Heat exchange system and heat exchange method

Abstract

The invention provides a heat exchange system and a heat exchange method. The heat exchange system comprises a turbulent flow gas supply component. The evaporator comprises a shell, an evaporation pipe and a turbulent flow pipe, the evaporation pipe and the turbulent flow pipe are both arranged in the shell, the turbulent flow pipe is located below the evaporation pipe, a plurality of spraying holes are formed in the turbulent flow pipe, and the turbulent flow inlet end of the turbulent flow pipe communicates with the outlet end of the turbulent flow gas supply component so that turbulent flow gas can be conveyed into the turbulent flow pipe. Turbulent flow gas is jetted to the surface of the evaporation pipe through the jet holes so as to destroy a thermal boundary layer formed on the surface of the turbulent flow pipe; the inlet end of the compressor is communicated with the outlet end of the evaporator; the inlet end of the condenser is communicated with the outlet end of the compressor, and the outlet end of the condenser is communicated with the inlet end of the evaporator; the problem that in the prior art, when a flooded evaporator is under the working conditions of low load, low flow speed and the like, the heat exchange efficiency is remarkably reduced due to the fact that a heat boundary layer is formed on the surface of an evaporation pipe is solved.

Description

Technical Field

[0001] This application relates to the field of evaporator technology, and more specifically, to a heat exchange system and heat exchange method. Background Technology

[0002] In the refrigeration industry, flooded evaporators are highly favored due to their efficient heat exchange capabilities and wide applicability. This evaporator design allows the refrigerant to evaporate under high liquid levels, expanding the contact area with the heat transfer medium and thus improving heat exchange efficiency. Traditional flooded evaporators typically enhance performance by improving the surface properties of the heat exchange tubes, such as using high-efficiency finned tubes or sintered surface tubes, to increase the heat exchange area and improve flow characteristics. However, while these passive heat transfer enhancement technologies improve the efficiency of flooded evaporators to some extent, their effectiveness becomes limited under specific operating conditions, such as low load, low flow rate, low superheat, or long-term stable operation.

[0003] Under the aforementioned operating conditions, a thermal boundary layer easily forms on the surface of the evaporator tube. This phenomenon, caused by the slow flow or stagnation of the refrigerant, leads to regular and low-frequency bubble formation, increased liquid film thickness, and thus significantly increased thermal resistance. The presence of this thermal boundary layer greatly reduces the heat transfer coefficient, forcing a larger evaporation temperature difference, thereby significantly reducing the system's coefficient of performance (COP). In some cases, efficiency can decrease by more than 20%. Furthermore, the stable structure of the boundary layer also leads to uneven evaporation, with the risk of localized overheating or drying. Simultaneously, stagnant areas of the liquid film are prone to the accumulation of oil, impurities, or moisture, which, in the long term, may cause scaling and carbon buildup, severely affecting heat exchange performance and shortening equipment lifespan. Summary of the Invention

[0004] The main objective of this invention is to provide a heat exchange system and method to solve the problem that the heat exchange efficiency of flooded evaporators in the prior art is significantly reduced due to the formation of a thermal boundary layer on the surface of the evaporator tubes under low load and low flow rate conditions.

[0005] To achieve the above objectives, according to one aspect of the present invention, a heat exchange system is provided, including a turbulent gas supply component for supplying turbulent gas;

[0006] The evaporator includes a shell, an evaporator tube, and a baffle tube. Both the evaporator tube and the baffle tube are located inside the shell. The baffle tube is located below the evaporator tube and has multiple injection holes. The baffle inlet end of the baffle tube is connected to the outlet end of the baffle gas supply component to deliver baffle gas into the baffle tube. The baffle gas is then injected onto the surface of the evaporator tube through the injection holes to disrupt the thermal boundary layer formed on the surface of the baffle tube.

[0007] The compressor has its inlet connected to the outlet of the evaporator.

[0008] The condenser has its inlet connected to the compressor outlet, and its outlet connected to the evaporator inlet.

[0009] Furthermore, multiple injection holes are arranged sequentially along the axial direction of the baffle tube; and / or, the outlet end of each injection hole is arranged facing the surface of the evaporator tube.

[0010] Furthermore, the heat exchange system also includes a first delivery pipe, the two ends of which are respectively connected to a turbulent gas supply component and a turbulent pipe, so as to deliver turbulent gas into the turbulent pipe through the first delivery pipe;

[0011] A first regulating component is disposed on a first conveying pipe to regulate the flow rate of the turbulent gas entering the turbulence pipe.

[0012] Furthermore, the heat exchange system also includes a second delivery pipe, the two ends of which are connected to the outlet end of the evaporator and the inlet end of the compressor, respectively, so as to deliver the gas in the shell to the compressor through the second delivery pipe. The gas includes turbulent gas and gaseous refrigerant.

[0013] Controller;

[0014] A detection structure is installed on the second delivery pipe and connected to the controller to detect the real-time superheat of the turbulent gas in the second delivery pipe, so as to control the flow rate of the turbulent gas entering the turbulent pipe according to the real-time superheat.

[0015] Furthermore, the detection structure includes a temperature detection component for detecting the real-time temperature of the gas in the second delivery pipe;

[0016] A pressure detection component is used to detect the real-time pressure of the gas in the second delivery pipeline;

[0017] The controller is also used to calculate the real-time superheat based on the real-time temperature and real-time pressure, so as to control the flow rate of the turbulent gas entering the turbulent tube according to the real-time superheat.

[0018] Furthermore, the turbulent gas supply component is a flash generator; and / or,

[0019] The heat exchange system also includes a third delivery pipe, the two ends of which are connected to the condenser and the shell, respectively, to deliver liquid refrigerant into the shell.

[0020] Furthermore, the heat exchange system also includes a second regulating component, which is disposed on the third conveying pipe;

[0021] The controller, connected to the second regulating component, controls the flow rate of refrigerant delivered from the condenser to the housing.

[0022] According to another aspect of the present invention, a heat exchange method is provided, applicable to the above-described heat exchange system, the heat exchange method comprising starting the heat exchange system into operation;

[0023] When a liquid film appears on the surface of the evaporator tube, the real-time thickness of the liquid film is determined to determine whether a thermal boundary layer has been formed.

[0024] The flow rate of the turbulent gas supplied by the turbulent gas supply component to the turbulent pipe is controlled according to the real-time thickness, so as to control the flow rate of the turbulent gas ejected from the injection hole to the surface of the evaporator tube.

[0025] Furthermore, the step of determining the real-time thickness of the liquid film includes obtaining the real-time superheat of the turbulent gas in the second delivery pipe of the heat exchange system.

[0026] When the real-time superheat is determined to be greater than or equal to the first critical value, the opening degree of the first regulating component and the second regulating component is increased to increase the flow rate of the turbulent gas entering the turbulence tube and the flow rate of the refrigerant entering the casing.

[0027] Furthermore, the method for obtaining real-time superheat includes obtaining the real-time temperature and real-time pressure of the gas in the second delivery pipeline;

[0028] The saturation temperature of the turbulent gas is determined based on the real-time pressure.

[0029] Calculate the difference between the real-time temperature and the saturation temperature to obtain the real-time superheat.

[0030] By applying the technical solution of this invention, the heat exchange system of this application effectively solves a series of technical problems caused by the thermal boundary layer, such as decreased heat exchange efficiency, local overheating or drying, and reduced system energy efficiency ratio, through continuous micro-disturbance of the liquid film on the surface of the evaporator tube by turbulent gas. This turbulence technology exhibits more significant advantages, especially during low-load operation or the initial stage of system startup. It not only improves heat exchange efficiency and reduces the evaporation temperature difference but also extends the service life of the evaporator and reduces maintenance costs. More importantly, by monitoring the superheat and automatically adjusting the supply of turbulent gas, the system achieves on-demand regulation, avoiding excessive or insufficient turbulence and ensuring the stability and efficient operation of the system under various operating conditions. This is an innovative solution for improving the performance and economy of refrigeration systems. Attached Figure Description

[0031] The accompanying drawings, which form part of this application, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings:

[0032] Figure 1 A structural diagram of a heat exchange system according to an embodiment of this application is shown;

[0033] Figure 2 A schematic diagram of the structure of the baffle tube according to an embodiment of this application is shown.

[0034] The above figures include the following reference numerals:

[0035] 1. Turbulent gas supply component; 2. Evaporator; 21. Shell; 22. Evaporator tube; 23. Turbulent tube; 231. Turbulent inlet end; 24. Injection hole; 3. Compressor; 4. Condenser; 5. First delivery pipe; 6. First regulating component; 7. Second delivery pipe; 8. Temperature detection component; 9. Third delivery pipe; 10. Second regulating component. Detailed Implementation

[0036] It should be noted that, unless otherwise specified, the embodiments and features described in this application can be combined with each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0037] In the refrigeration industry, flooded evaporators are highly favored due to their efficient heat exchange capabilities and wide applicability. This evaporator design allows the refrigerant to evaporate under high liquid levels, expanding the contact area with the heat transfer medium and thus improving heat exchange efficiency. Traditional flooded evaporators typically enhance performance by improving the surface properties of the heat exchange tubes, such as using high-efficiency finned tubes or sintered surface tubes, to increase the heat exchange area and improve flow characteristics. However, while these passive heat transfer enhancement technologies improve the efficiency of flooded evaporators to some extent, their effectiveness becomes limited under specific operating conditions, such as low load, low flow rate, low superheat, or long-term stable operation.

[0038] Under the aforementioned operating conditions, a thermal boundary layer easily forms on the surface of the evaporator tube. This phenomenon, caused by the slow flow or stagnation of the refrigerant, leads to regular and low-frequency bubble formation, increased liquid film thickness, and thus significantly increased thermal resistance. The presence of this thermal boundary layer greatly reduces the heat transfer coefficient, forcing a larger evaporation temperature difference, thereby significantly reducing the system's coefficient of performance (COP). In some cases, efficiency can decrease by more than 20%. Furthermore, the stable structure of the boundary layer also leads to uneven evaporation, with the risk of localized overheating or drying. Simultaneously, stagnant areas of the liquid film are prone to the accumulation of oil, impurities, or moisture, which, in the long term, may cause scaling and carbon buildup, severely affecting heat exchange performance and shortening equipment lifespan.

[0039] The main objective of this invention is to provide a heat exchange system and method to solve the problem that the heat exchange efficiency of flooded evaporators in the prior art is significantly reduced due to the formation of a thermal boundary layer on the surface of the evaporator tubes under low load and low flow rate conditions.

[0040] Example 1

[0041] like Figures 1 to 2 As shown, this application embodiment first provides a heat exchange system, including a turbulent gas supply component 1, which is used to supply turbulent gas;

[0042] Evaporator 2 includes a shell 21, an evaporation tube 22, and a baffle tube 23. The evaporation tube 22 and the baffle tube 23 are both disposed inside the shell 21. The baffle tube 23 is located below the evaporation tube 22. The baffle tube 23 is provided with multiple injection holes 24. The baffle inlet end 231 of the baffle tube 23 is connected to the outlet end of the baffle gas supply component 1 to deliver baffle gas into the baffle tube 23, so as to spray baffle gas onto the surface of the evaporation tube 22 through the injection holes 24 to destroy the thermal boundary layer formed on the surface of the baffle tube 23.

[0043] Compressor 3, the inlet end of compressor 3 is connected to the outlet end of evaporator 2;

[0044] The condenser 4 has its inlet end connected to the outlet end of the compressor 3 and its outlet end connected to the inlet end of the evaporator 2. The two ends of the turbulence pipe 23 are closed.

[0045] Optionally, the turbulent gas supply component 1 is a flash generator.

[0046] In the heat exchange system proposed in this application, the first component to operate is the turbulent gas supply component 1, which generates and supplies turbulent gas, typically superheated vapor generated by a flash evaporator. This gas is then guided to the turbulent tube 23 inside the evaporator 2. The evaporator 2, as a key component of the system, integrates a shell 21, an evaporator tube 22, and the turbulent tube 23 located below the evaporator tube 22. The shell 21 encapsulates the entire heat exchange structure, providing the physical environment for heat exchange between the refrigerant vapor and the external medium. The evaporator tube 22 and the turbulent tube 23 are arranged inside the shell 21. Multiple injection holes 24 on the turbulent tube 23 introduce the turbulent gas from the turbulent gas supply component 1 into the space of the evaporator 2, directly acting on the liquid film on the surface of the evaporator tube 22, effectively breaking the thermal boundary layer and promoting the improvement of evaporation efficiency.

[0047] As the turbulent gas is ejected at high speed from the injection hole 24, it forms micro-turbulence on the surface of the evaporator tube 22. This not only significantly reduces the thermal resistance of the liquid film, but also increases the frequency and intensity of bubble generation, thereby improving the heat transfer coefficient. Under low load and low flow rate conditions, the injection of turbulent gas ensures the continuity and uniformity of the evaporation process, avoids the risk of local overheating or drying, and effectively inhibits the accumulation of oil, impurities or moisture, preventing scaling and carbon buildup. This is crucial for maintaining the long-term stable operation and heat transfer performance of the evaporator.

[0048] Subsequently, the refrigerant vapor generated in evaporator 2 is drawn into compressor 3 through its outlet. Compressor 3 compresses it into high-temperature and high-pressure vapor, providing driving force for the subsequent heat exchange process. The compressed vapor then enters condenser 4, where it releases heat and condenses into liquid. It then returns to evaporator 2 through the outlet of condenser 4, completing the closed loop of refrigerant circulation. It should be noted that the turbulence gas supply of turbulence pipe 23 is not limited to the initial stage when evaporator 2 starts up, but is dynamically adjusted in real time according to the superheat at the outlet of evaporator 2, ensuring the efficiency and flexibility of the system throughout the entire operating cycle.

[0049] In summary, the heat exchange system of this application effectively solves a series of technical problems caused by the thermal boundary layer, such as decreased heat exchange efficiency, local overheating or drying, and reduced system energy efficiency ratio, through continuous micro-disturbance of the liquid film on the surface of the evaporator tube 22 by turbulent gas. This turbulence technology exhibits more significant advantages, especially during low-load operation or the initial stage of system startup. It not only improves heat exchange efficiency and reduces the evaporation temperature difference but also extends the service life of the evaporator tube 22 and reduces maintenance costs. More importantly, by monitoring superheat and automatically adjusting the supply of turbulent gas, the system achieves on-demand control, avoiding excessive or insufficient turbulence and ensuring the stability and efficient operation of the system under various operating conditions. This represents an innovative solution for improving the performance and economy of refrigeration systems.

[0050] Furthermore, multiple injection holes 24 are arranged sequentially along the axial direction of the baffle tube 23.

[0051] This application further optimizes the design of the turbulence-disrupting tube 23 by using multiple injection holes 24 arranged sequentially along its axial direction to achieve uniform and efficient disturbance of the liquid film on the surface of the evaporator tube 22. This carefully arranged injection hole 24 ensures that the turbulent gas can be uniformly distributed across the entire surface of the evaporator tube 22 in a continuous pulse form, effectively breaking the thermal boundary layer, reducing thermal resistance, and thus significantly improving heat exchange efficiency.

[0052] By employing axially arranged sequentially arranged injection holes 24, the turbulent gas generates a series of tiny but dense bubbles on the surface of the evaporator tube 22. The generation and movement of these bubbles intensify the turbulence of the liquid, enhancing local turbulence and maintaining the liquid film in a relatively ideal state, thus avoiding the problem of poor heat transfer caused by an excessively thick liquid film. More importantly, this uniform disturbance strategy can prevent the risk of local overheating or drying out, ensuring the uniformity and stability of the evaporation process. It avoids the "hot spot" problem that may occur in traditional flooded evaporators during low load or start-up phases, improving the overall safety and reliability of the system.

[0053] Furthermore, the outlet ends of each injection hole 24 are arranged facing the surface of the evaporator tube 22.

[0054] By ensuring that the outlet end of the injection orifice 24 directly faces the surface of the evaporator tube 22, the turbulent gas impacts the liquid film surface with the shortest path and highest efficiency, generating a denser and more effective microturbulence effect. This directional disturbance not only rapidly reduces the liquid film thickness and decreases the formation of the thermal boundary layer, but also significantly enhances the turbulence of the liquid due to the direct action of the turbulent gas, accelerating the phase change process of the refrigerant and achieving faster and more thorough evaporation, thereby improving the heat dissipation efficiency of the entire system. Compared with non-directional injection, this method can more accurately target the area requiring enhanced heat exchange, avoiding ineffective energy diffusion and loss, and improving energy utilization efficiency.

[0055] Furthermore, the heat exchange system also includes: a first conveying pipe 5, the two ends of which are respectively connected to the turbulent gas supply component 1 and the turbulent pipe 23, so as to convey turbulent gas into the turbulent pipe 23 through the first conveying pipe 5;

[0056] The first regulating component 6 is disposed on the first conveying pipe 5 to regulate the flow rate of the turbulent gas entering the turbulence pipe 23.

[0057] Optionally, the first regulating component 6 is a flow regulating valve.

[0058] Optionally, the heat exchange system also includes a controller connected to the first regulating component 6 to control the opening of the first regulating component 6, thereby controlling the flow rate of the turbulent gas entering the turbulence pipe 23.

[0059] In the heat exchange system of this application, the precise delivery and regulation of the turbulent gas is a key step in achieving efficient heat exchange. The system is equipped with a first delivery pipe 5, one end of which is tightly connected to the turbulent gas supply component 1, and the other end is directly connected to the turbulence pipe 23 inside the evaporator 2, forming a direct channel for the turbulent gas from generation to application. The first regulating component 6 on the first delivery pipe 5 enables real-time and dynamic control of the turbulent gas flow rate.

[0060] During operation, the turbulent gas generated by the turbulent gas supply component 1, such as superheated steam, flows along the first delivery pipe 5 and reaches the turbulent tube 23. To ensure that the turbulent gas can function most effectively, the outlet ends of all injection holes 24 are designed to be precisely aligned with the surface of the evaporator tube 22. When the turbulent gas is injected onto the surface of the evaporator tube 22 through these injection holes 24, it directly impacts and disrupts the thermal boundary layer of the liquid film, significantly reducing thermal resistance and thus greatly improving heat exchange efficiency.

[0061] Under low load or insufficient evaporation conditions, the controller increases the opening of the flow control valve, which automatically increases the supply of turbulent gas to enhance the turbulence effect and ensure that the liquid film on the surface of the evaporator tube 22 is maintained in an optimal state, preventing the formation of a thermal boundary layer. Conversely, under high load or excessive evaporation conditions, the flow control valve reduces the flow rate of the turbulent gas to prevent excessive disturbance, thereby maintaining stable operation and optimal energy efficiency ratio of the system under different operating conditions.

[0062] Furthermore, the heat exchange system also includes a second conveying pipe 7, the two ends of which are connected to the outlet end of the evaporator 2 and the inlet end of the compressor 3, respectively, so as to convey the gas in the shell 21 to the compressor 3 through the second conveying pipe 7. The gas includes turbulent gas and gaseous refrigerant.

[0063] The controller is connected to the first adjusting component 6 to control the opening degree of the first adjusting component 6;

[0064] A detection structure is installed on the second conveying pipe 7 and connected to the controller to detect the real-time superheat of the turbulent gas in the second conveying pipe 7, so as to control the flow rate of the turbulent gas entering the turbulent pipe 23 according to the real-time superheat.

[0065] The newly added second conveying pipe 7 in the heat exchange system of this application is connected at one end to the outlet end of the evaporator 2 and at the other end directly to the inlet end of the compressor 3, thus constructing a gas transmission bridge from the inside of the evaporator 2 to the compressor 3. Through this design, the gas in the evaporator 2, including the turbulent gas injected by the turbulence pipe 23 and fully mixed with the gaseous refrigerant, can be smoothly transported to the compressor 3 through the second conveying pipe 7 to complete the key step of refrigerant circulation.

[0066] The detection structure is placed on the second delivery pipe 7 and can monitor the superheat of the turbulent gas inside the second delivery pipe 7 in real time. This real-time data is crucial for assessing the operating status of the evaporator 2, especially for identifying whether a thermal boundary layer has formed on the surface of the evaporator tube 22 and determining whether the turbulent gas has achieved the expected disturbance effect.

[0067] The controller is closely connected to the detection structure, enabling it to acquire superheat information of the turbulent gas in real time. Based on this real-time feedback, the controller can adjust the opening of the first regulating component 6 connected to it, precisely controlling the flow rate of the turbulent gas entering the turbulence tube 23. This regulation mechanism ensures that the supply of turbulent gas always matches the actual heat exchange demand of the evaporator 2, avoiding both energy waste caused by excess turbulent gas and insufficient turbulent gas that would prevent effective disruption of the thermal boundary layer.

[0068] Furthermore, the detection structure includes a temperature detection component 8 for detecting the real-time temperature of the gas inside the second delivery pipe 7;

[0069] A pressure detection component is used to detect the real-time pressure of the gas in the second delivery pipe 7;

[0070] The controller is also used to calculate the real-time superheat based on the real-time temperature and real-time pressure, so as to control the flow rate of the turbulent gas entering the turbulence tube 23 according to the real-time superheat.

[0071] During system operation, the temperature detection component 8 continuously monitors the real-time temperature of the gas, while the pressure detection component records the real-time pressure. This data is transmitted to the controller in real time. The controller combines the real-time temperature and pressure information and uses thermodynamic principles to calculate the real-time superheat of the gas. This key parameter directly reflects the heat exchange state inside the evaporator 2, especially the thickness and disturbance effect of the liquid film on the surface of the evaporator tube 22. Based on the calculated real-time superheat, the controller adjusts the opening of the first regulating component 6 in real time, that is, adjusts the flow rate of the turbulent gas entering the turbulent tube 23 through the first delivery pipe 5, to ensure that the supply of turbulent gas is precisely matched with the heat exchange requirements of the evaporator 2.

[0072] When the system detects a high degree of superheat, indicating that the liquid film on the surface of the evaporator tube 22 is too thick and the heat exchange efficiency is reduced, the controller will instruct the first regulating component 6 to increase the opening degree, thereby increasing the flow rate of the turbulent gas to enhance the turbulence of the liquid film, break the thermal boundary layer, and promote more efficient evaporation. Conversely, if the superheat is low, it indicates that the evaporation process may have been overdone, and excessive turbulent gas may cause the liquid to be washed away too quickly, affecting system stability. In this case, the controller will reduce the opening degree of the first regulating component 6 to reduce the supply of turbulent gas, ensuring a smooth and efficient evaporation process.

[0073] Through this design, this application achieves precise control of the turbulent gas flow rate, effectively enhancing the heat exchange process. Especially under special operating conditions of low load and low flow rate, it can significantly improve heat exchange efficiency, avoid the risks of uneven heat exchange and local overheating, and ensure the stability and safety of the system under various operating conditions. Simultaneously, the closed-loop control mechanism based on real-time superheat further optimizes energy utilization, reduces unnecessary energy consumption, and improves the overall energy efficiency and economy of the system.

[0074] Furthermore, the turbulent gas supply component 1 is a flash generator; and / or,

[0075] The heat exchange system also includes a third delivery pipe 9, the two ends of which are connected to the condenser 4 and the shell 21 respectively, to deliver liquid refrigerant into the shell 21.

[0076] The flash evaporator can extract turbulent gas from the superheated steam generated in the system. This design utilizes the system's own byproducts, achieving cascaded energy utilization. It can effectively break the thermal boundary layer on the surface of the evaporator tube without additional energy consumption, thus improving heat exchange efficiency.

[0077] By using a flash evaporator as the source of turbulent gas and combining it with the optimized distribution of liquid refrigerant through the third delivery pipe 9, this application achieves comprehensive energy management and enhanced heat transfer. On one hand, the flash evaporator utilizes superheated steam as a turbulent gas source, and by dynamically adjusting its flow rate, effectively enhances liquid film turbulence, breaks the thermal boundary layer, significantly reduces thermal resistance, and improves the control accuracy of the heat transfer coefficient and evaporation temperature difference. On the other hand, the addition of the third delivery pipe 9 ensures efficient utilization of the refrigerant within the evaporator, avoiding the risk of localized drying or overheating due to insufficient liquid supply, while also preventing energy waste caused by excessive liquid supply.

[0078] Furthermore, the heat exchange system also includes a second regulating component 10, which is disposed on the third conveying pipe 9;

[0079] The controller, connected to the second regulating component 10, controls the flow rate of refrigerant delivered from the condenser 4 to the housing 21.

[0080] Optionally, the second regulating component 10 is an electronic expansion valve.

[0081] The heat exchange system of this application achieves comprehensive optimization of the evaporator 2's performance by introducing a flash evaporator as a turbulent gas supply component 1, and through the coordinated operation of the third delivery pipe 9 and the second regulating component 10. The flash evaporator, as a superheated steam generator, is designed to provide a stable and controllable turbulent gas. This gas is directly injected onto the surface of the evaporator tube 22 through the micropores of the turbulence pipe 23, effectively breaking the thermal boundary layer, reducing thermal resistance, and enhancing the heat exchange process.

[0082] Meanwhile, the third delivery pipe 9 ensures that liquid refrigerant can be directly and efficiently delivered from the condenser 4 to the shell 21, providing sufficient refrigerant supply to the evaporator 2. The second regulating component 10, such as an electronic expansion valve, installed on the third delivery pipe 9, is closely connected to the controller, enabling precise control of the refrigerant flow rate. Based on the operating status of the evaporator 2, especially the real-time superheat data obtained through the temperature detection component 8 and pressure detection component, the controller adjusts the opening of the second regulating component 10 to control the flow rate of liquid refrigerant entering the shell 21, ensuring uniform liquid distribution inside the evaporator and avoiding energy waste caused by insufficient liquid supply leading to localized drying or excessive liquid supply.

[0083] Example 2

[0084] This application also provides a heat exchange method applicable to the above-mentioned heat exchange system, the heat exchange method including starting the heat exchange system into operation;

[0085] When a liquid film appears on the surface of the evaporator tube 22, the real-time thickness of the liquid film is determined to determine whether a thermal boundary layer has been formed.

[0086] The flow rate of the turbulent gas supplied by the turbulent gas supply component 1 to the turbulent tube 23 is controlled according to the real-time thickness, so that when the thermal boundary layer is formed, the flow rate of the turbulent gas ejected from the injection hole 24 to the surface of the evaporator tube 22 is controlled to disrupt the thermal boundary layer.

[0087] Furthermore, the step of determining the real-time thickness of the liquid film includes obtaining the real-time superheat of the turbulent gas in the second delivery pipe 7 of the heat exchange system.

[0088] When the real-time superheat is determined to be greater than or equal to the first critical value, the opening degree of the first regulating component 6 and the second regulating component 10 is increased to increase the flow rate of the turbulent gas entering the turbulence tube 23 and the flow rate of the refrigerant entering the casing 21.

[0089] Furthermore, the method for obtaining real-time superheat includes obtaining the real-time temperature and real-time pressure of the gas in the second delivery pipeline 7;

[0090] The saturation temperature of the turbulent gas is determined based on the real-time pressure.

[0091] Calculate the difference between the real-time temperature and the saturation temperature to obtain the real-time superheat.

[0092] During operation, the heat exchange system is activated. Its core components include a flash evaporator as the turbulent gas supply component 1, and precise control of the second regulating component 10 on the third conveying pipe 9 and the first regulating component 6 on the first conveying pipe 5 to optimize the liquid film management on the surface of the evaporator tube 22. When the system detects a liquid film on the surface of the evaporator tube 22, it automatically determines the real-time thickness of the liquid film. This determination relies not only on temperature and pressure sensors but also on the accurate calculation of the real-time superheat of the turbulent gas. Based on the comparison between the real-time superheat and a preset first critical value, the system can determine the state of the liquid film on the surface of the evaporator tube 22, thereby automatically adjusting the opening of the first regulating component 6 to control the flow rate of the turbulent gas, turbulent the liquid film in the optimal state, breaking the thermal boundary layer and significantly improving heat exchange efficiency. Simultaneously, by controlling the second regulating component 10, the system dynamically adjusts the flow rate of the liquid refrigerant entering the shell 21 to achieve a reasonable distribution of the liquid film on the surface of the evaporator tube 22, further optimizing the heat exchange process.

[0093] The process of obtaining real-time superheat involves real-time monitoring of the gas temperature and pressure within the second delivery pipe 7. Using temperature and pressure detection components 8 and combining thermodynamic principles, the real-time superheat of the turbulent gas is quickly calculated. When the real-time superheat reaches or exceeds a first critical value, ensuring the formation of a thermal boundary layer, the controller increases the opening of the first regulating component 6 and the second regulating component 10, thereby increasing the supply of turbulent gas and liquid refrigerant. This ensures a reasonable thickness and turbulence of the thermal boundary layer on the surface of the evaporator tube 22, achieving efficient heat exchange.

[0094] The heat exchange method described in this application enables the system to determine whether a thermal boundary layer has formed based on the real-time state of the liquid film on the surface of the evaporator tube 22. This allows for automatic adjustment of the flow rates of turbulent gas and liquid refrigerant, breaking through the heat exchange bottleneck caused by the thermal boundary layer, effectively reducing thermal resistance, and improving heat exchange efficiency. Furthermore, this method avoids the risks of uneven evaporation, localized overheating, and drying out, significantly improving the system's coefficient of performance (COP). Its advantages are particularly pronounced under low load or variable operating conditions. The intelligent control strategy based on real-time superheat not only optimizes energy utilization and reduces energy waste but also extends the evaporator's lifespan and reduces maintenance costs, demonstrating its strong potential for achieving efficient, stable, and economical operation in the field of refrigeration technology.

[0095] As can be seen from the above description, the embodiments of the present invention achieve the following technical effects:

[0096] During use, the heat exchange system is activated, which includes a flash evaporator as a turbulent gas supply component 1, an evaporator 2, a condenser 4, and a series of valves and pipes, together forming a complete refrigeration cycle system. As the system starts to run, the superheated steam generated by the flash evaporator is directed to the turbulence pipe 23 located below the evaporator shell 21 through the first delivery pipe 5. The micropores on the turbulence-distributing tube 23 are uniformly distributed, spraying superheated vapor into the surface of the evaporator tube 22 in the form of a fine airflow. This disrupts the thermal boundary layer of the liquid film, enhancing heat exchange efficiency. To further optimize the heat exchange process, a third delivery pipe 9 is used to deliver liquid refrigerant from the condenser 4 to the shell 21. On the third delivery pipe 9, a second regulating component 10 (such as an electronic expansion valve) is connected to the controller to dynamically adjust the refrigerant flow rate, ensuring that the liquid film on the surface of the evaporator tube 22 is in optimal condition, avoiding overheating or drying. The superheat of the gas in the second delivery pipe 7 is monitored in real time by the temperature detection component 8 and the pressure detection component. Once the superheat of the gas is detected to reach or exceed the first preset critical value, the system responds immediately. The controller commands the first regulating component 6 and the second regulating component 10 to increase their opening, thereby increasing the flow rate of the turbulent gas and liquid refrigerant. Conversely, if the superheat is below the second preset critical value, the opening will be reduced to prevent excessive disturbance of the liquid film.

[0097] This application achieves precise control of the evaporator heat exchange process. The injection of turbulent gas breaks the thermal boundary layer of the liquid film, significantly reducing thermal resistance and improving the heat transfer coefficient, especially under low load and low flow rate conditions. Simultaneously, the dynamic supply of liquid refrigerant further ensures uniform liquid film distribution, avoiding localized overheating and drying, thus improving heat exchange uniformity and system stability. Combined with real-time superheat monitoring and control, the system can dynamically adjust the flow rates of turbulent gas and refrigerant according to actual operating conditions, achieving on-demand supply, reducing energy loss, and improving the overall coefficient of performance (COP). This demonstrates outstanding capabilities in achieving high performance, high stability, and efficient energy utilization in the field of flooded evaporators. This technical solution not only optimizes the heat exchange performance of the evaporator but also improves the operating efficiency of the entire refrigeration system, representing a significant advancement in the pursuit of efficient and green refrigeration models in the field of refrigeration technology.

[0098] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0099] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps set forth in these embodiments do not limit the scope of the invention. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following figures denote similar items; therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.

[0100] In the description of this invention, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this invention; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0101] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0102] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0103] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A heat exchange system, characterized in that, include: Turbulent gas supply component (1), the turbulent gas supply component (1) is used to supply turbulent gas; Evaporator (2), the evaporator (2) includes a shell (21), an evaporation tube (22), and a turbulence tube (23). The evaporation tube (22) and the turbulence tube (23) are both disposed in the shell (21). The turbulence tube (23) is located below the evaporation tube (22). The turbulence tube (23) is provided with a plurality of injection holes (24). The turbulence inlet end (231) of the turbulence tube (23) is connected to the outlet end of the turbulence gas supply component (1) to deliver the turbulence gas into the turbulence tube (23) so as to spray the turbulence gas onto the surface of the evaporation tube (22) through the injection holes (24) to destroy the thermal boundary layer formed on the surface of the turbulence tube (23). The compressor (3) is connected to the outlet end of the evaporator (2); The condenser (4) has its inlet end connected to the outlet end of the compressor (3) and its outlet end connected to the inlet end of the evaporator (2).

2. The heat exchange system according to claim 1, characterized in that, The plurality of the injection holes (24) are arranged sequentially along the axial direction of the baffle tube (23); and / or, the outlet end of each of the injection holes (24) is arranged facing the surface of the evaporator tube (22).

3. The heat exchange system according to claim 1, characterized in that, The heat exchange system also includes: The first delivery pipe (5) has two ports connected to the turbulent gas supply component (1) and the turbulent pipe (23) respectively, so as to deliver the turbulent gas into the turbulent pipe (23) through the first delivery pipe (5); A first regulating component (6) is disposed on the first delivery pipe (5) to regulate the flow rate of the turbulent gas entering the turbulence pipe (23).

4. The heat exchange system according to claim 2, characterized in that, The heat exchange system also includes: The second conveying pipe (7) has two ports connected to the outlet end of the evaporator (2) and the inlet end of the compressor (3) respectively, so as to convey the gas in the housing (21) to the compressor (3) through the second conveying pipe (7). The gas includes turbulent gas and gaseous refrigerant. Controller; A detection structure is installed on the second conveying pipe (7) and connected to the controller to detect the real-time superheat of the turbulent gas in the second conveying pipe (7) and to control the flow rate of the turbulent gas entering the turbulent pipe (23) according to the real-time superheat.

5. The heat exchange system according to claim 4, characterized in that, The detection structure includes: Temperature detection component (8) is used to detect the real-time temperature of the gas in the second delivery pipe (7); A pressure detection component is used to detect the real-time pressure of the gas in the second delivery pipe (7); The controller is also used to calculate the real-time superheat based on the real-time temperature and the real-time pressure, so as to control the flow rate of the turbulent gas entering the turbulence tube (23) based on the real-time superheat.

6. The heat exchange system according to claim 1, characterized in that, The turbulent gas supply component (1) is a flash generator; and / or, The heat exchange system also includes a third delivery pipe (9), the two ends of which are connected to the condenser (4) and the shell (21) respectively, to deliver liquid refrigerant into the shell (21).

7. The heat exchange system according to claim 6, characterized in that, The heat exchange system also includes: The second adjusting component (10) is disposed on the third conveying pipe (9); The controller, connected to the second regulating component (10), controls the flow rate of refrigerant delivered from the condenser (4) to the housing (21).

8. A heat exchange method applicable to the heat exchange system according to any one of claims 1 to 7, characterized in that, The heat exchange method includes: Start the heat exchange system to run; When a liquid film appears on the surface of the evaporator tube (22), the real-time thickness of the liquid film is determined to determine whether a thermal boundary layer is formed. The flow rate of the turbulent gas supplied by the turbulent gas supply component (1) to the turbulent pipe (23) is controlled according to the real-time thickness control, so as to control the flow rate of the turbulent gas ejected from the injection hole (24) to the surface of the evaporation pipe (22).

9. The heat exchange method according to claim 8, characterized in that, The steps for determining the real-time thickness of the liquid film include: Obtain the real-time superheat of the turbulent gas in the second delivery pipe (7) of the heat exchange system; When the real-time superheat is determined to be greater than or equal to the first critical value, the opening of the first regulating component (6) and the second regulating component (10) is increased to increase the flow rate of the turbulent gas entering the turbulence tube (23) and the flow rate of the refrigerant entering the housing (21).

10. The heat exchange method according to claim 9, characterized in that, The method for obtaining the real-time superheat includes: Obtain the real-time temperature and pressure of the gas in the second delivery pipeline (7); The saturation temperature of the turbulent gas is determined based on the real-time pressure. The difference between the real-time temperature and the saturation temperature is calculated to obtain the real-time superheat.

Images