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US20030170134A1 - Compressor and vane therefor - Google Patents

Compressor and vane therefor Download PDF

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Publication number
US20030170134A1
US20030170134A1 US10/380,039 US38003903A US2003170134A1 US 20030170134 A1 US20030170134 A1 US 20030170134A1 US 38003903 A US38003903 A US 38003903A US 2003170134 A1 US2003170134 A1 US 2003170134A1
Authority
US
United States
Prior art keywords
vane
cylinder assembly
oil
compressor
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.)
Abandoned
Application number
US10/380,039
Other languages
English (en)
Inventor
Young-Jong Kim
Jae-Sool Shim
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.)
LG Electronics Inc
Original Assignee
Individual
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 Individual filed Critical Individual
Assigned to LG ELECTRONICS INC. reassignment LG ELECTRONICS INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KIM, YOUNG-JONG, SHIM, JAE-SOOL
Publication of US20030170134A1 publication Critical patent/US20030170134A1/en
Abandoned 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • 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
    • 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

Definitions

  • the present invention relates to a compressor, and more particularly, to a compressor and a vane therefor, capable of reducing noise by minimizing friction and improving performance by reducing friction resistance.
  • a compressor is a device for converting mechanical energy into compression energy of compressible fluid
  • a refrigerating compressor is largely classified into a reciprocation compressor, a scroll compressor, a centrifugal compressor, and a rotary compressor by compression methods.
  • FIG. 1 is a longitudinal sectional view showing a main part of a Z-compressor in accordance with the conventional art
  • FIG. 2 is a perspective view showing a partially cut compression part in the Z-compressor in accordance with the conventional art
  • FIG. 3 is a plan view showing a Z-compressor in accordance with the conventional art.
  • the Z-compressor is a compressor which can be classified as a rotary compressor and it includes a hermetic vessel 10 , a motor part 12 which is disposed in the hermetic vessel 10 , for generating a rotational force and a compression part 14 for sucking, compressing and discharging gas by the rotational force generated by the motor part 12 .
  • the motor part 12 includes a stator 16 and rotor 18 as a conventional motor.
  • the compression part 14 includes a cylinder assembly 31 for forming a compression space V which is fixed inside the hermetic vessel 10 being fixed to the inside of the hermetic vessel 10 , a rotational shaft 20 for transmitting a rotational force generated by the rotor 18 of the motor part 12 , a Z-plate 23 which rotates being coupled with the rotational shaft 20 and dividing the compression space V of the cylinder assembly 31 into first and second spaces V 1 and V 2 simultaneously, and first and second vanes 60 and 70 which are respectively contacted with the upper and lower surfaces of the Z-plate 23 and divide the first and second spaces V 1 and V 2 into suction regions V 1 a and V 2 a and compression regions V 1 b and V 2 b respectively when the Z-plate 23 rotates.
  • the cylinder assembly 31 includes a cylinder 30 which is formed in a cylindrical shape, and first and second bearing plates 40 and 50 which are fixed at both sides of the cylinder 30 , for forming the compression space V.
  • the first and second bearing plates 40 and 50 are formed in a shape of circular plate having a predetermined thickness and area.
  • the first and second bearing plates 40 and 50 include journal portions 42 and 52 which are extended and protruded to have a predetermined height and outer diameter at the center and in which the rotational shaft 20 is inserted rotatably, first and second vane slots 44 and 54 in which the first and second vanes 60 and 70 are inserted at a side of the journal portions 42 and 52 for guiding the first and second vane so that they can perform a reciprocating movement, and a discharge flow path 90 respectively formed at the side of the first and second vane slots 44 and 54 , through which compressed gas is discharged.
  • the first and second vane slots 44 and 54 are formed in a shape of a square hole which is perforated through the first and second bearing plates 40 and 50 corresponding to the sizes of the first and second vanes 60 and 70 from the outer circumference of the first and second bearing plates 40 and 50 which are formed in the shape of a circular plate.
  • the rotational shaft 20 includes a shaft portion 21 which is formed to have a predetermined outer diameter and length and inserted in the journal portions 42 and 52 of the first and second bearing plates 40 and 50 , a hub portion 22 which is extended and formed at a side of the shaft portion 21 and coupled with the Z-plate 23 and further includes an oil flow path 25 which is bored inside of the shaft portion 21 and through which oil passes.
  • an oil feeder 24 for supplying oil filled at the lower side of the hermetic vessel 10 to the upper side of the hermetic vessel 10 is installed in the lower end of the oil flow path 25 .
  • the Z-plate 23 is formed in the shape of the circular plate to slide being contacted on the inner circumferential surface of the cylinder 30 , and formed as a cam surface of a sinuous wave curve having an identical thickness from the inner circumferential surface to the outer circumferential surface in the view of projecting a side surface. Accordingly, a surface which forms a upper dead point D 1 rotates under the condition that it is contacted with the lower surface of the first bearing plate 40 , and a surface which forms a lower dead point D 2 rotates under the condition that it is contacted with the upper surface of the second bearing plate 50 .
  • the first and second vanes 60 and 70 are formed in a shape of a square plate and formed to be cohered on the sine wave curve of the Z-plate 23 in the compression space V of the cylinder assembly 31 .
  • Z-plate contact portions 62 and 72 of a rounding shape which contact with the waveform surface of the Z-plate 23 are formed on a side surface of the vane bodies 61 and 71 which are formed in a square shape having a predetermined thickness.
  • outer surface portions 63 and 73 which are convexly formed to be contacted with the inner wall of the cylinder assembly 31
  • inner surface portions 64 and 74 which are concavely formed to be contacted with the outer circumferential surface of the hub portion 22 of the rotational shaft 20 are formed.
  • Such vanes 60 and 70 divides the compression spaces V 1 and V 2 into suction regions V 1 a and V 2 a , and compression region V 1 b and V 2 b performing a reciprocating movement in the upward and downward directions according to the height of the cam surface of the Z-plate 23 when the Z-plate 23 rotates in the compression spaces V 1 and V 2 of the cylinder assembly 31 .
  • reference numeral 35 designates a suction flow path through which gas is sucked into the hermetic vessel and cylinder
  • reference numerals 45 and 55 designate discharge mufflers for reducing discharging noise.
  • the first space V 1 which is positioned in the upper portion of the Z-plate 23 is divided into the suction region V 1 a and compression region V 1 b having the upper dead point D 1 of the Z-plate 23 and the first vane 60 as the border
  • the second space V 2 which is positioned in the lower portion of the Z-plate 23 is divided into the suction region V 2 a and compression region V 2 b having the lower dead point D 2 of the Z-plate 23 and the second vane 70 as the border.
  • the Z-plate 23 rotates and accordingly the upper and lower dead points D 1 and D 2 of the Z-plate 23 , thus to vary volumes of the suction regions V 1 a and V 2 a , and compression regions V 1 b and V 2 b of respective spaces.
  • the first vane 60 and second vane 70 perform a reciprocal movement in different directions according to the height of the cam surface of the Z-plate 23 .
  • the compressed gas is simultaneously discharged to the outside of the cylinder assembly 31 through the discharge flow paths 90 of the respective compression spaces V 1 and V 2 at the moment when the upper and lower dead points D 1 and D 2 of the Z-plate 23 reach the discharge starting point. Then, the gas passes the respective discharge mufflers 45 and 55 inside of the hermetic vessel 10 and discharged into the outside through the discharge tube (not shown).
  • Such friction generally occurs inside of the cylinder assembly, and sliding portion such as portions between the vane and Z-plate, between the vane and vane slot, between the Z-plate and the bearing plate, and the like.
  • an object of the present invention is to provide a Z-compressor, capable of improving performance of a compressor and reducing losses caused by abrasion of parts by reducing friction by supplying oil to sliding portions such as between the vane and vane slot, between the vane and Z-plate, between the upper and lower dead points of the Z-plate and the bearing plate, by forming an oil slot in the vane and flowing oil into the cylinder assembly through the oil slot.
  • a compressor including a cylinder assembly which is positioned inside a hermetic vessel having a suction flow path and discharging flow path, a Z-plate for dividing an inner space into a plurality of compression spaces in the cylinder assembly, rotating by a motor part so that gas is sucked, compressed and discharged, and a vane for dividing the respective compression spaces into a suction region and compression region, performing a reciprocating movement being contacted on both surfaces of the Z-plate.
  • an oil slot for flowing oil to the cylinder assembly is formed on a side surface of the vane.
  • FIG. 1 is a longitudinal sectional view showing a main part of a Z-compressor in accordance with the conventional art
  • FIG. 2 is a perspective view showing a partially cut compression part in the Z-compressor in accordance with the conventional art
  • FIG. 3 is a plan view showing a Z-compressor in accordance with the conventional art
  • FIG. 4 is a longitudinal sectional view showing a main part of a Z-compressor in accordance with the present invention.
  • FIG. 5 is a perspective view showing a partially cut compression part in the compressor in which a vane of the Z-compressor in accordance with the present invention is built;
  • FIG. 6 is a plan view showing a compression part of the Z-compressor in accordance with the present invention.
  • FIG. 7 is a graph illustrating change of position of an oil slot according to the change of position of the vane of the Z-compressor in accordance with the present invention.
  • FIG. 8A is a graph comparing input voltages of the Z-compressors in accordance with the conventional art and the present invention.
  • FIG. 8B is a graph comparing performance of the Z-compressors in accordance with the conventional art and the present invention.
  • FIGS. 4 to 6 A vane structure of a Z-compressor in accordance with the present invention will be described with reference to FIGS. 4 to 6 .
  • FIG. 4 is a longitudinal sectional view showing a main part of a Z-compressor in accordance with the present invention
  • FIG. 5 is a perspective view showing a partially cut compression part in the compressor in which a vane of the Z-compressor in accordance with the present invention is built
  • FIG. 6 is a plan view showing a the compression part of the Z-compressor in accordance with the present invention.
  • the Z-compressor in accordance with the present invention generally includes a hermetic vessel 110 , a motor part 112 which is disposed in the hermetic vessel 110 , for generating a rotational force, and a compression part 114 for sucking, compressing and discharging gas by the rotational force generated in the motor part 112 .
  • hermetic vessel 110 a predetermined amount of oil for lubricating a sliding part inside the hermetic vessel 110 is filled in the lower of the hermetic vessel 110 .
  • the motor part 112 is composed of a stator 116 and rotor 118 .
  • the compression part 114 includes a cylinder assembly 131 which is fixed at the lower part of the hermetic vessel 110 , for forming a compression space V in which sucked gas is compressed, a rotational shaft 120 which is connected with the rotor 118 of the motor part 112 , for transmitting a rotational force, a Z-plate 123 which is coupled with the rotational shaft 120 inside, the cylinder assembly 131 , for dividing the compression space V into a first space V 1 and second space V 2 , and the first and second vanes 160 and 170 which are respectively connected with the upper and lower surfaces of the Z-plate 123 , for dividing the first and second spaces V 1 and V 2 into suction regions V 1 a and V 2 a and compression regions V 1 b and V 2 b when the Z-plate 123 rotates.
  • the cylinder assembly 131 includes a cylinder 130 in the cylindrical shape and first and second bearing plates 140 and 150 which are fixed on both sides of the cylinder 130 , for forming a compression space V together with the cylinder 130 .
  • the first and second bearing plates 140 and 150 are formed in a shape of circular plate having a predetermined thickness and area.
  • the first and second bearing plates 140 and 150 include journal portions 142 and 152 which are extended and protruded to have a predetermined height and outer diameter at the center of the first and second bearing plates 140 and 150 and in which the rotational shaft 120 is inserted rotatably, first and second vane slots 144 and 154 in which the first and second vanes 160 and 170 are inserted at a side of the journal portions 142 and 152 for guiding the first and second vanes 160 and 170 so that they can perform a reciprocating movement, and a discharged flow path 190 respectively formed at the side of the first and second vane slots 144 and 154 , through which compressed gas is discharged.
  • the rotational shaft 120 includes a shaft portion 121 which is formed to have a predetermined outer diameter and length and is inserted in the journal portions 142 and 152 of the first and second bearing plates 140 and 150 , a hub portion 122 which is extended, formed at a side of the shaft portion 121 and coupled with the Z-plate 123 , and an oil flow path 125 which penetrates inside the shaft portion 121 .
  • an oil feeder 124 for supplying the oil filled in the lower of the hermetic vessel 110 to the upper portion is built.
  • the Z-plate 123 is formed in a shape of a circular plate in projecting a plane so that the outer circumferential surface is contacted sliding on the inner circumferential surface and formed as a cam surface of a sinuous wave curve having an identical thickness from the inner circumferential surface to the outer circumferential surface in view of projecting side surface. Accordingly, a surface which forms the upper dead point D 1 is contacted on the lower surface of the first bearing plate 140 and rotates, and a surface which forms the lower dead point D 2 is cohered on the upper surface of the second bearing plate 150 and rotates.
  • the first and second vanes 160 and 170 are formed in a square plate shape and formed to be cohered with the sinuous wave surface of the Z-plate 123 in the compression space V of the cylinder assembly 131 .
  • Z-plate contact portions 162 and 172 formed in a rounding shape being contacted on the wave form surface of the Z-plate 123 are formed on a side surface of the vane bodies 161 and 171 in the square shape having a predetermined thickness.
  • outer surface portions 163 and 173 which are convexly formed to be contacted on the inner wall of the inner space V of the cylinder assembly 131 , and an inner surface portion 164 which is concavely formed to be contacted on the outer circumferential surface of the rotational shaft 120 .
  • Such first and second vanes 160 and 170 are guided to the first and second vane slots 144 and 154 when the Z-plate 123 rotates in the compression space V 1 and V 2 of the cylinder assembly 131 and divides the compression space V 1 and V 2 into suction regions V 1 a and V 2 a , and compression spaces V 1 b and V 2 b , performing a reciprocating movement in the upward and downward directions according to the height of the cam surface of the Z-plate 123 .
  • oil slots 165 and 175 for flowing the oil positioned outside the cylinder assembly 131 into the compression space inside the cylinder assembly 131 are formed.
  • a plural number of the oil slots 165 and 175 are formed at an equal interval having a predetermined width and depth.
  • the oil slots 165 and 175 are formed in a direction that the first and second vanes moves to efficiently flowing the oil into the cylinder assembly 131 as the vanes 160 and 170 move.
  • FIG. 7 is a graph illustrating height of the vane which moves along the wave form surface in the upward and downward directions and change of position of an oil slot when the Z-plate rotates, as the angle of the wave form surface of the Z-plate.
  • suction regions V 1 a and V 2 a are positioned at the left side of the vanes 160 and 170 and the compression regions V 1 b and V 2 b in which gas is compressed is positioned at the right side of the vane.
  • the oil slots 165 and 175 are formed on a surface of the first and second vanes 160 and 170 which is positioned in the suction regions V 1 a and V 2 a inside the compression space V.
  • the oil slot 165 and 175 are formed to having a predetermined length from the outward direction to the inward direction of the cylinder assembly 131 so to connect the outer space and inner space of the cylinder assembly 131 when the vane is contacted on the Z-plate 123 and positioned near from the lower dead point.
  • the oil slots 165 and 175 are formed in a predetermined length.
  • the vanes 160 and 170 move into the cylinder 131 by rotation of the Z-plate 123 , since the position of the oil slots 165 and 175 is changed toward the cylinder assembly 131 , the outer and inner sides of the cylinder assembly 131 are gradually communicated each other.
  • the first and second vanes 160 and 170 are moved to the outside of the cylinder assembly 131 , the position of the oil slots 165 and 175 is gradually changed toward the outside of the cylinder assembly 131 , thus to block the outer and inner sides of the cylinder assembly 131 .
  • reference numeral 135 designates a suction flow path that the gas is sucked into the hermetic vessel and cylinder
  • reference numerals 145 and 155 designate discharge mufflers which reduce discharge noise.
  • the first and second vanes 160 and 170 which are vertically and radially positioned of the Z-plate 123 is elastically supported by an elastic supporting means 180 and perform an upward and downward linear reciprocal movement along the wave form surface of the Z-plate 123 as being guided to the first and second vane slots 144 and 154 .
  • the oil filled in the lower of the hermetic vessel 110 is sucked upwardly by the oil feeder 124 which is installed in the oil flow path 125 at the lower end of the rotational shaft 120 and flown away in the upper end of the rotational shaft 120 .
  • the oil is flowed into the cylinder assembly 131 through the oil slots 165 and 175 which communicate the inner and outer sides of the cylinder assembly 131 when the first and second vanes 160 and 170 move into the cylinder assembly 131 , and the oil flowed into the cylinder assembly 131 is supplied to sliding portions between the first and second vanes 160 and 170 and the Z-plate, and between the upper or lower dead point D 1 or D 2 of the Z-plate 123 and the first and second bearing plates 140 and 150 , thus to perform lubricating action and minimize friction resistance of such sliding portions.
  • FIG. 8A is a graph comparing input voltages of the Z-compressors in accordance with the conventional art and the present invention
  • FIG. 8B is a graph comparing performance of the Z-compressors in accordance with the conventional art and the present invention
  • FIG. 9 is a graph comparing generated noise of the Z-compressors in accordance with the conventional art and the present invention.
  • the performance of the Z-compressor in accordance with the present invention shows an improvement effect of 40.1% when related with the performance of the conventional art.
  • the occurred noise of the Z-compressor in accordance with the present invention when related with the conventional one is reduced from 69 dB to 64 dB.
  • the vane structure of the Z-compressor in accordance with the present invention can reduce friction between the vane and Z-plate, and the upper and lower dead points and bearing plate as the oil slot for flowing oil to the cylinder assembly at a side of the vane, thus to reduce noise and improve performance of the compressor.
  • the oil slot is formed on a side surface of the vane and has the oil flow into the cylinder assembly.
  • performance deterioration of the compression caused by operation noise and friction resistance can be prevented and wearing of the parts can be prevented by reducing friction in the sliding portion inside the cylinder assembly.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
US10/380,039 2001-12-28 2002-12-06 Compressor and vane therefor Abandoned US20030170134A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR10-2001-0087404A KR100414294B1 (ko) 2001-12-28 2001-12-28 압축기의 베인 구조
KR87404/2001 2001-12-28

Publications (1)

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US20030170134A1 true US20030170134A1 (en) 2003-09-11

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ID=19717844

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US10/380,039 Abandoned US20030170134A1 (en) 2001-12-28 2002-12-06 Compressor and vane therefor

Country Status (4)

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US (1) US20030170134A1 (fr)
KR (1) KR100414294B1 (fr)
AU (1) AU2002367051A1 (fr)
WO (1) WO2003060326A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102032185A (zh) * 2009-09-30 2011-04-27 三洋电机株式会社 旋转式空气压缩机
JPWO2017061014A1 (ja) * 2015-10-08 2018-04-26 三菱電機株式会社 ロータリー圧縮機

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
TWI363140B (en) * 2004-09-30 2012-05-01 Sanyo Electric Co Compressor
EP1643128A3 (fr) * 2004-09-30 2011-12-14 Sanyo Electric Co., Ltd. Compresseur
EP1647715A3 (fr) * 2004-09-30 2011-12-07 Sanyo Electric Co., Ltd. Compresseur
KR100679884B1 (ko) * 2004-10-06 2007-02-08 엘지전자 주식회사 누설방지 기능을 갖는 선회베인 압축기용 리니어 슬라이더
KR100679667B1 (ko) * 2005-12-16 2007-02-07 현경열 회전형 2단 압축기

Citations (5)

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Publication number Priority date Publication date Assignee Title
US848446A (en) * 1904-12-10 1907-03-26 Gilmer Crowell Lubricating system.
US1530973A (en) * 1923-12-22 1925-03-24 American Mach & Foundry Vacuum pump
US1690728A (en) * 1927-06-16 1928-11-06 Joseph F Jaworowski Rotary pump
US3111820A (en) * 1961-11-06 1963-11-26 Gen Electric Rotary compressor injection cooling arrangement
US4093408A (en) * 1976-12-03 1978-06-06 Yoshichika Yamaguchi Positive cam type compressor

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JPS57206788A (en) * 1981-06-15 1982-12-18 Mitsubishi Heavy Ind Ltd Sliding-vane type rotary compressor
JPS61145388A (ja) * 1984-12-19 1986-07-03 Hitachi Ltd ロ−タリ圧縮機
DE3532917C2 (de) * 1985-03-01 1994-03-10 Barmag Barmer Maschf Flügelzellenpumpe
KR880002665Y1 (ko) * 1985-06-24 1988-07-23 서건석 알미늄 스크린 압력조절 인쇄판
JPS6385282A (ja) * 1986-09-29 1988-04-15 Toshiba Corp ロ−タリコンプレツサの潤滑装置
KR900003833Y1 (ko) * 1987-11-30 1990-05-01 주식회사 금성사 로타리식 밀폐형 압축기의 베인 구조
JPH06264881A (ja) * 1993-03-12 1994-09-20 Hitachi Ltd ロータリ圧縮機
KR950019478U (ko) * 1993-12-13 1995-07-24 밀폐형 압축기의 베인 구조
JPH08159071A (ja) * 1994-12-02 1996-06-18 Matsushita Refrig Co Ltd 回転式圧縮機
KR100315954B1 (ko) * 1999-10-01 2001-12-12 구자홍 압축기

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US848446A (en) * 1904-12-10 1907-03-26 Gilmer Crowell Lubricating system.
US1530973A (en) * 1923-12-22 1925-03-24 American Mach & Foundry Vacuum pump
US1690728A (en) * 1927-06-16 1928-11-06 Joseph F Jaworowski Rotary pump
US3111820A (en) * 1961-11-06 1963-11-26 Gen Electric Rotary compressor injection cooling arrangement
US4093408A (en) * 1976-12-03 1978-06-06 Yoshichika Yamaguchi Positive cam type compressor

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102032185A (zh) * 2009-09-30 2011-04-27 三洋电机株式会社 旋转式空气压缩机
JPWO2017061014A1 (ja) * 2015-10-08 2018-04-26 三菱電機株式会社 ロータリー圧縮機

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Publication number Publication date
KR100414294B1 (ko) 2004-01-07
WO2003060326A1 (fr) 2003-07-24
AU2002367051A1 (en) 2003-07-30
KR20030057032A (ko) 2003-07-04

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