WO2020258795A1 - 多级压缩空调系统及其控制方法 - Google Patents

多级压缩空调系统及其控制方法 Download PDF

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WO2020258795A1
WO2020258795A1 PCT/CN2019/128422 CN2019128422W WO2020258795A1 WO 2020258795 A1 WO2020258795 A1 WO 2020258795A1 CN 2019128422 W CN2019128422 W CN 2019128422W WO 2020258795 A1 WO2020258795 A1 WO 2020258795A1
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Prior art keywords
impeller
stage compression
temperature
pipeline
low
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PCT/CN2019/128422
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English (en)
French (fr)
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张治平
李宏波
韩璐遥
赵全超
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Gree Electric Appliances Inc of Zhuhai
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Gree Electric Appliances Inc of Zhuhai
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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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • 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
    • 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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • 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
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • This application relates to the field of refrigeration, in particular to a multi-stage compression air conditioning system and a control method thereof.
  • a double-head hanging structure is generally adopted.
  • the double-head hanging structure is connected by pipelines between the low-pressure refrigerant exhaust port and the high-pressure refrigerant suction port, and conducts the refrigerant compressed in the low-pressure stage to the high-pressure stage for compression, reducing overheating loss.
  • the high-pressure liquid refrigerant in the condenser is throttled and pressure-reduced, and separated by the flasher.
  • the gaseous refrigerant enters the pipeline between the low-pressure refrigerant exhaust port and the high-pressure refrigerant suction port. But the general multi-stage compression centrifugal unit still has overheat loss.
  • This application provides a multi-stage compression air conditioning system and a control method thereof to further reduce the overheat loss.
  • a multi-stage compression air-conditioning system including a two-stage compression system and an exhaust gas cooling pipeline.
  • the two-stage compression system includes a low-stage compression assembly, a high-level compression assembly, a condenser, a first throttling device, a flasher, and an evaporator arranged in sequence
  • the pipeline between the exhaust port of the low-stage compression assembly and the suction port of the high-level compression assembly is the first pipeline.
  • One end of the exhaust gas cooling pipeline is connected to the condenser, and the other end of the exhaust gas cooling pipeline is connected to the first pipeline.
  • a pipeline is connected, and a second throttling device is arranged on the exhaust cooling pipeline.
  • the above solution provides a multi-stage compression air-conditioning system.
  • the exhaust gas cooling pipeline is used to conduct a small amount of refrigerant in the condenser to the first pipeline, thereby
  • the opening of the second throttling device on the exhaust cooling pipeline the temperature of the refrigerant introduced into the advanced compression assembly through the first pipeline is adjusted, so that the suction temperature of the advanced compression assembly is close to the saturated gas phase temperature under this pressure , To further reduce overheating loss.
  • the two-stage compression system further includes a third throttling device, and the third throttling device is connected between the flash generator and the evaporator.
  • the first throttle device is a primary throttle orifice
  • the third throttle device is a secondary throttle orifice
  • the second throttling device is an electronic expansion valve.
  • the low-level compression assembly and the high-level compression assembly form a double hanging head compressor.
  • the two ends of the motor shaft of the double hanging head compressor are respectively hung with a low-level impeller and a high-level impeller, and the first pipeline is connected to the lower-level impeller. Between the exhaust port and the suction port of the advanced impeller.
  • the end of the motor shaft with the low-level impeller is also provided with a first impeller, and the first pipeline is connected between the exhaust port of the first impeller and the suction port of the high-level impeller; or, the motor shaft There is also a second impeller at the end where the high-level impeller is hung.
  • the first pipeline is connected between the exhaust port of the low-level impeller and the suction port of the second impeller; or the end where the low-level impeller is hung on the motor shaft is also provided There is a third impeller, the first pipeline is two, one of the first pipeline is connected between the exhaust port of the low-level impeller and the suction port of the high-level impeller, and the other first pipeline is connected to the exhaust of the high-level impeller Between the inlet and the suction port of the third impeller; or, the end of the high-grade impeller hung on the motor shaft is also provided with a fourth impeller, the first pipeline is two, and one of the first pipelines is connected to the fourth impeller Between the exhaust port and the suction port of the low-level impeller, another first pipeline is connected between the exhaust port of the low-level impeller and the suction port of the high-level impeller.
  • the low-stage compression component is a low-stage compressor
  • the high-stage compression component is a high-grade compressor
  • the first pipeline is connected between the discharge port of the low-stage compressor and the suction port of the high-grade compressor.
  • a control method of a multi-stage compression air conditioning system includes the following steps:
  • the opening of the second throttling device is maintained
  • the opening of the second throttling device is reduced
  • the opening degree of the second throttle means is increased.
  • the above-described embodiment provides a method for controlling a multi-stage compression air conditioning system, by adjusting the opening degree of the second throttle device, so that eventually a difference between the saturation temperature of the intake air temperature T gas compression assembly is advanced in the high allowable difference T range of values, even when the compression assembly have advanced high temperature T of the intake gas temperature T close to saturation, thereby further reducing the loss of overheating.
  • the allowable difference range is -0.5°C to 0.5°C.
  • the saturated gas phase Increase the temperature T.
  • control method of the multi-stage compression air conditioning system further includes the following steps:
  • the opening degree of the second throttling device is adjusted according to the difference between the saturated gas phase temperature T and the suction temperature T high , and the relationship between the difference and the allowable difference range.
  • Figure 1 is a system diagram of the multi-stage compression air conditioning system of this embodiment
  • Fig. 2 is a flowchart of the control method of the multi-stage compression air-conditioning system of this embodiment.
  • Multi-stage compression air conditioning system 11. Exhaust cooling pipeline; 111. Second throttling device; 12. Two-stage compression system; 121. Low-stage compression assembly; 122. Advanced compression assembly; 123. Condenser; 124. The first throttle device; 125, the flasher; 126, the third throttle device; 127, the evaporator; 13, the first pipeline; 14, the suction pipeline; 15, the exhaust pipeline; 16, the air supplement pipe road.
  • a multi-stage compression air-conditioning system 10 including a two-stage compression system 12 and an exhaust gas cooling pipeline 11.
  • the two-stage compression system 12 includes a low-stage compression assembly 121, The advanced compression assembly 122, the condenser 123, the first throttling device 124, the flasher 125 and the evaporator 127.
  • the pipeline between the exhaust port of the low-level compression assembly 121 and the suction port of the high-level compression assembly 122 is the first pipeline 13, one end of the exhaust gas cooling pipeline 11 is connected to the condenser 123, and the exhaust gas cooling pipeline 11 The other end is in communication with the first pipeline 13, and a second throttling device 111 is provided on the exhaust gas cooling pipeline 11.
  • the refrigerant exchanges heat in the evaporator 127 and enters the low-stage compression assembly 121 through the suction line 14 to be compressed.
  • the compressed high-temperature and high-pressure refrigerant enters the high-level compression assembly 122 through the first pipeline 13 and passes through the high-level compression assembly 122.
  • the further compressed refrigerant enters the condenser 123 through the exhaust pipe 15.
  • the high-pressure liquid refrigerant in the condenser 123 is throttled and depressurized by the first throttling device 124, it is flashed and separated in the flasher 125, and the separated gaseous refrigerant is connected to the flasher 125 and the first tube
  • the supplemental gas pipeline 16 between the circuits 13 enters the first pipeline 13 to cool the refrigerant in the first pipeline 13, but the saturated refrigerant flashed from the flash generator 125 and the low-stage compression component 121 are compressed and discharged After the superheated refrigerant is mixed, it is impossible to reduce to the saturated state, that is, complete cooling cannot be achieved.
  • the two-stage compression system 12 consisting of the low-stage compression assembly 121, the high-stage compression assembly 122, the condenser 123, the first throttling device 124, the flasher 125, and the evaporator 127 connected in sequence is an incompletely cooled two-stage compression system.
  • the flash generator is improved in the multi-stage compression centrifugal unit to further reduce the superheat loss, but on the one hand, the cost is high, and on the other hand, the suction temperature of the advanced compression component cannot reach the saturated gas phase temperature.
  • the exhaust gas cooling pipeline 11 is further provided in the two-stage compression system 12, and the exhaust gas cooling pipeline 11 is used to conduct a small amount of refrigerant in the condenser 123 to the first pipeline 13, and then the first pipeline The refrigerant in 13 cools down.
  • the opening degree of the second throttling device 111 on the exhaust cooling pipeline 11 the temperature of the refrigerant introduced into the advanced compression assembly 122 through the first pipeline 13 is adjusted so that the suction temperature of the advanced compression assembly 122 is close to this
  • the saturated gas phase temperature under pressure further reduces the superheat loss.
  • the structure is simple and the cost is low.
  • the two-stage compression system 12 further includes a third throttling device 126, and the third throttling device 126 is connected between the flasher 125 and the evaporator 127.
  • the liquid refrigerant obtained by flash separation by the flash generator 125 passes through the third throttling device 126 and then enters the evaporator 127.
  • the low-level compression assembly 121 and the high-level compression assembly 122 form a double-head compressor.
  • the two ends of the motor shaft of the double-head compressor are respectively hung with a low-level impeller and a high-level impeller.
  • the pipeline 13 communicates between the exhaust port of the low-level impeller and the suction port of the high-level impeller.
  • the low-stage compression component 121 is a low-stage compressor
  • the high-grade compression component 122 is a high-grade compressor
  • the first pipeline 13 is connected between the discharge port of the low-stage compressor and the suction port of the high-grade compressor ,
  • the refrigerant compressed and discharged by the low-level compressor is introduced into the high-level compressor through the first pipeline 13.
  • the dual-head compressor may have a multi-stage compression function.
  • the end of the motor shaft where the low-level impeller is hung is further provided with a first impeller, and the first pipeline 13 is connected between the exhaust port of the first impeller and the suction port of the high-level impeller; or, The end of the motor shaft with the high-level impeller is also provided with a second impeller, and the first pipeline 13 is connected between the exhaust port of the low-level impeller and the suction port of the second impeller; or, the motor shaft is hung with a low-level impeller.
  • One end is also provided with a third impeller.
  • first pipelines 13 There are two first pipelines 13, one of which is connected between the exhaust port of the lower-stage impeller and the suction port of the higher-stage impeller, and the other first pipeline 13 is connected Between the exhaust port of the high-grade impeller and the suction port of the third impeller; or, the end of the high-grade impeller hanging on the motor shaft is also provided with a fourth impeller, the first pipeline 13 is two, one of which is the first pipe
  • the path 13 communicates between the exhaust port of the fourth impeller and the suction port of the lower-stage impeller
  • the other first pipe 13 communicates between the exhaust port of the lower-stage impeller and the suction port of the higher-stage impeller.
  • the refrigerant in the exhaust cooling pipeline 11 can pass through the first pipeline 13
  • the incoming refrigerant cools down to make it close to the saturated gas phase temperature.
  • the second throttling device 111 is an electronic expansion valve.
  • the electronic expansion valve can adjust the opening degree according to the temperature of the saturated gas phase, so that the suction temperature of the advanced compression component 122 is close to the temperature of the saturated gas phase, reducing the overheat loss.
  • the second throttling device 111 may also be other devices capable of performing throttling control, which is not specifically limited here.
  • the first throttle device 124 is a primary throttle orifice
  • the third throttle device 126 is a secondary throttle orifice
  • a method for controlling a multi-stage compression air conditioning system 10 which includes the following steps:
  • the saturated gas phase temperature T can be obtained according to the pressure average value P; for example, the saturated gas phase temperature T under the corresponding pressure can be found through the refrigerant physical parameter comparison table.
  • the opening degree of the second throttle device 111 is maintained
  • the opening of the second throttling device 111 is reduced ;
  • the opening of the second throttle device 111 is increased .
  • the above-described embodiment there is provided a method of controlling multi-stage compression air conditioning system 10 by adjusting the opening degree of the second throttle device 111, and finally the saturated vapor phase such that the difference between the temperature T advanced compression assembly 122, the intake air temperature high T Within the allowable difference range, the suction temperature T of the advanced compression component 122 is made high close to the saturated gas phase temperature T, thereby further reducing the superheat loss.
  • the allowable difference range can be set according to the actual situation.
  • the size of the range reflects the difference between the allowable inhalation temperature and the saturated gas temperature. The closer the difference range is to 0, the inhalation after the system is adjusted. The closer the temperature is to the saturated gas phase temperature.
  • the allowable difference range is -0.5°C to 0.5°C.
  • the exhaust gas temperature of the advanced compression component 122 is lower than the condensation temperature by ⁇ T within the preset time period ⁇ t, and ⁇ T is always less than the preset temperature difference value within the preset time period ⁇ t, it is proved that the first The refrigerant in the pipeline 13 is cooled too much, so that the saturated gas phase temperature T is increased, and then the opening of the second throttle device 111 is decreased according to the aforementioned steps.
  • the saturated gas phase temperature can be increased by 1°C each time, the preset time period ⁇ t is 3 min, and the preset temperature difference is 4°C.
  • control method of the multi-stage compression air conditioning system 10 further includes the following steps:
  • the opening degree of the second throttle device 111 is adjusted according to the difference between the saturated gas phase temperature T and the suction temperature T high , and the relationship between the difference and the allowable difference range.
  • each device When the system is just turned on, each device does not enter normal operation.
  • the refrigerant in the supplemental gas line 16 will have time to cool the refrigerant in the first line 13 in the future.
  • the opening of the second throttling device 111 is maintained. It is 0; after the system is started up, adjust the opening degree of the second throttling device 111 according to the aforementioned process.
  • the opening degree of the electronic expansion valve is adjusted according to the aforementioned steps.

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  • Physics & Mathematics (AREA)
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Abstract

一种多级压缩空调系统及其控制方法，系统包括：两级压缩系统(12)，包括依次连通的低级压缩组件(121)、高级压缩组件(122)、冷凝器(123)、第一节流装置(124)、闪发器(125)、第三节流装置(126)和蒸发器(127)，低级压缩组件(121)的排气口与高级压缩组件(122)的吸气口之间为第一管路(13)；还包括排气冷却管路(11)，一端与冷凝器(123)连通，将冷凝器(123)中的少量制冷剂传导至第一管路(13)。通过调节排气冷却管路(11)上第二节流装置(111)的开度，使得高级压缩组件(122)的吸气温度接近该压力下的饱和气相温度，进一步降低过热损失。

Description

多级压缩空调系统及其控制方法
本申请要求于2019年06月26日提交至中国国家知识产权局，申请号为201910562444.7，发明名称为“多级压缩空调系统及其控制方法”的专利申请的优先权。
技术领域
本申请涉及制冷领域，特别是涉及一种多级压缩空调系统及其控制方法。
背景技术
在多级(双级及双级以上的)压缩机离心机组中，为了减少推力，一般采用双头挂结构。双头挂结构在低压级冷媒排气口与高压级冷媒吸气口之间通过管路连接，将低压级压缩的冷媒传导给高压级压缩，减少过热损失。冷凝器的高压液态制冷剂则经过节流降压后，经闪发器进行分离后，气态制冷剂则进入低压级冷媒排气口与高压级冷媒吸气口之间的管路中。但是一般多级压缩离心机组仍然存在过热损失。
发明内容
本申请提供了一种多级压缩空调系统及其控制方法，以进一步降低过热损失。
一种多级压缩空调系统，包括两级压缩系统和排气冷却管路，两级压缩系统包括依次设置的低级压缩组件、高级压缩组件、冷凝器、第一节流装置、闪发器和蒸发器，低级压缩组件的排气口与高级压缩组件的吸气口之间的管路为第一管路，排气冷却管路的一端与冷凝器连通，排气冷却管路的另一端与第一管路连通，排气冷却管路上设有第二节流装置。
上述方案提供了一种多级压缩空调系统，通过在两级压缩系统中进一步设 置排气冷却管路，利用排气冷却管路将冷凝器中的少量制冷剂传导至第一管路中，从而通过调节排气冷却管路上的第二节流装置的开度大小，调整通过第一管路导入高级压缩组件的制冷剂的温度，使得高级压缩组件的吸气温度接近该压力下的饱和气相温度，进一步降低过热损失。
在其中一个实施例中，两级压缩系统中还包括第三节流装置，第三节流装置连通在闪发器和蒸发器之间。
在其中一个实施例中，第一节流装置为一级节流孔板，第三节流装置为二级节流孔板。
在其中一个实施例中，第二节流装置为电子膨胀阀。
在其中一个实施例中，低级压缩组件和高级压缩组件组成双挂头压缩机，双挂头压缩机的电机轴的两端分别挂有低级叶轮和高级叶轮，第一管路连通在低级叶轮的排气口与高级叶轮的吸气口之间。
在其中一个实施例中，电机轴上挂有低级叶轮的一端还设有第一叶轮，第一管路连通在第一叶轮的排气口与高级叶轮的吸气口之间；或者，电机轴上挂有高级叶轮的一端还设有第二叶轮，第一管路连通在低级叶轮的排气口与第二叶轮的吸气口之间；或者，电机轴上挂有低级叶轮的一端还设有第三叶轮，第一管路为两个，其中一个第一管路连通在低级叶轮的排气口与高级叶轮的吸气口之间，另一个第一管路连通在高级叶轮的排气口与第三叶轮的吸气口之间；或者，电机轴上挂有高级叶轮的一端还设有第四叶轮，第一管路为两个，其中一个第一管路连通在第四叶轮的排气口与低级叶轮的吸气口之间，另一个第一管路连通在低级叶轮的排气口与高级叶轮的吸气口之间。
在其中一个实施例中，低级压缩组件为低级压缩机，高级压缩组件为高级压缩机，第一管路连通在低级压缩机的排气口与高级压缩机的吸气口之间。
一种多级压缩空调系统的控制方法，包括以下步骤：
获取上述的多级压缩空调系统中低级压缩组件的排气压力P 1、高级压缩组件的吸气压力P 2和高级压缩组件的吸气温度T 高，并计算压力平均值P，其中压力平均值P＝(排气压力P 1+吸气压力P 2)/2；
根据压力平均值P获取饱和气相温度T；
比较饱和气相温度T与高级压缩组件的吸气温度T 高之间的大小；
若饱和气相温度T与吸气温度T 高之间的差值在预设的允许差值范围内，则维持第二节流装置的开度；
若饱和气相温度T高于吸气温度T 高，且饱和气相温度T与吸气温度T 高之间的差值大于允许差值范围的最大值，则减小第二节流装置的开度；
若饱和气相温度T低于吸气温度T 高，且饱和气相温度T与吸气温度T 高之间的差值小于允许差值范围的最小值，则增大第二节流装置的开度。
上述方案提供了一种多级压缩空调系统的控制方法，通过调节第二节流装置的开度，最终使得饱和气相温度T与高级压缩组件的吸气温度T 高之间的差值在允许差值范围内，即使得高级压缩组件的吸气温度T 高接近于饱和气相温度T，从而进一步降低过热损失。
在其中一个实施例中，允许差值范围为-0.5℃～0.5℃。
在其中一个实施例中，若在预设时长△t内高级压缩组件的排气温度比冷凝温度低△T，且在预设时长△t内△T始终小于预设温差值，则将饱和气相温度T调大。
在其中一个实施例中，多级压缩空调系统的控制方法还包括以下步骤：
判断开机过程是否完成；
若开机过程未完成则将第二节流装置的开度维持为0；
若开机过程已完成则根据饱和气相温度T与吸气温度T 高之间的差值，以及差值与允许差值范围之间的大小关系调节第二节流装置的开度大小。
附图说明
图1为本实施例的多级压缩空调系统的系统图；
图2为本实施例的多级压缩空调系统控制方法的流程图。
附图标记说明：
10、多级压缩空调系统；11、排气冷却管路；111、第二节流装置；12、两级压缩系统；121、低级压缩组件；122、高级压缩组件；123、冷凝器；124、第一节流装置；125、闪发器；126、第三节流装置；127、蒸发器；13、第一管路；14、吸气管路；15、排气管路；16、补气管路。
具体实施方式
为使本申请的上述目的、特征和优点能够更加明显易懂，下面结合附图对本申请的具体实施方式做详细的说明。在下面的描述中阐述了很多具体细节以便于充分理解本申请。但是本申请能够以很多不同于在此描述的其它方式来实施，本领域技术人员可以在不违背本申请内涵的情况下做类似改进，因此本申请不受下面公开的具体实施的限制。
需要说明的是，当元件被称为“固定于”另一个元件，它可以直接在另一个元件上或者也可以存在居中的元件。当一个元件被认为是“连接”另一个元件，它可以是直接连接到另一个元件或者可能同时存在居中元件。本文所使用的术语“垂直的”、“水平的”、“左”、“右”以及类似的表述只是为了说明的目的，并不表示是唯一的实施方式。
除非另有定义，本文所使用的所有的技术和科学术语与属于本申请的技术领域的技术人员通常理解的含义相同。本文中在本申请的说明书中所使用的术 语只是为了描述具体的实施例的目的，不是旨在于限制本申请。以上实施例的各技术特征可以进行任意的组合，为使描述简洁，未对上述实施例中的各个技术特征所有可能的组合都进行描述，然而，只要这些技术特征的组合不存在矛盾，都应当认为是本说明书记载的范围。
如图1所示，在一个实施例中提供了一种多级压缩空调系统10，包括两级压缩系统12和排气冷却管路11，两级压缩系统12包括依次连通的低级压缩组件121、高级压缩组件122、冷凝器123、第一节流装置124、闪发器125和蒸发器127。低级压缩组件121的排气口与高级压缩组件122的吸气口之间的管路为第一管路13，排气冷却管路11的一端与冷凝器123连通，排气冷却管路11的另一端与第一管路13连通，排气冷却管路11上设有第二节流装置111。
制冷剂在蒸发器127中进行换热后通过吸气管路14进入低级压缩组件121被压缩，压缩后的高温高压制冷剂再经过第一管路13进入高级压缩组件122，经过高级压缩组件122进一步压缩后的制冷剂通过排气管路15进入冷凝器123。冷凝器123的高压液态制冷剂在经过第一节流装置124节流降压后，在闪发器125中闪发分离，分离获得的气态制冷剂则通过连通在闪发器125与第一管路13之间的补气管路16进入第一管路13中，对第一管路13中的制冷剂进行冷却，但是闪发器125闪发出来的饱和态制冷剂和低级压缩组件121压缩排出的过热制冷剂混合后不可能降低到饱和态，即无法实现完全冷却。因此，依次连通的低级压缩组件121、高级压缩组件122、冷凝器123、第一节流装置124、闪发器125和蒸发器127组成的两级压缩系统12为不完全冷却两级压缩系统。一般多级压缩离心机组中通过对闪发器进行改进，以进一步降低过热损失，但是一方面成本较高，另一方面始终无法使得高级压缩组件的吸气温度达到饱和气相温度。
而本案通过在两级压缩系统12中进一步设置排气冷却管路11，利用排气冷却管路11将冷凝器123中的少量制冷剂传导至第一管路13中，进一步对第一管路13中的制冷剂进行降温。通过调节排气冷却管路11上的第二节流装置111的开度大小，调整通过第一管路13导入高级压缩组件122的制冷剂的温度，使得高级压缩组件122的吸气温度接近该压力下的饱和气相温度，进一步降低过热损失。而且结构简洁，成本较低。
在一个实施例中，如图1所示，两级压缩系统12还包括第三节流装置126，第三节流装置126连通在闪发器125和蒸发器127之间。经过闪发器125闪发分离获得的液态制冷剂则经过第三节流装置126后进入蒸发器127中。
在一个实施例中，如图1所示，低级压缩组件121和高级压缩组件122组成双挂头压缩机，双挂头压缩机的电机轴的两端分别挂有低级叶轮和高级叶轮，第一管路13连通在低级叶轮的排气口与高级叶轮的吸气口之间。
或者，在一个实施例中，低级压缩组件121为低级压缩机，高级压缩组件122为高级压缩机，第一管路13连通在低级压缩机的排气口与高级压缩机的吸气口之间，经过低级压缩机压缩排出的制冷剂通过第一管路13导入高级压缩机中。
在一个实施例中，当低级压缩组件121和高级压缩组件122组成双挂头压缩机时，双挂头压缩机可以具有多级压缩功能。例如，在一个实施例中，电机轴上挂有低级叶轮的一端还设有第一叶轮，第一管路13连通在第一叶轮的排气口与高级叶轮的吸气口之间；或者，电机轴上挂有高级叶轮的一端还设有第二叶轮，第一管路13连通在低级叶轮的排气口与第二叶轮的吸气口之间；或者，电机轴上挂有低级叶轮的一端还设有第三叶轮，第一管路13为两个，其中一个第一管路13连通在低级叶轮的排气口与高级叶轮的吸气口之间，另一个第一管 路13连通在高级叶轮的排气口与第三叶轮的吸气口之间；或者，电机轴上挂有高级叶轮的一端还设有第四叶轮，第一管路13为两个，其中一个第一管路13连通在第四叶轮的排气口与低级叶轮的吸气口之间，另一个第一管路13连通在低级叶轮的排气口与高级叶轮的吸气口之间。
无论几级压缩的形式，只要将第一管路13连通在电机轴两端的叶轮吸气口与排气口之间，排气冷却管路11中的制冷剂则能够对通过第一管路13进入的制冷剂进行降温，使其接近饱和气相温度。
在一个实施例中，第二节流装置111为电子膨胀阀。使用时电子膨胀阀能够根据饱和气相温度调节开度大小，使得高级压缩组件122的吸气温度接近饱和气相温度，降低过热损失。
在一个实施例中，第二节流装置111也可以是其他能够进行节流控制的器件，在这里不做具体限制。
在一个实施例中，第一节流装置124为一级节流孔板，第三节流装置126为二级节流孔板。
如图2所示，在另一个实施例中提供了一种多级压缩空调系统10的控制方法，包括以下步骤：
获取上述的多级压缩空调系统10中低级压缩组件121的排气压力P 1、高级压缩组件122的吸气压力P 2和高级压缩组件122的吸气温度T 高，并计算排气压力P 1与吸气压力P 2的压力平均值P；具体地，P＝(P 1+P 2)/2。
根据压力平均值P获取饱和气相温度T；例如可以通过冷媒物性参数对照表查找对应压力下的饱和气相温度T。
比较饱和气相温度T与高级压缩组件122的吸气温度T 高之间的大小；
若饱和气相温度T与吸气温度T 高之间的差值在预设的允许差值范围内，则 维持第二节流装置111的开度；
若饱和气相温度T高于吸气温度T 高，且饱和气相温度T与吸气温度T 高之间的差值大于允许差值范围的最大值，则减小第二节流装置111的开度；
若饱和气相温度T低于吸气温度T 高，且饱和气相温度T与吸气温度T 高之间的差值小于允许差值范围的最小值，则增大第二节流装置111的开度。
上述方案提供了一种多级压缩空调系统10的控制方法，通过调节第二节流装置111的开度，最终使得饱和气相温度T与高级压缩组件122的吸气温度T 高之间的差值在允许差值范围内，即使得高级压缩组件122的吸气温度T 高接近于饱和气相温度T，从而进一步降低过热损失。
在一个实施例中，允许差值范围可以根据实际情况设定，其范围的大小体现了允许的吸气温度与饱和气相温度之间的差距，差值范围越接近0则表示系统调节后吸气温度与饱和气相温度越接近。例如在一个实施例中，允许差值范围为-0.5℃～0.5℃。当饱和气相温度T与吸气温度T 高之间的差值不处于预设范围内时，则通过调整第二节流装置111的开度大小，调节第一管路13中制冷剂的温度，使得最终被高级压缩组件122吸入的制冷剂温度接近饱和气相温度。
在一个实施例中，若在预设时长△t内高级压缩组件122的排气温度比冷凝温度低△T，且在预设时长△t内△T始终小于预设温差值，则证明第一管路13中制冷剂冷却过多，从而将饱和气相温度T调大，进而按照前述步骤调小第二节流装置111的开度。
在一个实施例中，每次可以将饱和气相温度调大1℃，预设时长△t为3min，预设温差值为4℃。
进一步地，在一个实施例中，多级压缩空调系统10的控制方法还包括以下步骤：
判断开机过程是否完成；
若开机过程未完成则将第二节流装置111的开度维持为0；
若开机过程已完成则根据饱和气相温度T与吸气温度T 高之间的差值，以及差值与允许差值范围之间的大小关系调节第二节流装置111的开度大小。
在系统刚开启时各器件未进入正常运转，补气管路16中的制冷剂未来得及对第一管路13中的制冷剂进行冷却降温，此时先将第二节流装置111的开度维持为0；待系统开机完成后，再按照前述过程调节第二节流装置111的开度大小。
在一个实施例中，当第二节流装置111为电子膨胀阀时，则按照前述步骤调节电子膨胀阀的开度。
以上实施例的各技术特征可以进行任意的组合，为使描述简洁，未对上述实施例中的各个技术特征所有可能的组合都进行描述，然而，只要这些技术特征的组合不存在矛盾，都应当认为是本说明书记载的范围。
以上实施例仅表达了本申请的几种实施方式，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，在不脱离本申请构思的前提下，还可以做出若干变形和改进，这些都属于本申请的保护范围。因此，本申请专利的保护范围应以所附权利要求为准。

Claims (11)

  1. 一种多级压缩空调系统，其特征在于，包括两级压缩系统(12)和排气冷却管路(11)，所述两级压缩系统(12)包括依次连通的低级压缩组件(121)、高级压缩组件(122)、冷凝器(123)、第一节流装置(124)、闪发器(125)和蒸发器(127)，所述低级压缩组件(121)的排气口与所述高级压缩组件(122)的吸气口之间的管路为第一管路(13)，所述排气冷却管路(11)的一端与所述冷凝器(123)连通，所述排气冷却管路(11)的另一端与所述第一管路(13)连通，所述排气冷却管路(11)上设有第二节流装置(111)。
  2. 根据权利要求1所述的多级压缩空调系统，其特征在于，所述两级压缩系统(12)中还包括第三节流装置(126)，所述第三节流装置(126)连通在所述闪发器(125)和所述蒸发器(127)之间。
  3. 根据权利要求2所述的多级压缩空调系统，其特征在于，所述第一节流装置(124)为一级节流孔板，所述第三节流装置(126)为二级节流孔板。
  4. 根据权利要求1所述的多级压缩空调系统，其特征在于，所述第二节流装置(111)为电子膨胀阀。
  5. 根据权利要求1至4中任一项所述的多级压缩空调系统，其特征在于，所述低级压缩组件(121)和所述高级压缩组件(122)组成双挂头压缩机，所述双挂头压缩机的电机轴的两端分别挂有低级叶轮和高级叶轮，所述第一管路(13)连通在所述低级叶轮的排气口与所述高级叶轮的吸气口之间。
  6. 根据权利要求5所述的多级压缩空调系统，其特征在于，所述电机轴上挂有所述低级叶轮的一端还设有第一叶轮，所述第一管路(13)连通在所述第一叶轮的排气口与所述高级叶轮的吸气口之间；或者，所述电机轴上挂有所述高级叶轮的一端还设有第二叶轮，所述第一管路(13)连通在所述低级叶轮的排气口与所述第二叶轮的吸气口之间；或者，所述电机轴上挂有所述低级叶轮 的一端还设有第三叶轮，所述第一管路(13)为两个，其中一个第一管路(13)连通在所述低级叶轮的排气口与所述高级叶轮的吸气口之间，另一个第一管路(13)连通在所述高级叶轮的排气口与所述第三叶轮的吸气口之间；或者，所述电机轴上挂有所述高级叶轮的一端还设有第四叶轮，所述第一管路(13)为两个，其中一个第一管路(13)连通在所述第四叶轮的排气口与所述低级叶轮的吸气口之间，另一个第一管路(13)连通在所述低级叶轮的排气口与所述高级叶轮的吸气口之间。
  7. 根据权利要求1至4中任一项所述的多级压缩空调系统，其特征在于，所述低级压缩组件(121)为低级压缩机，所述高级压缩组件(122)为高级压缩机，所述第一管路(13)连通在所述低级压缩机的排气口与所述高级压缩机的吸气口之间。
  8. 一种多级压缩空调系统控制方法，其特征在于，包括以下步骤：
    获取权利要求1至7中任一项所述的多级压缩空调系统中所述低级压缩组件(121)的排气压力P 1、所述高级压缩组件(122)的吸气压力P 2和所述高级压缩组件(122)的吸气温度T 高，并计算压力平均值P，其中压力平均值P＝(排气压力P 1+吸气压力P 2)/2；
    根据压力平均值P获取饱和气相温度T；
    比较饱和气相温度T与所述高级压缩组件(122)的吸气温度T 高之间的大小；
    若饱和气相温度T与吸气温度T 高之间的差值在预设的允许差值范围内，则维持所述第二节流装置(111)的开度；
    若饱和气相温度T高于吸气温度T 高，且饱和气相温度T与吸气温度T 高之间的差值大于所述允许差值范围的最大值，则减小所述第二节流装置(111)的 开度；
    若饱和气相温度T低于吸气温度T 高，且饱和气相温度T与吸气温度T 高之间的差值小于所述允许差值范围的最小值，则增大所述第二节流装置(111)的开度。
  9. 根据权利要求8所述的多级压缩空调系统控制方法，其特征在于，所述允许差值范围为-0.5℃～0.5℃。
  10. 根据权利要求8或9所述的多级压缩空调系统控制方法，其特征在于，若在预设时长△t内所述高级压缩组件(122)的排气温度比冷凝温度低△T，且在预设时长△t内△T始终小于预设温差值，则将所述饱和气相温度T调大。
  11. 根据权利要求8或9所述的多级压缩空调系统控制方法，其特征在于，还包括以下步骤：
    判断开机过程是否完成；
    若开机过程未完成则将所述第二节流装置(111)的开度维持为0；
    若开机过程已完成则根据饱和气相温度T与吸气温度T 高之间的差值，以及差值与允许差值范围之间的大小关系调节所述第二节流装置(111)的开度大小。
PCT/CN2019/128422 2019-06-26 2019-12-25 多级压缩空调系统及其控制方法 Ceased WO2020258795A1 (zh)

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Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110307660B (zh) * 2019-06-26 2020-06-09 珠海格力电器股份有限公司 多级压缩空调系统及其控制方法
CN111023608A (zh) * 2019-12-30 2020-04-17 珠海格力电器股份有限公司 能耗低、效率和稳定性高的又可防止喘振的制冷机组
CN111256381B (zh) * 2020-01-19 2021-09-21 珠海格力电器股份有限公司 压缩机防喘补气系统、控制方法及空调设备
CN114165446A (zh) 2021-12-14 2022-03-11 珠海格力电器股份有限公司 多级压缩机及空调机组

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001133058A (ja) * 1999-11-05 2001-05-18 Matsushita Electric Ind Co Ltd 冷凍サイクル装置
KR20130134348A (ko) * 2012-05-30 2013-12-10 삼성전자주식회사 공기 조화기 및 그 제어 방법
CN104421188A (zh) * 2013-08-26 2015-03-18 珠海格力电器股份有限公司 多级离心压缩机及空调机组
CN104792072A (zh) * 2014-01-21 2015-07-22 珠海格力电器股份有限公司 空调机组及其冷媒流量控制方法
CN205316732U (zh) * 2016-01-11 2016-06-15 长乐太平洋食品有限公司 一种螺杆式制冷系统
CN109341153A (zh) * 2018-12-13 2019-02-15 珠海格力电器股份有限公司 冷媒循环系统和制冷设备
CN110307660A (zh) * 2019-06-26 2019-10-08 珠海格力电器股份有限公司 多级压缩空调系统及其控制方法

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3240700B2 (ja) * 1992-08-26 2001-12-17 株式会社日立製作所 非共沸混合冷媒を用いた冷凍サイクル
US20030167792A1 (en) * 2002-03-06 2003-09-11 Via Holdings, Llc Refrigeration system with liquid refrigerant injection to the condenser
US7137270B2 (en) * 2004-07-14 2006-11-21 Carrier Corporation Flash tank for heat pump in heating and cooling modes of operation
JP2006138525A (ja) * 2004-11-11 2006-06-01 Hitachi Home & Life Solutions Inc 冷凍装置及び空気調和機
JP4408413B2 (ja) * 2004-12-22 2010-02-03 日立アプライアンス株式会社 冷凍装置及びこれを用いた空気調和機
JP4833330B2 (ja) * 2009-11-27 2011-12-07 三菱電機株式会社 超臨界蒸気圧縮式冷凍サイクルおよびこれを用いる冷暖房空調設備とヒートポンプ給湯機
CN101957067B (zh) * 2010-11-01 2012-09-05 江苏天舒电器有限公司 一种热泵热水机的变频控制方法
CN102889641A (zh) * 2012-09-12 2013-01-23 青岛海信日立空调系统有限公司 用于高温环境下的空调器及控制方法
JP2014126225A (ja) * 2012-12-25 2014-07-07 Calsonic Kansei Corp 車両用空調システムおよび気液混合器
JP2015105783A (ja) * 2013-11-29 2015-06-08 荏原冷熱システム株式会社 ターボ冷凍機
CN104864620B (zh) * 2014-02-26 2019-01-01 荏原冷热系统株式会社 离心式制冷机
CN105004115B (zh) * 2015-06-12 2017-12-29 珠海格力电器股份有限公司 电子膨胀阀的控制方法
CN105571075B (zh) * 2016-01-20 2019-08-20 青岛海尔空调电子有限公司 一种水冷多联机回气增焓的控制方法
CN107091537A (zh) * 2016-02-17 2017-08-25 艾默生环境优化技术(苏州)有限公司 压缩机系统及提高压缩机系统的性能的方法
CN205678933U (zh) * 2016-03-21 2016-11-09 珠海格力电器股份有限公司 冷媒循环系统及具有其的空调器
CN206545975U (zh) * 2017-02-04 2017-10-10 青岛海尔空调器有限总公司 一种空调系统
CN109916109A (zh) * 2019-01-28 2019-06-21 珠海格力电器股份有限公司 一种热泵系统和空调器

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001133058A (ja) * 1999-11-05 2001-05-18 Matsushita Electric Ind Co Ltd 冷凍サイクル装置
KR20130134348A (ko) * 2012-05-30 2013-12-10 삼성전자주식회사 공기 조화기 및 그 제어 방법
CN104421188A (zh) * 2013-08-26 2015-03-18 珠海格力电器股份有限公司 多级离心压缩机及空调机组
CN104792072A (zh) * 2014-01-21 2015-07-22 珠海格力电器股份有限公司 空调机组及其冷媒流量控制方法
CN205316732U (zh) * 2016-01-11 2016-06-15 长乐太平洋食品有限公司 一种螺杆式制冷系统
CN109341153A (zh) * 2018-12-13 2019-02-15 珠海格力电器股份有限公司 冷媒循环系统和制冷设备
CN110307660A (zh) * 2019-06-26 2019-10-08 珠海格力电器股份有限公司 多级压缩空调系统及其控制方法

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