EP0683321A1 - Schwingender rotations-kompressor - Google Patents

Schwingender rotations-kompressor Download PDF

Info

Publication number
EP0683321A1
EP0683321A1 EP95902284A EP95902284A EP0683321A1 EP 0683321 A1 EP0683321 A1 EP 0683321A1 EP 95902284 A EP95902284 A EP 95902284A EP 95902284 A EP95902284 A EP 95902284A EP 0683321 A1 EP0683321 A1 EP 0683321A1
Authority
EP
European Patent Office
Prior art keywords
blade
roller
chamber
cylinder
oil
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.)
Granted
Application number
EP95902284A
Other languages
English (en)
French (fr)
Other versions
EP0683321A4 (de
EP0683321B1 (de
Inventor
Yasushi Shiga-Seisakusho Of Daikin Yamamoto
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.)
Daikin Industries Ltd
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
Publication of EP0683321A1 publication Critical patent/EP0683321A1/de
Publication of EP0683321A4 publication Critical patent/EP0683321A4/de
Application granted granted Critical
Publication of EP0683321B1 publication Critical patent/EP0683321B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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 a swing type rotary compressor primarily employed for a refrigeration apparatus.
  • a swing type rotary compressor there is known a rotary compressor wherein, as described, for example, in Japanese Patent Laid-Open Publication No. 5-202874, a blade for partitioning a cylinder chamber into a suction chamber and a compression chamber is integrally provided in a protruding manner on a roller fitted on an eccentric portion of a drive shaft and is swingably supported in a receiving groove of a support body rotatably provided in the cylinder, whereby gaseous fluid is compressed through the rotation of the roller.
  • a blade for partitioning a cylinder chamber into a suction chamber and a compression chamber is integrally provided in a protruding manner on a roller fitted on an eccentric portion of a drive shaft and is swingably supported in a receiving groove of a support body rotatably provided in the cylinder, whereby gaseous fluid is compressed through the rotation of the roller.
  • a roller B provided with an integral blade B1 protruding radially outwardly from the roller is disposed in the cylinder chamber A1 of a cylinder A which is fitted with a confronting front and rear heads on axially both sides so that upper and lower end faces of the roller B and blade B1 make a sliding contact with respective faces of the front and rear heads, and a circular pillar-shaped support body C making a sliding contact with each head is rotatably supported in the cylinder A and a tip portion of the blade B1 is supported on a receiving groove C1 formed in the support body C in such a manner that the blade B1 can swing and move back and forth.
  • the inner space of the cylinder chamber A1 is divided into the compression chamber X and the suction chamber Y by the roller B and blade B1. And, by fitting the roller B around the eccentric portion of the drive shaft and revolving the roller B within the cylinder chamber A1 by means of the drive shaft, gaseous fluid is sucked into the suction chamber Y and compressed in the compression chamber X.
  • a pressure difference from the inner periphery side of the roller B takes place in the suction chamber Y and even in the compression chamber X until the gaseous fluid is compressed to a predetermined pressure in the compression chamber X, and there also exists a pressure difference between the suction chamber Y and the compression chamber X.
  • the high pressure lubrication oil having lubricated the interface between the eccentric portion and the roller B is introduced from the inner periphery side of the roller B into the compression chamber X and the suction chamber Y via the upper and lower end faces of the roller B and from the compression chamber X into the suction chamber Y via the upper and lower end faces of the blade B1, as indicated by solid arrows n in Fig. 1, whereby the upper and lower end faces of the roller B and the blade B1 are lubricated.
  • the object of the present invention is therefore to provide a swing type rotary compressor which is able to securely lubricate the entire axial end surfaces of the roller and the blade and thus to improve the reliability.
  • a swing type rotary compressor comprises: a cylinder having a cylinder chamber formed therein; a roller fitted around an eccentric portion of a drive shaft and rotatably disposed within the cylinder chamber; a blade integrally provided on the roller so as to protrude therefrom and dividing the cylinder chamber into a compression chamber and a suction chamber; a support body swingably provided in the cylinder and having a receiving groove for receiving a tip portion of the blade in such a manner that the tip portion can move back and forth; and an oil groove provided on axial end faces of the blade and of a blade protrusion base portion of the roller from which the blade protrudes, said oil groove having one end opened to an inner peripheral surface of the roller and the other end opened to the tip of the blade.
  • the lubrication oil supplied to the inner periphery side of the roller is forcibly guided, by the centrifugal force acting on the roller during the revolution of the roller, to the tip portion of the blade through the oil groove.
  • the lubrication oil flowing in the oil grooves is supplied, through the revolution of the roller, to the axial end faces of the blade protrusion base portion of the roller and the axial end faces of the blade.
  • a high pressure chamber closed to outside of the cylinder is formed on a rear side of the blade at the receiving groove of the support body. More specifically, on the rear side of the blade is formed a high pressure chamber communicating to the inner peripheral side of the roller via the oil groove.
  • the high pressure chamber is filled with the lubrication oil introduced to the high pressure chamber from the oil groove, and the lubrication oil is then fed, by pressure difference, toward the suction chamber Y which is held lower in pressure relative to the high pressure chamber, along a suction-chamber-side outer periphery of the support body supported in the cylinder and a suction-chamber-side wall portion of the blade.
  • the lubrication oil in the high pressure chamber is fed, by this pressure difference, to the compression chamber along a compression-chamber-side outer periphery of the support body and a compression-chamber-side wall portion of the blade.
  • Figs. 2 and 3 show only the compression element portions of a swing type rotary compressor according to a first embodiment, and the compression element is so configured that a roller 2 integrally formed with a blade 21 protruding radially outward from the roller is arranged within a cylinder chamber 11 of a cylinder 1 closed by the faces of front and rear heads (not shown) so that the upper and lower end faces of the roller 2 and blade 21 slidingly contact the faces of the heads, an eccentric portion 31 of a drive shaft 3 is fitted into the roller 2 so as for the roller 2 to revolve through the rotation of the drive shaft 3 while contacting an outer peripheral surface of the roller with an inner wall surface of the cylinder chamber 11, and on the other hand, a cylindrical support hole 14 communicating to the inner space of the cylinder chamber 11 is formed in an intermediate position between a discharge port 12 and a suction port 13 provided in the cylinder 1, a support body 14 making a sliding contact with the heads is rotatably supported in the support hole 14 and a tip portion of the blade 21 is slidably and back
  • the support body 4 is formed of two semi-cylindrical, i.e., semi-columnar members 4A and 4B, the receiving groove 41 is defined between the two flat confronting faces of the semi-cylindrical members 4A and 4B, and the tip portion of the blade 21 is inserted into the receiving groove 41.
  • an internal space of the cylinder chamber 11 surrounded by a contact line on which the outer peripheral surface of the roller 2 comes into contact with the inner wall surface of the cylinder chamber 11 and a side wall surface of the blade 21 on its front side relative to the revolution direction of the roller 2 is set as the suction chamber Y communicating to the suction port 13
  • an internal space of the cylinder chamber 11 surrounded by the contact line and a side wall surface of the blade 21 on its rear side relative to the revolution direction is set as the compression chamber X communicating to the discharge port 12.
  • An oil supply passage 32 communicating to an oil supply pump is formed within the central portion of the drive shaft 3.
  • a branch passage 33 extending radially outward from the oil supply passage 32 is provided in the eccentric portion 31 of the drive shaft 3 to supply the high pressure oil pumped up to the oil supply passage 32, via the branch passage 33, to sliding contact positions between the inner peripheral surface of the roller 2 and the outer peripheral surface of the eccentric portion 31.
  • the high pressure oil supplied to the inner peripheral side of the roller 2 is fed from the inner peripheral portion of the roller to the suction chamber Y and the compression chamber X via upper and lower end faces of the roller 102 as shown by solid arrows n in Figs. 2 and 3.
  • the oil is introduced to the suction chamber Y and the compression chamber X, the upper and lower end faces of the roller 2 are supplied with the oil through the revolution of the roller 2.
  • a linear oil groove 22 one end of which is open to the inner peripheral surface of the roller 2 and the other end of which is open to the tip of the blade 21 is formed on the upper and lower end faces of a blade protrusion base portion of the roller 2 from which the blade protrudes and on the upper and lower end faces of the blade 21.
  • the lubrication oil pumped up to the oil supply passage 32 of the drive shaft 3 and supplied from the branch passage 33 to the sliding contact portions between the roller 2 and the eccentric portion 31 is then forcibly guided to the tip portion of the blade 21, as shown by solid arrows p of Figs. 2 and 3, along the respective oil grooves 22 by the centrifugal force generated by the revolution of the roller 2, and the lubrication oil flowing in these oil grooves 22 is supplied from these oil grooves 22 to the upper and lower end faces of the blade protrusion base portion of the roller 2 and the upper and lower end faces of the blade 21 through the revolution of the roller 2.
  • a high pressure chamber 15 communicating to the receiving groove 41 defined between the two members 4A and 4B of the support body 4 and also communicating to the inner peripheral side of the roller 2 via the oil grooves 22 provided on the blade 21 is formed so as to be closed to the outside of the cylinder 1.
  • the roller 2 when the roller 2 is operated to revolve so as to advance the blade 22 toward the high pressure chamber 15, the high pressure lubrication oil supplied to the inner peripheral portion of the roller 2 is introduced into the high pressure chamber 15 via the oil grooves 22 by the centrifugal force of the roller 2, and fills the high pressure chamber.
  • the lubrication oil within the high pressure chamber 15 is fed by pressure difference to the suction chamber Y along a suction-chamber-side outer peripheral portion of the support body 4 supported in the support hole 14 and a suction-chamber-side wall portion of the blade 21, as indicated by dotted arrows q in Fig. 4.
  • the lubrication oil in the high pressure chamber 15 is fed by pressure difference to the compression chamber X along a compression-chamber-side outer peripheral portion of the support body 4 and a compression-chamber-side wall portion of the blade 21.
  • the outer peripheral portion, upper and lower end faces and receiving hole 41 of the support body 4 can be supplied with oil, and therefore the outer peripheral portion and upper and lower end faces of the support body 4 and further the receiving groove 41 on which the blade 21 slides can be effectively lubricated.
  • Fig. 5 shows the overall configuration of a horizontal rotary compressor having a high pressure dome according to a third embodiment.
  • a motor 102 composed of a stator 121 and a rotor 122 is arranged on one lateral side of the horizontal casing, and a compression element 104 driven by a drive shaft 103 extending from the rotor 122 is arranged on the other side within the casing 101.
  • the compression element 104 has a cylinder 105 having a cylinder chamber 151 therein, and a front head 106 and a rear head 107 are arranged on both sides of the cylinder 105 in the axial direction.
  • a tube-shaped roller 108 fitted on the eccentric portion 131 of the drive shaft 103 is installed, and on the roller 108 is integrally formed a blade 109 partitioning the cylinder chamber 151 into a compression chamber X communicating to a discharge port 152 provided on the cylinder 105 and a suction chamber Y communicating to a suction port 153 so that the blade 109 protrudes from the outer periphery of the roller 108 outward in the radial direction, and the blade 109 is swingably supported by a support body 110 rotatably provided in the cylinder 105.
  • the roller 108 revolves within the cylinder chamber 151, and gaseous fluid introduced through a suction tube 101a connected to the suction port 153 is sucked into the suction chamber Y and then compressed in the compression chamber X, and the compressed gas is then discharged from the discharge port 152, via a muffler provided on the outer side of the front head 106, to an internal space of the casing 101 and then to the outside through a discharge tube 101b opened to the motor 102 within the casing 101.
  • the blade 109 is disposed slantwise in an upper portion of the cylinder 105 apart from the oil sump O of the casing 101.
  • an oil chamber 154 being a closed space is formed on a rear side of the blade 109 for supplying oil to the blade 109, and a high-pressure oil supplied to the compression chamber X is input, by the pressure difference from a pressure of the compression chamber X, into the oil chamber 154 via a clearance defined between the blade 109 and the support body 110.
  • the oil input into the oil chamber 154 is then output therefrom into the suction chamber Y via a clearance defined between the blade 109 and the support body 110. Contacting portions of the blade 109 is lubricated through the input and output of the oil.
  • the blade 109 is supplied with oil from the oil chamber 154 disposed on the rear side of the blade, as described above, it is not necessary to make the blade 109 confront the oil sump O. This makes it possible to set the blade in any desired position in the cylinder 105. Consequently, the blade 109 can be arranged in an upper portion of the cylinder 105 apart from the oil sump O. This makes it possible to provide the discharge port 152 and suction port 153, which must be provided in the vicinity of the blade 109, in positions apart from the oil sump O. Therefore, the suction gas entering from the suction port 153 is prevented from being overheated by the high temperature oil in the oil sump O, whereby the reduction in volume efficiency is suppressed and the power is increased.
  • the arrangement of the blade 109 in the upper position in the cylinder 105 allows the suction port 153 to be provided in the cylinder high above the oil sump O, the work for connecting the suction tube 101a to the suction port 153 is readily done from one lateral side of the casing 101. Thus, workability can be increased. Furthermore, because there is no necessity to secure a space for the suction tube 101a on a lower side of the casing 101, the height of the casing 101 can be reduced when assembled.
  • an oil groove 111 radially extending therethrough, one longitudinal end of which is open to the inner peripheral surface of the roller 108 and the other end of which is open to the oil chamber 154 provided on the rear side of the blade 109.
  • this high pressure oil maintains the oil chamber 154 in a high pressure state all the time, the oil in the oil chamber 154 can be fed, by pressure difference, to the suction chamber Y which is held lower in pressure relative to the oil chamber 154, via the clearance between the support body 110 supported within the cylinder 105 and the blade 109.
  • the lubrication oil in the oil chamber 154 is fed, by pressure difference, to the compression chamber X as well via the clearance between the support body 110 and the blade 109.
  • the blade 109 can be lubricated more securely and therefore the lubrication performance for the blade 109 is enhanced.
  • the swing type rotary compressor according to the present invention is primarily employed in the refrigeration apparatus.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
EP95902284A 1993-12-08 1994-12-01 Schwingender rotations-kompressor Expired - Lifetime EP0683321B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP30792493 1993-12-08
JP307924/93 1993-12-08
JP30792493A JP3473067B2 (ja) 1993-12-08 1993-12-08 揺動型ロータリー圧縮機
PCT/JP1994/002020 WO1995016136A1 (fr) 1993-12-08 1994-12-01 Compresseur rotatif oscillant

Publications (3)

Publication Number Publication Date
EP0683321A1 true EP0683321A1 (de) 1995-11-22
EP0683321A4 EP0683321A4 (de) 1996-05-15
EP0683321B1 EP0683321B1 (de) 2001-05-09

Family

ID=17974812

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95902284A Expired - Lifetime EP0683321B1 (de) 1993-12-08 1994-12-01 Schwingender rotations-kompressor

Country Status (10)

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

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0882780A1 (de) * 1995-12-28 1998-12-09 Daikin Industries, Limited Kältemaschinenöl und kältemaschine zur verwendung desselben
EP3643445A4 (de) * 2017-07-31 2020-07-08 Daikin Industries, Ltd. Produktionsverwaltungssystem und produktionsverwaltungsverfahren

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
KR101528643B1 (ko) * 2008-07-22 2015-06-16 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
CN102788017B (zh) * 2012-07-03 2015-04-08 邵阳学院 一种便携式打气筒
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
EP3604818A1 (de) * 2016-02-23 2020-02-05 Daikin Industries, Ltd. Schwingkolbenverdichter
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

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
US3269646A (en) * 1964-03-11 1966-08-30 August Paul Rotary compressor

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS48113011U (de) * 1972-03-28 1973-12-25
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
JP2776134B2 (ja) * 1992-04-28 1998-07-16 ダイキン工業株式会社 ロータリー圧縮機
JP3178559B2 (ja) * 1991-09-24 2001-06-18 ダイキン工業株式会社 ロータリー圧縮機
JP2768114B2 (ja) * 1992-03-04 1998-06-25 ダイキン工業株式会社 ロータリー圧縮機
JP2770648B2 (ja) * 1992-05-11 1998-07-02 ダイキン工業株式会社 ロータリー圧縮機

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
US3269646A (en) * 1964-03-11 1966-08-30 August Paul Rotary compressor

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO9516136A1 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0882780A1 (de) * 1995-12-28 1998-12-09 Daikin Industries, Limited Kältemaschinenöl und kältemaschine zur verwendung desselben
EP0882780A4 (de) * 1995-12-28 2000-08-16 Daikin Ind Ltd Kältemaschinenöl und kältemaschine zur verwendung desselben
US6569347B1 (en) 1995-12-28 2003-05-27 Daikin Industries, Ltd. Refrigerating machine oil and refrigerator using the same
EP3643445A4 (de) * 2017-07-31 2020-07-08 Daikin Industries, Ltd. Produktionsverwaltungssystem und produktionsverwaltungsverfahren

Also Published As

Publication number Publication date
WO1995016136A1 (fr) 1995-06-15
JP3473067B2 (ja) 2003-12-02
EP0683321A4 (de) 1996-05-15
ES2158069T3 (es) 2001-09-01
JPH07158574A (ja) 1995-06-20
CN1117755A (zh) 1996-02-28
KR960701306A (ko) 1996-02-24
KR100322269B1 (ko) 2002-06-20
DE69427186D1 (de) 2001-06-13
EP0683321B1 (de) 2001-05-09
SG43887A1 (en) 1997-11-14
DK0683321T3 (da) 2001-05-28
CN1041453C (zh) 1998-12-30
MY119158A (en) 2005-04-30
DE69427186T2 (de) 2001-09-20

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