Air handling unit with temperature and humidity dual sensor linkage control

Abstract

The present application relates to air conditioning technology field, disclose a kind of temperature and humidity double sensor linkage control's air unit, including unit host computer, ventilation pipe network, room end component and host computer control panel, multiple purification sterilization module, deep dehumidification surface cooler and variable frequency fan are sequentially arranged in unit host computer interior, main air duct and bypass air duct communicate deep dehumidification surface cooler leeward cavity, ventilation pipe network communicates variable frequency fan and quiet zone room, the pressure relief valve containing servo motor is installed in the bottom of the side wall of quiet zone room, temperature and humidity sensor and air detector are installed on the surface of the wall of quiet zone room, host computer control panel receives end detection signal.The present application generates feedforward intercept signal to block dewing condition by central processing unit extraction dew point approach rate, avoid cold air accumulation at room bottom by combining archimedes number to calculate transient air supply temperature, and enlarge the flow area of pressure relief valve to discharge air pollutants when ventilation pipe network air volume is limited, maintain indoor environmental quality.

Description

Technical Field

[0001] This invention relates to the field of air conditioning technology, specifically to an air handling unit with temperature and humidity controlled by a dual-sensor linkage. Background Technology

[0002] Air handling units typically consist of a variable frequency fan and a cooling coil, responsible for regulating indoor temperature and relative humidity. Current air handling units primarily rely on single-dimensional temperature or humidity data to activate dehumidification. The control system often only increases the cooling capacity of the cooling coil after liquid water has already condensed on the indoor wall surfaces. Relying solely on current values ​​cannot determine the condensation trend, leading to a lag in system response and resulting in condensation in the indoor environment.

[0003] Existing air handling units maintain a constant air temperature when delivering cold air. Due to the density difference between hot and cold air, the cold air sinks and accumulates at the bottom of the room after entering the indoor environment. Continuous cold airflow blowing towards areas where people are active causes a rigid airflow structure, resulting in cold air being blown directly towards the bottom of the room. A single constant-temperature airflow logic cannot break this localized cold air sinking and accumulation phenomenon.

[0004] The indoor environment contains carbon dioxide exhaled by people and volatile organic compounds (VOCs) released from indoor items. When the airflow velocity inside the ventilation duct reaches its operational limit, the variable frequency fan speed of existing air handling units is locked by a limiting mechanism, preventing the control board from further increasing the fresh air intake. Under these conditions, where the fresh air volume cannot be increased, existing air handling units lack independent pressure relief and venting mechanisms, and the control system cannot expel polluted air outdoors by increasing the exhaust cross-sectional area. The gradual accumulation of carbon dioxide and VOCs indoors leads to a decline in the quality of the indoor respiratory environment. Summary of the Invention

[0005] To address the shortcomings of existing technologies, this invention provides an air handling unit with dual temperature and humidity sensor linkage control. This solves the problems of single temperature control being unable to adapt to hot and humid environments, resulting in condensation indoors, and traditional constant air volume systems causing excessive fluctuations in indoor temperature during dehumidification, and being unable to dynamically release pressure and discharge pollutants based on indoor carbon dioxide and volatile organic compound concentrations.

[0006] To achieve the above objectives, the present invention provides an air handling unit with temperature and humidity dual-sensor linkage control, including a unit main unit, ventilation duct network, room terminal components and main unit control board.

[0007] The unit's main unit is equipped with multiple purification and sterilization modules, a deep dehumidification surface cooler, and a variable frequency fan arranged sequentially, and is divided into a main air duct and a bypass air duct. The air inlet of the main air duct and the air inlet of the bypass air duct are connected to the leeward side cavity of the deep dehumidification surface cooler, and a sensible heat temperature-regulating surface cooler and a bypass valve are installed respectively.

[0008] The multi-stage purification and sterilization module includes a pre-filter and a high-efficiency composite filter that are fitted in parallel. An array of ultraviolet germicidal lamps is fixed to the leeward side surface of the high-efficiency composite filter. The array of ultraviolet germicidal lamps emits light to irradiate the surface of the high-efficiency composite filter.

[0009] The ventilation duct network includes a main air supply duct, which connects the variable frequency fan to the terminal diffuser inside the quiet zone room and is equipped with a wind speed sensor; exhaust louvers are fixedly installed at the bottom of the side wall of the quiet zone room, and a pressure relief valve containing the first servo motor is installed parallel inside the exhaust louvers.

[0010] The pressure relief valve includes a valve body frame that runs through the exhaust louver grille, a support shaft, and a counterweight baffle. A first servo motor is installed on the outer wall surface of the valve body frame and is directly connected to one end of the support shaft. The first servo motor receives an external control signal to drive the support shaft to rotate, which in turn causes the counterweight baffle to deflect and adjust the flow area of ​​the internal channel of the valve body frame.

[0011] The walls of the quiet zone room are equipped with temperature and humidity sensors and an air quality detector, which are part of the room's terminal components. An independent detection chamber is fixed inside the air quality detector's housing. A carbon dioxide probe and a volatile organic compound probe are fixed parallel to each other on the bottom surface of the independent detection chamber. A sampling pipeline consisting of a front-end microtube, a miniature air pump, and a rear-end exhaust pipe is connected to the outside of the independent detection chamber. The first end of the front-end microtube connects to the quiet zone room, and the second end connects to the air inlet at the top of the independent detection chamber. The miniature air pump connects to the air outlet on the side wall of the independent detection chamber and the air inlet of the rear-end exhaust pipe.

[0012] The temperature and humidity sensor and the air quality detector are connected to the communication bus, which in turn connects to the main control board. The main control board receives the signals output by the temperature and humidity sensor and the air quality detector.

[0013] The host control board is equipped with a central processing unit, random access memory, and non-volatile memory chips divided into constant storage sectors. The analog micro-current signal output by the temperature and humidity sensor is converted into a digital discrete signal and stored in an independent data buffer queue.

[0014] The central processing unit (CPU) reads ten discrete digital signals and performs bubble sorting to arrange them. The CPU removes the discrete digital signal with the highest and lowest sorted values. The remaining eight discrete digital signals are multiplied by weighting coefficients and summed to obtain a weighted result, which is defined as the effective dry-bulb temperature and effective relative humidity, respectively. This bubble sorting combined with weighted summation logic truncates transient signal glitches caused by background noise in the sensor hardware circuitry, providing continuous environmental temperature and humidity benchmark data and improving the quality of underlying data acquisition.

[0015] The central processing unit (CPU) combines the effective dry-bulb temperature and effective relative humidity to extract the current dew point temperature data and stores it in a dew point cache queue containing ten consecutive storage blocks in random access memory (RAM). It reads the oldest timestamped initial dew point temperature data from the dew point cache queue and extracts the humidity change slope. It calculates the temperature difference between the current dew point temperature data and the initial dew point temperature data, and performs a division operation on the temperature difference using the total time of ten sampling periods to obtain the dew point convergence rate. When the dew point convergence rate is greater than the dew point change threshold parameter fixedly burned into the constant storage sector and the humidity change slope is greater than zero, a feedforward interception signal is generated, sending a simulated first control voltage to the first water valve connected to the deep dehumidifier. The above feedforward interception control logic judges the indoor water vapor accumulation trend based on the dew point convergence rate, and pre-activates the deep dehumidifier to intercept moisture before actual condensation, blocking condensation conditions.

[0016] The ratio calculation model embedded inside the main control board takes as input the target dry-bulb temperature data minus the supply air temperature difference limit to obtain the constant supply air temperature, the target dry-bulb temperature data, and the upper limit of the flow rate fixedly burned into the constant storage sector, and outputs the current Archimedes number. When the current Archimedes number is greater than the upper limit of the Archimedes number fixedly burned into the constant storage sector, a boundary conflict level signal is generated. Combining the constant supply air temperature, the temperature amplitude parameters fixedly burned into the constant storage sector, the oscillation frequency parameters, and the current cumulative running time, the transient supply air temperature is calculated, and a simulated third control voltage is sent to the second water valve connected to the sensible heat-regulating surface cooler. The above Archimedes number calculation logic defines the ratio of buoyancy and inertia of the supply air jet. When the wind speed reaches the upper limit boundary, the transient supply air temperature that changes over time is introduced to break the single low-temperature airflow sinking and gathering effect, avoiding cold air blowing directly into the bottom area of ​​the quiet room.

[0017] The central processing unit (CPU) calculates the transient density of humid air by combining the effective dry-bulb temperature and effective relative humidity. This transient density is subtracted from the standard air density recorded in the constant storage sector to obtain a density deviation value characterizing the fluctuation of air fluid properties. The density deviation value is multiplied by a density compensation gain coefficient to obtain a dynamic angle compensation amount, which is then added to the bypass valve's basic opening parameter, which is fixedly recorded in the constant storage sector, to obtain the target opening angle value. This is converted into an analog fourth control voltage and sent to the second servo motor within the bypass valve. The above density deviation compensation control principle corrects for the influence of air resistance based on the actual density of the mixed air fluid, dynamically adjusting the bypass valve's distribution angle to ensure that the flow rate inside the main air supply duct remains within the set range.

[0018] The central processing unit extracts the target opening angle value, calculates the reference momentum compensation difference caused by valve opening and closing interference with the variable frequency fan, and converts it into a frequency fine-tuning control word. It also reads the instantaneous flow velocity returned by the wind speed sensor. When the instantaneous flow velocity reaches the upper limit stored in the constant storage sector, a flow interception level signal is generated. Based on this signal, the accumulation of the frequency fine-tuning control word is locked, and a simulated fifth control voltage is sent to the inverter drive module inside the variable frequency fan to fix the impeller rotation speed. The frequency fine-tuning locking logic establishes a joint control relationship between the bypass valve opening and the variable frequency fan speed. When the flow velocity inside the main air duct reaches the upper limit red line, the speed increase command is rigidly cut off to avoid exceeding the acoustic load-bearing limit of the ventilation network and causing howling noise.

[0019] When the main control board analyzes the air detector signal and determines that the effective carbon dioxide concentration is not less than the carbon dioxide safety upper limit parameter recorded in the constant storage sector, or the effective organic matter concentration is not less than the volatile organic compound safety upper limit parameter recorded in the constant storage sector, and maintains a high-level flow interception level signal, it generates a discharge area amplification voltage signal. The first servo motor receives the discharge area amplification voltage signal and directly drives the pressure relief valve to increase the flow cross-sectional area, forming an expanded sewage discharge area at the exhaust louver grille. Under conditions where the supply fan speed is limited and cannot further increase the fresh air volume, the above sewage discharge action logic forcibly amplifies the opening area of ​​the pressure relief valve, utilizing the positive pressure potential energy originally accumulated indoors to accelerate the expulsion of polluted air rich in carbon dioxide and volatile organic compounds from the quiet zone room, maintaining the quality of the indoor breathing environment.

[0020] This invention provides an air handling unit with integrated temperature and humidity control via dual sensors. It offers the following advantages:

[0021] 1. This invention extracts the current dew point temperature data and calculates the dew point approach rate by combining the dry-bulb temperature and relative humidity output by the central processing unit with weighted summation. When the dew point approach rate is greater than the dew point change threshold parameter fixedly burned into the constant storage sector and the humidity change slope is greater than zero, the central processing unit generates a feedforward interception signal and sends a simulated first control voltage to the first water valve connected to the deep dehumidifier. The above control steps increase the cooling capacity of the deep dehumidifier to intercept moisture before the water vapor actually condenses, thus blocking the conditions for condensation to occur inside the quiet room.

[0022] 2. This invention outputs the current Archimedes number through the ratio calculation model inside the host control board. When the current Archimedes number is greater than the upper limit of the Archimedes number fixed in the constant storage sector, a boundary conflict level signal is generated. Combined with the constant air supply temperature, temperature amplitude parameters, oscillation frequency parameters and the current cumulative running time, the transient air supply temperature is calculated, and a simulated third control voltage is sent to the second water valve connected to the sensible heat-regulating surface cooler. The above operation process introduces a transient air supply temperature that changes over time to break the sinking and gathering effect of low temperature airflow, and avoids cold air blowing directly downwards to the bottom area of ​​the quiet room.

[0023] 3. This invention uses the host control board to analyze the air detector signal to obtain the carbon dioxide concentration and volatile organic compound concentration. When the air pollutant concentration reaches the safety upper limit parameter burned into the constant storage sector, and there is a flow interception level signal that maintains a high level, the host control board generates a discharge area amplification voltage signal. The first servo motor receives the discharge area amplification voltage signal and directly drives the pressure relief valve to increase the flow cross-sectional area. The above control strategy amplifies the sewage discharge area at the exhaust louver grille when the variable frequency fan speed is limited and the fresh air volume cannot be increased. It uses the positive pressure accumulated inside the quiet room to discharge polluted air to the outside and maintain the quality of the indoor breathing environment. Attached Figure Description

[0024] Figure 1 This is a schematic diagram of the overall layout of the air handling unit provided in an embodiment of the present invention;

[0025] Figure 2 This is a schematic diagram of sensor installation and airflow pattern inside a quiet zone room provided in an embodiment of the present invention;

[0026] Figure 3 This is a schematic diagram of the internal structure and air duct routing of the generator unit provided in an embodiment of the present invention;

[0027] Figure 4 This is a diagram showing the internal structure of an air detector and sampling pipeline provided in an embodiment of the present invention.

[0028] Figure 5 This is a schematic diagram of the pressure relief valve and bypass valve provided in an embodiment of the present invention;

[0029] Figure 6 This is a schematic diagram of the protective structure for a temperature and humidity sensor provided in an embodiment of the present invention;

[0030] Figure 7 This is a block diagram of the hardware topology of the control system provided in an embodiment of the present invention;

[0031] Figure 8 A flowchart of the closed-loop linkage control method for air parameters provided in an embodiment of the present invention.

[0032] The components include: 1. Unit main unit; 2. Ventilation duct network; 3. Room terminal components; 4. Independent equipment room; 5. Quiet zone room; 6. Soundproof wall; 7. Main air supply duct; 8. Terminal diffuser; 9. Exhaust louver grille; 10. Pressure relief valve; 11. Wind speed sensor; 12. Temperature and humidity sensor; 13. Air quality detector; 14. Main unit control board; 15. Multi-stage purification and sterilization module; 16. Deep dehumidification surface cooler; 17. Main air duct; 18. Bypass air duct; 19. Bypass valve; 20. Sensible heat temperature-regulating surface cooler; 21. Variable frequency fan; 22. First water valve; 23. Second water valve. Detailed Implementation

[0033] The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0034] See attached document Figure 1 -Appendix Figure 8 This invention provides an air handling unit with temperature and humidity dual-sensor linkage control, including a unit main unit 1, a ventilation duct network 2, and room terminal components 3. The unit main unit 1 is installed inside an independent equipment room 4, which is located outside a quiet zone room 5. A soundproof wall 6 is provided between the independent equipment room 4 and the quiet zone room 5. The quiet zone room 5 is equipped with sensing and actuation elements for environmental perception.

[0035] The main unit 1 has an air outlet on its casing surface. The ventilation duct network 2 includes a main air supply duct 7. The air inlet of the main air supply duct 7 is fixedly connected to the air outlet of the main unit. The air outlet passes through the soundproof wall 6 and enters the quiet zone room 5. A wind speed sensor 11 is fixedly installed at the end of the main air supply duct 7 to measure the instantaneous flow velocity discharged into the quiet zone room 5 in real time. The room terminal assembly 3 includes a terminal diffuser 8. The terminal diffuser 8 has a neck opening with a diffuser neck area. The terminal diffuser 8 is fixedly installed on the top surface of the quiet zone room 5. The air outlet of the main air supply duct 7 is connected to the upper air inlet of the terminal diffuser 8.

[0036] See attached document Figure 2and attached Figure 5 A ventilation louver grille 9 is fixedly installed at the bottom of the side wall of the quiet zone room 5. A pressure relief valve 10 is installed parallel to the interior of the ventilation louver grille 9. The pressure relief valve 10 includes a valve body frame, a support shaft, and a counterweight baffle that penetrate the ventilation louver grille 9. The air inlet side of the valve body frame is connected to the quiet zone room 5, and the exhaust side is connected to the building corridor environment. The support shaft is horizontally fixed in the cavity inside the valve body frame. The upper end of the counterweight baffle is movably sleeved on the support shaft, and the lower end hangs down and fits against the inner side of the valve body frame by gravity. The pressure relief valve 10 also includes a first servo motor, which is installed on the outer wall surface of the valve body frame. The first servo motor is directly connected to one end of the support shaft. The first servo motor receives external control signals to drive the support shaft to rotate, thereby causing the counterweight baffle to deflect and adjust the flow area of ​​the internal channel of the valve body frame.

[0037] The room terminal component 3 also includes a sensor array. The sensor array includes a temperature and humidity sensor 12 and an air quality detector 13. The air quality detector 13 integrates a carbon dioxide probe and a volatile organic compound probe.

[0038] Temperature and humidity sensor 12 and air quality detector 13 are installed on the wall surface of quiet room 5. The vertical elevation of the center point of temperature and humidity sensor 12 from the ground of quiet room 5 is set between 1.2m and 1.5m. The center point of air quality detector 13 is on the same horizontal line as the center point of temperature and humidity sensor 12. The horizontal projection distance between temperature and humidity sensor 12 and air quality detector 13 and the edge of the fixed end diffuser 8 on the top surface of quiet room 5 is greater than 1.5m, and the horizontal projection distance between them and the pressure relief valve 10 at the bottom of the wall of quiet room 5 is greater than 2.0m.

[0039] See attached document Figure 4 An independent detection chamber is fixed inside the air quality detector 13 housing. Carbon dioxide and volatile organic compound probes are fixed parallel to each other on the bottom surface of the independent detection chamber. A sampling pipeline is connected to the outside of the independent detection chamber. This pipeline includes a front-end microtube, a micro-pump, and a rear-end exhaust pipe. The first end of the front-end microtube penetrates the air quality detector 13 housing and connects to the quiet zone room 5, while the second end connects to the air inlet at the top of the independent detection chamber. The air outlet on the side wall of the independent detection chamber connects to the air inlet of the micro-pump, and the exhaust port of the micro-pump connects to the air inlet of the rear-end exhaust pipe. A micro one-way check valve is fixedly installed inside the rear-end exhaust pipe, and its end penetrates the air quality detector 13 housing and connects to the quiet zone room 5.

[0040] The miniature air pump draws air from the quiet zone room 5, which flows through the front microtube into the independent detection chamber for measurement by the carbon dioxide and volatile organic compound probes. The air entering the independent detection chamber opens the miniature one-way check valve and is then discharged back into the quiet zone room 5 through the rear exhaust pipe. The miniature one-way check valve prevents air from flowing back into the independent detection chamber from the quiet zone room 5 under a slightly positive pressure state.

[0041] See attached document Figure 6 The temperature and humidity sensor 12 is covered with a louvered protective cover, and its surface has an array of inclined ventilation slots. A dustproof and breathable membrane is adhered to the inside. Air from the quiet room 5 passes through the inclined ventilation slots and the dustproof and breathable membrane and comes into contact with the temperature-sensitive and humidity-sensitive elements inside the temperature and humidity sensor 12. The circuit boards inside the temperature and humidity sensor 12 and the air detector 13 are connected to a communication bus that penetrates the soundproof wall 6. The other end of the communication bus is connected to the main control board 14 inside the equipment room.

[0042] See attached document Figure 3 and attached Figure 5 Inside the main unit 1, along the airflow direction, are arranged a multi-stage purification and sterilization module 15, a deep dehumidification surface cooler 16, a bypass valve 19, a sensible heat regulating surface cooler 20, and a variable frequency fan 21. The multi-stage purification and sterilization module 15 includes a primary filter, a high-efficiency composite filter, and an ultraviolet germicidal lamp array. These components are arranged vertically and sequentially inside the main unit 1, with the primary filter and the high-efficiency composite filter arranged parallel and fitted together. The ultraviolet germicidal lamp array is fixed to the leeward side surface of the high-efficiency composite filter, emitting light that illuminates the surface of the filter.

[0043] The deep dehumidification surface cooler 16 is fixed downstream of the ultraviolet germicidal lamp array and includes a first heat exchange coil. The water inlet end of the first heat exchange coil is connected to a first low-temperature refrigerant inlet pipe, and the water outlet end is connected to a first low-temperature refrigerant return pipe. A first water valve 22 is installed on the surface of the first low-temperature refrigerant inlet pipe. The first water valve 22 receives a simulated first control voltage to change the internal flow cross-sectional area of ​​the first low-temperature refrigerant inlet pipe.

[0044] A metal partition is welded between the deep dehumidification surface cooler 16 and the sensible heat regulating surface cooler 20 in the internal cavity of the unit main unit 1, dividing the internal cavity of the unit main unit 1 into a main air duct 17 and a bypass air duct 18. The air inlet of the main air duct 17 and the air inlet of the bypass air duct 18 are connected to the leeward side cavity of the deep dehumidification surface cooler 16. The bypass valve 19 is installed inside the bypass air duct 18 and includes a circular valve cylinder, an adjusting butterfly plate, and a second servo motor. The two ends of the circular valve cylinder are connected to the air inlet and outlet of the bypass air duct 18, respectively. The adjusting butterfly plate is installed at the center of the circular valve cylinder via a central rotating shaft. The second servo motor is fixed to the outer wall surface of the circular valve cylinder and is directly connected to one end of the central rotating shaft. The second servo motor receives an analog fourth control voltage to drive the central rotating shaft to rotate, thereby causing the adjusting butterfly plate to change the flow area inside the circular valve cylinder.

[0045] The sensible heat regulating surface cooler 20 is installed inside the main air duct 17, in parallel with the bypass valve 19. It includes a second heat exchange coil, and a PTC micro-electric heating wire mesh is fixedly installed on the air outlet side of the sensible heat regulating surface cooler 20. The water inlet end of the second heat exchange coil is connected to a dual-effect hot and cold water inlet pipe, and the water outlet end is connected to a dual-effect hot and cold water return pipe. A second water valve 23 is installed on the surface of the dual-effect hot and cold water inlet pipe. The air outlet end of the main air duct 17 and the air outlet of the bypass air duct 18 converge and connect to the air inlet of the variable frequency fan 21. The variable frequency fan 21 is fixed to the air outlet end of the unit's main unit 1 casing, and the air outlet is directly connected to the main unit's air outlet. The variable frequency fan 21 is equipped with a motor and an inverter drive module, and the inverter drive module is connected to the main unit control board 14.

[0046] See attached document Figure 7 and attached Figure 8 The host control board 14 has a built-in timer module that generates an interrupt trigger signal with a period set to 100ms. The host control board 14 receives the interrupt trigger signal and sends a data request frame to the communication bus. The temperature and humidity sensor 12 and the air detector 13 receive the data request frame and respond accordingly.

[0047] The temperature-sensitive element inside the temperature and humidity sensor 12 outputs an analog micro-current signal representing the dry-bulb temperature, and the humidity-sensitive element inside the temperature and humidity sensor 12 outputs an analog micro-current signal representing the relative humidity. The carbon dioxide probe inside the air quality detector 13 outputs an analog micro-voltage signal representing the carbon dioxide concentration, and the volatile organic compound (VOC) probe inside the air quality detector 13 outputs an analog micro-voltage signal representing the VOC concentration. Both the internal circuit boards of the temperature and humidity sensor 12 and the air quality detector 13 have 24-bit analog-to-digital converter (ADC) chips soldered onto them. The 24-bit ADC chips convert the analog micro-current and analog micro-voltage signals into corresponding discrete digital signals. These discrete digital signals are transmitted in real-time to the host control board 14 via a communication bus.

[0048] The host control board 14 is equipped with random access memory (RAM), which has four independent data buffer queues corresponding to dry-bulb temperature, relative humidity, carbon dioxide concentration, and volatile organic compound concentration, respectively. The host control board 14 sequentially classifies and stores the digital discrete signals transmitted by the communication bus into the corresponding data buffer queues. Each data buffer queue has a fixed length of ten storage units and stores ten consecutive samples of the digital discrete signal. Whenever the host control board 14 receives a new digital discrete signal, it clears the oldest digital discrete signal in the corresponding data buffer queue and stores the new digital discrete signal into the data buffer queue.

[0049] The digital discrete signals transmitted via the communication bus are subject to spikes and abrupt changes caused by electromagnetic interference. The host control board 14 is equipped with a central processing unit (CPU). The CPU reads ten digital discrete signals from each data buffer queue, performs bubble sort on these ten signals, and removes the signal with the highest and lowest sorted value. The CPU assigns different weights to the remaining eight digital discrete signals, assigning a larger weight coefficient to the more recent timestamp. The sum of the eight weight coefficients is a constant 1. The CPU multiplies each of the eight digital discrete signals by its corresponding weight coefficient and sums the results to obtain a weighted calculation. This weighted calculation result is defined as the effective dry-bulb temperature, effective relative humidity, effective carbon dioxide concentration, and effective organic matter concentration at the current sampling time. The effective dry-bulb temperature, effective relative humidity, effective carbon dioxide concentration, and effective organic matter concentration are directly written into the internal registers of the host control board 14.

[0050] The main control board 14 is equipped with registers. The central processing unit reads the effective dry-bulb temperature and effective relative humidity stored in the registers according to a fixed calculation cycle, and substitutes the effective dry-bulb temperature into the curing function model to calculate the saturated water vapor partial pressure.

[0051] ;

[0052] In the formula, Defined as the partial pressure of saturated water vapor; Defined as a natural constant; Defined as the effective dry-bulb temperature.

[0053] The central processing unit completes the solution, writes the obtained saturated water vapor partial pressure into the specified address block of random access memory, retrieves the effective relative humidity from the internal register, and combines the saturated water vapor partial pressure and effective relative humidity stored in random access memory to calculate the actual moisture pressure state of the air inside room 5 in the quiet zone. The actual water vapor partial pressure is defined and calculated as follows:

[0054] ;

[0055] In the formula, Defined as the actual partial pressure of water vapor; Defined as the partial pressure of saturated water vapor; Defined as effective relative humidity.

[0056] The central processing unit completes the calculation and simultaneously writes the calculated actual water vapor partial pressure and saturated water vapor partial pressure into the operation cache area divided inside the random access memory. The operation cache area is kept powered on for a long time to store the most recently calculated saturated water vapor partial pressure and actual water vapor partial pressure.

[0057] The central processing unit reads the actual water vapor partial pressure stored in its internal processing cache and simultaneously reads the effective dry bulb temperature stored in its internal register.

[0058] The host control board 14 is soldered with a non-volatile memory chip, which is divided into constant storage sectors and has atmospheric absolute pressure, dry air gas constant, and water vapor gas constant burned in. The central processing unit retrieves the atmospheric absolute pressure, dry air gas constant, and water vapor gas constant from the constant storage sectors.

[0059] The central processing unit combines atmospheric absolute pressure, dry air gas constant, water vapor gas constant, actual water vapor partial pressure, and effective dry-bulb temperature to calculate the transient density of moist air flowing through the main supply duct 7 and the bypass duct 18.

[0060] ;

[0061] In the formula, Defined as the transient density of moist air; Defined as absolute atmospheric pressure; Defined as the actual partial pressure of water vapor; Defined as the gas constant for dry air; Defined as the water vapor gas constant; Defined as the effective dry-bulb temperature.

[0062] The host control board 14 is equipped with a feedforward register. The central processing unit (CPU) calculates the transient density of moist air, writes it to the feedforward register, and continuously overwrites it periodically. The non-volatile memory chip has an independent data table area, which contains a mapping table of water vapor pressure and dry-bulb temperature. The CPU reads the actual water vapor partial pressure stored in its internal cache, compares it with the water vapor pressure-dry-bulb temperature mapping table, locates the pressure entry equal to the actual water vapor partial pressure, reads the corresponding temperature reference value, and defines the temperature reference value as the current dew point temperature.

[0063] The random access memory (RAM) has a dew point cache queue. The internal CPU stores the current dew point temperature data into the dew point cache queue. The dew point cache queue always contains ten consecutive memory blocks, storing historical dew point temperature data for ten consecutive sampling periods. The CPU reads the most recently written current dew point temperature data from the dew point cache queue and simultaneously reads the oldest timestamped starting dew point temperature data from the dew point cache queue. It calculates the temperature difference between the current dew point temperature data and the starting dew point temperature data, and divides the temperature difference by the total time of the ten sampling periods to obtain the dew point convergence rate of the air inside room 5 in the quiet zone.

[0064] The constant storage sector contains a fixed dew point change threshold parameter. The value range of the dew point change threshold parameter is set between 0.1℃ / min and 0.3℃ / min.

[0065] The central processing unit (CPU) reads the dew point change threshold parameter from the constant storage sector and compares it with the dew point convergence rate. Simultaneously, it retrieves the effective relative humidity from the internal register and performs derivative calculations on the time axis to extract the humidity change slope. When the dew point convergence rate is greater than the dew point change threshold parameter and the humidity change slope is greater than 0, the CPU determines that the air inside the quiet zone room 5 is in a state of increased latent heat load and generates a high-level feedforward intercept signal. The host control board 14, equipped with an interrupt register, writes the feedforward intercept signal to the first address of the interrupt register. The high-level feedforward intercept signal causes the host control board 14 to lock the current dry-bulb temperature control.

[0066] The host control board 14 is equipped with a digital-to-analog conversion channel. When the central processing unit detects a high-level feedforward intercept signal at the first address of the interrupt register, it calls the digital-to-analog conversion channel to generate an analog first control voltage and sends the analog first control voltage to the first water valve 22. The first water valve 22 increases the flow cross-sectional area inside the first low-temperature refrigerant inlet pipe according to the analog first control voltage, causing more low-temperature refrigerant to flow into the first heat exchange coil, which in turn causes the surface temperature of the deep dehumidification surface cooler 16 to drop.

[0067] A patch-type temperature probe is fixedly installed on the outer wall of the first low-temperature refrigerant inlet pipe. The patch-type temperature probe measures the refrigerant temperature at the inlet of the first heat exchange coil in real time and outputs an analog electrical signal. The main control board 14 receives the analog electrical signal and converts it into a real-time refrigerant temperature value. The central processing unit synchronously reads the current dew point temperature data stored in the dew point cache queue and continuously compares the real-time refrigerant temperature value with the current dew point temperature data.

[0068] When the real-time refrigerant temperature drops to the set anti-frost limit temperature (e.g., between 2°C and 4°C), the central processing unit stops increasing the amplitude of the first control voltage and outputs a constant amplitude first control voltage to the first water valve 22, forcing the first water valve 22 to maintain its current valve opening and fix the internal flow cross-sectional area of ​​the first low-temperature refrigerant inlet pipe. The central processing unit sets the anti-frost limit temperature as the absolute lower limit condition of the first heat exchange coil's operating temperature to prevent moisture from condensing into frost on the surface of the deep dehumidification surface cooler 16 due to excessively low temperature, thus blocking the air circulation coil.

[0069] While the feedforward interception signal remains high, the central processing unit suspends the closed-loop temperature control of the sensible heat-regulating surface cooler 20 and outputs a static holding voltage to the second water valve 23. The second water valve 23 receives the static holding voltage to maintain the flow cross-sectional area of ​​the dual-effect hot and cold water inlet pipe, and the sensible heat-regulating surface cooler 20 stops responding to fluctuations in the effective dry-bulb temperature, preventing the deep dehumidification surface cooler 16 and the sensible heat-regulating surface cooler 20 from generating excessively low internal air temperature in the quiet zone room 5 due to the superposition of cooling capacity.

[0070] The central processing unit continuously calculates the dew point approach rate. When the dew point approach rate drops to be equal to or less than the dew point change threshold parameter, it determines that the latent heat load increase state has been eliminated, resets the feedforward intercept signal of the first address of the interrupt register to a low level, and releases the temperature closed-loop operation lock state for the sensible heat temperature control surface cooler 20 when the low level state is detected.

[0071] The host control board 14 has a dedicated address allocated to its internal registers to store the externally set target dry-bulb temperature. The central processing unit reads the target dry-bulb temperature data and the real-time updated valid dry-bulb temperature from the internal registers. The deep dehumidifier surface cooler 16 completes dehumidification by cooling and condensation, resulting in the actual air temperature inside the main air duct 17 being lower than the target dry-bulb temperature data.

[0072] The main control board 14 is equipped with a proportional-integral-derivative (PID) unit. The central processing unit calculates the target dry-bulb temperature data and subtracts the effective dry-bulb temperature to obtain the temperature deviation, which is then input into the PID unit. The PID unit, combined with the temperature deviation, outputs a digital second control voltage. The internal digital-to-analog converter of the main control board 14 converts the digital second control voltage into an analog second control voltage. The main control board 14 then transmits the analog second control voltage to the second water valve 23 via a communication cable.

[0073] The second water valve 23 receives the simulated second control voltage, increasing the cross-sectional area of ​​the heat transfer medium flow inside the dual-effect hot and cold water inlet pipe. Heat transfer medium flows into the second heat exchange coil, raising the surface temperature of the sensible heat-regulating surface cooler 20. The dehumidified, low-temperature dry air inside the main air duct 17 flows over the surface of the sensible heat-regulating surface cooler 20, absorbing heat. Since the surface temperature of the sensible heat-regulating surface cooler 20 is higher than the current dew point temperature, it does not dehumidify the low-temperature dry air and has no moisture-adding function. The sensible heat-regulating surface cooler 20 completes the isohumidity heating of the low-temperature dry air. The effective dry-bulb temperature of the air inside the main air duct 17 gradually rises to equal the target dry-bulb temperature, and the air state parameters on the outlet side of the sensible heat-regulating surface cooler 20 match the set temperature requirements of the quiet zone room 5.

[0074] The non-volatile memory chip inside the main control board 14 has constant storage sectors programmed with sensible heat load extremes and flow rate upper limits. The flow rate upper limit is fixed at 0.3 m / s to prevent a perceptible draft inside the quiet zone room 5. The sensible heat load extremes represent the constant cooling demand when the maximum heat source is present inside the quiet zone room 5.

[0075] The central processing unit retrieves the extreme value of sensible heat load and the upper limit of flow rate from the constant storage sector, reads the diffuser neck area stored inside the constant storage sector, multiplies the upper limit of flow rate by the diffuser neck area, and obtains the maximum volumetric flow rate discharged by the variable frequency fan 21 under no wind constraint. Simultaneously, it reads the continuously overwritten transient density of moist air in the feedforward register, multiplies the maximum volumetric flow rate by the transient density of moist air, and obtains the maximum supply air mass flow rate that meets the upper limit of flow rate.

[0076] The central processing unit reads the specific heat capacity of the air stored in the constant storage sector, multiplies the maximum supply air mass flow rate by the specific heat capacity of the air to obtain the heat capacity parameter, divides the extreme value of sensible heat load by the heat capacity parameter to obtain the supply air temperature difference limit value that must be met to offset the extreme value of sensible heat load, reads the target dry bulb temperature data stored in the dedicated address allocated in the internal register of the host control board 14, subtracts the supply air temperature difference limit value from the target dry bulb temperature data to obtain the constant supply air temperature.

[0077] The main control board 14 has a ratio calculation model embedded inside. The internal central processing unit inputs the constant supply air temperature, target dry bulb temperature data, and flow rate limit into the ratio calculation model, and outputs the current Archimedes number of the cold supply airflow entering the quiet zone room 5. The constant storage sector has the upper limit of the Archimedes number fixedly burned in. The central processing unit compares the current Archimedes number with the upper limit of the Archimedes number.

[0078] The main control board 14 is equipped with a status register. When the current Archimedes number exceeds the upper limit of the Archimedes number, the central processing unit determines that the gravitational settling force caused by the constant supply air temperature is greater than the initial micro-momentum provided by the upper limit of the flow velocity. The cold supply airflow cannot adhere to the top surface of the quiet zone room 5 and falls vertically downwards at an accelerated speed to the space where the temperature and humidity sensor 12 is located, which is 1.2m to 1.5m above the floor of the quiet zone room 5. The central processing unit generates a boundary conflict level signal, stores the boundary conflict level signal in the status register, and scans the status register according to a fixed operation cycle. If a boundary conflict level signal is detected in the status register, the normal operation mode of outputting a constant amplitude voltage is paused.

[0079] The constant storage sector contains fixed temperature amplitude and oscillation frequency parameters. The central processing unit (CPU) reads these parameters from the constant storage sector via its internal data bus. The host control board 14's internal timer module outputs the current cumulative running time. The CPU combines the constant supply air temperature, temperature amplitude, oscillation frequency, and current cumulative running time to calculate the transient supply air temperature.

[0080] ;

[0081] In the formula, Defined as transient supply air temperature; Defined as constant supply air temperature; Defined as a temperature wave amplitude parameter; Defined as the constant of pi; Defined as the oscillation frequency parameter; Defined as the current cumulative running time.

[0082] The central processing unit (CPU) inputs the calculated transient air supply temperature into the proportional-integral-derivative (PID) unit of the main control board 14. The PID unit outputs a periodically fluctuating digital value of the third control voltage. The internal digital-to-analog converter (DAC) channel of the main control board 14 converts the digital value of the third control voltage into an analog third control voltage. The main control board 14 continuously transmits the analog third control voltage to the second water valve 23 via a communication cable.

[0083] The second water valve 23 receives the simulated third control voltage. The second water valve 23 continuously changes the cross-sectional area of ​​the heat medium flow inside the cold and hot dual-effect water inlet pipe in accordance with the voltage waveform of the simulated third control voltage. The main control board 14 is equipped with a high-frequency fine-tuning signal output channel.

[0084] The flow rate of the heat transfer medium inside the dual-effect hot and cold water inlet pipe fluctuates periodically in response to the voltage waveform. Simultaneously, the PTC micro-heating wire mesh receives a high-frequency fine-tuning signal from the main unit control board 14 for compensating heating. The sensible heat-regulating surface cooler 20, in conjunction with the PTC micro-heating wire mesh, causes the overall surface outlet air temperature to alternately rise and fall periodically, in sync with the voltage waveform. The sensible heat-regulating surface cooler 20 and the PTC micro-heating wire mesh continuously transfer the periodically fluctuating temperature to the air flowing through the main air duct 17.

[0085] The cold airflow delivered from the main duct 17 has a transient supply air temperature that varies sinusoidally. This periodically changing transient supply air temperature continuously causes variations in the heat capacity parameter, and consequently alters the current Archimedes number of the cold airflow entering the quiet zone room 5. The current Archimedes number fluctuates around its upper limit. This fluctuation directly disrupts the continuous gravitational settling condition of the cold airflow accelerating vertically downwards. Driven by its upper velocity limit, the cold airflow forms a supply air wave with a small disturbance impulse, which then horizontally spreads and adheres to the top surface of the quiet zone room 5.

[0086] The terminal diffuser 8 continuously discharges a cold supply airflow with a transient supply air temperature into the quiet zone room 5. The transient supply air temperature exhibits continuous periodic fluctuations. At the outlet of the terminal diffuser 8, the cold supply airflow is divided into a first temperature air mass and a second temperature air mass that are discharged alternately. The first temperature air mass has a temperature absolute value lower than the constant supply air temperature, and the second temperature air mass has a temperature absolute value higher than the constant supply air temperature.

[0087] By comparing the calculated parameters of the transient density of moist air stored in the feedforward register, the first temperature air mass has a first local air density, and the second temperature air mass has a second local air density. The first local air density is greater than the second local air density. Driven by the initial micro-momentum at the upper limit of the flow velocity, the first and second temperature air masses leave the terminal diffuser 8 and enter the quiet zone room 5. The upper limit of the flow velocity is equal to 0.3 m / s. There is no additional mechanical air supply power outside the quiet zone room 5 and the terminal diffuser 8.

[0088] During the downward movement, the first temperature air mass, due to its first local air density, experiences a first settling velocity due to downward gravity. The second temperature air mass, due to its second local air density, experiences a second settling velocity due to upward thermal buoyancy. The first settling velocity is greater than the second settling velocity. The terminal diffuser 8 alternately discharges air masses according to a sinusoidal law. When the second temperature air mass with the second local air density is discharged first and slowly settles, the subsequently discharged first temperature air mass with the first local air density accelerates vertically downward, catching up with the second temperature air mass that was in the preceding position of the initial discharge cycle.

[0089] The first and second temperature air masses undergo volume infiltration and heat exchange during their descent without additional mechanical power. The first temperature air mass absorbs the heat energy carried by the second temperature air mass, causing its absolute temperature to rise and its local air density to decrease. Simultaneously, the second temperature air mass releases heat energy, causing its absolute temperature to fall and its local air density to rise. The first and second temperature air masses merge into a uniformly mixed cold air mass within the space where the temperature and humidity sensor 12 is located, at a vertical elevation of 1.2m to 1.5m from the floor of the quiet zone room 5.

[0090] A uniformly mixed cold air mass is distributed within a space ranging from 1.2m to 1.5m above the floor of room 5 in the quiet zone. The temperature difference between any two points within the uniformly mixed cold air mass is less than ±1℃. The horizontal and vertical movement velocities of the uniformly mixed cold air mass within this space range (1.2m to 1.5m above the floor) are both reduced to below 0.3m / s. The airflow velocity of the uniformly mixed cold air mass is below the windless constraint boundary condition index set at the upper limit of the flow velocity, and the cold supply airflow meets the requirement for offsetting the extreme sensible heat load under extremely low flow velocity constraints.

[0091] The sensible heat-regulating surface cooler 20 continuously outputs a periodically fluctuating transient supply air temperature, which continuously alters the thermal state of the cold air inside the main supply air duct 7. The central processing unit reads and continuously overwrites the transient density of humid air in the feedforward register, which exhibits a continuous nonlinear alternating fluctuation characteristic following the transient supply air temperature. The flow velocity of the cold supply air from the main air duct 17 into the quiet zone room 5 is limited by the upper velocity limit, and the target value of the supply air velocity inside the unit's main unit 1 remains a fixed constant.

[0092] The dynamic pressure carried by the air inside the main air supply duct 7 is equal to the mathematical product of a constant of 0.5, the transient density of the moist air, and the square of the supply air velocity. The supply air velocity remains a constant value, and the dynamic pressure is entirely controlled by the numerical variation of the transient density of the moist air. The nonlinear alternating fluctuations of the transient density of the moist air directly induce nonlinear oscillations of the dynamic pressure at the same frequency. These nonlinear oscillations continuously deplete the static pressure of the air supplied by the main air supply duct 7.

[0093] The constant storage sector contains fixed micro-positive pressure reference data and local resistance coefficients of the pipeline network. The target of the micro-positive pressure reference data setting is to force the quiet zone room 5 to maintain a positive pressure differential environment higher than the absolute pressure of the building corridor environment. The positive pressure differential environment prevents the infiltration and leakage of untreated air from the building corridor environment into the quiet zone room 5. The nonlinear oscillation of the dynamic pressure data causes a transient negative deviation in the positive pressure differential environment of the quiet zone room 5, which is lower than the set micro-positive pressure reference data.

[0094] The central processing unit calculates the total static pressure compensation required for the pipeline network to completely offset the nonlinear oscillations of the dynamic pressure:

[0095] ;

[0096] In the formula, Defined as the total static pressure compensation for the pipeline network; Defined as setting micro-positive pressure reference data; Defined as the transient density of moist air; Defined as the internal airflow velocity of unit host 1; Defined as the local resistance coefficient of the pipeline network.

[0097] The central processing unit (CPU) completes the calculation to obtain the total static pressure of the pipeline network compensation, writes it into the designated address block of the calculation cache, compares the total static pressure of the pipeline network compensation extracted in the current calculation cycle with the total static pressure of the pipeline network compensation extracted in the previous calculation cycle, and calculates the differential fluctuation component of the total static pressure of the pipeline network compensation caused by the transient density of humid air. The differential fluctuation component constitutes the control target data for the bypass valve 19 and the variable frequency fan 21 to compensate for the dynamic resistance.

[0098] The central processing unit (CPU) reads the differential fluctuation components stored in its internal arithmetic cache and continuously overwrites the transient density of humid air. The constant storage sector contains fixedly burned-in parameters for the basic opening of bypass valve 19, the standard air density, and the density compensation gain coefficient. The CPU subtracts the transient density of humid air from the standard air density to obtain a density deviation value characterizing the fluctuation of air fluid properties. Multiplying the density deviation value by the density compensation gain coefficient yields the dynamic angle compensation amount. Adding the basic opening parameters of bypass valve 19 to the dynamic angle compensation amount, the CPU obtains the target opening angle value for bypass valve 19.

[0099] The internal analog-to-digital converter of the main control board 14 converts the target opening angle value into the corresponding analog fourth control voltage. The main control board 14 sends the analog fourth control voltage to the second servo motor equipped with the bypass valve 19 in real time via a signal cable. The bypass valve 19 is installed at the junction of the main air supply duct 7 and the bypass air duct 18. The second servo motor receives the analog fourth control voltage and directly changes the rotation position of the valve body of the bypass valve 19.

[0100] When the transient density of humid air is in the peak range of nonlinear alternating fluctuation characteristics, the nonlinear oscillation of the dynamic pressure data generates excessive excitation resistance. The central processing unit outputs a simulated fourth control voltage that increases the target opening angle. The second servo motor increases the flow cross-sectional area of ​​the bypass valve 19, and the bypass valve 19 releases a portion of the airflow with high dynamic pressure data in the main air supply duct 7 to the bypass duct 18. This portion of the airflow generates a pressure relief expansion effect inside the bypass duct 18, directly reducing the peak dynamic pressure data inside the main air supply duct 7 of the unit's main unit 1.

[0101] When the transient density of humid air is in the trough of its nonlinear alternating fluctuation characteristic, the nonlinear oscillation of the dynamic pressure data causes a negative deviation in the static pressure supply of the pipeline network. The central processing unit outputs a simulated fourth control voltage to reduce the target opening angle. The second servo motor reduces the flow cross-sectional area of ​​the bypass valve 19, and the bypass valve 19 proportionally cuts off the airflow discharged into the bypass duct 18. The extra airflow that has been cut off is retained inside the main air supply duct 7 and forcibly converted into static pressure potential energy, completely filling the negative deviation gap in the positive pressure differential environment of the quiet zone room 5.

[0102] The target opening angle of bypass valve 19 is periodically adjusted in the same frequency and opposite direction according to the transient density of humid air. The pressure imbalance peaks and troughs in the pipeline caused by the nonlinear oscillation of dynamic pressure data are neutralized bidirectionally by the alternating release and interception of bypass valve 19. The actual static pressure data of the pipeline output at the end of the main air supply duct 7 overcomes the interference of differential fluctuation components and remains constant, ensuring that the quiet zone room 5 maintains an absolute positive pressure differential environment equal to the set micro-positive pressure reference data.

[0103] The central processing unit continuously outputs an analog fourth control voltage to control the rotation position of the bypass valve 19, and simultaneously reads the reference frequency burned into the constant storage sector. The airflow discharged from the main air duct 7 is directly affected by the alternating release and interception of the bypass valve 19, causing the internal air momentum to decrease or increase proportionally. The central processing unit extracts the target opening angle value of the bypass valve 19, calculates the reference momentum compensation difference of the variable frequency fan 21 caused by the valve opening and closing interference, and converts the reference momentum compensation difference into a frequency fine-tuning control word. The frequency fine-tuning control word is added to the reference frequency to obtain the target output frequency data of the variable frequency fan 21. The digital-to-analog conversion channel inside the main control board 14 converts the target output frequency data of the variable frequency fan 21 into an analog fifth control voltage.

[0104] The main control board 14 transmits the analog fifth control voltage to the inverter drive module inside the variable frequency fan 21 via a communication cable. The inverter drive module receives the analog fifth control voltage and changes the impeller rotation speed of the variable frequency fan 21 in real time. The change in impeller rotation speed of the variable frequency fan 21 synchronously replenishes the momentum of the main duct that has been lost in the delivery of cold air into the main air duct 7.

[0105] The central processing unit reads the instantaneous flow rate returned by the wind speed sensor 11 and continuously compares the instantaneous flow rate with the upper limit of the flow rate stored in the constant storage sector. The upper limit of the flow rate is an absolute no-wind constraint boundary condition index.

[0106] When the instantaneous flow velocity climbs to equal the upper limit, the central processing unit (CPU) determines that the momentum compensation intervention in the main pipeline conflicts with the windless constraint boundary and triggers a deadlock state. It immediately generates a high-level flow interception signal and writes it to the interrupt register. This high-level signal forces the main control board 14 to lock the accumulation of the frequency fine-tuning control word. The CPU outputs a constant analog fifth control voltage to the inverter drive module, maintaining the variable frequency fan 21 at a fixed impeller rotation speed, absolutely preventing the instantaneous flow velocity from exceeding the upper limit. The flow velocity environment in the quiet zone room 5 is maintained below 0.3 m / s.

[0107] The central processing unit reads the reference frequency stored in the constant storage sector. When it detects that the variable frequency fan 21 is running, it outputs a continuous power supply voltage to the ultraviolet germicidal lamp array inside the multi-stage purification and sterilization module 15. The primary filter intercepts large particulate matter suspended in the air inside the unit 1, and the high-efficiency composite filter intercepts small particulate matter. The ultraviolet germicidal lamp array continuously irradiates the surface of the high-efficiency composite filter with short-wave ultraviolet light, destroying the nucleic acid molecular chains of microorganisms carried in the air. The main air supply duct 7 continuously delivers cooled airflow that has been treated and purified by temperature and humidity control to the quiet room 5.

[0108] The purified cold airflow undergoes volumetric infiltration and heat exchange at a vertical distance below the terminal diffuser 8. Within the space where the temperature and humidity sensors 12 are located, at a vertical elevation of 1.2m to 1.5m above the floor of the quiet zone room 5, the cold airflow merges into a uniformly mixed cold air mass. The main air duct 7 inside the unit 1 outputs a constant actual static pressure data from the pipe network, maintaining an absolute positive pressure differential environment in the quiet zone room 5 equal to the set micro-positive pressure reference data. This absolute positive pressure differential environment causes the uniformly mixed cold air mass to form a top-down, horizontal airflow coverage surface in the quiet zone room 5.

[0109] The uniformly mixed cold air mass, constrained by its upper velocity limit, maintains a moving velocity below 0.3 m / s across the horizontally pushing airflow coverage surface. This surface overcomes internal airflow disturbances and steadily propels horizontally towards the bottom of the quiet zone room 5. The carbon dioxide and metabolic waste products already present in the quiet zone room 5 are continuously compressed downwards by the horizontally pushing airflow coverage surface. Because the bottom area of ​​the side walls of the quiet zone room 5 is equipped with exhaust louvers 9 that connect to the building corridor environment, the absolute positive pressure difference forces the downwardly compressed carbon dioxide and metabolic waste products through the exhaust louvers 9. The carbon dioxide and metabolic waste products are then discharged into the building corridor environment along the gaps in the exhaust louvers 9.

[0110] The original stale air in quiet room 5 is released unidirectionally into the building corridor environment. The purified cold air supply is continuously replenished to quiet room 5 to maintain the cleanliness index of quiet room 5 and match the set target values ​​of temperature and humidity sensor 12.

[0111] The central processing unit reads the effective carbon dioxide concentration and effective organic matter concentration stored in its internal registers.

[0112] In this embodiment, the constant storage sector is programmed with safety limits for carbon dioxide and volatile organic compounds (VOCs). The safety limit for carbon dioxide is set to the range of 1000 ppm to 1200 ppm, based on the national recommended standards for indoor air quality, and the safety limit for VOCs is set to 0.6 mg / m³. 3 Up to 0.8 mg / m 3The central processing unit continuously compares the effective carbon dioxide concentration with the upper limit of carbon dioxide safety, and simultaneously compares the effective organic matter concentration with the upper limit of volatile organic compounds safety.

[0113] The central processing unit (CPU) synchronously detects whether a high-level flow interception signal is present in the interrupt register. When the effective carbon dioxide concentration is greater than or equal to the carbon dioxide safety limit parameter, or the effective organic matter concentration is greater than or equal to the volatile organic compound (VOC) safety limit parameter, and the interrupt register maintains a high-level flow interception signal, the CPU determines that the volumetric flow rate of the cold air supply is completely limited by the flow velocity limit. The quiet room 5 cannot reduce the carbon dioxide content by increasing the airflow of the variable frequency fan 21, thus generating a leakage area amplification voltage signal. The main control board 14 sends the leakage area amplification voltage signal to the first servo motor equipped with the pressure relief valve 10 via a signal cable.

[0114] The first servo motor receives the amplified voltage signal of the discharge area and drives the support shaft to increase the deflection opening angle of the counterweight baffle. The flow cross-sectional area of ​​the pressure relief valve 10 increases synchronously with the deflection opening angle of the counterweight baffle, and the exhaust louver grille 9 forms an expanded sewage discharge area.

[0115] The uniformly mixed cold air mass is constrained by the high-level flow interception signal, and the instantaneous flow velocity remains constant. The uniformly mixed cold air mass has high-density air characteristics. The uniformly mixed cold air mass continuously generates downward thermal pressure displacement thrust in the quiet zone room 5, and the quiet zone room 5 continuously maintains an absolute positive pressure difference environment.

[0116] The expanded sewage discharge area directly reduces the airflow obstruction force on carbon dioxide gas discharged into the building corridor environment. The absolute positive pressure differential environment, combined with the expanded sewage discharge area, forces the carbon dioxide gas and human metabolic volatiles accumulated at the bottom of quiet room 5 to accelerate through the exhaust louver grille 9. During the expansion of the sewage discharge area, if the central processing unit detects that the positive pressure differential environment of quiet room 5 has fallen below the tolerance limit of the set micro-positive pressure reference data, it temporarily releases the flow deadlock state caused by the flow velocity limit, and proportionally slightly increases the impeller rotation speed of the variable frequency fan 21 to prioritize maintaining the positive pressure differential environment to prevent backflow. The unidirectional discharge flow rate of carbon dioxide gas into the building corridor environment increases. The effective carbon dioxide concentration and effective organic matter concentration decrease with the accelerated discharge of turbid gas.

[0117] The central processing unit continuously monitors the changing trends of effective carbon dioxide concentration and effective organic matter concentration. When the effective carbon dioxide concentration drops below the upper limit of carbon dioxide safety and the effective organic matter concentration drops below the upper limit of volatile organic matter safety, it stops outputting the venting area amplification voltage signal. The first servo motor drives the internal shaft to rotate in the opposite direction, and the pressure relief valve 10 returns to its initial set flow cross-sectional area. The quiet zone room 5 returns to its initial set airflow venting state and maintains a constant absolute positive pressure differential environment, realizing closed-loop linkage control of the air handling unit through dual-sensor linkage regulation of temperature and humidity.

Claims

1. An air handling unit with temperature and humidity dual-sensor linkage control, characterized in that, It includes a unit host (1), a ventilation duct network (2), a room terminal component (3) and a host control board (14). The unit host (1) is arranged in sequence with a multi-stage purification and sterilization module (15), a deep dehumidification surface cooler (16) and a variable frequency fan (21), and is divided into a main air duct (17) and a bypass air duct (18). The air inlet of the main air duct (17) and the air inlet of the bypass air duct (18) are connected to the leeward cavity of the deep dehumidification surface cooler (16), and a sensible heat temperature regulating surface cooler (20) and a bypass valve (19) are installed respectively. The ventilation network (2) includes a main air supply duct (7), which is connected to the variable frequency fan (21) and the terminal diffuser (8) inside the quiet room (5) and is equipped with a wind speed sensor (11). The bottom area of ​​the side wall of the quiet room (5) is fixedly provided with an exhaust louver grille (9). A pressure relief valve (10) containing a first servo motor is installed in parallel inside the exhaust louver grille (9). The wall surface of the quiet room (5) is provided with a temperature and humidity sensor (12) and an air detector (13) included in the room end component (3). The temperature and humidity sensor (12) and the air detector (13) are respectively connected to a communication bus. The communication bus is connected to the host control board (14). The host control board (14) receives the signals output by the temperature and humidity sensor (12) and the air detector (13).

2. The air handling unit with temperature and humidity dual-sensor linkage control according to claim 1, characterized in that, The multi-stage purification and sterilization module (15) includes a primary filter and a high-efficiency composite filter that are attached in parallel. An array of ultraviolet germicidal lamps is fixed on the leeward side surface of the high-efficiency composite filter. The ultraviolet germicidal lamp array emits light to illuminate the surface of the high-efficiency composite filter.

3. An air handling unit with temperature and humidity dual-sensor linkage control according to claim 1, characterized in that, The pressure relief valve (10) includes a valve body frame that penetrates the exhaust louver grille (9), a support shaft and a counterweight baffle. The first servo motor is installed on the outer wall surface of the valve body frame and is directly connected to one end of the support shaft. The first servo motor receives an external control signal to drive the support shaft to rotate, which in turn causes the counterweight baffle to deflect and adjust the flow area of ​​the internal channel of the valve body frame.

4. An air handling unit with temperature and humidity dual-sensor linkage control according to claim 1, characterized in that, The air detector (13) has an independent detection chamber fixed inside its outer shell, and a carbon dioxide probe and a volatile organic compound probe are fixed parallel to each other on the bottom plate surface of the independent detection chamber. The outer side of the independent detection chamber is connected to a sampling pipeline including a front microtube, a micro air pump, and a rear exhaust pipe. The first end of the front microtube is connected to the quiet zone room (5), and the second end is connected to the air inlet at the top of the independent detection chamber. The micro air pump is connected to the air outlet on the side wall of the independent detection chamber and the air inlet of the rear exhaust pipe.

5. An air handling unit with temperature and humidity dual-sensor linkage control according to claim 1, characterized in that, The host control board (14) is equipped with a central processing unit, a random access memory and a non-volatile memory chip divided into constant storage sectors. The analog micro-current signal output by the temperature and humidity sensor (12) is converted into a digital discrete signal and stored in an independent data buffer queue. The central processing unit reads ten discrete digital signals and performs bubble sorting to arrange them. The discrete digital signal with the largest sorted value and the discrete digital signal with the smallest sorted value are removed. The remaining eight discrete digital signals are multiplied by the weighting coefficients and summed to obtain the weighted operation result, which is defined as the effective dry-bulb temperature and the effective relative humidity, respectively.

6. An air handling unit with temperature and humidity dual-sensor linkage control according to claim 5, characterized in that, The central processing unit combines the effective dry-bulb temperature and the effective relative humidity to extract the current dew point temperature data and store it in the dew point cache queue containing ten consecutive storage blocks opened in the random access memory. It reads the starting dew point temperature data with the oldest timestamp in the dew point cache queue and extracts the humidity change slope. The dew point convergence rate is obtained by calculating the temperature difference between the current dew point temperature data and the initial dew point temperature data, and dividing the difference by the total time of ten sampling periods. When the dew point approach rate is greater than the dew point change threshold parameter fixedly burned in the constant storage sector and the humidity change slope is greater than 0, a feedforward interception signal is generated and a simulated first control voltage is sent to the first water valve (22) connected to the deep dehumidification surface cooler (16).

7. An air handling unit with temperature and humidity dual-sensor linkage control according to claim 5, characterized in that, The ratio calculation model solidified inside the host control board (14) inputs the target dry-bulb temperature data minus the supply air temperature difference limit value to obtain the constant supply air temperature, the target dry-bulb temperature data and the fixed flow rate limit burned inside the constant storage sector, and outputs the current Archimedes number. When the current Archimedes number is greater than the upper limit of the Archimedes number fixedly burned in the constant storage sector, a boundary conflict level signal is generated. The transient air supply temperature is calculated by combining the constant air supply temperature, the temperature amplitude parameter fixedly burned in the constant storage sector, the oscillation frequency parameter and the current cumulative running time. The simulated third control voltage is sent to the second water valve (23) connected to the sensible heat regulating surface cooler (20).

8. An air handling unit with temperature and humidity dual-sensor linkage control according to claim 5, characterized in that, The central processing unit calculates the transient density of moist air by combining the effective dry-bulb temperature and the effective relative humidity, and subtracts the transient density of moist air from the standard air density burned into the constant storage sector to obtain the density deviation value characterizing the fluctuation of air fluid properties. The density deviation value is multiplied by the density compensation gain coefficient to obtain the dynamic angle compensation amount, and added to the bypass valve basic opening parameter fixedly burned in the constant storage sector to obtain the target opening angle value, which is then converted into an analog fourth control voltage and sent to the second servo motor contained in the bypass valve (19).

9. An air handling unit with temperature and humidity dual-sensor linkage control according to claim 8, characterized in that, The central processing unit extracts the target opening angle value, calculates the reference momentum compensation difference generated by the valve opening and closing interference of the variable frequency fan (21) in combination with the transient density of the humid air, converts it into a frequency fine-tuning control word, and reads the instantaneous flow rate returned by the wind speed sensor (11). When the instantaneous flow rate is equal to the upper limit of the flow rate stored in the constant storage sector, a flow interception level signal is generated. The accumulation of the frequency fine-tuning control word is locked according to the flow interception level signal, and a simulated fifth control voltage is sent to the inverter drive module inside the variable frequency fan (21) to fix the impeller rotation speed.

10. An air handling unit with temperature and humidity dual-sensor linkage control according to claim 9, characterized in that, When the host control board (14) analyzes the signal from the air detector (13) and finds that the effective carbon dioxide concentration is greater than or equal to the carbon dioxide safety limit parameter burned in the constant storage sector, or the effective organic matter concentration is greater than or equal to the volatile organic matter safety limit parameter burned in the constant storage sector, and the flow interception level signal is maintained at a high level, a leakage area amplification voltage signal is generated. The first servo motor receives the amplified voltage signal of the discharge area and directly drives the pressure relief valve (10) to increase the flow cross-sectional area, thereby forming an expanded sewage discharge area at the exhaust louver grille (9).

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