US20120308425A1 - Rotary compressor - Google Patents

Rotary compressor Download PDF

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Publication number
US20120308425A1
US20120308425A1 US13/454,704 US201213454704A US2012308425A1 US 20120308425 A1 US20120308425 A1 US 20120308425A1 US 201213454704 A US201213454704 A US 201213454704A US 2012308425 A1 US2012308425 A1 US 2012308425A1
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United States
Prior art keywords
compressing unit
copper tube
injection
hole
horizontal hole
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US13/454,704
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English (en)
Inventor
Taku Morishita
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Fujitsu General Ltd
Original Assignee
Fujitsu General Ltd
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 Fujitsu General Ltd filed Critical Fujitsu General Ltd
Assigned to FUJITSU GENERAL LIMITED reassignment FUJITSU GENERAL LIMITED ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MORISHITA, TAKU
Publication of US20120308425A1 publication Critical patent/US20120308425A1/en
Abandoned legal-status Critical Current

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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
    • 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
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • 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
    • F04C2240/805—Fastening means, e.g. bolts
    • 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

Definitions

  • a conventional hermetic rotary compressor comprises, in a closed container, a driver and a rotary compression element that is driven by the driver and includes two cylinders.
  • Japanese Laid-open Patent Publication No. H7-127575 discloses a conventional technology for cooling such a hermetic rotary compressor, in which a mounting metal piece fixed to an injection copper tube by pressure bonding or welding is positioned precisely to the center in the thickness direction of a partition board between the two cylinders.
  • the inner diameter of a vertical through small hole for injection in the partition board is equal to the length to the upper and lower cylinders so that the same amount of refrigerant liquid is injected to the cylinders.
  • the mounting metal piece fixed to the injection copper tube is attached to the partition board by screws.
  • the mounting metal piece In the conventional technology, if the mounting metal piece is fixed to the injection copper tube by pressure bonding, it cannot be fixed reliably because the injection copper tube is soft. If the mounting metal piece is fixed to the injection copper tube by welding, it cannot also be fixed reliably because the stress concentrates on a welding part due to the vibration of the rotary compressor. Further, the attachment of the mounting metal piece to the partition board with screws increases the cost by screwing.
  • a rotary compressor is configured to suck in refrigerant gas from the low pressure side of a refrigeration cycle, compress the refrigerant gas, and discharge the refrigerant gas to the high pressure side of the refrigeration cycle.
  • the rotary compressor includes a compressor housing, a first compressing, a second compressing unit, and a partition board.
  • the first compressing unit and the second compressing unit are located in the compressor housing, and are arranged one on top of another with the partition board between them.
  • the partition board is provided with a vertical hole that is communicated with the first compressing unit and the second compressing unit, and a horizontal hole that is communicated with the vertical hole.
  • An injection copper tube to inject a refrigerant liquid to the first compressing unit and the second compressing unit is loose fit in the horizontal hole.
  • a columnar injection liner provided with an aperture and having an outer diameter larger than the inner diameter of the injection copper tube is inserted into the injection copper tube from the back end.
  • the injection liner is pressed into the injection copper tube up to the front end to increase the diameter of the front end of the injection copper tube, which is loose fit in the horizontal hole, such that the injection copper tube is tight fit in the horizontal hole.
  • FIG. 1 is a vertical cross-sectional view of a rotary compressor according to an embodiment
  • FIG. 2 is a horizontal cross-sectional view of first and second compressing units
  • FIG. 3 is a partially enlarged vertical cross-sectional view of a compressing unit of the rotary compressor according to the embodiment.
  • FIG. 4 is an enlarged view of a portion A in FIG. 3 .
  • FIG. 1 is a vertical cross-sectional view of a rotary compressor according to an embodiment.
  • FIG. 2 is a horizontal cross-sectional view of first and second compressing units.
  • FIG. 3 is a partially enlarged vertical cross-sectional view of a compressing unit of the rotary compressor according to the embodiment.
  • FIG. 4 is an enlarged view of a portion A in FIG. 3 .
  • a rotary compressor 1 of the embodiment comprises a compressor housing 10 , a compressing unit 12 , and a motor 11 .
  • the compressor housing 10 is a vertically placed cylindrical sealed housing.
  • the compressing unit 12 is located in the lower part of the compressor housing 10 .
  • the motor 11 is located in the upper part of the compressor housing 10 and drives the compressing unit 12 via a rotation shaft 15 .
  • the motor 11 includes a starter 111 and a rotor 112 .
  • the starter 111 is shrink fit to the inner periphery of the compressor housing 10 to be fixed thereto.
  • the rotor 112 is located in the center of the starter 111 and is shrink fit to the rotation shaft 15 to be fixed thereto.
  • the rotation shaft 15 mechanically connects between the motor 11 and the compressing unit 12 .
  • the compressing unit 12 comprises a first compressing unit 12 S and a second compressing unit 12 T.
  • the second compressing unit 12 T is located in parallel above the first compressing unit 12 S.
  • the first compressing unit 12 S includes a first cylinder 121 S having a first flared portion 122 S.
  • the second compressing unit 12 T includes a second cylinder 121 T having a second flared portion 122 T.
  • the first flared portion 122 S is provided with a first inlet 135 S, a first vane groove 128 S, and a first back-pressure chamber 129 S.
  • the second flared portion 122 T is provided with a second inlet 135 T, a second vane groove 128 T, and a second back-pressure chamber 129 T.
  • the first cylinder 121 S and the second cylinder 121 T have a circular first cylinder inner wall 123 S and a circular second cylinder inner wall 123 T, respectively, which are formed concentric with the motor 11 .
  • a first annular piston 125 S and a second annular piston 125 T are arranged, respectively, which have a smaller outer diameter than the inner diameter of the cylinders.
  • a first operation chamber 130 S compression space
  • a second operation chamber 130 T compression space
  • the first operation chamber 130 S and the second operation chamber 130 T compress refrigerant gas sucked therein and discharge the compressed refrigerant gas.
  • the first vane groove 128 S is formed from the first cylinder inner wall 123 S along the radial direction over the height of the first cylinder 121 S.
  • a flat plate-like first vane 127 S is slideably fitted in the first vane groove 128 S in an air-tight manner.
  • the second vane groove 128 T is formed from the second cylinder inner wall 123 T along the radial direction over the height of the second cylinder 121 T.
  • a flat plate-like second vane 127 T is slideably fitted in the second vane groove 128 T in an air-tight manner.
  • a first spring hole 124 S and a second spring hole 124 T are formed to be communicated with the first vane groove 128 S and the second vane groove 128 T from the periphery of the first flared portion 122 S and the second flared portion 122 T, respectively.
  • a vane spring (not illustrated) to press the back of the first vane 127 S and the second vane 127 T.
  • the first vane 127 S protrudes from the first vane groove 128 S into the first operation chamber 130 S
  • the second vane 127 T protrudes from the second vane groove 128 T into the second operation chamber 130 T.
  • the end of the first vane 127 S and the second vane 127 T comes in contact with the peripheral surface of the first annular piston 125 S and the second annular piston 125 T.
  • the first vane 127 S partitions the first operation chamber 130 S (compression space) into a first inlet chamber 131 S and a first compression chamber 133 S
  • the second vane 127 T partitions the second operation chamber 130 T (compression space) into a second inlet chamber 131 T and a second compression chamber 133 T.
  • the first back-pressure chamber 129 S is formed to allow the bottom of the first vane groove 128 S to be communicated with the inside of the compressor housing 10 through an opening R illustrated in FIG. 1 to introduce compressed refrigerant gas inside the compressor housing 10 .
  • the second back-pressure chamber 129 T is formed to allow the bottom of the second vane groove 128 T to be communicated with the inside of the compressor housing 10 through the opening R to introduce compressed refrigerant gas inside the compressor housing 10 .
  • the first back-pressure chamber 129 S and the second back-pressure chamber 129 T apply a back pressure to the first vane 127 S and the second vane 127 T, respectively, by the pressure of the compressed refrigerant gas.
  • the first flared portion 122 S of the first cylinder 121 S is provided with the first inlet 135 S that allows the first inlet chamber 131 S to be communicated with the outside so that refrigerant can be sucked into the first inlet chamber 131 S from the outside.
  • the second flared portion 122 T of the second cylinder 121 T is provided with the second inlet 135 T that allows the second inlet chamber 131 T to be communicated with the outside so that refrigerant can be sucked into the second inlet chamber 131 T from the outside.
  • a partition board 140 is located between the first cylinder 121 S and the second cylinder 121 T to partition between the first operation chamber 130 S of the first cylinder 121 S and the second operation chamber 130 T of the second cylinder 121 T.
  • a lower end plate 160 S is arranged at the lower end of the first cylinder 121 S to close the first operation chamber 130 S of the first cylinder 121 S.
  • an upper end plate 160 T is arranged at the upper end of the second cylinder 121 T to close the second operation chamber 130 T of the second cylinder 121 T.
  • a lower bearing 161 S is formed in the lower end plate 160 S.
  • the lower bearing 161 S rotatably supports a lower-bearing support portion 151 of the rotation shaft 15 .
  • An upper bearing 161 T is formed in the upper end plate 160 T.
  • the upper bearing 161 T rotatably supports an upper-bearing support portion 153 of the rotation shaft 15 .
  • the rotation shaft 15 is provided with a first eccentric portion 152 S and a second eccentric portion 152 T, the phases of which are shifted by 180° to be eccentric.
  • the first eccentric portion 152 S is rotatably fitted to the first annular piston 125 S of the first compressing unit 12 S.
  • the second eccentric portion 152 T is rotatably fitted to the second annular piston 125 T of the second compressing unit 12 T.
  • the first annular piston 125 S rotates and revolves counterclockwise in FIG. 2 along the first cylinder inner wall 123 S in the first cylinder 121 S.
  • the second annular piston 125 T rotates and revolves counterclockwise in FIG. 2 along the second cylinder inner wall 123 T in the second cylinder 121 T.
  • the first vane 127 S and the second vane 127 T move back and forth.
  • the compressing unit 12 continuously sucks in refrigerant gas and compresses it, thereby discharging the compressed refrigerant gas.
  • a lower muffler cover 170 S is located below the lower end plate 160 S such that a lower muffler chamber 180 S is formed between the lower end plate 160 S and the lower muffler cover 170 S.
  • the first compressing unit 12 S is open to the lower muffler chamber 180 S. That is, near the first vane 127 S of the lower end plate 160 S, there is provided a first outlet 190 S (see FIG. 2 ) that allows the first compression chamber 133 S of the first cylinder 121 S to be communicated with the lower muffler chamber 180 S.
  • the first outlet 190 S is provided with a first outlet valve 200 S that prevents the backflow of compressed refrigerant gas.
  • the lower muffler chamber 180 S is a circular chamber and is part of a communication path that allows the outlet side of the first compressing unit 12 S to be communicated with the inside of an upper muffler chamber 180 T via a refrigerant path 136 (see FIG. 2 ) passing through the lower end plate 160 S, the first cylinder 121 S, the partition board 140 , the second cylinder 121 T, and the upper end plate 160 T.
  • the lower muffler chamber 180 S reduces the pressure pulsation of discharged refrigerant gas.
  • a first outlet valve cap 201 S and the first outlet valve 200 S are fixed one on top of the other by a rivet to control the warping opening amount of the first outlet valve 200 S.
  • an upper muffler cover 170 T is located above the upper end plate 160 T such that the upper muffler chamber 180 T is formed between the upper end plate 160 T and the upper muffler cover 170 T.
  • a second outlet 190 T Near the second vane 127 T of the upper end plate 160 T, there is provided a second outlet 190 T (see FIG. 2 ) that allows the second compression chamber 133 T of the second cylinder 121 T to be communicated with the upper muffler chamber 180 T.
  • the second outlet 190 T is provided with a second outlet valve 200 T that prevents the backflow of compressed refrigerant gas.
  • a second outlet valve cap 201 T and the second outlet valve 200 T are fixed one on top of the other by a rivet to control the warping opening amount of the second outlet valve 200 T.
  • the upper muffler chamber 180 T reduces the pressure pulsation of discharged refrigerant gas.
  • the first cylinder 121 S, the lower end plate 160 S, the lower muffler cover 170 S, the second cylinder 121 T, the upper end plate 160 T, the upper muffler cover 170 T, and the partition board 140 are integrally fastened by a bolt 175 .
  • the compressing unit 12 integrally fastened by the bolt 175 the outer periphery of the upper end plate 160 T is fixed to the compressor housing 10 by spot welding, and thereby the compressing unit 12 is fixed to the compressor housing 10 .
  • a first through hole 101 and a second through hole 102 are formed in this order from the bottom to be separated from each other in the axial direction to let a first inlet tube 104 and a second inlet tube 105 pass therethrough.
  • an accumulator 25 formed of an independent cylindrical sealed container is held by an accumulator holder 252 and an accumulator band 253 .
  • the top center of the accumulator 25 is connected to a system connecting pipe 255 that is connected to the low pressure side of the refrigeration cycle.
  • the accumulator 25 is provided with a bottom through hole 257 at the bottom.
  • the bottom through hole 257 is connected to a first low-pressure communication tube 31 S and a second low-pressure communication tube 31 T.
  • One end of the first low-pressure communication tube 31 S and the second low-pressure communication tube 31 T extends to the upside in the accumulator 25 , and the other end is connected to an end of the first inlet tube 104 and the second inlet tube 105 .
  • the first low-pressure communication tube 31 S and the second low-pressure communication tube 31 T guide the low-pressure refrigerant of the refrigeration cycle to the first compressing unit 12 S and the second compressing unit 12 T, respectively, via the accumulator 25 .
  • the first low-pressure communication tube 31 S is connected to the first inlet 135 S (see FIG. 2 ) of the first cylinder 121 S via the first inlet tube 104 as an inlet.
  • the second low-pressure communication tube 31 T is connected to the second inlet 135 T (see FIG. 2 ) of the second cylinder 121 T via the second inlet tube 105 as an inlet. That is, the first inlet 135 S and the second inlet 135 T are communicated in parallel with the low pressure side of the refrigeration cycle.
  • the top of the compressor housing 10 is connected to an outlet tube 107 that is connected to the high pressure side of the refrigeration cycle to discharge high-pressure refrigerant gas to the high pressure side of the refrigeration cycle. That is, the first outlet 190 S and the second outlet 190 T are communicated with the high pressure side of the refrigeration cycle.
  • Lubricant oil is enclosed in the compressor housing 10 up to about the height of the second cylinder 121 T.
  • the lubricant oil circulates in the compressing unit 12 by a vane pump (not illustrated) inserted beneath the rotation shaft 15 .
  • the lubricant oil seals a portion that partitions the compression space of compressed refrigerant with the lubrication of sliding parts and tiny gaps.
  • the partition board 140 is provided with a vertical hole 141 and a horizontal hole 143 .
  • the vertical hole 141 is communicated with the first operation chamber 130 S of the first compressing unit 12 S and the second operation chamber 130 T of the second compressing unit 12 T.
  • the horizontal hole 143 is communicated with the vertical hole 141 via a horizontal communication hole 142 .
  • An front end portion 144 a of an injection copper tube 144 for liquid injection is loose fit in the horizontal hole 143 .
  • the inner diameter of the horizontal communication hole 142 is smaller than that of the horizontal hole 143 , and is larger than the inner diameter (for example, 1.0 ⁇ ) of an aperture 145 a of an injection liner 145 , which will be described later.
  • the vertical hole 141 which is located separate from the horizontal hole 143 , is communicated with the horizontal hole 143 through the horizontal communication hole 142 having a small inner diameter. Accordingly, the machine work is easier compared to the case where the horizontal hole 143 having a large inner diameter is directly communicated with the vertical hole 141 .
  • the front end portion 144 a of the injection copper tube 144 and an end portion of the injection liner 145 come in contact with an end surface of the horizontal hole 143 and thus are positioned, resulting in effective assembly.
  • the front end portion 144 a of the injection copper tube 144 passing through the compressor housing 10 is loose fit in the horizontal hole 143 .
  • the columnar injection liner 145 provided with the aperture 145 a and having an outer diameter larger than the inner diameter of the injection copper tube 144 is inserted into the injection copper tube 144 from a back end portion 144 b and is pressed up to the front end portion 144 a.
  • This increases the diameter of the front end portion 144 a of the injection copper tube 144 which is loose fit in the horizontal hole 143 , to be tight fit in the horizontal hole 143 .
  • an injection communication tube 146 is connected to the back end portion 144 b of the injection copper tube 144 .
  • the injection copper tube 144 has an outer diameter a of 6.35 ⁇ , an inner diameter b of 4.75 ⁇ , and a thickness c of 0.8 mm.
  • the inner diameter d of the horizontal hole 143 is 6.5 ⁇ (a gap 0.15 mm)
  • the outer diameter e of the injection liner 145 is larger than the inner diameter b of the injection copper tube 144 by about 0.2 ⁇ , i.e., 4.95 ⁇
  • the front end portion 144 a of the injection copper tube 144 is pressure bonded to the horizontal hole 143 (interference 0.05 mm) and can be firmly fixed in an air-tight manner.
  • the injection liner 145 is preferably made of an iron-based material (for example, carbon steel S45C, S50C, etc.).
  • the aperture 145 a (for example, having an inner diameter of 1.0 ⁇ ) of the injection liner 145 prevents an excessive increase in injection amount to the first operation chamber 130 S of the first compressing unit 12 S and the second operation chamber 130 T of the second compressing unit 12 T.
  • the aperture 145 a can serve as a capillary tube as a narrow tube that prevents the backflow of compressed refrigerant.
  • the injection copper tube 144 can be reliably fixed to the partition board 140 . Moreover, since screw fixing and a capillary tube are not used, the rotary compressor can be obtained at a low cost.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US13/454,704 2011-06-03 2012-04-24 Rotary compressor Abandoned US20120308425A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011-124892 2011-06-03
JP2011124892A JP2012251485A (ja) 2011-06-03 2011-06-03 ロータリ圧縮機

Publications (1)

Publication Number Publication Date
US20120308425A1 true US20120308425A1 (en) 2012-12-06

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
US13/454,704 Abandoned US20120308425A1 (en) 2011-06-03 2012-04-24 Rotary compressor

Country Status (5)

Country Link
US (1) US20120308425A1 (ja)
EP (1) EP2530324B1 (ja)
JP (1) JP2012251485A (ja)
CN (1) CN102808768B (ja)
AU (1) AU2012202072B9 (ja)

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WO2014144870A3 (en) * 2013-03-15 2015-11-26 Abbott Laboratories Light-blocking system for a diagnostic analyzer
US9322405B2 (en) 2013-10-29 2016-04-26 Emerson Climate Technologies, Inc. Rotary compressor with vapor injection system
US9841024B2 (en) * 2013-10-29 2017-12-12 Daikin Industries, Ltd. Compressor and method for producing compressor
US10436199B2 (en) 2015-12-21 2019-10-08 Fujitsu General Limited Rotary compressor
US11225971B2 (en) * 2017-07-27 2022-01-18 Fujitsu General Limited Rotary compressor
EP4206469A4 (en) * 2020-10-30 2024-02-07 Daikin Industries, Ltd. ROTARY COMPRESSOR

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CN104005958B (zh) * 2013-02-26 2017-06-20 上海日立电器有限公司 双转子压缩机中间板的防喷射窜气结构
JP6051936B2 (ja) * 2013-02-26 2016-12-27 株式会社富士通ゼネラル ロータリ圧縮機及びその組立方法
CN105402128A (zh) * 2014-09-12 2016-03-16 上海日立电器有限公司 旋转式压缩机的缸体结构及空调***
CN105020135A (zh) * 2015-08-18 2015-11-04 武汉凌达压缩机有限公司 一种制冷***及其压缩机
CN105156299B (zh) * 2015-08-18 2018-08-10 珠海格力电器股份有限公司 压缩机及其装配工艺
CN110469510B (zh) * 2018-05-11 2021-11-09 上海海立电器有限公司 压缩机
CN112513466B (zh) 2018-08-07 2022-11-04 三菱电机株式会社 旋转式压缩机和制冷循环装置

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EP2530324A3 (en) 2017-04-12
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EP2530324A2 (en) 2012-12-05

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