EP4102074A1 - Spiralverdichter - Google Patents

Spiralverdichter Download PDF

Info

Publication number
EP4102074A1
EP4102074A1 EP21751392.8A EP21751392A EP4102074A1 EP 4102074 A1 EP4102074 A1 EP 4102074A1 EP 21751392 A EP21751392 A EP 21751392A EP 4102074 A1 EP4102074 A1 EP 4102074A1
Authority
EP
European Patent Office
Prior art keywords
orbiting
scroll
bearing
tapered shape
eccentric shaft
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.)
Pending
Application number
EP21751392.8A
Other languages
English (en)
French (fr)
Other versions
EP4102074A4 (de
Inventor
Satoshi Iitsuka
Yusuke Imai
Akifumi HYODO
Atsushi Sakuda
Yoshinori Ishida
Yusaku ARAKI
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.)
Panasonic Intellectual Property Management Co Ltd
Original Assignee
Panasonic Intellectual Property Management Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Panasonic Intellectual Property Management Co Ltd filed Critical Panasonic Intellectual Property Management Co Ltd
Publication of EP4102074A1 publication Critical patent/EP4102074A1/de
Publication of EP4102074A4 publication Critical patent/EP4102074A4/de
Pending 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
    • F04C18/0215—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 only one member is moving
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/603—Centering; Aligning
    • 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
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • F04C2240/601—Shaft flexion
    • 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
    • F04C2240/60—Shafts
    • F04C2240/605—Shaft sleeves 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 disclosure relates to a scroll compressor used for, in particular, an air conditioner, a water heater, or a freezing machine of a refrigerator or the like.
  • PTL 1 discloses a scroll compressor used for an air conditioner or the like.
  • a back pressure region is provided on an anti-wrap surface of an orbiting scroll end plate, and an orbiting scroll is pressed against a fixed scroll, thereby suppressing turning of the orbiting scroll and reducing leakage loss to improve theoretical efficiency and capability of cooling and heating.
  • the present disclosure provides a highly efficient and highly reliable scroll compressor in which turning of an orbiting scroll is further reliably suppressed.
  • a back pressure region is formed on an anti-wrap surface of an orbiting scroll end plate, and an orbiting scroll is pressed against a fixed scroll.
  • the wrap side of an orbiting bearing of the orbiting scroll is closed by an end plate, and the crank shaft side is opened.
  • the orbiting bearing of the orbiting scroll has a tapered shape of which diameter gradually increases toward an open side of the orbiting bearing, or an eccentric shaft inserted in the orbiting bearing has a tapered shape of which diameter gradually decreases toward the open side of the orbiting bearing.
  • scroll compressors have been configured to press an orbiting scroll against a fixed scroll using back pressure to further stabilize the behavior of the orbiting scroll.
  • the inventors have found that such a configuration has a disadvantage in that the orbiting scroll may separate from the fixed scroll when the turning moment created by the tangential gas load acting on the side surface of the wrap of the orbiting scroll becomes larger than the stabilizing moment created by the back pressure acting on the orbiting scroll.
  • the performance of the scroll compressor is deteriorated due to leakage of refrigerant between adjacent compression chambers or between an intermediate pressure region and a compression chamber.
  • the inventors have come to construct the subject matter of the present disclosure in order to solve the problem.
  • the present disclosure provides a highly efficient and highly reliable scroll compressor that suppresses turning of an orbiting scroll.
  • scroll compressor 100 includes compression mechanism unit 10 that compresses a refrigerant and motor mechanism unit 20 that drives compression mechanism unit 10, compression mechanism unit 10 and motor mechanism unit 20 being disposed in hermetic container 1.
  • Hermetic container 1 includes barrel 1a having a cylindrical shape extending in the up-down direction, lower lid 1b closing a lower opening of barrel 1a, and upper lid 1c closing an upper opening of barrel 1a.
  • Hermetic container 1 is provided with refrigerant suction pipe 2 for introducing the refrigerant into compression mechanism unit 10, and refrigerant discharge pipe 3 for discharging the refrigerant compressed by compression mechanism unit 10 to the outside of hermetic container 1.
  • Compression mechanism unit 10 includes fixed scroll 11, orbiting scroll 12, and rotary shaft 13 for driving orbiting scroll 12 to orbit.
  • Motor mechanism unit 20 includes stator 21 fixed to hermetic container 1, and rotor 22 disposed inside stator 21.
  • Rotary shaft 13 is fixed to rotor 22.
  • Eccentric shaft 13a is provided at an upper end of rotary shaft 13 to be eccentric to rotary shaft 13.
  • an oil reservoir which is a recess opened to an upper surface of eccentric shaft 13a is provided.
  • Main bearing 30 that supports fixed scroll 11 and orbiting scroll 12 is provided below fixed scroll 11 and orbiting scroll 12.
  • Main bearing 30 includes bearing 31 that rotatably supports rotary shaft 13, and boss housing 32.
  • Main bearing 30 is fixed to hermetic container 1 by welding, shrink fit, or the like.
  • Fixed scroll 11 includes fixed scroll end plate 11a having a disk shape, fixed spiral wrap 11b having a spiral shape and erecting from fixed scroll end plate 11a, and outer peripheral wall portion 11c erecting so as to surround the circumference of fixed spiral wrap 11b.
  • Discharge port 14 is provided substantially at a center portion of fixed scroll end plate 11a.
  • Orbiting scroll 12 includes orbiting scroll end plate 12a having a disk shape, orbiting spiral wrap 12b erecting from one surface (wrap-side end surface) of orbiting scroll end plate 12a, and cylindrical boss portion 12c formed on the other surface (anti-wrap-side end surface) of orbiting scroll end plate 12a.
  • the other surface of orbiting scroll end plate 12a is a surface opposite to the wrap-side end surface of orbiting scroll end plate 12a.
  • orbiting bearing 13d is fit in cylindrical boss portion 12c.
  • the wrap side of orbiting bearing 13d is closed by orbiting scroll end plate 12a, and the anti-wrap side is opened.
  • Eccentric shaft 13a of rotary shaft 13 is inserted from the open side of orbiting bearing 13d.
  • first end 13da the end on the wrap side of orbiting bearing 13d
  • second end 13db the end on the open side
  • Fixed spiral wrap 11b of fixed scroll 11 and orbiting spiral wrap 12b of orbiting scroll 12 mesh with each other, and a plurality of compression chambers 15 is formed between fixed spiral wrap 11b and orbiting spiral wrap 12b.
  • Boss portion 12c is formed substantially at the center of orbiting scroll end plate 12a. Boss portion 12c is accommodated in boss housing 32 with eccentric shaft 13a inserted in boss portion 12c.
  • Fixed scroll 11 is fixed to main bearing 30 by outer peripheral wall 11c using a plurality of bolts (not shown). Meanwhile, the movement of orbiting scroll 12 with respect to fixed scroll 11 is restricted by spin-restraining member 17 such as an Oldham ring. Spin-restraining member 17 that restrains spinning of orbiting scroll 12 is provided between fixed scroll 11 and main bearing 30. This makes orbiting scroll 12 to orbit without spinning with respect to fixed scroll 11 as eccentric shaft 13a of rotary shaft 13 orbits.
  • Oil storage part 4 that stores lubricating oil is formed at the bottom of hermetic container 1.
  • Lower end 13b of rotary shaft 13 is rotatably supported by sub-bearing 18 disposed at the lower portion of hermetic container 1.
  • Oil pump 5 of a displacement type is provided at the lower end of rotary shaft 13. Oil pump 5 is disposed so as a suction port of oil pump 5 to be in oil storage part 4. Oil pump 5 is driven by rotary shaft 13 and reliably sucks up lubricating oil in oil storage part 4 provided at the bottom of hermetic container 1 at any pressure condition and operating speed, which eliminates concern about loss of oil.
  • Rotary shaft oil supply hole 13c extending from lower end 13b of rotary shaft 13 to eccentric shaft 13a is formed in rotary shaft 13.
  • the lubricating oil sucked up by oil pump 5 is supplied to a bearing of sub-bearing 18 and bearing 31, and into boss portion 12c through rotary shaft oil supply hole 13c in rotary shaft 13.
  • the refrigerant suctioned from refrigerant suction pipe 2 is introduced from suction port 15a to compression chamber 15.
  • Compression chamber 15 moves from the outer peripheral side toward the central portion while reducing its volume.
  • the refrigerant that has reached a predetermined pressure in compression chamber 15 is discharged to discharge chamber 6 from discharge port 14 provided at the central portion of fixed scroll 11.
  • Discharge port 14 is provided with a discharge reed valve (not shown).
  • the refrigerant that has reached a predetermined pressure in compression chamber 15 pushes open the discharge reed valve and is discharged to discharge chamber 6.
  • the refrigerant discharged to discharge chamber 6 is led out to the upper portion of hermetic container 1, and is then discharged through refrigerant discharge pipe 3.
  • boss housing 32 serves as high-pressure region A
  • the outer peripheral portion of orbiting scroll 12 in which spin-restraining member 17 is disposed serves as intermediate-pressure region B.
  • Orbiting scroll 12 is pressed against fixed scroll 11. The configuration will be described below.
  • Eccentric shaft 13a is inserted in boss portion 12c via orbiting bearing 13d so as to be driven to orbit.
  • Oil groove 13e is formed in an outer peripheral surface of eccentric shaft 13a.
  • Sealing member 33 having a ring shape is provided on a thrust surface of main bearing 30 that receives a thrust force from orbiting scroll end plate 12a. Sealing member 33 is disposed on the outer periphery of boss housing 32.
  • hermetic container 1 The inside of hermetic container 1 is filled with refrigerant of the same high pressure as the refrigerant discharged to discharge chamber 6.
  • Rotary shaft oil supply hole 13c is opened at the upper end of eccentric shaft 13a.
  • boss portion 12c serves as a high-pressure region A of which pressure is equivalent to the pressure of the discharged refrigerant.
  • boss portion 12c The lubricating oil introduced into boss portion 12c through rotary shaft oil supply hole 13c is supplied to orbiting bearing 13d and boss housing 32 through oil groove 13e formed in the outer peripheral surface of eccentric shaft 13a. Since sealing member 33 is provided at the outer periphery of boss housing 32, the inside of boss housing 32 serves as high-pressure region A.
  • Orbiting scroll end plate 12a is provided with first oil introduction hole 51 directed to the inside of boss portion 12c, first oil lead-out hole 52 which is a through hole in the outer peripheral portion of the wrap-side end surface, and first end plate oil communication passage 53 that provides communication between first oil introduction hole 51 and first oil lead-out hole 52.
  • Orbiting scroll end plate 12a is provided with second oil introduction hole 61 that opens to intermediate-pressure region B at the outer peripheral portion of orbiting scroll 12, second oil lead-out hole 62 that opens to compression chamber 15, and second end plate oil communication passage 63 that provides communication between second oil introduction hole 61 and second oil lead-out hole 62.
  • second oil introduction hole 61 opens at the upper surface of orbiting scroll end plate 12a.
  • second oil lead-out hole 62 of orbiting scroll 12 intermittently provides communication between intermediate-pressure region B and compression chamber 15. This introduces the intermediate pressure in compression chamber 15 to intermediate-pressure region B, and orbiting scroll 12 can be pressed against fixed scroll 11 with a minimum necessary load under various operating conditions. Accordingly, separation of orbiting scroll 12 from fixed scroll 11 can be prevented while reducing friction loss of the compressor, and thereby the airtightness of compression chamber 15 can be improved.
  • Figs. 3A to 3D are views illustrating the volumetric change of the compression chamber caused by the orbiting motion in the scroll compressor according to the present exemplary embodiment, where the views each illustrates a meshing state of orbiting scroll 12 and fixed scroll 11 looking from the back surface of orbiting scroll 12.
  • Fig. 3B illustrates a state in which the rotation is advanced by 90 degrees from Fig. 3A
  • Fig. 3C illustrates a state in which the rotation is further advanced by 90 degrees from Fig. 3B
  • Fig. 3D illustrates a state in which the rotation is further advanced by 90 degrees from Fig. 3C .
  • first compression chamber 15A is formed on an outer wall side of orbiting spiral wrap 12b
  • second compression chamber 15B is formed on an inner wall side of orbiting spiral wrap 12b.
  • first compression chamber 15A confines the refrigerant in a place that is shifted by approximately 180 degrees from the place where second compression chamber 15B confines the refrigerant.
  • the suction volume of first compression chamber 15A is larger than the suction volume of second compression chamber 15B.
  • bore surface 13dc of orbiting bearing 13d has a tapered shape (first tapered shape T1) of which diameter increases toward the open end (second end 13db) as illustrated in Fig. 5A .
  • eccentric shaft 13a may have a tapered shape (second tapered shape T2) of which diameter decreases toward the open side of orbiting bearing 13d as illustrated in Fig. 5B .
  • an angle ⁇ between first tapered shape T1 or second tapered shape T2 and the axis of orbiting bearing 13d may be set to an angle equal to or larger than the maximum angle at which rotary shaft 13 can tilt and to satisfy the following relational expression
  • L is the distance between the upper end of orbiting bearing 13d (first end 13da) and the start point of taper
  • d is the diameter of the eccentric shaft
  • D is the diameter of the inner wall of an eccentric bearing.
  • the maximum angle at which rotary shaft 13 can tilt is defined by the clearance between main bearing 30 and rotary shaft 13 and the clearance between sub-bearing 18 and rotary shaft 13 illustrated in Figs. 4A and 4B .
  • the tapered shape of orbiting bearing 13d or the tapered shape of eccentric shaft 13a may start from a position at a midway within a range along the axial direction of eccentric bearing 13d, in which range inner wall 13dc of eccentric bearing 13d and outer periphery 13ab of eccentric shaft 13a slide against each other.
  • the tapered shape of orbiting bearing 13d or eccentric shaft 13a may include a straight line, a continuous curve, or a combination thereof.
  • Figs. 4A and 4B illustrate the rotating state of rotary shaft 13 that makes the orbiting scroll orbit.
  • Fig. 4A illustrates a state with no compression load
  • Fig. 4B illustrates a state with a compression load.
  • eccentric shaft 13a located at an end of rotary shaft 13 rotates while pushing orbiting bearing 13d of orbiting scroll 12.
  • the back pressure acting on the anti-wrap surface of orbiting scroll end plate 12a of orbiting scroll 12 keeps orbiting scroll 12 pressed against fixed scroll 11.
  • eccentric shaft 13a receives a force in a direction substantially opposite to the direction in which the refrigerant is compressed, and rotary shaft 13 rotates with a tilt allowed by the clearance between rotary shaft 13 and main bearing 30 and the clearance between rotary shaft 13 and sub-bearing 18.
  • Figs. 6A and 6B The load and turning moment acting on orbiting bearing 13d in the gas compression process are as shown in Figs. 6A and 6B.
  • Fig. 6A illustrates a case where orbiting bearing 13d has no taper
  • Fig. 6B illustrates a case where orbiting bearing 13d has a taper. Illustrated in a lower left area in each of Figs. 6A and 6B is the magnitude of reaction force by gas compression (bearing load) acting on orbiting bearing 13d for each case.
  • the tapered shape of orbiting bearing 13d starts from a midway of the sliding surface of eccentric shaft 13a or the tapered shape of eccentric shaft 13a starts from a midway of the sliding surface of orbiting bearing 13d, so that the gap between eccentric shaft 13a and orbiting bearing 13d can be minimized at the start point of the taper. This prevents the surface pressure locally becoming large at the lower end on the open side of orbiting bearing 13d (second end 13db), which promotes formation of an oil film at the sliding portion.
  • the tapered shape of orbiting bearing 13d or eccentric shaft 13a may include a straight line, a continuous curve, or a combination thereof. This further distributes surface pressure to moderate a local surface pressure, and a scroll compressor with further lower input and higher efficiency can be provided.
  • the scroll compressor includes compression mechanism unit 10 that compresses the refrigerant, motor mechanism unit 20 that drives compression mechanism unit 10, and hermetic container 1 that accommodates compression mechanism unit 10 and motor mechanism unit 20.
  • Compression mechanism unit 10 includes fixed scroll 11, orbiting scroll 12, and rotary shaft 13 that drives orbiting scroll 12 to orbit.
  • Fixed scroll 11 includes fixed scroll end plate 11a having a disk shape and fixed spiral wrap 11b erecting from fixed scroll end plate 11a
  • orbiting scroll 12 includes orbiting scroll end plate 12a having a disk shape and orbiting spiral wrap 12b erecting from the wrap-side end surface of orbiting scroll end plate 12a.
  • Compression chamber 15 includes first compression chamber 15A formed on the outer wall side of the orbiting spiral wrap and second compression chamber 15B formed on the inner wall side of orbiting spiral wrap 12b.
  • Orbiting scroll 12 is pressed against fixed scroll 11 by back pressure created on the anti-wrap surface side of orbiting scroll end plate 12a.
  • the wrap side of orbiting bearing 13d of orbiting scroll 12 is closed by an end plate, and eccentric shaft 13a side of rotary shaft 13 is opened.
  • orbiting bearing 13d has a tapered shape of which diameter gradually increases toward the open side of orbiting bearing 13d, or eccentric shaft 13a of rotary shaft 13 inserted in orbiting bearing 13d has a tapered shape of which diameter gradually decreases toward the open side of orbiting bearing 13d.
  • the tapered shape of orbiting bearing 13d or eccentric shaft 13a shortens the distance between the point of effort, when the side surface of the wrap of the orbiting scroll receives a tangential gas load, and the point at which the orbiting bearing receives the reaction force, and thereby the turning moment that causes orbiting scroll 12 to turn can be suppressed.
  • the behavior of orbiting scroll 12 easily becomes unstable due to, for example, first compression chamber 15A having a larger suction volume than second compression chamber 15B as in the present exemplary embodiment, the behavior of orbiting scroll 12 can be stabilized more effectively.
  • the tapered shape of orbiting bearing 13d or eccentric shaft 13a starts from a midway of the sliding surface between orbiting bearing 13d and eccentric shaft 13a. This prevents the surface pressure from locally becoming large at the lower end on the opened side of orbiting bearing 13d (second end 13db), and promotes formation of an oil film between the sliding portions.
  • the tapered shape of orbiting bearing 13d or eccentric shaft 13a includes a straight line, a continuous curve, or a combination thereof. This further distributes surface pressure to moderate a local surface pressure, and a scroll compressor with further lower input and higher efficiency can be provided.
  • orbiting bearing 13d has a tapered shape of which diameter increases toward the open side of orbiting bearing 13d.
  • the angle ⁇ between the tapered shape and the axis of orbiting bearing 13d is set so as to satisfy the following relational expression, where L is the distance between the upper end of orbiting bearing 13d (first end 13da) and the start point of the taper, d is the diameter of the eccentric shaft, and D is the diameter of the orbiting bearing.
  • R32 carbon dioxide, or a refrigerant having a double bond between carbons can be used.
  • a scroll compressor according to the present disclosure can achieve high efficiency, and is therefore useful for various refrigeration cycle devices such as a hot water heating device, an air conditioner, a water heater, a freezing machine, or the like.

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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)
EP21751392.8A 2020-02-05 2021-01-19 Spiralverdichter Pending EP4102074A4 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2020017533 2020-02-05
PCT/JP2021/001571 WO2021157332A1 (ja) 2020-02-05 2021-01-19 スクロール圧縮機

Publications (2)

Publication Number Publication Date
EP4102074A1 true EP4102074A1 (de) 2022-12-14
EP4102074A4 EP4102074A4 (de) 2023-07-12

Family

ID=77199272

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21751392.8A Pending EP4102074A4 (de) 2020-02-05 2021-01-19 Spiralverdichter

Country Status (4)

Country Link
EP (1) EP4102074A4 (de)
JP (1) JPWO2021157332A1 (de)
CN (1) CN115053069B (de)
WO (1) WO2021157332A1 (de)

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB768854A (en) * 1953-10-29 1957-02-20 Chrysler Corp Improvements in or relating to a gas turbine power plant
US4836758A (en) * 1987-11-20 1989-06-06 Copeland Corporation Scroll compressor with canted drive busing surface
JPH0472484A (ja) * 1990-07-10 1992-03-06 Mitsubishi Electric Corp スクロール圧縮機
JP2930046B2 (ja) * 1997-03-07 1999-08-03 三菱電機株式会社 スクロール圧縮機
JP3214417B2 (ja) * 1997-11-11 2001-10-02 ダイキン工業株式会社 スクロール型流体機械
JP2000179481A (ja) * 1998-12-14 2000-06-27 Hitachi Ltd スクロール圧縮機
KR100414123B1 (ko) * 2001-12-26 2004-01-07 엘지전자 주식회사 스크롤 압축기의 마찰손실 저감 장치
KR100451232B1 (ko) * 2002-02-19 2004-10-02 엘지전자 주식회사 스크롤 압축기의 가스 압축력 지지구조
KR101166582B1 (ko) 2003-10-17 2012-07-18 파나소닉 주식회사 스크롤 압축기
JP6578504B2 (ja) * 2013-04-30 2019-09-25 パナソニックＩｐマネジメント株式会社 スクロール圧縮機
JP6484796B2 (ja) * 2014-04-24 2019-03-20 パナソニックＩｐマネジメント株式会社 スクロール圧縮機
JP2017082840A (ja) * 2015-10-26 2017-05-18 ダイキン工業株式会社 軸受構造、及びスクロール型圧縮機
CN109996962B (zh) * 2016-11-24 2021-02-26 松下知识产权经营株式会社 不对称涡旋式压缩机
JP6688972B2 (ja) * 2017-01-27 2020-04-28 パナソニックＩｐマネジメント株式会社 スクロール圧縮機
JP6767640B2 (ja) * 2019-02-06 2020-10-14 パナソニックＩｐマネジメント株式会社 スクロール圧縮機

Also Published As

Publication number Publication date
JPWO2021157332A1 (de) 2021-08-12
CN115053069B (zh) 2024-08-13
EP4102074A4 (de) 2023-07-12
WO2021157332A1 (ja) 2021-08-12
CN115053069A (zh) 2022-09-13

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