EP3557065A1 - Compresseur doté d'un mécanisme de compression fixé à un carter - Google Patents

Compresseur doté d'un mécanisme de compression fixé à un carter Download PDF

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Publication number
EP3557065A1
EP3557065A1 EP17881953.8A EP17881953A EP3557065A1 EP 3557065 A1 EP3557065 A1 EP 3557065A1 EP 17881953 A EP17881953 A EP 17881953A EP 3557065 A1 EP3557065 A1 EP 3557065A1
Authority
EP
European Patent Office
Prior art keywords
cylindrical portion
compression mechanism
dimension
fixing
compressor
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.)
Withdrawn
Application number
EP17881953.8A
Other languages
German (de)
English (en)
Other versions
EP3557065A4 (fr
Inventor
Naoto Tomioka
Kiyofumi SHIROUZU
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 EP3557065A4 publication Critical patent/EP3557065A4/fr
Publication of EP3557065A1 publication Critical patent/EP3557065A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
    • F01C1/356—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F01C1/3562—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F01C1/3564—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—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
    • 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
    • F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • 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
    • F04C2240/40—Electric motor
    • 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

Definitions

  • the present invention relates to a compressor including a compression mechanism fixed to a casing.
  • An object of the present invention is to suppress vibrations of a compressor.
  • a first aspect of the present invention provides a compressor including a casing, a motor, and a compression mechanism.
  • the casing includes a cylindrical portion having an inner diameter of a first dimension.
  • the motor includes a rotor having an outer diameter of a second dimension.
  • the compression mechanism is configured to compress a low-pressure refrigerant to generate the high-pressure refrigerant.
  • a ratio of the first dimension to the second dimension is equal to or less than 1.8.
  • the compression mechanism includes a fixing portion being in tight contact with an inner peripheral surface of the cylindrical portion at a position where the compression mechanism is disposed.
  • a third aspect of the present invention provides the compressor according to the first or second aspect, wherein an average value of distances from the cylindrical portion to the compression mechanism falls within a range from 0.00 mm or more to 0.15 mm or less in the overall circumference of the cylindrical portion.
  • This configuration brings about the small average value of the distances from the inner peripheral surface of the cylindrical portion to the fixing portion of the compression mechanism. This configuration therefore further enhances the degree of tight contact of the fixing portion with the inner peripheral surface. This configuration thus further suppresses vibrations of the compressor.
  • a fourth aspect of the present invention provides the compressor according to any one of the first to third aspects, further including four or more weld portions at which the compression mechanism is fixed to the cylindrical portion.
  • the four or more weld portions contribute to stiffness to joints between the compression mechanism and the cylindrical portion. This configuration thus further suppresses vibrations of the compressor.
  • a fifth aspect of the present invention provides the compressor according to the fourth aspect, including the weld portions the number of which is six or more.
  • This configuration shortens a difference in height from each joint between the compression mechanism and the cylindrical portion to the center of gravity of the rotor. This configuration thus further suppresses vibrations of the compressor.
  • a seventh aspect of the present invention provides the compressor according any one of the first to sixth aspects, wherein the cylindrical portion is a multi-segment expanded tube including eight or more inner diameter increased portions and eight or more inner diameter decreased portions.
  • An eighth aspect of the present invention provides a method for manufacturing a compressor.
  • the manufacturing method includes a step of preparing a cylindrical portion having an inner diameter of a first dimension, a motor including a rotor having an outer diameter of a second dimension, and a compression mechanism configured to compress a low-pressure refrigerant to generate the high-pressure refrigerant.
  • the manufacturing method also includes a step of fixing the compression mechanism to the cylindrical portion so as to bring a fixing portion of the compression mechanism into tight contact with an inner peripheral surface of the cylindrical portion.
  • a ratio of the first dimension to the second dimension is equal to or less than 1.8.
  • This method enables tight contact of the compression mechanism with the cylindrical portion. This configuration therefore enables firm fixation of the compression mechanism to the casing. This configuration thus suppresses vibrations of the compressor.
  • a ninth aspect of the present invention provides the manufacturing method according to the eighth aspect, wherein the fixing portion extends over the compression mechanism so as to occupy 80% or more of an overall circumference of the inner peripheral surface.
  • the fixing portion of the compression mechanism occupies 80% or more of the overall circumference of the inner peripheral surface of the cylindrical portion. This configuration therefore enables tight contact of the compression mechanism with the casing over a wide range. This configuration thus further suppresses vibrations of the compressor.
  • a tenth aspect of the present invention provides the manufacturing method according to the eighth or ninth aspect, wherein the fixing step includes a step of welding the compression mechanism to the cylindrical portion at four or more positions.
  • the four or more weld portions contribute to stiffness to joints between the compression mechanism and the cylindrical portion. This configuration thus further suppresses vibrations of the compressor.
  • An eleventh aspect of the present invention provides the manufacturing method according to the tenth aspect, wherein in the fixing step, an average value of distances from the fixing portion to the inner peripheral surface falls within a range from 0.00 mm or more to 0.15 mm or less in the entire fixing portion.
  • This method brings about the small average value of the distances from the fixing portion of the compression mechanism to the inner peripheral surface of the cylindrical portion. This configuration therefore further enhances the degree of tight contact of the fixing portion with the inner peripheral surface. This configuration thus further suppresses vibrations of the compressor.
  • a twelfth aspect of the present invention provides the manufacturing method according to the eighth or ninth aspect, wherein the fixing step includes: a step of increasing the first dimension by heat application to the cylindrical portion; a step of inserting the compression mechanism into the cylindrical portion; and a step of decreasing the first dimension by heat radiation from the cylindrical portion.
  • the compression mechanism is fixed by shrink fitting to the cylindrical portion.
  • This configuration therefore enables contact of the compression mechanism with the substantially overall circumference of the cylindrical portion. This configuration thus further suppresses vibrations of the compressor.
  • a thirteenth aspect of the present invention provides the manufacturing method according to the eighth or ninth aspect, wherein the fixing step includes a step of applying a strong force to the compression mechanism to insert the compressor into the cylindrical portion while elastically deforming the cylindrical portion.
  • the compression mechanism is fixed by press fitting to the cylindrical portion.
  • This configuration therefore enables contact of the compression mechanism with the substantially overall circumference of the cylindrical portion. This configuration thus further suppresses vibrations of the compressor.
  • the motor is firmly fixed by shrink fitting to the cylindrical portion. This configuration therefore suppresses wobbles of the motor relative to the casing. This configuration thus further suppresses vibrations of the compressor.
  • the compressor according to any one of the first to seventh aspects of the present invention suppresses vibrations thereof.
  • the manufacturing method according to any one of the eighth to fourteenth aspects of the present invention suppresses vibrations of the compressor.
  • the casing 10 is configured to house the constituents of the compressor 5, and is resistant to high pressure of the refrigerant.
  • the casing 10 includes a cylindrical portion 11, an upper portion 12, and a lower portion 13.
  • the cylindrical portion 11 is the largest one of the constituents of the casing 10, and has a cylindrical shape.
  • Each of the upper portion 12 and the lower portion 13 is joined to the cylindrical portion 11.
  • the casing 10 has on its lower side an oil reservoir 14 where a refrigerating machine oil 141 is retained.
  • the cylindrical portion 11 has a suction pipe 15 mounted thereto.
  • the upper portion 12 has a discharge pipe 16 and a terminal 17 each mounted thereto.
  • the suction pipe 15 is disposed for sucking the low-pressure refrigerant.
  • the discharge pipe 16 is disposed for discharging the high-pressure refrigerant.
  • the terminal 17 is configured to receive external power supply.
  • the motor 20 is configured to generate mechanical power from electric power supplied from the terminal 17 via a lead wire (not illustrated).
  • the motor 20 includes a stator 21 and a rotor 22. As illustrated in FIG. 2 , the stator 21 has a cylindrical shape, and is fixed to the cylindrical portion 11 of the casing 10. A clearance 23 is defined between the stator 21 and the rotor 22. The clearance 23 functions as a refrigerant passage.
  • the rotor 22 includes a rotor core 22a, a permanent magnet 22b, end plates 22c, a balance weight 22d, and bolts 22e.
  • the rotor core 22a includes a stack of steel plates.
  • the rotor core 22a has a space 223 where the crank shaft 30 is fixed.
  • the permanent magnet 22b is used for rotating the entire rotor 22 by interacting with the alternating-current magnetic field generated by the winding wire 21c.
  • the permanent magnet 22b is disposed in a cavity 224 of the rotor core 22a.
  • the end plates 22c are respectively disposed on a rotor core upper surface 221 and a rotor core lower surface 222 to prevent the permanent magnet 22b from slipping out of the cavity 224.
  • the balance weight 22d is used for adjusting the center of gravity of a rotatable body including the rotor 22 and the components rotatable in conjunction with the rotor 22.
  • the balance weight 22d is disposed on one of the end plates 22c.
  • Each bolt 22e secures the end plates 22c or the balance weight 22d to the rotor core 22a.
  • the crank shaft 30 is configured to transmit to the compression mechanism 40 power generated by the motor 20.
  • the crank shaft 30 rotates about an axis of rotation RA.
  • the crank shaft 30 includes a main shaft portion 31 and an eccentric portion 32. A part of the main shaft portion 31 is fixed to the rotor 22.
  • the eccentric portion 32 is eccentric relative to the axis of rotation RA.
  • the compression mechanism 40 is configured to compress the low-pressure refrigerant to generate the high-pressure refrigerant.
  • the compression mechanism 40 includes a cylinder 41, a piston 42, a shaft support portion 61, an auxiliary shaft support portion 62, and a muffler 45.
  • the cylinder 41 is a metal member, and has an internal space communicating with the outside of the casing 10 through the suction pipe 15.
  • the piston 42 is a cylindrical metal member, and is smaller than the cylinder 41.
  • the piston 42 is mounted to the eccentric portion 32.
  • the eccentric portion 32 and the piston 42 are disposed in the internal space of the cylinder 41.
  • the shaft support portion 61 supports the main shaft portion 31 located above the eccentric portion 32, in a rotatable manner.
  • the shaft support portion 61 has a function of closing an upper side of the internal space in the cylinder 41.
  • the shaft support portion 61 is fixed to the cylindrical portion 11 at weld portions 50.
  • the auxiliary shaft support portion 62 supports the main shaft portion 31 located below the eccentric portion 32, in a rotatable manner.
  • the auxiliary shaft support portion 62 has a function of closing a lower side of the internal space in the cylinder 41.
  • the cylinder 41, the piston 42, the shaft support portion 61, and the auxiliary shaft support portion 62 define a compression chamber 43.
  • the muffler 45 is mounted to the shaft support portion 61.
  • the shaft support portion 61 and the muffler 45 define a muffler chamber.
  • the compression chamber 43 has a volumetric capacity that increases or decreases by the revolution of the piston 42.
  • the compression mechanism 40 consequently compresses the low-pressure refrigerant to generate the high-pressure refrigerant.
  • the high-pressure refrigerant is discharged from the compression chamber 43 toward the muffler chamber through a passage 44 formed in the shaft support portion 61.
  • a discharge valve (not illustrated) is disposed on the passage 44. The discharge valve suppresses a backflow of the high-pressure refrigerant from the muffler chamber toward the compression chamber 43.
  • the high-pressure refrigerant passes through the passage 44 each time the piston 42 revolves once.
  • the high-pressure refrigerant intermittently passing through the passage 44 may cause noise.
  • the muffler 45 smooths variations in pressure of the gas refrigerant, thereby reducing noise.
  • the high-pressure refrigerant is discharged from the compression mechanism 40 through a discharge hole 46 formed in the muffler 45.
  • arrows each indicate a flow of the refrigerant.
  • the low-pressure refrigerant is sucked into the compression chamber 43 of the compression mechanism 40 through the suction pipe 15.
  • the compression mechanism 40 compresses the low-pressure refrigerant to generate the high-pressure refrigerant.
  • the high-pressure refrigerant passes through the passage 44 and the discharge hole 46.
  • the high-pressure refrigerant is then discharged from the compression mechanism 40. Thereafter, the high-pressure refrigerant is blown toward the rotor 22, and then flows toward the clearance 23.
  • the high-pressure refrigerant flows upward through the clearance 23, and then is discharged from the casing 10 through the discharge pipe 16.
  • the rotor 22 of the compressor 5 is configured to rotate at 100 to 150 rps (revolutions per second), preferably 120 to 130 rps. This rotational speed is faster than the rotational speed (e.g., 15 to 75 rps) of a rotor of a conventional compressor.
  • FIG. 5 illustrates dimensions of the respective components in the compressor 5.
  • a first dimension D1 refers to an inner diameter of the cylindrical portion 11 of the casing 10.
  • a second dimension D2 refers to an outer diameter of the rotor core 22a of the rotor 22.
  • a ratio D1/D2 of the first dimension D1 to the second dimension D2 is designed to be equal to or less than 1.8.
  • the first dimension D1 is 90 mm
  • the second dimension is 50 mm.
  • the ratio D1/D2 may be designed to be less than 1.8.
  • FIG. 7A illustrates the compression mechanism 40.
  • the compression mechanism 40 includes a fixing portion 49.
  • the fixing portion 49 extends over an outer periphery of the compression mechanism 40.
  • the outer periphery of the compression mechanism 40 corresponds to an overall circumference of the cylindrical portion 11.
  • the fixing portion 49 is brought into tight contact with the inner peripheral surface of the cylindrical portion 11 of the casing 10, at a position where the compression mechanism 40 is disposed, that is, a height position of the compression mechanism 40.
  • each of the compression mechanism 40 and the cylindrical portion 11 is formed with accurate roundness. Specifically, an average value of distances from the fixing portion 49 to the inner peripheral surface of the cylindrical portion 11 falls within a range from 0.00 mm or more to 0.15 mm or less in the entire fixing portion 49.
  • the compression mechanism 40 may have a configuration illustrated in FIG. 7B in place of the configuration illustrated in FIG. 7A .
  • the compression mechanism 40 has a cutout 48.
  • the cutout 48 is formed in a part of the outer periphery of the compression mechanism 40, and is out of contact with the inner peripheral surface of the cylindrical portion 11.
  • the fixing portion 49 extends over the outer periphery of the compression mechanism 40 so as to occupy 80% or more of the overall circumference of the cylindrical portion 11, rather than the overall circumference of the cylindrical portion 11.
  • an average value of distances from the fixing portion 49 to the inner peripheral surface of the cylindrical portion 11 falls within a range from 0.00 mm or more to 0.15 mm or less in the entire fixing portion 49.
  • a method for manufacturing the compressor 5 according to the present invention includes the following steps.
  • the average value of the distances from the fixing portion 49 of the compression mechanism 40 to the inner peripheral surface of the cylindrical portion 11 is small. This configuration therefore further enhances the degree of tight contact of the fixing portion 49 with the inner peripheral surface. This configuration thus further suppresses vibrations of the compressor 5.
  • FIG. 8 illustrates a cylindrical portion 11 of a casing 10 for use in a compressor 5 according to a modification of the foregoing embodiment.
  • the cylindrical portion 11 is a multi-segment expanded tube.
  • the cylindrical portion 11 is produced with a tube expander.
  • the cylindrical portion 11 thus includes eight or more inner diameter increased portions 121 and eight or more inner diameter decreased portions 122.
  • Patent Literature 1 JP 2006-144731 A

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
EP17881953.8A 2016-12-13 2017-12-07 Compresseur doté d'un mécanisme de compression fixé à un carter Withdrawn EP3557065A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016241042A JP2018096272A (ja) 2016-12-13 2016-12-13 ケーシングに固定された圧縮機構を備える圧縮機
PCT/JP2017/044014 WO2018110426A1 (fr) 2016-12-13 2017-12-07 Compresseur doté d'un mécanisme de compression fixé à un carter

Publications (2)

Publication Number Publication Date
EP3557065A4 EP3557065A4 (fr) 2019-10-23
EP3557065A1 true EP3557065A1 (fr) 2019-10-23

Family

ID=62558502

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17881953.8A Withdrawn EP3557065A1 (fr) 2016-12-13 2017-12-07 Compresseur doté d'un mécanisme de compression fixé à un carter

Country Status (5)

Country Link
EP (1) EP3557065A1 (fr)
JP (1) JP2018096272A (fr)
CN (1) CN110073108A (fr)
AU (1) AU2017375095B2 (fr)
WO (1) WO2018110426A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7381975B2 (ja) * 2022-03-31 2023-11-16 ダイキン工業株式会社 圧縮機及び空調装置

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4930166B1 (fr) * 1969-05-19 1974-08-10
JPS559856U (fr) * 1978-07-06 1980-01-22
JPS6040793A (ja) * 1983-08-12 1985-03-04 Matsushita Refrig Co 回転式圧縮機
JPS61138889A (ja) * 1984-12-11 1986-06-26 Matsushita Electric Ind Co Ltd 密閉型電動圧縮機
JPS6336087A (ja) * 1986-07-29 1988-02-16 Matsushita Refrig Co 回転型圧縮機
JPS6361794A (ja) * 1986-09-02 1988-03-17 Matsushita Refrig Co 回転型圧縮機
JPH1025552A (ja) * 1996-07-10 1998-01-27 Nippon Steel Corp 打抜き寸法精度の優れた無方向性電磁鋼板
JP2006115581A (ja) * 2004-10-13 2006-04-27 Matsushita Electric Ind Co Ltd 密閉型電動圧縮機
JP2006144731A (ja) 2004-11-24 2006-06-08 Matsushita Electric Ind Co Ltd 圧縮機
CN101153600A (zh) * 2006-09-29 2008-04-02 富士通将军股份有限公司 旋转压缩机和热泵系统
JP2008106738A (ja) * 2006-09-29 2008-05-08 Fujitsu General Ltd ロータリ圧縮機およびヒートポンプシステム
JP4932640B2 (ja) * 2007-08-23 2012-05-16 新日本製鐵株式会社 鉄損最適化システム
CN102046981A (zh) * 2008-05-28 2011-05-04 东芝开利株式会社 密闭型压缩机以及制冷循环装置
JP2010206956A (ja) * 2009-03-04 2010-09-16 Daikin Ind Ltd 圧縮機
JP5732716B2 (ja) * 2009-11-26 2015-06-10 Ｊｆｅスチール株式会社 モータコア
JP2011163142A (ja) * 2010-02-05 2011-08-25 Toshiba Carrier Corp 密閉型圧縮機及び冷凍サイクル装置
CN105275811A (zh) * 2014-06-17 2016-01-27 广东美芝制冷设备有限公司 旋转式压缩机和具有其的制冷系统

Also Published As

Publication number Publication date
EP3557065A4 (fr) 2019-10-23
AU2017375095A1 (en) 2019-07-25
CN110073108A (zh) 2019-07-30
AU2017375095B2 (en) 2020-09-10
WO2018110426A1 (fr) 2018-06-21
JP2018096272A (ja) 2018-06-21

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