US20190368486A1 - Co-rotating scroll compressor - Google Patents

Co-rotating scroll compressor Download PDF

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Publication number
US20190368486A1
US20190368486A1 US16/462,318 US201716462318A US2019368486A1 US 20190368486 A1 US20190368486 A1 US 20190368486A1 US 201716462318 A US201716462318 A US 201716462318A US 2019368486 A1 US2019368486 A1 US 2019368486A1
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US
United States
Prior art keywords
driven
driving
scroll member
side wall
end 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
US16/462,318
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English (en)
Inventor
Takahide Ito
Makoto Takeuchi
Takuma YAMASHITA
Keita Kitaguchi
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.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries 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 Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Assigned to MITSUBISHI HEAVY INDUSTRIES, LTD. reassignment MITSUBISHI HEAVY INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ITO, TAKAHIDE, KITAGUCHI, Keita, TAKEUCHI, MAKOTO, YAMASHITA, Takuma
Publication of US20190368486A1 publication Critical patent/US20190368486A1/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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/023—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where both members are moving
    • 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
    • F01C21/02—Arrangements of bearings
    • 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
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/56—Bearing bushings or details thereof
    • 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

Definitions

  • the present invention relates to a co-rotating scroll compressor.
  • the co-rotating scroll compressor includes a driving-side scroll and a driven-side scroll that rotates together with and in synchronization with the driving-side scroll.
  • the co-rotating scroll compressor rotates the driving shaft and the driven shaft in the same direction at the same angular velocity by offsetting a driven shaft that supports the rotation of the driven-side scroll from a driving shaft that rotates the driving-side scroll by the turning radius.
  • a tip seal is generally provided between a spiral wall and an end plate opposed thereto in order to prevent the leakage of compressed fluid.
  • a tip seal groove is formed in the distal end of the spiral wall.
  • the present invention has been made in view of the situation as above, and an object thereof is to provide a co-rotating scroll compressor capable of omitting a process of processing a tip seal groove in a distal end of a wall.
  • a co-rotating scroll compressor of the present invention employs the following solutions.
  • the co-rotating scroll compressor includes: a driving-side scroll member driven by a drive unit so as to rotate, and comprising a spiral driving-side wall arranged on a driving-side end plate; a driven-side scroll member in which a spiral driven-side wall corresponding to the driving-side wall is arranged on a driven-side end plate, the driven-side wall being engaged with the driving-side wall so as to form a compression space; a synchronous driving mechanism that transmits driving force from the driving-side scroll member to the driven-side scroll member so that the driving-side scroll member and the driven-side scroll member rotationally move in a same direction at a same angular velocity; and a biasing means for biasing a distal end of the driving-side wall and a distal end of the driven-side wall in a direction toward the driven-side end plate and the driving-side end plate that are respectively opposed to the distal end of the driving-side wall and the distal end of the driven-side wall.
  • the compressed space is formed when the driving-side wall arranged on the driving-side end plate of the driving-side scroll member and the driven-side wall of the driven-side scroll member are engaged with each other.
  • the driving-side scroll member is driven by the drive unit so as to rotate, and the driving force transmitted to the driving-side scroll member is transmitted to the driven-side scroll member via the synchronous driving mechanism.
  • the driven-side scroll member rotationally moves in the same direction at the same angular velocity as the driving-side scroll member while rotating.
  • the double rotating-type scroll-type compressor in which both of the driving-side scroll member and the driven-side scroll member rotate is provided.
  • the biasing means for biasing the distal end of the driving-side wall and the distal end of the driven-side wall in a direction toward the driven-type end plate and the driving-side end plate that are opposed thereto is provided.
  • a tip clearance that is the clearance between each of the distal ends of the walls and each of the end plates is reduced, and the leakage of the fluid from the compressed space can be reduced.
  • the tip seals provided on the distal ends of the walls can be omitted. Accordingly, the tip seal grooves for arranging the tip seals do not need to be formed in the distal ends of the walls. Therefore, the processing of the tip seal groove becomes unnecessary, and hence the workload when the scroll member is manufactured can be reduced.
  • synchronous driving mechanisms include a mechanism in which a pin and a ring are combined, an Oldham ring, and the like, for example.
  • the biasing means comprises an elastic member provided between a driven-side thrust bearing that receives thrust force of the driven-side scroll member and a housing that accommodates the driven-side scroll member.
  • the elastic member is provided between the driven-side thrust bearing that receives the thrust force of the driven-side scroll member and the housing that accommodates the driven-side scroll member. By the elastic member, the driven-side scroll member is biased to the driving-side scroll member side via the driven-side thrust bearing.
  • Elastic members include a coil spring, a ring spring, a corrugated plate spring, and the like, for example.
  • the co-rotating scroll compressor of the present invention further includes a driven-side rolling bearing provided between a driven-side shaft portion connected to the driven-side end plate and a housing that accommodates the driven-side scroll member, and the biasing means includes an elastic member provided between the driven-side rolling bearing and the housing.
  • the driven-side scroll member is rotatably supported by providing the driven-side rolling bearing between the driven-side shaft portion and the housing. Further, the elastic member is provided between the driven-side rolling bearing and the housing. By the elastic member, the driven-side scroll member is biased to the driving-side scroll member side via the driven-side rolling bearing.
  • Elastic members include a coil spring, a ring spring, a corrugated plate spring, and the like, for example.
  • the co-rotating scroll compressor of the present invention further includes a displacement amount restricting means for restricting a displacement amount between the driving-side scroll member and the driven-side scroll member.
  • Biasing is performed by the biasing means in the direction in which the distance between the driving-side scroll member and the driven-side scroll member decreases.
  • the displacement amount by the biasing force is restricted by the displacement amount restricting means.
  • the biasing means for biasing the distal end of the driving-side wall and the distal end of the driven-side wall in a direction toward the driven-type end plate and the driving-side end plate that are opposed thereto is provided, and hence a configuration that omits the tip seal of the distal end of the wall can be employed, and the processing of the tip seal groove becomes unnecessary.
  • FIG. 1 is a longitudinal cross-sectional view illustrating a co-rotating scroll compressor according to a first embodiment of the present invention.
  • FIG. 2 is a plan view illustrating a driving-side scroll member in FIG. 1 .
  • FIG. 3 is a plan view illustrating a driven-side scroll member in FIG. 1 .
  • FIG. 4 is a longitudinal cross-sectional view illustrating a co-rotating scroll compressor according to a second embodiment of the present invention.
  • FIG. 5 is a longitudinal cross-sectional view illustrating the region around a coil spring in FIG. 4 in an enlarged manner.
  • FIG. 6 is a longitudinal cross-sectional view illustrating a co-rotating scroll compressor according to a third embodiment of the present invention.
  • FIG. 7 is a longitudinal cross-sectional view illustrating the region around a stopper in FIG. 6 in an enlarged manner.
  • a first embodiment of the present invention is described below with reference to FIG. 1 and the like.
  • FIG. 1 illustrates a co-rotating scroll compressor 1 A.
  • the co-rotating scroll compressor 1 A can be used as a supercharger that compresses combustion air (fluid) to be supplied to an internal combustion engine such as a vehicle engine, a compressor for supplying compressed air to an air electrode of a fuel cell, or a compressor for supplying compressed air used in a braking device of a vehicle such as a train, for example.
  • the co-rotating scroll compressor 1 A includes a housing 3 , a motor (drive unit) 5 accommodated in one end side of the housing 3 , and a driving-side scroll member 7 and a driven-side scroll member 9 accommodated in the other end side of the housing 3 .
  • the housing 3 has a substantially cylindrical shape, and includes a motor accommodation portion 3 a that accommodates the motor 5 , and a scroll accommodation portion 3 b that accommodates the scroll members 7 and 9 .
  • Cooling fins 3 c for cooling the motor 5 are provided on the outer periphery of the motor accommodation portion 3 a .
  • An exhaust opening 3 d for exhausting air that has been compressed is formed in end portion of the scroll accommodation portion 3 b . Note that, although not shown in FIG. 1 , an air suction opening that sucks air is provided in the housing 3 .
  • the motor 5 is driven by being supplied with electric power from a power supply source (not shown).
  • the rotation control of the motor 5 is performed in accordance with instructions from a control unit (not shown).
  • a stator 5 a of the motor 5 is fixed to the inner peripheral side of the housing 3 .
  • a rotor 5 b of the motor 5 rotates about a driving-side rotational axis CL 1 .
  • a driving shaft 6 extending on the driving-side rotational axis CL 1 is connected to the rotor 5 b .
  • the driving shaft 6 is connected to the driving-side scroll member 7 .
  • the driving-side scroll member 7 includes a driving-side end plate 7 a , and a spiral driving-side wall 7 b provided on one side of the driving-side end plate 7 a .
  • the driving-side end plate 7 a is connected to the driving-side shaft portion 7 c connected to a driving shaft 6 , and extends in a direction orthogonal to the driving-side rotational axis CL 1 .
  • the tip seal is not provided on a distal end of the driving-side wall 7 b in the height direction. Therefore, the distal end of the driving-side wall 7 b has a flat surface because the tip seal groove is also not provided.
  • the driving-side shaft portion 7 c is provided so as to be rotatable with respect to the housing 3 via a driving-side radial sliding bearing 11 a .
  • a driving-side thrust sliding bearing 11 b that receives thrust force by coming into contact with a place between the housing 3 and a shoulder portion of the driving-side shaft portion 7 c is provided.
  • the driving-side end plate 7 a has a substantially disk-like shape when seen in planar view.
  • the driving-side scroll member 7 includes three spiral driving-side walls 7 b , that is, three lines of spiral driving-side walls 7 b .
  • the three lines of driving-side walls 7 b are provided about the driving-side rotational axis CL 1 at regular intervals.
  • Radially outside end portions 7 e of the driving-side walls 7 b are not fixed to other wall portions and are independent. That is, wall portions that connect the radially outside end portions 7 e to each other so as to provide reinforcement are not provided.
  • the driven-side scroll member 9 is arranged so as to engage with the driving-side scroll member 7 , and includes a driven-side end plate 9 a and a spiral driven-side wall 9 b arranged on one side of the driven-side end plate 9 a.
  • the tip seal is not provided on a distal end of the driven-side wall 9 b in the height direction. Therefore, the distal end of the driven-side wall 9 b has a flat surface because the tip seal groove is also not provided.
  • a driven-side shaft portion 9 c extending in the direction of a driven-side rotational axis CL 2 is connected to the driven-side end plate 9 a .
  • the driven-side shaft portion 9 c is provided so as to be rotatable with respect to the housing 3 via a driven-side radial sliding bearing 13 a .
  • a driven-side thrust sliding bearing 13 b that receives thrust force by coming into sliding contact with a place between the housing 3 and the driven-side end plate 9 a is provided.
  • a coil spring (elastic member, biasing means) 14 is provided so as to abut against an end surface of the driven-side thrust sliding bearing 13 b .
  • a plurality of the coil springs 14 are provided in the circumferential direction about the driven-side axis CL 2 at predetermined intervals.
  • the coil springs 14 are stored in bottomed holes formed in the housing 3 toward the direction of the driven-side rotational axis CL 2 .
  • the coil springs 14 are provided so as to bias the driven-side end plate 9 a in the direction of the driving-side end plate 7 a that is opposed thereto.
  • the driven-side end plate 9 a has a substantially disk-like shape when seen in planar view.
  • Three spiral driven-side walls 9 b that is, three lines of spiral driven-side walls 9 b are provided in the driven-side scroll member 9 .
  • the three lines of driven-side walls 9 b are arranged about the driven-side rotational axis CL 2 at regular intervals.
  • An exhaust port 9 d that exhausts air that has been compressed is formed in the driven-side end plate 9 a on the substantially middle thereof.
  • the exhaust port 9 d is in communication with the exhaust opening 3 d formed in the housing 3 .
  • the radially outside end portions 9 e of the driven-side wall 9 b are not fixed to other wall portions and are independent. That is, wall portions that connect the radially outside end portions 9 e to each other so as to provide reinforcement are not provided.
  • the driving-side scroll member 7 rotates about the driving-side rotational axis CL 1 and the driven-side scroll member 9 rotates about the driven-side rotational axis CL 2 .
  • the driving-side rotational axis CL 1 and the driven-side rotational axis CL 2 are offset from each other by a distance with which a compression chamber can be formed.
  • a plurality of pin ring mechanisms 15 are provided between the driving-side scroll member 7 and the driven-side scroll member 9 .
  • the pin ring mechanism 15 is used as a synchronous driving mechanism that transmits driving force from the driving-side scroll member 7 to the driven-side scroll member 9 so that both of the scroll members 7 and 9 rotationally move in the same direction at the same angular velocity.
  • the pin ring mechanism 15 includes a ring member 15 a that is a ball bearing, and a pin member 15 b .
  • the ring member 15 a is fixed in a state in which an outer ring is fitted in a hole portion formed in the driving-side end plate 7 a .
  • the pin member 15 b is fixed in a state of being inserted in a mounting hole formed in a distal end (the right end in FIG. 1 ) of the driven-side wall 9 b .
  • the state in which the pin member 15 b is inserted in the distal end of the driven-side wall 9 b is not clearly illustrated due to the position along which FIG. 1 is taken in the illustration, and only the pin member 15 b is illustrated for the ease of understanding.
  • a side portion of a distal end of the pin member 15 b moves while being in contact with an inner peripheral surface of an inner ring of the ring member 15 a , rotationally moving in the same direction at the same angular velocity is realized.
  • the co-rotating scroll compressor 1 A having the abovementioned configuration operates as follows.
  • both of the scroll members 7 and 9 rotationally and pivotally move, the air sucked from the suction opening in the housing 3 is sucked from the outer periphery side of both of the scroll members 7 and 9 , and is taken into the compression chamber formed by both of the scroll members 7 and 9 .
  • the capacity of the compression chamber decreases as the compression chamber approaches the center side, and air is compressed accordingly.
  • the air compressed as above flows through the exhaust port 9 d in the driven-side scroll member 9 and is exhausted to the outside from the exhaust opening 3 d in the housing 3 .
  • the driven-side wall 9 b is biased by the coil springs 14 in the direction of the driven-side rotational axis CL 2 via the driven-side thrust sliding bearing 13 b .
  • the driven-side scroll member 9 and the driving-side scroll member 7 are biased in directions in which the driven-side scroll member 9 and the driving-side scroll member 7 approach each other, the tip clearance between the distal end of the driven-side wall 9 b and the driving-side end plate 7 a and the tip clearance between the distal end of the driving-side wall 7 b and the driven-side end plate 9 a decrease, and the fluid leakage from the compressed space decreases.
  • the tip seals provided on the distal ends of the walls 7 b and 9 b can be omitted. Accordingly, the tip seal grooves for arranging the tip seals do not need to be formed in the distal ends of the walls 7 b and 9 b . Therefore, the processing of the tip seal groove becomes unnecessary, and hence the workload when the scroll member is manufactured can be reduced.
  • the sliding bearings 11 a , 11 b , 13 a , and 13 b are used as the bearings of the driving-side scroll member 7 and the driven-side scroll member 9 in the first embodiment, but this embodiment is different in that a ball bearing (rolling bearing) is used.
  • Other configurations are similar. Therefore, similar configurations are denoted by the same reference characters and description thereof is omitted.
  • the driving-side shaft portion 7 c of the driving-side scroll member 7 is rotatably supported by a driving-side ball bearing 17 .
  • the driven-side shaft portion 9 c of the driven-side scroll member 9 is provided so as to be rotatable with respect to the housing 3 via a driven-side ball bearing 18 formed as a double row angular ball bearing.
  • a plurality of coil springs 20 are provided so as to press the exhaust opening 3 d side and the outer ring side (stationary side) of the driven-side ball bearing 18 formed to have a double row.
  • the plurality of coil springs 20 are provided in the circumferential direction about the driven-side axis CL 2 at predetermined intervals.
  • the coil springs 20 are stored in bottomed holes formed in the housing 3 toward the direction of the driven-side rotational axis CL 2 .
  • the coil springs 20 are provided so as to bias the driven-side end plate 9 a in the direction of the driving-side end plate 7 a that is opposed thereto.
  • the biasing force from the coil spring 20 is transmitted from the outer ring of a ball bearing 18 a on the exhaust opening 3 d side to the outer ring of a ball bearing 18 b on the driven-side end plate 9 a side, and is transmitted to the driven-side end plate 9 a via the ball and the inner ring of the ball bearing 18 b on the driven-side end plate 9 a side.
  • DB combination back-to-back
  • the driven-side wall 9 b is biased by the coil springs 20 in the direction of the driven-side rotational axis CL 2 via the driven-side ball bearing 18 .
  • the driven-side scroll member 9 and the driving-side scroll member 7 are biased in directions in which the driven-side scroll member 9 and the driving-side scroll member 7 approach each other, the tip clearance between the distal end of the driven-side wall 9 b and the driving-side end plate 7 a and the tip clearance between the distal end of the driving-side wall 7 b and the driven-side end plate 9 a decrease, and the fluid leakage from the compressed space decreases.
  • the tip seals provided on the distal ends of the walls 7 b and 9 b can be omitted. Accordingly, the tip seal grooves for arranging the tip seals do not need to be formed in the distal ends of the walls 7 b and 9 b . Therefore, the processing of the tip seal groove becomes unnecessary, and hence the workload when the scroll member is manufactured can be reduced.
  • the coil springs 20 are formed so as to press the outer ring of the ball bearing 18 a on the exhaust opening 3 d side, and can press the stationary outer ring with respect to the housing 3 . Therefore, there is no fear of wear and seizing of the coil spring 20 .
  • FIG. 6 a third embodiment of the present invention is described with reference to FIG. 6 and the like.
  • This embodiment is different from the second embodiment in that a stopper that restricts the displacement amount of the driven-side ball bearing 18 is provided.
  • Other configurations are similar to that of the second embodiment. Therefore, similar configurations are denoted by the same reference characters and description thereof is omitted.
  • a stopper (displacement amount restricting means) 22 is provided on the side of the ball bearing 18 b on the driven-side end plate 9 a side.
  • the stopper 22 is a plate-like body having a predetermined thickness, and is fixed to the housing 3 side via a bolt 23 . Note that a shim having a predetermined thickness may be inserted between the stopper 22 and the housing 3 . As a result, the distance between the stopper 22 and the ball bearing 18 b on the driven end plate 9 a side can be adjusted.
  • This embodiment has the following effects in addition to the effects of the second embodiment.
  • Biasing is performed by the coil springs 20 in a direction in which the distance between the driving-side scroll member 7 and the driven-side scroll member 9 decreases.
  • the displacement amount by the biasing force is restricted by the stopper 22 .
  • the tip clearance between the distal ends of the walls 7 b and 9 b and the end plates 7 a and 9 a that are opposed thereto can be managed to be a predetermined amount, and seizing and excessive wear between the distal ends of the walls and the end plates that are opposed thereto can be prevented.
  • the coil spring is used as a member that biases the driven-side scroll member 9 in the abovementioned embodiments, but the present invention is not limited thereto, and a ring spring or a corrugated plate spring may be used, for example.

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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)
US16/462,318 2016-11-24 2017-11-22 Co-rotating scroll compressor Abandoned US20190368486A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2016-227830 2016-11-24
JP2016227830A JP6749829B2 (ja) 2016-11-24 2016-11-24 両回転スクロール型圧縮機
PCT/JP2017/042070 WO2018097199A1 (ja) 2016-11-24 2017-11-22 両回転スクロール型圧縮機

Publications (1)

Publication Number Publication Date
US20190368486A1 true US20190368486A1 (en) 2019-12-05

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ID=62195842

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Application Number Title Priority Date Filing Date
US16/462,318 Abandoned US20190368486A1 (en) 2016-11-24 2017-11-22 Co-rotating scroll compressor

Country Status (5)

Country Link
US (1) US20190368486A1 (enExample)
EP (1) EP3530945B1 (enExample)
JP (1) JP6749829B2 (enExample)
CN (1) CN109964036B (enExample)
WO (1) WO2018097199A1 (enExample)

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4610610A (en) * 1984-08-16 1986-09-09 Sundstrand Corporation Unloading of scroll compressors
US4575318A (en) * 1984-08-16 1986-03-11 Sundstrand Corporation Unloading of scroll compressors
JPS62210279A (ja) * 1986-03-07 1987-09-16 Mitsubishi Electric Corp スクロ−ル圧縮機
US4927339A (en) * 1988-10-14 1990-05-22 American Standard Inc. Rotating scroll apparatus with axially biased scroll members
JP2865376B2 (ja) * 1990-05-11 1999-03-08 三洋電機株式会社 スクロール圧縮機
JPH04292591A (ja) * 1991-03-20 1992-10-16 Sanyo Electric Co Ltd スクロール圧縮機
JPH07259774A (ja) * 1994-03-23 1995-10-09 Sanyo Electric Co Ltd 回転式スクロール圧縮機
DE10031143A1 (de) * 2000-06-27 2002-01-17 Knorr Bremse Systeme Spiralverdichter, Verfahren zur Kühlung einer Lageranordnung einer Spirale ines Spiralverdichters und Verwendung des Spiralverdichters
JP4556183B2 (ja) * 2005-07-12 2010-10-06 有限会社スクロール技研 スクロール流体機械
JP2014211095A (ja) * 2013-04-17 2014-11-13 三浦工業株式会社 スクロール流体機械
JP6768406B2 (ja) * 2016-08-19 2020-10-14 三菱重工業株式会社 両回転スクロール型圧縮機

Also Published As

Publication number Publication date
EP3530945B1 (en) 2020-12-30
WO2018097199A1 (ja) 2018-05-31
EP3530945A1 (en) 2019-08-28
JP6749829B2 (ja) 2020-09-02
EP3530945A4 (en) 2019-11-13
CN109964036A (zh) 2019-07-02
JP2018084199A (ja) 2018-05-31
CN109964036B (zh) 2020-10-27

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