EP1890093A2 - Sytème de gestion d'huile pour condenseurs multiples - Google Patents

Sytème de gestion d'huile pour condenseurs multiples Download PDF

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Publication number
EP1890093A2
EP1890093A2 EP07252844A EP07252844A EP1890093A2 EP 1890093 A2 EP1890093 A2 EP 1890093A2 EP 07252844 A EP07252844 A EP 07252844A EP 07252844 A EP07252844 A EP 07252844A EP 1890093 A2 EP1890093 A2 EP 1890093A2
Authority
EP
European Patent Office
Prior art keywords
oil
accumulator
refrigerant
management system
thermistors
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
EP07252844A
Other languages
German (de)
English (en)
Other versions
EP1890093A3 (fr
Inventor
Otaki Shizuo
Boon Siong Tee
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.)
Oyl Research & Development Centre Sdn Bhd
Original Assignee
Oyl Research & Development Centre Sdn Bhd
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 Oyl Research & Development Centre Sdn Bhd filed Critical Oyl Research & Development Centre Sdn Bhd
Publication of EP1890093A2 publication Critical patent/EP1890093A2/fr
Publication of EP1890093A3 publication Critical patent/EP1890093A3/fr
Ceased 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
    • F25B13/00—Compression machines, plants or systems, with reversible 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel 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
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors

Definitions

  • This invention relates to an oil management system for an air conditioning system consisting of a plurality of outdoor and indoor units.
  • the compressor of an air conditioner is charged with lubricating oil.
  • oil may be carried out of the compressor into the refrigerating system by the refrigerant when the system is operating, the level of oil in the compressor will decrease with time. This will over time adversely affect the working reliability of the compressor, as the decrease in oil level will have an adverse effect on the internal moving parts.
  • oil separators have been used to retain the oil discharged from the compressor and to return the same to the compressor. But when there are multiple compressors in a refrigeration cycle or where there are multiple outdoor units in a refrigeration cycle, the oil levels may differ from one compressor to another with some compressors operating with below optimum levels of oil.
  • a 4-way valve of at least one of the outdoor units is set to a heating mode while others are set to a cooling mode, runs the outdoor unit in heating mode and stops the other outdoor units.] Therefore, the discharged gas from the compressor of the outdoor unit in heating mode is directed into the casing of the compressors of the outdoor unit in the cooling mode through the gas-connecting pipe among the outdoor units. This pressurizes the casing of the compressor of the outdoor unit that is in a cooling mode and purge oil into the casing of the compressor of the outdoor unit that is in a heating mode through a oil balancing pipe that joins the outdoor units.
  • the present invention relates to an air-conditioning system that consists of multiple outdoor units (1), multiple indoor units, liquid connecting pipeline (20), gas connecting pipeline (21), a oil-balancing pipeline (22) and an electric system to control solenoid valves.
  • the outdoor unit (1) includes multiple compressors (2), 4-way valve (5), outdoor heat-exchanger (8), oil-separator (4) that is connected to the discharge pipe of the compressors, oil-accumulator (7) that is connected to an oil-return port of oil-separator (4) through a solenoid valve (6), an oil-return pipe (18) that connects the oil-accumulator (7) and a suction pipe of the each compressor (2) through metering device (17), a pipe (14) that connects the oil-accumulator (7) and a port (13) at outlet of outdoor unit through a solenoid valve (12) and a pipe (16) that connects the oil-accumulator (7) and a low pressure pipe through a solenoid valve (15), and a control system of these solenoid valves.
  • the liquid connecting pipeline (20) and the gas connecting pipeline (21) are shared among the multiple outdoor units and plural indoor units and the oil-balancing pipeline (22) is connected to every port (13).
  • the solenoid valves oil can be transferred among the outdoor units.
  • solenoid valves (6a) and (12a) are opened and (15a) is closed in outdoor unit (1a) and solenoid valves (12b) and (15b) are opened and (6b) is closed. Therefore, oil flows from the oil-accumulator (7a) in an outdoor unit (1a) to another oil-accumulator (7b) in an outdoor unit (1b).
  • the invention can also provide a system for detecting the oil level in the oil-accumulator and transferring the oil from an oil-accumulator containing more oil to another containing less oil, and thus balancing the oil level at all times.
  • the invention can further provide an oil-accumulator that sets a port of oil-balancing pipe between its centre and the bottom and a control system to operate those solenoid valves periodically and in same duration. Therefore, the oil level in every oil-accumulator is equalised.
  • Figure 1 is a piping diagram illustrative of a multiple air conditioning system including a preferred embodiment.
  • (1a) is an outdoor unit and includes two high-pressure compressors (2a-1) and (2a-2).
  • Check valves (3a-1) and (3a-2) are connected to the discharge pipe of each compressor.
  • the discharge pipes are joined and connected to an oil-separator (4a).
  • the oil-separator (4a) is connected with a pipe that the main refrigerant flows to a 4-way valve (5a) and a pipe that the separated oil flows to an oil-accumulator (7a) through a solenoid valve (6a).
  • the 4-way valve (5a) is connected through a pipe to the outdoor heat-exchanger (8a), gas connecting valve (10a) that is joined to the gas piping line (21) and a low pressure pipe (11a) to both suction pipes of the compressors (2a-1) and (2a-2).
  • the outdoor heat exchanger (8a) is also connected to the liquid connecting valve (9a) that is joined to the liquid piping line (20).
  • the oil-accumulator (7a) is connected with a pipe (14a) to the connecting valve (13a) that is joined to the oil-balancing pipeline (22) through a solenoid valve (12a), a pipe (16) connected to a low pressure pipe (11a) through a solenoid valve (15a) and two oil returning pipes (18a-1) and (18a-2) connected to each suction pipe of compressor (2a-1) or (2a-2) through each metering device (17a-1) or (17a-2).
  • Outdoor units (1b) and (1c) include the same structural elements as outdoor unit (1a) and are identified using sub-character a,b,c.
  • the liquid piping line (20) is connected to every liquid connecting valve (9a,9b,9c) and the gas piping line (21) is connected with every gas connecting valve (10a,10b,10c).
  • the oil-connecting valves (13a, 13b, 13c) are connected to the oil-balancing pipeline (22) and one another. Further, the liquid piping line (20) and the gas piping line (21) are connected in parallel with the indoor units (32) each that include the expansion device (30) and indoor heat-exchanger (31). Oil is charged in every compressor (2) and the same kind of oil is charged in the oil-accumulator (7).
  • solenoid valves (12) and (15) are closed and solenoid valve (6) is opened.
  • Refrigerant to be compressed by compressor (2) is discharged from compressor (2) with some oil and flows into the oil-separator (4) through the connected discharge pipe.
  • the oil-separator (4) the refrigerant and oil are separated and the refrigerant flows into the 4-way valve (5) and oil flows into the oil-accumulator (7) through the solenoid valve (6).
  • all oil cannot be separated from refrigerant at the oil-separator (4) and some oil flows out to refrigerating cycle with refrigerant.
  • Refrigerant entering the 4-way valve (5) flows to the low-pressure pipe (11) and distributes to each suction pipe of the compressor (2).
  • the gas refrigerant joins with oil that comes from the oil-accumulator (7) through oil returning pipe (18) and is inhaled by the compressor (2). At this time refrigerant brings oil that could not be separated at the oil-separator (4) back to the compressors (2).
  • oil return from the oil-accumulator (7a) to each compressor (2a-1) or (2a-2) is controlled by the metering device (17a-1) or (17a-2) on the oil returning pipes (18a-1) and (18a-2).
  • oil that goes through the entire refrigerant cycle is not distributed evenly at the gas piping line (21) when it comes back to each outdoor unit (1). If this uneven oil returning continues for long time, oil level in the oil-accumulator (7) of every outdoor unit (1) will be different.
  • the oil level in the oil-accumulator (7) is recovered by controlling solenoid valves (6, 12 and 15).
  • solenoid valve (6a) and (12a) are open and solenoid valve (15a) is closed in the outdoor unit (1a) and solenoid valve (12b) and (15b) are open and solenoid valve (6b) is closed in the outdoor unit (1b).
  • Pressure in the oil-accumulator (7a) is kept at high pressure by the opening solenoid valve (6a) and closing solenoid valve (15a).
  • pressure in the oil-accumulator (7b) will be low because solenoid valve (15b) is opened and solenoid valve (6b) is closed.
  • oil-accumulator (7a) and the oil-accumulator (7b) are linked through the oil-balancing pipeline (22) because of the opening of solenoid valves (12a) and (12b). Therefore oil in the oil-accumulator (7a) flows to the oil-accumulator (7b) due to pressure difference. And thus the oil levels can be equalised by flowing from oil-accumulator with more oil to oil-accumulator with less oil.
  • the intended structure is not to send oil from a casing of compressor directly, therefore the end result regardless of whether the high-pressure type compressor or low-pressure type compressor would be the same
  • FIG. 2 is a structural chart of one preferred embodiment of the present invention, where a ceiling of the oil-accumulator (7) has a port of the pipe that is connected the oil-separator (4) through a solenoid valve (6) and a port of the pipe (16) to go to a low pressure pipe (11) through a solenoid valve (15) and a bottom of the oil-accumulator (7) has two ports of oil returning pipes (18-1) and (18-2) to go to each suction pipe of compressor (2-1) or (2-2) through each metering device (17-1) or (17-2) and a port of the pipe (14) to go to oil connecting valve (13) that is joined with oil-balancing pipeline (22).
  • a thermistor (40) is set at the oil level in the vertical position, that is the same kind as the thermistor (40) is set at the bottom of the oil-accumulator and lead wire of thermistors (40) and (41) are connected to outside electronics circuit through a glass terminal (42).
  • Figure 3 is an electronics circuit diagram including these thermistors (40) and (41), where these thermistors (40) and (41) and two basic resisters form a bridged circuit and both intermediate voltage can be compared to output the result.
  • this circuit the same current flows through the thermistor (40) and (41), so if heat- radiation of the thermistors (40) and (41) is different, temperature of the thermistors (40) and (41) become different. This difference of temperature leads to a difference of resistance of the thermistors (40) and (41) and intermediate voltage is changed. As the thermistor (41) is near the bottom, it always submerged in oil.
  • both thermistors (40 and 41) When the oil level is enough to dip in the thermistor (40), both thermistors (40 and 41) will have the same heat-radiation performance so that the intermediate voltage of thermistors (40 and 41) is almost the same as the intermediate voltage of the basic resistors.
  • heat -radiation performance at thermistor (40) When oil level is poor to expose the thermistor (40) to gas refrigerant, heat -radiation performance at thermistor (40) will be decreased. This will subsequently lead to a decrease in resistance.
  • the intermediate voltage of thermistors (40 and 41) becomes higher than the intermediate voltage of the basic resistors.
  • the difference of the intermediate temperature between the thermistors and the basic resistors can be used to determine the level of oil; whether the oil level is sufficient to submerge the thermistor or if the oil level is poor to expose the thermistor to gas refrigerant. And by utilising this result oil, is able to be sent from the outdoor unit that is rich oil to the outdoor unit that is poor oil by choosing the solenoid valve control above mentioned.
  • oil detection is done by using thermistor.
  • thermistor The same result can be achieved by the use of a float and switch.
  • Figure 4 is a structural chart of one preferred embodiment of the present invention, where a ceiling of the oil-accumulator (7) has a port of the pipe that is connected the oil-separator (4) through a solenoid valve (6) and a port of the pipe (16) connected to a low pressure pipe (11) through a solenoid valve (15), the bottom of the oil-accumulator (7) has two ports of oil returning pipes (18-1) and (18-2) connected to each suction pipe of compressor (2-1) or (2-2) through each metering device (17-1) or (17-2).
  • a port of the pipe (14) is connected to connecting valve (13) that is joined with oil-balancing pipeline (22) is set on a wall in between midway and bottom in height.

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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)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Compressor (AREA)
EP07252844A 2006-07-18 2007-07-18 Sytème de gestion d'huile pour condenseurs multiples Ceased EP1890093A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
MYPI20063426A MY165544A (en) 2006-07-18 2006-07-18 Oil management system for multiple condensers

Publications (2)

Publication Number Publication Date
EP1890093A2 true EP1890093A2 (fr) 2008-02-20
EP1890093A3 EP1890093A3 (fr) 2011-02-16

Family

ID=38603391

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07252844A Ceased EP1890093A3 (fr) 2006-07-18 2007-07-18 Sytème de gestion d'huile pour condenseurs multiples

Country Status (5)

Country Link
EP (1) EP1890093A3 (fr)
CN (1) CN101226014A (fr)
AU (1) AU2007203328A1 (fr)
MY (1) MY165544A (fr)
SG (1) SG139673A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107110581A (zh) * 2014-11-21 2017-08-29 洋马株式会社 热泵
EP2416089A4 (fr) * 2009-03-31 2018-03-28 Mitsubishi Electric Corporation Dispositif de réfrigération
CN113503653A (zh) * 2021-08-04 2021-10-15 珠海格力电器股份有限公司 多压缩机制冷***及空调器
US11480369B2 (en) 2017-09-29 2022-10-25 Shanghai Highly Electrical Appliances Co., Ltd. Fresh-air air conditioning system and control method

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103512280B (zh) * 2013-04-17 2016-04-06 广东美芝制冷设备有限公司 空调器的油平衡方法
CN111207531B (zh) * 2020-01-13 2021-06-01 珠海格力电器股份有限公司 回油可靠的空调机组及控制方法

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0672875A2 (fr) 1994-03-15 1995-09-20 Mitsubishi Denki Kabushiki Kaisha Système de climatisation, accumulateur pour celui-ci et méthode de fabrication de l'accumulateur

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2564957B3 (fr) * 1984-05-23 1986-08-22 Electrolux Cr Sa Centrale de froid avec nouveau dispositif de controle du niveau d'huile des compresseurs
US6125642A (en) * 1999-07-13 2000-10-03 Sporlan Valve Company Oil level control system
JP4499863B2 (ja) * 2000-01-21 2010-07-07 東芝キヤリア株式会社 マルチ形空気調和機

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0672875A2 (fr) 1994-03-15 1995-09-20 Mitsubishi Denki Kabushiki Kaisha Système de climatisation, accumulateur pour celui-ci et méthode de fabrication de l'accumulateur

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2416089A4 (fr) * 2009-03-31 2018-03-28 Mitsubishi Electric Corporation Dispositif de réfrigération
CN107110581A (zh) * 2014-11-21 2017-08-29 洋马株式会社 热泵
EP3222938A4 (fr) * 2014-11-21 2018-07-18 Yanmar Co., Ltd. Pompe à chaleur
US10495325B2 (en) 2014-11-21 2019-12-03 Yanmar Co., Ltd. Heat pump
CN107110581B (zh) * 2014-11-21 2019-12-31 洋马株式会社 热泵
US11215370B2 (en) 2014-11-21 2022-01-04 Yanmar Power Technology Co., Ltd. Heat pump
US11480369B2 (en) 2017-09-29 2022-10-25 Shanghai Highly Electrical Appliances Co., Ltd. Fresh-air air conditioning system and control method
CN113503653A (zh) * 2021-08-04 2021-10-15 珠海格力电器股份有限公司 多压缩机制冷***及空调器

Also Published As

Publication number Publication date
AU2007203328A1 (en) 2008-02-07
MY165544A (en) 2018-04-03
EP1890093A3 (fr) 2011-02-16
CN101226014A (zh) 2008-07-23
SG139673A1 (en) 2008-02-29

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