Air conditioner and comfort control method and system thereof

Abstract

The invention provides an air conditioner and a comfort control method and system thereof, and belongs to the technical field of air conditioner control. The method comprises the following steps: acquiring a first static pressure value of an air outlet, a second static pressure value at a diffusion port, air outlet temperature, relative humidity and surface temperature of the diffusion port; determining air duct static pressure loss, and determining actual available static pressure of the diffuser port according to the air duct static pressure loss and the reference static pressure value; determining an air duct resistance coefficient, and dynamically setting target static pressure; the air outlet dew point temperature is calculated, whether the difference value between the flow diffusing opening surface temperature and the air outlet dew point temperature is smaller than or equal to a first safety threshold value or not is judged, and if yes, it is judged that the condensation risk exists; and according to the difference value between the actually available static pressure and the target static pressure of the diffuser port, the rotating speed of the fan and the opening degree of the water valve are adjusted by combining the condensation risk judgment result. The operation state is collected through multiple sensors, algorithm automatic adjustment is carried out according to the collected data, the effects of noise reduction, energy conservation and condensation prevention can be effectively achieved, and the comfort of the air conditioner is improved.

Description

Technical Field

[0001] This invention belongs to the field of air conditioning technology, and more specifically, relates to an air conditioner and its comfort control method and system. Background Technology

[0002] In commercial buildings, the actual operating conditions of air conditioning terminals (such as fan coil units and air handling units) often deviate significantly from their design conditions due to complex installation environments and diverse duct designs. To ensure cooling efficiency, high static pressure fans are commonly used in the design with a large static pressure margin. However, the equipment selection is often too large, resulting in a "large horse pulling a small cart" phenomenon. This not only leads to long-term high-speed operation of the fans, causing high noise and energy consumption, but also causes condensation at the diffusers due to excessively high air velocity and low outlet air temperature, affecting building safety and user experience.

[0003] In existing technologies, some air conditioning systems control cooling capacity by adjusting the opening of water valves based on temperature feedback, or by controlling fan speed to maintain airflow by setting a fixed static pressure value. However, such control strategies lack the ability to sense dynamic changes in the actual resistance of the air duct, and cannot perform fine-grained dynamic adjustments based on real-time operating conditions. Furthermore, traditional control methods typically use temperature or pressure as a single control objective, making it difficult to simultaneously achieve energy savings and reduce consumption while also meeting various comfort requirements. Summary of the Invention

[0004] To address the shortcomings of existing technologies, this invention provides an air conditioner and its comfort control method and system.

[0005] The present invention adopts the following technical solution.

[0006] A first aspect of the present invention provides an air conditioning comfort control method, comprising: The system obtains the first static pressure value at the air outlet of the air conditioner terminal, the second static pressure value at the diffuser, the air outlet temperature and relative humidity, and the diffuser surface temperature. The static pressure loss of the air duct is determined based on the difference between the first static pressure value and the second static pressure value, and the actual usable static pressure of the diffuser is determined based on the static pressure loss of the air duct and the reference static pressure value. The duct resistance coefficient is determined based on the static pressure loss of the duct and the current operating air volume, and the target static pressure is dynamically set based on the duct resistance coefficient. The outlet dew point temperature is calculated based on the outlet air temperature and the relative humidity, and it is determined whether the difference between the diffuser surface temperature and the outlet dew point temperature is less than or equal to the first safety threshold. If so, it is determined that there is a risk of condensation. Based on the static pressure difference between the actual available static pressure at the diffuser and the target static pressure, and combined with the condensation risk assessment results, adjust the fan speed and water valve opening.

[0007] Optionally, determining the duct resistance coefficient based on the duct static pressure loss and the current operating air volume includes: The current operating air volume is calculated based on a preset formula, wherein the preset formula is that the current operating air volume is equal to the product of the rated air volume and the proportional coefficient, and the proportional coefficient is the ratio of the current speed to the rated speed. The duct resistance coefficient is calculated based on the ratio of the static pressure loss in the duct to the square of the current operating air volume.

[0008] Optionally, dynamically setting the target static pressure based on the duct resistance coefficient includes: The target static pressure is equal to the product of the duct resistance coefficient and the adjustment coefficient, plus a preset base value. The adjustment coefficient is determined according to the following rules: When the duct resistance coefficient is less than the first resistance coefficient threshold, the first adjustment coefficient is used; When the duct resistance coefficient is greater than or equal to the first resistance coefficient threshold and less than the second resistance coefficient threshold, the second adjustment coefficient is used; When the duct resistance coefficient is greater than or equal to the second resistance coefficient threshold and less than the third resistance coefficient threshold, the third adjustment coefficient is used. When the duct resistance coefficient is greater than or equal to the third resistance coefficient threshold, the fourth adjustment coefficient is used.

[0009] Optionally, adjusting the fan speed and water valve opening includes: When the static pressure difference is greater than the second preset threshold and there is no risk of condensation, the fan speed is reduced according to the first preset adjustment model, and the water valve opening is adjusted according to the anti-condensation adjustment strategy. When the static pressure difference is greater than the second preset threshold and there is a risk of condensation, the fan speed is reduced according to the first preset adjustment model, and the water valve opening is adjusted according to the second preset adjustment model. When the static pressure difference is less than or equal to the second preset threshold and there is a risk of condensation, the water valve opening is reduced according to the second preset adjustment model, and the fan speed is adjusted according to the noise reduction adjustment strategy. When the static pressure difference is less than or equal to the second preset threshold and there is no risk of condensation, the current fan speed and water valve opening are maintained.

[0010] Optionally, the first preset adjustment model is a nonlinear decreasing function of the target rotational speed and the static pressure difference: Multiply the nth power of the static pressure difference by the fan adjustment coefficient, where n is an empirical coefficient, and then subtract the product from the initial speed to obtain the target speed after adjustment.

[0011] Optionally, the second preset adjustment model is a logarithmic function of the target water valve opening and the static pressure difference: First, calculate the natural logarithm of the sum of the static pressure difference and 1. Then, multiply the natural logarithm by the water valve adjustment coefficient, and subtract the product from 1. The resulting difference is the target water valve opening after adjustment.

[0012] Optionally, the method further includes the step of periodically performing a calibration procedure: It operates under standard conditions, records current operating data, and compares it with historical operating data. Based on the changing trend of the first static pressure value or the changing trend of the duct resistance coefficient, the reference static pressure value, the fan adjustment coefficient, or the water valve adjustment coefficient are corrected, and a fault prompt message is generated when the value exceeds the preset range.

[0013] Optionally, the step of correcting the reference static pressure value, the fan adjustment coefficient, or the water valve adjustment coefficient based on the changing trend of the first static pressure value or the changing trend of the duct resistance coefficient includes: If the correction is made based on the trend of the first static pressure value, then: When the attenuation percentage of the first static pressure value is less than the first preset attenuation threshold, the reference static pressure value is corrected by the first amplitude, while the fan adjustment coefficient and the water valve adjustment coefficient are not corrected. When the attenuation percentage of the first static pressure value is greater than or equal to the first preset attenuation threshold and less than the second preset attenuation threshold, the reference static pressure value is subject to a second amplitude correction, and the fan adjustment coefficient and the water valve adjustment coefficient are subject to a first amplitude correction. When the attenuation percentage of the first static pressure value is greater than or equal to the second preset attenuation threshold, the reference static pressure value is corrected by a third amplitude, the fan adjustment coefficient and the water valve adjustment coefficient are corrected by a second amplitude, and a fault prompt message is generated. If the correction is made based on the changing trend of the duct resistance coefficient, then: When the percentage increase in the duct resistance coefficient is less than the first preset increase threshold, the reference static pressure value, the fan adjustment coefficient, and the water valve adjustment coefficient are not corrected. When the percentage increase in the duct resistance coefficient is greater than or equal to the first preset increase threshold and less than the second preset increase threshold, the reference static pressure value is corrected by a fourth amplitude, and the fan adjustment coefficient and the water valve adjustment coefficient are corrected by a third amplitude. When the percentage increase in the duct resistance coefficient is greater than or equal to the second preset increase threshold, the reference static pressure value is corrected by a fifth magnitude, the fan adjustment coefficient and the water valve adjustment coefficient are corrected by a fourth magnitude, and a fault prompt message is generated.

[0014] A second aspect of the present invention provides an air conditioning comfort control system for implementing an air conditioning comfort control method as described in the first aspect of the present invention, comprising: Two pressure sensors, a temperature and humidity sensor, a temperature sensor, and a control board, including: The two pressure sensors are respectively installed at the air outlet and the diffuser of the air conditioner terminal, and are used to collect the first static pressure value and the second static pressure value. The temperature and humidity sensor is installed at the air outlet to collect the air outlet temperature and relative humidity; The temperature sensor is disposed on the surface of the diffuser and is used to collect the surface temperature of the diffuser. The control board is connected to the pressure sensor, the temperature and humidity sensor, and the temperature sensor respectively, and is used to execute the air conditioning comfort control method described in the first aspect of the present invention.

[0015] A third aspect of the present invention provides an air conditioner, including a fan, a water valve, and an air conditioning comfort control system as described in the second aspect of the present invention.

[0016] Compared with the prior art, the beneficial effects of the present invention include at least the following: 1. This invention obtains the first static pressure value at the air outlet of the air conditioner terminal, the second static pressure value at the diffuser, the air outlet temperature and humidity, and the diffuser surface temperature. Based on these parameters, it calculates the duct static pressure loss, actual available static pressure, duct resistance coefficient, target static pressure, and condensation risk. Finally, it coordinates the fan speed and water valve opening according to the static pressure difference and condensation risk. This solves the problem of the lack of multi-dimensional perception and dynamic adjustment capabilities in existing air conditioner terminal control, and achieves comprehensive optimized control of noise reduction, energy saving, and anti-condensation, significantly improving the comfort of air conditioning.

[0017] 2. This invention calculates the current operating air volume based on a preset formula and determines the duct resistance coefficient based on the ratio of duct static pressure loss to the square of the current operating air volume. This solves the problem of difficulty and low accuracy in directly measuring air volume, and realizes the simple and accurate calculation of the duct resistance coefficient, providing a reliable basis for the subsequent dynamic setting of the target static pressure.

[0018] 3. This invention solves the problem that a fixed target static pressure cannot adapt to different duct types (such as long straight pipes, pipes with multiple bends, and pipes with varying diameters) by setting the target static pressure as the product of the duct resistance coefficient and the segmented adjustment coefficient plus a preset base value, and by selecting different adjustment coefficients according to the resistance coefficient range. This achieves adaptive adjustment of the target static pressure and makes the fan control more in line with the actual duct resistance characteristics.

[0019] 4. Based on the comparison results between the static pressure difference and the second preset threshold and the condensation risk assessment, this invention adopts different adjustment strategies (noise reduction priority, anti-condensation priority, etc.) to combine and adjust the fan speed and water valve opening under four different operating conditions. This solves the problem that the traditional single adjustment mode cannot take into account multiple objectives of noise reduction, energy saving and anti-condensation at the same time, and realizes multi-objective collaborative optimization control.

[0020] 5. This invention reduces the fan speed by using a nonlinear decreasing function as the first preset adjustment model, which solves the problem of noise and discomfort caused by sudden speed changes, and realizes that the speed decreases smoothly as the static pressure difference increases, effectively reducing operating noise and energy consumption.

[0021] 6. This invention uses a logarithmic function as the second preset adjustment model to adjust the water valve opening, which solves the problem of insufficient cooling or increased condensation caused by excessive water valve adjustment, and achieves smooth adjustment of the water valve opening, thereby improving the stability and comfort of anti-condensation control.

[0022] 7. This invention solves the parameter drift problem caused by equipment aging, dust accumulation in the air duct, etc. by periodically performing calibration procedures, recording data under standard operating conditions and comparing it with historical data, correcting the reference static pressure value, fan adjustment coefficient or water valve adjustment coefficient according to the changing trend of the first static pressure value or air duct resistance coefficient, and generating fault prompts when the range is exceeded. This ensures the long-term effectiveness of the control strategy and the reliability of the system.

[0023] 8. This invention corrects the reference static pressure value, fan adjustment coefficient, and water valve adjustment coefficient by using a graded correction rule according to different ranges of the percentage decrease in the first static pressure value or the percentage increase in the duct resistance coefficient. It also generates a fault prompt when the condition is serious, which solves the problem of over- or under-compensation of parameters, realizes refined adaptive correction and timely early warning, and further improves the accuracy of control and the maintainability of the system.

[0024] 9. This invention provides an air conditioning comfort control system, including two pressure sensors respectively installed at the air outlet and diffuser of the air conditioning terminal, a temperature and humidity sensor installed at the air outlet, a temperature sensor installed on the surface of the diffuser, and a control board. It solves the problem of difficulty in obtaining key parameters in real time and accurately, provides a hardware foundation for the above control method, and the system structure is simple and easy to install and integrate.

[0025] 10. This invention provides an air conditioner that includes the above-mentioned control system, which solves the problem of ordinary air conditioners lacking intelligent comfort control functions, enabling the air conditioner to have dynamic sensing and adaptive adjustment capabilities, thereby improving the product's market competitiveness and user experience. Attached Figure Description

[0026] Figure 1This is a flowchart of a method provided according to an embodiment of the present invention; Figure 2 This is a schematic diagram of a system provided according to an embodiment of the present invention. Detailed Implementation

[0027] To make the objectives, technical solutions, and advantages of this invention clearer, the technical solutions of this invention will be clearly and completely described below with reference to the accompanying drawings of the embodiments of this invention. The described embodiments are merely some embodiments of this invention, and not all embodiments. Based on the spirit of this invention, all other embodiments obtained by those skilled in the art without creative effort are within the protection scope of this invention.

[0028] In Embodiment 1, the present invention provides an air conditioning comfort control method, such as... Figure 1 As shown, it includes: Step 1: Obtain the first static pressure value at the air outlet of the air conditioner terminal, the second static pressure value at the diffuser, the air outlet temperature and relative humidity, and the diffuser surface temperature.

[0029] Preferably, in step 1: The first static pressure value is obtained by a first pressure sensor installed at the air outlet of the air conditioner terminal. The second static pressure value is obtained by a second pressure sensor located at the diffuser. The outlet temperature and relative humidity are obtained by a temperature and humidity sensor installed at the air outlet; The surface temperature of the diffuser is obtained by a temperature sensor installed on the surface of the diffuser.

[0030] More preferably, multiple pressure sensors and temperature sensors can be deployed at multiple air outlets or diffusers to perform weighted averaging of the collected static pressure and temperature values, thereby improving detection accuracy.

[0031] Specifically, in this embodiment, two pressure sensors are used: one is placed at the air outlet of the air conditioner terminal to detect the static pressure P1 at the air outlet in real time, and the other is placed at the diffuser of the air duct to detect the static pressure P2 at the diffuser. A temperature and humidity sensor is placed at the air outlet to detect the outlet air temperature T and relative humidity RH; A temperature sensor is placed on the surface of the diffuser to detect its surface temperature Ts.

[0032] It should be noted that by setting up multiple pressure sensors, temperature and humidity sensors, and temperature sensors, this invention can obtain the static pressure value, air temperature and humidity, and diffuser surface temperature at the air outlet and diffuser of the air conditioner terminal in real time. This provides an accurate data basis for subsequent precise calculation of duct loss, condensation risk, etc., and solves the problem of traditional control relying on a single sensor or fixed parameters, realizing multi-dimensional state perception.

[0033] Step 2: Determine the static pressure loss of the air duct based on the difference between the first static pressure value and the second static pressure value, and determine the actual usable static pressure of the diffuser based on the static pressure loss of the air duct and the reference static pressure value.

[0034] Preferably, the static pressure loss P3 of the air duct is obtained by subtracting the first static pressure value P1 and the second static pressure value P2 collected in real time. P3 = P1 - P2 Based on the preset reference static pressure value P0, the actual usable static pressure P at the diffuser is calculated: P = P0 - P3 Specifically, the reference static pressure value P0 is the default static pressure setting value when the air conditioner leaves the factory.

[0035] It should be noted that the present invention determines the static pressure loss of the air duct by the difference between the first static pressure value and the second static pressure value, and calculates the actual available static pressure at the diffuser by combining the reference static pressure value. This allows for an accurate assessment of the impact of air duct resistance on the available air pressure at the end, solving the problem of inaccurate static pressure estimation caused by differences in air duct design and complex installation environment, and providing a reliable static pressure basis for subsequent adjustment.

[0036] Step 3: Determine the duct resistance coefficient based on the static pressure loss of the duct and the current operating air volume, and dynamically set the target static pressure based on the duct resistance coefficient.

[0037] Preferably, determining the duct resistance coefficient based on the duct static pressure loss and the current operating air volume includes: The current operating air volume is calculated based on a preset formula, wherein the preset formula is that the current operating air volume is equal to the product of the rated air volume and the proportional coefficient, and the proportional coefficient is the ratio of the current speed to the rated speed. The duct resistance coefficient is calculated based on the ratio of the static pressure loss in the duct to the square of the current operating air volume.

[0038] It should be noted that this invention calculates the current air volume by adjusting the rotation speed ratio and uses the ratio of static pressure loss to the square of the current operating air volume to calculate the duct resistance coefficient. This method can easily and accurately obtain the resistance coefficient, solving the problems of difficulty and high cost in directly measuring air volume and improving calculation efficiency and accuracy.

[0039] Preferably, the step of dynamically setting the target static pressure based on the duct resistance coefficient includes: The target static pressure is equal to the product of the duct resistance coefficient and the adjustment coefficient, plus a preset base value. The adjustment coefficient is determined according to the following rules: When the duct resistance coefficient is less than the first resistance coefficient threshold, the first adjustment coefficient is used; When the duct resistance coefficient is greater than or equal to the first resistance coefficient threshold and less than the second resistance coefficient threshold, the second adjustment coefficient is used; When the duct resistance coefficient is greater than or equal to the second resistance coefficient threshold and less than the third resistance coefficient threshold, the third adjustment coefficient is used. When the duct resistance coefficient is greater than or equal to the third resistance coefficient threshold, the fourth adjustment coefficient is used.

[0040] Specifically, the current operating air volume Q2 is derived from the current speed F, and the air volume and speed have a linear relationship: Q2 = Q1 × F1 / F2 Where Q1 is the rated air volume under rated operating conditions, F1 is the rated speed under rated operating conditions, and F2 is the current speed.

[0041] The duct resistance coefficient is calculated as follows: R=P3 / Q² The target static pressure P_t is calculated using the following formula: P_t=30+k×R Where k takes values ​​based on the range of the resistance coefficient: When 1 ≤ R < 1.2, k = 6; When 1.2 ≤ R < 1.5, k = 8; When R ≥ 1.5, k = 10; When R < 1, k = 0.

[0042] The above interval divisions and coefficients can be calibrated based on laboratory measured data and can be adjusted according to actual applications.

[0043] Preferably, step 3 further includes determining the corresponding duct type based on the duct resistance coefficient, wherein the duct type includes long straight pipes, multi-bend pipes, and variable diameter pipes, wherein: When the duct resistance coefficient is less than the first resistance coefficient threshold or greater than or equal to the third resistance coefficient threshold, it is determined to be a variable diameter pipe type. When the duct resistance coefficient is greater than or equal to the first resistance coefficient threshold and less than the second resistance coefficient threshold, it is determined to be a long straight pipe type. When the duct resistance coefficient is greater than or equal to the second resistance coefficient threshold and less than the third resistance coefficient threshold, it is determined to be a multi-bend pipe type.

[0044] Specifically, dividing the air duct type into intervals based on the R value includes: If 1 ≤ R < 1.2, it is determined to be a long straight pipe; If 1.2 ≤ R < 1.5, it is judged as a pipe with multiple bends; If R<1 or R≥1.5, it is determined to be a variable diameter pipe.

[0045] Step 4: Calculate the outlet dew point temperature based on the outlet air temperature and the relative humidity, and determine whether the difference between the diffuser surface temperature and the outlet dew point temperature is less than or equal to the first safety threshold. If so, it is determined that there is a risk of condensation.

[0046] Preferably, the first safety threshold is preset with a safety margin based on the detection error of the temperature sensor.

[0047] Specifically, the outlet dew point temperature Td is calculated from the outlet air temperature T and the relative humidity RH.

[0048] Set a first safety threshold ΔT, for example, ΔT=1.5℃. This value takes into account the detection error of the temperature sensor itself (usually ±1℃) and reserves a margin of 0.5℃.

[0049] If Ts≤Td+ΔT, then there is a risk of condensation; otherwise, there is no risk.

[0050] The value of ΔT can be adjusted according to the characteristics of the selected temperature sensing bulb model.

[0051] It should be noted that this invention calculates the dew point temperature by measuring the outlet air temperature and relative humidity, compares it with the surface temperature of the diffuser, and determines the risk of condensation by combining it with a safety threshold. This allows for early prediction of condensation, solving the problem of traditional methods that only passively handle condensation after it occurs, and achieving proactive prevention and control of condensation.

[0052] Step 5: Based on the static pressure difference between the actual available static pressure at the diffuser and the target static pressure, and combined with the condensation risk assessment results, adjust the fan speed and water valve opening.

[0053] Preferably, the adjustment of the fan speed and water valve opening includes: When the static pressure difference is greater than the second preset threshold and there is no risk of condensation, the fan speed is reduced according to the first preset adjustment model, and the water valve opening is adjusted according to the anti-condensation adjustment strategy. When the static pressure difference is greater than the second preset threshold and there is a risk of condensation, the fan speed is reduced according to the first preset adjustment model, and the water valve opening is adjusted according to the second preset adjustment model. When the static pressure difference is less than or equal to the second preset threshold and there is a risk of condensation, the water valve opening is reduced according to the second preset adjustment model, and the fan speed is adjusted according to the noise reduction adjustment strategy. When the static pressure difference is less than or equal to the second preset threshold and there is no risk of condensation, the current fan speed and water valve opening are maintained.

[0054] It should be noted that, based on different combinations of static pressure difference and condensation risk, this invention adopts differentiated adjustment strategies such as noise reduction priority and anti-condensation priority, thereby achieving synergistic optimization of multiple objectives (noise reduction, energy saving, and anti-condensation), avoiding the disadvantages caused by single control, and improving overall comfort.

[0055] More preferably, the first preset adjustment model is a nonlinear decreasing function of the target rotational speed and the static pressure difference: Multiply the nth power of the static pressure difference by the fan adjustment coefficient, where n is an empirical coefficient, and then subtract the product from the initial speed to obtain the target speed after adjustment.

[0056] It should be noted that the present invention uses a nonlinear decreasing function to adjust the rotational speed, so that the rotational speed decreases smoothly as the static pressure difference increases, avoiding noise and discomfort caused by sudden changes in rotational speed, while effectively reducing noise and energy consumption.

[0057] More preferably, the second preset adjustment model is a logarithmic function of the target water valve opening and the static pressure difference: First, calculate the natural logarithm of the sum of the static pressure difference and 1. Then, multiply the natural logarithm by the water valve adjustment coefficient, and subtract the product from 1. The resulting difference is the target water valve opening after adjustment.

[0058] It should be noted that the present invention uses a logarithmic function to adjust the opening of the water valve, so that the opening of the water valve is adjusted smoothly with the change of static pressure difference, which prevents condensation from occurring and avoids insufficient cooling due to excessive closure, thereby improving the stability of anti-condensation control.

[0059] Specifically, the adjustment of the fan speed and water valve opening includes: Let the difference between the actual available static pressure at the diffuser and the target static pressure be ΔP = P - P_t, and the second preset threshold be 20 Pa.

[0060] When ΔP>20Pa and there is no risk of condensation, the noise reduction priority mode is entered, and the fan speed is reduced according to the first preset adjustment model, i.e., calculated according to the following formula: F = F0 - α(ΔP) n Where F0 is the current speed, α is the fan adjustment coefficient, and n is the second empirical coefficient. For example, α = 0.5 and n = 1.2. Simultaneously, the water valve opening is adjusted according to an anti-condensation control strategy. For example, the anti-condensation control strategy is that when the fan speed drops significantly according to the calculated target speed, the water valve can be appropriately closed. For instance, in a certain project, ΔP=57Pa, and the calculated fan speed drops significantly to approximately 2kHz, so the water valve opening is adjusted to 90%.

[0061] When ΔP > 20Pa and there is a risk of condensation, noise reduction should still be prioritized. The fan speed should be reduced according to the first preset adjustment model, i.e., according to the formula F = F0 - α(ΔP). n calculate; Simultaneously, adjust the water valve opening according to the second preset adjustment model, i.e., calculate according to the following formula: K = 1 - βln(ΔP + 1) Where β is the water valve adjustment coefficient, for example, β=15.

[0062] It should be noted that the β value can be adjusted according to the degree of condensation risk (for example, appropriately reducing the β value to avoid insufficient cooling due to excessive closure of the water valve).

[0063] When ΔP≤20Pa and there is a risk of condensation, the anti-condensation priority mode is entered. The water valve opening is reduced according to the second preset adjustment model, that is, calculated according to the formula K=1-βln(ΔP+1) (for example, in a certain project, ΔP<20Pa, the calculated K=50%). At the same time, the fan speed is finely adjusted according to the noise reduction adjustment strategy (for example, by reducing it by 0.5kHz). Once the risk of condensation is eliminated, normal noise reduction and energy-saving control will be restored.

[0064] When ΔP≤20Pa and there is no risk of condensation, the system is in a relatively ideal state, maintaining the current fan speed and water valve opening.

[0065] The above coefficients are fixed empirical values ​​from the factory and can be adjusted according to the actual test results for different models of fan coil units.

[0066] Preferably, the method further includes the step of periodically performing a calibration procedure: It operates under standard conditions, records current operating data, and compares it with historical operating data. Based on the changing trend of the first static pressure value or the changing trend of the duct resistance coefficient, the reference static pressure value, the fan adjustment coefficient, or the water valve adjustment coefficient are corrected, and a fault prompt message is generated when the value exceeds the preset range.

[0067] It should be noted that this invention, through periodic calibration, can automatically compensate for parameter drift caused by equipment aging, dust accumulation in air ducts, etc., maintain long-term control effectiveness, and prompt maintenance when abnormalities occur, thereby improving the reliability and adaptability of the system.

[0068] More preferably, the step of correcting the reference static pressure value, the fan adjustment coefficient, or the water valve adjustment coefficient based on the changing trend of the first static pressure value or the changing trend of the duct resistance coefficient includes: If the correction is made based on the trend of the first static pressure value, then: When the attenuation percentage of the first static pressure value is less than the first preset attenuation threshold, the reference static pressure value is corrected by the first amplitude, while the fan adjustment coefficient and the water valve adjustment coefficient are not corrected. When the attenuation percentage of the first static pressure value is greater than or equal to the first preset attenuation threshold and less than the second preset attenuation threshold, the reference static pressure value is subject to a second amplitude correction, and the fan adjustment coefficient and the water valve adjustment coefficient are subject to a first amplitude correction. When the attenuation percentage of the first static pressure value is greater than or equal to the second preset attenuation threshold, the reference static pressure value is corrected by a third amplitude, the fan adjustment coefficient and the water valve adjustment coefficient are corrected by a second amplitude, and a fault prompt message is generated. If the correction is made based on the changing trend of the duct resistance coefficient, then: When the percentage increase in the duct resistance coefficient is less than the first preset increase threshold, the reference static pressure value, the fan adjustment coefficient, and the water valve adjustment coefficient are not corrected. When the percentage increase in the duct resistance coefficient is greater than or equal to the first preset increase threshold and less than the second preset increase threshold, the reference static pressure value is corrected by a fourth amplitude, and the fan adjustment coefficient and the water valve adjustment coefficient are corrected by a third amplitude. When the percentage increase in the duct resistance coefficient is greater than or equal to the second preset increase threshold, the reference static pressure value is corrected by a fifth magnitude, the fan adjustment coefficient and the water valve adjustment coefficient are corrected by a fourth magnitude, and a fault prompt message is generated.

[0069] It should be noted that this invention uses a graded correction rule to finely compensate the control parameters according to the different degrees of static pressure decay or resistance increase. This ensures the accuracy of control while avoiding over-correction. At the same time, it provides timely warnings through fault prompts to ensure the stable operation of the system.

[0070] Specifically, the control board's storage chip records data such as P1, P2, T, RH, F, K, and Ts for each run, forming an operation log; Calibration is performed automatically once a month or quarter: Tested under standard operating conditions (e.g., air supply mode, fan speed 900 rpm, water valve opening 80%, ambient temperature 26℃) and compared with historical data.

[0071] If the first static pressure value P1 shows a decreasing trend or the resistance coefficient R continues to increase, the reference static pressure value P0 and the adjustment parameters α and β are corrected according to preset rules. For example, the correction rules are as follows: Compared with P1 in the previous calibration, if the attenuation of P1 is less than the first preset attenuation threshold (e.g., 5%), the reference static pressure value P0 is increased by the first preset compensation percentage (e.g., 5%), and α and β are not corrected. If the attenuation of P1 is greater than or equal to the first preset attenuation threshold and less than the second preset attenuation threshold (e.g., 5%~10%), then P0 is increased by the second preset compensation percentage (e.g., 5%~10%), and α and β are increased by the first preset correction percentage (e.g., 5%). If the attenuation of P1 is greater than or equal to the second preset attenuation threshold (e.g., 10%), then P0 increases by the third preset compensation percentage (e.g., 15%), α and β increase by the second preset correction percentage (e.g., 10%), and a fault code is fed back to remind the user to perform maintenance.

[0072] Similarly, a similar adjustment can be made based on the percentage increase in R, setting the percentage increase in R as Rz: If Rz is less than the first preset increase threshold (e.g., 1%), then no correction is made; If Rz is greater than or equal to the first preset increase threshold and less than the second preset increase threshold (e.g., 1%~5%), then P0 increases by the fourth preset compensation percentage (e.g., 3%), and α and β increase by the third preset correction percentage (e.g., 5%). If Rz is greater than or equal to the second preset increase threshold (e.g., 5%), then P0 increases by the fifth preset compensation percentage (e.g., 5%), α and β increase by the fourth preset correction percentage (e.g., 10%), and a maintenance prompt is given.

[0073] Preferably, the method further includes the step of calculating a comprehensive comfort index: Noise levels are estimated based on fan speed, energy consumption levels are calculated based on operating parameters, and airflow uniformity is calculated based on the static pressure difference between multiple diffusers. The noise level, energy consumption level, and airflow uniformity index are weighted according to preset weighting coefficients to obtain a comprehensive comfort index. With the goal of minimizing the overall comfort index, the fan speed and water valve opening are optimized and adjusted.

[0074] Specifically, the Comprehensive Comfort Index (COMP): COMP = ω1·L + ω2·E + ω3·D Where L is the noise level (in dB, which can be estimated from the fan speed F). E represents energy consumption per unit time (kW); D represents the maximum static pressure difference ΔP_max between multiple diffusers; ω1, ω2, and ω3 are weighting coefficients (e.g., ω1=0.4, ω2=0.4, ω3=0.2, configurable).

[0075] The noise level L can be calculated using the following formula: L=L0+30 log 10 (F / F0) Among them, F0 and L0 are the electromagnetic noise levels at the rated speed, that is, the noise at the speed of F0 is L0dB, which can be obtained from the motor specification sheet.

[0076] In Embodiment 2, the present invention provides an air conditioning comfort control system, such as... Figure 2 As shown, an air conditioning comfort control method for implementing Embodiment 1 includes: Two pressure sensors, a temperature and humidity sensor, a temperature sensor, and a control board, including: The two pressure sensors are respectively installed at the air outlet and the diffuser of the air conditioner terminal, and are used to collect the first static pressure value and the second static pressure value. The temperature and humidity sensor is located at the air outlet and is used to collect the air outlet temperature and relative humidity. The temperature sensor is placed on the surface of the diffuser and is used to collect the surface temperature of the diffuser. The control board is connected to the pressure sensor, the temperature and humidity sensor and the temperature sensor respectively, and is used to execute the air conditioning comfort control method described in Embodiment 1.

[0077] Preferably, the system further includes a display panel for displaying fault information.

[0078] It should be noted that this invention, through a specific sensor layout and control board, can accurately collect key parameters in real time, providing a data foundation for the control method. The system structure is simple and reliable, and it is easy to add or integrate into existing air conditioning terminals.

[0079] In Embodiment 3, the present invention provides an air conditioner, including a fan, a water valve, and an air conditioning comfort control system as described in Embodiment 2.

[0080] It should be noted that the present invention integrates the above-mentioned control system into the air conditioner, enabling the air conditioner to have intelligent comfort control functions, thereby improving the product's market competitiveness and user experience.

[0081] In Embodiment 4, the present invention provides an application example of an air conditioning comfort control method, comprising the following steps: Step 1: Obtain the first static pressure value P1 by using the first pressure sensor set at the air outlet, obtain the second static pressure value P2 by using the second pressure sensor set at the diffuser, obtain the air outlet temperature T and relative humidity RH by using the temperature and humidity sensor set at the air outlet, and obtain the diffuser surface temperature Ts by using the temperature sensor set on the diffuser surface.

[0082] Step 2: Calculate the static pressure loss in the duct and the actual usable static pressure at the diffuser. The static pressure loss in the duct is P3 = P1 - P2, calculated from the difference between P1 and P2. Based on the system's preset reference static pressure value P0, the actual usable static pressure at the diffuser is calculated as P = P0 - P3.

[0083] Step 3: Determine the duct resistance coefficient based on the static pressure loss of the duct and the current operating air volume, and dynamically set the target static pressure based on the duct resistance coefficient.

[0084] Step 4: Calculate the outlet dew point temperature Td based on the outlet air temperature T and relative humidity RH. Set a first safety threshold ΔT (e.g., 1.5℃). If Ts ≤ Td + ΔT, then there is a risk of condensation; otherwise, there is no risk.

[0085] Step 5: Based on the difference between the actual available static pressure and the target static pressure, ΔP = P - P_t, and combined with the condensation risk assessment results, adjust the fan speed and water valve opening. Set the second preset threshold to 20Pa, and execute according to the following two typical operating conditions: Operating Condition 1: ΔP > 20Pa and no risk of condensation (noise reduction priority mode) Taking a certain project as an example, the reference static pressure value P0 is 80Pa, and the target static pressure P_t is set to 5Pa.

[0086] After the machine is running stably, P1 = 78 Pa and P2 = 60 Pa are measured. Therefore, P3 = P1 - P2 = 18 Pa and P = P0 - P3 = 62 Pa.

[0087] When ΔP=P P_t=62-5=57Pa, which is greater than 20Pa, so noise reduction priority mode is entered.

[0088] If the initial value of F0 is 6kHz, then F = F0 - α(ΔP) can be calculated. n ≈2KHz; At this point, the fan speed drops significantly, and the water valve can be appropriately closed and adjusted to 90%.

[0089] Simultaneously, the temperature was measured at T=12℃, RH=85%, Td≈9.6℃, and Ts=12.2℃>Td+1.5, indicating no risk of condensation and effective control.

[0090] Operating Condition 2: ΔP≤20Pa and there is a risk of condensation (anti-condensation priority mode) In another project, ΔP < 20 Pa, outlet air temperature T = 10℃, RH = 90%, and calculated Td ≈ 8.3℃, Ts = 9.5℃, which is less than Td + 1.5, indicating a risk of condensation. The system enters anti-condensation priority mode, and the calculated K = 1 - βln(ΔP + 1) = 50%.

[0091] At this point, the water valve opening is forcibly reduced from 100% to 50%, and the fan speed is reduced by 0.5kHz. After a period of time, when the Ts temperature rises to 10℃, the risk of condensation is eliminated, and the system returns to normal noise reduction and energy-saving control.

[0092] In addition, the system performs a calibration procedure regularly: the control board records operating data and automatically calibrates monthly or quarterly under standard operating conditions (such as 900 rpm for the fan, 80% opening of the water valve, and an ambient temperature of 26°C).

[0093] If the first static pressure value P1 is found to be decreasing or the resistance coefficient R is found to be continuously increasing, the reference static pressure value P0 and the adjustment parameters α and β are corrected according to the preset rules. For example, if P remains high under the same operating conditions after 30 days of operation, it is determined that dust has accumulated in the air duct. P0 is then corrected from 80Pa to 85Pa, and α and β are updated to make subsequent adjustments more accurate.

[0094] Through the above steps, this method achieves comprehensive optimization control of air conditioning in terms of noise reduction, energy saving, and anti-condensation.

[0095] This disclosure can be a system, method, and / or computer program product. A computer program product may include a computer-readable storage medium having computer-readable program instructions loaded thereon for causing a processor to implement various aspects of this disclosure.

[0096] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and not to limit it. Although the present invention has been described in detail with reference to the above embodiments, those skilled in the art should understand that modifications or equivalent substitutions can still be made to the specific implementation of the present invention. Any modifications or equivalent substitutions that do not depart from the spirit and scope of the present invention should be covered within the protection scope of the claims of the present invention.

Claims

1. An air conditioning comfort control method, characterized in that, include: The system obtains the first static pressure value at the air outlet of the air conditioner terminal, the second static pressure value at the diffuser, the air outlet temperature and relative humidity, and the diffuser surface temperature. The static pressure loss of the air duct is determined based on the difference between the first static pressure value and the second static pressure value, and the actual usable static pressure of the diffuser is determined based on the static pressure loss of the air duct and the reference static pressure value. The duct resistance coefficient is determined based on the static pressure loss of the duct and the current operating air volume, and the target static pressure is dynamically set based on the duct resistance coefficient. The outlet dew point temperature is calculated based on the outlet air temperature and the relative humidity, and it is determined whether the difference between the diffuser surface temperature and the outlet dew point temperature is less than or equal to the first safety threshold. If so, it is determined that there is a risk of condensation. Based on the static pressure difference between the actual available static pressure at the diffuser and the target static pressure, and combined with the condensation risk assessment results, adjust the fan speed and water valve opening.

2. The air conditioning comfort control method according to claim 1, characterized in that: The process of determining the duct resistance coefficient based on the duct static pressure loss and the current operating air volume includes: The current operating air volume is calculated based on a preset formula, wherein the preset formula is that the current operating air volume is equal to the product of the rated air volume and the proportional coefficient, and the proportional coefficient is the ratio of the current speed to the rated speed. The duct resistance coefficient is calculated based on the ratio of the static pressure loss in the duct to the square of the current operating air volume.

3. The air conditioning comfort control method according to claim 1, characterized in that: The step of dynamically setting the target static pressure based on the duct resistance coefficient includes: The target static pressure is equal to the product of the duct resistance coefficient and the adjustment coefficient, plus a preset base value. The adjustment coefficient is determined according to the following rules: When the duct resistance coefficient is less than the first resistance coefficient threshold, the first adjustment coefficient is used; When the duct resistance coefficient is greater than or equal to the first resistance coefficient threshold and less than the second resistance coefficient threshold, the second adjustment coefficient is used; When the duct resistance coefficient is greater than or equal to the second resistance coefficient threshold and less than the third resistance coefficient threshold, the third adjustment coefficient is used. When the duct resistance coefficient is greater than or equal to the third resistance coefficient threshold, the fourth adjustment coefficient is used.

4. The air conditioning comfort control method according to claim 1, characterized in that: The adjustment of the fan speed and water valve opening includes: When the static pressure difference is greater than the second preset threshold and there is no risk of condensation, the fan speed is reduced according to the first preset adjustment model, and the water valve opening is adjusted according to the anti-condensation adjustment strategy. When the static pressure difference is greater than the second preset threshold and there is a risk of condensation, the fan speed is reduced according to the first preset adjustment model, and the water valve opening is adjusted according to the second preset adjustment model. When the static pressure difference is less than or equal to the second preset threshold and there is a risk of condensation, the water valve opening is reduced according to the second preset adjustment model, and the fan speed is adjusted according to the noise reduction adjustment strategy. When the static pressure difference is less than or equal to the second preset threshold and there is no risk of condensation, maintain the current fan speed and water valve opening.

5. The air conditioning comfort control method according to claim 4, characterized in that: The first preset adjustment model is a nonlinear decreasing function of the target rotational speed and the static pressure difference: Multiply the nth power of the static pressure difference by the fan adjustment coefficient, where n is an empirical coefficient, and then subtract the product from the initial speed to obtain the target speed after adjustment.

6. The air conditioning comfort control method according to claim 5, characterized in that: The second preset adjustment model is a logarithmic function of the target water valve opening and the static pressure difference: First, calculate the natural logarithm of the sum of the static pressure difference and 1. Then, multiply the natural logarithm by the water valve adjustment coefficient, and subtract the product from 1. The resulting difference is the target water valve opening after adjustment.

7. The air conditioning comfort control method according to claim 6, characterized in that: The method also includes the step of periodically performing calibration procedures: It operates under standard conditions, records current operating data, and compares it with historical operating data. Based on the changing trend of the first static pressure value or the changing trend of the duct resistance coefficient, the reference static pressure value, the fan adjustment coefficient, or the water valve adjustment coefficient are corrected, and a fault prompt message is generated when the value exceeds the preset range.

8. The air conditioning comfort control method according to claim 7, characterized in that: The step of correcting the reference static pressure value, the fan adjustment coefficient, or the water valve adjustment coefficient based on the changing trend of the first static pressure value or the changing trend of the duct resistance coefficient includes: If the correction is made based on the trend of the first static pressure value, then: When the attenuation percentage of the first static pressure value is less than the first preset attenuation threshold, the reference static pressure value is corrected by the first amplitude, while the fan adjustment coefficient and the water valve adjustment coefficient are not corrected. When the attenuation percentage of the first static pressure value is greater than or equal to the first preset attenuation threshold and less than the second preset attenuation threshold, the reference static pressure value is subject to a second amplitude correction, and the fan adjustment coefficient and the water valve adjustment coefficient are subject to a first amplitude correction. When the attenuation percentage of the first static pressure value is greater than or equal to the second preset attenuation threshold, the reference static pressure value is corrected by a third amplitude, the fan adjustment coefficient and the water valve adjustment coefficient are corrected by a second amplitude, and a fault prompt message is generated. If the correction is made based on the changing trend of the duct resistance coefficient, then: When the percentage increase in the duct resistance coefficient is less than the first preset increase threshold, the reference static pressure value, the fan adjustment coefficient, and the water valve adjustment coefficient are not corrected. When the percentage increase in the duct resistance coefficient is greater than or equal to the first preset increase threshold and less than the second preset increase threshold, the reference static pressure value is corrected by a fourth amplitude, and the fan adjustment coefficient and the water valve adjustment coefficient are corrected by a third amplitude. When the percentage increase in the duct resistance coefficient is greater than or equal to the second preset increase threshold, the reference static pressure value is corrected by a fifth magnitude, the fan adjustment coefficient and the water valve adjustment coefficient are corrected by a fourth magnitude, and a fault prompt message is generated.

9. An air conditioning comfort control system, used to implement the air conditioning comfort control method according to any one of claims 1-8, characterized in that, include: Two pressure sensors, a temperature and humidity sensor, a temperature sensor, and a control board, including: The two pressure sensors are respectively installed at the air outlet and the diffuser of the air conditioner terminal, and are used to collect the first static pressure value and the second static pressure value. The temperature and humidity sensor is installed at the air outlet to collect the air outlet temperature and relative humidity; The temperature sensor is disposed on the surface of the diffuser and is used to collect the surface temperature of the diffuser. The control board is connected to the pressure sensor, the temperature and humidity sensor and the temperature sensor respectively, and is used to execute the air conditioning comfort control method according to any one of claims 1-8.

10. An air conditioner, characterized in that, It includes a fan, a water valve, and an air conditioning comfort control system as described in claim 9.

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