WO2008065802A1 - Compressor - Google Patents
Compressor Download PDFInfo
- Publication number
- WO2008065802A1 WO2008065802A1 PCT/JP2007/068821 JP2007068821W WO2008065802A1 WO 2008065802 A1 WO2008065802 A1 WO 2008065802A1 JP 2007068821 W JP2007068821 W JP 2007068821W WO 2008065802 A1 WO2008065802 A1 WO 2008065802A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- compressor
- compression element
- shaft
- rotor
- diameter portion
- Prior art date
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
- 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
- F04C18/32—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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/0085—Prime movers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
-
- 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
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/12—Vibration
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/12—Kind or type gaseous, i.e. compressible
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2240/00—Components
- F05B2240/10—Stators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2240/00—Components
- F05B2240/20—Rotors
Definitions
- the present invention relates to a compressor used in, for example, an air conditioner or a refrigerator.
- a compressor has a hermetic container, a compression element disposed in the hermetic container, and a motor that is disposed in the hermetic container and drives the compression element via a shaft.
- the compression element and the rotor of the motor are integrally assembled via the shaft to form an integral structure (see Japanese Patent No. 3586145).
- the natural frequency of the integral structure portion of the compression element and the rotor may coincide with five times the number of rotations during operation of the compressor. If the natural frequency of the monolithic structure coincides with five times the number of rotations during compressor operation, there was a problem of generating large noise and vibration during compressor operation.
- an object of the present invention is to provide a compressor capable of preventing a large noise and vibration during operation of the compressor.
- a compressor according to the present invention provides:
- a compressor in which a single-piece structure is formed by assembling the parts integrally through the shaft,
- the special characteristic of the unitary structure is that the natural frequency is greater than five times the maximum number of revolutions during compressor operation.
- the natural frequency of the integral structure portion of the compression element and the rotor is greater than five times the maximum rotational speed during operation of the compressor. Driving Large noise and vibration during operation can be prevented within the range of rotation speed.
- a small diameter portion and a large diameter portion are provided inside the cylindrical rotor core of the rotor,
- the shaft is fixed to the small diameter portion
- a bearing that is provided on the compression element and supports the shaft is inserted into the large-diameter portion.
- the large diameter portion of the rotor core of the rotor is inserted with a bearing that is provided on the compression element and supports the shaft.
- the size in the axial direction can be shortened, the deflection can be reduced, the rigidity can be improved, and the natural frequency can be increased more reliably. Therefore, large noise and vibration during operation can be reduced, and cost can be reduced.
- the refrigerant in the sealed container is carbon dioxide.
- the refrigerant in the sealed container is carbon dioxide having a large refrigeration capacity per unit volume. Therefore, the cylinder chamber of the compression element is reduced, so that the shaft The diameter of the bearing and the diameter of the bearing are also reduced, the rigidity is lowered, and it is difficult to increase the natural frequency. Therefore, it is particularly effective to increase the natural frequency of a compressor using a refrigerant having a large refrigerating capacity, by adopting a configuration in which the bearing is inserted into the large diameter portion of the rotor core.
- the natural frequency of the integral structure portion of the compression element and the rotor is greater than 5 times the maximum rotational speed during operation of the compressor. It is possible to prevent large noise and vibration during operation within the range of rotation speed during operation.
- FIG. 1 is a longitudinal sectional view showing an embodiment of a compressor of the present invention.
- FIG. 1 is a longitudinal sectional view showing an embodiment of a compressor according to the present invention.
- the compressor includes a hermetic container 1, a compression element 2 disposed in the hermetic container 1, and a motor 3 disposed in the hermetic container 1 and driving the compression element 2 via a shaft 12. ing.
- This compressor is a so-called vertical high-pressure dome-type rotary compressor, in which the compression element 2 is placed down and the motor 3 is placed up in the sealed container 1.
- the rotor 6 of the motor 3 drives the compression element 2 via the shaft 12.
- An electrical terminal 140 that is electrically connected to the motor 3 is attached to the sealed container 1.
- the compression element 2 sucks the refrigerant gas from the accumulator (not shown) through the suction pipe 11.
- the refrigerant gas is obtained by controlling a condenser, an expansion mechanism, and an evaporator (not shown) that constitute an air conditioner as an example of a refrigeration system together with the compressor.
- This refrigerant is, for example, carbon dioxide, HFC such as HC or R410A, or HC FC such as R22.
- the compressor discharges the compressed high-temperature and high-pressure refrigerant gas from the compression element 2 to fill the inside of the hermetic container 1, and the gap between the stator 5 of the motor 3 and the rotor 6 is filled. After the motor 3 is cooled through the gap, the discharge pipe 13 provided on the upper side of the motor 3 is discharged to the outside.
- An oil reservoir 9 in which lubricating oil is stored is formed at the lower part of the high-pressure region in the closed container 1.
- the lubricating oil moves from the oil reservoir portion 9 through an oil passage (not shown) provided in the shaft 12 to a sliding portion such as the bearing of the compression element 2 or the motor 3, Lubricate the sliding part.
- This lubricating oil is, for example, a polyalkylene glycol oil (such as polyethylene glycol or polypropylene glycol), an ether oil, an ester oil, or a mineral oil.
- the compression element 2 includes a cylinder 21 attached to the inner surface of the hermetic container 1, an upper end plate member 50 and a lower end plate attached to the upper and lower open ends of the cylinder 21, respectively. Member 60.
- a cylinder chamber 22 is formed by the cylinder 21, the upper end plate member 50 and the lower end plate member 60.
- the upper end plate member 50 includes a disc-shaped main body 51 and a boss 52 provided upward in the center of the main body 51. The main body 51 and the boss 52 are passed through the shaft 12.
- the main body 51 is provided with a discharge port 51a communicating with the cylinder chamber 22.
- a discharge valve 31 is attached to the main body 51 so as to be located on the opposite side of the main body 51 from the cylinder 21.
- the discharge valve 31 is, for example, a reed valve, and opens and closes the discharge port 51a.
- a cup-type muffler cover 40 is attached to the main body 51 so as to cover the discharge valve 31 on the side opposite to the cylinder 21.
- the muffler cover 40 is fixed to the main body 51 by a fixing member 35 (such as a bolt).
- the muffler cover 40 is passed through the boss portion 52 described above.
- a muffler chamber 42 is formed by the muffler cover 40 and the upper end plate member 50.
- the muffler chamber 42 and the cylinder chamber 22 are communicated with each other through the discharge port 51a.
- the muffler cover 40 has a hole 43.
- the hole 43 communicates the muffler chamber 42 with the outside of the muffler cover 40.
- the lower end plate member 60 includes a disk-shaped main body 61 and a boss 62 provided downward in the center of the main body 61.
- the main body 61 and the boss 62 are passed through the shaft 12.
- one end of the shaft 12 is supported by the upper end plate member 50 and the lower end plate member 60. That is, the upper end plate member 50 and the lower end plate member 60 constitute the bearing 7, and the shaft 12 is cantilevered by the bearing 7.
- One end portion (support end side) of the shaft 12 enters the cylinder chamber 22.
- An eccentric pin 26 is provided on the support end side of the shaft 12 so as to be positioned in the cylinder chamber 22 on the compression element 2 side.
- the eccentric pin 26 is fitted to the roller 27.
- the roller 27 is disposed in the cylinder chamber 22 so as to be capable of revolving, and performs a compressing action by the revolving motion of the roller 27.
- the cylinder chamber 22 is partitioned by a blade 28 provided integrally with the roller 27. That is, in the chamber on the right side of the blade 28, the suction pipe 11 opens on the inner surface of the cylinder chamber 22 to form a suction chamber (low pressure chamber) 22a.
- the discharge port 51a (shown in FIG. 1) opens on the inner surface of the cylinder chamber 22 to form a discharge chamber (high pressure chamber) 22b.
- the eccentric pin 26 rotates eccentrically with the shaft 12, and the roller 27 fitted to the eccentric pin 26 is connected to the outer peripheral surface of the roller 27 by the inner peripheral surface of the cylinder chamber 22. Revolves in contact with.
- the refrigerant gas discharged from the discharge port 51 a is discharged to the outside of the muffler cover 40 via the muffler chamber 42.
- the motor 3 includes the rotor 6 and the stator 5 arranged on the outer side in the radial direction of the rotor 6 via a gap. That is, the motor 3 is an inner rotor type motor.
- the stator 5 includes a stator core 510, an insulator 530 disposed opposite to both axial end surfaces of the stator core 510, and a coil 520 wound around the stator core 510 and the insulator 530 together. Have.
- the stator core 510 is composed of a plurality of laminated steel plates, and is fitted into the sealed container 1 by shrink fitting or the like.
- the stator core 510 has an annular portion (not shown), and projects radially inward from the inner peripheral surface of the annular portion and is arranged at equal intervals in the circumferential direction. ⁇ It has a plurality of teeth (not shown) that are IJ.
- the coil 520 is wound around each of the tooth portions and wound around the plurality of tooth portions! /, Not V, or a concentrated winding.
- the rotor 6 includes a rotor core 610 and a magnet (not shown) embedded in the rotor core 610.
- the rotor core 610 has a cylindrical shape, and is made of, for example, laminated electromagnetic steel sheets.
- the magnets are, for example, rare earth-based flat permanent magnets, and are arranged at a plurality of magnet forces at equal intervals in the circumferential direction of the rotor core 610.
- a small diameter portion 610a is provided at the upper portion and a large diameter portion 610b is provided at the lower portion.
- the inner diameter of the small diameter portion 610a is smaller than the inner diameter of the large diameter portion 610b.
- the shaft 12 is fixed to the small diameter portion 610a.
- the large diameter portion 610b is inserted with the bearing 7 provided on the compression element 2 and supporting the shaft 12.
- the upper end portion of the boss portion 52 of the upper end plate member 50 is inserted into the large diameter portion 610b of the rotor core 610.
- the inner diameter of the large-diameter portion 610b of the rotor core 610 is formed larger than the outer diameter of the boss portion 52, and the lower end of the rotor core 610 is located lower than the upper end of the boss portion 52.
- the compression element 2 and the rotor 6 are integrally assembled via the shaft 12 to form an integral structure portion 8.
- the natural frequency of this monolithic structure 8 is greater than 5 times the maximum rotational speed during operation of the compressor.
- FIG. 3 shows the relationship between the natural frequency of the integral structure 8 of the compression element 2 and the rotor 6 and the loudness of the compressor.
- the horizontal axis shows the natural frequency [Hz] of the monolithic structure 8, and the vertical axis shows 5n sound [dB].
- the number of poles of the motor is 4, and the operating speed of the compressor is 86s- 1 .
- the natural frequency of the integrated structure 8 is greater than five times the maximum number of revolutions during the operation of the compressor, so the range of the number of revolutions during the operation of the compressor This can prevent large noise and vibration during operation.
- the natural frequency of the integrated structure 8 is set to 5 times the maximum rotational speed, a large noise is generated at the maximum rotational speed.
- the natural frequency of the monolithic structure part 8 is smaller than 5 times the maximum speed, for example, 4 times the maximum speed, a large noise can be prevented at the maximum speed, but the maximum speed can be prevented.
- a loud noise is generated when the number of revolutions is 4/5 times the number.
- the natural frequency of the monolithic structure portion 8 is larger than five times the maximum rotational speed during operation of the compressor. It is theoretically known that the modulation component generated between the basic excitation force component and the 1N component due to the swing of the rotor, that is, the excitation force that is (number of poles ⁇ 1) times the number of rotations, will increase. .
- the number of poles of a motor that is generally used for compressors is 4 poles, and the number of revolutions is ⁇ 1, that is, the excitation force is 3 or 5 times the number of revolutions.
- the rotation speed is 3 or 5 times within the range of the rotation speed during operation of the compressor. Therefore, the frequency and natural frequency do not coincide with each other, and large noise and vibration during operation can be prevented.
- the bearing 7 is inserted into the large-diameter portion 610b of the rotor core 610, the axial size of the integrated structure portion 8 can be shortened, the deflection can be reduced, and the rigidity can be reduced.
- the natural frequency can be increased more reliably. Therefore, a large noise and vibration during operation can be reduced and the cost can be reduced.
- the refrigerant in the sealed container 1 is carbon dioxide
- the carbon dioxide is a refrigerant having a large refrigeration capacity per unit volume
- the cylinder chamber 22 force S of the compression element 2 is small.
- the diameter of the shaft 12 and the diameter of the bearing 7 are also reduced, the rigidity is lowered, and it is difficult to increase the natural frequency. Therefore, the configuration in which the bearing 7 is inserted into the large-diameter portion 610b of the rotor core 610 is particularly effective for increasing the natural frequency of a compressor using a refrigerant having a large refrigerating capacity. Become.
- the coil 520 is a concentrated winding, and since the concentrated winding has a large and concentrated electromagnetic force applied to one of the teeth portions, the coil 520 is interposed between the stator 5 and the rotor 6. Increase rate force S of excitation force due to change of air gap S, force S larger than distributed winding S, the natural frequency of the integrated structure 8 above is greater than 5 times the maximum rotation speed during compressor operation Therefore, it is possible to prevent a large noise and vibration during operation particularly effectively.
- the magnet of the rotor 6 is a rare-earth magnet, and the rare-earth magnet has a larger residual magnetic flux density and coercive force than a ferrite magnet, and the magnet has a smaller area and thickness.
- the required magnetic flux amount and demagnetization resistance can be obtained, which can contribute to the downsizing of the rotor 6.
- the large diameter portion 61 Ob can be obtained because the space from the small diameter portion 610a of the rotor core 610 to which the shaft 12 is fixed can be widened. Can be provided.
- the motor 3 may be an outer rotor type motor.
- the compression element 2 may be a rotary type in which a roller and a blade are separate.
- the compression element 2 may be a two-cylinder type having two cylinder chambers. The compression element 2 may be arranged on the top and the motor 3 may be arranged on the bottom.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Compressor (AREA)
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US12/516,613 US20100074774A1 (en) | 2006-11-30 | 2007-09-27 | Compressor |
CN2007800422054A CN101535645B (zh) | 2006-11-30 | 2007-09-27 | 压缩机 |
EP07828567.3A EP2090780B1 (en) | 2006-11-30 | 2007-09-27 | Compressor |
AU2007326724A AU2007326724A1 (en) | 2006-11-30 | 2007-09-27 | Compressor |
ES07828567.3T ES2628343T3 (es) | 2006-11-30 | 2007-09-27 | Compresor |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006322874A JP2008138526A (ja) | 2006-11-30 | 2006-11-30 | 圧縮機 |
JP2006-322874 | 2006-11-30 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2008065802A1 true WO2008065802A1 (en) | 2008-06-05 |
Family
ID=39467600
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2007/068821 WO2008065802A1 (en) | 2006-11-30 | 2007-09-27 | Compressor |
Country Status (8)
Country | Link |
---|---|
US (1) | US20100074774A1 (ja) |
EP (1) | EP2090780B1 (ja) |
JP (1) | JP2008138526A (ja) |
KR (1) | KR101073270B1 (ja) |
CN (1) | CN101535645B (ja) |
AU (1) | AU2007326724A1 (ja) |
ES (1) | ES2628343T3 (ja) |
WO (1) | WO2008065802A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2010090082A1 (ja) * | 2009-02-03 | 2010-08-12 | ダイキン工業株式会社 | 固定子、モータ及び圧縮機 |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6119962B2 (ja) * | 2012-11-15 | 2017-04-26 | 株式会社豊田自動織機 | 電動圧縮機 |
TWM472176U (zh) * | 2013-11-07 | 2014-02-11 | Jia Huei Microsystem Refrigeration Co Ltd | 迴轉式壓縮機改良 |
JP6648785B2 (ja) * | 2018-07-11 | 2020-02-14 | 株式会社富士通ゼネラル | 圧縮機 |
US11757330B2 (en) | 2019-12-19 | 2023-09-12 | Black & Decker, Inc. | Canned outer-rotor brushless motor for a power tool |
US11437900B2 (en) | 2019-12-19 | 2022-09-06 | Black & Decker Inc. | Modular outer-rotor brushless motor for a power tool |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS54137706A (en) * | 1978-04-19 | 1979-10-25 | Hitachi Ltd | Full enclosed type motor-driven compressor |
JPS551442A (en) * | 1978-06-19 | 1980-01-08 | Matsushita Electric Ind Co Ltd | Compressor |
JPS60259778A (ja) * | 1984-06-06 | 1985-12-21 | Toshiba Corp | 圧縮機 |
JPH02196188A (ja) * | 1989-01-23 | 1990-08-02 | Hitachi Ltd | ロータリ圧縮機 |
JP2001073948A (ja) * | 1999-07-02 | 2001-03-21 | Matsushita Refrig Co Ltd | 電動圧縮機 |
JP3586145B2 (ja) | 1999-09-01 | 2004-11-10 | 東芝キヤリア株式会社 | 圧縮機 |
JP2005330821A (ja) * | 2004-05-18 | 2005-12-02 | Matsushita Electric Ind Co Ltd | 密閉型回転圧縮機 |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
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US1925166A (en) * | 1930-08-21 | 1933-09-05 | Climax Engineering Company | Compression unit for refrigerating systems |
CN1179126C (zh) * | 1999-07-02 | 2004-12-08 | 松下电器产业株式会社 | 电动压缩机 |
US20040241018A1 (en) * | 2001-07-06 | 2004-12-02 | Jens-Wolf Jaisle | Compressor driveable by an electric motor |
JP2004245073A (ja) * | 2003-02-12 | 2004-09-02 | Matsushita Electric Ind Co Ltd | 電動圧縮機 |
KR100702913B1 (ko) * | 2003-03-17 | 2007-04-03 | 마쯔시다덴기산교 가부시키가이샤 | 브러시리스 dc 모터의 구동 방법 및 그 장치 |
JP4492043B2 (ja) * | 2003-06-09 | 2010-06-30 | ダイキン工業株式会社 | 圧縮機 |
JP2007518911A (ja) * | 2003-09-26 | 2007-07-12 | 松下電器産業株式会社 | 圧縮機 |
US7604466B2 (en) * | 2005-01-31 | 2009-10-20 | Tecumseh Products Company | Discharge muffler system for a rotary compressor |
-
2006
- 2006-11-30 JP JP2006322874A patent/JP2008138526A/ja active Pending
-
2007
- 2007-09-27 WO PCT/JP2007/068821 patent/WO2008065802A1/ja active Application Filing
- 2007-09-27 AU AU2007326724A patent/AU2007326724A1/en not_active Abandoned
- 2007-09-27 CN CN2007800422054A patent/CN101535645B/zh active Active
- 2007-09-27 US US12/516,613 patent/US20100074774A1/en not_active Abandoned
- 2007-09-27 KR KR1020097009672A patent/KR101073270B1/ko active IP Right Grant
- 2007-09-27 EP EP07828567.3A patent/EP2090780B1/en active Active
- 2007-09-27 ES ES07828567.3T patent/ES2628343T3/es active Active
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS54137706A (en) * | 1978-04-19 | 1979-10-25 | Hitachi Ltd | Full enclosed type motor-driven compressor |
JPS551442A (en) * | 1978-06-19 | 1980-01-08 | Matsushita Electric Ind Co Ltd | Compressor |
JPS60259778A (ja) * | 1984-06-06 | 1985-12-21 | Toshiba Corp | 圧縮機 |
JPH02196188A (ja) * | 1989-01-23 | 1990-08-02 | Hitachi Ltd | ロータリ圧縮機 |
JP2001073948A (ja) * | 1999-07-02 | 2001-03-21 | Matsushita Refrig Co Ltd | 電動圧縮機 |
JP3586145B2 (ja) | 1999-09-01 | 2004-11-10 | 東芝キヤリア株式会社 | 圧縮機 |
JP2005330821A (ja) * | 2004-05-18 | 2005-12-02 | Matsushita Electric Ind Co Ltd | 密閉型回転圧縮機 |
Non-Patent Citations (1)
Title |
---|
See also references of EP2090780A4 |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2010090082A1 (ja) * | 2009-02-03 | 2010-08-12 | ダイキン工業株式会社 | 固定子、モータ及び圧縮機 |
JP2010183653A (ja) * | 2009-02-03 | 2010-08-19 | Daikin Ind Ltd | 固定子、モータ及び圧縮機 |
CN102301568A (zh) * | 2009-02-03 | 2011-12-28 | 大金工业株式会社 | 定子、电动机以及压缩机 |
US9118234B2 (en) | 2009-02-03 | 2015-08-25 | Daikin Industries, Ltd. | Stator, motor, and compressor |
Also Published As
Publication number | Publication date |
---|---|
KR101073270B1 (ko) | 2011-10-12 |
CN101535645B (zh) | 2011-06-01 |
AU2007326724A1 (en) | 2008-06-05 |
US20100074774A1 (en) | 2010-03-25 |
JP2008138526A (ja) | 2008-06-19 |
CN101535645A (zh) | 2009-09-16 |
EP2090780A4 (en) | 2014-12-31 |
KR20090067205A (ko) | 2009-06-24 |
ES2628343T3 (es) | 2017-08-02 |
EP2090780A1 (en) | 2009-08-19 |
EP2090780B1 (en) | 2017-05-24 |
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