EP2497954B1 - Compresseur à spirales - Google Patents

Compresseur à spirales Download PDF

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Publication number
EP2497954B1
EP2497954B1 EP12158522.8A EP12158522A EP2497954B1 EP 2497954 B1 EP2497954 B1 EP 2497954B1 EP 12158522 A EP12158522 A EP 12158522A EP 2497954 B1 EP2497954 B1 EP 2497954B1
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EP
European Patent Office
Prior art keywords
orbiting
stationary
end plate
scroll
side end
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
EP12158522.8A
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German (de)
English (en)
Other versions
EP2497954A2 (fr
EP2497954A3 (fr
Inventor
Yoshiaki Miyamoto
Yoshiyuki Kimata
Youhei Hotta
Hajime Sato
Toshiyuki Goto
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
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Publication date
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Publication of EP2497954A2 publication Critical patent/EP2497954A2/fr
Publication of EP2497954A3 publication Critical patent/EP2497954A3/fr
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Publication of EP2497954B1 publication Critical patent/EP2497954B1/fr
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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
    • F04C18/0246—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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/602—Gap; Clearance

Definitions

  • the present invention relates to a compressor provided with a scroll compression mechanism.
  • a scroll compression mechanism is employed as, for example, a compression mechanism of a scroll compressor, as disclosed in Patent Literature 1, and as a higher-stage compression mechanism of a two-stage compressor, as disclosed in Patent Literature 2.
  • EP 0 106 287 and JP S59-192687 U disclose compressors provided with a scroll compression mechanism.
  • JP S59-912687 U discloses a compressor according to the preamble of claim 1.
  • a stationary scroll and an orbiting scroll are placed with spiral-shaped wall structures thereof combined with each other, and the volume of a compression chamber formed between the wall structures is gradually decreased by causing revolving motion of the orbiting scroll with respect to the stationary scroll, thus compressing a fluid in the compression chamber.
  • the fluid that is introduced to the compression chamber from a peripheral edge portion of the scroll compression mechanism is compressed so as to reach a high-temperature, high-pressure state and is discharged to an external space from a discharge hole provided at a center portion of the stationary scroll.
  • the high temperature and high pressure of the fluid act on the center portion of the scroll compression mechanism and on a rear side, that is, an external portion, of the stationary scroll.
  • a low-temperature, low-pressure fluid is present at a rear side, that is, an external portion, of the orbiting scroll.
  • an outer circumferential end portion of the stationary scroll is generally secured to a housing, and the orbiting scroll is supported at a position closer to the center thereof.
  • the stationary scroll is warped due to thermal expansion and pressure deformation such that the center portion thereof is positioned closer to the orbiting scroll, and the orbiting scroll is also warped in a similar shape.
  • the orbiting scroll does not move at the position where it is supported, an outer circumferential portion thereof deforms so as to approach the stationary scroll. Therefore, at a portion closer to the outer circumference than the position where the orbiting scroll is supported, the orbiting scroll and the stationary scroll deform in directions that cause them to approach each other; that is, they undergo pressure deformation.
  • CO 2 carbon dioxide
  • refrigerant gas when a high-pressure refrigerant, such as CO 2 , is used as refrigerant gas, because the temperature and pressure thereof, when compressed, become higher than those of ordinary refrigerant, the above-described deformation is increased, and tooth tips and tooth bases of the stationary scroll and orbiting scroll easily come in contact at the outer circumferential portions.
  • the present invention has been conceived in light of the above-described circumstances, and an object thereof is to provide a compressor that is capable of ensuring reliability and of enhancing efficiency.
  • an aspect of the present disclosure is a compressor having a scroll compression mechanism including a stationary scroll having a spiral-shaped stationary-side wall structure that is vertically provided on one surface of a stationary-side end plate secured at a stationary-side support position positioned at an outer circumference; and an orbiting scroll having an orbiting-side end plate that is provided with a spiral-shaped orbiting wall structure vertically on one surface thereof to be meshed with the stationary-side wall structure, and that is supported at a position closer to a center than the stationary-side support position in a manner that allows a revolving motion; wherein, for at least one of a clearance between a tip portion of the stationary-side wall structure and the orbiting-side end plate and a clearance between the orbiting-side wall structure and the stationary-side end plate, the clearance at a side further outward than the orbiting-side support position is made larger than the clearance at the center side.
  • the stationary-side wall structure of the stationary scroll and the orbiting-side wall structure of the orbiting scroll are placed so as to be meshed with each other, thus forming the scroll compression mechanism.
  • the stationary-side end plate of the stationary scroll is pressed by this compressed high-temperature, high-pressure medium, it undergoes thermal expansion and pressure deformation. Because the stationary-side end plate is secured at a stationary-side support position positioned closer to an outer circumference, it warps so that a center portion thereof is positioned on the orbiting scroll side.
  • the high temperature and high pressure of the compressed medium at the center portion sandwiched by the stationary scroll and the orbiting scroll act on the orbiting-side end plate of the orbiting scroll. Because low-temperature, low-pressure medium is present at a surface of the orbiting-side end plate on an opposite side with respect to the stationary scroll, the center portion of the orbiting-side end plate warps so as to be separated from the stationary scroll. Specifically, during the compression operation, the stationary-side end plate and the orbiting-side end plate both warp so that the center portions thereof protrude toward the orbiting scroll.
  • the orbiting scroll and the stationary scroll deform in the directions that cause them to approach each other.
  • the clearance at a side further outward than the orbiting-side support position is made larger than the clearance on the center side; therefore, even though the orbiting scroll and the stationary scroll deform in the directions that cause them to approach each other, it is possible to prevent them from coming into contact with each other. Because it is possible to prevent the orbiting scroll and the stationary scroll from coming into contact with each other in this way, it is possible to prevent damage to the stationary-side wall structure or the orbiting-side wall structure caused by the contact, and thus, the reliability can be ensured.
  • the clearance between the tip portion of the stationary-side wall structure and the orbiting-side end plate and the clearance between the orbiting-side wall structure and the stationary-side end plate at the center portion do not become large, a leakage gap does not become large, and it is possible to prevent deterioration of the efficiency.
  • the efficiency can be enhanced as compared with the case in which the overall clearance is increased to prevent a collision.
  • the clearances may be changed by adjusting height of the stationary-side wall structure or the orbiting-side wall structure.
  • the height of the stationary-side wall structure or that of the orbiting-side wall structure can be processed more easily than cutting the surface of the stationary-side end plate or that of the orbiting-side end plate, manufacturing thereof can be facilitated.
  • the clearances be changed so as to be 0.25 to 2.0 ⁇ 10 -3 times the thickness of the stationary-side end plate or the orbiting-side end plate.
  • the clearance at a side further outward than an orbiting-side support position is made larger than the clearance at a center side; therefore, it is possible to prevent damage to the stationary-side wall structure or the orbiting-side wall structure caused by contact between them, and thus, the reliability can be ensured. In addition, it is possible to prevent deterioration of the efficiency.
  • Fig. 1 is a longitudinal cross-sectional view of a compressor according to an embodiment of the present invention.
  • Fig. 2 is a cross-sectional view showing a scroll compression mechanism in Fig. 1 .
  • Fig. 3 is a partial longitudinal cross-sectional view showing a portion of the scroll compression mechanism in Fig. 1 .
  • the compressor 1 is provided with a cylindrical sealed housing 3, a lower-stage rotary compression mechanism 5 provided at a lower portion of the sealed housing 3, a higher-stage scroll compression mechanism 7, and an electric motor 9 that is provided between the rotary compression mechanism 5 and the scroll compression mechanism 7 and that drives the rotary compression mechanism 5 and the scroll compression mechanism 7.
  • the sealed housing 3 has a hollow cylindrical shape in which a cylindrical portion 11 is closed at the top and bottom by welding a bottom portion 13 and a lid portion 15 thereto.
  • the electric motor 9 is provided with a driving shaft 17 that is disposed so as to extend in the axial direction of the sealed housing 3, a rotating element 19 that is secured in the area surrounding the driving shaft 17, and a stationary element 21 that is secured to the sealed housing 3 so as to cover the area surrounding the rotating element 19.
  • the rotary compression mechanism 5 is provided with an eccentric portion 23 provided below the driving shaft 17; a rotor 25 rotatably fitted to the eccentric portion 23; a cylinder member 29 that has a space which forms a cylinder chamber 27, which has circular cross-sectional shape and linearly comes in sliding contact with an outer circumferential surface of the rotor 25 at one location thereof, and that is joined to the sealed housing 3, for example, by means of welding, in a state in which the rotor 25 is disposed in this space; a top bearing 31 that is secured to a top-end surface of the cylinder member 29 to support the driving shaft 17 in a freely rotatable manner above the rotor 25; a bottom bearing 33 that is secured to a bottom-end surface of the cylinder member 29 to support the driving shaft 17 in a freely rotatable manner below the rotor 25; a blade (not shown) that partitions the interior of the cylinder chamber 27 into an intake side and a discharge side; a blade-pressing spring; and so on.
  • the rotary compression mechanism 5 is not limited to this configuration, and a known structure may be employed.
  • low-pressure refrigerant gas (medium) is taken into the cylinder chamber 27 via an accumulator 35 and an intake pipe 37 and this refrigerant gas is discharged into the sealed housing 3 via a discharge chamber 39 after being compressed to intermediate pressure by rotation of the rotor 25.
  • the intermediate-pressure refrigerant gas discharged into the sealed housing 3 flows to a space above the electric motor 9 via a gas channel, etc. provided in the rotating element 19 of the electric motor 9, from where it is taken into the higher-stage scroll compression mechanism 7 to be compressed in two stages.
  • the scroll compression mechanism 7 is provided with a stationary scroll 41 and an orbiting scroll 43.
  • the stationary scroll 41 is provided with a stationary end plate (stationary-side end plate) 45 and a spiral-shaped stationary spiral structure (stationary-side wall structure) 47 that is vertically provided on a bottom surface of the stationary end plate 45.
  • the stationary end plate 45 is mounted on an annular base provided inside the cylindrical portion 11 and is secured to the sealed housing 3 by being connected at multiple locations with bolts. Specifically, the stationary end plate 45 is secured at stationary-side support positions F (see Fig. 2 ) on an outer circumference side where the bolts are positioned.
  • a discharge port 49 for the compressed refrigerant gas is formed at a substantially center portion of the stationary end plate 45 so as to pass therethrough.
  • the orbiting scroll 43 is provided with an orbiting end plate (orbiting-side end plate) 51 and a spiral-shaped orbiting spiral structure (orbiting-side wall structure) 53 that is vertically provided on a top surface of the orbiting end plate 51.
  • the orbiting scroll 43 is provided so that the orbiting spiral structure 53 meshes with the stationary spiral structure 47.
  • the stationary scroll 41 and the orbiting scroll 43 are meshed so as to have a 180° phase difference in a state in which they are decentered from each other by a predetermined distance, thereby forming sealed spaces, which serve as compression chambers P, at multiple locations having point-symmetrical positional relationships with respect to the centers of the stationary spiral structure 47 and the orbiting spiral structure 53.
  • a hollow-cylindrical orbiting boss 55 is provided so as to protrude downward.
  • a bearing member 59 provided with a bearing portion 57 that supports the driving shaft 17 is fixed in the sealed housing 3.
  • the orbiting scroll 43 is supported by the bearing member 59 at orbiting-side support positions C (see Fig. 2 ) on an outer circumference side of the orbiting boss 55.
  • the orbiting-side support positions C are located at inner positions closer to the axial center than the outer circumferential end of the orbiting end plate 51. Therefore, the orbiting-side support positions C are located at positions closer to the axial center than the stationary-side support positions F that are positioned at the outer circumference side of the stationary end plate 45.
  • Height (tooth size) H1 of the stationary spiral structure 47 at positions closer to the outer circumference than the orbiting-side support positions C is smaller than height H2 of the stationary spiral structure 47 at positions closer to the inner circumference than the orbiting-side support positions C. Therefore, a clearance S1 between the tip (tooth tip) of the stationary spiral structure 47 and the orbiting end plate 51 at locations closer to the outer circumference than the orbiting-side support positions C is larger than a clearance S2 between a tip of the stationary spiral structure 47 and the orbiting end plate 51 at locations closer to the inner circumference than the orbiting-side support positions C.
  • the difference between the height H2 and the height H1 in other words, the difference between the clearance S2 and the clearance S1 is determined by various conditions, it is preferable that the difference be, for example, 0.25 to 2.0 ⁇ 10 -3 times the thickness of the orbiting-side end plate 51.
  • the height of the stationary spiral structure 47 in this embodiment is adjusted to have the clearances described above. This is because the stationary end plate 45 structurally deforms more easily, and also because the clearance between the tip of the stationary spiral structure 47 and the orbiting end plate 51 is smaller than the clearance between the tip of the orbiting spiral structure 53 and the stationary end plate 45.
  • the height of the orbiting spiral structure 53 may be adjusted.
  • the height of the stationary spiral structure 47 and the height of the orbiting spiral structure 53 may both be adjusted.
  • the clearances may be adjusted by cutting surfaces of the stationary end plate 45 and/or the orbiting end plate 51.
  • a rotation prevention mechanism 61 that causes the orbiting scroll 43 to revolve while preventing it from rotating is provided between the orbiting scroll 43 and the bearing member 59.
  • An eccentric pin 63 whose axial center is decentered is provided at a tip portion of the driving shaft 17 positioned in a hollow portion of the orbiting boss 55.
  • An orbiting bearing 65 that engages with the orbiting boss 55 is provided at the outer circumference of the eccentric pin 63. The rotation of the driving shaft 17 is transmitted to the orbiting boss 55 via the eccentric pin 63 and the orbiting bearing 65, thereby driving the orbiting scroll 43 and causing it to revolve.
  • a discharge valve 67 that opens/closes the discharge port 49 and a discharge cover 71 that forms a discharge chamber 69 between the stationary end plate 45 and itself are secured at the top surface of the stationary end plate 45.
  • An end portion of a discharge pipe 73 that is connected to the exterior, that is, a refrigerating cycle, by passing through the lid portion 15 of the sealed housing 3 is attached to the discharge cover 71 so as to pass therethrough.
  • the scroll compression mechanism 7 takes the intermediate-pressure refrigerant gas, which has been compressed at the rotary compression mechanism 5 and discharged into the sealed housing 3, into the compression chambers P and discharges it into the discharge chamber 69 via the discharge valve 67 after compressing the intermediate-pressure refrigerant gas into a high-temperature, high-pressure state by means of the orbiting scroll 43 that is driven to revolve.
  • This high-temperature, high-pressure refrigerant gas is expelled outside the compressor 1, that is, to the refrigerating cycle, from the discharge chamber 69 via the discharge pipe 73.
  • a known displacement-type oil supply pump 75 is mounted between the bottom end of the driving shaft 17 and the bottom bearing 33 of the rotary compression mechanism 5.
  • the oil supply pump 75 pumps out lubricant loaded in an oil sump 77 formed at the bottom portion of the sealed housing 3 to forcedly supply the lubricant 13, via an oil supply hole 79 provided in the driving shaft 17, to sites requiring lubrication, such as the bearing portions, etc. in the lower-stage rotary compression mechanism 5 and the higher-stage scroll compression mechanism 7.
  • the low-temperature, low-pressure refrigerant gas that is taken into the cylinder chamber 27 of the lower-stage rotary compression mechanism 5 via the intake pipe 37 is discharged into the discharge chamber 39 after being compressed to intermediate pressure by means of the rotation of the rotor 25.
  • This intermediate-pressure refrigerant gas flows to the space above the electric motor 9 via a gas channel, etc. provided in the rotating element 19 of the electric motor 9, after being discharged from the discharge chamber 39 into a space below the electric motor 9.
  • the intermediate-pressure refrigerant gas that has flowed to the space above the electric motor 9 is guided to an inlet of the scroll compression mechanism 7 provided in the stationary scroll 41 by passing through gaps, etc. between the bearing member 31 and the sealed housing 3, which constitute the higher-stage scroll compression mechanism 7, and is then taken into the compression chambers P.
  • the intermediate-pressure refrigerant gas that has been taken in is gradually compressed to reach the high-temperature, high-pressure state.
  • the refrigerant gas that has undergone the two-stage compression to the high-temperature, high-pressure state at the scroll compression mechanism 7 in this way passes through the discharge port 49, pushes up the discharge valve 67, and is discharged into the discharge chamber 69.
  • the high-temperature, high-pressure refrigerant gas in the discharge chamber 69 is expelled outside the compressor 1, that is, to the refrigerating cycle, via the discharge pipe 73.
  • high-temperature, high-pressure refrigerant gas 81 is present in the discharge chamber 69 and high-temperature, high-pressure refrigerant gas 83 is present at a center portion of a space sandwiched by the stationary end plate 45 and the orbiting end plate 51.
  • the stationary end plate 45 of the stationary scroll 41 is pressed by this refrigerant gas 81, thermal expansion and pressure deformation thereof occur. Because the stationary-side end plate 45 is secured at stationary-side support positions F positioned on the outer circumferential side, it warps so that the center portion thereof is positioned closer to the orbiting scroll 43, as shown in Fig. 3 .
  • the orbiting end plate 51 warps so that the center portion thereof is separated from the stationary scroll 41, as shown in Fig. 3 . Specifically, during the compression operation, both the stationary end plate 45 and the orbiting end plate 51 warp so that the center portions thereof protrude downward.
  • the orbiting end plate 51 is supported at the orbiting-side support positions C such that the orbiting end plate does not move at these positions in the top-bottom direction, the orbiting end plate 51 deforms at a portion closer to the outer circumference than the orbiting-side support positions C so as to approach the stationary scroll 41.
  • the orbiting scroll 41 and the stationary scroll 43 deform in the directions that cause them to approach each other.
  • the clearance S1 between the tip of the stationary spiral structure 47 and the orbiting end plate 51 further toward the outer circumferential side than the orbiting-side support positions C is made larger than the clearance S2 between the tip of the stationary spiral structure 47 and the orbiting end plate 51 at further toward the inner circumferential side than the orbiting-side support positions C, even though the stationary scroll 41 and the orbiting scroll 43 deform in the directions that cause them to approach each other at the portions closer to the outer circumference than the orbiting-side support positions C, as described above, it is possible to prevent them from coming into contact with each other.
  • the stationary scroll 41 and the orbiting scroll 43 can be prevented from coming into contact with each other in this way, it is possible to prevent damage to the stationary spiral structure 47 or the orbiting spiral structure 53 caused by the contact, and thus, the reliability thereof can be ensured.
  • the efficiency can be enhanced as compared with the case in which the overall clearance is increased to prevent a collision.
  • the compressor is not limited to the two-stage compressor, and it may, of course, be a single-stage compressor (scroll compressor) provided only with a scroll compression mechanism.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Claims (2)

  1. Compresseur comprenant un mécanisme de compression à spirale (7) comprenant :
    une spirale fixe (41) et une spirale orbitale (43), dans lequel :
    la spirale fixe est prévue avec une plaque d'extrémité du côté fixe (45) et une structure de paroi du côté fixe en forme de spirale (47) qui est verticalement prévue sur une surface de la plaque d'extrémité du côté fixe (45), la plaque d'extrémité du côté fixe (45) étant fixée dans une position de support du côté fixe (F) positionnée à proximité d'une circonférence externe de la plaque d'extrémité du côté fixe (45) ; et
    la spirale orbitale (43) est prévue avec une plaque d'extrémité du côté orbital (51) et une structure de paroi du côté orbital en forme de spirale (53) qui est verticalement prévue sur une surface de la plaque d'extrémité du côté orbital (51) et qui s'engrène avec la structure de paroi du côté fixe (47),
    dans lequel un bossage orbital cylindrique creux (55) est prévu au niveau d'un centre d'une surface inférieure de la plaque d'extrémité du côté orbital (51) afin de faire saillie vers le bas,
    et dans lequel la plaque d'extrémité du côté orbital (51) est supportée dans une position (C) plus à proximité d'un centre de la plaque d'extrémité du côté orbital (51) qu'une position faisant face à la position de support du côté fixe (F) d'une manière qui permet un mouvement de révolution, la position de support du côté orbital (C) étant située sur un côté de circonférence externe du bossage orbital (55) ;
    un orifice de décharge (49) pour un gaz réfrigérant comprimé étant formé au niveau d'une partie sensiblement centrale de la plaque d'extrémité du côté fixe (45) de manière à passer à travers,
    une valve de décharge (67) qui ouvre / ferme l'orifice de décharge (49) et un couvercle de décharge (71) qui forme une chambre de décharge (69) entre la plaque d'extrémité du côté fixe (45) et lui-même étant fixé sur une surface supérieure de la plaque d'extrémité du côté fixe (45), et dans lequel pour au moins l'un parmi un jeu entre une partie de pointe de la structure de paroi du côté fixe (47) et la plaque d'extrémité du côté orbital (51) et un jeu entre une partie de bout de la structure de paroi du côté orbital (53) et la plaque d'extrémité du côté fixe (45), le jeu (S1) au niveau d'un côté davantage vers l'extérieur que la position de support du côté orbital (C) est plus important que le jeu (S2) au niveau du côté central davantage vers l'intérieur que la position de support du côté orbital (C), et les jeux (S1, S2) représentent de 0,25 à 2,0 x 10-3 fois une épaisseur de la plaque d'extrémité du côté fixe (45) ou de la plaque d'extrémité du côté orbital, et caractérisé en ce que la plaque d'extrémité du côté fixe (45) est configurée pour s'enrouler de sorte qu'une partie centrale de la plaque d'extrémité du côté fixe (45) fait saillie vers le côté de la spirale orbitale, la partie centrale de la plaque d'extrémité du côté fixe (45) étant plus proche d'un centre de la plaque d'extrémité du côté fixe (45) que la position de support du côté fixe (F), et la plaque d'extrémité orbitale (51) se déforme à une position plus proche de la circonférence externe de la plaque d'extrémité du côté orbital (51) que la position de support du côté orbital (C) afin de s'approcher de la spirale fixe (41), sous l'effet du gaz réfrigérant comprimé qui a subi la compression au niveau du mécanisme de compression à spirale (7) passant par l'orifice de décharge (49), poussant la valve de décharge (67) et étant déchargé dans la chambre de décharge (69).
  2. Compresseur selon la revendication 1, dans lequel les jeux (S1, S2) sont modifiés en ajustant la hauteur de la structure de paroi du côté fixe (47) ou de la structure de paroi du côté orbital (53).
EP12158522.8A 2011-03-09 2012-03-08 Compresseur à spirales Active EP2497954B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2011051846A JP5787559B2 (ja) 2011-03-09 2011-03-09 圧縮機

Publications (3)

Publication Number Publication Date
EP2497954A2 EP2497954A2 (fr) 2012-09-12
EP2497954A3 EP2497954A3 (fr) 2016-05-11
EP2497954B1 true EP2497954B1 (fr) 2019-09-25

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Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9039396B2 (en) 2012-07-03 2015-05-26 Emerson Climate Technologies, Inc. Piston and scroll compressor assembly
JP5879274B2 (ja) * 2013-01-15 2016-03-08 日立アプライアンス株式会社 スクロール圧縮機
WO2014134058A1 (fr) * 2013-02-26 2014-09-04 Emerson Climate Technologies, Inc. Système comportant des compresseurs côté haute pression et côté basse pression
KR101563740B1 (ko) 2013-12-26 2015-10-27 갑을오토텍(주) 냉방성능 조절이 가능한 스크롤 압축기
CN104696217B (zh) * 2014-08-29 2017-09-01 北京实验工厂 涡旋干式真空泵及其制造方法、真空系统
EP4074975A4 (fr) * 2019-12-12 2023-01-25 Daikin Industries, Ltd. Compresseur à spirales

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Publication number Priority date Publication date Assignee Title
JPS5968583A (ja) * 1982-10-09 1984-04-18 Sanden Corp スクロ−ル型流体装置
JPS59192687U (ja) * 1983-06-07 1984-12-21 株式会社豊田自動織機製作所 スクロ−ル圧縮機のスクロ−ル部材
JP2817386B2 (ja) * 1990-10-17 1998-10-30 株式会社デンソー スクロール型圧縮機
JPH0587074A (ja) 1991-07-30 1993-04-06 Mitsubishi Heavy Ind Ltd ２段圧縮機
JPH08261170A (ja) * 1995-03-28 1996-10-08 Mitsubishi Electric Corp スクロール圧縮機
JP3556935B2 (ja) 2001-11-21 2004-08-25 三菱重工業株式会社 スクロール型圧縮機

Non-Patent Citations (1)

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Title
None *

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JP2012188964A (ja) 2012-10-04
JP5787559B2 (ja) 2015-09-30
EP2497954A2 (fr) 2012-09-12
EP2497954A3 (fr) 2016-05-11

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