Integrated Cooling Supply Method and Device for Building Air Conditioning Based on High-Density New Media

Abstract

The present invention relates to an integrated cooling method and device for building air conditioners based on a high-density new medium. Among them, the method includes: obtaining environmental and building cooling demand data, calculating the cooling load per unit area and electricity price period data, correcting the cooling load according to the building type, reserving 10%-15% cooling capacity redundancy, determining the target cold storage density, and obtaining the preliminary design parameters of the cold plate; encapsulating the new phase change medium into the cold plate and calculating the arrangement and stacking conditions; building a three-zone series structure of the cold storage tank, placing the cold plate in the middle, and setting fluid channels on both sides and coupling them. Based on the heat transfer characteristics, set the heat exchange parameters of 4°C inlet water and the new phase change medium at 4-7°C; during the valley and flat periods of the electricity price, heat exchange the 4°C water through the cold storage tank and output 7-8°C chilled water; activate the cold release during the peak period, stop the refrigeration system, and continuously supply cooling by reverse heat exchange to achieve efficient and low-cost cold storage supply, solve the limitations of traditional cold storage technologies, and maximize building energy conservation and economic benefits.

Description

Technical Field

[0001] The present invention relates to the technical field of building energy conservation, and particularly to an integrated cooling supply method and device for building air conditioners based on a high-density new medium. Background Art

[0002] Energy utilization and building energy conservation are important fields for sustainable development in today's society. The core lies in how to efficiently utilize resources, reduce energy consumption, and maximize economic benefits. However, existing cold storage technologies face significant limitations in practical applications. Water cold storage relies on sensible heat storage, with a low cold storage density, resulting in a large cold storage space requirement, high construction and maintenance costs; although ice cold storage improves the cold storage density through latent heat of phase change, the refrigeration temperature drops significantly, and the energy efficiency decreases significantly. At the same time, the complex system design and the use of corrosive media further increase the initial investment and later maintenance burden. These defects jointly point to a practical problem: traditional cold storage technologies cannot technically achieve efficient and low-cost cold storage and supply.

[0003] The limitations of existing methods are mainly reflected in the contradiction between the operation mode and energy efficiency. Both water cold storage and ice cold storage need to separate cold storage and cold release operations, and cannot achieve simultaneous cold storage and supply, which not only increases the energy consumption of the secondary pump but also reduces the overall flexibility of the system. In addition, the energy efficiency of ice cold storage decreases due to low-temperature refrigeration, while water cold storage is limited by low cold storage density and is difficult to meet the cold demand of large-scale buildings. This technical disconnection directly affects the achievement of energy conservation goals. Summary of the Invention

[0004] The main object of the present invention is to provide an integrated cooling supply method and device for building air conditioners based on a high-density new medium, so as to achieve efficient and low-cost cold storage and supply, solve the limitations of traditional cold storage technologies, and achieve the goals of building energy conservation and maximum economic benefits.

[0005] To achieve the above object, the present invention provides an integrated cooling supply method for building air conditioners based on a high-density new medium, including the following steps:

[0006] Obtain environmental data and building cold demand data, calculate the cold load per unit area data and electricity price period distribution data, correct the cold load calculation value based on the building type, and reserve 10%-15% cold redundancy to determine the target cold storage density and refrigeration temperature range, and obtain the preliminary design parameters for cold plate encapsulation;

[0007] Encapsulate a new phase change medium with a density greater than that of ice cold storage into cold plates of a preset geometric shape, and calculate the cold plate arrangement and stacking quantity based on the preliminary design parameters;

[0008] Construct a three-zone series structure for the cold storage tank, with the middle cold storage zone accommodating stacked cold plates and fluid channels arranged in the heat exchange zones on both sides. The cold storage zone and the heat exchange zone are thermodynamically coupled through a preset partition ratio;

[0009] Based on the heat transfer characteristics of the three-zone series structure, set the heat exchange temperature parameters between the inlet water temperature of 4°C and the new phase change medium of 4 - 7°C;

[0010] During the valley and flat periods of the electricity price, perform coordinated cold storage and cooling operations, so that the 4°C inlet water exchanges heat with the new phase change medium with a temperature difference of 4 - 7°C when flowing through the cold storage tank, and output 7 - 8°C chilled water to the air-conditioning terminal;

[0011] During the peak period of the electricity price, activate the cold release mode of the cold storage tank, stop the operation of the refrigeration system, and continuously output 7 - 8°C chilled water to maintain cooling through the reverse heat exchange of the new phase change medium.

[0012] Further, the steps of obtaining environmental data and building cooling demand data, calculating the cooling load per unit area data and electricity price period distribution data, correcting the calculated value of the cooling load based on the building type, and reserving 10% - 15% cooling redundancy to determine the target cold storage density and refrigeration temperature range to obtain the preliminary design parameters of the cold plate packaging include:

[0013] Real-time collect outdoor temperature and humidity, solar radiation intensity environmental data through the building energy consumption monitoring system, and calculate the basic cooling load in combination with the thermal parameters of the building envelope structure;

[0014] Based on the time-of-use electricity price data, divide the peak-valley-flat periods, map the basic cooling load to the cooling demand in each period, and generate a dynamic load distribution curve;

[0015] According to the building type coefficient, correct the dynamic load distribution curve, determine the target cold storage density of the peak cooling load that needs to cover the peak period of the electricity price, and reserve 10% - 15% cooling redundancy;

[0016] Combined with the phase change characteristics of the phase change medium, calculate the cold storage capacity and heat exchange area of a single cold plate, and output the preliminary design parameters including the cold plate thickness and arrangement spacing.

[0017] Further, the steps of encapsulating the new phase change medium with a density greater than the ice cold storage density into a cold plate with a preset geometric shape and calculating the cold plate arrangement method and stacking quantity based on the preliminary design parameters include:

[0018] Encapsulate the high-density new phase change medium into a cold plate with a square honeycomb structure or a circular tube bundle structure with internal flow channels;

[0019] The density of the novel phase change medium is not less than 1000 kg / m³, the latent heat of phase change value is greater than 200 kJ / kg, and the phase change temperature range is from 4.5 ± 0.5 °C to 6.5 ± 0.5 °C;

[0020] Based on the target cold storage density requirement in the preliminary design parameters, calculate the matching relationship between the number of cold plate stacks and the interlayer diversion gap, and control the stacking spacing within the range of 5 - 10 cm.

[0021] Further, the steps of constructing the three - zone series structure of the cold storage tank, with the middle cold storage area accommodating the stacked cold plates and the fluid channels arranged in the two - side heat exchange areas, include:

[0022] Set up a cold storage tank with a three - zone series structure, set up a stacked cold plate array arranged longitudinally in the middle cold storage area, and configure tapered fluid channels in the two - side heat exchange areas;

[0023] The fluid channel layout of the three - zone series structure of the cold tank is adapted to the cross - sectional shape of the flow channels of the cold plates;

[0024] The fluid channels adopt a tapered channel design with a wide inlet and a narrow outlet, the cross - sectional area ratio of the inlet to the outlet is 1.2:1 to 1.5:1, and there are diversion fins with an inclination angle of 30° - 45° between adjacent cold plates;

[0025] Set the volume ratio of the cold storage area to the single - side heat exchange area to be 3:1 to 2:1, and the volume distribution ratio between the cold storage area and the heat exchange area is dynamically adjusted according to the cold plate stacking density and the heat exchange rate of the phase change medium.

[0026] Further, the steps of setting the heat exchange temperature parameters of the inlet water temperature of 4 °C and the novel phase change medium of 4 - 7 °C include:

[0027] Real - time monitor the difference between the temperature of the novel phase change medium and the inlet water temperature. When the medium temperature reaches the set threshold value, automatically adjust the inlet water flow rate to strengthen heat exchange and maintain an effective heat exchange temperature range of 4 - 7 °C.

[0028] Further, the steps of performing the coordinated operation of cold storage and cooling during the off - peak and flat - rate electricity periods include:

[0029] Start the cold storage mode during the off - peak electricity period, control 70% - 80% of the 4 °C inlet water flow rate to flow through the cold storage tank for cold storage, and the remaining water flow rate directly bypasses to the outlet end for mixing;

[0030] Switch to the cooling - priority mode during the flat - rate electricity period, adjust 30% - 50% of the inlet water flow rate to release cold through the cold storage tank to supplement the cooling capacity of the refrigeration host;

[0031] Real - time monitor the outlet water temperature. When the water temperature deviates from the range of 7 - 8 °C, perform temperature stability control by dynamically adjusting the water flow rate ratio between the cold storage tank and the bypass pipeline;

[0032] During the off-peak and flat-rate periods of electricity price, the outlet water temperature is monitored in real time, and the cooling load is adjusted through the flow distribution of the cold storage tank to keep the outlet water temperature stable within the target range of 7-8°C.

[0033] Further, the step of activating the cold quantity release mode of the cold storage tank during the peak period of electricity price includes:

[0034] When the peak period of electricity price starts, switch the inlet and outlet directions of the cold storage tank and control the cold release rate, so that the cold quantity release duration covers at least 80% of the peak period duration of electricity price;

[0035] Adjust the cold release intensity in real time according to the cold quantity demand at the air-conditioning terminal until the temperature of the new phase change medium rises back to the critical value of 7°C.

[0036] The present invention also provides an integrated building air-conditioning cooling device based on a high-density new medium, including:

[0037] A data processing module, which is used to obtain environmental data and building cooling demand data, calculate the cooling load data per unit area and the electricity price period distribution data, correct the calculated value of the cooling load based on the building type, reserve 10%-15% of the cooling capacity redundancy, determine the target cold storage density and the refrigeration temperature range, and obtain the preliminary design parameters for cold plate encapsulation;

[0038] A cold plate design module, which is used to encapsulate a new phase change medium with a density greater than the ice storage density into a cold plate with a preset geometric shape, and calculate the cold plate arrangement method and stacking quantity based on the preliminary design parameters;

[0039] A cold storage tank design module, which is used to construct a three-zone series structure of the cold storage tank, with the middle cold storage area accommodating the stacked cold plates and fluid channels arranged in the two side heat exchange areas;

[0040] A parameter calculation module, which is used to set the heat exchange temperature parameters of the inlet water temperature of 4°C and the new phase change medium of 4-7°C based on the heat transfer characteristics of the three-zone series structure;

[0041] A cold storage and supply coordination module, which is used to perform cold storage and supply coordination operations during the off-peak and flat-rate periods of electricity price, so that the 4°C inlet water exchanges heat with the new phase change medium with a temperature difference of 4-7°C when flowing through the cold storage tank, and outputs 7-8°C cold water to the air-conditioning terminal;

[0042] A peak period cold release module, which is used to activate the cold quantity release mode of the cold storage tank during the peak period of electricity price, stop the operation of the refrigeration system, and continuously output 7-8°C cold water to maintain cooling through the reverse heat exchange of the new phase change medium.

[0043] The present invention also provides a computer device, including a memory and a processor. A computer program is stored in the memory, and when the processor executes the computer program, the steps of the above-mentioned integrated cooling method for building air conditioners based on high-density new media are implemented.

[0044] The present invention also provides a computer-readable storage medium, on which a computer program is stored. When the computer program is executed by a processor, the steps of the above-mentioned integrated cooling method for building air conditioners based on high-density new media are implemented.

[0045] The integrated cooling method and device for building air conditioners based on high-density new media provided by the present invention have the following beneficial effects: In terms of cold storage performance, the present invention adopts a new phase change medium with a density greater than that of ice cold storage, greatly improving the cold storage density. Compared with water cold storage, it reduces the demand for cold storage space, lowers the construction and maintenance costs, and at the same time overcomes the problem of reduced energy efficiency caused by low-temperature refrigeration in ice cold storage. At the same time, by performing coordinated operations of cold storage and cooling during the valley and flat periods of electricity prices, the limitation of the separate operation of cold storage and cold release in traditional cold storage technologies is broken, reducing the energy consumption of secondary pumps, enhancing the flexibility of the system, and better meeting the cold demand of large-scale buildings. In addition, by constructing a cold storage tank with a three-zone series structure, optimizing the layout of fluid channels, combining precise setting of heat exchange temperature parameters and intelligent flow regulation, the cold output is accurately controlled, maintaining a stable water supply temperature of 7 - 8°C at the air conditioner terminal, improving the cooling quality, and effectively contributing to the realization of the building energy-saving goal. Description of the Drawings

[0046] Figure 1 is a schematic flowchart of an integrated cooling method for building air conditioners based on high-density new media in an embodiment of the present invention;

[0047] Figure 2 is a structural block diagram of an integrated cooling device for building air conditioners based on high-density new media in an embodiment of the present invention;

[0048] Figure 3 is a schematic structural block diagram of a computer device in an embodiment of the present invention.

[0049] The realization, functional characteristics, and advantages of the object of the present invention will be further described with reference to the embodiments and the accompanying drawings. Detailed Embodiments

[0050] In order to make the object, technical solution, and advantages of the present invention clearer, the present invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not used to limit the present invention.

[0051] Refer to Figure 1, which is a schematic flow chart of an integrated cooling supply method for building air conditioners based on a high-density new medium, includes the following steps:

[0052] S1. Obtain environmental data and building cooling demand data. By calculating the cooling load data per unit area and the electricity price time period distribution data, correct the calculated cooling load value based on the building type, and reserve 10%-15% cooling redundancy to determine the target cold storage density and the refrigeration temperature range, so as to obtain the preliminary design parameters of the cold plate encapsulation.

[0053] S2. Encapsulate a new phase change medium with a density greater than the ice cold storage density into a cold plate with a preset geometric shape, and calculate the cold plate arrangement method and the stacking quantity based on the preliminary design parameters.

[0054] S3. Construct a three-zone series structure of the cold storage tank. The middle cold storage zone accommodates the stacked cold plates, and fluid channels are arranged in the two side heat exchange zones. The cold storage zone and the heat exchange zone are thermodynamically coupled through a preset partition ratio.

[0055] S4. Based on the heat transfer characteristics of the three-zone series structure, set the heat exchange temperature parameters of the inlet water temperature of 4°C and the new phase change medium of 4-7°C.

[0056] S5. Execute the coordinated operation of cold storage and cooling supply during the valley and flat periods of the electricity price, so that the 4°C inlet water exchanges heat with the new phase change medium with a temperature difference of 4-7°C when flowing through the cold storage tank, and outputs 7-8°C cold water to the air conditioner terminal.

[0057] S6. Activate the cold quantity release mode of the cold storage tank during the peak period of the electricity price, stop the operation of the refrigeration system, and continuously output 7-8°C cold water to maintain the cooling supply through the reverse heat exchange of the new phase change medium.

[0058] As described in the above step S1, parameters such as outdoor temperature and humidity, solar radiation intensity, and wind speed are collected in real time by sensors, and the future cooling load demand is predicted by combining historical meteorological data. Based on the cooling load calculation standards for building types (such as office buildings and shopping malls), a dynamic cooling load model is established by combining the thermal parameters of the building envelope (heat transfer coefficient U value, thermal inertia index D value), indoor personnel density, equipment heat generation, etc. The time-of-use electricity price data of the power grid (peak period, valley period, flat period) is superimposed on the time series of the cooling load demand to generate a chilled water storage target curve that needs to cover the peak period of the electricity price. A correction factor (1.0 - 1.5) is introduced according to the building function characteristics (such as large fluctuations in the flow of people in shopping malls and stable heat generation of equipment in data centers) to adjust the basic cooling load value. A 10% - 15% redundancy is added to the corrected peak cooling load to cope with extreme weather or load mutations. According to the chilled water storage density (≥3.5 RT / m³) is calculated based on the redundant cooling load demand and the physical properties of the new phase change medium (latent heat of phase change, density). Based on the requirements of chilled water storage density and heat transfer efficiency, the thickness of the cold plate (10 - 15 cm), the arrangement spacing (5 - 10 cm), and the cross-sectional area of the flow channel are determined.

[0059] As described in the above step S2, a high-density composite phase change material is used as the phase change medium, with a density ≥1000 kg / m³, a latent heat of phase change >200 kJ / kg, and the phase change temperature is precisely controlled within the range of 4.5 ± 0.5°C to 6.5 ± 0.5°C, which matches the temperature difference (4°C - 12°C) between the supply and return water of the air conditioning system. The phase change medium is encapsulated into a square honeycomb structure or a circular tube bundle structure with internal flow channels, and the flow channel diameter is 3 - 5 mm. The uniformity of the flow channels is ensured through the injection molding process, increasing the heat transfer area and reducing the flow resistance. According to the thickness and spacing of the cold plates in the preliminary design parameters of S1, the longitudinal staggered stacking or transverse parallel arrangement method is adopted, and the CFD simulation is combined to optimize the flow field distribution. A 5 - 10 cm diversion gap is set between layers, and diversion fins with an inclination angle of 30° - 45° are added to the surface of the cold plate to enhance turbulent heat transfer. Among them, the density of the phase change medium ≥1000 kg / m³, and this density value is based on the formulation design of the new composite phase change material. By compounding a paraffin-based phase change material with high-density metal oxides (such as alumina, zinc oxide) and adding carbon nanotubes to enhance the structural stability, the material density is increased to more than 1000 kg / m³; the latent heat of phase change >200 kJ / kg, and by optimizing the ratio of the phase change material (such as the eutectic ratio of paraffin and fatty acid) and the doping amount of nano-additives (such as graphene), the latent heat value of the phase change material is increased; the phase change temperature range of 4.5°C - 6.5°C is selected to utilize the 4°C chilled water temperature of the air conditioning host during the valley period and flat period for efficient chilled water storage, while avoiding the low-temperature refrigeration (-3°C to -9°C) required for ice chilled water storage, thereby reducing the energy consumption loss of the refrigeration machine.

[0060] As described in step S3 above, a three-zone series-connected cold storage tank is constructed. The middle zone is the cold storage area, which accommodates a cold plate stacking array with a volume ratio of 60%-70%. The cold plates are arranged longitudinally to adapt to the water flow direction. The two side zones are heat exchange areas with tapered fluid channels, where the inlet cross-sectional area is larger than the outlet (ratio 1.2:1 - 1.5:1), and the heat exchange efficiency is enhanced through the change in flow velocity gradient (0.3m / s → 0.8m / s). A high thermal conductivity alloy partition (thermal conductivity > 200W / m·K) is set between the cold storage area and the heat exchange area, and the surface is coated with a graphene coating (thermal conductivity > 500W / m·K) to ensure rapid heat transfer to the cold plates. According to the heat exchange rate of the phase change medium (fed back by temperature sensors), the volume distribution ratio between the cold storage area and the heat exchange area (3:1 - 2:1) is adjusted in real time to maintain the overall heat exchange efficiency.

[0061] As described in step S4 above, the allowable temperature difference range between the new phase change medium and the inlet water temperature is set to 2°C - 3°C (inlet water temperature of 4°C and medium temperature of 4.5°C - 7°C). ΔT is monitored in real time through temperature sensors. When ΔT < 2°C, the water pump flow rate is increased to 120% of the design value; when ΔT > 3°C, the flow rate is reduced to 80% to ensure an effective heat exchange temperature zone.

[0062] As described in step S5 above, a dual-mode operation strategy is set. In the valley-section cold storage mode, during the valley-section of electricity price (such as 0:00 - 6:00), 70% - 80% of the 4°C cold water flow rate is controlled to flow through the cold storage tank for cold storage, and the remaining flow rate is directly transported to the end through a bypass pipeline. After mixing, the outlet water temperature is stabilized at 7 - 8°C. In the flat-section cooling priority mode, during the flat-section of electricity price (such as 6:00 - 10:00), 30% - 50% of the flow rate is adjusted to flow through the cold storage tank to release cold, supplementing the cooling capacity of the refrigeration host and reducing the host load. Through the feedback signal of the end temperature sensor, the water volume distribution ratio between the cold storage tank and the bypass pipeline is dynamically adjusted (PID control algorithm) to ensure that the outlet water temperature fluctuation ≤ ±0.5°C.

[0063] As described in step S6 above, during the peak-section of electricity price (such as 10:00 - 15:00), the water pump flow direction is switched, and the cold water flows reversely through the cold storage area from the two side heat exchange areas, using the latent heat of the phase change medium to release cold. According to the real-time cold demand (fed back by the end load sensor), the water pump flow rate is adjusted by frequency conversion (0.5 - 2.0m³ / s) so that the cold release duration covers more than 80% of the peak-section time. When the temperature of the phase change medium rises to the critical value of 7°C, an early warning is triggered and the standby refrigeration system is started to ensure the continuity of cooling supply.

[0064] Example 1, Comparison of the cold storage efficiency between the three-zone series structure and the single-zone structure. To verify the performance advantages of the three-zone series structure, a comparative experiment was designed: the experimental group used the three-zone cold storage tank of the present invention (total volume 500 m³, volume ratio of the cold storage area to the heat exchange area is 3:1), and the control group used a traditional single-zone cold storage tank (volume 500 m³, without partition design). Both were filled with new phase change medium cold plates of the same specification (density 1000 kg / m³, latent heat 200 kJ / kg). Under the conditions of an inlet water temperature of 4°C and a flow rate of 100 m³ / h, the performance during the cold storage stage (6 hours) and the cold release stage (4 hours) was tested. The experimental results showed that the cold storage rate of the three-zone structure reached 4.5 RT / h, a 40.6% increase compared to 3.2 RT / h of the single-zone structure; the cold release duration was extended to 4.8 hours, a 50% increase compared to 3.2 hours of the single-zone structure. In addition, the heat exchange efficiency of the three-zone structure reached 1.25 kW / m³·K, a 47% increase compared to the single-zone structure (0.85 kW / m³·K). Its core advantage lies in the tapered flow channel design (inlet cross-sectional area ratio 1.3:1) that enhances turbulent heat transfer through the change in flow velocity gradient (from 0.3 m / s to 0.8 m / s), and at the same time dynamically adjusts the volume ratio of the cold storage area to the heat exchange area (from 70% to 60%), extending the cold release duration. This example verified the optimization effect of the three-zone series structure on thermodynamic coupling.

[0065] Example 2, Comprehensive performance comparison with traditional water cold storage and ice cold storage. Aiming at the peak cold load demand (1200 RT, lasting 6 hours) of a 100,000 ㎡ office building, the performance differences among water cold storage, ice cold storage and the system of the present invention were compared. The water cold storage system needs to build a 10,000 m³ cold storage water tank (cold storage density 2.6 RT / m³), the ice cold storage system needs an 800 m³ ice tank (cold storage density 3.2 RT / m³), while the three-zone cold storage tank of the present invention only needs a volume of 500 m³ (cold storage density 5.7 RT / m³), and the floor area is reduced by 95%. In terms of energy efficiency, for ice cold storage, due to the need for low-temperature refrigeration at -6°C, the system COP is as low as 2.5, and the energy consumption reaches 7200 kWh; the present invention operates under the condition of 4°C, with a COP of 4.6, and the peak energy consumption is only 3600 kWh, saving 50% of energy. In addition, the present invention can store and supply cold simultaneously during the off-peak and flat electricity price periods, while traditional technologies need to operate at different times. This example highlights the synergistic advantages of the high-density phase change medium (density 1000 kg / m³, latent heat 200 kJ / kg) and the three-zone structure, supporting the function of storing and supplying cold simultaneously.

[0066] Example 3. For a 20,000-square-meter office building project, outdoor temperature and humidity (summer peak: 32°C / 65%RH), solar radiation intensity (600 W / m²), and indoor occupancy density (peak: 0.1 person / m²) are collected through a Building Energy Monitoring System (BEMS). Combining with the building envelope structure parameters (exterior wall heat transfer coefficient: 0.6 W / m²·K, SHGC value of double-glazed glass: 0.25), the basic cooling load is calculated to be 320 RT using the cooling load factor method. According to the time-of-use electricity price policy (peak period: 10:00 - 15:00, electricity price: 1.0 yuan / kWh; valley period: 22:00 - 6:00, electricity price: 0.25 yuan / kWh), a dynamic load curve is generated, and the cooling demand to be covered during the peak period is 260 RT. After introducing an office building type correction factor of 1.0, the corrected peak cooling load is 320 RT, and a 10% redundancy is added to reach 352 RT. Based on the characteristics of the phase change medium (density: 1000 kg / m³, latent heat: 200 kJ / kg), the target cold storage density is calculated to be 5.5 RT / m³, and the size of a single cold plate is determined to be 1.0 m × 0.5 m × 0.1 m, with a stacking spacing of 5 cm.

[0067] The composite phase change material (eutectic system of paraffin-stearic acid doped with 3 wt% graphene) is encapsulated into a circular tube bundle structure cold plate with an internal annular flow channel of 3 mm in diameter, and the cold storage capacity of a single plate is 0.8 RT. Based on the target cold storage density, the total number of cold plates to be stacked is calculated to be 440, arranged in a matrix of 15 layers longitudinally and 30 columns transversely, with a 5-cm diversion gap and 35°-inclined copper fins set between layers. The total occupied volume of the cold plate array is 1.0 m × 0.5 m × 0.1 m × 440 ≈ 22 m³, and the total volume of the cold storage tank is designed to be 80 m³ (including the heat exchange area and structural margin). The cold storage tank is prefabricated with fiberglass-reinforced plastic, with a total length of 8 m, width of 4 m, and height of 2.5 m. The middle cold storage area is 5 m long, accommodating the cold plate stacking array; the two side heat exchange areas are each 1.5 m long, equipped with tapered flow channels (inlet section: 0.8 m × 2.5 m → outlet section: 0.6 m × 2.5 m, cross-sectional area ratio: 1.33:1). A 2-mm-thick aluminum alloy heat conduction partition is set between the cold storage area and the heat exchange area, with a silicon carbide coating (thermal conductivity: 480 W / m·K) applied on the surface. The temperature of the phase change medium is monitored in real time through IoT sensors. When the heat exchange rate decreases, the volume ratio of the cold storage area is automatically adjusted from 65% to 60%, and at the same time, the cross-sectional area of the flow channel in the heat exchange area is increased by 8% to maintain the flow velocity within the range of 0.5 - 0.7 m / s.

[0068] During the cold storage stage, the 4°C influent water is pumped to the cold storage tank by a variable-frequency water pump (rated flow rate: 50 m³ / h). The surface temperature of the cold plate (4.8 - 6.2°C) and the temperature difference (ΔT) between the influent water temperature are monitored in real time through distributed temperature sensors. When ΔT < 1.5°C, the pump frequency is increased from 40 Hz to 48 Hz, and the flow rate increases to 60 m³ / h; when ΔT > 2.5°C, the frequency is decreased to 35 Hz, and the flow rate is reduced to 44 m³ / h. The fuzzy PID controller adjusts the parameters every 5 seconds to ensure that the outlet water temperature is stable at 7.5 ± 0.2°C. During the valley period (22:00 - 6:00), 75% of the flow rate (37.5 m³ / h) flows through the cold storage tank for cold storage, with a cold storage rate of 2.2 RT / h, and the remaining 25% of the flow rate (12.5 m³ / h) bypasses to the end, and the outlet water temperature after mixing is 7.8°C. During the flat period (6:00 - 10:00), it switches to the cooling priority mode. 40% of the flow rate (20 m³ / h) flows through the cold storage tank to release cold (cold release rate: 1.1 RT / h), the host load is reduced from 100% to 70%, and the COP is increased from 3.8 to 4.5. Through the feedback of the terminal thermostat, the opening of the bypass valve (20% - 60%) is dynamically adjusted to maintain the temperature in the office area at 25 ± 0.3°C. During the peak period (10:00 - 15:00), the reverse cold release mode is triggered, the flow direction of the water pump is switched, and the cold water flows reversely through the cold storage area from the two side heat exchange areas. The initial cold release rate is 0.6 m³ / s (corresponding to a cold output of 70 RT / h); according to the demand signal of the terminal fan coil unit, the cold release rate is adjusted variably (0.4 - 0.8 m³ / s), and the real-time cold output covers 85% - 110% of the peak period demand; when the cold plate temperature sensor detects that the medium temperature rises to 6.5°C, an early warning is started and the standby variable-frequency screw chiller is linked; at the end of the peak period, the total cold release amount of the cold storage tank reaches 210 RT (covering 80% of the demand), and the phase change medium temperature rises back to 6.3°C, and the system automatically switches back to the cold storage preparation state.

[0069] In this embodiment, through accurate cold load calculation, compact cold plate stacking design, and intelligent dynamic regulation, the core advantages of the present invention in reducing the initial investment (the volume of the cold storage tank is reduced by 74%), improving the energy efficiency (the COP is increased by 76%), and quickly responding to load changes are verified.

[0070] Refer to Figure 2 , which is the structural block diagram of the integrated building air-conditioning cooling device based on a high-density new medium in an embodiment of the present invention, including:

[0071] A data processing module, which is used to obtain environmental data and building cooling demand data, calculate the cooling load data per unit area and the time-of-use electricity price distribution data, correct the calculated cooling load value based on the building type, reserve 10% - 15% of the cooling redundancy, determine the target cold storage density and the refrigeration temperature range, and obtain the preliminary design parameters for cold plate encapsulation;

[0072] The cold plate design module is used to encapsulate a new phase change medium with a density greater than that of ice thermal energy storage into a cold plate with a preset geometric shape, and calculate the cold plate arrangement method and stacking quantity based on the preliminary design parameters;

[0073] The thermal energy storage tank design module is used to construct a three-zone series structure of the thermal energy storage tank. The middle thermal energy storage area accommodates stacked cold plates, and fluid channels are arranged in the two side heat exchange areas;

[0074] The parameter calculation module is used to set the heat exchange temperature parameters of the inlet water temperature of 4°C and the new phase change medium of 4 - 7°C based on the heat transfer characteristics of the three-zone series structure;

[0075] The thermal energy storage and supply cooling cooperation module is used to perform thermal energy storage and supply cooling cooperation operations during the valley and flat periods of the electricity price, so that the 4°C inlet water exchanges heat with the new phase change medium with a temperature difference of 4 - 7°C when flowing through the thermal energy storage tank, and outputs 7 - 8°C chilled water to the air-conditioning terminal;

[0076] The cold release module during the peak period is used to activate the cold release mode of the thermal energy storage tank during the peak period of the electricity price, stop the operation of the refrigeration system, and continuously output 7 - 8°C chilled water to maintain cooling through the reverse heat exchange of the new phase change medium.

[0077] For the specific implementation of each module in the above device example, please refer to that described in the above method embodiment, and details will not be elaborated here.

[0078] Refer to Figure 3 , and in the embodiment of the present invention, a computer device is further provided. This computer device can be a server, and its internal structure can be as Figure 3 shown. This computer device includes a processor, a memory, a display screen, an input device, a network interface, and a database connected through a system bus. Among them, the processor of this computer design is used to provide computing and control capabilities. The memory of this computer device includes a non-volatile storage medium and an internal memory. The non-volatile storage medium stores an operating system, a computer program, and a database. The internal memory provides an environment for the operation of the operating system and the computer program in the non-volatile storage medium. The database of this computer device is used to store the corresponding data in this embodiment. The network interface of this computer device is used to communicate with an external terminal through a network connection. When the computer program is executed by the processor, the above method is implemented.

[0079] Those skilled in the art can understand that Figure 3 the structure shown in

[0080] An embodiment of the present invention further provides a computer-readable storage medium, on which a computer program is stored. When the computer program is executed by a processor, the above method is implemented. It can be understood that the computer-readable storage medium in this embodiment can be a volatile readable storage medium or a non-volatile readable storage medium.

[0081] In summary, the present invention adopts an integrated cooling method for building air conditioners based on a high-density new medium. By obtaining environmental data and building cooling demand data, calculating the cooling load data per unit area and the time-of-use electricity price distribution data, correcting the calculated cooling load value based on the building type, and reserving 10%-15% cooling redundancy, the target cold storage density and the refrigeration temperature range are determined, and the preliminary design parameters of the cold plate packaging are obtained; a new phase change medium with a density greater than that of ice cold storage is packaged into a cold plate with a preset geometric shape, and the cold plate arrangement and stacking quantity are calculated based on the preliminary design parameters; a three-zone series structure of the cold storage tank is constructed, the middle cold storage zone accommodates the stacked cold plates, and fluid channels are arranged in the two side heat exchange zones. The cold storage zone and the heat exchange zone are thermodynamically coupled through a preset partition ratio; based on the heat transfer characteristics of the three-zone series structure, the heat exchange temperature parameters of the inlet water temperature of 4°C and the new phase change medium of 4-7°C are set; during the valley and flat periods of the electricity price, the cold storage and cooling are operated in coordination, so that the 4°C inlet water exchanges heat with the new phase change medium with a temperature difference of 4-7°C when flowing through the cold storage tank, and cold water at 7-8°C is output to the air-conditioning terminal; during the peak period of the electricity price, the cold release mode of the cold storage tank is activated, the operation of the refrigeration system is stopped, and reverse heat exchange is carried out through the new phase change medium to continuously output cold water at 7-8°C to maintain cooling, realizing efficient and low-cost cold storage and supply, solving the limitations of traditional cold storage technologies, and achieving the purpose of maximizing building energy conservation and economic benefits.

[0082] Those of ordinary skill in the art can understand that all or part of the processes in the methods of the above embodiments can be completed by instructing relevant hardware through a computer program. The computer program can be stored in a non-volatile computer-readable storage medium. When the computer program is executed, it can include the processes of the embodiments of the above methods. Among them, any reference to a memory, storage, database, or other medium provided by the present invention and used in the embodiments can include non-volatile and / or volatile memories. Non-volatile memory can include read-only memory (ROM), programmable ROM (PROM), electrically programmable ROM (EPROM), electrically erasable programmable ROM (EEPROM), or flash memory. Volatile memory can include random access memory (RAM) or external cache memory. By way of illustration and not limitation, RAM is available in various forms, such as static RAM (SRAM), dynamic RAM (DRAM), synchronous DRAM (SDRAM), double data rate SDRAM (SSRSDRAM), enhanced SDRAM (ESDRAM), synchronous link (Synchlink) DRAM (SLDRAM), Rambus direct RAM (RDRAM), direct memory bus dynamic RAM (DRDRAM), and memory bus dynamic RAM, etc.

[0083] It should be noted that in this article, the terms "include", "comprise", or any other variant thereof are intended to cover non-exclusive inclusion, such that a process, apparatus, article, or method that includes a series of elements includes not only those elements but also other elements not expressly listed, or elements that are inherent to such process, apparatus, article, or method. Without further limitation, an element defined by the statement "including one..." does not exclude the existence of additional identical elements in the process, apparatus, article, or method that includes such element.

[0084] The above are only the preferred embodiments of the present invention, and do not limit the patent scope of the present invention. Any equivalent structural or equivalent process transformation made by using the specification and drawings of the present invention, or directly or indirectly applied in other related technical fields, shall be equally included in the patent protection scope of the present invention.

Claims

1. A building air conditioning integrated cooling method based on a high-density new medium, characterized in that: The following steps are involved: Obtain environmental data and building cooling demand data, calculate the cooling load data per unit area and the electricity price period distribution data, correct the cooling load calculation value based on the building type, reserve 10%-15% cooling redundancy, determine the target cold storage density and cooling temperature range, and obtain the preliminary design parameters of the cold plate package; A cold plate with a square honeycomb structure or a circular tube bundle structure with an internal flow channel encapsulated with a high-density new phase change medium, wherein the density of the high-density new phase change medium is not less than 1000kg / m³, the latent heat of phase change is greater than 200kJ / kg, and the phase change temperature range is 4.5±0.5℃ to 6.5±0.5℃. Based on the target cold storage density requirements in the preliminary design parameters, the matching relationship between the number of cold plate stacking layers and the interlayer guide gap is calculated, and the stacking spacing is controlled within the range of 5-10cm; A cold storage tank with a three-zone series structure is provided, a longitudinally arranged cold plate stacking array is provided in the middle cold storage zone, and tapered fluid channels are configured in the heat exchange zones on both sides. The fluid channel layout of the three-zone series structure is adapted to the cross-sectional shape of the flow channel of the cold plate. The fluid channel adopts a tapered flow channel design with a wide inlet and a narrow outlet, and the ratio of the inlet and outlet cross-sectional areas is 1.2:1 to 1.5:

1. A guide fin with an inclination angle of 30°-45° is provided between adjacent cold plates. The volume ratio of the cold storage zone to the single-side heat exchange zone is set to 3:1 to 2:

1. The volume ratio of the cold storage zone to the single-side heat exchange zone is dynamically adjusted according to the cold plate stacking density and the heat exchange rate of the phase change medium. The cold storage zone and the single-side heat exchange zone are thermodynamically coupled through a preset partition ratio; Based on the heat transfer characteristics of the three-zone series structure, the heat exchange temperature parameters of the inlet water temperature of 4°C and the high-density new phase change medium of 4-7°C are set; Performing cold storage and cold supply coordinated operations in the valley and flat sections of electricity prices, so that the 4°C inlet water exchanges heat with the high-density new phase change medium at a temperature difference of 4-7°C when flowing through the cold storage tank, and outputting 7-8°C cold water to the air-conditioning terminal, the performing cold storage and cold supply coordinated operations in the valley and flat sections of electricity prices, including starting the cold storage mode in the valley section of electricity prices, controlling 70%-80% of the 4°C inlet water flow to flow through the cold storage tank for cold storage, and directly bypassing the remaining water flow to the water outlet for mixing, switching to the cold supply priority mode in the flat section of electricity prices, adjusting 30%-50% of the inlet water flow to release cold through the cold storage tank, supplementing the cooling capacity of the refrigeration host, monitoring the outlet water temperature in real time, and when the water temperature deviates from the range of 7-8°C, dynamically adjusting the water flow ratio of the cold storage tank and the bypass pipeline to stabilize the temperature, and during the valley and flat sections of electricity prices, monitoring the outlet water temperature in real time, adjusting the cold load through the flow distribution of the cold storage tank, and keeping the outlet water temperature stable in the target range of 7-8°C; During the peak electricity price period, the cold storage tank is activated in cold capacity release mode, the refrigeration system is stopped, and reverse heat exchange is performed through the high-density new phase change medium to continuously output 7-8°C cold water to maintain cooling.

2. The building air conditioning integrated cooling method based on high-density new medium according to claim 1 is characterized in that: The step of obtaining environmental data and building cooling demand data, calculating unit area cooling load data and electricity price time distribution data, correcting cooling load calculation value based on building type, reserving 10%-15% cooling redundancy, determining target cold storage density and cooling temperature range, and obtaining preliminary design parameters of cold plate packaging includes: The building energy consumption monitoring system collects outdoor temperature, humidity, and solar radiation intensity environmental data in real time, and calculates the basic cooling load in combination with the thermal parameters of the building envelope structure; Divide the peak, valley and normal periods based on the time-of-use electricity price data, map the basic cooling load with the cooling demand in each period, and generate a dynamic load distribution curve; The dynamic load distribution curve is modified according to the building type coefficient to determine the target cold storage density of the peak cold load that needs to cover the duration of the peak electricity price period, and reserve 10%-15% cold capacity redundancy; Combined with the phase change characteristics of the phase change medium, the cold storage capacity and heat exchange area of ​​the cold plate unit are calculated, and the preliminary design parameters including the cold plate thickness and arrangement spacing are output.

3. The building air conditioning integrated cooling method based on high-density new medium according to claim 1 is characterized in that: The step of setting the heat exchange temperature parameters of the inlet water temperature of 4°C and the high-density new phase change medium of 4-7°C includes: The difference between the temperature of the high-density new phase change medium and the inlet water temperature is monitored in real time. When the medium temperature reaches the set threshold, the inlet water flow rate is automatically adjusted to enhance heat exchange and maintain an effective heat exchange temperature zone of 4-7°C.

4. The building air conditioning integrated cooling method based on high-density new medium according to claim 1 is characterized in that: The step of activating the cold storage tank's cold capacity release mode during the electricity price peak period includes: When the electricity price peak period is started, the water inlet and outlet directions of the cold storage tank are switched and the cooling rate is controlled, and the cooling release time covers at least 80% of the duration of the electricity price peak period; The cooling intensity is adjusted in real time according to the cooling demand of the air-conditioning terminal until the temperature of the high-density new phase change medium returns to the critical value of 7°C.

5. A building air conditioning integrated cooling device based on a high-density new medium, characterized in that: include: The data processing module is used to obtain environmental data and building cooling demand data, calculate the cooling load data per unit area and the electricity price period distribution data, correct the cooling load calculation value based on the building type, reserve 10%-15% cooling redundancy, determine the target cold storage density and cooling temperature range, and obtain the preliminary design parameters of the cold plate package; A cold plate design module is used for a cold plate with a square honeycomb structure or a circular tube bundle structure that uses a high-density new phase change medium to encapsulate an internal flow channel. The density of the high-density new phase change medium is not less than 1000kg / m³, the latent heat of phase change is greater than 200kJ / kg, and the phase change temperature range is 4.5±0.5℃ to 6.5±0.5℃. Based on the target cold storage density requirements in the preliminary design parameters, the matching relationship between the number of cold plate stacking layers and the interlayer guide gap is calculated, and the stacking spacing is controlled within the range of 5-10cm; A cold storage tank design module is used to set a cold storage tank with a three-zone series structure, a longitudinally arranged cold plate stacking array is set in the middle cold storage zone, and a tapered fluid channel is configured in the heat exchange zones on both sides. The fluid channel layout of the three-zone series structure is adapted to the cross-sectional shape of the flow channel of the cold plate. The fluid channel adopts a tapered flow channel design with a wide inlet and a narrow outlet, and the inlet and outlet cross-sectional area ratio is 1.2:1 to 1.5:

1. A guide fin with an inclination angle of 30°-45° is provided between adjacent cold plates. The volume ratio of the cold storage zone to the single-side heat exchange zone is set to 3:1 to 2:1, and the volume ratio of the cold storage zone to the single-side heat exchange zone is dynamically adjusted according to the cold plate stacking density and the heat exchange rate of the phase change medium; A parameter calculation module, used to set the heat exchange temperature parameters of the inlet water temperature of 4°C and the high-density new phase change medium of 4-7°C based on the heat transfer characteristics of the three-zone series structure; A cold storage and supply coordination module, which is used to perform cold storage and cold supply coordination operations in the valley section and the flat section of electricity prices, so that the 4°C inlet water exchanges heat with the high-density new phase change medium at a temperature difference of 4-7°C when flowing through the cold storage tank, and outputs 7-8°C cold water to the air-conditioning terminal, and performs cold storage and cold supply coordination operations in the valley section and the flat section of electricity prices; The peak cooling release module is used to activate the cooling release mode of the cold storage tank during the peak electricity price period, stop the operation of the refrigeration system, and continuously output 7-8°C cold water to maintain cooling through reverse heat exchange of the high-density new phase change medium.

6. A computer device comprising a memory and a processor, wherein a computer program is stored in the memory, wherein: When the processor executes the computer program, the steps of the building air conditioning integrated cooling method based on high-density new medium as described in any one of claims 1 to 4 are implemented.

7. A computer-readable storage medium having a computer program stored thereon, characterized in that: When the computer program is executed by a processor, the steps of the building air conditioning integrated cooling method based on a high-density new medium as described in any one of claims 1 to 4 are implemented.

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