EP3887733A1 - Procédé et appareil de démarrage séquencé d'un système de réfrigération à l'ammoniac conditionné à basse charge refroidie par air - Google Patents

Procédé et appareil de démarrage séquencé d'un système de réfrigération à l'ammoniac conditionné à basse charge refroidie par air

Info

Publication number
EP3887733A1
EP3887733A1 EP19888679.8A EP19888679A EP3887733A1 EP 3887733 A1 EP3887733 A1 EP 3887733A1 EP 19888679 A EP19888679 A EP 19888679A EP 3887733 A1 EP3887733 A1 EP 3887733A1
Authority
EP
European Patent Office
Prior art keywords
condenser
refrigerant
compressor
refrigeration system
vapor
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.)
Granted
Application number
EP19888679.8A
Other languages
German (de)
English (en)
Other versions
EP3887733B1 (fr
EP3887733A4 (fr
Inventor
Jake William DENISON
Donald Lee HAMILTON
Samuel K VINEYARD
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.)
Evapco Inc
Original Assignee
Evapco Inc
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 Evapco Inc filed Critical Evapco Inc
Priority claimed from PCT/US2019/063621 external-priority patent/WO2020113011A1/fr
Publication of EP3887733A1 publication Critical patent/EP3887733A1/fr
Publication of EP3887733A4 publication Critical patent/EP3887733A4/fr
Application granted granted Critical
Publication of EP3887733B1 publication Critical patent/EP3887733B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from 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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line 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
    • F25B49/027—Condenser 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0401—Refrigeration circuit bypassing means for the compressor
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/027—Compressor control by controlling pressure
    • F25B2600/0271—Compressor control by controlling pressure the discharge pressure
    • 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
    • F25B2600/25—Control of valves
    • F25B2600/2519—On-off 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/02—Compression machines, plants or systems, with several condenser circuits arranged in parallel

Definitions

  • the present invention relates to ammonia refrigeration systems.
  • Chlorofluorocarbon refrigerant (CFC, HFC, HCFC) systems have utilized isolating valves on the outlet of condenser coils, which force liquid to back up in the condenser, reducing the surface area of the coil that is capable of condensing vapor.
  • CFC, HFC, HCFC Chlorofluorocarbon refrigerant
  • the present invention overcomes the problems of the prior art by allowing the condenser coils to isolate individually during the startup period, allowing individual sequencing of the coils until the condenser is warm enough to maintain discharge and oil pressure. This invention also eliminates the need for a stand-alone oil pump to maintain oil pressure during start-up.
  • Motorized valves can be installed on all or one of the condenser coil inlets, a main compressor discharge motorized valve is installed, a bypass pressure regulator valve in the main compressor piping is installed, check valves on the condenser outlets are installed and speed control of the condenser fans.
  • the condenser inlet motorized valves provide precise control of gas feed or act as an on/off valve for the condensers allowing pressure to build without collapsing the oil pressure.
  • the motorized valves provide precise control of the gas flow at a very low pressure drop or provide on/off control as needed.
  • the air-cooled condensers may be any style: tube and fin or microchannel, etc. in horizontal or vertical tube arrangements.
  • the condenser coil outlet contains vertically- oriented inline check valves to prevent liquid backflow when a coil is isolated. This allows each condenser coil to be isolated without trapping significant liquid refrigerant charge in a low-charge ammonia, refrigeration system.
  • the compressor discharge line contains a single motorized valve for regulating discharge pressure.
  • the motorized valve is used for coarse gas control at start-up.
  • the motorized valve in the compressor discharge piping also includes a bypass with a mechanical pressure regulator to allow precise regulation at the minimum discharge pressure. Once discharge pressure rises above the minimum setpoint, the condenser inlet solenoid coils will open one at a time.
  • the discharge pressure regulating motorized valve will simultaneously regulate the discharge pressure until the condenser coil has warmed up enough to maintain discharge pressure. Fan speed control is also utilized to maintain stable operation at start-up.
  • Figure l is a schematic of a refrigeration system according to a single compressor embodiment of the invention.
  • Figure 2 is a blow-up of the upper right hand portion of Figure 1.
  • Figure 3 is a schematic of a refrigeration system according to a dual compressor embodiment of the invention.
  • Figure 4 is a blow-up of the upper right hand portion of Figure 3.
  • Figure l is a process and instrumentation diagram for a single compressor, air cooled (non-evaporative) condenser, low charge packaged penthouse refrigeration system according to an embodiment of the invention.
  • a blow-up of the upper right quadrant of Figure 1 is presented in Figure 2.
  • Figure 3 is a process and instrumentation diagram for a dual compressor, air-cooled condenser, low charge packaged penthouse refrigeration system according to an embodiment of the invention.
  • a blow-up of the upper right quadrant of Figure 3 is presented in Figure 4.
  • the system includes evaporators 2a and 2b, including evaporator coils 4a and 4b, respectively, condenser 8, compressor(s) 10, expansion devices 11a and l ib (which may be provided in the form of valves, metering orifices or other expansion devices), pump 16, liquid- vapor separation device 12, and economizer 14.
  • liquid-vapor separation device 12 may be a recirculator vessel.
  • liquid- vapor separation device 12 and economizer 14 may one or both provided in the form of single or dual phase cyclonic separators.
  • the foregoing elements may be connected using standard refrigerant tubing in the manner shown in Figures 1-4.
  • low pressure liquid refrigerant (“LPL”) is supplied to the evaporator by pump 16 via expansion devices 11.
  • the refrigerant accepts heat from the refrigerated space, leaves the evaporator as low pressure vapor (“LPV”) and liquid and is delivered to the liquid-vapor separation device 12 (which may optionally be a cyclonic separator) which separates the liquid from the vapor.
  • LPL low pressure liquid refrigerant
  • Liquid refrigerant (“LPL”) is returned to the pump 16, and the vapor (“LPV”) is delivered to the compressor 10 which condenses the vapor and sends high pressure vapor (“HPV”) to the condenser 8 which compresses it to high pressure liquid (“HPL”).
  • HPL is delivered to the economizer 14 which improves system efficiency by reducing the high pressure liquid (“HPL”) to intermediate pressure liquid (“IPL”) then delivers it to the liquid-vapor separation device 12, which supplies the pump 16 with low pressure liquid refrigerant (“LPL”), completing the refrigerant cycle.
  • Figures 1-4 also include numerous control, isolation, and safety valves, as well as temperature and pressure sensors (a.k.a. indicators or gages) for monitoring and control of the system.
  • temperature and pressure sensors a.k.a. indicators or gages
  • motorized condenser inlet 101, 102 and 103 valves are installed on the inlet of the condenser coil bundles.
  • the motorized valves can function as variable control valves or on/off valves.
  • a single condenser bundle is open to ensure proper surface is available during start-up. As the system begins increasing load, valves 101, 102 and 103 will begin to open.
  • Motorized valve 104 and ammonia pressure regulator valve 105 provide precise ammonia gas control during start-up of the system in low ambient conditions. During start-up, all motorized valves are closed and the pressure regulator provides compressor differential pressure control to ensure proper oil flow. The ammonia pressure regulator 105 provides low volume flow control. As the compressor begins to load, more ammonia gas flow is generated. Motorized valve 104 begins to open and control the discharge pressure, compressor differential pressure and oil flow.
  • the next step during system start-up is to begin opening the condenser motorized valves 101, 102 and 103 and concomitant staging the startup of the condenser fans.
  • Check valves 106, 107, 108 and 109 installed at the outlet to the condenser bundles are utilized to ensure liquid ammonia does not backflow into the condenser or other coil bundles during periods of downtime or normal operating periods.
  • valves 101, 102, 103 and 105 are activated by attached microcontrollers or PLC (programmable logic control).
  • PLC programmable logic control
  • a central microcontroller or PLC monitors the status of each valve, as well as discharge pressure, and directs the action of the valves accordingly for sequential startup of the condenser coils while maintaining gas and oil pressure.
  • valves are required for a every ambient condition. In fact, above a certain ambient temperature, low ambient control may not be required. Therefore, valves can be installed and arranged to optimize operation at startup based on the ambient temperature.
  • Figures 3 and 4 show a process and instrumentation diagram for a dual compressor, air-cooled condenser, low charge packaged penthouse refrigeration system.
  • the dual compressor design utilizes and isolated compressor concept.
  • the compressors use different oil separators, oil coolers, and condenser bundles.
  • Motorized valves 110, 111, 112 and 113 are installed on the inlet of the condenser coil bundles.
  • the motorized valves can function as variable control valves or on/off valves.
  • valves 11 land 112 will be opened to a minimum position to allow ammonia gas flow to the condenser coil.
  • valves 111 and 112 will open to 100% and valves 113 and 110 will begin opening. Once all valves are open, variable fan control takes over pressure control.
  • the sequencing of the use of valves and fan operation can vary, based on system operation and design.
  • Fine ammonia gas control during start-up of the system is provided by:
  • Start-up requires all motorized valves are closed and the pressure regulator provides compressor differential pressure to ensure proper oil flow. During start-up, all motorized valves are closed and the pressure regulator provides compressor differential pressure control to ensure proper oil flow.
  • the ammonia pressure regulator provides low volume flow control. As the compressor begins to load, more ammonia gas flow is generated. Motorized valve #114 begins to open and control the discharge pressure, compressor differential pressure and oil flow.
  • Valve #117 Pressure regulator c. Start-up requires all motorized valves are closed and the pressure regulator provides compressor differential pressure to ensure proper oil flow. During start-up, all motorized valves are closed and the pressure regulator provides compressor differential pressure control to ensure proper oil flow. The ammonia pressure regulator provides low volume flow control. As the compressor begins to load, more ammonia gas flow is generated. Motorized valve #116 begins to open and control the discharge pressure, compressor differential pressure and oil flow.
  • the next stage is to begin opening the condenser motorized valves (110, 111, 112 and 113) and staging the condenser fans accordingly.
  • Check valves (118, 119, 120 and 121) are utilized to ensure liquid ammonia does not backflow into the condenser or other coil bundles during periods of downtime or normal operating periods.
  • each of valves 110-117 is activated by attached microcontrollers or PLC.
  • a central microcontroller or PLC monitors the status of each valve, as well as discharge pressure, and directs the action of the valves accordingly for sequential startup of the condenser coils while maintaining gas and oil pressure. Not all valves are required for every ambient condition. In fact, above a certain ambient temperature, low ambient control may not be required. Therefore, valves can be installed and arranged to optimize operation at startup based on the ambient temperature.
  • the evaporator is housed in the evaporator (penthouse) module, and the remaining components of the system shown in Figures 1-4 (except for the condenser coils and fans and associated structures) are housed in an enclosure such as a machine room module.
  • the condenser coils and fans may be mounted on top of the enclosure or machine room module for a complete self-contained rooftop system.
  • the air-cooled condenser may optionally be fitted with an adiabatic air pre-cooling system.
  • the entire system may be completely self-contained in two roof-top modules making it very easy for over-the-road transport to the install site, using e.g., flat bed permit load non-escort vehicles.
  • the penthouse and machine room modules can be separated for shipping and/or for final placement, but according to most preferred embodiments, the penthouse and machine room modules are mounted adjacent to one-another to maximize the reduction in refrigerant charge. According to a most preferred embodiment, the penthouse module and the machine room module are integrated into a single module, although the evaporator space is separated and insulated from the machine room space to comply with industry codes. According to an alternative embodiment, the evaporator coil may be mounted in a refrigerated space adjacent to, below, or remote from, the machine room module.
  • the present invention is configured to require less than six pounds of ammonia per ton of refrigeration capacity. According to a preferred embodiment, the present invention can require less than four pounds of ammonia per ton of refrigeration. And according to most preferred embodiments, the present invention can operate efficiently with less than two pounds per ton of refrigeration capacity.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Sorption Type Refrigeration Machines (AREA)

Abstract

L'invention concerne un appareil de démarrage séquencé d'un système de réfrigération à l'ammoniac conditionné à basse charge refroidie par air. Ledit appareil comprend des soupapes motorisées sur des entrées de serpentin de condenseur, une soupape motorisée de refoulement de compresseur principal, une soupape de régulation de pression de dérivation dans la conduite de compresseur principal, des clapets de non-retour sur les sorties de condenseur et une régulation de vitesse des ventilateurs de condenseur. Les soupapes motorisées d'entrée de condenseur fournissent une régulation précise de la charge en gaz aux condenseurs, de telle sorte que la pression peut s'accumuler sans écraser la pression d'huile. La sortie de serpentin du condenseur contient des clapets anti-retour en ligne pour empêcher un reflux de liquide lorsqu'un serpentin est isolé. La conduite de refoulement de compresseur contient une seule soupape motorisée pour réguler la pression de refoulement au démarrage. La soupape motorisée dans la conduite de refoulement de compresseur comprend également une dérivation avec un régulateur de pression mécanique pour permettre une régulation précise à la pression de refoulement minimale. Une fois que la pression de refoulement augmente au-dessus de la valeur de consigne minimale, les entrées de serpentin du condenseur s'ouvriront une à la fois. La soupape motorisée de régulation de pression de refoulement régule simultanément la pression de refoulement jusqu'à ce que le serpentin du condenseur soit suffisamment chauffée pour maintenir la pression de refoulement.
EP19888679.8A 2018-11-28 2019-11-27 Procédé et appareil de démarrage séquencé d'un système de réfrigération à l'ammoniac conditionné à basse charge refroidie par air Active EP3887733B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201862772334P 2018-11-28 2018-11-28
PCT/US2019/063621 WO2020113011A1 (fr) 2018-11-28 2019-11-27 Procédé et appareil de démarrage séquencé d'un système de réfrigération à l'ammoniac conditionné à basse charge refroidie par air

Publications (3)

Publication Number Publication Date
EP3887733A1 true EP3887733A1 (fr) 2021-10-06
EP3887733A4 EP3887733A4 (fr) 2022-08-24
EP3887733B1 EP3887733B1 (fr) 2025-06-18

Family

ID=77468446

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19888679.8A Active EP3887733B1 (fr) 2018-11-28 2019-11-27 Procédé et appareil de démarrage séquencé d'un système de réfrigération à l'ammoniac conditionné à basse charge refroidie par air

Country Status (5)

Country Link
EP (1) EP3887733B1 (fr)
CN (1) CN113348332B (fr)
DK (1) DK3887733T3 (fr)
ES (1) ES3041511T3 (fr)
PL (1) PL3887733T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117915634A (zh) * 2024-01-26 2024-04-19 科华数据股份有限公司 液冷系统控制方法及液冷系统

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN119289564A (zh) * 2024-11-19 2025-01-10 深圳市英维克科技股份有限公司 直冷系统的冷媒回收方法及装置

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US6843065B2 (en) * 2000-05-30 2005-01-18 Icc-Polycold System Inc. Very low temperature refrigeration system with controlled cool down and warm up rates and long term heating capabilities
US20080083237A1 (en) * 2006-10-06 2008-04-10 Hussmann Corporation Electronic head pressure control
CN201954826U (zh) * 2010-12-15 2011-08-31 广州恒星冷冻机械制造有限公司 一种风冷冷水机组
CN204063368U (zh) * 2014-06-24 2014-12-31 广东申菱空调设备有限公司 一种低温风冷冷水机组
MX384404B (es) * 2014-07-02 2025-03-14 Evapco Inc Sistema de refrigeración tipo paquete de baja carga
CN105910323B (zh) * 2016-06-03 2018-07-24 广东申菱环境系统股份有限公司 一种制冷系统、制冷机组及其制冷控制方法
CA3046495C (fr) * 2016-12-12 2024-06-25 Evapco, Inc. Systeme de refrigeration d'ammoniac integre a faible charge avec condenseur evaporatif
CN207146964U (zh) * 2017-07-06 2018-03-27 魏宇杰 一种制冷系统

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117915634A (zh) * 2024-01-26 2024-04-19 科华数据股份有限公司 液冷系统控制方法及液冷系统

Also Published As

Publication number Publication date
PL3887733T3 (pl) 2025-10-27
EP3887733B1 (fr) 2025-06-18
CN113348332A (zh) 2021-09-03
ES3041511T3 (en) 2025-11-12
EP3887733A4 (fr) 2022-08-24
DK3887733T3 (da) 2025-09-22
CN113348332B (zh) 2023-01-24

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