WO2011102413A1 - ロータリ圧縮機及び冷凍サイクル装置 - Google Patents

ロータリ圧縮機及び冷凍サイクル装置 Download PDF

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Publication number
WO2011102413A1
WO2011102413A1 PCT/JP2011/053372 JP2011053372W WO2011102413A1 WO 2011102413 A1 WO2011102413 A1 WO 2011102413A1 JP 2011053372 W JP2011053372 W JP 2011053372W WO 2011102413 A1 WO2011102413 A1 WO 2011102413A1
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WO
WIPO (PCT)
Prior art keywords
bearing
shaft
sub
main
rotary compressor
Prior art date
Application number
PCT/JP2011/053372
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English (en)
French (fr)
Japanese (ja)
Inventor
康治 里舘
俊公 青木
和 高島
Original Assignee
東芝キヤリア株式会社
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 東芝キヤリア株式会社 filed Critical 東芝キヤリア株式会社
Priority to JP2012500642A priority Critical patent/JP5358018B2/ja
Priority to CN201180009987.8A priority patent/CN102762868B/zh
Publication of WO2011102413A1 publication Critical patent/WO2011102413A1/ja

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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 and a refrigeration cycle apparatus using the same, and more particularly to a rotary compressor having an improved bearing support structure and a refrigeration cycle apparatus using the same.
  • a hermetic rotary compressor is provided with an electric motor part, a compression mechanism part, and a rotary shaft for transmitting rotational power generated in the motor part to the compression mechanism part in the hermetic case. It is rotatably supported by a main bearing and a sub-bearing provided to sandwich the cylinder of the compression mechanism section.
  • Patent Document 1 a clearance is required between the rotary shaft and the main and sub-bearings to maintain the lubrication of the sliding surface during the rotational movement.
  • the sliding surface of the rotating shaft, the main bearing, and the sub-bearing may cause wear of the sliding surface due to falling off of the lubricating film, poor contact, noise, and reduced reliability.
  • An object of the present invention is to provide a rotary compressor that can easily perform the alignment process when assembling the end bearing, is easy to manufacture, and has high reliability during operation, and a refrigeration equipped with the rotary compressor. To provide a cycle device.
  • a sealed case includes a rotating shaft having a main shaft portion, a sub-shaft portion, and a shaft end portion, a rotor fixed to the rotating shaft, and the sealed case.
  • a motor portion having a stator fixed to a wall surface, a main bearing that slides with the main shaft portion, a compression mechanism portion that has a sub-bearing that slides with the sub shaft portion, and an end portion of the rotating shaft on the motor side
  • a solid lubricant is applied to at least one sliding surface of the main shaft portion or the main bearing and at least one sliding surface of the sub shaft portion or the sub bearing, In the state of the base material in which the solid lubricant is not applied to each sliding surface, the gap between the main bearing portion and the main bearing is d1, the gap between the auxiliary bearing and the auxiliary bearing portion is d2, and the end bearing.
  • a rotating shaft having a main shaft portion, a sub-shaft portion, and a shaft end portion, a rotor fixed to the rotating shaft, and a wall surface of the sealed case are fixed in a sealed case.
  • a motor portion having a stator, a main bearing that slides with the main shaft portion, a compression mechanism portion that has a sub-bearing that slides with the sub shaft portion, and the shaft end that is located at an end of the rotating shaft on the motor side
  • the end bearing is a rolling bearing;
  • a solid lubricant is applied to at least one sliding surface of the main shaft portion or the main bearing and at least one sliding surface of the sub shaft portion or the sub bearing, In the state of the base material to which the solid lubricant is not applied, the gap between the main bearing and the main shaft portion is d1, the gap between the sub bearing and the sub bearing is d2, and the shaft end portions of the end bearing and the rotary shaft
  • a refrigeration cycle apparatus includes the above rotary compressor, a four-way valve, an outdoor heat exchanger, an expansion device, and an indoor heat exchanger, which are sequentially connected by piping.
  • a refrigeration cycle is configured.
  • a rotary compressor that can easily perform the alignment process when assembling the end bearing, is easy to manufacture, and has high reliability during operation is provided.
  • a refrigeration cycle apparatus including a rotary compressor having such characteristics.
  • the conceptual diagram of the refrigerating-cycle apparatus carrying the rotary compressor which concerns on embodiment of this invention The longitudinal cross-sectional view of one Embodiment of the rotary compressor which concerns on the 1st Embodiment of this invention.
  • the conceptual diagram which shows the clearance gap between the rotating shaft and each bearing of the rotary compressor which concerns on the 1st Embodiment of this invention.
  • the conceptual diagram which shows the state of the rotating shaft and each bearing which were inclined of the rotary compressor which concerns on embodiment of this invention.
  • the longitudinal cross-sectional view which shows the bearing member of the edge part bearing of the rotary compressor which concerns on the 2nd Embodiment of this invention.
  • the conceptual diagram which shows the clearance gap between the rotating shaft and each bearing of the rotary compressor which concerns on the 2nd Embodiment of this invention.
  • FIG. 1 shows an outline of the refrigeration cycle apparatus of the present invention.
  • the refrigeration cycle apparatus of the present invention is used in, for example, an air conditioner, and includes a hermetic rotary compressor 1, a four-way valve 2, an outdoor heat exchanger 3, an expansion device 4, and an indoor heat exchanger 5, which are sequentially piped.
  • the refrigeration cycle is configured by connecting with.
  • the refrigerant discharged from the rotary compressor 1 is supplied to the outdoor heat exchanger 3 through the four-way valve 2 as indicated by solid arrows, and is condensed by exchanging heat with the outside air.
  • the condensed refrigerant flows out of the outdoor heat exchanger 3 and flows to the indoor heat exchanger 5 through the expansion device 4, where it evaporates by exchanging heat with the indoor air and cools the indoor air.
  • the refrigerant that has flowed out of the indoor heat exchanger 5 is sucked into the hermetic compressor 1 through the four-way valve 2.
  • the refrigerant discharged from the rotary compressor 1 is supplied to the indoor heat exchanger 3 through the four-way valve 2 as indicated by broken arrows, where it is condensed by exchanging heat with indoor air, Heat the room air.
  • the condensed refrigerant flows out of the indoor heat exchanger 5 and flows to the outdoor heat exchanger 3 through the expansion device 4, where it evaporates by exchanging heat with outdoor air.
  • the evaporated refrigerant flows out of the outdoor heat exchanger 3 and is sucked into the hermetic compressor 1 through the four-way valve 2. Thereafter, the refrigerant is sequentially flown in the same manner, and the operation of the refrigeration cycle is continued.
  • This refrigeration cycle apparatus uses a chlorofluorocarbon refrigerant such as HFC or a natural refrigerant such as CO 2 as a working fluid.
  • this refrigeration cycle apparatus can be used for a heat pump water heater or a chilling unit.
  • FIG. 2 shows a longitudinal sectional view of the rotary compressor 1.
  • the rotary compressor 1 includes an electric motor part 12 in the upper part of the sealed case 11 and a compressor part 13 in the lower part.
  • the electric motor part 12 and the compressor part 13 are connected by a rotating shaft 14 for transmitting power. Yes.
  • the electric motor unit 12 includes a stator 31 fixed to the inner wall surface of the sealed case 11 and a rotor 32 fixed to the rotating shaft, and the stator 31 supplies input power through a connection line 25a. For this purpose, it is connected to a sealing terminal 25 for the purpose.
  • the compression mechanism unit 13 includes a first compression mechanism unit 13A and a second compression mechanism unit 13B.
  • the first compression mechanism unit 13A is disposed on the upper side and includes a first cylinder 41A.
  • the second compression mechanism portion 13B is disposed at a lower portion with respect to the first cylinder 41A via an intermediate partition plate 43, and includes a second cylinder 41B.
  • the first and second cylinders 41A and 41B have the same inner diameter.
  • a main bearing 15 as a first bearing is superposed on an upper surface portion of the first cylinder 41A, and is fixed to the first cylinder 41A by a mounting bolt 17a together with a discharge muffler 16a.
  • the secondary bearing 18 as a second bearing is overlaid on the lower surface of the second cylinder 41B, and is fixed to the second cylinder 41B with a mounting bolt (not shown) together with the discharge muffler 16b.
  • the integrated second cylinder 41B, auxiliary bearing 18 and discharge muffler 16b are fixedly attached to the first cylinder 41A by mounting bolts 17b, and the compression mechanism 13 is assembled.
  • the first cylinder 41A is fixed to the sealed case 11 by, for example, arc spot welding.
  • the lower end of the rotary shaft 14 is rotatably supported by the auxiliary bearing 18, and the upper portion thereof is rotatably supported by the main bearing 15. Further, the rotating shaft 14 penetrates through the first and second cylinders 41A and 41B, and integrally includes two eccentric portions 19a and 19b formed with a 180 ° phase difference.
  • the eccentric portions 19a and 19b have the same diameter, and are assembled so as to be positioned at the inner diameter portions of the first and second cylinders 41A and 41B.
  • the rollers 45a and 45b having the same diameter are fitted on the peripheral surfaces of the eccentric portions 19a and 19b.
  • the lengths in the axial direction of the rollers 45a and 45b are substantially the same as the plate thicknesses (axial lengths) of the first cylinder 41A and the second cylinder 41B.
  • the first cylinder 41A and the second cylinder 41B are divided into upper and lower surfaces by the main bearing 15, the intermediate partition plate 43, and the auxiliary bearing 18, and the rollers 45a and 45b are accommodated in the respective interiors so as to be eccentrically rotatable.
  • One cylinder chamber 42a and a second cylinder chamber 42b are formed.
  • Each roller 45a, 45b can rotate eccentrically in the first and second cylinder chambers 42a, 42b.
  • the first and second cylinders 41A and 41B are provided with blade grooves 46a and 46b, and the blade grooves 46a and 46b are open to the cylinder chambers 42a and 42b. Blades 47a and 47b and spring members 48a and 48b are accommodated in the blade grooves 46a and 46b, respectively.
  • Each blade 47a, 47b is formed in a substantially semicircular shape in a plan view at the tip portion on the side of each cylinder chamber 42a, 42b.
  • the spring members 48a and 48b are interposed between the rear ends of the blades 47a and 47b and the end surfaces of the blade grooves 46a and 46b.
  • the spring members 48a and 48b apply elastic force (back pressure) to the blades 47a and 47b, and the tip ends of the cylinder chambers 42a and 42b. And elastically contact the peripheral surfaces of the rollers 45a and 45b.
  • the blades 47a and 47b are formed in such a length dimension that the rear ends are located in the blade grooves 46a and 46b when the tips are at the most protruding portions into the cylinder chambers 42a and 42b.
  • the distance between the rear ends of the blades 47a and 47b and the end surfaces of the blade grooves 46a and 46b is formed to be slightly larger than the maximum compression length of the spring members 48a and 48b.
  • the main bearing 15 and the sub-bearing 18 are provided with a discharge valve mechanism (not shown), which respectively communicates with the cylinder chambers 42a and 42b and is covered with discharge mufflers 16a and 16b.
  • the discharge valve mechanism is opened with the refrigerant gas compressed in each cylinder chamber 42a, 42b rising to a predetermined pressure, and the refrigerant gas is discharged from each cylinder chamber 42a, 42b into the discharge mufflers 16a, 16b. It is supposed to be.
  • a refrigerating machine oil 50 as a liquid lubricant is stored below the inside of the sealed case 11 and is sucked up by a rotary pump (not shown) penetrating the center of the rotary shaft 14 to lubricate each sliding portion.
  • a bearing member 20 is provided between one end of the sealed case 11 and the electric motor unit 3, and the bearing member 20 includes an end bearing 21 that is a third bearing that pivotally supports the rotating shaft 14, and this end. It comprises a bearing frame portion 22 that holds the partial bearing 21.
  • the end bearing 21 is, for example, a sliding bearing or a rolling bearing. In the present embodiment, it is a sliding bearing, and supports the vicinity of the upper end of the rotating shaft 14.
  • the bearing frame portion 22 is provided with a disk-shaped main portion 22a.
  • a flange portion 22b for press-fitting is provided on the outer periphery of the main portion 22a.
  • the end bearing 21 is a bearing provided at the center of the bearing frame portion 22. It is attached to the attachment hole 22c and is fixed by a bolt (not shown).
  • an oil separation member 23 is screwed onto the upper end of the rotating shaft 14 above the bearing frame portion 22.
  • the refrigerant gas that has flowed out to the upper side of the electric motor unit 12 passes through a gas hole (not shown) provided in the bearing frame 22, and the oil contained in the refrigerant gas is separated by the oil separation member 23, and is sealed. It is discharged out of the sealed case 11 through a discharge pipe 24 provided on the upper part of the case 11.
  • a surface treatment with a solid lubricant 35 is performed between the rotary shaft 14 and the main bearing 15 and the sub-bearing 18.
  • the main shaft portion 36 that is a sliding surface with the main bearing 15 of the rotating shaft 14 and the subshaft portion 37 that is a sliding surface with the sub bearing 18 of the rotating shaft 14 are phosphoric acid that is a solid lubricant over the entire circumference.
  • a salt film is applied.
  • a main shaft gap and a sub shaft gap are provided as clearances for sliding between the rotary shaft 14 and the main bearing 15 and the sub bearing 18, and the main shaft gap between the base materials not including the solid lubricant 35 is provided.
  • the average of the sub-shaft gap are d1 and d2, respectively, and the width of the main shaft gap and the sub-shaft gap including the solid lubricant 35 are d1 ′ and d2 ′, respectively.
  • the gaps have a relationship of d1> d3, d2> d3, d1 ′ ⁇ d3, d2 ′ ⁇ d3.
  • the gap between the rotary shaft 14, the main bearing 15 and the auxiliary bearing 18 can be initially narrowed by the solid lubricant 35 during assembly. That is, as shown in FIGS. 4 and 5, the relationship between the maximum inclination angle ⁇ 1 when the solid lubricant is applied and assembled and the maximum inclination angle ⁇ 2 when only the base material is assembled is ⁇ 1 ⁇ 2. . Even when the rotary shaft 14 is tilted before the end bearing 21 is assembled, the solid lubricant 35 contacts the inner peripheral surface of the bearing, and the maximum tilt angle of the rotary shaft 14 is made smaller than that of the base material alone. can do. Therefore, when the end bearing 21 is assembled, the center of the end bearing 21 and the main bearing 15 and the sub-bearing 18 are misaligned with simple alignment without performing alignment using dedicated equipment. Integration is possible in the minimum state.
  • each bearing is large when the rotating shaft 14 is inclined, the amount of eccentricity of the rotating shaft 14 with respect to the center axis of each bearing becomes large, so that the width of the gap to be secured is allowed. This is because an appropriate bearing length is set according to the inclination angle.
  • d1> d2 is d1 ′> d2 ′.
  • the end bearing 21 is a rolling bearing, in particular, a ball bearing 28 having an automatic alignment mechanism, and supports the vicinity of one end of the rotating shaft 14, for example, the vicinity of the upper end. explain.
  • the compressor in the second embodiment is incorporated into the refrigeration cycle apparatus in the same manner as the rotary compressor 1 in the first embodiment, and the configuration thereof is the same as that of the rotary compressor in the first embodiment.
  • the configuration is almost the same (FIG. 2), and the configurations of the end bearing 21 and the bearing member 20 are different as shown in FIG.
  • the bearing frame portion 51 is provided with a disk-shaped main portion 51a, and a flange portion 51b for press-fitting is provided on the outer periphery of the main portion 51a. It is attached to a bearing attachment hole 51d provided in the boss portion 51c of 51.
  • the average of the main shaft gap and the average of the sub shaft gap between the base materials not including the solid lubricant 35 are d1 and d2, respectively.
  • the average shaft clearance is defined as d1 ′ and d2 ′, respectively.
  • the average d4 of the gap between the ball bearing 28 and the rotary shaft 14 is a value including the average of the internal gap which is the gap between the inner ring 28a, the outer ring 28b and the ball 28c of the ball bearing 28.
  • a phosphate film is used as the solid lubricant 35, but in addition to this, a fluorine-based resin such as molybdenum disulfide and PTFE (polytetrafluoroethylene), or a solid lubricant such as graphite may be used.
  • the example in which the solid lubricant is applied to the outer peripheral surfaces of the main shaft portion 36 and the sub shaft portion 37 of the rotating shaft 14 is shown. You may apply
  • the surface to which the solid lubricant is applied is the entire circumference of the rotating shaft and the sliding surface of the bearing. However, in order to reduce the contact area between the rotating shaft and each bearing, it is partially It may be applied.
  • a two-cylinder rotary compressor is used, but a one-cylinder rotary compressor may be used.
  • the embodiment of the present invention provides a refrigeration cycle apparatus including the rotary compressor according to the above-described embodiment of the present invention.
  • the refrigeration cycle apparatus includes a hermetic rotary compressor 1, a four-way valve 2, an outdoor heat exchanger 3, an expansion device 4, and an indoor heat exchanger 5 in the above-described embodiment.
  • the refrigeration cycle is configured by sequentially connecting them with piping.
  • the refrigerant discharged from the rotary compressor 1 is supplied to the outdoor heat exchanger 3 through the four-way valve 2 as indicated by solid arrows, where it is condensed by exchanging heat with the outside air.
  • the condensed refrigerant flows out of the outdoor heat exchanger 3 and flows to the indoor heat exchanger 5 through the expansion device 4, where it evaporates by exchanging heat with the indoor air and cools the indoor air.
  • the refrigerant that has flowed out of the indoor heat exchanger 5 is sucked into the hermetic compressor 1 through the four-way valve 2.
  • the refrigerant discharged from the rotary compressor 1 is supplied to the indoor heat exchanger 3 through the four-way valve 2 as indicated by broken arrows, where it is condensed by exchanging heat with indoor air, Heat the room air.
  • the condensed refrigerant flows out of the indoor heat exchanger 5 and flows to the outdoor heat exchanger 3 through the expansion device 4, where it evaporates by exchanging heat with outdoor air.
  • the evaporated refrigerant flows out of the outdoor heat exchanger 3 and is sucked into the hermetic compressor 1 through the four-way valve 2. Thereafter, the refrigerant is sequentially flown in the same manner, and the operation of the refrigeration cycle is continued.
  • This refrigeration cycle apparatus uses a chlorofluorocarbon refrigerant such as HFC or a natural refrigerant such as CO 2 as a working fluid.
  • this refrigeration cycle device can be used for heat pump water heaters, chilling units, and the like.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
PCT/JP2011/053372 2010-02-18 2011-02-17 ロータリ圧縮機及び冷凍サイクル装置 WO2011102413A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2012500642A JP5358018B2 (ja) 2010-02-18 2011-02-17 ロータリ圧縮機及び冷凍サイクル装置
CN201180009987.8A CN102762868B (zh) 2010-02-18 2011-02-17 回转式压缩机以及制冷循环装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010-033040 2010-02-18
JP2010033040 2010-02-18

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WO2011102413A1 true WO2011102413A1 (ja) 2011-08-25

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JP (1) JP5358018B2 (zh)
CN (1) CN102762868B (zh)
WO (1) WO2011102413A1 (zh)

Cited By (5)

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Publication number Priority date Publication date Assignee Title
CN104481877A (zh) * 2014-12-09 2015-04-01 广东美芝制冷设备有限公司 低背压旋转式压缩机
CN105090027A (zh) * 2015-09-17 2015-11-25 广东美芝制冷设备有限公司 多气缸旋转式压缩机
CN105114315A (zh) * 2015-09-17 2015-12-02 广东美芝制冷设备有限公司 多缸旋转式压缩机
CN105114316A (zh) * 2015-09-17 2015-12-02 广东美芝制冷设备有限公司 多缸旋转式压缩机
WO2018142564A1 (ja) * 2017-02-03 2018-08-09 三菱電機株式会社 圧縮機

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CN103452854B (zh) * 2013-08-19 2016-06-29 广东美芝制冷设备有限公司 旋转式压缩机
CN105090030B (zh) * 2015-09-17 2018-01-16 广东美芝制冷设备有限公司 电动回转式压缩机
CN105257545A (zh) * 2015-11-04 2016-01-20 安徽美芝精密制造有限公司 旋转式压缩机
CN105697378B (zh) * 2016-02-15 2018-08-07 珠海格力节能环保制冷技术研究中心有限公司 一种曲轴支撑结构及旋转式压缩机
CN109139469B (zh) * 2017-06-27 2020-05-08 上海海立电器有限公司 一种转子式压缩机
CN110685911A (zh) * 2019-09-29 2020-01-14 安徽美芝精密制造有限公司 压缩机及制冷设备

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Publication number Priority date Publication date Assignee Title
CN104481877A (zh) * 2014-12-09 2015-04-01 广东美芝制冷设备有限公司 低背压旋转式压缩机
CN105090027A (zh) * 2015-09-17 2015-11-25 广东美芝制冷设备有限公司 多气缸旋转式压缩机
CN105114315A (zh) * 2015-09-17 2015-12-02 广东美芝制冷设备有限公司 多缸旋转式压缩机
CN105114316A (zh) * 2015-09-17 2015-12-02 广东美芝制冷设备有限公司 多缸旋转式压缩机
WO2018142564A1 (ja) * 2017-02-03 2018-08-09 三菱電機株式会社 圧縮機
CN110249132A (zh) * 2017-02-03 2019-09-17 三菱电机株式会社 压缩机
CZ309104B6 (cs) * 2017-02-03 2022-02-02 Mitsubishi Electric Corporation Kompresor

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