WO2020217385A1 - Compresseur rotatif - Google Patents

Compresseur rotatif Download PDF

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Publication number
WO2020217385A1
WO2020217385A1 PCT/JP2019/017646 JP2019017646W WO2020217385A1 WO 2020217385 A1 WO2020217385 A1 WO 2020217385A1 JP 2019017646 W JP2019017646 W JP 2019017646W WO 2020217385 A1 WO2020217385 A1 WO 2020217385A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinders
suction
cylinder
inner diameter
pipe
Prior art date
Application number
PCT/JP2019/017646
Other languages
English (en)
Japanese (ja)
Inventor
隆史 渡辺
央幸 木全
陽平 堀田
創 佐藤
Original Assignee
三菱重工サーマルシステムズ株式会社
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 三菱重工サーマルシステムズ株式会社 filed Critical 三菱重工サーマルシステムズ株式会社
Priority to JP2021515410A priority Critical patent/JPWO2020217385A1/ja
Priority to EP19925955.7A priority patent/EP3951181A4/fr
Priority to PCT/JP2019/017646 priority patent/WO2020217385A1/fr
Publication of WO2020217385A1 publication Critical patent/WO2020217385A1/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
    • 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.
  • Patent Document 1 Conventionally, as a rotary compressor, for example, as shown in Patent Document 1, a housing, a rotary shaft extending in the vertical direction in the housing and rotating by an electric motor, and a rotary compressor having a cylinder supported by the rotary shaft. , An upper bearing that is rotatably supported by a rotating shaft and fixed to the top and bottom of the cylinder, and a lower bearing are known. A suction pipe capable of introducing a refrigerant into the compression chamber of the rotary compression unit is connected to the cylinder. Further, Patent Document 1 also discloses a twin rotary compressor in which cylinders are arranged in two stages vertically. Each cylinder is connected to at least one suction tube that extends separately from the accumulator.
  • the thickness of the separator plate interposed between the cylinders in order to reduce the vibration. This is because if the separator plate is made thicker, the two cylinders will be separated from each other, and the influence of vibration due to the eccentric movement of the piston rotor will increase. However, if the thickness of the separator plate is reduced, it becomes difficult to process the suction pipes at the connection portion between the two suction pipe housings. Therefore, in order to widen the space between the suction pipes in order to facilitate processing, it is necessary to make the separator plate thicker or the suction pipes thinner.
  • the present invention has been made in view of the above-mentioned problems, and an object of the present invention is to provide a rotary compressor having a plurality of cylinders, which can reduce vibration without lowering the compression efficiency.
  • the present invention has adopted the following aspects in order to solve the above problems and achieve the above object.
  • the rotary compressor according to one aspect of the present invention includes a rotating shaft extending along an axis, a bearing that rotatably supports the rotating shaft around the axis, a motor for rotating the rotating shaft, and the rotation.
  • a rotary compression unit that compresses the refrigerant by rotating the shaft, a housing that houses the rotary shaft, the bearing, the motor, and the rotary compression unit, and a suction pipe that can introduce the refrigerant into the compression chamber of the rotary compression unit.
  • the rotary compression unit includes, a plurality of cylinders forming the compression chamber and arranged side by side in the vertical direction, and a separator plate arranged between the plurality of cylinders, and the suction portion is provided.
  • the pipes are a main pipe arranged above or below the cylinder and extending through the housing in the radial direction of the rotation shaft, and a plurality of pipes connected to the main pipe and extending in the axial direction of the rotation shaft. It has a connecting pipe arranged between the plurality of cylinders on the radial outside of the compression chamber in the cylinder and communicating with each of the compression chambers.
  • the main pipe of the suction pipe is arranged above or below each of the plurality of cylinders, and in each of the compression chambers of the plurality of cylinders via the connecting pipe extending in the axial direction.
  • the refrigerant can be inhaled.
  • the refrigerant can be sucked into each of the compression chambers by one suction pipe without connecting the compression chambers of the plurality of cylinders to reduce the compression efficiency. If only one suction pipe can be used, it is easy to process the portion connecting the suction pipe to the housing even if the thickness of the separator plate is reduced.
  • the inner diameter of the main pipes is not limited by the thickness of the cylinders, and the inner diameter of the main pipes is increased. It becomes possible to do. Further, the inner diameter of the connecting pipe can be increased. Therefore, more refrigerant can be compressed and the compression efficiency can be improved.
  • the inner diameter of the suction pipe may be larger than the thickness of the cylinder.
  • each of the plurality of cylinders has a suction flow path extending in the radial direction and communicating the compression chamber and the connecting pipe. It may be provided.
  • each compression chamber can be supplied to each compression chamber via each suction flow path extending in the radial direction through a connecting pipe extending in the axial direction from the suction pipe. Therefore, the flow can be efficiently divided from one suction pipe into the compression chambers of a plurality of cylinders, and the compression efficiency can be improved.
  • the suction flow path is opened on the outer peripheral surface of the cylinder to provide an opening hole in the cylinder, and a sealing plug is provided in the opening hole. It may have been.
  • a lateral hole can be machined in each cylinder to form a suction flow path.
  • the opening hole is sealed by the sealing plug. Therefore, while easily processing the suction flow path, the refrigerant flowing through the connecting pipe is outside the cylinder from the opening hole. It is possible to avoid leaking to.
  • the inner diameter of the suction pipe and the inner diameter of the connecting pipe are the same, and the inner diameter of the main pipe and the inner diameter of the connecting pipe are the suction. It may be larger than the inner diameter of the flow path.
  • the inner diameters of the main pipe and the connecting pipe, which form the flow paths of the refrigerant supplied into the suction flow paths of the plurality of cylinders, can be made larger than the inner diameters of the suction flow paths of the cylinders. Refrigerant can be supplied to each compression chamber, and the compression efficiency can be improved.
  • the inner diameter of the suction flow path provided in the upper cylinder of the cylinders is the inner diameter of the suction flow path provided in the lower cylinder. It may be less than or equal to the inner diameter of the suction flow path.
  • vibration can be reduced by reducing the thickness of the separator plate without lowering the compression efficiency.
  • FIG. 1 is a vertical cross-sectional view showing the configuration of a rotary compressor according to the first embodiment of the present invention.
  • FIG. 2 is a vertical cross-sectional view showing a configuration of a main part around a rotary compression portion of the rotary compressor shown in FIG.
  • the rotary compressor according to the present embodiment (hereinafter, simply referred to as compressor 1) is a vertical closed rotary compressor used in, for example, an air conditioner or a refrigerating device.
  • the compressor 1 includes a housing 2, a rotating shaft 3, an upper bearing 4A and a lower bearing 4B, an electric motor 5, a rotary compression unit 6, a scroll compression unit 10, and a suction pipe 7.
  • the rotation axis 3 extends along an axis (rotation axis O described later).
  • the upper bearing 4A and the lower bearing 4B rotatably support the rotating shaft 3 around the rotating axis O.
  • the electric motor 5 rotates the rotating shaft 3.
  • the rotary compression unit 6 compresses the refrigerant by the rotation of the rotating shaft 3.
  • the suction pipe 7 makes it possible to introduce the refrigerant into the compression chambers 63A and 63B of the rotary compression unit 6.
  • the compressor 1 of the present embodiment is a two-stage compressor further including a scroll compression unit 10 above the rotary compression unit 6, but the scroll compression unit 10 does not necessarily have to be provided.
  • the central axis of the housing 2 and the rotation axis 3 are arranged on a common axis extending in the vertical direction (vertical direction), and this common axis is hereinafter referred to as a rotation axis O.
  • the rotating shaft 3 is arranged so that the extending direction is the vertical direction, and is rotatably housed in the housing 2 around the rotating axis O.
  • the housing 2 is a closed type and extends in the vertical direction, and houses a rotating shaft 3, bearings 4A and 4B, an electric motor 5, and a rotary compression unit 6.
  • the housing 2 has a cylindrical main body portion 21, and an upper lid portion 22 and a lower lid portion 23 that close the upper and lower openings of the main body portion 21.
  • the housing 2 has an opening 24 formed above the cylinders 60 (60A, 60B) at the lower part of the side wall.
  • the suction pipe 7 is fixed to the opening 24 in a state of being inserted with the pipe axis direction oriented in the horizontal direction.
  • An oil sump is formed at the bottom of the housing 2 by accumulating oil.
  • the liquid level of the oil pool at the time of initial filling of oil is located above the rotary compression unit 6.
  • the rotary compression unit 6 is driven in the oil pool.
  • the upper lid portion 22 is provided with a discharge pipe 13 that penetrates the peripheral wall portion in the thickness direction and communicates with the inside of the housing 2.
  • the discharge pipe 13 discharges the compressed refrigerant to the outside of the housing 2.
  • the electric motor 5 is housed in a central portion of the housing 2 in the vertical direction.
  • the electric motor 5 has a rotor 51 and a stator 52.
  • the rotor 51 is fixed to the outer peripheral surface of the rotating shaft 3 and is arranged above the rotary compression unit 6.
  • the stator 52 is arranged so as to surround the outer peripheral surface of the rotor 51, and is fixed to the inner surface 21a of the main body 21 of the housing 2.
  • a power supply (not shown) is connected to the electric motor 5 via the terminal 9.
  • the electric motor 5 rotates the rotating shaft 3 by the electric power from the power source.
  • the upper bearing 4A and the lower bearing 4B are arranged so as to sandwich the rotary compression portion 6 from above and below.
  • the upper bearing 4A and the lower bearing 4B are each formed of, for example, a metal material, and are fixed to the cylinder 60 constituting the rotary compression portion 6 by, for example, bolting. Further, the upper bearing 4A is fixed to the housing 2.
  • the rotary shaft 3 is rotatably supported by the housing 2 around the rotary axis O by the upper bearing 4A and the lower bearing 4B.
  • the rotary compression unit 6 is arranged at the bottom of the housing 2 below the electric motor 5 to compress the refrigerant.
  • the rotary compression unit 6 has a plurality of (two in this embodiment) disc-shaped cylinders 60 (60A, 60B), an eccentric shaft portion 61, and a piston rotor 62.
  • the two cylinders 60A and 60B are vertically arranged in the housing 2 along the rotation axis O direction, respectively.
  • the cylinder located on the upper side is referred to as an upper cylinder 60A
  • the cylinder located on the lower side is referred to as a lower cylinder 60B.
  • Compression chambers 63A and 63B are formed inside the cylinders 60A and 60B, respectively.
  • the compression chambers 63A and 63B accommodate the piston rotor 62.
  • the separator plate 69 is arranged between the cylinders 60A and 60B so as to be sandwiched vertically by the cylinders 60A and 60B.
  • the separator plate 69 separates the compression chambers 63A and 63B from each other.
  • the upper cylinder 60A and the lower cylinder 60B have suction holes 64, 65 (in a position facing the opening 24 in top view) communicating with the compression chambers 63A, 63B in the cylinders 60A, 60B via the suction pipe 7.
  • the suction flow path is formed.
  • the suction holes 64 and 65 are opened on the outer peripheral surfaces of the cylinders 60A and 60B, so that the cylinders 60A and 60B are formed with opening holes 60x.
  • the eccentric shaft portion 61 is provided at the lower end portion of the rotating shaft 3, and is provided inside the piston rotor 62 in a state of being offset in a direction orthogonal to the central axis of the rotating shaft 3.
  • the piston rotor 62 is arranged inside the cylinder 60 in a cylindrical shape having an outer diameter smaller than the inner diameter of the cylinder 60, and the eccentric shaft portion 61 is inserted and fixed to the eccentric shaft portion 61.
  • the piston rotor 62 rotates eccentrically with respect to the rotation axis O as the rotation shaft 3 rotates.
  • the suction holes 64 and 65 are holes for allowing the refrigerant to flow into the cylinders 60A and 60B.
  • the rotary compression unit 6 is provided with a discharge hole (not shown). Through this discharge hole, the refrigerant compressed by the rotary compression unit 6 is discharged into the internal space that is the intermediate pressure of the housing 2, that is, the space above the cylinders 60A and 60B.
  • the suction pipe 7 is arranged above the upper cylinder 60A, and includes a main pipe 70 extending in the radial direction of the rotating shaft 3 and penetrating the housing 2, and a connecting pipe 71 extending downward from the inner end 70a in the housing 2 of the main pipe 70. ,have.
  • the upper end 71a of the connecting pipe 71 is connected to the inner end 70a of the main pipe 70.
  • the connecting pipe 71 is arranged between the upper cylinder 60A and the lower cylinder 60B so as to be parallel to the rotation axis O on the radial outer side of each of the compression chambers 63A and 63B.
  • the inner end 70a of the main pipe 70 is inserted into the radial outer end of the upper bearing 4A.
  • the connecting 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 a through hole 71b that penetrates in the radial direction so as to communicate with each of the suction holes 64 and 65.
  • the through hole 71b is arranged on the axis of each of the suction holes 64 and 65.
  • a sealing plug 72 for sealing the suction holes 64 and 65 is fitted in the opening hole 60x at the radial outer end of the suction holes 64 and 65.
  • the sealing stopper 72 is, for example, a metal screw or the like.
  • the inner diameter d1 of the main pipe 70 is set to be larger than the thicknesses t1 and t2 of the cylinders 60A and 60B, respectively. Further, the inner diameter d1 of the main pipe 70 and the inner diameter d2 of the connecting pipe 71 have the same diameter, and the inner diameters d1 and the inner diameter d2 are larger than the inner diameters d3 and d4 of the suction holes 64 and 65, respectively. Further, the inner diameter d3 of the upper suction hole 64 provided in the upper cylinder 60A may be set to be equal to or less than the inner diameter d4 of the lower suction hole 65 provided in the lower cylinder 60B.
  • the refrigerant flows from the main pipe 70 of the suction pipe 7 to the compression chambers 63A and 63B which are the internal spaces of the cylinder 60 via the connection pipe 71 and the suction holes 64 and 65 of the cylinders 60A and 60B. Be supplied. Then, due to the eccentric movement of the piston rotor 62, the volumes of the compression chambers 63A and 63B are gradually reduced to compress the refrigerant. Discharge holes (not shown) for discharging the refrigerant are formed at predetermined positions of the cylinders 60A and 60B, and a lead valve (not shown) is provided in the discharge holes.
  • the reed valve is pushed open and the refrigerant is discharged to the outside of the cylinders 60A and 60B.
  • the discharged refrigerant is further compressed by the scroll compression unit 10 and then discharged from a discharge pipe 13 provided in the upper part of the housing 2 to an external pipe (not shown).
  • a main pipe 70 is arranged above each of the cylinders 60A and 60B, and communicates with each other via a connecting pipe 71 and suction holes 64 and 65. Can be connected. That is, the refrigerant can be sucked into each of the compression chambers of the two cylinders 60A and 60B by using one suction pipe 7.
  • each of the compression chambers 63A and 63B is not directly connected by the connecting pipe 71. Therefore, the refrigerant can be sucked into the respective compression chambers 63A and 63B by one suction pipe 7 without lowering the compression efficiency.
  • the inner diameter d1 of the main pipe 70 becomes the thickness of the cylinders 60A and 60B and the separator plate 69.
  • the inner diameter d2 of the connecting pipe 71 is not limited to the thicknesses of the cylinders 60A and 60B and the separator plate 69. As a result, the inner diameters d1 and d2 of the main pipe 70 and the connecting pipe 71 can be increased.
  • the inner diameter d1 of the main pipe 70 of the suction pipe 7 and the inner diameter d2 of the connecting pipe 71 are provided to have the same diameter, and are set larger than the inner diameters of the suction holes 64 and 65, respectively. As a result, more refrigerant can be compressed and the compression efficiency can be improved.
  • the refrigerant can be efficiently supplied from one suction pipe 7 to the compression chambers 63A and 63B of the pair of cylinders 60A and 60B.
  • the flow can be divided and the compression efficiency can be improved.
  • a processing tool such as a drill into the outer peripheral surfaces of the cylinders 60A and 60B from the outside in the radial direction
  • lateral holes are machined in the cylinders 60A and 60B to form suction holes 64, 65 can be formed.
  • the opening hole 60x is sealed by the sealing plug 72 after the processing of the horizontal hole, the refrigerant supplied from the main pipe 70 and flowing through the connecting pipe 71 does not go to the compression chambers 63A and 63B, but the cylinder 60A. , It is possible to prevent the outflow from 60B.
  • the upper cylinder 60A is compressed among the refrigerants flowing in the suction pipe 7. A large amount of refrigerant is not supplied to the chamber 63A. Therefore, the refrigerant can be sufficiently supplied to the compression chamber 63B of the lower cylinder 60B, it is possible to prevent the supply amount of the refrigerant from being insufficient to the lower cylinder 60B, and it is possible to avoid a decrease in the compression efficiency.
  • the twin rotary type compressor 1 having two cylinders 60A and 60B is targeted, but the compressor 1 is not limited to the twin rotary type and has more cylinders. You may.
  • the main pipe 70 of the suction pipe 7 is arranged above the cylinders 60A and 60B and extends in the radial direction of the rotating shaft 3 to communicate with the compression chambers 63A and 63B, but the main pipe 70 is a cylinder. It may be arranged below 60A and 60B.
  • the inner diameter d1 of the main pipe 70, the inner diameter d2 of the connecting 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 in each part.
  • the inner diameter d1 of the main pipe 70 is not limited to be larger than the thickness of the cylinders 60A and 60B.
  • the inner diameter d1 of the main pipe 70 and the inner diameter d2 of the connecting pipe 71 are provided to have the same diameter, and the inner diameters d1 and d2 are not limited to be larger than the inner diameters of the suction holes 64 and 65. Further, the inner diameter d3 of the suction hole 64 provided in the upper cylinder 60A is not limited to be equal to or less than the inner diameter d4 of the suction hole 65 provided in the lower cylinder 60B.
  • the suction holes 64 and 65 are provided, and the sealing plug 72 is provided in the opening holes 60x of the suction holes 64 and 65, but the opening holes 60x and the sealing plug 72 are not provided.
  • Refrigerant flow paths that connect the connection pipe 71 and the compression chambers 63A and 63B may be formed in the cylinders 60A and 60B.
  • the configuration such as, size, etc. can be set to an appropriate configuration.
  • vibration can be reduced without lowering the 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)

Abstract

Selon la présente invention, une partie de compression rotative (6) comporte une pluralité de cylindres (60A, 60B) qui forment des chambres de compression (63A, 63B) et sont disposés côte à côte dans la direction verticale, et une plaque de séparation (69) disposée entre la pluralité de cylindres (60A, 60B), le tuyau d'aspiration (7) ayant un tuyau principal (70) qui est disposé au-dessus ou au-dessous des cylindres (60A, 60B) et qui s'étend à travers un boîtier (2) dans une direction radiale d'un arbre rotatif (3), et un tuyau de raccordement (71) qui est relié au tuyau principal (70), s'étend dans la direction axiale (O) de l'arbre rotatif (3), est disposé entre la pluralité de cylindres (60A, 60B) sur un côté extérieur radial des chambres de compression (63A, 63B) dans la pluralité de cylindres (60A, 60B), et communique avec chacune des chambres de compression (63A, 63B).
PCT/JP2019/017646 2019-04-25 2019-04-25 Compresseur rotatif WO2020217385A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2021515410A JPWO2020217385A1 (fr) 2019-04-25 2019-04-25
EP19925955.7A EP3951181A4 (fr) 2019-04-25 2019-04-25 Compresseur rotatif
PCT/JP2019/017646 WO2020217385A1 (fr) 2019-04-25 2019-04-25 Compresseur rotatif

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2019/017646 WO2020217385A1 (fr) 2019-04-25 2019-04-25 Compresseur rotatif

Publications (1)

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WO2020217385A1 true WO2020217385A1 (fr) 2020-10-29

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EP (1) EP3951181A4 (fr)
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4080056A3 (fr) * 2021-04-22 2022-11-09 Mitsubishi Heavy Industries Thermal Systems, Ltd. Compresseur
WO2024111342A1 (fr) * 2022-11-25 2024-05-30 三菱重工サーマルシステムズ株式会社 Compresseur

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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
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
CN102644597A (zh) * 2011-02-16 2012-08-22 广东美芝制冷设备有限公司 双缸式旋转压缩机
JP2013227957A (ja) 2012-04-27 2013-11-07 Mitsubishi Heavy Ind Ltd ロータリ圧縮機

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001132673A (ja) * 1999-11-04 2001-05-18 Matsushita Electric Ind Co Ltd 密閉型ロータリー圧縮機
WO2018169072A1 (fr) * 2017-03-17 2018-09-20 ダイキン工業株式会社 Compresseur rotatif

Patent Citations (7)

* 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
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EP4080056A3 (fr) * 2021-04-22 2022-11-09 Mitsubishi Heavy Industries Thermal Systems, Ltd. Compresseur
WO2024111342A1 (fr) * 2022-11-25 2024-05-30 三菱重工サーマルシステムズ株式会社 Compresseur

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