WO2013146674A1 - Dispositif de compression à deux étages - Google Patents

Dispositif de compression à deux étages Download PDF

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Publication number
WO2013146674A1
WO2013146674A1 PCT/JP2013/058563 JP2013058563W WO2013146674A1 WO 2013146674 A1 WO2013146674 A1 WO 2013146674A1 JP 2013058563 W JP2013058563 W JP 2013058563W WO 2013146674 A1 WO2013146674 A1 WO 2013146674A1
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WO
WIPO (PCT)
Prior art keywords
stage compression
flow path
stage
compression section
volume
Prior art date
Application number
PCT/JP2013/058563
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English (en)
Japanese (ja)
Inventor
吉村　省二
大祐 和田
Original Assignee
株式会社神戸製鋼所
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Filing date
Publication date
Application filed by 株式会社神戸製鋼所 filed Critical 株式会社神戸製鋼所
Publication of WO2013146674A1 publication Critical patent/WO2013146674A1/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
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/02—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for several pumps connected in series or in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/21—Pressure difference

Definitions

  • the present invention relates to a two-stage compression apparatus.
  • a pair of male and female screw rotors that mesh with each other is accommodated in a rotor chamber formed in the casing, and the space in the rotor chamber is divided by the screw rotor, and the volume decreases as the screw rotor rotates.
  • a screw compressor that forms a compression space, sucks gas from the suction flow path into the compression space, compresses the gas, and discharges the gas into the discharge flow path is widely used.
  • Such a screw compressor has a gas back flow from the discharge flow path to the compression space or a gas in the discharge flow path when the pressure of the compression space at the moment of being connected to the discharge flow path is different from the pressure of the discharge flow path. Negative work such as expansion of the water occurs and efficiency decreases.
  • the pressure of the compression space at the moment of being connected to the discharge flow path is the pressure of the compression space at the moment of being isolated from the suction flow path, that is, the pressure of the compression space at the moment of being isolated from the suction flow path to the pressure of the suction flow path. It is determined by the volume ratio that is the ratio of the volume and the volume of the compression space at the moment connected to the discharge flow path.
  • the ratio between the pressure in the compression space at the moment isolated from the suction flow path and the pressure in the compression space at the moment connected to the discharge flow path is called the internal compression ratio
  • the volume ratio of the screw compressor is changed according to the pressure of the suction flow path and the pressure of the discharge flow path, and the internal compression ratio is changed.
  • a mechanism such as a slide valve has been proposed for bringing the valve closer to the external compression ratio.
  • a two-stage compression device in which two screw compressors are connected in series via an intermediate flow path is also used. Even in such a two-stage compressor, it is desirable to improve the efficiency by adjusting the internal compression ratio according to the external compression ratio.
  • Adjusting the internal compression ratio of the stage-side compressor changes the pressure in the intermediate flow path, so the external compression ratio of the high-stage compressor also changes, and the internal compression ratio required for the high-stage compressor Will change. That is, when two screw compressors of Patent Document 1 are connected in series, the adjustment of the internal compression ratio of the two screw compressors interferes with each other, so that control is difficult.
  • an object of the present invention is to provide a two-stage compression device that can adjust the internal compression ratio according to the external compression ratio.
  • a two-stage compression apparatus compresses the gas sucked from the suction flow path and discharges it to the intermediate flow path, and compresses the gas sucked from the intermediate flow path.
  • a pair of male and female screw rotors that engage with each other in a rotor chamber formed in the casing. And forming a compression space in the rotor chamber that is separated from each other by the screw rotor and decreases in volume as the screw rotor rotates, and is one shaft of the screw rotor of the low-stage compression unit.
  • the high-stage compression section is a suction volume that is an instantaneous volume isolated from the intermediate flow path of the compression space and the discharge flow.
  • the volume ratio which is the ratio of the discharge volume, which is the instantaneous volume connected to the, is adjusted according to the ratio of the pressure of the intermediate flow path and the pressure of the discharge flow path by changing the discharge volume It is assumed that capacity adjusting means is provided.
  • the internal compression ratio of the low-stage compression unit is fixed and only the internal compression ratio of the high-stage compression unit is changed, so that control is easy and internal compression of the entire two-stage compression device High efficiency can be obtained by matching the ratio to the external compression ratio.
  • the pressure in the discharge flow path of the low-stage compression section may be calculated from the pressure in the suction flow path.
  • the capacity adjusting means forms a part of the wall surface of the rotor chamber of the high-stage compression section, and advances and retreats in the axial direction of the screw rotor. It may be a slide valve that can change the opening position with respect to the discharge flow path.
  • the capacity adjusting means may be a bypass mechanism that opens a part of the wall surface of the rotor chamber of the high-stage compression section and communicates with the discharge flow path.
  • the efficiency can be improved by selecting two internal compression ratios while the configuration is simple and inexpensive.
  • the screw rotors of the low-stage compression section and the high-stage compression section may be driven by a motor capable of controlling the rotation speed.
  • the discharge flow rate can be adjusted by controlling the rotation speed while substantially maintaining the internal compression ratio of the entire stage compression apparatus, it is possible to prevent pressure fluctuations in the suction flow path and the discharge flow path.
  • FIG. 1 shows a configuration of a two-stage compression apparatus 1 according to the first embodiment of the present invention.
  • the two-stage compression apparatus 1 includes a low-stage compression section 7 and a high-stage compression section 8 that house a pair of male and female screw rotors 5 and 6 that mesh with each other in rotor chambers 3 and 4 formed in a casing 2.
  • the shaft of one screw rotor 5 of the low-stage compression unit 7 is integrally connected to the shaft of one screw rotor 6 of the high-stage compression unit 8.
  • the low-stage compression section 7 and the high-stage compression section 8 divide the rotor chambers 3 and 4 by the screw rotors 5 and 6 to form a plurality of compression spaces isolated from each other.
  • the low-stage compression unit 7 sucks gas from the suction flow path 9 formed in the casing 2 in the compression space, compresses the gas by reducing the volume of the compression space with the rotation of the screw rotor 5, and The compressed gas is discharged into the formed intermediate flow path 10.
  • the high stage compression unit 8 sucks the gas from the intermediate flow path 10 into the compression space, compresses the gas by the rotation of the screw rotor 6, and discharges the gas to the discharge flow path 11 formed in the casing 2.
  • the screw rotors 5 and 6 are driven by a motor 13 that can adjust the rotation speed when electric power is supplied from the inverter 12.
  • the high-stage compression unit 8 includes a slide valve 14 that constitutes a part of the inner wall of the rotor chamber 4 and is movable in the axial direction of the screw rotor 6.
  • the slide valve 14 is driven by a hydraulic cylinder 15 and adjusts the position where the compression space of the high stage compression unit 8 communicates with the discharge flow path 11. That is, the slide valve 14 is a capacity adjusting means that can adjust the instantaneous volume when the compression space of the high-stage compression unit 8 is connected to the discharge flow path 11.
  • the two-stage compression device 1 has a hydraulic circuit 16 for driving the hydraulic cylinder 15.
  • the hydraulic circuit 16 includes a four-way switching control valve 18 and a four-way switching control valve for switching the flow path so that pressure oil is supplied to the space before and after the piston 17 of the hydraulic cylinder 15 or oil is discharged from either space.
  • two solenoid valves 19 and 20 for switching between supply and exhaust of compressed air for driving 18.
  • the two-stage compressor 1 includes a suction pressure detector 21 that detects a suction pressure Ps that is a pressure in the suction flow path 9, and a discharge pressure detector 22 that detects a discharge pressure Pd that is a pressure in the discharge flow path 11. And a positioner 23 for detecting the position of the piston 17 of the hydraulic cylinder 15. Further, the two-stage compressor 1 includes an intermediate pressure calculation unit 24 that calculates an intermediate pressure Pm that is a pressure in the intermediate flow path 10 based on the suction pressure Ps detected by the suction pressure detector 21, and an intermediate pressure calculation unit 24.
  • a target position of the slide valve 14 that is, a valve target position calculator 25 for calculating the position of the piston 17 to be detected by the positioner 23;
  • the valve position control unit 26 controls the electromagnetic valves 19 and 20 of the hydraulic circuit 16 so that the detected value of the positioner 23 approaches the position calculated by the valve target position calculation unit 25.
  • the stroke volume of the low-stage compression section 7 is Vt1
  • the stroke volume of the high-stage compression section 8 is Vt2
  • the volume efficiency of the low-stage compression section 7 is ⁇ 1
  • the volume efficiency of the high-stage compression section 8 is ⁇ 2
  • the gas in the suction passage 9 The suction temperature that is the temperature of the gas is Ts
  • the intermediate temperature that is the gas temperature in the intermediate flow path 8 is Tm.
  • the stroke volumes Vt1 and Vt2 depend on the shape and size of the screw rotors 5 and 6 and are proportional to the number of rotations of the motor 13, so (Vt1 / Vt2) is constant.
  • the volumetric efficiency ⁇ 1, ⁇ 2, the suction temperature Ts, and the intermediate temperature Tm may vary depending on external factors, but hardly change depending on the operation parameters of the two-stage compressor 1 itself. Therefore, the intermediate pressure Pm can be calculated based on the coefficient determined by the shape of the screw rotors 5 and 6 and the suction pressure Ps detected by the suction pressure detector 21 regardless of the discharge pressure Pd.
  • the suction volume that is the instantaneous volume isolated from the suction flow path 9 in the compression space of the low-stage compression unit 7 is Vs1
  • the discharge volume that is the instantaneous volume connected to the intermediate flow path 10 is Vd1
  • the low-stage compression When the volume ratio, which is the ratio between the suction volume Vs1 of the part 7 and the discharge volume Vd1, is Vi1
  • the low stage internal pressure Pd1 is the instantaneous pressure connected to the intermediate flow path 10 in the compression space of the low stage compression part 7,
  • the suction volume that is the instantaneous volume isolated from the middle of the compression space of the high-stage compression unit 8 is Vs2
  • the discharge volume that is the instantaneous volume connected to the discharge flow path 11 is Vd2
  • the discharge volume Vd2 of the high stage compression unit 8 to be set by the slide valve 14 can be calculated and detected by the positioner 23 in order to achieve this target volume ratio Via.
  • the position of the power piston 17 can be determined.
  • the valve position control unit 26 controls the hydraulic circuit 16 so that the volume ratio Vi2 of the high-stage compression unit 8 approaches the target value Via.
  • the discharge volume Vd ⁇ b> 2 of the high stage compression unit 8 changes in proportion to the position of the slide valve 14.
  • the volume ratio Vi2 of the high stage compression unit 8 is proportional to the position of the piston 15 detected by the positioner 21 because the suction volume Vs2 of the high stage compression unit 8 is constant. Therefore, when the volume ratio Vi2 calculated from the detection value of the positioner 21 is larger than the target value Via by a predetermined allowable deviation ⁇ , for example, greater than 0.1 (Vi2 ⁇ Via> ⁇ ).
  • the hydraulic cylinder 15 is extended to increase the opening of the slide valve 14 and to reduce the volume ratio Vi2.
  • the valve position control unit 26 reverses the solenoid valve 19. Is set to the compressed air supply position, and the electromagnetic valve 20 is set to the exhaust position, thereby shortening the hydraulic cylinder 15 and reducing the opening of the slide valve 14.
  • the two-stage compression device 1 adjusts the volume ratio Vi2 of the high-stage compression section 8 by changing the discharge capacity Vd2 of the high-stage compression section 8, thereby adjusting the internal compression ratio of the high-stage compression section 8.
  • the external compression ratio (Pd / Pm) of the high-stage compression unit 8 is substantially matched. That is, since the internal compression ratio of the entire two-stage compression device 1 is adjusted to the external compression ratio (Ps / Pd) of the entire two-stage compression device 1 by adjusting the volume ratio Vi2 of the high-stage compression unit 8, power loss is reduced. Less efficient.
  • the two-stage compressor 1 is driven by the motor 13 whose frequency is controlled by the inverter 12, the internal compression ratio of the low-stage compressor 7 and the high-stage compressor 8 is substantially maintained while meeting the demand.
  • the discharge amount of the compressed gas can be adjusted. For this reason, the pressure fluctuation of the suction flow path 9 and the discharge flow path 11 can be prevented.
  • FIG. 2 shows a two-stage compressor 1a which is a second embodiment of the present invention.
  • the same components as those in the first embodiment are denoted by the same reference numerals, and redundant description is omitted.
  • the slide valve 14a is arranged at one of two positions on the suction side and the discharge side in the axial direction of the screw rotor 6 by a spring return type hydraulic cylinder 15a.
  • the slide valve 14 a has a communication hole 27, and moves to the discharge side to open a part of the outer wall of the rotor chamber 4 and communicate with the discharge flow path 11 through the communication hole 27. That is, the slide valve 14a is a capacity adjusting means that changes the volume ratio Vi2 of the high stage compression unit 8 in two stages.
  • the hydraulic circuit 16a is a simple one having only one solenoid valve 28 that can be switched between an oil supply position for supplying pressure oil to the hydraulic cylinder 15a and an oil discharge position for discharging oil from the hydraulic cylinder 15a. is there.
  • the two-stage compression apparatus 1a has an intermediate pressure detector 29 that directly detects the intermediate pressure Pm in the intermediate flow path 10. Therefore, the intermediate pressure detector 29 directly determines the position of the slide valve 14a from the detection value Pm and the detection value Pd of the discharge pressure detector 22, and the electromagnetic valve 28 of the hydraulic circuit 16 is set to the position of the slide valve 14a. It has a valve position determination unit 30 that switches to a corresponding oil supply position or oil discharge position.
  • FIG. 3 shows a change in the heat insulation efficiency with respect to the external compression ratio depending on the position of the slide valve 14a.
  • the capacity adjusting means can change the volume ratio Vi2 of the high-stage compression unit 8 in addition to the slide valve 14a having the slide valve 14 of the first embodiment and the communication hole 27 of the second embodiment. Anything may be used.
  • a valve mechanism such as a piston valve that can provide an opening in the axial end surface of the rotor chamber 4 and allow the opening to communicate with the discharge flow path 11 may be employed as the capacity adjusting means.
  • the intermediate pressure Pm may be detected by an intermediate pressure detector instead of being calculated from the suction pressure Ps.
  • the intermediate pressure Pm may be calculated from the suction pressure Ps instead of being detected by the intermediate pressure detector.

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

Abstract

L'invention porte sur un dispositif de compression à deux étages, qui peut régler un rapport de compression interne en fonction d'un rapport de compression externe. Un dispositif de compression à deux étages (1) a une unité de compression d'étage inférieur (7) et une unité de compression d'étage supérieur (8) et est conçu de telle sorte que l'arbre de l'un des rotors en forme de vis (5, 6) de l'unité de compression d'étage inférieur (7) et de l'unité de compression d'étage supérieur (8) y est relié. Un moyen de réglage de capacité (14) comporte l'unité de compression d'étage supérieur (8), et le rapport de volume, qui est le rapport entre un volume d'aspiration au moment où un espace de compression est isolé d'un passage d'écoulement intermédiaire (10) et un volume de refoulement au moment où l'espace de compression est relié à un passage d'écoulement de refoulement (11), est modifié en fonction du rapport entre la pression dans le passage d'écoulement intermédiaire (10) et la pression dans le passage d'écoulement de refoulement (11) par modification du volume de refoulement.
PCT/JP2013/058563 2012-03-30 2013-03-25 Dispositif de compression à deux étages WO2013146674A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012081312A JP2013209953A (ja) 2012-03-30 2012-03-30 ２段圧縮装置
JP2012-081312 2012-03-30

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2018017607A1 (fr) * 2016-07-18 2018-01-25 Johnson Controls Technology Company Compresseur de rapport de volumétrique variable
CN107917077A (zh) * 2017-12-21 2018-04-17 珠海格力电器股份有限公司 压缩机及控制方法、空气调节设备
CN110617218A (zh) * 2019-09-11 2019-12-27 珠海格力电器股份有限公司 双级压缩机及双级压缩机的控制方法及空调机组
CN110701047A (zh) * 2018-07-10 2020-01-17 日立江森自控空调有限公司 两级螺杆流体机械
EP3623629A1 (fr) * 2018-09-12 2020-03-18 Fu Sheng Industrial Co., Ltd. Machine à fluide
EP3786453A1 (fr) * 2019-09-02 2021-03-03 Allan McDiarmid Appareil et procédé
CN114087190A (zh) * 2021-11-12 2022-02-25 浙江科维节能技术股份有限公司 一种螺杆压缩机滑阀控制方法
US20220268280A1 (en) * 2019-09-11 2022-08-25 Gree Electric Appliances, Inc. Of Zhuhai Dual-Stage Compressor, Control Method Thereof and Air Conditioning Unit

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6342821B2 (ja) * 2015-01-14 2018-06-13 日立ジョンソンコントロールズ空調株式会社 スクリュー流体機械
TWI666387B (zh) * 2017-10-17 2019-07-21 復盛股份有限公司 壓縮機
TWI681125B (zh) * 2018-10-12 2020-01-01 復盛股份有限公司 螺旋式壓縮機及其排氣容積比的估算方法
EP3933204A4 (fr) * 2019-03-01 2022-03-09 Mitsubishi Electric Corporation Compresseur à vis

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JPS62121884A (ja) * 1985-11-19 1987-06-03 Kobe Steel Ltd スライド弁式スクリユ圧縮機
JPS63130687U (fr) * 1987-02-18 1988-08-26
JPH01134791U (fr) * 1988-03-08 1989-09-14
JPH03185293A (ja) * 1989-12-15 1991-08-13 Hitachi Ltd スクリュー等回転容積機械
JP2007138919A (ja) * 2005-10-17 2007-06-07 Kobe Steel Ltd ２段スクリュ圧縮機及びそれを用いた２段圧縮冷凍機

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JPS626490U (fr) * 1985-06-26 1987-01-16
JPS62121884A (ja) * 1985-11-19 1987-06-03 Kobe Steel Ltd スライド弁式スクリユ圧縮機
JPS63130687U (fr) * 1987-02-18 1988-08-26
JPH01134791U (fr) * 1988-03-08 1989-09-14
JPH03185293A (ja) * 1989-12-15 1991-08-13 Hitachi Ltd スクリュー等回転容積機械
JP2007138919A (ja) * 2005-10-17 2007-06-07 Kobe Steel Ltd ２段スクリュ圧縮機及びそれを用いた２段圧縮冷凍機

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10677246B2 (en) 2016-07-18 2020-06-09 Johnson Controls Technology Company Variable volume ratio compressor
WO2018017607A1 (fr) * 2016-07-18 2018-01-25 Johnson Controls Technology Company Compresseur de rapport de volumétrique variable
CN107917077A (zh) * 2017-12-21 2018-04-17 珠海格力电器股份有限公司 压缩机及控制方法、空气调节设备
CN110701047B (zh) * 2018-07-10 2021-06-22 日立江森自控空调有限公司 两级螺杆流体机械
CN110701047A (zh) * 2018-07-10 2020-01-17 日立江森自控空调有限公司 两级螺杆流体机械
US11255327B2 (en) 2018-09-12 2022-02-22 Fu Sheng Industrial Co., Ltd Two-stage screw rotor machine with slide valves
EP3623629A1 (fr) * 2018-09-12 2020-03-18 Fu Sheng Industrial Co., Ltd. Machine à fluide
EP3786453A1 (fr) * 2019-09-02 2021-03-03 Allan McDiarmid Appareil et procédé
CN110617218A (zh) * 2019-09-11 2019-12-27 珠海格力电器股份有限公司 双级压缩机及双级压缩机的控制方法及空调机组
US20220268280A1 (en) * 2019-09-11 2022-08-25 Gree Electric Appliances, Inc. Of Zhuhai Dual-Stage Compressor, Control Method Thereof and Air Conditioning Unit
CN110617218B (zh) * 2019-09-11 2023-12-22 珠海格力电器股份有限公司 双级压缩机的控制方法及空调机组
CN114087190A (zh) * 2021-11-12 2022-02-25 浙江科维节能技术股份有限公司 一种螺杆压缩机滑阀控制方法
CN114087190B (zh) * 2021-11-12 2022-10-04 浙江科维节能技术股份有限公司 一种螺杆压缩机滑阀控制方法

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