WO2019128519A1 - 空调器*** - Google Patents

空调器*** Download PDF

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Publication number
WO2019128519A1
WO2019128519A1 PCT/CN2018/115750 CN2018115750W WO2019128519A1 WO 2019128519 A1 WO2019128519 A1 WO 2019128519A1 CN 2018115750 W CN2018115750 W CN 2018115750W WO 2019128519 A1 WO2019128519 A1 WO 2019128519A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
air conditioner
conditioner system
refrigerant
throttle device
Prior art date
Application number
PCT/CN2018/115750
Other languages
English (en)
French (fr)
Chinese (zh)
Inventor
王飞
付裕
罗荣邦
许文明
Original Assignee
青岛海尔空调器有限总公司
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 青岛海尔空调器有限总公司 filed Critical 青岛海尔空调器有限总公司
Priority to JP2020535566A priority Critical patent/JP2021508024A/ja
Priority to EP18896327.6A priority patent/EP3734193A4/en
Publication of WO2019128519A1 publication Critical patent/WO2019128519A1/zh

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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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • 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
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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

Definitions

  • the invention belongs to the technical field of air conditioners, and in particular relates to an air conditioner system.
  • the existing air conditioner system usually forms a refrigeration/heating cycle by a condenser, a throttle device, an evaporator, and a compressor, and the high temperature and high pressure gaseous refrigerant discharged from the compressor is condensed into a low temperature and high pressure liquid in the condenser, and is throttled.
  • the device is throttled into a low temperature and low pressure liquid, and then enters the evaporator to absorb heat and evaporate to complete a refrigeration/heating cycle.
  • the high-temperature and high-pressure gaseous refrigerant forms a low-temperature and high-pressure liquid refrigerant after heat exchange through the condenser, and then throttling and depressurization through the throttling device to form a low-temperature low-pressure gas-liquid two-phase zone refrigerant to enter the evaporation.
  • Heat exchange The larger the evaporation area, the higher the relative evaporation capacity. Among them, the low temperature and high pressure liquid refrigerant will increase the degree of subcooling if it continues to exotherm, thereby increasing the cooling capacity of the system cycle.
  • the refrigerant When the refrigerant is in heat exchange, more than 95% of the heat exchange is derived from the latent heat of vaporization in the two-phase region, while the isobaric specific heat capacity of the unidirectional zone (pure liquid, pure gas) is relatively small, and the heat exchange capacity accounts for the total system.
  • the proportion of the loop is small.
  • the pressure drop of the gaseous refrigerant in the pipeline is large, which is the main source of the system cyclic pressure loss, which will increase the circulating work volume, that is, increase the energy consumption of the system cycle.
  • FIG. 3 is a cycle schematic diagram of a conventional air conditioner during heating operation.
  • the actual operating temperature of the air conditioner heating operation is generally: A point high temperature gaseous 70 ° C refrigerant, enter the indoor heat exchanger and 20 ° C indoor environment for heat exchange, the temperature is reduced to 30 ° C, flow through After the line tube enters the throttling device, the temperature between point B and the throttling device (about 30 ° C) is much higher than the outdoor ambient temperature of 7 ° C, and the waste heat is wasted. If the residual heat is absorbed and utilized, the system cycle can be increased. Too cold.
  • the air conditioner system in order to improve the heating cycle effect of the air conditioner, includes a compressor, an indoor heat exchanger, a first throttle device, and an outdoor unit connected in series in the main circuit. a heat exchanger, wherein the main circuit is further provided with a heat exchanger; one side of the heat exchanger is connected to a first pipeline between the first throttle device and the indoor heat exchanger, The other side of the heat exchanger is connected to a second line between the first throttle device and the outdoor heat exchanger; and the refrigerant passing through the first line and the refrigerant passing through the second line
  • the refrigerant can exchange heat in the heat exchanger.
  • the first conduit passes through one side of the heat exchanger and/or the second conduit passes through the other side of the heat exchanger.
  • a second throttle device is further disposed in the main circuit, and the second throttle device is located between the heat exchanger and the indoor heat exchanger. In the pipeline section.
  • the second throttle device when the air conditioner system is operating in heating, the second throttle device is in a fully open state, and the first throttle device is used for refrigerant throttling.
  • the first throttle device when the air conditioner system is in a cooling operation, the first throttle device is in a fully open state, and the second throttle device is used to throttle the refrigerant.
  • the compressor is provided with a gas-liquid separator, and the refrigerant passes through the gas-liquid separator and is returned to the compressor.
  • the air conditioner system further includes a mode switching device for switching the air conditioner system between a cooling mode and a heating mode.
  • the mode switching device is a four-way valve.
  • a heat exchanger is added to the air conditioner system, and two sides of the heat exchanger are respectively connected to the first pipeline and the second pipeline, so that the refrigerant in the first pipeline is And the refrigerant in the second pipeline can exchange heat at the heat exchanger, which not only effectively increases the degree of subcooling of the refrigerant in the first pipeline, but also promotes evaporation of the refrigerant in the second pipeline, thereby Increased system heat.
  • the air conditioner of the present invention also uses the second throttle device to replace the first throttle device when the air conditioner is switched to the cooling mode by setting the second throttle device (at this time, the first throttle device is at The fully open state is to throttle the refrigerant, thereby avoiding the phenomenon that the cooling capacity is reduced when the refrigeration cycle occurs.
  • FIG. 1 is a schematic structural view of a first embodiment of an air conditioner system of the present invention
  • Figure 2 is a schematic structural view of a second embodiment of the air conditioner system of the present invention.
  • Fig. 3 is a schematic diagram of the cycle of a conventional air conditioner during heating operation.
  • Fig. 1 is a schematic structural view of a first embodiment of an air conditioner system of the present invention.
  • the air conditioner system of the present invention includes a compressor 1 connected in series in the main circuit, an indoor heat exchanger 2, a first throttle device 3, and an outdoor heat exchanger 4, and heat is also disposed in the main circuit.
  • Switch 5 the pipeline between the first throttle device 3 and the indoor heat exchanger 2 is used as the first pipeline M, and the pipeline between the first throttle device 3 and the outdoor heat exchanger 4 is used as the second conduit.
  • the pipe N, one side of the heat exchanger 5 is connected to the first pipe M, and the other side of the heat exchanger 5 is connected to the second pipe N, as shown in FIG.
  • the first pipe M Passing through one side of the heat exchanger 5 the second line N passes through the other side of the heat exchanger N. Further, the refrigerant passing through the first line M and the refrigerant passing through the second line N can exchange heat in the heat exchanger 5.
  • the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 flows to the indoor heat exchanger 2, and performs heat exchange in the indoor heat exchanger 2 to become a low-temperature high-pressure liquid refrigerant, and the refrigerant passes along the first pipeline.
  • M reaches point C, at which time the temperature of the refrigerant is around 20 ° C (the heat here is not fully utilized for waste heat).
  • the refrigerant enters the second line N after being throttled by the first throttle device 3, and the temperature of the refrigerant at the point D (after the throttled refrigerant) is about 5 °C.
  • the refrigerant in the first line M and the refrigerant in the second line N have a temperature difference, and both pass through the heat exchanger 5, the refrigerant in the first line M and the second line N are The heat exchange of the refrigerant at the heat exchanger 5 not only effectively increases the degree of subcooling of the refrigerant in the first line M (ie, the portion of the refrigerant from the point C to the first throttle device 3 continues to radiate and cool down), Moreover, the evaporation of the refrigerant in the second pipe N can be promoted (that is, the low-temperature refrigerant at the point D can evaporate and absorb the heat of the residual heat at the point C, which is equivalent to increasing the evaporation area and effectively improving the heat exchange capacity). Thereby increasing the heating capacity of the system.
  • the refrigerant in the first pipeline M is subjected to heat exchange in the heat exchanger 5 and then enters the first throttle device 3 to form a gas-liquid two-phase region of low temperature and low pressure at point D, and then passes through the outdoor
  • the heat exchanger 4 is returned to the compressor 1.
  • the heat exchanger 5 in the above may be a water tank containing water or any other suitable form as long as the refrigerant upstream and downstream of the first throttle device 3 can be exchanged.
  • the above design can effectively increase the heating capacity for the heating cycle and reduce the cooling capacity for the refrigeration cycle.
  • the air conditioner system of the present invention further includes a mode switching device (such as the four-way valve Q in FIG. 1) for switching the air conditioner system between the cooling mode and the heating mode.
  • a mode switching device such as the four-way valve Q in FIG. 1 for switching the air conditioner system between the cooling mode and the heating mode.
  • Fig. 2 is a structural schematic diagram of a second embodiment of the air conditioner system of the present invention.
  • a second throttle device 6 is further disposed in the main circuit of the air conditioner system of the present invention, and the second throttle device 6 is located in the first tube between the heat exchanger 5 and the indoor heat exchanger 2.
  • the second throttle device 6 is in a fully open state, and the first throttle device 3 is used for refrigerant throttling.
  • the principle of the air conditioner system in the first embodiment is the same.
  • the first throttle device 3 When the air conditioner system is switched to the cooling operation by the four-way valve Q, the first throttle device 3 is in the fully open state, and the second throttle device 6 is used for the refrigerant throttling. At this time, the refrigerant on both sides of the heat exchanger 5 has almost no temperature difference, that is, the heat exchanger 5 does not function during the refrigeration cycle, and the entire refrigeration cycle is a conventional refrigeration cycle, thereby avoiding a reduction in the amount of refrigeration during the cooling operation.
  • the compressor 1 is provided with a gas-liquid separator 11, and the gaseous refrigerant entering the compressor 1 first passes through the gas-liquid separator 11, and is then sucked by the compressor 1, thereby opening the next cycle. .
  • a heat exchanger is added to the air conditioner system of the present invention, and two sides of the heat exchanger are respectively connected to the first pipeline and the second pipeline, so that the refrigerant in the first pipeline is obtained.
  • the refrigerant in the second pipeline can exchange heat at the heat exchanger, which not only effectively increases the degree of subcooling of the refrigerant in the first pipeline, but also promotes evaporation of the refrigerant in the second pipeline, thereby Increased system heat.
  • the air conditioner of the present invention also uses the second throttle device to replace the first throttle device when the air conditioner is switched to the cooling mode by setting the second throttle device (at this time, the first throttle device is at The fully open state is to throttle the refrigerant, thereby avoiding the phenomenon that the cooling capacity is reduced when the refrigeration cycle occurs.

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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)
PCT/CN2018/115750 2017-12-29 2018-11-15 空调器*** WO2019128519A1 (zh)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2020535566A JP2021508024A (ja) 2017-12-29 2018-11-15 空調機システム
EP18896327.6A EP3734193A4 (en) 2017-12-29 2018-11-15 AIR CONDITIONING SYSTEM

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201711474413.3 2017-12-29
CN201711474413.3A CN108302839A (zh) 2017-12-29 2017-12-29 空调器***

Publications (1)

Publication Number Publication Date
WO2019128519A1 true WO2019128519A1 (zh) 2019-07-04

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ID=62867620

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2018/115750 WO2019128519A1 (zh) 2017-12-29 2018-11-15 空调器***

Country Status (4)

Country Link
EP (1) EP3734193A4 (ja)
JP (1) JP2021508024A (ja)
CN (1) CN108302839A (ja)
WO (1) WO2019128519A1 (ja)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108302839A (zh) * 2017-12-29 2018-07-20 青岛海尔空调器有限总公司 空调器***
CN110173913A (zh) * 2019-04-24 2019-08-27 同济大学 一种超大过冷度的蒸气压缩高温热泵机组
CN112428772B (zh) * 2020-10-30 2023-03-21 三花控股集团有限公司 流体控制组件及热管理***
CN113251474A (zh) * 2021-04-28 2021-08-13 青岛海尔空调器有限总公司 双压缩机空调器

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CN101268312A (zh) * 2005-09-22 2008-09-17 大金工业株式会社 空调装置
JP2010008002A (ja) * 2008-06-30 2010-01-14 Mitsubishi Electric Corp 冷凍サイクル装置
JP2011052884A (ja) * 2009-09-01 2011-03-17 Mitsubishi Electric Corp 冷凍空調装置
CN102272534A (zh) * 2009-01-15 2011-12-07 三菱电机株式会社 空气调节装置
CN106796045A (zh) * 2014-11-19 2017-05-31 三菱电机株式会社 空气调节装置
CN107076467A (zh) * 2014-11-04 2017-08-18 三菱电机株式会社 空气调节装置
CN107084562A (zh) * 2017-04-13 2017-08-22 青岛海尔空调器有限总公司 一种空调器及空调器的控制方法
CN108302839A (zh) * 2017-12-29 2018-07-20 青岛海尔空调器有限总公司 空调器***

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JPH10141798A (ja) * 1996-11-08 1998-05-29 Denso Corp ヒ−トポンプ装置
WO2014129361A1 (ja) * 2013-02-19 2014-08-28 三菱電機株式会社 空気調和装置
EP3264010B1 (en) * 2015-02-27 2022-04-13 Hitachi-Johnson Controls Air Conditioning, Inc. Heat exchange apparatus and air conditioner using same
CN106016505B (zh) * 2016-06-12 2019-05-31 青岛海尔空调器有限总公司 空调电路板降温装置

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Publication number Priority date Publication date Assignee Title
CN101268312A (zh) * 2005-09-22 2008-09-17 大金工业株式会社 空调装置
JP2010008002A (ja) * 2008-06-30 2010-01-14 Mitsubishi Electric Corp 冷凍サイクル装置
CN102272534A (zh) * 2009-01-15 2011-12-07 三菱电机株式会社 空气调节装置
JP2011052884A (ja) * 2009-09-01 2011-03-17 Mitsubishi Electric Corp 冷凍空調装置
CN107076467A (zh) * 2014-11-04 2017-08-18 三菱电机株式会社 空气调节装置
CN106796045A (zh) * 2014-11-19 2017-05-31 三菱电机株式会社 空气调节装置
CN107084562A (zh) * 2017-04-13 2017-08-22 青岛海尔空调器有限总公司 一种空调器及空调器的控制方法
CN108302839A (zh) * 2017-12-29 2018-07-20 青岛海尔空调器有限总公司 空调器***

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Title
See also references of EP3734193A4 *

Also Published As

Publication number Publication date
EP3734193A4 (en) 2021-02-24
JP2021508024A (ja) 2021-02-25
EP3734193A1 (en) 2020-11-04
CN108302839A (zh) 2018-07-20

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