EP4098877A1 - Spiralverdichter - Google Patents

Spiralverdichter Download PDF

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Publication number
EP4098877A1
EP4098877A1 EP20916754.3A EP20916754A EP4098877A1 EP 4098877 A1 EP4098877 A1 EP 4098877A1 EP 20916754 A EP20916754 A EP 20916754A EP 4098877 A1 EP4098877 A1 EP 4098877A1
Authority
EP
European Patent Office
Prior art keywords
scroll
orbiting
fixed
orbiting scroll
fixed scroll
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
EP20916754.3A
Other languages
English (en)
French (fr)
Other versions
EP4098877A4 (de
Inventor
Akifumi HYODO
Yusuke Imai
Atsushi Sakuda
Satoshi Iitsuka
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 EP4098877A1 publication Critical patent/EP4098877A1/de
Publication of EP4098877A4 publication Critical patent/EP4098877A4/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
    • 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
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • 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
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/90—Improving properties of machine parts
    • F04C2230/92—Surface treatment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2251/00—Material properties
    • F05C2251/10—Hardness

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 and PTL 2 disclose scroll compressors used in air conditioners and the like.
  • a fixed spiral wrap of a fixed scroll and an orbiting spiral wrap of an orbiting scroll are engaged with each other and the orbiting scroll is made to orbit to compress a refrigerant.
  • surface treatment such as anodization coating treatment or plating treatment is performed on a surface of either one of the fixed scroll and the orbiting scroll to prevent seizing between the fixed scroll and the orbiting scroll.
  • an alloy containing aluminum as a main component is used for the fixed scroll and the orbiting scroll.
  • the orbiting scroll is subjected to alumite treatment and then the surface of the orbiting scroll is smoothed by pressure treatment.
  • aluminum is used for the fixed scroll and the orbiting scroll.
  • the coating on one of the fixed scroll and the orbiting scroll is of hard oxidized alumite, and the coating on the other is of semihard oxidized alumite.
  • the present disclosure provides a scroll compressor that prevents seizing between a fixed scroll and an orbiting scroll and has further improved efficiency and reliability.
  • both the fixed scroll and orbiting scroll are made of light metal, an axial gap is formed between an orbiting spiral wrap of the orbiting scroll and a fixed scroll bottom surface on the wrap surface side of the fixed scroll and between a fixed spiral wrap of the fixed scroll and an orbiting scroll bottom surface on the wrap surface side of the orbiting scroll, and an orbiting scroll end plate is pressed against an outer peripheral wall of the fixed scroll in a region with angle of rotation larger than outer wall maximum involute angle of the fixed scroll.
  • One or both of the fixed scroll and the orbiting scroll are subjected to a surface treatment, and one of the fixed scroll and the orbiting scroll has a higher hardness than the other.
  • the present disclosure provides a scroll compressor that has improved efficiency and reliability by suppressing an increase in the resistance against sliding between a fixed scroll and an orbiting scroll, an increase in rotational moment, and the like.
  • 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. Lower end 13b of rotary shaft 13 is rotatably supported by sub-bearing 18 disposed at the lower portion of hermetic container 1.
  • 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, an orbiting spiral wrap 12b erecting from a wrap side end surface of orbiting scroll end plate 12a, and cylindrical boss portion 12c formed on an anti-wrap side end surface of orbiting scroll end plate 12a (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. Eccentric shaft 13a is inserted in boss portion 12c, and boss portion 12c is accommodated in boss housing 32.
  • Fixed scroll 11 is fixed to main bearing 30 by outer peripheral wall 11c using a plurality of bolts (not shown). Meanwhile, orbiting scroll 12 is supported by fixed scroll 11 via 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. Accordingly, orbiting scroll 12 makes an orbit motion without spinning with respect to fixed scroll 11.
  • spin-restraining member 17 such as an Oldham ring.
  • Oil storage part 4 that stores lubricating oil is formed at the bottom 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, bearing 31, and into boss portion 12c through rotary shaft oil supply hole 13c formed in rotary shaft 13.
  • the refrigerant sucked through refrigerant suction pipe 2 is guided 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 an upper portion in hermetic container 1, and is discharged from refrigerant discharge pipe 3.
  • Fig. 2 illustrates a meshed configuration of fixed scroll 11 and orbiting scroll 12 of scroll compressor 100 according to the present exemplary embodiment.
  • An axial gap is formed between the distal end surface of fixed spiral wrap 11b and orbiting scroll bottom surface 12e and between fixed scroll bottom surface 11d and the distal end surface of orbiting spiral wrap 12b.
  • a region with angle of rotation larger than outer wall maximum involute angle of fixed scroll 11 is hatched.
  • the hatched region is a portion of fixed scroll 11 existing in the outer side of the involute curve extending to the maximum involute angle of fixed scroll 11 in a plan view of fixed scroll 11, and corresponds to outer peripheral wall 11c.
  • one or both of fixed scroll 11 and orbiting scroll 12 are subjected to surface treatment.
  • anodization coating (alumite) treatment is known.
  • the difference between the hardness of fixed scroll 11 and the hardness of orbiting scroll 12 causes the scroll having the lower hardness, among fixed scroll 11 and orbiting scroll 12, to wear by a proper amount.
  • an axial gap is formed between the distal end surface of fixed spiral wrap 11b of fixed scroll 11 and orbiting scroll bottom surface 12e of orbiting scroll 12 and between fixed scroll bottom surface 11d and the distal end surface of orbiting spiral wrap 12b. This avoids, even when the scroll having a low hardness wears by a proper amount, sandwiching of orbiting spiral wrap 12b of orbiting scroll 12 between fixed scroll bottom surface 11d and orbiting scroll bottom surface 12e.
  • orbiting scroll 12 can be pressed against fixed scroll 11. This reduces leakage of the refrigerant from compression chamber 15 to suction port 15a, and leakage loss can be reduced.
  • region with angle of rotation larger than outer wall maximum involute angle 11e (hatched portion in Fig. 3 ) of fixed scroll 11 is made to slide against the outer peripheral portion of orbiting scroll end plate 12a to reduce the turning moment of orbiting scroll 12 and improve the resistance against turning of orbiting scroll 12. Therefore, gas leakage due to turning of orbiting scroll 12 can be suppressed. Accordingly, the efficiency of the compressor can be further improved by a combination with the above-described effect of reducing the leakage loss of the refrigerant.
  • turning refers to a state in which orbiting scroll 12 separates from fixed scroll 11 by a push back force from compression chamber 15.
  • Fig. 4 is a sectional view illustrating a relationship between axial gap Hf between fixed spiral wrap 11b and orbiting scroll bottom surface 12e and axial gap Ho between orbiting spiral wrap 12b and fixed scroll bottom surface 11d.
  • Axial gap Hf between fixed spiral wrap 11b and orbiting scroll bottom surface 12e and axial gap Ho between orbiting spiral wrap 12b and fixed scroll bottom surface 11d are set to satisfy Hf ⁇ Ho in the present exemplary embodiment.
  • the hardness of fixed scroll 11 is higher than the hardness of orbiting scroll 12.
  • anodization coating (alumite) treatment is performed as the surface treatment.
  • the method of surface treatment is not limited to the anodization coating treatment.
  • a plating treatment can raise the hardness of a member such as a fixed scroll and an orbiting scroll, and thus can obtain a similar effect as that of the present disclosure.
  • both the fixed scroll and orbiting scroll are made of light metal, and an axial gap is formed between the orbiting spiral wrap of the orbiting scroll and the fixed scroll bottom surface on the wrap surface side of the fixed scroll and between the fixed spiral wrap of the fixed scroll and the orbiting scroll bottom surface on the wrap surface side of the orbiting scroll.
  • the end plate of the orbiting scroll is pressed against the region with angle of rotation larger than outer wall maximum involute angle of the fixed scroll, and one or both of the fixed scroll and the orbiting scroll are subjected to surface treatment so that either one has a higher hardness than the other.
  • the scroll compressor is configured such that axial gap Hf between the fixed spiral wrap of the fixed scroll and the orbiting scroll bottom surface and axial gap Ho between the orbiting spiral wrap of the orbiting scroll and the fixed scroll bottom surface satisfy the relationship of Hf ⁇ Ho.
  • the hardness of the fixed scroll is made higher than the hardness of the orbiting scroll.
  • the resistance against turning of the orbiting scroll can be further reliably improved, and the friction between the fixed spiral wrap and the orbiting spiral wrap is suppressed even in a transition period between operating states and an abnormal state of the compressor, so that the reliability of the scroll compressor can be improved.
  • R32 carbon dioxide, or a refrigerant having a double bond between carbons can be used.
  • the scroll compressor according to the present disclosure can improve reliability and efficiency, and is thus useful for a hot water heating device, an air conditioning device, a water heater, or a refrigeration cycle device such as a freezing machine.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP20916754.3A 2020-01-27 2020-12-22 Spiralverdichter Pending EP4098877A4 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2020010489 2020-01-27
PCT/JP2020/047805 WO2021153099A1 (ja) 2020-01-27 2020-12-22 スクロール圧縮機

Publications (2)

Publication Number Publication Date
EP4098877A1 true EP4098877A1 (de) 2022-12-07
EP4098877A4 EP4098877A4 (de) 2023-07-26

Family

ID=77078978

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20916754.3A Pending EP4098877A4 (de) 2020-01-27 2020-12-22 Spiralverdichter

Country Status (4)

Country Link
EP (1) EP4098877A4 (de)
JP (1) JP7454786B2 (de)
CN (1) CN115023550A (de)
WO (1) WO2021153099A1 (de)

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63171681U (de) 1987-04-30 1988-11-08
JPH0392590A (ja) * 1989-09-05 1991-04-17 Toyota Autom Loom Works Ltd スクロール型圧縮機
JPH05240174A (ja) * 1992-03-03 1993-09-17 Mitsubishi Heavy Ind Ltd スクロール型流体機械
JP3219497B2 (ja) * 1992-10-22 2001-10-15 三菱重工業株式会社 スクロール型流体機械
JPH06317269A (ja) * 1993-05-10 1994-11-15 Hitachi Ltd 密閉形スクロール圧縮機
JP4618478B2 (ja) * 2001-08-01 2011-01-26 株式会社豊田自動織機 スクロール型圧縮機
JP2007132297A (ja) 2005-11-11 2007-05-31 Sanden Corp スクロール型流体機械
JP2009008006A (ja) * 2007-06-28 2009-01-15 Panasonic Corp スクロール圧縮機
US8167594B2 (en) * 2009-02-03 2012-05-01 Scrolllabs Corporation Scroll compressor with materials to allow run-in
JP2014196691A (ja) * 2013-03-29 2014-10-16 アネスト岩田株式会社 旋回スクロール体およびそれを用いたスクロール流体機械

Also Published As

Publication number Publication date
CN115023550A (zh) 2022-09-06
JPWO2021153099A1 (de) 2021-08-05
EP4098877A4 (de) 2023-07-26
JP7454786B2 (ja) 2024-03-25
WO2021153099A1 (ja) 2021-08-05

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Ipc: F04C 18/02 20060101AFI20230620BHEP