EP4102074B1 - Spiralverdichter - Google Patents

Spiralverdichter

Info

Publication number
EP4102074B1
EP4102074B1 EP21751392.8A EP21751392A EP4102074B1 EP 4102074 B1 EP4102074 B1 EP 4102074B1 EP 21751392 A EP21751392 A EP 21751392A EP 4102074 B1 EP4102074 B1 EP 4102074B1
Authority
EP
European Patent Office
Prior art keywords
orbiting
scroll
bearing
tapered shape
rotary 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.)
Active
Application number
EP21751392.8A
Other languages
English (en)
French (fr)
Other versions
EP4102074A1 (de
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
Application granted granted Critical
Publication of EP4102074B1 publication Critical patent/EP4102074B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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.
  • Japanese Patent No. 4892238 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.
  • KR 100 414 123 B1 discloses a friction loss reducing device for a scroll compressor.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 .
  • 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.
  • 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.
  • 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.
  • 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.

Landscapes

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

Claims (5)

  1. Spiralverdichter, umfassend:
    eine Verdichtungsmechanismus-Einheit (10), die ein Kältemittel verdichtet und eine feststehende Spirale (11), eine umlaufende Spirale (12) und eine Drehwelle (13) umfasst, die eine Exzenterwelle (13a) aufweist, um die umlaufende Spirale (12) zum Umlaufen anzutreiben;
    eine Motormechanismus-Einheit (20), die die Verdichtungsmechanismus-Einheit (10) antreibt; und
    einen hermetischen Behälter (1), der die Verdichtungsmechanismus-Einheit (10) und die Motormechanismus-Einheit (20) aufnimmt,
    wobei die feststehende Spirale (11) eine Feststehende-Spirale-Endplatte (11a), die eine Scheibenform aufweist, und eine feststehende Spiralwindung (11b), die sich von der Feststehende-Spirale-Endplatte (11a) erhebt, umfasst,
    wobei die umlaufende Spirale (12) eine Umlaufende-Spirale-Endplatte (12a), die eine Scheibenform aufweist, eine umlaufende Spiralwindung (12b), die sich von einer Oberfläche der Umlaufende-Spirale-Endplatte (12a) erhebt, einen Nabenabschnitt (12c), der eine zylindrische Form aufweist und auf einer anderen Oberfläche der Umlaufende-Spirale-Endplatte (12a) angeordnet ist, und ein Umlauflager (13d), das in den Nabenabschnitt (12c) eingesetzt ist und die Exzenterwelle (13a) aufnimmt, umfasst,
    wobei die feststehende Spiralwindung (11b) und die umlaufende Spiralwindung (12b) ineinandergreifen, um zwischen der feststehenden Spiralwindung (11b) und der umlaufenden Spiralwindung (12b) eine Vielzahl von Verdichtungskammern (15) zu bilden,
    wobei die umlaufende Spirale (12) durch einen Gegendruck von einer Seite der anderen Oberfläche der Umlaufende-Spirale-Endplatte (12a) her gegen die feststehende Spirale (11) gepresst wird,
    wobei das Umlauflager (13d) ein erstes Ende (13da) auf einer Seite der Umlaufende-Spirale-Endplatte (12a) und ein zweites Ende (13db) auf einer entgegengesetzten Seite des ersten Endes (13da) aufweist, wobei die Exzenterwelle (13a) vom zweiten Ende (13db) her in das Umlauflager (13d) eingesetzt ist, und
    wobei der Spiralverdichter derart gestaltet ist, dass
    eine Innenwand (13dc) des Umlauflagers (13d) eine erste konische Form (T1) aufweist, deren Durchmesser von einer Seite eines ersten Endes (13da) in Richtung zu einer Seite eines zweiten Endes (13db) zunimmt, oder
    ein Außenumfang der in das Umlauflager (13d) einsetzten Exzenterwelle (13a) eine zweite konische Form (T2) aufweist, deren Durchmesser von der Seite des ersten Endes (13da) In Richtung zur Seite des zweiten Endes (13db) abnimmt,
    dadurch gekennzeichnet, dass
    in einer Schnittansicht in einer Ebene, die eine Achse des Umlauflagers (13d) umfasst, die erste konische Form (T1) oder die zweite konische Form (T2) derart ausgestaltet ist, dass
    ein Winkel θ zwischen einer Oberfläche der ersten konischen Form (T1) oder der zweiten konischen Form (T2) und der Achse größer ist als ein Winkel, um den die Drehwelle (13) kippen kann, und
    einen unten dargestellten relationalen Ausdruck erfüllt, wobei L ein Abstand zwischen dem ersten Ende (13da) des Umlauflagers (13d) und einem Anfangspunkt der ersten konischen Form (T1) oder der zweiten konischen Form (T2) ist, d ein Durchmesser der Exzenterwelle (13a) ist und D ein Durchmesser der Innenwand (13dc) des Umlauflagers (13d) ist, L tan θ + d / cosθ < D .
  2. Spiralverdichter nach Anspruch 1, wobei die erste konische Form (T1) oder die zweite konische Form (T2) ab einer Position in der Mitte eines Bereichs beginnt, der sich entlang einer axialen Richtung des Umlauflagers (13d) erstreckt und in dem die Innenwand (13dc) des Umlauflagers (13d) und der Außenumfang (13ab) der Exzenterwelle (13a) gegeneinander gleiten.
  3. Spiralverdichter nach Anspruch 1 oder 2, wobei die erste konische Form (T1) oder die zweite konische Form (T2) eine gerade Linie, eine kontinuierliche Kurve oder eine Kombination aus der geraden Linie und der kontinuierlichen Kurve umfasst.
  4. Spiralverdichter nach Anspruch 1, wobei
    der Spiralverdichter ein Hauptlager (31) und ein Nebenlager (18) umfasst, die die Drehwelle (13) drehbar lagern, und
    der Winkel, um den die Drehwelle (13) kippen kann, durch einen Zwischenraum zwischen dem Hauptlager (31) und der Drehwelle (13) und einen Zwischenraum zwischen dem Nebenlager (18) und der Drehwelle (13) definiert wird.
  5. Spiralverdichter nach einem der Ansprüche 1 bis 4, wobei
    die mehreren Verdichtungskammern (15) eine erste Verdichtungskammer (15A), die auf einer Außenwandseite der umlaufenden Spiralwindung (12b) angeordnet ist, und eine zweite Verdichtungskammer (15B), die auf einer Innenwandseite der umlaufenden Spiralwindung (12b) angeordnet ist, umfassen und
    ein Ansaugvolumen der ersten Verdichtungskammer (15A) größer ist als ein Ansaugvolumen der zweiten Verdichtungskammer (15B).
EP21751392.8A 2020-02-05 2021-01-19 Spiralverdichter Active EP4102074B1 (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 (3)

Publication Number Publication Date
EP4102074A1 EP4102074A1 (de) 2022-12-14
EP4102074A4 EP4102074A4 (de) 2023-07-12
EP4102074B1 true EP4102074B1 (de) 2025-07-23

Family

ID=77199272

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21751392.8A Active EP4102074B1 (de) 2020-02-05 2021-01-19 Spiralverdichter

Country Status (4)

Country Link
EP (1) EP4102074B1 (de)
JP (1) JP7689309B2 (de)
CN (1) CN115053069B (de)
WO (1) WO2021157332A1 (de)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102863008B1 (ko) * 2023-08-31 2025-09-23 엘지전자 주식회사 스크롤 압축기

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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
US11098715B2 (en) * 2016-11-24 2021-08-24 Panasonic Intellectual Property Management Co., Ltd. Asymmetrical scroll compressor
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
EP4102074A1 (de) 2022-12-14
CN115053069B (zh) 2024-08-13
EP4102074A4 (de) 2023-07-12
JPWO2021157332A1 (de) 2021-08-12
JP7689309B2 (ja) 2025-06-06
WO2021157332A1 (ja) 2021-08-12
CN115053069A (zh) 2022-09-13

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