EP0373876A2 - Compresseur de réfrigération du type à volutes hermétiquement étanche - Google Patents

Compresseur de réfrigération du type à volutes hermétiquement étanche Download PDF

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Publication number
EP0373876A2
EP0373876A2 EP89312960A EP89312960A EP0373876A2 EP 0373876 A2 EP0373876 A2 EP 0373876A2 EP 89312960 A EP89312960 A EP 89312960A EP 89312960 A EP89312960 A EP 89312960A EP 0373876 A2 EP0373876 A2 EP 0373876A2
Authority
EP
European Patent Office
Prior art keywords
end plate
isolated cavity
orbiting scroll
scroll
cavity
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
EP89312960A
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German (de)
English (en)
Other versions
EP0373876B1 (fr
EP0373876A3 (en
Inventor
Kazuto Kikuchi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sanden Corp
Original Assignee
Sanden Corp
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Filing date
Publication date
Application filed by Sanden Corp filed Critical Sanden Corp
Publication of EP0373876A2 publication Critical patent/EP0373876A2/fr
Publication of EP0373876A3 publication Critical patent/EP0373876A3/en
Application granted granted Critical
Publication of EP0373876B1 publication Critical patent/EP0373876B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid

Definitions

  • This invention relates to a hermetically sealed scroll type compressor, and more particularly, to a sealing mechanism disposed within an isolated cavity in a compressor housing for insulating the isolated cavity from discharge pressure in a compressor inner housing.
  • Hermetically sealed housing 200 includes inner chamber 210 which is maintained at discharge pressure.
  • the compression mechanism including inner fitting scrolls 220, 230 and the upward end of the drive mechanism including drive shaft 240, are disposed between partition 250 and the end plate of stationary scroll 220, and are isolated from inner chamber 210.
  • Drive shaft 240 is rotatably and closely supported by partition 250 through fixed plain bearing 251.
  • a plurality of fluid pockets 300 are formed between the spiral portions of inner fitting scrolls 220 and 230.
  • Channel 260 extends through the end plate of orbiting scroll 230 and links intermediate fluid pocket 301 with isolated chamber 270 formed between the end plate of orbiting scroll 230 and partition 250.
  • refrigerant gas flows through inlet port 260 and is compressed inwardly by scrolls 220 and 230 towards central fluid pocket 302 due to orbital motion of orbiting scroll 230.
  • Compressed fluid in central fluid pocket 302 is discharged into discharge chamber 211 through hole 221 extending through the end plate of stationary scroll 220.
  • Compressed refrigerant gas flows discharge chamber 211 into inner chamber 210 through cavity 210a, and thereafter flows out of the compressor to the external fluid circuit through outlet port (not shown). After circulating through the refrigerating system, the refrigerant gas which exits through the outlet port returns to the compressor.
  • channel 260 extends through the end plate of orbiting scroll 230 and links intermediate fluid pocket 301 with isolated chamber 270.
  • isolated chamber 270 is maintained at intermediate pressure which generates the appropriate upwardly axial urging force acting or orbiting scroll 230. Accordingly, the axial seal of fluid pockets 300 can be well done without generation of the excessive friction between the spiral portion and the end plate of scrolls 220 and 230.
  • a hermetically sealed scroll type compressor as another prior art of this invention was imagined by an inventor of this invention.
  • the imagined compressor comprises an isolated chamber formed between a stationary scroll and a partition both which are substantially identical to stationary scroll 220 and partition 250 in Figure 3, respectively.
  • the isolated chamber is maintained suction pressure due to suction pressure refrigerant gas being conducted thereinto from an external refrigeration circuit through a pipe member.
  • slight air gaps are created between a drive shaft and a fixed plain bearing as well as the above mentioned prior art. This may allow leakage of discharge refrigerant gas from an inner chamber, which is substantially identical to inner chamber 210 in Figure 3, into the isolated chamber, thereby causing increase of pressure in the isolated chamber, that is, causing a rise in temperature of suction refrigerant gas.
  • the defects of the compressor such as, a decline of compression efficiency and an excessive rise in temperature of discharged refrigerant gas may be occurred.
  • a compressor according to the present invention includes a fixed scroll and an orbiting scroll disposed within a hermetically sealed housing.
  • the fixed scroll includes a first end plate from which a first wrap or spiral element extends into the interior of the housing.
  • the orbiting scroll includes a second end plate from which a second spiral element extends.
  • the first and second spiral elements interfit at an angular and radial offset to form a plurality of line contacts which define at least one pair of sealed off fluid pockets therebetween.
  • An inner block member is fixedly secured within the compressor housing.
  • the first end plate of the fixed scroll is in contact with an annular upward extension of the inner block member to define an isolated cavity therebetween.
  • the discharge chamber is formed upward of the first end plate.
  • the remainder of the compressor housing which is exterior to the isolated cavity is linked to the discharge chamber.
  • a drive mechanism is operatively connected to the orbiting scroll to effect orbital motion thereof.
  • the drive mechanism includes a drive shaft rotatably supported by a fixed plain bearing within an axially downward extension of the inner block member.
  • a rotation preventing device prevents rotation of the orbiting scroll during orbital motion so that rotation of the drive shaft creates orbital motion of the orbiting scroll.
  • the volume of the fluid pockets is progressively decreased to compress refrigerant gas in the pockets inwardly from outermost pockets toward a central pocket.
  • the compressed gas in the central pocket flows through a channel formed in the first end plate of the fixed scroll and into the discharge chamber.
  • the second end plate of the orbiting scroll divides the isolated cavity into a first and second isolated cavities.
  • the first and second spiral elements are disposed in the first isolated cavity.
  • a communication path is axially formed through the second end plate of the orbiting scroll to introduce intermediately compressed refrigerant gas from an intermediately located fluid pocket into the second isolated cavity.
  • the first isolated cavity is provided with an inlet portion which introduces suction refrigerant gas thereinto from an external refrigeration circuit.
  • the remainder of the compressor housing is provided with an outlet portion which conducts the discharged refrigerant gas to the external refrigeration circuit from the remainder of the compressor housing.
  • a shaft seal mechanism is mounted around the drive shaft at a location within the second isolated cavity to insulate the second isolated cavity from the discharge pressure in the remainder of the compressor housing.
  • the isolated cavity is provided with an inlet portion which introduces suction refrigerant gas thereinto from an external refrigeration circuit.
  • the remainder of the compressor housing is provided with an outlet portion which conducts discharged refrigerant gas to the external refrigeration circuit from the remainder of the compressor housing.
  • a shaft seal mechanism is mounted around the drive shaft at a location within the isolated cavity to insulate the isolated cavity from discharge pressure in the remainder of the compressor housing.
  • a hermetically sealed scroll type compressor in accordance with one embodiment of the present invention is shown.
  • the compressor is designed to locate an axis of a drive shaft generally perpendicular to a horizontal plane, when installed. Accordingly, in general, the compressor is called a vertically installed type compressor.
  • the compressor includes hermetically sealed casing 10 comprising cylindrical portion 11 and a pair of shallow cup-shaped portions 12 and 13 hermetically fixed to the both opening ends of cylindrical portion 11, fixed and orbiting scrolls 20 and 30, inner block member 40 and motor 50.
  • Fixed scroll 20 includes circular end plate 21 and spiral element or wrap 22 extending downwardly from one end surface of circular end plate 21.
  • Circular end plate 21 is provided with annular wall 211 downwardly projecting from the one end surface thereof at an outermost peripheral location.
  • Orbiting scroll 30 includes circular end plate 31 and spiral element or wrap 32 extending upwardly from one end surface of circular end plate 31.
  • Spiral element 22 of fixed scroll 20 and spiral element 32 of orbiting scroll 30 interfit an an angular and radial offset to form a plurality of line contacts which define at least one pair of sealed off fluid pockets 71 therebetween.
  • Annular projection 33 projects axially from the other end surface of circular end plate 31.
  • Inner block member 40 is firmly secured at an inner peripheral surface of cylindrical portion 11 by forcible insertion.
  • Inner block member 40 includes central portion 43 and axial annular wall 41 upwardly projecting from central portion 43 at a peripheral location.
  • Axially annular projection 42 projects downwardly from central portion 43 at a central location.
  • the upward end surface of axial annular wall 41 is fixed by a plurality of screws 26 to the downward end surface of annular wall 211 through O-ring seal element 401.
  • Isolated cavity 70 is thereby created between annular wall 41 of inner block member 40, and fixed scroll 20.
  • Orbiting scroll 30 is disposed entirely within isolated cavity 70.
  • interior chamber 61 is created between inner block member 40, and cylindrical portion 11 and shallow cup-shaped portion 13.
  • Motor 50 includes stator 51 which is firmly secured at the inner peripheral surface of cylindrical portion 11 by forcible insertion.
  • Rotor 52 of motor 50 is disposed within stator 51 and is fixed to drive shaft 130 extending therethrough.
  • Drive shaft 130 extends through axial annular projection 42.
  • Axial annular projection 42 extends within an opening in rotor 52.
  • Drive shaft 130 is rotatably supported within axial annular projection 42 through fixed plain bearing 14 disposed between the exterior surface of drive shaft 130 and the interior surface of axial annular projection 42.
  • Drive shaft 130 extends through central portion 43 of inner block member 40 and fixed plain bearing 14 extends entirely within annular projection 42 to support drive shaft 130 at that location.
  • Pin member 15 is integrated with and projects axially from upward end surface of drive shaft 130. Pin member 15 is radially offset from the axis of drive shaft 130. Pin member 15 is rotatably disposed within axial annular projection 33 of orbiting scroll 30 and is supported therein by bearing 34.
  • Rotation preventing device 16 for example, Oldham coupling mechanism is disposed between a downward peripheral surface of circular end plate 31, exterior of annular projection 33, and an upward surface of inner block member 40 to prevent rotation of orbiting scroll 30 during orbital motion.
  • Rotation preventing device 16 and pin member 15, as well as spiral elements 22 and 32, are all contained in isolated cavity 70.
  • circular end plate 31 partitions isolated cavity 70 into upward cavity 70a and downward cavity 70b.
  • Suction gas inlet pipe 80 axially penetrates shallow cup-shaped portion 12 of casing 10 and circular end plate 21, and opens into upward cavity 70a. Therefore, upward cavity 70a is used for the suction chamber.
  • O-ring seal 81 is disposed around the outer peripheral surface of inlet pipe 80 and seals the mating surfaces between inlet pipe 80 and circular end plate 21.
  • Hole 25 if formed through a central location of circular end plate 21 and links cavity 60 at the top of circular end plate 21 with the central fluid pocket 71c formed between the spiral elements. Thereby, cavity 60 is maintained at discharge pressure.
  • Drive shaft 130 includes axial bore 131 extending from an opening at the downward end surface of drive shaft 130 and terminating to the upward end surface of pin member 15. A downward end portion of drive shaft 13 is immersed in the accumulated pool of lubricating oil at the inner bottom portion of casing 10.
  • a plurality of radial bores 132 extend through drive shaft 130, at a location within annular projection 42.
  • Another radial bore 133 extends through pin member 15 at a location within axial annular projection 33, near the terminal end of axial bore 131.
  • Lubricating oil which accumulates at the inner bottom portion of casing 10 flows through axial bore 131, radial bores 132 and radial bore 133 into the gap between fixed plain bearing 14 and the exterior surface of drive shaft 130, and the gap between bearing 34 and the exterior surface of pin member 15 to lubricate the contact surfaces by virtue of the centrifugal force generated during operation of the compressor.
  • Interior chamber 61 is linked to cavity 60 via cavity 60a located between the interior surface of cylindrical portion 11 of casing 10 and the exterior surface of forward annular wall 41. Therefore, interior chamber 61 is maintained at discharge chamber pressure.
  • Discharge gas outlet pipe 90 radially penetrates cylindrical portion 11 of casing 10, and opens to interior chamber 61.
  • Cavity 44 is formed in central portion 43 of inner block member 40, at a location upward of axial annular projection 42.
  • Drive shaft 130 extends into cavity 44.
  • a shaft seal mechanism for example, mechanical seals 18 is disposed within cavity 44, around drive shaft 130 to prevent gas from leaking from interior chamber 61 into downward cavity 70b due to the rotation of drive shaft 130.
  • the mechanical seals 18 can be replaced with a lip type seal.
  • Balance weight 35 is disposed on a downward extension of pin member 15 and serves to average the torque of drive shaft 130 acting on pin member 15 during rotation.
  • Small aperture 36 is formed at circular end plate 31 in axial direction to link downward cavity 70b with the intermediately located fluid pocket 71b of spiral elements 22 and 32. Thereby, a part of the intermediately compressed refrigerant gas is conducted into downward cavity 70b. Consequently, downward cavity 70b is maintained at intermediate pressure. Therefore, downward cavity 70b can be named the intermediate pressure chamber.
  • stator 51 In operation, stator 51 generates a magnetic field, causing rotation of rotor 52 to thereby rotate drive shaft 130. Rotation of drive shaft 130 is converted to orbital motion of orbiting scroll 30 by pin member 15, and rotational motion of orbiting scroll 30 is prevented by rotation preventing device 16.
  • Refrigerant gas is introduced into suction chamber 70a from the external refrigeration circuit through suction gas inlet pipe 80 and is taken into the outer of fluid pockets 71a between fixed scroll 20 and orbiting scroll 30. Refrigerant gas is compressed inwardly toward the central fluid pocket 71c of spiral elements 22 and 32 due to the orbital motion of orbiting scroll 30.
  • intermediate pressure chamber 70b is maintained intermediate pressure of which value is less than the value of discharge chamber pressure, and is greater than the value of suction chamber pressure.
  • the other end surface of circular end plate 31 opposite to spiral element 32 receives the intermediate pressure, thereby being urged axially upwardly. Since leakage of refrigerant gas from interior chamber 61 into intermediate pressure chamber 70b is prevented by mechanical seals 18, pressure in chamber 70b is maintained constant at intermediate pressure.
  • the compressor includes hermetically sealed casing 10′ comprising cup-shaped casings 12′ and 13′ hermetically fixed to each other at the opening end thereof, fixed and orbiting scrolls 20 and 30, inner block member 40 and motor 50.
  • Fixed scroll 20 includes circular end plate 21 and spiral element of wrap 22 extending downwardly from one end surface of end plate 21.
  • Orbiting scroll 30 includes circular end plate 31 and spiral element or wrap 32 extending upwardly from one end surface of circular end plate 31.
  • Spiral element 22 of fixed scroll 20 and spiral element 32 of orbiting scroll 30 interfit at an angular and radial offset to form a plurality of line contacts which define at least one pair of sealed off fluid pockets 71 therebetween.
  • Annular projection 33 projects axially from the other end surface of circular end plate 31.
  • Inner block member 40 includes central portion 43 and upward annular wall 41 axially projecting from central portion 43 at a peripheral location.
  • Downward annular wall 45 projects axially from central portion 43 of block member 40 at a peripheral location and is fixedly disposed on the interior side surface of cup-shaped casing 13′ by forcible insertion.
  • Axial annular projection 42 projects downwardly from central portion 43 at a central location.
  • the upward end surface of upward annular wall 41 is fixed by a plurality of screws 26 to the peripheral one end surface of circular end plate 21 of fixed scroll 20.
  • Isolated cavity 70′ is thereby created between annular wall 41 of inner block member 40, and fixed scroll 20.
  • Orbiting scroll 30 is disposed entirely within isolated cavity 70′.
  • interior chamber 61 is created between inner block member 40 and casing 13′.
  • Motor 50 includes stator 51 and rotor 52.
  • Ring member 46 is disposed on the peripheral end surface of stator 51 and includes an outer surface which extends beyond the side surfaces of stator 51.
  • Bolts 27 fit through a plurality of holes formed through the peripheral outer surface of ring member 46 and are fixedly secured within corresponding threaded receiving holes of downward annular wall 45.
  • Stator 51 contacts the downward end surface of downward annular wall 45 on its upward end surface. Therefore, stator 51 of motor 50 is secured between ring member 46 and downward annular wall 45 of inner block member 40.
  • Rotor 52 of motor 50 is disposed within stator 51 and is fixed to drive shaft 130 extending therethrough.
  • Drive shaft 130 extends through axial annular projection 42.
  • Axial annular projection 42 extends within an opening in rotor 52.
  • Drive shaft 130 is rotatably supported within axial annular projection 42 through fixed plain bearing 14 disposed between the exterior surface of drive shaft 130 and the interior surface of axial annular projection 42.
  • Drive shaft 130 extends through central portion 43 of inner block member 40 and fixed plain bearing 14 extends partly within central portion 43 to support drive shaft 13 at that location.
  • Pin member 15 is integrated with an projects axially from upward end surface of drive shaft 130. Pin member 15 is radially offset from the axis of drive shaft 130.
  • Bushing 17 is rotatably disposed within downward axial annular projection 33 of orbiting scroll 30 and is supported therein by bearing 34. Pin member 15 is inserted in hole 19 of bushing 17 which is offset from the center of bushing 17.
  • Rotation preventing device 16′ is disposed between a downward peripheral surface of circular end plate 31, exterior of annular projection 33, and a upward surface of inner block member 40 to prevent rotation of orbiting scroll 30 during orbital motion.
  • Rotation preventing device 16′ used in this embodiment is substantially identical to the device disclosed in U.S. Patent No. 4,492,543 issued to Iimori et al.
  • O-ring seal 23 is disposed between an inner peripheral surface of upward annular wall 41 and a part of the exterior peripheral surface of circular end plate 21 to seal the mating surfaces therebetween.
  • Rotation preventing device 16′, pin member 15 and bushing 17, as well as spiral elements 22 and 32, are all contained in isolated cavity 70′.
  • Suction gas inlet pipe 80 radially penetrates a side wall of casing 12′ and annular wall 41, and opens into isolated cavity 70′. Therefore, isolated cavity 70′ is used for suction chamber.
  • O-ring seal 81 is disposed around the outer peripheral surface of inlet pipe 80 and seals the mating surfaces between inlet pipe 80 and annular wall 41.
  • Hole 25 is formed through a central location of circular end plate 21 and links cavity 60 at the top of circular end plate 21 with the central fluid pocket 71c formed between the spiral elements. Thereby, cavity 60 is maintained at discharge pressure.
  • Anti-wear plate 23 is disposed on the one end surface of circular end plate 21. Seal elements 221 and 321 are disposed between the end surface of spiral element 22 and the surface of circular end plate 31, and the end surface of spiral element 32 and anti-wear plate 23, respectively.
  • Interior chamber 61 is linked to cavity 60 via cavity 60a located between the interior side surface of casing 12′ and the exterior surface of annular wall 41. Therefore, interior chamber 61 is maintained at discharge chamber pressure.
  • Discharge gas outlet pipe 90 penetrates a side wall of casing 13′, and opens to interior chamber 61.
  • Drive shaft 130 includes axial bore 131 extending from an opening at the downward end surface of drive shaft 130 and terminating within drive shaft 130 at a downward end of axial annular projection 42.
  • a downward end portion of drive shaft 130 is immersed in the accumulated pool of lubricating oil at the inner bottom portion of casing 10′.
  • Helical groove 134 is formed on the exterior surface of drive shaft 130 within axial annular projection 42. Hole 134a radially extends through drive shaft 130 to link upward end of axial bore 131 with the downward end of helical groove 134.
  • a plurality of communication holes 135 are formed through axial annular projection 42 and fixed plain bearing 14, and links the upward end of helical groove 134 with interior chamber 61.
  • Lubricating oil which accumulates at the inner bottom portion of casing 10′ flows through axial bore 131, hole 134a and helical groove 134 into the gap between fixed plain bearing 14 and the exterior surface of drive shaft 130 to lubricate the contact surfaces by virtue of the centrifugal force generated during operation of the compressor.
  • Cavity 44 is formed in central portion 43 of inner block member 40, at a location upward of axial annular projection 42.
  • Drive shaft 130 extends into cavity 44.
  • a shaft seal mechanism for example, mechanical seals 18 is disposed within cavity 44, around drive shaft 130 to prevent gas from leaking from interior chamber 61 into suction chamber 70′ due to the rotation of drive shaft 13.
  • the mechanical seals 18 can be replaced with a lip type seal.
  • Balance weight 35 is disposed on a downward extension of bushing 17 and serves to average the torque of drive shaft 130 acting on bushing 17 during rotation.
  • Opening 121 is formed in the side wall of casing 13′.
  • Hermetic seal base 120 is secured within opening 121 of casing 13′ and maintains the hermetic seal of casing 10′.
  • Wires 110 extend from the bottom end of stator 51, and pass through hermetic seal base 120 for connection to an external electrical power source (not shown).
  • Base 120 may be welded or brazed to the side wall of casing 13′ to provide the hermetic seal therebetween.
  • stator 51 In operation, stator 51 generates a magnetic field, causing rotation of rotor 52 to thereby rotate drive shaft 130. Rotation of drive shaft 130 is converted to orbital motion of orbiting scroll 30 by pin member 15 and bushing 17, and rotational motion of orbiting scroll 30 is prevented by rotation preventing device 16′.
  • Refrigerant gas is introduced into suction chamber 70′ from the external refrigeration circuit through suction gas inlet pipe 80 and is taken into the outer of fluid pockets 71a between fixed scroll 20 and orbiting scroll 30. Refrigerant gas is compressed inwardly toward the central fluid pocket 71c of spiral elements 22 and 32 due to the orbital motion of orbiting scroll 30.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP89312960A 1988-12-13 1989-12-12 Compresseur de réfrigération du type à volutes hermétiquement étanche Expired - Lifetime EP0373876B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP313061/88 1988-12-13
JP63313061A JPH02161191A (ja) 1988-12-13 1988-12-13 密閉形スクロール型圧縮機

Publications (3)

Publication Number Publication Date
EP0373876A2 true EP0373876A2 (fr) 1990-06-20
EP0373876A3 EP0373876A3 (en) 1990-09-26
EP0373876B1 EP0373876B1 (fr) 1993-05-26

Family

ID=18036743

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89312960A Expired - Lifetime EP0373876B1 (fr) 1988-12-13 1989-12-12 Compresseur de réfrigération du type à volutes hermétiquement étanche

Country Status (6)

Country Link
EP (1) EP0373876B1 (fr)
JP (1) JPH02161191A (fr)
KR (1) KR0144149B1 (fr)
AU (1) AU615365B2 (fr)
CA (1) CA2005379A1 (fr)
DE (1) DE68906767T2 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0548002A1 (fr) * 1991-12-17 1993-06-23 Carrier Corporation Mécanisme d'accouplement pour machine à volutes
CN114320907A (zh) * 2021-12-30 2022-04-12 杨伟光 一种涡旋式制冷压缩机

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6139295A (en) * 1998-06-22 2000-10-31 Tecumseh Products Company Bearing lubrication system for a scroll compressor
JP5180698B2 (ja) * 2008-06-20 2013-04-10 サンデン株式会社 スクロール型流体機械
CN117225277B (zh) * 2023-11-15 2024-02-13 湖南德景源科技有限公司 一种具有三重密封结构的锂电材料混合设备

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4475874A (en) * 1977-01-14 1984-10-09 Hitachi, Ltd. Scroll fluid apparatus with axial sealing force
DE3422389A1 (de) * 1983-06-17 1984-12-20 Hitachi, Ltd., Tokio/Tokyo Stroemungsmaschine in spiralbauweise

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2595017B2 (ja) * 1988-02-29 1997-03-26 サンデン株式会社 密閉形スクロール圧縮機

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4475874A (en) * 1977-01-14 1984-10-09 Hitachi, Ltd. Scroll fluid apparatus with axial sealing force
DE3422389A1 (de) * 1983-06-17 1984-12-20 Hitachi, Ltd., Tokio/Tokyo Stroemungsmaschine in spiralbauweise

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0548002A1 (fr) * 1991-12-17 1993-06-23 Carrier Corporation Mécanisme d'accouplement pour machine à volutes
CN114320907A (zh) * 2021-12-30 2022-04-12 杨伟光 一种涡旋式制冷压缩机

Also Published As

Publication number Publication date
EP0373876B1 (fr) 1993-05-26
DE68906767T2 (de) 1993-10-07
KR900010234A (ko) 1990-07-06
CA2005379A1 (fr) 1990-06-13
KR0144149B1 (ko) 1998-08-01
AU4672389A (en) 1990-06-21
EP0373876A3 (en) 1990-09-26
JPH02161191A (ja) 1990-06-21
AU615365B2 (en) 1991-09-26
DE68906767D1 (de) 1993-07-01

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