WO2019128516A1 - Système de climatisation - Google Patents

Système de climatisation Download PDF

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Publication number
WO2019128516A1
WO2019128516A1 PCT/CN2018/115747 CN2018115747W WO2019128516A1 WO 2019128516 A1 WO2019128516 A1 WO 2019128516A1 CN 2018115747 W CN2018115747 W CN 2018115747W WO 2019128516 A1 WO2019128516 A1 WO 2019128516A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
air conditioner
conditioner system
refrigerant
throttle device
Prior art date
Application number
PCT/CN2018/115747
Other languages
English (en)
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 JP2020535568A priority Critical patent/JP7175985B2/ja
Priority to FIEP18893462.4T priority patent/FI3734167T3/fi
Priority to ES18893462T priority patent/ES2939186T3/es
Priority to PL18893462.4T priority patent/PL3734167T3/pl
Priority to DK18893462.4T priority patent/DK3734167T3/da
Priority to EP18893462.4A priority patent/EP3734167B1/fr
Publication of WO2019128516A1 publication Critical patent/WO2019128516A1/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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/14—Heat exchangers specially adapted for separate outdoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/41—Defrosting; Preventing freezing
    • F24F11/42—Defrosting; Preventing freezing of outdoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/65—Electronic processing for selecting an operating mode
    • F24F11/67—Switching between heating and cooling modes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/30—Arrangement or mounting of heat-exchangers
    • 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
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B2400/23—Separators
    • 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

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 increases the amount of work done by the cycle, that is, increases 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 provided by the present invention 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 and a first gas-liquid separator, and a bypass defrost circuit is disposed between the compressor and the outdoor heat exchanger;
  • One side is connected to a first line between the first throttling device and the indoor heat exchanger, and the other side of the heat exchanger is in heat exchange with the first throttling device and the outdoor a second line between the tubes is connected;
  • a refrigerant passing through the first line and a refrigerant passing through the second line are capable of performing heat exchange in the heat exchanger;
  • the first gas-liquid separator is located a second pipeline section between the heat exchanger and the indoor heat exchanger, and a bypass pipeline is disposed between the first gas-liquid separator and the compressor; the bypass The defrost circuit is used to perform a defrosting operation on the outdoor heat exchanger during the heating of the air conditioner.
  • a second throttle device is disposed in the bypass line, and when the air conditioner system is heated, the second throttle device is used to control the gaseous refrigerant. flow.
  • 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 third throttle device is further disposed in the main circuit, and the third throttle device is located between the heat exchanger and the indoor heat exchanger. In the pipeline section.
  • the third throttle device when the air conditioner system is operating in heating, the third 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 third throttle device is used to throttle the refrigerant.
  • a throttle valve is disposed in the bypass defrost circuit, and when the outdoor heat exchanger requires defrosting, the throttle valve is opened to enable compression from the The refrigerant flowing out of the machine performs a defrosting operation on the outdoor heat exchanger through the bypass defrosting circuit; when the outdoor heat exchanger does not require defrosting, the throttle valve is closed.
  • the compressor is provided with a second gas-liquid separator, and the refrigerant is returned to the compressor after passing through the second gas-liquid separator.
  • bypass line is connected upstream of the second gas-liquid separator.
  • the air conditioner system further includes a four-way valve for switching the air conditioner system between a cooling mode and a heating mode.
  • 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.
  • a bypass line is disposed between the first gas-liquid separator of the present invention and the compressor, and the gaseous refrigerant passing through the gas-liquid separator can enter the suction port of the compressor through the bypass line, thereby reducing
  • the pressure loss of this part of the gaseous refrigerant in the heating cycle is equivalent to increasing the pressure of the suction port of the compressor, thereby reducing the power consumption of the compressor and increasing the circulation of the refrigerant in the heating cycle of the air conditioner system.
  • the invention also adds a bypass defrost circuit, in the process of defrosting the air conditioner, the refrigerant will continue to enter the indoor heat exchanger for heating, that is, the air conditioner can still be maintained in the heating condition, and the air conditioner is not stopped.
  • the purpose of defrosting the air conditioner of the present invention also uses the third throttle device to replace the first throttle device when the air conditioner is switched to the cooling mode by setting the third 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.
  • a first gas-liquid separator 6 is further disposed in the main circuit, and the first gas-liquid separator 6 is located in the second pipeline N section between the heat exchanger 5 and the outdoor heat exchanger 4, and the first gas A bypass line L is provided between the liquid separator 6 and the compressor 1.
  • a bypass defrosting circuit P is provided between the compressor 1 and the outdoor heat exchanger 4, and the bypass defrosting circuit P is used during the air conditioning heating cycle.
  • the outdoor heat exchanger 4 is subjected to a defrosting operation.
  • the bypass defrosting circuit P is provided with a throttle valve 9, and when the outdoor heat exchanger 4 needs defrosting, the throttle valve 9 is opened to pass the refrigerant through the bypass defrosting circuit P.
  • the outdoor heat exchanger 4 is subjected to a defrosting operation; when the outdoor heat exchanger 4 does not require defrosting, the throttle valve 9 is closed.
  • 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 heat production.
  • the refrigerant that has undergone heat exchange through the heat exchanger 5 enters the first gas-liquid separator 6, and the gaseous refrigerant separated by the first gas-liquid separator 6 is directly returned to the compressor 1 along the bypass line L.
  • the amount of refrigerant circulation at the time is used to enhance the heat production.
  • the liquid refrigerant passing through the first gas-liquid separator 6 is returned to the compressor 1 through the outdoor heat exchanger 4.
  • a second throttle device 7 is provided on the bypass line L.
  • the second throttle device 7 is used to control the flow rate of the gaseous refrigerant, that is, it can be adjusted according to actual operating conditions.
  • the opening of the second throttle device 7 facilitates flexible control of the amount of gaseous refrigerant passing.
  • the second throttle device 7 can be closed so that the bypass line L does not participate in the refrigeration cycle.
  • the heat exchanger 5 in the above may be a water tank containing water or any other suitable form as long as heat can be exchanged between the upstream and downstream refrigerants of the first throttle device 3.
  • 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 third throttle device 8 is disposed in the main circuit of the air conditioner system of the present invention, and the third throttle device 8 is located between the heat exchanger 5 and the indoor heat exchanger 2.
  • the third throttle device 8 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 third throttle device 8 is used for the refrigerant throttling while the second throttle device 7 is closed. 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. This avoids reducing the amount of cooling during 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.
  • the bypass line L is connected to the upstream of the second gas-liquid separator 11.
  • 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.
  • a bypass line is disposed between the first gas-liquid separator of the present invention and the compressor, and the gaseous refrigerant passing through the first gas-liquid separator can enter the suction port of the compressor through the bypass line, thereby The pressure loss of the part of the gaseous refrigerant in the heating cycle is reduced, which is equivalent to increasing the pressure of the compressor suction port, thereby reducing the power consumption of the compressor and increasing the refrigerant circulation of the air conditioner system during the heating cycle. Amount, to enhance the purpose of heating.
  • the invention also adds a bypass defrost circuit, in the process of defrosting the air conditioner, the refrigerant will continue to enter the indoor heat exchanger for heating, that is, the air conditioner can still be maintained in the heating condition, and the air conditioner is not stopped.
  • the purpose of defrosting the air conditioner of the present invention also uses the third throttle device to replace the first throttle device when the air conditioner is switched to the cooling mode by setting the third 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)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical & Material Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Signal Processing (AREA)
  • Fuzzy Systems (AREA)
  • Mathematical Physics (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Conditioning Control Device (AREA)
  • Central Air Conditioning (AREA)
  • Sorption Type Refrigeration Machines (AREA)

Abstract

L'invention concerne un système de climatisation 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 un circuit principal. Le circuit principal est muni également d'un échangeur de chaleur (5) et d'un premier séparateur gaz-liquide (6). Un circuit de dégivrage en dérivation (P) est disposé entre le compresseur (1) et l'échangeur de chaleur extérieur (4). Un côté de l'échangeur de chaleur (5) est relié à une première canalisation (M) entre le premier dispositif d'étranglement (3) et l'échangeur de chaleur intérieur (2), et l'autre côté de l'échangeur de chaleur (5) est relié à une seconde canalisation (N) entre le premier dispositif d'étranglement (3) et l'échangeur de chaleur extérieur (4). Un fluide frigorigène passant à travers la première canalisation (M), et un fluide frigorigène passant à travers la seconde canalisation (N), peuvent échanger de la chaleur dans l'échangeur de chaleur (5). Une canalisation de dérivation (L) est disposée entre le premier séparateur gaz-liquide (6) et le compresseur (1). Le système de climatisation peut atteindre le but d'effectuer un dégivrage sans être éteint, augmentant en même temps le degré de sur-refroidissement du fluide frigorigène dans la première canalisation (M).
PCT/CN2018/115747 2017-12-29 2018-11-15 Système de climatisation WO2019128516A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
JP2020535568A JP7175985B2 (ja) 2017-12-29 2018-11-15 空調機システム
FIEP18893462.4T FI3734167T3 (fi) 2017-12-29 2018-11-15 Ilmastointilaitejärjestelmä
ES18893462T ES2939186T3 (es) 2017-12-29 2018-11-15 Sistema de acondicionador de aire
PL18893462.4T PL3734167T3 (pl) 2017-12-29 2018-11-15 System klimatyzatora
DK18893462.4T DK3734167T3 (en) 2017-12-29 2018-11-15 Airconditionsystem
EP18893462.4A EP3734167B1 (fr) 2017-12-29 2018-11-15 Système de climatisation

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201711474368.1 2017-12-29
CN201711474368.1A CN108332285B (zh) 2017-12-29 2017-12-29 空调器系统

Publications (1)

Publication Number Publication Date
WO2019128516A1 true WO2019128516A1 (fr) 2019-07-04

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Application Number Title Priority Date Filing Date
PCT/CN2018/115747 WO2019128516A1 (fr) 2017-12-29 2018-11-15 Système de climatisation

Country Status (8)

Country Link
EP (1) EP3734167B1 (fr)
JP (1) JP7175985B2 (fr)
CN (1) CN108332285B (fr)
DK (1) DK3734167T3 (fr)
ES (1) ES2939186T3 (fr)
FI (1) FI3734167T3 (fr)
PL (1) PL3734167T3 (fr)
WO (1) WO2019128516A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114636224A (zh) * 2022-03-31 2022-06-17 青岛海尔空调电子有限公司 空调系统、用于控制空调系统的方法及装置、存储介质

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* Cited by examiner, † Cited by third party
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CN108332285B (zh) * 2017-12-29 2019-12-06 青岛海尔空调器有限总公司 空调器系统
CN110836480B (zh) * 2018-08-17 2021-10-29 青岛海尔空调器有限总公司 空调器除霜控制方法
CN108954920A (zh) * 2018-08-22 2018-12-07 珠海格力电器股份有限公司 空调器的换热机及空调器
CN109269017A (zh) * 2018-09-03 2019-01-25 南京天加环境科技有限公司 一种不停机除霜的多联机单模块系统
CN113646593B (zh) * 2019-04-05 2022-11-15 三菱电机株式会社 制冷循环装置
CN110736210B (zh) * 2019-09-26 2021-10-29 青岛海尔空调器有限总公司 用于空调除霜的控制方法、控制装置及空调
CN110736208B (zh) * 2019-09-26 2021-11-23 青岛海尔空调器有限总公司 用于空调除霜的控制方法、控制装置及空调
CN110736211B (zh) * 2019-09-26 2021-11-23 青岛海尔空调器有限总公司 用于空调除霜的控制方法、控制装置及空调
CN110736217B (zh) * 2019-09-27 2021-11-23 青岛海尔空调器有限总公司 用于空调除霜的控制方法、控制装置及空调
CN110736212B (zh) * 2019-09-27 2022-04-19 青岛海尔空调器有限总公司 用于空调除霜的控制方法、控制装置及空调
CN111578552A (zh) * 2020-05-22 2020-08-25 广东美的制冷设备有限公司 空调系统、空调器和空调系统的控制方法
CN112033035B (zh) * 2020-09-10 2021-07-20 珠海格力电器股份有限公司 制冷系统的喷液控制方法及冷凝机组
CN112539452B (zh) * 2020-12-18 2021-12-03 珠海格力电器股份有限公司 一种多联机空调及其控制方法
CN113465021A (zh) * 2021-04-28 2021-10-01 青岛海尔空调器有限总公司 用于双压缩机空调器的控制方法
CN115200179B (zh) * 2022-06-28 2023-09-29 珠海格力电器股份有限公司 一种空调系统及其节流控制方法、装置和存储介质

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005049002A (ja) * 2003-07-28 2005-02-24 Matsushita Electric Ind Co Ltd 空気調和機
CN103486783A (zh) * 2013-09-26 2014-01-01 广东美的制冷设备有限公司 空调器系统及其化霜控制方法
WO2015122056A1 (fr) * 2014-02-13 2015-08-20 日立アプライアンス株式会社 Dispositif climatiseur
JP2016106211A (ja) * 2016-01-20 2016-06-16 三菱電機株式会社 空気調和装置
CN108332285A (zh) * 2017-12-29 2018-07-27 青岛海尔空调器有限总公司 空调器系统

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001012811A (ja) * 1999-06-29 2001-01-19 Bosch Automotive Systems Corp 冷房装置
JP3918421B2 (ja) * 2000-09-21 2007-05-23 三菱電機株式会社 空気調和機、空気調和機の運転方法
JP2009228979A (ja) * 2008-03-24 2009-10-08 Mitsubishi Electric Corp 空気調和装置
JP5318099B2 (ja) * 2008-06-13 2013-10-16 三菱電機株式会社 冷凍サイクル装置、並びにその制御方法
CN102272534B (zh) * 2009-01-15 2014-12-10 三菱电机株式会社 空气调节装置
CN202328555U (zh) * 2011-12-07 2012-07-11 珠海格力电器股份有限公司 室外换热装置及空调系统
CN202928175U (zh) * 2012-08-14 2013-05-08 苏州必信空调有限公司 一种空调系统
CN103851838B (zh) * 2012-11-30 2016-06-15 苏州必信空调有限公司 板式一体化制冷剂热回收循环系统
JP6080939B2 (ja) * 2013-02-19 2017-02-15 三菱電機株式会社 空気調和装置
CN103486780A (zh) * 2013-09-13 2014-01-01 青岛海信日立空调系统有限公司 补气增焓多联式空调系统
AU2014391505B2 (en) * 2014-04-22 2018-11-22 Mitsubishi Electric Corporation Air conditioner
CN105333599A (zh) * 2014-07-08 2016-02-17 海信（山东）空调有限公司 一种补气增焓空调系统
JPWO2016059696A1 (ja) * 2014-10-16 2017-05-25 三菱電機株式会社 冷凍サイクル装置
WO2016189739A1 (fr) * 2015-05-28 2016-12-01 三菱電機株式会社 Dispositif de climatisation
CN105485767A (zh) * 2015-12-22 2016-04-13 珠海格力电器股份有限公司 多联机空调系统和控制方法
JP6643630B2 (ja) * 2016-02-17 2020-02-12 パナソニックＩｐマネジメント株式会社 空気調和装置
CN106440461B (zh) * 2016-11-03 2019-03-01 青岛海信日立空调系统有限公司 一种制冷剂填充的控制方法及空调

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005049002A (ja) * 2003-07-28 2005-02-24 Matsushita Electric Ind Co Ltd 空気調和機
CN103486783A (zh) * 2013-09-26 2014-01-01 广东美的制冷设备有限公司 空调器系统及其化霜控制方法
WO2015122056A1 (fr) * 2014-02-13 2015-08-20 日立アプライアンス株式会社 Dispositif climatiseur
JP2016106211A (ja) * 2016-01-20 2016-06-16 三菱電機株式会社 空気調和装置
CN108332285A (zh) * 2017-12-29 2018-07-27 青岛海尔空调器有限总公司 空调器系统

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3734167A4 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114636224A (zh) * 2022-03-31 2022-06-17 青岛海尔空调电子有限公司 空调系统、用于控制空调系统的方法及装置、存储介质
CN114636224B (zh) * 2022-03-31 2024-03-22 青岛海尔空调电子有限公司 空调系统、用于控制空调系统的方法及装置、存储介质

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