EP2589808A1 - Scroll compressor - Google Patents

Scroll compressor Download PDF

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Publication number
EP2589808A1
EP2589808A1 EP11803484.2A EP11803484A EP2589808A1 EP 2589808 A1 EP2589808 A1 EP 2589808A1 EP 11803484 A EP11803484 A EP 11803484A EP 2589808 A1 EP2589808 A1 EP 2589808A1
Authority
EP
European Patent Office
Prior art keywords
bearing member
scroll
movable scroll
main bearing
bottom plate
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP11803484.2A
Other languages
German (de)
English (en)
French (fr)
Inventor
Yuji Takei
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 Corp
Original Assignee
Sanden 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 Corp filed Critical Sanden Corp
Publication of EP2589808A1 publication Critical patent/EP2589808A1/en
Withdrawn legal-status Critical Current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
    • 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
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • 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
    • 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 scroll compressor, and specifically relates to improvements of a back pressure mechanism section provided at the back side of a movable scroll constituting the scroll compression mechanism.
  • a scroll compressor having a scroll compression mechanism made by a fixed scroll and a movable scroll to swing around the fixed scroll.
  • a compressive reaction force of fluid being compressed might generate a thrust load on the movable scroll, so as to cause the abrasion between the movable scroll and a housing supporting the movable scroll.
  • known is an effective measure where the pressurized fluid is introduced from the inside of the compression mechanism to the back side of the movable scroll so as to react a back pressure to the movable scroll in a direction opposing the thrust load, so that the back pressure reduces the thrust load which might cause the abrasion, etc.
  • Patent document 1 discloses a scroll compressor, comprising a back pressure chamber formed as a space between a back face of a bottom plate section of a movable scroll and a front face of main bearing member surface facing it, at least one annular groove formed on either the back face or the front face, an annular seal means which is movably attached to the inside of the annular groove and is brought into sliding contact with the other face, an annular shaft seal means which is movably attached to the inside of a gap between a crankshaft to drive the movable scroll and the main bearing member, and a pressure inlet hole to supply pressurized fluid to the back pressure chamber which is formed by sealing the gap with the seal means and the shaft seal means at the back face side of the bottom plate of the movable scroll.
  • annular groove and the annular seal means to form the back pressure chamber are located at the side of inside diameter of the rotation preventing mechanism of the movable scroll in a structure disclosed in Patent document 1, such a seal means, etc., which define the radial directional size of the back pressure chamber, are positioned as corresponding to comparatively small radius, so that the area to bear the back pressure in the back pressure chamber becomes comparatively small.
  • a seal means, etc. which define the radial directional size of the back pressure chamber
  • an object of the present invention is to provide a scroll compressor, in which a desirable back pressure mechanism can be realized without increasing the shell diameter of the compressor and the pressure can be kept low in the back pressure chamber as making the pressure-bearing area in the back pressure chamber greater, so as to meet a demand to downsize compressors and to improve the volume efficiency of the compressor by reducing the leakage at the sealed region in the back pressure chamber, while the annular seal means is prevented from aging deterioration, etc., in durability and sealing performance by reducing pressure in the back pressure chamber, the rotation preventing mechanism of the movable scroll is well lubricated and the reliability is improved.
  • a scroll compressor which has a scroll type compression mechanism consisting of a fixed scroll and a movable scroll to swing relatively to the fixed scroll and which comprises a shaft having an eccentric crank part on an end and driving the movable scroll by the crank part, a main bearing member to rotatably support the shaft through a main bearing, a rotation preventing mechanism which is provided between a back face of a bottom plate part of the movable scroll and a front face of the main bearing member facing the back face and which prevents the movable scroll from rotating, a back pressure chamber formed as a space between the back face of the bottom plate part of the movable scroll and the front face of the main bearing member facing the back face, at least one annular groove formed on a side either of the back face of the bottom plate part of the movable scroll or the front face of the main bearing member, a seal means which is movably attached in the annular groove and which is brought into sliding contact with another side, a shaft seal
  • a thrust bearing member is interposed separately from the annular seal means which is attached to the annular groove to form the back pressure chamber, so that the annular seal means, which has had both functions of the seal function and the thrust force bearing function in a conventional structure, chiefly has charge of only the seal function and that the thrust bearing member has charge of the thrust force bearing function.
  • the annular seal means can specialize in the seal function by omitting the function for bearing a thrust force. Consequently, the annular seal means can be designed flexibly, so as to increase the seal performance and the durability.
  • Such a high seal performance and a high durability makes it possible that the back pressure chamber has charge of desirable back pressure function, such as thrust load reduction function and pushing function toward the fixed scroll side, with respect to the movable scroll. Therefore, it is possible that the abrasion derived from the thrust load is suppressed so as to improve the volume efficiency and the coefficient of performance of the compressor.
  • the thrust bearing member is interposed such that the bottom plate part of the movable scroll contacts the thrust bearing member when the compressor starts up and the bottom plate part doesn't contact thrust bearing members in a steady operation. Because inner pressure of the back pressure chamber may not be sufficient at the start up, comparatively great thrust load might be applied to the front face of the main bearing member from the bottom plate part of the movable scroll. If the bottom plate part of the movable scroll contacts the thrust bearing member, the thrust bearing member can surely bear the thrust load to prevent the annular seal means from being subjected to the thrust load undesirably. Therefore, the abrasion derived from the thrust load can be suppressed while the annular seal means have further excellent seal performance and further excellent durability.
  • the pressurized fluid is supplied into the back pressure chamber sufficiently in a stable operation so that the inner pressure of the back pressure chamber is kept high enough to bear the thrust load, the non-contact between the bottom plate part of the movable scroll and the thrust bearing member can improve the durability and the lifetime of the thrust bearing member.
  • the thrust bearing member is made of a plate member which annularly extends on the front face of the main bearing member in a circumferential direction, or that the thrust bearing member is made of a plurality of circular members which are formed on the front face of the main bearing member and which are freely fitted (namely, which are movably attached) in a plurality of circular grooves placed intermittently in the circumferential direction.
  • the thrust bearing member is made of material, such as metal and resin, having high abrasion resistance to have charge of the thrust load.
  • the annular groove and the seal means are placed at a position including the rotation preventing mechanism in a radial direction so that the annular seal means is provided as having larger outer shape than the position disclosed in Patent document 1. Then the radial dimension of the back pressure chamber is increased, so as to enlarge the pressure-bearing area in the back pressure chamber. Namely, the pressure-bearing area can be extended in the back pressure chamber without extending the shell diameter of the compressor. Therefore, demand to downsize the compressor can be satisfied and the lowered pressure in the back pressure chamber can reduce the leakage at the sealed region in the back pressure chamber, so as to improve the volume efficiency of the compressor.
  • the lowered pressure in the back pressure chamber can reduce the loading condition of the annular seal means, so that the annular seal means are prevented from deteriorating in durability and the seal performance across the ages, etc, so as to improve the seal performance and the durability further.
  • the rotation preventing mechanism section of the movable scroll can be incorporated substantively in the back pressure chamber, the pressurized fluid containing lubricant oil introduced in the back pressure chamber through the pressure inlet hole from the compression mechanism can be utilized to lubricate the rotation preventing mechanism section, so as to improve the durability and the reliability.
  • the present invention makes it possible that the back pressure chamber which allows low pressure and has desirable pressure-bearing area can be configured without extending the shell diameter of the compressor, as achieving the excellent seal performance, durability and reliability of the back pressure mechanism section. Therefore, the present invention is suitable to a compressor in an air-conditioning system for vehicles, which strongly demands downsizing and durability improvement.
  • the sealing performance, durability and reliability, etc. can be excellent in the back pressure chamber, so as to achieve higher volume efficiency and higher coefficient of performance compared to a compressor which doesn't have a back pressure mechanism.
  • a compact and highly efficient scroll compressor can be provided without increasing the shell diameter of the compressor, because the back pressure chamber, of which sealing performance and durability are excellent and of which pressure-bearing area is kept large so as to require only low pressure, can be designed while the shell diameter of the compressor is the same as a compressor which doesn't have a back pressure mechanism.
  • FIG. 1 shows scroll compressor 100 according to the first embodiment of the present invention
  • Fig. 2 shows scroll compressor 200 according to the second embodiment of the present invention. Both of them are configured to be an electric compressor having built-in motor.
  • Scroll compressors 100 and 200 are used as a compressor for compressing refrigerant for an air conditioning system for vehicles, etc.
  • the first embodiment and the second embodiment are different only in thrust bearing members. Because the other parts are substantively the same, thrust bearing members are explained by different symbols while the same symbols are used to explain the same component parts as referring to Figs. 1 and 2 together.
  • scroll compressors 100 and 200 have scroll compression mechanism 3 consisting of fixed scroll 1 and movable scroll 2 to swing around fixed scroll 1. While moving toward the center of fluid pocket 4 formed in scroll compression mechanism 3, fluid, such as refrigerant, taken into fluid pocket 4 is supposed to be compressed. The compressed fluid is discharged in discharge chamber 7 formed in rear plate 6 from discharge hole 5 provided at the center of fixed scroll 1, and is delivered to the external circuit (not shown) through discharge port section 9 after lubricating oil contained is separated therefrom in separator pipe 8.
  • scroll compression mechanism 3 consisting of fixed scroll 1 and movable scroll 2 to swing around fixed scroll 1. While moving toward the center of fluid pocket 4 formed in scroll compression mechanism 3, fluid, such as refrigerant, taken into fluid pocket 4 is supposed to be compressed. The compressed fluid is discharged in discharge chamber 7 formed in rear plate 6 from discharge hole 5 provided at the center of fixed scroll 1, and is delivered to the external circuit (not shown) through discharge port section 9 after lubricating oil contained is separated therefrom in separator pipe 8.
  • fixed scroll 1 is fixed inside of an end of stator housing 10, and rear plate 6 is fixed to an end face of stator housing 10 with bolts, etc.
  • Motor 12 which drives to rotate shaft 11 for driving movable scroll 2 is built inside the other end of stator housing 10.
  • Motor 12 comprises stator 13 fixed inside stator housing 10 and rotor 14 to rotate around stator 13, and shaft rotates together with rotor 14.
  • Shaft 11 is rotatably supported by front bearing 17 attached to inverter case 16 housing inverter section 15 and main bearing 19 attached to main bearing member 18 fixed inside stator housing 10.
  • Crank section (crank pin) 20 is formed at a position eccentric to the center of shaft 11 at an end of shaft 11.
  • Rotation preventing mechanism 24 of movable scroll 2 comprises rotation preventing ring 26 attached in hole 25 formed on the back face of movable scroll 2 and rotation preventing pin 27 provided as extruding from main bearing member 18 in rotation preventing ring 26, while a plurality of rotation preventing mechanisms 24 consisting of ring 26 and pin 27 are arranged in a circumferential direction.
  • Back pressure chamber 28 is formed as a space between the back face of bottom plate part 2a of movable scroll 2 and the front face of main bearing member 18 facing the back face.
  • Back pressure chamber 28 is formed into a sealed space sealed by a seal section comprising at least one annular groove 29 formed on the back face of bottom plate part 2a of movable scroll 2 and annular seal 30 as an annular seal means, which is attached in groove 29 and is brought into sliding contact with the front face of main bearing member 18, and another seal section having shaft seal 31 attached between the outer peripheral surface of shaft 11 and the inner peripheral surface of main bearing member 18 at the side of main bearing 19.
  • pressurized fluid is supplied from the inside of compression mechanism 3 through pressure inlet hole 32 perforated on bottom plate part 2a of movable scroll 2.
  • the pressurized fluid introduced into back pressure chamber 28 makes inner pressure of back pressure chamber 28 act on movable scroll 2, so that the thrust load, which is a force to push movable scroll 2 toward main bearing member 18 and is caused by compressive reaction force to act on movable scroll 2, is reduced, or that movable scroll 2 is pushed toward fixed scroll 1.
  • the fluid pressurized in compression mechanism 3 is supplied into back pressure chamber 28 through pressure inlet hole 32 from compression mechanism 3.
  • the fluid is supplied from a discharge chamber or an oil separation chamber of the compressor into back pressure chamber 28.
  • a seal section comprising annular groove 29 and annular seal 30 which make back pressure chamber 28 a sealed space is positioned at a place including rotation preventing mechanism 24, and the pressure-bearing area is sufficiently ensured at bottom plate part 2a of movable scroll 2 in back pressure chamber 28.
  • Enlargement of such positioned pressure-bearing area in back pressure chamber 28 makes it possible to reduce inner pressure of back pressure chamber 28, so as to design annular seal 20 more flexibly and to improve the sealing performance and the durability of annular seal 30.
  • Such a positioning makes it possible that the pressure-bearing area in back pressure chamber 28 is increased without increasing the shell diameter of the compressor and the compressor is prevented from growing in size caused by providing a back pressure mechanism, so that the compressor is downsized while high seal performance and durability is ensured.
  • thrust bearing members 33 (shown in Fig. 1 ) and 34 (shown in Fig. 2 ) are interposed separately from annular seal 30 and movably in an axial direction, at a position closer to the inside diameter than annular seal 30.
  • annular seal 30 is designed to specialize the seal performance since the trust force which is applied from the side of movable scroll 2 toward main bearing member 18 is born only by thrust bearing members 33 and 34 without making annular seal 30 bear the trust force. Therefore, the seal performance and durability of annular seal 30 can be improved greatly.
  • annular seal 30 doesn't have to bear the thrust force and can be designed especially focused on its seal performance. Therefore, annular seal 30 can be designed in a great flexibility, so that appropriate design with appropriate materials make the seal performance and the durability of annular seal 30 greatly improved.
  • annular seal 30 can greatly reduce the leakage of the fluid introduced into back pressure chamber 28 from a region of annular seal 30, so as to improve the volume efficiency and the coefficient of performance of the compressor.
  • thrust bearing members 33 and 34 can be designed such that bottom plate part 2a of movable scroll 2 contacts thrust bearing members 33 and 34 when the compressor starts up and the bottom plate part doesn't contact thrust bearing members substantively in a steady operation. Therefore the durability of annular seal 30 and thrust bearing members 33 and 34 can be improved.
  • the first embodiment as shown in Fig. 1 can also be configured as shown in Fig. 3 and Fig. 5 .
  • the second embodiment as shown in Fig. 2 can also be configured as shown in Fig. 4 and Fig. 6 .
  • shallow annular low-level step 41 may be formed on the front face of main bearing member 18 which faces movable scroll 2 as shown in Fig. 3 .
  • Thrust bearing member 33 which has been made of comparatively thin plate material as extending annularly, can be placed on low-level step 41 so that thrust bearing member 33 is supported between low-level step 41 and the back face of bottom plate part 2a of movable scroll 2.
  • thrust bearing member 33 In order to prevent thrust bearing member 33 from interfering with rotation preventing pin 27 extruding from the front face of main bearing member 18, it is possible that opening 42 through which rotation preventing pin 27 is inserted is formed on thrust bearing member 33 as shown in Fig. 5 . Further, outer peripheral surface of thrust bearing member 33 on the front face of main bearing member 18 can be ensured as a broad area of seal surface 43 brought into sliding contact with annular seal 30 to swing together with movable scroll 2 as shown in Fig. 5 . It is preferable that an abrasion-resistant metal plate, such as carbon tool steels called SK material in Japan, is employed as the comparatively thin plate material to form thrust bearing member 33. Such a metal plate can achieve a desirable surface roughness easily.
  • a plurality of grooves 51 extending circularly in a circumferential direction are intermittently formed on the front face of main bearing member 18 facing movable scroll 2 in a condition where arc-like thrust bearing member 34 freely fits in each groove 51, as shown in Fig. 4 and Fig. 6 .
  • Arc-like grooves 51 and arc-like thrust bearing members 34 are placed away from rotation preventing pins 27.
  • Outer peripheral surface of grooves 51 and thrust bearing members 34 on the front face of main bearing member 18 can be ensured as a broad area of seal surface 52 brought into sliding contact with annular seal 30 to swing together with movable scroll 2 as shown in Fig. 6 .
  • an abrasion-resistant resin particularly engineering plastic
  • polyphenylene sulfide is employed as the arc-like member material to form thrust bearing material 34.
  • Such a resin can achieve a desirable sliding performance easily.
  • rotation preventing rings 26 are attached to holes 25 for a rotation preventing rings which are formed at the outer side of hole 62 for drive bearing 21 which is formed at the center as shown in Fig. 7 .
  • Annular groove 29 is formed as surrounding a plurality of rotation preventing rings 26 (rotation preventing mechanism), and annular seal 30 is attached to groove 29.
  • the structure of the scroll compressor according to the present invention is applicable to every scroll compressor, and is suitable for a compressor for an air-conditioning system for vehicles, which strongly requires downsizing and durability improvement.

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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)
EP11803484.2A 2010-07-06 2011-06-29 Scroll compressor Withdrawn EP2589808A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010153750A JP2012017656A (ja) 2010-07-06 2010-07-06 スクロール型圧縮機
PCT/JP2011/064885 WO2012005150A1 (ja) 2010-07-06 2011-06-29 スクロール型圧縮機

Publications (1)

Publication Number Publication Date
EP2589808A1 true EP2589808A1 (en) 2013-05-08

Family

ID=45441132

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11803484.2A Withdrawn EP2589808A1 (en) 2010-07-06 2011-06-29 Scroll compressor

Country Status (5)

Country Link
US (1) US20130209305A1 (ja)
EP (1) EP2589808A1 (ja)
JP (1) JP2012017656A (ja)
CN (1) CN102985696A (ja)
WO (1) WO2012005150A1 (ja)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017202385A1 (zh) * 2016-05-27 2017-11-30 艾默生环境优化技术(苏州)有限公司 涡旋压缩机
DE102020109556A1 (de) 2020-04-06 2021-10-07 Hanon Systems Vorrichtung zum Verdichten eines gasförmigen Fluids

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Publication number Priority date Publication date Assignee Title
JP5817760B2 (ja) * 2013-03-04 2015-11-18 株式会社豊田自動織機 スクロール型圧縮機
JP5601404B1 (ja) * 2013-06-20 2014-10-08 ダイキン工業株式会社 スクロール圧縮機
DE102014113435A1 (de) * 2014-09-17 2016-03-17 Bitzer Kühlmaschinenbau Gmbh Kompressor
CN105986997B (zh) * 2015-02-04 2019-11-01 艾默生环境优化技术(苏州)有限公司 涡旋压缩机
US11105332B2 (en) 2015-02-04 2021-08-31 Emerson Climate Technologies (Suzhou) Co., Ltd. Scroll compressor having stable back pressure chamber with sealing members
JP6686490B2 (ja) 2016-02-04 2020-04-22 ソニー株式会社 ユーザ端末、方法及びプログラム
WO2017175945A1 (en) * 2016-04-06 2017-10-12 Lg Electronics Inc. Motor-operated compressor
CN108884828A (zh) * 2016-04-06 2018-11-23 Lg电子株式会社 电机操作的压缩机
JP6715722B2 (ja) * 2016-07-29 2020-07-01 日立ジョンソンコントロールズ空調株式会社 スクロール圧縮機
JP6678762B2 (ja) * 2016-10-28 2020-04-08 三菱電機株式会社 スクロール圧縮機、冷凍サイクル装置およびシェル
KR102549777B1 (ko) 2016-12-21 2023-06-30 삼성전자주식회사 스크롤 압축기
CN107044416A (zh) * 2017-03-07 2017-08-15 无锡五洋川普涡旋科技有限公司 一种水冷式三级压缩无油涡旋空气压缩机
JP6760148B2 (ja) * 2017-03-10 2020-09-23 株式会社豊田自動織機 車両用電動圧縮機
JP7314452B2 (ja) * 2019-05-22 2023-07-26 司郎 澤 スクロール圧縮機用両頭円すいころ偏心接手
CN114033676A (zh) * 2021-12-23 2022-02-11 广州广涡压缩机有限公司 一种增压式涡旋空气压缩机

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017202385A1 (zh) * 2016-05-27 2017-11-30 艾默生环境优化技术(苏州)有限公司 涡旋压缩机
EP3467311A4 (en) * 2016-05-27 2020-01-01 Emerson Climate Technologies (Suzhou) Co., Ltd. TOURBILLON COMPRESSOR
US11976655B2 (en) 2016-05-27 2024-05-07 Copeland Climate Technologies (Suzhou) Co. Ltd. Scroll compressor
DE102020109556A1 (de) 2020-04-06 2021-10-07 Hanon Systems Vorrichtung zum Verdichten eines gasförmigen Fluids
DE102020109556B4 (de) 2020-04-06 2022-10-06 Hanon Systems Vorrichtungen zum Verdichten eines gasförmigen Fluids und Verfahren zum Betreiben der Vorrichtungen

Also Published As

Publication number Publication date
JP2012017656A (ja) 2012-01-26
WO2012005150A1 (ja) 2012-01-12
CN102985696A (zh) 2013-03-20
US20130209305A1 (en) 2013-08-15

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