EP2687727A1 - Compresseur - Google Patents

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Publication number
EP2687727A1
EP2687727A1 EP13176449.0A EP13176449A EP2687727A1 EP 2687727 A1 EP2687727 A1 EP 2687727A1 EP 13176449 A EP13176449 A EP 13176449A EP 2687727 A1 EP2687727 A1 EP 2687727A1
Authority
EP
European Patent Office
Prior art keywords
diameter portion
small
refrigerant gas
oil
oil separator
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
EP13176449.0A
Other languages
German (de)
English (en)
Other versions
EP2687727B1 (fr
Inventor
Takuro Yamashita
Kazuhiro Kuroki
Tatsuya Ito
Jun Yamazaki
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.)
Toyota Industries Corp
Original Assignee
Toyota Industries 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 Toyota Industries Corp filed Critical Toyota Industries Corp
Publication of EP2687727A1 publication Critical patent/EP2687727A1/fr
Application granted granted Critical
Publication of EP2687727B1 publication Critical patent/EP2687727B1/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
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/026—Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/16—Filtration; Moisture separation
    • 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
    • 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

Definitions

  • the present invention relates to a compressor.
  • pulsation of discharge refrigerant gas occurs.
  • the pulsation may be transmitted through a conduit of a refrigerant circuit to a passenger compartment of the vehicle and cause vibration to equipment in the compartment and abnormal noise.
  • various methods such as providing a large volume muffler on the side where refrigerant gas is discharged or throttling a passage where discharged refrigerant gas flows.
  • Japanese Unexamined PatentApplication Publication No. 2005-16454 discloses a compressor in which a muffler is formed by a large-volume discharge chamber where compressed refrigerant gas is discharged from a compression chamber.
  • the discharge chamber has therein a vertically extending pipe connected to an external refrigerant circuit and serving as an oil separator.
  • the discharge chamber is connected to the compression chamber through a discharge port and a discharge valve.
  • the pipe is positioned above the discharge port and the discharge valve.
  • the pipe has a throttling portion which is opened at its lower end to the discharge chamber and a diffuser portion which is connected at its upper end to the external refrigerant circuit.
  • the provision of the large discharge chamber as the muffler helps to reduce the pulsation of discharge refrigerant gas, and the throttling of discharged refrigerant gas flowing from the discharge chamber into the pipe helps to further reduce the pulsation.
  • the pressure of the refrigerant gas flowing through the pipe is reduced at the throttling portion, but recovered at the diffuser portion. Then the refrigerant gas flows out of the compressor into the external refrigerant circuit.
  • Japanese Unexamined Patent Application Publication No. 11-107959 discloses another compressor having in its hermetic housing a discharge space into which compressed refrigerant gas is discharged from a compression mechanism through a delivery pipe.
  • the discharge space is provided with a discharge pipe through which compressed refrigerant gas is discharged out of the housing.
  • the discharge pipe is closed at its lower end in the housing by a plate and has plural small holes in its peripheral surface adjacent to such bottom end.
  • the lubricating oil separated from the refrigerant gas by the hole and attached to the pipe surface adjacent to the holes may block refrigerant gas flow through the holes, which is disadvantageous in the prevention of increased pressure loss of refrigerant gas due to the throttling of refrigerant gas flow by the hole.
  • the lubricating oil separated from refrigerant gas may be blown up into the discharge pipe by the compressed gas entering through the holes, which does not necessarily lead to the desired separation of lubricating oil.
  • the present invention is directed to providing a compressor of a structure that prevents increased pressure loss of refrigerant gas and reduces pulsation of discharge refrigerant gas.
  • a compressor in accordance with an aspect of the present invention, includes a housing having a discharge chamber into which compressed refrigerant gas is discharged, an oil separation chamber in which lubricating oil contained in the discharged refrigerant gas is separated, a passage connecting between the discharge chamber and the oil separation chamber, and an outlet port through which the refrigerant gas passed through the oil separation chamber flows out of the housing; and a cylindrical oil separator provided in the oil separation chamber and connected at one end to the outlet port.
  • the oil separator includes a large-diameter portion, a small-diameter portion having a smaller diameter than the large-diameter portion, and an intermediate portion formed between the large-diameter portion and the small-diameter portion and tapered toward the small-diameter portion.
  • Plural holes are formed in the periphery of the small-diameter portion of the oil separator.
  • the passage is directed toward the small-diameter portion of the oil separator in such a manner that the refrigerant gas flowed through the passage into the oil separation chamber swirls around the small-diameter portion, so that the refrigerant gas from which lubricating oil is separated enters the oil separator through the hole and then exits the large-diameter portion of the oil separator.
  • Figs. 1 to 4 show the electric motor driven scroll compressor of the first embodiment according to the present invention. It is noted that the left-hand side and the right-hand side of the compressor as viewed in Fig. 1 correspond to its front side and rear side, respectively, and that the upper and lower sides of the compressor as viewed in Fig. 1 correspond to its upper and lower sides, respectively.
  • the compressor has a front housing 1 and a rear housing 2 which are fixed together by plural bolts 3 thereby to form a hermetic compressor housing.
  • the rear housing 2 and the front housing 1 has an inlet port 4 and an outlet port 5, respectively, which are connected to an external refrigerant circuit (not shown).
  • Refrigerant gas enters the compressor through the inlet port 4 of the rear housing 2 and flows in the rear housing 2 and the front housing 1 toward the outlet port 5 of the front housing 1.
  • the rear housing 2 accommodates therein a scroll compression mechanism 6 and an electric motor 7 for driving the compression mechanism 6.
  • the electric motor 7 is a three-phase AC motor and has a rotary shaft 8 rotatably supported in the rear housing 2 by bearings, a rotor 9 fixed to the rotary shaft 8, and a stator 10 fixed to the inner surface of the rear housing 2 around the rotor 9.
  • the stator 10 has a three-phase coil 11 that is electrically connected through a cluster block 12 to an inverter (not shown) provided in an inverter housing 13.
  • the compression mechanism 6 is mainly composed of a fixed scroll 14 fixed to the inner surface of the rear housing 2 and a movable scroll 15 disposed in facing relation to the fixed scroll 14 so as to form therebetween plural compression chambers 16, the volume of which is variable for compressing refrigerant gas.
  • the movable scroll 15 is connected through a bearing and an eccentric bush 17 to an eccentric pin 18 of the rotary shaft 8 and orbits about the fixed scroll 14 with the rotation of the rotary shaft 8 so as to vary the volume of the compression chambers 16.
  • the front and rear housings 1, 2 form therebetween a discharge chamber 19.
  • the front housing 1 forms therein an oil separation chamber 20.
  • the fixed scroll 14 has at the center thereof a discharge port 21 through which the compression chamber 16 then located at the innermost position communicates with the discharge chamber 19.
  • the discharge port 21 is normally closed by a discharge valve 22 provided in the discharge chamber 19. Refrigerant gas compressed in the compression chamber 16 is discharged into the discharge chamber 19 while pushing open the discharge valve 22.
  • the opening of the discharge valve 22 is restricted by a retainer 23.
  • the space of the discharge chamber 19 is formed large enough only to accommodate therein at least the discharge valve 22 and the retainer 23.
  • the discharge chamber 19 is connected at its upper part to the oil separation chamber 20 through a passage 24.
  • the oil separation chamber 20 is made in the form of a vertically extending space.
  • the lower part of the oil separation chamber 20 serves as an oil reservoir 25 and the upper part thereof is equipped with an oil separator 26.
  • Lubricating oil collected in the oil reservoir 25 is flowed toward the compression mechanism 6 through an oil return passage 27 provided adjacent to the bottom of the oil reservoir 25.
  • Figs. 2 and 3 show the structure of the oil separator 26 in detail.
  • the oil separator 26 is of a generally hollow cylindrical shape and has on its upper side a large-diameter portion 28 and on its lower side adjacent to the oil reservoir 25 a small-diameter portion 29 having a smaller inner diameter than the large-diameter portion 28.
  • the oil separator 26 further has an intermediate portion 30 formed between the large-diameter portion 28 and the small-diameter portion 29 and tapered toward the small-diameter portion 29.
  • the upper end of the large-diameter portion 28, that is, one end of the oil separator 26 is opened, while the lower end of the small-diameter portion 29 facing the oil reservoir 25, that is, the other end of the oil separator 26 is closed by a bottom plate 31.
  • the large-diameter portion 28 of the oil separator 26 is fixed to the inner surface of the oil separation chamber 20 and connected at its upper end to the outlet port 5 and hence to the external refrigerant circuit.
  • Plural round holes 32 are formed in the periphery of the lower part of the small-diameter portion 29 of the oil separator 26.
  • the holes 32 are divided into two vertically spaced groups each having eight holes 32 arranged at an equal angular interval along the circumference of the small-diameter portion 29. That is, the small-diameter portion 29 has a total of sixteen holes 32.
  • the holes 32 serve to provide fluid communication between the interior 33 and the exterior 37 of the oil separator 26.
  • the small-diameter portion 29 has a perforated region 34 where the holes 32 are formed and a non-perforated region 35 where no hole such as 32 is formed.
  • the hole 32 is formed in such a manner that the cross sectional area S2 of the hole 32 is as small as possible relative to the cross sectional area S1 of the passage 24 at the connection thereof to the oil separation chamber 20.
  • the oil separator 26 is disposed in such a manner that the non-perforated region 35 of the small-diameter portion 29 faces the passage 24.
  • the passage 24 is directed toward the small-diameter portion 29 and also directed in tangential relation to the small-diameter portion 29.
  • the passage 24 is formed in such a manner that, as shown in Fig. 3 , the central axis X1 of the passage 24 coincides with the tangent to the small-diameter portion 29, as seen in the direction in which refrigerant gas is discharged from the passage 24.
  • the central axis X1 of the passage 24 extends tangentially to the outer circumference of the small-diameter portion 29, as shown in Fig. 3 .
  • the passage 24 may be formed in such a manner that the central axis X1 of the passage 24 passes through a point located radially inward or outward of the small-diameter portion 29, and also that the formation of the passage 24 with the central axis X1 extending tangentially to any circle concentric with the outer circumference of the small-diameter portion 29 having the central axis X2 falls within the scope of the present invention.
  • Refrigerant gas flowed through the passage 24 into the oil separation chamber 20 swirls around the small-diameter portion 29 of the oil separator 26, so that lubricating oil contained in the refrigerant gas is separated therefrom by centrifugal force.
  • the separated lubricating oil is attached to the inner surface of the oil separation chamber 20 and moved downward therealong to be collected in the oil reservoir 25.
  • refrigerant gas compressed in the central compression chamber 16 of the compression mechanism 6 ( Fig. 1 ) is discharged through the discharge port 21 into the discharge chamber 19 while pushing open the discharge valve 22.
  • the refrigerant gas then flows through the passage 24 toward the non-perforated region 35 of the small-diameter portion 29 of the oil separator 26 in the oil separation chamber 20 and then moves down toward the perforated region 34 while swirling around the small-diameter portion 29 from the non-perforated region 35, as indicated by spiral arrow.
  • the refrigerant gas from which almost all lubricating oil having been separated swirls around the perforated region 34 of the oil separator 26 and then enters the interior 33 of the oil separator 26 through the holes 32 of the perforated region 34. Because of the small cross sectional area S2 of the hole 32, the flow of refrigerant gas passing through the holes 32 is effectively throttled, resulting in the reduction of pulsation of discharge refrigerant gas.
  • the provision of plural holes 32 in the perforated region 34 allows sufficient amount of refrigerant gas to flow and enter the interior 33 of the oil separator 26, which helps to prevent increased pressure loss of refrigerant gas due to the throttling of discharged refrigerant gas flow by the holes 32.
  • the pressure of the refrigerant gas is recovered because of the diverging structure of the intermediate portion 30 serving as a diffuser, which further helps to prevent an increase of the pressure loss of refrigerant gas.
  • the refrigerant gas flowed from the intermediate portion 30 to the large-diameter portion 28 in the oil separator 26 exits the compressor through the outlet port 5 and flows in the external refrigerant circuit.
  • Fig. 5 shows the second embodiment of the electric motor driven compressor according to the present invention.
  • same reference numerals are used for the common elements or components in the first and the second embodiments, and the description of such elements or components of the second embodiment will be omitted.
  • the second embodiment differs from the first embodiment in that three holes 36 are formed through the bottom plate 31 of the small-diameter portion 29 of the oil separator 26 in addition to the holes 32 formed in the small-diameter portion 29.
  • the cross sectional area S3 of the hole 36 is smaller than the cross sectional area S2 ( Fig. 2 ) of the hole 32.
  • Refrigerant gas flowed into the oil separation chamber 20 swirls around the small-diameter portion 29 of the oil separator 26 and lubricating oil contained in the refrigerant gas is separated therefrom by centrifugal force.
  • the refrigerant gas from which lubricating oil having been separated swirls around the small-diameter portion 29 and enters the interior 33 of the oil separator 26 through the holes 32 formed in the periphery of the oil separator 26 and also through the holes 36 formed in the bottom plate 31 of the oil separator 26.
  • the provision of the holes 36 makes it easy for the refrigerant gas swirling around the small-diameter portion 29 of the oil separator 26 to enter the interior 33 of the oil separator 26, which leads to an increased flow rate of refrigerant gas in the interior 33 and further helps to prevent an increase of pressure loss of refrigerant gas.
  • the lubricating oil collected in the oil reservoir 25 is blown up against the bottom plate 31 of the oil separator 26 by the swirling refrigerant gas flow, such lubricating oil is prevented from entering the interior 33 of the oil separator 26 through the hole 36 because the cross sectional area of the hole 36 formed in the bottom plate 31 is small.
  • a compressor includes a housing having a discharge chamber into which compressed refrigerant gas is discharged, an oil separation chamber, a passage connecting between the discharge chamber and the oil separation chamber, and an outlet port through which the refrigerant gas passed through the oil separation chamber flows out of the housing; and a cylindrical oil separator provided in the oil separation chamber.
  • the oil separator includes a large-diameter portion, a small-diameter portion, and an intermediate portion formed between the large-diameter portion and the small-diameter portion and tapered toward the small-diameter portion. Plural holes are formed in the periphery of the small-diameter portion of the oil separator.
  • the passage is directed toward the small-diameter portion of the oil separator in such a manner that the refrigerant gas swirls around the small-diameter portion, so that the refrigerant gas from which lubricating oil is separated enters the oil separator through the hole.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP13176449.0A 2012-07-19 2013-07-15 Compresseur Active EP2687727B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2012160804A JP5692177B2 (ja) 2012-07-19 2012-07-19 圧縮機

Publications (2)

Publication Number Publication Date
EP2687727A1 true EP2687727A1 (fr) 2014-01-22
EP2687727B1 EP2687727B1 (fr) 2017-03-15

Family

ID=48877014

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13176449.0A Active EP2687727B1 (fr) 2012-07-19 2013-07-15 Compresseur

Country Status (5)

Country Link
US (1) US20140023542A1 (fr)
EP (1) EP2687727B1 (fr)
JP (1) JP5692177B2 (fr)
KR (1) KR20140011953A (fr)
CN (1) CN103573639A (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3584443B1 (fr) * 2017-02-14 2023-04-19 Valeo Japan Co., Ltd. Compresseur

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KR102012372B1 (ko) * 2014-09-12 2019-08-20 한온시스템 주식회사 스크롤 압축기의 오일 분리장치
KR102080621B1 (ko) * 2015-03-06 2020-04-14 한온시스템 주식회사 전동압축기 및 상기 전동압축기의 유분리기 가공 방법
KR102080623B1 (ko) * 2015-03-06 2020-02-25 한온시스템 주식회사 전동압축기
JP6491526B2 (ja) * 2015-04-21 2019-03-27 カルソニックカンセイ株式会社 気体圧縮機
KR102141871B1 (ko) * 2015-05-26 2020-08-07 한온시스템 주식회사 오일회수 수단을 구비한 압축기
CN107044414A (zh) * 2016-02-05 2017-08-15 苏州中成新能源科技股份有限公司 一种具有油分离结构的涡旋式压缩机及其润滑油分离方法
JP2017172895A (ja) * 2016-03-24 2017-09-28 サンデン・オートモーティブコンポーネント株式会社 オイルセパレータ
CN106704197B (zh) * 2016-11-04 2018-12-07 珠海格力电器股份有限公司 油气分离器、压缩机及空调器
JP6745992B2 (ja) * 2017-06-06 2020-08-26 三菱電機株式会社 スクロール圧縮機および冷凍サイクル装置
JP6953213B2 (ja) * 2017-07-20 2021-10-27 三菱重工サーマルシステムズ株式会社 圧縮機
CN108869282B (zh) * 2018-06-29 2020-04-07 广东金霸智能科技股份有限公司 一种压缩机
CN108757473A (zh) * 2018-07-27 2018-11-06 苏州中成新能源科技股份有限公司 一种电动涡旋压缩机排气降噪机构
CN109296539A (zh) * 2018-09-21 2019-02-01 珠海凌达压缩机有限公司 一种压缩机前盖及压缩机
WO2020123273A1 (fr) 2018-12-10 2020-06-18 Carrier Corporation Système de décharge de compresseur modulaire
JP7462403B2 (ja) 2019-11-26 2024-04-05 サンデン株式会社 圧縮機
CN218581816U (zh) * 2022-05-19 2023-03-07 Lg电子株式会社 压缩机

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5733107A (en) * 1995-08-21 1998-03-31 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Lubricant oil separating mechanism for a compressor
JPH11107959A (ja) 1997-09-30 1999-04-20 Sanyo Electric Co Ltd 密閉型圧縮機の吐出管
JP2005016454A (ja) 2003-06-27 2005-01-20 Toyota Industries Corp ガス流路を備えた機器における脈動低減構造
EP2000672A1 (fr) * 2006-03-29 2008-12-10 Kabushiki Kaisha Toyoda Jidoshokki Compresseur
EP2131040A2 (fr) * 2008-06-05 2009-12-09 Kabushiki Kaisha Toyoda Jidoshokki Compresseur motorisé de type à spirale

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DE918043C (de) * 1952-03-25 1954-09-20 Paul Graefe Vorrichtung zur vollkommenen Abscheidung von festen, fluessigen und dampffoermigen Beimengungen aus Druckluft, Gasen und Daempfen
JP4894357B2 (ja) * 2006-06-02 2012-03-14 株式会社豊田自動織機 圧縮機
JP2010096167A (ja) * 2007-11-29 2010-04-30 Toyota Industries Corp 圧縮機におけるフィルタの取付構造
JP2010190074A (ja) * 2009-02-17 2010-09-02 Toyota Industries Corp スクロール型流体機械
JP5408073B2 (ja) * 2010-08-17 2014-02-05 株式会社豊田自動織機 圧縮機

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5733107A (en) * 1995-08-21 1998-03-31 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Lubricant oil separating mechanism for a compressor
JPH11107959A (ja) 1997-09-30 1999-04-20 Sanyo Electric Co Ltd 密閉型圧縮機の吐出管
JP2005016454A (ja) 2003-06-27 2005-01-20 Toyota Industries Corp ガス流路を備えた機器における脈動低減構造
EP2000672A1 (fr) * 2006-03-29 2008-12-10 Kabushiki Kaisha Toyoda Jidoshokki Compresseur
EP2131040A2 (fr) * 2008-06-05 2009-12-09 Kabushiki Kaisha Toyoda Jidoshokki Compresseur motorisé de type à spirale

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3584443B1 (fr) * 2017-02-14 2023-04-19 Valeo Japan Co., Ltd. Compresseur

Also Published As

Publication number Publication date
EP2687727B1 (fr) 2017-03-15
CN103573639A (zh) 2014-02-12
JP5692177B2 (ja) 2015-04-01
JP2014020306A (ja) 2014-02-03
KR20140011953A (ko) 2014-01-29
US20140023542A1 (en) 2014-01-23

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