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WO2004038225A1 - Compresseur - Google Patents

Compresseur Download PDF

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Publication number
WO2004038225A1
WO2004038225A1 PCT/KR2003/001469 KR0301469W WO2004038225A1 WO 2004038225 A1 WO2004038225 A1 WO 2004038225A1 KR 0301469 W KR0301469 W KR 0301469W WO 2004038225 A1 WO2004038225 A1 WO 2004038225A1
Authority
WO
WIPO (PCT)
Prior art keywords
compressor
space
rotational shaft
compression
cylinder
Prior art date
Application number
PCT/KR2003/001469
Other languages
English (en)
Inventor
Kwang-Sik Yang
Chang-Ryul Kim
Original Assignee
Lg Electronics Inc.
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 Lg Electronics Inc. filed Critical Lg Electronics Inc.
Priority to AU2003250560A priority Critical patent/AU2003250560A1/en
Publication of WO2004038225A1 publication Critical patent/WO2004038225A1/fr

Links

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
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • 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
    • 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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/127—Mounting of a cylinder block in a casing
    • 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
    • F04C18/3568—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 with axially movable vanes

Definitions

  • the present invention relates to a compressor, and more particularly, to a compressor which reduces a frictional loss by reducing a surface pressure of a sliding part in the compressor and thereby enhances efficiency thereof.
  • a compressor is a device for converting mechanical energy into compression energy of compressible fluid, and is classified into a reciprocating compressor, a scroll compressor, a centrifugal compressor, a rotary compressor, and etc. by a compression method.
  • the rotary compressor is a compressor for sucking, compressing, and discharging fluid by rotating a body of rotation and thus consecutively changing a suction region and a compression region under a state that a vane is inserted into the body of rotation and thus an inner space of a cylinder is divided into the suction region and the compression region.
  • Figure 1 is a longitudinal section view showing main parts of a compressor in accordance with the conventional art
  • Figure 2 is a perspective view showing a compression unit of the conventional compressor by partially cutting.
  • the conventional compressor comprises: a hermetic container 10 to which a suction pipe 35 and a discharge pipe (not shown) are connected; a electronic driving unit 12 installed in the hermetic container 10 for generating a rotation force; and a compression unit 14 installed in the hermetic container 10 with a predetermined interval from the driving unit 12 for sucking, compressing, and discharging compressible fluid by the rotation force generated from the driving unit 12.
  • the driving unit 12 is composed of a stator 16 closely fixed to an inner circumference surface of the hermetic container 10, and a rotor 18 installed to have a maintain a constant air gap from the inner circumference surface of the stator 16 for generating a rotation force by electromagnetic interaction with the stator 16.
  • the compression unit 14 comprises: a cylinder assembly 31 installed in the hermetic container 10 and forming a compression space V where compressible fluid sucked from outside is compressed; a rotational shaft 20 rotatably fixed to the cylinder assembly 31 and closely fixed to an inner circumference surface of the rotor 18 thus to be rotated together when the rotor 18 is rotated; a compression member 23 rotated by being engaged to the rotational shaft 20 and for dividing the compression space V in the cylinder assembly 31 into a first space V1 and a second space V2; and first and second vanes 60 and 70 respectively contacted on upper and lower surfaces of the compression member 23 and for dividing the first and second spaces V1 and V2 into suction regions Via, V2a and compression regions V1 b, V2b by being reciprocated towards inner and outer direction of the compression space V along the upper and lower surfaces of the compression member 23 when the compression member 23 is rotated.
  • the cylinder assembly 31 comprises: a cylinder 30 formed as a cylindrical shape and having a suction flow path 36 through which gas is sucked to the first and second spaces V1 and V2, the suction flow path 36 connected to the suction pipe 35; and first and second bearing plates 40 and 50 fixed to both sides of the cylinder 30 thus to form a compression space with the cylinder 30 and for supporting the rotational shaft 20.
  • the first and second bearing plates 40 and 50 are formed as a disc shape having a predetermined thickness and area, and comprises: journal portions 42 and 52 prolonged to have a predetermined height and an outer diameter, and having a penetrated center for rotatably inserting the rotational shaft 20; first and second vane slots 44 and 54 formed by penetrating the first and second bearing plates 40 and 50 for inserting the first and second vanes 60 and 70; discharge flow paths 46 and 56 formed at one side of the first and second vane slots 44 and 54 for discharging gas compressed in the compression space V of the cylinder assembly 31.
  • a first discharge muffler 45 and a second discharge muffler 55 are respectively formed at upper and lower sides of the first and second bearing plates 40 and 50 by being covered.
  • the rotational shaft 20 comprises: a shaft portion 21 formed to have a predetermined outer diameter and a length and inserted into the journal portions 42 and 52 of the first and second bearing plates 40 and 50; a hub portion 22 integrally enlarged at a periphery of the shaft portion 21 thus to be supported on inner surfaces of the first and second bearing plates 40 and 50, and engaged to the compression member 23 in the cylinder assembly 31 ; an oil flow path 25 penetratingly formed inside the shaft portion 21 ; and an oil feeder 24 installed at a lower end of the rotational shaft 20 for supplying oil contained at a lower portion of the hermetic container 10 to an upper side.
  • the hub portion 22 of the rotational shaft 20 is concentric with the shaft portion 21 of the rotational shaft 20.
  • a radial load of the rotational shaft 20 is supported on a radial bearing surface R of the journal portions 42 and 52 of the first and second bearing plates 40 and 50, and an axial load of the rotational shaft 20 is supported on a thrust bearing surface T of the inner surfaces of the first and second bearing plates 40 and 50.
  • the compression member 23 is formed as a disc shape in a plane view so that an outer circumference surface thereof can have a sliding contact with an inner circumference surface of the cylinder 30, and formed as a cam surface of sine wave having the same thickness from the inner circumference surface to the outer circumference surface in a lateral projection view. According to this, a side having an upper dead point D1 of the compression member 23 slidably contacts with a lower surface of the first bearing plate 40, and a side having a lower dead point D2 slidably contacts with an upper surface of the second bearing plate 50.
  • the first and second vanes 60 and 70 are formed as a rectangular plate shape and respectively adhere to an upper and lower surface of the compression member 23 in the compression space V of the cylinder assembly 31.
  • the vanes 60 and 70 reciprocate up and down along a height of the cam surface of the compression member 23 when the compression member 23 is rotated, and thus divide the compression spaces V1 and V2 into the suction regions Via, V2a and the compression regions V1 b, V2b.
  • the first and second vanes 60 and 70 are elastically supported by an elastic supporting member 90 mounted at the first and second bearing plates 40 and 50.
  • the first space V1 located at an upper portion of the compression member 23 is divided into the suction region Via and the compression region V1 b on the basis of the upper dead point D1 of the compression member 23 and the first vane 60.
  • the second space V2 located at a lower portion of the compression member 23 is divided into the suction region V2a and the compression region V2b on the basis of the lower dead point D2 and the second vane 70.
  • the fluid compressed is discharged outside the cylinder assembly 31 through the discharge flow paths 46 and 56 of the compression spaces V1 and V2. Then, the fluid discharged outside the cylinder assembly 31 passes through the first and second discharge mufflers 45 and 55 and inside of the hermetic container 10, and is discharged outside the hermetic container 10 through the discharge pipe (not shown).
  • the most influential factor to a performance of the compressor is a friction loss generating in a sliding part in the
  • the friction is generated at the sliding part between the vanes 60, 70 and the compression member 23, between the vanes 60, 70 and the vane slots 44, 54, between the compression member 23 and the bearing plates 40, 50, and between the rotational shaft 20 and the bearing plates 40, 50.
  • the friction causes noise of the com6pressor and abrasion of elements inside the compressor, thereby degrading performance and life span of the compressor. Also, by the friction of the sliding part, heat is generated thus to cause heat loss of refrigerant gas.
  • a supporting portion 22 for supporting the axial load of the rotational shaft 20 on the bearing plates 40, 50 and the thrust bearing surface T of the bearing plates 40, 50 rotate by being adhered as a radial width L of the supporting portion 22, so that great surface pressure is applied to the sliding part between the supporting portion 22 and the thrust bearing surface T.
  • the surface pressure By the surface pressure, friction and abrasion are generated, so that the performance of the compressor is lowered and damage of the components is generated.
  • a compressor comprising: a cylinder fixed in a hermetic container and for forming a compression space; a compression member arranged in the compression space of the cylinder thus to be rotated and for sucking, compressing, and discharging fluid by varying a capacity of the compression space; a rotational shaft fixed by a driving force generating means and for transmitting a rotation force generated from the driving force generating means to the compression member; and bearing plates for supporting an axial load and a radial load of the rotational shaft, wherein, a space portion having predetermined volume is formed at a sliding part between the rotational shaft and the bearing plate where the axial load of the rotational shaft is supported, and a connection passage for connecting outside of the cylinder to the space portion in order to introduce discharged gas outside the cylinder into the space portion is formed.
  • Figure 1 is a longitudinal section view showing main parts of a compressor in accordance with the conventional art
  • Figure 2 is a perspective view showing the conventional compressor by
  • Figure 3 is a partial section view showing a compression unit of the conventional compressor by disassembling
  • Figure 4 is a partial section view showing a part where a surface pressure is applied between a bearing plate and a rotational shaft of the conventional compressor;
  • Figure 5 is a perspective view showing a compression unit of a
  • Figure 6 is a partial section view showing the compression unit of the compressor according to one embodiment of the present invention by disassembling
  • Figure 7 is a plane view showing an inner surface of a bearing plate of the compressor according to one embodiment of the present invention
  • Figure 8 is a plane view showing an inner surface of a bearing plate of the compressor according to one embodiment of the present invention
  • Figure 9 is a section view showing a part where a surface pressure is applied between the bearing plate and a rotational shaft of the compressor according to one embodiment of the present invention.
  • Figure 10 is a longitudinal section view showing a compressor according to another embodiment of the present invention.
  • Figure 11 is a longitudinal section view showing a compressor according to still another embodiment of the present invention.
  • FIG. 5 is a perspective view showing a compression unit of a compressor according to one embodiment of the present invention by partially cutting
  • Figure 6 is a partial section view showing the compression unit of the compressor according to one embodiment of the present invention by disassembling.
  • the compressor according to one embodiment of the present invention comprises: a hermetic container to which a suction pipe and a discharge pipe are connected; a driving force generating means arranged in the hermetic container for generating a rotation force; and a compression unit 14 arranged in the hermetic container for sucking, compressing, and discharging compressible fluid by the driving force generated from the driving force generating means.
  • fluid is sucked into the compression unit 14, compressed, and discharged in the hermetic container.
  • the fluid is discharged outside the hermetic container through the discharge pipe engaged to the hermetic container. Accordingly, if the compressor is operated, a predetermined pressure is always applied in the hermetic container by discharged gas.
  • the compression unit 14 comprises: a cylinder assembly 31 installed in the hermetic container and forming compression spaces V1 and V2 therein; a rotational shaft 20 connected to the driving force generating means thus for transmitting a driving force; a compression member 23 arranged in the cylinder assembly 31 by being fixed to a circumference of the rotational shaft 20 and having a cam surface of a predetermined curvature so that capacities of the compression spaces V1 and V2 can be changed at the time of rotation; and first
  • the cylinder assembly 31 comprises: a cylinder 30 formed as a cylindrical shape; and first and second bearing plates 40 and 50 fixed to both sides of the cylinder 30 thus to form a compression space with the cylinder 30.
  • the first and second bearing plates 40 and 50 are formed as a disc shape having a predetermined thickness and area, and comprises: journal portions 42 and 52 prolonged to have a predetermined height and an outer diameter and having a penetrated center for rotatably inserting the rotational shaft 20; and first and second vane slots 54 formed at one side of the journal portions 42 and 52 for slidably inserting the first and second vanes 60 and 70.
  • the rotational shaft 20 formed to have a predetermined outer diameter and a length comprises: a shaft portion 21 inserted into the journal portions 42 and 52 of the first and second bearing plates 60 and 70 and for supporting a radial load of the rotational shaft 20 on the journal portions 42 and 52 of the first and second bearings 60 and 70; and a supporting portion 22 integrally enlarged at a periphery of the shaft portion 21 thus for supporting an axial load of the rotational shaft 20 on inner surfaces of the first and second bearing plates 40 and 50, and engaged to the compression member 23 in the cylinder assembly 31.
  • the supporting portion 22 of the rotational shaft 20 is formed to be concentric with the shaft portion 21 of the rotational shaft 20 in a plane view.
  • the radial load of the rotational shaft 20 is supported on a radial bearing surface R in the journal portions 42 and 52 of the first and second bearing plates 40 and 50, and the axial load of the rotational shaft 20 is supported on a thrust bearing surface T of the inner surfaces of the first and second bearing plates 40 and 50.
  • a space portion 48 and 58 having a predetermined width and depth is formed at the thrust bearing surface T of the first and second bearing plates 40 and 50 in order to reduce a surface pressure between the thrust bearing surface T and the supporting portion 22 of the rotational shaft 20.
  • connection passages 49 and 59 for introducing discharged gas outside the cylinder assembly 31 into the space portions 48 and 58 and introducing lubrication oil outside the cylinder assembly 31 into the space portions 48 and 58 are respectively formed by penetrating the first and second bearing plates 40 and 50. That is, a part of the discharged gas outside the cylinder assembly 31 is introduced into the space portions 48 and 58 through the connection passages 49 and 59, so that a predetermined pressure is applied to the space portions 48 and 58. Also, since the pressure is applied in the opposite direction to that of the surface pressure applied to the thrust bearing surface T and the supporting portion 22, a size of the surface pressure applied to the thrust bearing surface T and the supporting portion 22 can be reduced.
  • lubrication oil which is outside the cylinder assembly 31 is introduced into the space portions 48 and 58 through the connection passages 49 and 59, and the introduced oil is supplied to a sliding part between the thrust bearing surface T and the supporting portion 22, so that friction of the sliding part between the thrust bearing surface T and the supporting portion 22 can be reduced. Therefore, as the surface pressure generated at the sliding part between the thrust bearing surface T and the supporting portion 22 is reduced and oil performs the lubrication operation, friction of the sliding part is reduced thus to reduce a frictional loss of the compressor and to reduce abrasion of the components in the compressor, thereby greatly enhancing a performance of the compressor.
  • the space portions 48 and 58 can be formed as a ring shape in a plane view, or as shown in Figure 8, the space portions 48 and 58 can be formed as a circular arc shape. Also, the space portions 48 and 58 are not limited to said ring shape or the circular arc shape, but can be formed as various shapes. In case that the space portions 48 and 58 are plural, it is preferable that the plurality of the space portions are formed with the same interval without being eccentric from the center of the rotational shaft 20, and it is preferable that they are formed symmetrically on the basis of the radial direction of the rotational shaft 20. Meanwhile, the connection passages 49 and 59 are preferably formed at the first and second bearing plates 40 and 50 by penetrating towards the shaft
  • connection passages 49 and 59 are equally formed from outside of the first and second plates 40 and 50 to the space portions 48 and 58.
  • the sectional areas of the connection passages can be increased towards the space portions 48 and 58 in order to smoothly introduce discharged gas and oil outside the cylinder assembly 31 into the space portions 48 and 58.
  • the compression member 23 is formed as a disc shape in a plane view so that an outer circumference surface thereof can have a sliding contact with an inner circumference surface of the cylinder 30, and formed as a cam shape of sine wave having the same thickness from the inner circumference surface to the outer circumference surface in a lateral projection view. According to this, a side having an upper dead point slidably contacts with a lower surface of the first bearing plate 40, and a side having a lower dead point slidably contacts with an upper surface of the second bearing plate 50.
  • the first and second vanes 60 and 70 are formed as a rectangular plate shape and adhere to the cam surface of the compression member 23 in the compression space of the cylinder assembly 31.
  • the vanes reciprocate up and down along a height of the cam surface of the compression member 23 when the compression member 23 is rotated, and thus divide the compression spaces V1 and V2 into suction regions and compression regions. Operations and effects of the compressor according to the first embodiment of the present invention will be explained as follows.
  • the first space V1 located at an upper portion of the compression member 23 is divided into the suction region and the compression region on the basis of the upper dead point of the compression member 23 and the first vane 60.
  • the second space V2 located at a lower portion of the compression member 23 is divided into the suction region and the compression region on the basis of the lower dead point and the second vane 70.
  • first and second vanes 60 and 70 reciprocate towards different directions along the height of the cam surface of the compression member 23.
  • the fluid discharged outside the cylinder assembly 31 passes inside of the hermetic container and is discharged outside the hermetic container through the discharge pipe.
  • the rotational shaft 20 rotates by being inserted into the journal portions 42 and 52 of the first and second bearing plates 40 and 50.
  • the shaft portion 21 of the rotational shaft 20 is rotated by being supported on the radial bearing surface R of the first and second bearing plates 40 and 50, and both sides of the supporting portion 22 of the rotational shaft 20 are rotated by being supported on the thrust bearing surface T of the first and second bearing plates 40 and 50.
  • a predetermined surface pressure is applied to said both sides of the supporting portion 22 of the rotational shaft 20 which is opposite to the area of the thrust bearing surface T.
  • Figure 10 is a longitudinal section view showing a compressor according to another embodiment of the present invention.
  • connection passages 149 and 159 is formed by penetrating the first and second bearing plates 40 and 50 in order to connect the space portion 120 of the supporting portion 22 to the outside of the cylinder assembly 31.
  • Figure 11 is a longitudinal section view showing a compressor according to still another embodiment of the present invention.
  • first space portions 248 and 258 are formed at the thrust bearing surface T in order to reduce the surface pressure generated between the thrust bearing surface T of the first and second bearing plates 40 and 50 and the supporting portion 22 of the rotational shaft 20, and a second space portion 220 is formed at the supporting portion 22 of the rotational shaft 20.
  • connection passages 249 and 259 are formed by penetrating the first and second bearing plates 40 and 50 in order to connect the first space portions 248 and 258 and the second space portion 220 to the outside of the cylinder assembly 31.
  • first and second bearing plates 40 and 50 or thickness of the supporting portion 22 of the rotational shaft 20 was considered when the space portions 48, 58, and 120 are formed.
  • first space portions 248 and 258 and the second space portion 220 which reduce the surface pressure are respectively formed at the supporting portion 22 of the rotational shaft 20, so that volumes of the first and second space portions 248, 258, and 220 can be increased.
  • the space portions having a predetermined volume are formed at the sliding part between the thrust bearing surface and the supporting portion of the bearing plates where the axial load of the rotational shaft is rotatably supported, and the connection passage for connecting the space portions to the outside of the cylinder assembly is provided. According to this, the surface pressure applied to the sliding part is reduced thus to reduce the frictional loss and abrasion of the components, thereby enhancing a performance of the compressor.

Landscapes

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

Abstract

L'invention concerne un compresseur renfermant, d'une part, un espace de volume prédéterminé, situé au niveau d'une partie coulissante, entre une surface de butée (T) de plaques d'appui (40, 50) et une partie de support (22) servant à supporter la charge axiale d'un arbre rotatif (20), et, d'autre part, un passage servant à relier cet espace à l'extérieur d'un ensemble de cylindre. Ces caractéristiques permettent de réduire la pression en surface appliquée sur la partie coulissante et de réduire les pertes par frottement et l'usure des composantes, ce qui par conséquent augmente les performances du compresseur.
PCT/KR2003/001469 2002-10-25 2003-07-23 Compresseur WO2004038225A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2003250560A AU2003250560A1 (en) 2002-10-25 2003-07-23 Compressor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR10-2002-0065574 2002-10-25
KR1020020065574A KR20040036973A (ko) 2002-10-25 2002-10-25 밀폐형 압축기의 면압 저감 장치

Publications (1)

Publication Number Publication Date
WO2004038225A1 true WO2004038225A1 (fr) 2004-05-06

Family

ID=32171527

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/KR2003/001469 WO2004038225A1 (fr) 2002-10-25 2003-07-23 Compresseur

Country Status (3)

Country Link
KR (1) KR20040036973A (fr)
AU (1) AU2003250560A1 (fr)
WO (1) WO2004038225A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104454529A (zh) * 2014-12-04 2015-03-25 广东美芝制冷设备有限公司 用于旋转式压缩机的压缩机构和具有其的旋转式压缩机
CN104454530A (zh) * 2014-12-04 2015-03-25 广东美芝制冷设备有限公司 用于旋转式压缩机的压缩机构和具有其的旋转式压缩机
CN112727736A (zh) * 2020-12-29 2021-04-30 珠海格力电器股份有限公司 泵体组件和流体机械

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20040036978A (ko) * 2002-10-25 2004-05-04 엘지전자 주식회사 밀폐형 압축기의 면압 저감 장치

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09177683A (ja) * 1995-12-27 1997-07-11 Daikin Ind Ltd スクロール形流体機械
EP1211421A2 (fr) * 2000-12-01 2002-06-05 Delphi Technologies, Inc. Pompe rotative à actionnement hydraulique de palette
JP2002174190A (ja) * 2000-12-05 2002-06-21 Seiko Instruments Inc 気体圧縮機

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH1089266A (ja) * 1996-09-17 1998-04-07 Toyoda Mach Works Ltd ベーンポンプ
JP3942806B2 (ja) * 1999-08-27 2007-07-11 ユニシア ジェーケーシー ステアリングシステム株式会社 可変容量形ポンプ
KR20010105814A (ko) * 2000-05-18 2001-11-29 구자홍 압축기
KR20010105816A (ko) * 2000-05-18 2001-11-29 구자홍 압축기의 소음 저감구조

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09177683A (ja) * 1995-12-27 1997-07-11 Daikin Ind Ltd スクロール形流体機械
EP1211421A2 (fr) * 2000-12-01 2002-06-05 Delphi Technologies, Inc. Pompe rotative à actionnement hydraulique de palette
JP2002174190A (ja) * 2000-12-05 2002-06-21 Seiko Instruments Inc 気体圧縮機

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104454529A (zh) * 2014-12-04 2015-03-25 广东美芝制冷设备有限公司 用于旋转式压缩机的压缩机构和具有其的旋转式压缩机
CN104454530A (zh) * 2014-12-04 2015-03-25 广东美芝制冷设备有限公司 用于旋转式压缩机的压缩机构和具有其的旋转式压缩机
CN112727736A (zh) * 2020-12-29 2021-04-30 珠海格力电器股份有限公司 泵体组件和流体机械
CN112727736B (zh) * 2020-12-29 2022-02-11 珠海格力电器股份有限公司 泵体组件和流体机械

Also Published As

Publication number Publication date
AU2003250560A1 (en) 2004-05-13
KR20040036973A (ko) 2004-05-04

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