WO2020004167A1 - Compresseur à spirale - Google Patents

Compresseur à spirale Download PDF

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Publication number
WO2020004167A1
WO2020004167A1 PCT/JP2019/024242 JP2019024242W WO2020004167A1 WO 2020004167 A1 WO2020004167 A1 WO 2020004167A1 JP 2019024242 W JP2019024242 W JP 2019024242W WO 2020004167 A1 WO2020004167 A1 WO 2020004167A1
Authority
WO
WIPO (PCT)
Prior art keywords
peripheral surface
shaft member
bearing
eccentric shaft
annular portion
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.)
Ceased
Application number
PCT/JP2019/024242
Other languages
English (en)
Japanese (ja)
Inventor
拓 岩下
田口　正則
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.)
Sanden Automotive Components Corp
Original Assignee
Sanden Automotive Components Corp
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 Sanden Automotive Components Corp filed Critical Sanden Automotive Components Corp
Priority to CN201980040478.8A priority Critical patent/CN112334658B/zh
Priority to DE112019003289.5T priority patent/DE112019003289B4/de
Publication of WO2020004167A1 publication Critical patent/WO2020004167A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0064—Magnetic couplings
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • 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
    • F04C2240/50—Bearings
    • F04C2240/56—Bearing bushings or details thereof
    • 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
    • F04C2240/80—Other components
    • F04C2240/807—Balance weight, counterweight

Definitions

  • the present invention relates to a scroll compressor.
  • Patent Document 1 in a scroll compressor, a lubricating hole is formed in an eccentric bush in order to supply lubricating oil between an eccentric bush and a needle bearing.
  • An object of the present invention is to suppress the accumulation of lubricating oil and improve the cooling effect.
  • a scroll compressor according to one embodiment of the present invention, An eccentric shaft member fixed eccentrically with respect to the rotating shaft, an introduction flow path formed in the axial direction from the proximal end to the distal end is formed, and lubricating oil is introduced from the proximal end to the distal end by the introduction flow path, A bearing supported by the boss of the orbiting scroll, the inner peripheral surface of which is slidably fitted to the outer peripheral surface on the distal end side of the eccentric shaft member; An eccentric shaft member is provided on the eccentric shaft member to balance the weight, an annular portion is formed on the center side in the radial direction, the annular portion is disposed so as to cover the end face of the bearing, and the inner peripheral surface of the annular portion is the eccentric shaft.
  • the discharge flow path for discharging the lubricating oil is formed in the annular portion of the counterweight, the accumulation of the lubricating oil can be suppressed, and the cooling effect can be improved.
  • FIG. 1 is a cross-sectional view along the front-back direction of the compressor.
  • the compressor 11 is, for example, a belt-driven scroll compressor used in a refrigerant circuit of a car air conditioner, and sucks, compresses, and discharges the refrigerant.
  • the compressor 11 is integrated with a front housing 12, a center housing 13, and a rear housing 14 so as to maintain airtightness, which are arranged in order from the front side in the front-rear direction.
  • a suction port (not shown) for sucking refrigerant is formed in an upper part of the front housing 12, and a discharge port 16 for discharging compressed refrigerant is formed in an upper part of the rear housing 14.
  • a rotation shaft 21 is rotatably supported on the front side of the front housing 12.
  • the front end side of the rotating shaft 21 is connected to a pulley 23 via an electromagnetic clutch 22.
  • the power of the engine is transmitted to the pulley 23 via a drive belt.
  • a fixed scroll 24 is formed on the rear side of the center housing 13, and a movable scroll 25 is accommodated from the rear side of the front housing 12 to the front side of the center housing 13.
  • the fixed scroll 24 is formed so as to close the rear side of the center housing 13, and includes a fixed end plate 26 formed in a disc shape, and a fixed spiral 27 formed on the front surface of the fixed end plate 26.
  • the movable scroll 25 is arranged on the front side of the fixed end plate 26 and has a movable end plate 28 formed in a disk shape, a movable spiral 29 formed on the rear surface of the movable end plate 28 and meshing with the fixed spiral 27, Is provided.
  • a pressure chamber 31 for compressing the refrigerant is formed by a front surface of the fixed end plate 26, a fixed spiral 27, a rear surface of the movable end plate 28, and a section surrounded by the movable spiral 29. When viewed from the front-back direction, the pressure chamber 31 is a crescent-shaped closed space.
  • a boss 32 is formed on the front surface of the movable end plate 28, and an eccentric bush 33 (eccentric shaft member) is fixed to the rear end of the rotating shaft 21.
  • the eccentric bush 33 is rotatably fitted into the boss 32. ing.
  • the rotational motion of the rotary shaft 21 is converted into a turning motion of the movable scroll 25 via the eccentric bush 33.
  • the movable scroll 25 is prevented from rotating, for example, via a pin & hole, and is allowed to revolve with respect to the fixed scroll 24.
  • a discharge hole (not shown) penetrating in the front-rear direction is formed at the center of the fixed end plate 26, and the discharge hole communicates with a discharge chamber 35 formed on the rear side of the fixed end plate 26.
  • a discharge valve 36 that can open and close the rear end side of the discharge hole is provided.
  • FIG. 2 is an enlarged sectional view of a portion where the eccentric bush is fitted to the boss.
  • a crank pin 41 eccentric to the rotating shaft 21 is formed at the rear end of the rotating shaft 21.
  • the eccentric bush 33 is formed with a through hole 42 penetrating in the axial direction, and the crank pin 41 is inserted into the through hole 42 and fixed so as not to rotate relatively.
  • a sliding bearing 43 is fitted into the boss 32, and the inner peripheral surface of the sliding bearing 43 is slidably fitted on the outer peripheral surface of the eccentric bush 33 on the distal end side.
  • the eccentric bush 33 is formed with a counterweight 44 for balancing weight.
  • the eccentric bush 33 is formed with an introduction flow path 45 that penetrates in the axial direction from the front end to the rear end.
  • the introduction channel 45 is formed at a position different from the through hole 42 and at a position near the center of the rotating shaft 21.
  • the front side of the movable end plate 28 is set at a medium pressure, and oil separated from the refrigerant is supplied as lubricating oil.
  • This lubricating oil is introduced from the base end side of the eccentric bush 33 to the front end side by the introduction flow path 45.
  • a gap 46 is provided between the bottom surface of the boss 32 and the tip of the eccentric bush 33.
  • the lubricating oil introduced from the introduction channel 45 is supplied to the bearing 43 through the gap 46, so that a lubricating oil film is formed between the bearing 43 and the eccentric bush 33.
  • Block arrows indicate the flow of lubricating oil.
  • the counterweight 44 includes an annular portion 51 and a weight portion 52.
  • the inner peripheral surface of the annular portion 51 which is the center side in the radial direction is fixed to the outer peripheral surface on the base end side of the eccentric bush 33.
  • the annular portion 51 is arranged so as to cover the end face of the bearing 43, and is close to the end face of the bearing 43, but maintains a non-contact state.
  • the weight portion 52 is formed radially outside the annular portion 51.
  • a discharge channel 53 is formed in the annular portion 51.
  • the discharge channel 53 is formed on the end surface of the annular portion 51 that faces the boss 32 in the axial direction, and is a groove that extends in the radial direction.
  • FIG. 3 is a diagram illustrating an eccentric bush and a counterweight.
  • (A) in the figure is a plan view, and (b) in the figure is a perspective view.
  • the eccentric bush 33 has a load point 54 for transmitting power to the movable scroll 25 at a part of the outer peripheral surface in the circumferential direction.
  • the load point 54 corresponds to a portion of the outer peripheral surface of the eccentric bush 33 where the through hole 42 is closest, a portion surrounded by a broken line in (a) of the drawing, and a hatched portion in (b) of the drawing. It is.
  • the discharge channel 53 is formed at an angular position avoiding the load point 54 in the circumferential direction of the annular portion 51.
  • discharge flow path 53 is formed at an angular position outside the introduction flow path 45 with respect to the rotation center 55 of the rotating shaft 21 in the circumferential direction of the annular portion 51 and outside the rotation radius of the introduction flow path 45. Set to the outside angle position.
  • a discharge channel 53 for discharging lubricating oil is formed in the annular portion 51 of the counterweight 44. Specifically, a groove extending in the radial direction is formed on the end face of the annular portion 51 that faces the boss 32 in the axial direction. Thereby, the stagnation of the lubricating oil can be suppressed, and the cooling action can be improved.
  • the load point 54 of the eccentric bush 33 pushes the inner peripheral surface of the bearing 43. And are in close contact. Therefore, at the load point 54, the lubricating oil is not easily discharged.
  • the discharge passage 53 is formed at an angular position avoiding the load point 54 in the circumferential direction of the annular portion 51. This makes it easier to discharge the lubricating oil.
  • FIG. 4 is a diagram showing the inside and outside of the turning radius.
  • points A and B that are fixed to the rotating shaft 21 and turn with the rotation of the rotating shaft 21 are schematically illustrated.
  • Point A is inside the turning radius and point B is outside the turning radius.
  • the speed of the point B outside the turning radius is higher than that of the point A inside the turning radius.
  • a pressure difference occurs between the inside and outside of the turning radius. Therefore, by forming the discharge flow path 53 at an angular position that is the most radially outward with respect to the rotation center 55 of the rotary shaft 21 in the circumferential direction of the annular portion 51, the pressure difference due to the difference in the turning radius is formed. Is the largest. This pressure difference makes it easier to positively discharge the lubricating oil.
  • the diameter, the number, etc. of the introduction flow channel 45 may be adjusted. Further, in order to adjust the discharge amount of the lubricating oil, the circumferential width, the axial depth, the quantity, and the like of the discharge passage 53 may be adjusted.
  • FIG. 5 is a cross-sectional view of a second embodiment in which a portion where the eccentric bush is fitted to the boss is enlarged.
  • the configuration is the same as that of the above-described first embodiment, and the common components are denoted by the same reference numerals, and detailed description is omitted.
  • a groove 61 extending from the distal end to the proximal end and communicating with the discharge channel 53 is formed.
  • FIG. 6 is a diagram illustrating an eccentric bush and a counterweight according to the second embodiment. (A) in the figure is a plan view, and (b) in the figure is a perspective view.
  • the groove 61 is formed at the same angular position as the discharge channel 53 in the circumferential direction of the eccentric bush 33.
  • a groove 61 communicating with the discharge channel 53 is formed on the outer peripheral surface of the eccentric bush 33.
  • the lubricating oil supplied to the bearing 43 is mainly discharged from the discharge passage 53 through the groove 61. Since the groove 61 is formed over the entire eccentric bush 33 in the axial direction, the lubricating oil is also discharged from the base end side of the groove 61. Therefore, the lubricating oil can be more positively discharged.
  • the same functions and effects as those of the above-described first embodiment can be obtained, and the detailed description is omitted.
  • the groove 61 is formed on the outer peripheral surface of the eccentric bush 33 so as to extend from the rear end to the front base.
  • the present invention is not limited to this. Since the groove 61 only needs to be able to communicate with the discharge channel 53, the groove 61 does not have to be formed over the entire axial direction, but may be formed only in the section from the rear end to the front discharge channel 53.
  • FIG. 7 is a cross-sectional view of the third embodiment in which a portion where the eccentric bush fits the boss is enlarged.
  • the configuration is the same as that of the above-described first embodiment, and the common portions are denoted by the same reference numerals, and detailed description is omitted.
  • a discharge channel 71 is formed in the annular portion 51.
  • the discharge channel 71 is a groove formed on the inner peripheral surface of the annular portion 51 and extending in the axial direction.
  • FIG. 8 is a diagram illustrating an eccentric bush and a counterweight according to the third embodiment.
  • (A) in the figure is a plan view
  • (b) in the figure is a perspective view.
  • the discharge flow passage 71 is formed at an angular position avoiding the load point 54 in the circumferential direction of the annular portion 51. Further, the discharge passage 71 is formed at an angular position outside the introduction passage 45 with respect to the rotation center 55 of the rotary shaft 21 in the circumferential direction of the annular portion 51 and outside the introduction passage 45, and the turning radius is as small as possible. Set to the outside angle position.
  • a groove extending in the axial direction is formed on the inner peripheral surface of the annular portion 51 as the discharge channel 71.
  • the lubricating oil supplied to the bearing 43 can be discharged from the discharge flow path 71. Therefore, the retention of the lubricating oil can be suppressed, and the cooling effect can be improved.
  • the circumferential width, the radial depth, the quantity, and the like of the discharge flow passage 71 may be adjusted.
  • the same functions and effects as those of the above-described first embodiment can be obtained, and the detailed description is omitted.
  • FIG. 9 is a cross-sectional view of a fourth embodiment in which a portion where the eccentric bush fits the boss is enlarged.
  • the configuration is the same as that of the above-described first embodiment, and the common components are denoted by the same reference numerals, and detailed description is omitted.
  • a groove 81 is formed extending in the axial direction from the distal end to the proximal end.
  • a groove 81 communicating with the discharge channel 53 is formed on the inner peripheral surface of the bearing 43.
  • the lubricating oil supplied to the bearing 43 is discharged from the discharge passage 53 through the groove 81. Therefore, the lubricating oil can be more positively discharged.
  • the same functions and effects as those of the above-described first embodiment can be obtained, and the detailed description is omitted.
  • FIG. 10 is a view of a bearing showing a modification of the fourth embodiment.
  • (A) in the figure is a plan view
  • (b) in the figure is a perspective view.
  • Three grooves 81 are formed in the inner peripheral surface of the bearing 43 and extend spirally from the distal end to the proximal end. Each groove 81 is formed at equal intervals along the circumferential direction.
  • the angular position of the bearing 43 is determined so that one end of any one of the grooves 81 communicates with the discharge channel 53.
  • the bearing 43 in which the spirally extending groove 81 is formed can be used as it is without any processing because it is distributed as an existing bearing, leading to a reduction in man-hours.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Cette invention concerne un compresseur à spirale, comprenant : un élément d'arbre excentrique, fixé de manière excentrique par rapport à un arbre rotatif, dans lequel est formé un canal d'introduction qui s'étend d'une extrémité de base à une extrémité de pointe dans la direction axiale et à travers lequel est introduite une huile de lubrification depuis le côté d'extrémité de base vers le côté d'extrémité de pointe par l'intermédiaire du canal d'introduction; un palier qui est supporté par un bossage d'une spirale mobile et dont une surface périphérique interne s'ajuste de manière coulissante avec une surface périphérique externe sur le côté d'extrémité de pointe de l'élément d'arbre excentrique; et un contrepoids qui est disposé sur l'élément d'arbre excentrique afin d'obtenir un équilibre de poids et qui a une section de bague formée sur le côté radialement central de celui-ci, la section de bague étant disposée de manière à recouvrir une surface d'extrémité du palier, et une surface périphérique interne de la section de bague étant fixée à une surface périphérique externe sur le côté d'extrémité de base de l'élément d'arbre excentrique. Un canal d'évacuation pour évacuer l'huile de lubrification fournie au palier depuis le côté d'extrémité de pointe de l'élément d'arbre excentrique est formé dans la section de bague.
PCT/JP2019/024242 2018-06-29 2019-06-19 Compresseur à spirale Ceased WO2020004167A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201980040478.8A CN112334658B (zh) 2018-06-29 2019-06-19 涡旋式压缩机
DE112019003289.5T DE112019003289B4 (de) 2018-06-29 2019-06-19 Scrollverdichter

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2018-124783 2018-06-29
JP2018124783A JP7056820B2 (ja) 2018-06-29 2018-06-29 スクロール圧縮機

Publications (1)

Publication Number Publication Date
WO2020004167A1 true WO2020004167A1 (fr) 2020-01-02

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ID=68986629

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2019/024242 Ceased WO2020004167A1 (fr) 2018-06-29 2019-06-19 Compresseur à spirale

Country Status (4)

Country Link
JP (1) JP7056820B2 (fr)
CN (1) CN112334658B (fr)
DE (1) DE112019003289B4 (fr)
WO (1) WO2020004167A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022113558A1 (fr) * 2020-11-24 2022-06-02 サンデン・オートモーティブコンポーネント株式会社 Machine à fluide à spirales

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112539173B (zh) * 2020-12-03 2022-12-16 珠海格力节能环保制冷技术研究中心有限公司 动涡旋盘组件、涡旋压缩机及空调系统
DE102021210653A1 (de) 2021-09-23 2023-03-23 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Scrollmaschine
JP2024076712A (ja) 2022-11-25 2024-06-06 三菱重工サーマルシステムズ株式会社 バランスウェイト及びそれを備えた圧縮機

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002039083A (ja) * 2000-07-27 2002-02-06 Mitsubishi Heavy Ind Ltd スクロール型流体機械
JP2014169792A (ja) * 2009-01-12 2014-09-18 Dow Global Technologies Llc 改良されたジャーナル軸受構造
WO2017169596A1 (fr) * 2016-03-31 2017-10-05 三菱電機株式会社 Compresseur à spirale et dispositif à cycle de réfrigération

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Publication number Priority date Publication date Assignee Title
JPH11182461A (ja) * 1997-12-15 1999-07-06 Sanden Corp スクロール型圧縮機
KR100558814B1 (ko) 2003-12-16 2006-03-10 엘지전자 주식회사 오일 배출 기능을 갖는 스크롤 압축기의 편심부시
CN1766341A (zh) * 2004-10-27 2006-05-03 乐金电子(天津)电器有限公司 具有油排出功能的涡旋压缩机的偏心衬套
CN103375402B (zh) 2012-04-11 2017-02-15 艾默生环境优化技术(苏州)有限公司 涡旋压缩机
JP6685690B2 (ja) 2015-10-20 2020-04-22 三菱重工サーマルシステムズ株式会社 スクロール流体機械

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002039083A (ja) * 2000-07-27 2002-02-06 Mitsubishi Heavy Ind Ltd スクロール型流体機械
JP2014169792A (ja) * 2009-01-12 2014-09-18 Dow Global Technologies Llc 改良されたジャーナル軸受構造
WO2017169596A1 (fr) * 2016-03-31 2017-10-05 三菱電機株式会社 Compresseur à spirale et dispositif à cycle de réfrigération

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022113558A1 (fr) * 2020-11-24 2022-06-02 サンデン・オートモーティブコンポーネント株式会社 Machine à fluide à spirales
US20240011487A1 (en) * 2020-11-24 2024-01-11 Sanden Corporation Scroll fluid machine

Also Published As

Publication number Publication date
JP7056820B2 (ja) 2022-04-19
JP2020002904A (ja) 2020-01-09
DE112019003289B4 (de) 2024-06-27
CN112334658A (zh) 2021-02-05
DE112019003289T5 (de) 2021-03-18
CN112334658B (zh) 2023-02-28

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