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WO2013057946A1 - Compresseur rotatif présentant deux cylindres - Google Patents

Compresseur rotatif présentant deux cylindres Download PDF

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Publication number
WO2013057946A1
WO2013057946A1 PCT/JP2012/006665 JP2012006665W WO2013057946A1 WO 2013057946 A1 WO2013057946 A1 WO 2013057946A1 JP 2012006665 W JP2012006665 W JP 2012006665W WO 2013057946 A1 WO2013057946 A1 WO 2013057946A1
Authority
WO
WIPO (PCT)
Prior art keywords
crankshaft
compression
cylinders
hole
partition plate
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.)
Ceased
Application number
PCT/JP2012/006665
Other languages
English (en)
Japanese (ja)
Inventor
啓晶 中井
健 苅野
裕文 吉田
晃 鶸田
信吾 大八木
大輔 船越
竜一 大野
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.)
Panasonic Corp
Original Assignee
Panasonic Corp
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 Panasonic Corp filed Critical Panasonic Corp
Priority to JP2013539536A priority Critical patent/JP6156697B2/ja
Priority to EP12841299.6A priority patent/EP2770212B1/fr
Priority to CN201280043095.4A priority patent/CN103782036B/zh
Publication of WO2013057946A1 publication Critical patent/WO2013057946A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • 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
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • 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
    • F04C2240/20—Rotors
    • 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
    • F04C2240/50—Bearings
    • F04C2240/56—Bearing bushings or details thereof
    • 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
    • F04C2240/60—Shafts
    • F04C2240/605—Shaft sleeves or details thereof
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/02—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for several pumps connected in series or in parallel

Definitions

  • the present invention relates to a rotary compressor having two cylinders used for an air conditioner, a refrigerator, a blower, a water heater, and the like.
  • a compressor that sucks gas refrigerant evaporated by an evaporator, compresses it to a pressure necessary for condensation, and sends high-temperature and high-pressure gas refrigerant into a refrigerant circuit is used.
  • a rotary compressor is known as one of such compressors. Among them, the rotary compressor with two cylinders that constitute two compression chambers inside the compressor is being developed as a high-performance compressor because of its features such as low vibration, low noise and high speed operation. There is a need for a compact and higher volume compressor.
  • a method of increasing the volume by increasing the height of the cylinder, or a method of increasing the eccentric amount of the crankshaft and designing a larger confining volume of the compression chamber is adopted.
  • the cylinder height is increased to increase the volume, it is necessary to increase the diameter of the crankshaft in order to cope with an increase in bearing load, leading to a reduction in compressor efficiency.
  • the rotary compressor having two cylinders separates the two compression chambers by a partition plate, and the partition plate requires a through hole for passing the crankshaft.
  • the size of the through hole is limited to a diameter into which the crankshaft can be inserted at the time of assembly, and generally has a diameter slightly larger than the diameter of the crankshaft eccentric portion.
  • FIG. 5A is an assembly diagram of the crankshaft, the rolling piston, and the partition plate when the amount of eccentricity is small.
  • FIG. 5B is an assembly diagram when the eccentric amount is set large with the through holes of the partition plate kept the same.
  • the seal portion 140 In order to suppress leakage from the gap, it is desirable to make the length of the seal portion 140 as long as possible.
  • the seal portion 140 is increased by increasing the amount of eccentricity of the crankshaft eccentric portions 107a and 107b. This causes a problem that the length of the refrigerant decreases, and leakage of the refrigerant through the seal portion 140 increases.
  • FIGS. 6 is a side sectional view of the rotary compressor
  • FIG. 7 is an enlarged view of the main part.
  • the crankshaft 107 is divided into crankshaft eccentric parts 107a and 107b, and each unit is connected to a connecting part 141.
  • the through hole 105a of the partition plate 105 has a smaller diameter than the crankshaft eccentric portion 107b.
  • crankshaft 107 since the crankshaft 107 is divided into units, it is difficult to ensure the coaxiality after assembly.
  • an intermediate bearing is newly provided in the through hole 105a of the partition plate 105, problems such as an increase in bearing loss have occurred.
  • the present invention solves the conventional problems and improves the airtightness of the compression chamber by reducing the diameter of the through hole of the partition plate and ensuring the length of the seal part without increasing the number of parts.
  • the purpose is to provide a highly efficient compressor.
  • the rotary compressor having two cylinders of the present invention two compression elements having a rolling piston are arranged adjacent to each other with a partition plate in the cylinder, and are rotated by an electric element.
  • the crankshaft is inserted into the through hole of the partition plate, and the crankshaft rotates to cause the rolling piston inserted into the eccentric portion of the crankshaft to rotate eccentrically, and the working fluid in the cylinder is rotated to eccentrically rotate the rolling piston.
  • the inner diameter ⁇ Dc of the through hole is larger than the outer diameter ⁇ Db of one of the crankshaft eccentric portions, and is larger than the outer diameter ⁇ Da of the other crankshaft eccentric portion.
  • the outer diameter of the crankshaft eccentric portion needs to have a sufficient bearing resistance against the load received from the working fluid compressed by the rolling piston by the compression element. Therefore, in order to achieve a higher volume, it is necessary to increase the diameter of the crankshaft eccentric part.
  • the partition plate is The inner diameter of the through hole increases as the diameter of the crankshaft eccentric portion increases, and the length of the seal portion formed by the rolling piston end face and the partition plate inevitably decreases.
  • the outer diameter ⁇ Da of the other crankshaft eccentric portion is configured to be larger than the inner diameter of the through hole of the partition plate. It is possible to ensure the length of the seal portion as much as possible without increasing the inner diameter of the through hole of the partition plate.
  • the seal portion between the partition plate and the rolling piston end face can be lengthened, thereby improving the hermeticity of the compression chamber and providing a highly efficient rotary cylinder having two cylinders.
  • a compressor can be realized.
  • ⁇ Dc is larger than the outer diameter ⁇ Db of one crankshaft eccentric portion and smaller than the outer diameter ⁇ Da of the other crankshaft eccentric portion.
  • the outer diameter ⁇ Da of the other crankshaft eccentric portion is larger than the inner diameter of the through hole of the partition plate, it is possible to ensure a sufficient shaft diameter for the load received from the working fluid to be compressed in the compression element. it can.
  • the inner diameter of the through hole of the partition plate is not enlarged even when the amount of eccentricity is increased, the length of the seal portion can be ensured as much as possible.
  • the axial height Hb of one crankshaft eccentric part is the axial height Ha of the other crankshaft eccentric part. Higher than that. Even when the required bearing strength cannot be ensured only by the shaft diameter of the eccentric portion, the bearing strength can improve the bearing strength, and the expansion of the inner diameter of the through hole of the partition plate can be minimized.
  • the compression chamber volume of the compression element compressed at one crankshaft eccentric portion is the compression chamber of the other compression element. It is set smaller than the volume.
  • the compression element where the expansion of the shaft diameter of the eccentric part leads to the expansion of the inner diameter of the through hole of the partition plate reliability is ensured by making the compression chamber volume smaller than the other compression element and reducing the bearing load itself of the eccentric part. It becomes possible to do.
  • the compression element that compresses at the eccentric part of the other crankshaft is used as the main bearing that mainly supports the crankshaft. It is arranged closer. Therefore, since the compression element having a larger load can be pivotally supported near the bearing, the moment applied to the bearing is reduced, and high reliability can be ensured in realizing the present invention.
  • the main bearing that is mainly supported here means a bearing having the largest product of the square of the bearing diameter and the bearing length when the crankshaft itself is supported by a plurality of bearings, and has two cylinders.
  • the rotary compressor is provided on the electric element side.
  • the through hole is filled with lubricating oil or working fluid to which the discharge pressure of the working fluid compressed by the compression element is applied. It is what has been.
  • the inside of the compression chamber By configuring the inside of the compression chamber to be substantially the same pressure as the discharge pressure, it becomes easy to supply the lubricating oil to the sliding portion, so that the reliability of the compressor is excellent.
  • a rotary compressor having two cylinders is filled with high-pressure lubricating oil or working fluid inside the through-hole, there is a concern that it may leak into the compression chamber due to a pressure difference.
  • the compressed working fluid may leak from the compression chamber during compression and discharge through the seal portion.
  • FIG. 1 is a longitudinal sectional view of a rotary compressor having two cylinders according to an embodiment of the present invention
  • FIG. 2 is a plan view of a compression element.
  • the electric element 2 and the compression element 4 are accommodated in the sealed container 1.
  • the electric element 2 rotates the crankshaft 7, and the compression element 4 is driven by the crankshaft 7.
  • the compression element 4 is composed of compression elements 4a and 4b, each performing a compression operation independently.
  • the compression element 4a includes a cylinder 6a that forms a cylindrical space, and a rolling piston 8a that is disposed in the cylinder 6a.
  • the compression element 4b has a cylinder 6b that forms a cylindrical space, and a rolling piston 8b that is disposed in the cylinder 6b.
  • the crankshaft 7 is provided with crankshaft eccentric portions 7a and 7b.
  • the partition plate 5 is disposed between the two compression elements 4a and 4b.
  • a main bearing 31 is disposed on the electric element 2 side of the compression element 4a.
  • the main bearing 31 forms an upper end plate together with a bearing portion that supports the crankshaft main shaft portion 7c.
  • the upper end plate closes the electric element 2 side of the compression element 4a.
  • a sub bearing 32 is disposed on the oil storage section 20 side of the compression element 4b.
  • the auxiliary bearing 32 forms a lower end plate together with a bearing portion that supports the crankshaft auxiliary shaft portion 7d.
  • the lower end plate closes the oil storage section 20 side of the compression element 4b.
  • a cylinder 6 a is disposed on the upper surface of the partition plate 5, and a cylinder 6 b is disposed on the lower surface of the partition plate 5.
  • the other crankshaft eccentric portion 7a is accommodated in the cylinder 6a, and the other crankshaft eccentric portion 7b is accommodated in the cylinder 6b.
  • the crankshaft eccentric portions 7 a and 7 b are configured integrally with the crankshaft 7.
  • a rolling piston 8a is rotatably mounted on the other crankshaft eccentric portion 7a, and a rolling piston 8b is rotatably mounted on one crankshaft eccentric portion 7b.
  • a vane groove 21a is formed in the cylinder 6a, and a vane groove 21b is formed in the cylinder 6b.
  • a vane 22a is slidably disposed in the vane groove 21a, and a vane 22b is slidably disposed in the vane groove 21b.
  • a back pressure is applied to the vane 22a, and the vane 22a always abuts against the rolling piston 8a.
  • a back pressure is applied to the vane 22b, and the vane 22b always abuts against the rolling piston 8b.
  • the cylinder 6a is provided with a suction passage 9a
  • the cylinder 6b is provided with a suction passage 9b.
  • a suction pipe 10a is connected to the suction passage 9a, and a suction pipe 10b is connected to the suction passage 9b.
  • the suction passage 9a and the suction passage 9a are independent from each other, and the suction pipe 10a and the suction pipe 10b are independent from each other.
  • the suction pipe 10a communicates with the compression chamber 11a through the suction passage 9a, and the suction pipe 10b communicates with the compression chamber 11b through the suction passage 9b.
  • an accumulator 12 is provided in the suction pipes 10a and 10b.
  • the accumulator 12 gas-liquid separates the refrigerant and guides only the refrigerant gas to the suction pipes 10a and 10b.
  • a refrigerant gas introduction pipe 14 is connected to the upper part of a cylindrical case 13, and two refrigerant gas outlet pipes 15a and 15b are connected to the lower part.
  • One ends of the refrigerant gas outlet pipes 15 a and 15 b are connected to the suction pipes 10 a and 10 b, and the other ends of the refrigerant gas outlet pipes 15 a and 15 b extend to the upper part of the internal space of the case 13.
  • crankshaft 7 When the crankshaft 7 is rotated by the electric element 2, the crankshaft eccentric portions 7a and 7b are eccentrically rotated in the cylinders 6a and 6b, and the rolling pistons 8a and 8b are rotated while being in contact with the vanes 22a and 22b.
  • the suction and compression of the refrigerant gas are repeated in both cylinders 6a and 6b at a period in which the rolling piston 8a and the rolling piston 8b are shifted by a half rotation.
  • the low-pressure refrigerant sucked from the refrigerant gas introduction pipe 14 is gas-liquid separated in the case 13, and the refrigerant gas separated from the liquid refrigerant is refrigerant gas outlet pipes 15a and 15b, suction pipes 10a and 10b, and a suction passage 9a. 9b and is sucked into the compression chambers 11a and 11b.
  • the lubricating oil in the oil storage section 20 at the bottom of the closed container 1 is supplied from the lower end of the crankshaft countershaft section 7d to the through hole 5a via the inside of the crankshaft 7, and the partition plate 5 and the rolling piston 8a, The region surrounded by 8b and the crankshaft 7 is filled.
  • FIG. 3 is a side view of the main part showing the positional relationship during assembly of the crankshaft, partition plate, and rolling piston of the rotary compressor in the embodiment of the present invention.
  • the partition plate 5 is inserted from the crankshaft countershaft portion 7d side, and is disposed between one crankshaft eccentric portion 7a and the other crankshaft eccentric portion 7b through one crankshaft eccentric portion 7b. . Therefore, it is necessary to set the inner diameter ⁇ Dc of the through hole 5a of the partition plate 5 to be larger than the outer diameter ⁇ Db of the one crankshaft eccentric portion 7b.
  • the outer diameter ⁇ Da of the other crankshaft eccentric portion 7a is set larger than the inner diameter ⁇ Dc of the through hole 5a, and the partition plate 5 is inserted from the crankshaft main shaft portion 7c side. It is not possible.
  • the outer diameter ⁇ Da of the crankshaft main shaft portion 7a is set to be large, it is possible to improve the proof strength against the load received from the rolling piston 8a during compression, and it is high even if the volume of the compression element 4a is large. Reliability can be realized.
  • the through hole 5a is filled with lubricating oil.
  • a discharge pressure is applied to the lubricating oil in the through hole 5a.
  • the through hole 5a may be filled with the working fluid. Also in this case, a discharge pressure is applied to the working fluid in the through hole 5a.
  • a pressure difference between the compression chamber 11a and the compression chamber 11b is secured by the seal portion 40 formed by the end surface of the partition plate 5 and the end surfaces of the rolling pistons 8a and 8b.
  • the seal portion 40 is provided with a minute gap in the height direction so that the rolling piston 8 can rotate eccentrically, and the length of the seal portion 40 is required to suppress leakage from the gap. It is desirable to make (the length in the radial direction) as long as possible.
  • the inner diameter ⁇ Dc of the through hole 5a can be reduced by setting the outer diameter ⁇ Db of one crankshaft eccentric portion 7b to be small.
  • the seal portion 40 can be lengthened in the radial direction, and the compression chamber can be extended from the through hole 5a. It is possible to prevent the lubricating oil from leaking into 11a and 11b.
  • FIG. 4 shows an assembly diagram when the outer diameter ⁇ Db of one crankshaft eccentric portion 7b is set to be the same as the outer diameter ⁇ Da of the other crankshaft eccentric portion 7a.
  • the outer diameter ⁇ Db of one crankshaft eccentric portion 7b that passes through the through hole 5a increases, so the inner diameter ⁇ Dc of the through hole 5a increases, so the outer diameter of the rolling piston 8b and the eccentric amount of the one crankshaft eccentric portion 7b are as follows.
  • sticker part 40 becomes short and the leak from the through-hole 5a to the compression chambers 11a and 11b will increase.
  • the outer diameter ⁇ Db of one crankshaft eccentric portion 7b inserted into the through hole 5a of the partition plate 5 during assembly is set smaller than the outer diameter ⁇ Da of the other crankshaft eccentric portion 7a, and the inner diameter of the through hole 5a is set.
  • the length of the seal portion 40 can be increased by keeping ⁇ Dc large enough to allow the one of the crankshaft eccentric portions 7b having the smaller outer diameter to pass, and the high pressure lubricating oil can be prevented from entering the compression chamber 11. ing.
  • the shaft height Hb of the eccentric portion 7b may be set higher than the shaft height Ha of the other crankshaft eccentric portion 7a.
  • the compression chamber volume of the compression element 4b is the volume of the compression chamber 11a formed by the cylinder 6a, the rolling piston 8a, the upper end plate of the main bearing 31, and the partition plate 5, and the compression chamber volume of the compression element 4a is the cylinder 6b.
  • the compression element 4a to be compressed by the other crankshaft eccentric portion 7a may be disposed near the main bearing 31 that mainly supports the crankshaft 7. Since the compression element 4a having a larger load can be pivotally supported near the main bearing 31, the moment applied to the main bearing 31 is reduced, and high reliability can be ensured in realizing the present invention.
  • a rotary compressor having two cylinders is described.
  • a rotary compressor having two or more cylinders can achieve the effect by performing the same configuration. It is.
  • the rotary compressor having two cylinders according to the present invention improves the airtightness of the compression chamber by suppressing leakage through the partition plate and the seal portion between the end faces of the rolling piston. High efficiency can be achieved.
  • the air-conditioning compressor using HFC refrigerant such, they can be applied to applications such as air conditioning and heat pump water heater using CO 2 as a natural refrigerant.

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

Abstract

La présente invention concerne un compresseur rotatif présentant deux cylindres (6a, 6b), et deux éléments de compression (4a, 4b) disposés de chaque côté d'une cloison de séparation (5), lesdits éléments de compression présentant des pistons rotatifs (8) à l'intérieur de cylindres (6), et un vilebrequin (7) qui est mis en rotation par un élément électrique (2) inséré dans un trou traversant (5a) dans la cloison de séparation (5), les pistons rotatifs (8) qui sont insérés dans les pièces excentriques de vilebrequin (7a, 7b) se mettant en rotation de manière excentrique lorsque le vilebrequin (7) se met en rotation, comprimant ainsi un fluide de fonctionnement à l'intérieur des cylindres (6) au moyen de la rotation excentrique des pistons rotatifs (8). Avec ce compresseur rotatif, le diamètre interne φDc du trou traversant (5a) de la cloison de séparation (5) est défini de façon à être supérieur au diamètre externe φDb d'une partie excentrique de vilebrequin (7b) et inférieur au diamètre externe φDa de la partie excentrique de vilebrequin (7a), réduisant ainsi l'augmentation du diamètre interne φDc du trou traversant (5a) et proposant un compresseur à haut rendement (11a, 11b) pour lequel il est possible de supprimer les fuites entre l'intérieur du trou traversant (5a) et les chambres de compression (11a, 11b), améliorant ainsi l'étanchéité à l'air des chambres de compression (11a, 11b).
PCT/JP2012/006665 2011-10-18 2012-10-18 Compresseur rotatif présentant deux cylindres Ceased WO2013057946A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2013539536A JP6156697B2 (ja) 2011-10-18 2012-10-18 ２つのシリンダを持ったロータリ圧縮機
EP12841299.6A EP2770212B1 (fr) 2011-10-18 2012-10-18 Compresseur rotatif présentant deux cylindres
CN201280043095.4A CN103782036B (zh) 2011-10-18 2012-10-18 具有两个气缸的旋转式压缩机

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011228585 2011-10-18
JP2011-228585 2011-10-18

Publications (1)

Publication Number Publication Date
WO2013057946A1 true WO2013057946A1 (fr) 2013-04-25

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2012/006665 Ceased WO2013057946A1 (fr) 2011-10-18 2012-10-18 Compresseur rotatif présentant deux cylindres

Country Status (4)

Country Link
EP (1) EP2770212B1 (fr)
JP (1) JP6156697B2 (fr)
CN (1) CN103782036B (fr)
WO (1) WO2013057946A1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016031129A1 (fr) * 2014-08-27 2016-03-03 東芝キヤリア株式会社 Compresseur rotatif et dispositif à cycle de réfrigération
EP3141755A1 (fr) 2015-09-09 2017-03-15 Mitsubishi Heavy Industries, Ltd. Compresseur rotatif
EP3141754A1 (fr) 2015-09-09 2017-03-15 Mitsubishi Heavy Industries, Ltd. Compresseur rotatif et son procédé de fabrication
CN107327402A (zh) * 2017-08-21 2017-11-07 西安庆安制冷设备股份有限公司 一种滚动活塞压缩机及其压缩结构
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WO2019031411A1 (fr) * 2017-08-09 2019-02-14 ダイキン工業株式会社 Compresseur rotatif
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CN114109821A (zh) * 2021-11-09 2022-03-01 广东美芝精密制造有限公司 压缩机构、压缩机和制冷设备
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CN107476979A (zh) * 2017-08-10 2017-12-15 珠海格力节能环保制冷技术研究中心有限公司 压缩机、空调器及压缩机的装配方法
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WO2016031129A1 (fr) * 2014-08-27 2016-03-03 東芝キヤリア株式会社 Compresseur rotatif et dispositif à cycle de réfrigération
JP2016048032A (ja) * 2014-08-27 2016-04-07 東芝キヤリア株式会社 回転式圧縮機及び冷凍サイクル装置
EP3141755A1 (fr) 2015-09-09 2017-03-15 Mitsubishi Heavy Industries, Ltd. Compresseur rotatif
EP3141754A1 (fr) 2015-09-09 2017-03-15 Mitsubishi Heavy Industries, Ltd. Compresseur rotatif et son procédé de fabrication
US11473581B2 (en) 2017-08-09 2022-10-18 Daikin Industries, Ltd. Rotary compressor
WO2019031412A1 (fr) * 2017-08-09 2019-02-14 ダイキン工業株式会社 Compresseur rotatif
WO2019031411A1 (fr) * 2017-08-09 2019-02-14 ダイキン工業株式会社 Compresseur rotatif
JP2019031951A (ja) * 2017-08-09 2019-02-28 ダイキン工業株式会社 ロータリ圧縮機
JP2019031952A (ja) * 2017-08-09 2019-02-28 ダイキン工業株式会社 ロータリ圧縮機
CN110998095A (zh) * 2017-08-09 2020-04-10 大金工业株式会社 旋转式压缩机
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CN113738645A (zh) * 2020-05-29 2021-12-03 广东美芝精密制造有限公司 压缩机及空调系统
CN114109821A (zh) * 2021-11-09 2022-03-01 广东美芝精密制造有限公司 压缩机构、压缩机和制冷设备
CN114109821B (zh) * 2021-11-09 2023-10-24 广东美芝精密制造有限公司 压缩机构、压缩机和制冷设备
CN118622700A (zh) * 2024-06-25 2024-09-10 珠海格力电器股份有限公司 一种双转子泵体组件及双转子压缩机

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CN103782036A (zh) 2014-05-07
JP6156697B2 (ja) 2017-07-05
JPWO2013057946A1 (ja) 2015-04-02
EP2770212A4 (fr) 2015-03-04

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