EP3444476B1 - Scroll fluid machine - Google Patents

Scroll fluid machine Download PDF

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Publication number
EP3444476B1
EP3444476B1 EP17846367.5A EP17846367A EP3444476B1 EP 3444476 B1 EP3444476 B1 EP 3444476B1 EP 17846367 A EP17846367 A EP 17846367A EP 3444476 B1 EP3444476 B1 EP 3444476B1
Authority
EP
European Patent Office
Prior art keywords
tip
wall
scroll
end plate
tooth
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
EP17846367.5A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3444476A4 (en
EP3444476A1 (en
Inventor
Hajime Sato
Yoshiyuki Kimata
Yohei Hotta
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 Thermal Systems Ltd
Original Assignee
Mitsubishi Heavy Industries Thermal Systems 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 Thermal Systems Ltd filed Critical Mitsubishi Heavy Industries Thermal Systems Ltd
Publication of EP3444476A1 publication Critical patent/EP3444476A1/en
Publication of EP3444476A4 publication Critical patent/EP3444476A4/en
Application granted granted Critical
Publication of EP3444476B1 publication Critical patent/EP3444476B1/en
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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
    • F04C18/0269—Details concerning the involute wraps
    • F04C18/0276—Different wall heights
    • 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
    • F04C18/0269—Details concerning the involute wraps
    • F04C18/0284—Details of the wrap tips

Definitions

  • the present invention relates to a scroll fluid machine.
  • a scroll fluid machine in which a fixed scroll member and an orbiting scroll member each having a spiral wall provided on an end plate mesh with each other so as to perform a revolution orbiting movement and a fluid is compressed or expanded.
  • a so-called stepped scroll compressor which is described in PTL 1 and PTL 3 is known.
  • step portions are provided at positions of tooth tip surfaces and tooth bottom surfaces of spiral walls of a fixed scroll and an orbiting scroll in a spiral direction and a height on an outer peripheral side of each wall is higher than a height on an inner peripheral side thereof with each step portion as a boundary.
  • the stepped scroll compressor is compressed (three-dimensionally compressed) not only in a circumferential direction of the wall but also in a height direction thereof, and thus, compared to a general scroll compressor (two-dimensional compressed) which does not have the step portion, an amount of displacement increases, and thus, compressor capacity can increase.
  • the inventors are studying to provide a continuously inclined portion instead of the step portion provided on the wall and the end plate.
  • a groove portion for receiving a tip seal is formed on a tooth tip, which is a tip of the wall, along a spiral direction of the wall.
  • the tip seal comes into contact with a tooth bottom facing the tooth tip while sliding on the tooth bottom, and thus, a fluid leakage is suppressed.
  • the present invention is made in consideration of the above-described circumstances, and an object thereof is to provide a scroll fluid machine capable of effectively exerting a function of the tip seal even in a case where the continuously inclined portion is provided on the wall and the end plate so as to improve performance.
  • a scroll fluid machine of the present invention adopts the following means.
  • a scroll fluid machine including: a first scroll member in which a spiral first wall is provided on a first end plate; a second scroll member in which a spiral second wall is provided on a second end plate disposed to face the first end plate and the second wall meshes with the first wall such that the second scroll member performs a revolution orbiting movement relative to the first scroll member; and an inclined portion in which, if the first wall and the second wall are displayed to extend in spiral directions thereof, an inter-facing surface distance between the first end plate and the second end plate facing each other continuously decreases with a constant inclination in the spiral directions of the first wall and the second wall thereof from outer peripheral sides toward inner peripheral sides thereof, in which a tip seal which comes into contact with a facing tooth bottom so as to seal a fluid is provided in a groove portion formed on a tooth tip of each of the first wall and the second wall corresponding to the inclined portion, a biasing member which biases the tip seal toward the tooth bottom side is provided between the tip seal and the
  • the inclined portion is provided in which the inter-facing surface distance between the first end plate and the second end plate continuously decreases with constant inclination from outer peripheral side of the wall toward inner peripheral side thereof. Accordingly, as a fluid sucked from the outer peripheral side flows toward the inner peripheral side, the fluid not only is compressed by a decrease of a compression chamber according to a spiral shape of the wall but also is further compressed by a decrease of the inter-facing surface distance between the end plates.
  • both scroll members perform the revolution orbiting movement, in the inclined portion, positions of the tooth tip and the tooth bottom are relatively deviated, and thus, a tip clearance between the tooth tip and the tooth bottom is changed for each orbiting angle. Accordingly, the biasing member which biases the tip seal toward the tooth bottom side is provided between the tip seal and the groove bottom, and thus, even in a case where the tip clearance is changed for each orbiting angle, the tip clearance can follow the tip seal. Accordingly, a fluid leakage is reduced, a function of the tip seal is effectively exerted, and performance of the scroll fluid machine can be improved.
  • the biasing member has a deformation amount equal to or more than an amount by which a tip clearance between the tooth tip of the wall and the tooth bottom of the end plate facing the tooth tip is changed in an orbiting angle of 360°.
  • the biasing member can be deformed to be equal to or more than the change amount of the tip clearance, and thus, the tip seal can be always pressed to the tooth bottom over the entire orbiting angle.
  • the biasing member has a deformation amount which is smaller than a depth of the groove portion.
  • the deformation amount of the biasing member is smaller than the depth of the groove portion, and thus, during assembly, it is possible to prevent the tip seal from falling off from the groove portion.
  • the biasing member is a spring member which is disposed between the tip seal and the groove bottom.
  • the spring member is disposed the tip seal and the groove bottom.
  • a leaf spring is used as the spring member.
  • the biasing member is a plurality of protrusion portions which are formed on a bottom portion of the tip seal.
  • the plurality of protrusion portions formed on the bottom portion of the tip seal are set to the biasing member.
  • An elastic deformation is performed by extending or contracting the protrusion portions or bending the protrusion portions.
  • the protrusion portions are formed together with the tip seal, and thus, the number of parts is reduced and the assembly is easily performed.
  • the biasing member has a deformation amount less than an amount by which a tip clearance between the tooth tip of the wall and the tooth bottom of the end plate facing the tooth tip is changed in an orbiting angle of 360°, and is a plurality of protrusion portions formed on a bottom portion of the tip seal.
  • the deformation amount of the biasing member is less than the change amount of the tip clearance, and thus, if the tip clearance is equal to or more than a predetermined value, the tip seal floats from the groove bottom due to a pressure of the fluid entering the bottom surface side of the tip seal.
  • the plurality of protrusion portions are formed on the bottom portion of the tip seal, and thus, the flow of the fluid is obstructed by a labyrinth seal effect. Accordingly, it is possible to reduce the fluid leakage.
  • the respective protrusion portions are provided to be repeated in the spiral direction of the tip seal. Accordingly, it is possible to suppress the fluid leakage in the spiral direction.
  • the biasing member which biases the tip seal toward the tooth bottom side is provided between the tip seal and the groove bottom, and thus, even in a case where the tip clearance is changed for each orbiting angle, the tip clearance can follow the tip seal. Accordingly, a fluid leakage is reduced, a function of the tip seal is effectively exerted, and performance of the scroll fluid machine can be improved.
  • a fixed scroll (first scroll member) 3 and an orbiting scroll (second scroll member) 5 of a scroll compressor (scroll fluid machine) 1 are shown.
  • the scroll compressor 1 is used as a compressor which compresses a gas refrigerant (fluid) which performs a refrigerating cycle of an air conditioner or the like.
  • Each of the fixed scroll 3 and the orbiting scroll 5 is a metal compression mechanism which is formed of an aluminum alloy or steel, and is accommodated in a housing (not shown).
  • the fixed scroll 3 and the orbiting scroll 5 suck a fluid, which is introduced into the housing, from an outer peripheral side, and discharge the compressed fluid from a discharge port 3c positioned at a center of the fixed scroll 3 to the outside.
  • the fixed scroll 3 is fixed to the housing, and as shown in Figs. 1A , includes an approximately disk-shaped end plate (first end plate) 3a, and a spiral wall (first wall) 3b which is erected on one side surface of the end plate 3a.
  • the orbiting scroll 5 includes an approximately disk-shaped end plate (second end plate) 5a and a spiral wall (second wall) 5b which is erected on one side surface of the end plate 5a.
  • a spiral shape of each of the walls 3b and 5b is defined by using an involute curve or an Archimedes curve.
  • the fixed scroll 3 and the orbiting scroll 5 are assembled to each other such that centers thereof are separated from each other by an orbiting radius p, the walls 3b and 5b mesh with each other with phases deviated from each other by 180°, and a slight clearance (tip clearance) in a height direction at the room temperature is provided between tooth tips and tooth bottoms of the walls 3b and 5b of both scrolls. Accordingly, a plurality pairs of compression chambers which are formed to be surrounded by the end plates 3a and 5a and the walls 3b and 5b are symmetrically formed about a scroll center between both scrolls 3 and 5.
  • the orbiting scroll 5 performs a revolution orbiting movement around the fixed scroll 3 by a rotation prevention mechanism such as an Oldham ring (not shown).
  • an inclined portion is provided, in which an inter-facing surface distance L between both end plates 3a and 5a facing each other continuously decrease from an outer peripheral side of each of the spiral walls 3b and 5b toward an inner peripheral side thereof.
  • a wall inclined portion 5b1 whose height continuously decreases from an outer peripheral side toward an inner peripheral side is provided.
  • an end plate inclined portion 3a1 (refer to Fig. 1A ) which is inclined according to an inclination of the wall inclined portion 5b1 is provided.
  • a continuously inclined portion is formed by the wall inclined portion 5bl and the end plate inclined portion 3a1.
  • a wall inclined portion 3b1 whose height is continuously inclined from the outer peripheral side toward the inner peripheral side is provided on the wall 3b of the fixed scroll 3, and an end plate inclined portion 5a1 facing a tooth tip of the wall inclined portion 3b1 is provided on the end plate 5a of the orbiting scroll 5.
  • Coating is applied to the wall inclined portions 3b1 and 5b1 and/or the end plate inclined portions 3a1 and 5al.
  • the coating includes manganese phosphate processing, nickel phosphorus plating, or the like.
  • wall flat portions 5b2 and 5b3 each having a constant height are respectively provided on the innermost peripheral side and the outermost peripheral side of the wall 5b of the orbiting scroll 5.
  • Each of the wall flat portions 5b2 and 5b3 is provided over a region of 180° around a center O2 (refer to Fig. 1A ) of the orbiting scroll 5.
  • Wall inclined connection portions 5b4 and 5b5 which become curved portions are respectively provided at positions at which the wall flat portions 5b2 and 5b3 and the wall inclined portion 5b1 are connected to each other.
  • end plate flat portions 5a2 and 5a3 each having a constant height are provided.
  • Each of the end plate flat portions 5a2 and 5a3 is provided over a region of 180° around the center of the orbiting scroll 5.
  • End plate inclined connection portions 5a4 and 5a5 which become curved portions are respectively provided at positions at which the end plate flat portions 5a2 and 5a3 and the end plate inclined portion 5a1 are connected to each other.
  • end plate flat portions 3a2 and 3a3, wall flat portions 3b2 and 3b3, end plate inclined connection portions 3a4 and 3a5, and wall inclined connection portions 3b4 and 3b5 are provided.
  • Fig. 5 is a schematic view showing the walls 3b and 5b which are displayed to extend in a spiral direction.
  • the wall flat portions 3b2 and 5b2 on the innermost peripheral side are provided over a distance D2
  • the wall flat portions 3b3 and 5b3 on the outermost peripheral side are provided over a distance D3.
  • Each of the distance D2 and the distance D3 is a length corresponding to the region which becomes 180° around each of the centers O1 and O2 of the respective scrolls 3 and 5.
  • the wall inclined portions 3b1 and 5b1 are provided over the distance D1 between the wall flat portions 3b3 and 5b2 on the innermost peripheral side and the wall flat portions 3b3 and 5b3 on the outermost peripheral side.
  • the inclination ⁇ of the inclined portion is constant in a circumferential direction in which each of the spiral walls 3b and 5b extends.
  • Fig. 6 is a partially enlarged view showing a region indicated by a reference numeral Z in Fig. 1B in an enlarged manner.
  • a tip seal 7 is provided in the tooth tip of the wall 3b of the fixed scroll 3.
  • the tip seal 7 is formed of a resin and comes into contact with the tooth bottom of the end plate 5a of the facing orbiting scroll 5 so as to seal a fluid.
  • the tip seal 7 is accommodated in a tip seal groove 3d which is formed on the tooth tip of the wall 3b in the circumferential direction.
  • a compressed fluid enters the tip seal groove 3d, presses the tip seal 7 from a rear surface thereof to push the tip seal 7 toward the tooth bottom side, and thus, the tip seal 7 comes into contact with the facing the tooth bottom.
  • a tip seal is also provided in the tooth tip of the wall 5b of the orbiting scroll 5.
  • a height Hc of the tip seal 7 in the height direction of the wall 3b is constant in the circumferential direction.
  • both the scrolls 3 and 5 perform the revolution orbiting movement relative to each other, the positions of the tooth tip and the tooth bottom are relatively deviated by an orbiting diameter (orbiting radius p ⁇ 2).
  • the tip clearance between the tooth tip and the tooth bottom is changed due to the positional deviation between the tooth tip and the tooth bottom.
  • a tip clearance T decreases
  • Fig. 7B the tip clearance T increases.
  • the tip seal 7 is pressed to the tooth bottom side of the end plate 5a by the compressed fluid from the rear surface, and the tip seal 7 can follow the tooth bottom so as to seal the tooth bottom.
  • the present embodiment has the following configuration such that the tip seal 7 follows the tip clearance T changed for each orbiting angle as shown in Fig. 7 .
  • a leaf spring (spring member) 11 is installed between a bottom portion 7a of the tip seal 7 and a groove bottom 3dl of the tip seal groove 3d.
  • the leaf spring 11 biases the tip seal 7 to the facing tooth bottom side (upper side in Figs. 8A and 8B ).
  • An elastic deformation amount of the leaf spring 11 is set to be equal to or more than a tip clearance change amount ⁇ T.
  • the tip clearance change amount ⁇ T is an amount by which the tip clearance T is changed in the orbiting angle of 360° and is expressed by the following Expression using the orbiting radius p and the inclination ⁇ of each of the wall inclined portions 3b1 and 5b1.
  • ⁇ T 2 ⁇ ⁇ tan ⁇
  • a deformation amount of the leaf spring 11 is set to be smaller than a depth of the tip seal groove 3d. That is, in a case where only weight of the tip seal 7 is applied to the leaf spring 11, a spring constant of the leaf spring 11 is set such that a height (a dimension in a vertical direction in Figs. 8A and 8B ) of the leaf spring 11 is smaller than that of the tip seal groove 3d.
  • Fig. 8A shows a state in which the tip clearance T is the smallest tip clearance in the orbiting angle of 360°, the leaf spring 11 is greatly contracted, and the tip seal 7 is pressed to the facing tooth bottom side (refer to Fig. 9A ).
  • Fig. 8B shows a state in which the tip clearance T is the greatest tip clearance in the orbiting angle of 360° (refer to Fig. 9B ). Even in this state, the elastic deformation amount of the leaf spring 11 is sufficiently secured, and thus, the tip seal 7 is pressed to the facing tooth bottom side.
  • the above-described scroll compressor 1 is operated as follows.
  • the orbiting scroll 5 performs the revolution orbiting movement around the fixed scroll 3 by a drive source such as an electric motor (not shown). Accordingly, the fluid is sucked from the outer peripheral sides of the respective scrolls 3 and 5, and the fluid is taken into the compression chambers surrounded by the respective walls 3b and 5b and the respective end plates 3a and 5a. The fluid in the compression chambers is sequentially compressed while being moved from the outer peripheral side toward the inner peripheral side, and finally, the compressed fluid is discharged from a discharge port 3c formed in the fixed scroll 3.
  • a drive source such as an electric motor
  • the fluid When the fluid is compressed, the fluid is compressed in the height directions of the walls 3b and 5b in the inclined portions formed by the end plate inclined portions 3a1 and 5a1 and the wall inclined portions 3b1 and 5b1, and thus, the fluid is three-dimensionally compressed.
  • the leaf spring 11 which biases the tip seal 7 toward the tooth bottom side is provided between the tip seal 7 and the groove bottom 3dl, and thus, even in a case where the tip clearance T is changed for each orbiting angle, the tip clearance T can follow the tip seal 7. Accordingly, a fluid leakage is reduced, a function of the tip seal 7 is effectively exerted, and performance of the scroll compressor 1 can be improved.
  • the deformation amount of the leaf spring 11 is set to be equal or more than the tip clearance change amount ⁇ T, and thus, the tip seal 7 can be always pressed to the tooth bottom over the entire orbiting angle.
  • the deformation amount of the leaf spring 11 is set to be smaller than the depth of the tip seal groove 3d, and thus, during assembly, it is possible to prevent the tip seal 7 from falling off from the tip seal groove 3d.
  • the present embodiment is different from the first embodiment in that a protrusion portion 7c is provided in the tip seal 7 instead of the leaf spring 11 of the first embodiment, and other configurations are similar to those of the first embodiment. Accordingly, hereinafter, only matters different from the first embodiment will be described.
  • a plurality of protrusion portions (biasing members) 7c are integrally formed in the bottom portion 7a of the tip seal 7.
  • Each protrusion portion 7c is formed so as to protrude downward, that is, toward the groove bottom 3d1 side, from the bottom portion 7a.
  • the protrusion portions 7c are provided at predetermined intervals in the spiral direction (longitudinal direction) of the tip seal 7.
  • a length in an extension direction (approximately horizontal direction in Figs. 10A and 10B ) of the protrusion portion 7c is set to a length in which a tip of the protrusion portion 7c comes into contact with the groove bottom 3d1 even when the tip clearance is the greatest tip clearance in the orbiting angle of 360° and is elastically deformed. Accordingly, an elastic deformation amount of the protrusion portion 7c is equal to or more than the tip clearance change amount ⁇ T.
  • the plurality of protrusion portion 7c are bent, and thus, a biasing force is applied to the tip seal 7.
  • the protrusion portion 7c may be extend or contracted in the extension direction of the protrusion portion. That is, the tip seal 7 may be biased using an elastic force generated when the protrusion portion is extended or contracted in the extension direction.
  • the plurality of protrusion portions 7c are integrally formed in the bottom portion 7a of the tip seal 7, and thus, biasing means can be applied to the tip seal as one member, the number of parts are reduced, and the assembly is easily performed.
  • the present embodiment is different from the second embodiment in that the deformation amount of the protrusion portion of the second embodiment is less than the tip clearance change amount ⁇ T, and other configurations are similar to those of the second embodiment. Accordingly, hereinafter, only matters different from the second embodiment will be described.
  • each of protrusion portions 7d provided in the tip seal 7 of the present embodiment is shorter than the protrusion portion 7c of the second embodiment.
  • the deformation amount of the protrusion portion 7d is less than the tip clearance change amount ⁇ T.
  • a tip of the protrusion portion 7d comes into contact with the groove bottom 3dl, and thus, the tip seal 7 can be biased.
  • the tip clearance T is the greatest tip clearance in the orbiting angle of 360°
  • the tip of the protrusion portion 7d floats from the groove bottom 3dl due to a pressure of the fluid entering the bottom portion 7a side of the tip seal 7.
  • the plurality of protrusion portions 7d exert a labyrinth seal effect. That is, the plurality of protrusion portions 7d are provided in the spiral direction of the tip seal 7, and thus, it is possible to reduce the flow of the fluid flowing in the spiral direction by the labyrinth seal effect. As a result, the fluid leakage in the spiral direction can be suppressed, and the performance of the scroll compressor 1 can be improved.
  • the deformation amount of the protrusion portion 7d is set to be less than the tip clearance change amount ⁇ T, and thus, excessive pressing of the tip seal 7 to the tooth bottom can be avoided, and reliability of the tip seal 7 can be improved.
  • the end plate inclined portions 3a1 and 5a1 and the wall inclined portions 3b1 and 5b1 are provided on both scrolls 3 and 5.
  • the end plate inclined portions 3a1 and 5a1 and the wall inclined portions 3b1 and 5b1 may be provided at any one of both scrolls 3 and 5.
  • the wall inclined portion 5bl is provided on the one wall (for example, orbiting scroll 5) and the end plate inclined portion 3a1 is provided on the other end plate 3a
  • the other wall and the one end plate 5a may be flat.
  • it may be combined with a stepped shape of the related art, that is, it may be combined with a shape in which a step portion is provided on the end plate 5a of the orbiting scroll 5 while the end plate inclined portion 3a1 is provided on the end plate 3a of the fixed scroll 3.
  • the wall flat portions 3b2, 3b3, 5b2, and 5b3 and the end plate flat portions 3a2, 3a3, 5a2, and 5a3 are provided.
  • the flat portions on the inner peripheral side and/or the outer peripheral side may be omitted, and the inclined portion may be provided so as to extend to the entire walls 3b and 5b.
  • the scroll compressor is described.
  • the present invention can be applied to a scroll expander which is used as an expander.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP17846367.5A 2016-08-31 2017-08-25 Scroll fluid machine Active EP3444476B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016169193A JP6382268B2 (ja) 2016-08-31 2016-08-31 スクロール流体機械
PCT/JP2017/030636 WO2018043362A1 (ja) 2016-08-31 2017-08-25 スクロール流体機械

Publications (3)

Publication Number Publication Date
EP3444476A1 EP3444476A1 (en) 2019-02-20
EP3444476A4 EP3444476A4 (en) 2019-03-13
EP3444476B1 true EP3444476B1 (en) 2021-01-06

Family

ID=61301007

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17846367.5A Active EP3444476B1 (en) 2016-08-31 2017-08-25 Scroll fluid machine

Country Status (4)

Country Link
EP (1) EP3444476B1 (ja)
JP (1) JP6382268B2 (ja)
CN (1) CN109312739B (ja)
WO (1) WO2018043362A1 (ja)

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0318601A (ja) * 1989-06-14 1991-01-28 Matsushita Electric Ind Co Ltd スクロール流体装置
JPH05296168A (ja) * 1992-04-17 1993-11-09 Hitachi Ltd スクロール圧縮機
JP3205457B2 (ja) * 1994-03-16 2001-09-04 トキコ株式会社 スクロール式流体機械
JP3881861B2 (ja) * 2001-02-02 2007-02-14 三菱重工業株式会社 スクロール圧縮機
US6585501B2 (en) * 2000-11-06 2003-07-01 Mitsubishi Heavy Industries, Ltd. Scroll compressor sealing
JP4199135B2 (ja) * 2004-01-22 2008-12-17 サンデン株式会社 スクロール圧縮機
JP2009228476A (ja) * 2008-03-19 2009-10-08 Daikin Ind Ltd スクロール圧縮機
JP6180860B2 (ja) 2013-09-11 2017-08-16 三菱重工業株式会社 スクロール圧縮機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP3444476A4 (en) 2019-03-13
CN109312739A (zh) 2019-02-05
WO2018043362A1 (ja) 2018-03-08
CN109312739B (zh) 2020-04-03
JP2018035738A (ja) 2018-03-08
JP6382268B2 (ja) 2018-08-29
EP3444476A1 (en) 2019-02-20

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