Refrigerant purification device, air conditioner and control method

Abstract

The invention relates to a refrigerant purification device, an air conditioner and a control method. The system comprises a refrigeration cycle unit, a purification tank, a refrigerant introduction structure, a non-condensable gas discharge structure and a refrigerant backflow structure, the refrigeration cycle unit comprises a compressor, an evaporator, a condenser and a first electronic expansion valve, the compressor, the evaporator, the first electronic expansion valve and the condenser are sequentially communicated to form a closed refrigeration cycle, and a negative-pressure refrigerant is contained in the refrigeration cycle unit; a heat exchange pipe is arranged in the purification tank and is used for carrying out heat exchange on a refrigerant containing non-condensable gas and a low-temperature refrigerant so as to separate the non-condensable gas; the refrigerant leading-in structure comprises a first pipeline and a second pipeline, the first pipeline is used for leading a low-temperature liquid refrigerant in the evaporator into the heat exchange pipe, and the second pipeline is used for leading a high-temperature gaseous refrigerant containing non-condensable gas at the upper part of the condenser into the purification tank; the non-condensable gas discharge structure is communicated with the upper part of the purification tank and is used for discharging separated non-condensable gas; the refrigerant backflow structure communicates with the heat exchange pipe and is used for enabling the refrigerant obtained after heat exchange evaporation to flow back to the refrigeration circulation unit.

Description

TECHNICAL FIELD

[0001] The present disclosure relates to the technical field of air conditioners with refrigerant purification devices, and in particular to a refrigerant purification device, an air conditioner and a control method. BACKGROUND

[0002] In the field of large water chillers, the environmental protection and refrigeration efficiency of refrigerants are the core concerns of the industry. The refrigerant R134a widely used in traditional large water chillers has a high global warming potential (GWP) and does not meet the development requirements of global environmental protection regulations. The European Union, the United States, Japan and other countries have introduced policies to eliminate high-GWP refrigerants, and China also plans to gradually eliminate R134a in water chillers.

[0003] Under this background, the R1233zd(E) refrigerant has become the preferred solution to replace R134a and gradually become the development trend of water chiller refrigerants due to its extremely low ozone depletion potential (ODP), low global warming potential (GWP) and high refrigeration efficiency. However, R1233zd(E) is a negative pressure refrigerant, and when it operates in a refrigeration system, the pressure of some pipeline sections will be lower than atmospheric pressure. This characteristic causes external air and water vapor to easily penetrate into the interior of the refrigeration system and mix with R1233zd(E) refrigerant after participating in the cycle.

[0004] During the cycle, some components in the air and water vapor cannot condense and will gradually accumulate in the upper region of the condenser. These non-condensable gases will occupy the effective heat exchange area of the condenser tubes, reducing the contact area between the refrigerant and the cooling water, and severely affecting the heat exchange effect of the condenser. This not only reduces the ability of the condenser to remove heat from the system, causing the condensing temperature to rise, but also directly leads to a decrease in the refrigeration capacity and energy efficiency of the unit, which cannot meet the stable operation requirements of the water chiller.

[0005] In the prior art, the purification device for conventional positive pressure refrigerants cannot adapt to the characteristics of negative pressure refrigerants and cannot effectively separate non-condensable gases that penetrate in a negative pressure environment. At the same time, even if some solutions attempt to separate non-condensable gases, they do not consider integration with other functional systems of the unit, resulting in complex structure and insufficient stability of the entire machine.

[0006] Therefore, there is an urgent need for a refrigerant purification technology that can adapt to the characteristics of negative pressure refrigerants, efficiently separate non-condensable gases, and has a simple structure and adapts to the operation requirements of the unit, to solve the problem of energy efficiency and refrigeration capacity reduction caused by the accumulation of non-condensable gases in negative pressure refrigerant units, and to ensure the environmental protection and stable operation of water chillers. SUMMARY

[0007] The present disclosure provides a refrigerant purification device, an air conditioner and a control method to solve the technical problem of the above-mentioned existing technology that the non-condensable gas aggregation in the negative pressure refrigerant unit leads to the decline of energy efficiency and refrigeration capacity.

[0008] The refrigerant purification device provided by the present disclosure comprises a refrigeration cycle unit, a purification tank, a refrigerant introduction structure, a non-condensable gas discharge structure and a refrigerant backflow structure. The refrigeration cycle unit comprises a compressor, an evaporator, a condenser and a first electronic expansion valve. The compressor, the evaporator, the first electronic expansion valve and the condenser are sequentially connected by pipelines to form a closed refrigeration cycle. The refrigerant circulating in the refrigeration cycle unit is negative pressure refrigerant. The purification tank is provided with a heat exchange pipe for heat exchange between the refrigerant containing non-condensable gas and low-temperature refrigerant to separate the non-condensable gas. The refrigerant introduction structure comprises a first pipeline and a second pipeline. The first pipeline is used to introduce the low-temperature liquid refrigerant in the evaporator into the heat exchange pipe. The second pipeline is used to introduce the high-temperature gaseous refrigerant containing non-condensable gas at the upper part of the condenser into the internal space of the purification tank. The non-condensable gas discharge structure is in communication with the upper part of the purification tank and is used to discharge the separated non-condensable gas. The refrigerant backflow structure is in communication with the heat exchange pipe and is used to return the heat-exchanged and evaporated refrigerant to the refrigeration cycle unit.

[0009] Compared with the prior art, the above technical solution provided by the present disclosure has the following advantages: The refrigerant purification device, the air conditioner and the control method provided by the present disclosure are characterized in that the compressor, the evaporator, the first electronic expansion valve and the condenser are sequentially connected to form a closed refrigeration cycle. The negative pressure refrigerant completes the basic process of refrigeration cycle in the cycle. Specifically, the first pipeline of the refrigerant introduction structure introduces the low-temperature liquid refrigerant in the evaporator into the heat exchange pipe of the purification tank. The second pipeline synchronously introduces the high-temperature gaseous refrigerant containing non-condensable gas aggregated at the upper part of the condenser into the internal space of the purification tank. The two kinds of refrigerants exchange heat inside and outside the heat exchange pipe. The high-temperature gaseous refrigerant condenses into liquid outside the heat exchange pipe. The non-condensable gas is separated and aggregated at the upper part of the purification tank because it cannot condense. The low-temperature liquid refrigerant is evaporated after absorbing heat inside the heat exchange pipe and is reintroduced into the refrigeration cycle unit through the refrigerant backflow structure. The aggregated non-condensable gas is discharged in time through the non-condensable gas discharge structure, ensuring the continuous and effective purification process.

[0010] This combination of purification tank and heat exchange tubes adapts to the characteristics of negative pressure refrigerants, achieving efficient separation of non-condensable gases and refrigerant. It fundamentally solves the problem of non-condensable gases occupying the condenser heat exchange area in negative pressure refrigerant units, avoiding energy efficiency degradation due to increased condensation temperature and significantly improving the unit's cooling capacity and operational efficiency. The dual-pipe refrigerant inlet and refrigerant return structure form a closed loop, ensuring the refrigerant is recycled after separation without additional loss. The non-condensable gas exhaust structure ensures the continuity and thoroughness of the purification process. The entire device requires no complex separation components, featuring a simple and highly targeted structure. It effectively compensates for the shortcomings of traditional purification devices that cannot adapt to negative pressure refrigerants, providing reliable support for the stable and efficient operation of negative pressure refrigerant units. Attached Figure Description

[0011] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with the invention and, together with the description, serve to explain the principles of the invention.

[0012] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, for those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0013] One or more embodiments are illustrated by way of example with reference numerals in the accompanying drawings. These illustrations do not constitute a limitation on the embodiments. Elements with the same reference numerals in the drawings are denoted as similar elements. Unless otherwise stated, the figures in the drawings are not to be limited by scale.

[0014] Figure 1 Diagram of refrigerant purification system; Figure 2 This is a diagram of the cooling system.

[0015] Explanation of reference numerals in the attached figures: 1. Compressor; 2. Evaporator; 3. Condenser; 4. First electronic expansion valve; 5. Purification tank; 51. Heat exchange tube; 6. Refrigerant introduction structure; 61. First pipeline; 62. Second pipeline; 63. Ejector device; 64. Third pipeline; 65. Fourth solenoid valve; 7. Non-condensable gas discharge structure; 71. Vacuum pump; 72. Fifth pipeline; 73. Refrigerant leak sensor; 74. Second solenoid valve; 8. Refrigerant return structure; 9. Cooling unit; 91. Second electronic expansion valve 92. Motor cooling branch; 93. Sixth pipeline; 94. Fifth solenoid valve; 95. Oil tank cooling branch; 96. Sixth solenoid valve; 97. Inverter cooling branch; 98. Seventh solenoid valve; 101. Second temperature sensor; 103. First solenoid valve; 104. Third solenoid valve; 105. First temperature sensor; 111. Oil tank; 112. Inverter; 113. Third temperature sensor; 114. Fifth temperature sensor; 115. Fourth temperature sensor. Detailed Implementation

[0016] To make the objectives, technical solutions, and advantages of the embodiments of this disclosure clearer, the technical solutions of the embodiments of this disclosure will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this disclosure. Based on the embodiments of this disclosure, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this disclosure.

[0017] refer to Figures 1-2 The refrigerant purification device provided in this embodiment forms a closed refrigeration cycle by sequentially connecting the compressor 1, evaporator 2, first electronic expansion valve 4, and condenser 3. The negative pressure refrigerant completes the basic process of the refrigeration cycle in the cycle. Specifically, the first pipe 61 of the refrigerant introduction structure 6 introduces the low-temperature liquid refrigerant in the evaporator 2 into the heat exchange tube 51 of the purification tank 5. The second pipe 62 simultaneously introduces the high-temperature gaseous refrigerant containing non-condensable gases accumulated on the upper part of the condenser 3 into the internal space of the purification tank 5. The two refrigerants exchange heat inside and outside the heat exchange tube 51: the high-temperature gaseous refrigerant condenses into liquid outside the heat exchange tube 51, and the non-condensable gases separate and accumulate on the upper part of the purification tank 5 because they cannot condense. The low-temperature liquid refrigerant absorbs heat and evaporates inside the heat exchange tube 51, and then flows back into the refrigeration cycle unit through the refrigerant return structure 8. The accumulated non-condensable gases are discharged in time through the non-condensable gas discharge structure 7 to ensure that the purification process is continuously effective.

[0018] Specifically, the refrigerant purification device provided in this embodiment includes: a refrigeration cycle unit, a purification tank 5, a refrigerant inlet structure 6, a non-condensable gas discharge structure 7, and a refrigerant return structure 8. The refrigeration cycle unit includes a compressor 1, an evaporator 2, a condenser 3, and a first electronic expansion valve 4. The compressor 1, evaporator 2, first electronic expansion valve 4, and condenser 3 are sequentially connected by pipelines to form a closed refrigeration cycle. The refrigerant flowing in the refrigeration cycle unit is a negative pressure refrigerant. The purification tank 5 is equipped with heat exchange tubes 51 for reacting the refrigerant containing non-condensable gases with... Low-temperature refrigerant undergoes heat exchange to separate non-condensable gases; the refrigerant introduction structure 6 includes a first pipe 61 and a second pipe 62. The first pipe 61 is used to introduce the low-temperature liquid refrigerant in the evaporator 2 into the heat exchange tube 51, and the second pipe 62 is used to introduce the high-temperature gaseous refrigerant containing non-condensable gases from the upper part of the condenser 3 into the internal space of the purification tank 5; the non-condensable gas discharge structure 7 is connected to the upper part of the purification tank 5 and is used to discharge the separated non-condensable gases; the refrigerant return structure 8 is connected to the heat exchange tube 51 and is used to return the refrigerant after heat exchange and evaporation to the refrigeration cycle unit.

[0019] For example, negative pressure refrigerant refers to refrigerant that is in an environment with an ambient pressure lower than standard atmospheric pressure when it flows in the closed refrigeration cycle pipeline composed of compressor 1, evaporator 2, first electronic expansion valve 4, and condenser 3. This negative pressure state is adapted to the operating conditions of the refrigeration cycle unit and runs through the entire closed cycle process, ensuring the flow characteristics of the refrigerant in the system and the feasibility of subsequent purification and separation.

[0020] For example, heat exchange tube 51 is a dedicated flow channel for low-temperature liquid refrigerant, installed in the internal cavity of purification tank 5; its core function is to realize indirect heat exchange between two refrigerants. Low-temperature liquid refrigerant from evaporator 2, introduced by the first pipe 61, flows inside the tube, while high-temperature gaseous refrigerant containing non-condensable gas, introduced by the second pipe 62 and located in the internal space of purification tank 5, flows outside the tube. During the heat exchange process, the high-temperature gaseous refrigerant containing non-condensable gas outside the tube is cooled, and the refrigerant components in it condense and liquefy. The non-condensable gas remains gaseous because it cannot condense, thereby realizing the separation of refrigerant and non-condensable gas.

[0021] For example, one end of the first pipe 61 is sealed and connected to the low-temperature liquid refrigerant output end of the evaporator 2, and the other end extends into the purification tank 5 and is connected to the inlet end of the heat exchange tube 51, ensuring that the low-temperature liquid refrigerant in the evaporator 2 flows into the heat exchange tube 51 in a directional manner; one end of the second pipe 62 is sealed and connected to the high-temperature gaseous refrigerant containing non-condensable gas accumulation area in the upper part of the condenser 3, and the other end is connected to the cavity inlet of the purification tank 5, so that the high-temperature gaseous refrigerant containing non-condensable gas in the upper part of the condenser 3 can accurately enter the internal space of the purification tank 5, that is, the cavity area outside the heat exchange tube 51.

[0022] For example, according to the requirements of the application scenario, the upper part of the purification tank 5 refers to a specific area in the internal cavity of the purification tank 5 near the top of the tank, which is specifically used to collect non-condensable gases after heat exchange; the air inlet of the non-condensable gas discharge structure 7 is sealed and connected to the non-condensable gas collection area, and can directionally discharge the separated non-condensable gases.

[0023] For example, one end of the refrigerant reflux structure 8 is sealed and connected to the outlet end of the heat exchange tube 51, and the other end is connected to the inlet end of the compressor 1 of the refrigeration cycle unit; the gaseous refrigerant after heat exchange and evaporation flows into the compressor 1 through the reflux structure and re-participates in the closed refrigeration cycle composed of the compressor 1, evaporator 2, first electronic expansion valve 4, and condenser 3.

[0024] In this way, the combination of purification tank 5 and heat exchange tube 51 can adapt to the characteristics of negative pressure refrigerant, achieving efficient separation of non-condensable gas and refrigerant. This fundamentally solves the problem of non-condensable gas occupying the heat exchange area of ​​condenser 3 in negative pressure refrigerant units, avoiding the energy efficiency decrease caused by the increase in condensation temperature, and significantly improving the unit's cooling capacity and operating energy efficiency. The dual-pipe refrigerant inlet setting and refrigerant return structure 8 form a closed loop, ensuring the recycling of the separated refrigerant without additional loss. The non-condensable gas discharge structure 7 ensures the continuity and thoroughness of the purification process. The entire device does not require complex separation components, has a simple structure and strong targeting, effectively making up for the shortcomings of traditional purification devices that cannot adapt to negative pressure refrigerant, and providing reliable support for the stable and efficient operation of negative pressure refrigerant units.

[0025] In some specific embodiments, the refrigerant introduction structure 6 also includes an ejector device 63, which is connected in series with the second pipeline 62 and is connected to the first pipeline 61 through a third pipeline 64. A fourth solenoid valve 65 is provided on the third pipeline 64. The connection point between the first pipe 61 and the evaporator 2 is higher than the connection point between the first pipe 61 and the heat exchange tube 51, so as to use the height difference to cooperate with the ejector device 63 to realize the non-powered transport of low temperature liquid refrigerant.

[0026] For example, the ejector device 63 is connected in series in the middle section of the second pipeline 62, specifically located on the path from the upper interface of the condenser 3 to the internal space interface of the purification tank 5. After being connected in series, it does not change the core function of the second pipeline 62 in introducing the high-temperature gaseous refrigerant containing non-condensable gas from the upper part of the condenser 3 into the internal space of the purification tank 5. It only generates ejection suction by utilizing the flow of refrigerant in the second pipeline 62 through its own structure.

[0027] For example, one end of the third pipe 64 is sealed and connected to the ejector interface of the ejector device 63, and the other end is sealed and connected to the middle section of the first pipe 61. This position is between the connection end of the first pipe 61 and the evaporator 2 and the connection end of the heat exchange tube 51, ensuring that the negative pressure suction force generated by the ejector device 63 can effectively act on the low-temperature liquid refrigerant in the first pipe 61.

[0028] For example, the "position higher than" is determined by the central axis of the two connection ends. The vertical height of the central axis of the connection end of the first pipe 61 and the evaporator 2 is higher than the vertical height of the central axis of the connection end of the first pipe 61 and the heat exchange tube 51, forming a natural height difference that can be used to drive the flow of refrigerant by gravitational potential energy. There is no need to set a specific height value. It is only necessary to ensure that the refrigerant can flow naturally in the direction of the heat exchange tube 51 under the action of gravity.

[0029] For example, the collaborative logic of the non-powered delivery is as follows: the ejector device 63 generates negative pressure suction through the refrigerant flow in the second pipe 62, which forms a forward pulling force on the low-temperature liquid refrigerant in the first pipe 61; at the same time, the height difference of the first pipe 61 gives the refrigerant downward gravitational potential energy, forming a forward thrust; the pulling force and the thrust work together to drive the low-temperature liquid refrigerant from the evaporator 2 through the first pipe 61 into the heat exchange tube 51, without the need for additional power drive components throughout the process.

[0030] It should be noted that by connecting the ejector device 63 in series with the second pipe 62, the flow characteristics of the high-temperature gaseous refrigerant containing non-condensable gases discharged from the condenser 3 in the second pipe 62 are utilized to generate negative pressure suction in the ejector device 63. A communication channel between the ejector device 63 and the first pipe 61 is established through the third pipe 64, and the opening and closing of this channel is controlled by the fourth solenoid valve 65 to achieve precise start and stop of the ejection action. The connection end of the first pipe 61 with the evaporator 2 (refrigerant input end) is set higher than its connection end with the heat exchange tube 51 (refrigerant output end), forming a natural height difference, utilizing the gravitational potential energy of the refrigerant itself. Through the synergistic effect of the negative pressure suction of the ejector device 63 and the gravitational potential energy of the height difference, the stable delivery of low-temperature liquid refrigerant in the evaporator 2 to the heat exchange tube 51 can be achieved without an additional power device, which meets the overall functional requirements of the refrigerant introduction structure 6.

[0031] In this way, the low-temperature liquid refrigerant is transported without power by the purification tank 5 in conjunction with the ejector device 63 and the height difference. This can efficiently separate non-condensable gases in the negative pressure refrigerant, avoid occupying the heat exchange area of ​​the condenser 3, effectively improve the heat exchange effect of the condenser 3, and increase the unit's cooling capacity and energy efficiency. At the same time, the purified and separated liquid refrigerant is used for cooling the motor, bearings, and frequency converter 112 after throttling, which solves the cooling needs of the new refrigerant unit and prevents related components from overheating. Furthermore, through the integrated design of the purification system and the cooling system, there is no need to add additional power components and independent cooling devices, which simplifies the overall structure, reduces operating energy consumption, and achieves precise control of the refrigerant transport, purification, and cooling processes.

[0032] In some specific embodiments, the non-condensable gas discharge structure 7 includes a vacuum pump 71, a fifth pipeline 72, and a refrigerant leakage sensor 73. One end of the fifth pipeline 72 is connected to the upper part of the purification tank 5, and the other end is connected to the atmosphere. The vacuum pump 71 and the second solenoid valve 74 are connected in series in the fifth pipeline 72. The refrigerant leakage sensor 73 is set at the outlet end of the fifth pipeline 72 to detect the concentration of refrigerant in the discharged gas.

[0033] For example, one end of the fifth pipeline 72 is sealed and connected to a specific area on the upper part of the purification tank 5 for collecting non-condensable gases. This area is close to the top of the tank and corresponds to the collection space after the non-condensable gases are separated, ensuring that the non-condensable gases can be efficiently introduced into the fifth pipeline 72.

[0034] For example, along the direction of gas flowing from the purification tank 5 to the atmosphere in the fifth pipeline 72, the second solenoid valve 74 and the vacuum pump 71 are connected in series. That is, from the purification tank 5 side to the atmosphere side, the second solenoid valve 74 and the vacuum pump 71 are connected in series on the fifth pipeline 72 to ensure that the pipeline is controlled by the solenoid valve first, and then the vacuum pump 71 provides exhaust power.

[0035] For example, the outlet end of the fifth pipeline 72 refers to the end area that is far away from the purification tank 5 and directly connected to the atmosphere. This area is the final outflow section where the discharged gas enters the atmosphere.

[0036] For example, the refrigerant leakage sensor 73 is installed on the gas flow path at the outlet end of the fifth pipe 72. Its detection probe is in direct contact with the exhaust gas and can capture the refrigerant concentration data in the exhaust gas flowing through the outlet end in real time.

[0037] In this embodiment, a communication channel between the purification tank 5 and the atmosphere is established through the fifth pipeline 72. A second solenoid valve 74 and a vacuum pump 71 are connected in series on the pipeline to control the exhaust flow and power output. At the same time, a refrigerant leakage sensor 73 is installed at the outlet end of the fifth pipeline 72 to achieve directional, controllable and safe discharge of the separated non-condensable gas, avoid excessive refrigerant leakage during the discharge process, and adapt to the exhaust requirements of the negative pressure refrigerant purification system.

[0038] In this way, the vacuum pump 71 provides power, and the second solenoid valve 74 controls the on / off state, so that the non-condensable gas accumulated in the upper part of the purification tank 5 can be quickly and thoroughly discharged, ensuring the refrigerant purification effect; the refrigerant leakage sensor 73 monitors the refrigerant concentration in the discharged gas in real time, avoiding waste or environmental impact caused by leakage of negative pressure refrigerant, and improving system safety; through the coordinated control of the second solenoid valve 74 and the vacuum pump 71, the exhaust can be started and stopped precisely according to the purification process, adapting to the overall operating rhythm of the machine and ensuring the stability of the refrigeration cycle.

[0039] In some specific embodiments, a cooling unit 9 is also included. The cooling unit 9 includes a second electronic expansion valve 91 and at least one cooling branch. The lower part of the purification tank 5 is connected to the input end of the second electronic expansion valve 91 through a sixth pipe 93. The input end of the cooling branch is connected to the output end of the second electronic expansion valve 91, which is used to deliver the throttled low-temperature refrigerant to the component to be cooled for cooling.

[0040] For example, one end of the sixth pipeline 93 is sealed and connected to the liquid refrigerant accumulation area at the bottom of the purification tank 5, which is the bottom area of ​​the tank where the refrigerant drips and accumulates after condensation. The other end is sealed and connected to the refrigerant input end of the second electronic expansion valve 91, and is only used to transport the condensed liquid refrigerant in the purification tank 5.

[0041] For example, the input end of each cooling branch is sealed and connected to the refrigerant output end of the second electronic expansion valve 91. Each branch is set independently and can be flexibly increased or decreased according to the number of components to be cooled. Each branch only undertakes the function of delivering low-temperature refrigerant to the corresponding component to be cooled.

[0042] For example, the components to be cooled are core components that need to be cooled during unit operation, such as compressor 1 motor, oil tank 111, frequency converter 112, etc. Each cooling branch is connected to one or a group of components to be cooled. The low-temperature refrigerant after throttling flows through the heat exchange area of ​​the component to be cooled, such as the surface or internal channel, through the branch, and the component is cooled through heat exchange.

[0043] In this embodiment, the condensed liquid refrigerant collected at the bottom of the purification tank 5 is reused and introduced into the second electronic expansion valve 91 through the sixth pipeline 93 for throttling and cooling. Then, with the help of at least one independent cooling branch, the throttled low-temperature refrigerant is directed to the component to be cooled, thereby achieving targeted cooling of the component without the need for an additional independent cooling refrigerant source, which fits the setting logic of integrating purification and cooling.

[0044] In this way, by regulating the refrigerant throttling effect through the second electronic expansion valve 91, and cooperating with the directional delivery of the cooling branch, the overheating of the components to be cooled is effectively avoided, ensuring the normal operation of the core components of the unit. The purified refrigerant is reused as the cooling medium, eliminating the need for an additional independent cooling system and refrigerant storage device, thus reducing equipment complexity and cost. At least one cooling branch can be adapted to different numbers and locations of components to be cooled, and the branch can be configured as needed to adapt to diverse cooling scenarios. The cooling unit 9 only takes the refrigerant condensed in the purification tank 5, without additionally occupying the refrigerant in the main refrigeration cycle, ensuring that the refrigeration cycle efficiency and the refrigerant purification effect are not affected.

[0045] In some specific embodiments, the cooling branch includes motor cooling branch 92, oil tank cooling branch 95 and inverter cooling branch 97; The motor cooling branch 92 is connected in series with the fifth solenoid valve 94, and its output end is connected to the suction end of the compressor 1. The oil tank cooling branch 95 is connected in series with the sixth solenoid valve 96, and its output end is connected to the balance pipe at the top of the oil tank 111. The balance pipe is connected to the suction end of the compressor 1. The inverter cooling branch 97 is connected in series with a seventh solenoid valve 98, and its output end is connected to the upper part of the evaporator 2.

[0046] For example, the fifth solenoid valve 94 is connected in series in the middle section of the motor cooling branch 92, specifically between the branch input end (connected to the output end of the second electronic expansion valve 91) and the output end (connected to the suction end of the compressor 1). It is only used to control the on / off of the motor cooling branch 92 and does not change the core function of the branch in transporting low-temperature refrigerant and reflux.

[0047] For example, the output end of the motor cooling branch 92 is sealed and connected to the suction port of the compressor 1 to ensure that the refrigerant cooled by the motor can directly enter the compressor 1 and re-participate in the refrigeration cycle.

[0048] For example, the sixth solenoid valve 96 is connected in series in the middle section of the oil tank cooling branch 95, specifically between the branch input end (connected to the output end of the second electronic expansion valve 91) and the output end (connected to the upper balance pipe of the oil tank 111), and is only used to control the on / off of the oil tank cooling branch 95.

[0049] For example, the balance pipe is a pipe installed on the upper part of the oil tank 111 for the flow of gas in the oil tank 111. Its other end is connected to the suction end of the compressor 1. The output end of the oil tank cooling branch 95 is sealed and connected to the pipe body of the balance pipe, so that the refrigerant evaporated after cooling the oil tank 111 flows to the suction end of the compressor 1 through the balance pipe.

[0050] For example, the seventh solenoid valve 98 is connected in series in the middle section of the inverter cooling branch 97, specifically between the branch input end (connected to the output end of the second electronic expansion valve 91) and the output end (connected to the upper part of the evaporator 2), and is only used to control the on and off of the inverter cooling branch 97.

[0051] For example, the upper part of the evaporator 2 is the area near the top of its internal cavity used to receive the return refrigerant. The output end of the inverter cooling branch 97 is sealed and connected to the pipeline in this area, so that the cooled refrigerant flows back to the evaporator 2 to participate in the refrigeration cycle.

[0052] This embodiment of the disclosure sets up three independent cooling branches for three core components to be cooled: the motor, the oil tank 111, and the frequency converter 112. Each branch is connected in series with a corresponding solenoid valve to achieve precise on / off control. Differentiated refrigerant return paths are set according to the operating characteristics of each component. The motor cooling branch 92 returns to the suction end of the compressor 1, the oil tank cooling branch 95 returns to the suction end of the compressor 1 via the balance pipe of the oil tank 111, and the frequency converter cooling branch 97 returns to the upper part of the evaporator 2. This allows the low-temperature refrigerant after throttling to complete its cooling function and then smoothly return to the refrigeration cycle unit, achieving targeted cooling and refrigerant recycling.

[0053] In this way, the three branches precisely match the cooling needs of different components, effectively avoiding overheating or condensation problems of the motor, oil tank 111, and inverter 112, and extending the service life of the components. The start and stop of the corresponding branches are controlled by the fifth, sixth, and seventh solenoid valves, and cooling can be carried out as needed according to the temperature of each component, avoiding ineffective energy consumption. The cooled refrigerant flows back to the refrigeration cycle unit through a dedicated path, without the need for additional discharge or replenishment of refrigerant, reducing waste. The cooling branches directly reuse the refrigerant output from the purification tank 5 and the existing refrigeration cycle loop as the return channel, without the need to add an independent return system, further simplifying the overall layout of the machine.

[0054] In some specific embodiments, the refrigerant purification device includes a control and detection unit, which includes a second temperature sensor 101 and a controller. The second temperature sensor 101 is disposed in the condenser 3 and is used to detect the condensation temperature. A first solenoid valve 103 is provided on the first pipeline 61, and a third solenoid valve 104 is provided on the second pipeline 62. The controller is electrically connected to the first solenoid valve 103, the third solenoid valve 104, and the second temperature sensor 101 respectively. When the condensation temperature detected by the second temperature sensor 101 is higher than the first set value, the controller controls the first solenoid valve 103 and the third solenoid valve 104 to open, and starts the purification process.

[0055] For example, the second temperature sensor 101 is fixedly installed in the upper region of the condenser 3, that is, the region where non-condensable gases tend to accumulate. Its detection probe is in direct contact with the refrigerant in the condenser 3 to accurately collect the condensation temperature of the refrigerant containing non-condensable gases.

[0056] For example, the first solenoid valve 103 is located in the middle section of the first pipeline 61, between the connection end of the first pipeline 61 and the connection end of the evaporator 2 and the heat exchange tube 51, and is only used to control the on / off of the low-temperature liquid refrigerant in the first pipeline 61.

[0057] For example, the third solenoid valve 104 is located in the middle section of the second pipeline 62, between the connection end of the second pipeline 62 and the upper part of the condenser 3 and the connection end of the purification tank 5, and is only used to control the on / off of the high-temperature gaseous refrigerant containing non-condensable gas in the second pipeline 62.

[0058] For example, the first set value is a threshold value preset based on the optimal condensing temperature range of the condenser 3 when the unit is operating normally. This threshold value is higher than the normal condensing temperature when there is no obvious accumulation of non-condensable gas in the condenser 3, and is used to determine that the amount of non-condensable gas accumulation has affected the heat exchange efficiency.

[0059] For example, after the controller controls the first solenoid valve 103 and the third solenoid valve 104 to open, the first pipeline 61 delivers low-temperature liquid refrigerant to the heat exchange tube 51, and the second pipeline 62 delivers high-temperature gaseous refrigerant containing non-condensable gas to the internal space of the purification tank 5. The two exchange heat in the purification tank 5 through the heat exchange tube 51, and the separation and purification process of non-condensable gas and refrigerant is officially started.

[0060] In this embodiment, a second temperature sensor 101 is installed in the condenser 3 to detect the condensation temperature in real time. A first solenoid valve 103 controls the opening and closing of the first pipeline 61, and a third solenoid valve 104 controls the opening and closing of the second pipeline 62. The controller establishes an electrical connection with the above-mentioned components and realizes signal interaction. The condensation temperature is higher than a first set value as the criterion for determining that too much non-condensable gas has accumulated. The controller is triggered to automatically open the first solenoid valve 103 and the third solenoid valve 104 to start the refrigerant purification process, thereby realizing automated triggering and precise control of purification.

[0061] In this way, without manual intervention, the system can automatically identify cases of excessive non-condensable gases through temperature detection and promptly initiate purification, thus preventing a decrease in unit efficiency due to the accumulation of non-condensable gases. The purification process can be started and stopped simply by linking core temperature parameters with key valves, making the control method simple, reliable, and reducing the risk of failure.

[0062] In some specific embodiments, the heat exchange tubes 51 are arranged vertically inside the purification tank 5, and the outlet of the second pipe 62 is set towards the outer wall of the heat exchange tube 51, so that the non-condensable gas refrigerant introduced by the second pipe 62 condenses outside the heat exchange tube 51, and the low-temperature refrigerant introduced by the first pipe 61 evaporates inside the heat exchange tube 51.

[0063] For example, the heat exchange tubes 51 are arranged in parallel and spaced vertically along the vertical direction of the purification tank 5. The two ends of each heat exchange tube 51 are fixedly connected to the corresponding interface on the inner wall of the purification tank 5, forming a neat bundle of heat exchange tubes 51 to ensure smooth flow of refrigerant inside and outside the tubes.

[0064] For example, the outlet end of the second pipeline 62 extends to the side area of ​​the heat exchange tube 51 inside the purification tank 5. The outlet end face is set opposite to the outer wall of the heat exchange tube 51, and the central axis of the outlet forms an angle of 30°-90° with the tangent direction of the outer wall of the heat exchange tube 51, so as to ensure that the outgoing refrigerant containing non-condensable gas can directly blow or contact the outer wall of the heat exchange tube 51.

[0065] For example, after the non-condensable gaseous refrigerant is cooled by contact with the outer wall of the heat exchange tube 51, the refrigerant components condense into liquid and drip down along the outer wall of the heat exchange tube 51, eventually accumulating in the lower region of the purification tank 5.

[0066] For example, the low-temperature liquid refrigerant introduced into the first pipe 61 absorbs heat in the heat exchange tube 51 and evaporates into a gaseous state. It flows out from the tube outlet end along the internal channel of the heat exchange tube 51 and then flows back to the refrigeration cycle unit through the refrigerant return structure 8.

[0067] In this embodiment, the heat exchange tubes 51 are arranged vertically within the purification tank 5 to increase the contact area between the refrigerant containing non-condensable gases and the low-temperature refrigerant. Simultaneously, the outlet of the second pipeline 62 is oriented towards the outer wall of the heat exchange tubes 51, allowing the refrigerant containing non-condensable gases to directly act on the outer wall of the heat exchange tubes 51, forming an indirect heat exchange mode of condensation outside the tubes and evaporation inside the tubes. This ensures efficient heat exchange between the two refrigerants, thereby achieving the separation of non-condensable gases and refrigerants.

[0068] In this way, the vertical arrangement of heat exchange tubes 51 maximizes the use of the internal space of the purification tank 5 and increases the contact area of ​​the refrigerant; the outlet of the second pipe 62 is oriented towards the tube wall, so that the refrigerant containing non-condensable gas accurately covers the heat exchange surface, ensuring sufficient heat exchange; the directional flow setting of external condensation and internal evaporation allows the refrigerant components in the refrigerant containing non-condensable gas to liquefy quickly, and the non-condensable gas to be efficiently separated and collected in the upper part of the tank; the liquid refrigerant after external condensation of heat exchange tubes 51 can drip naturally along the tube wall, which is convenient for collection in the lower part of the purification tank 5, providing conditions for subsequent cooling and reuse; the vertical arrangement is compatible with the cavity shape of the purification tank 5, without the need for additional modification of the tank structure, simplifying installation and layout.

[0069] In some specific embodiments, the refrigerant purification device includes a control and detection unit, which includes a first temperature sensor 105 disposed in the refrigerant reflux structure 8 for detecting the temperature of the refrigerant after heat exchange and evaporation. When the temperature detected by the first temperature sensor 105 is lower than the fifth set value, the controller controls the third solenoid valve 104 to close, and after a delay of t1, closes the first solenoid valve 103, and then controls the second solenoid valve 74 and the vacuum pump 71 to open and discharge non-condensable gas. When the discharge time reaches t2 or the refrigerant leakage sensor 73 alarms, the vacuum pump 71 and the second solenoid valve 74 are shut off.

[0070] For example, the first temperature sensor 105 is fixedly installed on the pipeline of the refrigerant return structure 8 near the outlet end of the heat exchange tube 51. Its detection probe is in direct contact with the gaseous refrigerant in the return structure, and is used to accurately collect the temperature of the refrigerant after evaporation in the heat exchange tube 51 and about to return to the refrigeration cycle unit.

[0071] For example, the fifth setting value is a threshold value preset based on the standard temperature range of the refrigerant after heat exchange and evaporation under normal purification conditions of the unit. When the detected temperature is lower than the threshold value, it indicates that a large amount of non-condensable gas has accumulated in the purification tank 5 and covered the surface of the heat exchange tube 51, resulting in insufficient heat exchange, and the exhaust process needs to be started.

[0072] For example, the delay t1 is the time reserved to allow the high-temperature gaseous refrigerant containing non-condensable gases remaining in the purification tank 5 to fully condense into a liquid state. Its duration can be flexibly adjusted according to the volume of the purification tank 5 and the refrigerant condensation rate to ensure that the condensable refrigerant components in the tank condense as much as possible before the first solenoid valve 103 is closed.

[0073] For example, t2 is the time required for complete discharge of non-condensable gases, which is estimated in advance based on the rated volume of the purification tank 5 and the exhaust rate of the vacuum pump 71. The duration is adjustable to ensure that non-condensable gases are fully discharged even when there is no sensor alarm.

[0074] For example, the alarm condition of the refrigerant leakage sensor 73 is that it detects that the concentration of refrigerant in the exhaust gas is higher than a preset safety threshold. When the threshold is reached, it indicates that the amount of refrigerant leakage during the exhaust process exceeds the standard, and the exhaust must be stopped immediately to avoid refrigerant waste and environmental impact.

[0075] In this embodiment, the temperature of the refrigerant after heat exchange and evaporation in the refrigerant reflux structure 8, detected by the first temperature sensor 105, is used as the basis for determining that the non-condensable gas has accumulated sufficiently. The controller controls the timing of the operation of the third solenoid valve 104, the first solenoid valve 103 after a delay of t1, and the second solenoid valve 74 and the vacuum pump 71. A time t1 is reserved to allow the refrigerant containing non-condensable gas remaining in the purification tank 5 to fully condense, and then the non-condensable gas is discharged by the vacuum pump 71. At the same time, the discharge time t2 and the alarm of the refrigerant leakage sensor 73 are used as the conditions for stopping the discharge, so as to achieve accurate and safe discharge of non-condensable gas and avoid refrigerant waste.

[0076] In this way, the first temperature sensor 105 directly reflects the heat exchange effect. When the temperature is lower than the fifth set value, it indicates that the non-condensable gas has affected the heat exchange, ensuring that the exhaust timing matches the actual needs and avoiding exhausting too early or too late. The delay t1 is set to reserve condensation time for the remaining mixed gas containing refrigerant in the purification tank 5, reducing the refrigerant entrainment loss during exhaust and meeting the needs of refrigerant recycling. Without manual intervention, the controller accurately controls the start and stop of the valve and vacuum pump 71 according to the preset logic, improving the ease of operation and exhaust reliability. The dual stop conditions ensure that the non-condensable gas is completely discharged and avoid excessive refrigerant leakage.

[0077] This disclosure also provides an air conditioner, including the aforementioned refrigerant purification device, and further including a controller and a component to be cooled. The component to be cooled includes the motor of the compressor 1, the oil tank 111 and the frequency converter 112. Each cooling branch of the cooling unit 9 is adapted to the corresponding component to be cooled, and is used to perform targeted cooling on the component to be cooled. The controller is electrically connected to the first electronic expansion valve 4, the second electronic expansion valve 91, the vacuum pump 71, the refrigerant leakage sensor 73, the first temperature sensor 105, the second temperature sensor 101, the first solenoid valve 103, the second solenoid valve 74, the third solenoid valve 104, the fourth solenoid valve 65, the fifth solenoid valve 94, the sixth solenoid valve 96, and the seventh solenoid valve 98, respectively, and is used to control the start-up, shutdown, and operating status of each component according to the detection signals, so as to achieve coordinated control of purification and cooling.

[0078] In this way, by integrating the aforementioned refrigerant purification device, non-condensable gases in the negative pressure refrigerant can be efficiently separated, preventing the heat exchange area of ​​the condenser 3 from being occupied and ensuring the cooling capacity and energy efficiency of the air conditioner. At the same time, the dedicated branch of the cooling unit 9 can be used to specifically cool the compressor 1 motor, oil tank 111, and inverter 112, effectively preventing components from overheating or condensing, and ensuring the reliable operation of core components. Meanwhile, the controller, through electrical connection with each electronic expansion valve, vacuum pump 71, sensor, and solenoid valve, can accurately control the start-up, shutdown, and operating status of each component based on the detection signals, achieving coordinated adaptation between the purification process and cooling requirements. This eliminates the need for an additional independent system, simplifies the air conditioner structure, and reduces energy consumption.

[0079] This disclosure further provides a control method applied to the aforementioned air conditioner, including a purification control method, the method comprising: Acquisition steps: Acquire the detection signals of each temperature sensor and refrigerant leakage sensor 73. The detection signals include the condenser 3 condensing temperature, refrigerant return temperature, motor temperature, oil tank 111 temperature, inverter 112 temperature, and refrigerant concentration in the exhaust gas. Linkage control steps: Based on the detection signal, the linkage control of the refrigerant introduction, heat exchange, and non-condensable gas discharge process of the purification tank 5 and the start-stop process of the cooling branch of the cooling unit 9 are coordinated to achieve the coordinated operation of non-condensable gas separation and cooling of the components to be cooled.

[0080] In this way, by acquiring multi-dimensional detection signals such as the condenser temperature of condenser 3, refrigerant return temperature, motor / oil tank 111 / inverter 112 temperature, and refrigerant concentration in the exhaust gas, the entire process of refrigerant introduction, heat exchange, and non-condensable gas discharge in purification tank 5 is precisely linked with the start and stop of each cooling branch of cooling unit 9. This ensures efficient separation of non-condensable gas to maintain the heat exchange efficiency of condenser 3 and guarantee the unit's cooling capacity and energy efficiency. It also allows for the start and stop of cooling branches as needed to specifically cool the components to be cooled, preventing components from overheating or condensation. This makes purification and cooling work together to meet the unit's operating requirements and simplifies the control logic.

[0081] In some specific implementations, the refrigerant introduction and heat exchange control of purification tank 5 in the linkage control steps include: When the condensation temperature T2 detected by the second temperature sensor 101 is higher than the first set value, it is determined that the non-condensable gas in the condenser 3 is excessively accumulated. The first solenoid valve 103, the third solenoid valve 104, and the fourth solenoid valve 65 are opened synchronously. Through the ejector device 63 and the height difference, the low-temperature liquid refrigerant in the evaporator 2 is introduced into the heat exchange tube 51 of the purification tank 5. At the same time, the high-temperature gaseous refrigerant containing non-condensable gas in the upper part of the condenser 3 is introduced into the internal space of the purification tank 5 so that the refrigerant inside and outside the tube can exchange heat.

[0082] In this way, the condensing temperature T2 of the condenser 3 is accurately detected by the second temperature sensor 101. When T2 is higher than the first set value, it is automatically determined that the non-condensable gas is accumulating in excess, without the need for manual intervention. Then, the first solenoid valve 103, the third solenoid valve 104, and the fourth solenoid valve 65 are opened simultaneously. With the help of the negative pressure suction of the ejector device 63 and the gravitational potential energy of the height difference, the low-temperature liquid refrigerant is stably introduced without power. At the same time, the high-temperature gaseous refrigerant containing non-condensable gas is directionally introduced into the purification tank 5, ensuring that the two refrigerants quickly form efficient heat exchange inside and outside the heat exchange tube 51, laying a solid foundation for the subsequent full separation of non-condensable gas and refrigerant, effectively preventing non-condensable gas from occupying the heat exchange area of ​​the condenser 3, and ensuring the efficiency of the refrigeration cycle.

[0083] In some specific implementations, the non-condensable gas discharge control of purification tank 5 in the linkage control steps includes: When the refrigerant reflux temperature T1 detected by the first temperature sensor 105 is lower than the fifth set value, it is determined that the non-condensable gas in the purification tank 5 has accumulated to the preset amount. Control the third solenoid valve 104 and the fourth solenoid valve 65 to close, and delay for time t1 to condense and purify the remaining refrigerant in the tank 5. Close the first solenoid valve 103, open the second solenoid valve 74 and vacuum pump 71 to discharge non-condensable gas; When the discharge time reaches t2 or the refrigerant concentration detected by the refrigerant leakage sensor 73 is higher than the set threshold, the vacuum pump 71 and the second solenoid valve 74 are shut off.

[0084] In this way, the non-condensable gas discharge control detects the refrigerant return temperature T1 through the first temperature sensor 105. When T1 is lower than the fifth set value, it is accurately determined that the non-condensable gas in the purification tank 5 has accumulated to the preset amount. Then, the control is orderly controlled by closing the third solenoid valve 104 and the fourth solenoid valve 65, delaying for t1 to condense the remaining refrigerant, closing the first solenoid valve 103, and opening the second solenoid valve 74 and the vacuum pump 71 to discharge the gas. This not only minimizes the refrigerant entrainment loss during discharge by delaying for t1, but also achieves efficient discharge of non-condensable gas by using the vacuum pump 71. Finally, the discharge is terminated by the dual conditions of discharge time t2 and refrigerant concentration exceeding the set threshold. This effectively avoids the risk of excessive accumulation of non-condensable gas affecting heat exchange, refrigerant waste and leakage, and ensures that the purification process is thorough and safe.

[0085] In some specific implementations, the cooling branch control of cooling unit 9 in the linkage control step includes: Determine whether the motor temperature T3 detected by the third temperature sensor 113, the oil tank temperature T4 detected by the fourth temperature sensor 115, and the inverter temperature T5 detected by the fifth temperature sensor 114 are higher than the corresponding set values. If any temperature exceeds the corresponding set value, the second electronic expansion valve 91 is opened, and the solenoid valve of the corresponding cooling branch is opened simultaneously, so that the refrigerant condensed in the purification tank 5 is delivered to the component to be cooled after throttling.

[0086] In this way, the cooling branch control accurately detects the temperature of the motor, oil tank 111, and frequency converter 112 through the third temperature sensor 113, the fourth temperature sensor 115, and the fifth temperature sensor 114, respectively. When the temperature of any component is higher than the corresponding set value, the second electronic expansion valve 91 is automatically opened and the solenoid valve of the corresponding cooling branch is opened simultaneously. The refrigerant condensed in the purification tank 5 is throttled to form a low-temperature refrigerant, which is used to cool the overheated components. This effectively avoids the motor, oil tank 111, and frequency converter 112 from being affected by overheating or condensation, and eliminates the need for additional independent cooling media and systems, simplifying the overall structure and enabling on-demand response to cooling needs.

[0087] In some specific implementations, the specific control logic of the cooling branch is as follows: When T3 is higher than the second set value, the second electronic expansion valve 91 and the fifth solenoid valve 94 are opened, and the refrigerant flows back to the suction end of the compressor 1 after cooling the motor through the motor cooling branch 92. When T4 is higher than the third set value, the second electronic expansion valve 91 and the sixth solenoid valve 96 are opened. The refrigerant cools the lubricating oil and bearings through the oil tank cooling branch 95 and then flows back to the suction end of the compressor 1 through the balance pipe. When T5 is higher than the fourth set value, the second electronic expansion valve 91 and the seventh solenoid valve 98 are opened, and the refrigerant flows back to the upper part of the evaporator 2 after cooling the inverter 112 module and internal space through the inverter cooling branch 97. When T3, T4, and T5 are all lower than their respective set values, the second electronic expansion valve 91 and the corresponding solenoid valve are closed.

[0088] In this way, the cooling branch control logic accurately monitors the motor temperature T3, oil tank 111 temperature T4, and inverter 112 temperature T5. Using the second, third, and fourth set values ​​as trigger conditions, it opens the second electronic expansion valve 91 and the corresponding fifth, sixth, and seventh solenoid valves 94, 96, and 98 as needed. The refrigerant condensed in the purification tank 5 is throttled to form a low-temperature refrigerant, which is used to cool the motor, lubricating oil and bearings, inverter 112 module and internal space. After cooling, the refrigerant flows back to the suction end of compressor 1 or the upper part of evaporator 2 through dedicated paths to achieve refrigerant recycling. When the temperature of each component is lower than the corresponding set value, the relevant valves and electronic expansion valves are closed in time to avoid ineffective cooling energy consumption. This ensures that the components to be cooled do not overheat or condense, guaranteeing operational reliability, and eliminates the need for an additional independent cooling system, simplifying the overall structure.

[0089] In some specific implementations, the control logic for coordinated operation includes: When the purification trigger condition (T2 > first set value) and the cooling trigger condition (at least one of T3 > second set value, T4 > third set value, T5 > fourth set value) are met simultaneously, the refrigerant introduction and heat exchange process of purification tank 5 is started first. If the temperature of the component to be cooled is still higher than the corresponding set value, the cooling branch is opened simultaneously, and the opening of the second electronic expansion valve 91 is adjusted to prioritize the flow of refrigerant required for purification. When the purification tank 5 enters the non-condensable gas discharge stage, the cooling branch is kept running normally. If the refrigerant level in the purification tank 5 is lower than the preset threshold, the opening of the second electronic expansion valve 91 is appropriately reduced to avoid insufficient refrigerant supply.

[0090] In this way, when the purification and cooling trigger conditions are met simultaneously, the refrigerant introduction and heat exchange process of purification tank 5 is initiated first to ensure efficient separation of non-condensable gases and maintain the heat exchange efficiency of condenser 3. After the purification process stabilizes, if the components to be cooled are still overheating, the cooling branch is opened simultaneously, and the opening of the second electronic expansion valve 91 is adjusted to prioritize the refrigerant flow required for purification, avoiding interference from cooling demand with the purification effect. When purification tank 5 enters the non-condensable gas discharge stage, the cooling branch is kept running normally, and the opening of the second electronic expansion valve 91 is dynamically reduced according to the refrigerant level in purification tank 5 to prevent insufficient refrigerant supply from affecting the purification and refrigeration cycle. Ultimately, precise coordination between purification separation and component cooling is achieved, which not only ensures the unit's cooling capacity and energy efficiency but also avoids overheating of core components.

[0091] In some specific implementations, the value of t1 ranges from 10 to 60 seconds, the value of t2 ranges from 30 to 180 seconds, the first setting value is 40 to 60°C, and the fifth setting value is 5 to 15°C.

[0092] In this way, based on the above reasonable temperature range, the triggering time for excessive accumulation of non-condensable gas in condenser 3 and accumulation of non-condensable gas in purification tank 5 to a preset amount can be accurately determined, avoiding misjudgment or delayed triggering; at the same time, the delayed condensation time t1 and the non-condensable gas discharge time t2 are limited, which not only ensures that the remaining refrigerant in purification tank 5 is fully condensed to reduce emission losses, but also adapts to the capacity of purification tank 5 and the speed of vacuum pump 71 to achieve efficient removal of non-condensable gas. Combined with the whole set of purification and cooling coordinated control logic, the accuracy and reliability of the device operation are further improved.

[0093] To better understand the technical solutions of the embodiments of this disclosure, the following exemplary description is provided: The refrigerant purification device provided in this embodiment solves the problem of non-condensable gases accumulating in the condenser 3 due to the use of negative pressure refrigerant, thereby reducing cooling capacity and energy efficiency. It also solves the cooling problems of the motor, bearings, and inverter 112, ensuring continuous and stable operation of the unit. Furthermore, by combining the purification device and cooling system, the overall structure is simplified, improving unit stability and overall efficiency.

[0094] Specifically, the refrigerant purification device includes a purification tank 5, which draws low-temperature refrigerant from the evaporator 2 to condense the high-temperature gaseous refrigerant mixed with non-condensable gases taken from the condenser 3, thereby separating the non-condensable gases from the refrigerant and solving the refrigerant purification problem of the negative pressure refrigerant unit.

[0095] The following explanation is in conjunction with the accompanying drawings. Figure 1The diagram shows a refrigerant purification system according to an embodiment of this disclosure. The system includes: a compressor 1, an evaporator 2, a condenser 3, an ejector device 63, a first electronic expansion valve 4, a purification tank 5, a vacuum pump 71, a first temperature sensor for detecting the temperature of the cooled refrigerant, a second temperature sensor 101 for detecting the condensation temperature, a first solenoid valve 103 for controlling the opening and closing of the pipeline from the evaporator 2 to the purification tank 5, a second solenoid valve 74 for controlling the opening and closing of the pipeline for discharging non-condensable gas, a third solenoid valve 104 for controlling the opening and closing of the refrigerant pipeline for taking mixed non-condensable gas, a fourth solenoid valve 65 for controlling the opening and closing of the ejector, and a refrigerant leakage sensor 73 for detecting the refrigerant concentration in the discharged non-condensable gas.

[0096] Appendix Figure 2 The diagram shows a cooling system according to an embodiment of this disclosure. The system includes: a compressor 1, an evaporator 2, a condenser 3, an electronic expansion valve 1, a frequency converter 112, an oil tank 111, a second electronic expansion valve 91 for throttling and separating the refrigerant after condensation, a fifth solenoid valve 94 for controlling the opening and closing of the cooling motor pipeline, a sixth solenoid valve 96 for controlling the opening and closing of the cooling oil tank 111 pipeline, a seventh solenoid valve 98 for controlling the cooling pipeline of the frequency converter 112, a third temperature sensor 113 for detecting the motor temperature in the compressor 1, a fourth temperature sensor 115 for detecting the temperature of the oil tank 111, and a fifth temperature sensor 114 for detecting the temperature of the frequency converter 112.

[0097] Appendix Figure 1In this refrigeration cycle system, compressor 1, evaporator 2, first electronic expansion valve 4, and condenser 3 form the refrigeration cycle system. After being throttled by the first electronic expansion valve 4, the refrigerant in the section from the evaporator 2 to the suction end of compressor 1 is in a state below atmospheric pressure. Air and water vapor in this section enter the refrigeration cycle system, mix with the refrigerant, and enter compressor 1 for compression before entering condenser 3. In condenser 3, the high-temperature and high-pressure refrigerant gas condenses into liquid on the surface of heat exchange tube 51 and then leaves condenser 3. However, some gas cannot condense and accumulates in condenser 3 as the refrigeration cycle continues. The amount of non-condensable gas increases and spreads on the surface of heat exchange tube 51, occupying the refrigerant's space and reducing the contact area between the refrigerant and water. This reduces the heat exchange of the refrigerant, ultimately reducing the unit's cooling capacity. At the same time, the heat carried away by the cooling water from the refrigerant decreases, thus increasing the condensing temperature and affecting the overall energy efficiency of the unit. At this time, the second temperature sensor 101 detects that the condensation temperature T2 is higher than the set value, and determines that too much non-condensable gas has accumulated. It then opens the first solenoid valve 103, the third solenoid valve 104, and the fourth solenoid valve 65, drawing high-temperature, high-pressure liquid from the condenser 3. This liquid is then injected through the ejector device 63 to the purification tank 5. The inlet position of the purification tank 5 must be lower than the outlet position of the evaporator 2 to ensure that the low-temperature, low-pressure liquid refrigerant in the evaporator 2 is properly contained within the ejector device 63. Under the influence of the weight due to the height difference, it can enter the heat exchange tubes 51 arranged vertically in the purification tank 5 without power. Secondly, the high-temperature and high-pressure gaseous refrigerant mixed with non-condensable gases in the upper part of the condenser 3 also enters the purification tank 5. The two exchange heat through the heat exchange tubes 51. The refrigerant inside the tube absorbs heat and evaporates, returning to the suction end of the compressor 1 through the pipeline, and then returning to the refrigeration cycle. The refrigerant outside the tube condenses into gas and drips down along the heat exchange tubes 51, accumulating at the bottom of the purification tank 5. The remaining non-condensable gases accumulate at the top of the purification tank 5. As the amount of non-condensable gas in the purification tank 5 increases, it begins to cover the surface of the heat exchange tubes 51 arranged vertically, affecting the heat exchange effect. Once the temperature T1 of the evaporated refrigerant is detected to be lower than the set value, it is determined that there is enough non-condensable gas in the purification tank 5. The third solenoid valve 104 and the fourth solenoid valve 65 are closed, and the process is run for time t1 to condense the remaining refrigerant in the purification tank 5 as much as possible. Then, the first solenoid valve 103 is closed, and the second solenoid valve 74 and the vacuum pump 71 are opened to discharge the non-condensable gas in the purification tank 5 into the atmosphere. Time t2 is set (the discharge time is estimated based on the capacity of the purification tank 5 and the speed of the vacuum pump 71, and is adjustable). When time t2 is reached or the refrigerant leakage sensor 73 alarms, the vacuum pump 71 and the second solenoid valve 74 are closed.

[0098] Appendix Figure 2If a temperature of T3, T4, or T5 is detected to be higher than the set value, the corresponding fifth solenoid valve 94, sixth solenoid valve 96, and seventh solenoid valve 98 will be opened, and the second electronic expansion valve 91 will be opened. The high-temperature and high-pressure liquid refrigerant condensed in the purification tank 5 will be throttled into a low-temperature and low-pressure refrigerant, which will be used to cool the motor, oil tank 111, or frequency converter 112 that is overheating.

[0099] This solves the refrigerant purification problem of negative pressure refrigerant units; it also solves the cooling problem of new refrigerant units; and by combining the purification and cooling systems of new refrigerant units, it simplifies the overall structure and improves the stability of the units.

[0100] The above description is merely a specific embodiment of the present invention, enabling those skilled in the art to understand or implement the invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the invention. Therefore, the present invention is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A refrigerant purification device, characterized in that, include: The refrigeration cycle unit includes a compressor, an evaporator, a condenser, and a first electronic expansion valve. The compressor, evaporator, first electronic expansion valve, and condenser are connected in sequence through pipelines to form a closed refrigeration cycle. The refrigerant flowing in the refrigeration cycle unit is a negative pressure refrigerant. A purification tank is provided with heat exchange tubes for exchanging heat between a refrigerant containing non-condensable gases and a low-temperature refrigerant to separate the non-condensable gases. The refrigerant introduction structure includes a first pipe and a second pipe. The first pipe is used to introduce the low-temperature liquid refrigerant in the evaporator into the heat exchange tube, and the second pipe is used to introduce the high-temperature gaseous refrigerant containing non-condensable gases in the upper part of the condenser into the internal space of the purification tank. A non-condensable gas discharge structure is provided, which is connected to the upper part of the purification tank and is used to discharge the separated non-condensable gas. A refrigerant reflux structure is provided, which is connected to the heat exchange tube and is used to reflux the refrigerant after heat exchange and evaporation back to the refrigeration cycle unit.

2. The refrigerant purification device according to claim 1, characterized in that, The refrigerant introduction structure also includes an ejector device, which is connected in series with the second pipeline and is connected to the first pipeline through a third pipeline. A fourth solenoid valve is provided on the third pipeline. The connection end of the first pipeline to the evaporator is higher than the connection end of the first pipeline to the heat exchange tube, so as to use the height difference in conjunction with the ejector device to realize the non-powered transport of low temperature liquid refrigerant.

3. The refrigerant purification device according to claim 1, characterized in that, The non-condensable gas discharge structure includes a vacuum pump, a fifth pipeline, and a refrigerant leakage sensor. One end of the fifth pipeline is connected to the upper part of the purification tank, and the other end is connected to the atmosphere. The vacuum pump and the second solenoid valve are connected in series in the fifth pipeline. The refrigerant leakage sensor is located at the outlet end of the fifth pipeline and is used to detect the concentration of refrigerant in the discharged gas.

4. The refrigerant purification device according to claim 1, characterized in that, It also includes a cooling unit, which includes a second electronic expansion valve and at least one cooling branch. The lower part of the purification tank is connected to the input end of the second electronic expansion valve through a sixth pipeline, and the input end of the cooling branch is connected to the output end of the second electronic expansion valve, for delivering the throttled low-temperature refrigerant to the component to be cooled for cooling.

5. The refrigerant purification device according to claim 4, characterized in that, The cooling branch includes a motor cooling branch, an oil tank cooling branch, and a frequency converter cooling branch; The motor cooling branch is connected in series with a fifth solenoid valve, and its output end is connected to the suction end of the compressor. The oil tank cooling branch is connected in series with a sixth solenoid valve, the output end of which is connected to the balance pipe at the top of the oil tank, and the balance pipe is connected to the suction end of the compressor. The inverter cooling branch is connected in series with a seventh solenoid valve, and its output end is connected to the upper part of the evaporator.

6. The refrigerant purification apparatus according to claim 1, characterized in that, The refrigerant purification device includes a control and detection unit, which includes a second temperature sensor and a controller. The second temperature sensor is located in the condenser and is used to detect the condensation temperature. The first pipeline is equipped with a first solenoid valve, and the second pipeline is equipped with a third solenoid valve. The controller is electrically connected to the first solenoid valve, the third solenoid valve, and the second temperature sensor respectively. When the condensation temperature detected by the second temperature sensor is higher than the first set value, the controller controls the first solenoid valve and the third solenoid valve to open and start the purification process.

7. The refrigerant purification apparatus according to claim 1, characterized in that, The heat exchange tubes are arranged vertically inside the purification tank. The outlet of the second pipe is positioned facing the outer wall of the heat exchange tube, so that the refrigerant containing non-condensable gas introduced through the second pipe condenses outside the heat exchange tube, while the low-temperature refrigerant introduced through the first pipe evaporates inside the heat exchange tube.

8. The refrigerant purification apparatus according to claim 3, characterized in that, The refrigerant purification device includes a control and detection unit, which includes a first temperature sensor disposed in the refrigerant reflux structure for detecting the temperature of the refrigerant after heat exchange and evaporation. When the temperature detected by the first temperature sensor is lower than the fifth set value, the controller controls the third solenoid valve to close, and after a delay of t1, closes the first solenoid valve, and then controls the second solenoid valve and the vacuum pump to open to discharge non-condensable gas. When the discharge time reaches t2 or the refrigerant leakage sensor alarms, shut down the vacuum pump and the second solenoid valve.

9. An air conditioner, characterized in that, The device includes a refrigerant purification apparatus as described in any one of claims 1-8, and further includes a controller and a component to be cooled. The component to be cooled includes a compressor motor, an oil tank, and a frequency converter. Each cooling branch of the cooling unit is adapted to the corresponding component to be cooled for targeted cooling of the component to be cooled. The controller is electrically connected to the first electronic expansion valve, the second electronic expansion valve, the vacuum pump, the refrigerant leak sensor, the first temperature sensor, the second temperature sensor, the first solenoid valve, the second solenoid valve, the third solenoid valve, the fourth solenoid valve, the fifth solenoid valve, the sixth solenoid valve, and the seventh solenoid valve, respectively, and is used to control the start-up, shutdown, and operating status of each component according to the detection signals, so as to achieve coordinated control of purification and cooling.

10. A control method, characterized in that, The air conditioner as described in claim 9 includes a purification control method, the method comprising: Acquisition Steps: Acquire the detection signals from each temperature sensor and refrigerant leak sensor. The detection signals include condenser condensing temperature, refrigerant return temperature, motor temperature, oil tank temperature, inverter temperature, and refrigerant concentration in the exhaust gas. Linkage control steps: Based on the detection signal, the linkage control of the refrigerant introduction, heat exchange, non-condensable gas discharge process of the purification tank and the start-stop process of the cooling branch of the cooling unit are coordinated to achieve the coordinated operation of non-condensable gas separation and cooling of the components to be cooled.

11. The control method according to claim 10, characterized in that, The linkage control steps include: refrigerant introduction and heat exchange control of the purification tank. When the condensation temperature T2 detected by the second temperature sensor is higher than the first set value, it is determined that there is an excessive accumulation of non-condensable gas in the condenser. The first, third, and fourth solenoid valves are opened synchronously. Through the ejector device and the height difference, the low-temperature liquid refrigerant in the evaporator is introduced into the heat exchange tube of the purification tank. At the same time, the high-temperature gaseous refrigerant containing non-condensable gases in the upper part of the condenser is introduced into the internal space of the purification tank so that the refrigerant inside and outside the tube can exchange heat.

12. The control method according to claim 11, characterized in that, The linkage control steps include controlling the discharge of non-condensable gases from the purification tank: When the refrigerant reflux temperature T1 detected by the first temperature sensor is lower than the fifth set value, it is determined that the non-condensable gas in the purification tank has accumulated to the preset amount. Control the third and fourth solenoid valves to close, and delay for time t1 to condense and purify the remaining refrigerant in the tank. Close the first solenoid valve, open the second solenoid valve and vacuum pump to discharge non-condensable gases; When the discharge time reaches t2 or the refrigerant concentration detected by the refrigerant leakage sensor is higher than the set threshold, the vacuum pump and the second solenoid valve are shut off.

13. The control method according to claim 10, characterized in that, In the linkage control steps, the cooling branch control of the cooling unit includes: Determine whether the motor temperature T3 detected by the third temperature sensor, the oil tank temperature T4 detected by the fourth temperature sensor, and the inverter temperature T5 detected by the fifth temperature sensor are higher than the corresponding set values. If any temperature exceeds the corresponding set value, the second electronic expansion valve is opened, and the solenoid valve of the corresponding cooling branch is opened simultaneously, so that the refrigerant condensed in the purification tank is delivered to the component to be cooled after throttling.

14. The control method according to claim 13, characterized in that, The specific control logic for the cooling branch is as follows: When T3 is higher than the second set value, the second electronic expansion valve and the fifth solenoid valve are opened, and the refrigerant flows back to the compressor suction end after cooling the motor through the motor cooling branch. When T4 is higher than the third set value, the second electronic expansion valve and the sixth solenoid valve are opened. The refrigerant cools the lubricating oil and bearings through the oil tank cooling branch and then flows back to the compressor suction end through the balance pipe. When T5 is higher than the fourth set value, the second electronic expansion valve and the seventh solenoid valve are opened, and the refrigerant flows back to the upper part of the evaporator after cooling the inverter module and internal space through the inverter cooling branch. When T3, T4, and T5 are all lower than their respective set values, the second electronic expansion valve and the corresponding solenoid valve are closed.

15. The control method according to claim 10, characterized in that, The control logic for the coordinated operation includes: When both the purification trigger condition and the cooling trigger condition are met, the refrigerant introduction and heat exchange process of the purification tank will be started first. If the temperature of the component to be cooled is still higher than the corresponding set value, the cooling branch is opened simultaneously, and the opening of the second electronic expansion valve is adjusted to prioritize the flow of refrigerant required for purification. When the purification tank enters the non-condensable gas discharge stage, keep the cooling branch running normally. If the refrigerant level in the purification tank is lower than the preset threshold, appropriately reduce the opening of the second electronic expansion valve to avoid insufficient refrigerant supply.

16. The control method according to claim 12, characterized in that, The value of t1 is in the range of 10 to 60 seconds, the value of t2 is in the range of 30 to 180 seconds, the first set value is 40 to 60°C, and the fifth set value is 5 to 15°C.

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