EP3353476A1 - Système et procédé de régulation d'écoulement d'huile à l'intérieur d'un système frigorifique - Google Patents

Système et procédé de régulation d'écoulement d'huile à l'intérieur d'un système frigorifique

Info

Publication number
EP3353476A1
EP3353476A1 EP16784608.8A EP16784608A EP3353476A1 EP 3353476 A1 EP3353476 A1 EP 3353476A1 EP 16784608 A EP16784608 A EP 16784608A EP 3353476 A1 EP3353476 A1 EP 3353476A1
Authority
EP
European Patent Office
Prior art keywords
compressor
oil return
approximately
limit
run time
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.)
Ceased
Application number
EP16784608.8A
Other languages
German (de)
English (en)
Inventor
Sathish R. Das
Charles A. SEYMOUR
Jun Pyo LEE
Matthew Austin
Lynn A. Turner
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.)
Carrier Corp
Original Assignee
Carrier Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Carrier Corp filed Critical Carrier Corp
Publication of EP3353476A1 publication Critical patent/EP3353476A1/fr
Ceased legal-status Critical Current

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
    • 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
    • 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
    • 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
    • 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
    • F25B2600/0253—Compressor control by controlling speed with variable speed
    • 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
    • F25B2600/2513—Expansion 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
    • 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
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • 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

  • the presently disclosed embodiments generally relate to refrigeration systems, and more particularly, to a system and method of controlling an oil flow within a refrigeration system.
  • Refrigeration oils are soluble in liquid refrigerant and at normal room temperatures they will mix completely. Since oil typically must pass through the compressor to provide lubrication, a small amount of oil is typically in circulation with the refrigerant. Typically, oil and refrigerant vapor do not mix readily, and the oil can be properly circulated through the system typically only if gas velocities are high enough to sweep the oil along In some refrigeration compressors, for example inverter compressors, if refrigerant velocities are not sufficiently high, oil will tend to coat the walls of the evaporator tubing, decreasing heat transfer and possibly causing a shortage of oil in the compressor. Oil recovering devices are generally used in order to recover the oil; however, the addition of such devices increase the costs and size of the refrigeration system
  • a refrigeration system in one aspect, includes a compressor, an expansion device in flow communication with the compressor, and an electronic controller in communication with the expansion device and the compressor.
  • the electronic controller is configured to operate in an oil return mode based at least in part on an operational speed and a continuous operational run time of the compressor.
  • the electronic controller is further configured to command the compressor to operate at the minimal speed limit for an oil return duration of time if it is determined that the operational speed is less than the minimal speed limit and the continuous operational run time is greater than or equal to the run time limit, and command the expansion device to operate in order to decrease a target superheat value by an oil return target value if it is determined that the operational speed is less than the minimal speed limit and the continuous operational run time is greater than or equal to the run time limit.
  • the electronic controller is configured to determine whether the operational speed is less than a minimal speed limit, and determine whether the continuous operational run time is greater than or equal to a run time limit.
  • the minimal speed limit is approximately 3000 revolutions per minute. In one embodiment of the system, the run time limit is approximately 45 minutes. In one embodiment, the oil return duration of time is approximately 10 minutes. In one embodiment of the system, the oil return target value is approximately 5 degrees Fahrenheit.
  • an electronic controller includes a processor, and a memory, wherein the processor is configured to operate a program stored in memory, the program configured to command a compressor to operate at a demand operational speed, determine whether the compressor has operated at a speed less than a minimal speed limit for a continuous duration of time greater than or equal to a run time limit, and operate in an oil return mode if the compressor has operated at a speed less than the minimal speed limit for a continuous duration of time greater than or equal to the run time limit.
  • the program is further configured to command the compressor to operate at the minimal speed limit for an oil return duration of time, and command an expansion device to operate in order to decrease a target superheat value by an oil return target value.
  • the minimal speed limit is approximately
  • the run time limit is approximately 45 minutes. In one embodiment of the controller, the oil return duration of time is approximately 10 minutes. In one embodiment of the controller, the oil return target value is approximately 5 degrees Fahrenheit.
  • a method of controlling oil flow within a compressor is provided.
  • the method includes operating the compressor at a demand operational speed, operating the controller to determine whether the compressor has operated at a speed less than a minimal speed limit for a continuous duration of time greater than or equal to a run time limit, and operating the controller to enter an oil return mode if the compressor has operated at a speed less than the minimal speed limit for a continuous duration of time greater than or equal to the run time limit.
  • the oil return mode includes operating the compressor at the minimal speed limit for an oil return duration of time, and controlling the expansion device to decrease a target superheat value by an oil return target value.
  • the minimal speed limit is approximately 3000 revolutions per minute.
  • the run time limit is approximately 45 minutes.
  • the oil return duration of time is approximately 10 minutes.
  • the oil return target value is approximately 5 degrees Fahrenheit.
  • FIG. 1 illustrates a schematic diagram of a refrigerant system according to an embodiment of the present disclosure
  • FIG. 2 illustrates a schematic flow diagram of a method of controlling oil flow within the compressor according to an embodiment of the present disclosure
  • FIG. 3 illustrates a schematic flow diagram of an oil return mode according to an embodiment of the present disclosure.
  • FIG. 1 schematically illustrates an embodiment of a refrigerant system, generally indicated at 10.
  • the refrigerant system includes a compressor 12 configured to deliver compressed refrigerant downstream to a heat rejection heat exchanger 14 (e.g. a condenser).
  • the compressed refrigerant passes through an expansion device 16 (e.g. an electronic expansion valve to name one non- limiting example) and flows in sequence through an evaporator 18, and through a suction line 22 back to the compressor 12.
  • a temperature sensor 24 may be placed on the suction line entering the compressor 22.
  • the temperature sensor 24 is configured to measure a suction gas temperature entering the compressor.
  • a pressure sensor 28 may also be placed on the suction line to measure a suction pressure of the refrigerant entering the compressor 22.
  • the temperature sensor 24 is operably coupled to and communicates with an electronic controller 26.
  • the electronic controller 26 is configured to command the refrigerant system 10 to enter an oil return mode under certain conditions.
  • the electronic controller 26 is further coupled to, and configured to control the expansion device 16 to adjust and control a target superheat.
  • Target superheat is the recommended superheat for the given indoor and outdoor environmental conditions based on an outdoor dry-bulb temperature and an indoor wet- bulb temperature.
  • Sensors 24 and 28 are operably coupled to suction line 22 between the exit from the evaporator 18 and inlet to the compressor 12, and are in communication with the electronic controller 26. Sensors 24 and 28 are configured to measure a suction superheat value.
  • the sensor 28 may measure the suction pressure that would be used by the electronic controller 26 to determine the saturated refrigerant temperature.
  • Superheat is the difference between the actual refrigerant temperature at sensor 24 and the saturated refrigerant temperatures at approximately the same location. It will be appreciated that sensor 28 can be any other type of sensor typically used to measure a superheat value.
  • FIG. 2 illustrates a method of controlling an oil flow within the compressor 12, the method generally indicated at 100.
  • the method includes step 102 of operating the compressor 12 at a demand operational speed. For example, based on the demand of the refrigerant system 10, the compressor 12 may operate at a plurality of non-zero operating speeds to satisfy the demand.
  • the method 100 further includes step 104 of operating the controller 26 to determine whether the compressor 12 has operated at a speed less than a minimal speed limit for a continuous duration of time greater than or equal to a run time limit.
  • the minimal speed limit may be a pre-determined operational speed threshold at which oil does not adequately flow through the compressor 12.
  • the run time limit may be a pre-determine time threshold which may begin to affect the flow of oil within the compressor 12. It will be appreciated that if the demand of the system 10 changes before the expiration of the run time limit, the controller 26 adjusts the speed of the compressor 12 to meet the new demand, and returns to step 102.
  • the minimal speed limit is approximately 3000 revolutions per minute (RPM). In some embodiments, the minimal speed limit is adjustable, and may be greater than or less than 3000 RPM. In one embodiment, the run time limit is approximately 45 minutes. In some embodiments, the run time limit is adjustable, and may be greater than or less than 45 minutes. [0021] The method 100 further includes step 106 of operating the controller 26 to enter an oil return mode if the compressor 12 has operated at a speed less than the minimal speed limit for a continuous duration of time greater than or equal to the run time limit. In an embodiment, as shown in FIG.
  • operating in an oil return mode includes step 202 of operating the compressor 12 at a speed equal to the minimal speed limit for an oil return duration of time, and step 204 of controlling the expansion device 16 to decrease a target superheat value by an oil return target value. After the controller 26 completes the oil return mode, the method returns to step 102 of operating the compressor 12 at the demand operational speed.
  • the oil return duration of time is approximately 10 minutes. In some embodiments, the oil return duration of time is adjustable, and may be greater than or less than 10 minutes. In one embodiment, the oil return target value is approximately 5 degrees Fahrenheit (° F) (approximately 2.8 degrees Celsius). In some embodiments, the oil return target value is adjustable and may be greater than or less than 5° F (approximately 2.8 degrees Celsius).
  • the controller 26 commands the compressor 12 to enter an oil return mode by increasing the speed of the compressor 12 to the minimal speed limit (e.g. 3000 RPM).
  • the controller 26 also commands the adjustment of the expansion device 16 to lower the target superheat of the system 10 by approximately 5° F. Lowering the superheat target improves the solubility of the refrigerant-oil mixture, and increasing the compressor speed increases the refrigerant velocities to a sufficient level to allow the oil to return to the compressor 12.
  • the controller 26 operates the system 10 in the oil return mode for approximately 10 minutes; then, returns to the operational speed to meet the demand of the system 10.
  • the present embodiments includes a method of returning oil to the compressor 12 by increasing the speed of the compressor 12 to the minimal speed limit for an oil return duration of time and decreasing the superheat target by an oil return target value.

Landscapes

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

Abstract

L'invention concerne un système et un procédé de régulation d'un écoulement d'huile à l'intérieur d'un système frigorifique, le système comportant un compresseur, un détendeur en communication fluidique avec le compresseur, et un régulateur électronique en communication avec le détendeur et le compresseur, le régulateur électronique étant conçu pour fonctionner dans un mode de retour d'huile sur la base, au moins en partie, d'une vitesse de fonctionnement et d'un temps de marche en fonctionnement ininterrompu du compresseur.
EP16784608.8A 2015-09-24 2016-09-22 Système et procédé de régulation d'écoulement d'huile à l'intérieur d'un système frigorifique Ceased EP3353476A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201562232274P 2015-09-24 2015-09-24
PCT/US2016/053157 WO2017053596A1 (fr) 2015-09-24 2016-09-22 Système et procédé de régulation d'écoulement d'huile à l'intérieur d'un système frigorifique

Publications (1)

Publication Number Publication Date
EP3353476A1 true EP3353476A1 (fr) 2018-08-01

Family

ID=57178471

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16784608.8A Ceased EP3353476A1 (fr) 2015-09-24 2016-09-22 Système et procédé de régulation d'écoulement d'huile à l'intérieur d'un système frigorifique

Country Status (4)

Country Link
US (1) US20180283753A1 (fr)
EP (1) EP3353476A1 (fr)
CN (1) CN108351131A (fr)
WO (1) WO2017053596A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101816432B1 (ko) 2016-08-26 2018-01-08 현대자동차주식회사 에어컨 컴프레서의 제어 방법
WO2019087401A1 (fr) * 2017-11-06 2019-05-09 ダイキン工業株式会社 Dispositif de conditionnement d'air
CN110857809A (zh) * 2018-08-24 2020-03-03 青岛海尔空调器有限总公司 空调器及其回油控制方法
US10933718B2 (en) * 2019-05-16 2021-03-02 Ford Global Technologies, Llc Vehicle configured to prevent oil entrapment within refrigerant system and corresponding method
CN114198859A (zh) * 2021-12-10 2022-03-18 珠海格力电器股份有限公司 一种压缩机回油控制方法及空调器

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1922516A2 (fr) * 2005-09-05 2008-05-21 Arcelik Anonim Sirketi Dispositif de refroidissement
US20080134701A1 (en) * 2006-12-12 2008-06-12 Ole Moelgaard Christensen Variable Compressor Oil Return
JP2008241065A (ja) * 2007-03-26 2008-10-09 Daikin Ind Ltd 冷凍装置及び冷凍装置の油戻し方法
US20110314845A1 (en) * 2007-10-10 2011-12-29 Carrier Corporation Tadem compressor operation
US8402780B2 (en) * 2008-05-02 2013-03-26 Earth To Air Systems, Llc Oil return for a direct exchange geothermal heat pump
US20110314854A1 (en) * 2009-03-06 2011-12-29 Mitsubishi Electric Corporation Refrigerator
CN104180563B (zh) * 2013-05-27 2017-06-20 珠海格力电器股份有限公司 多联机系统制热时的回油方法

Also Published As

Publication number Publication date
WO2017053596A1 (fr) 2017-03-30
US20180283753A1 (en) 2018-10-04
CN108351131A (zh) 2018-07-31

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