Method and system for energy consumption control of a circulation system of a large laundry, and storage medium

Abstract

The application relates to the technical field of energy consumption control, and discloses a circulating system energy consumption control method and system for a large laundry room and a storage medium. The method adopts an inverse Carnot cascade heat pump system to construct series-connected low-temperature and high-temperature circulating systems, the systems are connected through an intermediate heat storage water tank, and the tank supplies cold air for an air supply system, hot water for a hot water system and steam for a steam system. The water temperature of the heat storage water tank and the output temperature of the high-temperature system are acquired in real time, the temperature distance is calculated based on a temperature distance algorithm, and the cold quantity, the hot water quantity and the steam quantity are dynamically adjusted through a differential coefficient. The application realizes cascade energy circulation reuse of cold, hot water and steam, reduces low-grade waste heat emission and improves the comprehensive energy utilization efficiency.

Description

Technical Field

[0001] This application relates to the technical field of energy consumption control, and in particular to a method, system and storage medium for energy consumption control of a circulating system in a large laundry room. Background Technology

[0002] Large-scale laundries are essential supporting facilities in hotels, medical facilities, and catering industries, capable of meeting the large-scale fabric cleaning needs of various sectors, significantly improving washing efficiency, and effectively reducing labor costs. Currently, the large-scale laundry industry is experiencing steady market growth, with its market share continuously increasing, and the application rate of automated and intelligent equipment gradually rising.

[0003] Energy costs account for a significant portion of the operating costs of large laundries, with core energy consumption concentrated in three areas: hot water preparation, steam ironing and shaping, and cooling of the work environment. Currently, the industry generally adopts a separate energy supply model, where steam is prepared by an independent gas or electric steam system, hot water for laundry is supplied by an independent hot water system, and cooling for the work environment is provided by an air conditioning unit driven by an independent refrigeration unit. Each system is designed and operates independently.

[0004] The current separate energy supply model in large laundries results in independent energy utilization for each stage of washing hot water, steam ironing, and environmental cooling, without forming an effective energy exchange and recycling mechanism. Low-grade heat energy, such as condensation heat generated by steam ironing, waste heat from hot water preparation, and waste heat generated by the operation of refrigeration units, is mostly directly emitted without being recovered and utilized, resulting in low overall energy utilization efficiency. Summary of the Invention

[0005] To improve the energy efficiency of large laundries, this application provides a method, system, and storage medium for controlling the energy consumption of a circulating system in a large laundry.

[0006] Firstly, this application provides a method for controlling energy consumption in the circulation system of a large laundry room, employing the following technical solution: A method for controlling energy consumption in the circulation system of a large laundry room includes the following steps: A series of low-temperature and high-temperature circulation systems are constructed using a heat pump system based on reverse Carnot cascade. The low-temperature circulation system takes the ambient heat source as input and its output temperature is within a preset first temperature range. The low-temperature circulation system has an evaporator connected to an air supply system to provide cooling capacity to the air supply system. A hot water storage tank is installed at the midpoint between the low-temperature circulation system and the high-temperature circulation system. The output of the low-temperature circulation system is connected to the hot water storage tank. The hot water storage tank is connected to a hot water system to provide hot water to the hot water system. The input of the high-temperature circulating system is connected to the hot water storage tank. The output temperature of the high-temperature circulating system is located in a preset second temperature range, wherein the value in the first temperature range is less than the value in the second temperature range. The high-temperature circulating system is equipped with a condenser, which is connected to a steam system and provides steam to the steam system. The system acquires the water temperature in the hot water storage tank in real time, calculates the temperature distance between the water temperature and a first temperature range based on a preset temperature distance algorithm, and adjusts the output cooling capacity according to the water temperature distance with a positive correlation using a first coefficient; it also adjusts the output hot water volume according to the water temperature distance with a negative correlation using a second coefficient, where the first coefficient is less than the second coefficient. The system also acquires the output temperature of the high-temperature circulation system in real time as the final temperature value, calculates the temperature distance between the final temperature value and a second temperature range based on a preset temperature distance algorithm, and adjusts the steam volume according to the final temperature distance with a negative correlation using a third coefficient, where the third coefficient is greater than the second coefficient.

[0007] By adopting the above technical solutions, the cascade energy cycle architecture and the dynamic adjustment mechanism of the differential coefficient constructed by the reverse Carnot cascade heat pump can achieve precise on-demand supply of cooling, hot water and steam and low-grade energy recovery and buffering, which can significantly reduce energy waste and emission losses, significantly improve the overall energy utilization efficiency, and accurately adapt to the energy needs of laundry rooms in multiple scenarios, effectively reducing the overall energy consumption and energy costs in the operation process.

[0008] Optionally, the temperature distance algorithm includes the following steps: The temperature distance algorithm takes temperature value and temperature range as input. Based on the preset rated operating conditions, the sum of the durations corresponding to the values ​​within the preset acquisition time is calculated as the stable duration, and the value with the longest stable duration is obtained as the stable temperature value. The temperature distance is calculated as the difference between the temperature value and the stable temperature value.

[0009] By adopting the above technical solutions, the core stable benchmark of the temperature range is accurately captured, and the adjustment deviation caused by instantaneous temperature fluctuations is avoided. This makes the temperature distance calculation more in line with the actual working conditions, providing accurate and reliable decision-making basis for the dynamic adjustment of cooling capacity, hot water capacity and steam capacity. In turn, it ensures the stability and adaptability of each energy supply link and helps to further improve the overall energy utilization efficiency.

[0010] Optionally, the method further includes the following steps: The ratio of the final temperature distance to the water temperature distance is calculated as the temperature distance ratio. The water storage capacity or volume of the hot water storage tank is adjusted according to the positive correlation of the temperature distance ratio. If the water storage capacity of the hot water storage tank is to be adjusted, a water pump connected to the hot water storage tank is installed. The water pump is connected to a water storage tank and the water pump is controlled to pump water into or out of the hot water storage tank. If the volume of the hot water storage tank is adjusted, the hot water storage tank is filled with water and is equipped with a drive component and a piston. Controlling the length of the drive component can drive the piston to move, thereby changing the volume of water that can be contained. The piston is equipped with an electric valve. When the piston moves, the electric valve opens, and when the piston stops, the electric valve closes.

[0011] By adopting the above technical solution, the dynamic adjustment of the water storage capacity or volume of the hot water storage tank is achieved through the temperature distance ratio linkage. Combined with the dual-mode adaptation design of water pump pumping / delivering and the piston driven by the drive component, it not only achieves a precise response to the energy supply and demand balance of the low-temperature stage and the high-temperature stage system, but also ensures the sealing and stability of the volume adjustment through the opening and closing control of the piston electronic valve. This effectively improves the energy buffering and adaptation capability of the hot water storage tank, ensures the smooth connection of the cascade energy cycle, and further enhances the system's adaptability to different laundry room operating conditions.

[0012] Optionally, the method further includes the following steps: The ratio of the final temperature distance to the water temperature distance is calculated as the temperature distance ratio. The power control of the low-temperature stage circulation system is adjusted based on the negative correlation of the temperature distance ratio. The ratio of the calculated water temperature value to the maximum value in the first temperature range is called the first water temperature ratio. The power control step size of the low-temperature stage circulation system is adjusted according to the first water temperature ratio.

[0013] By adopting the above technical solution, and through the dual-dimensional linkage adjustment logic of the temperature distance ratio and the first water temperature ratio, the power of the low-temperature stage circulation system is controlled by the negative correlation of the temperature distance ratio to achieve a precise response to the energy supply and demand balance of the high and low temperature stages. At the same time, the power control step size is optimized by the positive correlation of the first water temperature ratio, so that the power adjustment is more in line with the water temperature change gradient, avoiding energy loss caused by over-adjustment or adjustment lag. The synergistic effect of the dual-dimensional adjustment effectively improves the accuracy and dynamic adaptability of the power output of the low-temperature stage circulation system, and ensures the dynamic matching of cold energy supply and hot water buffer in the cascade energy cycle.

[0014] Optionally, the method further includes the following steps: The ratio of the final temperature distance to the water temperature distance is calculated as the temperature distance ratio. The power control of the high-temperature stage circulation system is adjusted according to the positive correlation of the temperature distance ratio. The ratio of the final temperature value to the maximum value in the second temperature range is calculated as the second water temperature ratio. The power control step size of the high-temperature stage circulation system is adjusted according to the positive correlation of the second water temperature ratio.

[0015] By adopting the above technical solution, and through the dual-dimensional linkage adjustment logic of the temperature distance ratio and the second water temperature ratio, the power of the high-temperature stage circulation system is controlled by the positive correlation of the temperature distance ratio, accurately responding to the energy supply and demand balance between the high and low temperature stage circulation systems. At the same time, the power control step size is optimized by the positive correlation of the second water temperature ratio, so that the power adjustment of the high-temperature stage circulation system fits its own temperature change gradient, avoiding ineffective energy consumption caused by over-adjustment or adjustment lag. The synergistic effect of the dual-dimensional adjustment effectively improves the energy conversion efficiency and steam output accuracy of the high-temperature stage circulation system, ensures stable energy supply in the steam preparation stage, ensures smooth connection of the entire laundry room's tiered energy cycle, and further improves the overall energy utilization efficiency of the system.

[0016] Optionally, the method further includes the following steps: The difference between the final temperature and the water temperature is calculated as the intermediate temperature difference. Calculate the temperature stability value for the first temperature range as the first stable value, calculate the temperature stability value for the second temperature range as the second stable value, and calculate the difference between the second stable value and the first stable value as the range temperature difference. The ratio of the intermediate temperature difference to the range temperature difference is calculated as the system temperature ratio. The cooling power of the air supply system is adjusted according to the positive correlation of the system temperature ratio.

[0017] By adopting the above technical solution, the cooling power of the air supply system can be adjusted based on the positive correlation between the system temperature ratio of the intermediate temperature difference and the range temperature difference. This can accurately reflect the overall energy gradient state of the high and low temperature stage circulation system, avoiding ineffective energy consumption caused by insufficient matching between cooling power and system energy. At the same time, it ensures that the cooling supply of the air supply system is highly matched with the real-time cooling demand of the laundry room working environment. This not only ensures that the comfort of the working environment meets the requirements of production operations, but also further coordinates the smoothness of the cascade energy cycle, effectively improving the efficiency of cooling utilization.

[0018] Optionally, the method further includes the following steps: Obtain the required amount of hot water and calculate the ratio of the hot water volume to the water storage capacity of the hot water tank as the hot water ratio. If the hot water ratio is within the preset first hot water range, then control multiple hot water storage tanks to be connected in series and provide hot water after a preset first time delay; If the hot water ratio is within the preset second hot water range, then control multiple hot water storage tanks to be connected in parallel and provide hot water after a preset second delay; Among them, the value in the first hot water range is less than the value in the second hot water range, and the first duration is shorter than the second duration; The ratio of the final temperature distance to the water temperature distance is calculated as the temperature distance ratio. The number of hot water storage tanks connected in series or in parallel is adjusted according to the positive correlation of the temperature distance ratio. If the hot water ratios are all outside the first and second hot water ranges, then one hot water storage tank will be reserved for storing hot water, and the other hot water storage tanks will be shut down.

[0019] By adopting the above technical solutions, through intelligent switching between series and parallel modes of hot water storage tanks based on hot water ratio, dynamic adjustment of the number of series and parallel tanks combined with temperature distance ratio, and timely disconnection of excess water tanks under abnormal operating conditions, the system can accurately adapt to the fluctuations in hot water demand in the laundry room at different times. The series mode can meet the energy-efficient buffering under small flow hot water demand, while the parallel mode can quickly respond to large flow hot water supply demand. The differentiated setting of delay time further ensures the stability of water supply temperature. At the same time, this adjustment method effectively optimizes the energy transfer efficiency between the hot water storage tank and the high and low temperature circulation system, avoiding ineffective energy storage and energy loss.

[0020] Optionally, the method further includes the following steps: The final duration is the time it takes for the final temperature value to reach the maximum value in the second temperature range. If the final duration is less than the preset reference duration, the ratio of the final duration to the reference duration is calculated as the duration ratio. The steam output duration of a single steam output by the steam system is adjusted according to the positive correlation of the duration ratio. Otherwise, the steam output duration is controlled to the preset maximum output duration.

[0021] By adopting the above technical solution, and through a dynamic control mechanism for steam output duration based on the duration for which the final temperature reaches the maximum value of the second temperature range, the actual energy supply capacity of the steam system is precisely matched with the real-time demand for steam ironing in the laundry room. This avoids ineffective energy consumption or insufficient steam supply caused by blindly extending or shortening the steam output time. The positive correlation adjustment of the duration ratio can ensure basic steam supply needs and control energy loss when the temperature target duration is insufficient, and ensure continuous steam supply stability by using the maximum output duration when the temperature is stable and the target is met, further optimizing the energy utilization efficiency of the steam preparation process.

[0022] Secondly, this application provides an energy consumption control system for a large laundry room's circulation system, employing the following technical solution: A circulating system energy consumption control system for a large laundry room includes a processor, wherein the processor performs the steps of the circulating system energy consumption control method for a large laundry room as described in any of the preceding claims.

[0023] Thirdly, this application provides a storage medium, which adopts the following technical solution: A storage medium storing a program that, when executed by a processor, implements the steps of the energy consumption control method for the circulation system of a large laundry room as described above.

[0024] In summary, this application includes at least one of the following beneficial technical effects: Based on the series circulation architecture of the low-temperature and high-temperature stages constructed by the reverse Carnot cascade heat pump, this application realizes the tiered energy recycling of the three core energy-consuming links of large laundry rooms: cooling, hot water, and steam preparation. This breaks through the barrier of energy incompatibility in the traditional discrete energy supply mode, significantly reducing the direct emission of low-grade heat energy such as condensation heat and waste heat, and significantly improving the comprehensive energy utilization efficiency. Through the temperature distance algorithm, the stable temperature value is accurately anchored, providing a reliable basis for the dynamic adjustment of cooling capacity, hot water volume, and steam volume, avoiding adjustment deviations caused by instantaneous temperature fluctuations, and ensuring the stable operation of each energy supply link. The dual-mode dynamic adjustment of the hot water storage tank's water storage capacity / volume... Intelligent switching and quantity control of dynamic regulation and series-parallel modes can accurately adapt to the fluctuations in hot water demand at different times, improving the energy buffer adaptability of the hot water storage tank and optimizing energy transfer efficiency, avoiding ineffective energy storage loss; the high and low temperature stage circulation system achieves precise response to energy supply and demand balance based on ratio dual-dimensional power control and step size optimization, avoiding ineffective energy consumption caused by over-regulation or regulation lag, and ensuring smooth connection of cascade energy circulation; the coordinated adjustment of cooling power of the air supply system can accurately match the cooling needs of the working environment, taking into account both environmental comfort and energy utilization efficiency; the dynamic control of steam output time can adapt to the actual energy supply capacity of the steam system, controlling energy consumption while ensuring stable energy supply for steam ironing. Attached Figure Description

[0025] Figure 1 This is a flowchart illustrating the steps of an energy consumption control method for a circulating system in a large laundry room.

[0026] Figure 2 This is a flowchart illustrating the steps of the temperature-distance algorithm. Detailed Implementation

[0027] The embodiments of this application are described in detail below, and examples of the embodiments are shown in the accompanying drawings.

[0028] In the description of this specification, the references to "certain embodiments," "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples" refer to specific features, structures, materials, or characteristics described in connection with the described embodiment or example, which are included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0029] This application discloses an energy consumption control method for a circulating system in a large laundry room, referring to... Figure 1 It includes the following steps: The heat pump unit, employing reverse Carnot cascade technology, serves as the core power unit. This unit integrates a series-connected low-temperature and high-temperature circulation systems. The low-temperature circulation system uses ambient heat sources as its energy input, such as low-grade heat sources like atmospheric heat energy or surface water heat energy around the laundry room. These heat sources form a closed loop through the low-temperature compressor, throttling device, and evaporator. The output temperature of the low-temperature circulation system is set to a preset first temperature range, specifically 45℃-55℃, to meet the hot water requirements of a large laundry room, accommodating the approximately 50℃ hot water standard needed for laundry processes. The evaporator in the low-temperature circulation system uses a shell-and-tube heat exchange structure. The evaporator's cold air outlet is connected to the laundry room's air supply system via a sealed duct. The air supply system includes a fan, ductwork, and air outlets. The 7℃-12℃ cooling capacity generated during the evaporator's cooling process is evenly distributed to the laundry room's work area through the air supply system, achieving the environmental cooling requirements for ironing, washing, and other processes.

[0030] A small insulated hot water storage tank is connected in series between the hot water output end of the low-temperature circulation system and the heat source input end of the high-temperature circulation system. The tank has a capacity of 500L-1000L, suitable for the 50-100L hot water consumption per hour of a large laundry room. The tank body uses a polyurethane foam insulation layer with an insulation coefficient ≤0.03W / (m·K), ensuring water temperature fluctuation ≤±2℃ / h. The hot water output pipe of the low-temperature circulation system is connected to the hot water storage tank and the laundry room's hot water system via a three-way valve. A temperature sensor is installed at the bottom of the hot water storage tank to collect real-time water temperature data. The hot water system includes a hot water storage tank, a circulation pump, and a water terminal (washing equipment inlet). The 45℃-55℃ hot water in the storage tank can be directly supplied to the hot water system to meet the hot water needs of fabric washing.

[0031] The high-temperature circulating system also uses a compressor, throttling device, and condenser to form a closed loop. Its energy input source is medium-temperature hot water in the hot water storage tank, such as 45℃-55℃. Through the multi-stage compression of the high-temperature compressor, the heat energy quality is improved, so that the output temperature of the high-temperature circulating system reaches the preset second temperature range. Combined with the steam ironing requirements of the laundry room, this second temperature range is specifically set to 120℃-150℃. The condenser of the high-temperature circulating system adopts a spiral tube heat exchange structure. The steam output end of the condenser is connected to the laundry room steam system through a pressure regulating valve. The steam system includes a steam storage tank, a pressure reducing valve, and an air inlet for the ironing equipment. The 120℃-150℃ saturated steam generated by the condenser is reduced to 0.4-0.6MPa before being supplied to the ironing and shaping process.

[0032] The water temperature is collected in real time by a temperature sensor inside the hot water storage tank at a frequency of once every 30 seconds. The water temperature distance D1 is calculated based on a preset temperature distance algorithm: Under rated operating conditions, such as an ambient temperature of 25℃ and a system load of 75%, with a collection duration of 1 hour, the duration of each temperature value within the first temperature range (45℃-55℃) is statistically analyzed. The temperature value with the longest duration is selected as the stable temperature value T0, such as 50℃. The difference between the real-time water temperature value and 50℃ is the water temperature distance D1, in ℃. Similarly, the final temperature value is collected in real time by a temperature sensor (measurement accuracy ±1℃) at the output end of the high-temperature circulating system. Using the stable temperature value T0 (such as 135℃) of the second temperature range (120℃-150℃) as a benchmark, the final temperature distance is calculated as the water temperature distance D1.

[0033] In this embodiment, the output cooling capacity Qc is adjusted in a positive correlation with the water temperature distance using a first coefficient; the output hot water capacity Qh is adjusted in a negative correlation with the water temperature distance using a second coefficient, where the first coefficient is less than the second coefficient; and the steam capacity Qs is adjusted in a negative correlation with the final temperature distance using a third coefficient, where the third coefficient is greater than the second coefficient.

[0034] The cooling capacity value is adjusted using the first coefficient positive correlation, and the formula is: The cooling capacity value Qc = Qc0 × (1 + k1 × D1); the first coefficient k1 ∈ [0.3, 0.5], and the example value is k1 = 0.4; When D1=0℃ (water temperature=50℃, meets the standard): Qc=Qc0×(1+0.4×0)=1.0×Qc0, rated cooling capacity output; When D1=2℃ (water temperature=48℃, which is too low): Qc=Qc0×(1+0.4×2)=1.8×Qc0, the cold output is increased, and the water tank temperature is accelerated; When D1=5℃ (water temperature=45℃, minimum value): Qc=Qc0×(1+0.4×5)=3.0×Qc0, maximum cooling output, extreme temperature compensation.

[0035] The hot water volume is adjusted using a second coefficient with negative correlation, and the formula is as follows: Hot water volume Qh = Qh0 × (1 - k2 × D1); the second coefficient k2 ∈ [0.6, 0.8], the example value is k2 = 0.7, and k2 > k1; When D1=0℃ (water temperature=50℃, meets the standard): Qh=Qh0×(1-0.7×0)=1.0×Qh0, rated hot water output; When D1=2℃ (water temperature=48℃, which is too low): Qh=Qh0×(1-0.7×2)=0.6×Qh0, reduce hot water output and prioritize heat storage; When D1=5℃ (water temperature=45℃, minimum value): Qh=Qh0×(1-0.7×5)=-2.5×Qh0. When the calculation result is <0.3Qh0, it will be executed directly according to 0.3Qh0, triggering the minimum hot water output threshold, and only 30%Qh0 will be retained to maintain basic water supply.

[0036] The steam quantity is adjusted using a third coefficient with negative correlation, and the formula is as follows: Steam quantity Qs = Qs0 × (1 - k3 × D2); the third coefficient k3 ∈ [0.9, 1.2], the example value is k3 = 1.0, and k3 > k2; When D2=0℃ (temperature=135℃, meets the standard): Qs=Qs0×(1-1.0×0)=1.0×Qs0, rated steam output; When D2=5℃ (temperature=130℃, which is too low): Qs=Qs0×(1-1.0×5)=-4.0×Qs0, the lower limit of steam volume is triggered, and 60% Qs0 is maintained to ensure ironing needs. When D2=15℃ (temperature=120℃, minimum value): Qs=Qs0×(1-1.0×15)=-14.0×Qs0, reduce to the minimum steam output threshold of 40%Qs0 to avoid system overload.

[0037] In the above formula, upper and lower limits are set for the output values ​​of cooling capacity, hot water capacity, and steam capacity. For example, the upper limit of cooling capacity is ≤3.0×Qc0, the lower limit of hot water capacity is ≥0.3×Qh0, and the lower limit of steam capacity is ≥0.4×Qs0, to prevent excessive adjustment from causing abnormal system operation. The coefficients k1, k2, and k3 can be adaptively calibrated according to the actual scale of the laundry room (such as a daily washing volume of 500kg / 1000kg) and the range of ambient temperature fluctuations, and the calibration range shall not exceed the above-mentioned set range. The temperature stability value T0 can be updated through the system's self-learning function. Every 72 hours, the stable duration within the 1-hour data collection period is recalculated, and T01 and T02 are updated to ensure that the adjustment benchmark matches the actual working conditions.

[0038] By adopting the above technical solutions, the cascade energy cycle architecture constructed by the reverse Carnot cascade heat pump and the dynamic adjustment mechanism of the differential coefficient are used to achieve cascade energy recycling, high energy utilization efficiency, precise adaptation to demand, and compact and efficient structure.

[0039] Reference Figure 2 The detailed steps of the temperature-distance algorithm are as follows: The input to the temperature distance algorithm includes two types of parameters: one is the real-time temperature value T, specifically the water temperature value Tw in the hot water storage tank or the output temperature value Ts of the high-temperature circulation system; the other is the preset temperature range, corresponding to the first temperature range T1=45℃-55℃ or the second temperature range T2=120℃-150℃.

[0040] Real-time temperature values ​​are acquired through high-precision temperature sensors, with a PT100 platinum resistance temperature sensor used in the hot water storage tank and a K-type thermocouple sensor used at the output of the high-temperature circulation system; the acquisition frequency is set to 1 time / 10 seconds to ensure real-time data.

[0041] The first temperature range T1 is set based on the standard for hot water use in the laundry room (50℃±5℃), and the second temperature range T2 is set based on the requirements of steam ironing process (120℃-150℃ saturated steam). Both are preset and stored by the system controller, and can be manually calibrated by ±5℃ according to actual working conditions (such as different fabric washing / ironing requirements).

[0042] The preset rated operating conditions are an ambient temperature of 25℃±3℃ and a system operating load of 75%±10%, which means the laundry room is in a medium washing capacity state, with a hot water consumption of 50L / h and a steam consumption of 30kg / h. This operating condition is the benchmark operating condition for normal system operation, ensuring the objectivity of temperature stability calculation.

[0043] Data Acquisition Duration and Statistics: The preset acquisition duration is set to 1 hour (3600 seconds). Under rated operating conditions, the system controller continuously collects and statistically analyzes the real-time temperature values. The temperature values ​​are classified according to integer precision, such as 45℃, 46℃…55℃, 120℃, 121℃…150℃. The duration of each temperature value within 1 hour is calculated in seconds, and the stable duration ti corresponding to each temperature value is accumulated, where i is the temperature value sequence number.

[0044] Temperature stability value selection: Sort the stability duration ti corresponding to all temperature values, and select the temperature value with the longest stability duration as the temperature stability value T0.

[0045] Example 1 (First temperature range T1 = 45℃-55℃): Statistically, within 1 hour, 45℃ lasts for 300 seconds, 46℃ lasts for 360 seconds, ..., 50℃ lasts for 1800 seconds, ..., 55℃ lasts for 240 seconds. Among them, the stable duration of 50℃ is the longest (1800 seconds). Therefore, the stable temperature value of the first temperature range T01 = 50℃.

[0046] Example 2 (Second temperature range T2 = 120℃-150℃): Statistical analysis shows that within 1 hour, 120℃ lasts for 240 seconds, 125℃ lasts for 300 seconds, ..., 135℃ lasts for 1500 seconds, ..., 150℃ lasts for 180 seconds. Among them, 135℃ has the longest stable duration (1500 seconds). Therefore, the stable temperature value of the second temperature range T02 = 135℃.

[0047] Stable value update mechanism: The system automatically recalculates the stable temperature value under rated operating conditions every 72 hours. If the deviation of the calculation results is ≤±1℃ for 3 consecutive times, the stable temperature value is updated and stored. If the deviation exceeds ±2℃, the system self-check is triggered to check for abnormal sensors or operating conditions.

[0048] The temperature distance D is calculated using the absolute value difference formula, as follows: D = |T - T0|; where: D is the temperature distance (unit: °C), T is the real-time temperature value (Tw or Ts), and T0 is the stable temperature value (T01 or T02).

[0049] Calculation example: When the real-time water temperature in the hot water storage tank is Tw=48℃, the water temperature distance D1=|48-50|=2℃; When the real-time water temperature in the hot water storage tank is Tw=55℃, the water temperature distance D1=|55-50|=5℃; When the high-temperature stage output temperature Ts=130℃, the final temperature distance D2=|130-135|=5℃; When the high-temperature stage output temperature Ts=150℃, the final temperature distance D2=|150-135|=15℃.

[0050] Calculation result storage: The temperature distance D is calculated in real time by the system controller, and the calculation results are synchronously stored in the local cache, retaining the data of the most recent 24 hours, and used as the core input parameter for adjusting the cooling capacity, hot water capacity, and steam capacity.

[0051] By adopting the above scheme, based on long-term data statistics under rated operating conditions for one hour, the temperature stability value with the longest stable duration is selected as the calculation benchmark. This effectively eliminates the interference of instantaneous temperature fluctuations (such as sensor errors and temperature abrupt changes caused by short-term load variations) on the adjustment logic, avoiding over-adjustment or adjustment lag caused by benchmark deviation. Both the temperature range and rated operating conditions support calibration according to the actual needs of the laundry room. The temperature stability value is automatically updated periodically to ensure that the algorithm is adaptable to operating conditions under different ambient temperatures and washing loads, improving the versatility of the adjustment logic. High-precision sensors and high-frequency acquisition mechanisms are used, combined with a simple calculation method of absolute value difference, to reduce the system's computational load while ensuring data accuracy and ensuring real-time response of adjustment decisions (calculation delay ≤ 1 second). The temperature distance output by the algorithm is directly used as the quantitative basis for adjusting the cooling capacity, hot water capacity, and steam capacity, forming a closed-loop control with the subsequent differential coefficient adjustment mechanism. This makes the adjustment of each energy supply link more targeted, thereby ensuring the operational stability and energy utilization efficiency of the entire cycle system.

[0052] To further optimize the energy supply and demand matching accuracy between the cryogenic and high-temperature cycling systems, the method also includes the following steps: Based on the previously defined water temperature distance (D1, the difference between the hot water tank temperature and the stable value of the first temperature range) and final temperature distance (D2, the difference between the high-temperature stage output temperature and the stable value of the second temperature range), the temperature distance ratio R is calculated using the following formula: R = D2 / D1, where D1 ≠ 0. If D1 = 0, then R = 1.0 by default, maintaining the current heat storage state. R reflects the matching relationship between the energy demand gap of the high-temperature stage system and the energy supply surplus of the low-temperature stage system. When R > 1, the energy demand gap for high-temperature stage steam preparation is greater than the supply surplus of low-temperature stage hot water, and the heat storage capacity of the hot water tank needs to be increased. When R < 1, the supply surplus of low-temperature stage hot water is greater than the demand gap of high-temperature stage, and the heat storage capacity needs to be reduced. When R ∈ [0.8, 1.2], the energy supply and demand are in a balanced state, maintaining the current heat storage parameters.

[0053] If the water storage capacity of the hot water storage tank is to be adjusted, a water pump connected to the hot water storage tank is installed. The water pump is connected to a water storage tank and controls the pump to deliver or pump water into the hot water storage tank.

[0054] This embodiment uses a variable frequency centrifugal water pump with a flow rate adjustment capability of 0-100% to adapt to different water replenishment needs. The volume of the water storage tank is set to 1.5 times the rated volume of the hot water storage tank. For example, if the rated volume of the hot water storage tank is 500L, the volume of the water storage tank is 750L. A polyurethane foam insulation layer is used with an insulation coefficient ≤0.03W / (m·K) to avoid water temperature loss. The water pump inlet is connected to the water storage tank outlet through a flange, and the water pump outlet is connected to the hot water storage tank inlet through a three-way valve. The hot water storage tank outlet is connected to the water pump return outlet through another three-way valve, forming a bidirectional water flow loop. A flow sensor and a check valve are installed in the loop to prevent backflow.

[0055] The preset ratio thresholds R1=0.8 (lower threshold) and R2=1.2 (upper threshold) are used to dynamically control the water pump operation based on the relationship between R and the thresholds. When R > R2 (e.g., R = 1.5): The demand gap for high-temperature water is relatively large. The water pump is controlled to pump water to the hot water storage tank in a variable frequency mode. The replenishment amount ΔV is positively correlated with R. The formula is ΔV = V0 × (R - R2) × k, where V0 is the rated volume of the hot water storage tank and k is the replenishment amount coefficient, which is 0.3. Example: When V0 = 500L and R = 1.5, ΔV = 500 × (1.5 - 1.2) × 0.3 = 45L. The water pump runs at a flow rate of 30L / min for 1.5 minutes to complete the replenishment. When R < R1 (e.g., R = 0.6): The low-temperature stage supply margin is excessive, so the water pump is controlled to run in reverse to pump water from the hot water storage tank to the storage tank. The pumping volume ΔV' = V0 × (R1 - R) × k', where k' is the pumping volume coefficient, with a value of 0.2. Example: When R = 0.6, ΔV' = 500 × (0.8 - 0.6) × 0.2 = 20L. The water pump runs in reverse at a flow rate of 20L / min for 1 minute to complete the pumping. When R∈[R1, R2]: Maintain the current water level in the hot water storage tank, stop the water pump, close the check valve, and ensure the water tank is sealed.

[0056] If the volume of the hot water storage tank is adjusted, the hot water storage tank is filled with water and is equipped with a drive component and a piston. Controlling the length of the drive component can drive the piston to move, thereby changing the volume of water that can be contained. The piston is equipped with an electric valve. When the piston moves, the electric valve opens, and when the piston stops, the electric valve closes.

[0057] In this embodiment, the main body of the water tank adopts a cylindrical structure (inner diameter 600mm, length 2000mm), made of 304 food-grade stainless steel, with anti-corrosion treatment on the inner wall; the initial volume of the water tank is 500L, and the adjustable range is 300L-700L to adapt to different heat storage requirements; the drive component is preferably a pneumatic cylinder (model example: SC50×300, cylinder diameter 50mm, stroke 300mm, working pressure 0.4-0.6MPa) or a hydraulic cylinder (model example: HOB50×300, rated pressure 16MPa), with position feedback function (accuracy ±0.5mm), and the extension and retraction are controlled by a solenoid valve group; The piston assembly has a piston diameter gap of ≤0.1mm with the inner diameter of the water tank. Two fluororubber O-rings (model O-ring 590×5) are installed on the outer ring to ensure sealing performance. A through hole is opened in the center of the piston to install an electromagnetic ball valve (model example: 2W-200-20, nominal diameter DN20, working pressure 0-1.6MPa, response time ≤0.5 seconds) as an electrically controlled valve. The valve coil voltage is 24VDC and is linked with the drive component. Pressure sensors and liquid level sensors are installed at both ends of the water tank to monitor the pressure and liquid level inside the tank in real time, preventing overpressure or dry burning.

[0058] Volume regulation control process: When the temperature distance ratio R exceeds the range of [0.8, 1.2] and the water storage adjustment reaches the limit (such as the water storage has reached the maximum of 80% or the minimum of 20%), it will automatically switch to the volume adjustment mode. When R > R2 (e.g., R = 1.8), the heat storage volume needs to be increased: The system controller sends an extension command to the solenoid valve assembly of the drive component and an opening signal to the electrically controlled valve at the same time; The piston rod of the driving component extends slowly (extension speed 5mm / s), driving the piston to move outward along the axial direction of the water tank, and the volume of the water tank that can hold the flowing water gradually increases. External water is supplied into the water tank through the through-hole of the electronically controlled valve. The liquid level sensor provides real-time feedback on the liquid level. When the volume reaches the target value (e.g., 700L), the drive mechanism stops operating and the electronically controlled valve closes. When R < R1 (e.g., R = 0.5), the heat storage volume needs to be reduced: The system controller sends a shortening command to the solenoid valve assembly of the drive component, and at the same time sends an opening signal to the electrically controlled valve; The piston rod of the driving component slowly shortens, causing the piston to move inward, and the internal volume of the water tank gradually decreases; Excess water in the water tank is discharged into the water storage tank through the through hole of the electronically controlled valve. The pressure sensor monitors the internal pressure in real time. When the volume reaches the target value (e.g., 300L), the drive stops and the electronically controlled valve closes. When the piston is stationary, the electronically controlled valve remains closed, and the O-ring seal double seals the valve to ensure that the water tank is leak-free and maintains a stable water temperature (fluctuation ≤ ±1℃ / h).

[0059] Dual-mode adjustment linkage control logic: Water storage regulation is the basic regulation mode (fast response and low energy consumption), while volume regulation is the supplementary regulation mode, which can adapt to large fluctuations in operating conditions. The system prioritizes water storage regulation. When the water storage reaches the upper or lower limit, such as the maximum water storage being 90% of the rated volume and the minimum being 10%, it automatically switches to volume regulation. The temperature-distance ratio R is positively correlated with the adjustment amount. The adjustment coefficient k3 is set to 0.1 (L / ℃), meaning that for every 0.1 change in R, the water storage or volume is adjusted by 50L. For example, if R increases from 1.2 to 1.4, the water storage increases by 100L. If the water storage has reached its upper limit, the volume will increase by 100L.

[0060] To address the issues of poor power adaptability during cold start-up, low heating efficiency at low temperatures, and ineffective energy consumption caused by energy supply and demand imbalance at high and low temperatures, the method in this application further includes the following steps: Using the previously defined water temperature distance D1=|Tw-T01| and final temperature distance D2=|Ts-T02|, where Tw is the real-time water temperature of the hot water storage tank, T01=50℃ is the stable value of the first temperature range, Ts is the output temperature of the high-temperature stage, and T02=135℃ is the stable value of the second temperature range, the temperature distance ratio R is calculated as: R=D2 / D1. If D1=0, the water temperature is fully up to standard, and R=1.0 is used to maintain the current power. If D1<2℃, the water temperature is close to up to standard, and R is set to the upper limit of 1.5 to avoid excessive power increase. If Tw<30℃, the initial temperature of the chiller is much lower than the lower limit of the first temperature range of 45℃, and R is temporarily set to 0.5 to execute the chiller preheating logic.

[0061] R directly reflects the matching relationship between the energy demand for high-temperature steam preparation and the supply of low-temperature hot water. The larger R is, the greater the energy gap in the high-temperature stage, and the lower the power adjustment range of the low-temperature stage needs to be reduced to avoid excessive consumption of hot water. The smaller R is, the greater the energy supply margin in the low-temperature stage, and the power of the low-temperature stage can be increased to accelerate the preparation of hot water.

[0062] The first water temperature ratio S is calculated using the following formula: S = Tw / T 1，max ; where T 1，max =55℃, the maximum value of the first temperature range, that is, the highest water temperature acceptable to the hot water system, S∈(0,1]; S represents the degree of closeness between the real-time water temperature and the upper limit of the first temperature range; the smaller S is, the lower the water temperature, indicating that the heating demand is more urgent under low temperature conditions, and the power adjustment step size needs to be increased to improve the heating speed; the larger S is, the closer the water temperature is to the upper limit, and the step size needs to be reduced to avoid the water temperature from exceeding the limit.

[0063] Power amplitude adjustment with negative correlation between temperature and distance ratio: The power regulation of the low-temperature stage circulation system is based on the rated power P0, which is set according to the system scale. For example, 50kW is suitable for a laundry room with a daily washing volume of 500kg. The negative correlation regulation formula is used: P=P0×[1-k4×(R-1.0)]; the coefficient setting is: the first regulation coefficient k4∈[0.2, 0.3], and the example value is k4=0.25 to ensure that the power regulation range is controllable and avoid system overload; where P∈[0.3P0, 1.2P0], that is, the minimum power is not less than 30% of the rated value to ensure the basic preheating requirements when the cold start is achieved, and the maximum power does not exceed 120% of the rated value to avoid compressor overpressure operation.

[0064] Based on the entire operating condition process, the power regulation logic is as follows: Operating Condition 1: Cold Start-up Stage (Tw=30℃, D1=20℃; High Temperature Stage Not Started, D2=0℃, R=0.5): P=50kW×[1-0.25×(0.5-1.0)]=56.25kW; High-power preheating accelerates water temperature rise; Operating Condition 2: Heat engine heating stage (Tw=40℃, D1=10℃; high temperature stage start-up, Ts=125℃, D2=10℃, R=1.0): P=50kW×[1-0.25×(1.0-1.0)]=50kW; maintain rated power operation, balance hot water preparation and cooling supply; Operating Condition 3: Water temperature close to standard (Tw=52℃, D1=2℃; high temperature level, high load, Ts=130℃, D2=5℃, R=2.5): P=50kW×[1-0.25×(2.5-1.0)]=31.25kW; no need to trigger minimum power constraint, actual output power is 31.25kW, power is appropriately reduced to adapt to high temperature level, high load, while avoiding excessive hot water consumption, ensuring energy supply and demand balance; Operating Condition 4: Water Temperature Stability Stage (Tw=50℃, D1=0℃, R=1.0): Output power is maintained at P0=50kW to ensure a stable supply of cooling and hot water.

[0065] Optimization of power regulation step size based on the first water temperature ratio: The power adjustment step size ΔP, i.e. the amplitude of each power adjustment, is determined using the positive correlation adjustment formula: ΔP = ΔP0 × S × k5; The baseline step size ΔP0 = 5kW (default minimum adjustment step size); The second adjustment coefficient k5∈[1.5, 2.5], with an example value of k5=2.0, strengthens the correlation between step size and water temperature; Step size upper and lower limits constraint: ΔP∈[2kW, 10kW], to avoid the adjustment lag caused by too small a step size or the water temperature fluctuation caused by too large a step size.

[0066] The goal of step size adjustment is to rapidly increase the temperature with large steps at low temperatures and precisely control the temperature with small steps at high temperatures. A specific example is shown below: Low temperature operation (Tw=30℃, S=30 / 55≈0.545): ΔP=5kW×0.545×2.0≈5.45kW; rounded to 5kW (close to the upper limit of the reference step size), each power adjustment is 5kW, achieving rapid temperature rise. For example, only 8 adjustments are needed to raise the temperature from 30℃ to 40℃, which is 60% more efficient than the fixed step size of 2kW. Medium temperature condition (Tw=45℃, S=45 / 55≈0.818): ΔP=5kW×0.818×2.0≈8.18kW; rounded to 8kW, large step continuous heating, suitable for water temperature rise requirements; High temperature condition (Tw=52℃, S=52 / 55≈0.945): ΔP=5kW×0.945×2.0≈9.45kW; trigger step size upper limit is 10kW, at which point the power is close to the rated value, and the stable state is quickly adapted by a large step size; Near-standard operating conditions (Tw=54℃, S=54 / 55≈0.982): ΔP=5kW×0.982×2.0≈9.82kW; As the water temperature approaches the upper limit, the step size automatically decreases to 5kW (the threshold for manual intervention to avoid overheating), achieving precise temperature control.

[0067] Dual-dimensional linkage control process and equipment configuration: The low-temperature stage circulation system starts with a minimum power chiller of 0.3P0. The temperature sensor collects Tw every 10 seconds and simultaneously acquires Ts of the high-temperature stage. Calculate D1, D2, R, and S in real time to determine the current operating condition (cold engine preheating / hot engine heating / stable water temperature). Calculate the target power P based on R, and determine the adjustment step size ΔP based on S; The operating frequency of the cryogenic compressor (model example: ZW34KSE-TFP-582, rated power 50kW, frequency adjustment range 30-70Hz) is controlled by a frequency converter to gradually approach the target power P by ΔP. When Tw∈[48℃, 52℃] and R∈[0.8, 1.2], it enters a stable operating state, and the adjustment step size is automatically reduced to 2kW to reduce power fluctuations.

[0068] The compressor is a scroll-type variable frequency compressor with a wide frequency adjustment range (30-70Hz) and power adjustment accuracy of ±1kW, adapting to dual-dimensional adjustment needs. Example inverter model: ABBACS580-01-072A-4, rated power 55kW, output frequency accuracy ±0.01Hz, response time ≤0.1 seconds, ensuring real-time step adjustment. Temperature acquisition uses a PT1000 platinum resistance sensor, sampling once every 10 seconds, avoiding misjudgments caused by instantaneous fluctuations. Compressor exhaust temperature protection (upper limit 120℃) and overcurrent protection (1.2 times rated current) are provided; when power adjustment triggers the protection threshold, the compressor automatically reduces to safe power operation.

[0069] By adopting the above technical solution, and through the dual-dimensional linkage adjustment logic of the temperature distance ratio and the first water temperature ratio, the power of the low-temperature stage circulation system is controlled by the negative correlation of the temperature distance ratio to achieve a precise response to the energy supply and demand balance of the high and low temperature stages. At the same time, the power control step size is optimized by the positive correlation of the first water temperature ratio, so that the power adjustment is more in line with the water temperature change gradient, avoiding energy loss caused by over-adjustment or adjustment lag. The synergistic effect of the dual-dimensional adjustment effectively improves the accuracy and dynamic adaptability of the power output of the low-temperature stage circulation system, and ensures the dynamic matching of cold energy supply and hot water buffer in the cascade energy cycle.

[0070] To address the technical challenges of rapid temperature rise leading to overheating during steam preparation in high-temperature circulating systems, delayed response during the isothermal phase, and energy supply-demand imbalance with the low-temperature stage, this application constructs a two-dimensional power regulation logic based on the temperature distance ratio and the second water temperature ratio. The specific method further includes the following steps: Using the key temperature parameters defined above: water temperature distance D1 = |Tw-T01|, final temperature distance D2 = |Ts-T02|; Tw is the real-time water temperature of the hot water storage tank, T01 = 50℃ is the stable value of the first temperature range; Ts is the output temperature of the high-temperature stage circulation system, T02 = 135℃ is the stable value of the second temperature range, and the temperature distance ratio R is calculated: R = D2 / D1; If D2=0 (steam temperature fully meets the standard), the default R=1.0, maintaining the current power; if the low-temperature stage water temperature does not meet the standard, Tw<40℃, D1>10℃, R takes the lower limit of 0.5, limiting the power of the high-temperature stage to avoid insufficient energy supply to the low-temperature stage; if the fluctuation range of Ts during the constant temperature stage is ≤±1℃, R is locked at 1.0, and fine constant temperature control is performed.

[0071] R directly reflects the matching relationship between the energy gap of high-temperature stage steam preparation and the hot water supply capacity of low-temperature stage; the smaller R is, the larger the energy gap of high-temperature stage and the sufficient supply of low-temperature stage, and the power of high-temperature stage needs to be increased to accelerate steam preparation; the larger R is, the high-temperature stage is close to constant temperature and the energy gap is reduced, and the power adjustment range needs to be reduced to maintain stability.

[0072] The second water temperature ratio S2 is calculated using the following formula: S2 = Ts / T 2，max ; Where T 2，max =150℃, the maximum value of the second temperature range, that is, the highest allowable temperature for steam preparation, S2∈(0,1]; S2 characterizes the degree of closeness between the high-temperature stage output temperature and the upper limit of the second temperature range; the closer S2 is to 1, the closer the temperature is to the constant temperature target, and the power adjustment step size needs to be increased to quickly respond to temperature fluctuations and avoid lag; the smaller S2 is, the lower the temperature, and the step size needs to be reduced to avoid power sudden changes causing equipment overload.

[0073] Power amplitude adjustment that is positively correlated with the temperature-distance ratio: The power regulation of the high-temperature circulating system is based on the rated power P02, which is set based on the steam demand. For example, 80kW is suitable for a laundry room with a steam output of 30kg per hour. The positive correlation regulation formula is used (to ensure that the power tends to stabilize when R increases): P2=P02×[1-k6×(R-1.0)]; Coefficient setting: The third adjustment coefficient k6∈[0.15, 0.25], the example value is k6=0.2, which takes into account both adjustment sensitivity and stability; Power upper and lower limit constraints: P2∈[0.4P02, 1.1P02], that is, the minimum power is not less than 40% of the rated value, to ensure the minimum operating load of the high temperature compressor and avoid frequent start-stop, and the maximum power does not exceed 110% of the rated value, to prevent system failure caused by excessively high compressor discharge temperature.

[0074] Example of control logic and full-condition adaptation: Based on the energy flow process of low-temperature stage preheating → high-temperature stage start-up → steam heating → constant temperature output, the power regulation logic is as follows: Operating Condition 1: Low-temperature stage preheating stage (Tw=40℃, D1=10℃; High-temperature stage initial start-up, Ts=110℃, D2=25℃, R=2.5): P2=80kW×[1-0.2×(2.5-1.0)]=56kW; Operating Condition 2: Steam Heating Stage (Tw=50℃, D1=0℃, R=1.0; Ts=125℃, D2=10℃): P2=80kW×[1-0.2×(1.0-1.0)]=80kW; Maintain rated power operation, accelerate steam heating, and simultaneously match stable supply of low temperature stage; Operating Condition 3: Approaching the constant temperature stage (Tw=52℃, D1=2℃; Ts=132℃, D2=3℃, R=1.5): P2=80kW×[1-0.2×(1.5-1.0)]=80kW×0.9=72kW; Reduce the power adjustment range to avoid overheating and gradually approach the constant temperature target; Operating Condition 4: Constant Temperature Output Stage (Ts=135℃, D2=0℃, R=1.0): The output power is maintained at 80kW, and the steam temperature fluctuation is ≤±0.5℃, which meets the stable steam supply requirements of the ironing process.

[0075] Optimization of power regulation step size based on the second water temperature ratio: The power adjustment step size ΔP2 (the amplitude of each power adjustment) adopts a positive correlation adjustment formula to ensure rapid response during the constant temperature stage: ΔP2=ΔP02×S2×k7; The baseline step size ΔP02 = 3kW (default minimum adjustment step size); The fourth adjustment coefficient k7∈[1.2, 2.0] (example value k7=1.5) strengthens the correlation between step size and constant temperature requirement; Step size upper and lower limits constraint: ΔP2∈[2kW, 8kW], to avoid response lag due to too small a step size (such as the inability to quickly replenish energy when the temperature drops during constant temperature) or overheating due to too large a step size (such as sudden power change during the heating stage).

[0076] Example of control logic and operating condition adaptation: Low temperature heating condition (Ts=110℃, S2=110 / 150≈0.733): ΔP2=3kW×0.733×1.5≈3.3kW; rounded to 3kW, small step-by-step stable heating to avoid sudden changes in compressor load; Under medium-temperature heating conditions (Ts=130℃, S2=130 / 150≈0.867): ΔP2=3kW×0.867×1.5≈3.9kW; rounded to 4kW, the step size is appropriately increased to accelerate the approach to the constant temperature target; Under constant temperature fluctuation conditions (Ts=134℃, S2=134 / 150≈0.893): ΔP2=3kW×0.893×1.5≈4.02kW; automatically increases to the upper limit of 6kW, which can quickly replenish energy and avoid steam pressure fluctuations caused by sudden power changes; Near the upper limit of operation (Ts=145℃, S2=145 / 150≈0.967): ΔP2=3kW×0.967×1.5≈4.35kW; As the temperature approaches the upper limit, the step size automatically decreases to 2kW for precise temperature control, avoiding overheating that could lead to a decrease in steam quality.

[0077] Details of the dual-dimensional linkage control process and equipment configuration: Start-up linkage: The high-temperature stage circulation system needs to be started when the low-temperature stage water temperature is ≥45℃ to avoid the compressor being overloaded by the low-temperature heat source. During the initial start-up, it runs at the minimum power of 0.4PO2. Parameter acquisition: Ts is acquired every 5 seconds by a K-type thermocouple sensor (accuracy ±0.3℃) at the output end of the high-temperature stage, and Tw of the hot water storage tank is acquired simultaneously. The acquisition frequency is consistent with that of the low-temperature stage. Parameter calculation: Real-time calculation of D1, D2, R, and S2 to determine the current operating condition (heating stage / constant temperature stage / fluctuation stage); Power decision: Calculate the target power P2 based on R, and determine the adjustment step size ΔP2 based on S2; Dynamic adjustment: The operating frequency of the high-temperature compressor (model example: ZW61KSE-TFP-582, rated power 80kW, frequency adjustment range 25-75Hz) is controlled by the frequency converter, and the power is gradually approached by ΔP2, with an adjustment delay of ≤0.2 seconds; Stable feedback: When Ts∈[134℃, 136℃] and there is no fluctuation for 30 consecutive seconds, it enters a constant temperature stable state, and the adjustment step size is locked at 8kW to ensure rapid response to load changes.

[0078] The high-temperature stage compressor uses an ultra-high temperature variable frequency scroll compressor, which has a wide pressure ratio operation capability (maximum pressure ratio 12:1) and is suitable for steam preparation requirements of 120℃-150℃. The exhaust temperature protection threshold is set at 160℃. The frequency converter, such as Siemens G120C, has a rated power of 90kW, an output frequency accuracy of ±0.01Hz, supports PID closed-loop control, and works in conjunction with the system controller to achieve precise power adjustment. The pressure coordination control is based on a pressure sensor (measurement range 0-2.5MPa, accuracy ±0.02MPa) installed at the outlet of the high-temperature stage condenser. When the steam pressure exceeds 0.6MPa (the rated pressure of the ironing equipment), the power is automatically reduced by 10% to avoid the risk of overpressure. In addition, compressor overcurrent protection (1.1 times the rated current), overtemperature protection (exhaust temperature 160℃), and low pressure protection (suction pressure 0.1MPa) are also set. When the protection is triggered, the power is reduced to the minimum and an alarm signal is issued at the same time.

[0079] By adopting the above technical solution, and through the dual-dimensional linkage adjustment logic of the temperature distance ratio and the second water temperature ratio, the power of the high-temperature stage circulation system is controlled by the positive correlation of the temperature distance ratio, accurately responding to the energy supply and demand balance between the high and low temperature stage circulation systems. At the same time, the power control step size is optimized by the positive correlation of the second water temperature ratio, so that the power adjustment of the high-temperature stage circulation system fits its own temperature change gradient, avoiding ineffective energy consumption caused by over-adjustment or adjustment lag. The synergistic effect of the dual-dimensional adjustment effectively improves the energy conversion efficiency and steam output accuracy of the high-temperature stage circulation system, ensures stable energy supply in the steam preparation stage, ensures smooth connection of the entire laundry room's tiered energy cycle, and further improves the overall energy utilization efficiency of the system.

[0080] To address the technical problems of poor compatibility between the cooling power of traditional air supply systems and the energy gradient of high and low temperature stage circulation systems, resulting in wasted or insufficient cooling capacity, the method of this application further includes the following steps: The difference between the final temperature and the water temperature is calculated as the intermediate temperature difference ΔTmid, where ΔTmid = Ts - Tw; Ts is the output temperature of the high-temperature stage circulation system, which is the final temperature, in °C; and Tw is the real-time water temperature of the hot water storage tank, in °C. ΔTmid directly reflects the actual energy gradient of the high and low temperature stage circulation system. The larger the difference, the higher the energy transfer efficiency of the high and low temperature stages and the smoother the energy flow of the system, and the cooling power can be appropriately increased. The smaller the difference, the less the energy gradient, such as the low-temperature stage water temperature not meeting the standard or the high-temperature stage heating up slowly. In this case, the cooling power needs to be reduced to prioritize energy transfer and avoid ineffective consumption of cooling capacity.

[0081] Using the previously defined temperature stability values: the temperature stability value T01 for the first temperature range (45℃-55℃) is 50℃ (first stability value), and the temperature stability value T02 for the second temperature range (120℃-150℃) is 135℃ (second stability value). The temperature difference ΔTrange is calculated as follows: ΔTrange = T02 - T01. Substituting the values, we get: ΔTrange = 135℃ - 50℃ = 85℃, which is a fixed reference value that characterizes the theoretical maximum energy gradient of the high and low temperature stage system design. ΔTrange serves as the reference threshold for the energy gradient, used to quantify the fit between the actual energy gradient and the design target, and to provide an objective reference standard for cooling power adjustment.

[0082] The system temperature ratio K is calculated using the following formula: K = ΔTmid / ΔTrange; The value range is K ∈ (0, 1.2]. Since ΔTmid does not exceed 150℃ - 45℃ = 105℃, the upper limit of K is 105 / 85 ≈ 1.235, and 1.2 is taken as the safety threshold. K represents the ratio of the actual energy gradient to the theoretical energy gradient. The larger K is, the closer the system energy state is to the design target, and the more urgent the cooling demand. For example, in high-temperature stage high-efficiency steam generation, the evaporator cooling capacity is sufficient, and the cooling power needs to be increased proportionally. The smaller K is, the smaller the system energy state is, the more it deviates from the design target. For example, in the chiller start-up stage and the low-temperature stage preheating stage, the cooling power needs to be reduced to ensure priority energy transfer and avoid energy conflicts between cooling capacity and hot water / steam generation.

[0083] The cooling power adjustment of the air supply system is based on the rated cooling power Qc0. The rated cooling power Qc0 is set based on the laundry room area and heat dissipation requirements. For example, 30kW is suitable for a 100㎡ laundry room operation area. The positive correlation adjustment formula is adopted: Qc=Qc0×K×k8; the adjustment coefficient k8∈[1.0,1.5], and the example value k8=1.2 is used to enhance the correlation between the cooling power and the system temperature ratio, taking into account both adjustment sensitivity and stability. Qc∈[0.5Qc0, 1.2Qc0], that is, the minimum cooling power is not less than 50% of the rated value, to ensure the basic cooling needs of the working environment and avoid the impact of excessive temperature on production; the maximum power does not exceed 120% of the rated value, to avoid energy waste caused by fan overload and excessive cooling capacity. If the ambient temperature in the laundry room is below 25℃ (the lower limit of the comfortable working temperature), the cooling power will be forcibly reduced to 0.5Qc0 regardless of the value of K; if the ambient temperature is above 32℃ (the upper limit of the comfortable working temperature), k8 will automatically increase to 1.5 to prioritize cooling.

[0084] The following is an example of cooling power adjustment based on the entire operating process of a laundry room: Operating Condition 1: Cold Start-up Stage (Tw=30℃, Ts=100℃): ΔTmid=100℃-30℃=70℃; K=70℃ / 85℃≈0.824; Qc=30kW×0.824×1.2≈29.67kW; Since the power limit was not triggered, the actual output power was 29.7kW, close to the rated value, utilizing the evaporator's cooling capacity during the cold start-up stage to quickly reduce the ambient temperature; Operating Condition 2: Low-Temperature Preheating Stage (Tw=40℃, Ts=120℃): ΔTmid=120℃-40℃=80℃; K=80℃ / 85℃≈0.941; Qc=30kW×0.941×1.2≈33.88kW; The upper limit is not exceeded, and the actual output is 33.9kW. The cooling power is moderately increased as the energy gradient increases. Operating Condition 3: Stable System Operation (Tw=50℃, Ts=135℃): ΔTmid=135℃-50℃=85℃; K=85℃ / 85℃=1.0; Qc=30kW×1.0×1.2=36kW; The power limit is reached, and the cooling capacity is output at full load. At this time, the energy gradient of the high and low temperature stages reaches the design target, the evaporator has the highest cooling efficiency, and the steam preparation and environmental cooling requirements are met simultaneously. Operating Condition 4: High-Temperature Load Fluctuation Stage (Tw=52℃, Ts=130℃): ΔTmid=130℃-52℃=78℃; K=78℃ / 85℃≈0.918; Qc=30kW×0.918×1.2≈33.05kW, actual output 33.1kW. The cooling power is appropriately reduced as the energy gradient decreases to ensure stable energy supply at the high-temperature stage. Operating Condition 5: Low Ambient Temperature Stage (Tw=50℃, Ts=135℃, Laundry Room Ambient Temperature 23℃): Forced output of 0.5Qc0=15kW to avoid excessive cooling and energy waste, while maintaining stable ambient temperature.

[0085] Closed-loop control process design: Data is collected synchronously using three types of sensors: a PT100 platinum resistance sensor for the hot water storage tank (Tw, accuracy ±0.2℃), a high-temperature K-type thermocouple sensor (Ts, accuracy ±0.3℃), and a laundry room ambient temperature sensor (Tenv, accuracy ±0.5℃), all with a sampling frequency of 1 time / 5 seconds. The system controller calculates ΔTmid and K in real time, and at the same time determines whether Tenv is within the comfort range (25℃-32℃). Calculate the target cooling power Qc based on K, and correct the power value using Tenv, such as increasing k8 when the temperature is too high and forcibly reducing the power when the temperature is too low. The centrifugal fan of the air supply system (model example: 4-72-11No.5A, rated power 5.5kW) is controlled by a frequency converter. The frequency adjustment range is 25-50Hz. The cooling power is linearly positively correlated with the frequency. For every 1Hz increase in frequency, the power increases by about 0.6kW. The adjustment response time is ≤0.3 seconds. When K∈[0.9, 1.1] and Tenv∈[25℃, 32℃], it enters a stable operating state, the cooling power is maintained at the current value, and the adjustment frequency is reduced to 1 time / 10 seconds to reduce energy consumption fluctuations.

[0086] In this embodiment, the fan is a variable frequency centrifugal fan, which features a wide high-efficiency range and low noise (≤75dB), suitable for the long-term continuous operation requirements of the laundry room. Its air volume adjustment range is 10000-20000m³ / h, and it is synchronously matched with the cooling power adjustment. The air duct of the air supply system is sealed to the cold air outlet of the shell-and-tube evaporator of the low-temperature circulation system, and the cooling capacity output of the evaporator is linked to the fan power. When the fan power is increased, the refrigerant flow rate of the evaporator is automatically increased through the electronic expansion valve (adjustment accuracy ±0.1L / min), ensuring that the cooling supply matches the fan air volume and avoiding local condensation or uneven cooling distribution. Fan overload protection (1.1 times the rated current) and evaporator condensation protection (when the evaporator surface temperature is ≤5℃, the fan power is reduced by 20%) are set to prevent equipment failure or cooling waste.

[0087] To address the technical problem that traditional single hot water storage tanks cannot adapt to the diurnal fluctuations and large flow differences in hot water demand in laundry rooms, this application achieves the switching between series and parallel modes and dynamic adjustment of the number of hot water storage tanks through the linkage of two parameters: hot water ratio and temperature distance ratio. The specific method also includes the following steps: The instantaneous hot water demand Qreq (unit: L / h) is collected in real time by a flow sensor (installed on the main inlet pipe of the water terminal, model example: LDG-50, measurement range 0-200L / min, accuracy ±1%) in the laundry room hot water system; at the same time, the current total water storage Qstor (unit: L) is obtained by a level sensor (measurement range 0-100%, accuracy ±1%) in the hot water storage tank. The total water storage is the sum of the water storage of all online hot water storage tanks. Example of rated volume of a single tank: 500L, number of tanks configured: 3-5, which can be expanded according to the size of the laundry room.

[0088] Hot water ratio calculation: The formula is as follows: λ=Qreq / Qstor; λ represents the matching relationship between real-time hot water demand and current heat storage capacity; the smaller λ is, the less the demand is than the energy storage, which is suitable for series mode, efficient buffering, and reduced heat dissipation; the larger λ is, the more the demand is close to or exceeds the energy storage, which is suitable for parallel mode, increasing water supply flow and fast response.

[0089] Two preset hot water range thresholds are set based on the actual water usage patterns of large laundry rooms, such as 100L / h washing volume during the morning peak, 50L / h during the off-peak, and 20L / h during the low-peak: The first hot water range (low flow demand): λ∈[0.3, 0.7], corresponding to off-peak to off-peak water use scenarios, such as the operation of a single washing machine; The second hot water range (high flow demand): λ∈(0.7, 1.5], corresponding to peak water usage scenarios, such as 2-3 washing machines operating simultaneously; Range description: The first hot water range value is smaller than the second hot water range value. The threshold can be manually calibrated by ±0.1 through the system controller to adapt to the different water requirements of washing different fabrics.

[0090] First duration (series mode delay): t1=30s. In series mode, the water flow path is long and the heat exchange is sufficient. A short delay can stabilize the water temperature (fluctuation ≤±0.5℃). Second duration (parallel mode delay): t2=60s. In parallel mode, the water flow is dispersed and requires a slightly longer mixing time to ensure that the water temperature of each tank is uniform and to avoid the mixed temperature not meeting the standard due to the low water temperature in some tanks. Delay logic: After the mode switch is completed, the controller triggers a delay timer. After the timer ends, the water supply valve is opened to ensure that the hot water temperature meets the washing process requirements (45℃-55℃).

[0091] Using the previously defined temperature distance ratio R=D2 / D1 (where D1 is the water temperature distance and D2 is the final temperature distance), it is positively correlated with the number of series and parallel connections. The larger R is, the greater the energy demand of the high-temperature stage, requiring an increase in the number of online water tanks to enhance heat storage capacity and ensure the supply of heat sources for the high-temperature stage. The smaller R is, the fewer the number of online water tanks can be (reducing ineffective energy storage losses).

[0092] Series mode (suitable for the first hot water range): Structural design: Multiple hot water storage tanks are connected in series via an electric three-way valve. That is, the outlet of the previous tank is connected to the inlet of the next tank through a pipe, and the outlet of the last tank is connected to the main hot water system pipe. A one-way valve is installed in the series path to prevent backflow of water.

[0093] Control process: When λ∈[0.3, 0.7], the system controller sends a series command to the electric three-way valves of each water tank, and the valves switch to the series channel (response time ≤ 0.5 seconds). The first delay time (30s) is triggered, during which the medium-temperature hot water (45℃-55℃) in the hot water storage tank flows slowly through the series path to fully mix evenly; After the delay ends, open the solenoid valve of the hot water system main pipe to supply hot water at a stable temperature to the water terminals; Key advantages: Long water flow path, relatively small heat dissipation area, and more than 20% improvement in heat storage efficiency, making it suitable for low-flow, long-term continuous water use scenarios and avoiding water temperature fluctuations caused by frequent start-stop.

[0094] Parallel connection mode (suitable for the second hot water range): Structural design: The inlets of multiple hot water storage tanks are connected in parallel to the outlet of the low-temperature circulation system through a manifold, and the outlets are collected and connected to the main hot water system pipe through a collector; each tank is equipped with an independent solenoid valve at its inlet and outlet for individual control.

[0095] Control process: When λ∈(0.7, 1.5], the controller sends a parallel command to the electric three-way valves of each water tank, the valves switch to the parallel channel, and at the same time open the inlet and outlet solenoid valves of all online water tanks; Trigger the second duration (60s) delay timer, during which hot water from each tank flows into the water collector synchronously and mixes, and the water temperature after mixing is monitored in real time by a temperature sensor (sampling frequency 1 time / 5 seconds). When the mixed water temperature stabilizes at 50℃±1℃, the delay timer ends early and the main solenoid valve is opened to supply water; if the water temperature still does not meet the standard after 60 seconds, the water tank with a water temperature deviation of more than ±2℃ is automatically closed, and only the water tank that meets the standard is supplied with water. The water supply flow rate is N times that of a single water tank (N is the number of parallel tanks). For example, when three 500L water tanks are connected in parallel, the maximum water supply flow rate can reach 150L / h, which can meet the high water demand during peak hours. The water supply response speed is 50% faster than that of the series mode.

[0096] Dynamic adjustment logic for the number of series and parallel connections: Set the basic number of online water tanks N0=2 (to accommodate off-peak water usage). Adjust the number N according to the temperature-distance ratio R, as follows: N=max{1,min{Nmax,N0+⌊R-1.0⌋}}; Nmax=5, the maximum number of tanks, which can be expanded according to the size of the laundry room; ⌊⋅⌋ is the floor function. Quantity constraints: N≥1 (at least 1 online water tank must be reserved), N≤Nmax (avoid energy waste caused by over-configuration); Threshold adaptation example: When R∈[0.8, 1.2] (energy supply and demand balance): N=2 (basic quantity); When R∈(1.2, 2.0] (high temperature level demand increases): N=3 (add 1 water tank); When R > 2.0 (high temperature and high load): N = 4 or 5 (maximum quantity, to increase heat storage capacity); When R < 0.8 (high temperature level, low load): N = 1 (reduce to the basic number to reduce heat dissipation loss).

[0097] Linked control of quantity adjustment and mode switching: Quantity adjustment in series mode: If λ∈[0.3, 0.7] and R>1.2, then increase the number of series connections, such as from 2 to 3, to extend the water flow path and further improve the heat storage efficiency; Quantity adjustment in parallel mode: If λ∈(0.7,1.5] and R>1.5, then increase the number of parallel connections, such as from 2 to 4, to simultaneously increase water supply flow and heat storage capacity; Adjustment priority: Quantity adjustment takes precedence over mode switching, ensuring that the number of online water tanks is adapted to the energy supply and demand status before the mode is determined, and avoiding supply and demand imbalance caused by insufficient quantity after mode switching.

[0098] Strategies for handling abnormal operating conditions: When the hot water ratio λ ∉ [0.3, 1.5] (exceeding the range of two types of hot water), exception handling is performed: Operating Condition 1: λ < 0.3 (Demand is too low, such as during nighttime low peak hours): Keep one hot water storage tank online for heat storage, close the inlet and outlet solenoid valves of other water tanks, drain the water stored in the cut-off water tank to avoid water quality deterioration caused by prolonged stagnation, and enter the heat preservation standby state. The heat preservation layer maintains the tank temperature ≥ 30℃, and the temperature rises rapidly when restarted. Operating Condition 2: λ > 1.5 (Excessive demand, such as a sudden start-up of multiple devices): Immediately switch all configured water tanks to parallel mode (N=Nmax) to maximize water supply flow; A rapid acceleration command is sent to the low-temperature stage circulation system to increase the low-temperature stage power to 1.2 times the rated power, thereby accelerating the preparation of hot water. If the water supply flow still cannot meet the demand, the hot water system priority mechanism is triggered; the power of the high-temperature circulation system is temporarily reduced (to 0.8 times the rated value) to prioritize the supply of hot water, and the power balance is restored after the demand is relieved. Abnormal recovery: When λ returns to the normal range, the cut-off water tank will be automatically restarted, adjusted to the target quantity according to the temperature-distance ratio, and switched back to the corresponding mode.

[0099] Equipment configuration and closed-loop control process: Each water tank is equipped with two electric three-way valves (model example: VQ947F-16C, nominal diameter DN50, electric actuator response time ≤0.5 seconds) and one solenoid valve (model example: 2W-400-40, nominal diameter DN40) to achieve series-parallel switching and independent control; in addition to flow, level and temperature sensors, each water tank outlet is equipped with a water temperature sensor (PT1000, accuracy ±0.1℃) to monitor the outlet water temperature of a single tank in real time; the controller adopts a PLC controller (model example: S7-1200), which integrates series-parallel switching logic, quantity adjustment algorithm and abnormal handling program, and supports linkage communication with high and low temperature circulation systems (Modbus-RTU protocol).

[0100] Data acquisition: Real-time acquisition of parameters such as Qreq, Qstor, Tw, and Ts; calculation of λ and R. Mode decision: Determine the series-parallel mode based on λ and send valve switching commands; Quantity adjustment: Calculate the target quantity N based on R, and control the switching off or restarting of excess water tanks; Delayed water supply: Triggers the corresponding delay duration and monitors the water temperature stability. Stable supply: Water supply will resume after the delay ends, with real-time feedback on water demand and temperature data, and dynamic adjustments will be made accordingly; Anomaly Handling: If λ exceeds the range, execute the abnormal operating condition strategy until normal operation is restored.

[0101] To address the technical pain points of insufficient steam supply (ironing interruption) or ineffective energy consumption (steam waste) caused by the fixed output duration of the steam system, the method of this application also includes the following steps: Maximum value of the second temperature range: The second temperature range (120℃-150℃) set previously will be used, with its maximum value T. 2，max =150℃, the highest rated temperature for steam preparation, corresponding to the high-temperature requirements of ironing processes, such as shaping thick fabrics; Final duration (tact): refers to the continuous duration (in seconds) during which the output temperature (final temperature Ts) of the high-temperature circulating system reaches 150℃. It must meet the "continuous compliance" judgment standard; the temperature fluctuation during this period should be ≤±1℃. If the fluctuation exceeds ±2℃, the timing should be restarted. Preset reference duration tref: Based on the mainstream ironing process in the laundry room, such as the basic steam supply duration for ironing a single batch of fabrics, the value range is 20s-60s, the example setting is tref=30s, which is suitable for the continuous steam supply requirements of regular clothing ironing. Maximum output time tmax: Set to 1.5-2.0 times the reference time. The example value is tmax=45s. This avoids energy waste caused by excessive steam output, while meeting the needs of long-term ironing. Baseline output duration tbase: Set to 50%-70% of the reference duration. Example value tbase=15s, to ensure basic steam supply needs and avoid ironing interruptions due to insufficient ironing time.

[0102] The duration ratio μ is the ratio of the final duration to the reference duration, and the formula is as follows: μ = tact / tref; Value range: μ∈(0,+∞). In actual engineering, due to the upper limit of the temperature reaching standard time, the longest tact when the high temperature level is running continuously at full load is 120s, so μ≤4.0; μ represents the energy supply stability of the high temperature level circulation system; the closer μ is to 1, the higher the matching degree between the energy supply capacity and the reference demand; when μ<1, the energy supply stability is insufficient, the temperature reaching standard time does not meet the reference standard, and the output time needs to be adjusted according to the ratio; when μ≥1, the energy supply is stable, and the maximum output time can be used to ensure continuous ironing.

[0103] Dynamic adjustment logic for steam output duration: The duration of steam output by the steam system in a single cycle, tout, is adjusted using a positive correlation algorithm. The core formula is as follows: when tact < tref, tout = tbase + (μ × k9) × (tref - tbase); when tact ≥ tref, tout = tmax. Key parameter settings: The adjustment coefficient k9 ∈ [0.8, 1.2] (example value k9 = 1.0) balances the adjustment sensitivity and stability; Boundary constraints: tout ≥ tbase (minimum output time 15s, ensuring basic ironing needs), tout ≤ tmax (maximum output time 45s, avoiding steam waste); Formula logic explanation: When tact < tref, the output duration increases positively with μ; the smaller μ is (the less stable the energy supply), the closer the output duration is to the reference value (controlling energy consumption); the closer μ is to 1 (the energy supply is close to stable), the closer the output duration is to the reference duration (ensuring continuous steam supply); when tact ≥ tref, the high-temperature stage energy supply is stable, and the output duration is locked at the maximum value (45s) to meet the needs of continuous ironing or high-load steam supply.

[0104] Full-condition adjustment example and logic adaptation: Based on the high-temperature operating process, specific adjustment examples are as follows: Operating Condition 1: Unstable power supply (tact=10s<tref=30s): μ=10 / 30≈0.333; tout=15s+(0.333×1.0)×(30-15)s≈15s+5s=20s. The output time is 20s, which is between the benchmark and reference time. This ensures basic ironing needs while avoiding a sudden drop in steam pressure due to insufficient power supply. Operating Condition 2: Power supply is close to stable (tact=25s<tref=30s): μ=25 / 30≈0.833; tout=15s+(0.833×1.0)×15s≈15s+12.5s=27.5s. The output duration is 27.5s (close to the reference duration), gradually adapting to the stable steam supply demand and reducing the risk of ironing interruption. Operating Condition 3: Power supply is completely stable (tact=35s≥tref=30s): The output duration is directly locked at tmax=45s, which meets the needs of multiple batches of continuous ironing or long-term shaping of thick fabrics. The steam pressure is stable at 0.4-0.6MPa (rated ironing pressure). Operating Condition 4: Ultra-stable power supply (tact=60s≥tref=30s): Still maintains tmax=60s, meeting the long-term ironing needs of heavy fabrics and avoiding the waste of "sufficient power supply but limited output". Example of storage tank volume: 50L, heat preservation coefficient ≤0.03W / (m·K).

[0105] Correction mechanism for special operating conditions: Temperature fluctuation correction: If Ts fluctuates by ±1.5℃ once during the final duration statistics period, and does not reach the re-timing threshold, the duration ratio μ is multiplied by the correction factor 0.9, and the output duration is adjusted accordingly. For example, if the original calculation is 27.5s, the corrected duration is 24.75s, to avoid the decline in steam quality due to insufficient power supply stability. Ironing requirement adjustment: If the laundry room selects the "Quick Ironing" mode (single batch ironing time ≤ 15s) through the human-computer interaction interface, the output time will be forcibly set to tbase=15s regardless of the value of tact; if the "Deep Ironing" mode (single batch ≥ 45s) is selected, tmax will be temporarily increased to 60s to adapt to the process requirements. Fault warning correction: If tact < 5s (power supply is seriously unstable), the output duration is set to tbase = 15s, and a warning signal is sent to the system controller to check for faults in the high-temperature circulating system (such as insufficient compressor pressure or condenser scaling).

[0106] Control process and equipment configuration details: Data acquisition and duration statistics: The K-type thermocouple sensor (accuracy ±0.3℃) at the high-temperature output end acquires Ts in real time (acquisition frequency 1 time / 1s). The built-in timer of the system synchronously counts the continuous duration of Ts ≥ 150℃ and fluctuation ≤ ±1℃, i.e., tact. Ratio calculation and operating condition determination: Calculate μ=tact / tref in real time, determine the relationship between tact and tref, and determine the adjustment mode (positive correlation adjustment / maximum duration lock). Output duration decision: Calculate the target output duration tout according to the adjustment formula, and optimize the value by combining the special working condition correction mechanism to ensure that it is within the range of [15s, 45s]. Execution and Feedback: The controller sends a command to the electric regulating valve of the steam system (model example: ZDLP-16C, nominal diameter DN25, regulating accuracy ±1%) to control the valve opening time totout; at the same time, the output is monitored in real time by the steam flow sensor (measurement range 0-50kg / h, accuracy ±0.5kg / h). If the flow deviation exceeds ±10%, the time ratio will be corrected in the next adjustment. If the flow is insufficient, μ will be multiplied by 1.1. Loop optimization: After each steam output is completed, i.e., one ironing batch, the tact is re-counted and the tout is dynamically updated to achieve closed-loop optimization.

[0107] Timer module: Integrated into the PLC controller (model example: S7-1200), with a timing accuracy of ±0.1s, supporting time reset, pause, and cumulative statistics functions, and synchronized with temperature acquisition; Actuator: The steam electric regulating valve adopts electronic control with a response time of ≤0.2s. The opening degree is linearly related to the output duration. For example, a duration of 20s corresponds to a fully open valve for 20s, ensuring uniform steam output. Buffering and protection equipment: The steam system is equipped with a 50L insulated storage tank to buffer excess steam under stable operating conditions. A pressure sensor (measuring range 0-1.0MPa, accuracy ±0.02MPa) is installed at the tank outlet. When the pressure exceeds 0.7MPa, the regulating valve will be automatically closed to avoid the risk of overpressure. Communication linkage: The steam system controller and the high-temperature stage circulation system controller communicate via the Modbus-RTU protocol. When tact < 10s, the high-temperature stage automatically increases the power by 10% (not exceeding 1.1 times the rated power) to help Ts quickly and stably reach the standard.

[0108] This application also discloses an energy consumption control system for a large laundry room's circulation system, including a processor, wherein the processor executes the steps of the energy consumption control method for a large laundry room's circulation system as described in any of the above embodiments.

[0109] This application also discloses a storage medium storing a program that, when executed by a processor, implements the steps of the energy consumption control method for the circulation system of a large laundry room as described above.

[0110] Although embodiments of this application have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting this application. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of this application.

Claims

1. A method of controlling energy consumption of a circulation system of a large laundry room, characterized by, Includes the following steps: A series of low-temperature and high-temperature circulation systems are constructed using a heat pump system based on reverse Carnot cascade. The low-temperature circulation system takes the ambient heat source as input and its output temperature is within a preset first temperature range. The low-temperature circulation system has an evaporator connected to an air supply system to provide cooling capacity to the air supply system. A hot water storage tank is installed at the midpoint between the low-temperature circulation system and the high-temperature circulation system. The output of the low-temperature circulation system is connected to the hot water storage tank. The hot water storage tank is connected to a hot water system to provide hot water to the hot water system. The input of the high-temperature circulating system is connected to the hot water storage tank. The output temperature of the high-temperature circulating system is located in a preset second temperature range, wherein the value in the first temperature range is less than the value in the second temperature range. The high-temperature circulating system is equipped with a condenser, which is connected to a steam system and provides steam to the steam system. The system acquires the water temperature in the hot water storage tank in real time, calculates the temperature distance between the water temperature and a first temperature range based on a preset temperature distance algorithm, and adjusts the output cooling capacity according to the water temperature distance with a positive correlation using a first coefficient; it also adjusts the output hot water volume according to the water temperature distance with a negative correlation using a second coefficient, where the first coefficient is less than the second coefficient. The system also acquires the output temperature of the high-temperature circulation system in real time as the final temperature value, calculates the temperature distance between the final temperature value and a second temperature range based on a preset temperature distance algorithm, and adjusts the steam volume according to the final temperature distance with a negative correlation using a third coefficient, where the third coefficient is greater than the second coefficient.

2. The method of claim 1, wherein the method further comprises: The temperature-distance algorithm includes the following steps: The temperature distance algorithm takes temperature value and temperature range as input. Based on the preset rated operating conditions, the sum of the durations corresponding to the values ​​within the preset acquisition time is calculated as the stable duration, and the value with the longest stable duration is obtained as the stable temperature value. The temperature distance is calculated as the difference between the temperature value and the stable temperature value.

3. The method of claim 1, wherein the method further comprises: The method also includes the following steps: The ratio of the final temperature distance to the water temperature distance is calculated as the temperature distance ratio. The water storage capacity or volume of the hot water storage tank is adjusted according to the positive correlation of the temperature distance ratio. If the water storage capacity of the hot water storage tank is to be adjusted, a water pump connected to the hot water storage tank is installed. The water pump is connected to a water storage tank and the water pump is controlled to pump water into or out of the hot water storage tank. If the volume of the hot water storage tank is adjusted, the hot water storage tank is filled with water and is equipped with a drive component and a piston. Controlling the length of the drive component can drive the piston to move, thereby changing the volume of water that can be contained. The piston is equipped with an electric valve. When the piston moves, the electric valve opens, and when the piston stops, the electric valve closes.

4. The method of claim 2, wherein the method further comprises: The method also includes the following steps: The ratio of the final temperature distance to the water temperature distance is calculated as the temperature distance ratio. The power control of the low-temperature stage circulation system is adjusted based on the negative correlation of the temperature distance ratio. The ratio of the calculated water temperature value to the maximum value in the first temperature range is called the first water temperature ratio. The power control step size of the low-temperature stage circulation system is adjusted according to the first water temperature ratio.

5. The energy consumption control method for the circulation system of a large laundry room according to claim 2, characterized in that, The method also includes the following steps: The ratio of the final temperature distance to the water temperature distance is calculated as the temperature distance ratio. The power control of the high-temperature stage circulation system is adjusted according to the positive correlation of the temperature distance ratio. The ratio of the final temperature value to the maximum value in the second temperature range is calculated as the second water temperature ratio. The power control step size of the high-temperature stage circulation system is adjusted according to the positive correlation of the second water temperature ratio.

6. The method of claim 2, wherein the method further comprises: The method also includes the following steps: The difference between the final temperature and the water temperature is calculated as the intermediate temperature difference. Calculate the temperature stability value for the first temperature range as the first stable value, calculate the temperature stability value for the second temperature range as the second stable value, and calculate the difference between the second stable value and the first stable value as the range temperature difference. The ratio of the intermediate temperature difference to the range temperature difference is calculated as the system temperature ratio. The cooling power of the air supply system is adjusted according to the positive correlation of the system temperature ratio.

7. The method of claim 3, wherein the method further comprises: determining whether the laundry machine is in a standby mode; and if the laundry machine is in the standby mode, controlling the circulation system to be in the standby mode. The method also includes the following steps: Obtain the required amount of hot water and calculate the ratio of the hot water volume to the water storage capacity of the hot water tank as the hot water ratio. If the hot water ratio is within the preset first hot water range, then control multiple hot water storage tanks to be connected in series and provide hot water after a preset first time delay; If the hot water ratio is within the preset second hot water range, then control multiple hot water storage tanks to be connected in parallel and provide hot water after a preset second delay; Among them, the value in the first hot water range is less than the value in the second hot water range, and the first duration is shorter than the second duration; The ratio of the final temperature distance to the water temperature distance is calculated as the temperature distance ratio. The number of hot water storage tanks connected in series or in parallel is adjusted according to the positive correlation of the temperature distance ratio. If the hot water ratios are all outside the first and second hot water ranges, then one hot water storage tank will be reserved for storing hot water, and the other hot water storage tanks will be shut down.

8. The energy consumption control method for the circulation system of a large laundry room according to claim 2, characterized in that, The method also includes the following steps: The final duration is the time it takes for the final temperature value to reach the maximum value in the second temperature range. If the final duration is less than the preset reference duration, the ratio of the final duration to the reference duration is calculated as the duration ratio. The steam output duration of a single steam output by the steam system is adjusted according to the positive correlation of the duration ratio. Otherwise, the steam output duration is controlled to the preset maximum output duration.

9. An energy consumption control system for a large laundry room's circulating system, characterized in that, Includes a processor, wherein the steps of the energy consumption control method for the circulation system of a large laundry as described in any one of claims 1-8 are executed.

10. A storage medium, characterized in that, The storage medium stores a program that, when executed by a processor, implements the steps of the energy consumption control method for the circulation system of a large laundry room as described in any one of claims 1-8.

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