WO2008033123A1 - Démarrages hors-saison permettant d'améliorer la fiabilité d'un système à frigorigène - Google Patents

Démarrages hors-saison permettant d'améliorer la fiabilité d'un système à frigorigène Download PDF

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Publication number
WO2008033123A1
WO2008033123A1 PCT/US2006/035406 US2006035406W WO2008033123A1 WO 2008033123 A1 WO2008033123 A1 WO 2008033123A1 US 2006035406 W US2006035406 W US 2006035406W WO 2008033123 A1 WO2008033123 A1 WO 2008033123A1
Authority
WO
WIPO (PCT)
Prior art keywords
set forth
compressor
vapor compression
compression system
refrigerant
Prior art date
Application number
PCT/US2006/035406
Other languages
English (en)
Inventor
Alexander Lifson
Michael F. Taras
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 PCT/US2006/035406 priority Critical patent/WO2008033123A1/fr
Priority to CN2006800558064A priority patent/CN101512254B/zh
Priority to US12/440,786 priority patent/US20100011788A1/en
Publication of WO2008033123A1 publication Critical patent/WO2008033123A1/fr
Priority to HK10101496.5A priority patent/HK1135167A1/xx

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
    • F25B31/00—Compressor arrangements
    • F25B31/002—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
    • 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
    • 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
    • F25B2400/01—Heaters
    • 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
    • F25B2600/01—Timing
    • 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
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off operation
    • 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
    • F25B2600/11—Fan speed control
    • F25B2600/111—Fan speed control of condenser fans
    • 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
    • F25B2600/11—Fan speed control
    • F25B2600/112—Fan speed control of evaporator fans
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2104—Temperatures of an indoor room or compartment
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2106—Temperatures of fresh outdoor air
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • This invention relates generally to vapor compression systems and, more particularly, to a method and apparatus for preventing severe flooded starts caused by the system operational seasonality.
  • a typical air conditioning system includes, in serial flow communication, a compressor, a condenser, an expansion device and an evaporator.
  • the compressor compresses refrigerant and passes this high pressure refrigerant vapor to the condenser where it is desuperheated, condensed and typically subcooled, as a result of heat transfer interaction with a secondary fluid such as air or water.
  • the liquid refrigerant then flows to the expansion device where it is expanded to a lower pressure and temperature forming a two-phase (liquid and vapor) refrigerant mixture at the expansion device exit, while a portion of the refrigerant is flashed to vapor.
  • This vapor and liquid refrigerant mixture then flows to the evaporator, where heat is absorbed by the refrigerant while cooling another secondary fluid that is typically delivered to the space to be conditioned, with the resultant evaporated and typically superheated refrigerant vapor passing to the compressor to complete the cycle.
  • the air conditioning cooling systems are mostly used during the hot and/or humid summer months, but they are typically shut down during the winter seasons (and potentially during fall and summer months as well) for the prolonged time intervals measured in months. Since refrigerant tends to migrate to the coldest spot within the system, and since the compressor is normally located in the outdoor section of the unit, during the winter months, the liquid refrigerant accumulates in the outdoor components, including the condenser and compressor. Therefore over the prolonged periods when the unit has been shut down, the liquid refrigerant will fill the volumes of the outdoor system components.
  • HVAC air conditioning, heating and ventilation
  • the lubricating oil in the compressor sump is diluted and mixed with this liquid refrigerant such that its lubrication characteristics are diminished. If the system is then started up in the summer or spring with the compressor sump and other compressor elements being flooded with the refrigerant, the liquid refrigerant will slug through the compressor and can result in compressor damage. Furthermore, after prolonged periods of time without the startups or even intermittent operation, all the residual lubricating oil which normally is collected on the compressor contact services during operation (i.e.
  • crankcase heaters have also been used in the prior art to heat the compressor oil sump before the startup and evaporate at least some liquid refrigerant that has been accumulated in the sump since the last shutdown. Although this technique is helpful, it doesn't affect other components within the vapor compression system that are filled with the ' liquid refrigerant. Also crankcase heaters present their own reliability problems, and may fail after several years of operation. Crankcase heaters also add extra cost and reduce overall system efficiency. Therefore, it is desired to provide a reliable and inexpensive method to reduce or eliminate severe flooded starts caused by seasonal operational pattern of the air conditioning equipment.
  • a timer is installed in communication with or integrated into the system control so as to periodically start the system during the off-season months to prevent the excessive migration of refrigerant to the compressor sump and thus eliminate severe flooded startups.
  • the environmental conditions are recorded to determine if sufficient amount of liquid refrigerant could accumulate within the compressor volume, and the compressor sump in particular, to execute an off-season startup procedure.
  • Such environmental conditions may include (but are not limited to) the ambient and indoor temperatures.
  • vapor compression system components would be started in a predetermined sequence that is defined by environmental and operational parameters.
  • the compressor, the evaporator fan and the condenser fan may start simultaneously.
  • the compressor and the evaporator fan would start first, followed by the delayed start of the condenser fan or some of the condenser fans.
  • Such operational and environmental parameters may include, for instance, discharge pressure, suction pressure, ambient temperature and indoor temperature.
  • FIG. 1 is an exemplary vapor compression system with the present invention incorporated therein.
  • FIG. 2 is a flow chart showing the method in accordance with the present invention.
  • a basic vapor compression system 10 normally includes a compressor 11, a condenser 12, an expansion device 13 and an evaporator 14 interconnected in serial refrigerant flow communication.
  • a refrigerant vapor from the evaporator 14 is delivered to the compressor 11 where it is compressed, and the compressed vapor then flows to the condenser 12 where it is desuperheated, condensed and typically subcooled by a secondary fluid such as ambient air. Then the liquid refrigerant passes to the expansion device 13 where it is expanded to a lower pressure and temperature to form a two-phase (liquid and vapor) mixture with a portion of the refrigerant being flashed to a vapor.
  • a vapor and liquid refrigerant mixture than passes to the evaporator 14 where it is evaporated and typically superheated by another secondary fluid such as air to be delivered to a conditioned space, while cooling this secondary fluid.
  • the refrigerant vapor then passes to the compressor 11 to complete the cycle.
  • the basic air conditioning system 10 of Fig. 1 is exemplary and could include a number of different options and enhancement features. All these various system configurations are within the scope of the invention. Also, as known in the art, if a vapor compression system employs the refrigerant with a relatively low critical point such as CO 2 , the condenser 12 becomes a single-phase gas cooler in the transcritical (rather than conventional subcritical) refrigerant cycle. These systems as well could equally benefit from the invention.
  • a condenser fan 16 circulates ambient air over the condenser 12 to provide heat transfer interaction with the refrigerant flowing within its passages (heat is transferred from the refrigerant to air), and an evaporator fan 17 circulates air, to be cooled and delivered to a conditioned space, over the evaporator 14 to provide heat transfer interaction with the evaporating refrigerant and to cool the air.
  • the air conditioning system 10 shown in the Fig.l embodiment is a so-called air-to- air system, where one stream of air is cooled and delivered to a conditioned space while another stream of air (typically ambient air) is heated by the refrigerant.
  • the refrigerant in the system tends to migrate toward the coolest component (or components) within the vapor compression system.
  • the liquid refrigerant will accumulate in the outdoor section of the unit, and typically within the condenser 12 and compressor 11. Therefore over the prolonged periods of time when the unit has been shut down, the liquid refrigerant fills the volumes of the outdoor system components.
  • the lubricating oil in the compressor sump is diluted and mixed with this liquid refrigerant such that its lubrication characteristics are diminished.
  • a timer 18 has been added to a control 19.
  • the timer 18 is started when the system is shut down. After a predetermined sufficiently long period of time during an off-season, the system is turned on and allowed to operate for a second predetermined relatively short period of time. This timed operation allows the compressor components to be lubricated as well as it allows refrigerant to circulate, redistribute and at least partially evaporate any liquid refrigerant accumulated within the compressor sump and other components throughout the system. After the expiration of the second predetermined period of time, the system is shut down and the timer 18 is reset for the first predetermined period of time after which the off-season startup cycle is repeated.
  • the off-season startup procedure can be improved.
  • the sensed environmental conditions are monitored and recorded to determine if sufficient amount of liquid refrigerant could accumulate within the system components such as the compressor 11 (and the compressor sump in particular), condenser 12 and evaporator 14 to execute the off-season startup procedure. If it is determined that sufficient amount of liquid refrigerant could have been accumulated, the off-season startup procedure is executed. Otherwise, the timer is reset once again, with the time interval potentially adapted to the sensed environmental conditions (colder temperature would suggest shorter time intervals between the startups).
  • Such environmental conditions may include (but are not limited to) the ambient temperature T AMB sensed by a temperature sensor 21 and the indoor temperature Ti ND oo R sensed by a temperature sensor 22.
  • the temperature sensors can be, for instance, of a thermistor or thermocouple type.
  • these components of the vapor compression system 10 could be started by the control 19 in a predetermined sequence defined by the environmental and operational parameters.
  • operational and environmental parameters may include, for instance, the discharge pressure P D measured by a sensor 23, the suction ⁇ pressure Ps measured by a sensor 24, the ambient temperature T AMB measured by the sensor 21, the indoor temperature T] NDOOR measured by the sensor 22 or a combination of thereof.
  • the compressor heater 20, typically inserted into the oil sump or wrapped around the compressor shell at the oil sump location, could be switched on first, usually for a time period of a few hours, to boil off at least some of the refrigerant accumulated in the oil sump of the compressor 11 prior to the compressor startup.
  • the compressor 11 and the evaporator fan 17 are started first, while the discharge pressure P D is monitored by the sensor 23 and communicated to the control 19.
  • the condenser fan (or some of the condenser fans) 16 are turned on to move air over the condenser 12 and thus reduce this pressure.
  • the condenser fan (or some of the condenser fans) 16 are turned off to maintain the discharge pressure P D between the upper and the lower limits, as desired.
  • the time intervals between the oil sump heater 20 and compressor 11 startup and the compressor 11 and condenser fan 16 startup depends on a particular system configuration and refrigerant charge amount.
  • the time intervals between subsequent startups can be adjusted based on various factors such as vapor compression system configuration and schematic, amount of refrigerant charge, ambient temperature, ambient temperature swings, etc.
  • the time between the subsequent startups i.e. the first predetermined time as described above
  • the time of operation i.e. the second predetermined period of time
  • the running time of operation would be in the range of 2-15 minutes.
  • the selection of the appropriate time for the off-season unit startups can also take into consideration the occupancy schedule, such as to avoid periods of time when the building is occupied and execute the off-season startup procedure during the nighttime, on the weekends or holidays to cause minimum disruption and occupant discomfort.
  • Fig. 2 the methodology and the control logic of the present invention is shown in the flowchart format.
  • the control determines whether the vapor compression system is sophisticated enough to have the provisions for sensing environmental and operating conditions indicative of a need of the off-season startup and to communicate these conditions to the system control to initiate the off-season startup procedure in order to avoid the severe flooded conditions and associated problems as discussed hereinabove.
  • the system for instance, does not include various sensors mentioned above to sense the temperatures and/or pressures at various locations associated with the vapor compression system that are indicative of the problem, then it is presumed that the need exists to proceed with the present off-season startup method and the control steps to a block 24. If the system is of a type that does include the various sensors that will be indicative of a need to take an action, then the method proceeds to a block 22 wherein such operational parameters are sensed.
  • Such environmental conditions may include (but are not limited to) the ambient temperature TAMB and the indoor temperature T 1 N D OOR-
  • the control determines in a block 23 whether the off-season startup is required. For instance, if the ambient temperature TAMB falls below 4O 0 F then the determination could be made that the off-season startup is required. If the determination is made that the off-season startup is not required, then the control steps to a block 28 to reset the timer, after which the process is repeated. It should be pointed out that the reset timer interval could be potentially adapted based on sensed environmental conditions (colder temperature would suggest shorter time intervals between the startups). [0022] If the control determines in the block 23 that the off-season startup is required, the compressor 11 and the evaporator fan 17 are started first.
  • the operational sequence for the condenser fan (or fans) 16 is started to keep the discharge pressure P D between the upper and lower limits.
  • the system is shut down and the timer is reset (possibly to a new value based on the environmental conditions, as discussed above) at a block 28. After the first predetermined period of time has expired, the process is repeated.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

La présente invention concerne un système à compression de vapeur qui comprend un temporisateur et un contrôleur permettant de démarrer périodiquement le système pendant les périodes hors saison (principalement les mois sans climatisation), durant lesquelles le système est habituellement éteint. L'invention permet de lubrifier périodiquement les éléments du compresseur et d'éviter les graves démarrages noyés causés par unue accumulation excessive de réfrigérant dans le compresseur (carter d'huile du compresseur en particulier) et d'autres éléments du système. L'invention permet également d'allumer et d'éteindre consécutivement des éléments du système tels que le compresseur, le ventilateur de l'évaporateur et le ventilateur du condensateur afin d'améliorer le fonctionnement du système. Les séquences temporelles sont fournies pour les intervalles de temps séparant les démarrages, ainsi que pour la durée du cycle de fonctionnement hors saison.
PCT/US2006/035406 2006-09-12 2006-09-12 Démarrages hors-saison permettant d'améliorer la fiabilité d'un système à frigorigène WO2008033123A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
PCT/US2006/035406 WO2008033123A1 (fr) 2006-09-12 2006-09-12 Démarrages hors-saison permettant d'améliorer la fiabilité d'un système à frigorigène
CN2006800558064A CN101512254B (zh) 2006-09-12 2006-09-12 改善制冷系统可靠性的关机季节启动
US12/440,786 US20100011788A1 (en) 2006-09-12 2006-09-12 Off-season start-ups to improve reliability of refrigerant system
HK10101496.5A HK1135167A1 (en) 2006-09-12 2010-02-10 Off-season startups to improve reliability of refrigerant system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2006/035406 WO2008033123A1 (fr) 2006-09-12 2006-09-12 Démarrages hors-saison permettant d'améliorer la fiabilité d'un système à frigorigène

Publications (1)

Publication Number Publication Date
WO2008033123A1 true WO2008033123A1 (fr) 2008-03-20

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PCT/US2006/035406 WO2008033123A1 (fr) 2006-09-12 2006-09-12 Démarrages hors-saison permettant d'améliorer la fiabilité d'un système à frigorigène

Country Status (4)

Country Link
US (1) US20100011788A1 (fr)
CN (1) CN101512254B (fr)
HK (1) HK1135167A1 (fr)
WO (1) WO2008033123A1 (fr)

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WO2011048428A3 (fr) * 2009-10-23 2011-11-24 Hubbard Products Limited Installation de réfrigération et procédés de régulation
EP2438369A1 (fr) * 2009-06-05 2012-04-11 Ace Action Limited Dispositif d'économie d'énergie et procédé pour appareil de refroidissement et de chauffage
WO2013007627A1 (fr) * 2011-07-12 2013-01-17 A.P. Møller - Mærsk A/S Régulation de l'humidité dans un conteneur de transport réfrigéré comprenant un compresseur actionné par intermittence
WO2014169212A1 (fr) * 2013-04-12 2014-10-16 Emerson Climate Technologies, Inc. Compresseur à commande de démarrage à l'état noyé
US9791175B2 (en) 2012-03-09 2017-10-17 Carrier Corporation Intelligent compressor flooded start management

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US9903627B2 (en) * 2012-11-06 2018-02-27 Carrier Corporation Method of operating an air conditioning system including reducing the energy consumed by the compressor crank case heaters
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US10564116B2 (en) * 2016-04-28 2020-02-18 Fluke Corporation Optical image capture with position registration and RF in-wall composite image
US10315495B2 (en) 2016-06-30 2019-06-11 Emerson Climate Technologies, Inc. System and method of controlling compressor, evaporator fan, and condenser fan speeds during a battery mode of a refrigeration system for a container of a vehicle
US10414241B2 (en) 2016-06-30 2019-09-17 Emerson Climate Technologies, Inc. Systems and methods for capacity modulation through eutectic plates
US10569620B2 (en) 2016-06-30 2020-02-25 Emerson Climate Technologies, Inc. Startup control systems and methods to reduce flooded startup conditions
US10562377B2 (en) 2016-06-30 2020-02-18 Emerson Climate Technologies, Inc. Battery life prediction and monitoring
US10532632B2 (en) 2016-06-30 2020-01-14 Emerson Climate Technologies, Inc. Startup control systems and methods for high ambient conditions
US10300766B2 (en) 2016-06-30 2019-05-28 Emerson Climate Technologies, Inc. System and method of controlling passage of refrigerant through eutectic plates and an evaporator of a refrigeration system for a container of a vehicle
US10828963B2 (en) 2016-06-30 2020-11-10 Emerson Climate Technologies, Inc. System and method of mode-based compressor speed control for refrigerated vehicle compartment
US10328771B2 (en) 2016-06-30 2019-06-25 Emerson Climated Technologies, Inc. System and method of controlling an oil return cycle for a refrigerated container of a vehicle
US10538146B2 (en) 2016-12-06 2020-01-21 Ford Global Technologies Llc Reducing externally variable displacement compressor (EVDC) start-up delay
CN110446894B (zh) * 2017-04-07 2021-02-12 三菱电机株式会社 空调机的室外机
US11668505B2 (en) 2017-10-10 2023-06-06 Carrier Corporation HVAC heating system and method
US11073313B2 (en) * 2018-01-11 2021-07-27 Carrier Corporation Method of managing compressor start for transport refrigeration system
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CN105121981A (zh) * 2013-04-12 2015-12-02 艾默生环境优化技术有限公司 具有带液起动控制的压缩机
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US10385840B2 (en) 2013-04-12 2019-08-20 Emerson Climate Technologies, Inc. Compressor with flooded start control
US10519947B2 (en) 2013-04-12 2019-12-31 Emerson Climate Technologies, Inc. Compressor with flooded start control
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US20100011788A1 (en) 2010-01-21
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CN101512254A (zh) 2009-08-19

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