WO2007112671A1 - Unité d'entreposage frigorifique de glace super refroidie, système de conditionnement d'air utilisant l'unité et son procédé de gestion - Google Patents

Unité d'entreposage frigorifique de glace super refroidie, système de conditionnement d'air utilisant l'unité et son procédé de gestion Download PDF

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Publication number
WO2007112671A1
WO2007112671A1 PCT/CN2007/001014 CN2007001014W WO2007112671A1 WO 2007112671 A1 WO2007112671 A1 WO 2007112671A1 CN 2007001014 W CN2007001014 W CN 2007001014W WO 2007112671 A1 WO2007112671 A1 WO 2007112671A1
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Prior art keywords
valve
electronic expansion
state
air conditioning
conditioning system
Prior art date
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Ceased
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PCT/CN2007/001014
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English (en)
French (fr)
Inventor
Honghai Xiao
Hua Zhang
Tao Zhang
Long Zhang
Jun Shen
Huayun Fan
Weilin Yan
Yuyou Huang
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Gree Electric Appliances Inc of Zhuhai
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Gree Electric Appliances Inc of Zhuhai
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Application filed by Gree Electric Appliances Inc of Zhuhai filed Critical Gree Electric Appliances Inc of Zhuhai
Priority to EP07720588A priority Critical patent/EP2003402B1/en
Priority to BRPI0709461-2A priority patent/BRPI0709461B1/pt
Publication of WO2007112671A1 publication Critical patent/WO2007112671A1/zh
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
    • F24F5/0017—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning using cold storage bodies, e.g. ice
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/14—Thermal energy storage

Definitions

  • the present invention relates to the field of air conditioning technology, and more particularly to a supercooled ice storage unit having a simple structure, a cold storage and a heat storage function, and an air conditioning system using the ice storage unit and a control method therefor.
  • the existing ice storage air conditioning system utilizes low-cost power during low-load period of the power grid, such as nighttime power, and the cold amount of the refrigeration system is stored in the water by a brine (usually an aqueous solution of ethylene glycol), and the water is frozen into Ice; in the high-load period of the electricity grid, such as during the day, the cold in the ice is released to provide cooling to the air-conditioning system, thereby reducing the power requirements during the high-load period of the grid, and realizing the "shifting peaks and valleys" of the power system.
  • a brine usually an aqueous solution of ethylene glycol
  • the ice storage system can achieve “load transfer” – transferring the cooling load during peak hours of power supply to the period of low power load, improving energy efficiency and solving power supply problems during peak hours. Therefore, this technology has been greatly welcomed by users and the power policy of the power sector, and has developed rapidly in China.
  • the heat exchanger regulating valve, the brine agent and the cold regulating valve are arranged on the pipeline of the inlet;
  • the ice tank pipeline is connected to the pipeline between the brine pump and the cold regulating valve, and the ice tank is arranged in turn on the ice tank pipeline
  • Valve and ice trough, the other end of the ice trough line is connected to the line between the refrigerating unit outlet and the heat exchanger inlet;
  • the bypass line is connected to the line between the heat exchanger regulating valve and the brine pump,
  • a bypass regulating valve is disposed on the bypass line, and the other end of the bypass line is connected to the pipeline between the ice tank regulating valve and the ice tank.
  • the technical problem to be solved by the present invention is to provide a supercooled ice storage unit having a simple structure, a cold storage and a heat storage function, and an air conditioning system and a control method using the above-described supercooled ice storage unit.
  • a supercooled ice storage unit including an ice storage device 61 and a closed circulation line, and the closed circulation line passes through the ice storage device 61,
  • the closed circulation line includes an electronic expansion valve 62 and three solenoid valves 63, 64, 65.
  • the electronic expansion valve 62 is connected in parallel with the solenoid valve 65, and the solenoid valves 63, 64 are connected in parallel.
  • the supercooled ice thermal storage unit further includes three external contacts 67, 68, 69; the external contact 67 is located on a side of the electronic expansion valve 62 remote from the ice storage device 61; the external contact 68 is located at the electromagnetic valve 63, 64 and Between the ice devices 61; a solenoid valve 66 is connected to a side of the solenoid valves 63, 64 adjacent to the external contact 68, and the other end of the solenoid valve 66 is an external contact 69.
  • An air conditioning system comprising a compressor 1, a gas-liquid separator 2, a four-way valve 3, an outdoor heat exchanger 4, a valve block 41 composed of an electronic expansion valve 42 and a check valve 43, and a high-pressure accumulator 5
  • the parallel indoor unit 7 and 8, the front end of the parallel indoor unit 7 and the 8 branch are respectively connected with electronic expansion valves 71 and 81, and the components are sequentially connected to form a closed circuit, and the high-pressure liquid storage unit 5 and the parallel indoor A supercooled ice storage unit 6 is also connected between the machines 7, 8.
  • the subcooled ice thermal storage unit 6 includes an ice storage device 61 and a closed circulation pipeline, and the closed circulation pipeline passes through the ice storage device 61, and the closed circulation pipeline includes an electronic expansion valve 62 and three electromagnetic Valves 63, 64, 65, the electronic expansion valve 62 and the solenoid valve 65 are connected in parallel, and the electromagnetic widths 63, 64 are connected in parallel.
  • the supercooled ice storage unit 6 also includes three external contacts 67, 68, 69, the external contact 67 is located on the side of the electronic expansion wide 62 away from the ice storage device 61; the external contact 68 is located between the electromagnetic valves 63, 64 and the ice storage device 61; A solenoid valve 66 is connected to a side of the valve 63, 64 adjacent to the external contact 68. The other end of the solenoid valve 66 is an external contact 69.
  • the external contact 67 and the external contact 68 are connected to the high pressure accumulator 5 and the indoor unit 7. Between 8, the external point 67 is close to the 5-terminal of the high-pressure accumulator; the external point 69 is connected between the four-way wide 3 and the indoor units 7, 8.
  • the air conditioning system is operated in ice storage by adjusting the working states of the valve block 41, the electronic expansion valve 62, the electromagnetic valves 63, 64, 65, 66 and the electronic expansion valves 71, 81 in the air conditioning system Switching between the six operating modes of ice-melting operation, conventional cooling operation, conventional heat pump operation, regenerative operation and heat release operation.
  • the specific operating modes and the status of each valve are as follows:
  • the supercooled ice cold storage unit designed by the invention can realize the switching of six operation modes of ice storage, ice melting refrigeration, conventional refrigeration, heat pump, heat storage and heat release, maximally utilize the capacity of ice storage equipment, and reasonably control to achieve the most Good energy saving effect.
  • the ice storage equipment acts as an evaporator in the summer evening, and uses the low price of electricity to carry out ice storage and cold storage; during the peak of daytime electricity consumption, the ice storage device acts as a subcooler of the condenser to improve the subcooling of the refrigerant, thereby improving the performance of the unit and increasing Cooling capacity, reduce air conditioning power consumption;
  • the air conditioning load of the room is small, it is possible to directly perform the conventional air conditioning operation without going through the ice storage device.
  • the system can also realize the heat storage operation.
  • the ice storage device acts as a condenser in the winter night, and uses the low electricity price to carry out the heat storage operation.
  • the ice storage device acts as an evaporator to improve the evaporation temperature of the whole machine. Therefore, the performance of the unit can be improved for a period of time, the heating capacity is increased, the power consumption of the air conditioner is reduced, and the optimal control and utilization of the ice storage device is realized, thereby achieving energy saving requirements.
  • FIG. 1 is a structural view of an ice storage device in the prior art
  • FIG. 2 is a structural view of an air conditioning system of the present invention
  • FIG. 3 is a flow chart of the operation of the refrigerant in the air conditioning system of the present invention when the ice storage operation is performed;
  • FIG. 4 is a flow chart showing the operation of the refrigerant in the air-conditioning system of the present invention when the ice-melting operation is performed;
  • FIG. 5 is a flow chart of the operation of the refrigerant in the conventional refrigeration operation of the air conditioning system of the present invention
  • FIG. 6 is a flow chart of the operation of the refrigerant in the air conditioning system of the present invention for realizing the operation of the conventional heat pump; Flow chart of the agent;
  • FIG. 8 is a flow chart showing the operation of the refrigerant in the air conditioning system of the present invention when the heat release heat pump is operated. detailed description
  • a subcooled ice thermal storage unit 6 is shown in the dashed box, which includes an ice storage device 61, a closed circulation line and three external contacts 67, 68, 69.
  • the closed circulation line passes through the ice storage device 61.
  • the closed circulation line includes an electronic expansion valve 62 and three solenoid valves 63, 64, 65.
  • the electronic expansion valve 62 is connected in parallel with one of the solenoid valves 65, and the other two solenoid valves 63 and 64 are connected in parallel.
  • the external contact 67 is located on a side of the electronic expansion valve 62 remote from the ice storage device 61; the external contact 68 is located between the electromagnetic valves 63, 64 and the ice storage device 61; and the electromagnetic valve 63, 6 is adjacent to the external contact 68 a solenoid valve 66 is connected to the side, and the other end of the solenoid valve 66 is an external contact 69;
  • an air conditioning system is provided, which comprises a compressor 1, a gas-liquid separator 2, a four-way valve 3, an outdoor heat exchanger 4, an electronic expansion flange 42 and a check valve 43.
  • the valve block 41, the high pressure accumulator 5, the parallel indoor unit 7, 8, and the front end of each indoor unit branch are respectively connected with electronic expansion valves 71, 81, and the components are sequentially connected to form a closed loop.
  • the air conditioning system further includes a subcooling type ice storage unit 6, wherein the external point 67 and the external point 68 are connected between the high pressure accumulator 5 and the indoor units 7, 8, and the external point 67 is adjacent to the high pressure accumulator 5 -
  • the external contact 68 is adjacent to the indoor unit 7, 8-end; the external contact 69 is connected between the four-way valve 3 and the indoor units 7, 8.
  • the above air conditioning system can be performed by the on/off control of the four solenoid valves 63, 64, 65, 66 1) and the adjustment control of an electronic expansion valve 62, and the adjustment control of the valve block 41 and the electronic expansion valves 71, 81. Control and switch between different operating modes. In a preferred embodiment of the present invention, switching and control of the air conditioning system between six operating modes, such as ice storage operation, ice melting operation, conventional cooling, conventional heat pump, heat storage operation, and heat release heat pump, can be realized. The control status of each of the above valves is shown in the following table: Status 41 62 63 64 65 71 81 66 Ice storage
  • FIG. 3 it is a flow chart of the operation of the refrigerant in the air conditioning system of the present invention.
  • the valve block 41 is in a bypass state, which means that the refrigerant passes only through the check valve 43 without passing through the electronic expansion valve 42.
  • the electronic expansion valve 42 in the bypass state can be in any state.
  • the electronic expansion valve 62 is in a throttle state, and the degree of throttling is automatically adjusted by the electronic expansion valve without a specific prescribed state.
  • the solenoid valves 63, 64, 65 and the electronic expansion valves 71, 81 are in a closed state, and the solenoid valve 66 is in an open state.
  • FIG. 4 it is a flow chart of the operation of the refrigerant in the air-conditioning system of the present invention.
  • the valve block 41 When the air conditioning system is in the ice-melting mode, the valve block 41 is in a bypass state, which means that the refrigerant passes only through the check valve 43, and does not pass through the electronic expansion valve 42.
  • the electronic expansion valve 42 in the bypass state can be in any state.
  • the electronic expansion width 62 is in any state, the solenoid valves 63, 64, 66 are in a closed state, and the electronic expansion valves 71, 81 are in a throttle state, and the degree of throttling is automatically adjusted by the electronic expansion valve without a specific regulation state.
  • the solenoid valve 65 is in the open state.
  • the ice storage device 61 When operating in the ice-melting mode, the ice storage device 61 acts as a subcooler of the outdoor heat exchanger 4 to increase the degree of refrigerant subcooling, thereby improving the performance of the unit, increasing the amount of refrigeration, and reducing the amount of electricity used by the air conditioner during peak hours.
  • FIG. 5 it is a flow chart of the operation of the refrigerant in the conventional refrigeration operation of the air conditioning system of the present invention.
  • the valve block 41 is in a bypass state, which means that the refrigerant passes only through the check valve 43, and does not pass through the electronic expansion valve 42.
  • the electronic expansion valve 42 in the bypass state can be in any state.
  • the electronic expansion valve 62 is in a closed state
  • the electromagnetic valve 63 is in an open state
  • the electromagnetic valve 64 is in an arbitrary state
  • the electromagnetic valves 65, 66 are in a closed state
  • the electronic expansion valves 71, 81 are in a throttle state
  • the degree of throttling is expanded by electrons.
  • the valve is automatically adjusted without specific conditions.
  • FIG. 6 it is a flow chart of the operation of the refrigerant in the air conditioning system of the present invention to realize the operation of the conventional heat pump.
  • the valve block 41 When the air conditioning system is in the normal heat pump operation mode, the valve block 41 is in a throttle state, and the throttle means The refrigerant only passes through the electronic expansion valve, and does not pass through the check valve. The degree of throttling is automatically adjusted by the electronic expansion valve without specific regulation.
  • the electronic expansion valve 62 is in a closed state
  • the solenoid valve 63 is in any state
  • the solenoid valve 64 is in an open state
  • the solenoid valves 65, 66 are in a closed state
  • the electronic expansion valves 71, 81 are in a fully open state.
  • FIG. 7 it is a flow chart of the operation of the refrigerant in the air conditioning system of the present invention.
  • the valve block 41 is in a throttling state, and the throttling means that the refrigerant only passes through the electronic expansion valve, and does not pass through the one-way valve, and the degree of throttling is automatically adjusted by the electronic expansion valve, without Specific regulatory status.
  • the electronic expansion valve 62 is in the fully open state
  • the solenoid valves 63, 64, 66 are in the closed state
  • the solenoid valve 65 is in any state
  • the electronic expansion valves 71, 81 are in the fully open state.
  • FIG. 8 it is a flow chart of the operation of the refrigerant in the air-conditioning system of the present invention.
  • the valve block 41 is in the fully open state
  • the electronic expansion valve 62 is in the fully open state
  • the solenoid valves 63, 66 are in the closed state
  • the solenoid valve 64 is in the open state
  • the solenoid valve 65 is in any state.
  • the electronic expansion valves 71, 81 are in a throttle state, and the degree of throttling is automatically adjusted by the electronic expansion valve without a specific prescribed state. '

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Description

技术领域
本发明涉及空调技术领域， 更具体地说， 涉及一种结构简单、 同时具有 蓄冷和蓄热功能的过冷式冰蓄冷机组， 以及使用该冰蓄冷机组的空调系统及 其控制方法。
背景技术
现有的冰蓄冷空调系统， 是利用电网低负荷期的廉价电力， 如夜间电力， 通过载冷剂 （通常为乙二醇水溶液） 将制冷系统制取的冷量贮存在水中， 把 水冻结成冰； 而在电价昂贵的电网高负荷期， 如白天， 将冰中的冷量释放出 来向空调系统供冷，从而减少电网高负荷期对电力的要求、实现电力系统 "移 峰填谷"的空调系统。 在供电紧张的地区， 冰蓄冷系统可以实现 "负荷转移" ——将电力供应高峰时段的冷负荷转移到电力负荷低谷时段， 提高能源利用 效率， 解决电力高峰期电力供应问题。 因此， 该技术受到了用户的欢迎和电 力部门的电力政策的大力支持， 在国内迅速发展。
2005年 3月 2日公开的申请日号为 200410074074. 6的中国专利"冰蓄冷 装置"， 参见图 1 , 该装置中制冷机组与换热器连接构成环路， 在换热器出口 与制冷机组入口的管路上设置换热器调节阀、 载冷剂和冷机调节阀； 在载冷 剂泵与冷机调节阀之间的管路上接冰槽管路， 冰槽管路上依次设置冰槽调节 阀和冰槽， 冰槽管路的另一端与制冷机组出口和换热器入口之间的管路连接； 在换热器调节阀和载冷剂泵之间的管路上接旁通管路， 旁通管路上设置旁通 调节阀， 旁通管路的另一端与冰槽调节阀和冰槽之间的管路连接。 賺认 这种冰蓄冷机组的不足之处在于： 1、 在原有制冷机组基础上改动较大， 另外需要载冷剂和载冷剂泵， 结构复杂， 成本高； 2、 这种冰蓄冷机组只具有 蓄冷功能， 而无蓄热功能； 3、 这种冰蓄冷机组无法提高制冷机组的过冷度。 发明内容
本发明所要解决的技术问题在于， 提供一种结构简单、 同时具有蓄冷和 蓄热功能的过冷式冰蓄冷机组， 以及使用上述过冷式冰蓄冷机组的空调系统 及其控制方法。
本发明所要解决的技术问题是通过如下技术方案实现的： 一种过冷式冰 蓄冷机组， 其中包括蓄冰装置 61和封闭循环管路， 所述封闭循环管路通过所 述蓄冰装置 61 , 所述封闭循环管路上包括一个电子膨胀阀 62和三个电磁阀 63、 64、 65, 所述电子膨胀阀 62和所述电磁阀 65并联， 所述电磁阀 63、 64 并联。 该过冷式冰蓄冷机组还包括三个外接点 67、 68、 69； 所述外接点 67位 于电子膨胀阀 62的远离蓄冰装置 61的一侧； 外接点 68位于电磁阀 63、 64 与蓄冰装置 61之间； 电磁阀 63、 64的靠近外接点 68的一侧连接有一电磁阀 66， 所述电磁阀 66的另一端为外接点 69。
一种空调系统， 其中包括压縮机 1、 气液分离器 2、 四通阀 3、 室外换热 器 4、 由电子膨胀阀 42和单向阀 43组成的阀组 41、高压储液器 5、并联室内 机 7、 8, 所述并联室内机 7、 8支路前端分别连接有电子膨胀阀 71、 81， 各 组件按顺序连接组成封闭回路， 所述高压储液器 5和所述并联室内机 7、 8之 间还连接有过冷式冰蓄冷机组 6。 所述过冷式冰蓄冷机组 6包括蓄冰装置 61 和封闭循环管路， 所述封闭循环管路通过所述蓄冰装置 61， 所述封闭循环管 路上包括一个电子膨胀阀 62和三个电磁阀 63、 64、 65， 所述电子膨胀阀 62 和所述电磁阀 65并联， 所述电磁阔 63、 64并联。 所述过冷式冰蓄冷机组 6 还包括三个外接点 67、 68、 69， 所述外接点 67位于电子膨胀阔 62的远离蓄 冰装置 61的一侧； 外接点 68位于电磁阀 63、 64与蓄冰装置 61之间； 电磁 阀 63、 64的靠近外接点 68的一侧连接有一电磁阀 66，所述电磁阀 66的另一 端为外接点 69;外接点 67和外接点 68连接于高压储液器 5与室内机 7、 8之 间， 外接点 67靠近高压储液器 5—端； 外接点 69接于四通阔 3与室内机 7、 8之间。
一种上述空调系统的控制方法， 通过调节空调系统中阀组 41、 电子膨胀 阀 62、 电磁阀 63、 64、 65、 66和电子膨胀阀 71、 81的工作状态， 使空调系 统在蓄冰运行、 融冰运行、 常规制冷运行、 常规热泵运行、 蓄热运行和释热 运行这六种运行模式间切换。 具体各运行模式与各阀门的状态参照表如下:
Figure imgf000005_0001
本发明设计的过冷式冰蓄冷机组能够实现蓄冰、 融冰制冷、 常规制冷、 热泵、 蓄热与释热六种运行模式的切换， 最大程度地利用蓄冰设备能力， 合 理控制， 达到最佳节能效果。 蓄冰设备在夏季夜晚作为蒸发器， 利用低谷优 惠的电价进行制冰蓄冷； 白天用电高峰期， 蓄冰设备作为冷凝器的过冷器提 高制冷剂过冷度， 从而改善机组的性能， 增加制冷量， 减少空调用电量； 当 房间空调负荷较小时， 又可以实现不经过蓄冰设备， 直接进行常规空调运行。 到了冬季， 此系统还可以实现蓄热运行， 冰蓄冷装置在冬季夜晚作为冷凝器， 利用低谷优惠的电价进行蓄热运行； 白天用电高峰期， 蓄冰设备作为蒸发器 提高整机运行蒸发温度， 从而在一段时间内提高机组性能， 增加制热量， 减 少空调用电量， 实现对蓄冰装置的最佳控制与利用， 达到节能要求。
附图说明
图 1为现有技术中冰蓄冷装置的结构图；
图 2为本发明空调系统的结构图；
图 3为本发明空调系统实现蓄冰运行时制冷剂的运行流程图；
图 4为本发明空调系统实现融冰运行时制冷剂的运行流程图；
图 5为本发明空调系统实现常规制冷运行时制冷剂的运行流程图； 图 6为本发明空调系统实现常规热泵运行时制冷剂的运行流程图； 图 7为本发明空调系统实现蓄热运行时 令剂的运行流程图；
图 8为本发明空调系统实现释热热泵运行时制冷剂的运行流程图。 具体实施方式
如图 2所示，虚线框中给出了一种过冷式冰蓄冷机组 6，其中包括蓄冰装 置 61、 封闭循环管路和三个外接点 67、 68、 69。 该封闭循环管路通过该蓄冰 装置 61。 封闭循环管路上包括一个电子膨胀阀 62和三个电磁阀 63、 64、 65， 电子膨胀阀 62和其中一个电磁阀 65并联， 另外两个电磁阀 63和 64并联。 其中所述外接点 67位于电子膨胀阀 62的远离蓄冰装置 61的一侧；外接点 68 位于电磁阀 63、 64与蓄冰装置 61之间； 电磁阀 63、 6 的靠近外接点 68的 一侧连接有一电磁阀 66， 所述电磁阀 66的另一端为外接点 69; 如图 2所示， 其中给出了一种空调系统， 其中包括压缩机 1、气液分离器 2、 四通阀 3、 室外换热器 4、 由电子膨胀阔 42和单向阀 43组成的阀组 41、 高压储液器 5、 并联室内机 7、 8， 各室内机支路前端分别连接有电子膨胀阀 71、 81， 各组件按顺序连接组成封闭回路。 另外， 该空调系统还包括一前述 过冷式冰蓄冷机组 6， 外接点 67和外接点 68接于高压储液器 5与室內机 7、 8之间， 外接点 67靠近高压储液器 5—端， 而外接点 68靠近室内机 7、 8— 端； 外接点 69接于四通阀 3与室内机 7、 8之间。 通过四个电磁阀 63、 64、 65、 66的通断控 1)与一个电子膨胀阀 62的调 节控制， 并配合阀组 41和电子膨胀阀 71、 81的调节控制， 可对上述空调系 统进行控制并在不同运行模式下切换。 在本发明的一个优选实施例中， 可实 现空调系统在蓄冰运行、 融冰运行、 常规 冷、 常规热泵、 蓄热运行和释热 热泵等六种运行模式间的切换和控制， 各运行模式下上述各阀门的控制状态 如下表所示： 状态 41 62 63 64 65 71 81 66 蓄冰
旁通 节流 关 关 关 关闭 关闭 .开
运行
融冰
旁 任意 关 关 开 节流 节流 ：关
运行
常规
旁通 关闭 开 任意 关 节流 节流 关
制冷
常规
节流 关闭 任意 开 关 全开 全开 关
蓄 By换八、、
节流 全开 关 关 任意 全开 全开 关
运行
释扭
1冤 全开 全开 关 开 任意 节流 节流 关 如图 3所示， 是本发明空调系统实现蓄冰运行时制冷剂的运行流程图。 当空调系统处于蓄冰运行模式时， 阀组 41处于旁通状态， 该旁通状态是指制 冷剂只通过单向阀 43， 而不经过电子膨胀阀 42。 旁通状态下电子膨胀阀 42 可以为任何状态。 电子膨胀阀 62处于节流状态， 其节流程度由电子膨胀阀自 动调节， 而无具体的规定状态。 电磁阀 63、 64、 65和电子膨胀阀 71、 81处 于关闭状态， 而电磁阀 66处于开启状态。
如图 4所示， 是本发明空调系统实现融冰运行时制冷剂的运行流程图。 当空调系统处于融冰运行模式时， 阀组 41处于旁通状态， 该旁通状态是指制 冷剂只通过单向阀 43, 而不经过电子膨胀阀 42。 旁通状态下电子膨胀阀 42 可以为任何状态。 电子膨胀阔 62处于任意状态， 电磁阀 63、 64、 66处于关 闭状态， 电子膨胀阀 71、 81处于节流状态， 其节流程度由电子膨胀阀自动调 节，而无具体的规定状态。而电磁阀 65处于开启状态。在融冰模式下运行时， 蓄冰装置 61作为室外换热器 4的过冷器提高制冷剂过冷度， 从而改善机组的 性能， 增加制冷量， 减少空调在电力高峰期用电量。
如图 5所示， 是本发明空调系统实现常规制冷运行时制冷剂的运行流程 图。 当空调系统处于常规制冷运行模式时， 阀组 41处于旁通状态， 该旁通状 态是指制冷剂只通过单向阀 43， 而不经过电子膨胀阀 42。 旁通状态下电子膨 胀阀 42可以为任何状态。 电子膨胀阀 62处于关闭状态， 电磁阀 63处于幵启 状态， 电磁阀 64处于任意状态， 电磁阀 65、 66处于关闭状态， 电子膨胀阀 71、 81处于节流状态， 其节流程度由电子膨胀阀自动调节， 而无具体的规定 状态。
如图 6所示， 是本发明空调系统实现常规热泵运行时制冷剂的运行流程 图。 当空调系统处于常规热泵运行模式时， 阀组 41处于节流状态， 节流是指 制冷剂只通过电子膨胀阀， 而不通过单向阀， 其节流程度由电子膨胀阀自动 调节， 而无具体的规定状态。 电子膨胀阀 62处于关闭状态， 电磁阀 63处于 任意状态， 电磁阀 64处于开启状态， 电磁阀 65、 66处于关闭状态， 电子膨 胀阀 71、 81处于全开状态。
如图 7所示， 是本发明空调系统实现蓄热运行时制冷剂的运行流程图。 当空调系统处于蓄热运行模式时， 阀组 41处于节流状态， 节流是指制冷剂只 通过电子膨胀阀， 而不通过单向阀， 其节流程度由电子膨胀阀自动调节， 而 无具体的规定状态。 电子膨胀阀 62处于全开状态， 电磁阀 63、 64、 66处于 关闭状态， 电磁阀 65处于任意状态， 电子膨胀阀 71、 81处于全开状态。
如图 8所示， 是本发明空调系统实现释热运行时制冷剂的运行流程图。 当空调系统处于释热运行模式时， 阀组 41处于全开状态， 电子膨胀阀 62处 于全开状态， 电磁阀 63、 66处于关闭状态， 电磁阀 64处于开启状态， 电磁 阀 65处于任意状态， 电子膨胀阀 71、 81处于节流状态， 其节流程度由电子 膨胀阀自动调节， 而无具体的规定状态。 '
由上述可见， 通过空调系统中各阀门的控制^ I以实现过冷式冰蓄冷机组 在六种运行模式中自由切换， 从而实现蓄冷和蓄热的最佳利用。
本发明还有其他一些变形或者改进。 如果本技术领域的技术人员受到本 发明的启发做出的显而易见的非实质性的改变或者改进， 均属于本发明权利 要求书的保护范围。

Claims

权 利 要 求
1、 一种过冷式冰蓄冷机组， 其特征在于， 其中包括蓄冰装置 （61)和封 闭循环管路， 所述封闭循环管路通过所述蓄冰装置 （61 ) ， 所述封闭循环管 路上包括一个电子膨胀阀 （62)和三个电磁阀 （63、 64、 65) ， 所述电子膨 胀阀 （62)和所述电磁阀 （65) 并联， 所述电磁阀 （63、 64) 并联。
2、 根据权利要求 1所述的过冷式冰蓄冷机组， 其特征在于， 还包括三个 外接点 （67、 68、 69) ； 所述外接点 （67)位于电子膨胀阀 （62) 的远离蓄 冰装置 （61 ) 的一侧； 外接点 （68)位于电磁阀 （63、 64) 与蓄冰装置 （61 ) 之间； 电磁阀 （63、 64) 的靠近外接点 （68) 的一侧连接有一电磁阀 （66) ， 所述电磁阀 （66) 的另一端为外接点 （69) 。 .
3、一种空调系统，其中包括压缩机 ( 1)、气液分离器（2)、四通阀（3)、 室外换热器（4) 、 由电子膨胀阀（42)和单向阀 （43)组成的阀组 （41 ) 、 高压储液器（5) 、 并联室内机（7'、 8) ， 所述并联室内机 （7、 8>支路前端 分别连接有电子膨胀阀 （71、 81 ) ， 各组件按顺序连接组成封闭回路， 其特 征在于， 还包括一过冷式冰蓄冷机组 （6) ， 所述过冷式冰蓄冷机组 （6)连 接在所述高压储液器 （5)和所述并联室内机 （7、 8)之间。
4、 根据权利要求 3所述的空调系统， 其特征在于， 所述过冷式冰蓄冷机 组（6) 包括蓄冰装置 （61 )和封闭循环管路， 所述封闭循环管路通过所述蓄 冰装置 （61 ) ， 所述封闭循环管路上包括一个电子膨胀阀 （62〉和三个电磁 阀 （63、 64、 65) ， 所述电子膨胀阀 （62)和所述电磁阀 （65) 并联， 所述 电磁阀 （63、 64) 并联。
5、 根据权利要求 4所述的空调系统， 其特征在于， 所述过冷式冰蓄冷机 组 （6)还包括三个外接点 （67、 68、 69) ， 所述外接点 （67) 位于电子膨胀 阀 （62) 的远离蓄冰装置 （61 ) 的一侧； 外接点 （68)位于电磁阀 （63、 64) 与蓄冰装置 （61 ) 之间； 电磁阀 （63、 64) 的靠近外接点 （68) 的一侧连接 有一电磁阀（66)， 所述电磁阀（66)的另一端为外接点（69)； 外接点（67) 和外接点（68)连接于高压储液器（5)与室内机（7、 8)之间， 外接点（67) 靠近高压储液器（5)—端； 外接点 （69)接于四通阀 （3)与室内机（7、 8) 之间。
6、 一种控制权利要求 3- 5所述空调系统的方法， 其特征在于， 调节空调 系统中阀组 （41 ) 、 电子膨胀阀（62) 、 电磁阀 （63、 64、 65、 66)和电子 膨胀阀 （71、 81 ) 的工作状态， 使空调系统在蓄冰运行、 融冰运行、 常规制 冷运行、 常规热泵运行、 蓄热运行和释热运行这六种运行模式间切换。
7、 根据权利要求 6所述的方法， 其特征在于， 当空调系统处于蓄冰运行 模式时， 阀组（41 ) 处于旁通状态， 电子膨胀阀 （62) 处于节流状态， 电磁 阀 （63、 64、 65) 和电子膨胀阀 （71、 81 ) 处于关闭状态， 而电磁阀 （66) 处于开启状态。
8、 根据权利要求 6所述的方法， 其特征在于， 当空调系统处于融冰运行 模式时， 阀组（41 ) 处于旁通状态， 电子膨胀阀 （62)处于任意状态， 电磁 阀 （63、 64、 66) 处于关闭状态， 电子膨胀阀 （71、 81 )处于节流状态， 而 电磁阀 （65) 处于开启状态。
9、 根据权利要求 6所述的方法， 其特征在于， 当空调系统处于常规制冷 运行模式时， 阀组 （41 ) 处于旁通状态， 电子膨胀阀 （62) 处于关闭状态， 电磁阀 （63) 处于开启状态， 电磁阀 （64) 处于任意状态， 电磁阀 （65、 66) 处于关闭状态， 电子膨胀阀 （71、 81 ) 处于节流状态。
10、 根据权利要求 6所述的方法， 其特征在于， 当空调系统处于常规热 泵运行模式时， 阀组（41 )处于节流状态， 电子膨胀阀 （62) 处于关闭状态， 电磁阀 （63)处于任意状态， 电磁阀 （64) 处于开启状态， 电磁阀 （65、 66) 处于关闭状态， 电子膨胀阀 （71、 81 ) 处于全开状态。
11、 根据权利要求 6所述的方法， 其特征在于， 当空调系统处于蓄热运 行模式时， 阀组 （41 ) 处于节流状态， 电子膨胀阀 （62)处于全开状态， 电 磁阀 （63、 64、 66) 处于关闭状态， 电磁阀 （65) 处于任意状态， 电子膨胀 阀 （71、 81 ) 处于全开状态。
12、 根据权利要求 6所述的方法， 其特征在于， 当空调系统处于释热运 行模式时， 阀组 （41 ) 处于全开状态， 电子膨胀阀 （62)处于全开状态， 电 磁阀 （63、 66) 处于关闭状态， 电磁阀 （64) 处于开启状态， 电磁阀 （65) 处于任意状态， 电子膨胀阀 （71、 81 )处于节流状态。
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EP2003402A9 (en) 2009-04-15
RU2008143068A (ru) 2010-05-10
EP2003402A2 (en) 2008-12-17
CN1825011A (zh) 2006-08-30
EP2003402A4 (en) 2009-04-29
BRPI0709461A2 (pt) 2011-07-12
EP2003402B1 (en) 2012-06-13
RU2419038C2 (ru) 2011-05-20

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