WO1995016136A1 - Compresseur rotatif oscillant - Google Patents

Compresseur rotatif oscillant Download PDF

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Publication number
WO1995016136A1
WO1995016136A1 PCT/JP1994/002020 JP9402020W WO9516136A1 WO 1995016136 A1 WO1995016136 A1 WO 1995016136A1 JP 9402020 W JP9402020 W JP 9402020W WO 9516136 A1 WO9516136 A1 WO 9516136A1
Authority
WO
WIPO (PCT)
Prior art keywords
blade
roller
chamber
cylinder
oil
Prior art date
Application number
PCT/JP1994/002020
Other languages
English (en)
Japanese (ja)
Inventor
Yasushi Yamamoto
Original Assignee
Daikin Industries, 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 Daikin Industries, Ltd. filed Critical Daikin Industries, Ltd.
Priority to DK95902284T priority Critical patent/DK0683321T3/da
Priority to KR1019950703289A priority patent/KR100322269B1/ko
Priority to EP95902284A priority patent/EP0683321B1/fr
Priority to DE69427186T priority patent/DE69427186T2/de
Priority to US08/500,847 priority patent/US5577903A/en
Publication of WO1995016136A1 publication Critical patent/WO1995016136A1/fr

Links

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
    • F04C18/32—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 both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
    • F04C18/322—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 both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and 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
    • 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

Definitions

  • the present invention relates to an oscillating rotary compressor mainly used for a refrigeration system.
  • a blade for partitioning a cylinder chamber into a suction chamber and a compression chamber is provided.
  • the blade is integrally protruded from the roller inserted into the eccentric part of the drive, and the blade is swingably supported in the receiving groove of the support rotatably arranged on the cylinder to expose the roller.
  • an apparatus that compresses a gas fluid That is, as shown in FIG. 1, the conventional rotary compressor of the conventional type has a radially outward direction in a cylinder chamber A1 of a cylinder A in which a front and a head are contacted on both axial sides.
  • a roller B integrally provided with a protruding blade B 1 is disposed such that both upper and lower end surfaces of the roller B and the blade B 1 are in sliding contact with the fusing surfaces of the respective heads.
  • a cylindrical support C which is slidably contacted with each of the above-mentioned heads is rotatably supported inside the cylinder A, and a receiving groove C1 formed in the support C is provided at a tip end of the blade B1. Oscillates and advances and retreats, thereby partitioning the interior of the cylinder chamber A1 into a compression chamber X and a suction chamber Y via the roller B and the blade B1, while being driven by the roller B.
  • the eccentric part of the shaft is inserted and the roller B is By revolving driven by Da chamber A within 1 sucks the gaseous fluid into the suction chamber Y, also, the pressure The compression of the gas fluid is performed in the contraction chamber X.
  • the pressure between the pressure on the inner circumferential surface side of the roller B and the compression chamber X is higher or lower.
  • a pressure difference is generated, and a height difference pressure is also generated between the suction chamber Y and the compression chamber X.
  • a pressure difference between the roller 1B and the eccentric portion is obtained.
  • An object of the present invention is to provide an oscillating rotary compressor capable of reliably lubricating the entire surfaces of both ends in the axial direction of a roller and a blade and improving reliability.
  • an oscillating rotary compressor of the present invention includes: a cylinder having a cylinder chamber formed therein;
  • a support having a receiving groove, which is swingably disposed in the cylinder, and which freely receives a protruding end portion of the blade to advance and retreat;
  • the lubricating oil supplied to the inner peripheral side of the roller flows through the oil groove due to the centrifugal force acting on the roller at the time of its orbital drive, and flows toward the tip end of the blade. Is forcibly guided.
  • the lubricating oil flowing through the oil groove is supplied from the oil groove to the axial end face of the blade projecting base portion of the roller and the axial end face of the blade by the revolution drive of the roller. is there. Therefore, the entire end face of the roller and the blade in the direction of the cross section is formed by the inner peripheral surface of the roller and the compression chamber and the suction chamber.
  • a high-pressure chamber closed to the outside of the cylinder is formed on the back side of the blade in the receiving groove of the support.
  • a high-pressure chamber communicating with the inner peripheral side of the roller 1 through the oil groove is formed on the back side of the blade. Therefore, the lubricating oil introduced from the oil groove into the high-pressure chamber can be filled in the high-pressure chamber during the revolution IE of the roller, and therefore, the suction chamber maintained in a low-pressure state with respect to the high-pressure chamber.
  • the pressure can be caused to flow by the differential pressure along the suction chamber-side outer peripheral portion of the support supported in the cylinder and the suction chamber side wall of the blade.
  • the lubricating oil in the high pressure chamber is compressed by the differential pressure of the support until the gas fluid compressed therein becomes equal to the internal pressure of the high pressure chamber.
  • the air can be flowed to the compression chamber along the outer peripheral portion on the chamber side or along the side wall of the compression chamber of the blade. As a result, it is possible to effectively lubricate the outer peripheral portion and both end surfaces of the support and the receiving groove.
  • FIG. 1 is a perspective view of a conventional roller integrally formed with a blade.
  • FIG. 2 is a perspective view showing a compression element including a roller 1 in the oscillating rotary compressor according to the first embodiment of the present invention.
  • FIG. 3 is a plan view showing a main part of the first embodiment.
  • FIG. 4 is a plan view showing a main part of the second embodiment of the present invention.
  • FIG. 5 is a longitudinal sectional view showing the overall structure of a horizontal rotary compressor according to a third embodiment of the present invention.
  • FIG. 6 is a sectional view showing a main part of the third embodiment. BEST MODE FOR CARRYING OUT THE INVENTION
  • FIGS. 2 and 3 show only the compression element portion of the oscillating rotary compression contact of the first embodiment, which is closed by the face surfaces of the front and rear heads (not shown).
  • a roller 2 integrally provided with a blade 21 protruding radially outward in the cylinder chamber 11 of the cylinder 1 is attached to the roller 2 and the upper and lower end surfaces of the blade 21 with the above-mentioned respective heads.
  • the eccentric part 31 of the drive shaft 3 is inserted into the roller 2 while being slidably in contact with the fuser surface, and the roller 2 is rotated with the rotation of the drive shaft 3 so that the outer peripheral surface of the roller 2 is rotated.
  • the revolving drive is performed while making contact with the inner wall surface of the cylinder chamber 11.
  • an intermediate portion between the discharge port 12 and the suction hole 13 provided in the cylinder 1 is provided inside the cylinder chamber 11.
  • a circular support hole 14 communicating with the support hole 14 is formed.
  • the support 4 slidably in contact with each of the above-mentioned heads is rotatably supported, and the receiving groove 41 provided in the support 4 supports the distal end side of the blade 21 so as to swing and advance and retreat. ing.
  • the support 4 is formed of two semi-cylindrical members 4A and 4B, and the flat portion between the flat surfaces of the members 4A and 4B is defined as the receiving groove 41. The leading end of the blade 21 is inserted into the receiving groove 41.
  • the cylinder chamber 1 When the roller 2 is driven to revolve, the cylinder chamber 1 surrounded by a contact whose outer peripheral surface is in contact with the inner wall surface of the cylinder chamber 11 and the front wall surface of the blade 2 1 in the revolving direction of the roller 2.
  • the interior space 1 is not provided with the suction chamber Y communicating with the suction hole 13, and the inside of the cylinder chamber 11 is surrounded by the contact point and the rear wall surface of the blade 2 2 in the revolving direction of the roller 2.
  • an oil supply passage 32 communicating with the oil supply pump is formed inside the center of the drive shaft 3 and extends outward from the lined oil passage 3 2 in the eccentric portion 31 of the IS drive shaft 3 in the strange direction.
  • a branch passage 33 is provided, and high-pressure lubricating oil pumped into the lined oil passage 32 is passed through the branch passage 33 between the inner peripheral surface of the roller 2 and the outer peripheral surface of the eccentric portion 31. Oil is supplied to the sliding contact area.
  • the high-pressure lubricating oil pumped up by the oil supply pump is supplied to the inner peripheral side of the roller 2 to have a high pressure. Therefore, the inner peripheral side of the roller 2 And a predetermined pressure difference is always generated between the suction chamber Y and the compression chamber X. On the compression chamber X side, the gas fluid flows in the compression chamber X with the pressure on the inner peripheral side of the roller 2. Until compressed to the same pressure, a predetermined height differential pressure is generated between the inner peripheral portion and the inner peripheral portion.
  • the high-pressure lubricating oil supplied to the inner peripheral portion of the roller 2 is supplied from the inner peripheral side of the roller 2 to the compression chamber X and the suction chamber Y as shown by a solid line arrow n in FIGS.
  • the lubricating oil is introduced into the compression chamber X and the suction chamber Y through the upper and lower ends of the roller 2, the lubricating oil is supplied to the upper and lower ends of the roller 2 as the roller 2 revolves.
  • one end of the roller 2 is attached to the upper and lower end surfaces of the blade protruding base and the upper and lower end surfaces of the blade 21.
  • a linear oil groove 22 was formed on the peripheral surface, and the other end was released toward the protruding tip side of the blade 21.
  • the lubricating oil that has been supplied to the sliding contact area between the roller 2 and the eccentric part 3 1 from above is the centrifugal force generated when the roller 2 revolves.
  • the lubricating oil that is forcibly guided along the oil grooves 22 to the protruding tip side of the blade 21 and flows through the oil grooves 22 is revolved by the rollers 2 so that the lubricating oil flows out of the oil grooves 22. Oil is supplied to the upper and lower end surfaces of the roller 2 at the protruding base of the blade and the upper and lower end surfaces of the blade 21.
  • the entire upper and lower end surfaces of the roller 2 and the blade 21 can be reliably lubricated, and the reliability can be improved.
  • the protruding tip side of the blade 21 in the receiving groove 41 of the support 4 is opened, but it is closed to the outside of the cylinder 1. In any case, the entire upper and lower end surfaces of the roller 2 and the blade 21 can be surely lubricated.
  • the second embodiment shown in FIG. 4 is characterized in that the two members 4 A, 4 B
  • the high-pressure chamber 15 continuous with the receiving groove 41 formed therebetween and communicating with the inner peripheral side of the roller 2 via the oil groove 22 provided in the blade 21 is formed as described above. It is formed in a closed shape to the outside of the cylinder 1.
  • the lubricating oil in the high-pressure chamber 15 is subjected to a differential pressure until the gas fluid compressed therein becomes equal to or higher than the internal pressure of the high-pressure chamber 15. It flows to the compression chamber X along the compression chamber-side outer peripheral portion of the support 4 and the compression chamber side wall of the blade 21, and thus flows from the high-pressure chamber 14 to the compression chamber X and the suction chamber Y. Oil can be supplied to the outer peripheral portion, upper and lower end surfaces, and the receiving groove 41 of the support 4 by the oil flow due to the differential pressure of the above, and the outer peripheral portion, upper and lower end surfaces of the support 4 and the blade 21 slide. Lubrication of the receiving groove 41 can also be effectively performed.
  • FIG. 5 shows the overall structure of a high-pressure dome-shaped horizontal rotary compressor according to a third embodiment, which is located on one side in the longitudinal direction inside a horizontal casing 101 having an oil sump 0 at the inner bottom.
  • a motor 102 composed of a stay 1 2 1 and a rotor 1 2 2 is provided, and a drive shaft 10 extending from the opening 1 2 2 is provided on the other side inside the casing 101.
  • a compression element 104 driven by 3 is provided.
  • This compression element 104 is composed of a cylinder 105 having a cylinder chamber 15 1 therein, a front head 106 and a rear head 1 disposed on both axial sides of the cylinder 105. 07.
  • the cylinder chamber 150 of the cylinder 105 has a cylindrical roller 108 into which the eccentric part 131 of the driving vehicle 103 is inserted.
  • a blade 109, which is defined as Y, is integrally protruded radially outward from an outer peripheral surface of the roller 108, and the blade 109 is rotatably provided on the cylinder 105. It is swingably supported on the support 110.
  • the roller 108 is rotated. Revolving in the cylinder chamber 151, the fluid gas introduced from the suction pipe 10la connected to the suction port 1553 is sucked into the suction chamber Y, compressed in the compression chamber X, The compressed gas is discharged from the discharge port 152 to the internal space of the casing 101 through the inside of the muffler 161, which is provided outside the front head 106, and A discharge pipe 10 lb opened to the motor 102 side inside the thing 101 is discharged to the outside.
  • the blade 109 is disposed obliquely on the upper side of the cylinder 105 away from the oil reservoir 0 of the casing 101.
  • an oil chamber 154 serving as a closed space for supplying oil to the blade 109 is formed on the back side of the blade 109, and the high-pressure oil lined up in the compression chamber X is supplied to the above-described high-pressure oil. Due to the pressure difference between the suction chamber Y and the suction chamber Y, the oil is introduced into the oil chamber 154 through a gap formed between the blade 109 and the support 110, and is introduced into the oil chamber 154. The introduced oil is further led to the suction chamber Y through a gap formed between the blade 109 and the support 110, and the oil is introduced and led to slide the blade 109. The parts are lubricated.
  • the oil supply to the blade 109 can be performed from the oil chamber 154 provided on the back side of the blade 109, so that the blade 109 does not need to be moved to the oil reservoir 0.
  • the blade 109 can be set at an arbitrary position of the cylinder 105. As a result, as shown in FIG. 5, the blade 109 can be disposed on the upper side of the cylinder 105 separated from the oil reservoir 0.
  • the discharge port 152 and the suction port 1553 provided in the vicinity of the blade 109 can also be formed at a position separated from the oil reservoir 0, and the high-temperature oil in the oil reservoir 0 It is possible to prevent the suction gas sucked from the suction port 153 from being overheated, so that a decrease in volumetric efficiency can be reduced and the performance can be improved.
  • the blade 109 is connected to the cylinder 1 By disposing the suction port on the upper side of the oil reservoir 0 in the cylinder 105, the suction port 153 can be formed above the oil reservoir 0.
  • the suction pipe 101a can be easily connected from one side in the lateral direction of the casing 101, and the assembling workability can be improved. There is no need to separately secure a space for connecting the suction pipe 101a to the side, and the mounting height of the casing 101 can be reduced.
  • one end in the length direction is opened to the inner peripheral surface of the roller 108, and the other end is opened to the upper and lower end surfaces of the blade protruding base of the upper blade 109 and the roller 108, respectively.
  • An oil groove 111 is formed in the oil chamber 154 provided on the back side of the blade 109 so as to open in a radial direction and extend in a radial direction.
  • the oil chamber 154 can be positively refilled with oil through the step 111, the oil chamber 154 can always be filled with high-pressure oil, so that there is no shortage of oil.
  • the oil chamber 154 can always be set at a high pressure with high-pressure oil, the oil chamber 154 is supported in the cylinder 105 on the suction chamber Y side maintained at a low pressure state with respect to the oil chamber 154.
  • the lubricating oil can be caused to flow by the differential pressure through the gap between the support 110 and the blade 109, and the gas fluid compressed inside the compression chamber X is compressed by the oil in the compression chamber X side.
  • the oscillating rotary compressor of the present invention is mainly used for a refrigeration system.

Abstract

L'invention concerne un compresseur rotatif oscillant comprenant un cylindre (1) pourvu d'une chambre de cylindre (11), un galet (2) monté dans la partie excentrique (31) d'un arbre d'entraînement (3) et placé dans la chambre de cylindre (11), une aube (21) ne formant qu'une seule pièce avec le galet (2) et faisant saillie sur celui-ci pour diviser la chambre de cylindre (11) en une chambre de compression (X) et une chambre d'aspiration (Y). Un corps de support (4) est placé dans le cylindre (1) de façon à pouvoir osciller librement dans celui-ci, et comporte une rainure (41) dans laquelle vient se loger, de façon rétractable, l'extrémité avant de l'aube (21). Une rainure de graissage (22) est formée dans l'aube (21) et dans les surfaces terminales axiales de la partie du galet (2) à partir de laquelle l'aube fait saillie, de façon que cette rainure débouche sur la surface circonférentielle intérieure du galet (2), à une de ses extrémités, et sur l'extrémité avant de l'aube (21) faisant saillie, à l'autre extrémité. Une chambre haute pression (15) fermée par rapport à l'extérieur du cylindre (1) est formée dans la rainure (41) du corps de support (4), sur le côté arrière de l'aube (21). Ainsi, les parties en contact glissant entre les surfaces d'extrémité supérieure et inférieure de l'aube (21) et le galet (2), ainsi qu'entre l'aube (21) et le corps de support (4) portant l'aube, sont lubrifiées de façon sûre, ce qui améliore la fiabilité du compresseur.
PCT/JP1994/002020 1993-12-08 1994-12-01 Compresseur rotatif oscillant WO1995016136A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
DK95902284T DK0683321T3 (da) 1993-12-08 1994-12-01 Rotationskompressor af svingtypen
KR1019950703289A KR100322269B1 (ko) 1993-12-08 1994-12-01 요동형로타리압축기
EP95902284A EP0683321B1 (fr) 1993-12-08 1994-12-01 Compresseur rotatif oscillant
DE69427186T DE69427186T2 (de) 1993-12-08 1994-12-01 Schwingender rotations-kompressor
US08/500,847 US5577903A (en) 1993-12-08 1994-12-01 Rotary compressor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP5/307924 1993-12-08
JP30792493A JP3473067B2 (ja) 1993-12-08 1993-12-08 揺動型ロータリー圧縮機

Publications (1)

Publication Number Publication Date
WO1995016136A1 true WO1995016136A1 (fr) 1995-06-15

Family

ID=17974812

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP1994/002020 WO1995016136A1 (fr) 1993-12-08 1994-12-01 Compresseur rotatif oscillant

Country Status (10)

Country Link
EP (1) EP0683321B1 (fr)
JP (1) JP3473067B2 (fr)
KR (1) KR100322269B1 (fr)
CN (1) CN1041453C (fr)
DE (1) DE69427186T2 (fr)
DK (1) DK0683321T3 (fr)
ES (1) ES2158069T3 (fr)
MY (1) MY119158A (fr)
SG (1) SG43887A1 (fr)
WO (1) WO1995016136A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102788017A (zh) * 2012-07-03 2012-11-21 邵阳学院 一种便携式打气筒

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Publication number Priority date Publication date Assignee Title
WO1997024415A1 (fr) * 1995-12-28 1997-07-10 Daikin Industries, Ltd. Huile d'installation de refrigeration et refrigerateur fonctionnant avec elle
US6336336B1 (en) 2000-03-20 2002-01-08 Hitachi, Ltd. Rotary piston compressor and refrigerating equipment
JP3731127B2 (ja) * 2004-01-22 2006-01-05 ダイキン工業株式会社 スイング圧縮機
JP4961961B2 (ja) * 2006-11-13 2012-06-27 ダイキン工業株式会社 回転式流体機械
JP2010025103A (ja) * 2008-06-16 2010-02-04 Daikin Ind Ltd ロータリ圧縮機
CN101328891B (zh) * 2008-07-22 2012-08-08 温岭市鑫磊空压机有限公司 双转子平动式旋转压缩装置
KR101467577B1 (ko) * 2008-07-22 2014-12-05 엘지전자 주식회사 압축기
JP5861456B2 (ja) * 2011-12-28 2016-02-16 ダイキン工業株式会社 回転式圧縮機
JP5948209B2 (ja) * 2012-10-11 2016-07-06 東芝キヤリア株式会社 密閉型圧縮機および冷凍サイクル装置
CN104595195B (zh) * 2014-12-04 2016-06-29 广东美芝制冷设备有限公司 低背压旋转式压缩机
CN111306064A (zh) * 2016-02-23 2020-06-19 大金工业株式会社 摆动活塞式压缩机
JP6520999B2 (ja) * 2017-07-31 2019-05-29 ダイキン工業株式会社 生産管理システムおよび生産管理方法
CN116906328B (zh) * 2023-08-08 2024-03-15 广州市德善数控科技有限公司 一种一体式摆动转子式泵体组件

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JPS4216099B1 (fr) * 1964-03-11 1967-09-02
JPS48113011U (fr) * 1972-03-28 1973-12-25
JPH05202874A (ja) * 1991-09-24 1993-08-10 Daikin Ind Ltd ロータリー圧縮機
JPH05248380A (ja) * 1992-03-04 1993-09-24 Daikin Ind Ltd ロータリー圧縮機
JPH05306691A (ja) * 1992-04-28 1993-11-19 Daikin Ind Ltd ロータリー圧縮機
JPH05312169A (ja) * 1992-05-11 1993-11-22 Daikin Ind Ltd ロータリー圧縮機

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FR698476A (fr) * 1928-11-27 1931-01-31 Thomson Houston Comp Francaise Perfectionnements aux pompes rotatives
FR937086A (fr) * 1946-10-07 1948-08-06 Compresseur rotatif
GB729281A (en) * 1952-11-22 1955-05-04 Vadim Stephane Makaroff Improvements in rotary fluid motors, compressors, pumps and the like
JP2576235B2 (ja) * 1989-08-10 1997-01-29 ダイキン工業株式会社 ロータリ式圧縮機

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Publication number Priority date Publication date Assignee Title
JPS4216099B1 (fr) * 1964-03-11 1967-09-02
JPS48113011U (fr) * 1972-03-28 1973-12-25
JPH05202874A (ja) * 1991-09-24 1993-08-10 Daikin Ind Ltd ロータリー圧縮機
JPH05248380A (ja) * 1992-03-04 1993-09-24 Daikin Ind Ltd ロータリー圧縮機
JPH05306691A (ja) * 1992-04-28 1993-11-19 Daikin Ind Ltd ロータリー圧縮機
JPH05312169A (ja) * 1992-05-11 1993-11-22 Daikin Ind Ltd ロータリー圧縮機

Non-Patent Citations (1)

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Title
See also references of EP0683321A4 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102788017A (zh) * 2012-07-03 2012-11-21 邵阳学院 一种便携式打气筒

Also Published As

Publication number Publication date
MY119158A (en) 2005-04-30
DE69427186D1 (de) 2001-06-13
EP0683321B1 (fr) 2001-05-09
SG43887A1 (en) 1997-11-14
KR100322269B1 (ko) 2002-06-20
EP0683321A4 (fr) 1996-05-15
JP3473067B2 (ja) 2003-12-02
JPH07158574A (ja) 1995-06-20
DK0683321T3 (da) 2001-05-28
ES2158069T3 (es) 2001-09-01
CN1117755A (zh) 1996-02-28
EP0683321A1 (fr) 1995-11-22
CN1041453C (zh) 1998-12-30
DE69427186T2 (de) 2001-09-20
KR960701306A (ko) 1996-02-24

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