EP0282782A2 - Système de conditionnement d'air pour plusieurs chambres et procédé pour sa commande - Google Patents

Système de conditionnement d'air pour plusieurs chambres et procédé pour sa commande Download PDF

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Publication number
EP0282782A2
EP0282782A2 EP88102741A EP88102741A EP0282782A2 EP 0282782 A2 EP0282782 A2 EP 0282782A2 EP 88102741 A EP88102741 A EP 88102741A EP 88102741 A EP88102741 A EP 88102741A EP 0282782 A2 EP0282782 A2 EP 0282782A2
Authority
EP
European Patent Office
Prior art keywords
indoor units
refrigerant
inoperating
expansion valves
amount
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
EP88102741A
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German (de)
English (en)
Other versions
EP0282782B1 (fr
EP0282782A3 (en
Inventor
Kenji Yamazaki
Kaname Sotome
Tomio Yoshikawa
Tsuyoshi Hiyoshi
Osamu Seki
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.)
Hitachi Ltd
Original Assignee
Hitachi Ltd
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
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Publication of EP0282782A2 publication Critical patent/EP0282782A2/fr
Publication of EP0282782A3 publication Critical patent/EP0282782A3/en
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Publication of EP0282782B1 publication Critical patent/EP0282782B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—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
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • 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
    • F25B2600/19—Refrigerant outlet condenser temperature
    • 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
    • F25B2600/21—Refrigerant outlet evaporator temperature
    • 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
    • F25B2700/04—Refrigerant level
    • 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
    • F25B45/00—Arrangements for charging or discharging refrigerant

Definitions

  • the present invention relates to a multiple room type heat pump air conditioning system in which a single outdoor unit and a plurality of indoor units connected to the outdoor unit and to a method for controlling excess flow of refrigerant in refrigeration cycle when any indoor unit is inoperated.
  • the conventional system if the refrigerant flow circulating through the operating cycle is changed, another significant controlled variable is also changed, whereby making a considerable effect on another control.
  • the conventional system does not take it into the consideration. Accordingly the excess flow control causes the problem that the refrigerant distribution control based on the super heating degree of the refrigerant from the compressor.
  • An object of the present invention is to provide an air conditioning system by which the above mentioned problems are solved, and in which the excess flow of refrigerant is properly controlled corresponding to the conditions of the operating cycle to form an effective and steady refrigeration cycle, whereby obtaining a comfortable circumstance.
  • the system comprises a controller for receiving data from the sensors for detecting the subcooling degree and the super heating degree of the refrigerant and for calculat­ing signals regarding to the expansion valves associated with the inoperating indoor units, or not only to such expansion valves but also the solenoid valves associated with the inoperating indoor units on the basis of such data from the sensors, and a control signal outputting means for outputting open/close control command signals to such expansion valves, or such expansion valves and such solenoid valves, in compliance with the calculated signals in the controller, to intermittently open or close such valves.
  • the controller receives the data corresponding to the super heating degree of the refrigerant from the compressor from the sensor for detecting such data and the controller outputs signals to the control signal out­putting means so as to interrupt a discharge flow from the inoperating indoor units.
  • a refrigeration cycle of an air conditioning system comprises a single outdoor unit A and three indoor units B, C and D connected to the outdoor unit A.
  • the indoor unit A includes a compressor 1, a four-way valve 2, an accumulator 3, an outdoor heat exchanger 4 and a receiver 5 disposed in a liquid side primary pipe 6 through which the liquid refrigerant flows.
  • the pipe 6 branches out into three liquid side branching pipes 7b, 7c and 7d.
  • the indoor units B, C and D comprise indoor heat exchangers 8b, 8c and 8d, respectively.
  • Electric reversible expansion valves 9b, 9c and 9d are disposed in the respective liquid side branching pipes 7b, 7c and 7d through which the low temperature and low pressure liquid refrigerant flows.
  • solenoid valves 10b, 10c and 10d are disposed in the respective gas side branching pipes 11b, 11c and 11d through which the low temperature and low pressure gaseous refrigerant flows.
  • the branching pipes 11b, 11c and 11d are integrated into a gas side primary pipe 12 through which the low temperature and low pressure gaseous refrigerant flows.
  • a control system which includes a sensor 13 for detecting a refrigerant condensation temperature, provided in a condensation pipe connected to a refrigerant discharge pipe from the compressor, a sensor 14 for detecting a temperature of a gaseous refrigerant discharg­ed from the compressor, sensors 15b, 15c and 15d for detecting the respective temperatures of the refrigerant before pressure decrease by the expansion valves 9b, 9c and 9d in heating operation mode, a controller 16 for processing the data from these sensors 13, 14, 15b, 15c and 15d and a means 17 for outputting command signals, on the basis of the commands from the controller 16, to the expansion valves 9b, 9c and 9d to make the opening degrees thereof in determined levels and to the solenoid valves 10b, 10c and 10d to close or open them.
  • the control system further includes sensors 18b, 18c and 18d provided in a conduit wall of the respective indoor heat exchangers 8b, 8c and 8d for detecting a saturation temperature of the refrigerant therein, and sensors 19b, 19c and 19d provided in the respective branching pipes 11b, 11c and 11d for detecting a temperature of the refrigerant therein.
  • reference numerals 20 and 21 desig­nate a wave form representing an opening degree of the electric reversible expansion valve associated with the inoperating indoor unit and a wave form representing an open/close condition of the solenoid valve associated with the inoperating indoor unit, respectively.
  • the gaseous refrigerant is delivered from the compressor 1, via the gas side primary pipe 12, the gas side branching pipe 11b, and the solenoid valve 10b, to the heat exchanger 8b in which the gaseous refrigerant is heat-exchanged with the indoor air and radiates heat outsides to condense into condensation or liquid refrigerant.
  • the liquid refrigerant is further delivered, through the expansion valve 9b, the liquid side branching pipe 7b, the liquid side primary pipe 6 and the receiver 5, to the heat exchanger 4 in which the liquid refrigerant is heat-exchanged with the outdoor air and absorbs heat to evaporate into gaseous refrigerant.
  • the gaseous refrigerant returns to the compressor 1 through the four-way valve 2 and the accumulator 3.
  • the expansion valves 9c and 9d, and the solenoid valves 10c and 10d associated with the inoperating indoor units C and D are fully closed.
  • the controller 16 calculates a temperature difference between the refrigerant temperature detected by the sensor 18b and the refrigerant temperature detected by the sensor 19b, or the subcooling degree SC of the refrigerant (step 301). If the subcooling degree SC is lower than the predetermined level E (step 302), i.e. the subcooling degree SC is with in a range 22a (Fig. 2), the controller 16 decides that the amount of the refrigerant circulating through the refrigeration cycle is insuf­ficient (step 303). Thereafter, in step 304, the controller 16 outputs commands to the means 17 to hold the solenoid valves 10c and 10d associated with the inoperat­ing units C and D in closed positions (as designated by 21a in Fig.
  • the controller 16 outputs commands to the means 17 to close the expansion valves 9c and 9d (step 306).
  • the control­ler 16 calculates the temperature difference (SC) again (step 301). If such difference is still with the range 22a, the above flow is repeated to extract the refrigerant from the inoperating units C and D.
  • step 302 if the subcooling degree SC is higher than the predetermined level F (step 302), i.e. the subcooling degree SC is with in a range 22b (Fig. 2), the controller 16 decides that the amount of the refrigerant circulating through the refrigeration cycle is excessive (step 308). Thereafter, in step 309, the controller 16 outputs commands to the means 17 to hold the expansion valves 9c and 9d associated with the inoperating units C and D in closed positions (as designated by 20a in Fig. 2) and to open the solenoid valves 10c and 10d for a period t3 (as designated by 21a in Fig. 2) by means of supplying a voltage HI (v) to the solenoid coil thereof.
  • step 310 the controller 16 outputs commands to the means 17 to close the solenoid valves 10c and 10d (step 311).
  • step t4 the controller 16 calcu­lates the temperature difference (SC) again (step 301). If such difference is still with the range 22b, the above flow is repeated to introduce the refrigerant into the inoperating units C and D.
  • step 302 when the subcooling degree SC is within a range 22c (Fig. 2) (step 302) and the amount of the refrigerant circulat­ing through the refrigeration cycle is proper (step 313), the solenoid valves 10c, 10d and the expansion valves 9c, 9d associated with the inoperating units C and D is held in closed positions (as designated by 21c and 20c in Fig. 2) so as to maintain the refrigerant within the inoperat­ing indoor units C and D.
  • step 314 After the lapse of sampling time period t5 (step 314), the process returns back to the step 301.
  • the gaseous refrigerant is delivered from the compressor 1, via the four-way valve 2, to the heat exchanger 4 in which the gaseous refrigerant is heat-exchanged with the indoor air and radiates heat outsides to condense into condensate or liquid refrige­rant.
  • the liquid refrigerant is further delivered, through the receiver 5, the liquid side primary pipe 6, the liquid side branching pipe 7b, and the expansion valve 9b, to the heat exchanger 8b in which the liquid refrigerant is heat-exchanged with the indoor air and absorbs heat to evaporate into gaseous refrigerant.
  • the gaseous refrigerant returns to the compressor 1 through the solenoid valve 10b, the gas side branching pipe 11b, the gas side primary pipe 12, the four-way valve 2 and the accumulator 3.
  • the expansion valves 9c and 9d, and the solenoid valves 10c and 10d associated with the inoperating indoor units C and D are fully closed.
  • the controller 16 calculates a temperature difference between the refrigerant temperature detected by the sensor 18b and the refrigerant temperature detected by the sensor 19b, or the super heat degree SH of the refrigerant (step 315). If the super heat degree SH is higher than the predetermined level G (step 316), the controller 16 decides that the amount of the refrigerant circulating through the refrigeration cycle is insuf­ficient (step 317). Proceeded are the same steps 318 to 321 as in case that the subcooling degree SC is lower than the predetermined level in heating operation mode. Therefore, the refrigerant in the inoperating units C and D is extracted therefrom.
  • step 316 the controller 16 decides that the amount of the refrigerant circulating through the refrigeration cycle is excessive (step 322). Proceeded are the same steps 323 to 326 as in case that the subcooling degree SC is higher than the predetermined level in heating opera­tion mode. Therefore, the refrigerant is introduced into the inoperating units C and D. In this case, since the refrigeration cycle is reversed one, the expansion valves 9c, 9d and the solenoid valves 10c, 10d operate reversely to each other in step 323.
  • step 316 When the super heat degree SH is within a range 23c (Fig. 2) (step 316) and the amount of the refrigerant circulating through the refrigeration cycle is proper (step 327), as same as in the subcooling degree SC is within the range 22c in the heating operation mode, the refrigerant is maintained within the inoperating indoor unit. After the lapse of sampling time period t6 (step 328), the process returns back to the step 315.
  • the controller decides that the refrigerant circulates through the refrigeration cycle in the amount greater than that for the proper operation of the cycle, and then outputs the commands to the command signal outputting means so that the expansion valves associated with the inoperating units are held in closed position and the solenoid valves associated with the inoperating units are switched over and held in open position for a predetermined period in the heating operation mode, and such expansion valves are switched over and held in open position and such solenoid valves are held in closed position in the cooling opera­tion mode.
  • the refrigerant circulating through the refrigeration cycle is introduced into and maintained within the inoperating units to reduce the amount of the circulating refrigerant.
  • the expansion valves and the solenoid valves are switched over into the open posi­tions.
  • the valves are held in the closed positions for the predetermined period of time so that the refrigeration cycle is subject to the above mentioned control and then the subcooling degree SC of the refrigerant and the super heating degree SH can change. Thereafter, if the subcooling degree SC and the super heating degree SH are not within the desired range, the above mentioned control is repeatedly conducted intermittently to reduce the excess refrigerant.
  • the controller decides that the refrigerant circulates through the refrigeration cycle in the amount less than that for the proper operation of the cycle, and then outputs the commands to the command signal outputting means so that the expansion valves associated with the inoperating units are switched over and held in open position and the solenoid valves associated with the inoperating units are held in closed position for a predetermined period in the heating operation mode, and such expansion valves are held in closed position and such solenoid valves are switched over and held in open position in the cooling operation mode. Therefore, the refrigerant maintained within the inoperating units is discharged into the refrigeration cycle to increase the amount of the circulating refrigerant. In this case, the control is conducted intermittently.
  • Such control changes the amount of the circulating refrigerant and makes any effects on the controlled variables except such amount, e.g. the super heating degree of the refrigerant from the compressor.
  • steps 329 to 332 Fig. 4
  • the expansion valves and the solenoid valves associated with the inoperating units are operated to interrupt the refrigerant flow from the inoperating units into the refrigeration cycle regardless of the values of the detected controlled variables in the excess refrigerant control, e.g. the subcooling degree SC and the super heating degree SH.
  • the controller 16 calculates a temperature difference between the temperature of the gaseous refrigerant from the compressor detected by the sensor 14 and the condensing temperature of the refrigerant detected by the sensor 13, or the super heating degree TdSH of the refrigerant from the compressor.
  • the controller 16 interrupts the excess refrigerant control when the following conditions, or the process K (steps 330 and 332 in Fig. 4) are satisfied.
  • the excess refrigerant control is temporary interrupted when the super heating degree TdSH of the refrigerant from the compressor becomes lower than the pre-set value SHset which makes the refri­gerant distribution control proper, i.e. TdSH-SHSet ⁇ 0 (Figs. 5 and 6).
  • TdSH-SHSet ⁇ 0 (Figs. 5 and 6).
  • the super heating degree TdSH is higher than the pre-set value SHset, in a J zone between the pre-set value SHset and a pre-set value J°C which is close to the pre-set value SHset, in case that the super heating degree TdSH has an intention of fallin down, i.e.
  • the super heating degree TdSH at the sampling point 2 becomes lower than the super heating degree TdSH ⁇ at the preceding sampling point 1 and closer to the pre-set value SHset, it is interrupted to discharge the refrigerant from the inoperating indoor units into the operating cycle by means of the steps 329, 330 or 331, 332, regardless of the subcooling degree or the super heating degree.
  • the super heating degree TdSH has an intention of increasing as designated by the dotted line in Fig. 6, it is continued to discharge the refrigerant from the inoperating indoor units into the operating cycle, even though the super heating degree TdSH is within the J zone. Accordingly, in this embodiment, it becomes possible to eliminate the interference between the excess refrigerant control and the refrigerant distribution control both of which are important for the multiple room type air conditioning system.
  • the present invention is not limited to the above embodiments, but the following modifications may be possible.
  • the sensors if the sensors are disposed in other positions, they can detect any other objects which correspond to such objections.
  • the sensors 18b, 18c and 18d are dispensed with, it is possible to calculate the saturation temperatures which should be detected by the sensors 18b, 18c and 18d by means of compensating for the detected values by the sensors 13, 15b, 15c and 15d with compensa­tion coefficients such as indoor unit capacities.
  • compensa­tion coefficients such as indoor unit capacities.
  • the amount of the refrigerant circulating through the cycle is always kept proper correspondence with the air conditioning conditions. Therefore, it is possible to prevent the increase in the pressure and the temperature of the refrigerant from the compressor, which increase is caused by the increase of the amount of the refrigerant circulating through the cycle. The inoperation of the compressor which is caused by the operation of the protection means therefor due to such increase in the pressure and the temperature is also prevented. Further, it is possible to prevent the increase of the compressor temperature which is caused by decrease of the refrigerant circulating through the cycle and to prevent the genera­tion of flash gas. Accordingly, the refrigeration cycle is kept in steady and proper, whereby a comfortable air conditioned circumstance is obtained.
  • the present invention even though one or some indoor units of the multiple room type air conditioning system become inoperating conditions, it is possible to make the refrigerant in the proper amount circulate through the refrigeration cycle correspondence with the number of the operating indoor units, so that the meritorious advantages that a comfortable air conditioned circumstance is obtained is given.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Conditioning Control Device (AREA)
EP88102741A 1987-03-20 1988-02-24 Système de conditionnement d'air pour plusieurs chambres et procédé pour sa commande Expired - Lifetime EP0282782B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP63855/87 1987-03-20
JP62063855A JPH07111283B2 (ja) 1987-03-20 1987-03-20 多室形空気調和装置

Publications (3)

Publication Number Publication Date
EP0282782A2 true EP0282782A2 (fr) 1988-09-21
EP0282782A3 EP0282782A3 (en) 1989-11-15
EP0282782B1 EP0282782B1 (fr) 1993-05-26

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EP88102741A Expired - Lifetime EP0282782B1 (fr) 1987-03-20 1988-02-24 Système de conditionnement d'air pour plusieurs chambres et procédé pour sa commande

Country Status (4)

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EP (1) EP0282782B1 (fr)
JP (1) JPH07111283B2 (fr)
KR (1) KR920004952B1 (fr)
DE (1) DE3881242T2 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2215867A (en) * 1988-02-09 1989-09-27 Toshiba Kk Air conditioner control system
ES2155745A1 (es) * 1998-04-20 2001-05-16 Samsung Electronics Co Ltd Acondicionador de aire de tipo multiple.
EP1662212A2 (fr) * 2004-11-23 2006-05-31 LG Electronics Inc. Conditionneur d'air et procédé de commande de celui-ci
WO2010118745A3 (fr) * 2009-04-16 2011-02-03 Danfoss A/S Procédé de régulation du fonctionnement d'un système de compression de vapeur
US9303901B2 (en) 2007-06-12 2016-04-05 Danfoss A/S Method for controlling a vapour compression system
US10365025B2 (en) * 2014-11-25 2019-07-30 Lennox Industries, Inc. Methods and systems for operating HVAC systems in low load conditions
CN112484274A (zh) * 2020-12-03 2021-03-12 佛山市顺德区美的电子科技有限公司 空调器及其控制方法、控制装置以及存储介质和电子设备

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KR100395919B1 (ko) * 2000-06-07 2003-08-27 삼성전자주식회사 공기조화기의 과열도 제어 시스템 및 그 제어 방법
KR100390434B1 (ko) * 2001-03-22 2003-07-07 엘지전자 주식회사 멀티에어컨의 냉매회수 제어방법
DE10149757A1 (de) * 2001-10-04 2003-04-10 Behr Gmbh & Co Verfahren zur scheibenbeschlagverhindernden Wärmepumpenleistungsregelung einer Fahrzeug-Klimaanlage
KR100626696B1 (ko) * 2005-07-25 2006-09-22 삼성전자주식회사 멀티 에어컨 시스템
US7977959B2 (en) 2007-09-27 2011-07-12 Formfactor, Inc. Method and apparatus for testing devices using serially controlled intelligent switches
JP6155824B2 (ja) * 2013-05-08 2017-07-05 ダイキン工業株式会社 空気調和装置
CN105276749B (zh) * 2014-06-24 2018-01-30 青岛海信日立空调系统有限公司 一种多联机空调系统的控制方法及装置

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US4307576A (en) * 1978-10-19 1981-12-29 Matsushita Electric Industrial Co., Ltd. Air conditioning system having a plurality of indoor units
US4484452A (en) * 1983-06-23 1984-11-27 The Trane Company Heat pump refrigerant charge control system
US4499739A (en) * 1982-11-22 1985-02-19 Mitsubishi Denki Kabushiki Kaisha Control device for refrigeration cycle
US4523435A (en) * 1983-12-19 1985-06-18 Carrier Corporation Method and apparatus for controlling a refrigerant expansion valve in a refrigeration system
US4644756A (en) * 1983-12-21 1987-02-24 Daikin Industries, Ltd. Multi-room type air conditioner

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4307576A (en) * 1978-10-19 1981-12-29 Matsushita Electric Industrial Co., Ltd. Air conditioning system having a plurality of indoor units
US4499739A (en) * 1982-11-22 1985-02-19 Mitsubishi Denki Kabushiki Kaisha Control device for refrigeration cycle
US4484452A (en) * 1983-06-23 1984-11-27 The Trane Company Heat pump refrigerant charge control system
US4523435A (en) * 1983-12-19 1985-06-18 Carrier Corporation Method and apparatus for controlling a refrigerant expansion valve in a refrigeration system
US4644756A (en) * 1983-12-21 1987-02-24 Daikin Industries, Ltd. Multi-room type air conditioner

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4926652A (en) * 1988-02-09 1990-05-22 Kabushiki Kaisha Toshiba Air conditioner system with control for optimum refrigerant temperature
GB2215867B (en) * 1988-02-09 1992-09-02 Toshiba Kk Air conditioner system with control for optimum refrigerant temperature
GB2215867A (en) * 1988-02-09 1989-09-27 Toshiba Kk Air conditioner control system
ES2155745A1 (es) * 1998-04-20 2001-05-16 Samsung Electronics Co Ltd Acondicionador de aire de tipo multiple.
EP1662212A2 (fr) * 2004-11-23 2006-05-31 LG Electronics Inc. Conditionneur d'air et procédé de commande de celui-ci
EP1662212A3 (fr) * 2004-11-23 2006-09-06 LG Electronics Inc. Conditionneur d'air et procédé de commande de celui-ci
US9303901B2 (en) 2007-06-12 2016-04-05 Danfoss A/S Method for controlling a vapour compression system
WO2010118745A3 (fr) * 2009-04-16 2011-02-03 Danfoss A/S Procédé de régulation du fonctionnement d'un système de compression de vapeur
US10365025B2 (en) * 2014-11-25 2019-07-30 Lennox Industries, Inc. Methods and systems for operating HVAC systems in low load conditions
US20190323750A1 (en) * 2014-11-25 2019-10-24 Lennox Industries Inc. Methods and systems for operating hvac systems in low load conditions
US11092368B2 (en) * 2014-11-25 2021-08-17 Lennox Industries Inc. Methods and systems for operating HVAC systems in low load conditions
US11493250B2 (en) 2014-11-25 2022-11-08 Lennox Industries Inc. Methods and systems for operating HVAC systems in low load conditions
US11573038B2 (en) 2014-11-25 2023-02-07 Lennox Industries Inc. Methods and systems for operating HVAC systems in low load conditions
CN112484274A (zh) * 2020-12-03 2021-03-12 佛山市顺德区美的电子科技有限公司 空调器及其控制方法、控制装置以及存储介质和电子设备
CN112484274B (zh) * 2020-12-03 2022-03-29 佛山市顺德区美的电子科技有限公司 空调器及其控制方法、控制装置以及存储介质和电子设备

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DE3881242T2 (de) 1993-12-09
KR880011537A (ko) 1988-10-28
KR920004952B1 (ko) 1992-06-22
JPS63233260A (ja) 1988-09-28
DE3881242D1 (de) 1993-07-01
JPH07111283B2 (ja) 1995-11-29
EP0282782B1 (fr) 1993-05-26
EP0282782A3 (en) 1989-11-15

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