EP3734199B1 - Système de climatisation - Google Patents

Système de climatisation Download PDF

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Publication number
EP3734199B1
EP3734199B1 EP18894319.5A EP18894319A EP3734199B1 EP 3734199 B1 EP3734199 B1 EP 3734199B1 EP 18894319 A EP18894319 A EP 18894319A EP 3734199 B1 EP3734199 B1 EP 3734199B1
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EP
European Patent Office
Prior art keywords
heat exchanger
pipeline
air conditioner
refrigerant
conditioner system
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
EP18894319.5A
Other languages
German (de)
English (en)
Other versions
EP3734199A4 (fr
EP3734199A1 (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
Chongqing Haier Air Conditioner Co Ltd
Original Assignee
Qingdao Haier Air Conditioner Gen Corp Ltd
Chongqing Haier Air Conditioner Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Qingdao Haier Air Conditioner Gen Corp Ltd, Chongqing Haier Air Conditioner Co Ltd filed Critical Qingdao Haier Air Conditioner Gen Corp Ltd
Publication of EP3734199A1 publication Critical patent/EP3734199A1/fr
Publication of EP3734199A4 publication Critical patent/EP3734199A4/fr
Application granted granted Critical
Publication of EP3734199B1 publication Critical patent/EP3734199B1/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
    • 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
    • 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
    • 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
    • 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
    • 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
    • F25B2313/021—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
    • 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
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/31—Low ambient temperatures

Definitions

  • the present invention belongs to the technical field of air conditioners, and more particularly relates to an air conditioner system.
  • An existing air conditioner system generally uses a condenser, a throttle device, an evaporator and a compressor to form a refrigeration/heating cycle circuit.
  • a high-temperature high-pressure gaseous refrigerant discharged by the compressor is condensed into low-temperature high-pressure liquid in the condenser, is throttled into low-temperature low-pressure liquid through the throttle device, and then enters the evaporator to absorb heat and evaporate to finish a refrigeration/heating cycle.
  • the heat exchange apparatus includes: a heat-transfer pipe through which a refrigerant flows; a heat exchanger in which a plurality of the heat-transfer pipes are connected to one another; a distributor that distributes the refrigerant to the plurality of heat- transfer pipes; an inflow pipe that causes the refrigerant to flow into the distributor; and a confluent pipe which is connected to an intermediate position of the inflow pipe and in which the refrigerant flowing through an inside thereof is to merge with the refrigerant flowing through an inside of the inflow pipe.
  • document WO 2017/215281 A1 discloses a cooling device for an air conditioner circuit board, comprising a compressor (1), an outdoor heat exchanger (2), a gas-liquid separator (3) and an indoor heat-exchanger (4) which are connected in sequence.
  • a low-temperature high-pressure liquid refrigerant is formed after the high-temperature high-pressure gaseous refrigerant exchanges heat through the condenser, and then, through throttling and pressure reduction by the throttle device, a low-temperature low-pressure gas-liquid two-phase region refrigerant is formed, and enters the evaporator for heat exchange.
  • FIG. 3 is a schematic cycle diagram of a conventional air conditioner during heating operation.
  • actual operation temperature points of the heating operation of the air conditioner are generally as follows: from a point A, a high-temperature gaseous refrigerant being 70°C enters an indoor heat exchanger and an indoor environment being 20°C for heat exchange to lower the temperature to 30°C, and enters the throttle device after flowing through an on-line pipe, wherein the temperature (about 30°C) between a point B and the throttle device is much higher than an outdoor environment temperature being 7°C, and afterheat is wasted. If the afterheat is absorbed and used, the degree of supercooling of the system refrigerant cycle can also be increased.
  • the heat exchanger is added to the air conditioner system, and the two sides of the heat exchanger are respectively connected to the first pipeline and the second pipeline. Therefore, the refrigerant in the first pipeline and the refrigerant in the second pipeline can exchange heat in the heat exchanger. Not only is the degree of supercooling of the refrigerant in the first pipeline effectively increased, but also the evaporation of the refrigerant in the second pipeline can be promoted, so that a heating capacity of the system is improved.
  • bypass pipeline is disposed between the first gas-liquid separator and the compressor, and the gaseous refrigerant passing through the first gas-liquid separator can enter an air suction opening of the compressor through this bypass pipeline, so that the pressure loss of this part of the gaseous refrigerant in a heating cycle is reduced, which is equivalent to that the pressure of the air suction opening of the compressor is increased, the power consumption of the compressor is further reduced, the circulation volume of the refrigerant during the heating cycle of the air conditioner system is increased, and the purpose of improving the heating capacity is achieved.
  • the air conditioner of the present invention is also provided with the third throttle device, so that when the air conditioner is switched to the refrigeration mode, the third throttle device is used to replace the first throttle device (at the moment, the first throttle device is in the fully open state) to throttle the refrigerant. Therefore, the occurrence of a phenomenon that a refrigeration capacity is reduced in a refrigeration cycle is avoided.
  • Figure 1 is a schematic structure diagram of an embodiment 1.
  • the air conditioner system of the present invention includes a compressor 1, an indoor heat exchanger 2, a first throttle device 3, and an outdoor heat exchanger 4 connected in series in a main circuit.
  • the main circuit is also provided with a heat exchanger 5.
  • a pipeline between the first throttle device 3 and the indoor heat exchanger 2 is used as a first pipeline M
  • a pipeline between the first throttle device 3 and the outdoor heat exchanger 4 is used as a second pipeline N.
  • One side of the heat exchanger 5 is connected to the first pipeline M
  • the other side of the heat exchanger 5 is connected to the second pipeline N.
  • 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.
  • a refrigerant passing through the first pipeline M and a refrigerant passing through the second pipeline N can exchange heat in the heat exchanger 5.
  • the main circuit is also provided with a first gas-liquid separator 6.
  • the first gas-liquid separator 6 is positioned in a second pipeline N section between the heat exchanger 5 and the outdoor heat exchanger 4, and a bypass pipeline L is disposed between the first gas-liquid separator 6 and the compressor 1.
  • a high-temperature high-pressure gaseous refrigerant discharged by the compressor 1 flows to the indoor heat exchanger 2, and exchanges heat in the indoor heat exchanger 2 to become a low-temperature high-pressure liquid refrigerant.
  • the refrigerant reaches a point C through the first pipeline M.
  • the temperature of the refrigerant is about 20°C (heat here is waste heat which is not sufficiently utilized).
  • the refrigerant enters the second pipeline N after being throttled by the first throttle device 3, and at the moment, the temperature of the refrigerant (throttled refrigerant) at a point D is about 5°C.
  • the refrigerant in the first pipeline M and the refrigerant in the second pipeline N have temperature differences, and both pass through the heat exchanger 5, so that the refrigerant in the first pipeline M and the refrigerant in the second pipeline N exchange heat in the heat exchanger 5.
  • the degree of supercooling of the refrigerant in the first pipeline M effectively increased (i.e., the part of refrigerant from the point C to the first throttle 3 continues to release heat to lower the temperature), but also the evaporation of the refrigerant in the second pipeline N can be promoted (i.e., the low-temperature refrigerant at the point D can perform evaporation heat absorption on afterheat at the point C, which is equivalent to that the evaporation area is increased, and the heat exchange capability is effectively improved), so that a heating capacity is improved.
  • the refrigerant exchanging heat through the heat exchanger 5 enters the first gas-liquid separator 6.
  • the gaseous refrigerant separated by the first gas-liquid separator 6 directly flows back into the compressor 1 along the bypass pipeline L, so that the pressure loss of this part of the gaseous refrigerant in a heating cycle is reduced, which is equivalent to that the pressure of an air suction opening of the compressor 1 is increased, the power consumption of the compressor 1 is further reduced, the circulation volume of the refrigerant during the heating cycle of the air conditioner system is increased, and the purpose of improving the heating capacity is achieved.
  • the liquid refrigerant passing through the first gas-liquid separator 6 flows back into the compressor 1 through the outdoor heat exchanger 4.
  • a second throttle device 7 is disposed on the bypass pipeline L.
  • the second throttle device 7 is configured to control the flow rate of the gaseous refrigerant, that is, an open degree of the second throttle device 7 may be regulated according to the actual operation work conditions so as to flexibly control the passing quantity of the gaseous refrigerant.
  • the second throttle device 7 may be closed, so that the bypass pipeline L does not participate in the refrigeration cycle.
  • the above-mentioned heat exchanger 5 may be a water tank containing water or may be in any other suitable form, provided that the refrigerants at the upstream and downstream of the first throttle device 3 can exchange heat. Additionally, the design can effectively improve the heating capacity for the heating cycle and reduce a refrigeration capacity for the refrigeration cycle.
  • the air conditioner system further includes a mode switching device (e.g., a four-way valve Q in Figure 1 ).
  • the mode switching device is configured to switch the air conditioner system between a refrigeration mode and a heating mode.
  • FIG. 2 is a schematic structure diagram of an embodiment 2 of the air conditioner system.
  • a third throttle device 8 is also disposed in the main circuit of the air conditioner system of the present invention.
  • the third throttle device 8 is positioned in a first pipeline M section between the heat exchanger 5 and the indoor heat exchanger 2.
  • the first throttle device 3 is configured to throttle the refrigerant.
  • a principle is identical to that of the air conditioner system in the embodiment 1.
  • the first throttle device 3 When the air conditioner system is switched to refrigeration operation through the four-way valve Q, the first throttle device 3 is in a fully open state, the third throttle device 8 is configured to throttle the refrigerant, and meanwhile, the second throttle device 7 is closed.
  • the refrigerants at the two sides of the heat exchanger 5 basically have no temperature difference, that is, the heat exchanger 5 does not function in a process of the refrigeration cycle, and the whole refrigeration cycle is a conventional refrigeration cycle. Therefore, the reducing of refrigeration capacity during the refrigeration operation is avoided.
  • the compressor 1 is provided with a second gas-liquid separator 11, the gaseous refrigerant entering the compressor 1 firstly passes through the second gas-liquid separator 11 and is then sucked in by the compressor 1, so that a next cycle is started.
  • the bypass pipeline L is connected to the upstream of the second gas-liquid separator 11.
  • the heat exchanger is added to the air conditioner system of the present invention, and the two sides of the heat exchanger are respectively connected to the first pipeline and the second pipeline. Therefore, the refrigerant in the first pipeline and the refrigerant in the second pipeline can exchange heat in the heat exchanger. Not only is the degree of supercooling of the refrigerant in the first pipeline effectively increased, but also the evaporation of the refrigerant in the second pipeline can be promoted, so that the heating capacity of the system is improved.
  • bypass pipeline is disposed between the first gas-liquid separator and the compressor, and the gaseous refrigerant passing through the first gas-liquid separator can enter the air suction opening of the compressor through this bypass pipeline, so that the pressure loss of this part of the gaseous refrigerant in the heating cycle is reduced, which is equivalent to that the pressure of the air suction opening of the compressor is increased, the power consumption of the compressor is further reduced, the circulation volume of the refrigerant during the heating cycle of the air conditioner system is increased, and the purpose of increasing the heating capacity is achieved.
  • the air conditioner is also provided with the third throttle device, so that when the air conditioner is switched to the refrigeration mode, the third throttle device is used to replace the first throttle device (at the moment, the first throttle device is in the fully open state) to throttle the refrigerant. Therefore, the occurrence of a phenomenon that the refrigeration capacity is reduced in the refrigeration cycle is avoided.

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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)

Claims (6)

  1. Système de climatisation, comprenant un compresseur (1), un échangeur de chaleur interne (2), un premier dispositif d'étranglement (3), et un échangeur de chaleur externe (4) reliés en série dans un circuit principal,
    où le circuit principal est également pourvu d'un échangeur de chaleur (5) et d'un premier séparateur gaz-liquide (6) ;
    un côté de l'échangeur de chaleur est relié à un premier conduit (M) entre le premier dispositif d'étranglement et l'échangeur de chaleur interne, et l'autre côté de l'échangeur de chaleur est relié à un second conduit (N) entre le premier dispositif d'étranglement et l'échangeur de chaleur externe, de sorte qu'un réfrigérant passant par le premier conduit et un réfrigérant passant par le second conduit peuvent échanger de la chaleur dans l'échangeur de chaleur ; et où le premier conduit (M) passe par un côté de l'échangeur de chaleur (5) et/ou le second conduit (N) passe par l'autre côté de l'échangeur de chaleur (5), caractérisé en ce que
    le premier séparateur gaz-liquide est positionné dans une seconde section de conduit (N) entre l'échangeur de chaleur et l'échangeur de chaleur externe, et en ce qu'un conduit de dérivation (L) est disposé entre le premier séparateur gaz-liquide et le compresseur.
  2. Système de climatisation selon la revendication 1, où un second dispositif d'étranglement est disposé dans le conduit de dérivation, et au cours de l'opération de chauffage du système de climatisation, le second dispositif d'étranglement est configuré pour contrôler un débit d'un réfrigérant gazeux.
  3. Système de climatisation selon la revendication 1, où un troisième dispositif d'étranglement est également disposé dans le circuit principal, et le troisième dispositif d'étranglement est positionné dans une première section de conduit entre l'échangeur de chaleur et l'échangeur de chaleur interne.
  4. Système de climatisation selon la revendication 1, où le conduit de dérivation est relié à un amont du second séparateur gaz-liquide.
  5. Système de climatisation selon l'une quelconque des revendications 1 à 3, où le système de climatisation comprend également un dispositif de commutation de mode, et le dispositif de commutation de mode est configuré pour commuter le système de climatisation entre un mode de refroidissement et un mode de chauffage.
  6. Système de climatisation selon la revendication 5, où le dispositif de commutation de mode est une valve à quatre voies.
EP18894319.5A 2017-12-29 2018-11-15 Système de climatisation Active EP3734199B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201711471669.9A CN108375255B (zh) 2017-12-29 2017-12-29 空调器系统
PCT/CN2018/115748 WO2019128517A1 (fr) 2017-12-29 2018-11-15 Système de climatisation

Publications (3)

Publication Number Publication Date
EP3734199A1 EP3734199A1 (fr) 2020-11-04
EP3734199A4 EP3734199A4 (fr) 2021-02-24
EP3734199B1 true EP3734199B1 (fr) 2022-07-27

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EP18894319.5A Active EP3734199B1 (fr) 2017-12-29 2018-11-15 Système de climatisation

Country Status (4)

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EP (1) EP3734199B1 (fr)
JP (1) JP6982692B2 (fr)
CN (1) CN108375255B (fr)
WO (1) WO2019128517A1 (fr)

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* Cited by examiner, † Cited by third party
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CN108375255B (zh) * 2017-12-29 2019-12-06 青岛海尔空调器有限总公司 空调器系统
CN111059615A (zh) * 2019-12-20 2020-04-24 青岛海尔空调电子有限公司 多联机空调系统

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Publication number Priority date Publication date Assignee Title
US8763424B1 (en) * 2013-09-30 2014-07-01 Heat Pump Technologies, LLC Subcooling heat exchanger adapted for evaporator distribution lines in a refrigeration circuit

Also Published As

Publication number Publication date
CN108375255B (zh) 2019-12-06
CN108375255A (zh) 2018-08-07
JP6982692B2 (ja) 2021-12-17
JP2021508025A (ja) 2021-02-25
WO2019128517A1 (fr) 2019-07-04
EP3734199A4 (fr) 2021-02-24
EP3734199A1 (fr) 2020-11-04

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