WO2018051567A1 - 回転式圧縮機及び冷凍サイクル装置 - Google Patents

回転式圧縮機及び冷凍サイクル装置 Download PDF

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Publication number
WO2018051567A1
WO2018051567A1 PCT/JP2017/015299 JP2017015299W WO2018051567A1 WO 2018051567 A1 WO2018051567 A1 WO 2018051567A1 JP 2017015299 W JP2017015299 W JP 2017015299W WO 2018051567 A1 WO2018051567 A1 WO 2018051567A1
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WO
WIPO (PCT)
Prior art keywords
sealed case
rotary compressor
cylinder
discharge
cylinder chamber
Prior art date
Application number
PCT/JP2017/015299
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
平山　卓也
鈴木　秀明
昌宏 畑山
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 EP17850474.2A priority Critical patent/EP3514391B1/en
Priority to CN201780023665.6A priority patent/CN109072917B/zh
Publication of WO2018051567A1 publication Critical patent/WO2018051567A1/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
    • 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
    • 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
    • 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
    • F04C23/003—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 having complementary function

Definitions

  • Embodiments of the present invention relate to a rotary compressor and a refrigeration cycle apparatus using the rotary compressor.
  • An object of an embodiment of the present invention is to provide a rotary compressor having a small discharge capacity and a large discharge capacity, and a refrigeration cycle apparatus using the rotary compressor.
  • a sealed case an electric motor having six or more poles accommodated in the upper part of the sealed case, and a rotary shaft accommodated in the lower part of the sealed case and connected to the electric motor And a discharge pipe provided at the top of the sealed case.
  • the compression mechanism has two cylinders that are closed at both the upper and lower ends and in which a cylinder chamber is formed. Then, the roller fitted to the rotating shaft in the cylinder chamber rotates eccentrically to compress the working fluid, and the compressed working fluid in the cylinder chamber is discharged into the sealed case.
  • the electric motor rotates integrally with the rotating shaft.
  • a discharge passage for guiding the working fluid discharged from the cylinder chamber to the discharge pipe side is formed, and the maximum discharge pressure of the working fluid is 3 MPa or more.
  • the inner diameter of the Linda chamber is D1
  • the total height of the cylinder chambers of the two cylinders is H
  • the distance from the upper end of the stator to the upper inner wall surface of the sealed case is L1
  • the inner sectional area of the sealed case is Ac
  • the discharge flow path The following relational expressions (1) to (3) are all satisfied, where Ad is the total cross-sectional area of T and T is the thickness of the stator core of the stator.
  • a refrigeration cycle apparatus 1 includes a rotary compressor 2, a condenser 3 that is a radiator connected to the rotary compressor 2, an expansion device 4 connected to the condenser 3, And an evaporator 5 that is a heat absorber connected to the expansion device 4.
  • the rotary compressor 2 is provided with an accumulator 6.
  • the refrigerant that is the working fluid circulates while changing in phase between a gaseous gas refrigerant and a liquid liquid refrigerant, and is dissipated in the process of phase change from the gas refrigerant to the liquid refrigerant. Heat is absorbed during the phase change of the gas refrigerant, and heating, cooling, heating, cooling, and the like are performed using these heat dissipation and heat absorption.
  • the gas refrigerant is compressed.
  • the condenser 3 the compressed gas refrigerant is condensed into a liquid refrigerant.
  • the expansion device 4 the condensed liquid refrigerant is decompressed.
  • the evaporator 5 the decompressed liquid refrigerant evaporates to become a gas refrigerant.
  • the accumulator 6 of the rotary compressor 2 when the liquid refrigerant is contained in the gas refrigerant evaporated in the evaporator 5, the liquid refrigerant is removed.
  • the rotary compressor 2 has a cylindrical sealed case 7 that is closed at both upper and lower ends to be airtight.
  • An electric motor 8 is accommodated in an upper portion of the sealed case 7, and a gas is disposed in a lower portion of the sealed case 7.
  • the compression mechanism part 9 which is a part which compresses a refrigerant
  • a rotating shaft 10 is connected to the electric motor 8, and the compression mechanism unit 9 is driven through the rotating shaft 10.
  • the gas refrigerant compressed by the compression mechanism 9 is discharged into the sealed case 7, and the sealed case 7 is filled with high-pressure gas refrigerant.
  • a discharge pipe 11 is provided in the upper part of the sealed case 7, and the high-pressure gas refrigerant in the sealed case 7 is guided to the condenser 3 through the discharge pipe 11.
  • a lubricating oil 12 is stored at the bottom of the sealed case 7.
  • the electric motor 8 includes a rotor 13 that is fixed to the rotating shaft 10 and rotates integrally with the rotating shaft 10, and a stator 14 that surrounds the outer periphery of the rotor 13, and has six or more poles. ing.
  • the rotor 13 includes a rotor core 13a in which electromagnetic steel plates are laminated, and a plurality of permanent magnets 13b inserted into the rotor core 13a.
  • the stator 14 has a stator core 14a in which electromagnetic steel plates are laminated, and a field winding 14b wound around the stator core 14a.
  • the electric motor 8 includes a plurality of discharge passages 15, such as a rotor 13, that guide the gas refrigerant discharged from the compression mechanism 9 into the sealed case 7 to the discharge pipe 11 side, which is the upper side of the sealed case 7.
  • a through hole formed so as to penetrate in the vertical direction, a gap between the inner peripheral surface of the sealing case 7 and the outer peripheral surface of the stator 14, and a gap between the outer peripheral surface of the rotor 13 and the inner peripheral surface of the stator 14 are formed.
  • the compression mechanism unit 9 includes two cylinders 16a and 16b arranged in the vertical direction, a partition plate 17 arranged between the cylinders 16a and 16b and closing one end face of the cylinders 16a and 16b,
  • the main bearing 18 which is one bearing which is disposed on the motor 8 side which is the upper side of the cylinder 16a and closes the upper end surface of the cylinder 16a and the motor 8 which is the lower side of the other cylinder 16b are opposite to the motor 8.
  • the auxiliary bearing 19 is the other bearing that is disposed and closes the lower end face of the cylinder 16b.
  • a cylinder chamber 20a is formed inside the cylinder 16a whose both end surfaces are closed by the main bearing 18 and the partition plate 17, and the cylinder chamber 20a is formed inside the cylinder 16b whose both end surfaces are closed by the partition plate 17 and the auxiliary bearing 19.
  • a chamber 20b is formed.
  • a rotary shaft 10 is inserted through the cylinders 16 a and 16 b, and the rotary shaft 10 is pivotally supported by a main bearing 18 and a sub bearing 19.
  • the rotary shaft 10 is formed with two columnar eccentric portions 21a and 21b.
  • One eccentric portion 21a is disposed in the cylinder chamber 20a, and the other eccentric portion 21b is disposed in the cylinder chamber 20b.
  • a roller 22a is fitted to the eccentric portion 21a, and a roller 22b is fitted to the eccentric portion 21b.
  • These rollers 22a and 22b are provided so as to be eccentrically rotated while the outer peripheral surface thereof is in sliding contact with the inner peripheral surfaces of the cylinder chambers 20a and 20b as the rotary shaft 10 rotates.
  • the cylinder 16a is provided with a reciprocating blade 23a
  • the cylinder 16b is provided with a reciprocating blade 23b.
  • the cylinder chambers 20a and 20b are partitioned into a suction chamber for sucking in the low-pressure gas refrigerant and a compression chamber for compressing the sucked-in gas refrigerant.
  • the main bearing 18 is provided with a discharge hole 24a and a discharge valve 25a for discharging the gas refrigerant compressed in the cylinder chamber 20a into the sealed case 7.
  • the sub bearing 19 is provided with a discharge hole 24 b and a discharge valve 25 b for discharging the gas refrigerant compressed in the cylinder chamber 20 b into the sealed case 7.
  • a muffler case 26a is attached to the main bearing 18 at a position surrounding the discharge valve 25a, and the gas refrigerant discharged by opening the discharge valve 25a is discharged into the muffler case 26a and then formed in the muffler case 26a.
  • the discharge hole 27 is discharged into the sealed case 7.
  • a muffler case 26b is attached to the auxiliary bearing 19 at a position surrounding the discharge valve 25b, and the gas refrigerant discharged by opening the discharge valve 25b is discharged into the muffler case 26b and then passes through a communication path (not shown). Then, it flows into the muffler case 26a and is discharged into the sealed case 7 from the discharge hole 27 of the muffler case 26a.
  • the rotary compressor 2 is set so that the maximum discharge pressure of the gas refrigerant during operation is 3 megapascals (MPa) or more, and the dimensions of each part in the rotary compressor 2 are as follows. explain in detail.
  • the cylinder chambers 20a and 20b have the same inner diameter, and the cylinder chambers 20a and 20b have an inner diameter D1.
  • the height of one cylinder chamber 20a is H1
  • the height of the other cylinder chamber 20b is H2
  • the distance from the upper end of the stator 14 to the upper inner wall surface of the sealed case 7 is L1.
  • the cross-sectional area of the space inside the sealed case 7 is Ac.
  • the total cross-sectional area of the discharge channel 15 is Ad.
  • the thickness of the stator core 14a of the stator 14 is T.
  • the distance from the lower end of the rotor 13 of the electric motor 8 to the lower inner wall surface of the sealed case 7 is L2.
  • the compressor 13 is driven by the rotation of the rotor 13 and the rotating shaft 10 by energization of the electric motor 8.
  • the compression mechanism 9 By driving the compression mechanism 9, the low-pressure gas refrigerant passes through the accumulator 6 and is sucked into the cylinder chambers 20a and 20b. The sucked gas refrigerant is compressed in the cylinder chambers 20a and 20b.
  • the gas refrigerant compressed to high pressure in the cylinder chamber 20a is discharged from the discharge valve 25a into the muffler case 26a and discharged into the sealed case 7 from the discharge hole 27 of the muffler case 26a.
  • the gas refrigerant compressed to high pressure in the cylinder chamber 20b is discharged from the discharge valve 25b into the muffler case 26b and flows into the muffler case 26a through a communication path (not shown). It is discharged from the discharge hole 27 into the sealed case 7.
  • the gas refrigerant discharged from the discharge hole 27 into the sealed case 7 is guided to the discharge pipe 11 side, which is the upper side of the sealed case 7, through the discharge flow path 15 formed in the electric motor 8. It is led to the condenser 3 through.
  • FIG. 2 shows the inner diameter “D1” of the cylinder chambers 20a and 20b and the inner diameter of the sealed case 7 under rated conditions using a refrigerant (for example, R410A, R32, carbon dioxide) having a maximum discharge pressure of 3 MPa or more during operation.
  • a refrigerant for example, R410A, R32, carbon dioxide
  • COP coefficient of performance ratio (COP when using a 6-pole motor / 4 COP when using a 4-pole motor).
  • FIG. 2 a case where a 6-pole motor is compared with a 4-pole motor is described as an example. However, the same effect can be obtained in a motor having 6 or more poles, for example, an 8-pole motor or a 10-pole motor. Is obtained.
  • FIG. 3 shows that when 0.85 ⁇ D1 ⁇ H is satisfied and the distance L1 from the upper end of the stator 14 to the upper inner wall surface of the sealed case 7 is larger than the total height H of the cylinder chambers 20a and 20b ( The result of measuring the oil discharge amount of the lubricating oil 12 from the discharge pipe 11 with respect to Ad (total cross-sectional area of the discharge flow path 15) / Ac (cross-sectional area of the inner space portion of the sealed case 7) of H ⁇ L1) is shown. ing.
  • the oil discharge amount is expressed as a weight ratio to the circulation amount of the gas refrigerant.
  • the discharge flow path of the electric motor 8 is increased. Since the flow rate of the gas refrigerant at 15 increases, it becomes difficult for the lubricating oil to be separated from the gas refrigerant in the discharge flow path 15, and in particular, it is understood that the amount of discharged oil increases rapidly when Ad / Ac ⁇ 0.06.
  • FIG. 4 shows the efficiency ratio of the 6-pole motor 8 with respect to Ad / Ac.
  • Ad / Ac 0.13
  • the space factor of the field winding 14 b and the cross-sectional area of the permanent magnet 13 b are decreased in order to secure the area of the discharge flow path 15. It can be seen that the efficiency of is significantly reduced. From these facts, by satisfying H ⁇ L1 and 0.06 ⁇ Ad / Ac ⁇ 0.13 (relational expression 2), it is possible to reduce the amount of oil discharged while suppressing the deterioration of the motor efficiency.
  • FIG. 5 shows that T (thickness of the stator core 14a) / when satisfying 0.85 ⁇ D1 ⁇ H ⁇ L1 (relational expression 1) and 0.06 ⁇ Ad / Ac ⁇ 0.13 (relational expression 2).
  • the efficiency ratio of the 6-pole motor 8 with respect to H (the total height of the cylinder chambers 20a and 20b) is shown.
  • FIG. 6 shows the ratio (T / H) of the thickness T of the stator core 14a of the stator 14 to the total height H of the cylinder chambers 20a and 20b, and the gas in the discharge passage 15 of the electric motor 8 with respect to the compressor theoretical work Wth.
  • coolant is shown.
  • Wd / Wth increases rapidly. From these things, 1.2 ⁇ T / H ⁇ 1.5 (relational expression 3) can reduce the pressure loss of the discharge flow path 15 while suppressing the deterioration of the motor efficiency.
  • the rotary compression has high pressure resistance, small size and light weight, large discharge capacity, high resource saving, and low oil discharge and high reliability.
  • Machine 2 can be provided.
  • D2 / H is the ratio of the inner diameter D2 of the main bearing 18 and the auxiliary bearing 19 to the total height H of the cylinder chambers 20a and 20b.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
PCT/JP2017/015299 2016-09-14 2017-04-14 回転式圧縮機及び冷凍サイクル装置 WO2018051567A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP17850474.2A EP3514391B1 (en) 2016-09-14 2017-04-14 Rotary compressor and refrigeration cycle device
CN201780023665.6A CN109072917B (zh) 2016-09-14 2017-04-14 旋转式压缩机以及制冷循环装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-179607 2016-09-14
JP2016179607A JP6703921B2 (ja) 2016-09-14 2016-09-14 回転式圧縮機及び冷凍サイクル装置

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Publication Number Publication Date
WO2018051567A1 true WO2018051567A1 (ja) 2018-03-22

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PCT/JP2017/015299 WO2018051567A1 (ja) 2016-09-14 2017-04-14 回転式圧縮機及び冷凍サイクル装置

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EP (1) EP3514391B1 (zh)
JP (1) JP6703921B2 (zh)
CN (1) CN109072917B (zh)
WO (1) WO2018051567A1 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023142560A1 (zh) * 2022-01-26 2023-08-03 珠海格力电器股份有限公司 自起动同步磁阻压缩机和制冷设备系统

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109058109B (zh) * 2018-10-10 2024-02-27 珠海凌达压缩机有限公司 一种压缩机及空调器
WO2021039573A1 (ja) * 2019-08-23 2021-03-04 東芝キヤリア株式会社 圧縮機、および冷凍サイクル装置
CN111608913B (zh) * 2020-05-29 2022-04-12 广东美芝精密制造有限公司 压缩机及空调系统

Citations (3)

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JP2006177225A (ja) * 2004-12-22 2006-07-06 Hitachi Home & Life Solutions Inc ロータリ圧縮機
JP2008014150A (ja) * 2006-07-03 2008-01-24 Toshiba Kyaria Kk 回転式圧縮機及びこれを用いた冷凍サイクル装置
WO2013065706A1 (ja) * 2011-10-31 2013-05-10 東芝キヤリア株式会社 密閉型回転式圧縮機と冷凍サイクル装置

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JP4909597B2 (ja) * 2006-01-27 2012-04-04 東芝キヤリア株式会社 密閉型回転式圧縮機、及び冷凍サイクル装置
JP5068719B2 (ja) * 2008-09-22 2012-11-07 東芝キヤリア株式会社 回転式圧縮機と冷凍サイクル装置
BR112013031245B1 (pt) * 2011-06-08 2021-06-22 Toshiba Carrier Corporation Compressor selado e dispositivo de ciclo de refrigeração
CN103541902A (zh) * 2012-07-10 2014-01-29 广东美芝制冷设备有限公司 壳体低背压的旋转式压缩机
CN203655642U (zh) * 2013-12-26 2014-06-18 广东美芝精密制造有限公司 旋转式压缩机及其气缸、制冷系统和空调
WO2016056065A1 (ja) * 2014-10-07 2016-04-14 三菱電機株式会社 永久磁石埋込型電動機、圧縮機、および冷凍空調機

Patent Citations (3)

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Publication number Priority date Publication date Assignee Title
JP2006177225A (ja) * 2004-12-22 2006-07-06 Hitachi Home & Life Solutions Inc ロータリ圧縮機
JP2008014150A (ja) * 2006-07-03 2008-01-24 Toshiba Kyaria Kk 回転式圧縮機及びこれを用いた冷凍サイクル装置
WO2013065706A1 (ja) * 2011-10-31 2013-05-10 東芝キヤリア株式会社 密閉型回転式圧縮機と冷凍サイクル装置

Non-Patent Citations (1)

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Title
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023142560A1 (zh) * 2022-01-26 2023-08-03 珠海格力电器股份有限公司 自起动同步磁阻压缩机和制冷设备系统

Also Published As

Publication number Publication date
CN109072917B (zh) 2020-03-17
EP3514391A1 (en) 2019-07-24
JP6703921B2 (ja) 2020-06-03
JP2018044489A (ja) 2018-03-22
CN109072917A (zh) 2018-12-21
EP3514391B1 (en) 2024-05-29
EP3514391A4 (en) 2020-01-22

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