WO2013179677A1 - Compresseur rotatif - Google Patents

Compresseur rotatif Download PDF

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Publication number
WO2013179677A1
WO2013179677A1 PCT/JP2013/003446 JP2013003446W WO2013179677A1 WO 2013179677 A1 WO2013179677 A1 WO 2013179677A1 JP 2013003446 W JP2013003446 W JP 2013003446W WO 2013179677 A1 WO2013179677 A1 WO 2013179677A1
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WO
WIPO (PCT)
Prior art keywords
piston
rotary compressor
peripheral surface
gap
crankshaft
Prior art date
Application number
PCT/JP2013/003446
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English (en)
Japanese (ja)
Inventor
大輔 船越
裕文 吉田
雄司 尾形
優 塩谷
啓晶 中井
健 苅野
Original Assignee
パナソニック株式会社
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 パナソニック株式会社 filed Critical パナソニック株式会社
Priority to JP2014518295A priority Critical patent/JP6350916B2/ja
Priority to CN201380002908.XA priority patent/CN103782037B/zh
Priority to EP13797726.0A priority patent/EP2857688B1/fr
Publication of WO2013179677A1 publication Critical patent/WO2013179677A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F04C2230/602—Gap; Clearance
    • 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

Definitions

  • the present invention relates to a rotary compressor used for an air conditioner, a refrigerator, a blower, a water heater, and the like.
  • a compressor that sucks gas refrigerant evaporated in an evaporator, compresses it to the pressure necessary for condensation, and discharges high-temperature and high-pressure refrigerant into the refrigerant circuit has been used.
  • a rotary compressor is known as one of such compressors.
  • FIG. 18 is a cross-sectional view of a main part of a conventional rotary compressor.
  • the rotary compressor has an electric motor (not shown) and a compression mechanism unit 3 connected by a crankshaft 31 and accommodated in the sealed container 1.
  • the compression mechanism unit 3 includes a compression chamber 39, a piston 32, and a vane (not shown).
  • the compression chamber 39 is formed by a cylinder 30 and an upper bearing 34 and a lower bearing 35 that close both end surfaces of the cylinder 30.
  • the piston 32 is in the compression chamber 39 and is fitted to the eccentric portion 31 a of the crankshaft 31 supported by the upper bearing 34 and the lower bearing 35.
  • the vane contacts the piston outer peripheral surface 32a of the piston 32, reciprocates following the eccentric rotation of the piston 32, and partitions the inside of the compression chamber 39 into a low pressure portion and a high pressure portion.
  • the cylinder 30 is opened with a suction port 40 for sucking gas toward the low pressure portion in the compression chamber 39.
  • the upper bearing 34 is opened with a discharge port 38 that discharges gas from a high-pressure portion formed by turning from a low-pressure portion in the compression chamber 39.
  • the piston 32 is accommodated in a compression chamber 39 formed by an upper bearing 34 and a lower bearing 35 and a cylinder 30 that is closed by these.
  • the discharge port 38 is formed as a circular hole passing through the upper bearing 34 in plan view.
  • a discharge valve 36 is provided on the upper surface of the discharge port 38 that is released when a pressure of a predetermined magnitude or more is applied.
  • a cup muffler 37 is provided above the upper bearing 34 to mute the discharged gas.
  • the piston outer peripheral surface 32a and the cylinder inner peripheral surface 30a are in strong contact with each other, causing problems such as seizure and wear, and increasing the input to lower the efficiency of the compressor. There is concern to do. For this reason, as shown in FIG. 16, a minimum gap W during operation is provided between the piston outer peripheral surface 32a and the cylinder inner peripheral surface 30a.
  • the size of the leakage area S determined by the minimum gap W during operation and the height H of the compression chamber 39 affects the efficiency of the compressor.
  • the minimum gap W during operation is set large, the amount of the compressed fluid flowing out from the high pressure portion to the low pressure portion through the minimum gap W during operation increases. For this reason, the compressed refrigerant gas leaks from the minimum gap W during operation and increases the loss (hereinafter referred to as “leakage loss”), thereby reducing the efficiency of the compressor.
  • the minimum clearance W during operation is set large so that the piston outer peripheral surface and the cylinder inner peripheral surface do not come into strong contact with each other, so that problems of seizure and wear are eliminated and sliding loss is reduced.
  • FIG. 17 is a schematic diagram showing a cylinder shape of a non-circular (composite circle) cross section in a conventional rotary compressor described in Patent Document 1.
  • the compression chamber has a non-circular cross-sectional shape composed of a plurality of curvatures.
  • the present invention has been made in view of the above circumstances, without deteriorating the reliability, thoroughly reducing the leakage loss from the minimum gap W during operation, and without increasing the sliding loss.
  • the purpose is to further increase the efficiency of the compressor.
  • the invention relating to the rotary compressor according to claim 1 comprises an electric motor and a compression mechanism in a sealed container, and the compression mechanism connected to the electric motor by a crankshaft includes a cylinder and both end faces of the cylinder.
  • Upper and lower bearings closed from above and below to form a compression chamber, a piston fitted in an eccentric part of the crankshaft provided in the cylinder, and provided in the cylinder following the eccentric rotation of the piston
  • Rotary compression comprising a vane that reciprocates in the slot to partition the compression chamber into a low pressure part and a high pressure part, a suction port that communicates with the low pressure part, and a discharge port that communicates with the high pressure part
  • the eccentric portion is disposed at a predetermined crank angle position from the vane position, and the piston is at the most eccentric position of the eccentric portion.
  • the minimum value ⁇ min of the gap ⁇ is set at a crank angle substantially opposite to the maximum load direction of the crankshaft during operation of the rotary compressor.
  • a first bearing gap is formed between the piston and the eccentric portion, and the upper bearing and the A second bearing gap is formed between the main shaft portion of the crankshaft, the crankshaft is moved by the first bearing gap in the load direction during operation at each crank angle, and the piston is operated.
  • the minimum clearance formed between the outer periphery of the piston and the imaginary line of the cylinder is ⁇
  • the crank angle is around 45 degrees and around 225 degrees.
  • the direction of the minimum value ⁇ min is set so that the minimum gap ⁇ is substantially equal.
  • the invention according to claim 3 is the rotary compressor according to claim 1 or 2, wherein the rotary compressor has two compression chambers.
  • the ⁇ min is about 5 ⁇ m to 10 ⁇ m.
  • the minimum gap W during operation increases at a crank angle opposite to the maximum load direction.
  • the minimum clearance ⁇ min is set in advance at the crank angle opposite to the maximum load direction, so that leakage can be reduced and high efficiency can be achieved. . Therefore, since the leakage gap can be reduced by reducing the minimum gap W during operation without increasing the sliding loss, the efficiency of the compressor can be further increased.
  • movement of a rotary compressor Cross-sectional view showing each gap during operation of the rotary compressor
  • size and direction of the load of a crankshaft in a 1 piston rotary compressor The figure which showed the locus
  • size and direction of the load of a crankshaft in a 2-piston rotary compressor The figure which showed the locus
  • the eccentric part of the crankshaft is arranged at a position of a predetermined crank angle from the position of the vane, and the piston is arranged at the eccentric part of the crankshaft.
  • the minimum value ⁇ min of the gap ⁇ is set at a crank angle substantially opposite to the maximum load direction of the crankshaft.
  • the crankshaft moves in the maximum load direction, so the minimum gap W during operation increases at a crank angle opposite to the maximum load direction.
  • the minimum clearance ⁇ min is set in advance at the crank angle opposite to the maximum load direction, the operating minimum clearance W is reduced. Therefore, leakage can be reduced and high efficiency can be achieved.
  • a first bearing gap is formed between the piston and the eccentric portion of the crankshaft during assembly, and the upper bearing and the crank
  • a second bearing gap is formed between the main shaft portion of the shaft, and at each crank angle, only the first bearing gap in the load direction during operation of the crankshaft and the second in the load direction during operation of the piston are provided.
  • the minimum gap W during operation near the crank angle of 45 degrees and 225 degrees is substantially equal, and the gap is balanced with the imaginary line in the load direction of the crankshaft being symmetrical. There is no sliding loss. Therefore, leakage from the minimum gap W during operation can be reduced and efficiency can be improved while suppressing a decrease in reliability such as wear and seizure.
  • the third embodiment of the present invention is a two-piston rotary compressor having two compression chambers in the rotary compressor according to the first or second embodiment.
  • the load direction of the two-piston rotary is substantially constant and the load is larger than that of the one-piston rotary. Therefore, leakage from the minimum gap W during operation can be reduced and efficiency can be improved while further suppressing deterioration in reliability such as wear and seizure.
  • ⁇ min is about 5 ⁇ m to 10 ⁇ m.
  • the gap is balanced with the imaginary line in the load direction of the crankshaft being symmetrical. Therefore, even if the minimum gap ⁇ min is excessively reduced, a large sliding loss does not occur at a crank angle of around 45 degrees and around 225 degrees during operation. Therefore, leakage from the minimum gap W during operation can be reduced and efficiency can be improved while suppressing a decrease in reliability such as wear and seizure.
  • FIG. 1 is a longitudinal sectional view of a rotary compressor in one embodiment of the present invention
  • FIG. 6 is a plan view of a main part showing a compression chamber of the rotary compressor during operation.
  • the rotary compressor of the present embodiment houses the electric motor 2 and the compression mechanism 3 in the hermetic container 1.
  • the electric motor 2 and the compression mechanism unit 3 are connected by a crankshaft 31.
  • the electric motor 2 includes a stator 22 and a rotor 24.
  • the compression mechanism unit 3 includes a cylinder 30, a piston 32, a vane 33, an upper bearing 34 and a lower bearing 35.
  • the compression chamber 39 is formed by a cylinder 30 and an upper bearing 34 and a lower bearing 35 that close both end faces of the cylinder 30.
  • the piston 32 is accommodated in the compression chamber 39 and is fitted to an eccentric portion 31 a of the crankshaft 31 supported by the upper bearing 34 and the lower bearing 35.
  • the vane 33 reciprocates in the slot 33a provided in the cylinder 30 and always contacts the piston outer peripheral surface 32a, thereby partitioning the compression chamber 39 into a low pressure portion 39a and a high pressure portion 39b.
  • two spaces are formed by the vane 33 and the minimum gap W during operation.
  • the space connected to the suction port 40 becomes the low pressure part 39a, and the space connected to the discharge port 38 becomes the high pressure part 39b.
  • the minimum gap W during operation is a gap during operation that occurs at a position where the piston 32 is closest to the cylinder 30.
  • the suction port 40 is opened in the cylinder 30, and the suction port 40 sucks (supplies) the refrigerant gas into the low pressure part 39 a in the compression chamber 39.
  • a discharge port 38 is opened in the upper bearing 34, and the discharge port 38 discharges gas from the high-pressure portion 39b.
  • the discharge port 38 is formed as a circular hole that penetrates the upper bearing 34.
  • a discharge valve 36 is provided on the upper surface of the discharge port 38, and the discharge valve 36 is opened when receiving a pressure of a predetermined magnitude or more.
  • the discharge valve 36 is covered with a cup muffler 37.
  • the low-pressure part 39a of the compression mechanism part 3 gradually expands its capacity as the minimum gap W during operation increases from the suction port 40. Then, the refrigerant gas flows from the suction port 40 due to the expansion of the volume.
  • the low pressure part 39a moves while changing the volume due to the eccentric rotation of the piston 32, and becomes a high pressure part 39b when the volume starts to decrease.
  • the high-pressure portion 39b gradually reduces the volume, and the pressure increases due to the volume reduction.
  • the discharge valve 36 is opened, and the high pressure refrigerant gas flows out from the discharge port 38.
  • the refrigerant gas is discharged from the cup muffler 37 into the sealed container 1. Then, it passes through the notch 28 formed by the stator 22 and the inner periphery of the sealed container 1 and the air gap 26 of the electric motor 2 and is sent out into the upper shell 4 at the upper part of the electric motor 2. Then, the refrigerant is discharged from the refrigerant discharge pipe 5 to the outside of the sealed container 1.
  • the arrows in FIG. 1 indicate the flow of the refrigerant.
  • the height of the cylinder 30 must be set slightly larger than the height of the piston 32 so that the piston 32 can slide inside.
  • FIG. 2 is a cross-sectional view of the main part showing the relationship between the piston and the crankshaft gap of the rotary compressor of this embodiment during assembly
  • FIG. 3 is a plan view of the main part showing the compression chamber of the rotary compressor during assembly
  • FIG. 4 is a main part plan view showing the arrangement of the upper bearing in FIG. 3
  • FIG. 5 is a sectional view taken along the line VV in FIG.
  • a gap between the piston inner peripheral surface 32b of the piston 32 and the eccentric portion outer peripheral surface 31b of the eccentric portion 31a of the crankshaft 31 is provided as the first bearing.
  • the clearance is c1.
  • the crankshaft 31 is arranged so that the eccentric portion 31 a is at an angle ⁇ from the vane 33.
  • the angle ⁇ is an angle substantially opposite to the maximum load direction of the crankshaft 31.
  • a minimum gap ⁇ min which will be described later, is disposed so as to be closer to the discharge port 38 than an imaginary line connecting the vane 33 and the center of the crankshaft 31.
  • the piston 32 is brought into contact with the most eccentric position of the eccentric portion 31a in a state where the eccentric portion 31a is arranged at the position of the angle ⁇ .
  • a minimum gap ⁇ min is formed between the piston outer peripheral surface 32a and the cylinder inner peripheral surface 30a at the position of the angle ⁇ .
  • a first bearing gap c1 is formed between the piston inner peripheral surface 32b and the eccentric portion outer peripheral surface 31b.
  • the upper bearing 34 is brought into contact with the main shaft portion 31c of the crankshaft 31 in the direction of the angle ⁇ with the vane 33 (the most eccentric position of the eccentric portion 31a), so that the inner peripheral surface 34a of the upper bearing 34 and the crank A second bearing gap c ⁇ b> 2 is formed between the main shaft portion 31 c of the shaft 31.
  • the minimum gap ⁇ min, the first bearing gap c1, and the second bearing gap c2 are arranged on the phantom line with the vane 33 and the angle ⁇ .
  • FIG. 5 shows an arrangement state of the minimum gap ⁇ min, the first bearing gap c1, and the second bearing gap c2.
  • a minimum gap W during operation is provided between the piston outer peripheral surface 32a and the cylinder inner peripheral surface 30a.
  • the size of the leakage area S determined by the minimum gap W during operation and the height H of the compression chamber 39 affects the efficiency of the compressor.
  • the minimum gap W during operation is set large, the amount of compressed fluid flowing out from the high pressure portion to the low pressure portion through the minimum gap W during operation increases. For this reason, the compressed refrigerant gas leaks from the minimum gap W during operation, and leakage loss increases, thereby reducing the efficiency of the compressor.
  • a minimum gap ⁇ min is formed between the piston outer peripheral surface 32a and the cylinder inner peripheral surface 30a.
  • a differential pressure X is applied to the piston 32 as shown by the arrow in FIG.
  • the differential pressure X acts from the high pressure portion 39b side toward the low pressure portion 39a side because the compression chamber 39 forms a low pressure portion 39a and a high pressure portion 39b.
  • the piston 32 is pressed and displaced to the low-pressure part 39a side. Therefore, during operation, the position of the minimum clearance ⁇ min set at the time of assembly does not become the minimum clearance W during operation, and the position of the angle ( ⁇ + ⁇ ) is during operation where the piston outer peripheral surface 32a and the cylinder inner peripheral surface 30a are closest to each other.
  • the minimum gap W is obtained.
  • the minimum gap W during operation is a gap narrower than the minimum gap ⁇ min ( ⁇ is a minute angle that varies depending on the operating state).
  • the eccentric portion 31a of the crankshaft 31 inside the piston 32 and the crankshaft 31 inside the upper bearing 34 each move to the center due to the oil film pressure. Accordingly, the minimum gap ⁇ min set at the time of assembly is narrowed by 1/2 of the first bearing gap c1 and 1/2 of the second bearing gap c2 during operation. Thereby, the minimum gap W during operation is formed theoretically close to zero, and the operation is actually performed with a gap size corresponding to the oil film.
  • the minimum gap W during operation increases at a crank angle opposite to the maximum load direction.
  • the minimum gap ⁇ min is set in advance at the crank angle opposite to the maximum load direction, the minimum gap W during operation can be kept small at the crank angle opposite to the maximum load direction. And leakage is reduced. Further, at other crank angles, the minimum gap W during operation does not become small, so that there is no increase in input and high efficiency can be achieved.
  • FIG. 8 shows the load during one rotation applied to the crankshaft 31 of the one-piston rotary compressor, and shows the magnitude and direction of the load at each crank angle (the vane direction is the y-axis plus side, and the suction direction is x Axis minus side, y axis plus side). As shown in the figure, the maximum load is obtained near a crank angle of 225 degrees.
  • FIG. 11 shows the load during one rotation applied to the crankshaft 31 of a two-piston rotary compressor (not shown), and shows the magnitude and direction of the load at each crank angle. As shown in the figure, the maximum load is near the crank angle of 225 degrees.
  • FIGS. 12 and 13 assume that there is no cylinder 30 at each crank angle. At each crank angle, the crankshaft 31 is moved in the load direction during operation to move the second bearing gap c2, and the piston 32 is moved. The positional relationship between the locus of the piston outer peripheral surface 32a and the imaginary line of the cylinder inner peripheral surface 30a when the first bearing gap c1 moves in the load direction during operation is shown (only one cylinder 30 is shown).
  • the direction of the minimum gap ⁇ min is set in a general direction.
  • the direction of the minimum clearance ⁇ min is set so that the minimum clearance ⁇ near the crank angle of 45 degrees and 225 degrees are substantially equal. Comparing FIG. 12 and FIG.
  • the minimum gap ⁇ can be made uniform over a wide range of crank angles, leakage loss can be reduced, and high efficiency can be achieved.
  • the bearing load direction is substantially constant, and the minimum gap ⁇ around 45 degrees and 225 degrees in the crank angle can be made uniform with better balance.
  • FIG. 14 is a diagram in which the direction of the minimum gap ⁇ min is set in a general direction, and the minimum gap ⁇ min is minimized to 5 to 10 ⁇ m.
  • FIG. 15 is a diagram showing minimum crank gaps around 45 degrees and 225 degrees.
  • FIG. 6 is a diagram when the direction of the minimum gap ⁇ min is set so that ⁇ is substantially equal, and the minimum gap ⁇ min is minimized to 5 to 10 ⁇ m. Comparing FIG. 14 and FIG. 15, in FIG. 14, the length of the sliding portion is greatly increased, whereas in FIG. 15, the minimum gap ⁇ is made uniform over the entire circumference. Further, in FIG. 14, the minimum gap ⁇ is not reduced while the minimum gap ⁇ min is reduced. Therefore, the volume efficiency is not improved, and only the input increases.
  • the input does not increase so much, and the volumetric efficiency is greatly improved.
  • reducing the minimum gap ⁇ min is considered to improve volumetric efficiency, but the limit value is about 10 ⁇ m. If the minimum clearance ⁇ min is set in a direction substantially opposite to the maximum load direction of the crankshaft 31 as in the present embodiment, further efficiency improvement can be achieved even if the minimum clearance ⁇ min is 10 ⁇ m or less (FIGS. 13 and 15). And compare).
  • the rotary compressor according to the present invention can suppress deterioration of reliability such as wear and seizure, and simultaneously reduce leakage loss and sliding loss, thereby improving the efficiency of the compressor. It becomes. Thereby, it can apply also to uses, such as a compressor for air conditioners using HFC system refrigerant and HCFC system refrigerant, an air conditioner using carbon dioxide which is a natural refrigerant, and a heat pump type hot water heater.

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

Abstract

Lorsqu'un compresseur rotatif est assemblé, une section excentrique est disposée dans une position selon un angle prédéterminé du vilebrequin à partir de la position d'une ailette, un piston est mis en contact avec la position la plus excentrique de la section excentrique, et la surface périphérique intérieure d'un palier supérieur est mise en contact avec la surface périphérique extérieure d'une section de l'arbre principal de l'arbre du vilebrequin. Dans cet état, la valeur minimale δmin de l'intervalle δ est réglée à l'angle du vilebrequin sur le côté pratiquement opposé de la direction de charge maximale de l'angle du vilebrequin pendant que le compresseur rotatif est en fonctionnement, δ représentant l'intervalle formé entre une surface périphérique extérieure du piston et une surface périphérique intérieure du cylindre.
PCT/JP2013/003446 2012-06-01 2013-05-31 Compresseur rotatif WO2013179677A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2014518295A JP6350916B2 (ja) 2012-06-01 2013-05-31 ロータリ圧縮機
CN201380002908.XA CN103782037B (zh) 2012-06-01 2013-05-31 旋转压缩机
EP13797726.0A EP2857688B1 (fr) 2012-06-01 2013-05-31 Compresseur rotatif

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012-125719 2012-06-01
JP2012125719 2012-06-01

Publications (1)

Publication Number Publication Date
WO2013179677A1 true WO2013179677A1 (fr) 2013-12-05

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PCT/JP2013/003446 WO2013179677A1 (fr) 2012-06-01 2013-05-31 Compresseur rotatif

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EP (1) EP2857688B1 (fr)
JP (1) JP6350916B2 (fr)
CN (1) CN103782037B (fr)
WO (1) WO2013179677A1 (fr)

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CN107061273B (zh) * 2016-12-01 2019-09-06 广东美芝制冷设备有限公司 旋转式压缩机

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JPS5514278B2 (fr) * 1972-07-26 1980-04-15
JPS61142389A (ja) * 1984-12-14 1986-06-30 Daikin Ind Ltd ロ−タリ−圧縮機におけるクランク軸の芯出し方法
JP2002098075A (ja) * 2000-09-22 2002-04-05 Matsushita Electric Ind Co Ltd 密閉型圧縮機
JP2003214369A (ja) 2002-01-23 2003-07-30 Mitsubishi Heavy Ind Ltd ロータリ圧縮機
JP2005240564A (ja) * 2004-02-24 2005-09-08 Mitsubishi Electric Corp ロータリ圧縮機
JP2006152950A (ja) * 2004-11-30 2006-06-15 Sanyo Electric Co Ltd 多段圧縮式ロータリコンプレッサ

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Publication number Priority date Publication date Assignee Title
JPH0751951B2 (ja) * 1987-11-24 1995-06-05 ダイキン工業株式会社 回転式圧縮機
JP3490950B2 (ja) * 2000-03-15 2004-01-26 三洋電機株式会社 ２シリンダ型２段圧縮式ロータリーコンプレッサ
JP5363486B2 (ja) * 2008-07-28 2013-12-11 パナソニック株式会社 ロータリ圧縮機
JP2010116782A (ja) * 2008-11-11 2010-05-27 Daikin Ind Ltd 流体機械

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5514278B2 (fr) * 1972-07-26 1980-04-15
JPS61142389A (ja) * 1984-12-14 1986-06-30 Daikin Ind Ltd ロ−タリ−圧縮機におけるクランク軸の芯出し方法
JP2002098075A (ja) * 2000-09-22 2002-04-05 Matsushita Electric Ind Co Ltd 密閉型圧縮機
JP2003214369A (ja) 2002-01-23 2003-07-30 Mitsubishi Heavy Ind Ltd ロータリ圧縮機
JP2005240564A (ja) * 2004-02-24 2005-09-08 Mitsubishi Electric Corp ロータリ圧縮機
JP2006152950A (ja) * 2004-11-30 2006-06-15 Sanyo Electric Co Ltd 多段圧縮式ロータリコンプレッサ

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Title
See also references of EP2857688A4 *

Also Published As

Publication number Publication date
CN103782037B (zh) 2016-01-20
JP6350916B2 (ja) 2018-07-04
CN103782037A (zh) 2014-05-07
EP2857688A1 (fr) 2015-04-08
EP2857688B1 (fr) 2020-04-29
JPWO2013179677A1 (ja) 2016-01-18
EP2857688A4 (fr) 2015-05-27

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