EP2894341B1 - Compressor - Google Patents

Compressor Download PDF

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Publication number
EP2894341B1
EP2894341B1 EP13846059.7A EP13846059A EP2894341B1 EP 2894341 B1 EP2894341 B1 EP 2894341B1 EP 13846059 A EP13846059 A EP 13846059A EP 2894341 B1 EP2894341 B1 EP 2894341B1
Authority
EP
European Patent Office
Prior art keywords
muffler
shaft
refrigerant
encircling
main body
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
EP13846059.7A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2894341A4 (en
EP2894341A1 (en
Inventor
Shunsuke Yakushiji
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.)
Mitsubishi Heavy Industries Thermal Systems Ltd
Original Assignee
Mitsubishi Heavy Industries Thermal Systems 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 Mitsubishi Heavy Industries Thermal Systems Ltd filed Critical Mitsubishi Heavy Industries Thermal Systems Ltd
Publication of EP2894341A4 publication Critical patent/EP2894341A4/en
Publication of EP2894341A1 publication Critical patent/EP2894341A1/en
Application granted granted Critical
Publication of EP2894341B1 publication Critical patent/EP2894341B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30Rotary-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
    • F04C18/34Rotary-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
    • F04C18/356Rotary-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06Silencing
    • F04C29/065Noise dampening volumes, e.g. muffler chambers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06Silencing
    • F04C29/068Silencing the silencing means being arranged inside the pump housing
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00Combinations 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
    • F04C23/008Hermetic pumps

Definitions

  • the present invention relates to a compressor.
  • a rotary compressor used in a refrigeration cycle includes a cylinder into which a refrigerant is suctioned through a suction pipe, and a piston rotor which is rotated eccentrically inside the cylinder (e.g., Patent Literature 1).
  • the piston rotor is fixed on an eccentric shaft part of a shaft, and bearings which rotatably support the shaft are disposed on each side of the cylinder in the axial direction.
  • a compression chamber is formed by these bearings closing the inside of the cylinder.
  • a refrigerant suctioned into the compression chamber is compressed with rotation of the piston rotor, and is cyclically discharged from a discharge port formed in the bearing.
  • a muffler is provided so as to cover the bearing.
  • the muffler has a shape bulged in the direction away from the bearing, and circular muffler outlets penetrating through the bulged wall are formed in it.
  • the muffler reduces pressure pulsations of a refrigerant by causing the refrigerant to impinge on its inner surface, it is a challenge to reduce pressure pulsations in higher-power compressors of recent years. If a refrigerant with large pressure pulsations is discharged from the muffler outlet, large noise is generated on the outside of the muffler. Therefore, it is desirable to minimize the pressure pulsations of the refrigerant discharged from the muffler outlet.
  • pressure pulsations are linked to the intrinsic resonance property which is determined by the shape of the internal space of the muffler.
  • two outlets of the muffler are disposed in the vicinity of a node of a first-order resonance mode inside the muffler in order to reduce noise, and the muffler is given an asymmetric shape in planar view to displace these outlets from the positions of antinodes of a second-order resonance mode.
  • Patent Literature 1 although the positions of the antinodes of the first-order resonance mode and the second-order resonance mode are avoided in disposing the outlets of the muffler, actually, the muffler outlets are not completely removed from the positions of the antinodes of the second-order resonance mode, so that a refrigerant at the positions of the antinodes having large pressure fluctuations is discharged from the muffler outlets. Moreover, given third- and higher-order resonance modes, the positions of the muffler outlets of Patent Literature 1 always fall within the vicinity of the antinodes of at least one of the resonance modes.
  • the present invention aims to provide a compressor which can produce a high noise reduction effect by sufficiently reducing pressure pulsations of a refrigerant discharged from a muffler outlet.
  • Patent Literature 2 discloses a rotary compressor used for an air conditioner, having an envelopment portion that is provided in the main portion of the muffler, and is bent in the downward direction from an inner periphery of the main portion of the muffler.
  • a compressor of the present invention includes: a compression mechanism which compresses a refrigerant with rotation of a shaft; and a muffler which is provided around the shaft opposite to the compression mechanism and receives the refrigerant discharged from the compression mechanism.
  • a muffler outlet for discharging the refrigerant inside the muffler opens annularly along an outer periphery of the shaft, and a constriction, at which a passage of the refrigerant flowing toward the muffler outlet is narrowed in the length direction of the shaft, is formed around the shaft inside the muffler, an encircling part, which is provided in a main body of the muffler and encircles the outer periphery of the shaft inside the muffler, is bent downward from an inner peripheral edge part of the main body of the muffler, wherein the encircling part is further bent upward in the vicinity of an upper surface of the fixed part, and is continuous with a circular cylindrical flow straightening part lying on an upper side of the main body of the muffler, said cylindrical flow straightening part forming an outlet of the muffler, and wherein a passage is formed along the shaft between the encircling part and the shaft, and the constriction communicates with
  • the constriction in the present invention can be formed by disposing an encircling part, which encircles the outer periphery of the shaft, inside the muffler.
  • the constriction faces one end of the encircling part in the length direction.
  • the term "around the shaft” in the present invention also refers to around a member such as a bearing which is disposed around the shaft.
  • the muffler outlet since the muffler outlet is disposed along the outer periphery of the shaft, the muffler outlet lies in the vicinity of a node, at which pressure pulsations are minimum, in any resonance mode.
  • the refrigerant inside the muffler can be discharged from the vicinity of the node of any resonance mode, it is not necessary to give the muffler an asymmetric shape based on a specific mode. Thus, the design flexibility of the muffler can be improved.
  • the encircling part is provided in a main body of the muffler and protrudes to the inside of the muffler; a passage is formed along the shaft between the encircling part and the shaft; and the constriction communicates with the muffler outlet through the passage.
  • the encircling part in the present invention can also be configured, for example, by deep drawing so as to be integrally continuous with the main body of the muffler and constricted toward the inside of the muffler.
  • the compressor of the present invention it is possible to obtain a high noise reduction effect by sufficiently reducing pressure pulsations of a refrigerant discharged from a muffler outlet.
  • a rotary compressor 1 which is used for an air conditioner, a refrigerator, etc., includes a substantially circular cylindrical case 11, a motor 12 housed in the case 11, and a compression mechanism 20 driven by the motor 12 inside the case 11, and is connected with a refrigerant circuit (not shown).
  • the case 11 has a cylindrical shell 110, an upper lid 111 provided at the upper end of the shell 110, and a bottom lid 112 provided at the lower end of the shell 110.
  • the motor 12 and the compression mechanism 20 are hermetically sealed inside the case 11.
  • the shell 110 is provided with a suction pipe 15 for suctioning a refrigerant into the compression mechanism 20.
  • the suctioned refrigerant is compressed by the compression mechanism 20 and released to the inside of the case 11 and fills it.
  • the high-pressure refrigerant is discharged to the refrigerant circuit through a discharge pipe 17 provided through the upper lid 111.
  • the motor 12 includes a stator 121 fixed on the inner peripheral surface of the case 11, and a rotor 122 disposed on the inside of the stator 121 and rotated upon application of current to the stator 121.
  • the rotary drive force of the motor 12 is output to a shaft 123 fixed on the rotor 122.
  • the shaft 123 is disposed along the vertical direction and extends further to the lower side than the rotor 122.
  • the compression mechanism 20 includes: an eccentric shaft part 21 which is eccentric relative to the axial center of the shaft 123; a piston rotor 22 which is fitted on the outer periphery of the eccentric shaft part 21; a cylinder 23 on the inside of which the piston rotor 22 is disposed; and a first bearing 24 and a second bearing 25 which rotatably support the shaft 123.
  • This compression mechanism 20 compresses the refrigerant by gradually reducing the volume of a compression chamber 20P, which is formed inside the cylinder 23, with rotation of the piston rotor 22.
  • the eccentric shaft part 21 is formed integrally with the shaft 123 between the first bearing 24 and the second bearing 25, and is turned around the axis of the shaft 123.
  • the piston rotor 22 is rotated inside the cylinder 23 as the eccentric shaft part 21 turns.
  • the cylinder 23 has a circular cylindrical inner peripheral surface which comes into sliding contact with the outer peripheral surface of the piston rotor 22.
  • the axial center of the inner peripheral surface of the cylinder 23 coincides with the axial center of the shaft 123.
  • the inside of the cylinder 23 is closed by the first bearing 24 and the second bearing 25.
  • the cylinder 23 is provided with a blade (not shown) which partitions the inside of the cylinder 23 into a suction side and a discharge side, and a spring (not shown) which presses down the blade.
  • a suction port 26 penetrating through the side wall of the cylinder 23 is formed in the vicinity of the blade.
  • the suction port 26 is connected with the suction pipe 15.
  • This cylinder 23 is fixed on the inner wall of the case 11, and the first bearing 24 and the second bearing 25 are fixed on the upper and lower end surfaces, respectively, of the cylinder 23.
  • the first bearing 24 lying on the upper side of the cylinder 23 has a disc-like fixed part 241 to be fixed on the cylinder 23 and a sliding part 242 which rises up from a central part of the fixed part 241 and slides with the outer periphery of the shaft 123.
  • the fixed part 241 has a discharge port 27 (indicated by the broken line), which opens to the inside of the cylinder 23, formed in it so as to penetrate in the thickness direction.
  • a discharge port 27 (indicated by the broken line), which opens to the inside of the cylinder 23, formed in it so as to penetrate in the thickness direction.
  • the discharge port 27 is provided with a reed valve (not shown) which opens when the refrigerant pressure inside the compression chamber 20P reaches a predetermined value.
  • a muffler 30 is provided around the sliding part 242 opposite to the upper surface of the fixed part 241.
  • the muffler 30 reduces the pressure pulsations of the refrigerant and discharges the refrigerant from its muffler outlet 38 into the case 11.
  • the rotary compressor 1 of this embodiment features the structure of the muffler 30 shown in FIG. 2 .
  • the muffler 30 forms a discharge chamber 30A, between the muffler 30 and the upper surface of the fixed part 241, for the refrigerant discharged from the discharge port 27.
  • the muffler 30, which is formed in a substantially annular shape in planar view, includes a muffler main body 31 which receives the refrigerant ejected from the discharge port 27, an encircling part 32 encircling the outer periphery of the sliding part 242, and a flow straightening part 33 forming the muffler outlet 38.
  • the muffler 30 has the muffler main body 31, the encircling part 32, and the flow straightening part 33 integrally formed by deep drawing.
  • An outer peripheral edge part 311 of the muffler main body 31 is fixed with bolts (not shown) on the fixed part 241. While the muffler main body 31 of this embodiment is formed in a dome-like shape, the shape is arbitrary.
  • the encircling part 32 is continuous with an inner peripheral edge part 312 of the muffler main body 31 so as to be constricted toward the inside of the muffler 30.
  • the encircling part 32 is formed so as to be bent downward from the inner peripheral edge part 312 of the muffler main body 31, further bent to turn upward in the vicinity of the upper surface of the fixed part 241, and then be continuous with the circular cylindrical flow straightening part 33 lying on the upper side of the muffler main body 31.
  • a leading end 32A of the encircling part 32 has a curved surface.
  • the clearance in the height direction left between this leading end 32A and the upper surface of the fixed part 241 corresponds to a constriction 36 through which the refrigerant passes.
  • the constriction 36 is formed along the entire periphery of the sliding part 242.
  • the shaft 123 and the sliding part 242 are inserted into the encircling part 32 and the flow straightening part 33.
  • the inner diameters of these encircling part 32 and flow straightening part 33 are set to be larger than the outer diameter of the sliding part 242.
  • a passage 37 through which the refrigerant flows is formed between the sliding part 242 and the encircling part 32 and the flow straightening part 33 along the shaft 123.
  • the terminal end of this passage 37 is the muffler outlet 38 which opens annularly along the outer periphery of the sliding part 242.
  • the constriction 36 communicates with the muffler outlet 38 through the passage 37.
  • the rotary compressor 1 of this embodiment compresses a low-pressure refrigerant gas, which is suctioned through the suction pipe 15 from an accumulator (gas-liquid separator) (not shown) connected with the refrigerant circuit into the compression chamber 20P, and discharges the compressed refrigerant from the discharge port 27 into the muffler 30.
  • the refrigerant discharged from the muffler outlet 38 into the case 11 flows through the longitudinal groove 121A of the stator 121 to the upper space of the case 11 and is discharged to the external refrigerant circuit through the discharge pipe 17.
  • the refrigerant inside the muffler 30 resonates while repeatedly expanding and contracting according to the intrinsic resonance property of the muffler 30.
  • the muffler outlet 38 is formed in the vicinity of a node N, at which pressure fluctuations are small, in each resonance mode, it is possible to avoid discharging a refrigerant with large pressure fluctuations to the outside of the muffler 30, so that noise can be reduced.
  • muffler outlets 98 are provided beside the node N.
  • the positions of the muffler outlets 98 fall within the vicinity of antinodes AN of the second-order resonance mode shown in FIG. 3B .
  • the muffler outlets 98 always fall within at least the vicinity of the antinodes AN of the superimposed higher-order resonance modes.
  • the muffler outlet 38 is disposed along the outer periphery of the sliding part 242, but also the encircling part 32 is disposed inside the muffler 30 to form the constriction 36 facing the leading end 32A of the encircling part 32.
  • the muffler outlet 38 is disposed along the outer periphery of the sliding part 242, the muffler outlet 38 lies in the vicinity of the node N in any resonance mode.
  • the flow of the refrigerant is straightened along the shaft 123 by the passage 37 from the constriction 36 to the muffler outlet 38, which also contributes to noise reduction.
  • the refrigerant inside the muffler 30 can be discharged from the vicinity of the node N of any resonance mode, it is not necessary to give the muffler 30 an asymmetric shape based on a specific mode. Since the muffler 30 of this embodiment may have an arbitrary shape as long as it has the encircling part 32, the design flexibility of the muffler 30 can be improved.
  • the positions of the bolts fixing the muffler 30 There is also no restriction on the positions of the bolts fixing the muffler 30.
  • the muffler main body 31 is formed in a shape constricted toward the planar center at a plurality of positions on the circumference in order to form a plurality of bolt holes 39 into which the bolts are inserted, the resonance property of the muffler 30 is changed, but the positions of the bolt holes 39 can be set at arbitrary positions without the need for taking into account the positions of nodes and antinodes.
  • a muffler 40 in the first example includes a muffler main body 41 and an encircling part 42, which are separate parts.
  • the muffler main body 41 is formed by deep drawing almost in the same manner as the muffler main body 31 of the first embodiment, and has an opening 41A, into which the encircling part 42 is inserted, formed at the center.
  • the encircling part 42 is fixed by interference-fitting, shrink-fitting, etc. on the inner peripheral surface of the opening 41A of the muffler main body 41.
  • the encircling part 42 is formed by extrusion etc. into a circular cylinder having an inner diameter larger than the outer diameter of the sliding part 242.
  • a lower end 42A side of the encircling part 42 corresponds to the above-described encircling part 32, and an upper end 42B side of the encircling part 42 corresponds to the above-described flow straightening part 33.
  • the passage 37 is formed between the inner peripheral surface of the encircling part 42 and the outer peripheral surface of the sliding part 242.
  • the constriction 36 is formed between the lower end 42A of the encircling part 42 and the upper surface of the fixed part 241.
  • the muffler main body 41 of this first example has no folded part, it is easy to deep-draw. Since the muffler 40 can be produced simply by fixing the encircling part 42 on the muffler main body 41, the ease of processing can be improved.
  • the opening of the constriction 36 can be easily reduced by extending the encircling part 42 in the axial direction, the pressure pulsations of the refrigerant can be reduced more sufficiently.
  • the member to be used and the processing method of the muffler can be appropriately selected in consideration of the ease of processing.
  • encircling part 52 which rises up from the fixed part 241. There is no passage formed between the encircling part 52 and the sliding part 242.
  • a passage 57 is formed between the inner peripheral part of the muffler main body 41 and the outer peripheral surface of the shaft 123, and the terminal end of the passage 57 is the muffler outlet 38 which opens annularly along the outer periphery of the sliding part 242.
  • a leading end 52A of the encircling part 52 extends close to the passage 57, and forms a constriction 56 between the leading end 52A and the muffler main body 41.
  • the constriction 56 is formed along the entire circumference around the sliding part 242.
  • an encircling part 53 which protrudes downward from an inner peripheral part of the muffler main body 41.
  • the muffler main body 41 and the encircling part 53 are integrally formed by deep drawing. Since this muffler has no part which is bent to be turned up (in a hairpin shape), it is easy to deep-draw.
  • the passage 37 may be formed so as not to extend upward beyond the muffler main body 41.
  • the position of the constriction in the examples not falling under the scope of the claims is not limited to the vicinity of the upper surface of the fixed part 241 or the vicinity of the inner peripheral part of the muffler main body 41, but the constriction may be formed at an intermediate position in the height of the muffler. In that case, for example, an encircling part rising up from the fixed part 241, and an encircling part fixed on the muffler main body 41 and extending downward should be formed, and a constriction should be formed between the ends of these encircling parts.
  • the present invention is also applicable to a twin rotary compressor which includes two sets of cylinders and piston rotors.
  • the present invention is applicable to various types of compressors including a scroll compressor which has one scroll making revolving motion relative to the other scroll.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP13846059.7A 2012-10-11 2013-08-26 Compressor Active EP2894341B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012226183A JP6130642B2 (ja) 2012-10-11 2012-10-11 圧縮機
PCT/JP2013/005026 WO2014057602A1 (ja) 2012-10-11 2013-08-26 圧縮機

Publications (3)

Publication Number Publication Date
EP2894341A4 EP2894341A4 (en) 2015-07-15
EP2894341A1 EP2894341A1 (en) 2015-07-15
EP2894341B1 true EP2894341B1 (en) 2019-03-20

Family

ID=50477086

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13846059.7A Active EP2894341B1 (en) 2012-10-11 2013-08-26 Compressor

Country Status (3)

Country Link
EP (1) EP2894341B1 (ja)
JP (1) JP6130642B2 (ja)
WO (1) WO2014057602A1 (ja)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104863819B (zh) * 2015-04-07 2017-03-15 珠海凌达压缩机有限公司 压缩机消音结构的设计方法
CN106246558A (zh) * 2016-09-18 2016-12-21 珠海凌达压缩机有限公司 压缩机的消音器及具有其的压缩机
CN106837803A (zh) * 2017-03-06 2017-06-13 珠海凌达压缩机有限公司 消音器及压缩机
CN106917750A (zh) * 2017-04-20 2017-07-04 西安庆安制冷设备股份有限公司 一种降低旋转式压缩机噪声的结构

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Publication number Priority date Publication date Assignee Title
JPS5840591U (ja) * 1981-09-11 1983-03-17 株式会社東芝 密閉形圧縮機
JPH07103862B2 (ja) * 1990-07-31 1995-11-08 ダイキン工業株式会社 密閉形圧縮機
JPH04143482A (ja) * 1990-10-05 1992-05-18 Daikin Ind Ltd ローリングピストン型圧縮機
JPH0518373A (ja) * 1991-07-10 1993-01-26 Toshiba Corp スクロール式圧縮機
JP2005189627A (ja) * 2003-12-26 2005-07-14 Daikin Ind Ltd 消音装置及び圧縮機
JP3832468B2 (ja) * 2003-12-26 2006-10-11 ダイキン工業株式会社 圧縮機
JP2006283592A (ja) * 2005-03-31 2006-10-19 Daikin Ind Ltd 流体機械
CN100529406C (zh) * 2007-11-09 2009-08-19 广东美芝制冷设备有限公司 壳体低压的旋转式压缩机及其冷媒、回油的控制方式和应用
JP4911147B2 (ja) 2008-08-29 2012-04-04 ダイキン工業株式会社 マフラ部材及びそのマフラ部材を備えた圧縮機
JP5338275B2 (ja) * 2008-11-25 2013-11-13 ダイキン工業株式会社 吐出弁機構及び回転式圧縮機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
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Also Published As

Publication number Publication date
JP6130642B2 (ja) 2017-05-17
WO2014057602A1 (ja) 2014-04-17
JP2014077410A (ja) 2014-05-01
EP2894341A4 (en) 2015-07-15
EP2894341A1 (en) 2015-07-15

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