EP3734192B1 - Système de climatiseur - Google Patents

Système de climatiseur Download PDF

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Publication number
EP3734192B1
EP3734192B1 EP18893890.6A EP18893890A EP3734192B1 EP 3734192 B1 EP3734192 B1 EP 3734192B1 EP 18893890 A EP18893890 A EP 18893890A EP 3734192 B1 EP3734192 B1 EP 3734192B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
air conditioner
pipeline
throttling device
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.)
Active
Application number
EP18893890.6A
Other languages
German (de)
English (en)
Other versions
EP3734192A4 (fr
EP3734192A1 (fr
Inventor
Fei Wang
Yu Fu
Rongbang LUO
Wenming XU
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.)
Qingdao Haier Air Conditioner Gen Corp Ltd
Original Assignee
Qingdao Haier Air Conditioner Gen Corp Ltd
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Publication date
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Publication of EP3734192A1 publication Critical patent/EP3734192A1/fr
Publication of EP3734192A4 publication Critical patent/EP3734192A4/fr
Application granted granted Critical
Publication of EP3734192B1 publication Critical patent/EP3734192B1/fr
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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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • 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
    • F25B2313/021—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit
    • F25B2313/0211—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit the auxiliary heat exchanger being only used during defrosting
    • 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
    • F25B2313/021—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit
    • F25B2313/0213—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit the auxiliary heat exchanger being only used during heating
    • 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
    • F25B2500/09—Improving heat transfers
    • 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
    • F25B2600/2501—Bypass 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves

Definitions

  • the present invention belongs to the technical field of air conditioners, and particularly relates to an air conditioner system.
  • An existing air conditioner system usually consists of a condenser, a throttling device, an evaporator, and a compressor to form a cooling/heating circulating loop.
  • a high-temperature and high-pressure gaseous refrigerant discharged from the compressor is condensed into low-temperature and high-pressure liquid in the condenser, and is throttled into low-temperature and low-pressure liquid through the throttling device. Then, the liquid enters the evaporator to absorb heat and be evaporated, thus completing one cooling/heating cycle.
  • Prior art document CN 106796045 (A ) discloses an air conditioning system (100) according to the preamble of claim 1, with an internal heat exchanger (20) for exchanging heat between a refrigerant flowing through refrigerant piping between an outdoor heat exchanger (3) and an expansion device (4), and a refrigerant flowing through refrigerant piping between the expansion device (4) and an indoor heat exchanger (5), a pressure detection device (31), a first temperature detection device (32) for detecting the temperature of a refrigerant flowing into the expansion device (4) during cooling operation, and a control unit (51) configured so that, during cooling operation, the control unit (51) controls the degree of opening of the expansion device (4) on the basis of the results of detection by the pressure detection device (31) and the first temperature detection device (32).
  • FIG. 3 is a schematic diagram of a cycle during heating operation of a traditional air conditioner.
  • an actual operation temperature point of the air conditioner for the heating operation is generally that: at point A, a high-temperature (70°C) gaseous refrigerant enters an indoor heat exchanger and an indoor environment being 20°C for heat exchange. After the temperature is reduced to 30°C, the high-temperature gaseous refrigerant flows through an online pipe, and then enters the throttling device. The temperature (about 30°C) between point B and the throttling device is much higher than the temperature (7°C) of an outdoor environment, so after heat is wasted. If the after heat is absorbed and used, the degree of supercooling of the system cycle would be increased.
  • an air conditioner system according to the present invention comprises the features of claim 1.
  • FIG. 1 is a schematic structure diagram of embodiment I of an air conditioner system not according to the present invention.
  • the air conditioner system includes a compressor 1, an indoor heat exchanger 2, a first throttling device 3, and an outdoor heat exchanger 4 which are connected in series in a main loop.
  • a heat exchanger 5 is further disposed in the main loop.
  • a pipeline between the first throttling device 3 and the indoor heat exchanger 2 is used as a first pipeline M
  • a pipeline between the first throttling device 3 and the outdoor heat exchanger 4 is used as a second pipeline N.
  • a connection mode as shown in FIG. 1 is that: the first pipeline M passes through one side of the heat exchanger 5, and the second pipeline N passes through the other side of the heat exchanger N. Furthermore, a refrigerant passing through the first pipeline M and a refrigerant passing through the second pipeline N may exchange heat in the heat exchanger 5.
  • a bypass defrosting loop P is further disposed between the compressor 1 and the outdoor heat exchanger 4. The bypass defrosting loop P is used for defrosting the outdoor heat exchanger 4 in a heating cycle process of an air conditioner.
  • a throttling valve 7 is disposed on the bypass defrosting loop P.
  • the throttling valve 7 is opened to enable the refrigerant to defrost the outdoor heat exchanger 4 through the bypass defrosting loop P.
  • the throttling valve 7 is closed.
  • a high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 flows to the indoor heat exchanger 2 to exchange heat in the indoor heat exchanger 2, and then becomes a low-temperature and high-pressure liquid refrigerant.
  • the refrigerant reaches a point C along the first pipeline M.
  • the temperature of the refrigerant is about 20°C (the heat here is after heat which is not fully used).
  • the refrigerant enters the second pipeline N after being throttled by the first throttling device 3.
  • the temperature of the refrigerant at a point D (the throttled refrigerant) is about 5°C.
  • the refrigerant in the first pipeline M and the refrigerant in the second pipeline N have a temperature difference, and the two refrigerants both pass through the heat exchanger 5.
  • the refrigerant in the first pipeline M and the refrigerant in the second pipeline N exchange heat in the heat exchanger 5, thereby not only effectively increasing the degree of supercooling of the refrigerant in the first pipeline M (i.e., the refrigerant from the point C to the first throttling device 3 continues to release heat for cooling), but also promoting the evaporation of the refrigerant in the second pipeline N (i.e., the low-temperature refrigerant at the point D may be evaporated to absorb the after heat at the point C, and this is equivalent to enlarging the evaporation area, which effectively improves the heat exchange capacity), thus improving the heating capacity of the system.
  • the refrigerant in the first pipeline M exchanges heat in the heat exchanger 5, then enters the first throttling device 3, so as to form a low-temperature and low-pressure gas-liquid two-phase region at the point D, and flows back to the compressor 1 through the outdoor heat exchanger 4.
  • the after heat may be reused to improve the heating capacity of the whole system.
  • the heat exchanger 5 above may be a water tank with water, or may be in any other suitable forms, as long as the refrigerants at the upper reach and the lower reach of the first throttling device 3 may exchange heat.
  • the foregoing design may effectively improve the heating capacity for a heating cycle, and may lower the cooling capacity for a cooling cycle.
  • the mode switching device is used for switching the air conditioner system between a cooling mode and a heating mode.
  • FIG. 2 is a schematic structure diagram of embodiment II of an air conditioner system of the present invention.
  • a second throttling device 6 is further disposed in the main loop of the air conditioner system of the present invention, and is located in a zone of the first pipeline M between the heat exchanger 5 and the indoor heat exchanger 2.
  • the second throttling device 6 is in a full open state, and the first throttling device 3 is used for throttling the refrigerant.
  • the principle is the same as the principle of the air conditioner system in embodiment I.
  • the first throttling device 3 When the air conditioner system is switched into cooling operation through the four-way valve Q, the first throttling device 3 is in a full open state, and the second throttling device 6 is used for throttling the refrigerant. At this time, the refrigerants on two sides of the heat exchanger 5 nearly have no temperature difference. That is, the heat exchanger 5 does not exert the effect in the cooling cycle process.
  • the whole cooling cycle is a conventional cooling cycle, thereby avoiding the lowering of the cooling capacity during the cooling operation.
  • the compressor 1 is provided with a gas-liquid separator 11.
  • a gaseous refrigerant entering the compressor 1 firstly passes through the gas-liquid separator 11, and then is absorbed by the compressor, so as to start the next cycle.
  • the heat exchanger is added in the air conditioner system of the present invention, and the two sides of the heat exchanger are connected with the first pipeline and the second pipeline.
  • the refrigerant in the first pipeline and the refrigerant in the second pipeline may exchange heat in the heat exchanger, thereby effectively increasing the degree of supercooling of the refrigerant in the first pipeline and promoting the evaporation of the refrigerant in the second pipeline, thus improving the heating capacity of the system.
  • the bypass defrosting loop is further added in the present invention.
  • the refrigerant In the defrosting process of the air conditioner, the refrigerant would continue to enter the indoor heat exchanger for heating, i.e., the refrigerant may enable the air conditioner to be still maintained in a heating working condition, thus achieving the objective of non-stop defrosting of the air conditioner.
  • the second throttling device when the air conditioner is switched into the cooling mode, the second throttling device is used to replace the first throttling device (at this time, the first throttling device is in the full open state) to throttle the refrigerant, thereby avoiding the phenomenon of the lowering of the cooling capacity in the cooling cycle.

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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)

Claims (3)

  1. Un système de climatiseur, comprenant un compresseur (1), un échangeur de chaleur intérieur (2), un premier dispositif d'étranglement (3), et un échangeur de chaleur extérieur (4) reliés en série dans une boucle principale,
    dans lequel un échangeur de chaleur (5) est en outre disposé dans la boucle principale, un côté de l'échangeur de chaleur (5) étant relié à une première conduite (M) entre un premier dispositif d'étranglement (3) et l'échangeur de chaleur intérieur (2), et un autre côté de l'échangeur de chaleur (5) étant relié à une deuxième conduite (N) entre le premier dispositif d'étranglement (3) et l'échangeur de chaleur extérieur (4), de telle sorte qu'un fluide frigorigène passant par la première conduite et un fluide frigorigène passant par la deuxième conduite échangent de la chaleur dans l'échangeur de chaleur,
    dans lequel la première conduite (M) traverse un côté de l'échangeur de chaleur, et la deuxième conduite (N) traverse l'autre côté de l'échangeur de chaleur (5),
    dans lequel le système de climatiseur comprend en outre un dispositif de commutation de mode étant une vanne à quatre voies (Q), caractérisé en ce que
    une boucle de dégivrage de dérivation (P) est disposée entre le compresseur et l'échangeur de chaleur extérieure, étant conçue pour dégivrer l'échangeur de chaleur extérieur dans un processus de chauffage du système de climatiseur,
    dans lequel un deuxième dispositif d'étranglement (6) est en outre disposé dans la boucle principale, et est situé dans une zone de la première conduite entre l'échangeur de chaleur et l'échangeur de chaleur intérieur, et
    le dispositif de commutation de mode est conçu pour basculer le système de climatiseur entre un mode de refroidissement où le premier dispositif d'étranglement (3)
    est dans un état complètement ouvert et le deuxième dispositif d'étranglement (6) est configuré de manière à réguler le fluide frigorigène, et un mode de chauffage où le deuxième dispositif d'étranglement (6) est dans un état complètement ouvert et le premier
    dispositif d'étranglement (3) est configuré de manière à réguler le fluide frigorigène.
  2. Le système de climatiseur selon la revendication 1, dans lequel une vanne d'étranglement (7) est disposée dans la boucle de dégivrage de dérivation, et est conçue de sorte que :
    lorsque l'échangeur de chaleur extérieur doit être dégivré, la vanne d'étranglement est ouverte pour permettre au fluide frigorigène sortant du compresseur de dégivrer l'échangeur de chaleur extérieur par la boucle de dégivrage de dérivation; et
    lorsque l'échangeur de chaleur extérieur n'a pas besoin d'être dégivré, la vanne d'étranglement est fermée.
  3. Le système de climatiseur selon l'une quelconque des revendications 1 à 2, dans lequel le compresseur est pourvu d'un séparateur gaz-liquide (11), et le fluide frigorigène retourne dans le compresseur après avoir traversé le séparateur gaz-liquide.
EP18893890.6A 2017-12-29 2018-11-15 Système de climatiseur Active EP3734192B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201711471670.1A CN108375248A (zh) 2017-12-29 2017-12-29 空调器***
PCT/CN2018/115749 WO2019128518A1 (fr) 2017-12-29 2018-11-15 Système de climatiseur

Publications (3)

Publication Number Publication Date
EP3734192A1 EP3734192A1 (fr) 2020-11-04
EP3734192A4 EP3734192A4 (fr) 2021-03-03
EP3734192B1 true EP3734192B1 (fr) 2024-01-10

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP18893890.6A Active EP3734192B1 (fr) 2017-12-29 2018-11-15 Système de climatiseur

Country Status (5)

Country Link
EP (1) EP3734192B1 (fr)
JP (1) JP2021508809A (fr)
CN (1) CN108375248A (fr)
ES (1) ES2970620T3 (fr)
WO (1) WO2019128518A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108375248A (zh) * 2017-12-29 2018-08-07 青岛海尔空调器有限总公司 空调器***
US20220187027A1 (en) * 2019-04-23 2022-06-16 Ckd Corporation Heat exchange system

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009228979A (ja) * 2008-03-24 2009-10-08 Mitsubishi Electric Corp 空気調和装置
JP4789978B2 (ja) * 2008-06-30 2011-10-12 三菱電機株式会社 冷凍サイクル装置
CN102272534B (zh) * 2009-01-15 2014-12-10 三菱电机株式会社 空气调节装置
JP2010164257A (ja) * 2009-01-16 2010-07-29 Mitsubishi Electric Corp 冷凍サイクル装置及び冷凍サイクル装置の制御方法
JP5452138B2 (ja) * 2009-09-01 2014-03-26 三菱電機株式会社 冷凍空調装置
JP5434460B2 (ja) * 2009-10-15 2014-03-05 三菱電機株式会社 ヒートポンプ装置
JP2016061537A (ja) * 2014-09-22 2016-04-25 株式会社マック 二段減圧式熱交換器及びそれを組み入れた冷凍サイクル
AU2014410881B2 (en) * 2014-11-04 2018-01-18 Mitsubishi Electric Corporation Air-conditioning apparatus
US10247440B2 (en) * 2014-11-19 2019-04-02 Mitsubishi Electric Corporation Air-conditioning apparatus with control of expansion valve to maintain desired degree of subcooling
CN106016535B (zh) * 2016-05-31 2019-01-08 广东美的制冷设备有限公司 喷气增焓空调***及其除霜控制方法
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
CN107300240A (zh) * 2017-05-17 2017-10-27 青岛海尔空调器有限总公司 空调器除霜控制方法
CN108375248A (zh) * 2017-12-29 2018-08-07 青岛海尔空调器有限总公司 空调器***

Also Published As

Publication number Publication date
ES2970620T3 (es) 2024-05-29
EP3734192A4 (fr) 2021-03-03
WO2019128518A1 (fr) 2019-07-04
EP3734192A1 (fr) 2020-11-04
CN108375248A (zh) 2018-08-07
JP2021508809A (ja) 2021-03-11

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