WO2019128517A1 - Système de climatisation - Google Patents

Système de climatisation Download PDF

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Publication number
WO2019128517A1
WO2019128517A1 PCT/CN2018/115748 CN2018115748W WO2019128517A1 WO 2019128517 A1 WO2019128517 A1 WO 2019128517A1 CN 2018115748 W CN2018115748 W CN 2018115748W WO 2019128517 A1 WO2019128517 A1 WO 2019128517A1
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WO
WIPO (PCT)
Prior art keywords
air conditioner
heat exchanger
conditioner system
refrigerant
throttle device
Prior art date
Application number
PCT/CN2018/115748
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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 EP18894319.5A priority Critical patent/EP3734199B1/fr
Priority to JP2020535567A priority patent/JP6982692B2/ja
Publication of WO2019128517A1 publication Critical patent/WO2019128517A1/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
    • 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
    • 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 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 refrigerant circulation 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 refrigerant can also be added. The degree of subcooling of the cycle.
  • 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; a side of the heat exchanger between the first throttling device and the indoor heat exchanger a pipeline is connected, the other side of the heat exchanger is connected to a second pipeline between the first throttle device and the outdoor heat exchanger; and the refrigerant and the passage through the first pipeline
  • the refrigerant of the second pipeline is capable of performing heat exchange in the heat exchanger;
  • the first gas-liquid separator is located in a second pipeline section between the heat exchanger and the outdoor heat exchanger And a bypass line is disposed between the first gas-liquid separator and the compressor.
  • 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.
  • 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 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.
  • 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 of the air conditioner system during the heating cycle.
  • the amount of circulation plays the role of increasing heat.
  • 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.
  • 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.
  • 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.
  • 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, according to actual operating conditions.
  • the opening of the second throttle device 7 is adjusted to flexibly control the amount of passage of the gaseous refrigerant.
  • 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 second gas-liquid separator 11, and the gaseous refrigerant entering the compressor 1 first passes through the second gas-liquid separator 11, and is then sucked by the compressor 1, thereby Open the next loop.
  • 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 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)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

La présente 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) raccordés en série à un circuit principal, un dispositif d'échange de chaleur (5) étant en outre prévu dans le circuit principal. Un tuyau entre le premier dispositif d'étranglement (3) et l'échangeur de chaleur intérieur (2) sert de premier tuyau M, un tuyau entre le premier dispositif d'étranglement (3) et l'échangeur de chaleur extérieur (4) sert de second tuyau N, un côté du dispositif d'échange de chaleur (5) est raccordé au premier tuyau M, et l'autre côté du dispositif d'échange de chaleur (5) est raccordé au second tuyau N. Le premier tuyau M passe à travers un côté du dispositif d'échange de chaleur (5), et le second tuyau N passe à travers l'autre côté du dispositif d'échange de chaleur (5). Un fluide frigorigène traversant le premier tuyau M et un fluide frigorigène traversant le second tuyau N peuvent échanger de la chaleur dans le dispositif d'échange de chaleur (5). Un premier séparateur gaz-liquide (6) est en outre disposé dans le circuit principal, le premier séparateur gaz-liquide (6) étant situé dans une section du second tuyau N entre le dispositif d'échange de chaleur (5) et l'échangeur de chaleur extérieur (4), et un tuyau de dérivation L est disposé entre le premier séparateur gaz-liquide (6) et le compresseur (1).
PCT/CN2018/115748 2017-12-29 2018-11-15 Système de climatisation WO2019128517A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP18894319.5A EP3734199B1 (fr) 2017-12-29 2018-11-15 Système de climatisation
JP2020535567A JP6982692B2 (ja) 2017-12-29 2018-11-15 空調機システム

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201711471669.9 2017-12-29
CN201711471669.9A CN108375255B (zh) 2017-12-29 2017-12-29 空调器系统

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WO2019128517A1 true WO2019128517A1 (fr) 2019-07-04

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

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CN108375255A (zh) 2018-08-07
EP3734199B1 (fr) 2022-07-27
JP2021508025A (ja) 2021-02-25
EP3734199A1 (fr) 2020-11-04
JP6982692B2 (ja) 2021-12-17
CN108375255B (zh) 2019-12-06
EP3734199A4 (fr) 2021-02-24

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