EP3514391A1 - Compresseur rotatif et dispositif à cycle de réfrigération - Google Patents

Compresseur rotatif et dispositif à cycle de réfrigération Download PDF

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Publication number
EP3514391A1
EP3514391A1 EP17850474.2A EP17850474A EP3514391A1 EP 3514391 A1 EP3514391 A1 EP 3514391A1 EP 17850474 A EP17850474 A EP 17850474A EP 3514391 A1 EP3514391 A1 EP 3514391A1
Authority
EP
European Patent Office
Prior art keywords
electric motor
hermetic case
rotary compressor
cylinder chambers
discharge
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.)
Pending
Application number
EP17850474.2A
Other languages
German (de)
English (en)
Other versions
EP3514391A4 (fr
Inventor
Takuya Hirayama
Hideaki Suzuki
Masahiro HATAYAMA
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.)
Toshiba Carrier Corp
Original Assignee
Toshiba Carrier 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 Toshiba Carrier Corp filed Critical Toshiba Carrier Corp
Publication of EP3514391A1 publication Critical patent/EP3514391A1/fr
Publication of EP3514391A4 publication Critical patent/EP3514391A4/fr
Pending 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
    • F04C23/008—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 invention relate to a rotary compressor and a refrigerating cycle device which uses the rotary compressor.
  • a rotary compressor which houses an electric motor and a compression mechanism portion that is driven via a rotary shaft connected to the electric motor in a hermetic case and which compresses a working fluid such as a refrigerant
  • various measures are taken in order to increase a discharge volume of the working fluid to be compressed and discharged, for example, a measure described in the following Patent Document 1 is taken.
  • H/D ⁇ 0.4 is set for a 1-cylinder type and H/D ⁇ 0.3 is set for a 2-cylinder type where an inner diameter of a cylinder chamber is D and a height of the cylinder chamber is H.
  • An object of an embodiment of the invention is to provide a rotary compressor which is small in size yet large in discharge volume and a refrigerating cycle device using the rotary compressor.
  • the rotary compressor comprises a hermetic case, an electric motor which is housed at an upper portion in the hermetic case and has six or more poles, a compression mechanism portion which is housed at a lower portion in the hermetic case and is driven via a rotary shaft connected to the electric motor, and a discharge pipe which is provided at the upper portion in the hermetic case, wherein the compression mechanism portion has two cylinders which have covered upper and lower both ends and cylinder chambers formed inside, compresses a working fluid by eccentric rotation of a roller fitted to the rotary shaft in the cylinder chambers and discharges the compressed working fluid into the hermetic case, the electric motor has a rotor which rotates with the rotary shaft and a stator which surrounds the outer periphery of the rotor, a discharge flow channel which leads the working fluid discharged from the insides of the cylinder chambers to a side of the discharge pipe is formed, and a maximum discharge pressure of the working fluid becomes three or more MPa
  • a refrigerating cycle device 1 has a rotary compressor 2, a condenser 3 which is a radiator connected to the rotary compressor 2, an expansion device 4 connected to the condenser 3, and an evaporator 5 which is a heat sink connected to the expansion device 4.
  • An accumulator 6 is provided in the rotary compressor 2.
  • a refrigerant which is a working fluid circulates while phase-changing to a gas refrigerant in a gas state and to a liquid refrigerant in a liquid state.
  • Heat is radiated in a process of phase-change from a gas refrigerant to a liquid refrigerant. Heat is absorbed in a process of phase-change from a liquid refrigerant to a gas refrigerant. Using these heat radiation and heat absorption, air heating, air cooling, heating, cooling etc. are performed.
  • a gas refrigerant is compressed in the rotary compressor 2.
  • the condenser 3 the compressed gas refrigerant is condensed and becomes a liquid refrigerant.
  • the condensed liquid refrigerant is decompressed in the expansion device 4.
  • the evaporator 5 the decompressed liquid refrigerant evaporates and becomes a gas refrigerant.
  • liquid refrigerant is removed when the liquid refrigerant is contained in the gas refrigerant which is evaporated in the evaporator 5.
  • the rotary compressor 2 has a cylindrical hermetic case 7. Upper and lower ends of the hermetic case 7 are covered, and the hermetic case 7 is kept in an air-sealed state.
  • An electric motor 8 is housed at an upper portion in the hermetic case 7.
  • a compression mechanism portion 9 which is a portion to compress a gas refrigerant is housed at a lower portion in the hermetic case 7.
  • a rotary shaft 10 is connected to the electric motor 8, and the compression mechanism portion 9 is driven via the rotary shaft 10.
  • a gas refrigerant compressed in the compression mechanism portion 9 is discharged into an interior of the hermetic case 7, and the interior of the hermetic case 7 is filled with a high-pressure gas refrigerant.
  • a discharge pipe 11 is provided at an upper portion of the hermetic case 7, and the high-pressure gas refrigerant in the interior of the hermetic case 7 is led to the condenser 3 through the inside of the discharge pipe 11.
  • a lubricating oil 12 is reserved at a bottom portion in the hermetic case 7.
  • the electric motor 8 has a rotor 13 which is fixed to the rotary shaft 10 and rotates with the rotary shaft 10, and a stator 14 which surrounds the outer periphery of the rotor 13.
  • the number of the poles of the electric motor 8 is six or more.
  • the rotor 13 has a rotor core 13a which is formed by laminating electromagnetic steel sheets, and a plurality of permanent magnets 13b which are inserted in an inside of the rotor core 13a.
  • the stator 14 has a stator core 14a which is formed by laminating electromagnetic steel sheets and has a field winding 14b which is wound around the stator core 14a.
  • a plurality of discharge flow channels 15 are formed.
  • the discharge flow channels 15 lead a gas refrigerant discharged into the interior of the hermetic case 7 from the compression mechanism portion 9 to a side of the discharge pipe which is an upper side in the hermetic case 7.
  • the discharge flow channels 15 are, for example, a through-hole formed to penetrate in an up-and-down direction in the rotor 13, a gap between an inner periphery of the hermetic case 7 and an outer periphery of the stator 14, a gap between an outer periphery of the rotor 13 and an inner periphery of the stator 14 etc.
  • the compression mechanism portion 9 has two cylinders 16a, 16b arranged in an up-and-down direction, a partition plate 17 arranged between the cylinders 16a, 16b to cover one end faces of these cylinders 16a, 16b, a main bearing 18 arranged at a side of the electric motor that is an upward side of the cylinder 16a and is one bearing to cover an end face of the cylinder 16a on the upward side, and a sub-bearing 19 arranged at a side opposite to the electric motor that is an downward side of the other cylinder 16b and is the other bearing to cover an end face of the cylinder 16b on the downward side.
  • a cylinder chamber 20a is formed in the interior of the cylinder 16a whose both end faces are covered by the main bearing 18 and the partition plate 17.
  • a cylinder chamber 20b is formed in the interior of the cylinder 16b whose both end faces are covered by the partition plate 17 and the sub-bearing 19.
  • the rotary shaft 10 is inserted through these cylinders 16a, 16b.
  • the rotary shaft 10 is supported pivotally by the main bearing 18 and the sub-bearing 19.
  • Two eccentric portions 21a, 21b of a cylindrical shape are formed at the rotary shaft 10.
  • One eccentric portion 21a is arranged in the cylinder chamber 20a, and the other eccentric portion 21b is arranged 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 rotate eccentrically while their outer peripheral faces contacts the inner peripheral faces of the cylinder chambers 20a, 20b slidably with rotation of the rotary shaft 10.
  • a blade 23a is provided in the cylinder 16a, and a blade 23b which is reciprocating and slidable is provided in the cylinder 16b.
  • blades 23a, 23b partition the interiors of the cylinder chambers 20a, 20b into suction chambers which sucks a low-pressure gas refrigerant and compression chambers which compress the sucked gas refrigerant, by making tip portions of the blades 23a, 23b contact outer peripheral faces of the rollers 22a and 22b.
  • the main bearing 18 is provided with a discharge hole 24a and discharge valve 25a to cause the gas refrigerant compressed in the cylinder chamber 20a to discharge into hermetic case 7.
  • the sub-bearing 19 is provided with a discharge hole 24b and a discharge valve 25b to cause the gas refrigerant compressed in the cylinder chamber 20b to discharge into the hermetic case 7.
  • a muffler case 26a is attached to the main bearing 18 at a position surrounding the discharge valve 25a.
  • a gas refrigerant discharged by opening the discharge valve 25a is discharged into the muffler case 26a, and then is discharged into the interior of the hermetic case 7 from a discharge hole 27 formed in the muffler case 26a.
  • a muffler case 26b is attached to the sub-bearing 19 at a position surrounding the discharge valve 25b.
  • a gas refrigerant discharged by opening the discharge valve 25b is discharged into the muffler case 26b, and then flows into the interior of the muffler case 26a through a communicating passage (not illustrated) and is discharged into the interior of the hermetic 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 a gas refrigerant at the time of operation becomes three or more Mega Pascal (MPa). The size of each portion in the rotary compressor 2 will be explained in detail below.
  • the inner diameters of the cylinder chambers 20a, 20b are the same size, and the inner diameter of these cylinder chambers 20a and 20b is expressed as D1.
  • the height of one cylinder chamber 20a is expressed as H1.
  • the height of the other cylinder chamber 20b is expressed as H2.
  • the distance from an upper end portion of the stator 14 to an inner wall surface of the upper portion of the hermetic case 7 is expressed as L1.
  • the sectional area in a space portion inside the hermetic case 7 is expressed as Ac.
  • the total sectional area of the discharge flow channel 15 is expressed as Ad.
  • the thickness of the stator core 14a of the stator 14 is expressed as T.
  • the distance from a lower end portion of the rotor 13 of the electric motor 8 to an inner wall surface of the lower portion of the hermetic case 7 is expressed as L2.
  • the inner diameter of the main bearing 18 and the sub-bearing 19 is expressed as D2.
  • the compression mechanism portion 9 is driven by rotation of the rotor 13 and the rotary shaft 10 through energization to the electric motor 8.
  • a low-pressure gas refrigerant passes the accumulator 6 and is sucked into the cylinder chambers 20a, 20b.
  • the sucked gas refrigerant is compressed in the cylinder chambers 20a, 20b.
  • the gas refrigerant which is compressed in the cylinder chamber 20a and becomes high pressure is discharged into the muffler case 26a from the discharge valve 25a, and is discharged into the hermetic case 7 from the discharge hole 27 of the muffler case 26a.
  • the gas refrigerant which is compressed in the cylinder chamber 20b and becomes high pressure is discharged into the muffler case 26b from the discharge valve 25b, flows into the muffler case 26a through the communicating passage which is not illustrated, then is discharged into the hermetic case 7 from the discharge hole 27 of the muffler case 26a.
  • the gas refrigerant discharged into the hermetic case 7 from the discharge hole 27 is led to the side of the discharge pipe 11, which is the side of the upper portion in the hermetic case 7, through the discharge flow channel 15 formed in the electric motor 8, and is led to the condenser 3 through the discharge pipe 11.
  • Fig. 2 shows s a relation between "H/D1" and a ratio of a COP (Coefficient Of Performance) at a time of using a 4-pole electric motor and a COP at a time of using a 6-pole electric motor (a COP at a time of using a 4-pole electric motor / a COP at a time of using a 6-pole electric motor), in a case of enlarging the total height "H" of the cylinder chambers 20a, 20b to increase a discharge volume of a gas refrigerant while the inner diameter "D1" of the cylinder chambers 20a, 20b and the inner diameter of the hermetic case 7 are kept to be the same, under a rated condition using a refrigerant by which the maximum discharge pressure at a time of operation is three or more MPa (for example, R410A, R32, carbon dioxide).
  • MPa for example, R410A, R32, carbon dioxide
  • a 6-pole electric motor is compared to a 4-pole electric motor is described as an example, but a similar effect can be obtained in an electric motor of 6 or more poles, for example, an 8-pole electric motor, a 10-pole electric motor etc.
  • Fig. 3 shows a measurement result of an oil discharge volume of the lubricating oil 12 from the discharge pipe 11 with respect to Ad (a total sectional area of the discharge flow channel 15)/Ac (a sectional area of the space portion of the inner side of the hermetic case 7) when 0.85 ⁇ D1 ⁇ H is satisfied and the distance L1 from the upper end portion of the stator 14 to the inner wall surface of the upper portion of the hermetic case 7 is made larger than a total height H of the cylinder chambers 20a, 20b (H ⁇ L1).
  • the oil discharge quantity is denoted by a weight ratio to a circulation quantity of a gas refrigerant.
  • the flow velocity of the gas refrigerant in the discharge flow channel 15 of the electric motor 8 becomes large as the discharge volume of the gas refrigerant is increased by changing the total height "H" of the cylinder chambers 20a, 20b without changing the inner diameter of the cylinder chambers 20a, 20b.
  • Ad/Ac ⁇ 0.06 it becomes difficult to separate lubricating oil from the gas refrigerant in the discharge flow channel 15, and it is found that the oil discharge quantity increases rapidly in a case of Ad/Ac ⁇ 0.06, especially.
  • Fig. 4 shows an efficiency ratio of the 6-pole electric motor 8 to Ad/Ac.
  • Fig. 5 shows an efficiency ratio of the 6-pole electric motor 8 to T (a thickness of the stator core 14a)/H (a total height of the cylinder chambers 20a, 20b) when 0.85 ⁇ D1 ⁇ H ⁇ L1 (the relational expression 1) and 0.06 ⁇ Ad/Ac ⁇ 0.13 (the relational expression 2).are satisfied
  • Fig. 6 shows a relation between a ratio (T/H) of a thickness T of the stator core 14a of the stator 14 to a total height H of the cylinder chambers 20a, 20b and a ratio of a pressure loss Wd of a gas refrigerant at the discharge flow channel 15 of the electric motor 8 to a theoretical work Wth of the compressor.
  • T/H a ratio of a thickness T of the stator core 14a of the stator 14 to a total height H of the cylinder chambers 20a, 20b
  • Wd/Wth increases rapidly. From these, the pressure loss of the discharge flow channel 15 can be reduced while suppressing deterioration of the efficiency of the electric motor, under 1.2 ⁇ T/H ⁇ 1.5 (the relational expression 3).
  • the rotary compressors 2 which has a high pressure resistance, is small and light in weight, has a large discharge volume, has a high resource-saving property, and moreover has a small oil discharge quantity and is high reliability can be provided.
  • a sufficient quantity of the lubricating oil 12 can be reserved at the bottom of the hermetic case 7, by setting as Av/Ac>0.1 (the relational expression 4) and H ⁇ L2 (a distance from the lower end portion of the rotor 13 to an inner wall surface of a lower portion of the hermetic case 7)/2 (the relational expression 5). Even when the lubricating oil 12 is discharged, rapid fall of the oil surface of the lubricating oil 12 can be prevented and a more reliable rotary compressor 2 can be provided.
  • Fig. 7 shows a COP ratio under a rated conditions to D2/H which is a ratio of an inner diameter D2 of the main bearing 18 and the sub-bearing 19 and a total height H of the cylinder chambers 20a, 20b.
  • D2/H a distance between principal axes becomes large by enlarging H, the rigidity of the rotary shaft 10 becomes insufficient and bending of the rotary shaft 10 becomes excessive so that COP falls greatly.
EP17850474.2A 2016-09-14 2017-04-14 Compresseur rotatif et dispositif à cycle de réfrigération Pending EP3514391A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
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
PCT/JP2017/015299 WO2018051567A1 (fr) 2016-09-14 2017-04-14 Compresseur rotatif et dispositif à cycle de réfrigération

Publications (2)

Publication Number Publication Date
EP3514391A1 true EP3514391A1 (fr) 2019-07-24
EP3514391A4 EP3514391A4 (fr) 2020-01-22

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EP17850474.2A Pending EP3514391A4 (fr) 2016-09-14 2017-04-14 Compresseur rotatif et dispositif à cycle de réfrigération

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EP (1) EP3514391A4 (fr)
JP (1) JP6703921B2 (fr)
CN (1) CN109072917B (fr)
WO (1) WO2018051567A1 (fr)

Families Citing this family (4)

* 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 (fr) * 2019-08-23 2021-03-04 東芝キヤリア株式会社 Compresseur et dispositif à cycle de réfrigération
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
CN114598077A (zh) * 2022-01-26 2022-06-07 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

Family Cites Families (9)

* Cited by examiner, † Cited by third party
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
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
JP4864572B2 (ja) * 2006-07-03 2012-02-01 東芝キヤリア株式会社 回転式圧縮機及びこれを用いた冷凍サイクル装置
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
JP5564617B2 (ja) * 2011-06-08 2014-07-30 東芝キヤリア株式会社 密閉型圧縮機及び冷凍サイクル装置
JP5786030B2 (ja) * 2011-10-31 2015-09-30 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
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 (fr) * 2014-10-07 2016-04-14 三菱電機株式会社 Moteur électrique du type à aimants permanents encastrés, compresseur, et appareil de réfrigération et de climatisation

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Publication number Publication date
CN109072917B (zh) 2020-03-17
WO2018051567A1 (fr) 2018-03-22
JP2018044489A (ja) 2018-03-22
EP3514391A4 (fr) 2020-01-22
CN109072917A (zh) 2018-12-21
JP6703921B2 (ja) 2020-06-03

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