Gravity heat pipe heat exchanger fan control method, storage medium and heat exchanger

Abstract

The invention relates to the technical field of heat exchangers, in particular to a gravity assisted heat pipe heat exchanger fan control method, a storage medium and a heat exchanger. Adjustment of the four fans and four functional areas of working medium circulation in the heat pipe are subjected to correlation mapping, differentiated collaborative rotating speed adjustment is executed, and the service target of each fan is made to clearly point to the core thermal requirement of the corresponding area. According to the cooperative control mode of partition management and accurate strategy application, dynamic balance between vaporization power and liquefaction backflow in the heat pipe can be actively maintained and rapidly recovered. It is ensured that heat is efficiently transferred from a heat source to a cold source, meanwhile, the internal unbalance problems such as circulation stagnation, heat pipe local overheating or condensate accumulation possibly caused by local heat exchange mismatching are effectively avoided, and therefore the maximization of heat exchange efficiency and the fundamental improvement of operation reliability are achieved on the system level.

Description

Technical Field

[0001] This invention relates to the field of heat exchanger technology, and more particularly to a fan control method, storage medium, and heat exchanger for a gravity heat pipe heat exchanger. Background Technology

[0002] Gravity heat pipe heat exchangers are high-efficiency heat exchange devices based on the principle of closed-loop two-phase heat transfer. Their core working unit is the gravity heat pipe (also known as a thermosiphon), which is evacuated and filled with a suitable amount of working fluid. During operation, the evaporation section absorbs heat from the hot fluid, causing the working fluid inside the pipe to evaporate and vaporize. The vapor rises to the condensation section under pressure difference, releasing latent heat to the cold fluid before condensing into a liquid. The liquid working fluid flows back to the evaporation section under gravity, thus completing a continuous and efficient cyclic heat transfer process. This equipment has advantages such as high heat transfer efficiency, complete isolation of fluids on both sides, no moving parts, and reliable operation, and is widely used in industrial waste heat recovery, building air conditioning and ventilation energy conservation, and other fields.

[0003] To enhance convective heat transfer between the external fluid (usually air or flue gas) and the surface of the heat pipe fins, axial or centrifugal fans (hereinafter collectively referred to as "fans") are typically installed in the evaporator and condenser ducts of the heat exchanger. In existing technology, a typical fan arrangement is as follows: one or more fans are connected in parallel at the inlet or outlet of the evaporator duct to drive the heat source fluid (such as hot flue gas) through the evaporator section; similarly, one or more fans are connected in parallel at the inlet or outlet of the condenser duct to drive the cold source fluid (such as fresh air or cooling air) through the condenser section. This arrangement constitutes a basic forced convection heat transfer system.

[0004] Regarding fan control methods, existing technologies are generally quite rudimentary and simple, mainly existing in the following modes: ① Constant speed operation mode: The fan runs continuously at a fixed speed, unable to adjust according to changes in heat load, resulting in significant energy waste under partial load. ② Unified start / stop or speed regulation mode: Based on a threshold value of a single measuring point temperature (such as the inlet air temperature of the evaporator section, or the outer wall temperature of a representative heat pipe), all fans in the same air duct are uniformly controlled to "on / off" or synchronously adjusted to "high / low" speed. For example, when the temperature exceeds the set value, all fans on that side are turned on or accelerated. ③ Simple feedback control based on external fluid temperature: The air inlet and outlet temperatures of the evaporator and condenser sections are monitored separately, and based on this feedback, the overall speed of the fans on both sides is adjusted through an independent PID controller, aiming to maintain a certain outlet temperature or heat transfer temperature difference.

[0005] However, the aforementioned existing technologies have the following obvious drawbacks: Coarse control granularity and insufficient energy efficiency optimization: Existing methods treat the fan groups on the evaporator or condenser side as a whole for control, failing to finely adjust the heat transfer intensity according to the different needs of the "evaporation, rise, condensation, and reflux" stages inside the heat pipe. This causes the system to fail to operate at its optimal energy efficiency point, with some areas potentially experiencing excessive heat transfer while others experience insufficient heat transfer, resulting in unnecessary energy consumption of the fans.

[0006] The lack of awareness and response to critical operating states inside the heat pipe is a significant issue. Current control logic relies on feedback signals from external fluid temperature or individual pipe wall temperatures, failing to directly or indirectly characterize the core phase change state of the working fluid within the heat pipe (e.g., whether the bottom of the evaporation section has sufficiently absorbed heat and vaporized, whether the top of the condensation section has liquefied in time, and whether the gas-liquid two-phase circulation is dynamically balanced). The control system is like a blind man describing an elephant, unable to prevent or address performance degradation or safety hazards caused by internal imbalances (such as near-dry burning or condensation buildup).

[0007] The system exhibits lag in dynamic response and is prone to oscillations: Due to the strong coupling and inertia between the internal phase change process and external fluid heat exchange in the gravity heat pipe, simple single-point temperature feedback control strategies (such as PID) often result in lag in response. When the operating conditions of the heat or cold source change, the system requires a long time to regain stability, and may even experience control coupling oscillations between different fans or between the two side air ducts due to improper adjustment, affecting stable operation.

[0008] The ability to cope with extreme operating conditions and ensure safety is weak: existing methods struggle to identify risky conditions such as overheating of the evaporation section (which may lead to working fluid decomposition or pipe wall overheating) or overcooling of the condensation section (which may lead to premature condensation of the working fluid and blockage of backflow) in a timely and accurate manner. There is a lack of targeted, coordinated protection and control strategies based on the internal operating limits of the heat pipe, resulting in a low safety margin for equipment operation.

[0009] Therefore, there is an urgent need in this field for a technical solution that can intelligently and precisely control multiple fans in a coordinated manner, so as to fundamentally solve the above problems and achieve a leap in the performance of gravity heat pipe heat exchangers in terms of efficiency, safety, stability and energy saving. Summary of the Invention

[0010] This invention provides a fan control method, storage medium, and heat exchanger for a gravity heat pipe heat exchanger. This method is used to solve the technical problems of coarse fan control granularity and insufficient energy efficiency optimization in the prior art.

[0011] The first aspect of this invention provides a fan control method for a gravity heat pipe heat exchanger, comprising: S1: Obtain the outer wall temperature of the lower heat pipe of the evaporation section Te1, the outer wall temperature of the upper heat pipe of the evaporation section Te2, the outer wall temperature of the upper heat pipe of the condensation section Tc1, and the outer wall temperature of the lower heat pipe of the condensation section Tc2; S2: Based on Te1 and the temperature difference ΔTec between the upper outer wall of the evaporation-condensation section calculated from Te2 and Tc1, determine the current operating mode of the heat exchanger; S3: Based on the determined operating mode, the speeds of the first fan F1, the second fan F2, the third fan F3, and the fourth fan F4 are adjusted in a differentiated and coordinated manner. F1 and F2 are set in the lower and upper parts of the evaporation section, respectively, and F3 and F4 are set in the lower and upper parts of the condensation section, respectively.

[0012] In the first possible implementation of the first aspect, S2 includes: S21: If Te1 is lower than the first temperature threshold T1 and ΔTec is less than the first temperature difference threshold δ1, then the operating mode is determined to be the insufficient vaporization mode. S22: If Te1 is not lower than the second temperature threshold T2 and not higher than the third temperature threshold T3, and ΔTec is not lower than the second temperature difference threshold δ2 and not higher than the third temperature difference threshold δ3, then the working condition mode is determined to be the high-efficiency balance mode. S23: If Te1 is higher than the fourth temperature threshold T4 and ΔTec is greater than the fourth temperature difference threshold δ4, then the operating mode is determined to be the insufficient condensation mode. Among them, T1<T2<T3<T4, and δ1<δ2<δ3<δ4.

[0013] In conjunction with the first possible implementation of the first aspect, in the second possible implementation of the first aspect, when the insufficient vaporization mode is determined, S3 includes: S31a: Increase the speed of F1 to the first set speed N1; S31b: Increase the speed of F3 to the second set speed N2, where the ratio k1 of N2 to N1 satisfies: 0.6 < k1 < 0.8; S31c: Control F2 to run at the third set speed N3, and control F4 to run at the fourth set speed N4, where N3 and N4 are both less than or equal to the preset base speed Nb, and Nb < N2.

[0014] In conjunction with the first possible implementation of the first aspect, in the third possible implementation of the first aspect, when the efficient balancing mode is determined, S3 includes: S32a: Control F1 to run at the first equilibrium speed P1, and control F3 to run at the second equilibrium speed P2, where P1 equals P2; S32b: Control F2 to run at the third equilibrium speed P3, and control F4 to run at the fourth equilibrium speed P4, where P3 is less than P1 and P4 is less than P2.

[0015] In conjunction with the third possible implementation of the first aspect, the fourth possible implementation of the first aspect further includes the following before S2: S0: Obtain the air-side temperature rise ΔTa in the evaporation section and the air-side temperature rise ΔTc in the condensation section; S3 also includes: S32c: If both ΔTa and ΔTc are less than the preset energy-saving temperature difference threshold, the speeds of F1, F2, F3 and F4 will be reduced simultaneously in the same proportion.

[0016] In conjunction with the first possible implementation of the first aspect, in the fifth possible implementation of the first aspect, when the condensation deficiency mode is determined, S3 includes: S33a: Increase the speed of F3 to the first target speed R1; S33b: Reduce the rotational speed of F1 to the second target rotational speed R2, where the ratio of R2 to R1, k2, satisfies: 0 < k2 < 1; S33c: Increase the rotational speed of F2 to the third target rotational speed R3, where the ratio of R3 to R2, k3, satisfies: k3 > 1; S33d: Increase the rotational speed of F4 to the fourth target rotational speed R4, where the ratio of R4 to R1, k4, satisfies: 0 < k4 < 1.

[0017] In the sixth possible implementation of the first aspect, S2 also includes: S24: If Te1 is higher than the fifth temperature threshold T5, then the operating mode is determined to be the evaporator section over-temperature protection mode; where T5 > T4; S25: If Tc2 is lower than the sixth temperature threshold T6, then the operating mode is determined to be the condensation section subcooling protection mode, T6 < T1; S3 also includes: S36: When the evaporation section is determined to be in over-temperature protection mode, control F1 to run at the first protection speed Q1 and control F4 to run at the second protection speed Q2, wherein the ratio r1 of Q1 to a preset safe speed Qs satisfies: 0 ≤ r1 < 0.5, and the ratio r2 of Q2 to Qs satisfies: r2 > 1.5; S37: When the condensing section is judged to be in the subcooling protection mode, control F3 to run at the third protection speed Q3 and control F2 to run at the fourth protection speed Q4, where the ratio of Q3 to Qs, r3, satisfies: 0 ≤ r3 < 0.5, and the ratio of Q4 to Qs, r4, satisfies: r4 > 1.5.

[0018] The second aspect of the present invention provides a computer-readable storage medium having a computer program stored thereon, which, when executed by a processor, implements the steps of any of the possible implementations of the gravity heat pipe heat exchanger fan control method provided in the first aspect.

[0019] A heat exchanger provided in a third aspect of the present invention includes: Temperature sensor assembly for acquiring the outer wall temperature Te1 of the lower heat pipe in the evaporation section, the outer wall temperature Te2 of the upper heat pipe in the evaporation section, the outer wall temperature Tc1 of the upper heat pipe in the condensation section, and the outer wall temperature Tc2 of the lower heat pipe in the condensation section; The fan assembly includes a first fan F1 disposed at the lower part of the evaporation section, a second fan F2 disposed at the upper part of the evaporation section, a third fan F3 disposed at the lower part of the condensation section, and a fourth fan F4 disposed at the upper part of the condensation section; The controller is communicatively connected to both the temperature sensor assembly and the fan assembly. The controller is configured to perform the gravity heat pipe heat exchanger fan control method as described in any one of claims 1 to 7.

[0020] In the first possible implementation of the heat exchanger in the third aspect, the controller includes: The data acquisition module is used to acquire the temperature data detected by the temperature sensor component; The operating condition judgment module is used to calculate the temperature difference ΔTec between the upper outer wall of the evaporation and condensation sections based on the temperature data, and to determine the current operating condition mode based on Te1 and ΔTec. The collaborative control module is used to generate differentiated collaborative speed control commands for F1, F2, F3, and F4 in the fan assembly based on the judgment result of the working condition judgment module.

[0021] As can be seen from the above technical solutions, the present invention has the following advantages: This solution maps the adjustment of the four fans to the four functional zones of the working fluid circulation within the heat pipe (heat absorption in the lower part of the evaporation section, airflow protection in the upper part of the evaporation section, heat release in the upper part of the condensation section, and reflux stabilization in the lower part of the condensation section), and performs differentiated coordinated speed regulation, ensuring that each fan's service target is clearly directed to the core thermal needs of its corresponding zone. For example, when enhanced evaporation is needed, the fan in the lower part of the evaporation section will be driven first; when insufficient heat dissipation in the upper part of the condensation section needs to be prevented, the speed of the fan in that zone will be increased. This coordinated control mode of "zonal management and precise implementation" can proactively maintain and quickly restore the dynamic balance between "vaporization power" and "liquefaction reflux" within the heat pipe. It ensures that heat is efficiently "transferred" from the heat source to the cold source, while effectively avoiding internal imbalances such as circulation stagnation, local overheating of the heat pipe, or condensate accumulation that may be caused by local heat exchange mismatch, thereby maximizing heat exchange efficiency and fundamentally improving operational reliability at the system level. Attached Figure Description

[0022] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0023] Figure 1 A schematic flowchart of a fan control method for a gravity heat pipe heat exchanger provided in an embodiment of the present invention; Figure 2 This is a schematic diagram of the structure of a heat exchanger provided in an embodiment of the present invention; Figure 3 This is another structural schematic diagram of a heat exchanger provided in an embodiment of the present invention; Among them, F1 is the first fan; F2 is the second fan; F3 is the third fan; and F4 is the fourth fan. Detailed Implementation

[0024] This invention provides a fan control method, storage medium, and heat exchanger for a gravity heat pipe heat exchanger. The technical problem it addresses is that the fan control granularity in the prior art is coarse and the energy efficiency optimization is insufficient.

[0025] To make the objectives, features, and advantages of this invention more apparent and understandable, the technical solutions of the embodiments of this invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the embodiments described below are only some embodiments of this invention, and not all embodiments. Based on the embodiments of this invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this invention. Example

[0026] Please see Figure 1 The gravity heat pipe heat exchanger fan control method provided in this embodiment of the invention includes: S1: Obtain the outer wall temperature of the lower heat pipe of the evaporation section Te1, the outer wall temperature of the upper heat pipe of the evaporation section Te2, the outer wall temperature of the upper heat pipe of the condensation section Tc1, and the outer wall temperature of the lower heat pipe of the condensation section Tc2; The purpose of this step is to establish a non-invasive, real-time sensing capability for the critical state of the phase change cycle of the working fluid inside the gravity heat pipe. Traditional control methods rely on the inlet and outlet temperatures of the fluid, which are lagging signals and cannot directly reflect the heat transfer intensity of the pipe wall and the internal phase change process. This step constructs a spatial temperature field reflecting the state of the internal working fluid by simultaneously collecting the outer surface temperature of the pipe wall at four specific locations: the lower part of the evaporation section (Te1), the upper part of the evaporation section (Te2), the upper part of the condensation section (Tc1), and the lower part of the condensation section (Tc2). Among them, Te1 is directly related to the saturated heat absorption state of the liquid working fluid at the bottom of the evaporation section, which is the source indicator of vaporization power; Te2 reflects the temperature of the vapor during the rising process after the working fluid evaporates, which can be used to determine whether there is a risk of premature condensation; Tc1 is directly related to the liquefaction heat release intensity of the vapor at the top of the condensation section; and Tc2 reflects the subcooling and reflux state of the liquid working fluid after condensation. Obtaining these four temperatures is the physical basis and data prerequisite for subsequent accurate logical judgments based on the heat pipe's own operating characteristics (rather than external fluids). The key to its implementation lies in the selection and installation of the sensor. A temperature sensor with fast response and the required accuracy (such as a thermocouple or platinum resistance thermometer) should be selected, and a reliable thermally conductive installation process (such as welding or high thermal conductivity adhesive bonding) should be used to ensure that it is in close contact with the outer wall of the heat pipe, so as to accurately sense the temperature of the pipe wall rather than the ambient temperature.

[0027] In practical implementation, four independent temperature sensors can be distributed and installed on representative tube walls of the corresponding heat pipes. The controller directly acquires signals from each point through analog or digital input channels. Alternatively, an integrated temperature sensor array module can be used. This module pre-positions four sensing units on a mechanical carrier. During installation, each unit is aligned with its corresponding tube bundle area. After preliminary signal processing within the module, the four temperature data streams are packaged and sent to the controller via bus communication (such as CAN or RS-485). This method simplifies wiring and improves anti-interference capabilities.

[0028] S2: Based on Te1 and the temperature difference ΔTec between the upper outer wall of the evaporation and condensation sections calculated from Te2 and Tc1, determine the current operating mode of the heat exchanger; The purpose of this step is to transform the raw temperature data obtained in step S1 into a condition mode identifier that represents the overall operating status of the heat pipe and can be used for decision-making. Its design principle abandons simple threshold judgments based on a single absolute temperature, instead focusing on two key derived parameters reflecting the core contradiction of the "vaporization-condensation" cycle dynamics within the heat pipe: the absolute thermal state at the bottom of the evaporation section (Te1) and the driving temperature difference between the upper parts of the evaporation and condensation sections (ΔTec = Te2 - Tc1). A low Te1 indicates insufficient heat input, preventing sufficient vaporization of the working fluid; a low ΔTec means insufficient pressure difference driving the steam from the evaporation to the condensation section, resulting in weak circulation; a high Te1 and a high ΔTec indicate that the condensation section's heat dissipation capacity cannot match the intense vaporization of the evaporation section, posing a risk of overheating. By comprehensively evaluating these two parameters, step S2 can intelligently distinguish between fundamentally different physical conditions such as "insufficient vaporization," "high-efficiency balance," and "insufficient condensation," providing a precise "condition map" for subsequent implementation of matching control strategies.

[0029] The specific implementation of this judgment logic can be achieved through the following algorithmic strategies: First, a rule-based judgment method based on explicit numerical thresholds can be adopted. This involves pre-determining several sets of thresholds through experiments or theoretical calculations, and then directly determining the operating mode based on the numerical range falling within the real-time Te1 and ΔTec values. Second, a state classifier based on fuzzy logic or a simple neural network can be used. Te1 and ΔTec are used as input features, processed by a pre-trained classification model (whose training data comes from different operating states labeled in a large amount of historical operating data), directly outputting the most likely operating mode identifier. This method has better adaptability to threshold drift and nonlinear relationships.

[0030] S3: Based on the determined operating mode, the speeds of the first fan F1, the second fan F2, the third fan F3, and the fourth fan F4 are adjusted in a differentiated and coordinated manner. F1 and F2 are set in the lower and upper parts of the evaporation section, respectively, and F3 and F4 are set in the lower and upper parts of the condensation section, respectively.

[0031] This step, based on the operating mode output from step S2, differentiates the speed settings of four fans: F1 (lower part of the evaporation section), F2 (upper part of the evaporation section), F3 (upper part of the condensation section), and F4 (lower part of the condensation section), to achieve a forced convection environment that matches the current internal thermal requirements. This design breaks away from the traditional approach of treating the evaporator-side or condenser-side fans as a whole and adjusting them synchronously. It creatively couples the control target of each fan with a specific functional area of ​​the working fluid circulation within the heat pipe. Its core function is to proactively shape optimal external heat exchange conditions through precise "zonal airflow" to support, maintain, or restore the efficient and stable two-phase circulation within the heat pipe. For example, when the system is identified as having "insufficient vaporization," the logic in step S3 will prioritize increasing the speed of F1, which serves the liquid zone of the evaporation section, to strongly "feed heat," while moderately increasing the speed of F3, which serves the condensation section, to provide matching condensation capacity. Meanwhile, F2 and F4 will maintain low speeds to avoid interfering with the core process. This targeted approach to coordinated regulation allows the energy consumption of the external fan to be directly used to resolve the main contradictions in the internal circulation, thereby achieving the overall optimization of heat exchange efficiency, operational stability, and energy efficiency at the system level.

[0032] The specific implementation of this coordinated adjustment function can be achieved through the following control architecture: First, a feedforward control method using a "operating mode-speed mapping table" is adopted. A table is pre-stored in the controller, with row indices representing different operating modes and column indices representing the four fans. Each cell stores the set speed (or speed reference value) of the corresponding fan under that mode. Step S3 directly looks up the table based on the mode determined in step S2 and outputs the corresponding speed control command. Second, a "weighted PID controller based on operating conditions" is adopted. An independent PID controller is designed for each fan, but its setpoint and PID parameters are not fixed but determined by the current operating mode. For example, in the "high-efficiency balance" mode, the setpoints of F1 and F3 are the same, and the PID parameters emphasize rapid following; in the "insufficient condensation" mode, the setpoint of F3 is significantly increased, and its PID controller is given higher output authority, while the setpoint of F1 is lowered. This method combines the speed of feedforward with the accuracy of feedback.

[0033] The beneficial effects of this embodiment include: ① This solution maps the adjustment of the four fans to the four functional areas of the working fluid circulation inside the heat pipe (heat absorption in the lower part of the evaporation section, airflow protection in the upper part of the evaporation section, heat release in the upper part of the condensation section, and reflux stabilization in the lower part of the condensation section), and performs differentiated coordinated speed adjustment, ensuring that each fan's service target is clearly directed to the core thermal needs of its corresponding area. For example, when enhanced evaporation is needed, the fan in the lower part of the evaporation section will be driven first; when insufficient heat dissipation in the upper part of the condensation section needs to be prevented, the speed of the fan in that area will be increased. This coordinated control mode of "zonal management and precise implementation" can proactively maintain and quickly restore the dynamic balance between "vaporization power" and "liquefaction reflux" inside the heat pipe. It ensures that heat is efficiently "transferred" from the heat source to the cold source, while effectively avoiding internal imbalances such as circulation stagnation, local overheating of the heat pipe, or condensate accumulation that may be caused by local heat exchange mismatch, thereby maximizing heat exchange efficiency and fundamentally improving operational reliability at the system level.

[0034] ② This invention indirectly and accurately captures the core state information of the working fluid circulation inside the gravity heat pipe by acquiring the temperature of the outer wall of four key locations at the top and bottom of the evaporation and condensation sections in real time. Specifically, it captures the phase change process of the liquid working fluid absorbing heat and vaporizing in the evaporation section and the gaseous working fluid releasing heat and liquefying in the condensation section. Based on this, the scheme further utilizes the temperature difference between the upper parts of the evaporation and condensation sections as a key indicator for judging the circulation dynamics, thereby achieving accurate identification of different internal operating conditions such as "insufficient vaporization," "high-efficiency equilibrium," and "insufficient condensation." This pattern recognition method, which goes from the surface to the core and is based on direct thermal state parameters, fundamentally overcomes the perception bias and response delay caused by the reliance on indirect and lagging air temperature parameters in traditional control. Its direct beneficial effect is that the control system can understand the true working state inside the heat pipe as if through a microscope, laying an irreplaceable and solid foundation for implementing precise control that matches the internal physical processes, and achieving a deep integration of control logic and the principles of two-phase flow circulation dynamics inside the heat pipe.

[0035] ③ The "state perception - mode judgment - partition cooperation" closed - loop control logic constructed in the present invention also demonstrates its overall advantages in terms of excellent energy - efficiency self - optimization and internal safety guarantee. Since the regulation instructions directly originate from the recognition and maintenance of an efficient balance state, the system can automatically adapt to changes in external heat loads, only driving the corresponding fans when necessary, thus completely avoiding the energy waste caused by the continuous full - speed operation or frequent start - stop of fans in traditional methods. At the same time, since the rotational speeds of the four fans are differentially allocated according to a unified and coordinated internal state model, their operations cooperate with each other rather than cancel each other out, which further reduces the overall flow resistance and fan energy consumption of the system. More importantly, this solution incorporates a safety logic based on the temperature at key positions, which can keenly identify early signs of potential hazards such as dry burning in the evaporation section or over - cooling in the condensation section, and take forced intervention by immediately adjusting the rotational speed of specific fans (such as urgently replenishing liquid for the over - heated evaporation section or reducing cooling for the over - cooled condensation section). Thus, before the hardware protection mechanism activates, the system is actively pulled back to the safe range through software control strategies, greatly enhancing the self - protection ability and operating life of the device under complex or extreme working conditions.

[0036] Optimization Example 1 In order to transform the abstract working condition judgment into a series of clear and unambiguous logical comparison operations to ensure the precise and stable execution of the control strategy. This optimization example optimizes S2 into the following steps: S21: If Te1 is lower than the first temperature threshold T1 and ΔTec is less than the first temperature difference threshold δ1, then judge that the working condition mode is the insufficient vaporization mode; This step aims to accurately identify the specific working condition of "insufficient vaporization". Its design purpose is that when the heat input from the heat source is not sufficient to fully vaporize the working medium at the lower part of the evaporation section, and the circulating power of the entire heat pipe (reflected by the driving temperature difference ΔTec for the steam to rise) is also weak, the system can make a reliable judgment. The role of this step is to provide a clear trigger signal for the subsequent implementation of the control strategy centered on "strengthening evaporation". The key to implementation lies in the setting of two thresholds: the "first temperature threshold T1" and the "first temperature difference threshold δ1". T1 should be set slightly lower than the saturation temperature of the working medium under the expected working pressure, and its physical meaning is the temperature threshold at which the working medium can start to be effectively vaporized; δ1 should be set as a small positive number, representing the minimum temperature difference required for the working medium vapor to overcome the flow resistance and start flowing towards the condensation section. The overall logic of step S₂₁ is that only when both conditions of "insufficient temperature at the root of the evaporation section" (Te1 < T1) and "lack of system circulating power" (ΔTec < δ1) are met can it be confirmed as the insufficient vaporization mode, which avoids misjudgment caused by short - term fluctuations of individual parameters.

[0037] In practical implementation, the above thresholds can be determined in two ways: The first method is based on the derivation and calibration of the working fluid's thermal properties and system design parameters. For example, for a system using water as the working fluid and operating at near-normal pressure, its saturation temperature Ts is approximately 100℃. T1 can be calibrated as Ts-5℃ (i.e., 95℃), and δ1 as 3℃. The second method is based on statistical learning from historical system operating data. During system commissioning, a recognized "insufficient vaporization" state (such as extremely low heat source temperature or the initial stage of system startup) is artificially created or naturally recorded. A large amount of Te1 and ΔTec data at this time is collected, and the upper limit or a specific quantile (such as the 95th percentile) of its statistical distribution is taken as the values ​​of T1 and δ1. For example, using the first method, for the above water-based working fluid system, when Te1 = 92℃ (<95℃) and ΔTec = 2℃ (<3℃) are monitored in real time, the controller will determine that the current mode is insufficient vaporization.

[0038] S22: If Te1 is not lower than the second temperature threshold T2 and not higher than the third temperature threshold T3, and ΔTec is not lower than the second temperature difference threshold δ2 and not higher than the third temperature difference threshold δ3, then the operating mode is determined to be the high-efficiency balance mode. This step defines and identifies the ideal operating state of the system, namely the "high-efficiency equilibrium mode." The purpose of this step is to establish a clear "healthy operating range." When the system's key state parameters fall within this range, it indicates that the vaporization and condensation processes inside the heat pipe are well-matched, resulting in a highly efficient and stable cycle. Its core function is to provide the controller with a clear steady-state target, enabling the control strategy to focus on maintaining the system within this optimal region. The key point of this step is the definition of four thresholds, which together constitute a two-dimensional "high-efficiency range": the temperature range [T2, T3] and the temperature difference range [δ2, δ3]. T2 and T3 should be closely set around the working fluid saturation temperature Ts, for example, T2 = Ts - 2℃, T3 = Ts + 2℃, which physically means that the working fluid at the root of the evaporation section is in the high-efficiency phase transition region. δ2 and δ3 define the optimal driving temperature difference range to ensure cycle efficiency, for example, 8℃ to 15℃. Step S22, through an "AND" logical connection, requires that Te1 and ΔTec must simultaneously fall within their respective high-efficiency ranges, which together ensures that the system is in a comprehensively optimal state from two dimensions.

[0039] In practical implementation, there are two main methods for determining the high-efficiency range: The first is a combination of theoretical and experimental calibration. The system is run under design conditions for an extended period until it stabilizes. The stable Te1 and ΔTec values ​​are then measured and recorded, serving as the center of the high-efficiency range. A certain tolerance buffer (e.g., ±2℃, ±3℃) is then applied to determine T2, T3, δ2, and δ3. The second method is an adaptive threshold method. The system continuously records and evaluates its performance indicators (e.g., heat exchange rate, energy efficiency ratio) during operation. When these performance indicators consistently exceed a certain excellent level, Te1 and ΔTec are dynamically updated to reference values ​​for the high-efficiency range. For example, in design condition testing, if Te1 is consistently 101℃ and ΔTec is consistently 10℃ when the system stabilizes, then T2 can be set to 99℃, T3 to 103℃, δ2 to 8℃, and δ3 to 12℃. When the real-time parameters are Te1=102℃ (between 99~103℃) and ΔTec=11℃ (between 8~12℃), it is judged to be in efficient balance mode.

[0040] S23: If Te1 is higher than the fourth temperature threshold T4 and ΔTec is greater than the fourth temperature difference threshold δ4, then the operating mode is determined to be the insufficient condensation mode; where T1 < T2 < T3 < T4, and δ1 < δ2 < δ3 < δ4.

[0041] This step is responsible for detecting the critical condition of "insufficient condensation." Its purpose is to issue a timely and accurate alarm when the heat dissipation capacity on the condenser side cannot match the strong steam generation rate on the evaporator side, leading to a risk of overheating. This step triggers a protective control strategy aimed at "enhancing condensation" and "suppressing evaporation," preventing damage to the heat pipe due to excessive internal pressure or wall overheating. The judgment criteria for this step are two "above-threshold" conditions: Te1 must be higher than the "fourth temperature threshold T4," and ΔTec must be higher than the "fourth temperature difference threshold δ4." T4 should be set higher than the upper limit T3 of the high-efficiency range, representing the temperature at which overheating has already occurred in the evaporator section; δ4 should be set higher than the upper limit δ3 of the high-efficiency range, representing the temperature difference that leads to steam accumulation and an abnormally large circulating pressure difference due to poor condensation. The logic of step S23 means that only when both overheating in the evaporator section and excessive circulating pressure difference occur simultaneously is the insufficient condensation mode determined, which improves the accuracy of the judgment and its anti-interference capability.

[0042] In specific implementation, the ways to obtain the threshold values T4 and δ4 include: The first one is a conservative setting based on the safety margin. According to the allowable temperature of the heat pipe material or the critical pressure of the working medium, the maximum allowable temperature of the evaporation section is deduced inversely, and a safety margin is reduced from this temperature as T4; δ4 can be set based on the theoretical temperature difference corresponding to the maximum allowable pressure difference of the system. The second one is an observational setting based on performance degradation. Through experiments, gradually increase the heat load until the heat transfer of the system starts to decrease significantly (indicating that condensation becomes the bottleneck), and record the values of Te1 and ΔTec at this time as the references for T4 and δ4. For example, according to the safety analysis, if the maximum allowable temperature of the evaporation section is set to 110 °C, then T4 can be set to 108 °C; according to the test, when ΔTec exceeds 18 °C, the system efficiency drops sharply, so δ4 can be set to 18 °C. When it is monitored that Te1 = 109 °C (>108 °C) and ΔTec = 20 °C (>18 °C), the insufficient condensation mode is triggered.

[0043] By introducing a set of quantization thresholds with strict mathematical magnitude relationships (T1 < T2 < T3 < T4, δ1 < δ2 < δ3 < δ4), the judgment of the operating mode is transformed from a fuzzy concept into a series of precise and programmable logical comparison operations. This limitation ensures that under different operating conditions, the system's recognition of its own state is unique, definite, and repeatable, fundamentally solving the problems of unreliable and unclear control logic.

[0044] Optimization Example 2 On the basis of being able to accurately identify the "insufficient vaporization mode", the next core problem faced by the control system is: how to design and execute a set of clear, coordinated, and efficient fan control actions for this specific operating condition. Therefore, for the insufficient vaporization mode in this optimization example, S3 is optimized into the following steps: S31a: Increase the rotational speed of F1 to the first set rotational speed N1; This step is the primary and most direct action to deal with the insufficient vaporization condition. Its purpose is to immediately maximize the forced convection heat transfer intensity in the lower part of the evaporation section (the core area of the liquid working medium), so as to quickly "press" the heat of the external heat source into the heat pipe, and overcome the main contradiction that the working medium cannot be fully vaporized. The key to this step is to increase the rotational speed of F1 to a clear "first set rotational speed N1". The set value of this rotational speed N1 represents the maximum or most reasonable fan power resource that the control system can invest to overcome insufficient vaporization under the current operating condition. The implementation key is to ensure that this instruction can be executed quickly and accurately, so that the air volume of F1 instantaneously increases, directly impacts and thins the thermal boundary layer of the finned tube wall in the lower part of the evaporation section, thereby greatly increasing the heat transfer coefficient and prompting Te1 to quickly rise back to the effective vaporization temperature of the working medium (such as T1 = 95 °C and above in the previous example).

[0045] S31b: Increase the rotational speed of F3 to the second set rotational speed N2, where the ratio k1 of N2 to N1 satisfies: 0.6 < k1 < 0.8; The design of step S31b is based on a profound insight into system dynamics: while enhancing evaporation, condensation must be strengthened synchronously and moderately. Otherwise, the rapidly generated steam will accumulate in the condensation section, causing the pressure to rise, which will instead inhibit further vaporization in the evaporation section and form an internal blockage. The role of this step is to provide a "drainage channel" for the newly added vaporizing working medium and maintain the smooth circulation. The technical key lies in setting a specific proportional relationship (0.6 < k1 < 0.8) between the rotational speed of F3 (N2) and the rotational speed of F1 (N1). This proportional range ensures that the enhancement of the condensation capacity is "follow-up", rather than "dominant" or "lagging". A ratio greater than 0.6 ensures that the condensation has sufficient capacity to handle the newly added steam; a ratio less than 0.8 prevents excessive enhancement of condensation, avoiding premature and rapid liquefaction and reflux of the working medium, thus depriving the evaporation section of the time required to continue absorbing heat to complete the full vaporization process. This echoes the logic of suppressing the rotational speed of F4 in step S31c and jointly ensures the continuity of the vaporization process.

[0046] S31c: Control F2 to operate at the third set rotational speed N3 and control F4 to operate at the fourth set rotational speed N4, where both N3 and N4 are less than or equal to the preset basic rotational speed Nb, and Nb < N2.

[0047] Step S31c aims to handle the fans in the non-core area, and its purpose is to prevent the operation of these fans from interfering with the core "vaporization - condensation" matching process carefully constructed in steps S31a and S31b. This step clearly limits the rotational speeds of F2 and F4 below a "preset basic rotational speed Nb", which is usually set to a low rotational speed level that can only maintain the most basic air circulation in the air duct and prevent local dead zones. The role is to keep the upper part of the evaporation section (F2) ventilated minimally, preventing this area from becoming a heat sink or causing slight condensation due to complete non-flow; at the same time, let the lower part of the condensation section (F4) operate at a low speed, deliberately slowing down the downward reflux speed of the liquefied working medium, thus leaving a more sufficient time window for the evaporation section to absorb heat and vaporize. The technical key point "Nb < N2" ensures that this low-speed limit is absolute, that is, the rotational speeds of the auxiliary fans must be significantly lower than the rotational speed of the core condensation fan F3, solidifying the functional distinction between "core drive" and "auxiliary stability maintenance" from the rotational speed level.

[0048] In practical implementation, the above speed setting rules can be achieved through the following control strategies: The first is a lookup table method based on a preset speed table. The controller stores a speed table corresponding to the "insufficient vaporization mode," which directly specifies the specific values ​​or calculation formulas of N1, N2 (or k1), N3, N4, and Nb. For example, N1 can be calculated linearly or by PID based on the difference between the heat source temperature and the target Te1; ​​k1 is fixed at 0.7; Nb is set to a constant low value (such as 25% of the rated speed); N3 and N4 are directly equal to Nb. The second is a calculation method based on dynamic feedforward. The system calculates in real time the theoretical heat exchange required to make Te1 reach the target value (such as T2), and dynamically calculates the required F1 air volume and the corresponding speed N1 accordingly; then, based on the real-time calculated system heat load, the matching N2 is dynamically calculated proportionally to k1; N3, N4, and Nb are set as fixed percentages related to the current N1 or the total system air volume (such as N3=N4=0.2*N1) based on design experience. For example, using the previous water system, when the system is determined to be in a state of insufficient vaporization, a lookup table method is employed: the controller calls up parameters, setting N1 to 1200 rpm (rated speed), taking k1=0.7, then N2=840 rpm; setting the base speed Nb=300 rpm, then both F2 and F3 operate at 300 rpm or lower. This series of actions ensures that heat is concentrated and coordinated to address the primary problem of insufficient vaporization.

[0049] By concretizing the response strategy under the "insufficient vaporization mode" into a series of speed setting commands with clear mathematical relationships, the control actions were implemented from principle to practice. It clearly defines enhanced evaporation (F1 speed-up) as the primary response and creatively couples enhanced condensation (F3 speed-up) with it through a proportional coefficient k1, avoiding both condensation bottlenecks and excessive condensation. Simultaneously, by imposing low-speed limits on non-core fans (F2, F4), system resources are concentrated on the primary issue, protecting the continuity of the vaporization process. In summary, this optimization example enables the four fans to perform their respective functions precisely and efficiently under insufficient vaporization conditions, rapidly and smoothly propelling the system from an "insufficient heat absorption" state to a highly efficient equilibrium zone, significantly improving the system's response speed, energy efficiency, and stability during low load or start-up phases.

[0050] Optimization Example 3 Once the system is accurately identified as being in "high-efficiency balance mode," maintaining this ideal state becomes the core objective of control. However, without specific and stable control rules, relying solely on "coordinated adjustment" commands, the system is highly susceptible to deviating from the equilibrium point due to minor disturbances or inconsistencies in control commands, leading to decreased energy efficiency or unnecessary operating condition switching. To avoid this situation, this optimization example optimizes S3 for high-efficiency balance mode as follows: S32a: Control F1 to operate at the first balanced speed P1 and control F3 to operate at the second balanced speed P2, where P1 is equal to P2; Step S32a is a fundamental measure to maintain an efficient balanced state, and its design directly stems from the inherent physical requirements of the heat pipe under optimal operating conditions: the steam flow generated in the evaporation section must be precisely matched with the steam flow that can be liquefied in the condensation section. This step constructs this dynamic balance at the external forced convection level by mandating that the fan F1 serving the core area of the evaporation section and the fan F3 serving the core area of the condensation section operate at exactly the same speed (P1 = P2). Its core role is to keep the cooling / heat dissipation intensity externally applied to the evaporation section and the condensation section symmetric, so that the external environment provides a stable and balanced support condition for the internal "vaporization-condensation" cycle. The key to its implementation lies in ensuring that the equation "P1 is equal to P2" is strictly satisfied within the control period. This means that the controller needs to adopt a synchronous control strategy to send exactly the same speed setting value commands to F1 and F3, or adopt a master-slave tracking control to ensure that the speed of one fan precisely follows the other in real time.

[0051] S32b: Control F2 to operate at the third balanced speed P3 and control F4 to operate at the fourth balanced speed P4, where P3 is less than P1 and P4 is less than P2.

[0052] Step S32b aims to optimize the flow field distribution and prevent local interference. Its purpose is to conduct "stabilizing" management on the fans in the non-core areas on the premise of ensuring heat transfer balance in the core areas (the lower part of the evaporation section and the upper part of the condensation section). This step stipulates that the fans F2 located in the upper part of the evaporation section and F4 located in the lower part of the condensation section must have their speeds (P3 and P4) lower than the speeds of their corresponding core fans (P1 and P2) respectively. This relationship of "P3 < P1, P4 < P2" has a dual physical meaning: First, it ensures that the air flow intensity in the upper part of the evaporation section is weaker than that in the lower part, avoiding excessive cooling of the steam that has not fully absorbed heat and risen in the upper part of the evaporation section by too strong air flow, resulting in premature condensation of the steam; Second, it ensures that the air flow intensity in the lower part of the condensation section is weaker than that in the upper part, avoiding unnecessary excessive cooling (excessive subcooling) of the liquefied working medium in the lower part of the condensation section, thus affecting the temperature and state of the reflux working medium. This setting makes F2 and F4 play the roles of "flow field smoothers" and "process protectors", rather than the main heat transfer forces.

[0053] In specific implementation, the above balance control rules can be achieved through the following architectures: The first is the set value control based on a constant equilibrium point. A set of balanced speeds is pre-stored in the controller or calculated according to the current heat load level (which can be estimated through the inlet air temperature or historical data). For example, under the design conditions, the optimal total air volume required to maintain efficient balance is determined through experiments and divided equally into the core air volume and the auxiliary air volume, so as to directly calculate the absolute values of P1 (=P2), P3, and P4 (such as P1 = P2 = 900 rpm, P3 = P4 = 450 rpm). The second is the dynamic coupling control based on the proportional coefficient. The system does not directly set the absolute speed, but sets the proportional relationship between speeds. For example, the core balanced speed reference value Pb is defined (which can be fine-tuned according to the deviation between ΔTec and the target value δ), and then P1 = P2 = Pb; at the same time, the auxiliary fan speed ratio is defined as r (0 < r < 1, such as r = 0.5), then P3 = r * P1, P4 = r * P2. Taking an example, continue with the example of the aforementioned water working fluid system in the efficient balance mode (Te1 = 102°C, ΔTec = 11°C). Using the first method, the controller calls the preset parameters to control F1 and F3 to run synchronously at 900 rpm; control F2 and F4 to run at 400 rpm, strictly meeting the condition of 400 < 900. This set of instructions together shape a stable, uniform, and internally coordinated external flow field, providing an ideal external environment for the continuous efficient circulation inside the heat pipe.

[0054] By specifically quantifying the fan control in the efficient balance mode into the clear rule of "the core fans have the same speed and the auxiliary fans have a low speed", it provides a clear operation guide for the long-term stable operation of the system at the optimal working point. It makes "maintaining dynamic balance" no longer an abstract goal, but a set of measurable, verifiable, and repeatable control instructions. The same speed of the core fans (P1 = P2) mirrors the flow balance between internal vaporization and condensation from the aspect of external forced convection, which is the technical key to maintaining the efficient state; the low speed of the auxiliary fans (P3 < P1, P4 < P2) plays a role in preventing local overheating or overcooling and smoothing the overall flow field by suppressing potential disturbances in non-core areas.

[0055] Optimization Example 4 Under the efficient balance control rules established in Optimization Example 3, the system can already operate stably near the optimal operating point. However, during actual operation, external heat loads (such as heat source temperature, ambient temperature) may fluctuate within a certain range. Even if the internal state of the system (Te1, ΔTec) indicates being in the efficient balance mode, the heat transfer capacity provided by the current fan speed may still be higher than the actual requirement, that is, there is redundancy of "over-cooling" or "over-heating", resulting in unnecessary consumption of fan electrical energy. This optimization example aims to solve this problem. On the premise of maintaining the basic structure of efficient balance, it introduces direct feedback (ΔTa, ΔTc) of the actual heat transfer effect on the air side, and realizes "energy supply on demand" by intelligently synchronously reducing the speeds of all fans when the heat transfer demand is insufficient, so as to further explore the energy-saving potential of the system while ensuring sufficient heat transfer. Specifically, add the following step S0 before S2: Obtain the air-side temperature rise ΔTa in the evaporation section and the air-side temperature rise ΔTc in the condensation section; correspondingly, add step S32c to S3: If both ΔTa and ΔTc are less than the preset energy-saving temperature difference threshold, then synchronously reduce the speeds of F1, F2, F3 and F4 by the same proportion.

[0056] Step S0 is the perception basis of this energy-saving optimization strategy. The two parameters ΔTa (Ta_out - Ta_in) and ΔTc (Tc_out - Tc_in) directly and real-time reflect the sensible heat change amount obtained by the air after flowing through the heat exchanger, and are direct indicators for measuring the actual heat transfer intensity of the external fluid. Its purpose is to bypass the indirect inference of the internal state and directly evaluate whether the current fan air volume matches the actual heat load demand from the level of the final heat transfer effect. Step S32c is the decision-making and execution link based on this evaluation. Its core logic is: When and only when the air temperature rises in both the evaporation section and the condensation section are simultaneously lower than a preset "energy-saving temperature difference threshold", it is determined that there is redundant air volume that can be reduced in the current total air volume. This threshold represents the minimum air temperature rise allowed to maintain effective heat transfer, and its physical meaning is the lower limit of the temperature difference to ensure that there is still sufficient heat transfer driving force between the air and the heat pipe surface. "Synchronously reducing the speeds of F1, F2, F3 and F4 by the same proportion" is the key to implementing the energy-saving action. It requires the speeds of the four fans to be multiplied by the same scale factor (less than 1), which means that the core speed ratio relationships of "P1 = P2" and "P3 < P1, P4 < P2" established in Optimization Example 3 are strictly maintained during the speed reduction process. This ensures that after the overall air volume of the system is reduced, the relative relationships of the flow field structure and the forced convection intensity in each internal area of the system remain unchanged, so that while reducing energy consumption, the internal coordination of the achieved efficient balance state is not damaged, and only the entire operating point is translated to an operating curve with lower power consumption but still maintaining the optimal structure.

[0057] In practical implementation, this energy-saving optimization function can be achieved through the following control strategies: The first is a step-by-step speed reduction method based on a fixed threshold. A specific energy-saving temperature difference threshold ΔTe (e.g., 5℃) is preset. When the system is running in high-efficiency balance mode, ΔTa and ΔTc are continuously monitored. If the average value of both is lower than ΔTe within several consecutive control cycles (e.g., 5 cycles), a speed reduction action is triggered: the set speed of all current fans is multiplied by a fixed discount factor (e.g., 0.9). After speed reduction, monitoring continues. If the temperature rise is still lower than the threshold, the speed reduction continues at the same ratio until any temperature rise rises above the threshold or the speed reaches the minimum allowable limit. The second is a progressive optimization method based on continuous feedback. The optimization objective is to make "ΔTa and ΔTc as close as possible to but slightly higher than a minimum allowable value ΔTmin". The controller employs a slow outer-loop PID controller, whose input is the smaller of (ΔTa - ΔTmin) and (ΔTc - ΔTmin) (the smaller value is chosen to ensure sufficient performance on both sides). Its output acts on a common proportional coefficient K (initially 1), which is multiplied in real-time by the base rotational speed (P1, P2, P3, P4) calculated by the efficient balancing rule. By adjusting K, the minimum temperature rise is stabilized within a small range around ΔTmin, thereby achieving continuous, smooth, and adaptive adjustment of the airflow.

[0058] For example, using the aforementioned system in high-efficiency balance mode, the current rotational speeds are P1=P2=900 rpm and P3=P4=400 rpm. Assume a preset energy-saving temperature difference threshold ΔTe=5℃. The system monitors the evaporator section air inlet temperature Tain=80℃ and outlet temperature Taout=83.5℃, resulting in ΔTa=3.5℃; the condenser section air inlet temperature Tcin=25℃ and outlet temperature Tcout=28.8℃, resulting in ΔTc=3.8℃. Both are less than 5℃, triggering the energy-saving logic. Using a stepped speed reduction method with a discount factor of 0.85, the new set rotational speeds are: P1'=P2'=900*0.85=765 rpm and P3'=P4'=400*0.85=340 rpm. After the speed reduction, the airflow decreases, the contact time between the air and the heat pipe increases, and the temperature rises ΔTa and ΔTc will increase. If the temperature remains below 5°C after increasing the speed, the airflow can be further reduced. If any temperature rise exceeds 5°C, it indicates that the airflow is approaching the critical value, and further speed reduction should be stopped or the rotation speed should be slightly increased.

[0059] This optimization example superimposes a layer of refined energy efficiency optimization based on the final heat exchange effect on a robust and efficient balanced operation framework. By introducing the air-side temperature rise, a parameter directly reflecting heat exchange demand, it enables the control system to "sense demand and supply on demand." Its core rule of "proportional speed reduction" cleverly reduces total power consumption while fully preserving the collaborative relationship between the fans within the system, ensuring that energy-saving operation does not cause internal flow field turbulence or state imbalance. This allows the system to automatically shift its operating point to a lower energy consumption state when facing partial load conditions, significantly reducing the fan's operating power consumption. Furthermore, because this optimization is a fine-tuning based on the efficient balanced mode, it always maintains the system under optimal or near-optimal heat exchange architecture, avoiding insufficient heat exchange or localized deterioration that may result from blindly reducing speed.

[0060] Optimization Example 5 When the system is identified as "insufficient condensation mode," it indicates that the heat dissipation capacity on the condenser side has become a bottleneck limiting system performance and may even lead to overheating risks. In this case, simply adjusting all fans in the same direction (e.g., increasing their speed) will not only fail to solve the core problem but may also exacerbate vaporization on the evaporator side, worsening the issue. To avoid this situation, this optimization example optimizes S3 for insufficient condensation mode as follows: S33a: Increase the speed of F3 to the first target speed R1; Step S33a is the most direct and critical measure to address the insufficient condensation problem. Its purpose is to immediately maximize the forced convection heat dissipation intensity in the upper part of the condensation section (the core heat release zone of the gaseous working fluid) to quickly expel the latent heat of vapor accumulated in the heat pipe. This step is achieved by increasing the speed of F3 to a higher "first target speed R1". The set value of R1 represents the maximum heat dissipation resources that the system can allocate to address the current insufficient condensation. Its purpose is to quickly reduce the temperature Tc1 of the upper pipe wall in the condensation section, thereby increasing the driving force for vapor condensation, reducing the pressure in the condensation section, and providing a smooth "pressure relief channel" for the rising vapor in the evaporation section. The key to its implementation is to ensure that the increase of R1 is rapid and sufficient, often requiring it to reach or approach the safe operating limit of the fan to establish new and stronger condensation capacity in the shortest possible time.

[0061] S33b: Reduce the rotational speed of F1 to the second target rotational speed R2, where the ratio of R2 to R1, k2, satisfies: 0 < k2 < 1; Step S33b is designed based on a key balance principle: when condensation capacity becomes the primary concern, without intervention on the steam generation rate on the evaporation side, efforts to enhance condensation may be offset by the continuously high-speed steam generation. This step aims to suppress excessive vaporization in the evaporation section by actively and moderately reducing the speed of the lower fan F1 in the evaporation section to the "second target speed R2," thereby slowing down the steam generation rate at its source. This, in conjunction with step S33a, helps reduce the internal pressure and temperature of the system. The key technical aspect lies in the ratio of R2 to R1: "0 < k2 < 1." This ratio ensures that the speed reduction of F1 is relative to its original speed or a baseline value, and that the reduced speed R2 must be lower than R1. For example, k2 = 0.7 means that the new speed R2 of F1 is 70% of the new speed R1 of F3. The selection of this ratio requires a balance between suppressing evaporation and maintaining the basic cycle: k2 cannot be too small (e.g., close to 0), otherwise excessive suppression of evaporation may lead to cycle stagnation; k2 also cannot be too large (e.g., close to 1), otherwise the suppression effect will be insufficient. k2 is typically set between 0.5 and 0.9, depending on the system design and safety margin.

[0062] S33c: Increase the rotational speed of F2 to the third target rotational speed R3, where the ratio of R3 to R2, k3, satisfies: k3 > 1; Step S33c aims to manage the airflow in the upper part of the evaporation section, with the purpose of helping to prevent overheating or poor steam flow in the upper region of the evaporation section due to suppression of the lower part of the evaporation section (F1 speed reduction). This step is achieved by increasing the speed of the upper fan F2 in the evaporation section to the "third target speed R3", and specifying that "the ratio of R3 to R2 k3 > 1". This means that in the insufficient condensation mode, the speed R3 of F2 will be higher than the reduced speed R2 of F1. Its physical effects are threefold: First, by enhancing the airflow in the upper part of the evaporation section, the sensible heat of the pipe wall in this area can be more effectively removed, preventing heat accumulation and abnormal temperature Te2 rise in this area due to F1 speed reduction; Second, the appropriately enhanced airflow helps maintain the smooth upward flow of steam, avoiding insufficient upward steam power due to F1 speed reduction; Third, by setting k3 > 1, it is clarified that under this special operating condition, the role of F2 temporarily changes from "auxiliary stabilization" (such as low-speed operation in high-efficiency balance mode) to "active auxiliary cooling" to cope with the risk of local overheating in the evaporation section.

[0063] S33d: Increase the rotational speed of F4 to the fourth target rotational speed R4, where the ratio of R4 to R1, k4, satisfies: 0 < k4 < 1.

[0064] Step S33d is used to adjust the fan F4 at the lower part of the condensation section. Its purpose is to optimize the overall heat dissipation distribution of the condensation section and promote the stable reflux of the liquid working medium. In this step, the rotational speed of F4 is increased to the "fourth target rotational speed R4", and it is stipulated that "the ratio k4 of R4 to R1 satisfies: 0 < k4 < 1". This proportional relationship indicates that the speed increase of F4 follows that of F3, but its rotational speed R4 is always lower than the rotational speed R1 of the core condensation fan F3. This positioning ensures that the cooling intensity at the lower part of the condensation section is enhanced to help further cool the liquefied working medium (increase the degree of subcooling), which is beneficial for its stable reflux relying on gravity and prevents re-evaporation from occurring at the lower part of the condensation section. At the same time, the limitation of k4 < 1 prevents the rotational speed of F4 from being too high, avoiding interference with the air flow organization in the core condensation area at the upper part of the condensation section or causing the liquid working medium to be over-cooled (which may cause problems such as viscosity changes). Usually, k4 is set at a medium level, such as 0.4 to 0.8, to reflect its auxiliary rather than dominant role.

[0065] During specific implementation, the above-mentioned collaborative regulation rules can be achieved through the following control strategies: The first is the calculation method based on a preset proportional coefficient. When entering the condensation insufficiency mode, the controller determines the value of R1 according to the current state or preset rules (for example, directly set to 95% of the fan rated rotational speed). Then, R2, R3, and R4 are calculated according to the pre-calibrated proportional coefficients k2, k3, and k4 (for example, k2 = 0.7, k3 = 1.2, k4 = 0.6): R2 = k2 * R1, R3 = k3 * R2, R4 = k4 * R1. The second is the backward deduction method based on the target state. The system first sets a target, such as reducing ΔTec from the current value to δ3 (the upper limit of the efficient balance temperature difference) within a specified time. The total heat dissipation required on the condensation side is estimated according to the thermodynamic model, so as to calculate the approximate air volume and rotational speed R1 required for F3; at the same time, to limit the heat generation on the evaporation side, the proportion of the heat exchange amount on the evaporation side that needs to be reduced is estimated according to the model, so as to deduce the rotational speed R2 that F1 should be reduced to; the rotational speeds of F2 and F4 are set as functions related to R1 and R2 according to empirical formulas, ensuring that the conditions of k3 > 1 and 0 < k4 < 1 are satisfied.

[0066] For example, using the aforementioned water system, when the system is determined to be in a condensation deficiency mode (Te1=109℃, ΔTec=20℃), a preset proportional coefficient method is employed. R1 is set to the rated speed of F3, 1000 rpm. With a preset k2=0.7, R2=700 rpm (F1 speed reduced to 700 rpm). With a preset k3=1.3, R3=1.3 * 700 = 910 rpm (F2 speed increased to 910 rpm). With a preset k4=0.5, R4=0.5 * 1000 = 500 rpm (F4 speed increased to 500 rpm). This series of actions works in tandem: F3 exerts maximum heat dissipation to reduce the pressure and temperature in the condensing section; F1 moderately slows down to reduce the generation of new steam; F2 speeds up to prevent overheating in the upper part of the evaporation section and assists in steam rise; and F4 moderately speeds up to stabilize the reflux. The coordinated proportions of all actions ensure that the system can quickly and smoothly escape the risk of overheating.

[0067] By defining a specific proportional relationship between the speeds of the four fans under insufficient condensation mode, a refined, coordinated, and physically meaningful asymmetric control strategy was constructed. It doesn't simply increase the speed of all fans, but rather precisely identifies the different roles of each fan under insufficient condensation conditions: F3, as the "main attacker," is maximized to address the primary problem; F1, as the "regulator," is moderately suppressed to support the main attack; and F2 and F4, as "auxiliary units," are adjusted specifically to stabilize the flow field and recirculation process. The introduction of proportional coefficients k2, k3, and k4 quantifies and solidifies the synergistic relationships between these roles, ensuring the inherent coordination and predictability of the control actions.

[0068] Optimization Example 6 The aforementioned optimization example establishes a fine-grained control system for the system within its predictable normal operating range. However, in practical applications, abnormal operating conditions (such as sudden changes in heat sources, severe blockage of air ducts, or partial sensor failure) may cause critical temperature parameters to deviate significantly from the normal range, entering a dangerous area that could jeopardize equipment safety. In such cases, continuing to use the optimized control logic for conventional operating conditions like "insufficient vaporization" and "insufficient condensation" may not be sufficient to prevent the situation from worsening. Therefore, this optimization example adds the following steps to S2: S24: If Te1 is higher than the fifth temperature threshold T5, the operating mode is determined to be the evaporator section over-temperature protection mode; where T5 > T4; Step S24 is the determination stage for over-temperature risk, and its design is based on a strict safety margin principle. It sets a "fifth temperature threshold T5" (T5>T4) which is higher than the threshold T4 of the "insufficient condensation mode". The purpose of this design is to establish a "last line of defense": only when the temperature Te1 at the lower part of the evaporation section not only exceeds the efficient equilibrium range (T3), but even exceeds the "insufficient condensation" threshold (T4) indicating insufficient heat dissipation, and continues to rise to T5, it is determined that the system has exceeded the conventional regulation ability and enters the "over-temperature protection mode of the evaporation section" that requires emergency intervention. This avoids misjudgment between the conventional high-temperature working condition (insufficient condensation mode) and the truly dangerous working condition of the system, and ensures the seriousness and accuracy of the protection action.

[0069] S25: If Tc2 is lower than the sixth temperature threshold T6, it is determined that the working condition mode is the over-cooling protection mode of the condensation section, T6<T1; Step S25 is the determination for another extreme risk - over-cooling. It sets a "sixth temperature threshold T6" (T6<T1) which is lower than the threshold T1 of the "insufficient vaporization mode". When the temperature Tc2 on the outer wall of the lower part of the condensation section is lower than T6, it indicates that the temperature of the liquid working medium reflux area is too low, which may cause the viscosity of the working medium to be too large and affect the reflux, or in extreme cases cause the working medium to freeze, which will also damage the cycle. This judgment logic is independent of the temperature of the evaporation section and is specifically for the independent risk of over-cooling on the condensation side.

[0070] Correspondingly, add the following steps to S3: S36: When it is determined that it is the over-temperature protection mode of the evaporation section, control F1 to operate at the first protection speed Q1, and control F4 to operate at the second protection speed Q2, where the ratio r1 of Q1 to a preset safety speed Qs satisfies: 0 ≤ r1 < 0.5, and the ratio r2 of Q2 to Qs satisfies: r2 >1.5; Step S36 is the emergency execution plan for the extreme risk of S24. Its core strategy is "cut off the source and strongly supplement": by forcibly reducing the speed of F1 to an extremely low level (Q1 / Qs = r1 < 0.5, and even can be zero), minimize or reduce the "fuel" of supplying hot air to the overheated evaporation section to the greatest extent, and inhibit vaporization from the source; at the same time, by greatly increasing the speed of F4 to a high level (Q2 / Qs = r2 > 1.5), strongly drive the air flow at the lower part of the condensation section. The purpose is not only to strengthen cooling, but also to use the enhanced air flow to exert a "suction" effect on the liquid working medium in the condensation section, so as to promote the liquid working medium to flow back to the evaporation section as quickly as possible and perform emergency "fluid supplement" cooling for the evaporation section that may face the risk of dryness. The preset safety speed Qs serves as a common benchmark here, which can be the rated speed of the fan, the historical average speed, or a preset safe operating point.

[0071] S37: When it is determined to be in the subcooling protection mode of the condensation section, control F3 to operate at the third protection speed Q3 and control F2 to operate at the fourth protection speed Q4, where the ratio r3 of Q3 to Qs satisfies: 0 ≤ r3 < 0.5, and the ratio r4 of Q4 to Qs satisfies: r > < 1.5.

[0072] For the extreme risk of S25, the execution strategy of step S37 is "suppress cooling and ensure passage": by forcibly reducing the speed of F3 responsible for the main heat dissipation of the condensation section to an extremely low level (Q3 / Qs = r3 < 0.5), significantly weakening the cooling intensity of the condensation section and preventing the temperature from further dropping; at the same time, by significantly increasing the speed of F2 in the upper part of the evaporation section (Q4 / Qs = r4 > 1.5), injecting relatively high-temperature air into the upper part of the evaporation section (or preventing this area from being subcooled), the purpose is to increase the wall temperature of the upper part of the evaporation section, prevent the steam rising here from being prematurely condensed due to the subcooled environment, thus keeping the steam rising channel unobstructed and avoiding blocking the circulation due to the condensation of steam during the rising process. [[ID=!]]

[0073] In specific implementation, this protection logic can be implemented through the following architectures: The first is immediate interruption and override control based on the highest priority. The judgment logic (S24, S25) of the protection mode has the highest scan priority and interruption ability. Once the conditions are met, immediately interrupt any regular control logic currently being executed and forcibly set the fan speed to the protection speed (Q1 to Q4) calculated according to the fixed ratios (r1 to r4) and the reference Qs. For example, if Qs = 1000 rpm, r1 = 0.3, r2 = 2.0, then when over-temperature protection is triggered, immediately set F1 = 300 rpm and F4 = 2000 rpm. The second is robust protection with hysteresis and delay confirmation. To avoid false triggering of the protection mode due to sensor noise or instantaneous interference, add delay confirmation (such as Te1 being higher than T5 for more than 3 seconds) and hysteresis (the condition for exiting the protection mode is looser than the entry condition, for example, exiting over-temperature protection requires Te1 to be lower than T5 - 2°C) to the judgment conditions. At the same time, the set value of the speed for the protection action can be not fixed, but adjusted in grades according to the amplitude exceeding the threshold (for example, the more Te1 exceeds T5, the smaller the r1 value is set, and the larger the r2 value is set).

[0074] For example, continue to use the parameter system of the aforementioned water working medium system (T1 = 95°C, T4 = 108°C). Set the over-temperature protection threshold T5 = 110°C (satisfying > T4), and the subcooling protection threshold T6 = 90°C (satisfying < T1). Set the reference safe speed Qs = 1000 rpm, and the protection ratios r1 = r3 = 0.3, r2 = r4 = 1.8. This example is for demonstrating the logical relationship, and the actual threshold needs to be strictly set according to the characteristics of the working medium (such as anti-freezing requirements). For working media with a low freezing point, T6 will be significantly reduced.

[0075] Scenario 1 (triggering overtemperature protection): An anomaly causes Te1 to rapidly rise to 111 °C (>T5). The system immediately interrupts the current mode and enters overtemperature protection. Control F1 to operate at Q1 = 0.3 * 1000 = 300 revolutions per minute (extremely low speed), and control F4 to operate at Q2 = 1.8 * 1000 = 1800 revolutions per minute (high speed). This is aimed at urgently cooling down and promoting reflux.

[0076] Scenario 2 (triggering subcooling protection): In a severe cold environment, the temperature Tc2 at the lower part of the condensation section drops to 89 °C (<T6). The system immediately enters subcooling protection. Control F3 to operate at Q3 = 300 revolutions per minute (extremely low speed), and control F2 to operate at Q4 = 1800 revolutions per minute (high speed). This is aimed at reducing the cooling of the condensation section and preventing blockage of the steam passage at the upper part of the evaporation section.

[0077] Based on the complete operating condition control system, an independent and high-priority equipment safety "firewall" is constructed. It precisely defines the boundaries of the dangerous area by setting safety thresholds (T5 and T6) more extreme than all normal operating thresholds. Its protection control strategies (S36, S37) are no longer optimization adjustments, but rather adopt extremely strong asymmetric interventions (a combination of significant speed reduction and significant speed increase), directly targeting the physical causes of specific safety hazards for rapid correction. This can not only resolve risks through active software control before the hardware protection devices (such as fuses, pressure switches) may act, thereby avoiding unnecessary shutdowns, but also effectively prevent irreversible equipment damage caused by local dry burning or freezing. Embodiment

[0078] A heat exchanger provided by an embodiment of the present invention includes: A temperature sensor assembly for obtaining the outer wall temperature Te of the heat pipe at the lower part of the evaporation section, the outer wall temperature Te2 of the heat pipe at the upper part of the evaporation section, the outer wall temperature Tc1 of the heat pipe at the upper part of the condensation section, and the outer wall temperature Tc2 of the heat pipe at the lower part of the condensation section; a fan assembly including a first fan F1 provided at the lower part of the evaporation section, a second fan F2 provided at the upper part of the evaporation section, a third fan F3 provided at the lower part of the condensation section, and a fourth fan F4 provided at the upper part of the condensation section; a controller communicatively connected to the temperature sensor assembly and the fan assembly respectively; wherein, the controller is configured to execute any one of the gravity heat pipe heat exchanger fan control methods provided by Embodiment 1.

[0079] Specifically, the temperature sensor assembly is designed to overcome the limitations and lag in state perception caused by relying solely on fluid inlet / outlet temperatures or single-point tube wall temperatures in traditional heat exchanger control. Its core function is to synchronously and directly measure the outer wall temperatures (Te1, Te2, Tc1, Tc2) at key locations in the upper and lower sections of the gravity heat pipe during evaporation and condensation. This provides the controller with the fundamental and critical temperature field data necessary for inferring the internal working fluid phase change cycle state (such as vaporization sufficiency, condensation efficiency, and cycle power). The temperature sensors must be securely attached to the outer wall of a representative heat pipe (typically located in the middle of the tube bundle or the airflow center) using reliable thermally conductive mounting techniques (such as welding, high-strength thermally conductive adhesive bonding, or specialized clamps). The mounting points of the four sensors must strictly correspond to the four functional regions: the lower part of the evaporation section (liquid zone), the upper part of the evaporation section (steam rising zone), the upper part of the condensation section (steam condensation zone), and the lower part of the condensation section (liquid reflux zone). The fan assembly design breaks away from the conventional layout of traditional gravity heat pipe heat exchangers, which only installs one or multiple synchronous fans in parallel in the evaporation and condensation sections. Its core function is to provide the physical basis for achieving "zoned precise airflow control". By independently setting four fans (F1, F2, F3, F4) in the lower and upper parts of the evaporation section and the upper and lower parts of the condensation section, the controller can independently and differentiate the external forced convection environment of different functional areas of the heat pipe. F1 and F2 are installed at the lower and upper air vents (or inside the air duct) of the evaporation section shell, respectively, and F3 and F4 are installed at the lower and upper air vents of the condensation section shell, respectively. Specifically, they can be designed as "blowing" or "suction" modes; and their air outlet or inlet direction must be optimized to match the direction of the heat pipe fins to form a uniform airflow through the fin bundle and avoid ventilation dead zones or short circuits. The controller is designed to carry and execute the complex intelligent control algorithm defined in Example 1, solving the problems of multi-parameter fusion judgment and multi-actuator collaborative nonlinear control that traditional PLCs or simple temperature controllers cannot achieve. Its core function is to act as the "brain" of the entire system, processing data from temperature sensors in real time, making operating condition judgments and decisions based on embedded control logic, and generating corresponding PWM or analog voltage signals to independently and precisely drive the four fans to operate at the target speed. The key to implementation lies in its hardware composition and software architecture: On the hardware side, an industrial-grade microprocessor (such as an ARM Cortex-M series), DSP, or high-performance PLC can be used as the core, equipped with necessary analog / digital input modules for acquiring temperature signals, and analog output or PWM output modules for controlling fan speed (for AC fans, a frequency converter or voltage regulator module may also be required); on the software side, a program implementing the control method needs to be embedded, including data acquisition and filtering, operating condition mode judgment logic (S2), and four-fan collaborative speed control logic for different modes (S3).

[0080] The optimized controller is equipped with a data acquisition module to acquire temperature data detected by the temperature sensor assembly; an operating condition judgment module to calculate the temperature difference ΔTec between the upper outer wall of the evaporator and condenser based on the temperature data, and to determine the current operating condition mode based on Te1 and ΔTec; and a collaborative control module to generate differentiated collaborative speed control commands for F1, F2, F3, and F4 in the fan assembly based on the judgment result of the operating condition judgment module.

[0081] The data acquisition module is designed to encapsulate the interface functions between the controller and physical sensors in a specialized manner. This addresses the issues of bloated code, poor real-time performance, and weak anti-interference capabilities that arise from directly processing raw analog signals in the main control logic. Its core function is to act as the "sensory nerve endings" of the controller, responsible for periodically and reliably reading the raw electrical signals (such as the microvolt voltage of a thermocouple or the resistance value of a resistance temperature detector) from the temperature sensor components Te1, Te2, Tc1, and Tc2, and converting them into accurate and stable digital temperature values ​​for use by subsequent logic modules. The key to implementation lies in the complete processing chain: First, it needs to include signal conditioning circuitry (such as cold junction compensation and amplification for thermocouples, and constant current source driving and differential measurement for Pt100) to improve signal quality and common-mode interference immunity; second, it needs to configure a reasonable analog-to-digital converter (ADC) sampling rate and filtering algorithm (such as moving average filtering and median filtering) to suppress noise while ensuring real-time data transmission; finally, the module should have basic fault diagnosis functions, such as detecting sensor open circuits, short circuits, or readings exceeding the range, and be able to report abnormal states to the upper-level module. Through the collaboration of hardware and the underlying driver, this module transforms unstable physical signals into clean and reliable digital data streams. Its direct effect is to provide a highly reliable and accurate sensing foundation for the entire control system, isolating hardware fluctuations from interference with the upper-level intelligent algorithms.

[0082] The operating condition judgment module is the "decision center" of the control strategy. Its design is essential because it modularly encapsulates the complex logical judgment process based on comparing multiple temperature parameters and thresholds in the implementation, decoupling it from specific data acquisition and equipment control. Its core function is to receive clean temperature data from the data acquisition module, calculate the key state parameter ΔTec in real time, and determine the precise operating condition mode (e.g., insufficient vaporization, high-efficiency balance, insufficient condensation, over-temperature protection, over-cooling protection) that the system should be in based on a series of preset thresholds (e.g., T1-T6, δ1-δ4) and logical rules. The key to implementation lies in the determinism, real-time performance, and robustness of the judgment algorithm: the algorithm must ensure a definite and unique mode output under any input; the calculation and judgment process must be completed within a single control cycle without introducing delays; the algorithm should be able to handle fluctuations in sensor data within a reasonable range, avoiding frequent mode jumps, for example, through software hysteresis comparison or a state maintenance timer. This module condenses multi-dimensional temperature information into a clear operating condition identifier by executing a rigorous logical decision tree. Its direct effect is to provide a clear and unambiguous basis for the generation of subsequent control commands, which is the core link for the entire system to achieve intelligent operation.

[0083] The collaborative control module acts as the "executor" of the control strategy. Its design aims to centrally and uniformly schedule and implement the four-fan collaborative speed control rules defined in Implementation Example 1 for different operating modes. Its core function is to receive the current mode command from the operating condition judgment module and, based on this mode, call the corresponding control law or lookup table algorithm to calculate the target speed setpoints for F1, F2, F3, and F4 (e.g., N1 / N2, P1 / P2 / P3 / P4, R1 / R2 / R3 / R4, Q1 / Q2 / Q3 / Q4). These setpoints are then output through the corresponding interfaces to drive the fan components. The key to implementation lies in the accuracy and coordination of the control command generation, as well as the smooth transition during mode switching: for each mode, the module must strictly calculate the setpoints for each fan according to the speed relationships specified in the corresponding claims (e.g., proportional coefficient k1, constant speed P1=P2, protection ratio r1 / r2, etc.); when switching modes, a transition algorithm (e.g., setpoint ramp change) should be designed to avoid sudden changes in fan speed that could cause airflow impact or system oscillation. This module translates high-level decisions into precise action commands for low-level equipment. Its direct effect is to achieve refined shaping of the external flow field of the heat exchanger and its dynamic matching with the internal thermal state, making it the ultimate executor for improving overall energy efficiency and reliability. Example

[0084] This invention also provides a computer-readable storage medium storing a computer program that, when executed by a processor, implements the gravity heat pipe heat exchanger fan control method of Embodiment 1. The computer-readable storage medium can be any available medium capable of being stored by a computing device, or a data storage device such as a data center containing one or more available media. The available media can be magnetic media (e.g., floppy disks, hard disks, magnetic tapes), optical media (e.g., high-density digital video discs (DVDs)), or semiconductor media (e.g., solid-state drives). The computer-readable storage medium includes instructions that instruct a computing device to execute any of the gravity heat pipe heat exchanger fan control methods provided in Embodiment 1.

[0085] Those skilled in the art will clearly understand that, for the sake of convenience and brevity, other working processes of the method described above can be referred to the corresponding processes in the foregoing embodiments, and will not be repeated here.

[0086] Through the above description of the embodiments, those skilled in the art can clearly understand that this application can be implemented by means of software plus necessary general-purpose hardware, or it can be implemented by special-purpose hardware including application-specific integrated circuits, special-purpose CPUs, special-purpose memory, special-purpose components, etc. Generally, any function performed by a computer program can be easily implemented by corresponding hardware, and the specific hardware structure used to implement the same function can also be diverse, such as analog circuits, digital circuits, or special-purpose circuits. However, for this application, software program implementation is more often the preferred implementation method. Based on this understanding, the technical solution of this application, in essence, or the part that contributes to the prior art, can be embodied in the form of a software product. This computer software product is stored in a readable storage medium, such as a computer floppy disk, USB flash drive, mobile hard disk, ROM, RAM, magnetic disk, or optical disk, etc., and includes several instructions to cause a computer device (which may be a personal computer, training equipment, or network device, etc.) to execute the methods of the various embodiments of this application.

[0087] In the above embodiments, implementation can be achieved, in whole or in part, through software, hardware, firmware, or any combination thereof. When implemented in software, it can be implemented, in whole or in part, as a computer program product.

[0088] A computer program product includes one or more computer instructions. When the computer program instructions are loaded and executed on a computer, all or part of the flow or function according to the embodiments of this application is generated. The computer may be a general-purpose computer, a special-purpose computer, a computer network, or other programmable device. The computer instructions may be stored in a computer-readable storage medium or transmitted from one computer-readable storage medium to another. For example, computer instructions may be transmitted from one website, computer, training device, or data center to another website, computer, training device, or data center via wired (e.g., coaxial cable, fiber optic, digital subscriber line (DSL)) or wireless (e.g., infrared, wireless, microwave, etc.) means. The computer-readable storage medium may be any available medium that a computer can store or a data storage device such as a training device or data center that integrates one or more available media. The available media may be magnetic media (e.g., floppy disks, hard disks, magnetic tapes), optical media (e.g., DVDs), or semiconductor media (e.g., solid-state drives (SSDs)).

[0089] The above embodiments are only used to illustrate the technical solutions of the present invention, and are not intended to limit it. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A fan control method for a gravity heat pipe heat exchanger, characterized in that, include: S1: Obtain the outer wall temperature of the lower heat pipe of the evaporation section Te1, the outer wall temperature of the upper heat pipe of the evaporation section Te2, the outer wall temperature of the upper heat pipe of the condensation section Tc1, and the outer wall temperature of the lower heat pipe of the condensation section Tc2; S2: Based on Te1 and the temperature difference ΔTec between the upper outer wall of the evaporation-condensation section calculated from Te2 and Tc1, determine the current operating mode of the heat exchanger; S3: Based on the determined operating mode, the speeds of the first fan F1, the second fan F2, the third fan F3, and the fourth fan F4 are adjusted in a differentiated and coordinated manner. F1 and F2 are set in the lower and upper parts of the evaporation section, respectively, and F3 and F4 are set in the lower and upper parts of the condensation section, respectively.

2. The fan control method for a gravity heat pipe heat exchanger according to claim 1, characterized in that, S2 include: S21: If Te1 is lower than the first temperature threshold T1 and ΔTec is less than the first temperature difference threshold δ1, then the operating mode is determined to be the insufficient vaporization mode. S22: If Te1 is not lower than the second temperature threshold T2 and not higher than the third temperature threshold T3, and ΔTec is not lower than the second temperature difference threshold δ2 and not higher than the third temperature difference threshold δ3, then the operating mode is determined to be the high-efficiency balance mode. S23: If Te1 is higher than the fourth temperature threshold T4 and ΔTec is greater than the fourth temperature difference threshold δ4, then the operating mode is determined to be the insufficient condensation mode. Among them, T1<T2<T3<T4, and δ1<δ2<δ3<δ4.

3. The fan control method for a gravity heat pipe heat exchanger according to claim 2, characterized in that, When the insufficient vaporization mode is determined, S3 includes: S31a: Increase the speed of F1 to the first set speed N1; S31b: Increase the speed of F3 to the second set speed N2, where the ratio k1 of N2 to N1 satisfies: 0.6 < k1 < 0.8; S31c: Control F2 to run at the third set speed N3, and control F4 to run at the fourth set speed N4, where N3 and N4 are both less than or equal to the preset base speed Nb, and Nb < N2.

4. The fan control method for a gravity heat pipe heat exchanger according to claim 2, characterized in that, When the system is determined to be in the efficient balance mode, S3 includes: S32a: Control F1 to run at the first equilibrium speed P1, and control F3 to run at the second equilibrium speed P2, where P1 equals P2; S32b: Control F2 to run at the third equilibrium speed P3, and control F4 to run at the fourth equilibrium speed P4, where P3 is less than P1 and P4 is less than P2.

5. The fan control method for a gravity heat pipe heat exchanger according to claim 4, characterized in that, S2 also includes: S0: Obtain the air-side temperature rise ΔTa in the evaporation section and the air-side temperature rise ΔTc in the condensation section; S3 also includes: S32c: If both ΔTa and ΔTc are less than the preset energy-saving temperature difference threshold, then the rotation speeds of F1, F2, F3 and F4 will be reduced synchronously in the same proportion.

6. The fan control method for a gravity heat pipe heat exchanger according to claim 2, characterized in that, When the condensation deficiency mode is determined, S3 includes: S33a: Increase the speed of F3 to the first target speed R1; S33b: Reduce the rotational speed of F1 to the second target rotational speed R2, where the ratio of R2 to R1, k2, satisfies: 0 < k2 < 1; S33c: Increase the rotational speed of F2 to the third target rotational speed R3, where the ratio of R3 to R2, k3, satisfies: k3 > 1; S33d: Increase the rotational speed of F4 to the fourth target rotational speed R4, where the ratio of R4 to R1, k4, satisfies: 0 < k4 < 1.

7. The fan control method for a gravity heat pipe heat exchanger according to claim 1, characterized in that, S2 also includes: S24: If Te1 is higher than the fifth temperature threshold T5, then the operating mode is determined to be the evaporation section over-temperature protection mode; where T5 > T4; S25: If Tc2 is lower than the sixth temperature threshold T6, then the operating mode is determined to be the condensation section undercooling protection mode, T6 < T1; S3 also includes: S36: When the evaporation section is determined to be in over-temperature protection mode, control F1 to run at the first protection speed Q1 and control F4 to run at the second protection speed Q2, wherein the ratio r1 of Q1 to a preset safe speed Qs satisfies: 0 ≤ r1 < 0.5, and the ratio r2 of Q2 to Qs satisfies: r2 > 1.5; S37: When the condensation section is determined to be in the subcooling protection mode, control F3 to run at the third protection speed Q3 and control F2 to run at the fourth protection speed Q4, wherein the ratio r3 of Q3 to Qs satisfies: 0 ≤ r3 < 0.5, and the ratio r4 of Q4 to Qs satisfies: r4 > 1.

5.

8. A computer-readable storage medium having a computer program stored thereon, characterized in that: When the computer program is executed by the processor, it implements the steps of the gravity heat pipe heat exchanger fan control method according to any one of claims 1 to 7.

9. A heat exchanger, characterized in that, include: Temperature sensor assembly for acquiring the outer wall temperature Te1 of the lower heat pipe in the evaporation section, the outer wall temperature Te2 of the upper heat pipe in the evaporation section, the outer wall temperature Tc1 of the upper heat pipe in the condensation section, and the outer wall temperature Tc2 of the lower heat pipe in the condensation section; The fan assembly includes a first fan F1 disposed at the lower part of the evaporation section, a second fan F2 disposed at the upper part of the evaporation section, a third fan F3 disposed at the lower part of the condensation section, and a fourth fan F4 disposed at the upper part of the condensation section; The controller is communicatively connected to both the temperature sensor assembly and the fan assembly. The controller is configured to perform the gravity heat pipe heat exchanger fan control method as described in any one of claims 1 to 7.

10. The heat exchanger according to claim 9, characterized in that, The controller includes: The data acquisition module is used to acquire the temperature data detected by the temperature sensor assembly; The operating condition judgment module is used to calculate the temperature difference ΔTec between the upper outer wall of the evaporation and condensation sections based on the temperature data, and to determine the current operating condition mode based on Te1 and ΔTec. The collaborative control module is used to generate differentiated collaborative speed control commands for F1, F2, F3, and F4 in the fan assembly based on the judgment result of the working condition judgment module.

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