WO2020105171A1 - ロータリ式圧縮機 - Google Patents

ロータリ式圧縮機

Info

Publication number
WO2020105171A1
WO2020105171A1 PCT/JP2018/043177 JP2018043177W WO2020105171A1 WO 2020105171 A1 WO2020105171 A1 WO 2020105171A1 JP 2018043177 W JP2018043177 W JP 2018043177W WO 2020105171 A1 WO2020105171 A1 WO 2020105171A1
Authority
WO
WIPO (PCT)
Prior art keywords
spring
cylinder
hole
compression mechanism
vane
Prior art date
Application number
PCT/JP2018/043177
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
公平 櫻田
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 PCT/JP2018/043177 priority Critical patent/WO2020105171A1/ja
Priority to CN201880099484.6A priority patent/CN113056609B/zh
Priority to JP2020557101A priority patent/JPWO2020105171A1/ja
Priority to CZ2021220A priority patent/CZ309342B6/cs
Publication of WO2020105171A1 publication Critical patent/WO2020105171A1/ja

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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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • 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

Definitions

  • the present invention relates to a rotary compressor, and more specifically to a spring fixing structure for pressing a vane against a piston.
  • a conventional rotary compressor has an annular cylinder, a piston that rotates in a cylinder chamber formed in the cylinder, a vane that advances and retreats in a through hole that radially penetrates the cylinder, and the tip of the vane is the outer circumference of the piston. And a spring for pressing the vane so as to abut the surface.
  • the spring is accommodated in a through hole formed in the cylinder in the radial direction so as to be expandable and contractible in the radial direction, and the end of the spring is screwed and held in a spiral groove formed on the inner peripheral surface of the through hole.
  • the present invention has been made to solve the above problems, and an object of the present invention is to provide a rotary compressor that can improve insertability when screwing a spring into a through hole.
  • a rotary compressor according to the present invention is a rotary compressor including a compression mechanism portion that compresses a refrigerant, and the compression mechanism portion includes an annular cylinder and a piston that rotates in a cylinder chamber formed in the cylinder. And a vane that advances and retracts in a through hole that radially penetrates the cylinder, and a spring that presses the vane so that the tip of the vane contacts the outer peripheral surface of the piston.
  • the spring is fixed to the through hole by screwing the end turn part, which is the male screw part, into the female screw part formed on the inner peripheral surface of the through hole. It has a gripping part that is folded back into.
  • the spring is provided with the grip portion, the insertability when screwing the spring into the through hole can be improved.
  • FIG. 3 is a schematic vertical cross-sectional view of the rotary compressor according to Embodiment 1 of the present invention.
  • FIG. 3 is a schematic cross-sectional view of a compression mechanism portion of the rotary compressor according to Embodiment 1 of the present invention. It is a figure which shows the fixing structure of the spring of the rotary compressor in Embodiment 1 of this invention. It is a figure which shows the spring of FIG. It is the figure which looked at the end turn part of the spring of FIG. 3 from the rear end part side. It is a figure which shows the fixing structure of the spring of the rotary compressor in Embodiment 2 of this invention.
  • Embodiment 1. 1 is a schematic vertical sectional view of a rotary compressor according to Embodiment 1 of the present invention.
  • FIG. 2 is a schematic transverse sectional view of a compression mechanism portion of the rotary compressor according to Embodiment 1 of the present invention.
  • the rotary compressor is one of the components of a refrigerant circuit used in a heat pump device such as an air conditioner, a refrigerating device, a refrigerating device, or a water heater.
  • the rotary compressor is a hermetic electric compressor, and has a configuration in which a compression mechanism section 3 and an electric mechanism section 2 for driving the compression mechanism section 3 via a rotary shaft 4 are arranged in a hermetic container 1. Have.
  • the compression mechanism part 3 is arranged in the lower part of the closed container 1, and the electric mechanism part 2 is arranged in the upper part of the closed container 1.
  • a space A is provided between the compression mechanism section 3 and the electric mechanism section 2.
  • the closed container 1 is composed of, for example, a cylindrical central container 1a, an upper container 1b, and a lower container 1c.
  • the upper container 1b is fitted in the upper opening of the central container 1a
  • the lower container 1c is fitted in the lower opening of the central container 1a, so that the inside of the closed container 1 is in a hermetically sealed state.
  • a discharge pipe 5 is connected to the upper container 1b.
  • the discharge pipe 5 is a connection pipe for discharging the high-temperature and high-pressure gas refrigerant in the closed container 1 compressed by the compression mechanism unit 3 to the refrigerant pipe.
  • Lubricating oil is stored in the lower part of the closed container 1, and the lubricating oil is pumped up by an oil supply mechanism (not shown) provided at the lower end of the rotary shaft 4 to supply the oil to the respective parts. Lubrication is maintained.
  • the electric mechanism section 2 includes a stator 2a and a rotor 2b.
  • the rotor 2b is fixed to the rotary shaft 4, and the rotary shaft 4 is rotated by the rotation of the rotor 2b, and the rotary power is transmitted to the compression mechanism unit 3.
  • a gas hole 21 is formed in the rotor 2b so as to penetrate therethrough in the rotation axis direction.
  • An air gap 22 is provided between the rotor 2b and the stator 2a.
  • the gas holes 21 and the air gaps 22 are passages through which the refrigerant gas passes, and the refrigerant gas discharged from the compression mechanism section 3 moves above the electric mechanism section 2 through the passages, and the discharge pipe 5 Is discharged from the outside.
  • the compression mechanism section 3 includes a first compression mechanism section 30A, a second compression mechanism section 30B, an upper bearing 40 arranged on the upper end surface of the first compression mechanism section 30A, and a lower end surface of the second compression mechanism section 30B.
  • the lower bearing 50 and the intermediate plate 60 are provided.
  • the upper bearing 40 includes a hollow cylindrical bearing portion 41 that rotatably supports the rotating shaft 4, and a flat plate annular end plate 42 that closes an upper end surface of a cylinder 31 described later.
  • the lower bearing 50 includes a hollow cylindrical bearing portion 51 that rotatably supports the rotating shaft 4 and a flat plate-shaped end plate 52 that closes a lower end surface of a cylinder 31 described later.
  • each of the end plate 42 and the end plate 52 is formed with a discharge port 42a and a discharge port 52a provided with a discharge valve that opens when a pressure in a compression chamber, which will be described later, becomes equal to or higher than a predetermined pressure.
  • a muffler 43 and a muffler 53 are attached to the end plates 42 and 52 so as to cover the discharge ports.
  • first compression mechanism section 30A and the second compression mechanism section 30B of the compression mechanism section 3 will be described. Since the first compression mechanism unit 30A and the second compression mechanism unit 30B have basically the same configuration, the first compression mechanism unit 30A will be described below as a representative.
  • the first compression mechanism portion 30A includes an annular cylinder 31 having a through hole that penetrates in the rotation axis direction, a piston 32 that rotates in a cylinder chamber (described later) formed in the cylinder 31, and a vane 33.
  • the upper bearing 40 and the intermediate plate 60 are disposed on both end surfaces of the cylinder 31 in the rotational axis direction, and the through hole is closed by the end plate 42 of the upper bearing 40 and the intermediate plate 60, so that the inside of the cylinder 31 is closed.
  • a cylinder chamber 44 is formed in the.
  • the piston 32 is housed in the cylinder chamber 44 in the cylinder 31 while being rotatably fitted to the eccentric portion 4a of the rotary shaft 4.
  • a through hole 34 is formed in the cylinder 31 to penetrate the cylinder 31 in the radial direction.
  • the through hole 34 has a front end communicating with the cylinder chamber 44 and a rear end opening to the outer peripheral surface of the cylinder 31.
  • the vane 33 is arranged in the through hole 34 so as to be movable back and forth in the radial direction.
  • a spring 35 is arranged radially outside the vane 33 in the through hole 34 and is pressed radially inward by the spring 35 so that the tip 33b of the vane 33 is always in contact with the piston 32. In this way, the tip end portion 33b of the vane 33 contacts the piston 32, whereby the inside of the cylinder chamber 44 is partitioned into the suction chamber 44a and the compression chamber 44b.
  • the cylinder 31 is provided with a suction port 36 that penetrates the vane 33 in the radial direction on both sides, and a discharge notch 37 that communicates with a discharge port 42 a formed in an end plate 42 of the upper bearing 40.
  • An outlet pipe 73 of the accumulator 70 which will be described later, is connected to the suction port 36 from the outside of the central container 1a of the closed container 1.
  • the discharge notch 37 communicates with a discharge port 42 a formed in the end plate 42 of the upper bearing 40.
  • the member that closes the through hole formed in the substantially center of the cylinder 31 of the second compression mechanism portion 30B is the intermediate plate 60 and the lower bearing 50, and the first compression mechanism portion 30A.
  • other configurations are basically the same as those of the first compression mechanism portion 30A.
  • the accumulator 70 includes a container 71, an inflow pipe 72, an outflow pipe 73, and an inner pipe 74 that communicates with the outflow pipe 73 inside the container 71.
  • the accumulator 70 separates the refrigerant flowing into the container 71 from the inflow pipe 72 into a liquid refrigerant and a gas refrigerant.
  • the separated gas medium flows out of the container 71 through the inner pipe 74, passes through the outflow pipe 73, and flows into the suction chamber 44 a of the cylinder chamber 44 from the suction port 36 of the cylinder 31.
  • the operation of the rotary compressor according to the first embodiment will be described.
  • the electric mechanism unit 2 rotates the rotating shaft 4.
  • the eccentric portion 4a of the rotating shaft 4 rotates eccentrically in the cylinder chamber 44
  • the piston 32 rotates eccentrically in the cylinder chamber 44.
  • the gas refrigerant is sucked from the accumulator 70 into the suction chamber 44a of the cylinder chamber 44 through the suction port 36.
  • the sucked gas refrigerant is compressed as the volume of the compression chamber 44b is gradually reduced as the piston 32 rotates.
  • the compressed gas refrigerant When the compressed gas refrigerant reaches a predetermined pressure, it is discharged into the internal space B of the silencer 43 through the discharge notch 37 of the cylinder 31 through the discharge port 42a provided in the upper bearing 40.
  • the gas refrigerant discharged into the internal space B of the silencer 43 is discharged into the space A in the closed container 1 from a discharge port (not shown) provided in the silencer 43.
  • the gas refrigerant sucked from the accumulator 70 is compressed and discharged into the space inside the closed container 1.
  • the rotation and rotation of the rotary shaft 4 causes the refrigerant gas to be sucked and compressed repeatedly.
  • the gas refrigerant compressed in each of the first compression mechanism section 30A and the second compression mechanism section 30B and discharged into the space in the closed container is a gap formed in the electric mechanism section 2, that is, the gas hole 21 and the air. It reaches the upper part in the closed container 1 through the gap 22 and is discharged from the discharge pipe 5 to the refrigerant circuit.
  • a flammable refrigerant such as R290 is used as the refrigerant, but the kind of the refrigerant is not limited to this.
  • the characteristic structure of the first embodiment is the fixing structure of the spring 35.
  • the fixing structure of the spring 35 will be described below.
  • the first compression mechanism 30A and the second compression mechanism 30B have the same spring fixing structure. Therefore, in this specification, the fixing structure of the spring 35 will be described on behalf of the first compression mechanism portion 30A.
  • FIG. 3 is a diagram showing a spring fixing structure of the rotary compressor according to the first embodiment of the present invention.
  • FIG. 4 is a diagram showing the spring of FIG.
  • FIG. 5 is a view of the end turn portion of the spring of FIG. 3 viewed from the rear end side.
  • the spring 35 is formed by spirally winding an elastic wire.
  • the end turn portion 35a on the rear end side of the spring 35 has a larger diameter than the tip end portion 35b.
  • a grip portion 35c is formed at the end of the end turn portion 35a.
  • the grip portion 35c is configured by a folded portion in which the end of the end turn portion 35a is folded back in the inner diameter direction of the spring 35.
  • a female screw portion 34a is formed on the radially outer inner peripheral surface of the through hole 34 in which the spring 35 is arranged.
  • the end turn portion 35a, which is the male screw portion, is screwed into the female screw portion 34a, and the spring 35 passes through the through hole. It is fixed to 34.
  • the depth H of the female screw portion 34a of the through hole 34 is larger than the wire diameter J of the spring 35.
  • the diameter K of the female screw portion 34a is smaller than the diameter D of the end turn portion 35a of the spring 35.
  • the operation of the grip portion 35c will be described.
  • an operator grasps the outer periphery of the spring 35 and inserts the spring 35 into the through hole 34 from the outside in the radial direction.
  • the end turn portion 35a is positioned at the radially outer end of the through hole 34, for example, the thumb and the index finger are inserted into the spring 35 to grip the grip portion 35c.
  • the worker rotates the gripping portion while gripping the gripping portion 35c to rotate the spring 35 and screw the end turn portion 35a into the female screw portion 34a.
  • the spring 35 is fixed to the through hole 34.
  • by providing the spring 35 with the grip portion 35c it is possible to improve the insertability when the end turn portion 35a is rotationally inserted into the female screw portion 34a.
  • the grip portion 35c is provided on the end turn portion 35a of the spring 35, the insertability when screwing the spring 35 into the female screw portion 34a can be improved.
  • Embodiment 2 relates to positioning of the insertion position of the spring 35.
  • the points of difference between the second embodiment and the first embodiment will be mainly described.
  • FIG. 6 is a diagram showing a spring fixing structure of the rotary compressor according to the second embodiment of the present invention.
  • the spring 35 is fixed by screwing the end turn portion 35a into the female screw portion 34a. Therefore, the insertion depth L1 of the spring 35 into the through hole 34 of the end turn portion 35a is equal to the radial depth of the female screw portion 34a. Limited by L2. That is, the maximum value of the insertion depth L1 becomes equal to the depth L2 of the female screw portion 34a. Therefore, the insertion depth L1 of the spring 35 can be limited by limiting the depth L2 of the female screw portion 34a.
  • the amount of deformation of the spring 35 during operation is determined by the "cylinder inner diameter”, "piston outer diameter” and "vane length". As described above, the amount of deformation of the spring 35 during operation is determined, so that the spring 35 has a length and a spring constant that take the amount of deformation into consideration. Therefore, if the spring 35 is inserted deeper than necessary into the through hole 34, that is, if the insertion depth L1 is too long, the spring 35 will be installed in the through hole 34 in a state of being compressed more than necessary. .. At the time of operation, the amount of deformation is further added to the state, and therefore, there is a high possibility that the spring 35 will be overstressed and broken.
  • the insertion depth L1 of the spring 35 can be limited by limiting the depth L2 of the female screw portion 34a as described above.
  • the female screw portion 34a is provided in a depth range where the generation of excessive stress on the spring 35 can be avoided.
  • the depth L2 of the female screw portion 34a is set to a length that allows the amount of deformation of the spring 35 during operation in a state where the spring 35 is inserted to the radially inner end of the female screw portion 34a. ing. As a result, the margin of the fatigue strength design of the spring 35 can be reduced.
  • the same effect as that of the first embodiment can be obtained, and the insertion depth L1 of the spring 35 can be limited by the depth L2 of the female screw portion 34a. Therefore, by setting the depth L2 of the female screw portion 34a to a length that allows the amount of deformation of the spring 35 during operation in a state where the spring 35 is inserted to the radially inner end of the female screw portion 34a, The margin of the fatigue strength design of the spring 35 can be reduced.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
PCT/JP2018/043177 2018-11-22 2018-11-22 ロータリ式圧縮機 WO2020105171A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
PCT/JP2018/043177 WO2020105171A1 (ja) 2018-11-22 2018-11-22 ロータリ式圧縮機
CN201880099484.6A CN113056609B (zh) 2018-11-22 2018-11-22 旋转式压缩机
JP2020557101A JPWO2020105171A1 (ja) 2018-11-22 2018-11-22 ロータリ式圧縮機
CZ2021220A CZ309342B6 (cs) 2018-11-22 2018-11-22 Rotační kompresor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2018/043177 WO2020105171A1 (ja) 2018-11-22 2018-11-22 ロータリ式圧縮機

Publications (1)

Publication Number Publication Date
WO2020105171A1 true WO2020105171A1 (ja) 2020-05-28

Family

ID=70773167

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2018/043177 WO2020105171A1 (ja) 2018-11-22 2018-11-22 ロータリ式圧縮機

Country Status (4)

Country Link
JP (1) JPWO2020105171A1 (cs)
CN (1) CN113056609B (cs)
CZ (1) CZ309342B6 (cs)
WO (1) WO2020105171A1 (cs)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5411294U (cs) * 1977-06-25 1979-01-24
JP2002039242A (ja) * 2000-07-26 2002-02-06 Denso Corp コイルスプリング組付け方法およびその装置
JP2010084575A (ja) * 2008-09-30 2010-04-15 Mitsubishi Heavy Ind Ltd ロータリー式圧縮機

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001254690A (ja) * 2000-03-09 2001-09-21 Sanyo Electric Co Ltd 回転式圧縮機
JP3728227B2 (ja) * 2001-09-27 2005-12-21 三洋電機株式会社 ロータリコンプレッサ
CN100376799C (zh) * 2001-09-27 2008-03-26 三洋电机株式会社 压缩机
JP2009228522A (ja) * 2008-03-21 2009-10-08 Daikin Ind Ltd ロータリ圧縮機

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5411294U (cs) * 1977-06-25 1979-01-24
JP2002039242A (ja) * 2000-07-26 2002-02-06 Denso Corp コイルスプリング組付け方法およびその装置
JP2010084575A (ja) * 2008-09-30 2010-04-15 Mitsubishi Heavy Ind Ltd ロータリー式圧縮機

Also Published As

Publication number Publication date
CN113056609B (zh) 2023-03-24
CZ309342B6 (cs) 2022-09-07
CZ2021220A3 (cs) 2021-06-02
JPWO2020105171A1 (ja) 2021-09-02
CN113056609A (zh) 2021-06-29

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