EP2418386B1 - Rotary compressor - Google Patents

Rotary compressor Download PDF

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Publication number
EP2418386B1
EP2418386B1 EP10761437.2A EP10761437A EP2418386B1 EP 2418386 B1 EP2418386 B1 EP 2418386B1 EP 10761437 A EP10761437 A EP 10761437A EP 2418386 B1 EP2418386 B1 EP 2418386B1
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EP
European Patent Office
Prior art keywords
piston
rotary compressor
vane
cylinder
high pressure
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.)
Active
Application number
EP10761437.2A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2418386A4 (en
EP2418386A2 (en
Inventor
Daisuke Funakoshi
Noboru Iida
Tsuyoshi Karino
Masao Nakano
Kiyoshi Sawai
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.)
Panasonic Corp
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Panasonic Corp
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Filing date
Publication date
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Publication of EP2418386A2 publication Critical patent/EP2418386A2/en
Publication of EP2418386A4 publication Critical patent/EP2418386A4/en
Application granted granted Critical
Publication of EP2418386B1 publication Critical patent/EP2418386B1/en
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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
    • F04C18/324—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 inner member and reciprocating with respect to the outer member
    • 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • 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
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F04C2210/261—Carbon dioxide (CO2)
    • 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
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F04C2210/263—HFO1234YF
    • 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
    • F04C2250/00—Geometry
    • 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

Definitions

  • the present invention relates to a rotary compressor having a vane including a columnar portion, in which a compression chamber is divided into a high pressure-side space and a low pressure-side space by the vane by inserting the columnar portion into a slot formed in a cylinder.
  • a compressor In a conventional refrigerating appliance and air conditioner, a compressor is used for sucking gas refrigerant evaporated by an evaporator, for compressing the gas refrigerant to a pressure required for condensing the sucked gas refrigerant, and for sending out the high temperature and high pressure gas refrigerant.
  • a rolling piston type rotary compressor (simply rotary compressor, hereinafter) is known as one of such compressors.
  • Fig. 10 is a partial vertical sectional view showing one example of the conventional rotary compressor.
  • Fig. 11 is a transverse sectional view of the rotary compressor shown in Fig. 10 taken along a plane A-A.
  • the rotary compressor includes a container 201, and an electric motor 202, a compressing mechanism 203 and a shaft 231 are accommodated in the container 201, and the electric motor 202 and the compressing mechanism 203 are connected to each other through the shaft 231.
  • the compressing mechanism 203 includes a cylinder 230, an upper bearing 234 and a lower bearing 235 which respectively close an upper end surface and a lower end surface of the cylinder 230.
  • the cylinder 230, the upper bearing 234 and the lower bearing 235 form a space called a compression chamber 239.
  • a piston 232 is provided in the compression chamber 239.
  • the piston 232 is fitted into an eccentric portion 231a of the shaft 231 supported by the upper bearing 234 and the lower bearing 235.
  • a vane 233 is provided in the compression chamber 239. The vane 233 follows eccentric rotation of an outer periphery of the piston 232 and reciprocates, and the vane 233 divides the compression chamber 239 into a low pressure-side space and a high pressure-side space.
  • An oil hole 241 is formed in the shaft 231 along a center axis of the shaft 231, and an oil supply hole 242 and an oil supply hole 243 which are in communication with the oil hole 241 are formed in a lower end of the upper bearing 234 and an upper end of the lower bearing 235.
  • an oil supply hole 244 which is in communication with the oil hole 241 is provided in the shaft 231 at a location adjacent to the eccentric portion 231a.
  • An oil groove 245 passing through an opening of the oil supply hole 244 is formed in an outer periphery of the shaft 231.
  • a suction port 240 through which gas is sucked is formed in the cylinder 230 in a low pressure-side space of the cylinder 239.
  • a discharge port 238 through which gas is discharged from a high pressure-side space or the compression chamber 239 which is formed from the low pressure-side space is formed in the upper bearing 234.
  • the discharge port 238 penetrates the upper bearing 234, and the discharge port 238 is a circular hole as viewed from above.
  • a discharge valve 236 is provided in the upper bearing 234 above the discharge port 238. When the discharge valve 236 receives a pressure greater than a predetermined value from the discharge port 238, the discharge valve 236 opens the discharge port 238.
  • a cup muffler 237 is disposed on the upper bearing 234 such as to cover the discharge valve 236.
  • the low pressure-side space of the compression chamber 239 is gradually enlarged. While the low pressure-side space of the compression chamber 239 is enlarged, gas is sucked from the suction port 240 into the low pressure-side space.
  • the discharge valve 236 opens and the gas flows from the discharge port 238 to the cup muffler 237. Gas in the cup muffler 237 is discharged into the container 201.
  • Fig. 12 is a transverse sectional view showing an essential portion of a swinging piston type rotary compressor, which is one solving means of the wearing problem.
  • the swinging piston type rotary compressor includes a cylinder 130 in which a slot 130b is formed, a piston 132 disposed in the cylinder 130, and a vane 133 which is swingably connected to the piston 132 and which reciprocates in the slot 130b as the piston 132 moves.
  • the piston 132 is fitted into an eccentric portion of a crankshaft 131.
  • the present invention provides a rotary compressor comprising the features recited in claim 1. According to the above-described configuration, since the arc portion of the groove formed in the piston can be increased, a sealing width between the high pressure-side space and the low pressure-side space is increased. According to this, when the vane reciprocates in the slot, leakage of gas and oil from the high pressure-side space to the low pressure-side space can be minimized and therefore, it is possible to provide a rotary compressor having high efficiency.
  • the present invention is characterized in that the groove is formed into a columnar shape having an arc whose angle is greater than 180°, and a fictitious extension of the arc is located inside of an outer periphery fictitious line of the piston.
  • the sealing width between the high pressure-side space and the low pressure-side space is increased. According to this, when the vane reciprocates in the slot, leakage of gas and oil from the high pressure-side space to the low pressure-side space of the compression chamber can be reduced and as a result, the efficiency of the rotary compressor is enhanced.
  • the groove of the piston is formed, a hole is first formed in the piston and then, portions other than arc can be formed. According to this, the machining precision such as the roundness of the arc portion of the groove and the squareness is enhanced, and the machining cost can be reduced, and the efficiency of the rotary compressor is enhanced.
  • a body of the vane includes one of side surfaces facing the low pressure-side space, the other side surface facing the high pressure-side space, an upper end surface which is in contact with an upper end of the one side surface and an upper end of the other side surface, and a lower end surface which is in contact with a lower end of the one side surface and a lower end of the other side surface, a low pressure-side constriction is provided between the one side surface and the columnar portion, a high pressure-side constriction is provided between the other side surface and the columnar portion, in a state where the piston is in contact with the slot, a top clearance volume is formed by the high pressure-side constriction, the piston and the cylinder, a clearance volume is formed by the low pressure-side constriction, the piston and the cylinder, and the clearance volume is smaller than the top clearance volume.
  • a fictitious surface which passes through a center of the columnar portion and which is in parallel to the fictitious center surface is deviated toward the other side surface width respect to the fictitious center surface of the pair of the side surfaces.
  • the high pressure-side constriction is smaller than the low pressure-side constriction.
  • the rotary compressor it is necessary to provide a low pressure-side constriction, a high pressure-side constriction and a releasing space.
  • the top clearance volume formed by the high pressure-side constriction, the piston and the cylinder again expands at the time of the suction operation, and a loss is generated.
  • the top clearance volume is made smaller than the clearance volume, a moving amount of the high pressure gas toward the low pressure-side space is reduced, and the efficiency of the compressor is enhanced.
  • the present invention is characterized in that a mark is provided on an upper end surface or the lower end surface.
  • the mark functions as a réelle for determining upper and lower directions when the compressor is assembles, and a loss caused by erroneous assembling operation can be reduced.
  • the mark may be provided in a lower end surface instead of the upper end surface of the vane. It is preferable that the mark is a dip.
  • the rotary compressor of the present invention it is possible to use a CO 2 refrigerant as the working fluid.
  • the CO 2 refrigerant has a great pressure difference, a sliding loss and a leakage loss are high, but if the columnar portion and the groove are designed as described above, it becomes preferable to use CO 2 as the working fluid. According to this, the efficiency and the reliability of the compressor can be enhanced.
  • a refrigerant having hydrofluoroolefin as a base ingredient having a carton-carbon double bond in which hydrofluorocarbon having no double bond is mixed. Since this refrigerant does not include chlorine, the refrigerant is extremely severe in terms of reliability of the sliding portions. However, if the groove is formed as described above and this refrigerant is used, it is possible to enhance the efficiency and the reliability of the compressor more effectively. Further, since this refrigerant has a low warming potential and is free from ozone destruction, it is possible to contribute to configuration of an dearth-friendly air-conditioning cycle.
  • Fig. 1 is a partial vertical sectional view of a swinging piston type rotary compressor according to one embodiment of the present invention.
  • Fig. 2 is an enlarged sectional view of a compressing mechanism of the rotary compressor shown in Fig. 1 .
  • the rotary compressor has a container 1.
  • An electric motor 2, a compressing mechanism 3 and a shaft 31 are accommodated in the container 1.
  • the electric motor 2 and the compressing mechanism 3 are connected to each other through the shaft 31.
  • the compressing mechanism 3 includes a cylinder 30.
  • the compressing mechanism 3 further includes an upper bearing 34 and a lower bearing 35 which respectively close an upper end surface and a lower end surface of the cylinder 30.
  • the upper bearing 34 and the lower bearing 35 support the shaft 31.
  • the shaft 31 forms an eccentric portion 31a, and the eccentric portion 31a is disposed in the cylinder 30.
  • a piston 32 is fitted into the eccentric portion 31a.
  • a compression chamber 39 is formed by a space surrounded by the upper bearing 34 and the lower bearing 35 between the cylinder 30 and the piston 32.
  • a vane 33 is provided in the compression chamber 39. The vane 33 divides the compression chamber 39 into a low pressure-side space 39a and a high pressure-side space 39b.
  • a slot 30b is provided in the cylinder 30.
  • a body portion of the vane 33 is inserted into the slot 30b such that the body portion can reciprocate therein.
  • a columnar portion 33a as shown in Figs. 3 to 5 is formed on one of ends of the vane 33.
  • the columnar portion 33a of the vane 33 is swingably fitted into a groove 32a formed in an outer periphery of the piston 32.
  • the groove 32a is formed in parallel to a rotation axis of the piston 32.
  • An oil hole 41 is formed in the shaft 31 along a center axis of the shaft 31, and an oil supply hole 42 and an oil supply hole 43 which are in communication with the oil hole 41 are provided in a lower end of the upper bearing 34 and an upper end of the lower bearing 35.
  • An oil supply hole 44 which is in communication with the oil hole 41 is provided in the shaft 31 at a location adjacent to the eccentric portion 31a.
  • An oil groove 45 passing through the oil supply hole 44 is formed in an outer periphery of the shaft 31.
  • a suction port 40 through which gas as working fluid is sucked is formed in the low pressure-side space 39a of the compression chamber 39 of the cylinder 30.
  • a discharge port 38 through which gas is discharged from the high pressure-side space 39b of the compression chamber 39 changed from the low pressure-side space 39a is formed in the upper bearing 34.
  • the discharge port 38 penetrates the upper bearing 34, and is formed as a circular hole as viewed from above.
  • a discharge valve 36 is provided above the discharge port 38 of the upper bearing 34, and the discharge valve 36 opens when it receives a pressure greater than a predetermined value from the discharge port 38.
  • a cup muffler 37 is disposed in the upper bearing 34 such as to cover the discharge valve 36.
  • Fig. 3 is a diagram showing a state transition of the compressing mechanism 3 while the shaft 31 shown in Fig. 1 makes one rotation.
  • a position where the columnar portion 33a of the vane 33 most approaches an inner wall of the cylinder 30 is defined as 0°.
  • the low pressure-side space 39a of the compression chamber 39 is gradually enlarged to suck gas from the suction port 40.
  • the high pressure-side space 39b of the compression chamber 39 is gradually contracted to compress gas in the high pressure-side space 39b.
  • the discharge valve 36 opens, and the gas flows out from the discharge port 38.
  • the gas which flowed out is discharged into the container 1 from the cup muffler 37 shown in Fig. 1 , more specifically, into a high pressure discharge space 52 which is outside of the compressing mechanism 3.
  • a space 46 (see Fig. 2 ) is formed between the eccentric portion 31a, the upper bearing 34 and the piston 32, and a space 47 (see Fig. 2 ) is formed between the eccentric portion 31a, the lower bearing 35 and the piston 32. Oil leaks from the oil hole 41 into the spaces 46 and 47 through the oil supply holes 42 and 43. Pressures in the spaces 46 and 47 are higher than that in the compression chamber 39 at the time of normal operation.
  • Fig. 4 is an exploded perspective view of the piston 32 and the vane 33 shown in Figs. 1 and 2 .
  • a columnar portion 33a is provided on one of ends of the vane 33.
  • a body of the vane 33 includes one side surface 33b facing the low pressure-side space 39a, the other side surface 33c facing the high pressure-side space 39b, an upper end surface 33d connected to an upper end of the one side surface 33b and an upper end of the other side surface 33c, and a lower end surface 33e connected to a lower end of the one side surface 33b and a lower end of the other side surface 33c.
  • a low pressure-side constriction 33f is provided between the one side surface 33b and the columnar portion 33a, and a high pressure-side constriction 33g is provided between the other side surface 33c and the columnar portion 33a.
  • the columnar groove 32a is formed in the piston 32.
  • the groove 32a has substantially the same diameter as that of the columnar portion 33a, and an angle of an arc of the groove 32a is greater than 180°.
  • the columnar portion 33a is swingably fitted into the groove 32a, and they are connected to each other.
  • a fictitious extension La of the arc of the groove 32a is located inside of an outer periphery fictitious line Lb of the piston 32.
  • the arc of the groove 32a can be made large, and an inner peripheral area of the groove 32a with which the columnar portion 33a is in contact can be increased. Therefore, a sealing width between the high pressure-side space 39b and the low pressure-side space 39a of the compression chamber 39 is increased, leakage of gas and oil is reduced and thus, the efficiency of the compressor can be enhanced.
  • the groove 32a of the piston 32 When the groove 32a of the piston 32 is formed, a columnar hole is first formed in the piston 32 and then, portions other than arc are removed by cutting and the groove 32a can be formed. According to this, the machining precision such as the roundness of the arc portion of the groove 32a and the squareness with respect to the piston 32 is enhanced, and the machining cost can be reduced, and the efficiency is enhanced.
  • the fictitious extension La is located outside from the outer periphery fictitious line Lb as in a comparative example shown in Fig. 6 , the arc portion of the groove 32a is reduced and the sealing width is also reduced.
  • the columnar portion 33a is provided on the vane 33 such that a fictitious surface Pb which passes through a center of the columnar portion 33a and which is in parallel to a fictitious center surface Pa of the pair of side surfaces 33b and 33c is deviated toward the other side surface 33c than the fictitious center surface Pa with respect to the fictitious center surface Pa as shown in Fig. 7 .
  • a fictitious surface Pb which passes through a center of the columnar portion 33a and which is in parallel to a fictitious center surface Pa of the pair of side surfaces 33b and 33c is deviated toward the other side surface 33c than the fictitious center surface Pa with respect to the fictitious center surface Pa as shown in Fig. 7 .
  • the swinging piston type rotary compressor to prevent the piston 32 and the vane 33 from coming into contact with each other during operation, it is necessary to provide the low pressure-side constriction 33f and the high pressure-side constriction 33g to form a
  • a top clearance volume Vg is formed by the high pressure-side constriction 33g, the piston 32 and the cylinder 30, and a clearance volume Vf is formed by the low pressure-side constriction 33f, the piston 32 and the cylinder 30.
  • a clearance volume Vf is formed by the low pressure-side constriction 33f, the piston 32 and the cylinder 30.
  • the top clearance volume Vg since gas is expanded when it is sucked, a loss is generated. Therefore, if the high pressure-side constriction 33g is made smaller than the low pressure-side constriction 33f as shown in Fig. 7 , the top clearance volume Vg becomes smaller than the clearance volume Vf, the loss when the gas is sucked is reduced, and the efficiency of the compressor is enhanced.
  • the columnar portion 33a is provided such that the top clearance volume Vg becomes smaller than the clearance volume Vf as shown in Fig. 7 , the loss when the gas is sucked is reduced and the efficiency of the compressor is enhanced as compared with a case where the columnar portion 33a is provided on the vane 33 such that the fictitious center surface Pa matches with the fictitious surface Pb as shown in Fig. 8 .
  • a small dip is provided in the upper end surface 33d of the vane 33 as a mark 33h as shown in Fig. 9 for example.
  • the mark functions as a réelle for determining upper and lower directions when the compressor is assembled, and a loss caused by erroneous assembling operation can be reduced.
  • the mark 33h may be provided in a lower end surface 33e instead of the upper end surface 33d of the vane 33.
  • This compressor is suitable when CO 2 refrigerant is used as the working fluid.
  • the CO 2 refrigerant has a large pressure difference, a leakage loss and a sliding loss are high, but if the piston 32 and the vane 33 of this embodiment are employed, the efficiency and the reliability of the compressor can be enhanced more effectively.
  • this compressor as the working fluid, it is possible to use a refrigerant having hydrofluoroolefin as a base ingredient having a carbon-carbon double bond in which hydrofluorocarbon having no double bond is mixed. Since this refrigerant does not include chlorine, the refrigerant is extremely severe in terms of reliability of the sliding portions, but the reliability and efficiency can be enhanced more effectively by employing the piston 32 and the vane 33 of the embodiment. Further, since this refrigerant has a low warming potential and is free from ozone destruction, it is possible to constitute an earth-friendly air-conditioning cycle.
  • the rotary compressor of the present invention gas and oil are less prone to leak from the high pressure-side space to the low pressure-side space of the compression chamber, and the rotary compressor is suitable for a hot water supply apparatus, air conditioner, a refrigerator-freezer, a dehumidifier and the like.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP10761437.2A 2009-04-10 2010-04-07 Rotary compressor Active EP2418386B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2009095844A JP5504681B2 (ja) 2009-04-10 2009-04-10 ロータリ圧縮機
PCT/JP2010/002544 WO2010116733A2 (ja) 2009-04-10 2010-04-07 ロータリ圧縮機

Publications (3)

Publication Number Publication Date
EP2418386A2 EP2418386A2 (en) 2012-02-15
EP2418386A4 EP2418386A4 (en) 2014-07-23
EP2418386B1 true EP2418386B1 (en) 2017-12-20

Family

ID=42936655

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10761437.2A Active EP2418386B1 (en) 2009-04-10 2010-04-07 Rotary compressor

Country Status (4)

Country Link
EP (1) EP2418386B1 (zh)
JP (1) JP5504681B2 (zh)
CN (1) CN102317631B (zh)
WO (1) WO2010116733A2 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3767071A1 (en) * 2019-07-17 2021-01-20 LG Electronics Inc. Rotary compressor

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Publication number Priority date Publication date Assignee Title
DE102012004145A1 (de) 2012-02-29 2013-08-29 Dieter Brox Ringkolbenkompressor
KR102249115B1 (ko) 2014-09-19 2021-05-07 엘지전자 주식회사 압축기
CN106939886A (zh) * 2016-01-04 2017-07-11 熵零技术逻辑工程院集团股份有限公司 流体机构及应用其的系统
CN107061264A (zh) * 2016-01-04 2017-08-18 熵零技术逻辑工程院集团股份有限公司 流体机构及应用其的系统

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JP2000120572A (ja) 1998-10-12 2000-04-25 Sanyo Electric Co Ltd 回転式圧縮機
JP2003003967A (ja) * 2001-06-25 2003-01-08 Hitachi Ltd 揺動ピストン形圧縮機およびその圧縮機を用いた冷凍装置または空調装置
TWI558685B (zh) * 2005-06-24 2016-11-21 哈尼威爾國際公司 含有經氟取代之烯烴之組合物
JP5018008B2 (ja) * 2006-10-13 2012-09-05 ダイキン工業株式会社 回転式流体機械
JP2008223551A (ja) * 2007-03-09 2008-09-25 Daikin Ind Ltd 空気調和装置の圧縮機

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3767071A1 (en) * 2019-07-17 2021-01-20 LG Electronics Inc. Rotary compressor

Also Published As

Publication number Publication date
CN102317631A (zh) 2012-01-11
JP5504681B2 (ja) 2014-05-28
EP2418386A4 (en) 2014-07-23
EP2418386A2 (en) 2012-02-15
CN102317631B (zh) 2014-02-26
WO2010116733A3 (ja) 2010-12-16
JP2010248911A (ja) 2010-11-04
WO2010116733A2 (ja) 2010-10-14

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