WO2020072154A1 - Procédé et système de refroidissement de moteur pendant le démarrage du moteur - Google Patents

Procédé et système de refroidissement de moteur pendant le démarrage du moteur

Info

Publication number
WO2020072154A1
WO2020072154A1 PCT/US2019/049019 US2019049019W WO2020072154A1 WO 2020072154 A1 WO2020072154 A1 WO 2020072154A1 US 2019049019 W US2019049019 W US 2019049019W WO 2020072154 A1 WO2020072154 A1 WO 2020072154A1
Authority
WO
WIPO (PCT)
Prior art keywords
liquid coolant
condenser
motor
compressor
reservoir
Prior art date
Application number
PCT/US2019/049019
Other languages
English (en)
Inventor
Jinliang Wang
Ahmad M. Mahmoud
Federick J. COGSWELL
Parmesh Verma
Original Assignee
Carrier Corporation
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 Carrier Corporation filed Critical Carrier Corporation
Priority to CN201980042609.6A priority Critical patent/CN112334718B/zh
Priority to US16/973,567 priority patent/US20210247107A1/en
Publication of WO2020072154A1 publication Critical patent/WO2020072154A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • F25B31/008—Cooling of compressor or motor by injecting a liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F25B31/026—Compressor arrangements of motor-compressor units with compressor of rotary type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/025—Motor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/16—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/23—Time delays
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication

Definitions

  • the present disclosure relates generally to compressor motor cooling and lubrication, and more specifically to compressor motor cooling and lubrication during a startup sequence.
  • HVAC heating, ventilation and cooling
  • GWP Global Warming Potential
  • High-efficiency compressors such as high speed centrifugal compressors
  • High speed motors require that the motor bearings be cooled and lubricated via a cooling system in order to keep the motor system below a limitation temperature and prevent the bearings from overheating.
  • Traditional air cooling of such systems can be inadequate for a high speed motor, and independent oil based liquid cooling leads to complex systems and increases costs.
  • a heating ventilation and air conditioning (HVAC) system includes a compressor comprising a low pressure input and a high pressure output, the compressor driven by a motor, the motor including a liquid coolant flowpath configured to cool and lubricate the motor and having a liquid coolant input and a liquid coolant output, an evaporator in fluid communication with the compressor, the evaporator including a liquid coolant input, and a vapor coolant output, the vapor coolant output being connected to the low pressure input of the compressor, a condenser in fluid communication with the evaporator and the compressor, the condenser including a vapor cooling input and a liquid coolant output, the vapor cooling input being connected to a high pressure output of the compressor, a first liquid coolant flowpath, including a liquid coolant drive system connecting the liquid coolant output of the condenser to the input of a valve switching device, a second liquid coolant flowpath connecting the liquid coolant output of the condenser to the liquid input of
  • the liquid coolant drive system comprises an electric pump.
  • HVAC heating ventilation and air conditioning
  • HVAC heating ventilation and air conditioning
  • HVAC heating ventilation and air conditioning
  • HVAC heating ventilation and air conditioning
  • the controller is configured to activate the electric pump at least five seconds prior to activating the motor.
  • the liquid coolant drive system comprises a liquid coolant reservoir.
  • the liquid coolant reservoir is disposed above the motor, relative to a force of gravity, such that a liquid coolant is gravity fed from the reservoir to the motor when the valve switching device is in a first state.
  • the liquid coolant reservoir includes an electric heater disposed within the liquid coolant reservoir.
  • HVAC heating ventilation and air conditioning
  • HVAC heating ventilation and air conditioning
  • the second liquid coolant flowpath includes an expansion device connecting the liquid coolant output of the condenser to the liquid input of the evaporator.
  • the first liquid coolant flowpath includes a check valve connecting the liquid coolant output of the condenser to the liquid coolant drive system.
  • An exemplary method for operating a heating ventilation and air conditioning (HVAC) system includes driving a liquid coolant from a condenser to a compressor motor during a startup sequence of the compressor motor using a liquid coolant drive system, thereby cooling and lubricating the compressor motor, and drawing liquid coolant from the condenser to the compressor motor using a pressure differential between the condenser and an evaporator once the startup sequence has completed.
  • HVAC heating ventilation and air conditioning
  • HVAC heating ventilation and air conditioning
  • HVAC heating ventilation and air conditioning
  • HVAC heating ventilation and air conditioning
  • HVAC heating ventilation and air conditioning
  • Figure 1 illustrates a high level schematic view compressor motor cooling system for a high speed motor for a heating, ventilation and air condition (HVAC) system.
  • HVAC heating, ventilation and air condition
  • Figure 2 schematically illustrates a variation of the configuration of Figure 1.
  • Figure 3A schematically illustrates a second variation on the configuration of Figure 1.
  • Figure 3B schematically illustrates a variation on the configuration of Figure 3A.
  • Figure 4 schematically illustrates a third variation on the configuration of Figure
  • FIG. 1 schematically illustrates a vapor compression system with a compressor motor cooling subsystem 10 for a compressor 20 driven by a high speed motor 22 for HVAC applications.
  • the high speed motor 20 is a motor for a mini centrifugal compressor.
  • the system includes a condenser 30, an evaporator 40, and an expansion device 11 in fluid communication with the compressor 20.
  • a pressure rise generated by the compressor 20 provides liquid coolant from the condenser 30 to the motor 22 along a fluid flowpath 50 during full speed operations of the compressor 20.
  • the liquid coolant cools and lubricates the motor 22, and is then provided to the evaporator 40 via the flowpath 58. Once in the evaporator 40, the coolant is evaporated, and provided to the compressor 20 in a vapor form along a vapor flowpath 60.
  • the vapor flowpath 60 provides the evaporated coolant from the compressor to the condenser 30.
  • the pressure buildup due to the operation of the compressor 20 is sufficient to drive the liquid coolant through the motor 20 and provide the cooling and lubricating effects.
  • a liquid coolant driving system 70 provides supplemental pressure to drive the liquid coolant through the motor 20.
  • the liquid coolant driving system 70 can include multiple variations configured to generate the requisite compressor rise. Figures 2-4 describe exemplary embodiments of the liquid coolant driving system.
  • the flowpath 50 includes a first leg 52 that provides coolant from the condenser 30 to an input of a three-way valve 80.
  • the first leg 52 includes the liquid coolant driving system 70.
  • the three-way valve 80 can be replaced with any other type of valve or regulator capable of regulating flow or flow switching between two input flow sources.
  • a second leg 54 that connects the condenser 30 directly to the three-way valve 80, or other flow switching device, to an expansion device 11, and to a liquid coolant input of the evaporator 40.
  • a“valve switching device” generically refers to any flow switching device capable of switching a connection of an output between at least two inputs.
  • a third leg 56 connects an output of the three-way valve 80 to a liquid coolant input of the motor 22, and a fourth leg 58 connects an output of the motor 22 to the output of the expansion device 11 in the second leg 54. After merging the coolant flows into the evaporator 40.
  • the three-way valve 80 is set to receive liquid coolant from the condenser 30 via the liquid coolant driving system 70.
  • the liquid coolant driving system 70 drives liquid coolant from the condenser 30 (via the first leg 52) to the motor 22, through the three way valve 80 and the expansion device 11, as the motor 22 begins operating thereby lubricating and cooling the motor 22.
  • the three way valve 80 switches to receiving the liquid coolant from the second leg 54, and the liquid coolant driving system 70 is switched off. In this way, coolant is actively provided to the motor 22 directly from the condenser 30 through the second leg 54, the three way valve 80 and the third leg 56. Once provided to the evaporator 40, the liquid coolant evaporates and absorbs heat from another fluid that flows through the evaporator 40.
  • the controller 90 can be a dedicated cooling system controller, a motor controller, or any other controller capable of storing and implementing the control sequences described herein.
  • the liquid coolant can be any suitable low global warming potential refrigerant.
  • FIG. 2 schematically illustrates an HVAC system 100, according to the example of Figure 1, with the inclusion of a heat driven liquid coolant driving system 170.
  • the heat driven liquid coolant driving system 170 is connected to an outlet of the condenser 130 via a check valve 172 positioned in a first leg 152 of a liquid coolant flowpath 150.
  • the heat driven liquid coolant driving system 170 includes a reservoir 174, where liquid coolant is pooled.
  • the reservoir 174 refers to any component capable of storing liquid refrigerant, and can include oversized lines, a fluid tank, a portion of the condenser, etc.
  • an electric heater 176 i.e. a device that generates heat using electricity
  • the electric heater 176 raises the temperature of the liquid coolant within the reservoir 174 when activated.
  • Alternative heat sources beyond those using electricity to generate heat can be utilized to the same effect with minor modifications to the described system. Raising the temperature in the reservoir 174 increases the pressure in the reservoir 174, and the increased pressure drives liquid coolant along the second leg 152 of the liquid coolant flowpath when a three way valve 180 connects the first leg 152 of the liquid coolant flow from the reservoir 174 to the third leg 156 of the liquid coolant flowpath.
  • the electric heater 176 is activated prior to the activation of the motor 122. In some examples, this can include activation as many as 5 or 10 minutes prior to motor 122 activation and is governed by controller 90. The specific length of time by which the activation of the electric heater 176 must precede the activation of the motor 122 is determined by multiple factors including, but not limited to, the volume of coolant, the type of refrigerant, etc. Alternatively, activation of the motor is controlled by the pressure difference between the reservoir 174 and the evaporator 140.
  • FIGs 3A and 3B illustrate an HVAC system 200 utilizing an electric pump 272 as the liquid coolant driver.
  • other means to drive the liquid coolant e.g. electrohydrodynamics, etc.
  • the HVAC system 200 is substantially identical to the systems described with regards to Figures 1 and 2, with the exception of the electric pump 272 being utilized to drive the liquid coolant in place of the heat driven liquid coolant driving system 170 of Figure 2.
  • the electric pump 272 can be included inside the base of the condenser 230, as shown in the example of Figure 3A, or can be outside of the condenser 230 within the first liquid coolant flowpath 252.
  • the electric pump 272 receives electrical power via a connection to an external power source, such as a building electrical grid, or from an electrical connection to the HVAC system, and is activated by the controller configured to control the motor 220.
  • the electric pump 272 can be any conventional electric pump having sufficient size and power to drive the liquid coolant.
  • the pump driven system of Figures 3 A or 3B requires a minimal amount of lead up time after being activated and before the motor 22 can begin startup operations.
  • the lead-up time can be less than ten seconds. In some such examples, the lead-up time can be five seconds.
  • Figure 4 illustrates an HVAC system 300 having third variation on the liquid coolant driving system 70 of Figure 1.
  • the liquid coolant driving system of Figure 4 utilizes a gravity fed reservoir 374 positioned physically above the motor, relative to a force of gravity, the reservoir is filled with liquid coolant from the condenser 330.
  • the reservoir 374 is connected to an outlet of the condenser 330 via a check valve 372 positioned in a first leg 352 of a liquid coolant loop 350.
  • a check valve 372 positioned in a first leg 352 of a liquid coolant loop 350.
  • the gravity fed coolant system of Figure 4 carries with it additional packaging restrictions, and the physical structure of the motor 322 is constructed to support the weight of the liquid coolant reservoir.

Abstract

L'invention concerne un système CVC comprenant un compresseur comportant une entrée à basse pression et une sortie à haute pression. Le compresseur est entraîné par un moteur comportant un circuit d'écoulement d'agent de refroidissement liquide, conçu pour refroidir et lubrifier le moteur. Le moteur comporte une entrée d'agent de refroidissement et une sortie d'agent de refroidissement. Un évaporateur est en communication avec le compresseur, et comprend une entrée d'agent de refroidissement et une sortie d'agent de refroidissement. Un condenseur est en communication fluidique avec l'évaporateur et avec le compresseur. Un premier circuit d'écoulement d'agent de refroidissement comprend un système d'entraînement d'agent de refroidissement reliant la sortie du condenseur à un dispositif de commutation de soupape. Un deuxième circuit d'écoulement d'agent de refroidissement relie la sortie du condenseur à l'entrée de l'évaporateur et à une seconde entrée du dispositif de commutation de soupape. Un troisième circuit d'écoulement d'agent de refroidissement relie le dispositif de commutation de soupape aux entrées du moteur. Un quatrième circuit d'écoulement d'agent de refroidissement relie les sorties du moteur à l'entrée de l'évaporateur.
PCT/US2019/049019 2018-10-03 2019-08-30 Procédé et système de refroidissement de moteur pendant le démarrage du moteur WO2020072154A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201980042609.6A CN112334718B (zh) 2018-10-03 2019-08-30 用于在马达起动期间冷却马达的方法和系统
US16/973,567 US20210247107A1 (en) 2018-10-03 2019-08-30 Method and system for cooling a motor during motor startup

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201862740476P 2018-10-03 2018-10-03
US62/740,476 2018-10-03

Publications (1)

Publication Number Publication Date
WO2020072154A1 true WO2020072154A1 (fr) 2020-04-09

Family

ID=67957411

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2019/049019 WO2020072154A1 (fr) 2018-10-03 2019-08-30 Procédé et système de refroidissement de moteur pendant le démarrage du moteur

Country Status (3)

Country Link
US (1) US20210247107A1 (fr)
CN (1) CN112334718B (fr)
WO (1) WO2020072154A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2891391A (en) * 1957-08-26 1959-06-23 Vilter Mfg Co Refrigerated hermetically sealed motors
US20140216102A1 (en) * 2013-02-05 2014-08-07 Emerson Climate Technologies, Inc. Compressor cooling system
WO2014179032A1 (fr) * 2013-05-02 2014-11-06 Carrier Corporation Refroidissement d'un palier de compresseur par l'intermédiaire d'une unité de purge

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3443443B2 (ja) * 1993-12-24 2003-09-02 株式会社神戸製鋼所 スクリュ式冷凍機
EP0730128B1 (fr) * 1995-02-06 1999-06-23 Carrier Corporation ContrÔle en logique floue de l'injection du liquide pour le refroidissement d'un moteur
JP2003159933A (ja) * 2001-11-26 2003-06-03 Sanyo Electric Co Ltd カーエアコン用圧縮機の冷却手段
WO2009088846A1 (fr) * 2007-12-31 2009-07-16 Johnson Controls Technology Company Procédé et système de refroidissement de rotor
WO2013039572A1 (fr) * 2011-09-16 2013-03-21 Danfoss Turbocor Compressors B.V. Circuits de refroidissement et de sous-refroidissement de moteur pour compresseur
TWI577949B (zh) * 2013-02-21 2017-04-11 強生控制科技公司 潤滑及冷卻系統
CN204345959U (zh) * 2014-12-15 2015-05-20 珠海格力电器股份有限公司 空调器

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2891391A (en) * 1957-08-26 1959-06-23 Vilter Mfg Co Refrigerated hermetically sealed motors
US20140216102A1 (en) * 2013-02-05 2014-08-07 Emerson Climate Technologies, Inc. Compressor cooling system
WO2014179032A1 (fr) * 2013-05-02 2014-11-06 Carrier Corporation Refroidissement d'un palier de compresseur par l'intermédiaire d'une unité de purge

Also Published As

Publication number Publication date
CN112334718B (zh) 2023-10-31
CN112334718A (zh) 2021-02-05
US20210247107A1 (en) 2021-08-12

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