WO2016139731A1 - ロータリ型圧縮機、およびその製造方法 - Google Patents

ロータリ型圧縮機、およびその製造方法 Download PDF

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Publication number
WO2016139731A1
WO2016139731A1 PCT/JP2015/056117 JP2015056117W WO2016139731A1 WO 2016139731 A1 WO2016139731 A1 WO 2016139731A1 JP 2015056117 W JP2015056117 W JP 2015056117W WO 2016139731 A1 WO2016139731 A1 WO 2016139731A1
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WO
WIPO (PCT)
Prior art keywords
mounting groove
vane
vane mounting
cylinder
groove surface
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2015/056117
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English (en)
French (fr)
Japanese (ja)
Inventor
政明 檜田
朴木　継雄
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to CZ2017-565A priority Critical patent/CZ307900B6/cs
Priority to PCT/JP2015/056117 priority patent/WO2016139731A1/ja
Priority to JP2017503234A priority patent/JP6437088B2/ja
Priority to CN201620156234.XU priority patent/CN205478324U/zh
Priority to CN201610115718.4A priority patent/CN105937494B/zh
Publication of WO2016139731A1 publication Critical patent/WO2016139731A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B19/00—Single-purpose machines or devices for particular grinding operations not covered by any other main group
    • B24B19/14—Single-purpose machines or devices for particular grinding operations not covered by any other main group for grinding turbine blades, propeller blades or the like
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • 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
    • F04C29/06—Silencing
    • 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
    • F04C2230/90—Improving properties of machine parts
    • F04C2230/92—Surface treatment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/20—Rotors

Definitions

  • the present invention relates to a rotary compressor related to a vane mounting groove surface of a cylinder for forming a vane mounting groove in the cylinder, and a manufacturing method thereof.
  • a cylinder forming a compression chamber of a rotary compressor has a cylinder inside so that a vane dividing the cylinder into a low pressure side and a high pressure side can slide in the radial direction of the cylinder.
  • a vane mounting groove is provided from the peripheral surface toward the outer periphery.
  • a fixing part for fixing to the tip of the processing apparatus main body, an arm part for holding the grindstone so as to be sandwiched from both side surfaces with a part of the grindstone protruding outside, and driving of the processing apparatus main body
  • a support member composed of a belt that transmits rotational power from a motor (not shown) to the grindstone shaft of the grindstone and a bearing portion that rotatably supports the grindstone shaft of the grindstone is provided at the tip of the processing apparatus main body. In this state, the grindstone is inserted inside the cylinder in the direction perpendicular to the cylinder.
  • JP 7-124818 A Japanese Patent Laid-Open No. 2003-340705
  • the eccentric ring rotates at a high speed, and the vane guided to the vane mounting groove surface of the cylinder contacts the eccentric vane mounting groove surface of the cylinder. Accordingly, the vane mounting groove is reciprocated (slided) while being restrained by a spring.
  • a gap (clearance) is provided between the vane and the vane mounting groove surface, and the vane is slid in the vane mounting groove. If the gap is large between the vane and the vane mounting groove surface, The compressed refrigerant gas in the cylinder leaks from the gap, reducing the compression efficiency and increasing the input of the compressor. Therefore, in the conventional processing method (secondary processing) of the vane mounting groove surface of the cylinder, the gap between the vane and the vane mounting groove surface is filled by grinding the surface to suppress the leakage of the compressed refrigerant gas. As a result, leakage loss was reduced and compression efficiency was improved.
  • the present invention has been made to solve the above-described problems, and an object of the present invention is to provide a rotary compressor capable of suppressing noise and sliding loss, and a manufacturing method thereof.
  • a rotary compressor according to the present invention includes a hermetic container, and a rotary compression mechanism part that is provided inside the hermetic container and compresses a refrigerant, and the rotary compression mechanism part moves from an inner peripheral surface toward an outer periphery. And a vane that is disposed in the vane mounting groove and slides along the vane mounting groove surface that forms the vane mounting groove. Is formed with concave valleys, the pitch W of the valleys is 2 ⁇ m or more and 3 ⁇ m or less, and the protruding valley depth Rvk is 3.0 ⁇ m or more and less than 5.0 ⁇ m in the vane mounting groove surface. Is.
  • the recess-shaped valley portion is formed on the vane attachment groove surface forming the vane attachment groove, and the pitch W of the valley portions is 2 ⁇ m or more and 3 ⁇ m or less.
  • the part depth Rvk is 3 ⁇ m or more and less than 5.0 ⁇ m. Therefore, it is possible to improve the retention of oil that has entered the clearance (clearance) between the vane and the vane mounting groove surface when the vane slides, and the vane sliding property is improved, and noise and sliding loss are reduced. Can be reduced.
  • FIG. 1 is a longitudinal sectional view of a rotary compressor according to an embodiment of the present invention. It is a top view of the rotary compression mechanism part of the rotary compressor which concerns on embodiment of this invention.
  • FIG. 3 is an enlarged view of a main part of FIG. 2. It is a figure which shows the 1st process member fixed to the front-end
  • FIG. 1 is a longitudinal sectional view of a rotary compressor 1 according to an embodiment of the present invention
  • FIG. 2 is a plan view of a rotary compression mechanism section 4 of the rotary compressor 1 according to an embodiment of the present invention
  • FIG. 3 is an enlarged view of a main part of FIG.
  • a rotary compressor 1 according to the present embodiment is a single cylinder type as shown in FIG. 1, and is disposed below a cylindrical sealed container 2 made of a steel plate and an internal space in the sealed container 2.
  • a rotary compression mechanism unit 4 that compresses the refrigerant gas, and an electric element 12 that is disposed above the internal space of the sealed container 2 and that rotates and drives the rotary compression mechanism unit 4 connected via the rotary shaft 3. It is configured.
  • oil that lubricates each bearing is stored in the bottom of the sealed container 2.
  • the rotary compression mechanism 4 includes a hollow cylinder 5 that forms a compression chamber for compressing refrigerant gas, an eccentric portion 8 that is located in the cylinder 5 and is provided on the rotary shaft 3, and this eccentricity. And an eccentric ring 6 attached to the portion 8.
  • the eccentric ring 6 rotates in the cylinder 5 by the rotating shaft 3 driven by the electric element 12.
  • An upper cover 10 and a lower cover 7 that also serve as bearings for the rotary shaft 3 are attached to the upper and lower sides of the cylinder 5, and the opening surface of the cylinder 5 is closed by the upper cover 10 and the lower cover 7.
  • a vane mounting groove 11 for arranging the vane 9 in the cylinder 5 is formed in the cylinder 5 from the inner peripheral surface of the cylinder 5 toward the outer periphery. And the vane 9 arrange
  • an eccentric ring 6 attached to an eccentric portion 8 provided on the rotary shaft 3 rotates at a high speed, and a surface on which the vane mounting groove 11 of the cylinder 5 is formed in the eccentric ring 6 (hereinafter referred to as “the eccentric ring 6”)
  • the vane 9 guided by the vane mounting groove surface 5a) is disposed in the vane mounting groove 11 and reciprocates (slids) in the radial direction along the vane mounting groove surface 5a according to the eccentricity.
  • the refrigerant gas is compressed.
  • FIG. 4 is a view showing the first processing member 20 fixed to the tip portion of the processing apparatus main body used during the secondary processing according to the embodiment of the present invention
  • FIG. 5 shows the embodiment of the present invention. It is the schematic of the grindstone 13 which fixed the abrasive grain to the outer periphery.
  • a processing apparatus main body (not shown) is used at the time of secondary processing for forming the vane mounting groove 11 in the cylinder 5, and the first processing member shown in FIG. 20 is fixed.
  • the first processing member 20 includes a fixing portion 14 for fixing to the tip of the processing apparatus main body, an arm portion 15 for holding the grindstone 13 so as to be sandwiched from both side surfaces thereof, with a part of the grindstone 13 protruding to the outside,
  • the belt 16 transmits rotational power from a drive motor (not shown) of the processing apparatus main body to the grindstone shaft 18 of the grindstone 13, and a bearing portion 17 that rotatably supports the grindstone shaft 18 of the grindstone 13. Yes.
  • the grindstone 13 has a disk shape, and abrasive grains are fixed to the outer peripheral surface thereof.
  • the grindstone 13 is inserted into the cylinder 5 in the direction perpendicular to the cylinder 5 (the direction perpendicular to the plane of FIG. 2).
  • the grindstone 13 is inserted into the vane mounting groove 11 of the cylinder 5 while rotating the grindstone 13, and the outer peripheral surface to which the abrasive grains of the grindstone 13 are fixed is brought into contact with the vane mounting groove surface 5 a of the cylinder 5.
  • the cylinder 5 is moved in the radial direction (vertical direction in FIG. 2) in the contact state, and the surface flatness (surface roughness), flatness, parallelism, groove width of the vane mounting groove surface 5a of the cylinder 5 Grind etc.
  • FIG. 11 is a diagram showing the relationship between the radial position on the vane mounting groove surface of the cylinder formed by the conventional secondary processing and the surface flatness.
  • the horizontal axis indicates the radial position
  • the vertical axis indicates the surface flatness (surface roughness of the vane mounting groove surface)
  • the number on the + side of the vertical axis indicates the vane.
  • the height of the peak protruding from the flat reference position (0.0 ⁇ m) of the mounting groove surface, and the minus number (for example, ⁇ 2.0 ⁇ m) indicates the depth of the valley recessed from the reference position.
  • # 140 is used as the particle size of the abrasive grains fixed to the outer peripheral surface of the grindstone, and Rzjis (extensive) indicating the surface roughness of the vane mounting groove surface of the cylinder as shown in FIG. Point average roughness) was processed within 3.0 ⁇ m.
  • the grain size of the abrasive grains fixed to the outer peripheral surface of the grindstone 13 is changed to # 60 to # 100 larger than the conventional grain size, and the secondary processing according to the present embodiment is performed.
  • a recessed trough portion portion recessed from the flat reference position of the vane mounting groove surface 5a) is formed.
  • FIG. 6 is a diagram showing the relationship between the radial position and the surface flatness of the vane mounting groove surface 5a of the cylinder 5 formed by the secondary processing according to the embodiment of the present invention.
  • Rvk in FIG. 6 is the depth of the valley formed on the vane mounting groove surface 5a of the cylinder 5 (projection valley depth), and W is the pitch dimension of the valley (the dimension between adjacent peaks). ) Respectively.
  • a peak with a sharp tip is also formed. Therefore, the formation of the recessed valley portion improves the slidability of the vane 9 by eliminating the oil film breakage, but the formation of the peak portion having a sharp tip results in the vane being formed.
  • 9 and the vane attachment groove surface 5a cause a catch that causes the slidability of the vane 9 to deteriorate. Further, there is a problem that a gap (clearance) between the vane 9 and the vane mounting groove surface 5a is widened and the compressed refrigerant gas leaks, leading to leakage loss.
  • finishing processing is added to the vane mounting groove surface 5a of the cylinder 5 to eliminate the sharp tip of the peak portion of the vane mounting groove surface 5a. To do.
  • FIG. 7 is a diagram showing the second processed member 30 used during the finishing process according to the embodiment of the present invention.
  • a processing apparatus main body (not shown) is used during the finishing process for finishing the vane mounting groove surface 5a of the cylinder 5, and the second processing member 30 shown in FIG.
  • the second processing member 30 includes a fixing portion 31 for fixing to the tip of the processing apparatus main body, a carbide plate 32 having a thickness larger than the width of the vane mounting groove 11, and an arm portion 33 for holding the carbide plate 32 , Is composed of.
  • the cemented carbide plate 32 is inserted into the vane mounting groove 11 of the cylinder 5 in the direction orthogonal to the cylinder 5 (the direction orthogonal to the plane of FIG. 2), and the cemented carbide plate 32 is inserted into the vane mounting groove 11 in the radial direction of the cylinder 5. Move outward.
  • the thickness of the cemented carbide plate 32 is larger than the width of the vane mounting groove 11, but when the cemented carbide plate 32 is inserted, the cylinder 5 is bent by an external force and the vane mounting groove 11 is widened, so that it can be inserted. .
  • the carbide plate 32 having a thickness larger than the width of the vane mounting groove 11 is used in the finishing process for finishing the vane mounting groove surface 5a of the cylinder 5. Therefore, at the time of finishing, the carbide plate 32 is restrained, and the tip of the peak portion of the vane mounting groove surface 5a of the cylinder 5 is uniformly crushed to a flat shape without bending the carbide plate 32. It becomes possible.
  • the thickness of the cemented carbide plate 32 is larger than the width of the vane mounting groove 11 and the material is cemented carbide.
  • the material is not limited to this, and the material is harder than the cylinder 5. If it is a thing.
  • a plate-like one is used, but a cylindrical one, a plate-like, a cylindrical tool in which abrasives, abrasive grains, etc. are fixed, and abrasive grains are attached. Cloth, etc. may be used.
  • FIG. 8 is a diagram showing the relationship between the radial position and the surface flatness of the vane mounting groove surface 5a of the cylinder 5 after finishing according to the embodiment of the present invention.
  • Rvk in FIG. 8 represents the depth of the valley formed in the vane mounting groove surface 5a of the cylinder 5 (projection valley depth), and W represents the pitch dimension of the valley.
  • the finished vane mounting groove surface 5 a of the cylinder 5 is flattened by uniformly crushing the tip of the crest of the vane mounting groove surface 5 a of the cylinder 5.
  • the concave valley formed in the present embodiment remains on the vane mounting groove surface 5a of the cylinder 5 after finishing.
  • Rvk (projection valley depth) 3.0 ⁇ m or more and less than 5.0 ⁇ m
  • Rpk (projection peak height) representing surface flatness 0.2 ⁇ m or less.
  • FIG. 9 is a diagram showing the relationship between the test elapsed time of the vane mounting groove surface 5a of the cylinder 5 and the friction coefficient in the processing method according to the embodiment of the present invention and the conventional processing method.
  • the horizontal axis represents the test elapsed time
  • the vertical axis represents the friction coefficient.
  • the surface shape having the depth of the valley portion of the vane mounting groove surface 5a according to the present embodiment having a depth of 3.0 ⁇ m or more and less than 5.0 ⁇ m can reduce the frictional resistance as compared with the conventional case.
  • the reason why the depth of the trough is less than 5.0 ⁇ m is that the friction coefficient increases when the depth is 5.0 ⁇ m or more.
  • the tip of the crest of the vane mounting groove surface 5a of the cylinder 5 is uniformly crushed to form a flat shape, so that the vane 9 reciprocates in the vane mounting groove 11.
  • the vane 9 can slide without being caught by the peak portion of the vane mounting groove surface 5 a of the cylinder 5.
  • the recessed valley portion remains on the vane mounting groove surface 5a, it is easy to allow oil to enter the clearance (clearance) between the vane 9 and the vane mounting groove surface 5a of the cylinder 5, and the effect of the oil pool Can be expected and has the effect of reducing frictional resistance. Therefore, the slidability of the vane 9 is improved and the input of the compressor is suppressed.
  • the rotary compressor 1 can be operated at the time of operation. Noise can be reduced.
  • the flatness of the vane mounting groove surface 5a is improved by finishing the vane mounting groove surface 5a of the cylinder 5 with high accuracy as in the present embodiment, and the vane mounting groove surface 5a of the vane 9 and the cylinder 5 is improved. Leakage loss from a gap (clearance) between them can be suppressed, and high performance can be obtained.
  • the present invention is applied to the single cylinder type rotary compressor 1, but it is also effective to apply the present invention to an internal intermediate pressure type multi-stage rotary compressor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
PCT/JP2015/056117 2015-03-02 2015-03-02 ロータリ型圧縮機、およびその製造方法 Ceased WO2016139731A1 (ja)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CZ2017-565A CZ307900B6 (cs) 2015-03-02 2015-03-02 Rotační kompresor a způsob jeho výroby
PCT/JP2015/056117 WO2016139731A1 (ja) 2015-03-02 2015-03-02 ロータリ型圧縮機、およびその製造方法
JP2017503234A JP6437088B2 (ja) 2015-03-02 2015-03-02 ロータリ型圧縮機、およびその製造方法
CN201620156234.XU CN205478324U (zh) 2015-03-02 2016-03-01 旋转型压缩机
CN201610115718.4A CN105937494B (zh) 2015-03-02 2016-03-01 旋转型压缩机、以及旋转型压缩机的制造方法

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2015/056117 WO2016139731A1 (ja) 2015-03-02 2015-03-02 ロータリ型圧縮機、およびその製造方法

Publications (1)

Publication Number Publication Date
WO2016139731A1 true WO2016139731A1 (ja) 2016-09-09

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PCT/JP2015/056117 Ceased WO2016139731A1 (ja) 2015-03-02 2015-03-02 ロータリ型圧縮機、およびその製造方法

Country Status (4)

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JP (1) JP6437088B2 (cs)
CN (2) CN205478324U (cs)
CZ (1) CZ307900B6 (cs)
WO (1) WO2016139731A1 (cs)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6437088B2 (ja) * 2015-03-02 2018-12-12 三菱電機株式会社 ロータリ型圧縮機、およびその製造方法
CN110312870A (zh) * 2017-02-24 2019-10-08 三菱电机株式会社 回转型压缩机以及回转型压缩机的制造方法

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5177612U (cs) * 1974-12-16 1976-06-18
JPS63189681A (ja) * 1987-02-03 1988-08-05 Matsushita Electric Ind Co Ltd 回転式圧縮機の仕切りベ−ン
JPH01305188A (ja) * 1988-05-31 1989-12-08 Toshiba Corp ロータリー式圧縮機のシリンダ
JP2003269351A (ja) * 2002-03-13 2003-09-25 Sanyo Electric Co Ltd ロータリコンプレッサ
JP2005030232A (ja) * 2003-07-08 2005-02-03 Hitachi Home & Life Solutions Inc ロータリ圧縮機とそのシリンダの加工法
JP2009257274A (ja) * 2008-04-21 2009-11-05 Panasonic Corp ロータリ圧縮機
US8602755B2 (en) * 2009-12-11 2013-12-10 Lg Electronics Inc. Rotary compressor with improved suction portion location

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100398563B1 (ko) * 1999-11-15 2003-09-19 마츠시타 덴끼 산교 가부시키가이샤 회전압축기 및 그 제조 방법
CN101230857A (zh) * 2003-09-12 2008-07-30 三洋电机株式会社 旋转式压缩机的制造方法
CN1954150A (zh) * 2004-08-02 2007-04-25 松下电器产业株式会社 叶片旋转式空气泵
JP5366884B2 (ja) * 2010-05-21 2013-12-11 三菱電機株式会社 ベーンロータリー型圧縮機
JP6437088B2 (ja) * 2015-03-02 2018-12-12 三菱電機株式会社 ロータリ型圧縮機、およびその製造方法

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5177612U (cs) * 1974-12-16 1976-06-18
JPS63189681A (ja) * 1987-02-03 1988-08-05 Matsushita Electric Ind Co Ltd 回転式圧縮機の仕切りベ−ン
JPH01305188A (ja) * 1988-05-31 1989-12-08 Toshiba Corp ロータリー式圧縮機のシリンダ
JP2003269351A (ja) * 2002-03-13 2003-09-25 Sanyo Electric Co Ltd ロータリコンプレッサ
JP2005030232A (ja) * 2003-07-08 2005-02-03 Hitachi Home & Life Solutions Inc ロータリ圧縮機とそのシリンダの加工法
JP2009257274A (ja) * 2008-04-21 2009-11-05 Panasonic Corp ロータリ圧縮機
US8602755B2 (en) * 2009-12-11 2013-12-10 Lg Electronics Inc. Rotary compressor with improved suction portion location

Also Published As

Publication number Publication date
CN105937494B (zh) 2018-12-07
CN205478324U (zh) 2016-08-17
CZ307900B6 (cs) 2019-08-07
CN105937494A (zh) 2016-09-14
JPWO2016139731A1 (ja) 2017-09-14
CZ2017565A3 (cs) 2017-11-01
JP6437088B2 (ja) 2018-12-12

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