WO2015018214A1 - 空调系统 - Google Patents

空调系统 Download PDF

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Publication number
WO2015018214A1
WO2015018214A1 PCT/CN2014/076880 CN2014076880W WO2015018214A1 WO 2015018214 A1 WO2015018214 A1 WO 2015018214A1 CN 2014076880 W CN2014076880 W CN 2014076880W WO 2015018214 A1 WO2015018214 A1 WO 2015018214A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
temperature heat
branch
air conditioning
high temperature
Prior art date
Application number
PCT/CN2014/076880
Other languages
English (en)
French (fr)
Inventor
张仕强
Original Assignee
珠海格力电器股份有限公司
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Publication of WO2015018214A1 publication Critical patent/WO2015018214A1/zh

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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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/02—Compression machines, plants or systems, with several condenser circuits arranged in parallel
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • 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
    • F25B41/31—Expansion 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems

Definitions

  • the present invention relates to the field of refrigeration and air conditioning, and in particular to an air conditioning system.
  • the current air conditioning system also provides the function of providing hot water while providing cooling or heating.
  • the air conditioning heating and the hot water heating adopt the same working mode, but in fact, the high pressure required for air conditioning heating is much lower than the high pressure of the hot water, so that a control mode using a working mode leads to a large amount of The refrigerant enters the hot water heat exchanger, resulting in a reduction in air conditioning capacity.
  • the technical problem to be solved by the present invention is to provide an air conditioning system that avoids energy efficiency degradation caused by uneven distribution of refrigerant, optimizes system control, and saves energy consumption.
  • the air conditioning system disclosed by the invention comprises: a compressor, a medium temperature heat exchanger, a high temperature heat exchanger, a low temperature heat exchanger and a throttling device, a compressor, a medium temperature heat exchanger, a high temperature heat exchanger, a low temperature heat exchanger and a section
  • the flow device is connected to form a refrigerant circulation loop, the intermediate temperature heat exchanger is connected in parallel with the high temperature heat exchanger, the branch of the medium temperature heat exchanger is the first branch, and the branch of the high temperature heat exchanger is the second branch, and the first branch is also included.
  • the pressure device is disposed on the first branch between the intermediate temperature heat exchanger and the exhaust port of the compressor.
  • a second pressure reducing device is further included, and the second pressure reducing device is disposed on the second branch between the high temperature heat exchanger and the exhaust port of the compressor.
  • the first branch and the second branch form a parallel branch, and the throttling device is disposed on the main refrigerant circuit between the low temperature heat exchanger and the parallel branch.
  • a first flow regulating device is further disposed between the throttle device and the intermediate temperature heat exchanger.
  • a second flow regulating device is further disposed between the throttle device and the high temperature heat exchanger.
  • the throttling device comprises a first throttling device and a second throttling device, the first throttling device being disposed on the first branch between the intermediate temperature heat exchanger and the low temperature heat exchanger; the second throttling device setting On the second branch, it is located between the high temperature heat exchanger and the low temperature heat exchanger.
  • a first flow regulating device is disposed between the first throttle device and the intermediate temperature heat exchanger.
  • a second flow regulating device is disposed between the second throttle device and the high temperature heat exchanger.
  • the inlet of the intermediate temperature heat exchanger is provided with a first pressure sensor
  • the exhaust port of the compressor is provided with a second pressure sensor.
  • the inlet of the high temperature heat exchanger is provided with a third pressure sensor.
  • the air conditioning system provided by the invention has the following technical effects: by providing a pressure reducing device in front of the medium temperature heat exchanger, the refrigerant is supplied with different pressures for the medium temperature heat exchanger and the high temperature heat exchanger, thereby avoiding the energy efficiency reduction caused by uneven distribution of the refrigerant. Optimized system control and saves energy.
  • FIG. 1 is a system diagram of one embodiment of the present invention
  • FIG. 2 is a system diagram of another embodiment of the present invention.
  • Figure 1 is a system diagram of one embodiment of the present invention.
  • the air conditioning system comprises: a compressor 1, a medium temperature heat exchanger 31, a high temperature heat exchanger 32, a low temperature heat exchanger 4 and a throttling device 5, a compressor 1, a medium temperature heat exchanger 31, and a high temperature heat exchanger 32.
  • the low temperature heat exchanger 4 and the throttling device 5 are connected to form a refrigerant circulation circuit, wherein the intermediate temperature heat exchanger 31 and the high temperature heat exchanger 32 are connected in parallel, and the branch of the medium temperature heat exchanger 31 is the first branch.
  • the branch of the high temperature heat exchanger 32 is a second branch, and further includes a first pressure reducing device 21 disposed on the first branch between the intermediate temperature heat exchanger 31 and the exhaust port of the compressor 1.
  • the working cycle of the air conditioning system is as follows: the compressor exhaust gas enters the first branch and the second branch respectively, and the high temperature and high pressure refrigerant entering the first branch is depressurized by the first pressure reducing device 21 and enters the intermediate temperature heat exchanger 31.
  • the heat exchange, the high temperature and high pressure refrigerant entering the second branch heats up inside the high temperature heat exchanger 32 and merges with the first branch refrigerant to the main refrigerant circuit, and is throttled by the throttling device 5 and enters the low temperature heat exchanger 4 to absorb heat. Evaporate and finally enter the compressor from the compressor suction port to complete a working cycle.
  • the air conditioning system adjusts the pressure of the high temperature and high pressure refrigerant entering the intermediate temperature heat exchanger 31 by providing the first pressure reducing device 21 at the inlet of the intermediate temperature heat exchanger 31, thereby providing the pressure required for the condensation operation of the medium temperature heat exchanger 31. At the same time, preventing the compressor exhaust gas from entering the medium temperature heat exchanger 31 in a large amount causes the high temperature heat exchanger 32 to have insufficient energy, and the energy consumption of the unit is increased.
  • the first pressure reducing device 21 may be a capillary tube or a manual pressure reducing valve, and the pressure of the high temperature and high pressure refrigerant is reduced after passing through the capillary or the pressure reducing valve.
  • the first pressure reducing device 21 is preferably an electronic expansion valve.
  • a first pressure sensor 10 is further disposed between the inlet of the intermediate temperature heat exchanger 31 and the first pressure reducing device 21, and the first pressure sensor 10 is configured to detect the refrigerant pressure entering the intermediate temperature heat exchanger 31, and control the pressure according to the measured pressure value.
  • the opening degree of the pressure reducing device 21 is adjusted to adjust the pressure of the refrigerant entering the intermediate temperature heat exchanger 31.
  • the air conditioning system uses an inverter compressor, and the adjustment of the refrigerant pressure entering the high temperature heat exchanger 32 can be realized by adjusting the rotation speed of the compressor 1.
  • a second pressure reducing device 22 may be disposed on the second branch between the high temperature heat exchanger 32 and the exhaust port of the compressor 1, and directly pass the second drop according to the operation of the system. Pressing device to adjust the inlet refrigerant pressure of the high temperature heat exchanger.
  • the second pressure reducing device 22 is preferably an electronic expansion valve, the exhaust port of the compressor 1 is provided with a second pressure sensor 11, and the pressure of the exhaust port of the compressor 1 detected by the second pressure sensor 11 is equal to entering the high temperature
  • the refrigerant pressure of the heat exchanger 32 can adjust the opening degree of the second pressure reducing device 22 according to the pressure value detected by the second pressure sensor 11.
  • the flow regulating device 6 is disposed in front of the throttle device 5 in the air conditioning system. Since the pressure of the refrigerant flowing out from the intermediate temperature heat exchanger 31 and the high temperature heat exchanger 32 is different, the flow rate is passed before entering the throttle device 5.
  • the regulating device 6 performs flow adjustment to help improve the throttling effect and the stability of the system.
  • the throttle device 5 is preferably an electronic expansion valve
  • the flow rate adjusting device 6 is preferably an electronic expansion valve, and may be another ordinary flow regulating valve such as a capillary tube or a manual valve.
  • the flow regulating device 6 can be disposed on the first branch, between the intermediate temperature heat exchanger 31 and the throttling device 5, and after the refrigerant is condensed in the intermediate temperature heat exchanger 31, the flow regulating device 6 performs flow regulation and then performs
  • the flow regulating device 6 may also be disposed on the second branch between the high temperature heat exchanger 32 and the throttling device 5. After the refrigerant is condensed in the high temperature heat exchanger 32, the flow regulating device 6 is first used for flow adjustment.
  • FIG. 2 is a system diagram of another embodiment of the present invention.
  • two throttling devices are respectively a first throttling device 51 and a second throttling device 52.
  • the flow device 51 is disposed on the first branch; the second throttle device 52 is disposed on the second branch.
  • the refrigerant in the first branch is condensed in the intermediate temperature heat exchanger 31, it is throttled by the first throttling device 51 and flows into the main refrigerant circuit, and the refrigerant in the second branch is condensed in the high temperature heat exchanger 32,
  • the second throttle device 52 is throttled and flows into the main refrigerant circuit.
  • the two-way throttled and reduced pressure refrigerant merges, it enters the low-temperature heat exchanger 4, and evaporates in the low-temperature heat exchanger 4 and returns to the compressor.
  • the two channels of refrigerant are throttled and depressurized separately, thereby improving the throttling effect and making the system more stable.
  • a first flow regulating device 61 is disposed between the 31s. After the refrigerant is condensed in the intermediate temperature heat exchanger 31, the flow rate is adjusted by the first flow regulating device 61 and then throttled by the first throttling device 51, thereby further improving The throttling effect improves the stability of the system.
  • a second flow regulating device 62 is disposed between the second throttle device 52 and the high temperature heat exchanger 32 on the second branch. After the refrigerant is condensed in the high temperature heat exchanger 32, the refrigerant is first passed through the second flow regulating device 62. The flow regulation is further throttled by the second throttling device 52, thereby further improving the throttling effect and improving the stability of the system.
  • the inlet of the high temperature heat exchanger 32 is provided with a third pressure sensor 12 that detects the pressure of the refrigerant entering the high temperature heat exchanger 32
  • the second pressure reducing device 22 is an electronic expansion valve that controls the opening degree of the second pressure reducing device 22 based on the measured pressure value, thereby adjusting the pressure of the refrigerant entering the high temperature heat exchanger 32.
  • the air conditioning system provided by the invention has the following technical effects: by providing a pressure reducing device in front of the medium temperature heat exchanger, the refrigerant is supplied with different pressures for the medium temperature heat exchanger and the high temperature heat exchanger, thereby avoiding the energy efficiency reduction caused by uneven distribution of the refrigerant.

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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 For Vehicles (AREA)

Abstract

一种空调系统，包括：压缩机（1）、中温换热器（31）、高温换热器（32）、低温换热器（4）和节流装置连通形成冷媒循环回路，中温换热器（31）和高温换热器（32）并联，中温换热器（31）所在支路为第一支路，高温换热器（32）所在支路为第二支路，还包括第一降压装置（21），设置在第一支路上，位于中温换热器（31）和压缩机（1）的排气口之间。

Description

空调系统 技术领域 本发明涉及制冷空调领域， 特别是涉及一种空调系统。 背景技术 随着人们生活水平的提高， 对空调的功能要求也越来越多样， 目前的空调系统在 提供制冷或制热的同时还会具有提供热水的功能。 但是， 目前空调系统中， 空调制热 和制热水采用同一种工作模式， 而实际上空调制热所需高压远低于制热水的高压， 这 样采用一种工作模式的控制方式就会导致大量冷媒进入制热水换热器， 导致空调能力 的降低， 为保证空调能力， 压缩机需要输出更多的能力， 这就导致整机功率过高， 耗 能过高。 发明内容 针对上述现有技术现状， 本发明所要解决的技术问题在于， 提供一种空调系统， 避免了冷媒分布不均导致的能效降低， 优化了系统控制， 节省了能耗。 本发明公开的空调系统， 包括： 压缩机、 中温换热器、 高温换热器、 低温换热器 和节流装置， 压缩机、 中温换热器、 高温换热器、 低温换热器和节流装置连通形成冷 媒循环回路， 中温换热器和高温换热器并联， 中温换热器所在支路为第一支路， 高温 换热器所在支路为第二支路， 还包括第一降压装置， 设置在第一支路上， 位于中温换 热器和压缩机的排气口之间。 优选地， 还包括第二降压装置， 第二降压装置设置在第二支路上， 位于高温换热 器和压缩机的排气口之间。 优选地， 第一支路与第二支路形成并联支路， 节流装置设置在低温换热器与并联 支路之间的主冷媒回路上。 优选地， 节流装置与中温换热器之间还设置有第一流量调节装置。 优选地， 节流装置与高温换热器之间还设置有第二流量调节装置。 优选地， 节流装置包括第一节流装置和第二节流装置， 第一节流装置设置在第一 支路上， 位于中温换热器和低温换热器之间； 第二节流装置设置在第二支路上， 位于 高温换热器和低温换热器之间。 优选地， 第一节流装置与中温换热器之间设置有第一流量调节装置。 优选地， 第二节流装置与高温换热器之间设置有第二流量调节装置。 优选地， 中温换热器的进口设置有第一压力传感器， 压缩机的排气口设置有第二 压力传感器。 优选地， 高温换热器的进口设置有第三压力传感器。 本发明提供的空调系统具有以下技术效果， 通过在中温换热器前设置降压装置， 从而为中温换热器和高温换热器提供不同压力的冷媒， 避免冷媒分布不均导致的能效 降低， 优化了系统控制， 节省了能耗。 附图说明 图 1为本发明其中一个实施例中的系统图； 图 2为本发明另一个实施例中的系统图。 图中标号： 1压缩机； 21第一降压装置； 22第二降压装置； 31 中温换热器； 32 高温换热器； 4低温换热器； 5节流装置； 51第一节流装置； 52第二节流装置； 6流 量调节装置； 61第一流量调节装置； 62第二流量调节装置； 10第一压力传感器； 11 第二压力传感器； 12第三压力传感器。 具体实施方式 下面参考附图并结合实施例对本发明进行详细说明。 需要说明的是， 在不冲突的 情况下， 以下各实施例及实施例中的特征可以相互组合。 参见图 1， 图 1为本发明其中一个实施例中的系统图。 本发明提供的空调系统包 括： 压缩机 1、 中温换热器 31、 高温换热器 32、 低温换热器 4和节流装置 5， 压缩机 1、 中温换热器 31、 高温换热器 32、 低温换热器 4和节流装置 5连通形成冷媒循环回 路， 其中中温换热器 31和高温换热器 32并联， 中温换热器 31所在支路为第一支路， 高温换热器 32所在支路为第二支路， 还包括第一降压装置 21， 设置在第一支路上， 位于中温换热器 31和压缩机 1的排气口之间。 上述空调系统的工作循环流程是： 压缩机排气分别进入第一支路和第二支路， 进 入第一支路的高温高压冷媒经第一降压装置 21降压后进入中温换热器 31换热， 进入 第二支路的高温高压冷媒在高温换热器 32 内部换热后与第一支路冷媒汇合到主冷媒 回路， 经节流装置 5节流后进入低温换热器 4吸热蒸发， 最后从压缩机吸气口进入压 缩机， 完成一个工作循环。 该空调系统由于在中温换热器 31入口设置了第一降压装置 21， 从而对进入中温 换热器 31的高温高压冷媒的压力进行调节， 提供中温换热器 31冷凝工况所需要的压 力， 同时防止压缩机排气大量进入中温换热器 31导致高温换热器 32能量不足， 机组 能耗增加。 上述第一降压装置 21可以选用毛细管， 也可以选用手动降压阀， 高温高压冷媒经 过毛细管或降压阀后压力被降低。 为达到更好的控制效果， 第一降压装置 21优选为电子膨胀阀。 中温换热器 31入 口与第一降压装置 21之间还设置有第一压力传感器 10， 第一压力传感器 10用来检测 进入中温换热器 31的冷媒压力， 根据测得的压力值控制第一降压装置 21的开度， 从 而调节进入中温换热器 31中的冷媒的压力。 本空调系统采用变频压缩机，对进入高温换热器 32的冷媒压力的调节可以通过调 节压缩机 1的转速来实现。 为了提高对高温换热器的控制效果， 可以在高温换热器 32 和压缩机 1的排气口之间的第二支路上设置第二降压装置 22， 根据系统运行情况直接 通过第二降压装置来进行高温换热器入口冷媒压力的调节。 进一步地，第二降压装置 22优选为电子膨胀阀，压缩机 1的排气口设置有第二压 力传感器 11， 第二压力传感器 11检测到的压缩机 1 的排气口压力等于进入高温换热 器 32的冷媒压力， 该空调系统可以根据第二压力传感器 11检测的压力值对第二降压 装置 22的开度进行调节。 进一步地， 上述空调系统中的节流装置 5前设置有流量调节装置 6， 由于从中温 换热器 31和高温换热器 32流出的冷媒压力不同， 所以在进入节流装置 5前先经过流 量调节装置 6进行流量调节， 有助于提高节流效果和系统的稳定性。 节流装置 5优选 为电子膨胀阀， 流量调节装置 6优选为电子膨胀阀， 也可以是毛细管、 手动阀等其他 普通的流量调节阀。 其中， 流量调节装置 6可以设置在第一支路上， 位于中温换热器 31和节流装置 5 之间，冷媒在中温换热器 31中冷凝后，先经过流量调节装置 6进行流量调节再进行节 流;流量调节装置 6也可以设置在第二支路上，位于高温换热器 32和节流装置 5之间， 冷媒在高温换热器 32中冷凝后，先经过流量调节装置 6进行流量调节再进行节流；流 量调节装置 6也可以设置在主冷媒回路上， 位于节流装置 5进口之前， 冷媒在高温换 热器 32和中温换热器 31中冷凝后先经过流量调节装置 6进行流量调节， 再进入节流 装置 5进行节流。 参见图 2， 图 2为本发明另一个实施例中的系统图， 在该实施例中， 节流装置为 两个， 分别为第一节流装置 51和第二节流装置 52， 第一节流装置 51设置在第一支路 上； 第二节流装置 52设置在第二支路上。 第一支路中的冷媒在中温换热器 31中冷凝 后， 经第一节流装置 51节流后流入主冷媒回路， 第二支路中的冷媒在高温换热器 32 中冷凝后， 经第二节流装置 52节流后流入主冷媒回路。两路节流降压后的冷媒汇合后 进入低温换热器 4， 在低温换热器 4内蒸发后回到压缩机。 通过在两个支路上分别设 置节流装置， 对两路冷媒分别进行节流降压， 从而提高节流效果， 系统更加平稳。 进一步地， 流量调节装置为两个， 在第一支路上第一节流装置 51 和中温换热器
31之间设置有第一流量调节装置 61， 冷媒在中温换热器 31中冷凝后， 先经过第一流 量调节装置 61进行流量调节再经过第一节流装置 51进行节流， 从而进一步提高了节 流效果， 提高了系统的稳定性。 进一步地， 第二支路上第二节流装置 52和高温换热器 32之间设置有第二流量调 节装置 62， 冷媒在高温换热器 32中冷凝后， 先经过第二流量调节装置 62进行流量调 节再经过第二节流装置 52进行节流， 从而进一步提高了节流效果，提高了系统的稳定 性。 参见图 1和图 2， 为进一步优化系统控制， 高温换热器 32的进口设置有第三压力 传感器 12， 该第三压力传感器 12检测进入高温换热器 32的冷媒压力， 第二降压装置 22为电子膨胀阀， 该空调系统根据测得的压力值控制第二降压装置 22的开度， 从而 调节进入高温换热器 32中的冷媒压力。 本发明提供的空调系统具有以下技术效果， 通过在中温换热器前设置降压装置， 从而为中温换热器和高温换热器提供不同压力的冷媒， 避免冷媒分布不均导致的能效 降低， 优化了系统控制， 节省了能耗； 同时， 采用不同压力支路分别进行节流的方式， 提高了节流效果， 提高了系统运行的平稳性； 另外， 通过在节流装置前设置流量调节 装置， 进一步优化了冷媒的控制， 提高了系统运行的平稳性， 提高了系统的可靠性。 以上所述实施例仅表达了本发明的几种实施方式， 其描述较为具体和详细， 但并 不能因此而理解为对本发明专利范围的限制。 应当指出的是， 对于本领域的普通技术 人员来说， 在不脱离本发明构思的前提下， 还可以做出若干变形和改进， 这些都属于 本发明的保护范围。

Claims

权 利 要 求 书 、 一种空调系统， 包括： 压缩机、 中温换热器、 高温换热器、 低温换热器和节流 装置， 所述压缩机、 中温换热器、 高温换热器、 低温换热器和节流装置连通形 成冷媒循环回路， 所述中温换热器和所述高温换热器并联， 所述中温换热器所 在支路为第一支路， 所述高温换热器所在支路为第二支路， 其特征在于， 还包 括第一降压装置， 设置在所述第一支路上， 位于所述中温换热器和所述压缩机 的排气口之间。 、 根据权利要求 1所述的空调系统， 其特征在于， 还包括第二降压装置， 所述第 二降压装置设置在所述第二支路上， 位于所述高温换热器和所述压缩机的排气 口之间。 、 根据权利要求 1或 2所述的空调系统， 其特征在于， 所述第一支路与所述第二 支路形成并联支路， 所述节流装置设置在所述低温换热器与所述并联支路之间 的主冷媒回路上。 、 根据权利要求 3所述的空调系统， 其特征在于， 所述节流装置与所述中温换热 器之间还设置有第一流量调节装置。 、 根据权利要求 3所述的空调系统， 其特征在于， 所述节流装置与所述高温换热 器之间还设置有第二流量调节装置。 、 根据权利要求 1或 2所述的空调系统， 其特征在于， 所述节流装置包括第一节 流装置和第二节流装置， 所述第一节流装置设置在所述第一支路上， 位于所述 中温换热器和所述低温换热器之间；所述第二节流装置设置在所述第二支路上， 位于所述高温换热器和所述低温换热器之间。 、 根据权利要求 6所述的空调系统， 其特征在于， 所述第一节流装置与所述中温 换热器之间设置有第一流量调节装置。 、 根据权利要求 7所述的空调系统， 其特征在于， 所述第二节流装置与所述高温 换热器之间设置有第二流量调节装置。 、 根据权利要求 1、 2或 8所述的空调系统， 其特征在于， 所述中温换热器的进口 设置有第一压力传感器， 所述压缩机的排气口设置有第二压力传感器。 根据权利要求 9所述的空调系统， 其特征在于， 所述高温换热器的进口设置有 第三压力传感器。
PCT/CN2014/076880 2013-08-08 2014-05-06 空调系统 WO2015018214A1 (zh)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108917067A (zh) * 2018-09-17 2018-11-30 宁波奥克斯电气股份有限公司 一种多联机空调系统

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114992812A (zh) * 2022-06-17 2022-09-02 珠海格力电器股份有限公司 空调系统及控制方法

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2139021A1 (en) * 1994-12-23 1996-06-24 Reinhold Kittler Transferring heat from two different heat exchangers connected in series without the use of control valves
CN1936459A (zh) * 2006-10-14 2007-03-28 蔡志鸿 双电子膨胀阀空调热水两用机组
CN200958879Y (zh) * 2006-08-03 2007-10-10 邱致琏 变频节能热泵冷冻空调机组改良
CN203464540U (zh) * 2013-08-08 2014-03-05 珠海格力电器股份有限公司 空调系统

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101526280B (zh) * 2009-04-20 2010-09-08 广东志高空调有限公司 一种热水空调器
US9068766B2 (en) * 2010-04-05 2015-06-30 Mitsubishi Electric Corporation Air-conditioning and hot water supply combination system
CN103026150B (zh) * 2010-07-29 2015-06-03 株式会社日立制作所 空调热水供给系统
CN102829571A (zh) * 2011-06-15 2012-12-19 李思模 带双冷凝器的空调

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2139021A1 (en) * 1994-12-23 1996-06-24 Reinhold Kittler Transferring heat from two different heat exchangers connected in series without the use of control valves
CN200958879Y (zh) * 2006-08-03 2007-10-10 邱致琏 变频节能热泵冷冻空调机组改良
CN1936459A (zh) * 2006-10-14 2007-03-28 蔡志鸿 双电子膨胀阀空调热水两用机组
CN203464540U (zh) * 2013-08-08 2014-03-05 珠海格力电器股份有限公司 空调系统

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108917067A (zh) * 2018-09-17 2018-11-30 宁波奥克斯电气股份有限公司 一种多联机空调系统
CN108917067B (zh) * 2018-09-17 2023-07-18 宁波奥克斯电气股份有限公司 一种多联机空调系统

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