WO2020103521A1 - 一种补气增焓系统及其控制方法 - Google Patents

一种补气增焓系统及其控制方法

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Publication number
WO2020103521A1
WO2020103521A1 PCT/CN2019/104050 CN2019104050W WO2020103521A1 WO 2020103521 A1 WO2020103521 A1 WO 2020103521A1 CN 2019104050 W CN2019104050 W CN 2019104050W WO 2020103521 A1 WO2020103521 A1 WO 2020103521A1
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WO
WIPO (PCT)
Prior art keywords
gas
heat exchanger
compressor
superheat
pipeline
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PCT/CN2019/104050
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English (en)
French (fr)
Inventor
魏会军
罗惠芳
吴健
杨欧翔
巩庆霞
邹鹏
陈圣
柯达俊
Original Assignee
珠海格力节能环保制冷技术研究中心有限公司
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Application filed by 珠海格力节能环保制冷技术研究中心有限公司 filed Critical 珠海格力节能环保制冷技术研究中心有限公司
Publication of WO2020103521A1 publication Critical patent/WO2020103521A1/zh

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24HEATING; RANGES; VENTILATING
    • F24FAIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00Air-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
    • F24F5/0003Exclusively-fluid systems
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00Compression machines, plants or systems, with reversible cycle
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00Fluid-circulation arrangements
    • F25B41/30Expansion means; Dispositions thereof
    • F25B41/31Expansion valves

Definitions

  • the present application relates to the technical field of compressors and air-conditioning systems, in particular to an air supplement and enthalpy increasing system and a control method thereof.
  • This application requires the priority of the patent application submitted to the State Intellectual Property Office of China on November 19, 2018, with the application number 201811377572.6 and the invention titled "A system for supplementing gas and enthalpy and its control method".
  • the two-stage compressed air supplementary compression technology with flash evaporator can effectively solve the problems of insufficient heating, low energy efficiency and poor reliability of the air source heat pump at low ambient temperature.
  • abnormal phenomena such as unstable control, compressor burnout, or abnormal wear of the compressor often occur.
  • the present application provides an air supplement and enthalpy increase system and a control method thereof.
  • the gas supplementation and enthalpy increasing system includes a gas-liquid pipeline, a gas-phase pipeline, and a heat exchange channel between the gas-liquid pipeline and the gas-phase pipeline;
  • the gas-liquid pipeline includes a pipeline between the exhaust port of the compressor and the gas-liquid inlet of the flash evaporator;
  • the gas-phase pipeline includes a pipeline between the gas-phase outlet of the flash evaporator and the air-filling port of the compressor.
  • the supplemental gas and enthalpy-increasing system includes a compressor, a first heat exchanger, a flash evaporator, and a second heat exchanger;
  • the inlet is connected;
  • the gas phase outlet of the flash evaporator is connected to the air supply port of the compressor, and the liquid phase outlet of the flash evaporator is connected to the second heat exchanger and the suction port of the compressor in turn.
  • gas-liquid pipeline includes a pipeline between the first heat exchanger and the gas-liquid inlet of the flash evaporator.
  • gas-liquid pipeline includes a pipeline parallel to a pipeline between the exhaust port of the compressor and the first heat exchanger.
  • the heat exchange channel includes a bidirectional countercurrent heat exchanger; the heat release channel of the heat exchanger is provided on the gas-liquid pipeline; and the heat absorption channel of the heat exchanger is provided on the gas phase pipeline.
  • a first throttle device is provided between the gas-liquid inlet of the first heat exchanger and the flash evaporator; a second node is provided between the liquid phase outlet of the flash evaporator and the second heat exchanger ⁇ ⁇ Flow device.
  • the temperature sensing element of the first throttling device is provided on the pipeline at the air inlet of the compressor; the temperature sensing element of the second throttling device is provided at the suction port of the compressor On the pipeline.
  • a first check valve that can only flow to the air inlet of the compressor is provided in front of the air inlet of the compressor.
  • the supplemental gas and enthalpy increasing system includes an exchange valve assembly for exchanging the position of the first heat exchanger in the system and the position of the second heat exchanger in the system.
  • the exchange valve assembly includes a first four-way valve and a second four-way valve
  • the pipeline between the exhaust port of the compressor and the first heat exchanger and the pipeline between the second heat exchanger and the suction port of the compressor meet at the first four-way valve;
  • the pipeline between the liquid phase outlet of the flash evaporator and the second heat exchanger and the pipeline between the gas and liquid inlets of the first heat exchanger and the flash evaporator meet at the second four-way valve;
  • the first throttling device is provided between the second four-way valve and the gas-liquid inlet of the flash evaporator; the third throttling device is provided between the first heat exchanger and the second four-way valve.
  • the temperature sensing element of the third throttling device is arranged on the pipeline at the suction port of the compressor;
  • a second bypass is connected in parallel between the two ends of the second throttle device, and the second bypass is provided with a second check valve that can only flow to the second four-way valve;
  • a third bypass is connected in parallel between the two ends, and the third bypass is provided with a third check valve that can only flow to the second four-way valve;
  • the first exchange is changed by adjusting the communication modes of the four ports of the first four-way valve and the second four-way valve and the on-off of the second throttle device and the third throttle device
  • the position of the heat exchanger in the system is exchanged with the position of the second heat exchanger in the system.
  • the first heat exchanger includes an outdoor side heat exchanger.
  • the second heat exchanger includes an indoor side heat exchanger.
  • a first temperature sensor is provided at the suction port of the compressor, a second temperature sensor is provided at the wall of the second heat exchanger tube, and a third temperature sensor is provided at the air supply port of the compressor , A fourth temperature sensor is provided at the gas-liquid inlet of the flash evaporator, and a fifth temperature sensor is provided on the wall of the first heat exchanger tube.
  • the present application also provides a method for controlling the air supplement and enthalpy increase system, the method includes the following steps:
  • S2 Determine the supplementary gas superheat degree according to the supplemental gas temperature T 3 and the gas-liquid temperature T 4 and control the supplemental gas superheat degree to be within a preset range of the supplemental gas superheat degree;
  • S3 Determine the suction superheat degree according to the suction temperature T 1 and the second heat exchanger tube wall temperature T 2 and control the suction superheat degree to be within a preset range of the suction superheat degree;
  • S4 Determine the supplementary gas superheat degree according to the supplemental gas temperature T 3 and the gas-liquid temperature T 4 and control the supplemental gas superheat degree to be within a preset range of the supplemental gas superheat degree.
  • the determining of the superheat degree of supplemental gas according to the supplemental gas temperature T 3 and the gas-liquid temperature T 4 includes:
  • controlling the degree of supplemental gas superheat within the preset range of the degree of supplemental gas superheat includes:
  • the supplementary gas superheat is adjusted to the preset range of the supplemental gas superheat by adjusting the opening degree of the first throttle device.
  • controlling the degree of supplemental gas superheat within the preset range of the degree of supplemental gas superheat includes:
  • the determining the suction superheat degree according to the suction temperature T 1 and the second heat exchanger tube wall temperature T 2 includes:
  • controlling the degree of suction superheat within the preset range of the degree of suction superheat includes:
  • the suction superheat is adjusted to be adjusted by adjusting the opening of the second or third throttling device communicating with the liquid phase outlet of the flash evaporator to The suction superheat degree is within a preset range.
  • the preset range of the supplementary gas superheat includes: 0.5-8 ° C.
  • the preset range of the supplementary gas superheat includes: 2-5 ° C.
  • the preset range of the suction superheat includes: 1-10 ° C.
  • the preset range of the suction superheat includes: 3-8 ° C.
  • the supplementary gas and enthalpy increasing system provided by the technical solution provided by the present application, through the gas-liquid pipeline between the exhaust port of the compressor and the gas-liquid inlet of the flash evaporator and the gas phase outlet of the flash evaporator and the compressor
  • a heat exchange channel is provided between the gas phase pipelines between the gas ports to realize the heat exchange between the high-temperature gas at the compressor exhaust port and the gas in front of the compressor air supplement port, and the heat of the supplement air injected into the compressor is increased by heat exchange to make it
  • There is a stable degree of superheat which greatly improves the reliability of the compressor and its air conditioning system.
  • FIG. 1 is a schematic diagram of the first air-conditioning system mentioned in the background art of this application;
  • FIG. 2 is a schematic diagram of a second air-conditioning system mentioned in the background technology of this application;
  • FIG. 3 is a schematic diagram of a third air-conditioning system mentioned in the background technology of this application.
  • FIG. 4 is a schematic diagram of a fourth air-conditioning system mentioned in the background of this application.
  • FIG. 5 is a schematic diagram of the air supplement and enthalpy increasing system provided in Example 1 of the present application.
  • Example 6 is a flowchart of a control method of a supplemental gas and enthalpy-enhancing system provided in Example 2 of the present application;
  • Example 7 is a schematic diagram of an air supplement and enthalpy increase system provided in Example 3 of the present application.
  • Example 8 is a schematic diagram of the flow direction in different modes of the supplemental gas and enthalpy increase system provided in Example 3 of the present application;
  • Example 9 is a flowchart of a control method of a supplemental gas and enthalpy-enhancing system provided in Example 4 of the present application.
  • the present application provides an air supplementation and enthalpy increase system, which is a single-cooling air conditioning system or a single heat heat pump system;
  • the supplemental gas and enthalpy-increasing system includes a compressor 1, a flash evaporator 8, a first heat exchanger 5 and a second heat exchanger 13; the exhaust port 2 of the compressor is in turn connected with the first heat exchanger 5 and the flash evaporator The gas-liquid inlet 9 of the flasher is connected; the gas-phase outlet 10 of the flash evaporator is connected to the air supply port 4 of the compressor; Air port 3 connection;
  • the gas supplementation and enthalpy increase system includes a heat exchange channel 6 between a gas-liquid pipeline and a gas-phase pipeline;
  • the gas-liquid pipeline includes a pipeline between the exhaust port 2 of the compressor and the gas-liquid inlet 9 of the flash evaporator;
  • the gas-phase pipeline includes a pipeline between the gas-phase outlet 10 of the flash evaporator and the air supply port 4 of the compressor;
  • the gas-liquid pipeline includes a pipeline between the first heat exchanger 5 and the gas-liquid inlet 9 of the flash evaporator.
  • the heat exchange channel 6 includes a bidirectional countercurrent heat exchanger; the heat release channel of the heat exchanger is provided on the gas-liquid pipeline; and the heat absorption channel of the heat exchanger is provided on the gas phase pipeline.
  • a first throttle device 7 is provided between the first heat exchanger 5 and the gas-liquid inlet 9 of the flash evaporator; a liquid phase outlet 11 of the flash evaporator and a second heat exchanger 13 are provided Two throttle device 12.
  • the temperature-sensing element 26 of the first throttle device is provided on the pipeline at the air inlet 4 of the compressor; the temperature-sensing element 27 of the second throttle device is provided at the suction port 3 of the compressor On the pipeline.
  • a first check valve 29 that can only flow to the air supply port 4 of the compressor is provided in front of the air supply port 4 of the compressor.
  • a first temperature sensor 14 is provided at the suction port 3 of the compressor, a second temperature sensor 15 is provided on the tube wall of the second heat exchanger 13, and a third temperature is provided at the air supply port 4 of the compressor.
  • the temperature sensor 16 is provided with a fourth temperature sensor 17 at the gas-liquid inlet 9 of the flash evaporator.
  • the first heat exchanger 5 includes a condenser; the second heat exchanger 13 includes an evaporator; and the first and second throttling devices 7 and 12 are used to adjust the degree of superheat of intake air and the degree of superheat of supplemental air , To ensure a stable suction superheat and a stable supplemental air superheat, greatly improving the reliability of the compressor and its air conditioning system.
  • this embodiment is the control method of the air supplement and enthalpy-enhancing system in Embodiment 1.
  • the method includes the following steps:
  • S2 Determine the supplementary gas superheat degree according to the supplemental gas temperature T 3 and the gas-liquid temperature T 4 and control the supplemental gas superheat degree to be within a preset range of the supplemental gas superheat degree;
  • S3 Determine the suction superheat degree according to the suction temperature T 1 and the second heat exchanger tube wall temperature T 2 and control the suction superheat degree to be within a preset range of the suction superheat degree;
  • S4 Determine the supplementary gas superheat degree according to the supplemental gas temperature T 3 and the gas-liquid temperature T 4 and control the supplemental gas superheat degree to be within a preset range of the supplemental gas superheat degree.
  • the determining of the superheat degree of supplemental gas according to the supplemental gas temperature T 3 and the gas-liquid temperature T 4 includes:
  • SH supplementary gas T 3 -T 4; the SH supplementary gas is supplemental gas superheat.
  • the controlling of the supplementary gas superheat degree within the preset range of the supplemental gas superheat degree includes:
  • the supplementary gas superheat is adjusted to the preset range of the supplementary gas superheat by adjusting the opening degree of the first throttle device; specifically, when When the supplementary gas superheat degree is lower than the lower limit of the preset range of the supplementary gas superheat degree, the opening degree of the first throttle device is adjusted down, when the supplemental gas superheat degree is higher than the supplemental gas superheat degree When the upper limit of the preset range of is set, the opening of the first throttle device is increased;
  • the opening degree and the opening degree of the first throttle device adjust the supplementary gas superheat to a preset range of the supplemental gas superheat; specifically, when the supplemental gas superheat is lower than the supplemental gas
  • the opening of the second throttle device and the opening of the first throttle device are adjusted separately, when the supplementary gas superheat is higher than the preset value of the supplemental gas superheat
  • the opening of the second throttle device and the opening of the first throttle device are increased respectively.
  • Said determining the degree of suction superheat according to said suction temperature T1 and said second heat exchanger tube wall temperature T2 includes:
  • SH inhalation T 1- T 2 ; the SH inhalation is inhalation superheat.
  • the controlling the degree of suction superheat within the preset range of the degree of suction superheat includes:
  • the suction superheat is adjusted to the suction superheat by adjusting the opening of the second throttle device communicating with the liquid phase outlet of the flash evaporator Within the preset range; specifically, when the supplementary gas superheat is lower than the lower limit of the preset range of supplemental gas superheat, then the opening of the second throttle device is adjusted down when the supplement When the gas superheat degree is higher than the upper limit of the preset range of the supplementary gas superheat degree, the opening degree of the second throttle device is increased.
  • the preset range of the supplemental gas superheat includes: 0.5-8 ° C.
  • the preset range of the supplemental gas superheat includes: 2-5 ° C.
  • the preset range of the suction superheat includes: 1-10 ° C.
  • the preset range of the suction superheat includes: 3-8 ° C.
  • the air supplement and enthalpy increase system provided in this embodiment is a heat pump air conditioning system with both heating and cooling functions.
  • the difference from Embodiment 1 is that:
  • the gas-liquid pipeline includes a pipeline parallel to the pipeline between the discharge port 2 of the compressor and the first heat exchanger 5.
  • the system includes an exchange valve assembly for exchanging the position of the first heat exchanger 5 in the system and the position of the second heat exchanger 13 in the system.
  • the exchange valve assembly includes a first four-way valve 18 and a second four-way valve 19;
  • the pipeline between the exhaust port 2 of the compressor and the first heat exchanger 5 and the pipeline between the second heat exchanger 13 and the suction port 3 of the compressor meet at the first four Through valve 18; the pipeline between the liquid phase outlet 11 of the flash evaporator and the second heat exchanger 13 and the pipeline between the first heat exchanger 5 and the gas-liquid inlet 9 of the flash evaporator meet at the Describe the second four-way valve 19;
  • the first throttling device 7 is provided between the second four-way valve 19 and the gas-liquid inlet 9 of the flash evaporator; a third is provided between the first heat exchanger 5 and the second four-way valve 19 Throttling device 20; the temperature sensing element 28 of the third throttling device is provided on the pipeline at the suction port 3 of the compressor.
  • a second bypass is connected in parallel between the two ends of the second throttle device 12, the second bypass is provided with a second check valve 21 that can only flow to the second four-way valve 19;
  • the third section A third bypass is connected in parallel between the two ends of the flow device 20, and the third bypass is provided with a third check valve 22 that can only flow to the second four-way valve 19;
  • the first heat exchanger 5 includes an outdoor side heat exchanger.
  • the second heat exchanger 13 includes an indoor-side heat exchanger.
  • the first throttle device 7 includes a first thermal expansion valve
  • the second throttle device 12 includes a second thermal expansion valve
  • the third throttle device 20 includes a third thermal expansion valve.
  • the compressor in this embodiment is a two-cylinder, two-stage air-filled rotor compressor. Its high-pressure stage cylinder 23 communicates with the compressor's exhaust port 2 and its low-pressure stage cylinder 25 communicates with the compressor's suction port 3 Communicate, the intermediate chamber 24 is provided between the high-pressure stage cylinder 23 and the low-pressure stage cylinder 25 and communicates with the air supply port 4 of the compressor; the superheated medium-pressure gas received in the air supply port and The intermediate-pressure gas compressed by the low-pressure stage cylinder 25 merges and enters the high-pressure stage cylinder 23.
  • the air supplement and enthalpy increase system provided in this embodiment may be in two modes of cooling and heating;
  • the positions of the first heat exchanger 5 and the second heat exchanger 13 in the system are the same as those in Embodiment 1, and the first four-way valve and the compressor exhaust port 2
  • the communicating port communicates with the first heat exchanger 5; the communicating port with the second heat exchanger and the suction port 3 of the compressor communicate; the second section
  • the flow device 12 is turned on; the third throttle device 20 is turned off.
  • the positions of the first heat exchanger 5 and the second heat exchanger 13 in the system are opposite to those in Embodiment 1, namely, the first heat exchanger 5 and the second heat exchanger 13
  • the positions in the system are interchanged, specifically, the port in the first four-way valve communicating with the discharge port 2 of the compressor and the port in communication with the second heat exchanger 13 are in communication with the first
  • the port communicating with the heat exchanger 5 communicates with the port communicating with the suction port 3 of the compressor; the second throttle device 12 is turned off; and the third throttle device 20 is turned off.
  • this embodiment is the control method in the heating mode of the air supplementation and enthalpy-enhancing system in Embodiment 3.
  • the positions of the first heat exchanger and the second heat exchanger are exchanged in the system Therefore, the method is different from Example 2 in that the tube wall temperature T 2 of the second heat exchanger collected in Example 2 is replaced by the tube wall temperature T 5 of the first heat exchanger, and all subsequent applications of T 2 Everywhere is replaced by T 5 ; and the step of adjusting the opening of the second throttle device needs to be replaced by adjusting the opening of the third throttle device.

Abstract

一种补气增焓系统及其控制方法,补气增焓系统包括气液管路、气相管路和气液管路与气相管路间的换热通道(6);气液管路包括压缩机(1)的排气口(2)与闪蒸器(8)的气液进口(9)间的管路;气相管路包括闪蒸器(8)的气相出口(10)与压缩机(1)的补气口(4)间的管路。通过在压缩机(1)的排气口(2)与闪蒸器(8)的气液进口(9)间的气液管路和闪蒸器(8)的气相出口(10)与压缩机的补气口(4)间的气相管路间设置换热通道(6),实现了压缩机(1)排气口(2)的高温气体与压缩机(1)补气口(4)前的气体的换热,通过换热增加喷入压缩机(1)的补气的热量,使其存在稳定的过热度,大幅度提升了压缩机(1)及其空调系统的可靠性。

Description

一种补气增焓系统及其控制方法 技术领域
本申请涉及压缩机、空调系统技术领域,尤其涉及一种补气增焓系统及其控制方法。本申请要求于2018年11月19日提交至中国国家知识产权局、申请号为201811377572.6、发明名称为“一种补气增焓系统及其控制方法”的专利申请的优先权。
背景技术
带闪蒸器的中间补气双级压缩技术,可有效地解决空气源热泵在低环境温度下的制热量不足、能效低和可靠性差等问题,但是带闪蒸器的中间补气双级压缩技术在实际热泵设备,在变工况和变负荷运行时,时常出现控制不稳定、压缩机烧毁或者压缩机异常磨损等异常现象。
为解决上述技术问题,现有技术有一类空调系统,如图1所示,通过三个电子膨胀阀分别精确控制高压回路、低压回路和补气回路的冷媒流量,基于排气过热度、吸气过热度和冷凝器出口过冷度解耦性调节3支电子膨胀阀,但控制策略过于复杂,且成本颇高;还有一类空调系统,如图2所示,具有可视化窗口的闪蒸器、恒定电热源加热喷射管路的PID控制策略,但PID控制更加复杂,成本较高;还有一类空调系统,如图3所示,为一种带闪蒸器的中间补气双级压缩系统的补气控制方法,其特点是补气状态不受控,压缩机极易补气带液运行,导致压缩机的异常磨损;还有一种空调系统,如图4所示,为一种带闪蒸器的中间补气双级压缩系统的补气控制方法,补气过热度仅依靠阀门调节冷媒流量,缺少一个换热设备进行过热度的调节,因此过热度控制范围非常窄。
因此,需要提供一种补气增焓系统及其控制方法来解决现有技术的不足。
发明内容
为了解决现有技术中的问题,本申请提供了一种补气增焓系统及其控制方法。
一种补气增焓系统,
所述补气增焓系统包括气液管路、气相管路和气液管路与气相管路间的换热通道;
所述气液管路包括压缩机的排气口与闪蒸器的气液进口间的管路;
所述气相管路包括所述闪蒸器的气相出口与所述压缩机的补气口间的管路。
进一步的,所述补气增焓系统包括压缩机、第一换热器、闪蒸器和第二换热器;所述压缩机的排气口依次与第一换热器和闪蒸器的气液进口连接;所述闪蒸器的气相出口与所述压缩机的补气口连接,所述闪蒸器的液相出口依次与第二换热器和所述压缩机的吸气口连接。
进一步的,所述气液管路包括第一换热器与所述闪蒸器的气液进口间的管路。
进一步的,所述气液管路包括与所述压缩机的排气口与所述第一换热器间管路并联的管路。
进一步的,所述换热通道包括双向逆流换热器;所述换热器的放热通道设于所述气液管路上;所述换热器的吸热通道设于所述气相管路上。
进一步的,所述第一换热器与所述闪蒸器的气液进口间设有第一节流装置;所述闪蒸器的液相出口与所述第二换热器间设有第二节流装置。
进一步的,所述第一节流装置的感温件设于所述压缩机的补气口处的管路上;所述第二节流装置的感温件设于所述压缩机的吸气口处的管路上。
进一步的,所述压缩机的补气口前设有只能流向所述压缩机的补气口的第一止回阀。
进一步的,所述补气增焓系统包括用于交换所述第一换热器在系统中位置和所述第二换热器在系统中位置的交换阀门组件。
进一步的,所述交换阀门组件包括第一四通阀和第二四通阀;
所述压缩机的排气口与所述第一换热器间管路和所述第二换热器与所述压缩机的吸气口间管路交汇于所述第一四通阀;所述闪蒸器的液相出口与所述第二换热器间管路和所述第一换热器与所述闪蒸器的气液进口间管路交汇于所述第二四通阀;
第一节流装置设于所述第二四通阀与所述闪蒸器的气液进口间;所述第一换热器与所述第二四通阀间设有第三节流装置,所述第三节流装置的感温件设于所述压缩机的吸气口处的管路上;
所述第二节流装置的两端间并联第二旁路,所述第二旁路设有只能流向所述第二四通阀的第二止回阀;所述第三节流装置的两端间并联第三旁路,所述第三旁路设有只能流向所述第二四通阀的第三止回阀;
分别通过调节所述第一四通阀和所述第二四通阀的四个口的连通方式以及所述第二节流装置和所述第三节流装置的通断将所述第一换热器在系统中的位置和所述第二换热器的在系统中的位置交换。
进一步的,所述第一换热器包括室外侧换热器。
进一步的,所述第二换热器包括室内侧换热器。
进一步的,所述压缩机的吸气口处设有第一温度传感器,所述第二换热器管壁上设有第二温度传感器,所述压缩机的补气口处设有第三温度传感器,所述闪蒸器的气液进口处设有第四温度传感器,所述第一换热器管壁上设有第五温度传感器。
基于同一发明思路,本申请还提供了一种补气增焓系统的控制方法,所述方法包括下述步骤:
S1:采集压缩机的吸气口前的吸气温度T 1、第二换热器管壁温度T 2、压缩机补气口处的补气温度T 3和闪蒸器的气液进口前的气液温度T 4
S2:根据所述补气温度T 3和所述气液温度T 4确定补气过热度并控制所述补气过热度在所述补气过热度的预设范围内;
S3:根据所述吸气温度T 1和所述第二换热器管壁温度T 2确定吸气过热度并控制所述吸气过热度在所述吸气过热度的预设范围内;
S4:根据所述补气温度T 3和所述气液温度T 4确定补气过热度并控制所述补气过热度在所述补气过热度的预设范围内。
进一步的,所述根据所述补气温度T 3和所述气液温度T 4确定补气过热度包括:
按照下式计算所述补气过热度:
补气过热度=T 3-T 4
进一步的,所述控制所述补气过热度在所述补气过热度的预设范围内包括:
比较所述补气过热度是否在所述补气过热度的预设范围内;
在所述补气过热度的范围内无动作;
不在所述补气过热度的范围内,则通过调节第一节流装置的开度将所述补气过热度调节至所述补气过热度的预设范围内。
进一步的,所述控制所述补气过热度在所述补气过热度的预设范围内包括:
比较所述补气过热度是否在所述补气过热度的预设范围内;
在所述补气过热度的预设范围内无动作;
不在所述补气过热度的预设范围内,则通过依次调节与所述闪蒸器的液相出口相通的第二节流装置或第三节流装置的开度和所述第一节流装置的开度将所述补气过热度调节至所述补气过热度的预设范围内。
进一步的,所述根据所述吸气温度T 1和所述第二换热器管壁温度T 2确定吸气过热度包括:
按照下式计算所述吸气过热度:
吸气过热度=T 1-T 2
进一步的,所述控制所述吸气过热度在所述吸气过热度的预设范围内包括:
比较所述吸气过热度是否在所述吸气过热度的预设范围内;
在所述吸气过热度的预设范围内无动作;
不在所述吸气过热度的预设范围内,则通过调节与所述闪蒸器的液相出口相通的第二节流装置或第三节流装置的开度将所述吸气过热度调节至所述吸气过热度的预设范围内。
进一步的,所述补气过热度的预设范围包括:0.5-8℃。
进一步的,所述补气过热度的预设范围包括:2-5℃。
进一步的,所述吸气过热度的预设范围包括:1-10℃。
进一步的,所述吸气过热度的预设范围包括:3-8℃。
本申请的技术方案与最接近的现有技术相比具有如下优点:
本申请提供的技术方案提供的补气增焓系统,通过在压缩机的排气口与闪蒸器的气液进口间的气液管路和所述闪蒸器的气相出口与所述压缩机的补气口间的气相管路间设置换热通道,实现了压缩机排气口的高温气体与压缩机补气口前的气体的换热,通过换热增加喷入压缩机的补气的热量,使其存在稳定的过热度,大幅度提升了压缩机及其空调系统的可靠性。
附图说明
图1是本申请背景技术中提到的第一种空调系统的示意图;
图2是本申请背景技术中提到的第二种空调系统的示意图;
图3是本申请背景技术中提到的第三种空调系统的示意图;
图4是本申请背景技术中提到的第四种空调系统的示意图;
图5是本申请实施例1提供的补气增焓系统的示意图;
图6是本申请实施例2提供的补气增焓系统的控制方法的流程图;
图7是本申请实施例3提供的补气增焓系统的示意图;
图8是本申请实施例3提供的补气增焓系统不同模式下的流向示意图;
图9是本申请实施例4提供的补气增焓系统的控制方法的流程图。
其中,1、压缩机;2、压缩机的排气口;3、压缩机的吸气口;4、压缩机的补气口;5、第一换热器;6、换热通道;7、第一节流装置;8、闪蒸器;9、闪蒸器的气液进口;10、闪蒸器的气相出口;11、闪蒸器的液相出口;12、第二节流装置;13、第二换热器;14、第一温度传感器;15、第二温度传感器;16、第三温度传感器;17、第四温度传感器;18、第一四通阀;19、第二四通阀;20、第三节流装置;21、第二止回阀;22、第三止回阀;23、高压级气缸;24、中间腔;25、低压级气缸;26、第一节流装置的感温件;27、第二节流装置的 感温件;28、第三节流装置的感温件;29、第一止回阀;30、第五温度传感器。
具体实施方式
为使本申请实施例的目的、技术方案和优点更加清楚,下面将结合本申请实施例中的附图,对本申请实施例中的技术方案进行清楚、完整地描述,显然,所描述的实施例是本申请的一部分实施例,而不是全部的实施例。基于本申请中的实施例,本领域普通技术人员在没有做出创造性劳动的前提下所获得的所有其他实施例,都属于本申请保护的范围。
实施例1
如图5所示,本申请提供了一种补气增焓系统,该补气增焓系统为单冷的空调系统或者单热的热泵系统;
所述补气增焓系统包括压缩机1、闪蒸器8、第一换热器5和第二换热器13;所述压缩机的排气口2依次与第一换热器5和闪蒸器的气液进口9连接;所述闪蒸器的气相出口10与所述压缩机的补气口4连接,所述闪蒸器的液相出口11依次与第二换热器13和所述压缩机的吸气口3连接;
所述补气增焓系统包括气液管路与气相管路间的换热通道6;
所述气液管路包括压缩机的排气口2与闪蒸器的气液进口9间的管路;
所述气相管路包括所述闪蒸器的气相出口10与所述压缩机的补气口4间的管路;
所述气液管路包括第一换热器5与所述闪蒸器的气液进口9间的管路。
所述换热通道6包括双向逆流换热器;所述换热器的放热通道设于所述气液管路上;所述换热器的吸热通道设于所述气相管路上。
所述第一换热器5与所述闪蒸器的气液进口9间设有第一节流装置7;所述闪蒸器的液相出口11与所述第二换热器13间设有第二节流装置12。
所述第一节流装置的感温件26设于所述压缩机的补气口4处的管路上;所述第二节流装置的感温件27设于所述压缩机的吸气口3处的管路上。
所述压缩机的补气口4前设有只能流向所述压缩机的补气口4的第一止回阀29。
所述压缩机的吸气口3处设有第一温度传感器14,所述第二换热器13管壁上设有第二温度传感器15,所述压缩机的补气口4处设有第三温度传感器16,所述闪蒸器的气液进口9处设有第四温度传感器17。
所述第一换热器5包括冷凝器;所述第二换热器13包括蒸发器;通过第一节流装置7和第二节流装置12对吸气过热度和补气过热度进行调节,保证了稳定的吸气过热度和稳定的补气过热度,大幅度提升了压缩机及其空调系统的可靠性。
实施例2
如图6所示,本实施例为实施例1中补气增焓系统的控制方法,所述方法包括下述步骤:
S1:采集压缩机的吸气口前的吸气温度T 1、第二换热器管壁温度T 2、压缩机补气口处的补气温度T 3和闪蒸器的气液进口前的气液温度T 4
S2:根据所述补气温度T 3和所述气液温度T 4确定补气过热度并控制所述补气过热度在所述补气过热度的预设范围内;
S3:根据所述吸气温度T 1和所述第二换热器管壁温度T 2确定吸气过热度并控制所述吸气过热度在所述吸气过热度的预设范围内;
S4:根据所述补气温度T 3和所述气液温度T 4确定补气过热度并控 制所述补气过热度在所述补气过热度的预设范围内。
所述根据所述补气温度T 3和所述气液温度T 4确定补气过热度包括:
按照下式计算所述补气过热度:
SH 补气=T 3-T 4;所述SH 补气为补气过热度。
所述控制所述补气过热度在所述补气过热度的预设范围内包括:
比较所述补气过热度是否在所述补气过热度的预设范围内;
在所述补气过热度的范围内无动作;
不在所述补气过热度的预设范围内,则通过调节第一节流装置的开度将所述补气过热度调节至所述补气过热度的预设范围内;具体地,当所述补气过热度低于所述补气过热度的预设范围的下限时,则调小所述第一节流装置的开度,当所述补气过热度高于所述补气过热度的预设范围的上限时,则调大所述第一节流装置的开度;
若通过第一节流装置不能将所述补气过热度调节至所述补气过热度的预设范围内,则通过依次调节与所述闪蒸器的液相出口相通的第二节流装置的开度和所述第一节流装置的开度将所述补气过热度调节至所述补气过热度的预设范围内;具体地,当所述补气过热度低于所述补气过热度的预设范围的下限时,则分别调小第二节流装置的开度和第一节流装置的开度,当所述补气过热度高于所述补气过热度的预设范围的上限时,则分别调大第二节流装置的开度和第一节流装置的开度。
所述根据所述吸气温度T1和所述第二换热器管壁温度T2确定吸气过热度包括:
按照下式计算所述吸气过热度:
SH 吸气=T 1-T 2;所述SH 吸气为吸气过热度。
所述控制所述吸气过热度在所述吸气过热度的预设范围内包括:
比较所述吸气过热度是否在所述吸气过热度的预设范围内;
在所述吸气过热度的预设范围内无动作;
不在所述吸气过热度的预设范围内,则通过调节与所述闪蒸器的液相出口相通的第二节流装置的开度将所述吸气过热度调节至所述吸气过热度的预设范围内;具体地,当所述补气过热度低于所述补气过热度的预设范围的下限时,则调小所述第二节流装置的开度,当所述补气过热度高于所述补气过热度的预设范围的上限时,则调大所述第二节流装置的开度。
在本申请的一些实施例中,所述补气过热度的预设范围包括:0.5-8℃。
在本申请的一些实施例中,所述补气过热度的预设范围包括:2-5℃。
在本申请的一些实施例中,所述吸气过热度的预设范围包括:1-10℃。
在本申请的一些实施例中,所述吸气过热度的预设范围包括:3-8℃。
实施例3
如图7和图8所示,本实施例提供的补气增焓系统为冷暖两用的热泵式空调系统,其与实施例1的不同之处在于:
所述气液管路包括与所述压缩机的排气口2与所述第一换热器5间管路并联的管路。
所述系统包括用于交换所述第一换热器5在系统中位置和所述第二换热器13在系统中位置的交换阀门组件。
所述交换阀门组件包括第一四通阀18和第二四通阀19;
所述压缩机的排气口2与所述第一换热器5间管路和所述第二换热器13与所述压缩机的吸气口3间管路交汇于所述第一四通阀18;所述闪蒸器的液相出口11与所述第二换热器13间管路和所述第一换热器5与所述闪蒸器的气液进口9间管路交汇于所述第二四通阀19;
第一节流装置7设于所述第二四通阀19与所述闪蒸器的气液进口9间;所述第一换热器5与所述第二四通阀19间设有第三节流装置20;所述第三节流装置的感温件28设于所述压缩机的吸气口3处的管路上。
所述第二节流装置12的两端间并联第二旁路,所述第二旁路设有只能流向所述第二四通阀19的第二止回阀21;所述第三节流装置20的两端间并联第三旁路,所述第三旁路设有只能流向所述第二四通阀19的第三止回阀22;
分别通过调节所述第一四通阀18和所述第二四通阀19的四个口的连通方式以及所述第二节流装置12和所述第三节流装置20的通断将所述第一换热器5在系统中的位置和所述第二换热器13的在系统中的位置交换。
所述第一换热器5包括室外侧换热器。
所述第二换热器13包括室内侧换热器。
所述第一节流装置7包括第一热力膨胀阀,所述第二节流装置12包括第二热力膨胀阀,第三节流装置20包括第三热力膨胀阀。
本实施中的压缩机为双缸双级补气转子式压缩机,其高压级气缸23与所述压缩机的排气口2连通,其低压级气缸25与所述压缩机的吸气口3连通,所述中间腔24设于所述高压级气缸23与所述低压级气缸25间且与所述压缩机的补气口4连通;所述补气口中接收的过热度稳定的中压气体与经过低压级气缸25压缩的中压气体汇合后进入高压 级气缸23。
本实施例提供的补气增焓系统可为制冷和制热两个模式;
制冷模式时,所述第一换热器5和所述第二换热器13在系统中的位置与实施例1相同,此时第一四通阀中与所述压缩机的排气口2相通的口和与所述第一换热器5相通的口连通;与所述第二换热器相通的口和与所述压缩机的吸气口3相通的口连通;所述第二节流装置12开启;所述第三节流装置20关断。
制热模式时,所述第一换热器5和所述第二换热器13在系统中的位置与实施例1中相反,即第一换热器5与所述第二换热器13在系统中的位置互换,具体地,第一四通阀中与所述压缩机的排气口2相通的口和与所述第二换热器13相通的口连通;与所述第一换热器5相通的口和与所述压缩机的吸气口3相通的口连通;所述第二节流装置12关断;所述第三节流装置20关断。
本实施例中由于制热模式时第一换热器5和第二换热器13在系统中的位置互换,因此需要在第一换热器5的管壁上设有第五温度传感器30。
本实施例通过设置两个四通阀和第三节流装置20以及第二止回阀21和第三止回阀22,实现了该系统制冷模式和制热模式的转换。
实施例4
如图9所示,本实施例为实施例3中补气增焓系统制热模式时的控制方法,此模式下第一换热器与所述第二换热器在系统中的位置互换,因此所述方法与实施例2的不同在于,实施例2中所采集的第二换热器管壁温度T 2替换为第一换热器管壁温度T 5,且后续所有应用T 2之处皆替换为T 5;且需要调节第二节流装置的开度的步骤则需要替换为调节第三节流装置的开度。
需要说明的是,在本文中,诸如“第一”和“第二”等之类的关系术语仅仅用来将一个实体或者操作与另一个实体或操作区分开来,而不一定要求或者暗示这些实体或操作之间存在任何这种实际的关系或者顺序。
最后应说明的是:以上实施例仅用以说明本申请的技术方案,而非对其限制;尽管参照前述实施例对本申请进行了详细的说明,本领域的普通技术人员应当理解:其依然可以对前述各实施例所记载的技术方案进行修改,或者对其中部分技术特征进行等同替换;而这些修改或者替换,并不使相应技术方案的本质脱离本申请各实施例技术方案的精神和范围。

Claims (23)

  1. 一种补气增焓系统,其特征在于,包括气液管路、气相管路和气液管路与气相管路间的换热通道(6)以及压缩机(1);
    所述气液管路包括压缩机的排气口(2)与闪蒸器的气液进口(9)间的管路;
    所述气相管路包括所述闪蒸器的气相出口(10)与所述压缩机(1)的补气口(4)间的管路。
  2. 根据权利要求1所述的补气增焓系统,其特征在于,
    所述补气增焓系统包括第一换热器(5)、闪蒸器(8)和第二换热器(13);所述压缩机(1)的排气口(2)依次与第一换热器(5)和闪蒸器的气液进口(9)连接;所述闪蒸器(8)的气相出口(10)与所述压缩机(1)的补气口(4)连接,所述闪蒸器(8)的液相出口(11)依次与第二换热器(13)和所述压缩机(1)的吸气口(3)连接。
  3. 根据权利要求2所述的补气增焓系统,其特征在于,所述气液管路包括第一换热器(5)与所述闪蒸器(8)的气液进口(9)间的管路。
  4. 根据权利要求2所述的补气增焓系统,其特征在于,所述气液管路包括与所述压缩机(1)的排气口(2)与所述第一换热器(5)间管路并联的管路。
  5. 根据权利要求1所述的补气增焓系统,其特征在于,所述换热通道(6)包括双向逆流换热器;所述换热器的放热通道设于所述气液管路上;所述换热器的吸热通道设于所述气相管路上。
  6. 根据权利要求2所述的补气增焓系统,其特征在于,所述第一换热器(5)与所述闪蒸器(8)的气液进口(9)间设有第一节流装置 (7);所述闪蒸器(8)的液相出口(11)与所述第二换热器(13)间设有第二节流装置(12)。
  7. 根据权利要求6所述的补气增焓系统,其特征在于,所述第一节流装置的感温件(26)设于所述压缩机(1)的补气口(4)处的管路上;所述第二节流装置的感温件(27)设于所述压缩机(1)的吸气口(3)处的管路上。
  8. 根据权利要求2所述的补气增焓系统,其特征在于,所述压缩机(1)的补气口(4)前设有只能流向所述压缩机(1)的补气口(4)的第一止回阀(29)。
  9. 根据权利要求2所述的补气增焓系统,其特征在于,所述补气增焓系统包括用于交换所述第一换热器(5)在系统中位置和所述第二换热器(13)在系统中位置的交换阀门组件。
  10. 根据权利要求9所述的补气增焓系统,其特征在于,所述交换阀门组件包括第一四通阀(18)和第二四通阀(19);
    所述压缩机(1)的排气口(2)与所述第一换热器(5)间管路和所述第二换热器(13)与所述压缩机(1)的吸气口(3)间管路交汇于所述第一四通阀(18);所述闪蒸器(8)的液相出口(11)与所述第二换热器(13)间管路和所述第一换热器(5)与所述闪蒸器(8)的气液进口(9)间管路交汇于所述第二四通阀(19);
    第一节流装置(7)设于所述第二四通阀(19)与所述闪蒸器(8)的气液进口(9)间;所述第一换热器(5)与所述第二四通阀(19)间设有第三节流装置(20);所述第三节流装置的感温件(28)设于所述压缩机(1)的吸气口(3)处的管路上;
    所述第二节流装置(12)的两端间并联第二旁路,所述第二旁路设有只能流向所述第二四通阀(19)的第二止回阀(21);所述第三节 流装置(20)的两端间并联第三旁路,所述第三旁路设有只能流向所述第二四通阀(19)的第三止回阀(22);
    分别通过调节所述第一四通阀(18)和所述第二四通阀(19)的四个口的连通方式以及所述第二节流装置(12)和所述第三节流装置(20)的通断将所述第一换热器(5)在系统中的位置和所述第二换热器(13)的在系统中的位置交换。
  11. 根据权利要求9所述的补气增焓系统,其特征在于,所述第一换热器(5)包括室外侧换热器。
  12. 根据权利要求9所述的补气增焓系统,其特征在于,所述第二换热器(13)包括室内侧换热器。
  13. 根据权利要求2所述的补气增焓系统,其特征在于,所述压缩机(1)的吸气口(3)处设有第一温度传感器(14),所述第二换热器(13)管壁上设有第二温度传感器(15),所述压缩机(1)的补气口(4)处设有第三温度传感器(16),所述闪蒸器(8)的气液进口(9)处设有第四温度传感器(17),所述第一换热器(5)管壁上设有第五温度传感器(30)。
  14. 一种如权利要求1至13任一项所述的补气增焓系统的控制方法,其特征在于,所述方法包括下述步骤:
    S1:采集压缩机(1)的吸气口(3)处的吸气温度T 1、第二换热器(13)管壁温度T 2、压缩机(1)补气口(4)处的补气温度T 3和闪蒸器(8)的气液进口(9)处的气液温度T 4
    S2:根据所述补气温度T 3和所述气液温度T 4确定补气过热度并控制所述补气过热度在所述补气过热度的预设范围内;
    S3:根据所述吸气温度T 1和所述第二换热器管壁温度T 2确定吸气过热度并控制所述吸气过热度在所述吸气过热度的预设范围内;
    S4:根据所述补气温度T 3和所述气液温度T 4确定补气过热度并控制所述补气过热度在所述补气过热度的预设范围内。
  15. 根据权利要求14所述的控制方法,其特征在于,所述根据所述补气温度T 3和所述气液温度T 4确定补气过热度包括:
    按照下式计算所述补气过热度:
    SH 补气=T 3-T 4;所述SH 补气为补气过热度。
  16. 根据权利要求14所述的控制方法,其特征在于,所述控制所述补气过热度在所述补气过热度的预设范围内包括:
    比较所述补气过热度是否在所述补气过热度的预设范围内;
    在所述补气过热度的范围内无动作;
    不在所述补气过热度的范围内,则通过调节第一节流装置(7)的开度将所述补气过热度调节至所述补气过热度的预设范围内。
  17. 根据权利要求14所述的控制方法,其特征在于,所述控制所述补气过热度在所述补气过热度的预设范围内包括:
    比较所述补气过热度是否在所述补气过热度的预设范围内;
    在所述补气过热度的预设范围内无动作;
    不在所述补气过热度的预设范围内,则通过依次调节与所述闪蒸器(8)的液相出口(11)相通的第二节流装置(12)或第三节流装置(20)的开度和所述第一节流装置(7)的开度将所述补气过热度调节至所述补气过热度的预设范围内。
  18. 根据权利要求14所述的控制方法,其特征在于,所述根据所述吸气温度T 1和所述第二换热器管壁温度T 2确定吸气过热度包括:
    按照下式计算所述吸气过热度:
    SH 吸气=T 1-T 2;所述SH 吸气为吸气过热度。
  19. 根据权利要求14所述的控制方法,其特征在于,所述控制所 述吸气过热度在所述吸气过热度的预设范围内包括:
    比较所述吸气过热度是否在所述吸气过热度的预设范围内;
    在所述吸气过热度的预设范围内无动作;
    不在所述吸气过热度的预设范围内,则通过调节与所述闪蒸器(8)的液相出口相通的第二节流装置(12)或第三节流装置(20)的开度将所述吸气过热度调节至所述吸气过热度的预设范围内。
  20. 根据权利要求14所述的控制方法,其特征在于,所述补气过热度的预设范围包括:0.5-8℃。
  21. 根据权利要求20所述的控制方法,其特征在于,所述补气过热度的预设范围包括:2-5℃。
  22. 根据权利要求14所述的控制方法,其特征在于,所述吸气过热度的预设范围包括:1-10℃。
  23. 根据权利要求22所述的控制方法,其特征在于,所述吸气过热度的预设范围包括:3-8℃。
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