WO2024036593A1 - 一种空气能制冷和变流量的控制系统及其方法 - Google Patents

一种空气能制冷和变流量的控制系统及其方法 Download PDF

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Publication number
WO2024036593A1
WO2024036593A1 PCT/CN2022/113536 CN2022113536W WO2024036593A1 WO 2024036593 A1 WO2024036593 A1 WO 2024036593A1 CN 2022113536 W CN2022113536 W CN 2022113536W WO 2024036593 A1 WO2024036593 A1 WO 2024036593A1
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Prior art keywords
refrigerant
pressure
compressor
heat exchanger
air energy
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PCT/CN2022/113536
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English (en)
French (fr)
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杨凡
邹鑫
郁伟荣
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广东颐柏流体技术有限公司
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Application filed by 广东颐柏流体技术有限公司 filed Critical 广东颐柏流体技术有限公司
Priority to PCT/CN2022/113536 priority Critical patent/WO2024036593A1/zh
Priority to CN202280003298.4A priority patent/CN116507861A/zh
Publication of WO2024036593A1 publication Critical patent/WO2024036593A1/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
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • 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

  • the invention relates to the technical field of air conditioning and refrigeration, and in particular to an air energy refrigeration and variable flow control system and a method thereof.
  • phase change refrigeration is liquid vaporization refrigeration, that is, the liquid absorbs heat during the process of vaporization into steam, thereby achieving the purpose of refrigeration.
  • Increasing the subcooling degree of the liquid refrigerant in phase change refrigeration technology can increase the cooling capacity and improve the energy efficiency ratio.
  • Gas expansion refrigeration uses the adiabatic expansion of high-pressure gaseous or supercritical refrigerant to obtain low-temperature refrigerant, and then uses the heat absorption of the expanded low-temperature refrigerant during the reheating process to cool the refrigerant. At the same time, the refrigerant is completely Vaporize.
  • the enthalpy change value during the throttling and expansion process of the refrigerant determines the cooling capacity.
  • Increasing the enthalpy change value of the refrigerant can increase the cooling capacity and improve the energy efficiency ratio.
  • the purpose of the present invention is to provide an air energy refrigeration and variable flow control system and a method thereof, which through improvement form a technical solution that can effectively maintain a high energy efficiency ratio and save power, and It also has the advantages of low operating cost, simple equipment structure, energy saving and environmental protection. At the same time, it also solves other problems in the existing technology.
  • An air energy refrigeration and variable flow control system including:
  • Storage tank compressor, first air energy heat exchanger, second air energy heat exchanger, refrigerant heat exchanger, first expansion valve and second expansion valve;
  • the outlet of the storage tank is connected to the low-pressure inlet end of the compressor through a pipeline provided with the first expansion valve and the first air energy heat exchanger in order to convert the refrigerant output from the storage tank into Gaseous low-temperature refrigerant with superheat is input into the compressor;
  • the high-pressure outlet end of the compressor is connected to the inlet of the second air energy heat exchanger through a pipeline to convert the gaseous low-temperature refrigerant with superheat output from the first air energy heat exchanger into high-pressure and high-temperature refrigerant.
  • the second air energy heat exchanger ;
  • the outlet of the second air energy heat exchanger is arranged in parallel with the entrance of the storage tank and the entrance of the secondary refrigerant heat exchanger through pipes, and a certain point is provided at the entrance of the secondary refrigerant heat exchanger.
  • the second expansion valve is used to convert the high-pressure and high-temperature refrigerant output by the compressor into high-pressure normal-temperature refrigerant by the second air energy heat exchanger, and then the high-pressure normal-temperature refrigerant can be input into the storage tank for storage. Or throttle and expand through the second expansion valve, and absorb the heat of the refrigerant in the refrigerant heat exchanger to become gaseous refrigerant and discharge it from the refrigerant heat exchanger;
  • the outlet of the brine refrigerant heat exchanger is connected to the low-pressure inlet end of the compressor through a pipeline, so that the gaseous refrigerant discharged from the brine refrigerant heat exchanger is pressurized through the compressor and recycled or input to the storage tank for storage.
  • a second solenoid valve for cooperating with the first solenoid valve is also provided on the pipeline connected to the compressor; a first control valve and a second control valve are respectively provided at the outlet and inlet of the storage tank.
  • a proportional valve is also provided at the outlet of the secondary refrigerant heat exchanger for controlling the opening to adjust the refrigerant flow to control the cooling capacity.
  • the pressure setting value of the low-pressure inlet end of the compressor is between 0.15MPa and 4MPa, and the pressure setting value of the high-pressure outlet end of the compressor is between 3.5MPa and 12MPa.
  • pressure sensors are respectively provided at the low-pressure inlet end and the high-pressure outlet end of the compressor.
  • the excess mass of refrigerant is pressurized by the compressor and then flows into the storage tank for storage;
  • the refrigerant in the storage tank is output, and the refrigerant passes through the first expansion valve and the vaporization of the first air energy heat exchanger. Then it flows into the low-pressure inlet end of the compressor to supplement the quality of refrigerant required by the control system.
  • the present invention also provides a control method for air energy refrigeration and variable flow, which adopts the above-mentioned air energy refrigeration and variable flow control system and includes the following steps:
  • the converted gaseous low-temperature refrigerant with superheat becomes high-pressure and high-temperature refrigerant after being pressurized by the compressor, and then the high-pressure and high-temperature refrigerant enters the second air energy heat exchanger;
  • the high-pressure and high-temperature refrigerant entering the second air energy heat exchanger is converted into high-pressure normal-temperature refrigerant by releasing heat to the air in the environment, and then the high-pressure normal-temperature refrigerant enters the second expansion valve;
  • the low-temperature refrigerant After the low-temperature refrigerant enters the secondary refrigerant heat exchanger, it performs heat exchange with the secondary refrigerant on the outer surface of the secondary refrigerant heat exchanger. The secondary refrigerant releases heat to the refrigerant to achieve cooling of the secondary refrigerant. And the low-temperature refrigerant absorbs the heat of the refrigerant and then reheats and completely vaporizes;
  • the gaseous refrigerant discharged from the refrigerant heat exchanger then enters the compressor through the pipeline and is pressurized into high-pressure and high-temperature refrigerant for recycling;
  • step S1 after the compressor is operated, when the pressure at the high-pressure outlet end of the compressor is lower than the set value, first the refrigerant in the secondary refrigerant heat exchanger is The refrigerant is discharged and vaporized through the first expansion valve and the first air energy heat exchanger and converted into gaseous refrigerant with superheat and input into the low-pressure inlet end of the compressor; such as the pressure in the tube of the brine heat exchanger
  • the refrigerant will flow out of the storage tank for replenishment, and the secondary refrigerant heat exchanger will be discharged from the subsequent control system refrigeration process.
  • the gaseous refrigerant is directly input to the compressor without flowing out into the first expansion valve and the first air energy heat exchanger.
  • the pressure at the high-pressure outlet end of the compressor is lowered than the set value, so that the outlet of the storage tank is opened and the refrigerant is released. for filling until the pressure at the high-pressure outlet end of the compressor reaches the set value;
  • the pressure at the high-pressure outlet end of the compressor is greater than the set value, so that the inlet of the storage tank is opened and excess mass of refrigerant flows in until the compressor It stops when the pressure at the high-pressure outlet reaches the set value.
  • the refrigerant of the present invention is vaporized by the first expansion valve and the first air energy heat exchanger and then input into the compressor.
  • the refrigerant is pressurized by increasing the gaseous refrigerant pressure at the compressor inlet, thereby improving the energy efficiency ratio of the refrigerant circulation system.
  • the second air energy heat exchanger is then used for cooling, thereby turning the refrigerant into a high-pressure, normal-temperature refrigerant.
  • the high-pressure, normal-temperature refrigerant is decompressed and adiabatically expanded into a low-temperature refrigerant through the second expansion valve, thereby improving the performance of the refrigerant during refrigeration.
  • the enthalpy change value is used to obtain a higher energy efficiency ratio.
  • the refrigerant After the refrigerant enters the secondary refrigerant heat exchanger, it finally achieves the cooling purpose of the secondary refrigerant through the secondary refrigerant heat exchanger. Therefore, it has a higher energy efficiency ratio and operates The cost is low, the equipment structure is simple, energy saving and environmental protection.
  • the refrigerant in the present invention is heat-exchanged by the refrigerant heat exchanger
  • the refrigerant is further pressurized and cooled by heat exchange through the compressor and the second air energy heat exchanger, and then is input to the second expansion valve and In the secondary refrigerant heat exchanger, recycling is achieved, effectively reducing the operating cost of the control system.
  • the present invention is equipped with two air energy heat exchangers, one of which is used to vaporize the refrigerant by absorbing the heat of the ambient air, omitting the use of a gas-liquid separator for the refrigerant, and also preventing the liquid refrigerant from being vaporized input into the compressor causing damage to the compressor, the other is used to allow the refrigerant to cool down by releasing heat to the air in the environment.
  • the two air energy heat exchangers cooperate with the settings of the pipelines and storage tanks to make the low pressure of the compressor
  • the pressure at both the inlet end and the high-pressure outlet end can be maintained at the set value; when the pressure at the high-pressure outlet end of the compressor is lower than the set value, the storage tank continues to release refrigerant to compensate for the pressure until the pressure at the high-pressure outlet end of the compressor reaches the set value.
  • control system of the present invention can adjust the flow rate of the refrigerant in real time according to the real-time usage situation, for example, when the number of use of the secondary refrigerant heat exchanger increases or decreases, and realizes the use of the refrigerant under different working conditions in closed operation.
  • the change in mass flow rate allows the compressor to basically maintain a high energy efficiency ratio of the control system and achieve power saving while ensuring that the set pressures at both ends remain unchanged.
  • a pipe is provided between the pipe connecting the outlet of the brine refrigerant heat exchanger to the compressor and the pipe connecting the outlet of the storage tank to the inlet of the first air energy heat exchanger, and then the first electromagnetic pair is arranged to cooperate with each other. valve and the second solenoid valve. Since the refrigerant of the secondary refrigerant heat exchanger needs to be vaporized through the first expansion valve and the first air energy heat exchanger before being input to the compressor, it can be used to clear the load when the control system has just been turned on. The small amount of liquid refrigerant retained in the refrigerant heat exchanger prevents the mixing of liquid and gas refrigerants in the compressor and damages the compressor, extending the service life of the compressor.
  • Figure 1 is a framework schematic diagram of an air energy refrigeration and variable flow control system of the present invention
  • Figure 2 is a process principle diagram of an air energy refrigeration and variable flow control method of the present invention.
  • an air energy refrigeration and variable flow control system includes: a storage tank 1, a compressor 2, a first air energy heat exchanger 3, a second air energy heat exchanger 4, and a brine refrigerant heat exchanger. 5.
  • the storage tank 1 is used to provide refrigerant to the control system, for example, to provide R744 or carbon dioxide refrigerant without lubricating oil to the system.
  • the compressor 2 can be used to help transfer excess refrigerant on the pipeline into the storage tank 1 .
  • the first air-energy heat exchanger 3 and the second air-energy heat exchanger 4 serve as the outdoor unit part
  • the brine refrigerant heat exchanger 5 serves as the indoor unit part.
  • Both the first air energy heat exchanger 3 and the second air energy heat exchanger 4 include an outdoor unit, a silent fan with adjustable air volume, a refrigerant heat exchanger, and two air energy heat exchangers respectively installed at the outlet and inlet of the air energy heat exchanger.
  • the secondary refrigerant heat exchanger 5 is a sealed structure with a heat exchanger and a pressure gauge inside. The secondary refrigerant transfers cold energy through the tube wall of the heat exchanger.
  • Carbon dioxide is an emerging natural working fluid. From the perspective of its impact on the environment, apart from water and air, it is the most environmentally friendly refrigeration fluid. Carbon dioxide supercritical fluid expansion refrigeration is a highly efficient refrigeration method. In addition, carbon dioxide also has good safety and chemical stability.
  • the outlet of the storage tank 1 is connected to the low-pressure inlet end of the compressor 2 through a pipeline equipped with a first expansion valve 6 and a first air energy heat exchanger 3 in order to store the
  • the carbon dioxide refrigerant output from the tank 1 is converted into gaseous low-temperature carbon dioxide refrigerant with a certain degree of superheat and is input into the compressor 2.
  • the first expansion valve 6 can be used to expand and reduce pressure, so that the carbon dioxide refrigerant output from the storage tank 1 first passes through The first expansion valve 6 then flows into the first air energy heat exchanger 3 to absorb outdoor ambient heat and then vaporizes, and finally becomes a gaseous low-temperature refrigerant, that is, the carbon dioxide refrigerant output from the storage tank 1 is vaporized.
  • the high-pressure outlet end of the compressor 2 is connected to the inlet of the second air energy heat exchanger 4 through a pipeline to convert the gaseous low-temperature carbon dioxide refrigerant with a certain degree of superheat output by the first air energy heat exchanger 3 into gaseous or supercritical state.
  • the high-pressure and high-temperature carbon dioxide refrigerant is input into the second air energy heat exchanger 4 .
  • the outlet of the second air energy heat exchanger 4 is arranged in parallel with the inlet of the storage tank 1 and the inlet of the brine heat exchanger 5 through pipes, and a second expansion valve 7 is provided at the inlet of the brine heat exchanger 5 , to convert the gaseous or supercritical high-pressure and high-temperature carbon dioxide refrigerant output by the compressor into high-pressure normal-temperature carbon dioxide refrigerant by the second air energy heat exchanger 4, and then the high-pressure normal-temperature carbon dioxide refrigerant can be input into the storage tank 1 for storage or through
  • the second expansion valve 7 throttles and expands, absorbs the heat of the refrigerant in the refrigerant heat exchanger 5 and then discharges it as gaseous refrigerant from the refrigerant heat exchanger.
  • the high-pressure and high-temperature carbon dioxide refrigerant output by the compressor 2 passes through the second air energy heat exchanger 4 and is converted into high-pressure and normal-temperature carbon dioxide refrigerant by releasing heat to the air in the outdoor environment; wherein, during normal operation, the high-pressure and normal-temperature carbon dioxide refrigerant The carbon dioxide refrigerant is used to pass through the second expansion valve 7 and is converted into low-temperature carbon dioxide refrigerant due to the JT effect, and then is input into the brine refrigerant heat exchanger 5 to absorb the heat of the brine refrigerant, and is then discharged as gaseous refrigerant; if the compressor 2 When the pressure at the high-pressure outlet of the compressor exceeds the predetermined value, the inlet of the storage tank 1 is opened, and the excess mass of high-pressure normal temperature carbon dioxide refrigerant is input into the storage tank 1 using the pressure difference until the pressure at the high-pressure outlet of the compressor 2 reaches the predetermined value. stop.
  • the outlet of the secondary refrigerant heat exchanger 5 is connected to the low-pressure inlet end of the compressor 2 through a pipeline, so that the gaseous carbon dioxide refrigerant discharged from the secondary refrigerant heat exchanger 5 is pressurized and converted into high-pressure and high-temperature refrigerant through the compressor 2, and then passed through
  • the second air energy heat exchanger 4 and the second expansion valve 7 are connected to the secondary refrigerant heat exchanger 5, that is, recycling is realized, or after the compressor 2 pressurizes the carbon dioxide refrigerant, if the high-pressure outlet of the compressor 2 When the pressure exceeds the predetermined value, the refrigerant is input to the storage tank 1 through the second air energy heat exchanger 4 for storage.
  • a pipe equipped with a first solenoid valve 8 is connected between the pipe connecting the outlet of the refrigerant heat exchanger 5 to the compressor 2 and the pipe connecting the outlet of the storage tank 1 to the inlet of the first air energy heat exchanger 3, that is,
  • the pipe connecting the outlet of the brine refrigerant heat exchanger 5 to the compressor 2 and the pipe connecting the outlet of the storage tank 1 to the inlet of the first air energy heat exchanger 3 are arranged in parallel for convenient heat exchange of the brine.
  • the carbon dioxide refrigerant in the refrigerant 5 is input into the first air energy heat exchanger 3; a second solenoid for cooperating with the first solenoid valve 8 is also provided on the pipe connecting the outlet of the refrigerant heat exchanger 5 to the compressor 2.
  • Valve 9; a first control valve 10 and a second control valve 11 are respectively provided at the outlet and inlet of the storage tank 1.
  • the compressor 2 can first be used to extract a small amount of gaseous or liquid refrigerant retained in the refrigerant heat exchanger 5.
  • the second solenoid valve 9 is closed, and the first solenoid valve 8 is open, to prevent the refrigerant extracted from the refrigerant heat exchanger 5 from directly entering the compressor 2 through the second solenoid valve 9 and being extracted.
  • the refrigerant will vaporize after passing through the first expansion valve 6 and the first air energy heat exchanger 3 in sequence, and finally enter the compressor 2, thereby ensuring that no liquid refrigerant enters the compressor 2 at the inlet of the compressor 2, so as to This avoids damage to the compressor 2 and extends the life of the compressor 2; if the pressure in the tube of the refrigerant heat exchanger 5 reaches the set value but the pressure at the high-pressure outlet end of the compressor 2 does not reach the set value, the first The control valve 10 is opened to output the carbon dioxide refrigerant in the storage tank 1 for replenishment. At the same time, the first solenoid valve 8 is closed and the second solenoid valve 9 is opened.
  • the carbon dioxide refrigerant in the storage tank 1 passes through the first expansion valve 6 and the first air After vaporization in the heat exchanger 3, it is input into the compressor 2 until the pressure at the high-pressure outlet end of the compressor 2 reaches the set value and the first control valve 10 stops. Therefore, the arrangement of the above structure can be used to clear a small amount of liquid refrigerant in the refrigerant heat exchanger 5 when the control system is just started, to prevent the liquid refrigerant from entering the compressor 2 and damaging the compressor 2, and prolonging the compression time. The service life of machine 2.
  • the first control valve 10 and the second control valve 11 may be proportional valves to improve precise control of the flow rate.
  • a third solenoid valve 14 for controlling the opening and closing of the pipeline may also be provided on the pipeline between the first air energy heat exchanger 3 and the first expansion valve 6 .
  • Two or more secondary refrigerant heat exchangers 5 can be installed in parallel, so that people can increase or decrease the number of secondary refrigerant heat exchangers 5 at any time to increase or decrease the cooling capacity.
  • Each inlet of the agent heat exchanger 5 is provided with a second expansion valve 7 .
  • a proportional valve 12 is also provided at the outlet of the secondary refrigerant heat exchanger 5 for adjusting the opening of the refrigerant flow to control the cooling capacity, so that the secondary refrigerant temperature at the outlet of the secondary refrigerant heat exchanger 5 is maintained at the set value. value, the brine temperature will not fluctuate due to changes in mass flow or volume flow of the brine.
  • a one-way valve 13 is also provided on the pipe connecting the outlet of the refrigerant heat exchanger 5 to the compressor 2 to ensure the flow direction of the refrigerant and prevent the refrigerant from flowing back.
  • a one-way valve 13 can also be provided at the inlet and outlet of the compressor 2 respectively.
  • the pressure setting value of the low-pressure inlet end of the compressor 2 is between 0.15MPa and 4MPa, and the pressure setting value of the high-pressure outlet end of the compressor 2 is between 3.5MPa and 12MPa.
  • Pressure sensors are also provided at the low-pressure inlet end and the high-pressure outlet end of the compressor 2 for accurately detecting the pressure at corresponding locations in real time.
  • the excess mass of carbon dioxide refrigerant is pressurized by the compressor 2 and then flows into the storage tank 1 for storage;
  • the carbon dioxide refrigerant in the storage tank 1 is output, and the carbon dioxide refrigerant flows into the low-pressure inlet end of the compressor 2 after being vaporized by the first expansion valve 6 and the first air energy heat exchanger 3. Used to supplement the quality of refrigerant required by the control system.
  • the secondary refrigerant on the secondary refrigerant heat exchanger is a gaseous refrigerant or a liquid refrigerant.
  • the gaseous refrigerant is air, nitrogen or argon
  • the liquid refrigerant is water, brine, ethylene glycol or propylene glycol solution.
  • this embodiment provides an air energy refrigeration and variable flow control method, which adopts the air energy refrigeration and variable flow control system of Embodiment 1 and includes the following steps:
  • the converted gaseous low-temperature carbon dioxide refrigerant with a certain degree of superheat is pressurized by the compressor 2 and becomes a gaseous or supercritical high-pressure and high-temperature carbon dioxide refrigerant. Then the gaseous or supercritical high-pressure and high-temperature carbon dioxide refrigerant enters the second air for heat exchange.
  • the device 4 Inside the device 4;
  • the gaseous or supercritical high-pressure and high-temperature carbon dioxide refrigerant entering the second air energy heat exchanger 4 is correspondingly transformed into the gaseous or supercritical high-pressure and normal-temperature carbon dioxide refrigerant by releasing heat to the air in the environment, and then the gaseous or supercritical carbon dioxide refrigerant is The high-pressure and normal-temperature carbon dioxide refrigerant enters the second expansion valve 7;
  • the gaseous or supercritical high-pressure normal temperature carbon dioxide refrigerant enters the second expansion valve 7 and is transformed into a low-temperature carbon dioxide refrigerant due to the JT effect. Then the low-temperature carbon dioxide refrigerant enters the corresponding secondary refrigerant heat exchanger 5;
  • the low-temperature carbon dioxide refrigerant After the low-temperature carbon dioxide refrigerant enters the secondary refrigerant heat exchanger 5, it enters heat exchange with the secondary refrigerant on the outer surface of the secondary refrigerant heat exchanger 5, causing the secondary refrigerant to release heat to the carbon dioxide refrigerant to achieve cooling of the secondary refrigerant.
  • the low-temperature refrigerant absorbs the heat of the refrigerant and then reheats and completely vaporizes;
  • the gaseous carbon dioxide refrigerant discharged from the refrigerant heat exchanger 5 then enters the compressor 2 through the pipeline and is pressurized into high-pressure and high-temperature carbon dioxide refrigerant for recycling;
  • step S1 after the compressor 2 is running, the first solenoid valve 8 is opened and the second solenoid valve 9 is closed.
  • the brine is first replaced.
  • a small amount of refrigerant retained in the heater 5 flows out (for example, liquid refrigerant) and the refrigerant is vaporized by the first expansion valve 6 and the first air energy heat exchanger 3 and converted into a gaseous refrigerant with a certain degree of superheat and is input into the compressor 2
  • the low-pressure inlet end can prevent the refrigerant extracted from the brine refrigerant heat exchanger 5 from entering the compressor 2 directly through the second solenoid valve 9; if the pressure in the tube of the brine refrigerant heat exchanger 5 reaches the set value, If the pressure at the high-pressure outlet of compressor 2 is still lower than the set value, the refrigerant will flow out of the storage tank 1 to replenish it, and the gaseous refrigerant in
  • the pressure at the high-pressure outlet end of the compressor 2 will be less than the set value, thereby allowing the outlet of the storage tank 1 to open and release the refrigerant. It is used for filling until the pressure at the high-pressure outlet end of the compressor 2 reaches the set value and stops;
  • the pressure at the high-pressure outlet end of the compressor 2 is greater than the set value, so that the inlet of the storage tank 1 is opened and excess mass of refrigerant flows in until The compressor 2 stops when the pressure at the high-pressure outlet reaches the set value.
  • the pressure setting value of the low-pressure inlet end of the compressor 2 is between 0.15MPa-4MPa, and the pressure setting value of the high-pressure outlet end of the compressor is between 3.5MPa-12MPa.
  • a pressure sensor is used to detect the pressure at the low-pressure inlet end and the high-pressure outlet end of the compressor 2 .
  • the refrigerant on the refrigerant heat exchanger is a gaseous refrigerant or a liquid refrigerant.
  • the gaseous refrigerant is air, nitrogen or argon.
  • the liquid refrigerant is water, salt water, ethyl alcohol, etc. glycol or propylene glycol solution.
  • connection can be a fixed connection or a fixed connection without affecting the relationship between components. It can be performed indirectly through intermediate components on the basis of technical effects, or it can be integral connection or partial connection. As in this example, those of ordinary skill in the art can understand the specific meaning of the above terms in the present invention according to specific circumstances.

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Abstract

一种空气能制冷和变流量的控制系统及其方法，该控制系统包括有贮存罐（1）、压缩机（2）、第一空气能换热器（3）、第二空气能换热器（4）、载冷剂换热器（5）、第一膨胀阀（6）和第二膨胀阀（7）；贮存罐（1）的出口通过依次设有第一膨胀阀（6）和第一空气能换热器（3）的管道连接至压缩机（2）的低压进口端；压缩机（2）的高压出口端通过管道连接第二空气能换热器（4）的入口；第二空气能换热器（4）的出口通过管道分别与贮存罐（1）的入口和载冷剂换热器（5）的入口并联设置，且在载冷剂换热器（5）的入口设置有第二膨胀阀（7）；载冷剂换热器（5）的出口通过管道连接压缩机（2）的低压进口端。该控制系统可有效保持高能效比，运行费用较低，设备结构简单、节能环保。

Description

一种空气能制冷和变流量的控制系统及其方法 技术领域
本发明涉及空调制冷技术领域，具体是涉及一种空气能制冷和变流量的控制系统及其方法。
背景技术
人工制冷方式主要有四种，相变制冷、气体膨胀制冷、涡流管制冷和热电制冷，每种制冷方法各有其特点。相变制冷是液体汽化制冷，即液体汽化成蒸气的过程中吸收热量，从而达到制冷的目的，相变制冷技术中提高液态冷媒的过冷度可提高制冷量，提高能效比。气体膨胀制冷是利用高压气态或超临界态冷媒的绝热膨胀来得到低温冷媒，再利用膨胀后的低温冷媒在复热过程中的吸热来使载冷剂降温，同时冷媒在复热过程中完全汽化。冷媒节流膨胀过程中的焓变值决定了制冷量，提高冷媒的焓变值可提高制冷量，提高能效比。
现有技术中也有不少制冷系统，但是，现有的制冷系统基本都是在使用过程中不能让冷媒在封闭运行时根据不同工况实现质量流量的变化的，从而出现不能保持高能效比的情况，亦即不够省电，因此其还存在改进的空间。
发明内容
针对以上现有技术所存在的问题，本发明的目的是提供一种空气能制冷和变流量的控制系统及其方法，其通过改进，形成可有效保持高能效比以及省电的技术方案，且其还具有运行费用较低、设备结构简单、节能环保等优点，同时，其还解决了现有技术中的其他问题。
为了实现上述目的，本发明的技术方案是：
一种空气能制冷和变流量的控制系统，包括：
贮存罐、压缩机、第一空气能换热器、第二空气能换热器、载冷剂换热器、第一膨胀阀和第二膨胀阀；
所述贮存罐的出口通过依次设有所述第一膨胀阀和所述第一空气能换热器的管道连接至所述压缩机的低压进口端，以将所述贮存罐输出的冷媒转换为具有过热度的气态低温冷媒输入所述压缩机；
所述压缩机的高压出口端通过管道连接所述第二空气能换热器的入口，以将所述第一空气能换热器输出的具有过热度的气态低温冷媒转换为高压高温冷媒输入所述第二空气能换热器；
所述第二空气能换热器的出口通过管道分别与所述贮存罐的入口和所述载冷剂换热器的入口并联设置，且在所述载冷剂换热器的入口设置有所述第二膨胀阀，以将所述压缩机所输出的高压高温冷媒由所述第二空气能换热器转换为高压常温冷媒，然后使所述高压常温冷媒可输入到所述贮存罐进行贮存或通过所述第二膨胀阀节流膨胀，并在所述载冷剂换热器内吸收载冷剂热量成为气态冷媒排出所述载冷剂换热器；
所述载冷剂换热器的出口通过管道连接所述压缩机的低压进口端，以将所述载冷剂换热器排出的气态冷媒通过所述压缩机进行增压并实现循环利用或者输入到所述贮存罐进行贮存。
对于以上技术方案的附加结构，还包括以下方案：
作为一种具体的实施例，在所述载冷剂换热器的出口连接所述压缩机的管道与所述贮存罐的出口连接所述第一空气能换热器的入口的管道之间还连通有一设置有第一电磁阀的管道，以用于将所述载冷剂换热器内的冷媒输入到所述第一空气能换热器内；在所述载冷剂换热器的出口连接所述压缩机的管道上还设置有用于与所述第一电磁阀配合的第二电磁阀；在所述贮存罐的出口和入口 处分别设置有第一控制阀和第二控制阀。
作为一种具体的实施例，所述载冷剂换热器设有两个以上且并联设置，在每个所述载冷剂换热器的入口均设置有一所述第二膨胀阀。
作为一种具体的实施例，在所述载冷剂换热器的出口还设置有比例阀，以用于控制开度来调节冷媒流量以达到控制制冷量。
作为一种具体的实施例，所述压缩机的低压进口端的压力设定值在0.15MPa-4MPa间，所述压缩机的高压出口端的压力设定值在3.5MPa-12MPa间。
进一步地，在所述压缩机的低压进口端和高压出口端还分别设置有压力传感器。
作为一种具体的实施例，在控制系统由于所需制冷量降低而需减少控制系统的冷媒的质量时，多余质量的冷媒通过所述压缩机增压后流入所述贮存罐贮存；
在控制系统由于所需制冷量增加而需增加控制系统的冷媒的质量时，输出所述贮存罐内的冷媒，且冷媒通过所述第一膨胀阀和所述第一空气能换热器的汽化后流入所述压缩机的低压进口端，以用于补充控制系统所需质量的冷媒。
本发明还提供一种空气能制冷和变流量的控制方法，采用如上述的空气能制冷和变流量的控制系统，包括如下步骤：
S1、启动控制系统，压缩机运转，当所述压缩机的高压出口端的压力低于设定值时，贮存罐内的冷媒流出并经过第一膨胀阀和第一空气能换热器汽化转换为具有过热度的气态低温冷媒并输入到所述压缩机的低压进口端，以使保持所述压缩机的高压出口端的压力达到设定值，同时用于保持所述压缩机的低压进口端压力在设定值；
S2、转换出的具有过热度的气态低温冷媒经所述压缩机增压后成为高压高 温冷媒，接着高压高温冷媒进入第二空气能换热器内；
S3、进入所述第二空气能换热器内的高压高温冷媒通过向环境中的空气释放热量而转变为高压常温冷媒，接着高压常温冷媒进入到所述第二膨胀阀；
S4、高压常温冷媒进入所述第二膨胀阀后由于JT效应转换为低温冷媒进入载冷剂换热器；
S5、低温冷媒进入到所述载冷剂换热器之后，与所述载冷剂换热器外表面的载冷剂进行热交换，载冷剂向冷媒释放热量实现载冷剂的降温制冷，且低温冷媒吸收载冷剂热量后复热和完全汽化；
S6、经所述载冷剂换热器排出后的气态冷媒再经管道进入所述压缩机增压成为高压高温冷媒后循环利用；
S7、在所述压缩机的高压出口端的压力未达到设定值时，则所述贮存罐持续放出冷媒，而在所述压缩机的高压出口端的压力达到设定值时，所述贮存罐的出口停止放出冷媒；
S8、在所述压缩机的高压出口端的压力超过设定值时，则多余的冷媒经所述贮存罐的入口流入，直至所述压缩机的高压出口端的压力达到设定值时，所述贮存罐的入口停止流入冷媒。
作为一种具体的实施例，在步骤S1中，所述压缩机运转后，当所述压缩机的高压出口端的压力低于设定值时，首先使所述载冷剂换热器内的冷媒排出且冷媒经所述第一膨胀阀和所述第一空气能换热器汽化转换为具有过热度的气态冷媒并输入所述压缩机的低压进口端；如载冷剂换热器的管内压力达到设定值而所述压缩机的高压出口端的压力仍低于设定值时，则由所述贮存罐流出冷媒补充，且后续的控制系统制冷过程中的所述载冷剂换热器排出的气态冷媒直接输入至所述压缩机而不再流出到所述第一膨胀阀和所述第一空气能换热器内。
作为一种具体的实施例，所述载冷剂换热器的使用数量增加后，使所述压缩机的高压出口端的压力小于设定值，从而让所述贮存罐的出口打开并放出冷媒，以用于填充，直至所述压缩机的高压出口端的压力达到设定值时停止；
所述载冷剂换热器的使用数量减少后，使所述压缩机的高压出口端的压力大于设定值，从而让所述贮存罐的入口打开并流入多余质量的冷媒，直至所述压缩机的高压出口端的压力达到设定值时停止。
本发明的有益效果为：
(一)本发明的冷媒利用第一膨胀阀和第一空气能换热器汽化后输入压缩机，通过增加压缩机入口处的气态冷媒压力对冷媒进行增压，提高冷媒循环系统的能效比，再利用第二空气能换热器进行降温，从而能够让冷媒变为高压常温冷媒，接着再通过第二膨胀阀将高压常温的冷媒进行降压、绝热膨胀为低温冷媒，提高冷媒在制冷时的焓变值来得到更高的能效比，冷媒进入到载冷剂换热器后，从而通过载冷剂换热器最终实现载冷剂的制冷目的，因此，其具有较高的能效比，运行费用较低，设备结构简单，节能环保。
(二)本发明中的冷媒经载冷剂换热器换热后，冷媒再经压缩机和第二空气能换热器进行再次增压和换热降温后，再输入到第二膨胀阀和载冷剂换热器内，实现循环利用，有效降低控制系统的运行成本。
(三)本发明设置有两台空气能换热器，其中一台用于让冷媒通过吸收环境空气热量而汽化，省略了冷媒的气液分离器的使用，也可以防止没有被汽化的液态冷媒输入到压缩机内而造成压缩机损坏，另一台用于让冷媒通过向环境中的空气释放热量而降温，两台空气能换热器再配合管道与贮存罐的设置，使得压缩机的低压进口端和高压出口端的压力均可以保持在设定值；当压缩机的高压出口端的压力低于设定值时，贮存罐持续放出冷媒，以进行压力的补偿， 直至压缩机的高压出口端的压力达到设定值时停止放出冷媒；当压缩机的高压出口端的压力高于设定值时，则利用压差将多余质量的冷媒流入到贮存罐内，以降低压缩机的高压出口端的压力，直至压缩机的高压出口端的压力达到设定值时，贮存罐停止流入冷媒；如果压缩机的高压出口端的压力一直处于设定值，则贮存罐不需要放出冷媒，也不需要流入冷媒。因此，本发明的控制系统能够根据实时的使用情况来实时调整冷媒的流量，例如用于载冷剂换热器的使用数量增加或减少时的情况，实现了冷媒在封闭运行中不同工况时质量流量的变化，同时使得压缩机在保证两端设定值压力不变的状态下，基本能够保持控制系统的高能效比，实现省电的目的。
(四)本发明通过在载冷剂换热器的出口连接压缩机的管道与贮存罐的出口连接第一空气能换热器的入口的管道之间设置管道，再设置相互配合的第一电磁阀和第二电磁阀，由于载冷剂换热器的冷媒需要经过第一膨胀阀和第一空气能换热器汽化后才能输入压缩机，从而能够用于在控制系统刚刚开启的时候清除载冷剂换热器内存留的如液态状的少量冷媒，避免液体和气体的冷媒在压缩机内混合而损坏了压缩机，延长了压缩机的使用寿命。
附图说明
图1是本发明的一种空气能制冷和变流量的控制系统的框架原理图；
图2是本发明的一种空气能制冷和变流量的控制方法的工艺原理图。
附图标记：
1、贮存罐；2、压缩机；3、第一空气能换热器；4、第二空气能换热器；5、载冷剂换热器；6、第一膨胀阀；7、第二膨胀阀；8、第一电磁阀；9、第二电磁阀；10、第一控制阀；11、第二控制阀；12、比例阀；13、单向阀；14、第三电磁阀。
具体实施方式
下面结合附图和具体实施例对发明做进一步阐述，下述说明仅是示例性的，不限定发明的保护范围。
实施例一：
参考图1，一种空气能制冷和变流量的控制系统，包括：贮存罐1、压缩机2、第一空气能换热器3、第二空气能换热器4、载冷剂换热器5、第一膨胀阀6和第二膨胀阀7。
其中，该贮存罐1用于为控制系统提供冷媒，例如用于为系统提供R744或不含润滑油的二氧化碳冷媒。压缩机2可以用于帮助将管道上多余的冷媒输入到贮存罐1内。在该控制系统中，第一空气能换热器3、第二空气能换热器4是作为室外机部分的，而载冷剂换热器5是作为室内机部分的。第一空气能换热器3和第二空气能换热器4都包括有室外机、风量可调节的静音风机、冷媒换热器、分别安装在空气能换热器的出口和入口的两个环境空气测温探头以及安装在冷媒换热器管内的冷媒压力计。载冷剂换热器5为密封结构，内部设置有热交换器和压力计，载冷剂通过热交换器的管壁传递冷量。
二氧化碳是一种新兴的自然工质，从对环境的影响来看，除水和空气以外，是与环境最为友善的制冷工质，而且二氧化碳超临界流体膨胀制冷是一种高效率的制冷方式。此外，二氧化碳还具有良好的安全性和化学稳定性等。
在该控制系统中，如图1所示，贮存罐1的出口通过依次设有第一膨胀阀6和第一空气能换热器3的管道连接至压缩机2的低压进口端，以将贮存罐1输出的二氧化碳冷媒转换为具有一定过热度的气态低温二氧化碳冷媒输入压缩机2，其中，第一膨胀阀6可用于起到膨胀、降压效果，使得贮存罐1所输出的二氧化碳冷媒首先经过第一膨胀阀6，接着再通入第一空气能换热器3中通过吸收 室外环境热量后而汽化，最终成为气态低温冷媒，亦即贮存罐1输出的二氧化碳冷媒被汽化。
压缩机2的高压出口端通过管道连接第二空气能换热器4的入口，以将第一空气能换热器3输出的具有一定过热度的气态低温二氧化碳冷媒转换成气态或超临界态的高压高温二氧化碳冷媒输入第二空气能换热器4。
第二空气能换热器4的出口通过管道分别与贮存罐1的入口和载冷剂换热器5的入口并联设置，且在载冷剂换热器5的入口设置有第二膨胀阀7，以将压缩机所输出的气态或超临界态的高压高温二氧化碳冷媒由第二空气能换热器4转换为高压常温二氧化碳冷媒，然后使高压常温二氧化碳冷媒可输入到贮存罐1进行贮存或通过第二膨胀阀7节流膨胀，并在载冷剂换热器5内吸收载冷剂热量后以气态冷媒排出载冷剂换热器。例如：压缩机2所输出的高压高温二氧化碳冷媒通入第二空气能换热器4后通过向室外环境中的空气释放热量而转换为高压常温二氧化碳冷媒；其中，在正常工作时，该高压常温二氧化碳冷媒用于通入第二膨胀阀7后由于JT效应而转换为低温二氧化碳冷媒，接着再输入到载冷剂换热器5内吸收载冷剂热量，然后以气态冷媒排出；如果压缩机2的高压出口端的压力超过预定值时，则贮存罐1的入口打开，并利用压差将多余质量的高压常温二氧化碳冷媒输入到贮存罐1内，直至压缩机2的高压出口端的压力达到预定值时停止。
载冷剂换热器5的出口通过管道连接压缩机2的低压进口端，以将载冷剂换热器5排出的气态二氧化碳冷媒通过压缩机2进行增压转换为高压高温冷媒，接着再经第二空气能换热器4和第二膨胀阀7通入载冷剂换热器5中，即实现循环利用，又或者压缩机2将二氧化碳冷媒增压后，如果压缩机2的高压出口端的压力超过预定值时，则冷媒经第二空气能换热器4输入到贮存罐1进行贮 存。
在载冷剂换热器5的出口连接压缩机2的管道与贮存罐1的出口连接第一空气能换热器3的入口的管道之间连通有一设有第一电磁阀8的管道，即载冷剂换热器5的出口连接压缩机2的管道与贮存罐1的出口连接第一空气能换热器3的入口的管道之间并联设置，以用于方便地将载冷剂换热器5内的二氧化碳冷媒输入到第一空气能换热器3内；在载冷剂换热器5的出口连接压缩机2的管道上还设置有用于与第一电磁阀8配合的第二电磁阀9；在贮存罐1的出口和入口处分别设置有第一控制阀10和第二控制阀11。通过设置带有第一电磁阀8的管道，可以在控制系统刚刚开始的时候，可以首先利用压缩机2将载冷剂换热器5内存留的少量气态或液态冷媒先抽出来，这时的第二电磁阀9为关闭的，而第一电磁阀8为开启的，以防止载冷剂换热器5内被抽出的冷媒直接通过第二电磁阀9而进入到压缩机2内，被抽出的冷媒会依次经第一膨胀阀6和第一空气能换热器3后而汽化，最后进入到压缩机2内，从而能够保证压缩机2入口处不会有液体冷媒进入压缩机2，以避免对压缩机2进行损坏，延长了压缩机2的寿命；如果载冷剂换热器5内管内压力达到设定值而压缩机2的高压出口端的压力未达到设定值时，则第一控制阀10打开，用于输出贮存罐1内的二氧化碳冷媒补充，同时，第一电磁阀8关闭而第二电磁阀9打开，贮存罐1内的二氧化碳冷媒经第一膨胀阀6和第一空气换热器3汽化后输入压缩机2，直至压缩机2的高压出口端的压力达到设定值后第一控制阀10停止。因此，通过上述结构的设置能够用于在控制系统刚刚开启的时候清除载冷剂换热器5内的如液态的少量冷媒，避免液体冷媒进入压缩机2而损坏了压缩机2，延长了压缩机2的使用寿命。
为了方便控制贮存罐1内的二氧化碳冷媒的流出和流入，第一控制阀10和 第二控制阀11可以选用比例阀，以用于提高流量的精准控制。
为了方便控制二氧化碳冷媒，在第一空气能换热器3与第一膨胀阀6之间的管道上也可以设置有用于控制管道开关的第三电磁阀14。
载冷剂换热器5可以设有两个以上且并联设置，以用于人们可以随时增加或减少载冷剂换热器5的使用数量，实现制冷量的增多或减少，在每个载冷剂换热器5的入口均设置有一第二膨胀阀7。
在载冷剂换热器5的出口还设置有比例阀12，以用于开度调节冷媒流量来控制制冷量，从而使载冷剂换热器5出口处的载冷剂温度保持在设定值，载冷剂温度不会由于载冷剂质量流量或体积流量变化而波动。
在载冷剂换热器5的出口连接压缩机2的管道上还设置有单向阀13，以用于保证冷媒的流动方向，防止冷媒倒流。当然，同样是为了保证冷媒的流动方向，防止冷媒倒流，在压缩机2的入口和出口也可以分别设置一个单向阀13。
在本实施例中，压缩机2的低压进口端的压力设定值在0.15MPa-4MPa间，而压缩机2的高压出口端的压力设定值在3.5MPa-12MPa间。
在压缩机2的低压进口端和高压出口端还分别设置有压力传感器，以用于实时准确地检测对应位置的压力。
在控制系统由于所需制冷量降低而需减少控制系统的二氧化碳冷媒的质量时，多余质量的二氧化碳冷媒通过压缩机2增压后流入贮存罐1贮存；在控制系统由于所需制冷量增加而需增加控制系统的二氧化碳冷媒的质量时，输出贮存罐1内的二氧化碳冷媒，且二氧化碳冷媒通过第一膨胀阀6和第一空气能换热器3的汽化后流入压缩机2的低压进口端，以用于补充控制系统所需质量的冷媒。
载冷剂换热器上的载冷剂为气态载冷剂或液态载冷剂，气态载冷剂为空气、 氮气或氩气，液体载冷剂为水、盐水、乙二醇或丙二醇溶液。
实施例二：
参考图2，本实施例提供一种空气能制冷和变流量的控制方法，其采用实施例一的空气能制冷和变流量的控制系统，包括如下步骤：
S1、启动控制系统，压缩机2运转，当压缩机2的高压出口端的压力低于设定值时，贮存罐1内的二氧化碳冷媒流出，二氧化碳冷媒经过第一膨胀阀6和第一空气能换热器3汽化转换为具有一定过热度的气态低温二氧化碳冷媒并输入到压缩机2的低压进口端，以用于使保持压缩机2的高压出口端的压力在设定值，同时用于保持压缩机2的低压进口端压力不低于设定值，即这时的第一电磁阀8为关闭状态，而第二电磁阀9为打开状态；
S2、转换出的具有一定过热度的气态低温二氧化碳冷媒经压缩机2增压后成为气态或超临界态高压高温二氧化碳冷媒，接着该气态或超临界态高压高温二氧化碳冷媒进入第二空气能换热器4内；
S3、进入第二空气能换热器4内的气态或超临界态高压高温二氧化碳冷媒通过向环境中的空气释放热量而对应转变为气态或超临界态高压常温二氧化碳冷媒，接着该气态或超临界态高压常温二氧化碳冷媒进入到第二膨胀阀7；
S4、气态或超临界态高压常温二氧化碳冷媒进入到第二膨胀阀7后由于JT效应转变为低温二氧化碳冷媒，接着低温二氧化碳冷媒进入到对应的载冷剂换热器5内；
S5、低温二氧化碳冷媒进入到载冷剂换热器5内之后，与载冷剂换热器5外表面的载冷剂进入热交换，使载冷剂向二氧化碳冷媒释放热量实现载冷剂的降温制冷，低温冷媒吸收载冷剂热量后复热和完全汽化；
S6、经载冷剂换热器5排出后的气态二氧化碳冷媒再经管道进入到压缩机2 增压成为高压高温二氧化碳冷媒后循环利用；
S7、在压缩机2的高压出口端的压力未达到设定值时，则贮存罐1持续放出二氧化碳冷媒，而在压缩机2的高压出口端的压力达到设定值时，贮存罐1的出口停止放出二氧化碳冷媒；
S8、在压缩机2的高压出口端的压力超过设定值时，则多余的二氧化碳冷媒经贮存罐1的入口流入，直至压缩机2的高压出口端的压力达到设定值时，贮存罐1的入口停止流入二氧化碳冷媒。
优选的，在步骤S1中，压缩机2运转后，第一电磁阀8打开而第二电磁阀9关闭，当压缩机2的高压出口端的压力低于设定值时，首先使载冷剂换热器5内存留的少量冷媒流出(例如液态状的冷媒)且冷媒经第一膨胀阀6和第一空气能换热器3汽化后转换为具有一定过热度的气态冷媒并输入压缩机2的低压进口端，从而可防止载冷剂换热器5内被抽出的冷媒直接通过第二电磁阀9而进入到压缩机2内；如果载冷剂换热器5的管内压力达到设定值而压缩机2的高压出口端的压力仍低于设定值，则由贮存罐1流出冷媒补充，且后续的控制系统制冷过程中的载冷剂换热器5内的气态冷媒直接输入至压缩机2而不再流出到第一膨胀阀6和第一空气能换热器3内，即这时的第一电磁阀8是关闭的而第二电磁阀9是打开的。
优选的，载冷剂换热器2的使用数量增加后(即开启数量增加时)，会使压缩机2的高压出口端的压力小于设定值，从而让贮存罐1的出口打开并放出冷媒，以用于填充，直至压缩机2的高压出口端的压力达到设定值时停止；
载冷剂换热器5的使用数量减少后(即关闭数量增多时)，使压缩机2的高压出口端的压力大于设定值，从而让贮存罐1的入口打开并流入多余质量的冷媒，直至压缩机2的高压出口端的压力达到设定值时停止。
所述压缩机2的低压进口端的压力设定值在0.15MPa-4MPa间，而所述压缩机的高压出口端的压力设定值在3.5MPa-12MPa间。
在检测压缩机2的低压进口端和高压出口端的压力时使用压力传感器进行检测。
所述载冷剂换热器上的载冷剂为气态载冷剂或液态载冷剂，所述气态载冷剂为空气、氮气或氩气，所述液体载冷剂为水、盐水、乙二醇或丙二醇溶液。
本发明所实施的用于辅助技术方案实施的其它相应的技术特征，技术人员可结合现有常规技术手段进行相应的实施或在其基础上进行改进，对于其他有关方面的技术手段此处不再赘述。
在本说明书的描述中，若出现术语“实施例一”、“本实施例”、“具体实施”等描述意指结合该实施例或示例描述的具体特征、结构、材料或特点包含于本发明或发明的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不一定指的是相同的实施例或示例；而且，所描述的具体特征、结构、材料或特点可以在任何一个或多个实施例或示例中以恰当的方式结合。
在本说明书的描述中，如有术语“连接”、“安装”、“固定”、“设置”、“具有”等均做广义理解，例如，“连接”可以是固定连接或在不影响部件关系与技术效果的基础上通过中间组件间接进行，也可以是一体连接或部分连接，如同此例的情形对于本领域普通技术人员而言，可根据具体情况理解上述术语在本发明中的具体含义。
上述对实施例的描述是为了便于该技术领域的普通技术人员能够理解和应用，熟悉本领域技术的人员显然可轻易对这些实例做出各种修改，并把在此说明的一般原理应用到其它实施例中而不必经过创造性的劳动。因此，本案不限于以上实施例，对于以下几种情形的修改，都应该在本案的保护范围内：①以 本发明技术方案为基础并结合现有公知常识所实施的新的技术方案；②采用公知技术对本发明技术方案的部分特征的等效替换，所产生的技术效果与本发明技术效果相同，例如，对于工艺中所用到常规生产设备、装置等进行等效替换；③以本发明技术方案为基础进行拓展，拓展后的技术方案的实质内容没有超出本发明技术方案之外；④利用本发明文本记载内容或说明书附图所作的等效变换，将所得技术手段应用在其它相关技术领域的方案。

Claims (10)

  1. 一种空气能制冷和变流量的控制系统，其特征在于，包括：
    贮存罐、压缩机、第一空气能换热器、第二空气能换热器、载冷剂换热器、第一膨胀阀和第二膨胀阀；
    所述贮存罐的出口通过依次设有所述第一膨胀阀和所述第一空气能换热器的管道连接至所述压缩机的低压进口端，以将所述贮存罐输出的冷媒转换为具有过热度的气态低温冷媒输入所述压缩机；
    所述压缩机的高压出口端通过管道连接所述第二空气能换热器的入口，以将所述第一空气能换热器输出的具有过热度的气态低温冷媒转换为高压高温冷媒输入所述第二空气能换热器；
    所述第二空气能换热器的出口通过管道分别与所述贮存罐的入口和所述载冷剂换热器的入口并联设置，且在所述载冷剂换热器的入口设置有所述第二膨胀阀，以将所述压缩机所输出的高压高温冷媒由所述第二空气能换热器转换为高压常温冷媒，然后使所述高压常温冷媒可输入到所述贮存罐进行贮存或通过所述第二膨胀阀节流膨胀，并在所述载冷剂换热器内吸收载冷剂热量成为气态冷媒排出所述载冷剂换热器；
    所述载冷剂换热器的出口通过管道连接所述压缩机的低压进口端，以将所述载冷剂换热器排出的气态冷媒通过所述压缩机进行增压并实现循环利用或者输入到所述贮存罐进行贮存。
  2. 根据权利要求1所述的空气能制冷和变流量的控制系统，其特征在于：
    在所述载冷剂换热器的出口连接所述压缩机的管道与所述贮存罐的出口连接所述第一空气能换热器的入口的管道之间还连通有一设置有第一电磁阀的管道，以用于将所述载冷剂换热器内的冷媒输入到所述第一空气能换热器内；
    在所述载冷剂换热器的出口连接所述压缩机的管道上还设置有用于与所述 第一电磁阀配合的第二电磁阀；
    在所述贮存罐的出口和入口处分别设置有第一控制阀和第二控制阀。
  3. 根据权利要求1所述的空气能制冷和变流量的控制系统，其特征在于：
    所述载冷剂换热器设有两个以上且并联设置，在每个所述载冷剂换热器的入口均设置有一所述第二膨胀阀。
  4. 根据权利要求1-3任一项所述的空气能制冷和变流量的控制系统，其特征在于：
    在所述载冷剂换热器的出口还设置有比例阀，以用于控制开度来调节冷媒流量以达到控制制冷量。
  5. 根据权利要求1所述的空气能制冷和变流量的控制系统，其特征在于：
    所述压缩机的低压进口端的压力设定值在0.15MPa-4MPa间，所述压缩机的高压出口端的压力设定值在3.5MPa-12MPa间。
  6. 根据权利要求5所述的空气能制冷和变流量的控制系统，其特征在于：
    在所述压缩机的低压进口端和高压出口端还分别设置有压力传感器。
  7. 根据权利要求1所述的空气能制冷和变流量的控制系统，其特征在于：
    在控制系统由于所需制冷量降低而需减少控制系统的冷媒的质量时，多余质量的冷媒通过所述压缩机增压后流入所述贮存罐贮存；
    在控制系统由于所需制冷量增加而需增加控制系统的冷媒的质量时，输出所述贮存罐内的冷媒，且冷媒通过所述第一膨胀阀和所述第一空气能换热器的汽化后流入所述压缩机的低压进口端，以用于补充控制系统所需质量的冷媒。
  8. 一种空气能制冷和变流量的控制方法，其特征在于，采用如权利要求1-7任一项所述的空气能制冷和变流量的控制系统，包括如下步骤：
    S1、启动控制系统，压缩机运转，当所述压缩机的高压出口端的压力低于 设定值时，贮存罐内的冷媒流出并经过第一膨胀阀和第一空气能换热器汽化转换为具有过热度的气态低温冷媒并输入到所述压缩机的低压进口端，以使保持所述压缩机的高压出口端的压力达到设定值，同时用于保持所述压缩机的低压进口端压力在设定值；
    S2、转换出的具有过热度的气态低温冷媒经所述压缩机增压后成为高压高温冷媒，接着高压高温冷媒进入第二空气能换热器内；
    S3、进入所述第二空气能换热器内的高压高温冷媒通过向环境中的空气释放热量而转变为高压常温冷媒，接着高压常温冷媒进入到所述第二膨胀阀；
    S4、高压常温冷媒进入所述第二膨胀阀后由于JT效应转换为低温冷媒进入载冷剂换热器；
    S5、低温冷媒进入到所述载冷剂换热器之后，与所述载冷剂换热器外表面的载冷剂进行热交换，载冷剂向冷媒释放热量实现载冷剂的降温制冷，且低温冷媒吸收载冷剂热量后复热和完全汽化；
    S6、经所述载冷剂换热器排出后的气态冷媒再经管道进入所述压缩机增压成为高压高温冷媒后循环利用；
    S7、在所述压缩机的高压出口端的压力未达到设定值时，则所述贮存罐持续放出冷媒，而在所述压缩机的高压出口端的压力达到设定值时，所述贮存罐的出口停止放出冷媒；
    S8、在所述压缩机的高压出口端的压力超过设定值时，则多余的冷媒经所述贮存罐的入口流入，直至所述压缩机的高压出口端的压力达到设定值时，所述贮存罐的入口停止流入冷媒。
  9. 根据权利要求8所述的空气能制冷和变流量的控制方法，其特征在于：
    在步骤S1中，所述压缩机运转后，当所述压缩机的高压出口端的压力低于 设定值时，首先使所述载冷剂换热器内的冷媒排出且冷媒经所述第一膨胀阀和所述第一空气能换热器汽化转换为具有过热度的气态冷媒并输入所述压缩机的低压进口端；如载冷剂换热器的管内压力达到设定值而所述压缩机的高压出口端的压力仍低于设定值时，则由所述贮存罐流出冷媒补充，且后续的控制系统制冷过程中的所述载冷剂换热器排出的气态冷媒直接输入至所述压缩机而不再流出到所述第一膨胀阀和所述第一空气能换热器内。
  10. 根据权利要求8所述的空气能制冷和变流量的控制方法，其特征在于：
    所述载冷剂换热器的使用数量增加后，使所述压缩机的高压出口端的压力小于设定值，从而让所述贮存罐的出口打开并放出冷媒，以用于填充，直至所述压缩机的高压出口端的压力达到设定值时停止；
    所述载冷剂换热器的使用数量减少后，使所述压缩机的高压出口端的压力大于设定值，从而让所述贮存罐的入口打开并流入多余质量的冷媒，直至所述压缩机的高压出口端的压力达到设定值时停止。
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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007155143A (ja) * 2005-11-30 2007-06-21 Daikin Ind Ltd 冷凍装置
CN201463433U (zh) * 2009-06-12 2010-05-12 深圳市艾斯兰德冷机制造有限公司 多组并联蒸发器制冷系统的热气冲霜装置
CN205980123U (zh) * 2016-08-24 2017-02-22 武汉克莱美特环境设备有限公司 一种大型制冷系统
WO2018211682A1 (ja) * 2017-05-19 2018-11-22 三菱電機株式会社 チリングユニット及び水循環温調システム
CN215909273U (zh) * 2021-04-05 2022-02-25 上海复璐帝流体技术有限公司 二氧化碳相变液化循环制热系统及空调制热器
CN114396667A (zh) * 2021-12-01 2022-04-26 杨景峰 二氧化碳冷媒空气能循环空调系统及其制冷和制热方法

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007155143A (ja) * 2005-11-30 2007-06-21 Daikin Ind Ltd 冷凍装置
CN201463433U (zh) * 2009-06-12 2010-05-12 深圳市艾斯兰德冷机制造有限公司 多组并联蒸发器制冷系统的热气冲霜装置
CN205980123U (zh) * 2016-08-24 2017-02-22 武汉克莱美特环境设备有限公司 一种大型制冷系统
WO2018211682A1 (ja) * 2017-05-19 2018-11-22 三菱電機株式会社 チリングユニット及び水循環温調システム
CN215909273U (zh) * 2021-04-05 2022-02-25 上海复璐帝流体技术有限公司 二氧化碳相变液化循环制热系统及空调制热器
CN114396667A (zh) * 2021-12-01 2022-04-26 杨景峰 二氧化碳冷媒空气能循环空调系统及其制冷和制热方法

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