EP2169230A2 - Zylinder und Rotationskompressor mit diesem Zylinder - Google Patents

Zylinder und Rotationskompressor mit diesem Zylinder Download PDF

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Publication number
EP2169230A2
EP2169230A2 EP08169527A EP08169527A EP2169230A2 EP 2169230 A2 EP2169230 A2 EP 2169230A2 EP 08169527 A EP08169527 A EP 08169527A EP 08169527 A EP08169527 A EP 08169527A EP 2169230 A2 EP2169230 A2 EP 2169230A2
Authority
EP
European Patent Office
Prior art keywords
vane
rotary compressor
groove
cylinder
suction port
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Withdrawn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
EP08169527A
Other languages
English (en)
French (fr)
Other versions
EP2169230A3 (de
Inventor
Yamanaka Masaji
Young Min Choi
Sung Oug Cho
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.)
Samsung Electronics Co Ltd
Original Assignee
Samsung Electronics Co 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 Samsung Electronics Co Ltd filed Critical Samsung Electronics Co Ltd
Publication of EP2169230A2 publication Critical patent/EP2169230A2/de
Publication of EP2169230A3 publication Critical patent/EP2169230A3/de
Withdrawn legal-status Critical Current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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0827—Vane tracking; control therefor by mechanical means
    • F01C21/0845—Vane tracking; control therefor by mechanical means comprising elastic means, e.g. springs
    • 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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/02—Liquid sealing for high-vacuum pumps or for compressors
    • 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
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/101—Geometry of the inlet or outlet of the inlet
    • 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
    • F04C27/001—Radial sealings for working fluid
    • F04C27/004—Radial sealing elements specially adapted for intermeshing-engagement type pumps, e.g. gear pumps

Definitions

  • the present invention relates to a cylinder and a rotary compressor having the same. More particularly, the present invention relates to a rotary compressor using carbon dioxide coolant that is natural coolant.
  • HFC hydro-fluorocarbon
  • CO 2 carbon dioxide
  • a rotary compressor using such CO 2 as coolant is also spotlighted.
  • a rotary compressor including a cylinder, which includes a compressing chamber receiving a roller, a suction port supplying a fluid to the compressing chamber, and a vane groove receiving a vane and allowing the vane to reciprocate in the vane groove such that the compressing chamber is divided into a suction area and a discharge area by the vane, and an expansion groove formed adjacent to an outlet of the suction port and obtained by enlarging a sectional area of the suction port.
  • upper and lower portions of the expansion groove are open.
  • the cylinder is provided with an oil supply passage connecting the expansion groove with the vane groove.
  • the oil supply passage has a stepped portion on at least one of top and bottom surfaces of the cylinder.
  • the stepped portion of the oil supply passage has a height in a range of 0.05 mm to 0.2 mm.
  • the oil supply passage comprises a guide unit guiding a direction of oil to one side of a side surface of the vane groove, and the guide unit is inclined from the expansion groove to a front end of the vane groove.
  • the oil supply passage comprises a guide unit guiding a direction of oil to one side of a side surface of the vane groove, and the guide unit is curved from the expansion groove to a front end of the vane groove.
  • the fluid introduced into the suction port is mixture of oil and carbon dioxide that is natural coolant.
  • the suction port is formed with an outlet having a size identical to a height of an inner circumferential surface of the cylinder.
  • the rotary compressor includes an oil supply passage configured to be stepped between an expansion groove and the vane groove.
  • a rotary compressor including a cylinder, which includes a compressing chamber receiving a roller, a suction port supplying a fluid to the compressing chamber, and a vane groove receiving a vane and allowing the vane to reciprocate in the vane groove such that the compressing chamber is divided into a suction area and a discharge area by the vane.
  • the suction port is formed with an outlet enlarged corresponding to a height of an inner circumferential surface of the cylinder.
  • the rotary compressor further includes an oil supply passage configured to be stepped between the suction port of the cylinder and the vane groove.
  • sealing performance can be improved due to oil and the abrasion of components can be prevented, so that reliability and compression efficiency of the rotary compressor can be improved.
  • a rotary compressor may perform compressing by one compressing unit, but the present invention is applicable for a twin rotary compressor performing compressing by two compressing units.
  • FIG. 1 is a sectional view schematically showing the structure of the rotary compressor according to one embodiment of the present invention
  • FIG. 2 is a sectional view showing a compressing unit according to the present invention.
  • the rotary compressor includes a case 10 forming an outer portion, a driving unit 30 generating a driving force, and a compressing unit 50 receiving the driving force of the driving unit 30 to compress coolant gas.
  • the driving unit 30 and the compressing unit 50 are installed in the case 10 having a cylindrical shape.
  • a suction pipe 11 is connected to one lower side of the case 10 to supply the coolant gas from an accumulator 70, which processes the liquid-phase coolant, to the compressing unit 50.
  • a discharge pipe 13 is provided at an upper portion of the case 10 to discharge the coolant gas compressed in the compressing unit 50.
  • An oil storage space 15 filled with a predetermined amount of oil is provided at a lower portion of the case 10 in order to lubricate and cool a member performing friction motion.
  • the driving unit 30 includes a stator 31 fixed to the case 10, a rotor 33 rotatably supported in the stator 31, and a rotating shaft 35 press-fitted into the rotator 33. Accordingly, if power is supplied to the rotor 33, the rotor 33 rotates by electromagnetic force, and the rotating shaft 35 press-fitted and integrally formed with the rotor 33 transmits rotational force to the compressing unit 50.
  • the compressing unit 50 includes an eccentric unit 51 formed at one lower side of the rotating shaft 35, a roller 52 fitted around the eccentric unit 51, a cylinder 100 provided with a compressing chamber 110 receiving the roller 52, and upper and lower bearings 53 and 57 coupled to upper and lower portions of the cylinder 100 to seal the compressing chamber 110 and support the rotating shaft 35.
  • the cylinder 100 and the upper and lower bearings 53 and 57 are formed with bolt coupling holes 101, 54, and 58. As a coupling bolt 59 is inserted into the bolt coupling holes 101, 54, and 58, the upper and lower bearings 53 and 57 closely make contact with top and bottom surfaces of the cylinder 100 to seal the compressing chamber 110.
  • the cylinder 100 is provided at one side thereof with a suction port 130 connected to the suction pipe 11 coupled to the accumulator 70 to supply coolant gas, and at the other side thereof with a discharge port 150 to guide the coolant gas compressed in the compressing chamber 110 to the outside of the compressing chamber 110.
  • a discharge hole 55 is formed at one side of the upper bearing 53 such that the discharge hole 55 communicates with the discharge port 150 to discharge coolant gas, which has been guided to the discharge port 150, to an outside.
  • a valve unit 56 is provided at an upper portion of the upper bearing 53 placed at a side of the discharge hole 55 to open/close the discharge hole 50.
  • the mixture of carbon dioxide coolant and oil is introduced into the suction port 130 and supplied to the compressing chamber 110, and the inside of the compressing chamber 110 is sealed by the oil.
  • the oil supplied to the compressing chamber 110 can be mixed with the carbon oxide coolant to the extent that volumetric efficiency is not lowered.
  • the suction port 130 is formed through an outer peripheral surface of the cylinder 100 and an inner peripheral surface of the cylinder 100.
  • An expansion groove 131 is formed at an outlet of the suction port 130 adjacent to an inner peripheral surface of the cylinder 100 constituting the compressing chamber 110.
  • the expansion groove 131 can be obtained by enlarging the size of the outlet of the suction port 130.
  • the expansion groove 131 is recessed from the inner circumferential surface of the cylinder 100 by a predetermined depth, and upper and lower portions of the expansion groove 131 are open. This is necessary to allow the outlet of the expansion groove 131, which communicates with the compressing chamber 110, to have a height h identical to a height of an inner surface of the cylinder 100.
  • oil introduced through the suction port 130 can be sufficiently supplied to upper and lower portions of the roller 52 as well as a central portion of an outer circumferential surface of the roller 52 by the expansion groove 131.
  • the oil introduced through the suction port 130 is directly supplied from the outlet of the suction port 130 to the central portion and the upper and lower portions of the roller 52 due to the structure of the expansion groove 131.
  • an oil film is sufficiently formed between an outer circumferential surface of the roller 52 in the compressing chamber 110 and the inner circumferential surface of the cylinder 100. Therefore, when compressing high-pressure carbon dioxide coolant, gas leakage can be prevented from occurring in the longitudinal direction at a region between the inner circumference surface of the cylinder 100 and the central portion of the roller 52. That is, the gas is prevented from being leaked from the high-pressure discharge area 113 of the cylinder 100 to the lower-pressure suction area 111. Accordingly, volumetric efficiency can be prevented from being lowered due to the gas leakage.
  • a vane groove 170 is formed between the suction port 130 and the discharge port 150 of the cylinder 100 and a vane 171 is provided in the vane groove 170.
  • the vane 171 reciprocates relative to the compressing chamber 110 by an elastic port 173 provided at a rear portion of the vane 171 when the roller 52 rotates in a state in which a front end of the vane 171 makes contact with the outer circumferential surface of the roller 52.
  • an internal space of the compressing chamber 110 is partitioned into the suction area 111 placed at a side of the suction pipe 11 and the discharge area 113 placed at a side of the discharge port 150 by the vane 171 so that gas existing at the inside of the discharge area 113 can be compressed.
  • the vane 171 reciprocates while making contact with the roller 52.
  • High-pressure coolant gas of the discharge area 113 is introduced into the suction area 111 from the vane groove 170 due to high pressure difference between the lower-pressure suction area 111 and the high-pressure discharge area 113.
  • micro-gaps are created at lateral sides of the vane groove 170 and the vane 171 and at a contact surface between of the roller 52 and the vane 171 to cause gas leakage.
  • an oil supply passage 190 is formed between the expansion groove 131 and the vane groove 170 to connect the expansion groove 131 to the vane groove 170 so that oil can be sufficiently supplied to the side surface of the vane groove 170 provided at a side the suction area 111 having high pressure difference.
  • the oil supply passage 190 is necessary to induce oil, which is introduced through the suction port 130, from the expansion groove 131 to the vane 171.
  • the oil supply passage 130 is stepped on top and bottom surfaces of the cylinder 100 such that the oil introduced through the suction port 130 can be supplied to the side surface of the vane groove 170 from the upper and lower portions of the expansion groove 131.
  • the oil supply passage 190 includes a recess unit 191, which is recessed by a predetermined depth from the top and bottom surfaces of the cylinder 100 such that a passage is formed to allow oil to flow from the expansion groove 131 to the vane groove 170 when the upper and lower bearings 53 and 57 closely make contact with the top and bottom surfaces of the cylinder 100, and a guide unit 193 guiding the direction of the oil such that the oil is supplied within a movement range of the vane 171 reciprocating in the vane groove 170.
  • the depth of the recess unit 191 stepped according to one embodiment of the present invention can be suitably set by taking into compression efficiency consideration, and may be in the range of about 0.05mm to 0.2mm. Preferably, the depth of the recess unit 191 is about 0.1 mm.
  • the guide unit 193 is inclined in a straight line toward the front end of the vane groove 170 from one upper side of the expansion groove 131 such that oil is prevented from being introduced to a rear portion of the vane groove 170 as shown in FIG. 3 .
  • the present invention is not limited thereto, but the guide unit 193 may be formed in the curved shape as shown in FIG. 5 such that hydraulic resistance of oil can be reduced.
  • oil passing through the suction port 130 is introduced from the upper and lower portions of the expansion groove 131 to the side surface of the vane groove 170 through the oil supply passage 190, so that oil films are sufficiently formed on the contact surface of the vane 171 and the vane groove 170, and the contact surface of the front end of the vane 171 and the roller 52. Accordingly, gas leakage caused by gap creation is prevented, and components are prevented from being damaged due to the abrasion of the components in a compression operation.
  • the mixture introduced through the suction port 130 is supplied to upper and lower portions of the roller 52 as well as the central portion of the roller 52 by the expansion groove 131 provided at the outlet of the suction port 130 as shown in FIG. 4 so that oil can be sufficiently supplied to the outer circumferential surface of the roller 52. Accordingly, a sealing area is significantly increased on the contact surface between the inner circumferential surface of the cylinder 100 and the outer circumferential surface of the roller 52.
  • the mixture introduced into the suction area 111, which is provided in the compressing chamber 110, is changed into a high-pressure state in the discharge area 113 of the compressing chamber 110, in which the size of the discharge area 113 is gradually reduced due to the eccentric rotation motion of the roller 52 and the reciprocation motion of the vane 171 supported on the outer circumference surface of the roller 52.
  • carbon dioxide coolant having a pressure corresponding to about three times that of coolant such as R410A is used, so that a gap is created at a contact surface between components provided in the compressing chamber 110.
  • this gap is a main cause of gas leakage from the lateral sides of the vane 171 and the contact surface between the front end of the vane 171 and the roller 52 representing the highest pressure difference.
  • oil sucked through the suction port 130 is sufficiently supplied to the side surface of the vane groove 170 through the oil supply passage 190 formed between the expansion groove131 and the vane groove 170, so that gas sealing is sufficiently achieved due to oil.
  • the oil introduced through the suction port 130 is sufficiently uniformly supplied to a connection part of the roller 52 and the inner circumferential surface of the cylinder 100 by the expansion groove 131, so that sealing performance of the compressing chamber110 is improved due to the oil.
  • oil is sufficiently supplied to the side surface of the vane 171 having the highest pressure difference through the oil supply passage 190, the reliability and the efficiency of the rotary compressor is remarkably increased when high-pressure carbon dioxide coolant is used.
  • coefficient of performance (COP) and volumetric efficiency in all operational areas of the compressor can be improved by 20% relative to a conventional compressor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP08169527.2A 2008-09-25 2008-11-20 Zylinder und Rotationskompressor mit diesem Zylinder Withdrawn EP2169230A3 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020080094154A KR20100034914A (ko) 2008-09-25 2008-09-25 로터리 압축기용 실린더 및 이를 구비한 로터리 압축기

Publications (2)

Publication Number Publication Date
EP2169230A2 true EP2169230A2 (de) 2010-03-31
EP2169230A3 EP2169230A3 (de) 2014-01-08

Family

ID=41507952

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08169527.2A Withdrawn EP2169230A3 (de) 2008-09-25 2008-11-20 Zylinder und Rotationskompressor mit diesem Zylinder

Country Status (3)

Country Link
EP (1) EP2169230A3 (de)
KR (1) KR20100034914A (de)
CN (1) CN101684812A (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20180090324A (ko) * 2016-02-15 2018-08-10 미쓰비시덴키 가부시키가이샤 로터리 압축기
US11002279B2 (en) * 2017-07-24 2021-05-11 Lg Electronics Inc. Rotary compressor
US11060522B2 (en) 2016-11-09 2021-07-13 Fujitsu General Limited Rotary compressor having reduced pressure loss of refrigerant flow

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103161729B (zh) * 2011-12-12 2015-10-28 珠海格力节能环保制冷技术研究中心有限公司 旋转式压缩机及空调器
CN103629115B (zh) * 2012-08-22 2016-09-28 上海日立电器有限公司 滚动转子式压缩机斜置式叶片槽结构
CN103174653B (zh) * 2013-03-05 2017-02-15 珠海格力电器股份有限公司 一种压缩机的吸气结构
CN106015011B (zh) * 2016-06-27 2018-11-02 珠海凌达压缩机有限公司 一种压缩机及具有该压缩机的空调
CN105927544A (zh) * 2016-07-01 2016-09-07 珠海格力节能环保制冷技术研究中心有限公司 冷媒压缩系统、旋转压缩机及其气缸
CN108087274A (zh) * 2017-12-11 2018-05-29 加西贝拉压缩机有限公司 一种转子压缩机的吸气结构
KR102481674B1 (ko) 2021-06-23 2022-12-27 엘지전자 주식회사 로터리 압축기
CN114183363A (zh) * 2021-12-08 2022-03-15 珠海凌达压缩机有限公司 润滑组件、压缩机和空调系统
KR102759208B1 (ko) 2022-11-22 2025-01-24 엘지전자 주식회사 로터리 압축기

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JPS5888487A (ja) * 1981-11-24 1983-05-26 Toshiba Corp ロ−タリ−コンプレツサ
JPH04203387A (ja) * 1990-11-30 1992-07-23 Hitachi Ltd ロータリ圧縮機
US5829960A (en) * 1996-04-30 1998-11-03 Tecumseh Products Company Suction inlet for rotary compressor
JP4380045B2 (ja) * 2000-09-14 2009-12-09 パナソニック株式会社 ロータリ式多段圧縮機
JP3580365B2 (ja) * 2001-05-01 2004-10-20 株式会社日立製作所 ロータリ圧縮機
JP2007146747A (ja) * 2005-11-28 2007-06-14 Matsushita Electric Ind Co Ltd 冷凍サイクル装置

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20180090324A (ko) * 2016-02-15 2018-08-10 미쓰비시덴키 가부시키가이샤 로터리 압축기
US11060522B2 (en) 2016-11-09 2021-07-13 Fujitsu General Limited Rotary compressor having reduced pressure loss of refrigerant flow
US11002279B2 (en) * 2017-07-24 2021-05-11 Lg Electronics Inc. Rotary compressor

Also Published As

Publication number Publication date
EP2169230A3 (de) 2014-01-08
KR20100034914A (ko) 2010-04-02
CN101684812A (zh) 2010-03-31

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