WO2019128518A1 - 空调器系统 - Google Patents

空调器系统 Download PDF

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Publication number
WO2019128518A1
WO2019128518A1 PCT/CN2018/115749 CN2018115749W WO2019128518A1 WO 2019128518 A1 WO2019128518 A1 WO 2019128518A1 CN 2018115749 W CN2018115749 W CN 2018115749W WO 2019128518 A1 WO2019128518 A1 WO 2019128518A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
air conditioner
conditioner system
refrigerant
compressor
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PCT/CN2018/115749
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English (en)
French (fr)
Inventor
王飞
付裕
罗荣邦
许文明
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青岛海尔空调器有限总公司
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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 EP18893890.6A priority Critical patent/EP3734192B1/en
Priority to ES18893890T priority patent/ES2970620T3/es
Priority to JP2020535565A priority patent/JP2021508809A/ja
Publication of WO2019128518A1 publication Critical patent/WO2019128518A1/zh

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    • 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
    • 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
    • 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 invention belongs to the technical field of air conditioners, and in particular relates to an air conditioner system.
  • the high-temperature and high-pressure gaseous refrigerant forms a low-temperature and high-pressure liquid refrigerant after heat exchange through the condenser, and then throttling and depressurization through the throttling device to form a low-temperature low-pressure gas-liquid two-phase zone refrigerant to enter the evaporation.
  • Heat exchange The larger the evaporation area, the higher the relative evaporation capacity. Among them, the low temperature and high pressure liquid refrigerant will increase the degree of subcooling if it continues to exotherm, thereby increasing the cooling capacity of the system cycle.
  • the refrigerant When the refrigerant is in heat exchange, more than 95% of the heat exchange is derived from the latent heat of vaporization in the two-phase region, while the isobaric specific heat capacity of the unidirectional zone (pure liquid, pure gas) is relatively small, and the heat exchange capacity accounts for the total system.
  • the proportion of the loop is small.
  • the pressure drop of the gaseous refrigerant in the pipeline is large, which is the main source of the system cyclic pressure loss, which will increase the circulating work volume, that is, increase the energy consumption of the system cycle.
  • FIG. 3 is a cycle schematic diagram of a conventional air conditioner during heating operation.
  • the actual operating temperature of the air conditioner heating operation is generally: A point high temperature gaseous 70 ° C refrigerant, enter the indoor heat exchanger and 20 ° C indoor environment for heat exchange, the temperature is reduced to 30 ° C, flow through After the line tube enters the throttling device, the temperature between point B and the throttling device (about 30 ° C) is much higher than the outdoor ambient temperature of 7 ° C, and the waste heat is wasted. If the residual heat is absorbed and utilized, the system cycle can be increased. Too cold.
  • the air conditioner system provided by the present invention includes a compressor connected in series in the main circuit, an indoor heat exchanger, a first throttle device, and an outdoor unit.
  • a heat exchanger wherein a heat exchanger is further disposed in the main circuit, and a bypass defrosting circuit is disposed between the compressor and the outdoor heat exchanger; one side of the heat exchanger and the first a first line between the flow device and the indoor heat exchanger, the other side of the heat exchanger and a second tube between the first throttle device and the outdoor heat exchanger The road is connected; the refrigerant passing through the first line and the refrigerant passing through the second line are capable of performing heat exchange in the heat exchanger; the bypass defrost circuit is used in the process of heating the air conditioner Defrosting the outdoor heat exchanger.
  • the first conduit passes through one side of the heat exchanger and/or the second conduit passes through the other side of the heat exchanger.
  • a second throttle device is further disposed in the main circuit, and the second throttle device is located between the heat exchanger and the indoor heat exchanger. In the pipeline section.
  • the second throttle device when the air conditioner system is operating in heating, the second throttle device is in a fully open state, and the first throttle device is used for refrigerant throttling.
  • the first throttle device when the air conditioner system is in a cooling operation, the first throttle device is in a fully open state, and the second throttle device is used to throttle the refrigerant.
  • a throttle valve is disposed in the bypass defrost circuit, and when the outdoor heat exchanger requires defrosting, the throttle valve is opened to allow the compression to flow out
  • the refrigerant of the machine performs a defrosting operation on the outdoor heat exchanger through the bypass defrost circuit; when the outdoor heat exchanger does not require defrosting, the throttle valve is closed.
  • the compressor is provided with a gas-liquid separator, and the refrigerant passes through the gas-liquid separator and is returned to the compressor.
  • the air conditioner system further includes a mode switching device for switching the air conditioner system between a cooling mode and a heating mode.
  • the mode switching device is a four-way valve.
  • a heat exchanger is added to the air conditioner system, and two sides of the heat exchanger are respectively connected to the first pipeline and the second pipeline, so that the refrigerant in the first pipeline is And the refrigerant in the second pipeline can exchange heat at the heat exchanger, which not only effectively increases the degree of subcooling of the refrigerant in the first pipeline, but also promotes evaporation of the refrigerant in the second pipeline, thereby Increased system heat.
  • the present invention also adds a bypass defrost circuit. During the defrosting process of 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 realized.
  • the air conditioner of the present invention also uses the second throttle device to replace the first throttle device when the air conditioner is switched to the cooling mode by setting the second throttle device (at this time, the first throttle device is at The fully open state is to throttle the refrigerant, thereby avoiding the phenomenon that the cooling capacity is reduced when the refrigeration cycle occurs.
  • FIG. 1 is a schematic structural view of a first embodiment of an air conditioner system of the present invention
  • Figure 2 is a schematic structural view of a second embodiment of the air conditioner system of the present invention.
  • Fig. 3 is a schematic diagram of the cycle of a conventional air conditioner during heating operation.
  • Fig. 1 is a schematic structural view of a first embodiment of an air conditioner system of the present invention.
  • the air conditioner system of the present invention includes a compressor 1 connected in series in the main circuit, an indoor heat exchanger 2, a first throttle device 3, and an outdoor heat exchanger 4, and heat is also disposed in the main circuit.
  • Switch 5 the pipeline between the first throttle device 3 and the indoor heat exchanger 2 is used as the first pipeline M, and the pipeline between the first throttle device 3 and the outdoor heat exchanger 4 is used as the second conduit.
  • the pipe N, one side of the heat exchanger 5 is connected to the first pipe M, and the other side of the heat exchanger 5 is connected to the second pipe N, as shown in FIG.
  • the bypass defrost circuit P is provided with a throttle valve 7, and when the outdoor heat exchanger 4 requires defrost, the throttle valve 7 is opened to pass the refrigerant through the bypass defrost 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 7 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 heating capacity of the system.
  • the refrigerant in the first line M undergoes heat exchange in the heat exchanger 5 and then enters the first throttle device 3 to form a gas-liquid two-phase region of low temperature and low pressure at point D, and then The outdoor heat exchanger 4 is returned to the compressor 1.
  • waste heat can be reused during the heating operation of the air conditioner to increase the heat generation of the entire system.
  • 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 second throttle device 6 is further disposed in the main circuit of the air conditioner system of the present invention, and the second throttle device 6 is located in the first tube between the heat exchanger 5 and the indoor heat exchanger 2.
  • the second throttle device 6 is in a fully open state, and the first throttle device 3 is used for refrigerant throttling.
  • the principle of the air conditioner system in the first embodiment is the same.
  • the first throttle device 3 When the air conditioner system is switched to the cooling operation by the four-way valve Q, the first throttle device 3 is in the fully open state, and the second throttle device 6 is used for the refrigerant throttling. At this time, the refrigerant on both sides of the heat exchanger 5 has almost no temperature difference, that is, the heat exchanger 5 does not function during the refrigeration cycle, and the entire refrigeration cycle is a conventional refrigeration cycle, thereby avoiding a reduction in the amount of refrigeration during the cooling operation.
  • the compressor 1 is provided with a gas-liquid separator 11, and the gaseous refrigerant entering the compressor 1 first passes through the gas-liquid separator 11, and is then sucked by the compressor 1, thereby opening the next cycle. .
  • a heat exchanger is added to the air conditioner system of the present invention, and two sides of the heat exchanger are respectively connected to the first pipeline and the second pipeline, so that the refrigerant in the first pipeline is obtained.
  • the refrigerant in the second pipeline can exchange heat at the heat exchanger, which not only effectively increases the degree of subcooling of the refrigerant in the first pipeline, but also promotes evaporation of the refrigerant in the second pipeline, thereby Increased system heat.
  • the 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 present invention also provides a second throttling device by using the second throttling device instead of the first throttling device when the air conditioner is switched to the cooling mode (the first throttling device is in the fully open state)
  • the throttling of the refrigerant avoids 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)
  • Air Conditioning Control Device (AREA)

Abstract

一种空调器系统，包括串联在主回路的压缩机（1）、室内换热器（2）、第一节流装置（3）和室外换热器（4），主回路中还设置有热交换器（5），压缩机（1）和室外换热器（4）之间设置有旁通除霜回路（P）；热交换器（5）的一侧与第一节流装置（3）和室内换热器（2）之间的第一管路（M）相连，热交换器（5）的另一侧与第一节流装置（3）和室外换热器（4）之间的第二管路（N）相连；通过第一管路（M）的冷媒与通过第二管路（N）的冷媒能够在热交换器（5）内进行热交换；旁通除霜回路（P）用于在空调制热的过程中，对室外换热器（4）进行除霜。由此不仅有效地增加第一管路（M）中冷媒的过冷度，而且还可以促进第二管路（N）中冷媒的蒸发，提升系统的制热量，且实现了不停机除霜的目的。

Description

空调器系统 技术领域
本发明属于空调器技术领域，具体涉及一种空调器系统。
背景技术
现有的空调器系统通常由冷凝器、节流装置、蒸发器、压缩机形成制冷/制热循环回路，压缩机排出的高温高压气态冷媒在冷凝器中凝结成低温高压液体，并经节流装置节流成低温低压液体，然后进入蒸发器吸热蒸发，完成一个制冷/制热循环。
空调器在制热运行时，高温高压的气态冷媒在经过冷凝器换热后，形成低温高压的液态冷媒，而后经过节流装置节流降压，形成低温低压气液两相区冷媒，进入蒸发器换热。蒸发面积越大，则相对蒸发能力越高。其中，低温高压的液态冷媒如果继续放热会增加过冷度，从而增加系统循环的制冷制热量。制冷剂在换热时，95％以上的换热量来源于其两相区的汽化潜热量，而单向区(纯液体、纯气体)的等压比热容相对很小，换热量占总系统循环的比例小。此外，气态制冷剂在管路中的压降大，是系统循环压损的主要来源，会增加循环做功量，即增加了系统循环的能耗。
此外，参照图3，图3是传统空调器制热运行时的循环原理图。如图3所示，空调器制热运行的实际运行温度点一般为，A点高温气态70℃冷媒，进入室内换热器和20℃的室内环境进行换热，温度降低为30℃，流经联机管后进入节流装置，其中，B点和节流装置之间的温度(30℃左右)远远高于室外环境温度7℃，余热被浪费，如果余热被吸收利用，还可以增加系统循环的过冷度。
基于此，特提出本发明。
发明内容
为了解决现有技术中的上述问题，即为了提高空调器的制热循环效果，本发明提供的空调器系统，包括串联在主回路的压缩机、室内换热器、第一节流装置和室外换热器，所述主回路中还设置有热交换器，并且所述压缩机和所述室外换热器之间设置有旁通除霜回路；所述热交换器的一侧与所述第 一节流装置和所述室内换热器之间的第一管路相连，所述热交换器的另一侧与所述第一节流装置和所述室外换热器之间的第二管路相连；通过所述第一管路的冷媒与通过所述第二管路的冷媒能够在所述热交换器内进行热交换；所述旁通除霜回路用于在空调制热的过程中，对所述室外换热器进行除霜操作。
在上述空调器系统的优选实施方式中，所述第一管路穿过所述热交换器的一侧，并且/或者所述第二管路穿过所述热交换器的另一侧。
在上述空调器系统的优选实施方式中，所述主回路中还设置有第二节流装置，所述第二节流装置位于所述热交换器与所述室内换热器之间的第一管路区段中。
在上述空调器系统的优选实施方式中，当所述空调器系统制热运行时，所述第二节流装置处于全开状态，所述第一节流装置用于冷媒节流。
在上述空调器系统的优选实施方式中，当所述空调器系统制冷运行时，所述第一节流装置处于全开状态，所述第二节流装置用于冷媒节流。
在上述空调器系统的优选实施方式中，所述旁通除霜回路中设置有节流阀，当所述室外换热器需要除霜时，所述节流阀被打开以使流出所述压缩机的冷媒通过所述旁通除霜回路对所述室外换热器进行除霜操作；当所述室外换热器不需要除霜时，所述节流阀被关闭。
在上述空调器系统的优选实施方式中，所述压缩机设置有气液分离器，冷媒经过所述气液分离器后回流到所述压缩机中。
在上述空调器系统的优选实施方式中，所述空调器系统还包括模式切换装置，所述模式切换装置用于在制冷模式与制热模式之间切换所述空调器系统。
在上述空调器系统的优选实施方式中，所述模式切换装置是四通阀。
在本发明的技术方案中，空调器系统中增加了热交换器，并且该热交换器的两侧分别与第一管路和第二管路相连，这样一来，第一管路中的冷媒和第二管路中的冷媒能够在热交换器处进行热交换，不仅有效地增加了第一管路中的冷媒的过冷度，而且还可以促进第二管路中的冷媒的蒸发，从而提升了系统的制热量。并且，本发明还增加了旁通除霜回路，在空调器除霜的过程中，冷媒会继续进入室内换热器进行制热，即可以使空调器仍然维持在制热工况，实现空调器不停机除霜的目的。此外，本发明的空调器还通过设置 第二节流装置的方式，使得空调器在切换为制冷模式时，利用该第二节流装置替代第一节流装置(此时第一节流装置处于全开状态)给冷媒进行节流，从而避免了出现在制冷循环时制冷量被降低的现象。
附图说明
图1是本发明的空调器系统的实施例一的结构原理图；
图2是本发明的空调器系统的实施例二的结构原理图；
图3是传统空调器制热运行时的循环原理图。
具体实施方式
为使本发明的实施例、技术方案和优点更加明显，下面将结合附图对本发明的技术方案进行清楚、完整地描述，显然，所述的实施例是本发明的一部分实施例，而不是全部实施例。本领域技术人员应当理解的是，这些实施方式仅仅用于解释本发明的技术原理，并非旨在限制本发明的保护范围。
首先参照图1，图1是本发明的空调器系统的实施例一的结构原理图。如图1所示，本发明的空调器系统包括串联在主回路的压缩机1、室内换热器2、第一节流装置3和室外换热器4，在该主回路中还设置有热交换器5。为了便于说明，将第一节流装置3与室内换热器2之间的管路作为第一管路M，将第一节流装置3与室外换热器4之间的管路作为第二管路N，热交换器5的一侧与第一管路M相连，热交换器5的另一侧与第二管路N相连，如图1中所示的连接方式：第一管路M穿过热交换器5的一侧，第二管路N穿过热交换器N的另一侧。并且，通过第一管路M的冷媒与通过第二管路N的冷媒能够在热交换器5中进行热交换。此外，在本发明的空调器系统中，压缩机1和室外换热器4之间还设置有旁通除霜回路P，该旁通除霜回路P用于在空调制热循环过程中，对室外换热器4进行除霜操作。
作为示例，如图1所示，旁通除霜回路P上设置有节流阀7，当室外换热器4需要除霜时，节流阀7被打开以使冷媒通过旁通除霜回路P对室外换热器4进行除霜操作；当室外换热器4不需要除霜时，节流阀7被关闭。通过增加旁通除霜回路P，在空调器除霜的过程中，冷媒会继续进入室内换热器2进行制热，即可以使空调器仍然维持在制热工况，实现空调器不停机除霜的目的。
在空调器制热循环过程中，压缩机1排出的高温高压气态冷媒流向室内 换热器2，在室内换热器2进行热交换，变为低温高压的液态冷媒，冷媒通过沿第一管路M到达C点，此时冷媒温度在20℃左右(此处的热量为废热没有被充分利用)。然后，冷媒经过第一节流装置3节流后进入第二管路N，此时D点冷媒(经过节流后的冷媒)的温度作5℃左右。由于第一管路M中的冷媒和第二管路N中的冷媒存在温差，且两者都通过热交换器5，这样一来，第一管路M中的冷媒和第二管路N中的冷媒在热交换器5处进行热交换，不仅有效地增加了第一管路M中的冷媒的过冷度(即C点到第一节流装置3的那部分冷媒继续放热降温)，而且还可以促进第二管路N中的冷媒的蒸发(即D点处的低温冷媒可以对C点处余热进行蒸发吸热，这也相当于增加了蒸发面积，有效提升了换热能力)，从而提升了系统的制热量。
在空调器的制热运行过程中，第一管路M中的冷媒在热交换器5进行热交换后再进入第一节流装置3，形成D点低温低压的气液两相区，再经过室外换热器4回流至压缩机1。通过上述设计，在空调器制热运行的过程中能够使废热再利用，以提升整个系统的制热量。
需要说明的是，上文中的热交换器5可以是一个盛有水的水箱也可以是任意其他适宜的形式，只要能够使第一节流装置3上游和下游的冷媒进行换热即可。此外，上述设计对于制热循环能有效提升制热量，而对于制冷循环时降低制冷量。
作为一种示例，本发明的空调器系统还包括模式切换装置(例如图1中的四通阀Q)，该模式切换装置用于在制冷模式与制热模式之间切换空调器系统。
作为一种示例，参照图2，图2是本发明的空调器系统的实施例二的结构原理图。如图2所示，本发明的空调器系统的主回路中还设置有第二节流装置6，该第二节流装置6位于热交换器5与室内换热器2之间的第一管路M区段中。当空调器制热运行时，第二节流装置6处于全开状态，第一节流装置3用于冷媒节流。此时与实施例一中的空调器系统的原理相同。通过四通阀Q将空调器系统切换为制冷运行时，第一节流装置3处于全开状态，第二节流装置6用于冷媒节流。此时，热交管器5两侧的冷媒几乎无温差，即热交换器5在制冷循环的过程中不发挥作用，整个制冷循环为常规制冷循环，从而避免降低制冷运行时的制冷量。
优选地，参照图1和图2，压缩机1设置有气液分离器11，进入压缩机 1的气态冷媒首先经过该气液分离器11后，再被压缩机1吸入，从而开启下一循环。
综上所述，本发明的空调器系统中增加了热交换器，并且该热交换器的两侧分别与第一管路和第二管路相连，这样一来，第一管路中的冷媒和第二管路中的冷媒能够在热交换器处进行热交换，不仅有效地增加了第一管路中的冷媒的过冷度，而且还可以促进第二管路中的冷媒的蒸发，从而提升了系统的制热量。本发明还增加了旁通除霜回路，在空调器除霜的过程中，冷媒会继续进入室内换热器进行制热，即可以使空调器仍然维持在制热工况，实现空调器不停机除霜的目的。此外，本发明还通过设置第二节流装置的方式，使得空调器在切换为制冷模式时，利用该第二节流装置替代第一节流装置(此时第一节流装置处于全开状态)给冷媒进行节流，从而避免了出现在制冷循环时制冷量被降低的现象。
至此，已经结合附图所示的优选实施方式描述了本发明的技术方案，但是，本领域技术人员容易理解的是，本发明的保护范围显然不局限于这些具体实施方式。在不偏离本发明的原理的前提下，本领域技术人员可以对相关技术特征作出等同的更改或替换，这些更改或替换之后的技术方案都将落入本发明的保护范围之内。

Claims (9)

  1. 一种空调器系统，包括串联在主回路的压缩机、室内换热器、第一节流装置和室外换热器，
    其中，所述主回路中还设置有热交换器，并且所述压缩机和所述室外换热器之间设置有旁通除霜回路；
    所述热交换器的一侧与所述第一节流装置和所述室内换热器之间的第一管路相连，所述热交换器的另一侧与所述第一节流装置和所述室外换热器之间的第二管路相连，使通过所述第一管路的冷媒与通过所述第二管路的冷媒能够在所述热交换器内进行热交换；
    所述旁通除霜回路配置成在空调制热的过程中，对所述室外换热器进行除霜操作。
  2. 根据权利要求1所述的空调器系统，其中，所述第一管路穿过所述热交换器的一侧，并且/或者所述第二管路穿过所述热交换器的另一侧。
  3. 根据权利要求2所述的空调器系统，其中，所述主回路中还设置有第二节流装置，所述第二节流装置位于所述热交换器与所述室内换热器之间的第一管路区段中。
  4. 根据权利要求3所述的空调器系统，其中，当所述空调器系统制热运行时，所述第二节流装置配置成处于全开状态，所述第一节流装置配置成用于冷媒节流。
  5. 根据权利要求3所述的空调器系统，其中，当所述空调器系统制冷运行时，所述第一节流装置配置成处于全开状态，所述第二节流装置配置成用于冷媒节流。
  6. 根据权利要求1所述的空调器系统，其中，所述旁通除霜回路中设置有节流阀，且配置成：
    当所述室外换热器需要除霜时，所述节流阀被打开以使流出所述压缩机的冷媒通过所述旁通除霜回路对所述室外换热器进行除霜操作；
    当所述室外换热器不需要除霜时，所述节流阀被关闭。
  7. 根据权利要求1至6中任一项所述的空调器系统，其中，所述压缩机设置有气液分离器，冷媒经过所述气液分离器后回流到所述压缩机中。
  8. 根据权利要求1至6中任一项所述的空调器系统，其中，所述空调器系统还包括模式切换装置，所述模式切换装置用于在制冷模式与制热模式之 间切换所述空调器系统。
  9. 根据权利要求8所述的空调器系统，其特征在于，所述模式切换装置是四通阀。
PCT/CN2018/115749 2017-12-29 2018-11-15 空调器系统 WO2019128518A1 (zh)

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