Refrigerant cycle system coupled with dual-source evaporator and multi-working-condition regulation method thereof

Abstract

The application discloses a refrigerant circulation system coupled with double-source evaporators and a multi-working-condition regulation method thereof, and proposes a system integrating air-cooled and water-cooled double evaporators and intelligent valve regulation. The system realizes efficient multi-mode operation through optimization of a refrigerant circulation path and working-condition switching logic, including a heating mode, a winter defrosting mode, a summer refrigeration / ice-making mode and a summer ice-melting mode. The innovative regulation method enables the winter defrosting and summer ice-melting processes to be completed without interrupting the main operation cycle, thereby significantly improving the continuity, energy efficiency and environmental adaptability of the system.

Description

Technical Field

[0001] This invention relates to the field of heat pump technology, and in particular to a refrigerant circulation system with dual-source evaporators coupled and its multi-condition control method. Background Technology

[0002] Current heat pump technology still faces significant limitations in addressing seasonal demand fluctuations. Traditional systems often employ a single heat source, either air-cooled or water-cooled. Outdoor air temperature and humidity vary considerably depending on region, season, and diurnal frequency, significantly impacting the heat pump's heating capacity and coefficient of performance (COP). In areas with low winter temperatures or relatively humid outdoor air, air-cooled heat pump systems are prone to frost formation, leading to a significant reduction in overall system efficiency. Air has a low heat capacity, requiring a larger volume of air to obtain the same amount of heat. Water source heat pumps also face other challenges, as their performance is highly dependent on the stability of the water source temperature. While water temperatures are generally more stable than air temperatures, fluctuations in water temperature within extreme climates or specific water bodies can still cause a significant decrease in the heat pump's heating / cooling capacity and efficiency, preventing it from reaching its design operating conditions.

[0003] To overcome the shortcomings of a single heat source, the concept of a "dual-source heat pump" system emerged. However, existing dual-source heat pump technology still suffers from the following key deficiencies in practical applications, severely restricting its performance improvement and widespread application. Existing solutions often employ independent parallel or simple series loop designs, with air-cooled and water-cooled evaporators frequently forming self-contained subsystems. Existing dual-source systems generally lack efficient, uninterrupted defrosting / ice-melting mechanisms. When the air-cooled evaporator frosts and requires defrosting, the heating cycle typically needs to be stopped, switching to reverse-cycle defrosting or electric auxiliary heating defrosting mode, resulting in heating interruption, decreased comfort, and a significant increase in energy consumption. Similarly, in summer ice-making conditions, if the evaporator is at risk of freezing, there is a lack of effective, uninterrupted ice-melting methods. Key components within the system (such as the liquid receiver and evaporator) have limited functionality. Traditional liquid receivers are only used to store refrigerant balance flow and lack integrated functions such as preheating return water, preventing subcooled water ice crystals, and gas-liquid separation flash evaporation. This limits further improvements in system energy efficiency and increases the difficulty and risk of handling special operating conditions. Existing designs struggle to seamlessly and intelligently switch and optimize operation across multiple core operating conditions within a compact and efficient system, including: efficient heating, uninterrupted winter defrosting, flexible summer cooling / ice making, and safe and rapid summer ice melting.

[0004] In summary, existing heat pump technologies, especially dual-source heat pump systems, face several core shortcomings when dealing with complex and variable operating conditions throughout the year. These include system redundancy, low mode switching efficiency, interruption of the main cycle during critical processes (defrosting / de-icing), low functional integration, and the inability to achieve efficient and continuous multi-mode operation. These shortcomings directly lead to problems such as low system energy efficiency, poor operational stability, unsatisfactory user experience, and increased maintenance costs, limiting the application potential and energy-saving benefits of dual-source heat pump technology in a wider range of scenarios. Therefore, there is an urgent need to develop a new type of highly integrated, intelligently controlled dual-source heat pump system and its control method that can achieve uninterrupted operation of critical processes. Summary of the Invention

[0005] The main objective of this invention is to provide a refrigerant circulation system with dual-source evaporator coupling and its multi-condition control method, aiming to solve existing technical problems.

[0006] To achieve the above objectives, the present invention provides a refrigerant circulation system with dual-source evaporator coupling, including a compressor, a plate evaporator, a liquid receiver evaporator, a condenser, a four-way reversing valve, an expansion valve, a constant pressure valve, a heat recovery unit, an air-cooled evaporator, and a gas-liquid separator. The compressor is connected to the first port of the first solenoid valve via a pipeline. The second port of the first solenoid valve is connected to the first port of the four-way reversing valve via a pipeline. The second port of the four-way reversing valve is connected to the first port of the second solenoid valve via a pipeline. The second port of the second solenoid valve is connected to the plate evaporator via a pipeline. The plate evaporator is connected to the first port of the third solenoid valve via a pipeline. The second port of the third solenoid valve is connected to the first port of the fourth solenoid valve via a pipeline. The second port of the fourth solenoid valve is connected to the liquid storage evaporator via a pipeline. The liquid storage evaporator is connected to the first port of the fifth solenoid valve via a pipeline. The second port of the fifth solenoid valve is connected to the gas-liquid separator via a pipeline. The gas-liquid separator is connected to the compressor via a constant pressure valve. The liquid storage evaporator is connected to the third port of the four-way reversing valve via a pipeline. The fourth port of the four-way reversing valve is connected to the first port of the first expansion valve via a pipeline. The second port of the first expansion valve is connected to the first port of the sixth solenoid valve via a pipeline. The second port of the sixth solenoid valve is connected to the first port of the second solenoid valve via a pipeline. The third port of the first solenoid valve is connected to the heat recovery unit via a pipeline. The heat recovery unit is connected to the condenser via the seventh solenoid valve. The condenser is connected to the first port of the eighth solenoid valve via a pipeline. The second port of the eighth solenoid valve is connected to the first port of the expansion valve. The third port of the eighth solenoid valve is connected to the first port of the ninth solenoid valve via a pipeline. The second port of the ninth solenoid valve is connected to the third port of the fourth solenoid valve. The second port of the third solenoid valve is connected to the first port of the tenth solenoid valve via a pipeline. The second port of the tenth solenoid valve is connected to the air-cooled evaporator via a pipeline. The air-cooled evaporator is connected to the first port of the eleventh solenoid valve via a pipeline. The second port of the eleventh solenoid valve is connected to the first port of the twelfth solenoid valve via a pipeline. The second port of the twelfth solenoid valve is connected to the first port of the thirteenth solenoid valve via a pipeline. The second port of the thirteenth solenoid valve is connected to the third port of the fifth solenoid valve via a pipeline.

[0007] Furthermore, a first throttling device is provided between the eleventh solenoid valve and the twelfth solenoid valve.

[0008] Furthermore, a second throttling device is provided between the third solenoid valve and the liquid storage evaporator, and a fourteenth solenoid valve is provided on one side of the second throttling device.

[0009] Furthermore, the third port of the second solenoid valve is connected to the third port of the ninth solenoid valve via a pipeline.

[0010] Furthermore, the third port of the seventh solenoid valve is connected to the third port of the twelfth solenoid valve via a pipeline.

[0011] Furthermore, the fourth port of the fourth solenoid valve is connected to the third port of the thirteenth solenoid valve via a pipeline.

[0012] Furthermore, it also includes a cooling tower, which is connected to the condenser via a circulation pipeline, and the circulation pipeline is equipped with a water pump and valves.

[0013] Furthermore, the liquid storage evaporator is connected to the inlet of the integrated filter / regenerator via a pipeline, the integrated filter / regenerator is connected to the plate evaporator via a pipeline, the plate evaporator is connected to the crystallizer via a pipeline, the crystallizer is connected to the ice slurry buffer tank via a pipeline, the ice slurry buffer tank is connected to the ice storage tank via a pipeline, the ice storage tank is connected to the integrated filter / regenerator, and the outlet of the integrated filter / regenerator is connected to the liquid storage evaporator via a pipeline equipped with an ice-making pump.

[0014] A multi-condition control method for a refrigerant cycle system coupled with a dual-source evaporator, including winter mode, water source heating mode, winter defrosting mode, summer mode, and summer ice melting mode. Winter Mode: After the high-temperature, high-pressure gaseous refrigerant is discharged from the compressor, it first enters the plate evaporator through a four-way reversing valve for condensation. Here, it releases latent heat through heat exchange with the environment or hot water, gradually condensing into a high-pressure, medium-temperature liquid refrigerant. Subsequently, the liquid refrigerant flows into the liquid receiver evaporator through the open third and fourth solenoid valves, balancing the supply and demand between the condenser and evaporator. Through heat exchange with the external water source via internal coils, the refrigerant flow is further stabilized and the system pressure is balanced. At this time, the refrigerant remains in a liquid state. The liquid receiver evaporator preheats the hot water return water through internal coils, increasing the inlet water temperature and improving the system COP. The refrigerant then enters the expansion valve through the four-way reversing valve, where it undergoes an adiabatic throttling process, causing a sharp drop in pressure and temperature, becoming a low-temperature, low-pressure mixture of liquid and gas. The mixed refrigerant then enters the air-cooled evaporator, fully absorbing the low-temperature heat from the ambient air and completely evaporating into a low-temperature, low-pressure gas. Finally, the gaseous refrigerant flows through the constant pressure valve to regulate its pressure and returns to the compressor inlet, completing the cycle. Water source heating mode: After the high-temperature, high-pressure gaseous refrigerant is discharged from the compressor, it first enters the plate evaporator through a four-way reversing valve for condensation. Here, it releases latent heat through heat exchange with the environment or hot water, gradually condensing into a high-pressure, medium-temperature liquid refrigerant. Subsequently, the liquid refrigerant flows into the liquid receiver evaporator through the open third and fourth solenoid valves, balancing the supply and demand between the condenser and evaporator. Through heat exchange with the external water source via internal coils, the refrigerant flow is further stabilized and the system pressure is balanced. At this time, the refrigerant remains in a liquid state. The liquid receiver evaporator preheats the hot water return water through internal coils, increasing the inlet water temperature and improving the system COP. The refrigerant enters the expansion valve through the four-way reversing valve, where it undergoes an adiabatic throttling process, causing a sharp drop in pressure and temperature, becoming a low-temperature, low-pressure liquid-gas mixture. The mixed refrigerant then enters the evaporator, fully absorbing the low-temperature heat from the ambient air and completely evaporating into a low-temperature, low-pressure gas. Finally, the gaseous refrigerant flows through the constant pressure valve to regulate the pressure and returns to the compressor inlet, completing the cycle. Winter defrosting mode: After the high-temperature, high-pressure gaseous refrigerant is discharged from the compressor, it first enters the plate evaporator through a four-way reversing valve for condensation. The high-temperature, high-pressure gaseous refrigerant condenses into a relatively high-temperature liquid refrigerant in the plate evaporator. Subsequently, the refrigerant directly enters the air-cooled evaporator through the third and tenth solenoid valves, utilizing its high-temperature characteristics to rapidly heat and defrost the frosted evaporator. During this process, the refrigerant releases a large amount of sensible heat, causing a slight temperature drop while maintaining a relatively high pressure. Some of the refrigerant condenses into a high-pressure, medium-temperature liquid due to heat release. The mixed refrigerant first passes through the eleventh solenoid valve and the first throttling device, undergoing a throttling process to become a low-temperature, low-pressure liquid. The liquid and gaseous refrigerant mixture flows into the liquid receiver evaporator through the twelfth, thirteenth, and fourteenth solenoid valves. Inside the evaporator, a gas-liquid separation function temporarily stores the liquid refrigerant at the bottom, while the gaseous refrigerant enters the fifth solenoid valve through the top pipe. The liquid receiver evaporator performs gas-liquid separation: the liquid refrigerant temporarily stored at the bottom participates in the system circulation, while the gaseous refrigerant returns to the compressor via the fifth solenoid valve, completely preventing liquid slugging. After mixing with the low-temperature refrigerant circulating in the system within the liquid receiver tank, the liquid refrigerant enters the fifth solenoid valve and undergoes further gas-liquid separation. It is then regulated to a suitable pressure by a constant pressure valve and finally returns to the compressor inlet in a low-temperature, low-pressure gaseous state. Summer Mode: After being discharged from the compressor, the high-temperature, high-pressure gaseous refrigerant enters the heat recovery unit, where waste heat from the compressor exhaust is recovered to produce domestic hot water, improving the overall energy efficiency ratio of the system. It then enters the condenser, where it releases heat through cooling water or ambient air, gradually condensing into a high-pressure, medium-temperature liquid refrigerant. The liquid refrigerant then enters the liquid receiver-evaporator, acting as a subcooler: reducing the amount of refrigerant evaporating before throttling, increasing cooling capacity; simultaneously, it preheats the subcooled water, eliminating the risk of ice crystal formation during ice making. It continues to release heat through cooling water here, and then the liquid refrigerant flows through the four-way reversing valve and the expansion valve, undergoing an adiabatic throttling process, causing a sharp drop in pressure and temperature, becoming a low-temperature, low-pressure mixture of liquid and gas. This mixture enters the evaporator through the second and sixth solenoid valves, exchanging heat with cold water, fully absorbing heat from the water and completely evaporating into a low-temperature, low-pressure gas. Simultaneously, the water is cooled, and the evaporated gaseous refrigerant enters the constant pressure valve through the fifth and thirteenth solenoid valves, adjusting to the appropriate pressure at the compressor inlet before returning to the compressor, completing the cycle. Summer De-icing Mode: High-temperature, high-pressure gaseous refrigerant is discharged from the compressor and enters the heat recovery unit, then the condenser. Here, it releases heat through cooling water or ambient air, gradually condensing into a high-pressure, medium-temperature liquid refrigerant. After being regulated by the second, eighth, and ninth solenoid valves, the refrigerant directly enters the evaporator, utilizing its high-temperature characteristics to provide anti-freezing protection. During this process, the refrigerant releases a large amount of sensible heat, causing a slight temperature drop while maintaining a relatively high pressure. Some of the refrigerant condenses into a high-pressure, medium-temperature liquid due to heat release. The refrigerant then enters the second throttling device... After the throttling device, the mixed refrigerant flows into the liquid receiver evaporator for flash separation. The liquid refrigerant is temporarily stored at the bottom of the tank via a gas-liquid separation function, while the gaseous refrigerant enters the fifth solenoid valve through the top pipe and then undergoes gas-liquid separation via a gas-liquid separator. The gaseous refrigerant returns stably to the compressor via a constant pressure valve, ensuring continuous de-icing. The liquid refrigerant mixes with the low-temperature refrigerant circulating in the system in the liquid receiver tank, then enters the fifth solenoid valve, undergoes gas-liquid separation via a gas-liquid separator, and is then adjusted to a suitable pressure by the constant pressure valve before finally returning to the compressor inlet in a low-temperature, low-pressure gaseous state. In summer, depending on the different ice-making conditions required, the subcooled water channel and the standard chilled water channel can be selected. In the standard chilled water channel, the chilled water does not pass through the regenerator and directly enters the liquid storage evaporator and the evaporator for subsequent processes. In the subcooled water channel, the subcooled water first passes through the regenerator, which is also an integrated filter, and exchanges heat with the subcooled water generated after heat exchange from the liquid storage evaporator before passing through the evaporator for subsequent processes.

[0015] A refrigerant circulation system coupled with a dual-source evaporator is characterized by comprising a compressor, a plate evaporator, a liquid receiver evaporator, a condenser, an expansion valve, a constant pressure valve, a heat recovery unit, an air-cooled evaporator, and a gas-liquid separator. The compressor is connected to the first port of the first solenoid valve via a pipeline. The second port of the first solenoid valve is connected to the plate evaporator via a pipeline. The plate evaporator is connected to the first port of the third solenoid valve via a pipeline. The second port of the third solenoid valve is connected to the first port of the thirteenth solenoid valve via a pipeline. The second port of the thirteenth solenoid valve is connected to the gas-liquid separator. The gas-liquid separator is connected to the compressor via a constant pressure valve. The liquid storage evaporator is connected to the first port of the fifteenth solenoid valve via a pipeline. The second port of the fifteenth solenoid valve is connected to the first port of the expansion valve via a pipeline. The second port of the expansion valve is connected to the first port of the sixth solenoid valve via a pipeline. The second port of the sixth solenoid valve is connected to the plate evaporator via a pipeline. The third port of the first solenoid valve is connected to the heat recovery unit via a pipeline. The heat recovery unit is connected to the first port of the seventh solenoid valve and the condenser via pipelines. The condenser is connected to the first port of the eighth solenoid valve via a pipeline. The second port of the eighth solenoid valve is connected to the first port of the expansion valve. The third port of the eighth solenoid valve is connected to the first port of the ninth solenoid valve via a pipeline. The second port of the ninth solenoid valve is connected to the third port of the third solenoid valve, the first port of the fourteenth solenoid valve, and the first port of the tenth solenoid valve via pipelines. The second port of the fourteenth solenoid valve is connected to the liquid storage evaporator via the second expansion valve. The liquid storage evaporator is connected to the first port of the fifth solenoid valve and the sixteenth solenoid valve via pipelines. The second port of the fifth solenoid valve is connected to the gas-liquid separator via a pipeline. The second port of the sixteenth solenoid valve is connected to the compressor via a pipeline. The second port of the tenth solenoid valve is connected to the air-cooled evaporator via a pipeline. The air-cooled evaporator is connected to the first port of the check valve and the second port of the seventh solenoid valve via pipelines. The second port of the check valve is connected to the third port of the thirteenth solenoid valve via a pipeline.

[0016] The beneficial effects of this invention are reflected in: 1. Uninterrupted defrosting and de-icing technology: Solves the problem of heating interruption and energy efficiency reduction caused by low temperature frost in winter - by optimizing the defrosting process, the high temperature refrigerant discharged from the compressor flows directly through the frosted air-cooled evaporator to achieve rapid defrosting without stopping the machine. The heating process is continuous and stable, while reducing the energy waste caused by traditional electric auxiliary heating or shutdown defrosting, thus improving heating energy efficiency in winter.

[0017] To mitigate the risks associated with ice-making operations in summer, directly using subcooled water to make ice can easily lead to ice crystal formation, causing evaporator freezing or decreased system stability. This solution utilizes the high-temperature refrigerant discharged from the compressor to directly power the frozen water-cooled evaporator, ensuring the refrigeration cycle remains uninterrupted during the ice-melting process and guaranteeing system continuity.

[0018] 2. Multifunctional Integration of Liquid Receiver Evaporator: Integrating liquid storage, evaporation, gas-liquid separation, and subcooling functions, it uses internal coils to preheat hot water return (in winter) or heat subcooled water (in summer) to prevent freezing, and balances refrigerant supply and demand between the condenser and evaporator, eliminating the risk of liquid refrigerant flowing back into the compressor. Replacing the traditional evaporator with a liquid receiver evaporator flash tank enables frequent defrosting in short intervals, improving heat exchange efficiency, system energy efficiency and operational stability, and reducing the likelihood of frosting.

[0019] 3. Intelligent switching between multiple operating conditions: By simplifying the valve assembly, multiple modes (heating, winter defrosting, summer cooling / ice making, summer ice melting) can be switched with one click, reducing redundant piping and equipment size compared to traditional systems. Furthermore, the system allows selection of subcooled water or standard chilled water flow channels according to different cooling requirements.

[0020] 4. Enhanced Energy Utilization and Safety: In summer, waste heat is recovered and domestic hot water is produced through the compressor exhaust via a heat recovery unit, improving the overall energy efficiency ratio of the system; the addition of a regenerator and a liquid storage evaporator work together to eliminate ice crystals, improving the stability of ice-making operations and avoiding the risk of evaporator freezing and cracking. Attached Figure Description

[0021] Figure 1 This is a schematic diagram of the refrigerant circulation system with dual-source evaporator coupling according to the present invention (first embodiment); Figure 2 For the present invention Figure 1 Schematic diagram of a local structure in the middle; Figure 3 This is a schematic diagram of the refrigerant circulation system structure of the dual-source evaporator coupled according to the present invention (second embodiment); Figure 4 For the present invention Figure 3 A schematic diagram of a local part of the structure.

[0022] Explanation of reference numerals in the attached figures: 1. Compressor; 2. Plate evaporator; 3. Liquid receiver evaporator; 4. Condenser; 5. Four-way reversing valve; 6. Expansion valve 1; 7. Constant pressure valve; 8. Heat recovery unit; 9. Air-cooled evaporator; 10. Gas-liquid separator; 11. First throttling device; 12. Second throttling device; 13. First solenoid valve; 14. Second solenoid valve; 15. Third solenoid valve; 16. Fourth solenoid valve; 17. Fifth solenoid valve; 18. Sixth solenoid valve; 19. Seventh solenoid valve. Valves; 20. Eighth solenoid valve; 21. Ninth solenoid valve; 22. Tenth solenoid valve; 23. Eleventh solenoid valve; 24. Twelfth solenoid valve; 25. Thirteenth solenoid valve; 26. Fourteenth solenoid valve; 27. Cooling tower; 28. Integrated filter and regenerator; 29. ​​Crystallizer; 30. Ice slurry buffer tank; 31. Ice storage tank; 32. Ice pump; 33. Check valve; 34. Sixteenth solenoid valve; 35. Fifteenth solenoid valve; 36. Expansion valve II. Detailed Implementation

[0023] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of them. Unless otherwise specified, the embodiments and features in the embodiments of this application can be combined with each other. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0024] Please see Figure 1 and 2The present invention provides a refrigerant circulation system with dual-source evaporator coupling, including a compressor 1, a plate evaporator 2, a liquid storage evaporator 3, a condenser 4, a four-way reversing valve 5, an expansion valve 6, a constant pressure valve 7, a heat recovery unit 8, an air-cooled evaporator 9, and a gas-liquid separator 10. Compressor 1 is connected to the first port of first solenoid valve 13 via a pipeline. The second port of first solenoid valve 13 is connected to the first port of four-way reversing valve 5 via a pipeline. The second port of four-way reversing valve 5 is connected to the first port of second solenoid valve 14 via a pipeline. The second port of second solenoid valve 14 is connected to plate evaporator 2 via a pipeline. Plate evaporator 2 is connected to the first port of third solenoid valve 15 via a pipeline. The second port of third solenoid valve 15 is connected to the first port of fourth solenoid valve 16 via a pipeline. The second port of fourth solenoid valve 16 is connected to liquid storage evaporator 3 via a pipeline. Liquid storage evaporator 3 is connected to the first port of fifth solenoid valve 17 via a pipeline. The second port of fifth solenoid valve 17 is connected to gas-liquid separator 10 via a pipeline. Gas-liquid separator 10 is connected to compressor 1 via constant pressure valve 7. The liquid storage evaporator 3 is connected to the third port of the four-way reversing valve 5 through a pipeline. The fourth port of the four-way reversing valve 5 is connected to the first port of the expansion valve 6 through a pipeline. The second port of the expansion valve 6 is connected to the first port of the sixth solenoid valve 18 through a pipeline. The second port of the sixth solenoid valve 18 is connected to the first port of the second solenoid valve 14 through a pipeline. The third port of the first solenoid valve 13 is connected to the heat recovery unit 8 through a pipeline. The heat recovery unit 8 is connected to the condenser 4 through the seventh solenoid valve 19. The condenser 4 is connected to the first port of the eighth solenoid valve 20 through a pipeline. The second port of the eighth solenoid valve 20 is connected to the first port of the expansion valve 6. The third port of the eighth solenoid valve 20 is connected to the first port of the ninth solenoid valve 21 through a pipeline. The second port of the ninth solenoid valve 21 is connected to the third port of the fourth solenoid valve 16. The second port of the third solenoid valve 15 is connected to the first port of the tenth solenoid valve 22 via a pipeline. The second port of the tenth solenoid valve 22 is connected to the air-cooled evaporator 9 via a pipeline. The air-cooled evaporator 9 is connected to the first port of the eleventh solenoid valve 23 via a pipeline. The second port of the eleventh solenoid valve 23 is connected to the first port of the twelfth solenoid valve 24 via a pipeline. The second port of the twelfth solenoid valve 24 is connected to the first port of the thirteenth solenoid valve 25 via a pipeline. The second port of the thirteenth solenoid valve 25 is connected to the third port of the fifth solenoid valve 17 via a pipeline.

[0025] In one embodiment, a first throttling device 11 is provided between the eleventh solenoid valve 23 and the twelfth solenoid valve 24.

[0026] In one embodiment, a second throttling device 12 is provided between the third solenoid valve 15 and the liquid storage evaporator 3, and a fourteenth solenoid valve 26 is provided on one side of the second throttling device 12.

[0027] Specifically, the third port of the second solenoid valve 14 is connected to the third port of the ninth solenoid valve 21 via a pipeline.

[0028] Specifically, the third port of the seventh solenoid valve 19 is connected to the third port of the twelfth solenoid valve 24 via a pipeline.

[0029] Specifically, the fourth port of the fourth solenoid valve 16 is connected to the third port of the thirteenth solenoid valve 25 via a pipeline.

[0030] In one embodiment, a cooling tower 27 is also included, which is connected to the condenser 4 via a circulation pipeline, and the circulation pipeline is equipped with a water pump and valves.

[0031] In one embodiment, the liquid storage evaporator 3 is connected to the inlet of the integrated filter / regenerator 28 via a pipeline. The integrated filter / regenerator 28 is connected to the plate evaporator 2 via a pipeline. The plate evaporator 2 is connected to the crystallizer 29 via a pipeline. The crystallizer 29 is connected to the ice slurry buffer tank 30 via a pipeline. The ice slurry buffer tank 30 is connected to the ice storage tank 31 via a pipeline. The ice storage tank 31 is connected to the integrated filter / regenerator 28. The outlet of the integrated filter / regenerator 28 is connected to the liquid storage evaporator 3 via a pipeline equipped with an ice-making pump 32.

[0032] The present invention also provides a multi-condition control method for a refrigerant cycle system coupled with the above-mentioned dual-source evaporator, including a winter mode, a water source heating mode, a winter defrosting mode, a summer mode, and a summer ice melting mode. Winter Mode: After the high-temperature, high-pressure gaseous refrigerant is discharged from the compressor 1, it first enters the plate evaporator 2 through the four-way reversing valve 5 for condensation. Here, it releases latent heat through heat exchange with the environment or hot water, gradually condensing into a high-pressure, medium-temperature liquid refrigerant. Subsequently, the liquid refrigerant flows into the liquid receiver evaporator 3 through the open third solenoid valve 15 and fourth solenoid valve 16, balancing the supply and demand between the condenser 4 and the evaporator. Through heat exchange with the external water source via the internal coil, the refrigerant flow is further stabilized and the system pressure is balanced. At this time, the refrigerant remains in a liquid state. The liquid receiver evaporator 3 preheats the hot water return water through the internal coil, increasing the inlet water temperature and improving the system COP. The refrigerant enters the expansion valve 6 through the four-way reversing valve 5, where it undergoes an adiabatic throttling process, causing a sharp drop in pressure and temperature, becoming a low-temperature, low-pressure mixture of liquid and gas. The mixed refrigerant then enters the air-cooled evaporator 9, fully absorbing the low-temperature heat from the ambient air and completely evaporating into a low-temperature, low-pressure gas. Finally, the gaseous refrigerant flows through the constant pressure valve 7 to regulate the pressure and returns to the compressor 1 inlet, completing the cycle. Water source heating mode: After the high-temperature and high-pressure gaseous refrigerant is discharged from the compressor 1, it first enters the plate evaporator 2 through the four-way reversing valve 5 for condensation. Here, it releases latent heat through heat exchange with the environment or hot water, and gradually condenses into a high-pressure, medium-temperature liquid refrigerant. Then, the liquid refrigerant flows into the liquid storage evaporator 3 through the open third solenoid valve 15 and fourth solenoid valve 16, balancing the supply and demand between the condenser 4 and the evaporator. Through heat exchange with the external water source through the internal coil, the refrigerant flow is further stabilized and the system pressure is balanced. At this time, the refrigerant still remains in a liquid state. The liquid storage evaporator 3 preheats the hot water return water through the internal coil, increasing the inlet water temperature and improving the system COP. The refrigerant enters the expansion valve 6 through the four-way reversing valve 5, where it undergoes an adiabatic throttling process, and the pressure and temperature drop sharply, becoming a low-temperature, low-pressure liquid-gas mixture. The mixed refrigerant then enters the evaporator, fully absorbs the low-temperature heat from the ambient air, and completely evaporates into a low-temperature, low-pressure gas. Finally, the gaseous refrigerant flows through the constant pressure valve 7 to regulate the pressure and returns to the compressor 1 inlet, completing the cycle. Winter defrosting mode: After the high-temperature, high-pressure gaseous refrigerant is discharged from the compressor 1, it first enters the plate evaporator 2 through the four-way reversing valve 5 for condensation. The high-temperature, high-pressure gaseous refrigerant condenses into a relatively high-temperature liquid refrigerant after passing through the plate evaporator 2. Subsequently, the refrigerant directly enters the air-cooled evaporator 9 through the third solenoid valve 15 and the tenth solenoid valve 22, using its high-temperature characteristics to quickly heat and defrost the frosted evaporator. During this process, the refrigerant releases a large amount of sensible heat, and the temperature drops slightly but still maintains a high pressure. Some of the refrigerant condenses into a high-pressure, medium-temperature liquid due to heat release. The mixed refrigerant first passes through the eleventh solenoid valve 23 and the first throttling device 11 for throttling, becoming a low-temperature, low-pressure liquid. The gaseous refrigerant mixture flows into the liquid receiver evaporator 3 through the twelfth solenoid valve 24, the thirteenth solenoid valve 25, and the fourteenth solenoid valve 26. The liquid refrigerant is temporarily stored at the bottom of the tank through the gas-liquid separation function, while the gaseous refrigerant enters the fifth solenoid valve 17 through the top pipe. The liquid receiver evaporator 3 performs gas-liquid separation: the liquid refrigerant is temporarily stored at the bottom of the tank and participates in the system circulation, while the gaseous refrigerant returns to the compressor 1 through the fifth solenoid valve 17, which completely prevents liquid slugging. After the liquid refrigerant mixes with the low-temperature refrigerant circulating in the system in the liquid receiver tank, it enters the fifth solenoid valve 17 and then undergoes gas-liquid separation through the gas-liquid separator 10. After that, it is adjusted to a suitable pressure by the constant pressure valve 7 and finally returns to the inlet of the compressor 1 in a low-temperature, low-pressure gaseous form. Summer Mode: After the high-temperature, high-pressure gaseous refrigerant is discharged from compressor 1, it enters heat recovery unit 8. Heat recovery unit 8 recovers the waste heat from compressor 1's exhaust to produce domestic hot water, improving the system's overall energy efficiency ratio. It then enters condenser 4, where it releases heat through cooling water or ambient air, gradually condensing into high-pressure, medium-temperature liquid refrigerant. Subsequently, the liquid refrigerant enters liquid evaporator 3, acting as a subcooler: reducing the amount of refrigerant evaporating before throttling, increasing cooling capacity; at the same time, it preheats the subcooled water, eliminating the risk of ice crystal formation during ice-making operations, and continues to release heat through cooling water or ambient air here. Subsequently, the liquid refrigerant flows through the four-way reversing valve 5 and the expansion valve 6, undergoing an adiabatic throttling process, causing a sudden drop in pressure and temperature, and becoming a low-temperature, low-pressure mixture of liquid and gas. The mixed refrigerant enters the evaporator through the second solenoid valve 14 and the sixth solenoid valve 18, where it exchanges heat with the cold water, fully absorbing the heat from the water and completely evaporating into a low-temperature, low-pressure gas. At the same time, after cooling the water, the evaporated gaseous refrigerant enters the constant pressure valve 7 through the fifth solenoid valve 17 and the thirteenth solenoid valve 25, and returns to the compressor 1 after being adjusted to the appropriate pressure at the compressor 1 inlet, completing the cycle. Summer De-icing Mode: High-temperature, high-pressure gaseous refrigerant is discharged from compressor 1 and enters heat recovery unit 8, then condenser 4. Here, it releases heat through cooling water or ambient air, gradually condensing into high-pressure, medium-temperature liquid refrigerant. After being regulated by the second solenoid valve 14, the eighth solenoid valve 20, and the ninth solenoid valve 21, the refrigerant directly enters the evaporator, utilizing its high-temperature characteristics to provide anti-freezing protection. During this process, the refrigerant releases a large amount of sensible heat, causing a slight temperature drop while maintaining a relatively high pressure. Some of the refrigerant condenses into a high-pressure, medium-temperature liquid due to heat release. The refrigerant then enters the second throttling device... After setting 12, the mixed refrigerant flows into the liquid receiver evaporator 3 for flash separation. The liquid refrigerant is temporarily stored at the bottom of the tank through the gas-liquid separation function, while the gaseous refrigerant enters the fifth solenoid valve 17 through the top pipe and then undergoes gas-liquid separation through the gas-liquid separator 10. The gaseous refrigerant returns to the compressor 1 stably through the constant pressure valve 7 to ensure continuous de-icing. After the liquid refrigerant mixes with the low-temperature refrigerant circulating in the system in the liquid receiver tank, it enters the fifth solenoid valve 17 and then undergoes gas-liquid separation through the gas-liquid separator 10. After being adjusted to a suitable pressure by the constant pressure valve 7, it finally returns to the inlet of the compressor 1 in a low-temperature, low-pressure gaseous form. In summer, depending on the different ice-making conditions required, the subcooled water channel and the standard chilled water channel can be selected. In the standard chilled water channel, the chilled water does not pass through the regenerator and directly enters the liquid storage evaporator 3 and the evaporator for subsequent processes. In the subcooled water channel, the subcooled water first passes through the regenerator and integrated filter, and exchanges heat with the subcooled water generated after heat exchange from the liquid storage evaporator 3, and then passes through the evaporator for subsequent processes.

[0033] Please see Figure 3 and 4The present invention also provides a refrigerant circulation system coupled with a dual-source evaporator, which includes a compressor 1, a plate evaporator 2, a liquid storage evaporator 3, a condenser 4, an expansion valve 6, a constant pressure valve 7, a heat recovery unit 8, an air-cooled evaporator 9, and a gas-liquid separator 10. The compressor 1 is connected to the first port of the first solenoid valve 13 through a pipeline. The second port of the first solenoid valve 13 is connected to the plate evaporator 2 through a pipeline. The plate evaporator 2 is connected to the first port of the third solenoid valve 15 through a pipeline. The second port of the third solenoid valve 15 is connected to the first port of the thirteenth solenoid valve 25 through a pipeline. The second port of the thirteenth solenoid valve 25 is connected to the gas-liquid separator 10. The gas-liquid separator 10 is connected to the compressor 1 through the constant pressure valve 7. The liquid storage evaporator 3 is connected to the first port of the fifteenth solenoid valve 35 through a pipeline. The second port of the fifteenth solenoid valve 35 is connected to the first port of the expansion valve 6 through a pipeline. The second port of the expansion valve 6 is connected to the first port of the sixth solenoid valve 18 through a pipeline. The second port of the sixth solenoid valve 18 is connected to the plate evaporator 2 through a pipeline. The third port of the first solenoid valve 13 is connected to the heat recovery unit 8 via a pipeline. The heat recovery unit 8 is connected to the first port of the seventh solenoid valve 19 and the condenser 4 via pipelines. The condenser 4 is connected to the first port of the eighth solenoid valve 20 via a pipeline. The second port of the eighth solenoid valve 20 is connected to the first port of the expansion valve 6 via a pipeline. The third port of the eighth solenoid valve 20 is connected to the first port of the ninth solenoid valve 21 via a pipeline. The second port of the ninth solenoid valve 21 is connected to the third port of the third solenoid valve 15, the first port of the fourteenth solenoid valve 26, and the first port of the tenth solenoid valve 22 via pipelines. The second port of the fourteenth solenoid valve 26 is connected to the liquid storage evaporator 3 via the expansion valve 26. The liquid storage evaporator 3 is connected to the first port of the fifth solenoid valve 17 and the sixteenth solenoid valve 34 via pipelines. The second port of the fifth solenoid valve 17 is connected to the gas-liquid separator 10 via a pipeline. The second port of the sixteenth solenoid valve 34 is connected to the compressor 1 via a pipeline. The second port of the tenth solenoid valve 22 is connected to the air-cooled evaporator 9 through a pipeline. The air-cooled evaporator 9 is connected to the first port of the check valve 33 and the second port of the seventh solenoid valve 19 through pipelines. The second port of the check valve 33 is connected to the third port of the thirteenth solenoid valve 25 through a pipeline.

[0034] Figure 3 and Figure 4 In this example, compared to Figure 1 and Figure 2 Some valve structures were simplified, the refrigerant path was optimized, and a branch for refrigerant to supply gas from the flash tank to the compressor was added. This increases the subcooling of the liquid refrigerant before throttling, allowing the liquid refrigerant to better absorb energy from the air in the evaporator.

[0035] It should be noted that if the embodiments of the present invention involve directional indicators such as up, down, left, right, front, back, etc., the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture as shown in the attached figure. If the specific posture changes, the directional indicators will also change accordingly.

[0036] Furthermore, if the embodiments of this invention involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the meaning of "and / or" throughout the text includes three parallel solutions; for example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied. Furthermore, "multiple" refers to two or more. Moreover, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, such a combination of technical solutions should be considered non-existent.

[0037] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A refrigerant cycle system with dual-source evaporators coupled, characterized in that: Includes a compressor (1), a plate evaporator (2), a liquid storage evaporator (3), a condenser (4), a four-way reversing valve (5), an expansion valve (6), a constant pressure valve (7), a heat recovery unit (8), an air-cooled evaporator (9), a gas-liquid separator (10), a first solenoid valve (13), a second solenoid valve (14), a third solenoid valve (15), a fourth solenoid valve (16), a fifth solenoid valve (17), a sixth solenoid valve (18), a seventh solenoid valve (19), an eighth solenoid valve (20), a ninth solenoid valve (21), a tenth solenoid valve (22), an eleventh solenoid valve (23), a twelfth solenoid valve (24), a thirteenth solenoid valve (25), an integrated filter and regenerator (28), a crystallizer (29), an ice slurry buffer tank (30), an ice storage tank (31), and an ice pump (32); The exhaust port of the compressor (1) is connected to the first port of the first solenoid valve (13) via a pipeline; the second port of the first solenoid valve (13) is connected to the first port of the four-way reversing valve (5) via a pipeline; the third port of the first solenoid valve (13) is connected to the refrigerant side inlet of the heat recovery unit (8) via a pipeline; the refrigerant side outlet of the heat recovery unit (8) is connected to the refrigerant inlet of the condenser (4) via the seventh solenoid valve (19); the refrigerant outlet of the condenser (4) is connected to the first port of the eighth solenoid valve (20); the second port of the eighth solenoid valve (20) is connected to the first port of the expansion valve (6) via a pipeline; the third port of the eighth solenoid valve (20) is connected to the first port of the ninth solenoid valve (21) via a pipeline; the second port of the ninth solenoid valve (21) is connected to the third port of the fourth solenoid valve (16). The second port of the four-way reversing valve (5) is connected to the first port of the second solenoid valve (14) through a pipeline; the second port of the second solenoid valve (14) is connected to the refrigerant port of the plate evaporator (2); the second port of the expansion valve (6) is connected to the first port of the sixth solenoid valve (18); the second port of the sixth solenoid valve (18) is connected to the pipeline where the first port of the second solenoid valve (14) is located. The refrigerant outlet of the plate evaporator (2) is connected to the first port of the third solenoid valve (15) via a pipeline; the second port of the third solenoid valve (15) is divided into two paths: the first path is connected to the first port of the fourth solenoid valve (16), and the second port of the fourth solenoid valve (16) is connected to the liquid storage evaporator (3); the second path is connected to the first port of the tenth solenoid valve (22); the second port of the tenth solenoid valve (22) is connected to the refrigerant inlet of the air-cooled evaporator (9); the refrigerant outlet of the air-cooled evaporator (9) is connected to the first port of the eleventh solenoid valve (23); the second port of the eleventh solenoid valve (23) is connected to the first port of the twelfth solenoid valve (24); the second port of the twelfth solenoid valve (24) is connected to the first port of the thirteenth solenoid valve (25); the second port of the thirteenth solenoid valve (25) is connected to the third port of the fifth solenoid valve (17). The gas phase interface of the liquid storage evaporator (3) is connected to the third interface of the four-way reversing valve (5) through a pipeline; the outlet of the gas-liquid separator (10) is connected to the inlet of the compressor (1) through the constant pressure valve (7); the first interface of the fifth solenoid valve (17) is connected to the liquid storage evaporator (3), and the second interface of the fifth solenoid valve (17) is connected to the inlet of the gas-liquid separator (10); The system also includes an ice slurry ice-making circulation loop: the liquid phase interface of the liquid storage evaporator (3) is connected to the inlet of the integrated filter and regenerator (28) via a pipeline; the first outlet of the integrated filter and regenerator (28) is connected to the plate evaporator (2); the ice slurry outlet of the plate evaporator (2) is connected to the inlet of the crystallizer (29); the outlet of the crystallizer (29) is connected to the inlet of the ice slurry buffer tank (30); the outlet of the ice slurry buffer tank (30) is connected to the ice storage tank (31); the liquid outlet of the ice storage tank (31) is returned to the integrated filter and regenerator (28); the second outlet of the integrated filter and regenerator (28) is returned to the liquid storage evaporator (3) via a pipeline equipped with an ice-making pump (32).

2. The refrigerant cycle system with dual-source evaporator coupling as described in claim 1, characterized in that: A first throttling device (11) is connected in series on the pipeline between the second port of the eleventh solenoid valve (23) and the first port of the twelfth solenoid valve (24).

3. The refrigerant cycle system with dual-source evaporator coupling as described in claim 2, characterized in that: A second throttling device (12) is installed on the pipeline between the third solenoid valve (15) and the liquid storage evaporator (3); a fourteenth solenoid valve (26) is connected in series on one side of the pipeline of the second throttling device (12).

4. The refrigerant cycle system with dual-source evaporator coupling as described in claim 1, characterized in that: The third port of the second solenoid valve (14) is connected to the third port of the ninth solenoid valve (21) via a pipeline.

5. The refrigerant cycle system coupled with a dual-source evaporator as described in claim 1, characterized in that: The third port of the seventh solenoid valve (19) is connected to the third port of the twelfth solenoid valve (24) via a pipeline.

6. The refrigerant cycle system with dual-source evaporator coupling as described in claim 1, characterized in that: The fourth port of the fourth solenoid valve (16) is connected to the third port of the thirteenth solenoid valve (25) via a pipeline.

7. The refrigerant cycle system with dual-source evaporator coupling as described in claim 1, characterized in that: It also includes a cooling tower (27), which is equipped with a cooling water circulation pipeline. The cooling water circulation pipeline forms a closed water circulation loop with the water side port of the condenser (4). A water pump and a control valve are configured on the cooling water circulation pipeline.

8. A multi-condition control method for a refrigerant cycle system coupled with a dual-source evaporator according to claim 3, characterized in that: Includes winter mode, water source heating mode, winter defrosting mode, summer mode, and summer ice melting mode; Winter mode: After the high-temperature and high-pressure gaseous refrigerant is discharged from the compressor (1), it first enters the plate evaporator (2) through the four-way reversing valve (5) for condensation. Here, it releases latent heat by exchanging heat with the environment or hot water and gradually condenses into high-pressure medium-temperature liquid refrigerant. Then, the liquid refrigerant flows into the liquid storage evaporator (3) through the opened third solenoid valve (15) and fourth solenoid valve (16) to balance the supply and demand between the condenser (4) and the evaporator. Through heat exchange between the internal coil and the external water source, the refrigerant flow rate is further stabilized and the system pressure is balanced. At this time, the refrigerant... The refrigerant remains in a liquid state; the liquid storage evaporator (3) preheats the hot water return water through the internal coil, raising the inlet water temperature and increasing the system COP; the refrigerant enters the expansion valve (6) through the four-way reversing valve (5), where it undergoes an adiabatic throttling process, causing a sudden drop in pressure and temperature, becoming a low-temperature, low-pressure liquid-gas mixture; the mixed refrigerant then enters the air-cooled evaporator (9), fully absorbing the low-temperature heat from the ambient air and completely evaporating into a low-temperature, low-pressure gaseous state; finally, the gaseous refrigerant flows through the constant pressure valve (7) to regulate the pressure and returns to the compressor (1) inlet, completing the cycle; Water source heating mode: After the high-temperature and high-pressure gaseous refrigerant is discharged from the compressor (1), it first enters the plate evaporator (2) through the four-way reversing valve (5) for condensation. Here, it releases latent heat by exchanging heat with the environment or hot water, and gradually condenses into high-pressure medium-temperature liquid refrigerant. Then, the liquid refrigerant flows into the liquid storage evaporator (3) through the opened third solenoid valve (15) and fourth solenoid valve (16), balancing the supply and demand between the condenser (4) and the evaporator. Through heat exchange between the internal coil and the external water source, the refrigerant flow rate is further stabilized and the system pressure is balanced. The refrigerant remains in a liquid state; the liquid evaporator (3) preheats the hot water return water through the internal coil, raising the inlet water temperature and increasing the system COP; the refrigerant enters the expansion valve (6) through the four-way reversing valve (5), where it undergoes an adiabatic throttling process, causing a sudden drop in pressure and temperature, becoming a low-temperature, low-pressure liquid-gas mixture; the mixed refrigerant then enters the evaporator, fully absorbing the low-temperature heat from the ambient air and completely evaporating into a low-temperature, low-pressure gas; finally, the gaseous refrigerant flows through the constant pressure valve (7) to regulate the pressure and returns to the compressor (1) inlet, completing the cycle; Winter defrosting mode: After the high-temperature and high-pressure gaseous refrigerant is discharged from the compressor (1), it first enters the plate evaporator (2) through the four-way reversing valve (5) for condensation. The high-temperature and high-pressure gaseous refrigerant is condensed into a relatively high-temperature liquid refrigerant through the plate evaporator (2). Then, the refrigerant directly enters the air-cooled evaporator (9) through the third solenoid valve (15) and the tenth solenoid valve (22). It uses its high-temperature characteristics to quickly heat and defrost the frosted evaporator. During this process, the refrigerant releases a large amount of sensible heat, and the temperature drops slightly but still maintains a high pressure. Some of the refrigerant condenses into a high-pressure medium-temperature liquid due to heat release. The mixed refrigerant first passes through the eleventh solenoid valve (23) and the first throttling device (11) through the throttling process, and becomes a low-temperature and low-pressure liquid mixed with gas. The liquid refrigerant flows into the liquid storage evaporator (3) through the 12th solenoid valve (24), 13th solenoid valve (25), and 14th solenoid valve (26). The liquid refrigerant is temporarily stored at the bottom of the tank through the gas-liquid separation function, while the gaseous refrigerant enters the 5th solenoid valve (17) through the top pipe. The liquid storage evaporator (3) performs gas-liquid separation: the liquid refrigerant is temporarily stored at the bottom of the tank and participates in the system circulation, while the gaseous refrigerant returns to the compressor (1) through the 5th solenoid valve (17), which completely prevents liquid slugging. After the liquid refrigerant mixes with the low-temperature refrigerant circulating in the system in the liquid storage tank, it enters the 5th solenoid valve (17) and then undergoes gas-liquid separation through the gas-liquid separator (10). After that, it is adjusted to a suitable pressure by the constant pressure valve (7) and finally returns to the compressor (1) inlet in the form of low-temperature and low-pressure gas. Summer mode: After the high temperature and high pressure gaseous refrigerant is discharged from the compressor (1), it enters the heat recovery unit (8). The waste heat of the compressor (1) can be recovered through the heat recovery unit (8) to produce domestic hot water, and the overall energy efficiency ratio of the system is improved. Then it enters the condenser (4), where it releases heat through cooling water or ambient air and gradually condenses into a high-pressure, medium-temperature liquid refrigerant. The liquid refrigerant then enters the liquid storage evaporator (3) as a subcooler: reducing the amount of refrigerant evaporation before throttling and increasing the cooling capacity. At the same time, it preheats the subcooled water to eliminate the risk of ice crystal formation during ice making. It continues to pass through the cooling water or release heat here. Then the liquid refrigerant flows through the four-way reversing valve (5) and through the expansion valve (6), undergoing an adiabatic throttling process. The pressure and temperature drop sharply, and it becomes a low-temperature, low-pressure liquid and gaseous mixture. The mixed refrigerant enters the evaporator through the second solenoid valve (14) and the sixth solenoid valve (18), where it exchanges heat with the cold water, fully absorbs the heat in the water, and completely evaporates into a low-temperature, low-pressure gaseous state. At the same time, after cooling the water, the evaporated gaseous refrigerant enters the constant pressure valve (7) through the fifth solenoid valve (17) and the thirteenth solenoid valve (25), and returns to the compressor (1) after being adjusted to the appropriate pressure at the compressor (1) inlet, completing the cycle. Summer De-icing Mode: After the high-temperature and high-pressure gaseous refrigerant is discharged from the compressor (1), it enters the heat recovery unit (8) and then the condenser (4). Here, it releases heat through cooling water or ambient air and gradually condenses into a high-pressure, medium-temperature liquid refrigerant. After being regulated by the second solenoid valve (14), the eighth solenoid valve (20), and the ninth solenoid valve (21), the refrigerant directly enters the evaporator. Its high-temperature characteristics are used to protect the evaporator from freezing. During this process, the refrigerant releases a large amount of sensible heat, and the temperature drops slightly but still maintains a high pressure. Some of the refrigerant condenses into a high-pressure, medium-temperature liquid due to heat release. The refrigerant enters the second throttling device (12). After that, the mixed refrigerant flows into the liquid storage evaporator (3) and performs flash separation. The liquid refrigerant is temporarily stored at the bottom of the tank through the gas-liquid separation function, while the gaseous refrigerant enters the fifth solenoid valve (17) through the top pipe and then passes through the gas-liquid separator (10) for gas-liquid separation. The gaseous refrigerant returns to the compressor (1) stably through the constant pressure valve (7) to ensure the continuity of de-icing. After the liquid refrigerant mixes with the low-temperature refrigerant circulating in the system in the liquid storage tank, it enters the fifth solenoid valve (17) and then passes through the gas-liquid separator (10) for gas-liquid separation. After being adjusted to a suitable pressure by the constant pressure valve (7), it finally returns to the compressor (1) inlet in the form of low-temperature and low-pressure gas. In summer, depending on the different ice-making conditions required, the subcooled water channel and the standard chilled water channel can be selected. In the standard chilled water channel, the chilled water does not pass through the regenerator and directly enters the liquid storage evaporator (3) and the evaporator for subsequent processes. In the subcooled water channel, the subcooled water first passes through the regenerator and integrated filter and exchanges heat with the subcooled water generated after heat exchange from the liquid storage evaporator (3), and then passes through the evaporator for subsequent processes.

9. A refrigerant cycle system with dual-source evaporators coupled together, characterized in that: Includes compressor (1), plate evaporator (2), liquid storage evaporator (3), condenser (4), expansion valve one (6), constant pressure valve (7), heat recovery unit (8), air-cooled evaporator (9), gas-liquid separator (10), first solenoid valve (13), third solenoid valve (15), fifth solenoid valve (17), sixth solenoid valve (18), seventh solenoid valve (19), eighth solenoid valve (20), ninth solenoid valve (21), tenth solenoid valve (22), thirteenth solenoid valve (25), fourteenth solenoid valve (26), fifteenth solenoid valve (35), sixteenth solenoid valve (34), check valve (33), expansion valve two (36); The exhaust port of the compressor (1) is connected to the first interface of the first solenoid valve (13) through a pipeline; The second port of the first solenoid valve (13) is connected to the refrigerant inlet of the plate evaporator (2) through a pipeline; the third port of the first solenoid valve (13) is connected to the refrigerant side inlet of the heat recovery unit (8) through a pipeline. The refrigerant outlet of the plate evaporator (2) is connected to the first port of the third solenoid valve (15); the second port of the third solenoid valve (15) is connected to the first port of the thirteenth solenoid valve (25); the second port of the thirteenth solenoid valve (25) is connected to the inlet of the gas-liquid separator (10); the outlet of the gas-liquid separator (10) is connected to the return port of the compressor (1) via the constant pressure valve (7). The first outlet of the liquid storage evaporator (3) is connected to the first port of the fifteenth solenoid valve (35); the second port of the fifteenth solenoid valve (35) is connected to the first port of the expansion valve (6); the second port of the expansion valve (6) is connected to the first port of the sixth solenoid valve (18); the second port of the sixth solenoid valve (18) is connected to the refrigerant inlet of the plate evaporator (2). The refrigerant side outlet of the heat recovery unit (8) is divided into two paths, one path is connected to the first interface of the seventh solenoid valve (19), and the other path is connected to the refrigerant inlet of the condenser (4). The refrigerant outlet of the condenser (4) is connected to the first port of the eighth solenoid valve (20); the second port of the eighth solenoid valve (20) is connected to the first port of the expansion valve (6); the third port of the eighth solenoid valve (20) is connected to the first port of the ninth solenoid valve (21). The second interface of the ninth solenoid valve (21) is a multi-branch node, which is connected to the third interface of the third solenoid valve (15), the first interface of the fourteenth solenoid valve (26), and the first interface of the tenth solenoid valve (22). The second port of the fourteenth solenoid valve (26) is connected to the liquid storage evaporator (3) via the expansion valve (36); The liquid storage evaporator (3) is also provided with two sets of output branches: the first branch is connected to the first interface of the fifth solenoid valve (17), and the second interface of the fifth solenoid valve (17) is connected to the air inlet of the gas-liquid separator (10); the second branch is connected to the first interface of the sixteenth solenoid valve (34), and the second interface of the sixteenth solenoid valve (34) is connected to the air return port of the compressor (1). The second port of the tenth solenoid valve (22) is connected to the refrigerant inlet of the air-cooled evaporator (9); the refrigerant outlet of the air-cooled evaporator (9) branches into two pipelines: the first pipeline is connected to the first port of the check valve (33), the second port of the check valve (33) is connected to the third port of the thirteenth solenoid valve (25); the second pipeline is connected to the second port of the seventh solenoid valve (19).

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