EP3015710A1 - Compresseur - Google Patents

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Publication number
EP3015710A1
EP3015710A1 EP14831427.1A EP14831427A EP3015710A1 EP 3015710 A1 EP3015710 A1 EP 3015710A1 EP 14831427 A EP14831427 A EP 14831427A EP 3015710 A1 EP3015710 A1 EP 3015710A1
Authority
EP
European Patent Office
Prior art keywords
central axis
refrigerant path
refrigerant
discharge port
open end
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP14831427.1A
Other languages
German (de)
English (en)
Other versions
EP3015710B1 (fr
EP3015710A4 (fr
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 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 Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP3015710A1 publication Critical patent/EP3015710A1/fr
Publication of EP3015710A4 publication Critical patent/EP3015710A4/fr
Application granted granted Critical
Publication of EP3015710B1 publication Critical patent/EP3015710B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • 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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0253—Details concerning the base
    • F04C18/0261—Details of the ports, e.g. location, number, 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
    • 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
    • F04C29/06—Silencing
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
    • F04C29/128—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type of the elastic type, e.g. reed valves
    • 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
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/102—Geometry of the inlet or outlet of the outlet

Definitions

  • the present invention relates to a compressor, and in particular, to a scroll compressor.
  • a scroll compressor which is used in a refrigeration cycle such as in an air conditioning device, a refrigerator, or the like, includes a fixed scroll and an orbiting scroll.
  • the fixed scroll and the orbiting scroll each have a spiral wrap formed integrally therewith on one surface side of a disk-shaped end plate.
  • the fixed scroll and the orbiting scroll are arranged so as to oppose each other with the respective wraps engaging each other, and the orbiting scroll is caused to revolve in relation to the fixed scroll by an electric motor or the like.
  • the refrigerant gas compressed in the compression chamber flows through a discharge port formed in the end plate of the fixed scroll and flows into a high pressure chamber between a discharge cover and a housing, and is discharged towards a refrigerant circuit from a discharge pipe provided in the housing.
  • the discharge port is often provided in an eccentric fashion in relation to a central axis of the fixed scroll in consideration of performance or the compression ratio of the refrigerant.
  • the discharge port formed in the fixed scroll has an effect on the performance of the scroll compressor or noise, and various configurations have been proposed.
  • Patent Document 1 proposes a configuration in which a cylindrical collar with a hollow center is fitted onto the discharge port in order to mitigate vibration/noise resulting from the discharge of fluid compressed by the revolution of the scroll.
  • a collar By providing a collar, it is possible to reduce excitation force from pressure pulsation within the cylinder and to mitigate noise.
  • Patent Document 1 Japanese Unexamined Utility Model Application Publication No. H4-82391U
  • Vibrations/noise generated by the scroll compressor have a wide frequency range, and noise occurs due to resonance in a plurality of different frequency bands. Thus, it is difficult to reduce noise in all frequency bands by using one noise reduction means as in Patent Document 1.
  • the present invention is made in view of such technical problems, and an object thereof is to provide a scroll compressor by which it is possible to reduce noise in a plurality of frequency bands occurring in a scroll compressor.
  • a compressor of the present invention is provided with an orbiting scroll that is rotatably linked to an eccentric shaft portion of a main shaft, a fixed scroll that forms a compression chamber that compresses the refrigerant by opposing the orbiting scroll and that, in the end plate, has a first refrigerant path through which the compressed refrigerant passes and that communicates with the compression chamber, and a second refrigerant path that communicates with the downstream side of the first refrigerant path and has a larger interior volume than that of the first refrigerant path.
  • the first refrigerant path is provided with an open end on the upstream side and an open end on the downstream side.
  • the upstream open end is eccentric relative to the central axis of the fixed scroll and the central axis of the second refrigerant path is in the area occupied by the downstream open end.
  • the refrigerant is discharged from the downstream side open end of the first refrigerant path towards nodes of a plurality of resonance modes formed in the central axis of the second refrigerant path.
  • it is possible to reduce the number of resonance modes generated and to reduce noise in the second refrigerant path.
  • a center of a downstream side open end of the first refrigerant path coincide with a central axis of the second refrigerant path.
  • the first refrigerant path be formed at an incline with respect to the central axis of the second refrigerant path.
  • the first refrigerant path By forming the first refrigerant path at an incline with respect to the central axis of the second refrigerant path, it is possible to discharge the refrigerant from the first refrigerant path towards the central axis of the second refrigerant path.
  • the first refrigerant path instead of forming the first refrigerant path at an incline with respect to the central axis of the second refrigerant path, it is possible to form the first refrigerant path such that the central axis thereof coincides with the central axis of the fixed scroll extending in the vertical direction.
  • the present invention can also provide a compressor in which the first refrigerant path and the second refrigerant path are formed in an end plate of the fixed scroll.
  • the upstream discharge port portion in the discharge port of the compressor such that refrigerant is discharged from the upstream discharge port portion towards the central axis of the discharge cavity, it is possible to reduce noise occurring in the discharge cavity.
  • a scroll compressor 1 of the present embodiment includes an electric motor 12, and a scroll compression mechanism 2 driven by the electric motor 12 within a housing 10.
  • the scroll compressor 1 compresses a refrigerant and supplies it to a refrigerant circuit in an air conditioner, a refrigerator, or the like, for example.
  • a configuration of the scroll compressor 1 will be described below.
  • the housing 10 includes a main housing body 101 that is a bottomed cylinder with an open top, and a housing top 102 that covers the open top of the main housing body 101.
  • the side surface of the main housing body 101 is provided with an intake pipe 13 through which refrigerant is introduced from an accumulator (not illustrated) into the main housing body 101.
  • the housing top 102 is provided with a discharge pipe 14 that discharges refrigerant that has been compressed by the scroll compression mechanism 2.
  • the interior of the housing 10 is partitioned by a discharge cover 27 into a low pressure chamber 10A and a high pressure chamber 10B.
  • the electric motor 12 includes a stator 15 and a rotor 16.
  • the stator 15 is provided with a coil that generates a magnetic field as a result of power being supplied thereto through a power supply unit (not illustrated) attached to the side surface of the main housing body 101.
  • the rotor 16 includes as primary components a permanent magnet and a yoke, and furthermore, a main shaft 17 is joined integrally therewith in the center of the rotor 16.
  • An upper bearing 18 and a lower bearing 19, which rotatably support the main shaft 17, are provided on either end of the main shaft 17 across the electric motor 12.
  • An eccentric pin 17A provided on the upper end of the main shaft 17 protrudes into and is accommodated in an accommodation space 190 formed in the upper bearing 18.
  • the scroll compression mechanism 2 includes a fixed scroll 20 and an orbiting scroll 30 that revolves in relation to the fixed scroll 20.
  • the fixed scroll 20 includes a fixed end plate 21 and a spiral wrap 22 that is stood upright from one surface of the fixed end plate 21.
  • the fixed end plate 21 includes a discharge port 23.
  • the fixed scroll 20 is provided such that the central axis C thereof coincides with the central axis of the main shaft 17.
  • the discharge port 23 includes an upstream discharge port portion 24 and a discharge cavity 25 that communicates with the upstream discharge port portion 24 and has a larger interior volume than that of the upstream discharge port portion 24, both the upstream discharge port portion 24 and the discharge cavity 25 having a circular opening shape.
  • the upstream discharge port portion 24 corresponds to the first refrigerant path of the present invention
  • the discharge cavity 25 corresponds to the second refrigerant path of the present invention.
  • the upstream discharge port portion 24 is disposed to the upstream side according to a flow direction A of the refrigerant, and the discharge cavity 25 is disposed to the downstream side.
  • the center of the open end 24B on the upstream side of the upstream discharge port portion 24 is formed so as to be eccentric in relation to the central axis C of the fixed scroll 20.
  • the center P1 of the open end 24A on the downstream side coincides with the central axis C2, which coincides with the central axis C, of the discharge cavity 25.
  • the upstream discharge port portion 24 is formed so as to be inclined in relation to the central axis C2 (flow direction A of refrigerant).
  • the upstream discharge port portion 24 is formed in an inclined fashion in this manner is a characteristic of the present embodiment, and the refrigerant passing through the upstream discharge port portion 24 is discharged towards the central axis C2 of the discharge cavity 25. Details will be described later, but as a result of the flow of refrigerant, the scroll compressor 1 can prevent the generation of a number of resonance modes.
  • the upstream side of the upstream discharge port portion 24 communicates with a compression chamber PR formed between the fixed scroll 20 and the orbiting scroll 30.
  • the downstream side of the discharge cavity 25 communicates with a downstream discharge port portion 26 of the discharge cover 27 covering the top of the fixed scroll 20.
  • the discharge cavity 25, the downstream discharge port portion 26, and the high pressure chamber 10B are provided such that the respective central axes C2, C3, and C4 thereof coincide with the central axis C of the fixed scroll 20 along the vertical direction.
  • the center P2 of the downstream side open end 26A of the downstream discharge port portion 26 coincides with the central axis C4 of the high pressure chamber 10B
  • the center of the upstream side open end 26B coincides with the central axis C2.
  • the orbiting scroll 30 also includes an orbiting end plate 31 having a disk shape and a spiral wrap 32 that is stood upright from one surface of the orbiting end plate 31.
  • the rear surface of the orbiting end plate 31 of the orbiting scroll 30 is provided with a boss 34, and a drive bush 36 is attached to the boss 34 through a bearing.
  • the eccentric pin 17A is fitted into the inside of the drive bush 36. In this manner, the orbiting scroll 30 is joined in an eccentric manner to the center of main shaft 17, and thus, when the main shaft 17 rotates, the orbiting scroll 30 rotates (revolves) with the eccentric distance from the center of the main shaft 17 being the turning radius.
  • the orbiting scroll 30 is provided with an Oldham ring (not illustrated) that restricts rotation between the orbiting scroll 30 and the main shaft 17 such that the orbiting scroll 30 revolves but does not rotate.
  • Wraps 22 and 32 which are eccentric with respect to each other by a prescribed amount and are engaged with each other while being shifted by a 180° phase, are in contact with each other in a plurality of positions according to the rotational angle of the orbiting scroll 30.
  • the compression chamber PR is formed so as to have point symmetry about the center (innermost periphery) of the spirals of the wraps 22 and 32, and as a result of the revolution of the orbiting scroll 30, the compression chamber is moved gradually inward while the inner volume thereof decreases. The refrigerant is compressed to the maximum in the center of the spirals.
  • the compression chamber PR of FIG. 1 illustrates this portion.
  • the electric motor 12 is excited and refrigerant is introduced into the housing 10 through the intake pipe 13.
  • the main shaft 17 rotates, and as a result, the orbiting scroll 30 revolves in relation to the fixed scroll 20.
  • the refrigerant compressed in the compression chamber PR passes through the discharge port 23 of the fixed end plate 21 and the downstream discharge port portion 26 of the discharge cover 27 in that order, is discharged into the high pressure chamber 10B, and is then discharged outside through the discharge pipe 14. In this manner, the refrigerant is drawn in, compressed, and discharged in succession.
  • An object of the present embodiment is to reduce noise by reducing the number of resonance modes generated.
  • a plurality of resonance modes from a primary mode to a high-order mode are generated (six resonance modes (i) to (vi) are illustrated in FIG. 3A ).
  • these resonance modes are generated by the inflow of refrigerant from the upstream discharge port portion 24, noise is generated in the discharge cavity 25.
  • the resonance mode is not generated.
  • FIG. 3A the positions of the nodes of the plurality of resonance modes generated in the discharge cavity 25 are depicted with the broken lines DL.
  • the upper portion of FIG. 3A illustrates plan views of the discharge cavity 25 whereas the lower portion illustrates a vertical edge face.
  • the two circles 28 and 29 in each discharge cavity 25 each illustrate positions where the refrigerant is discharged (hereinafter referred to as a vibration input position).
  • the solid line circle 28 illustrates a case in which the vibration input position coincides with the central axis C2 of the discharge cavity 25, and the broken line circle 29 illustrates a case in which the vibration input position is shifted from the central axis C2 and the node.
  • a node is formed on the inner wall of the discharge cavity 25.
  • the node is formed directly on a diametrical line passing through the central axis C2 of the discharge cavity 25.
  • Nodes formed in other resonance modes are illustrated in (iii) to (vi) of FIG. 3A , and are formed in various positions on the discharge cavity 25, but with the exception of (i), which depicts the primary mode, and (iv), which depicts a high-order mode, the node of each of the resonance modes passes through the central axis C2 of the discharge cavity 25.
  • nodes of a plurality of different resonance modes include the central axis C2 of the discharge cavity 25 as a common point.
  • the refrigerant discharged from the upstream discharge port portion 24 passes through the discharge cavity 25 as a spherical wave. Consequently, by having the center P1 of the downstream side open end 24A coincide with the central axis C2, the refrigerant passes through the central axis C2 and is discharged to the downstream discharge port portion 26.
  • the scroll compressor 1 has realized this effect of reducing noise.
  • the upstream discharge port portion 24 is formed at an incline, and the center P1 coincides with the central axis C2.
  • the refrigerant discharged from the upstream discharge port portion 24 passes through nodes of a plurality of resonance modes formed on the central axis C2. These plurality of resonance modes are not generated, and thus, noise within the discharge cavity 25 is reduced.
  • the most preferable example of the center P1 of the upstream discharge port portion 24 coinciding with the central axis C2 is applied to the scroll compressor 1 above, but the only requirement is that the refrigerant passes through nodes of resonance modes.
  • the center P1 is shifted from the central axis C2, as long as the central axis C2 is present in the area occupied by the open end 24B, the effects of the present invention can still be attained.
  • the position of the discharge cavity 25 is shifted, thereby causing the central axis C2 of the discharge cavity 25 to coincide with the central axis C1 (center P1) of the upstream discharge port portion 24. In this manner, noise occurring in the discharge cavity 25 is reduced.
  • the upstream discharge port portion 24 is formed such that the central axis C thereof traces the vertical direction.
  • the shift in position here refers to the shifting of the discharge cavity 25 of the present embodiment in relation to the discharge cavity 25 of the first embodiment.
  • the discharge cavity 25 is eccentric in relation to the central axis C of the fixed scroll 20, and by combining this eccentricity with the position shift of the discharge cover 27 and the housing top 102, the central axes C3 and C4 coincide with the central axis C1.
  • the second embodiment exhibits an improvement in terms of ease of processing.
  • the positions of the discharge cover 27 and the housing top 102 are shifted in conjunction with the shift in position of the discharge cavity 25, and thus, the central axis C3 of the downstream discharge port portion 26 continues to coincide with the central axis C4 of the high pressure chamber 10B. Consequently, by mitigating an increase in the number of resonance modes generated in the high pressure chamber 10B, it is possible to prevent an increase in noise in the high pressure chamber 10B.
  • the present invention can also be applied to a scroll compressor that is not provided with the discharge cover 27.
  • the fixed end plate would only include a discharge port of the same diameter (because no portions corresponding to the discharge cavity 25 would be present), and the discharge port would be directly connected to the high pressure chamber 10B.
  • the discharge port corresponds to the first refrigerant path of the present invention
  • the high pressure chamber corresponds to the second refrigerant path of the present invention.
  • the upstream discharge port portion 24 or the downstream discharge port portion 26 is formed at an incline, it may be formed in a curve or inclined in a stepwise fashion such as in a crank shape or a step shape, instead of forming in a straight line.
  • the horizontal cross-sectional shape of the discharge cavity 25 is not limited to being a circle, and another cross-sectional shape may be adopted.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP14831427.1A 2013-08-02 2014-06-16 Compresseur Active EP3015710B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013161337A JP6147605B2 (ja) 2013-08-02 2013-08-02 圧縮機
PCT/JP2014/003201 WO2015015695A1 (fr) 2013-08-02 2014-06-16 Compresseur

Publications (3)

Publication Number Publication Date
EP3015710A1 true EP3015710A1 (fr) 2016-05-04
EP3015710A4 EP3015710A4 (fr) 2016-07-20
EP3015710B1 EP3015710B1 (fr) 2020-03-18

Family

ID=52431261

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14831427.1A Active EP3015710B1 (fr) 2013-08-02 2014-06-16 Compresseur

Country Status (4)

Country Link
EP (1) EP3015710B1 (fr)
JP (1) JP6147605B2 (fr)
CN (1) CN105247214B (fr)
WO (1) WO2015015695A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11493040B2 (en) * 2018-06-29 2022-11-08 Emerson Climate Technologies (Suzhou) Co., Ltd. Damping apparatus for exhaust valve in compressor, exhaust valve assembly, and compressor
EP4336043A3 (fr) * 2022-08-16 2024-04-03 BITZER Kühlmaschinenbau GmbH Machine à spirales et système frigorifique
US12078174B2 (en) 2019-04-26 2024-09-03 Copeland Climate Technologies (Suzhou) Co. Ltd. Scroll compressor

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7084109B2 (ja) * 2017-03-17 2022-06-14 三菱重工サーマルシステムズ株式会社 圧縮機

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JP2740297B2 (ja) * 1989-10-03 1998-04-15 三洋電機株式会社 スクロール圧縮機の吐出装置
CA2046548C (fr) * 1990-10-01 2002-01-15 Gary J. Anderson Machine a volute dotee d'une garniture d'etancheite mobile
JPH0482391U (fr) 1990-11-29 1992-07-17
JP3030135B2 (ja) * 1991-09-19 2000-04-10 三洋電機株式会社 スクロール圧縮機
JP2554488Y2 (ja) * 1992-05-15 1997-11-17 三菱電機株式会社 スクロール圧縮機
JPH08319963A (ja) * 1995-03-22 1996-12-03 Mitsubishi Electric Corp スクロール圧縮機
JPH1065560A (ja) * 1996-08-21 1998-03-06 Mitsubishi Electric Corp Ｆｍ多重受信機
JP2000110744A (ja) * 1998-09-30 2000-04-18 Fujitsu General Ltd スクロール圧縮機
JP2001132666A (ja) * 1999-11-09 2001-05-18 Hitachi Ltd 容積形圧縮機
US8118563B2 (en) * 2007-06-22 2012-02-21 Emerson Climate Technologies, Inc. Tandem compressor system and method
CN102076962B (zh) * 2008-05-30 2013-09-18 艾默生环境优化技术有限公司 一种具有容量调节系统的压缩机
JP2010065560A (ja) * 2008-09-09 2010-03-25 Daikin Ind Ltd スクロール圧縮機
JP5178668B2 (ja) * 2009-09-11 2013-04-10 日立アプライアンス株式会社 スクロール圧縮機
US8517703B2 (en) * 2010-02-23 2013-08-27 Emerson Climate Technologies, Inc. Compressor including valve assembly
JP5459078B2 (ja) * 2010-06-02 2014-04-02 株式会社豊田自動織機 スクロール型圧縮機
JP5758112B2 (ja) * 2010-12-07 2015-08-05 三菱重工業株式会社 スクロール圧縮機
FR2969226B1 (fr) * 2010-12-16 2013-01-11 Danfoss Commercial Compressors Compresseur frigorifique a spirales
US9267501B2 (en) * 2011-09-22 2016-02-23 Emerson Climate Technologies, Inc. Compressor including biasing passage located relative to bypass porting

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11493040B2 (en) * 2018-06-29 2022-11-08 Emerson Climate Technologies (Suzhou) Co., Ltd. Damping apparatus for exhaust valve in compressor, exhaust valve assembly, and compressor
US12078174B2 (en) 2019-04-26 2024-09-03 Copeland Climate Technologies (Suzhou) Co. Ltd. Scroll compressor
EP4336043A3 (fr) * 2022-08-16 2024-04-03 BITZER Kühlmaschinenbau GmbH Machine à spirales et système frigorifique

Also Published As

Publication number Publication date
JP6147605B2 (ja) 2017-06-14
JP2015031206A (ja) 2015-02-16
EP3015710B1 (fr) 2020-03-18
CN105247214A (zh) 2016-01-13
EP3015710A4 (fr) 2016-07-20
WO2015015695A1 (fr) 2015-02-05
CN105247214B (zh) 2017-10-03

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