EP2918773B1 - Compresseur rotatif - Google Patents

Compresseur rotatif Download PDF

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Publication number
EP2918773B1
EP2918773B1 EP15158793.8A EP15158793A EP2918773B1 EP 2918773 B1 EP2918773 B1 EP 2918773B1 EP 15158793 A EP15158793 A EP 15158793A EP 2918773 B1 EP2918773 B1 EP 2918773B1
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EP
European Patent Office
Prior art keywords
main body
cylinder main
cylinder
deformation
bolt hole
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
EP15158793.8A
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German (de)
English (en)
Other versions
EP2918773A1 (fr
Inventor
Makoto Ogawa
Shigeki Miura
Ikuo Esaki
Masanari Uno
Yuichi Muroi
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
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Publication of EP2918773A1 publication Critical patent/EP2918773A1/fr
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Publication of EP2918773B1 publication Critical patent/EP2918773B1/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
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
    • 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
    • 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
    • F04C2240/80—Other components
    • F04C2240/805—Fastening means, e.g. bolts

Definitions

  • the present invention relates to a rotary compressor.
  • a rotary compressor which includes a cylinder and a rotor that rotates inside the cylinder eccentrically to the axis of the cylinder is known as a compressor provided in a refrigeration cycle in an air conditioner, a chiller, etc.
  • This rotary compressor suctions a low-pressure refrigerant, which circulates through a refrigerant circuit, into a cylinder chamber through a suction pipe connected to the side wall of the cylinder, and delivers a high-pressure refrigerant, which has been compressed inside the cylinder chamber by rotation of the rotor, through a discharge pipe to the outside of the compressor.
  • Such rotary compressors generally have a structure with members constituting a rotary compression mechanism, such as a cylinder main body, an upper bearing, a lower bearing, and a muffler forming a muffler chamber, fastened with a bolt.
  • a separator plate which separates between the cylinders is also fastened with a bolt on the cylinder main body, etc.
  • a groove for alleviating distortion due to bolt fastening is provided at a position on an inner peripheral side (cylinder chamber side) relative to a bolt fastening part of the cylinder, namely, between the cylinder inner wall and the bolt hole.
  • JP H06 307363 discloses a compressor according to the preamble of claim 1.
  • the conventional rotary compressor employs a structure with the members constituting the rotary compression mechanism, such as the cylinder main body, the bearings, and the muffler, laid on top of one another and integrated by fastening bolts. This raises a concern that deformation may occur in the cylinder bore due to bolt fastening.
  • an inner wall surface 9b of a cylinder chamber 8 can deform so as to bulge out toward the inside (toward the center of the cylinder chamber) in the vicinity of the bolt fastening part.
  • the clearance (face-to-face distance) between the outer peripheral surface of a rotating rotor 12 and the inner wall surface 9b of the cylinder main body 9 forming the cylinder chamber 8 becomes the smallest in the region around the bolt hole 9a.
  • the deformation due to bolt fastening is exaggerated for clear illustration of the deformation.
  • the position of the rotational axial center of the rotor 12 is adjusted so as to secure a predetermined clearance set value g in the region around the bolt hole where the clearance becomes smallest. Specifically, the position of the rotational axial center of the rotor 12 is changed from C for a situation where there is no deformation to C'.
  • the present invention aims to provide a rotary compressor which can achieve higher efficiency by suppressing change in the inner diameter in the cylinder bore due to bolt fastening and reducing the amount of leakage of a compressed fluid during compression.
  • a rotary compressor according to the present invention is a rotary compressor as defined in appended claim 1.
  • the deformation absorbing part which leads deformation due to bolt fastening toward at least one of the radially outward direction and the circumferential direction is provided in the region around the bolt hole of the cylinder main body.
  • deformation of the cylinder main body due to bolt fastening is directed from the bolt fastening part toward the outer peripheral direction or the circumferential direction of the cylinder main body. It is therefore possible to prevent the inner wall surface of the cylinder chamber from bulging out toward the axial center of the cylinder main body and from reducing the cylinder bore during bolt fastening, or it is possible to suppress the bulging out and the bore reduction.
  • the above-described deformation absorbing part is a region with a smaller rigidity, for example, by thinning the radial side of the cylinder main body, which is the outer peripheral side relative to the bolt fastening part such that deformation of the cylinder main body caused by bolt fastening is led in other directions than the direction toward the inside of the cylinder chamber.
  • the deformation absorbing part is a slit which is provided in a region other than a region positioned radially inward of the bolt hole and which is penetrating in the axial direction of the crankshaft. Accordingly, deformation of the cylinder main body due to bolt fastening is directed toward the outside in the radial direction relative to the bolt fastening part or in the circumferential direction throughout the cylinder main body in its thickness direction (axial direction). Therefore, deformation of the bore of the cylinder chamber bulging out toward the axial center of the cylinder main body can be prevented or suppressed throughout the cylinder main body in its thickness direction. Since such a through-slit also functions as a hollow heat-insulating layer, heat transmission from the outer periphery to the compression space can be suppressed.
  • the deformation absorbing part may be formed as a cutaway portion provided on an outer peripheral surface of the cylinder main body so as to penetrate the cylinder main body in the axial direction of the crankshaft.
  • a cutaway portion When such a cutaway portion is provided, the radial dimension of the cylinder main body becomes smaller on the outer peripheral side of the bolt fastening part throughout the cylinder main body in its thickness direction.
  • the rotary compressor of the present invention since deformation of the cylinder main body caused by bolt fastening can be led in other directions than the radially inward direction, it is possible to prevent or suppress deformation of the inner wall of the cylinder chamber, i.e., bulging out toward the inside of the cylinder chamber.
  • the clearance between the outer peripheral surface of the rotor and the inner wall surface of the cylinder main body forming the cylinder chamber can be uniformized to the predetermined clearance set value g (see Fig. 7 ) throughout the entire circumference. It is therefore possible to achieve higher efficiency by reducing the amount of leakage of compressed fluid flowing out from the high-pressure side to the low-pressure side during compression of the rotary compressor.
  • Fig. 6 is a longitudinal cross-sectional view showing the configuration of an hermetic single-cylinder compressor as one example of a rotary compressor.
  • an embodiment applied to a single-cylinder rotary compressor will be described below.
  • the present invention is also applicable to a rotary compression mechanism in a two-cylinder rotary compressor as well as in a compressor having a number of different compression mechanisms.
  • An hermetic rotary compressor 1 has a housing 2 having an hermetic structure.
  • This housing 2 is composed of a cylindrical center housing 2A, an upper housing 2B enclosing the upper part of the center housing 2A, and a lower housing 2C enclosing the lower part of the center housing 2A.
  • An electric motor 4, which has a stator 5 and a rotor 6, is fixedly installed as a drive source on the upper side of the inside the center housing 2A.
  • the rotor 6 is integrally connected with a crankshaft (rotating shaft) 7.
  • this electric motor 4 has an axial offset between the stator 5 and the rotor 6, and by means of a force in the pulling direction of an axial magnet acting between the stator 5 and the rotor 6, this electric motor 4 has functions to pull the rotor 6 and the crankshaft 7 upward during stable operation.
  • This function provides a thrust force reduction mechanism which reduces a thrust force acting between a thrust end surface formed in an eccentric part of the crankshaft 7 and end surfaces of an upper bearing 10 and a lower bearing 11, which will be described later.
  • a single-cylinder rotary compression mechanism 3 is installed under the electric motor 4.
  • This rotary compression mechanism 3 includes the following elements: a cylinder main body 9 in which a cylinder chamber 8 is formed; the upper bearing 10 and the lower bearing 11 fixedly installed on the upper part and the lower part of the cylinder main body 9 and enclosing the upper part and the lower part of the cylinder chamber 8; a rotor 12 which is fitted to an eccentric part 7A of the crankshaft 7 and rotates along the inner peripheral surface of the cylinder chamber 8; and a blade and a blade holddown spring (which are not shown), which partition the inside of the cylinder chamber 8 into a suction side and a discharge side.
  • This rotary compression mechanism 3 is fixedly installed by making either the cylinder main body 9 or the upper bearing 10 plug-welded or fixed by caulking at a plurality of positions on the circumference in the inner peripheral surface of the center housing 2A, while other members are integrally assembled to the fixedly installed member.
  • the rotary compression mechanism 3 suctions a low-pressure refrigerant gas, which is a fluid to be compressed, from an accumulator 14 provided integrally in the rotary compressor 1 through a suction pipe 13 and into the cylinder chamber 8, and after compressing this refrigerant gas through rotation of the rotor 12, discharges the refrigerant gas into an upper muffler chamber 15 and a lower muffler chamber 16 formed by the upper bearing 10 and the lower bearing 11.
  • the high-pressure refrigerant gas thus compressed merges in the upper muffler chamber 15 before being discharged into the center housing 2A. There is substantially no pressure difference between the inside of the upper muffler chamber 15 and the lower muffler chamber 16 and the inside of the center housing 2A.
  • This high-pressure refrigerant gas flows through a gas passage hole (not shown) provided around the electric motor 4 and is guided to a space above the electric motor 4, and further is delivered through a discharge pipe 17 to the outside of the rotary compressor 1, namely, to the refrigeration cycle side.
  • the cylinder main body 9, the upper bearing 10 and the lower bearing 11 disposed on the upper and lower sides of the cylinder main body 9, and a lower muffler 16A forming the lower muffler chamber 16 under the lower bearing 11 are integrally assembled through screw fastening of a bolt 18 which penetrates in the axial direction of the crankshaft 7.
  • the upper muffler chamber 15 and the lower muffler chamber 16 are parts which are both free of pressure difference between the inside thereof and the outside.
  • the lower muffler 16A is fastened with the bolt 18.
  • there is no particular limit for the structure of an upper muffler 15A and the lower muffler 16A, and therefore a structure with both mufflers fastened with the bolt 18, a structure with only either of the mufflers fastened with the bolt 18, etc. are possible.
  • the rotary compressor 1 has the rotary compression mechanism 3 driven through the crankshaft 7 coupled with the electric motor 4 serving as a drive source includes the cylinder main body 9 forming the cylinder chamber 8, the upper bearing 10 and the lower bearing 11 installed on the upper and lower surfaces, respectively, of the cylinder main body 9 and supporting the crankshaft 7, and the rotor 12 fitted to the eccentric part 7A of the crankshaft 7 and rotating inside the cylinder chamber 8.
  • the compressor 1 at least the cylinder main body 9 and the upper bearing 10 and the lower bearing 11 are integrated by fastening the bolt 18 penetrating in the axial direction of the crankshaft 7.
  • the compressor 1 includes, for example, as shown in Fig. 1 , a through-slit 20 as a deformation absorbing part provided in the region around a bolt hole 9a which is provided in the cylinder main body 9 and into which the bolt 18 is screwed and fastened.
  • This through-slit 20 forms a low-rigidity region such that deformation of the cylinder main body 9 due to the bolt 18 screwed into the bolt hole 9a of the cylinder main body 9 during fastening of the bolt 18 is led to at least one of the radially outward direction and the circumferential direction of the cylinder main body 9.
  • the through-slit 20 of the embodiment shown in Fig. 1 is an arc-shaped slit formed in the vicinity of the bolt hole 9a and at the outer peripheral side relative to the bolt hole 9a, and is provided so as to penetrate the cylinder main body 9 along its thickness t in the axial direction of the crankshaft 7.
  • a dimension L2 on the radially outer peripheral side is set to be smaller than a dimension L1 on the inner peripheral side (L2 ⁇ L1).
  • the radially outer peripheral side in which the dimension L2 is made smaller than the dimension L1, becomes lower in rigidity than the inner peripheral side, so that a low-rigidity region having a lower rigidity than the surrounding area is formed at the radially outer peripheral side of the bolt hole 9a.
  • the area surrounding the bolt hole 9a of the cylinder main body 9 deforms by an input in the direction of enlarging the diameter of the bolt hole 9a, which occurs as the bolt 18 is screwed in and fastened.
  • this deformation takes the form of bulging out to the inside of the through-slit 20 toward the radially outer peripheral side where the rigidity is low around the bolt hole 9a.
  • the deformation due to bolt fastening is exaggerated for clear illustration of the deformation.
  • the through-slit 20 which serves as a relief of deformation caused by bolt fastening, is provided between the bolt hole 9a and the outer wall surface 9c of the cylinder main body 9 such that the outer peripheral side of the bolt hole 9a deforms preferentially.
  • a predetermined clearance set value g can be secured along the entire circumference even when the position of the rotational axial center of the rotor 12 is positioned at C.
  • the amount of leakage of compressed fluid which leaks from the high-pressure side to the low-pressure side can be reduced.
  • the through-slit 20 is provided so as to penetrate in the axial direction of the crankshaft 7, deformation of the cylinder main body 9 due to bolt fastening is directed toward the radially outside from the bolt hole 9a throughout the thickness t. Therefore, deformation during bolt fastening which reduces the bore of the cylinder chamber 8 can be prevented or suppressed throughout the cylinder main body 9 in its thickness direction.
  • a hollow heat-insulating layer is formed on the outer peripheral side of the cylinder chamber 8, which can suppress transmission of heat input from the outer periphery, in which the temperature is higher, into the low-temperature cylinder chamber 8, and contribute to improve compression efficiency.
  • the above-described slit serving as the deformation absorbing part is not limited to the arc-shaped through-slit 20 shown in Fig. 1 and Fig. 2 , but various modified examples described below are also possible.
  • a substantially semicircular through-slit 20A is formed on the radially outer peripheral side relative to the bolt hole 9a.
  • This through-slit 20A forms a low-rigidity region surrounding a substantially semicircular region on the outer peripheral side relative to the bolt hole 9a, and not only absorbs deformation during bolt fastening toward the radially outer peripheral side but also absorbs deformation in the circumferential direction.
  • deformation of the cylinder bore of the cylinder chamber 8 can be suppressed.
  • each of the arc-shaped through-slits 20L, 20R is formed on each side of the bolt hole 9a so as to extend in the circumferential direction of the cylinder main body 9.
  • These through-slits 20L, 20R form a low-rigidity region on each side of the bolt hole 9a in the circumferential direction, and thereby absorb deformation during bolt fastening mainly in the circumferential direction.
  • a cutaway part 30, which is formed, for example, as shown in Fig. 5 , by providing a recessed groove part 9d of the outer peripheral surface of the cylinder main body 9 so as to penetrate in the axial direction of the crankshaft 7, serves as the deformation absorbing part.
  • a cutaway part 30 which is formed, for example, as shown in Fig. 5 , by providing a recessed groove part 9d of the outer peripheral surface of the cylinder main body 9 so as to penetrate in the axial direction of the crankshaft 7, serves as the deformation absorbing part.
  • the recessed groove part 9d shown in Fig. 5 is a groove having a substantially semicircular cross-section and extending in the thickness direction.
  • the recessed groove part 9d is provided in an outer wall surface 9c of the cylinder main body 9 throughout the thickness t and positioned on a radial extension line passing through the centers of the cylinder chamber 8 and the bolt hole 9a.
  • the cross-sectional shape of the recessed groove part 9d may have a rectangular cross-sectional shape or a triangular cross-sectional shape, for example.
  • the radial dimension of the cylinder main body 9 becomes smaller on the outer peripheral side of the bolt hole 9a, which is provided with the cutaway part 30, relative to the inner peripheral side, throughout the thickness of the cylinder main body 9.
  • the cutaway forming part 30, which is the outer peripheral side of the bolt hole 9a becomes a low-rigidity region having a smaller radial dimension than the inner peripheral side of the bolt hole 9a. Accordingly, deformation of the cylinder main body 9 due to bolt fastening is directed toward the radially outside relative to the bolt hole 9a. As a result, deformation of the bore of the cylinder chamber 8 bulging out to the axial center side is prevented or suppressed throughout the thickness of the cylinder main body 9.
  • Formation of the low-rigidity region by means of such a recessed groove part 9c can be appropriately combined with the Through-slit 20 of the aforementioned embodiment or its modified examples described above.
  • the deformation absorbing part is included which leads deformation of the cylinder main body 9 caused by fastening the bolt in other directions than the direction toward the inside of the cylinder chamber 8. Accordingly, deformation of the cylinder main body 9 due to bolt fastening is directed from the bolt hole 9a in the bolt fastening part toward the outer peripheral direction (radially outward direction) or the circumferential direction of the cylinder main body 9.
  • Such a deformation absorbing part is a region in which the rigidity is reduced, for example, by reducing the dimension in the radial direction or the circumferential direction of the cylinder main body 9 (dimension in which the mass of the cylinder main body 9 exists) which is positioned at the outer peripheral side relative to the bolt hole 9a serving as the bolt fastening part.
  • the clearance between the outer peripheral surface of the rotor 12 and the inner wall surface 9b of the cylinder main body 9 forming the cylinder chamber 8 can be uniformized to the predetermined clearance set value g along the entire circumference, higher efficiency can be achieved by reducing the amount of leakage of the compressed fluid flowing out from the high-pressure side to the low-pressure side during compression of the rotary compressor 1.
  • Such an increase in efficiency of the rotary compressor 1 becomes more remarkable especially when a compressed fluid used at high pressure (e.g., an R32 refrigerant) is handled.
  • this embodiment in which the deformation absorbing part is provided on the outer peripheral side, has also an advantage in which it is easy to reduce the size of the rotary compressor 1 or to secure favorable sealability.
  • the present invention is not limited to the above-described embodiments, but is also applicable, for example, to a rotary compression mechanism of a compressor having a rotary compression mechanism and a scroll compression mechanism in combination.
  • changes can be made appropriately within the scope of the present invention.

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

Claims (2)

  1. Compresseur rotatif (1) comprenant un mécanisme de compression rotatif (3) entraîné par un vilebrequin (7) couplé à une source d'entraînement, le mécanisme de compression comprenant : un corps principal de cylindre (9) formant une chambre de cylindre (8) ; des paliers (10, 11) respectivement installés sur les surfaces supérieure et inférieure du corps principal de cylindre et supportant le vilebrequin ; et un rotor (12) qui est monté sur une partie excentrique (7A) du vilebrequin et qui tourne à l'intérieur de la chambre de cylindre (8), le compresseur rotatif étant caractérisé en ce qu'au moins le corps principal de cylindre (9) et les paliers (10, 11) sont assemblés de manière solidaire en fixant un boulon (18) pénétrant dans la direction axiale du vilebrequin (7), le corps principal de cylindre (9) comprenant un trou de boulon (9a) ayant un côté périphérique, et une partie d'absorption de déformation (20 ; 20A ; 20L, 20R ; 30) étant prévue sur le côté périphérique du trou de boulon (9a) du corps principal de cylindre (9) afin de pénétrer dans le corps principal de cylindre dans la direction axiale du vilebrequin (7),
    ladite partie d'absorption de déformation étant positionnée soit sur une ligne d'extension radiale passant par les centres de la chambre de cylindre et du trou de boulon, soit de chaque côté du trou de boulon afin de s'étendre dans la direction circonférentielle du corps principal de cylindre.
  2. Compresseur rotatif selon la revendication 1, dans lequel la partie d'absorption de déformation est formée comme une partie découpée (30) prévue sur une surface périphérique externe du corps principal de cylindre (9).
EP15158793.8A 2014-03-14 2015-03-12 Compresseur rotatif Active EP2918773B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2014051615A JP6437204B2 (ja) 2014-03-14 2014-03-14 ロータリ圧縮機

Publications (2)

Publication Number Publication Date
EP2918773A1 EP2918773A1 (fr) 2015-09-16
EP2918773B1 true EP2918773B1 (fr) 2020-01-01

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EP15158793.8A Active EP2918773B1 (fr) 2014-03-14 2015-03-12 Compresseur rotatif

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EP (1) EP2918773B1 (fr)
JP (1) JP6437204B2 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7443170B2 (ja) * 2020-02-27 2024-03-05 ナブテスコ株式会社 減速機

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS55156292A (en) * 1979-05-23 1980-12-05 Hitachi Ltd Rotary compressor
JPS63186988A (ja) 1987-01-29 1988-08-02 Matsushita Electric Ind Co Ltd 回転圧縮機
JPS63186988U (fr) * 1987-05-21 1988-11-30
JPH0633783B2 (ja) * 1987-05-29 1994-05-02 松下電器産業株式会社 ２気筒回転式密閉型電動圧縮機の組立方法
JP3319026B2 (ja) * 1993-04-20 2002-08-26 株式会社日立製作所 ロータリ圧縮機
JPH11324958A (ja) * 1998-05-14 1999-11-26 Matsushita Electric Ind Co Ltd 密閉型回転式圧縮機
JP5010295B2 (ja) * 2007-01-26 2012-08-29 三菱重工業株式会社 密閉型ロータリ圧縮機
JP2010116782A (ja) * 2008-11-11 2010-05-27 Daikin Ind Ltd 流体機械
JP2012122458A (ja) * 2010-12-10 2012-06-28 Daikin Industries Ltd ロータリ式流体機構

Non-Patent Citations (1)

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

Also Published As

Publication number Publication date
JP6437204B2 (ja) 2018-12-12
JP2015175273A (ja) 2015-10-05
EP2918773A1 (fr) 2015-09-16

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