A temperature control method, device and medium of a hot air circulating heating device

Abstract

The application relates to the technical field of automatic control of industrial heating equipment, and provides a temperature control method and device for hot air circulation heating equipment and a medium, which comprises the following steps: acquiring a current temperature deviation and a temperature change rate; determining a current control state based on the current temperature deviation and the temperature change rate, and distributing a heat source adjustment weight and a circulation adjustment weight; generating a temperature control basic output quantity based on a temperature feedback control strategy, and determining a heat source basic control quantity and a circulation basic control quantity in combination with the weights; acquiring a state change quantity of a circulation adjustment unit, and determining a heat exchange disturbance compensation quantity; generating a heat source control instruction based on the heat source basic control quantity and the heat exchange disturbance compensation quantity, and generating a circulation control instruction based on the circulation basic control quantity, so as to cooperatively control a heat source adjustment unit and the circulation adjustment unit. The application realizes air-heat decoupling control, effectively suppresses secondary heat disturbance caused by air volume adjustment, and improves temperature control precision and system stability.

Description

Technical Field

[0001] This application relates to the field of automatic control technology for industrial heating equipment, specifically to a temperature control method, device, and medium for a hot air circulation heating equipment. Background Technology

[0002] Currently, in the temperature control process of hot air circulation heating equipment, independent feedback loops are typically used to regulate the heat source supply and hot air circulation separately. However, changes in the intensity of hot air circulation directly affect the convective heat transfer coefficient and heat dissipation rate within the furnace, thus causing secondary disturbances in the temperature field. Existing control strategies often lack effective decoupling mechanisms for this multivariate, strongly coupled characteristic. This leads to secondary temperature fluctuations or response lags when adjusting the circulating air volume to improve temperature uniformity, making it difficult to simultaneously achieve both heating efficiency and constant temperature accuracy. Therefore, there is an urgent need for a temperature control method that can effectively eliminate thermal disturbances caused by air volume adjustment and achieve coordinated control of the heat source and circulation. Summary of the Invention

[0003] To address the problem of decreased temperature control accuracy caused by secondary thermal disturbances resulting from airflow regulation in existing multivariable strongly coupled systems, this application proposes a temperature control method, device, and medium for a hot air circulation heating device. This method achieves dynamic weight allocation between heat source regulation and circulation regulation, as well as feedforward compensation for heat exchange disturbances, thereby eliminating temperature fluctuations caused by multivariable coupling.

[0004] To achieve the above objectives, this application adopts the following technical solution: The system acquires the current temperature deviation and temperature change rate of the hot air circulation heating equipment; determines the current control state based on the current temperature deviation and temperature change rate, and assigns heat source regulation weights and cycle regulation weights corresponding to the current control state; generates basic temperature control outputs based on the temperature feedback control strategy, and determines basic heat source control quantities and basic cycle control quantities by combining the heat source regulation weights and cycle regulation weights; acquires the state change of the cycle regulation unit, and determines the heat exchange disturbance compensation quantity based on the state change; generates heat source control commands based on the basic heat source control quantities and heat exchange disturbance compensation quantities, and generates cycle control commands based on the basic cycle control quantities, to coordinate the control of the heat source regulation unit and the cycle regulation unit.

[0005] The above scheme solves the problem that a single fixed parameter cannot simultaneously take into account both the heating rate and temperature uniformity by dynamically identifying the control state based on the temperature deviation and its rate of change, and adaptively allocating the control weights of the heat source and the circulation accordingly. At the same time, it introduces a heat exchange disturbance compensation based on the state change of the circulation adjustment unit, and superimposes it into the heat source control command. In principle, this cancels the secondary interference on temperature caused by the change in the convective heat transfer coefficient due to the change in air volume, realizes wind-heat decoupling control, and significantly improves the dynamic response quality and steady-state accuracy of the system.

[0006] In one implementation, when the current temperature deviation is greater than a first deviation threshold, the current control state is determined to be a heating state, and a first heat source regulation weight and a first cycle regulation weight are assigned, wherein the first heat source regulation weight is greater than the first cycle regulation weight; when the current temperature deviation is less than or equal to the first deviation threshold and greater than a second deviation threshold, the current control state is determined to be a near-target state, and a second heat source regulation weight and a second cycle regulation weight are assigned, wherein the second cycle regulation weight is greater than the second heat source regulation weight; when the current temperature deviation is less than or equal to the second deviation threshold, the current control state is determined to be a constant temperature state, and a third heat source regulation weight and a third cycle regulation weight are assigned.

[0007] This preferred scheme divides the system into three typical operating conditions: heating, approaching the target, and isothermal. It also differentiates the weight and priority of heat source and circulation in each condition. This allows the system to prioritize energy input efficiency when moving away from the target, prioritize enhancing thermal field uniformity to suppress overshoot when approaching the target, and maintain a fine balance during the isothermal stage. This results in the optimal matching of performance indicators in different control stages.

[0008] As one implementation method, in the near-target state, the second heat source regulation weight Wh2 and the second cycle regulation weight Wc2 are determined by the following formula: in, The second heat source is used to adjust the weight. The second cycle adjustment weight, and These are the basic weights for heat sources and the basic weights for cycles, respectively. The temperature change rate is denoted as α, and β are the preset heat source attenuation coefficient and cycle gain coefficient, respectively.

[0009] This preferred scheme uses the absolute value of the temperature change rate as a dynamic adjustment factor, so that the heat source weight decreases smoothly as the temperature approaches the target temperature, and the circulation weight is enhanced accordingly. This avoids overshoot caused by the inertia of the heat source when approaching the target temperature, while strengthening the ability of airflow mixing to eliminate local hot spots, thus achieving flexibility and stability in the transition process.

[0010] As one implementation method, the difference between the current operating parameters of the circulating control unit and the historical operating parameters of the previous control cycle is obtained as the state change quantity; based on the mapping relationship between the state change quantity and the heat exchange disturbance coefficient, the convective heat transfer rate is determined; based on the convective heat transfer rate and the current heat load demand, the heat exchange disturbance compensation quantity is determined to offset the interference of the state change of the circulating control unit on the heat exchange rate in the hot air circulating heating equipment.

[0011] This preferred scheme quantifies the real-time state changes of the circulating control unit into the rate of change of convective heat transfer, and calculates the compensation amount in combination with the current heat load demand. This makes the feedforward compensation not only reflect the magnitude of the air volume change, but also take into account the current thermal inertia state of the system, improving the timeliness and accuracy of the compensation, and effectively preventing temperature drops or spikes caused by sudden changes in air volume.

[0012] As one implementation method, the heat exchange disturbance compensation amount Uff is calculated using the following formula: in, This is the amount of compensation for the heat exchange disturbance. ΔQ is the feedforward compensation gain coefficient, and ΔQ is the circulating air volume change value corresponding to the state change. The current convective heat transfer coefficient is... The reference convective heat transfer coefficient is used; the current convective heat transfer coefficient is calculated based on the current operating parameters of the circulation regulating unit through a preset fluid dynamics correlation.

[0013] This preferred scheme introduces the ratio of the current convective heat transfer coefficient to the benchmark to perform nonlinear correction on the change in air volume, so that the compensation can truly reflect the degree of change in actual heat transfer conditions, rather than a simple linear extrapolation. This enhances the adaptability of the feedforward model under different operating conditions and further improves the robustness of wind-heat decoupling.

[0014] As one implementation method, the basic control quantity of the heat source and the heat exchange disturbance compensation quantity are weighted and fused to obtain the initial heat source control quantity; the initial heat source control quantity is subjected to a limiting process, and the limiting result is used as the heat source control command; wherein, the boundary conditions of the limiting process include the maximum heat source supply threshold and the minimum heat source supply threshold.

[0015] This preferred solution applies physical safety boundary constraints after fusing feedback and feedforward signals, which not only ensures rapid response of control commands, but also prevents the risk of actuator overload or shutdown due to algorithm anomalies or sensor noise, thus ensuring the operational safety of the equipment during various disturbance recovery processes.

[0016] As one implementation method, the heat source control command is generated using the following formula: in, This refers to the heat source control command. This refers to the basic control quantity of the heat source. The heat exchange disturbance compensation amount is Kw, the fusion weight coefficient is Umax, the maximum heat source supply threshold is Umin, and the minimum heat source supply threshold is Umin.

[0017] This preferred scheme clarifies the role of the fusion weight coefficient Kw, allows for flexible adjustment of the intervention intensity of feedforward compensation based on the system identification results, and ensures that the final output is always within the safe and feasible region through a dual limiting function, thus achieving a mathematical unification of control performance and safety constraints.

[0018] As one implementation method, before acquiring the current temperature deviation and temperature change rate of the hot air circulation heating device, the method further includes: acquiring the original temperature signal inside the hot air circulation heating device and converting the original temperature signal into a temperature electrical signal; performing sliding window sampling on the temperature electrical signal to acquire multiple electrical signal samples; performing median filtering and outlier removal processing on the multiple electrical signal samples to obtain a corrected temperature value; determining the current temperature deviation based on the difference between the corrected temperature value and the target temperature value, and determining the temperature change rate based on the corrected temperature values ​​of adjacent control cycles.

[0019] This preferred scheme effectively suppresses the contamination of temperature deviation and rate of change calculation by on-site electromagnetic interference and instantaneous impulse noise through multiple preprocessing steps such as sliding window sampling, median filtering, and outlier removal on the original temperature signal. This provides a high-confidence data foundation for upper-level dynamic weight allocation and feedforward compensation, and avoids malfunctions caused by signal distortion.

[0020] Furthermore, this application also provides a temperature control device for a hot air circulation heating equipment, comprising: a state and weight allocation module, used to acquire the current temperature deviation and temperature change rate of the hot air circulation heating equipment, determine the current control state based on the current temperature deviation and temperature change rate, and allocate heat source regulation weight and cycle regulation weight corresponding to the current control state; a basic control quantity determination module, used to generate a basic temperature control output quantity based on a temperature feedback control strategy, and determine the heat source basic control quantity and cycle basic control quantity by combining the heat source regulation weight and cycle regulation weight; a feedforward compensation calculation module, used to acquire the state change quantity of the cycle regulation unit, and determine the heat exchange disturbance compensation quantity based on the state change quantity; and a control command generation module, used to generate a heat source control command based on the heat source basic control quantity and the heat exchange disturbance compensation quantity, and generate a cycle control command based on the cycle basic control quantity, so as to coordinate the control of the heat source regulation unit and the cycle regulation unit.

[0021] The aforementioned device achieves a complete logical mapping of the aforementioned method through a modular architecture. The data flow between modules is clear and unambiguous, facilitating engineering implementation and maintenance. At the same time, it retains the core advantages of dynamic weight allocation and feedforward compensation working together, ensuring that the device-level product has the same temperature control performance as the method.

[0022] In addition, this application also provides a computer-readable storage medium having a computer program stored thereon, which, when executed by a processor, implements the method described above.

[0023] This storage medium enables the aforementioned temperature control method to be deployed in software form in various general-purpose or special-purpose controllers, enhancing the portability and upgrade convenience of the technical solution and providing a standardized intelligent temperature control solution for different models of hot air circulation heating equipment.

[0024] Beneficial effects: This application fundamentally solves the technical problem of secondary thermal disturbances caused by airflow regulation in hot air circulating heating equipment by dynamically allocating the weights of heat source and circulation regulation based on temperature deviation and rate of change, and calculating the heat exchange disturbance compensation amount in conjunction with the change in circulation state. The principle is as follows: First, the dynamic weighting mechanism adaptively adjusts the priority of energy input and thermal field uniformity according to the system's operating conditions, avoiding performance trade-offs under fixed parameter control. Second, the feedforward compensation mechanism pre-maps the changes in convective heat transfer coefficient caused by circulation intensity variations into heat source compensation amounts, which are then integrated with the feedback control output and output after safety limiting, achieving active decoupling of multivariable coupling effects. The synergistic effect of these two mechanisms not only significantly suppresses temperature overshoot and fluctuations and shortens disturbance recovery time, but also improves temperature control accuracy and system stability across the entire operating range, making it particularly suitable for precision baking or heat treatment scenarios with high requirements for temperature uniformity and response speed. Attached Figure Description

[0025] Figure 1 This is a flowchart of the temperature control method for a hot air circulating heating device provided in the embodiments of this application; Figure 2 This is a structural block diagram of the temperature control system of the hot air circulation heating equipment provided in the embodiments of this application; Figure 3 This is a flowchart of temperature signal acquisition and preprocessing provided in an embodiment of this application; Figure 4 This is a schematic diagram of the dynamic weight allocation and heat exchange disturbance compensation logic provided in the embodiments of this application; Figure 5 This is a flowchart of the heat source and circulation coordinated control command generation provided in the embodiments of this application; Figure 6 This is a schematic diagram illustrating the changes in adjustment weights under different control states provided in the embodiments of this application; Figure 7 This is a schematic diagram of the heat exchange disturbance feedforward compensation provided in the embodiments of this application. Detailed Implementation

[0026] To make the objectives, technical solutions, and beneficial effects of this application clearer, the embodiments of this application are described below in conjunction with the accompanying drawings. It should be understood that the following embodiments are only used to explain the technical solutions of this application and are not intended to limit the scope of protection of this application; where there is no conflict, the technical features of each embodiment can be combined with each other. Based on the disclosure of this application, other implementation methods obtained by those skilled in the art without creative effort should all fall within the scope of protection of this application.

[0027] Unless otherwise defined, the technical and scientific terms used in this specification have the meanings commonly understood by one of ordinary skill in the art to which this application pertains. The terminology used herein is for description of specific embodiments only and should not be construed as limiting the scope of protection of this application.

[0028] Example 1 like Figure 1 and Figure 2 As shown, this embodiment provides a temperature control method for a hot air circulation heating device. This method can be executed by a temperature control system 100 and is used to reduce secondary thermal disturbances caused by airflow regulation in scenarios where heat source regulation and hot air circulation regulation have coupled effects, thereby improving temperature control accuracy and operational stability. The method of this embodiment includes the following steps.

[0029] Step S100: Obtain the current temperature deviation and temperature change rate of the hot air circulation heating equipment. Specifically, the signal acquisition unit 110 collects the temperature signal inside the equipment in real time, and the central processing unit 120 determines the current temperature deviation based on the difference between the temperature signal and the preset target temperature value, and determines the temperature change rate by performing differential or derivative operations on the temperature data within a continuous control cycle. The current temperature deviation characterizes the degree of deviation of the equipment temperature from the target temperature, and the temperature change rate characterizes the trend of temperature change; both serve as inputs for subsequent state identification and control quantity allocation. It should be understood that in other embodiments, auxiliary variables such as temperature integral, ambient temperature, or material load status can be combined to further improve the characterization of the equipment's thermodynamic state.

[0030] Step S200: Based on the current temperature deviation and temperature change rate, the current control state is determined, and heat source regulation weights and cycle regulation weights corresponding to the current control state are assigned. Specifically, the central processing unit 120 has pre-set state division logic, which divides the equipment operating conditions into control states such as heating state, approaching target state, and constant temperature state according to the numerical range or combination relationship of the current temperature deviation and temperature change rate. For different control states, the system configures or calculates the corresponding heat source regulation weights and cycle regulation weights, enabling the control strategy to dynamically balance energy input efficiency and thermal field uniformity. For example, the heat source regulation weight is increased during the rapid heating phase, and the cycle regulation weight is increased when approaching the target temperature to enhance airflow mixing, reduce local temperature difference, and suppress overshoot. In this way, this embodiment quantifies different control objectives into executable weight parameters, providing a basis for subsequent decoupling control of the heat source and cycle.

[0031] In step S300, a basic temperature control output is generated based on the temperature feedback control strategy, and the basic control quantities for the heat source and the cycle are determined by combining the heat source adjustment weight and the cycle adjustment weight. Specifically, the temperature feedback control strategy can employ PID control, fuzzy control, or other closed-loop control algorithms to generate the basic temperature control output based on the current temperature deviation. This basic output represents the overall control requirement needed to reach or maintain the target temperature. Subsequently, the central processing unit 120 allocates the overall control requirement into the basic control quantity for the heat source and the basic control quantity for the cycle based on the heat source adjustment weight and the cycle adjustment weight, thereby converting the single temperature adjustment requirement into basic control components adapted to the heat source adjustment unit 131 and the cycle adjustment unit 132, respectively.

[0032] Step S400: Obtain the state change of the circulation regulating unit and determine the heat exchange disturbance compensation amount based on the state change. Specifically, in the hot air circulation heating equipment, the change in the operating state of the circulation regulating unit 132 not only affects the temperature uniformity inside the furnace but also changes the convective heat transfer coefficient and heat dissipation rate inside the furnace, thereby creating a secondary disturbance to the temperature field. To reduce the impact of this disturbance, this embodiment monitors the state change of the circulation regulating unit 132 in real time. The state change can be a change in fan speed, a change in inverter frequency, a change in damper opening, or a change in wind speed, etc. Based on the state change, the central processing unit 120 calculates the heat exchange disturbance compensation amount through a preset physical model, mapping table, or empirical formula. This compensation amount serves as a feedforward signal to pre-correct the heat source output when the circulation intensity changes, thereby reducing the response lag caused by relying solely on temperature deviation feedback.

[0033] In step S500, a heat source control command is generated based on the heat source basic control quantity and the heat exchange disturbance compensation quantity, and a cycle control command is generated based on the cycle basic control quantity to coordinate the control of the heat source regulating unit and the cycle regulating unit. Specifically, for the heat source channel, the central processing unit 120 superimposes or weights the heat source basic control quantity obtained in step S300 and the heat exchange disturbance compensation quantity obtained in step S400 to generate a heat source control command and sends it to the heat source regulating unit 131; for the cycle channel, the central processing unit 120 generates a cycle control command based on the cycle basic control quantity and sends it to the cycle regulating unit 132, and can also make corrections based on actual operating conditions and other compensation strategies. The execution unit 130 drives the heat source regulating unit 131 and the cycle regulating unit 132 to operate according to the above commands, thereby forming a control flow of "state perception - dynamic weight allocation - disturbance feedforward compensation - coordinated control output", which ensures the matching of control performance under different operating conditions while reducing secondary temperature fluctuations caused by airflow regulation.

[0034] Example 2 like Figure 3 As shown, this embodiment, based on Embodiment 1, further explains the partitioning logic of the control state and the calculation method of the dynamic weights. By distinguishing between stages such as heating, approaching the target, and isothermal control, this embodiment can avoid the problem of difficulty in balancing heating efficiency and isothermal accuracy when using fixed parameter control. As one implementation method, the current control state is determined based on the current temperature deviation and temperature change rate, and heat source adjustment weights and cycle adjustment weights corresponding to the current control state are assigned, specifically including the following:

[0035] Specifically, when the current temperature deviation exceeds a first deviation threshold, the current control state is determined to be a heating state, and a first heat source regulation weight and a first cycle regulation weight are allocated, with the first heat source regulation weight being greater than the first cycle regulation weight. During this stage, the system's control focus is on shortening the time to reach the target temperature, thus prioritizing increasing the proportion of heat source output. For example, the first heat source regulation weight can be set to 0.8 to 0.9, and the first cycle regulation weight can be set to 0.1 to 0.2, allowing the heat source regulation unit 131 to handle the main heating output, while the cycle regulation unit 132 maintains a basic airflow that meets the requirements of heat distribution and equipment safety, thus balancing the heating rate and suppressing local overheating.

[0036] When the current temperature deviation is less than or equal to the first deviation threshold and greater than the second deviation threshold, the current control state is determined to be close to the target state. A second heat source regulation weight and a second cycle regulation weight are assigned, with the second cycle regulation weight being greater than the second heat source regulation weight. This stage is a critical transition zone to prevent overshoot. As the temperature approaches the target value, maintaining a high heat source weight may cause the temperature to exceed the setpoint due to heat accumulation in the heating elements and furnace body. Therefore, the system shifts its control focus from heat source output to cycle regulation. By increasing the operating ratio of the cycle regulation unit 132, airflow mixing is enhanced, local hot spots are weakened, and heat source output is suppressed, making the temperature curve more smoothly approach the target temperature.

[0037] When the current temperature deviation is less than or equal to the second deviation threshold, the current control state is determined to be a constant temperature state, and the third heat source regulation weight and the third cycle regulation weight are allocated. Under the constant temperature state, the system enters the fine balance control stage. The heat source regulation weight and the cycle regulation weight can be balanced or slightly modified according to the equipment insulation performance, the heat absorption state of the material, and the process uniformity requirements to maintain long-term temperature stability and resist external slow-changing disturbances.

[0038] To make the weight adjustments under the near-target state more accurate and in accordance with thermodynamic laws, this embodiment introduces a dynamic calculation formula based on the rate of temperature change. As one implementation method, under the near-target state, the second heat source regulation weight Wh2 and the second cycle regulation weight Wc2 are determined by the following formula: in, The second heat source is used to adjust the weight. The second cycle adjustment weight, and These are the basic weights for heat sources and the basic weights for cycles, respectively. The temperature change rate is denoted as α, and β are the preset heat source attenuation coefficient and cycle gain coefficient, respectively.

[0039] The physical meaning of this formula lies in using the absolute value of the rate of temperature change, vT, as a dynamic adjustment factor to reflect the thermal inertia trend of the system in real time. The heat source attenuation coefficient α characterizes the system's sensitivity to thermal inertia, and its engineering setting value is usually related to the heat capacity of the heating element and the insulation performance of the furnace body; the larger the value of α, the faster the heat source weight decays under the same heating rate, thus triggering overshoot protection earlier. The cycle gain coefficient β characterizes the contribution of airflow mixing to eliminating temperature differences; the larger the value of β, the more it relies on enhanced convective heat transfer to homogenize the temperature field when approaching the target.

[0040] For example, suppose in a certain baking process, the heat source is based on... =0.6, the basic weight of the loop =0.4, and the system identification yielded a heat source attenuation coefficient α=0.2 and a cycle gain coefficient β=0.3. When the equipment enters a state close to the target and the temperature change rate... When the temperature is 0.5℃ / s, the following calculations are made: =0.6×1−0.2×0.5=0.54, =0.4×1+0.3×0.5=0.46. At this point, the heat source weight is still slightly higher than the cycle weight, maintaining a gentle convergence. However, if the temperature change rate spikes due to a large initial heating power... =2.0℃ / s, then It rapidly decreased to 0.6 × 1 − 0.2 × 2.0 = 0.36, while The value increases to 0.4 × 1 + 0.3 × 2.0 = 0.64. The above calculation results show that when the temperature approaches the target value at a relatively high rate, the system can automatically reduce the heat source output weight and increase the circulation regulation weight, weakening the local temperature difference and releasing some of the stored heat through airflow mixing, thereby reducing the risk of overshoot caused by thermal inertia. It should be understood that the above coefficients are only examples. In practical applications, step response tests or self-learning algorithms can be used to tune different models of hot air circulation heating equipment to obtain dynamic performance that adapts to the thermal response characteristics of the equipment.

[0041] Example 3 like Figure 4 and Figure 5 As shown, this embodiment, based on Embodiment 1, further explains the generation logic of the heat exchange disturbance compensation amount, so as to achieve air-thermal decoupling through feedforward control based on a physical model. As one implementation method, the central processing unit 120 obtains the difference between the current operating parameters of the cyclic adjustment unit and the historical operating parameters of the previous control cycle, and uses this difference as the state change quantity. Specifically, the central processing unit 120 reads the operating parameters of the cyclic adjustment unit 132 in each control cycle. These operating parameters can be the inverter output frequency, the actual motor speed, the wind speed sensor detection value, or the damper actuator opening feedback value, etc. By comparing the current operating parameters with the historical operating parameters of the previous control cycle, the state change quantity characterizing the magnitude and direction of the cyclic intensity change can be obtained. This differential processing method can promptly capture airflow changes caused by system adjustment actions or external disturbances, providing a trigger basis for subsequent feedforward compensation. It should be understood that in other embodiments, the average rate of change of a sliding window, the trend of change after low-pass filtering, or other equivalent parameters can also be used as the state change quantity to achieve a balance between response speed and noise immunity.

[0042] Furthermore, based on the mapping relationship between the state change and the heat exchange disturbance coefficient, the convective heat transfer rate is determined. In hot air circulation heating equipment, changes in the circulating air volume not only alter the airflow velocity but also affect the convective heat transfer coefficient between the furnace air and the heating elements and material surfaces. According to the principles of heat transfer, the convective heat transfer coefficient is typically non-linearly related to the flow velocity. Therefore, this embodiment uses empirical formulas, lookup tables, neural network models, or other preset mapping relationships to convert the state change of the circulation regulating unit 132 into the convective heat transfer rate, thereby quantifying the impact of air volume changes on the actual heat exchange efficiency. This step converts the actuator operating parameters into thermodynamic parameters, providing a physical basis for the compensation calculation.

[0043] Furthermore, based on the convective heat transfer rate of change and the current heat load demand, a heat exchange disturbance compensation amount is determined to offset the interference of the state change of the circulation regulating unit on the heat exchange rate within the hot air circulation heating equipment. Specifically, the heat exchange disturbance compensation amount serves as a feedforward control signal, its magnitude being related to the convective heat transfer rate of change and corrected in conjunction with the current heat load demand. When an increase in circulating air volume is detected leading to enhanced convective heat transfer, the system can predict changes in the furnace heat dissipation rate or material heat absorption efficiency, and accordingly increase or decrease the heat source output in advance. Compared to feedback control that only adjusts after a temperature deviation occurs, this embodiment can intervene in compensation promptly when air volume changes, thereby reducing secondary temperature fluctuations and disturbance recovery lag.

[0044] To make the aforementioned feedforward compensation mechanism more accurate and easier to implement in engineering, this embodiment provides a specific calculation formula. As one implementation method, the heat exchange disturbance compensation amount Uff is calculated using the following formula: in, This is the amount of compensation for the heat exchange disturbance. ΔQ is the feedforward compensation gain coefficient, and ΔQ is the circulating air volume change value corresponding to the state change. The current convective heat transfer coefficient is... The reference convective heat transfer coefficient is used; the current convective heat transfer coefficient is calculated based on the current operating parameters of the circulation regulating unit through a preset fluid dynamics correlation.

[0045] In this formula, the ratio It has a clear physical meaning, reflecting the degree of deviation of the actual heat transfer capacity under the current airflow condition from the baseline state. Since the convective heat transfer coefficient and wind speed typically have a nonlinear relationship (for example, approximately following a 0.8 power law under turbulent conditions), directly using this ratio for correction can overcome the model mismatch problem caused by relying solely on linear compensation based on the airflow change value ΔQ, ensuring that the feedforward quantity maintains high accuracy across different wind speed ranges. The feedforward compensation gain coefficient Kf is used to adjust the overall intensity of the compensation effect; its value can be determined through system identification experiments to adapt to the heat capacity characteristics of different equipment and the heater response speed. The circulating airflow change value ΔQ can be directly calculated from the frequency difference of the frequency converter or obtained differentially through the wind speed sensor; this application does not impose any restrictions on this.

[0046] To more clearly illustrate the technical solution of this embodiment, a specific industrial baking scenario is used as an example for demonstration. Assume that a hot air circulating heating device is operating in steady state with a circulating fan speed of 30Hz. The corresponding reference convective heat transfer coefficient at this time is... Normalized to 1.0. When process requirements change or the temperature equalization stage is reached, the central processing unit 120 issues a command to increase the fan speed to 40Hz. During this process, the system monitors in real time the state change ΔQ corresponding to a frequency increment of 10Hz. According to the preset fluid dynamics correlation, the current convective heat transfer coefficient hcurr at 40Hz becomes 1.2, meaning the heat transfer capacity increases by 20%. If the feedforward compensation gain coefficient... If the value is set to 5.0, then the heat exchange disturbance compensation is calculated by substituting it into the formula. =5.0 × 10 × 1.2 / 1.0 = 60. This means that as the fan accelerates, the control output of the heat source regulation unit 131 automatically adds an extra heat supply equivalent to 60 units. This feedforward action compensates in advance for the increased instantaneous heat dissipation caused by the increase in fan speed, preventing the furnace temperature from dropping at the moment the fan speed changes. Conversely, if the fan decelerates, the calculated... When the value is negative, the heat source output decreases accordingly, avoiding temperature overshoot caused by reduced heat exchange. Through this real-time calculation and superposition based on a physical model, this embodiment successfully minimizes the coupling interference of airflow regulation on the temperature field, significantly improving the dynamic quality and temperature control accuracy of the system.

[0047] Example 4 like Figure 5As shown, this embodiment, based on embodiments 1 to 3, further illustrates the generation logic and safety constraint mechanism of the heat source control command. As one implementation method, the basic heat source control quantity and the heat exchange disturbance compensation quantity are weighted and fused to obtain the initial heat source control quantity; the initial heat source control quantity is then subjected to amplitude limiting processing, and the limited result is used as the heat source control command. The boundary conditions for amplitude limiting processing include the maximum heat source supply threshold and the minimum heat source supply threshold. Specifically, the heat exchange disturbance compensation quantity is a feedforward value obtained based on a physical model or empirical formula. Under conditions such as equipment aging, changes in environmental conditions, or model simplification, there may be a deviation between the theoretical compensation quantity and the actual heat demand. If the compensated output is not constrained, under extreme conditions such as sudden fan stoppage, sensor noise spikes, or abnormal actuator feedback, the heat source output may exceed the actuator's capacity or the process safety range. Therefore, this embodiment, through weighted fusion and amplitude limiting constraints, ensures that the heat source control command can respond to cyclic disturbances while always remaining within the range allowed by safe equipment operation and the process.

[0048] To make the above fusion and limiting process more accurate and adaptable to the thermal response characteristics of different devices, this embodiment provides a specific calculation formula. As one implementation method, the heat source control command is generated using the following formula:

[0049] in, This refers to the heat source control command. This refers to the basic control quantity of the heat source. The heat exchange disturbance compensation amount is Kw, the fusion weight coefficient is Umax, the maximum heat source supply threshold is Umin, and the minimum heat source supply threshold is Umin.

[0050] In this formula, the fusion weighting coefficient Kw plays a crucial role in adjusting the intensity of feedforward compensation. In practical engineering applications, the value of Kw is usually between 0 and 1, but it can also be slightly greater than 1 based on the system identification results to enhance the compensation effect. When the equipment has a large thermal inertia or the heater response is slow, Kw can be appropriately reduced to make the feedforward effect gentler and avoid temperature oscillations caused by overcompensation. Conversely, for a sensitive heating system, Kw can be increased to improve the timeliness of disturbance rejection. For example, during the commissioning of a precision baking equipment, a slight overshoot was found in the temperature recovery curve when Kw was initially set to 1.0. After analysis, it was determined that this was due to the feedforward model overestimating the heat dissipation. Subsequently, Kw was adjusted to 0.85, and the system eliminated the overshoot phenomenon while maintaining its rapid recovery capability. This indicates that Kw can be used as a correction parameter between the feedforward model and the actual thermal response of the equipment.

[0051] Regarding the limiting boundaries, the settings of Umax and Umin are directly derived from the safe operating envelope of the equipment and process constraints. Umax typically corresponds to the rated maximum power of the heat source regulating unit or the heating amount corresponding to the upper limit of the process temperature to prevent material coking. Its function is to prevent heater overload damage or safety accidents caused by algorithm anomalies or feedforward overcompensation. Umin has a dual meaning: for gas heating equipment, it represents the minimum flow threshold for maintaining stable flame combustion; below this value may lead to flameout or incomplete combustion. For electric heating equipment, it represents the minimum power for maintaining basic thermal balance in the furnace or preventing heating elements from aging and failing due to frequent start-stop cycles. It should be understood that although this embodiment uses a fixed threshold as an example, in other embodiments, Umax and Umin can also be functions that dynamically change with the operating conditions. For example, a higher Umax is allowed during the heating phase, while Umax is automatically reduced during the constant temperature phase to improve temperature control accuracy, as long as it can define the safe control feasible domain at the current moment.

[0052] The dual limiting functions maxUmin, minUmax, ... in the formula form a robust logical defense in terms of execution timing. The inner function minUmax, ... first intercepts any abnormally high output exceeding the safety upper limit, while the outer function maxUmin, ... then provides a fallback to ensure that the output does not fall below the safety lower limit. This nested structure guarantees that regardless of fluctuations in the intermediate calculation result Ubase + Kw ⋅ Uff, the final output Ufinal will always fall within the Umin, Umax range. Compared to control methods without limiting, this embodiment incorporates safety constraints upfront into the control algorithm, enabling the system to respond quickly to strong disturbances such as sudden changes in airflow while preventing the output from exceeding the equipment's safe operating boundaries. This improves the reliability and robustness of the hot air circulation heating equipment across all operating conditions.

[0053] Example 5 like Figure 3 As shown, this embodiment, based on Embodiment 1, further illustrates the temperature signal acquisition and preprocessing process to provide a stable and reliable data foundation for the upper-level control algorithm. As one implementation method, before acquiring the current temperature deviation and temperature change rate of the hot air circulation heating equipment, the following signal conditioning steps are also included.

[0054] Step S101 involves acquiring the raw temperature signal within the hot air circulation heating equipment and converting it into an electrical temperature signal. Specifically, the signal acquisition unit 110 senses the thermodynamic state inside the furnace through a temperature sensor, which can be a thermocouple, a resistance temperature detector (RTD), or an infrared temperature probe, etc. To facilitate sampling and processing by the central processing unit 120, the raw temperature signal can be converted into an electrical temperature signal or digital temperature data via a transmitter, isolation amplifier circuit, analog-to-digital converter, or communication bus. It should be understood that the core of this step is to establish a signal mapping channel between the physical temperature field and the digital control domain, and it is not limited to a specific hardware circuit form.

[0055] Step S102 involves performing sliding window sampling on the temperature electrical signal to acquire multiple electrical signal samples. Specifically, the central processing unit 120 continuously reads the temperature electrical signal at a preset sampling period and writes it into a fixed-length first-in-first-out buffer, forming a sliding window containing N historical data points. The window length N can be set according to the system response speed and filtering requirements. For example, a smaller window length can be selected under conditions with a high heating rate to maintain control sensitivity; a larger window length can be selected under conditions with high temperature control accuracy requirements to enhance signal smoothing. Sliding window sampling reduces the probability of single-point sampling being affected by transient interference.

[0056] Step S103 involves performing median filtering and outlier removal on multiple electrical signal samples to obtain the corrected temperature value. Specifically, the outlier removal logic identifies and handles outlier samples caused by on-site electromagnetic interference, poor line contact, or transient sensor failures. For example, the mean and standard deviation of the samples within the window can be calculated, and samples deviating from the mean by more than a preset multiple of the standard deviation can be identified as outliers and discarded or replaced by nearby valid values; alternatively, a mutation threshold can be set based on the maximum allowable temperature change rate of the process, and samples exceeding the threshold can be considered noise. Subsequently, median filtering is performed on the samples after outlier removal, and the median value after sorting is selected as the corrected temperature value for the current moment. Compared to simple mean filtering, median filtering can better preserve the true temperature change trend while suppressing impulse noise, reducing control lag caused by excessive smoothing.

[0057] Step S104: Determine the current temperature deviation based on the difference between the corrected temperature value and the target temperature value, and determine the temperature change rate based on the corrected temperature values ​​of adjacent control cycles. Since the corrected temperature value has undergone sampling, outlier removal, and filtering, its signal-to-noise ratio is high, and the current temperature deviation calculated based on this corrected temperature value can more accurately reflect the actual temperature state of the equipment. Furthermore, the temperature change rate v_T is a differential or derivative calculation of the temperature signal, which can easily amplify high-frequency noise; if the unprocessed raw signal is used directly, it may cause malfunctions in dynamic weight allocation or oscillations in the feedforward compensation. Therefore, this embodiment reduces the impact of noise on the temperature change rate calculation through pre-signal conditioning, providing reliable input for the dynamic weight allocation in Embodiment 2 and the feedforward compensation calculation in Embodiment 3.

[0058] It should be understood that although this embodiment uses a combination of sliding window sampling, outlier removal, and median filtering as an example, other embodiments may employ low-pass filtering, Kalman filtering, moving average, or other equivalent signal processing methods, or the execution order of each processing step may be adjusted according to the device's response characteristics. Any implementation that can reduce measurement noise and improve the reliability of temperature change rate calculation can be considered an optional implementation of this application.

[0059] Example 6 like Figure 2 As shown, this embodiment provides a temperature control device for a hot air circulation heating equipment. This device can be implemented using software, firmware, hardware, or a combination thereof, and is used to execute the temperature control method described in the foregoing embodiments. As one implementation, the temperature control device includes a state and weight allocation module, a basic control quantity determination module, a feedforward compensation calculation module, and a control command generation module.

[0060] The state and weight allocation module is used to acquire the current temperature deviation and temperature change rate of the hot air circulation heating equipment, determine the current control state based on the current temperature deviation and temperature change rate, and allocate heat source adjustment weights and circulation adjustment weights corresponding to the current control state. Specifically, this module receives pre-processed temperature data from the signal acquisition unit 110 and executes the state recognition algorithm and weight mapping logic. During operation, this module first divides the current operating condition of the equipment into state intervals such as heating state, near-target state, or constant temperature state according to the deviation between the actual temperature and the target temperature and the temperature change trend; then, it outputs the corresponding weight coefficients according to the preset strategy table or dynamic calculation formula. Through this module, the control strategy can adaptively adjust the priority of heat source output and airflow mixing according to the real-time thermal field state. This module can be implemented as program code in the central processing unit 120, an independent function library, controller firmware, or programmable logic circuit.

[0061] The basic control quantity determination module is used to generate the basic output quantity of temperature control based on the temperature feedback control strategy, and determine the basic control quantity of the heat source and the basic control quantity of the cycle by combining the heat source regulation weight and the cycle regulation weight. Specifically, this module receives the weight parameters output by the state and weight allocation module and the current temperature deviation signal, and can integrate PID regulation, fuzzy control or other closed-loop feedback algorithms internally. This module first calculates the overall control requirement required to maintain the target temperature, and then decomposes the overall control requirement into two basic control components according to the heat source regulation weight and the cycle regulation weight, so that the heat source regulation unit 131 and the cycle regulation unit 132 can respond collaboratively based on a unified temperature control target.

[0062] The feedforward compensation calculation module is used to acquire the state changes of the circulating control unit and determine the heat exchange disturbance compensation amount based on the state changes. Specifically, this module is communicatively connected to the state feedback interface of the circulating control unit 132 to acquire operating parameters such as fan speed, damper opening, inverter frequency, or wind speed detection value in real time. When a change in circulation intensity is detected, this module calculates the heat load disturbance caused by the change in convective heat transfer coefficient according to a preset fluid dynamics correlation, heat exchange disturbance coefficient mapping table, or equivalent model, and quantifies it as a heat exchange disturbance compensation amount. Since this compensation amount is triggered by the disturbance source parameters, it can intervene in the heat source control loop before a significant temperature deviation occurs, improving the system's resistance to disturbances caused by changes in airflow.

[0063] The control command generation module generates heat source control commands based on the heat source basic control quantity and the heat exchange disturbance compensation quantity, and generates cycle control commands based on the cycle basic control quantity, to coordinate the control of the heat source regulating unit and the cycle regulating unit. Specifically, for the heat source channel, this module performs a weighted fusion of the heat source basic control quantity output by the basic control quantity determination module and the heat exchange disturbance compensation quantity output by the feedforward compensation calculation module, and performs amplitude limiting processing on the fusion result to ensure that the final heat source control command includes both the fast response of feedforward compensation and meets the safe operation boundary of the equipment. For the cycle channel, this module converts the cycle basic control quantity into a drive signal adapted to the cycle regulating unit 132. Through the above modular structure, the device of this embodiment can fully realize the state recognition, weight allocation, disturbance compensation and coordinated control logic of the aforementioned method, and is easy to port and apply in different models of hot air circulation heating equipment.

[0064] Example 7 This embodiment provides a computer-readable storage medium storing a computer program thereon. When executed by a processor, the computer program implements the temperature control method of the hot air circulation heating device described in any one of Embodiments 1 to 6. Specifically, the computer-readable storage medium may include volatile memory, such as random access memory, dynamic random access memory, or static random access memory; it may also include non-volatile memory, such as read-only memory, programmable read-only memory, erasable programmable read-only memory, electrically erasable programmable read-only memory, or flash memory. The storage medium may also be an external storage device such as a disk, optical disk, or magnetic tape. Any storage medium capable of storing program instructions for implementing the temperature control method of this application and capable of being read and executed by a computing device can be used as the computer-readable storage medium described in this application.

[0065] When the aforementioned computer program is loaded and executed by the processor in the electronic device, the electronic device can execute the temperature control method of this application. The electronic device can be the aforementioned central processing unit 120, or it can be an independent temperature controller, industrial computer, embedded control board, or server integrating the central processing unit 120. During execution, the processor reads and runs program instructions to complete logical operations such as acquiring temperature deviation and temperature change rate, determining control state, dynamic weight allocation, calculating heat exchange disturbance compensation, and generating cooperative control instructions. Therefore, the control algorithm of this application can be deployed as a software product to different hardware platforms, improving the portability, maintenance convenience, and upgrade efficiency of the technical solution.

[0066] Example 8 like Figure 6 As shown, this embodiment provides an application scenario of a temperature control method for a hot air circulation heating device in the whole-process temperature control of an industrial baking oven, illustrating the synergistic effect of the dynamic weight allocation mechanism and the heat exchange disturbance feedforward compensation mechanism under actual working conditions. It should be understood that this embodiment uses an industrial baking oven as an example for illustration, but the technical solution of this application is also applicable to heating devices with hot air circulation structures such as drying rooms, heat treatment furnaces, and aging test chambers. This embodiment does not constitute a limitation on the application scenario.

[0067] In this application scenario, the baking process requirements for a certain precision electronic component are as follows: the target temperature is 200℃, the allowable steady-state error is ±2℃, the maximum heating rate is 5℃ / min, and there may be disturbances during the baking process, such as opening the door to take out or put in materials. The central processing unit 120 performs full-process temperature control according to the methods described in Examples 1 to 5 above, which may specifically include the following four typical stages.

[0068] The first stage is the cold start heating stage. When the baking oven starts running from an ambient temperature of, for example, 25°C, the current temperature deviation is 175°C, which is greater than the preset first deviation threshold of, for example, 30°C. At this time, the system determines the current control state as the heating state according to the state determination logic described in Embodiment 2, and allocates the first heat source regulation weight and the first cycle regulation weight. In order to enable the oven temperature to enter the process requirement range more quickly, the system can set the first heat source regulation weight to 0.9 and the first cycle regulation weight to 0.1, so that the heat source regulation unit 131 outputs heat at a higher power, while the cycle regulation unit 132 maintains the basic speed, so as to reduce the risk of local overheating near the heater while ensuring the heating rate.

[0069] The second stage is the approach-target stage. As the furnace temperature rises above 190℃, the current temperature deviation narrows to within 10℃ and exceeds the second deviation threshold (e.g., 2℃), at which point the system automatically switches to the approach-target state. During this stage, if the high heat source weight continues to be used, the temperature is likely to exceed the 200℃ setpoint due to the thermal inertia of the heating elements and furnace body. Therefore, the system uses the dynamic weight calculation formula described in Example 3 to adjust the control weight allocation in real time. Assuming the current temperature change rate vT is 1.5℃ / s, the heat source attenuation coefficient α = 0.2, the cycle gain coefficient β = 0.3, the heat source base weight Wh_base = 0.6, and the cycle base weight Wc_base = 0.4, the calculated second heat source adjustment weight Wh2 = 0.6 × 1 − 0.2 × 1.5 = 0.42, and the second cycle adjustment weight Wc2 = 0.4 × 1 + 0.3 × 1.5 = 0.58. It can be seen that as the temperature approaches faster, the heat source weight is actively suppressed, while the cycle weight is significantly increased. The enhanced airflow mixing effect effectively eliminates the temperature gradient caused by unilateral heating in the furnace, causing the temperature difference at each measuring point to quickly converge to within 1℃. At the same time, air convection removes excess sensible heat from the surface of the heating element, fundamentally suppressing the occurrence of temperature overshoot.

[0070] The third stage is the isothermal phase. When the temperature stabilizes within the range of 200℃±2℃, the system enters the isothermal state and allocates the third heat source regulation weight and the third cycle regulation weight. At this time, the weight allocation can tend to be balanced, or it can be finely adjusted according to the measured temperature uniformity in the furnace; the heat source regulation unit 131 outputs the control quantity required to maintain thermal balance, and the cycle regulation unit 132 maintains an appropriate speed to maintain thermal field stability. In this state, the system mainly resists slow-changing disturbances such as environmental heat dissipation and material heat absorption changes through feedback regulation to ensure temperature stability during long-term baking.

[0071] The fourth stage is the door-opening disturbance recovery stage, which is a crucial step in verifying the effectiveness of the core technology of this application. During constant-temperature operation, when the operator opens the furnace door to add a new batch of materials, the air resistance inside the furnace changes instantaneously, causing drastic fluctuations in the circulating air volume. In traditional PID control schemes, due to the lag in temperature sensor detection of temperature drop, the controller often only starts increasing the heating power after the temperature has dropped by more than 5°C, resulting in a long recovery time and a tendency to generate secondary oscillations. In this embodiment, the central processing unit 120 immediately triggers the heat exchange disturbance feedforward compensation mechanism described in Embodiments 4 and 5 the instant it detects a sudden change in the rotational speed of the circulating adjustment unit or the frequency of the inverter. Specifically, the system calculates the rate of change of the convective heat transfer coefficient caused by the increase in air volume and generates a heat exchange disturbance compensation amount Uff based on the current heat load demand, which is then superimposed on the basic control amount of the heat source. In other words, while the furnace door opening causes increased heat dissipation, the heat source adjustment unit 131 can increase the corresponding heating power in advance to actively offset heat loss. Test results show that, under the same door opening time and environmental conditions, the temperature drop using the method described in this application is 1.8℃, which is significantly lower than that of the traditional PID control scheme, and the time for the temperature to recover to steady state is also shortened. These results demonstrate that the feedforward compensation mechanism based on a physical model can effectively cope with strongly coupled disturbances, reduce secondary thermal disturbances caused by airflow regulation, and thus improve the stability and production consistency of the industrial baking process.

[0072] Comparative Example 1 like Figure 7 As shown, to further verify the necessity and inventiveness of the heat exchange disturbance feedforward compensation mechanism in the technical solution of this application, a set of control experiments was set up in this comparative example. This comparative example uses the same industrial baking oven equipment, sensor configuration, target temperature value (200℃), and dynamic weight allocation strategy for the heating and isothermal stages as Example 8. The only difference is that the function of the feedforward compensation calculation module is turned off, that is, the heat exchange disturbance compensation amount Uff is forcibly set to 0, causing the system to degenerate into a conventional feedback control system that only relies on temperature deviation for adjustment. During the test of this comparative example, when the equipment enters the isothermal stage and performs the same door opening and material loading / unloading operation as in Example 8, the operation state of the circulation adjustment unit fluctuates drastically due to the change in wind resistance and the intrusion of cold air caused by the opening of the oven door, thereby causing an instantaneous change in the convective heat transfer coefficient inside the oven. Actual measurement data shows that at the moment of disturbance, due to the lack of pre-intervention of feedforward compensation, the heat source regulation unit failed to adjust its output power in time to offset the increased heat dissipation, resulting in a temperature drop of up to 5.2°C inside the furnace. Furthermore, the time required for the temperature to recover to the steady-state allowable error range (±2°C) was as long as 180 seconds. In contrast, under the same operating conditions, Example 8 experienced a temperature drop of only 1.8°C, with a recovery time shortened to less than 85 seconds.

[0073] The performance differences mentioned above stem from different control mechanisms. Conventional feedback control strategies follow a passive "deviation-adjustment" response mode, typically requiring the temperature sensor to detect a deviation of the actual temperature from the target value and generate a sufficient deviation signal before the controller calculates and outputs compensation. However, the thermal response of the temperature sensor has a certain lag, and the thermal inertia transfer of the heating element also takes time. Therefore, when facing rapid thermal disturbances caused by sudden changes in airflow, the feedback loop cannot completely avoid dynamic delay. In this comparative example, heat replenishment lags behind heat loss, resulting in larger temperature troughs and a longer recovery process. In contrast, the embodiments of this application introduce a heat exchange disturbance feedforward compensation mechanism based on a physical model, which can generate energy compensation values ​​as the state of the circulating adjustment unit changes and superimpose them into the heat source control command. This "disturbance-compensation" active decoupling mode reduces the impact of feedback lag and can more promptly offset secondary thermal disturbances. As can be seen from Comparative Example 1, the heat exchange disturbance feedforward compensation feature is an important technical means to improve the multivariable coupled temperature control performance of hot air circulating heating equipment.

[0074] The above description is merely a specific embodiment of this application and is not intended to limit the scope of protection of this application. For those skilled in the art, any equivalent substitutions, combinations, or modifications made to the relevant technical features without departing from the technical concept of this application shall fall within the scope of protection of this application. The scope of protection of this application shall be determined by the scope defined in the claims.

Claims

1. A temperature control method for a hot air circulation heating device, characterized in that, include: Obtain the current temperature deviation and temperature change rate of the hot air circulation heating equipment; The current control state is determined based on the current temperature deviation and the temperature change rate, and the heat source regulation weight and cycle regulation weight corresponding to the current control state are assigned. The temperature control basic output quantity is generated based on the temperature feedback control strategy, and the heat source basic control quantity and the cycle basic control quantity are determined by combining the heat source adjustment weight and the cycle adjustment weight. The state change of the circulating control unit is obtained, and the heat exchange disturbance compensation amount is determined based on the state change. Heat source control commands are generated based on the heat source basic control quantities and the heat exchange disturbance compensation quantities, and cycle control commands are generated based on the cycle basic control quantities, so as to coordinate the control of the heat source regulating unit and the cycle regulating unit.

2. The method according to claim 1, characterized in that, The process of determining the current control state based on the current temperature deviation and the temperature change rate, and allocating heat source regulation weights and cycle regulation weights corresponding to the current control state, includes: When the current temperature deviation is greater than the first deviation threshold, the current control state is determined to be a heating state, and a first heat source regulation weight and a first cycle regulation weight are assigned, wherein the first heat source regulation weight is greater than the first cycle regulation weight. When the current temperature deviation is less than or equal to the first deviation threshold and greater than the second deviation threshold, the current control state is determined to be close to the target state, and a second heat source regulation weight and a second cycle regulation weight are assigned, wherein the second cycle regulation weight is greater than the second heat source regulation weight. When the current temperature deviation is less than or equal to the second deviation threshold, the current control state is determined to be a constant temperature state, and a third heat source regulation weight and a third cycle regulation weight are assigned.

3. The method according to claim 2, characterized in that, In the near-target state, the second heat source regulation weight and the second cycle regulation weight are determined by the following formula: in, The second heat source is used to adjust the weight. The second cycle adjustment weight, and These are the basic weights for heat sources and the basic weights for cycles, respectively. The temperature change rate is denoted as α, and β are the preset heat source attenuation coefficient and cycle gain coefficient, respectively.

4. The method according to claim 1, characterized in that, The step of acquiring the state change of the circulating control unit and determining the heat exchange disturbance compensation amount based on the state change includes: The difference between the current operating parameters of the cyclic adjustment unit and the historical operating parameters of the previous control cycle is obtained as the state change quantity; Based on the mapping relationship between the state change and the heat exchange disturbance coefficient, the convective heat transfer rate is determined. Based on the convective heat transfer rate of change and the current heat load demand, the heat exchange disturbance compensation amount is determined to offset the interference of the state change of the circulation regulating unit on the heat exchange rate within the hot air circulation heating equipment.

5. The method according to claim 4, characterized in that, The heat exchange disturbance compensation amount is calculated using the following formula: in, This is the amount of compensation for the heat exchange disturbance. ΔQ is the feedforward compensation gain coefficient, and ΔQ is the circulating air volume change value corresponding to the state change. The current convective heat transfer coefficient is... The reference convective heat transfer coefficient is used; the current convective heat transfer coefficient is calculated based on the current operating parameters of the circulation regulating unit through a preset fluid dynamics correlation.

6. The method according to claim 1, characterized in that, The generation of heat source control commands based on the heat source basic control quantity and the heat exchange disturbance compensation quantity includes: The initial heat source control quantity is obtained by weighted and fused with the heat exchange disturbance compensation quantity. The initial heat source control quantity is subjected to a limiting process, and the limiting result is used as the heat source control command. The boundary conditions for the limiting process include the maximum heat source supply threshold and the minimum heat source supply threshold.

7. The method according to claim 6, characterized in that, The heat source control command is generated using the following formula: in, This refers to the heat source control command. This refers to the basic control quantity of the heat source. The heat exchange disturbance compensation amount is Kw, the fusion weight coefficient is Umax, the maximum heat source supply threshold is Umin, and the minimum heat source supply threshold is Umin.

8. The method according to claim 1, characterized in that, Before obtaining the current temperature deviation and temperature change rate of the hot air circulation heating equipment, the method further includes: The original temperature signal inside the hot air circulation heating device is collected and converted into a temperature electrical signal; Perform sliding window sampling on the temperature electrical signal to acquire multiple electrical signal samples; Median filtering and outlier removal are performed on the multiple electrical signal samples to obtain the corrected temperature value; The current temperature deviation is determined based on the difference between the corrected temperature value and the target temperature value, and the temperature change rate is determined based on the corrected temperature value of the adjacent control cycle.

9. A temperature control device for a hot air circulation heating equipment, characterized in that, include: The state and weight allocation module is used to obtain the current temperature deviation and temperature change rate of the hot air circulation heating equipment, determine the current control state based on the current temperature deviation and temperature change rate, and allocate heat source adjustment weight and circulation adjustment weight corresponding to the current control state. The basic control quantity determination module is used to generate a basic temperature control output quantity based on the temperature feedback control strategy, and determine the basic control quantity of the heat source and the basic control quantity of the cycle by combining the heat source adjustment weight and the cycle adjustment weight. The feedforward compensation calculation module is used to obtain the state change of the circulating control unit and determine the heat exchange disturbance compensation amount based on the state change. The control command generation module is used to generate heat source control commands based on the heat source basic control quantity and the heat exchange disturbance compensation quantity, and to generate cycle control commands based on the cycle basic control quantity, so as to coordinate the control of the heat source regulating unit and the cycle regulating unit.

10. A computer-readable storage medium having a computer program stored thereon, characterized in that, When the computer program is executed by a processor, it implements the method as described in any one of claims 1 to 8.

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