール圧縮機
JP6518026B1 (ja) 圧縮機、及び、これを備える冷凍サイクル装置
KR100738712B1 (ko) 스크롤 압축기의 오일공급구조
KR102182171B1 (ko) 스크롤 압축기
JP2019035391A (ja) 圧縮機
KR200382915Y1 (ko) 압축기용 어큐뮬레이터의 연결 구조
KR101698085B1 (ko) 밀폐형 압축기
KR101738454B1 (ko) 밀폐형 압축기
JP5520762B2 (ja) スクロール圧縮機，電動圧縮機
JP4573614B2 (ja) 圧縮機

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 16890452

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2017567578

Country of ref document: JP

Kind code of ref document: A

ENP Entry into the national phase

Ref document number: 20187018808

Country of ref document: KR

Kind code of ref document: A

WWE Wipo information: entry into national phase

Ref document number: 1020187018808

Country of ref document: KR

WWE Wipo information: entry into national phase

Ref document number: PV2018-394

Country of ref document: CZ

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 16890452

Country of ref document: EP

Kind code of ref document: A1