EP3951181A1 - Rotationsverdichter - Google Patents

Rotationsverdichter Download PDF

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Publication number
EP3951181A1
EP3951181A1 EP19925955.7A EP19925955A EP3951181A1 EP 3951181 A1 EP3951181 A1 EP 3951181A1 EP 19925955 A EP19925955 A EP 19925955A EP 3951181 A1 EP3951181 A1 EP 3951181A1
Authority
EP
European Patent Office
Prior art keywords
cylinders
rotary
inner diameter
suction
pipe
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
EP19925955.7A
Other languages
English (en)
French (fr)
Other versions
EP3951181A4 (de
Inventor
Takashi Watanabe
Yoshiyuki Kimata
Youhei Hotta
Hajime Sato
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 EP3951181A1 publication Critical patent/EP3951181A1/de
Publication of EP3951181A4 publication Critical patent/EP3951181A4/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
    • F04C18/30—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
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C23/001—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 of similar working principle
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C2240/806—Pipes for fluids; Fittings therefor

Definitions

  • the present invention relates to a rotary compressor.
  • a rotary compressor as shown in PTL 1 which includes a housing, a rotary shaft that extends in a vertical direction in the housing and is rotated by an electric motor, a rotary compression portion including a cylinder supported by the rotary shaft, and an upper bearing and a lower bearing that are rotatably supported by the rotary shaft and fixed above and below the cylinder, is known.
  • a suction pipe through which a refrigerant can be introduced into a compression chamber of the rotary compression portion is connected to the cylinder.
  • PTL 1 also discloses a twin rotary compressor in which cylinders are vertically disposed in two stages. Each cylinder is connected to at least one of suction pipes that separately extend from an accumulator.
  • the thickness of a separator plate interposed between the cylinders is made small for vibration reduction. This is because the two cylinders are separated from each other and the influence of vibration caused by eccentric movement of a piston rotor is large if the separator plate is thick.
  • the thickness of the separator plate is small, it is difficult to perform processing between the suction pipes at a connecting portion between the two suction pipes and a housing. Therefore, to widen a space between the suction pipes to facilitate the processing, it is necessary to make the separator plate thick or make the suction pipes thin.
  • the present invention has been made in view of such circumstances and an object thereof is to provide a rotary compressor with which it is possible to reduce vibration without a decrease in compression efficiency in a rotary compressor including a plurality of cylinders.
  • the present invention adopts the following aspects in order to solve the above problems and achieve the object.
  • the main pipe of the suction pipe is disposed above or below the plurality of cylinders and the refrigerant can be sucked into each of the compression chambers of the plurality of cylinders through the connection pipe extending in the axial direction. Accordingly, the compression chambers of the plurality of the cylinders are connected to each other and thus the refrigerant can be sucked into each of the compression chambers through one suction pipe without a decrease in compression efficiency.
  • the number of suction pipes can be reduced to one, it is easy to perform processing on a portion where the suction pipe is connected to the housing even if the thickness of the separator plate is small.
  • the main pipe of the suction pipe is disposed above or below the plurality of cylinders and thus the inner diameter of the main pipe is not limited to the thickness of the cylinders and the inner diameter of the main pipe can be made large.
  • the inner diameter of the connection pipe can be made large. Accordingly, a larger amount of refrigerant can be compressed and the compression efficiency can be improved.
  • an inner diameter of the suction pipe may be larger than a thickness of the cylinder.
  • each of the plurality of cylinders may be provided with a suction flow path that extends in the radial direction and through which the compression chamber and the connection pipe communicate with each other.
  • each compression chamber can be performed via each suction flow path that extends in the radial direction through the connection pipe that extends in the axial direction from the suction pipe. Accordingly, branched flow to the compression chambers of the plurality of cylinders from one suction pipe can be made efficiently and thus the compression efficiency can be improved.
  • the suction flow path may be open to an outer peripheral surface of the cylinder so that an opening hole is provided in the cylinder and the opening hole may be provided with a sealing plug.
  • an inner diameter of the main pipe and an inner diameter of the connection pipe may be the same as each other and the inner diameter of the main pipe and the inner diameter of the connection pipe may be larger than an inner diameter of the suction flow path.
  • the inner diameter of each of the main pipe and the connection pipe constituting a flow path for the refrigerant supplied into the suction flow paths of the plurality of cylinders can be made larger than the inner diameter of the suction flow paths of the cylinders. Therefore, a large amount of the refrigerant can be supplied to each compression chamber and the compression efficiency can be improved.
  • an inner diameter of the suction flow path provided in one of the cylinders that is on an upper side may be equal to or smaller than an inner diameter of the suction flow path provided in the other of the cylinders that is on a lower side.
  • a rotary compressor according to the present embodiment (hereinafter, simply referred to as compressor 1) is, for example, a vertical hermetic rotary compressor which is used for an air conditioner, a freezer, or the like.
  • the compressor 1 includes a housing 2, a rotary shaft 3, an upper bearing 4A, a lower bearing 4B, an electric motor 5, a rotary compression portion 6, a scroll compression portion 10, and a suction pipe 7.
  • the rotary shaft 3 extends along an axis (rotational axis O which will be described later).
  • the upper bearing 4A and the lower bearing 4B support the rotary shaft 3 such that the rotary shaft 3 is rotatable around the rotational axis O.
  • the electric motor 5 rotates the rotary shaft 3.
  • the rotary compression portion 6 compresses a refrigerant by means of rotation of the rotary shaft 3. Through the suction pipe 7, the refrigerant can be introduced into compression chambers 63A and 63B of the rotary compression portion 6.
  • the compressor 1 of the present embodiment is a two-stage compressor that further includes the scroll compression portion 10 above the rotary compression portion 6, the scroll compression portion 10 does not need to be provided.
  • the central axis of the housing 2 and the rotary shaft 3 are disposed on a common axis extending in the vertical direction (vertical direction) and the common axis will be referred to as the rotational axis O.
  • the rotary shaft 3 is disposed such that a direction in which the rotary shaft 3 extends is parallel to the vertical direction and is accommodated in the housing 2 such that the rotary shaft 3 can rotate around the rotational axis O.
  • the housing 2 is a hermetic housing, extends in the vertical direction, and accommodates the rotary shaft 3, the bearings 4A and 4B, the electric motor 5, and the rotary compression portion 6.
  • the housing 2 includes a main body portion 21 that has a cylindrical shape, an upper cover portion 22, and a lower cover portion 23, the upper cover portion 22 and the lower cover portion 23 closing upper and lower openings of the main body portion 21.
  • an opening 24 is formed above cylinders 60 (60A and 60B) at a lower portion of a side wall.
  • the suction pipe 7 is fixed to the opening 24 in a state of being inserted thereinto with a pipe axis direction being parallel to a horizontal direction.
  • the upper cover portion 22 is provided with a discharge pipe 13 that penetrates a peripheral wall member in a thickness direction and communicates with the inside of the housing 2. Through the discharge pipe 13, a compressed refrigerant is discharged to the outside of the housing 2.
  • the electric motor 5 is accommodated in a central portion of the housing 2 in the vertical direction.
  • the electric motor 5 includes a rotor 51 and a stator 52.
  • the rotor 51 is fixed to an outer peripheral surface of the rotary shaft 3 and is disposed above the rotary compression portion 6.
  • the stator 52 is disposed to surround an outer peripheral surface of the rotor 51 and is fixed to an inner surface 21a of the main body portion 21 of the housing 2.
  • a power source (not shown) is connected to the electric motor 5 via a terminal 9.
  • the electric motor 5 rotates the rotary shaft 3 by using electric power from the power source.
  • the upper bearing 4A and the lower bearing 4B are disposed such that the rotary compression portion 6 is vertically interposed therebetween.
  • the upper bearing 4A and the lower bearing 4B are formed of, for example, a metallic material and are fixed to the cylinders 60 constituting the rotary compression portion 6 by being bolted thereto, for example.
  • the upper bearing 4A is fixed to the housing 2.
  • the rotary shaft 3 is supported by the upper bearing 4A and the lower bearing 4B in the housing 2 such that the rotary shaft 3 can freely rotate around the rotational axis O.
  • the rotary compression portion 6 is disposed at a bottom portion in the housing 2 while being disposed below the electric motor 5 and compresses a refrigerant.
  • the rotary compression portion 6 includes a plurality of (two in present embodiment) cylinders 60 (60A and 60B) having a disk shape, eccentric shaft portions 61, and piston rotors 62.
  • the two cylinders 60A and 60B are vertically disposed in the housing 2 in a direction along the rotational axis O.
  • the cylinder on an upper side will be referred to as the upper cylinder 60A and the cylinder on a lower side will be referred to as the lower cylinder 60B.
  • the compression chambers 63A and 63B are formed inside the cylinders 60A and 60B, respectively.
  • the compression chambers 63A and 63B accommodate the piston rotors 62.
  • a separator plate 69 is disposed between the cylinders 60A and 60B to be vertically interposed between the cylinders 60A and 60B.
  • the separator plate 69 separates the compression chambers 63A and 63B from each other.
  • Suction holes 64 and 65 are formed in the upper cylinder 60A and the lower cylinder 60B, the suction holes 64 and 65 being at positions facing the opening 24 as seen in a top view and communicating with the compression chambers 63A and 63B in the cylinders 60A and 60B via the suction pipe 7.
  • the suction holes 64 and 65 are open at outer peripheral surfaces of the cylinders 60A and 60B and thus opening holes 60x are formed in the cylinders 60A and 60B.
  • the eccentric shaft portions 61 are provided at a lower end portion of the rotary shaft 3 and are provided inside the piston rotors 62 in a state of being offset from the central axis of the rotary shaft 3 in a direction orthogonal to the central axis.
  • Each piston rotor 62 has a cylindrical shape of which the outer diameter is smaller than the inner diameter of the cylinder 60, is disposed inside the cylinder 60, and is fixed to the eccentric shaft portion 61 with the eccentric shaft portion 61 inserted thereinto.
  • the piston rotors 62 rotate eccentrically with respect to the rotational axis O as the rotary shaft 3 rotates.
  • the suction holes 64 and 65 are holes through which a refrigerant can flow into the cylinders 60A and 60B.
  • the rotary compression portion 6 is provided with a discharge hole (not shown). Through the discharge hole, the refrigerant compressed at the rotary compression portion 6 is discharged to an internal space of the housing 2 with a middle pressure, that is, a space above the cylinders 60A and 60B.
  • the suction pipe 7 includes a main pipe 70 that is disposed above the upper cylinder 60A and extends in a radial direction of the rotary shaft 3 to penetrate the housing 2 and a connection pipe 71 that extends downward from an inner end 70a of the main pipe 70 that is in the housing 2.
  • An upper end 71a of the connection pipe 71 is connected to the inner end 70a of the main pipe 70.
  • the connection pipe 71 is disposed over the upper cylinder 60A and the lower cylinder 60B to be parallel with the rotational axis O radially outside the compression chambers 63A and 63B.
  • the inner end 70a of the main pipe 70 is inserted into a radial outer end portion of the upper bearing 4A.
  • the connection pipe 71 extends downward from the inner end 70a of the main pipe 70 through the inside of the upper bearing 4A.
  • connection pipe 71 is provided with through-holes 71b that radially penetrate the connection pipe 71 to respectively communicate with the suction holes 64 and 65.
  • the through-holes 71b are disposed on the axes of the suction holes 64 and 65.
  • Sealing plugs 72 that seal the suction holes 64 and 65 are fitted into the opening holes 60x of radial outer end portions of the suction holes 64 and 65.
  • the sealing plugs 72 are, for example, metal screws or the like. Accordingly, the compression chambers 63A and 63B and the connection pipe 71 communicate with each other via the suction holes 64 and 65 and the through-holes 71b.
  • An inner diameter d1 of the main pipe 70 is set to be larger than thicknesses t1 and t2 as dimensions of the cylinders 60A and 60B in a direction of the rotational axis.
  • the inner diameter d1 of the main pipe 70 and an inner diameter d2 of the connection pipe 71 are the same as each other and the inner diameter d1 and the inner diameter d2 are larger than inner diameters d3 and d4 of the suction holes 64 and 65.
  • the inner diameter d3 of the upper suction hole 64 provided in the upper cylinder 60A may be set to be equal to or smaller than the inner diameter d4 of the lower suction hole 65 provided in the lower cylinder 60B.
  • a refrigerant is supplied from the main pipe 70 of the suction pipe 7 to the compression chambers 63A and 63B, which are internal spaces of the cylinders 60, via the connection pipe 71 and the suction holes 64 and 65 of the cylinders 60A and 60B.
  • Discharge holes (not shown) through which the refrigerant is discharged are formed at predetermined positions in the cylinders 60A and 60B and the discharge holes are provided with a reed valve (not shown). Accordingly, when the pressure of the compressed refrigerant is increased, the reed valve is pressed and opened so that the refrigerant is discharged to the outside of the cylinders 60A and 60B. The discharged refrigerant is further compressed at the scroll compression portion 10 and then discharged to an external pipe (not shown) from the discharge pipe 13 provided in an upper portion of the housing 2.
  • the main pipe 70 can be disposed above the cylinders 60A and 60B and connected thereto such that the main pipe 70 communicates with the cylinders 60A and 60B via the connection pipe 71 and the suction holes 64 and 65. That is, a refrigerant can be sucked into each of the compression chambers of the two cylinders 60A and 60B through one suction pipe 7.
  • connection pipe 71 Since the connection pipe 71 is disposed radially outside the compression chambers 63A and 63B, the compression chambers 63A and 63B are not directly connected to each other by the connection pipe 71. Therefore, the refrigerant can be sucked into the compression chambers 63A and 63B through one suction pipe 7 without a decrease in compression efficiency.
  • each of the cylinders 60A and 60B is provided with one suction pipe 7, it is difficult to perform processing when connecting the suction pipes 7 to the housing 2 at positions where the suction pipes 7 penetrate the housing 2. That is, a processing operation between the two suction pipes 7 is difficult.
  • the thickness of the separator plate 69 since it is possible to reduce the number of suction pipes 7 to one.
  • the distance between the two cylinders 60A and 60B can be made small and thus it is possible to reduce vibration caused by the eccentric movement of the piston rotors 62.
  • the main pipe 70 of the suction pipe 7 is disposed above the plurality of cylinders 60A and 60B and thus the inner diameter d1 of the main pipe 70 is not limited to the thickness of the cylinders 60A and 60B or the separator plate 69.
  • the inner diameter d2 of the connection pipe 71 is not also limited to the thickness of the cylinders 60A and 60B or the separator plate 69. As a result, the inner diameters d1 and d2 of the main pipe 70 and the connection pipe 71 can be made large.
  • the inner diameter d1 of the main pipe 70 of the suction pipe 7 and the inner diameter d2 of the connection pipe 71 are the same as each other and are set to be larger than the inner diameter of the suction holes 64 and 65.
  • the suction holes 64 and 65 communicating with the connection pipe 71 are provided in the cylinders 60A and 60B and thus the compression efficiency is improved since a refrigerant efficiently branches and flows into the compression chambers 63A and 63B of a pair of the cylinders 60A and 60B from one suction pipe 7.
  • a processing tool such as a drill
  • the opening holes 60x are in a state of being sealed by the sealing plugs 72 after the lateral holes are processed, it is possible to avoid that a refrigerant that is supplied from the main pipe 70 and flows through the connection pipe 71 flows out of the cylinders 60A and 60B without being directed to the compression chambers 63A and 63B.
  • the refrigerant can be sufficiently supplied to the compression chamber 63B of the lower cylinder 60B as well, insufficiency of the amount of the refrigerant supplied to the lower cylinder 60B can be prevented, and a decrease in compression efficiency can be avoided.
  • the twin rotary type compressor 1 including the two cylinders 60A and 60B has been described as a subject.
  • the compressor 1 is not limited to a twin rotary type compressor and may include a larger number of cylinders.
  • the main pipe 70 of the suction pipe 7 is disposed above the cylinders 60A and 60B, extends in the radial direction of the rotary shaft 3, and communicates with the compression chambers 63A and 63B has been described.
  • the main pipe 70 may be disposed below the cylinders 60A and 60B.
  • the inner diameter d1 of the main pipe 70, the inner diameter d2 of the connection pipe 71, the inner diameters d3 and d4 of the suction holes 64 and 65 of the cylinders 60A and 60B, and the thicknesses t1 and t2 of the cylinders 60A and 60B are set with respect to each part.
  • the present invention is not limited thereto.
  • the inner diameter d1 of the main pipe 70 may not be larger than the thickness of the cylinders 60A and 60B.
  • the inner diameter d1 of the main pipe 70 and an inner diameter d2 of the connection pipe 71 may not be the same as each other and the inner diameters d1 and d2 may not be larger than the inner diameter of the suction holes 64 and 65.
  • the inner diameter d3 of the suction hole 64 provided in the upper cylinder 60A may be set to be equal to or smaller than the inner diameter d4 of the suction hole 65 provided in the lower cylinder 60B.
  • a cooling channel that connects the connection pipe 71 and the compression chambers 63A and 63B may be formed in the cylinders 60A and 60B without providing the opening holes 60x and the sealing plugs 72.
  • the shapes, the sizes, and the like of the housing 2, the rotary shaft 3, the upper bearing 4A, the lower bearing 4B, the electric motor 5, the rotary compression portion 6 (cylinders 60, eccentric shaft portions 61, and piston rotors 62), the scroll compression portion 10, and the suction pipe 7 can be set appropriately.
  • vibration can be reduced without a decrease in compression efficiency.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP19925955.7A 2019-04-25 2019-04-25 Rotationsverdichter Pending EP3951181A4 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2019/017646 WO2020217385A1 (ja) 2019-04-25 2019-04-25 ロータリ圧縮機

Publications (2)

Publication Number Publication Date
EP3951181A1 true EP3951181A1 (de) 2022-02-09
EP3951181A4 EP3951181A4 (de) 2022-04-13

Family

ID=72941146

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19925955.7A Pending EP3951181A4 (de) 2019-04-25 2019-04-25 Rotationsverdichter

Country Status (3)

Country Link
EP (1) EP3951181A4 (de)
JP (1) JPWO2020217385A1 (de)
WO (1) WO2020217385A1 (de)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2022167023A (ja) * 2021-04-22 2022-11-04 三菱重工サーマルシステムズ株式会社 圧縮機

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5939794U (ja) * 1982-09-06 1984-03-14 三菱重工業株式会社 ベ−ン型回転流体機械
JPS619584U (ja) * 1984-06-20 1986-01-21 三洋電機株式会社 多気筒回転式圧縮機
JPH08270580A (ja) * 1995-03-31 1996-10-15 Sanyo Electric Co Ltd 密閉型回転圧縮機
JP2001132673A (ja) * 1999-11-04 2001-05-18 Matsushita Electric Ind Co Ltd 密閉型ロータリー圧縮機
JP2003120529A (ja) * 2001-10-17 2003-04-23 Toyota Industries Corp 真空ポンプにおけるガス供給装置
JP2010150949A (ja) * 2008-12-24 2010-07-08 Daikin Ind Ltd 回転式圧縮機
CN102644597B (zh) * 2011-02-16 2014-09-24 广东美芝制冷设备有限公司 双缸式旋转压缩机
JP5984486B2 (ja) 2012-04-27 2016-09-06 三菱重工業株式会社 ロータリ圧縮機
ES2953629T3 (es) * 2017-03-17 2023-11-14 Daikin Ind Ltd Compresor rotativo

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Publication number Publication date
JPWO2020217385A1 (de) 2020-10-29
EP3951181A4 (de) 2022-04-13
WO2020217385A1 (ja) 2020-10-29

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