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WO2018199061A1 - Compresseur à compression à deux étages, à pression interne moyenne - Google Patents

Compresseur à compression à deux étages, à pression interne moyenne Download PDF

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Publication number
WO2018199061A1
WO2018199061A1 PCT/JP2018/016541 JP2018016541W WO2018199061A1 WO 2018199061 A1 WO2018199061 A1 WO 2018199061A1 JP 2018016541 W JP2018016541 W JP 2018016541W WO 2018199061 A1 WO2018199061 A1 WO 2018199061A1
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WO
WIPO (PCT)
Prior art keywords
compression
stage
compression mechanism
pressure
internal
Prior art date
Application number
PCT/JP2018/016541
Other languages
English (en)
Japanese (ja)
Inventor
松崎　章
佐藤　孝
Original Assignee
パナソニックＩｐマネジメント株式会社
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 パナソニックＩｐマネジメント株式会社 filed Critical パナソニックＩｐマネジメント株式会社
Priority to EP18790603.7A priority Critical patent/EP3617514B1/fr
Priority to CN201880027972.6A priority patent/CN110573741A/zh
Publication of WO2018199061A1 publication Critical patent/WO2018199061A1/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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0238—Hermetic compressors with oil distribution channels
    • F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B37/00—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00
    • F04B37/10—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use
    • F04B37/12—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use to obtain high pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • 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
    • 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
    • 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
    • F04C29/02—Lubrication; Lubricant separation

Definitions

  • the present invention relates to an internal / intermediate pressure two-stage compression compressor suitable particularly when carbon dioxide is used as a refrigerant.
  • Patent Document 1 discloses an internal medium pressure type two-stage compression compressor.
  • the oil is pumped up from the oil sump at the bottom of the sealed container and rises in the oil supply passage in the shaft. It enters the through hole and passes through the through hole, and is supplied to the low pressure chamber side (suction side) of the high stage side cylinder.
  • the internal pressure (suction pressure) in the low pressure chamber of the high-stage side cylinder is lower than the pressure on the inner peripheral edge side of the intermediate partition plate due to suction pressure loss during the suction process. Due to this pressure difference, the oil is injected from the oil supply passage in the shaft through the through hole of the intermediate partition plate into the low pressure chamber in the high-stage cylinder and supplied.
  • FIG. 4A is a plan view of the main part of the compression mechanism section on the high stage side of the internal medium pressure type two-stage compression compressor as disclosed in Patent Document 1.
  • FIG. FIG. 4B is a further enlarged plan view of the main part of FIG.
  • the compression mechanism unit 100 includes a cylinder 101, a piston 102 disposed in the cylinder 101, and a vane 103 that partitions the cylinder 101.
  • an oil supply passage 105 is formed in the suction passage 104 of the compression mechanism unit 100.
  • a closed space 106 is formed between the vane 103, the cylinder 101, and the piston 102 when the piston 102 turns from the top dead center to the position of the suction passage 104.
  • the closed space 106 is in a negative pressure state.
  • the suction pressure in the suction passage 104 is lowered by the closed space 106.
  • the pressure difference between the case internal pressure and the suction pressure in the sealed container is increased, and the lubricating oil exceeding the set value flows into the compression chamber from the oil supply passage 105, and the discharge amount of the lubricating oil from the high-stage compression chamber is reduced. It will increase.
  • the refrigerant is directly discharged from the high-stage compression mechanism part to the outside of the sealed container, the refrigerant is discharged into the sealed container and the lubricating oil is separated and collected in the sealed container.
  • the OCR lubricating oil circulation ratio
  • an object of the present invention is to provide an internal / intermediate pressure type two-stage compression compressor that can prevent the lubricating oil from flowing into the high-stage side compression chamber beyond the set value.
  • the internal medium pressure type two-stage compression compressor includes an electric motor part and a compression mechanism part in a sealed container, and the electric motor part and the compression mechanism part are connected by a shaft, and the compression mechanism part Includes a cylinder, a piston disposed in the cylinder, and a vane that partitions the cylinder, and the compression mechanism includes a first compression mechanism that performs first-stage low-stage compression, and two stages.
  • a second compression mechanism that performs high-stage compression of the eyes, an oil supply passage is formed in the suction passage of the second compression mechanism, and the refrigerant gas compressed by the first compression mechanism is placed in the sealed container
  • the refrigerant gas is compressed by the second compression mechanism and discharged outside the sealed container, and the difference between the case internal pressure in the sealed container and the suction pressure in the suction passage of the second compression mechanism
  • the second compression mechanism from the oil supply passage by pressure
  • a closed space is not formed.
  • the internal intermediate pressure type two-stage compression compressor according to the first aspect of the present invention, wherein the pressure communication groove is provided on a vane side wall surface located on the vane side of the suction passage. It is formed.
  • the internal medium pressure type two-stage compression compressor according to claim 3 of the present invention is the internal medium pressure type two stage compression compressor according to claim 2, wherein the pressure communication groove is provided with a virtual central axis parallel to the central axis of the shaft. It is characterized by being formed with a circular arc surface at the center.
  • the internal intermediate pressure type two-stage compression compressor according to the third aspect of the present invention, wherein the arc surface extends from one end surface of the cylinder to the other end surface. It is characterized by being formed.
  • the internal medium pressure type two-stage compression compressor of the present invention according to claim 5 is the internal medium pressure type two stage compression compressor according to claim 3 or 4, wherein the same curvature as that of the arc surface about the virtual central axis.
  • a curved surface is formed on an anti-vane side wall surface facing the vane side wall surface.
  • the internal medium pressure type two-stage compression compressor of the present invention described in claim 6 is the internal medium pressure type two stage compression compressor according to any one of claims 1 to 5, wherein an oil pickup is provided at a lower end of the shaft.
  • the shaft includes an in-shaft oil supply passage through which lubricating oil sucked up by the oil pickup passes, and an intermediate partition plate is provided between the first compression mechanism portion and the first compression mechanism portion.
  • the intermediate partition plate is formed with an intermediate partition plate oil supply passage for guiding the lubricating oil in the shaft oil supply passage to the oil supply passage.
  • the internal medium pressure type two-stage compression compressor of the present invention according to claim 7 is the internal medium pressure type two stage compression compressor according to any one of claims 1 to 6, wherein the refrigerant is compressed by the compression mechanism section. It is characterized by using carbon dioxide.
  • the lubricating oil can be prevented from flowing into the second compression chamber beyond the set value, and the discharge amount of the lubricating oil from the second compression chamber can be suppressed.
  • FIG. 1 is a cross-sectional view of an internal medium pressure type two-stage compression compressor according to an embodiment of the present invention. 1 is an enlarged cross-sectional view of the main part of FIG. Top view of the main part of the compression mechanism on the high stage side of the internal medium pressure type two-stage compression compressor The principal part top view of the compression mechanism part of the high stage side of the conventional internal medium pressure type two-stage compression compressor
  • a closed space is not formed between the vane, the cylinder and the piston when the piston turns from the top dead center to the position of the suction passage.
  • a pressure communication groove is formed on the vane side wall surface located on the vane side of the suction passage. According to the second aspect, by forming the pressure communication groove, the closed space between the vane, the cylinder and the piston, which is formed when the piston turns from the top dead center to the position of the suction passage, is eliminated. Can do.
  • the pressure communication groove is formed by an arc surface having a virtual central axis parallel to the central axis of the shaft. According to the third aspect, the pressure communication groove can be formed by suppressing the surface pressure of the vane and the vane groove.
  • an arc surface is formed from one end surface of the cylinder to the other end surface.
  • the pressure communication groove can be formed by rotary cutting.
  • a curved surface having the same curvature as the arc surface with the virtual central axis as the center is formed on the anti-vane side wall surface facing the vane side wall surface.
  • the excluded volume adjusting space can be formed simultaneously with the formation of the pressure communication groove.
  • an oil pickup is provided at the lower end of the shaft, and an oil supply passage in the shaft through which lubricating oil sucked up by the oil pickup passes is formed in the shaft.
  • An intermediate partition plate is provided between the first compression mechanism portion and the first compression mechanism portion, and the intermediate partition plate is formed with an intermediate partition plate oil supply passage for guiding the lubricating oil in the shaft oil supply passage to the oil supply passage. It is.
  • the lubricating oil in the hermetic container can be supplied to the suction passage of the second compression mechanism section using the pressure drop during refrigerant suction.
  • carbon dioxide is used as a refrigerant to be compressed by the compression mechanism.
  • the internal pressure of the sealed container is set to an intermediate pressure, so that the sealed container can be made thin, small and light. Since the differential pressure per stage is reduced and the volume efficiency is improved.
  • FIG. 1 is a cross-sectional view of an internal medium pressure type two-stage compression compressor according to this embodiment
  • FIG. 2 is an enlarged cross-sectional view of a main part of FIG.
  • the internal intermediate pressure type two-stage compression compressor according to this embodiment includes an electric motor unit 20 and a compression mechanism unit 30 in a hermetic container 10.
  • the electric motor unit 20 and the compression mechanism unit 30 are connected by a shaft 40.
  • the electric motor unit 20 includes a stator 21 that is fixed to the inner surface of the sealed container 10 and a rotor 22 that rotates within the stator 21.
  • the internal intermediate pressure type two-stage compression compressor includes, as the compression mechanism section 30, a first compression mechanism section 30A that performs first-stage low-stage compression and a second compression mechanism section that performs second-stage high-stage compression. 30B.
  • the first compression mechanism 30A includes a first cylinder 31A, a first piston 32A disposed in the first cylinder 31A, and a vane (not shown) that partitions the first cylinder 31A. 32A revolves in the first cylinder 31A, and sucks and compresses the low-pressure refrigerant gas.
  • the second compression mechanism section 30B includes a second cylinder 31B, a second piston 32B disposed in the second cylinder 31B, and a vane 33 that partitions the second cylinder 31B (see FIG. 3), and the second piston 32B revolves in the second cylinder 31B to suck and compress the medium-pressure refrigerant gas.
  • a lower bearing 51 is disposed on one surface of the first cylinder 31A, and an intermediate partition plate 52 is disposed on the other surface of the first cylinder 31A.
  • An intermediate partition plate 52 is disposed on one surface of the second cylinder 31B, and an upper bearing 53 is disposed on the other surface of the second cylinder 31B. That is, the intermediate partition plate 52 partitions the first cylinder 31A and the second cylinder 31B.
  • the intermediate partition plate 52 has an opening that is larger than the diameter of the shaft 40.
  • the shaft 40 includes a main shaft portion 41 to which the rotor 22 is attached and supported by the lower bearing 51, a first eccentric portion 42 to which the first piston 32A is attached, a second eccentric portion 43 to which the second piston 32B is attached,
  • the secondary shaft portion 44 is supported by the lower bearing 51.
  • the first eccentric part 42 and the second eccentric part 43 are formed with a phase difference of 180 degrees, and a connecting shaft part 45 is provided between the first eccentric part 42 and the second eccentric part 43. Forming.
  • the first compression chamber 34A is formed between the lower bearing 51 and the intermediate partition plate 52 between the inner peripheral surface of the first cylinder 31A and the outer peripheral surface of the first piston 32A.
  • the second compression chamber 34B is formed between the intermediate partition plate 52 and the upper bearing 53 between the inner peripheral surface of the second cylinder 31B and the outer peripheral surface of the second piston 32B.
  • the exclusion volume ratio of the high-stage compression exclusion volume of the second compression mechanism section 30B to the low-stage compression exclusion volume of the first compression mechanism section 30A is 50% to 110%.
  • An oil sump 11 is formed at the bottom of the sealed container 10, and an oil pickup 12 is provided at the lower end of the shaft 40. Further, an in-shaft oil supply passage 46 is formed in the shaft 40 in the axial direction.
  • the in-shaft oil supply passage 46 is formed with a communication passage 47 for supplying oil to the sliding surface of the compression mechanism 30.
  • the communication passage 47 is formed in the first eccentric portion 42 and the second eccentric portion 43.
  • An oil supply passage 36 is formed in the suction passage 35B of the second compression mechanism portion 30B.
  • the intermediate partition plate 52 is formed with an intermediate partition plate oil supply passage 60 that guides the lubricating oil in the shaft oil supply passage 46 to the oil supply passage 36.
  • the intermediate partition plate oil supply passage 60 includes a first passage 61 extending from the inner peripheral surface 52 a to the outer peripheral surface 52 b of the intermediate partition plate 52, one end opening in the first passage 61, and the other end opening in the oil supply passage 36. And two passages 62.
  • a first suction pipe 13A and a second suction pipe 13B are connected to the side surface of the sealed container 10, and an intermediate pressure discharge pipe 14 and a discharge pipe (not shown) are connected to the sealed container 10.
  • the intermediate pressure discharge pipe 14 is connected to the intermediate pressure discharge port 15.
  • the first suction pipe 13A is connected to the suction passage 35A of the first compression mechanism section 30A
  • the second suction pipe 13B is connected to the suction passage 35B of the second compression mechanism section 30B.
  • the suction passage 35A is connected to the first compression chamber 34A
  • the suction passage 35B is connected to the second compression chamber 34B.
  • the intermediate pressure discharge pipe 14 is connected to an intercooler 16 that cools the medium pressure refrigerant gas, and the intercooler 16 is connected to the second suction pipe 13B.
  • a cup muffler 71 is provided below the lower bearing 51, and an upper cover 72 is provided above the upper bearing 53.
  • a first silencing chamber 81 is formed between the lower bearing 51 and the cup muffler 71, and a second silencing chamber 82 is formed between the upper bearing 53 and the upper cover 72.
  • Medium pressure refrigerant gas compressed in the first compression chamber 34A is discharged into the first silencing chamber 81, and high pressure refrigerant gas compressed in the second compression chamber 34B is discharged into the second silencing chamber 82.
  • the first piston 32A and the second piston 32B revolve in the first compression chamber 34A and the second compression chamber 34B.
  • the gas refrigerant sucked into the first compression chamber 34A from the first suction pipe 13A through the suction passage 35A by the revolving motion of the first piston 32A is compressed in the first compression chamber 34A and then into the first silencing chamber 81. Discharged.
  • the medium pressure refrigerant gas discharged into the first silencing chamber 81 passes through a refrigerant passage (not shown) formed in the lower bearing 51, the first cylinder 31A, the intermediate partition plate 52, the second cylinder 31B, and the upper bearing 53. And discharged into the sealed container 10.
  • the medium-pressure refrigerant gas discharged to the sealed container 10 is guided from the intermediate pressure discharge port 15 to the intermediate pressure discharge pipe 14, further cooled by the intercooler 16, and then guided to the second suction pipe 13 ⁇ / b> B.
  • the gas refrigerant sucked into the second compression chamber 34B from the second suction pipe 13B through the suction passage 35B by the revolving motion of the second piston 32B is compressed in the second compression chamber 34B and then into the second silencer chamber 82. Discharged.
  • the high-pressure refrigerant gas discharged into the second silencing chamber 82 is discharged out of the sealed container 10 from a discharge pipe (not shown).
  • the high-pressure refrigerant gas discharged to the outside of the sealed container 10 is led to the first suction pipe 13A as a low-pressure refrigerant gas via a radiator, a decompressor, and an evaporator.
  • the lubricating oil sucked up from the oil reservoir 11 by the rotation of the shaft 40 is supplied from the communication passage 47 to the compression mechanism unit 30 to lubricate the sliding surface of the compression mechanism unit 30.
  • Part of the lubricating oil supplied from the communication passage 47 is the pressure in the oil supply passage 46 in the shaft, that is, the case internal pressure in the sealed container 10 and the suction pressure in the suction passage 35B of the second compression mechanism portion 30B. Due to the differential pressure, the intermediate partition plate oil supply passage 60 is guided to the second compression chamber 34B of the second compression mechanism 30B through the oil supply passage 36.
  • FIG. 3A is a plan view of the main part of the compression mechanism section on the high stage side of the internal intermediate pressure type two-stage compression compressor according to this embodiment.
  • FIG. 3B is a further enlarged plan view of the main part of FIG.
  • a pressure communication groove 91 is formed in the vane side wall surface 35B1 located on the vane 33 side of the suction passage 35B.
  • the pressure communication groove 91 is formed by an arc surface centered on a virtual central axis X that is parallel to the central axis of the shaft 40.
  • the pressure communication groove 91 is formed from one end surface of the second cylinder 31B to the other end surface.
  • a curved surface having the same curvature as the arc surface of the pressure communication groove 91 with the virtual central axis X as the center is formed on the anti-vane side wall surface 35B2 facing the vane side wall surface 35B1, thereby eliminating the pressure communication groove 91 at the same time.
  • a volume adjusting space 92 can be formed.
  • the pressure communication groove 91 is formed by an arc surface centered on the virtual central axis X parallel to the central axis of the shaft 40, thereby suppressing the surface pressure of the vane 33 and the vane groove.
  • the pressure communication groove 91 can be formed.
  • the pressure communication groove 91 can be easily formed by cutting by forming the pressure communication groove 91 from one end surface to the other end surface of the second cylinder 31B.
  • the ratio of the excluded volume of the high-stage compression exclusion volume of the second compression mechanism section 30B to the low-stage compression exclusion volume of the first compression mechanism section 30A is 50% to 110%. The effect of reducing the amount of oil discharged from the container 10 can be expected.
  • the internal medium pressure type two-stage compression compressor of the present embodiment can use carbon dioxide as a refrigerant. According to the present embodiment, even when carbon dioxide having a high refrigerant pressure and a large pressure difference between suction and discharge is used as the refrigerant, since the internal pressure of the sealed container 10 is set to an intermediate pressure, the sealed container 10 can be thinned. Since the size and weight can be reduced and the differential pressure per stage is reduced, volume efficiency is improved.
  • the present invention has been described as an internal medium pressure type two-stage compression compressor, it can also be applied to a compression compressor having three or more stages.

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

Abstract

L'invention concerne un compresseur à compression à deux étages et à pression interne moyenne, le compresseur comprenant, en tant que partie mécanisme de compression (30), une première partie mécanisme de compression (30A) destinée à effectuer une compression d'étage inférieur en tant que premier étage, et une seconde partie mécanisme de compression (30B) destinée a effectuer une compression d'étage supérieur en tant que second étage. Un passage d'alimentation en huile (36) est formé dans un passage d'aspiration (35B) de la seconde partie mécanisme de compression (30B). Le gaz réfrigérant comprimé par la première partie mécanisme de compression (30A) est évacué vers un récipient fermé hermétiquement (10). Le gaz réfrigérant est comprimé par la seconde partie mécanisme de compression (30B) et évacué vers l'extérieur du récipient fermé hermétiquement (10). L'alimentation en huile, du passage d'alimentation en huile (36) vers une seconde chambre de compression (34B) de la seconde partie mécanisme de compression (30B), est effectuée au moyen d'une différence de pression entre une pression interne d'enveloppe à l'intérieur du récipient fermé hermétiquement (10) et la pression d'aspiration à l'intérieur du passage d'aspiration (35B) de la seconde partie mécanisme de compression (30B). Lors du pivotement d'un piston (32B) du point mort haut à la position du passage d'aspiration (35B), un espace renfermé (106) n'est pas formé entre une aube (33), un cylindre (31B) et un piston (32B), permettant en conséquence d'empêcher l'écoulement d'une quantité d'huile lubrifiante, égale ou supérieure à une quantité définie, dans la chambre de compression côté étage supérieur (seconde chambre de compression (34B)).
PCT/JP2018/016541 2017-04-28 2018-04-24 Compresseur à compression à deux étages, à pression interne moyenne WO2018199061A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP18790603.7A EP3617514B1 (fr) 2017-04-28 2018-04-24 Compresseur à compression à deux étages, du type à pression moyenne interne
CN201880027972.6A CN110573741A (zh) 2017-04-28 2018-04-24 内部中压型二级压缩压缩机

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017-089843 2017-04-28
JP2017089843A JP2018188986A (ja) 2017-04-28 2017-04-28 内部中圧型２段圧縮コンプレッサ

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WO2018199061A1 true WO2018199061A1 (fr) 2018-11-01

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JP (1) JP2018188986A (fr)
CN (1) CN110573741A (fr)
WO (1) WO2018199061A1 (fr)

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CN118775268A (zh) * 2024-09-06 2024-10-15 珠海凌达压缩机有限公司 一种泵体组件、压缩机及空调器

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JP7378044B2 (ja) * 2019-11-27 2023-11-13 パナソニックＩｐマネジメント株式会社 内部中圧型多段圧縮コンプレッサ
CN112983820A (zh) * 2021-05-19 2021-06-18 广东美芝制冷设备有限公司 压缩机、制冷系统和制冷设备
JP2023005307A (ja) * 2021-06-28 2023-01-18 パナソニックＩｐマネジメント株式会社 圧縮機

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EP3617514B1 (fr) 2023-02-22
EP3617514A1 (fr) 2020-03-04
CN110573741A (zh) 2019-12-13
JP2018188986A (ja) 2018-11-29
EP3617514A4 (fr) 2020-03-04

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