WO2019091240A1 - 空调制热循环***及空调器 - Google Patents

空调制热循环***及空调器 Download PDF

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Publication number
WO2019091240A1
WO2019091240A1 PCT/CN2018/107875 CN2018107875W WO2019091240A1 WO 2019091240 A1 WO2019091240 A1 WO 2019091240A1 CN 2018107875 W CN2018107875 W CN 2018107875W WO 2019091240 A1 WO2019091240 A1 WO 2019091240A1
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Prior art keywords
heat exchanger
air conditioner
air conditioning
compressor
heating
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PCT/CN2018/107875
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English (en)
French (fr)
Inventor
王飞
吴洪金
付裕
许文明
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青岛海尔空调器有限总公司
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Publication of WO2019091240A1 publication Critical patent/WO2019091240A1/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
    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • 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

Definitions

  • the invention belongs to the technical field of air conditioners, and particularly relates to an air conditioning heating cycle system and an air conditioner.
  • the existing air conditioning heating and heating system usually forms a heating cycle by a condenser, a throttling device, an evaporator, a compressor, and a four-way valve, and the high-temperature and high-pressure gaseous refrigerant discharged from the compressor is condensed into a room condenser through a four-way valve.
  • the low temperature and high pressure liquid is throttled into a low temperature and low pressure liquid through a throttling device, and then enters the outdoor evaporator to evaporate and absorb heat to form a gaseous refrigerant, which is then sucked by the compressor through the four-way valve to complete the 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 a throttling device to form a low-temperature low-pressure gas-liquid two-phase zone refrigerant and enter the evaporator.
  • Heat exchange The larger the evaporation area, the higher the relative evaporation capacity.
  • 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 present invention proposes a new heating cycle system and an air conditioner.
  • the present invention provides an air conditioning heating and heating cycle system, comprising a compressor connected in series in a main circuit, an indoor heat exchanger, and a first throttling device. And an outdoor heat exchanger, a bypass circuit is disposed between the main circuit and the compressor; a portion of the refrigerant flowing out of the indoor heat exchanger flows into the bypass circuit, and another portion flows along the main circuit.
  • the bypass circuit is provided with a second throttle device for controlling the amount of refrigerant entering the bypass circuit.
  • the air conditioning heating and heating system further includes a heat exchanger, and the main circuit and the bypass circuit pass through the heat exchanger, and the heat exchanger is used for The refrigerant in the bypass circuit and the refrigerant in the main circuit are exchanged.
  • the main circuit passing through the heat exchanger is a section between the indoor heat exchanger outlet and the first throttle device.
  • the bypass circuit through the heat exchanger is a section between the compressor and the second throttle device.
  • the compressor is provided with a gas-liquid separator, and a gaseous refrigerant passing through the gas-liquid separator is sucked by the compressor.
  • the present invention also provides an air conditioner which is equipped with the above-described air conditioning heating and circulation system.
  • the air conditioner is provided with a four-way valve for switching the air conditioner between a refrigeration cycle and a heating cycle.
  • the air conditioner is equipped with the above air conditioning heating and heating system; when the air conditioner is refrigerating, the second throttle device is closed.
  • the air conditioner further includes a bypass defrosting circuit disposed between the compressor and the outdoor heat exchanger, and the bypass defrosting circuit is provided with a third Throttling device.
  • the beneficial effects of the technical scheme of the present invention are as follows: (1) The system supercooling section can be effectively increased, that is, the medium-temperature high-pressure liquid refrigerant flowing out from the indoor heat exchanger can continue to release heat and cool before passing through the first throttling device; (2) The medium-temperature high-pressure liquid refrigerant flowing out of the indoor heat exchanger is subjected to evaporation and heat absorption in two ways, which is equivalent to increasing the evaporation area of the refrigerant, thereby effectively improving the heat exchange capacity of the system.
  • FIG. 1 is a schematic structural view of an air conditioning heating and heating cycle system of the present invention
  • Fig. 2 is a schematic view showing the structure of an air conditioner of the present invention.
  • the air conditioning heating and heating 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.
  • a bypass circuit N is provided between the main circuit and the compressor 1; a part of the refrigerant flowing out of the indoor heat exchanger 2 flows into the bypass circuit N, and the other portion flows along the main circuit.
  • the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 1 reaches the indoor heat exchanger 2 (the condenser at this time) to perform heat exchange, and becomes a medium-temperature high-pressure liquid refrigerant, and a medium-temperature high-pressure liquid refrigerant.
  • the indoor heat exchanger 2 the condenser at this time
  • the refrigerant circulation is divided into two paths, one of which continues to flow along the main circuit, and the other of which flows into the bypass circuit N.
  • the bypass circuit N is provided with a second throttle device 5 for controlling the amount of refrigerant entering the bypass circuit N.
  • the medium-temperature high-pressure liquid refrigerant at point A forms a low-temperature low-pressure gas-liquid mixed liquid refrigerant through the second throttling device 5.
  • the heating cycle system further includes a heat exchanger 6 through which the main circuit and the bypass circuit N pass.
  • the main circuit passing through the heat exchanger 6 is a section between the outlet of the indoor heat exchanger 2 (specifically, point A in FIG. 1) and the first throttle device 3; bypassing through the heat exchanger 6
  • the circuit N is a section between the compressor 1 and the second throttle device 5. That is to say, during the heating cycle operation, the medium-temperature high-pressure liquid refrigerant is divided into two paths at point A, one through the heat exchanger 6 ⁇ the first throttling device 3 ⁇ the outdoor heat exchanger 4; the other pass through the first Two throttle device 5 ⁇ heat exchanger 6 ⁇ compressor 1.
  • the heat exchanger 6 is for exchanging heat between the refrigerant in the bypass circuit N and the refrigerant in the main circuit. In this way, the low-temperature and low-pressure gas-liquid mixed refrigerant formed by the second expansion device 5 in the bypass circuit N and the medium-temperature high-pressure liquid refrigerant that has not passed through the first throttle device 3 in the main circuit can be exchanged by heat. 6 heat exchange.
  • the heat exchanger 6 may be a water tank containing water (the heat exchanger 6 may be in any other suitable form, the water tank is merely illustrative), and the medium-temperature high-pressure liquid refrigerant flowing out of the indoor heat exchanger 2 passes through Before the first throttling device 3, first, heat exchange with the water in the heat exchanger 6, and the low-temperature and low-pressure gas-liquid mixed refrigerant formed by the second throttling device 5 is also exchanged with the heat when flowing in the bypass circuit N. The water in the heat exchange. That is, the gas-liquid mixed refrigerant in the bypass circuit N exchanges heat with the medium-temperature high-pressure liquid refrigerant in the main circuit.
  • the heat exchanger 6 realizes the heat exchange between the gas-liquid mixed state refrigerant in the bypass circuit N and the medium temperature and high pressure liquid refrigerant in the main circuit, and can effectively increase the system supercooling section, that is, the point A to the first throttling device.
  • the refrigerant in the section 3 can continue to release heat and cool down; on the other hand, the medium-temperature high-pressure liquid refrigerant flowing out of the indoor heat exchanger 2 is subjected to evaporation and heat absorption in two ways, that is, the first throttling device 3 and the second throttling device. 5, this is equivalent to increasing the evaporation area of the refrigerant, thus effectively improving the heat transfer capacity of the system.
  • the low-temperature low-pressure gas liquid refrigerant in the bypass circuit N is absorbed by the heat exchanger 6 and evaporated to the return port of the compressor 1; the medium-temperature high-pressure liquid refrigerant in the main circuit is discharged through the heat exchanger 6 Then, the first throttling device 3 forms a low-temperature low-pressure gas-liquid mixed state refrigerant, enters the outdoor heat exchanger 4 for heat exchange, and then returns to the gas return port of the compressor 1.
  • the compressor 1 is provided with a gas-liquid separator 11, and the gaseous refrigerant entering the compressor 1 from the bypass circuit N or the main circuit first passes through the gas-liquid separator 11 and is then sucked by the compressor 1 to open the lower portion. A cycle.
  • the heating cycle system of the present invention can effectively increase the system supercooling section, that is, the point A to the first throttling device, by exchanging the refrigerant in the bypass circuit N with the refrigerant in the main circuit.
  • the refrigerant in the section 3 can continue to release heat and cool down; on the other hand, the medium-temperature high-pressure liquid refrigerant flowing out of the indoor heat exchanger 2 is subjected to evaporation and heat absorption in two ways, that is, the first throttling device 3 and the second throttling device. 5, this is equivalent to increasing the evaporation area of the refrigerant, thus effectively improving the heat transfer capacity of the system.
  • the present invention also provides an air conditioner which is equipped with the above-described air conditioning heating and circulation system.
  • the purpose of the above heating cycle system is to strengthen the heat generation, perform charging calculation according to the multiple refrigerants required for ultra-low temperature heating, and increase the mass flow rate and heat exchange amount during the heating cycle, and the air conditioner of the present invention is installed in the above system.
  • a four-way valve can also be provided to switch the air conditioner between the refrigeration cycle and the heating cycle.
  • Fig. 2 is a schematic structural view of an air conditioner of the present invention.
  • the air conditioner includes the above-described heating cycle system (refer to the above description, which will not be described herein), and the four-way valve 7.
  • the air conditioner can switch between the cooling mode and the heating mode through the four-way valve 7, and the four-way valve 7 is switched to the refrigeration cycle in FIG.
  • the second throttle device 5 can be closed during cooling operation of the air conditioner.
  • the air conditioner further includes a bypass defrost circuit M disposed between the compressor 1 and the outdoor heat exchanger 4, and the bypass defrost circuit M is provided with a third throttle device 8.
  • the third throttle device 8 is closed and does not participate in the refrigeration/heating cycle.
  • the third throttling device 8 is opened, and the high-temperature and high-pressure refrigerant discharged from the compressor 1 is divided into two paths, and all the way enters the indoor heat exchanger 2 for heat exchange, bringing heat to the room; another way Defrosting is carried out through the first throttling device 8 into the frosted outdoor heat exchanger 4, thus ensuring continuous operation of the heating.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

一种空调制热循环***及空调器，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），主回路与压缩机（1）之间设置有旁通回路（N）；从室内换热器（2）流出的一部分冷媒流入旁通回路（N），另一部分沿主回路流动。一方面可以有效增加***过冷段，从室内换热器（2）流出的中温高压液态冷媒在经过第一节流装置（3）之前能够继续放热降温，另一方面使得从室内换热器（2）流出的中温高压液态冷媒分两路进行蒸发吸热，相当于增加了冷媒的蒸发面积，有效提升了***的换热能力。

Description

空调制热循环***及空调器 技术领域
本发明属于空调器技术领域，具体涉及一种空调制热循环***及空调器。
背景技术
现有的空调制热循环***通常由冷凝器、节流装置、蒸发器、压缩机、四通阀形成制热循环回路，压缩机排出的高温高压气态冷媒经四通阀到室内冷凝器凝结成低温高压液体，并经节流装置节流成低温低压液体，然后进入室外蒸发器蒸发吸热，形成气态冷媒，再经四通阀被压缩机吸入，完成制热循环。
在制热循环运行时，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***循环的制冷制热量。
基于此，本发明提出了一种新的制热循环***及空调器。
发明内容
为了解决现有技术中的上述问题，即为了提高空调制热循环效果，本发明提供了一种空调制热循环***，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，所述主回路与所述压缩机之间设置有旁通回路；从所述室内换热器流出的一部分冷媒流入所述旁通回路，另一部分沿所述主回路流动。
在上述空调制热循环***的优选实施方式中，所述旁通回路上设置有第二节流装置，所述第二节流装置用于控制进入所述旁通回路的冷媒量。
在上述空调制热循环***的优选实施方式中，所述空调制热循环***还包括热交换器，所述主回路和所述旁通回路均通过所述 热交换器，所述热交换器用于使所述旁通回路内的冷媒和所述主回路内的冷媒进行换热。
在上述空调制热循环***的优选实施方式中，通过所述热交换器的主回路为位于所述室内换热器出口与所述第一节流装置之间的区段。
在上述空调制热循环***的优选实施方式中，通过所述热交换器的旁通回路为位于所述压缩机与所述第二节流装置之间的区段。
在上述空调制热循环***的优选实施方式中，所述压缩机设置有气液分离器，经所述气液分离器的气态冷媒被所述压缩机吸入。
本发明还提供了一种空调器，所述空调器安装有上述的空调制热循环***。
在上述空调器的优选实施方式中，所述空调器设置有四通阀，所述四通阀用于在制冷循环与制热循环之间切换所述空调器。
在上述空调器的优选实施方式中，所述空调器安装有上述空调制热循环***；当所述空调器制冷循环时，所述第二节流装置被关闭。
在上述空调器的优选实施方式中，所述空调器还包括设置于所述压缩机和所述室外换热器之间的旁通除霜回路，所述旁通除霜回路中设置有第三节流装置。
本发明技术方案的有益效果为：(1)可以有效增加***过冷段，即从室内换热器流出的中温高压液态冷媒在经过第一节流装置之前能够继续放热降温；(2)从室内换热器流出的中温高压液态冷媒分两路进行蒸发吸热，这样相当于增加了冷媒的蒸发面积，从而有效提升了***的换热能力。
附图说明
图1是本发明的空调制热循环***的结构示意图；
图2是本发明的空调器的一种结构示意图。
具体实施方式
下面参照附图来描述本发明的优选实施方式。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。
如图1所示，本发明的空调制热循环***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。其中，主回路与压缩机1之间设置有旁通回路N；从室内换热器2流出的一部分冷媒流入旁通回路N，另一部分沿主回路流动。
具体而言，在制热循环运行时，压缩机1排出的高温高压气态冷媒到达室内换热器2(此时为冷凝器)进行热交换，变为中温高压的液态冷媒，中温高压的液态冷媒沿主回路到达A点，此时，冷媒循环分为两路，一路沿主回路继续流动，另一路流入旁通回路N。
在本实施例中，旁通回路N设置有第二节流装置5，其用于控制进入旁通回路N的冷媒量。具体地，A点的中温高压液态冷媒经第二节流装置5形成低温低压的气液混合液态冷媒。
在本实施例中，制热循环***还包括热交换器6，主回路和旁通回路N均通过该热交换器6。具体地，通过热交换器6的主回路为位于室内换热器2出口(具体为图1中的A点)与第一节流装置3之间的区段；通过热交换器6的旁通回路N为位于压缩机1与第二节流装置5之间的区段。也就是说，在制热循环运行时，中温高压的液态冷媒在A点分为两路，一路依次经过热交换器6→第一节流装置3→室外换热器4；另一路依次经过第二节流装置5→热交换器6→压缩机1。
热交换器6用于使旁通回路N内的冷媒和主回路内的冷媒进行换热。这样一来，旁通回路N中经过第二节流装置5形成的低温低压的气液混合态冷媒，与主回路中未经过第一节流装置3的中温高压的液态冷媒，能够通过热交换6进行换热。例如，热交换器6可以是一个盛有水的水箱(热交换器6也可以是其他任意适宜的形式，水箱仅为示例性说明)，从室内换热器2流出的中温高压液态冷媒在经过第一节流装置3之前，首先与热交换器6内的水换热，经第二节流装置5形成的低温低压的气液混合态冷媒在旁通回路N中流动时同样与热交换6中的水进行换热。也就相当于，旁通回路N内的气液混合态冷媒与主回路的中温高压液态冷媒进行热交换。
通过上述热交换器6实现旁通回路N中的气液混合态冷媒与主回路中的中温高压液态冷媒进行换热，一方面可以有效增加***过冷段，即点A到第一节流装置3区段部分的冷媒能够继续放热降温；另一方面，从室内换热器2流出的中温高压液态冷媒分两路进行蒸发吸热，即第一节流装置3处和第二节流装置5处，这样相当于增加了冷媒的蒸发面积，从而有效提升了***的换热能力。
更具体地，旁通回路N中的低温低压气液态冷媒经热交换器6吸收热量蒸发后，回流至压缩机1的回气口；主回路中的中温高压液态冷媒经热交换器6放出热量后，再经第一节流装置3形成低温低压的气液混合态冷媒，进入室外换热器4进行热交换，后回流至压缩机1的回气口。
优选地，压缩机1设置有气液分离器11，无论从旁通回路N还是主回路进入压缩机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，本发明的制热循环***通过使旁通回路N中的冷媒与主回路中的冷媒进行换热，一方面可以有效增加***过冷段，即点A到第一节流装置3区段部分的冷媒能够继续放热降温；另一方面，从室内换热器2流出的中温高压液态冷媒分两路进行蒸发吸热，即第一节流装置3处和第二节流装置5处，这样相当于增加了冷媒的蒸发面积，从而有效提升了***的换热能力。
本发明还提供了一种空调器，该空调器安装有上述中的空调制热循环***。上述制热循环***的目的是为了强化制热量，按照超低温制热所需的多冷媒进行充注核算，增加制热循环时的质量流量和换热量，而本发明的空调器在安装上述制热循环***后，还可以设置四通阀实现空调器在制冷循环与制热循环之间的切换。
具体而言，参照图2，图2是本发明的空调器的一种结构示意图。如图2所示，在本实施例中，空调器包括上述中的制热循环***(具体参照上文描述，在此不再赘述)，以及四通阀7。空调器通过四通阀7可以实现制冷模式与制热模式的切换，图2中示出了四通阀7切换为制冷循环。在空调器制冷运行时，可以关闭第二节流装置5。
优选地，继续参照图2，空调器还包括设置于压缩机1和室外换热器4之间的旁通除霜回路M，旁通除霜回路M设置有第三节流装 置8。在制冷/制热运行时，第三节流装置8关闭不参与制冷/制热循环。当在制热过程中需要除霜时，打开第三节流装置8，压缩机1排出的高温高压冷媒分两路，一路进入室内换热器2进行热交换，给室内带来热量；另一路通过第一节流装置8进入结霜的室外换热器4进行除霜，这样保证了制热的连续运行。
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 (10)

  1. 一种空调制热循环***，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，
    其特征在于，所述主回路与所述压缩机之间设置有旁通回路；
    从所述室内换热器流出的一部分冷媒流入所述旁通回路，另一部分沿所述主回路流动。
  2. 根据权利要求1所述的空调制热循环***，其特征在于，所述旁通回路上设置有第二节流装置，所述第二节流装置用于控制进入所述旁通回路的冷媒量。
  3. 根据权利要求2所述的空调制热循环***，其特征在于，所述空调制热循环***还包括热交换器，所述主回路和所述旁通回路均通过所述热交换器，
    所述热交换器用于使所述旁通回路内的冷媒和所述主回路内的冷媒进行换热。
  4. 根据权利要求3所述的空调制热循环***，其特征在于，通过所述热交换器的主回路为位于所述室内换热器出口与所述第一节流装置之间的区段。
  5. 根据权利要求4所述的空调制热循环***，其特征在于，通过所述热交换器的旁通回路为位于所述压缩机与所述第二节流装置之间的区段。
  6. 根据权利要求1至5中任一项所述的空调制热循环***，其特征在于，所述压缩机设置有气液分离器，经所述气液分离器的气态冷媒被所述压缩机吸入。
  7. 一种空调器，其特征在于，所述空调器安装有权利要求1至6中任一项所述的空调制热循环***。
  8. 根据权利要求7所述的空调器，其特征在于，所述空调器设置有四通阀，所述四通阀用于在制冷循环与制热循环之间切换所述空调器。
  9. 根据权利要求8所述的空调器，其特征在于，所述空调器安装有权利要求4至6中任一项所述的空调制热循环***；
    当所述空调器制冷循环时，所述第二节流装置被关闭。
  10. 根据权利要求7至9中任一项所述的空调器，其特征在于，所述空调器还包括设置于所述压缩机和所述室外换热器之间的旁通除霜回路，所述旁通除霜回路中设置有第三节流装置。
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