Heat exchanger assisted cooling device and method

Abstract

The application relates to a heat exchanger auxiliary cooling device and method, and belongs to the technical field of heat exchanger related equipment. The heat exchanger auxiliary cooling device comprises a spray head assembly and a temperature and pressure control assembly. The output end of the spray head assembly faces the heat exchanger. The temperature and pressure control assembly is connected with the input side of the heat exchanger, and the temperature and pressure control assembly is electrically connected with the spray head assembly. The temperature and pressure control assembly is configured to detect the real-time temperature of the input side and adjust the spraying pressure of the spray head assembly according to the real-time temperature. That is, the application can change the liquid supply flow and gas supply flow of the spray head assembly according to the actual temperature of the input side of the heat exchanger, so as to change the cooling intensity, and solves the problems of environmental limitations, poor adaptability and inability to adjust.

Description

Technical Field

[0001] This application relates to the technical field of heat exchanger-related equipment, and in particular to an auxiliary cooling device and method for heat exchangers. Background Technology

[0002] As a core component of refrigeration and heat exchange systems, heat exchangers are prone to problems such as localized overheating, decreased heat exchange efficiency, coking, scaling, and even component damage under high load, high temperature, flow fluctuation, or poor heat dissipation conditions. Traditional heat exchanger cooling methods mostly rely on the heat exchange of the medium itself or passive heat dissipation, which have drawbacks such as slow response, uneven cooling, and low temperature control accuracy.

[0003] Chinese patent CN203258669U discloses a composite flow layer heat exchanger that addresses the problem in existing technologies where the low heat transfer coefficient of flue gas-liquid heat exchangers leads to flue gas temperatures exceeding 100°C upon exiting the heat exchanger, resulting in water vapor generation during subsequent dust removal processes. This solution uses a liquid sprayer to atomize water at the heat exchanger inlet. After mixing with the high-temperature flue gas, the water rapidly evaporates, carrying away a significant amount of heat and significantly reducing the inlet temperature, thereby improving the heat transfer coefficient. While this solution effectively lowers the inlet temperature, it relies on mixing with the internal heat exchange medium, limiting its applicability to various heat exchanger types, and it lacks automatic adjustment and the ability to ensure the spray volume is suitable for different operating conditions.

[0004] Therefore, there is a need to develop an auxiliary cooling device for heat exchangers that is applicable to all types of heat exchangers and has an automatic adjustment function. Summary of the Invention

[0005] The present application provides an auxiliary cooling device for a heat exchanger, which dynamically adjusts the spray pressure of the nozzle assembly according to the real-time temperature of the heat exchanger, effectively solving the technical problems of limited use environment, poor adaptability, and inability to adjust; another objective of the present application is to provide an auxiliary cooling method for a heat exchanger.

[0006] To achieve the above objectives, according to a first aspect of this application, a heat exchanger auxiliary cooling device is provided, comprising:

[0007] A nozzle assembly, the output end of which faces the heat exchanger;

[0008] A temperature and pressure control component is connected to the input side of the heat exchanger and is electrically connected to the nozzle assembly; the temperature and pressure control component is configured to detect the real-time temperature of the input side and to adjust the injection pressure of the nozzle assembly according to the real-time temperature.

[0009] This solution uses a temperature and pressure control component to detect the real-time temperature on the input side of the heat exchanger, and adjusts the spray pressure of the nozzle assembly according to the real-time temperature, thereby achieving efficient cooling of the input side of the heat exchanger.

[0010] In some embodiments, the nozzle assembly includes:

[0011] Multiple nozzles are provided, spaced apart from the heat exchanger. Each nozzle has a liquid supply chamber, an air supply chamber, and a spray nozzle. The liquid supply chamber and the air supply chamber are spaced apart, and the spray nozzle is connected to the air supply chamber.

[0012] The liquid supply pipeline has multiple liquid outlets and at least one liquid inlet, each of the liquid outlets being connected to the liquid supply chamber of one of the nozzles, and the liquid inlet being connected to external coolant.

[0013] The air supply pipeline has multiple air outlets and at least one air inlet, each of the air outlets being connected to the air supply chamber of one of the nozzles, and the air inlet being connected to an external gas medium.

[0014] The swirling atomizing core is housed within the liquid supply chamber;

[0015] A solenoid valve is installed on the liquid supply line and electrically connected to the temperature and pressure control component. The temperature and pressure control component can adjust the solenoid valve according to the real-time temperature so as to adjust the spray pressure of the nozzle assembly.

[0016] This solution has multiple nozzles, allowing the spray range to cover a larger area on the input side of the heat exchanger, resulting in a larger and more uniform spray range. Furthermore, this solution uses a temperature and pressure control component to detect the real-time temperature on the input side of the heat exchanger and adjusts the solenoid valve based on the real-time temperature, thereby regulating the spray pressure and achieving efficient cooling of the input side of the heat exchanger.

[0017] In some embodiments, the nozzle assembly further includes a one-way valve disposed on the air supply line.

[0018] This design incorporates a check valve to prevent the gas medium from flowing back into the gas supply line.

[0019] In some embodiments, the temperature and pressure control component includes:

[0020] A housing having a receiving cavity;

[0021] A temperature detection module is located on the side of the housing facing the heat exchanger and is in contact with the input side;

[0022] The processing module is housed within the receiving cavity and connected to the housing, and the processing module is electrically connected to the temperature detection module;

[0023] A pressure control module is housed within the receiving cavity and spaced apart from the processing module. The pressure control module is electrically connected to both the processing module and the solenoid valve.

[0024] The housing in this solution is used to protect the internal components of the temperature and pressure control assembly. The processing module is used to receive and process real-time temperature signals, and the pressure control module adjusts the solenoid valve to regulate the spray pressure of the nozzle.

[0025] In some embodiments, the nozzle further includes:

[0026] The nozzle body is connected to the liquid supply line and the air supply line respectively. The liquid supply chamber and the air supply chamber are both opened inside the nozzle body. The spray port is opened at the end of the nozzle body away from the liquid supply line.

[0027] A liquid supply channel extends along the axial direction of the nozzle, passing through one end of the nozzle body facing the liquid supply pipeline, and communicates with the liquid supply chamber;

[0028] An air supply channel, one end of which is connected to the air supply chamber, and the other end of which is connected to an air outlet.

[0029] This solution can achieve spraying, which, compared to direct liquid spraying that impacts the heat exchanger's outer shell, not only achieves a cooling effect but also prevents damage caused by impact. In addition, the airflow from the nozzle in this solution makes the spray droplets finer, so the airflow entrained in the spray can accelerate the evaporation heat exchange and the convective heat exchange between the droplets and the heat exchanger.

[0030] In some embodiments, the central axis of the liquid supply channel intersects the central axis of the gas supply channel.

[0031] In this scheme, the liquid and gas have an angle between their entry directions, and the liquid or gas enters with a certain acceleration, which can improve the mixing effect.

[0032] According to a second aspect of this application, a heat exchanger auxiliary cooling method is provided, which utilizes the heat exchanger auxiliary cooling device described in any of the preceding claims for cooling, the heat exchanger auxiliary cooling method comprising:

[0033] S100. The real-time temperature of the heat exchanger input side is detected by the temperature detection module of the temperature and pressure control component, and the real-time temperature is transmitted to the processing module of the temperature and pressure control component.

[0034] S200. Based on the real-time temperature received by the processing module, and according to the graded control rules built into the processing module, determine the working mode of the nozzle assembly.

[0035] S300, The pressure control module of the temperature and pressure control component adjusts the spray pressure of the nozzle assembly according to the working mode.

[0036] In some embodiments, the hierarchical control rules in step S200 include a first threshold range, a second threshold range, and a third threshold range, wherein the maximum value of the third threshold range is less than the minimum value of the first threshold range, and the maximum value of the first threshold range is less than the minimum value of the second threshold range.

[0037] In some embodiments, the working modes in step S200 include standby mode, first-level intensity cooling mode and second-level intensity cooling mode. In the standby mode, the nozzle assembly is only powered on and does not perform cooling operations.

[0038] In both the first-level intensity cooling mode and the second-level intensity cooling mode, the nozzle assembly undergoes cooling operations, and the spray pressure of the nozzle assembly in the first-level intensity cooling mode is lower than the spray pressure of the nozzle assembly in the second-level intensity cooling mode.

[0039] The third threshold range corresponds to the standby mode, the first threshold range corresponds to the first-level intensity cooling mode, and the second threshold range corresponds to the second-level intensity cooling mode.

[0040] In some embodiments, the processing module includes a PID controller, which incorporates a fuzzy PID adaptive control algorithm, the fuzzy PID adaptive control algorithm being based on temperature deviation. Rate of change with temperature deviation For fuzzy input, the scaling factor is adjusted online via fuzzy inference. Integral coefficient Differential coefficients Output ratio increment Integral increment Differential increment To adapt to the real-time temperature changes of the heat exchanger under the first-level intensity cooling mode and the second-level intensity cooling mode, the specific steps of the fuzzy PID adaptive control algorithm are as follows:

[0041] S400, Input fuzzification, calculate the temperature deviation Rate of change with temperature deviation The data is converted into a fuzzy set, and the fuzzy set is divided into fuzzy subsets {NB (negative large), NS (negative small), ZO (zero), PS (positive small), PB (positive large)}, and the membership function of the fuzzy subsets is determined.

[0042] S500, Formulate fuzzy rules;

[0043] S600. Fuzzy inference: Based on the input fuzzy set and fuzzy rules, obtain the fuzzy parameter correction amount. , , ;

[0044] S700. Defuzzify, and adjust the fuzzy parameter correction amount obtained in the fuzzy inference. , , Convert to precise values ​​for real-time parameters , , Perform online correction and output the current parameters. , , ;

[0045] S800, Obtain the injection pressure based on the current parameters. , , The injection pressure of the nozzle assembly was calculated.

[0046] In some embodiments, temperature deviation The calculation formula is as follows:

[0047]

[0048] In formula (1): This represents the real-time temperature of the heat exchanger at time I-1. The real-time temperature of the heat exchanger at time I;

[0049] Temperature deviation change rate The calculation formula is as follows:

[0050]

[0051] In formula (2): This represents the temperature deviation change, specifically the temperature deviation difference between two sampling times. This refers to the time variation, i.e., the sampling period or the time interval between two calculations;

[0052] Current parameters , , The calculation formulas are as follows:

[0053]

[0054]

[0055]

[0056] In formulas (3), (4) and (5): This is a real-time scaling factor. For real-time integral coefficients, For real-time differential coefficients, For proportional increments, For the integral increment, For differential increments, This is the corrected current scaling factor. The corrected current integral coefficients, These are the corrected current differential coefficients;

[0057] Injection pressure The calculation formula is as follows:

[0058]

[0059] In formula (6): This is the corrected current scaling factor. For temperature deviation, The corrected current integral coefficients, This refers to the time variation, i.e., the sampling period or the time interval between two calculations. These are the corrected current differential coefficients. This represents the change in temperature deviation, specifically the temperature deviation difference between two samplings.

[0060] This application has one of the following beneficial effects:

[0061] The heat exchanger auxiliary cooling device of this application includes a nozzle assembly and a temperature and pressure control assembly. The output end of the nozzle assembly faces the heat exchanger, and the temperature and pressure control assembly is connected to the input side of the heat exchanger and electrically connected to the nozzle assembly. The temperature and pressure control assembly is configured to detect the real-time temperature on the input side and adjust the injection pressure of the nozzle assembly according to the real-time temperature. In other words, this application can change the liquid supply flow rate of the nozzle assembly according to the real-time temperature on the input side of the heat exchanger, thereby changing the cooling intensity and solving the problems of limited operating environment, poor adaptability, and inability to adjust.

[0062] Other features and advantages of this application will be described in detail in the following detailed description section. Attached Figure Description

[0063] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0064] To gain a more complete understanding of this application and its beneficial effects, the following description will be provided in conjunction with the accompanying drawings, wherein the same reference numerals in the following description denote the same parts.

[0065] Figure 1 This is a schematic diagram showing the location and installation of an auxiliary cooling device for a heat exchanger provided in an exemplary embodiment of this disclosure;

[0066] Figure 2 This is a schematic diagram of the structure of the nozzle assembly provided in an exemplary embodiment of this disclosure;

[0067] Figure 3 This is a cross-sectional structural diagram of the nozzle provided in an exemplary embodiment of this disclosure;

[0068] Figure 4 This is a schematic diagram of signal transmission of components within a temperature and pressure control assembly provided in an exemplary embodiment of this disclosure;

[0069] Figure 5 This is an example flowchart of an auxiliary cooling method for a heat exchanger provided in an exemplary embodiment of this disclosure;

[0070] Figure 6 This is a real-time temperature change graph of the evaporator input side in an example provided in an exemplary embodiment of this disclosure;

[0071] Figure 7 This is a graph showing the spray pressure variation of the corrected fuzzy control output in one example provided in an exemplary embodiment of this disclosure.

[0072] Explanation of reference numerals in the attached figures:

[0073] 100, Heat exchanger; 110, First heat exchanger body; 120, Second heat exchanger body; 130, Inlet pipe; 140, First transfer pipe; 150, Second transfer pipe; 160, Outlet pipe; 170, Flat tube; 180, Fin;

[0074] 200. Nozzle assembly; 210. Nozzle; 211. Spray nozzle; 212. Nozzle body; 213. Liquid supply channel; 214. Air supply channel; 215. Liquid supply chamber; 216. Air supply chamber; 220. Liquid supply pipeline; 230. Air supply pipeline; 240. Swirl atomizing core; 250. Solenoid valve;

[0075] 300. Temperature and pressure control component; 310. Housing; 320. Temperature detection module; 330. Processing module; 340. Pressure control module. Detailed Implementation

[0076] The technical solutions of the embodiments of this application 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 this application, and not all of them. All other embodiments obtained by those skilled in the art based on the embodiments of this application without creative effort are within the protection scope of this application.

[0077] It should be noted that the terms "first," "second," etc., in the specification, claims, and accompanying drawings of this application are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate so that the embodiments of this application described herein can be implemented in orders other than those illustrated or described herein. Furthermore, they should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, features defined with "first" or "second" may explicitly or implicitly include one or more features. In the description of this application, unless otherwise stated, "multiple" means two or more. "And / or" describes the relationship between related objects, indicating that three relationships can exist; for example, A and / or B can represent: A alone, A and B simultaneously, or B alone. The character " / " generally indicates that the preceding and following related objects are in an "or" relationship. Furthermore, the terms “comprising” and “having”, and any variations thereof, are intended to cover non-exclusive inclusion, such that a process, method, system, product, or apparatus that includes a series of steps or units is not necessarily limited to those steps or units that are explicitly listed, but may include other steps or units that are not explicitly listed or that are inherent to such process, method, product, or apparatus.

[0078] As a core component of refrigeration and heat exchange systems, heat exchangers are prone to problems such as localized overheating, decreased heat exchange efficiency, coking, scaling, and even component damage under high load, high temperature, flow fluctuation, or poor heat dissipation conditions. Traditional heat exchanger cooling methods mostly rely on the heat exchange of the medium itself or passive heat dissipation, which have drawbacks such as slow response, uneven cooling, and low temperature control accuracy.

[0079] Although cooling devices for heat exchangers exist in related technologies, these devices mostly use continuous cooling methods and cannot be dynamically adjusted according to actual operating conditions. This can have an adverse effect on the heat exchange efficiency of the heat exchanger even when it is not in a poor operating condition.

[0080] Therefore, this application provides an auxiliary cooling device for heat exchangers to at least solve some of the problems existing in related technologies.

[0081] According to the first aspect of this application, please refer to Figure 1This embodiment provides an auxiliary cooling device for a heat exchanger, which includes a nozzle assembly 200 and a temperature and pressure control assembly 300. The output end of the nozzle assembly 200 faces the heat exchanger 100, enabling it to spray a cooling medium onto the heat exchanger 100 to achieve gas-liquid composite cooling. The temperature and pressure control assembly 300 is connected to the input side of the heat exchanger 100 and is electrically connected to the nozzle assembly 200. The temperature and pressure control assembly 300 detects the real-time temperature of the input side of the heat exchanger 100 and adjusts the spray pressure of the nozzle assembly 200 according to the real-time temperature, thereby regulating the cooling intensity.

[0082] It should be noted that the input side of heat exchanger 100 refers to the side where the cooling medium inlet is located. That is, the input side is the starting area where the cooling medium enters the heat exchanger 100. By detecting the temperature in this area, the temperature and pressure control component 300 can more timely and accurately reflect the current heat load status of the heat exchanger 100.

[0083] In some examples, the temperature and pressure control component 300 is connected to the housing of the heat exchanger 100 and is located on the input side of the heat exchanger 100. Regarding the installation method of the nozzle assembly 200, the nozzle assembly 200 can be directly connected to the housing of the heat exchanger 100, in which case the nozzle assembly 200 and the temperature and pressure control component 300 are structurally independent; the nozzle assembly 200 can also be directly connected to the temperature and pressure control component 300.

[0084] In some embodiments, please refer to Figure 1 and Figure 2 The aforementioned nozzle assembly 200 includes multiple nozzles 210, a liquid supply line 220, a gas supply line 230, a solenoid valve 250, and a swirl atomizing core 240. The multiple nozzles 210 are spaced apart from the heat exchanger 100, with appropriate spray spacing reserved for the nozzles 210 to ensure that the cooling medium can uniformly cover the surface of the heat exchanger 100 near the input side. Each nozzle 210 has a liquid supply chamber 215, a gas supply chamber 216, and a spray nozzle 211. The liquid supply chamber 215 and the gas supply chamber 216 are spaced apart, meaning they are independent of each other. The outlet of the liquid supply chamber 215 faces the heat exchanger 100, and the spray nozzle 211 communicates with the gas supply chamber 216. Specifically, the liquid output from the liquid supply chamber 215 and the gas output from the gas supply chamber 216 mix outside the nozzle 210 to form a cooling medium, which is then sprayed towards the heat exchanger 100.

[0085] Understandably, multiple nozzles 210 can increase the spray coverage and improve uniformity. The spray coverage area of ​​a single nozzle 210 is limited, making it difficult to fully cover a large or irregularly shaped heat exchanger 100. Arranging multiple nozzles 210 allows the spray areas to overlap or connect, forming a complete cooling coverage layer and avoiding cooling blind spots. Furthermore, multiple nozzles 210 provide redundancy: when one nozzle 210 becomes clogged or malfunctions, the remaining nozzles 210 can still maintain basic cooling functions, preventing the entire cooling assembly from failing, thereby improving reliability and fault tolerance.

[0086] The liquid supply line 220 has multiple outlets (not shown in the figure) and at least one inlet (not shown in the figure). Each outlet is connected to the liquid supply chamber 215 of a nozzle 210, and the inlet is connected to coolant. The inlet is connected to a coolant reservoir or other storage device containing coolant, which can be water, cooling water, or a liquid mixture with added antifreeze. It should be noted that the liquid supply line 220 can be configured with a main pipe combined with branch pipes. The main pipe connects to the inlet, and the branch pipes extend from the main pipe, forming outlets at their ends and connecting to each nozzle 210. This arrangement is simple in structure, provides balanced pressure, and ensures that each nozzle 210 receives a consistent liquid supply pressure. The material of the liquid supply line 220 can be selected according to the properties of the coolant, such as stainless steel, copper, or corrosion-resistant plastic.

[0087] The air supply line 230 has multiple air outlets (not shown in the figure) and at least one air inlet (not shown in the figure). Each air outlet is connected to the air supply chamber 216 of a nozzle 210, and the air inlet is connected to a gaseous medium. It should be noted that the gaseous medium includes, but is not limited to, compressed air, nitrogen, carbon dioxide, argon, or other inert gases. Specifically, coolant enters the liquid supply chamber 215 of the nozzle 210 via the liquid supply line 220, while the gaseous medium also enters the air supply chamber 216 via the air supply line 230.

[0088] The swirling atomizing core 240 is housed within the liquid supply chamber 215. After flowing in through the liquid supply channel 213, the coolant undergoes high-speed rotation under the action of the swirling atomizing core 240, forming a liquid film. The injection nozzle 211 is arranged circumferentially along the nozzle 210. When the liquid film is ejected from the swirling atomizing core 240, the gas medium output from the air supply chamber 216 is simultaneously ejected through the injection nozzle 211, impacting the liquid film at high speed and further breaking it into tiny droplets, thereby achieving fine atomization.

[0089] Solenoid valve 250 is installed on the liquid supply line 220 and electrically connected to the temperature and pressure control component 300. The temperature and pressure control component 300 can adjust solenoid valve 250 according to the real-time temperature to regulate the spray pressure of nozzle assembly 200. It should be noted that when the detected real-time temperature is high, the temperature and pressure control component 300 increases the opening of solenoid valve 250, while simultaneously increasing the liquid supply pressure and air supply pressure, thereby increasing the liquid flow rate and atomization intensity, and improving the composite cooling effect. When the real-time temperature is low, the opening of solenoid valve 250 is reduced, decreasing the liquid supply flow rate and air supply pressure to avoid excessive cooling that could adversely affect the heat exchange efficiency of heat exchanger 100. This achieves on-demand, rapid cooling control.

[0090] In some examples, see 2 and Figure 3 The air supply chamber 216 is a cavity surrounding the liquid supply chamber 215. Each nozzle 210 is connected to one liquid inlet and multiple air inlets, which are distributed circumferentially around the nozzle 210. Multiple airflows from different directions can be more evenly distributed after entering the air supply chamber 216, thus making the internal pressure of the air supply chamber 216 more balanced, and the gas flow rate and velocity ejected from each nozzle 211 tend to be consistent. When the liquid film is ejected from the swirling atomizing core 240, the uniform and stable airflow can exert a more balanced impact and shear on the liquid film, breaking it into smaller and more evenly distributed droplets, thereby improving the atomization effect and atomization uniformity.

[0091] In some embodiments, pressure regulating valves (not shown in the figure) are provided on both the liquid supply line 220 and the gas supply line 230. The function of the pressure regulating valve is to maintain the pressure stability in the line and eliminate pressure pulsations caused by upstream pressure fluctuations or downstream flow changes.

[0092] A pressure stabilizing valve is installed on the liquid supply line 220 to avoid pressure fluctuations caused by changes in the liquid level of the storage tank and ensure the controllability of the liquid supply flow. A pressure stabilizing valve is installed on the air supply line 230 to avoid air pressure instability caused by fluctuations in the air source pressure or uneven flow distribution from multiple nozzles 210, ensuring the stability of the atomization effect.

[0093] In some embodiments, the nozzle assembly 200 further includes a one-way valve (not shown) disposed on the air supply line 230. It should be noted that the one-way valve allows gas to flow unidirectionally in the air supply direction (i.e., from the air source to the air supply chamber 216), while preventing the gas medium from flowing back into the air supply line 230.

[0094] In some embodiments, please refer to Figure 4 The aforementioned temperature and pressure control assembly 300 includes a housing 310, a temperature detection module 320, a processing module 330, and a pressure control module 340. The housing 310 has a receiving cavity for housing and protecting the internal components.

[0095] The temperature detection module 320 is located on the side of the housing 310 facing the heat exchanger 100 and is in contact with the input side. It is used to collect the temperature signal from the input side in real time. That is, the detection point of the temperature detection module 320 is set on the input side of the heat exchanger 100 because the temperature on the input side of the heat exchanger 100 is the highest. Detecting this location can reflect the current peak heat load faced by the heat exchanger 100, thereby promptly initiating cooling regulation and reducing the occurrence of overheating under high load. Specifically, the temperature detection module 320 can be a surface-mount high-precision temperature sensor. The surface-mount sensor surface is tightly attached to the outer wall of the input side of the heat exchanger 100, offering advantages such as small size, fast response, and convenient installation. It eliminates the need for mounting holes in the pipes, avoiding the risk of leakage. To further improve measurement accuracy, thermally conductive silicone grease can be applied to the contact surface to reduce contact thermal resistance. The sensor can be fixed to the outer wall of the input side by clamps or adhesive. It should be noted that the temperature monitoring accuracy is ≤ ±0.5℃, and the response time is ≤ 100ms.

[0096] The processing module 330 is housed within the receiving cavity and connected to the housing 310, and is electrically connected to the temperature detection module 320. The processing module 330 has pre-set control logic that stores the correspondence between temperature thresholds and pressure regulation. After receiving the temperature signal acquired by the temperature detection module 320, the processing module 330 compares and calculates it with the threshold in the pre-set logic, and generates corresponding control commands based on the comparison result.

[0097] The pressure control module 340 is housed within the receiving cavity and spaced apart from the processing module 330 to reduce electromagnetic interference. The pressure control module 340 is electrically connected to both the processing module 330 and the solenoid valve 250. The pressure control module 340 converts the commands issued by the processing module 330 into electrical signals, driving the solenoid valve 250 to adjust the liquid supply pressure, thereby changing the liquid supply flow rate of the nozzle assembly 200.

[0098] As can be seen from the above technical solution, the temperature and pressure control component 300 of this embodiment sets the temperature detection module 320 on the input side of the heat exchanger 100 with the highest temperature, which can directly reflect the peak heat load. The processing module 330 judges the temperature signal according to the preset control logic, and drives the solenoid valve 250 to adjust the liquid supply pressure through the pressure control module 340, thereby changing the liquid supply flow of the nozzle assembly 200, realizing dynamic cooling of the heat exchanger 100. It can not only start the cooling regulation in time under high load or high temperature conditions to reduce the risk of overheating, but also avoid excessive cooling under low load conditions, which would have an adverse effect on the heat exchange efficiency of the heat exchanger 100 itself.

[0099] In some examples, the processing module 330 within the temperature and pressure control component 300 incorporates a fuzzy PID adaptive closed-loop algorithm. This algorithm uses the real-time temperature collected by the temperature detection module 320 as feedback input and the gas-liquid two-phase spray pressure as control output, automatically tuning the proportional, integral, and derivative coefficients of the PID controller online using fuzzy logic. The processing module 330 transmits the algorithm's calculation results to the pressure control module 340, which converts them into electrical signals to drive the solenoid valve 250, achieving precise adjustment of the spray pressure of the nozzle assembly 200 and stably controlling the thermodynamic temperature fluctuation of the heat exchanger 100 to meet ≤±3K.

[0100] In some embodiments, please refer to Figure 2 and Figure 3 The aforementioned nozzle 210 includes a nozzle body 212, a liquid supply channel 213, and a gas supply channel 214. The nozzle body 212 is connected to both the liquid supply line 220 and the gas supply line 230, and is used to receive liquid and gaseous media. Both the liquid supply chamber 215 and the gas supply chamber 216 are located within the nozzle body 212. The injection port 211 is located at the end of the nozzle body 212 furthest from the liquid supply line 220, and is used to spray the gaseous medium towards the liquid film.

[0101] The liquid supply channel 213 extends axially through one end of the nozzle body 212 toward the liquid supply line 220 and is connected to the liquid supply chamber 215, for introducing liquid medium into the liquid supply chamber 215. One end of the gas supply channel 214 is connected to the gas supply chamber 216, and the other end of the gas supply channel 214 is connected to a gas outlet, for introducing gas medium into the gas supply chamber 216.

[0102] Specifically, after the coolant enters the supply chamber 215 through the supply channel 213, it undergoes high-speed rotation under the action of the swirling atomizing core 240, forming a liquid film. The gaseous medium enters the supply chamber 216 through the supply channel 214, is evenly distributed circumferentially, and is ejected at high speed from the injection port 211. When the liquid film is ejected from the swirling atomizing core 240, it encounters the high-speed airflow and is broken into tiny droplets under the action of aerodynamic shear force, thus achieving atomization.

[0103] In some embodiments, please refer to Figure 2 and Figure 3The central axis of the liquid supply channel 213 intersects with the central axis of the air supply channel 214. It should be noted that arranging the liquid supply channel 213 and the air supply channel 214 with intersecting central axes allows the coolant output from the liquid supply line 220 and the gas output from the air supply line 230 to flow in opposite directions upon entering the nozzle 210. During this process, the gas medium already possesses initial acceleration within the air supply channel 214, resulting in a high flow velocity. This airflow with initial velocity collides and mixes with the liquid in the intersection area, more effectively tearing the liquid apart and providing favorable conditions for the subsequent atomization process. This intersecting arrangement helps improve the uniformity of gas-liquid mixing, thereby improving the atomization effect.

[0104] In some embodiments, please refer to Figure 3 The central axis of the liquid supply channel 213 intersects the central axis of the gas supply channel 214 to form an angle α, satisfying 0° < α ≤ 90°. Specifically, the angle α can be any value from 1°, 10°, 20°, 30°, 40°, 50°, 60°, 70°, 80°, and 90°, or any value within any range between any two of the above values. By reasonably configuring the angle α, the high-speed gas can have a certain inlet acceleration, which can enhance the gas-liquid collision effect.

[0105] For a specific example, please refer to Figure 1 The heat exchanger 100 may include a first heat exchange body 110 and a second heat exchange body 120. The first heat exchange body 110 and the second heat exchange body 120 are arranged sequentially along the thickness direction of the heat exchanger 100. The first heat exchange body 110 has an inlet pipe 130 on one side of the length direction of the heat exchanger 100 and a first transfer pipe 140 on the other side. The second heat exchange body 120 has an outlet pipe 160 on the same side as the inlet pipe 130, and a second transfer pipe 150 on the side away from the outlet pipe 160. The first transfer pipe 140 and the second transfer pipe 150 are connected. Multiple flat tubes 170 are distributed between the inlet pipe 130 and the first transfer pipe 140 along the width direction of the heat exchanger 100. Each flat tube 170 is connected to both the inlet pipe 130 and the first transfer pipe 140. Multiple fins 180 are arranged between adjacent flat tubes 170.

[0106] The cooling medium enters through the inlet pipe 130, flows through the flat tube 170 of the first heat exchanger body 110 to the first transfer pipe 140, then to the second transfer pipe 150, and is branched off to the flat tube 170 of the second heat exchanger body 120, finally entering the outlet pipe 160. The aforementioned inlet pipe 130 is the inlet side of the heat exchanger 100, where the medium temperature is highest.

[0107] The aforementioned input pipe 130 is the input side of the heat exchanger 100. The nozzle assembly 200 sprays water to cool the first heat exchange body 110. The temperature detection module 320 is in close contact with the outer wall of the input pipe 130 to monitor the temperature inside the input pipe 130 in real time. The nozzle 210 is located on the side of the first heat exchange body 110 away from the second heat exchange body 120 (in the thickness direction of the heat exchanger 100) and can spray water to cool this side, achieving cooling on the outside of the first heat exchange body 110 where the medium temperature is highest.

[0108] Please see Figure 3 The nozzle contains a swirling atomizing core 240. Cooling liquid flows downward along the supply chamber 215 and impacts the swirling atomizing core 240. The continuous liquid column is sheared and cut by the edges and swirling channels of the swirling atomizing core 240, and is pre-broken into discrete droplets. High-pressure airflow enters the supply chamber 216 from the supply channel 214. The high-speed airflow impacts the rotating droplet group after pre-broken by the swirling atomizing core 240. The gas and liquid phases mix outside the nozzle 210, and the droplets are further refined through airflow shearing and turbulent collision, ultimately forming a spray with a finer and more uniform particle size. The refined droplets can increase the heat exchange contact area with the heat exchanger shell. The airflow carrying the droplets can enhance evaporative heat exchange and wall convective heat exchange. At the same time, the atomized spray replaces the direct liquid column spray, avoiding structural damage caused by the impact of high-pressure liquid flow on the shell.

[0109] According to a second aspect of this application, a heat exchanger auxiliary cooling method is provided, which utilizes any of the aforementioned heat exchanger auxiliary cooling devices for cooling, the heat exchanger auxiliary cooling method comprising:

[0110] S100: The real-time temperature of the heat exchanger 100 input side is detected by the temperature detection module 320 of the temperature and pressure control component 300, and the real-time temperature is transmitted to the processing module 330 of the temperature and pressure control component 300.

[0111] It should be noted that the temperature detection point is set on the input side of the heat exchanger 100 because the input side is the starting point where the cooling medium enters the heat exchanger 100, and the temperature in this area is the highest in the heat exchanger 100. Detecting this location can directly and quickly reflect the current heat load status of the heat exchanger 100.

[0112] S200: Based on the real-time temperature received by the processing module 330 and the built-in hierarchical control rules of the processing module 330, determine the working mode of the nozzle assembly 200.

[0113] S300, the pressure control module 340 of the temperature and pressure control component 300 adjusts the spray pressure of the nozzle assembly 200 according to the working mode.

[0114] The temperature and pressure control component 300 uses the detected real-time temperature as the control basis, dynamically adjusting the liquid supply pressure of the nozzle assembly 200 to change the liquid supply flow rate, thereby regulating the cooling intensity. Its control logic is as follows: the higher the real-time temperature, the greater the heat load of the heat exchanger 100, so the pressure of the nozzle assembly 200 is adjusted higher, the liquid supply flow rate is greater, and the cooling intensity is stronger; conversely, the lower the real-time temperature, the lower the injection pressure is reduced, the liquid supply flow rate is decreased, and over-cooling is avoided. Specifically, the processing module 330 in the temperature and pressure control component 300 receives the temperature signal collected by the temperature detection module 320, compares and calculates it with a preset temperature threshold, and generates a control command based on the comparison result. This control command is converted into an electrical signal by the pressure control module 340, driving the solenoid valve 250 installed on the liquid supply pipeline 220. By changing the opening degree of the solenoid valve 250, the liquid supply pressure is adjusted, thereby controlling the liquid supply flow rate of the nozzle assembly 200.

[0115] Through the coordinated operation of the above steps, the heat exchanger auxiliary cooling method of this application dynamically adjusts the cooling intensity of the heat exchanger 100: when the heat exchanger 100 is under high load or high temperature conditions, the liquid supply flow rate is automatically increased to enhance cooling; when the heat exchanger 100 is under low load or normal temperature conditions, the liquid supply flow rate is automatically reduced to avoid unnecessary energy consumption and adverse effects on the heat exchange efficiency of the heat exchanger 100 itself. Compared with traditional constant flow cooling or passive heat dissipation methods, this method has advantages such as fast response speed, high temperature control accuracy, and low energy consumption.

[0116] In some embodiments, the hierarchical control rules in step S200 above include a first threshold range, a second threshold range, and a third threshold range, wherein the maximum value of the third threshold range is less than the minimum value of the first threshold range, and the maximum value of the first threshold range is less than the minimum value of the second threshold range.

[0117] Among them, the maximum value of the first threshold range is less than the minimum value of the second threshold range, that is, the two temperature ranges do not overlap and the temperature corresponding to the first threshold range is lower than the temperature corresponding to the second threshold range; that is, the liquid supply flow rate of the nozzle assembly 200 under the first intensity is less than the liquid supply flow rate of the nozzle assembly 200 under the second intensity.

[0118] The working modes in step S200 above include standby mode, first-level intensity cooling mode and second-level intensity cooling mode. In standby mode, the nozzle assembly 200 is only powered on and does not perform cooling operation.

[0119] In both the first-level intensity cooling mode and the second-level intensity cooling mode, the nozzle assembly 200 performs cooling operations, and the spray pressure of the nozzle assembly 200 in the first-level intensity cooling mode is less than that in the second-level intensity cooling mode; the third threshold range corresponds to the standby mode, the first threshold range corresponds to the first-level intensity cooling mode, and the second threshold range corresponds to the second-level intensity cooling mode.

[0120] It should be noted that the use of tiered control allows for differentiated adjustment of cooling intensity, avoiding the problems of insufficient or excessive cooling caused by simple on / off control. Specifically:

[0121] The first threshold range corresponds to the medium-high temperature range of heat exchanger 100. At this point, heat exchanger 100 has entered a state that requires auxiliary cooling but has not yet reached overheating. Within this range, the injection pressure is adjusted to the first-level intensity cooling mode to provide gentle cooling with a smaller liquid supply flow rate. This can suppress further temperature rise and avoid adverse effects on the heat exchange efficiency of heat exchanger 100 due to excessive liquid supply flow rate.

[0122] The second threshold range corresponds to the high-temperature overheating range of heat exchanger 100. At this point, the temperature of heat exchanger 100 is already high, and if cooling is not strengthened in time, local overheating, coking, scaling, or even component damage may occur. Within this range, the injection pressure is adjusted to the secondary intensity cooling mode, with a larger liquid supply flow rate and gas supply flow rate for enhanced cooling, quickly removing heat and reducing the temperature of heat exchanger 100 to a safe range.

[0123] By coordinating the first and second threshold ranges, as well as the first and second intensity cooling modes, this application achieves multi-level cooling control. At lower temperatures, a small flow rate is used for gentle cooling, while at higher temperatures, a large flow rate is switched to enhanced cooling. This tiered adjustment method ensures effective cooling under high-temperature conditions while avoiding over-cooling under moderate-temperature conditions.

[0124] In some embodiments, the first threshold range satisfies a value greater than or equal to 66.85°C and less than or equal to 76.85°C; the second threshold range satisfies a value greater than 76.85°C. That is, the first threshold can be any value among 66.85°C, 67°C, 68°C, 69°C, 70°C, 71°C, 72°C, 73°C, 74°C, 75°C, 76°C, and 76.85°C, or any value within any range between any two of the above values.

[0125] It should be noted that the above temperature range is selected based on the thermal characteristics of heat exchanger 100 under different load conditions. 66.85°C corresponds to a thermodynamic temperature of 340K, and 76.85°C corresponds to a thermodynamic temperature of 350K. When the input temperature of heat exchanger 100 is between 66.85°C and 76.85°C, it indicates that heat exchanger 100 has entered a medium-to-high load range, and its own heat exchange capacity is insufficient to maintain normal operation, requiring the activation of primary-level auxiliary cooling. When the temperature exceeds 76.85°C, it indicates that heat exchanger 100 has entered a high-load overheating state, necessitating the activation of secondary-level enhanced cooling to prevent localized overheating, coking, scaling, or even component damage.

[0126] It should be noted that the standby state is set so that when the heat exchanger 100 temperature is low and has not yet reached the cooling start-up conditions, the nozzle assembly 200 remains energized and ready to operate. This allows it to respond promptly to temperature increases and initiate cooling in a timely manner, while also avoiding the adverse effects of ineffective spraying under low-load conditions on the heat exchanger 100's heat exchange efficiency. In standby mode, only basic circuit power is maintained, the solenoid valve 250 remains closed, and the nozzle 210 does not spray or only maintains a minimal pre-spray, thereby reducing energy consumption.

[0127] In some embodiments, the third threshold range satisfies a value greater than or equal to 56.85°C and less than 66.85°C. That is, the third threshold can be any value among 56.85°C, 57°C, 58°C, 59°C, 60°C, 61°C, 62°C, 63°C, 64°C, 65°C, 66°C, and 66.85°C, or any value within any range between any two of the above values.

[0128] It should be noted that 56.85°C corresponds to a thermodynamic temperature of 330K. When the input temperature of heat exchanger 100 is between 56.85°C and 66.85°C, it indicates that heat exchanger 100 is in the medium-low temperature range. Within this range, heat exchanger 100 can still maintain normal heat exchange efficiency without the need for enhanced cooling, but the temperature is close to the boundary, so it remains in standby mode for rapid response. When the temperature is below 56.85°C, it indicates that heat exchanger 100 is in a low-load operating condition, and its own heat exchange can meet the requirements. The device can enter a low-power sleep state or be completely shut down.

[0129] In one example, a fuzzy PID adaptive control algorithm is used, taking heat exchanger 100 as an evaporator. It should be noted that the fuzzy PID adaptive control algorithm works in conjunction with the hierarchical control described above (first-level intensity corresponding to the first threshold range, and second-level intensity corresponding to the second threshold range). The hierarchical control, as the state switching logic, is responsible for determining the appropriate operating mode of the device based on the temperature range; the fuzzy PID, as the continuous adjustment algorithm, is responsible for adjusting the spray pressure in the cooling operating mode.

[0130] Specifically, the graded control is responsible for determining the appropriate operating mode (standby, primary intensity, secondary intensity) based on the temperature range, while the fuzzy PID controller is responsible for continuously and precisely adjusting the spray pressure in the cooling operating mode (i.e., primary intensity, secondary intensity). For example:

[0131] When the real-time temperature is within the third threshold range (56.85°C ≤ T < 66.85°C), the device is in standby mode. At this time, the fuzzy PID algorithm is not activated, and the nozzle 210 does not spray or only maintains a minimum amount of pre-spray.

[0132] When the real-time temperature is within the first threshold range (66.85°C < T ≤ 76.85°C), the device is in the first-level intensity cooling mode. At this time, the fuzzy PID algorithm is activated and the adjustment is performed near the reference pressure of the first-level intensity.

[0133] When the real-time temperature is within the second threshold range (T > 76.85°C), the device is in a secondary intensity cooling mode, at which point the fuzzy PID algorithm adjusts near the reference pressure of the secondary intensity.

[0134] Processing module 330 includes a PID controller, which has a built-in fuzzy PID adaptive control algorithm. The fuzzy PID adaptive control algorithm uses temperature deviation... Rate of change with temperature deviation For fuzzy input, the scaling factor is adjusted online via fuzzy inference. Integral coefficient Differential coefficients Output ratio increment Integral increment Differential increment To adapt to the real-time temperature changes of the heat exchanger under primary and secondary intensity cooling modes, and to ensure that the device maintains good control characteristics across different temperature ranges, the specific steps of the fuzzy PID adaptive control algorithm are as follows:

[0135] S400, Input fuzzification, calculate the temperature deviation Rate of change with temperature deviation Convert to a fuzzy set, divide the fuzzy set into fuzzy subsets {NB (negative large), NS (negative small), ZO (zero), PS (positive small), PB (positive large)}, and determine the membership function of the fuzzy subsets;

[0136] Temperature deviation The calculation formula is as follows:

[0137]

[0138] In formula (1): This represents the real-time temperature of the heat exchanger at time I-1. The real-time temperature of the heat exchanger at time I;

[0139] Temperature deviation change rate The calculation formula is as follows:

[0140]

[0141] In formula (2): This represents the temperature deviation change, specifically the temperature deviation difference between two sampling times. This refers to the time variation, i.e., the sampling period or the time interval between two calculations;

[0142] S500. Formulate fuzzy rules, which are manually formulated based on experience. The specific rules are as follows:

[0143]

[0144]

[0145]

[0146] Table 1 shows the adjustment amount for the proportional coefficient. The rule is as follows: when the rate of change of temperature deviation is negative, if the current deviation is negative (either large or small), then the output is positive. The increment outputs a positive value when the deviation is zero, and a positive value of small or large when the deviation is small or zero, respectively. When the rate of change is negative, the output changes sequentially from small to medium, then to small, zero, and finally small. When the rate of change is zero, the output gradually transitions from small to medium. When the rate of change is positive, the output gradually decreases from small to medium. When the rate of change is large, if the deviation is large, the output is zero, and then changes sequentially to small, medium, large, and large as the deviation increases. Overall, The adjustment direction is roughly opposite to the sign of the deviation and the rate of change. It aims to significantly reduce the proportional effect to suppress overshoot when the deviation is large and the deterioration trend is obvious, and to significantly enhance the proportional effect to accelerate the correction speed when the deviation is large but the improvement trend is obvious.

[0147] Table 2 shows the adjustment amount for the integral coefficient. The rule is as follows: when the rate of change is negative, the output will be negative whether the deviation is negative or negative. The increment outputs a small negative value when the deviation is zero, and zero when the deviation is small positive or large positive. When the rate of change is small negative, the output starts from large negative, progresses through small negative, small negative, and gradually transitions to zero and small positive. When the rate of change is zero, the output is small negative, small negative, zero, small positive, and small positive in sequence. When the rate of change is small positive, the output progresses from small negative, through zero, small positive, and small positive, eventually rising to large positive. When the rate of change is large positive, the output is small negative with a large deviation, and then, as the deviation increases, it sequentially becomes zero, small positive, large positive, and large positive. Therefore, The adjustment focuses on the cumulative trend of the deviation. When the deviation remains in the same direction for a long time and the rate of change is also in the same direction, the integral action is enhanced to eliminate static error. However, when the deviation changes rapidly in the opposite direction, the integral action is weakened to prevent integral saturation from causing oscillation.

[0148] Table 3 shows the adjustment amount for the differential coefficient. The rules are as follows: when the rate of change is large negative, the outputs corresponding to the deviations from large negative to large positive are, in order: small positive, small negative, large negative, large negative, small positive; when the rate of change is small negative, the outputs are, in order: small positive, small negative, large negative, small negative, zero; when the rate of change is zero, the outputs are, in order: zero, small negative, small negative, small negative, zero; when the rate of change is small positive, the outputs are, in order: zero, zero, small negative, small negative, small positive; when the rate of change is large positive, the outputs are, in order: large positive, large positive, small positive, small negative, small positive. Overall, The adjustment is mainly based on the severity of the deviation change. When the deviation and the rate of change are in the same direction and the amplitude is large, the derivative action is adjusted appropriately to suppress the rapid shock and oscillation of the system. When the change is relatively gentle, a small adjustment amount is maintained. The rule shows a certain degree of asymmetry to better adapt to the different dynamic characteristics of the heating and cooling processes in temperature control.

[0149] The above three fuzzy rule tables together form a set of rules based on temperature deviation. For horizontal input, using the rate of change of deviation For a system with vertical input, the system outputs online adjustments for the proportional, integral, and derivative coefficients, respectively. It is primarily responsible for the current magnitude and trend of response deviation, and employs a reverse adjustment strategy to balance rapid response and prevent overshoot; It is primarily responsible for the long-term accumulation tendency of response bias, and adopts a unidirectional adjustment strategy to eliminate static error and prevent integral saturation; This is primarily responsible for assessing the swiftness of changes in response deviations, applying targeted compensation to enhance system stability during periods of drastic change. The three components work together... and The real-time combination of states enables adaptive tuning of PID parameters, allowing the temperature control system to balance speed, stability, and anti-interference under different operating conditions.

[0150] S600. Fuzzy inference: Based on the input fuzzy set and fuzzy rules, the Mamdani minimum implication inference method is used to calculate the fuzzy parameter correction. , , ;

[0151] The membership degree output of a single rule inference satisfies The total output fuzzy membership degree of all rules combined satisfies In the formula Let e ​​be the fuzzy subset membership degree of the temperature deviation e. Let be the fuzzy subset membership degree of the rate of change of temperature deviation (ec). Let l be the membership degree of the output fuzzy set corresponding to the l-th fuzzy rule. The total output fuzzy membership set of the parameter correction is given, and l is the fuzzy rule number. Temperature deviation e and temperature deviation change rate ec are both divided into 5 fuzzy subsets: {NB (negative large), NS (negative small), ZO (zero), PS (positive small), PB (positive large)}, generating a total of 25 fuzzy inference rules.

[0152] S700. Defuzzify, and adjust the fuzzy parameter correction amount obtained in the fuzzy inference. , , Convert to precise values ​​for real-time parameters , , Perform online correction and output the current parameters. , , ;

[0153] Current parameters , , The calculation formulas are as follows:

[0154]

[0155]

[0156]

[0157] In formulas (3), (4) and (5): This is a real-time scaling factor. For real-time integral coefficients, For real-time differential coefficients, For proportional increments, For the integral increment, For differential increments, This is the corrected current scaling factor. The corrected current integral coefficients, These are the corrected current differential coefficients.

[0158] S800, Obtain the injection pressure based on the current parameters. , , The injection pressure of the nozzle assembly (200) was calculated.

[0159] Injection pressure The calculation formula is as follows:

[0160]

[0161] In formula (6): This is the corrected current scaling factor. For temperature deviation, The corrected current integral coefficients, This refers to the time variation, i.e., the sampling period or the time interval between two calculations. These are the corrected current differential coefficients. This represents the change in temperature deviation, specifically the temperature deviation difference between two samplings.

[0162] It should be noted that the following five operating conditions correspond to the working modes and temperature ranges described above:

[0163] High temperature rise condition: when For PB, When the value is PB, it indicates that the evaporator wall temperature far exceeds the target value and the heating rate is rapid, indicating an overheating trend. This condition typically corresponds to the second threshold range (T > 76.85°C, i.e., secondary enhanced operating mode). Under this condition, the corresponding increase... , , reduce To accelerate the spray pressure adjustment speed, quickly curb the temperature rise, and avoid overheating damage to the equipment. When the temperature approaches the minimum value of the second threshold range, decrease the proportional coefficient and increase the integral coefficient to eliminate steady-state error and improve temperature control stability.

[0164] Slightly higher temperature condition: When e is PS and ec is ZO or PS, it indicates that the heat exchanger temperature 100 is slightly higher than the target value and the temperature change is gradual. This condition typically corresponds to the upper half of the first threshold range (66.85°C < T ≤ 76.85°C, i.e., first-level intensity cooling mode). Under this condition, moderately increase... Slight adjustments , Medium spray intensity is used for stable cooling.

[0165] Steady-state temperature condition: When e and ec are both ZO, it indicates that the temperature of heat exchanger 100 is stable within the target range. This condition typically corresponds to the middle of the first threshold range or near the target temperature Ts (e.g., Ts = approximately 65°C). Under this condition, reducing... ,promote This weakens the differential effect, eliminates steady-state temperature deviation, and maintains temperature control stability.

[0166] For a specific example, please refer to Figure 5 The temperature and pressure control component 300 is activated, and the temperature detection module 320 collects the real-time temperature T1 on the input side of the heat exchanger 100.

[0167] The processing module 330 compares the real-time temperature T1 with a preset threshold and executes corresponding control actions based on the different ranges of T1. When T1 < 330K, the nozzle assembly 200 stops spraying, and the device enters a dormant state. When 330K ≤ T1 < 340K, the nozzle assembly 200 is powered on and in standby mode, the solenoid valve 250 is closed, and no spraying occurs, but the device continuously monitors temperature changes and is ready to respond at any time. When 340K ≤ T1 ≤ 350K, it enters the first-level intensity cooling mode, the solenoid valve 250 is partially opened, and the nozzle assembly 200 performs gentle cooling with a small liquid supply flow rate to suppress further temperature rise. When T1 > 350K, it enters the second-level intensity cooling mode, the solenoid valve 250 is opened to the maximum set opening, and the nozzle assembly 200 performs enhanced cooling with a large liquid supply flow rate to quickly reduce the temperature of the heat exchanger 100.

[0168] The device continuously cycles through the above temperature acquisition and graded control steps to achieve adaptive control that automatically adjusts the cooling intensity based on the real-time temperature.

[0169] In a specific example, the aforementioned heat exchanger auxiliary cooling device and method are used to perform auxiliary cooling control on the evaporator. The target control temperature Ts of the evaporator is set to 340K (66.85°C), with preset thresholds of 330K (56.85°C), 340K (66.85°C), and 350K (76.85°C). The temperature and pressure control component 300 continuously acquires the real-time input temperature T1 and performs hierarchical control and fuzzy PID adaptive adjustment according to the range of T1.

[0170] Please see Figure 6 and Figure 7Initially, the evaporator temperature T1 is below 330K, the device is in a stopped spray state, the nozzle assembly 200 is de-energized and in sleep mode, and the solenoid valve 250 is closed, without cooling. As the heat load increases, the temperature gradually rises. When the temperature rises to 330K, the device enters a standby state, the nozzle assembly 200 is energized and ready to operate, the solenoid valve 250 remains closed but continuously monitors temperature changes in preparation for response.

[0171] When the temperature rises to 340K, the device switches from standby mode to the first-level intensity cooling mode. Solenoid valve 250 partially opens, and the nozzle assembly 200 provides gentle cooling with a smaller liquid flow rate, activating the fuzzy PID adaptive control algorithm. The fuzzy PID controller uses the temperature deviation e and the rate of change of deviation ec as inputs to tune the PID parameters online, suppressing further temperature increases. As shown in the figure, the temperature fluctuates around 340K before stabilizing, indicating that the fuzzy PID effectively controls the temperature rise.

[0172] When the temperature rises above 350K, the device switches from Level 1 to Level 2 cooling mode. Solenoid valve 250 opens to its maximum extent, and nozzle assembly 200 undergoes enhanced cooling with a high liquid flow rate. Simultaneously, the fuzzy PID controller employs more aggressive control parameters (increasing...). , , reduce This accelerates the adjustment of spray pressure. As can be seen from the graph, the temperature drops rapidly after reaching a peak of approximately 365K.

[0173] When the temperature drops below 350K, the device switches back to the first-level intensity cooling mode to continue gentle cooling; when the temperature drops below 340K, the device switches back to standby mode, and the solenoid valve 250 closes to stop spraying; when the temperature drops below 330K, the device enters shutdown mode, and the nozzle assembly 200 is powered off and goes into hibernation.

[0174] The device continuously cycles through the above temperature acquisition and graded control steps, achieving adaptive control that automatically adjusts the cooling intensity based on real-time temperature, effectively controlling evaporator temperature fluctuations and preventing overheating damage.

[0175] In the above embodiments, the descriptions of each embodiment have different focuses. For parts not described in detail in a certain embodiment, please refer to the relevant descriptions in other embodiments.

[0176] The embodiments, implementation methods, and related technical features of this application can be combined and substituted for each other without conflict.

[0177] The above are merely preferred embodiments of this application and are not intended to limit this application in any way. Any simple modifications, equivalent changes, and alterations made to the above embodiments based on the technical essence of this application without departing from the scope of the technical solution of this application shall still fall within the scope of the technical solution of this application.

Claims

1. A heat exchanger auxiliary cooling device, characterized in that, include: Nozzle assembly (200), the output end of which faces the heat exchanger (100); A temperature and pressure control component (300) is connected to the input side of the heat exchanger (100) and is electrically connected to the nozzle assembly (200); the temperature and pressure control component (300) is configured to detect the real-time temperature of the input side and to adjust the injection pressure of the nozzle assembly (200) according to the real-time temperature.

2. The heat exchanger auxiliary cooling device according to claim 1, characterized in that, The nozzle assembly (200) includes: Multiple nozzles (210) are spaced apart from the heat exchanger (100). Each nozzle (210) has a liquid supply chamber (215), an air supply chamber (216), and a spray nozzle (211). The liquid supply chamber (215) and the air supply chamber (216) are spaced apart, and the spray nozzle (211) is connected to the air supply chamber (216). The liquid supply line (220) has multiple liquid outlets and at least one liquid inlet, each of the liquid outlets being connected to the liquid supply chamber (215) of one of the nozzles (210), and the liquid inlet being connected to external coolant; The air supply line (230) has multiple air outlets and at least one air inlet, each of the air outlets being connected to the air supply chamber (216) of one of the nozzles (210), and the air inlet being connected to an external gas medium. The swirling atomizing core (240) is housed within the liquid supply chamber (215); A solenoid valve (250) is installed on the liquid supply line (220) and electrically connected to the temperature and pressure control component (300). The temperature and pressure control component (300) can adjust the solenoid valve (250) according to the real-time temperature so as to adjust the spray pressure of the nozzle assembly (200).

3. The heat exchanger auxiliary cooling device according to claim 2, characterized in that, The temperature and pressure control component (300) includes: The housing (310) has a receiving cavity; A temperature detection module (320) is located on the side of the housing (310) facing the heat exchanger (100) and is in contact with the input side; The processing module (330) is housed in the receiving cavity and connected to the housing (310), and the processing module (330) is electrically connected to the temperature detection module (320); The pressure control module (340) is housed in the receiving cavity and is spaced apart from the processing module (330). The pressure control module (340) is electrically connected to the processing module (330) and the solenoid valve (250) respectively.

4. The heat exchanger auxiliary cooling device according to claim 2, characterized in that, The nozzle (210) also includes: The nozzle body (212) is connected to the liquid supply line (220) and the air supply line (230) respectively. The liquid supply chamber (215) and the air supply chamber (216) are both opened in the nozzle body (212). The spray port (211) is opened at the end of the nozzle body (212) away from the liquid supply line (220). The liquid supply channel (213) extends along the axial direction of the nozzle (210) through one end of the nozzle body (212) toward the liquid supply pipeline (220) and is connected to the liquid supply chamber (215); An air supply channel (214) is provided, one end of which is connected to the air supply chamber (216), and the other end of which is connected to an air outlet.

5. The heat exchanger auxiliary cooling device according to claim 4, characterized in that, The central axis of the liquid supply channel (213) intersects with the central axis of the gas supply channel (214).

6. A method for auxiliary cooling of a heat exchanger, characterized in that, Cooling is performed using the heat exchanger auxiliary cooling device according to any one of claims 1 to 5, wherein the heat exchanger auxiliary cooling method comprises: S100, The real-time temperature of the heat exchanger (100) input side is detected by the temperature detection module (320) of the temperature and pressure control component (300), and the real-time temperature is transmitted to the processing module (330) of the temperature and pressure control component (300); S200: Based on the real-time temperature received by the processing module (330), the working mode of the nozzle assembly (200) is determined according to the graded control rules built into the processing module (330); S300, the pressure control module (340) of the temperature and pressure control component (300) adjusts the spray pressure of the nozzle assembly (200) according to the working mode.

7. The heat exchanger auxiliary cooling method according to claim 6, characterized in that, The hierarchical control rules in step S200 include a first threshold range, a second threshold range, and a third threshold range. The maximum value of the third threshold range is less than the minimum value of the first threshold range, and the maximum value of the first threshold range is less than the minimum value of the second threshold range.

8. The heat exchanger auxiliary cooling method according to claim 7, characterized in that, The working modes in step S200 include standby mode, first-level intensity cooling mode and second-level intensity cooling mode. In the standby mode, the nozzle assembly (200) is only powered on and does not perform cooling operation. In both the first-level intensity cooling mode and the second-level intensity cooling mode, the nozzle assembly (200) is cooled, and the spray pressure of the nozzle assembly (200) in the first-level intensity cooling mode is less than the spray pressure of the nozzle assembly (200) in the second-level intensity cooling mode. The third threshold range corresponds to the standby mode, the first threshold range corresponds to the first-level intensity cooling mode, and the second threshold range corresponds to the second-level intensity cooling mode.

9. The heat exchanger auxiliary cooling method according to claim 8, characterized in that, The processing module (330) includes a PID controller, which has a built-in fuzzy PID adaptive control algorithm. The fuzzy PID adaptive control algorithm uses temperature deviation as the basis for its operation. Rate of change with temperature deviation For fuzzy input, the scaling factor is adjusted online via fuzzy inference. Integral coefficient Differential coefficients Output ratio increment Integral increment Differential increment To adapt to the real-time temperature changes of the heat exchanger under the first-level intensity cooling mode and the second-level intensity cooling mode, the specific steps of the fuzzy PID adaptive control algorithm are as follows: S400, Input fuzzification, calculate the temperature deviation Rate of change with temperature deviation The data is converted into a fuzzy set, and the fuzzy set is divided into fuzzy subsets {NB (negative large), NS (negative small), ZO (zero), PS (positive small), PB (positive large)}, and the membership function of the fuzzy subsets is determined. S500, Formulate fuzzy rules; S600. Fuzzy inference: Based on the input fuzzy set and fuzzy rules, obtain the fuzzy parameter correction amount. , , ; S700. Defuzzify, and adjust the fuzzy parameter correction amount obtained in the fuzzy inference. , , Convert to precise values ​​for real-time parameters , , Perform online correction and output the current parameters. , , ; S800, Obtain the injection pressure based on the current parameters. , , The injection pressure of the nozzle assembly (200) was calculated.

10. The heat exchanger auxiliary cooling method according to claim 9, characterized in that, Temperature deviation The calculation formula is as follows: ； In formula (1): This represents the real-time temperature of the heat exchanger at time I-1. The real-time temperature of the heat exchanger at time I; Temperature deviation change rate The calculation formula is as follows: ； In formula (2): This represents the temperature deviation change, specifically the temperature deviation difference between two sampling times. This refers to the time variation, i.e., the sampling period or the time interval between two calculations; Current parameters , , The calculation formulas are as follows: ； ； ； In formulas (3), (4) and (5): This is a real-time scaling factor. For real-time integral coefficients, For real-time differential coefficients, For proportional increments, For the integral increment, For differential increments, This is the corrected current scaling factor. The corrected current integral coefficients, These are the corrected current differential coefficients; Injection pressure The calculation formula is as follows: ； In formula (6): This is the corrected current scaling factor. For temperature deviation, The corrected current integral coefficients, This refers to the time variation, i.e., the sampling period or the time interval between two calculations. These are the corrected current differential coefficients. This represents the change in temperature deviation, specifically the temperature deviation difference between two samplings.

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