Central air conditioning terminal household metering and control method, device, equipment and medium

Abstract

The application provides a centralized air conditioner terminal sub-metering and control method, device, equipment and medium, and belongs to the technical field of air conditioner control. The method comprises the following steps: acquiring the supply-return water temperature difference of each floor in an air conditioner chilled water system and a design supply-return water temperature difference, the air conditioner chilled water system comprising a horizontal pipe arranged on each floor, the horizontal pipe being connected with at least one air conditioner terminal, and the horizontal pipe being provided with a control valve for controlling the air conditioner terminal; adjusting the control valve to make the supply-return water temperature difference of the floor equal to the design supply-return water temperature difference; sub-metering the actual return water temperature of the air conditioner terminal according to the cooling area of the air conditioner terminal and the hourly cooling load of the air conditioner terminal; when the control valve is in an open state, calculating the supply-return water pressure difference of the horizontal pipe; and if the actual return water temperature is greater than a preset return water temperature, increasing the supply-return water pressure difference or the opening degree of the control valve, so that the actual return water temperature is less than or equal to the preset return water temperature. The application can control the terminal in the form of centralized air conditioner.

Description

Technical Field

[0001] This application relates to the field of air conditioning control technology, and in particular to a method, device, equipment and medium for centralized air conditioning terminal metering and control. Background Technology

[0002] Air conditioning terminals in large public buildings are divided into two types: split-system air conditioners and centralized air conditioning systems. Split-system air conditioners generally use variable refrigerant volume (VRV) systems, with each room using an independent air conditioning terminal. Each terminal or group of terminals is operated and stopped via a switching power supply. Centralized air conditioning systems are equipped with a centralized chiller room and supply cooling to each air conditioning terminal through chilled water pipes. Compared with split-system air conditioners, centralized air conditioning systems have higher operating efficiency, longer service life, and more stable cooling operation, therefore, they are more commonly used in large public buildings. The cooling source for centralized air conditioning can be supplied by the building's own chiller room or by a district cooling system. However, the terminal control and user experience of centralized air conditioning systems are more complex. 1) Many property management companies charge for centralized air conditioning users based on area, without quantifying the actual cooling load consumed by users, easily leading to energy waste; 2) Based on the existing building structure's centralized air conditioning chilled water system design, due to the real-time changing characteristics of air conditioning load, hydraulic imbalances can easily occur between different floors or fan coil units, resulting in uneven cooling supply, affecting user comfort and increasing adjustment difficulty; 3) During overtime hours outside of working hours, due to the overtime air conditioning demand on some floors, chilled water flows to the chilled water pipes and fan coil units of other floors without air conditioning demand, causing unnecessary cooling consumption and increasing the air conditioning operating costs for property management companies during overtime hours. Therefore, how to control the air conditioning terminals in centralized air conditioning systems has become an urgent problem to be solved by both self-built chiller rooms and district cooling systems. Based on the information from individual metering of air conditioning terminals, this invention proposes an air conditioning terminal control method. Summary of the Invention

[0003] The main objective of this application is to propose a method, device, equipment, and medium for centralized air conditioning terminal metering and control, which aims to control the centralized air conditioning terminals based on the metering information of the individual air conditioning terminals.

[0004] To achieve the above objectives, a first aspect of this application proposes a method for centralized air conditioning terminal metering and control, the method comprising:

[0005] The supply and return water temperature difference and the design supply and return water temperature difference for each floor in the air conditioning chilled water system are obtained; wherein, the air conditioning chilled water system includes a horizontal pipe installed on each floor, the horizontal pipe is connected to at least one air conditioning terminal, and the horizontal pipe is equipped with a control valve for controlling the air conditioning terminal;

[0006] Adjust the control valve so that the supply and return water temperature difference of the floor is equal to the design supply and return water temperature difference;

[0007] The cooling area and hourly cooling load of the air conditioning terminal are obtained, and the actual return water temperature of the air conditioning terminal is measured for each household based on the cooling area and the hourly cooling load.

[0008] When the control valve is in the open state, calculate the supply and return water pressure difference of the horizontal pipe;

[0009] If the actual return water temperature is greater than the preset return water temperature, the supply and return water pressure difference is increased or the opening of the control valve is increased so that the actual return water temperature is less than or equal to the preset return water temperature.

[0010] In some embodiments, the horizontal pipe is equipped with a chilled water meter, and the calculation of the supply and return water pressure difference of the horizontal pipe includes:

[0011] The chilled water flow rate of the horizontal pipe is obtained through the chilled water meter, or the chilled water flow rate is calculated based on the hourly cooling load.

[0012] The supply and return water pressure difference is calculated based on the chilled water flow rate and the control valve.

[0013] In some embodiments, calculating the supply and return water pressure difference based on the chilled water flow rate and the control valve includes:

[0014] If the control valve includes a static balancing valve and a regulating valve, then the first valve differential pressure of the static balancing valve, the fan coil unit differential pressure of the floor, and the second valve differential pressure of the regulating valve are calculated based on the chilled water flow rate.

[0015] The supply and return water pressure difference is obtained by summing the pressure difference of the first valve, the pressure difference of the fan coil unit, and the pressure difference of the second valve.

[0016] In some embodiments, calculating the supply and return water pressure difference based on the chilled water flow rate and the control valve includes:

[0017] If the control valve includes a differential pressure valve and a regulating valve, then the operating differential pressure of the control valve and the differential pressure of the fan coil unit on the floor are calculated based on the chilled water flow rate.

[0018] Obtain the control pressure differential of the control valve;

[0019] The supply and return water pressure difference is obtained by summing the working pressure difference, the control pressure difference, and the fan coil unit pressure difference.

[0020] In some embodiments, after calculating the supply and return water pressure difference of the horizontal pipe when the control valve is in the open state, the following steps are included:

[0021] Select the maximum supply and return water pressure difference as the target pressure difference;

[0022] Calculate the total chilled water flow rate of the air conditioning chilled water system;

[0023] The pump head of the air conditioning chilled water system is calculated based on the target pressure difference and the total flow rate of the chilled water.

[0024] In some embodiments, after calculating the pump head of the air conditioning chilled water system based on the target pressure difference and the total chilled water flow rate, the method further includes:

[0025] The pump efficiency is determined based on the total chilled water flow rate, the pump head, the preset pump speed, and the preset number of pumps in operation.

[0026] Select the preset pump speed and preset number of pumps that maximize the pump efficiency.

[0027] In some embodiments, the step of metering the actual return water temperature of the air conditioning terminal for each household based on the cooling area and the hourly cooling load includes:

[0028] The fan speed setting of the air conditioning terminal is obtained for each household, and the heat transfer coefficient is determined based on the fan speed setting.

[0029] The room temperature of the air conditioning terminal is obtained for each household;

[0030] The actual return water temperature is calculated for each household based on the cooling area, the hourly cooling load, the heat transfer coefficient, and the room temperature.

[0031] To achieve the above objectives, a second aspect of this application provides a centralized air conditioning terminal metering and control device, the device comprising:

[0032] The first acquisition module is used to acquire the supply and return water temperature difference and the design supply and return water temperature difference for each floor in the air conditioning chilled water system; wherein, the air conditioning chilled water system includes a horizontal pipe installed on each floor, the horizontal pipe is connected to at least one air conditioning terminal, and the horizontal pipe is equipped with a control valve for controlling the air conditioning terminal;

[0033] The adjustment module is used to adjust the control valve so that the supply and return water temperature difference of the floor is equal to the design supply and return water temperature difference;

[0034] The second acquisition module is used to acquire the cooling area of ​​the air conditioning terminal and the hourly cooling load of the air conditioning terminal, and to measure the actual return water temperature of the air conditioning terminal for each household based on the cooling area and the hourly cooling load.

[0035] The calculation module is used to calculate the supply and return water pressure difference of the horizontal pipe when the control valve is in the open state.

[0036] The control module is used to increase the supply and return water pressure difference or increase the opening of the control valve if the actual return water temperature is greater than the preset return water temperature, so that the actual return water temperature is less than or equal to the preset return water temperature.

[0037] To achieve the above objectives, a third aspect of this application provides an electronic device, which includes a memory and a processor. The memory stores a computer program, and the processor executes the computer program to implement the method described in the first aspect.

[0038] To achieve the above objectives, a fourth aspect of the present application provides a computer-readable storage medium storing a computer program that, when executed by a processor, implements the method described in the first aspect.

[0039] The centralized air conditioning terminal metering and control method, centralized air conditioning terminal metering and control device, electronic equipment, and computer-readable storage medium proposed in this application embodiment obtain the supply and return water temperature difference and the design supply and return water temperature difference for each floor in the air conditioning chilled water system. The control valve is adjusted to make the supply and return water temperature difference equal to the design temperature difference for each floor. This is achieved by using an equal temperature difference control method, thus ensuring that the cooling capacity of each floor meets its cooling load demand. Considering that different load rates at the air conditioning terminals can cause the actual return water temperature to deviate from the design return water temperature, to achieve optimized control of each air conditioning terminal, the cooling area and hourly cooling load of the air conditioning terminal are obtained. Based on the cooling area and hourly cooling load, the actual return water temperature of each air conditioning terminal is metered. When the control valve is open, the supply and return water pressure difference of the horizontal pipe is calculated. If the actual return water temperature is greater than the preset return water temperature, it indicates that the air conditioning terminal does not meet the cooling load demand. Therefore, the supply and return water pressure difference is increased or the opening of the control valve is increased to make the actual return water temperature less than or equal to the preset return water temperature, thereby regulating the hydraulics of the floor where the air conditioning terminal is located. Attached Figure Description

[0040] Figure 1 This is a schematic diagram of a traditional air conditioning chilled water system;

[0041] Figure 2 This is a schematic diagram of an air conditioning chilled water system provided in an embodiment of this application;

[0042] Figure 3 This is another schematic diagram of the air conditioning chilled water system provided in the embodiments of this application;

[0043] Figure 4 This is a flowchart of the centralized air conditioning terminal metering and control method provided in the embodiments of this application;

[0044] Figure 5 This is a schematic diagram reflecting the hourly load factor changes of different types of buildings, provided in the embodiments of this application;

[0045] Figure 6 This is a schematic diagram reflecting the changes in daily cooling capacity per unit area of ​​different types of buildings, provided in the embodiments of this application.

[0046] Figure 7 yes Figure 4 The flowchart of step S430 in the middle;

[0047] Figure 8 yes Figure 4 The flowchart of step S440 in the middle;

[0048] Figure 9 yes Figure 8 The flowchart of step S820 in the middle;

[0049] Figure 10 yes Figure 8 Another flowchart of step S820 in the process;

[0050] Figure 11 This is another flowchart of the centralized air conditioning terminal metering and control method provided in the embodiments of this application;

[0051] Figure 12 This is another flowchart of the centralized air conditioning terminal metering and control method provided in the embodiments of this application;

[0052] Figure 13 This is a schematic diagram of the water pump frequency conversion curve provided in the embodiments of this application;

[0053] Figure 14 This is a schematic diagram of the structure of the centralized air conditioning terminal metering and control device provided in the embodiments of this application;

[0054] Figure 15 This is a schematic diagram of the hardware structure of the electronic device provided in the embodiments of this application. Detailed Implementation

[0055] To make the objectives, technical solutions, and advantages of this application clearer, the following detailed description is provided in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the scope of this application.

[0056] It should be noted that although functional modules are divided in the device schematic diagram and a logical order is shown in the flowchart, in some cases, the steps shown or described may be performed in a different order than the module division in the device or the order in the flowchart. The terms "first," "second," etc., in the specification, claims, and the aforementioned drawings are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence.

[0057] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. The terminology used herein is for the purpose of describing embodiments of this application only and is not intended to limit this application.

[0058] Air conditioning terminals in large public buildings are divided into two types: split-system air conditioners and centralized air conditioning systems. Split-system air conditioners generally use variable refrigerant flow (VRF) systems, with each room using an independent terminal. Each terminal or group of terminals operates and stops via a switching power supply. Centralized air conditioning systems are equipped with a centralized chiller room and supply cooling to each terminal via chilled water pipes. Compared to split-system air conditioners, centralized air conditioning systems offer higher operating efficiency, longer service life, and more stable cooling operation, making them the most common choice for large public buildings. However, centralized air conditioning terminal control is more complex, leading to issues such as wasted cooling capacity during overtime work and hydraulic or thermal imbalances during peak hours. Therefore, how to control the terminals in centralized air conditioning systems has become a pressing problem to be solved.

[0059] Based on this, embodiments of this application provide a method for metering and controlling individual households in a centralized air conditioning terminal, a device for metering and controlling individual households in a centralized air conditioning terminal, an electronic device, and a computer-readable storage medium, which are intended to control air conditioning terminals in a centralized air conditioning system.

[0060] The centralized air conditioning terminal metering and control method, centralized air conditioning terminal metering and control device, electronic equipment and computer-readable storage medium provided in this application embodiment are specifically described through the following embodiments. First, the centralized air conditioning terminal metering and control method in this application embodiment is described.

[0061] The centralized air conditioning terminal metering and control method provided in this application relates to the field of air conditioning control technology. This method can be applied to a terminal, a server, or software running on either a terminal or a server. In some embodiments, the terminal can be a smartphone, tablet, laptop, desktop computer, etc.; the server can be configured as an independent physical server, a server cluster or distributed system composed of multiple physical servers, or a cloud server providing basic cloud computing services such as cloud services, cloud databases, cloud computing, cloud functions, cloud storage, network services, cloud communication, middleware services, domain name services, security services, CDN, and big data and artificial intelligence platforms; the software can be an application implementing the centralized air conditioning terminal metering and control method, but is not limited to the above forms.

[0062] This application can be used in a wide variety of general-purpose or special-purpose computer system environments or configurations. Examples include: personal computers, server computers, handheld or portable devices, tablet devices, multiprocessor systems, microprocessor-based systems, set-top boxes, programmable consumer electronics, network PCs, minicomputers, mainframe computers, and distributed computing environments including any of the above systems or devices. This application can be described in the general context of computer-executable instructions executed by a computer, such as program modules. Generally, program modules include routines, programs, objects, components, data structures, etc., that perform specific tasks or implement specific abstract data types. This application can also be practiced in distributed computing environments where tasks are performed by remote processing devices connected via a communication network. In distributed computing environments, program modules can reside in local and remote computer storage media, including storage devices.

[0063] Please see Figure 1 , Figure 1This is a traditional building air conditioning chilled water system, which includes a chilled water system in the chiller room and chilled water systems for fan coil units on each floor. The chiller room system includes variable frequency pumps and chillers. The chillers provide cooling to each floor, while the variable frequency pumps deliver chilled water to each room as needed. The fan coil chilled water system is configured with a static balancing valve, a solenoid on / off valve, and air conditioning terminals. The air conditioning terminals are in the form of fan coil units. These terminals include fan coil units, variable air volume (VAV) systems, and cooling beams. The solenoid on / off valve switches the chilled water flow path based on the temperature of the terminal room. The fan coil units use fans to force indoor air through the coils, exchanging sensible heat with the water inside. Each floor is equipped with a static balancing valve for adjustment during the commissioning phase after project construction and before the air conditioning system is put into formal use. Adjustment is typically manual, ensuring that each floor operates simultaneously based on the design flow rate and design temperature difference, achieving hydraulic balance between floors. After the adjustment phase, the opening of the static balancing valve is generally fixed and will not be adjusted during operation. The water supply temperature of the j-th air conditioning terminal on the i-th floor is expressed as... The return water temperature is expressed as The terminal room temperature is expressed as The chilled water flow rate is expressed as The chilled water flow rate of the i-th floor is expressed as... It is the sum of the chilled water flow rates of all air conditioning terminals on that floor.

[0064] In the chilled water system of the chiller room, fluid resistance is mainly formed by local resistance, including that of the chiller evaporator, check valve, and filter. In the chilled water system of each floor's fan coil unit, fluid resistance is mainly composed of local resistance formed by static balancing valves, electric regulating valves, and fan coil units. In the entire chilled water system, the friction resistance of the station building pipes, supply and return water risers, and supply and return water horizontal pipes on each floor can be ignored.

[0065] Commissioning and acceptance testing are typically conducted under design conditions. If the actual load deviates from the design load, the balance of the water systems in each branch system cannot be guaranteed. Especially when the actual load deviates significantly from the design load, it can easily lead to excessive flow in some areas and insufficient flow in others, resulting in wasted cooling capacity and significantly impacting comfort. The operating conditions of fan coil units vary from floor to floor. For example, if some fan coil units stop operating or the solenoid on / off valves close, the system impedance coefficient of that floor will change, disrupting the hydraulic balance maintained by the original static balancing valves between floors. This type of system usually uses differential pressure control or temperature difference control. Because there is no control over the supply and return water temperature difference for each floor, it is difficult to achieve temperature difference control through the main pipe. When using differential pressure control, considering that the air conditioning load changes dynamically throughout the year, the control process often sacrifices thermal optimization. Both of these control methods are ineffective, specifically manifested in the temperature difference between the supply and return water main pipes being consistently much lower than the design temperature difference during operation, or insufficient cooling in some rooms, resulting in energy waste.

[0066] In order to achieve optimized control of air conditioning terminals and reduce energy consumption, this application embodiment installs a chilled water meter and a control valve on the horizontal pipe of each floor to control the supply and return water temperature difference of the horizontal pipe on each floor, and to verify the cooling supply of the rooms within the cooling range of each coil, so as to meet the cooling needs of the end users while ensuring energy-saving operation of the air conditioning terminals on each floor. The chilled water meter is used to measure the chilled water flow rate of the horizontal pipe. There are two ways to set the control valve: (1) such as Figure 2 As shown, an electric regulating valve is installed on the basis of the existing air conditioning chilled water system; (2) as Figure 3 As shown, the original static balancing valve is eliminated, and a differential pressure control valve + regulating valve or a pressure independent control valve (PICV) is added. By adjusting the valve opening and combining it with the chilled water capacity meters on each floor, dynamic adjustment of the hydraulic balance between floors can be achieved, overcoming the problem that the original system could not adjust the hydraulic balance in real time during operation. A corresponding control method is also proposed. During overtime hours outside of working hours, the chilled water supply to floors that do not require overtime air conditioning can be shut off as needed, thus avoiding unnecessary waste of cooling capacity caused by chilled water flowing to other floors due to overtime air conditioning demand on some floors. It should be noted that the main equipment information in the air conditioning chilled water system is all connected to the building air conditioning control system. Figure 2 The electric regulating valve in the air conditioning chilled water system shown is... Figure 3 The regulating valves in the air conditioning chilled water system shown can all be referred to as regulating valves.

[0067] The load rate of each fan coil unit varies, causing the chilled water return temperature of each coil to deviate from or fall below the design return temperature. By adjusting the regulating valve, the overall supply and return water temperature difference of the floor can be adjusted, and combined with the operating parameter information of each coil, the hydraulics of a single floor can be adjusted to achieve the purpose of optimized control.

[0068] exist Figures 1 to 3 In the middle, the chilled water supply temperature of each fan coil unit They are the same, both equal to the water supply temperature of the chiller room. ,Right now .

[0069] Figure 4 This is an optional flowchart of the centralized air conditioning terminal metering and control method provided in the embodiments of this application. Figure 4 The method may include, but is not limited to, steps S410 to S450.

[0070] Step S410: Obtain the supply and return water temperature difference and the design supply and return water temperature difference for each floor in the air conditioning chilled water system; wherein, the air conditioning chilled water system includes a horizontal pipe installed on each floor, the horizontal pipe is connected to at least one air conditioning terminal, and the horizontal pipe is equipped with a control valve for controlling the air conditioning terminal.

[0071] Step S420: Adjust the control valve to make the supply and return water temperature difference of the floor equal to the design supply and return water temperature difference;

[0072] Step S430: Obtain the cooling area and hourly cooling load of the air conditioning terminal, and measure the actual return water temperature of the air conditioning terminal for each household according to the cooling area and hourly cooling load.

[0073] Step S440: When the control valve is in the open state, calculate the supply and return water pressure difference of the horizontal pipe;

[0074] In step S450, if the actual return water temperature is greater than the preset return water temperature, the supply and return water pressure difference is increased or the opening of the control valve is increased so that the actual return water temperature is less than or equal to the preset return water temperature.

[0075] In step S410 of some embodiments, the chilled water return temperature of the horizontal pipe on each floor and the chilled water supply temperature of the chiller room are obtained during the operation of the air conditioning chilled water system. The chilled water return temperature and chilled water supply temperature of the corresponding floor are subtracted to obtain the supply and return water temperature difference of the horizontal pipe on each floor. The design return water temperature under the design conditions is obtained, and the design return water temperature is subtracted from the chilled water supply temperature to obtain the design supply and return water temperature difference. The air conditioning chilled water system includes a horizontal pipe installed on each floor. The horizontal pipe is connected to at least one air conditioning terminal. The horizontal pipe is equipped with a chilled water meter and a control valve for controlling each air conditioning terminal on the corresponding floor. Figure 2As shown, the control valve includes a static balancing valve and a regulating valve. Figure 3 As shown, the control valve includes a differential pressure control valve and a regulating valve.

[0076] In step S420 of some embodiments, the regulating valve for each floor is adjusted using an equal temperature difference control method, so that the supply and return water temperature difference of the horizontal pipes on each floor is equal to the design supply and return water temperature difference, i.e. , Indicates the first Chilled water return temperature of the horizontal pipes on each floor This indicates the chilled water supply temperature of the chiller room. This indicates the design return water temperature. When the supply and return water temperature difference in the horizontal pipe is equal to the design supply and return water temperature difference, it can be considered that the cooling capacity of this floor meets the overall cooling load demand of the floor.

[0077] In step S430 of some embodiments, considering the differences in cooling load, chilled water flow rate, and regulation status of each fan coil unit, the return water temperature of different fan coil units may vary. Higher or lower than the design return water temperature Therefore, it is necessary to implement further individualized optimization control for each air conditioning terminal by combining the operating parameters of the fan coil units. Individual metering refers to independent calculation and measurement for each air conditioning terminal. Specifically, for each air conditioning terminal, the cooling area and hourly cooling load of the air conditioning terminal are obtained separately. The hourly cooling load is the cooling capacity supplied by the fan coil unit of the air conditioning terminal at a preset operating time. Based on the cooling area and hourly cooling load, the actual return water temperature of the air conditioning terminal is calculated separately for each household.

[0078] For building cooling load, the hourly cooling load coefficient is often used to represent the change in cooling load, and is defined as:

[0079] ,

[0080] in, Indicates the first Building type in month m Hourly cooling load factor at the operating time; Indicates the first Building type in month m Hourly cooling load per unit area at operating time, in units of ; express No. The daily cooling demand per unit area of ​​building type m in month m, in units of ; It represents 1 hour.

[0081] According to operational data statistics, the hourly load factor changes for different types of buildings are as follows: Figure 5As shown, the daily cooling demand per unit area varies for different types of buildings. Figure 6 As shown. Figure 5 It displays the hourly load factor changes of various buildings such as commercial buildings, office buildings, and schools from 0:00 to 23:30. The trend of change can be divided into peak, flat and valley segments. %Eday represents the placeholder for the daily energy consumption field. Figure 6 It shows the monthly average daily cooling capacity per unit area for various types of buildings, including commercial buildings, office buildings, and schools, from January to mid-December, based on weekdays, the whole month, and weekends and holidays.

[0082] according to Figure 5 and Figure 6 And combining the above formula for the hourly cooling load coefficient, we obtain the first... Building type in month m Hourly cooling load per unit area during operation :

[0083] .

[0084] For the hourly cooling load per unit area on a 24-hour day in month m, the following relationship holds:

[0085] .

[0086] Taking a certain type of building as an example, the hourly cooling load coefficient, daily cooling capacity per unit area, and hourly cooling load per unit area for month m are respectively written as: , , The hourly cooling load of the air conditioning terminal is calculated based on the hourly cooling load coefficient, the daily cooling capacity per unit area, and the cooling area of ​​the air conditioning terminal. Therefore, the hourly cooling load of the j-th coil on the i-th floor, i.e., the hourly cooling load of the air conditioning terminal, is expressed as:

[0087] ,

[0088] in, and Indicates the first The hourly cooling load and cooling area of ​​the j-th air conditioning terminal on the floor.

[0089] Please see Figure 7 In some embodiments, step S430 may include, but is not limited to, steps S710 to S730:

[0090] Step S710: Obtain the fan speed setting of the air conditioning terminal for each household, and determine the heat transfer coefficient based on the fan speed setting.

[0091] Step S720: Obtain the room temperature of the air conditioning terminal for each household;

[0092] Step S730: Calculate the actual return water temperature for each household based on the cooling area, hourly cooling load, heat transfer coefficient, and room temperature.

[0093] In step S710 of some embodiments, the fan speed includes four levels: high, medium, low, and off. The high speed (level 3) has the highest fan speed, while the medium speed (level 2) and low speed (level 1) gradually decrease in fan speed. At level 0, the fan is off, and the solenoid on / off valve is closed. For each air conditioning terminal, the fan speed level is obtained individually, and the fan speed level can be any one of high, medium, low, or off. The heat transfer coefficient of the air conditioning terminal coil mainly depends on the air-side heat transfer coefficient, which is adjusted by the fan speed.

[0094] Fan coil units are generally designed based on the fan's operation at medium speed (second speed), meaning the heat transfer coefficient at second speed is the design heat transfer coefficient of the coil. As the terminal cooling load increases, the fan speed gradually increases. When cooling is not required, the speed is set to level 0. The heat transfer coefficients of levels 0, 1, 2, and 3 for the j-th air conditioning terminal on the i-th floor are respectively expressed as... , , , The heat transfer coefficients for different speed ranges can be obtained through equipment selection, with speed range 0 being one example. 0, Level 2 To design heat transfer coefficient The relationship between the heat transfer coefficients of different speed ranges can be determined according to the design standards of fan coil units. Based on the fan coil unit's factory data, the parameters of a certain model of coil unit were determined as follows: Fan coil units are used to regulate room temperature. Each coil has a control panel at the end, and the fan operation is controlled by the control panel, with both manual and automatic control modes. The greater the room load demand, the higher the corresponding fan speed.

[0095] If the fan speed setting is 0, the heat transfer coefficient of the coil is determined to be 0; if the fan speed setting is 2, the heat transfer coefficient of the coil is determined to be the design heat transfer coefficient of the coil; if the fan speed setting is 1 or 3, the relationship between the heat transfer coefficients of different settings is obtained, and the heat transfer coefficient of the coil is calculated based on the relationship and the design heat transfer coefficient of the coil.

[0096] In step S720 of some embodiments, for each air conditioning terminal, the maximum value of the design room temperature and the panel set temperature is selected for each household to obtain the room temperature of the air conditioning terminal. The design room temperature is the room temperature under design operating conditions, and the panel set temperature is the temperature set on the control panel of the coil. The room temperature of the j-th air conditioning terminal on the i-th floor can be expressed as:

[0097] ,

[0098] in, Indicates the designed room temperature; This indicates the temperature set on the panel.

[0099] In step S730 of some embodiments, the cooling capacity of the fan coil unit is... That is, the first The hourly cooling load of the j-th air conditioning terminal on the floor can be expressed as:

[0100] ,

[0101] in, , , , , and These represent the cooling capacity, heat transfer coefficient, cooling area, room temperature, chilled water supply temperature, and chilled water return temperature of the j-th coil in the i-th layer, respectively.

[0102] When the fan operates at different speeds, the chilled water return temperature of the coils varies. For all coils, the chilled water supply temperature is equal to the chiller room supply temperature. Or, in other words, equal to the design supply water temperature. Coil return water temperature. It depends on the heat exchange capacity of the coil. There is a design return water temperature in the coil design. .

[0103] Under the design conditions, the above formula becomes:

[0104] ,

[0105] in, , , and These represent the design cooling capacity, design heat transfer coefficient, design room temperature, and design return water temperature of the j-th coil on the i-th floor under the design conditions.

[0106] For the same coil, the cooling load is a fixed value. When the fan is running at speed 2, the heat transfer coefficient is the design heat transfer coefficient, and the above formula becomes:

[0107] ,

[0108] in, This indicates the return water temperature when the fan speed is set to level 2. .

[0109] When the fan is running at speed 3, the above equation becomes:

[0110] ,

[0111] in, This indicates the return water temperature when the fan speed is set to level 3.

[0112] Based on the formula for calculating the cooling capacity of fan coil units, the chilled water return temperature corresponding to the fan speed setting is calculated according to the cooling area, hourly cooling load, heat transfer coefficient, room temperature, and chilled water supply temperature. This chilled water return temperature is then used as the actual return water temperature.

[0113] Based on the cooling load calculation formulas for the second and third speed settings, the relationship between the return water temperatures for the two fan speed settings is as follows:

[0114] .

[0115] Based on this formula, For example, according to , , ,get .

[0116] Through the above steps S710 to S730, the actual return water temperature of the air conditioning terminal can be obtained, so as to optimize the control of the air conditioning terminal based on the actual return water temperature.

[0117] Please see Figure 8 In some embodiments, step S440 may include, but is not limited to, steps S810 to S820:

[0118] Step S810: Obtain the chilled water flow rate of the horizontal pipe through a chilled water meter, or calculate the chilled water flow rate based on the hourly cooling load;

[0119] Step S820: Calculate the supply and return water pressure difference based on the chilled water flow rate and control valve.

[0120] In step S810 of some embodiments, the chilled water flow rate of the horizontal pipe can be collected by a chilled water meter, or the hourly cooling load of each air conditioning terminal on the same floor can be added together to obtain the hourly total cooling load of the horizontal pipe on that floor. The hourly total cooling load of the i-th floor is:

[0121] ,

[0122] in, Indicates the first Total hourly cooling load of the floor; Indicates the first The number of air conditioning terminals on each floor.

[0123] As can be seen from the above formula, the hourly total cooling load of each floor depends on the sum of the cooling areas of all air conditioning terminals on that floor. Operating month m and operating time The hourly total cooling load of each floor can also be expressed as:

[0124] ,

[0125] in, Indicates the density of water; This indicates the specific heat capacity at constant pressure. and They represent the first Chilled water return temperature and chilled water flow rate of the layer; This indicates the chilled water supply temperature of the refrigeration room.

[0126] Based on the hourly total cooling load of the i-th floor Actual return water temperature Water supply temperature Specific heat capacity at constant pressure Density of water Calculate the chilled water flow rate of the i-th horizontal pipe. .

[0127] In step S820 of some embodiments, the control valve can be configured in two ways. Depending on the configuration, the supply and return water pressure difference of the horizontal pipe is calculated based on the chilled water flow rate of the horizontal pipe. It should be noted that the pressure difference caused by the friction resistance along the riser is not considered here.

[0128] Through the above steps S810 to S820, the supply and return water pressure difference of each floor can be obtained, so as to control the air conditioning terminal pressure difference according to the supply and return water pressure difference.

[0129] When the control valve is in the open state, that is, when the regulating valve or the differential pressure valve is in the open state, calculate the supply and return water pressure difference of the horizontal pipe.

[0130] Please see Figure 9 In some embodiments, step S820 may include, but is not limited to, steps S910 to S920:

[0131] Step S910: If the control valve includes a static balancing valve and a regulating valve, calculate the first valve differential pressure of the static balancing valve, the fan coil unit differential pressure of the floor, and the second valve differential pressure of the regulating valve based on the chilled water flow rate.

[0132] Step S920: Sum the pressure difference of the first valve, the pressure difference of the fan coil unit, and the pressure difference of the second valve to obtain the supply and return water pressure difference.

[0133] In some embodiments, in steps S910 to S920, if the control valve includes a static balancing valve and a regulating valve, the supply and return water pressure difference of the i-th horizontal pipe is expressed as:

[0134] ,

[0135] in, , , , These represent the supply and return water pressure difference of the i-th horizontal pipe, the static balancing valve pressure difference, the fan coil unit pressure difference, and the electric regulating valve pressure difference, respectively.

[0136] The pressure difference of the static balancing valve is the first valve pressure difference of the static balancing valve, and the pressure difference of the electric regulating valve is the second valve pressure difference of the regulating valve. Without considering the friction resistance along the horizontal pipe, the pressure difference is the same for each fan coil unit on the same floor. The pressure drop distribution of the static balancing valve, fan coil units, and regulating valve is calculated based on the chilled water flow rate of the horizontal pipe. The three pressure drop distributions of the static balancing valve, fan coil units, and regulating valve are expressed as follows:

[0137] ,

[0138] ,

[0139] ,

[0140] in, The chilled water flow rate at the inlet of the main horizontal pipe of the i-th layer is expressed in units of... ; Let be the flow coefficient of the i-th static balancing valve, in units of . ; For the i-th layer regulating valve at an opening degree of The flow coefficient at that time, in units of ; The chilled water flow rate of the j-th fan coil unit on the i-th floor is expressed in units of... ; The impedance coefficient of the j-th fan coil unit on the i-th floor is given by [value]. h represents hours; Let be the total number of coils in the i-th layer. The chilled water flow rate of the horizontal pipes in the i-th layer can be expressed as:

[0141] ,

[0142] or,

[0143] ,

[0144] or,

[0145] ,

[0146] or,

[0147] ,

[0148] in, Let be the total impedance coefficient of all fan coil units on the i-th floor. As the number of closed on / off valves increases, the total impedance coefficient of the fan coil units on the floor increases, expressed as:

[0149] ,

[0150] Each fan coil unit's electromagnetic on / off valve has only two states: open and closed. Its impedance coefficient is expressed as:

[0151] ,

[0152] We can obtain:

[0153] ,

[0154] Based on the above formula, according to the chilled water flow rate of the horizontal pipe The chilled water flow rate for each coil can be obtained. .

[0155] The pressure difference between the supply and return water in each horizontal pipe layer is expressed as:

[0156] ,

[0157] or,

[0158] ,

[0159] in, The total impedance coefficient of the horizontal pipe on the i-th floor can be expressed as:

[0160] .

[0161] Through the above steps S910 to S920, the horizontal pipe supply and return water pressure difference in the form of a combination of static balancing valve and regulating valve can be obtained.

[0162] Please see Figure 10 In some embodiments, step S820 may include, but is not limited to, steps S1010 to S1030:

[0163] Step S1010: If the control valve includes a differential pressure valve and a regulating valve, calculate the working differential pressure of the control valve and the differential pressure of the fan coil units on the floor based on the chilled water flow rate.

[0164] Step S1020: Obtain the control pressure differential of the control valve;

[0165] Step S1030: Sum the working pressure difference, control pressure difference, and fan coil unit pressure difference to obtain the supply and return water pressure difference.

[0166] In some embodiments, in steps S1010 to S1030, if the control valve includes a differential pressure valve and a regulating valve, the supply and return water pressure difference of the i-th horizontal pipe is expressed as:

[0167] ,

[0168] in, The pressure difference between the differential pressure valve and the regulating valve combination at the i-th layer, respectively, in kPa, can be expressed as:

[0169] ,

[0170] ,

[0171] in, To control the operating pressure differential of the valve; The control pressure differential of the control valve is typically a constant, such as 2m, which is taken here. m; To control the valve at an opening degree of The flow coefficient at that time.

[0172] Flow coefficient of control valve This is an inherent characteristic of the control valve and can be obtained from the factory specifications. The operating differential pressure of the control valve... In the design flow rate The maximum opening degree of the valve core is At that time, there is a minimum working pressure difference. , usually taken as , can be represented as:

[0173] ,

[0174] then,

[0175] ,

[0176] For the combination of differential pressure valve and regulating valve, the supply and return water pressure difference of the horizontal pipe on each floor is expressed as:

[0177] ,

[0178] or,

[0179] .

[0180] Through the above steps S1010 to S1030, the supply and return water pressure difference of the horizontal pipe in the form of a combination of differential pressure valve and regulating valve can be obtained.

[0181] For different valve combinations, when the control valve opening on a certain floor is 100%, that is... or It was generally agreed that there was no excess pressure on that floor that required the valve to overcome, thus failing to meet the conditions for the most unfavorable branch. For the static balancing valve + regulating valve combination, the opening degree of the regulating valve on each floor can be read. This allows you to obtain the floors with a maximum opening of 100%; for the differential pressure valve + regulating valve combination (PICV), the differential pressure of each floor's differential pressure valve can be used to determine the floor level. chilled water flow rate Combined with the factory-designed flow coefficient of the differential pressure valve The opening degree of the working valve core is obtained. When the opening is 100%, the floor is considered the most unfavorable branch.

[0182] Based on the opening degree of the regulating valve and the chilled water flow rate of the most unfavorable floor, the supply and return water pressure difference of the most unfavorable floor is obtained as follows:

[0183] ,

[0184] or,

[0185] .

[0186] chilled water flow rate of layer i for:

[0187] ,

[0188] As can be seen from the formula, With return water temperature Relevant. For a given return water temperature, such as the design return water temperature. chilled water flow rate It is month m and time. The function.

[0189] The supply and return water pressure difference of the most unfavorable floor can be re-expressed as:

[0190] ,

[0191] or,

[0192] ,

[0193] For a given return water temperature, such as the design return water temperature The most unfavorable pressure difference between the supply and return water pipes on the floor is determined by the month (m) and time. The function.

[0194] Please see Figure 11 In some embodiments, after step S440, the centralized air conditioning terminal metering and control method may also include, but is not limited to, steps S1110 to S1130:

[0195] Step S1110: Select the maximum supply and return water pressure difference as the target pressure difference;

[0196] Step S1120: Calculate the total chilled water flow rate of the air conditioning chilled water system;

[0197] Step S1130: Calculate the pump head of the air conditioning chilled water system based on the target pressure difference and the total chilled water flow rate.

[0198] In step S1110 of some embodiments, the largest supply and return water pressure difference is selected as the target pressure difference from all the supply and return water pressure differences of the horizontal pipes on all floors. That is:

[0199] ,

[0200] in, The target pressure difference is expressed in kPa. This represents the supply and return water pressure difference in the i-th horizontal pipe; This indicates the total number of floors.

[0201] The supply and return water pressure difference of the horizontal pipes on each floor can be assumed to be equal, which can be expressed as:

[0202] ,

[0203] in, The pressure drop of the main water supply and return pipes of a building is the target pressure difference.

[0204] In step S1120 of some embodiments, the chilled water flow rates of the horizontal pipes on each floor are summed to obtain the total flow rate of the main pipe, which is then the total chilled water flow rate of the air conditioning chilled water system. The total flow rate V of the main pipe is:

[0205] .

[0206] Total flow rate It can also be expressed as:

[0207] ,

[0208] in, This indicates the total number of floors.

[0209] In step S1130 of some embodiments, the pump head of the air conditioning chilled water system is calculated based on the target pressure difference and the total chilled water flow rate. The pump head is the head of the variable frequency pump in the chiller room, expressed as:

[0210] ,

[0211] in, The pump head is expressed in meters (m). The impedance coefficient of the refrigeration room, in units of .

[0212] For a given return water temperature, such as the design return water temperature Pump head It is month m and time. The function.

[0213] Through the above steps S1110 to S1130, the pump head can be predicted.

[0214] Please see Figure 12 In some embodiments, after step S1130, the centralized air conditioning terminal metering and control method may also include, but is not limited to, steps S1210 to S1220:

[0215] Step S1210: Determine the pump efficiency based on the total chilled water flow rate, pump head, preset pump speed, and preset number of pumps in operation.

[0216] Step S1220: Select the preset pump speed and preset number of pumps that maximize pump efficiency.

[0217] In step S1210 of some embodiments, after determining the total chilled water flow rate V and the pump head H, the preset pump speed N and the preset number of pumps in operation n (the number of pumps turned on) can be determined according to the pump frequency conversion curve. The pump frequency conversion curve is used to reflect the characteristics of the variable frequency pump, and the pump frequency conversion curve is as follows: Figure 13 As shown. For any set of values ​​(Vx, Hx), different pump speeds can be determined based on the number of pumps in operation. For example... Figure 13 As shown, for the pump head Hx and flow rate Vx, both Hx and Vx are greater than 0. When one pump is running, the corresponding pump speed is N1, and the pump efficiency of each pump is... When two water pumps are running, the corresponding pump speed is N2. At this time, the efficiency of each pump is... Similarly, when n water pumps are running, the corresponding pump speed is Nn, and the efficiency of each pump is... Pump efficiency refers to the operating efficiency of the pump.

[0218] In step S1220 of some embodiments, for various combinations of pump operating numbers and pump speeds, the pump operating numbers and pump speeds with the highest pump efficiency are selected as the optimal pump operating parameters, and fine-tuning is performed within this range. That is:

[0219] ,

[0220] in, This indicates the maximum pump efficiency.

[0221] The number of operating pumps and their speed corresponding to the maximum pump efficiency can be expressed as follows: and After meeting the control requirements of the regulating valves on each floor, the number and speed of water pumps can be further optimized under a determined combination of total chilled water flow and pump head. Presetting the number of operating pumps and their speeds can serve as a basis for adjusting pump operating parameters according to seasonal changes.

[0222] Through the above steps S1210 to S1220, the pump speed and the number of pumps in operation can be optimized.

[0223] In some embodiments, in step S450, if the actual return water temperature is greater than the preset return water temperature, where the preset return water temperature is the return water temperature of the air conditioning terminal when the fan speed setting is 3, that is... This indicates that the chilled water supply to the air conditioning terminal coil is insufficient to meet the cooling load demand. Since the floor where the air conditioning terminal is located is the most unfavorable floor, the solution is to increase the supply and return water pressure difference to increase the water supply. This means increasing the total water supply to that floor, or increasing the opening of the regulating valve on that floor, until the actual return water temperature is less than or equal to the preset return water temperature. .

[0224] It should be noted that when the opening of the regulating valve is increased, the chilled water flow rate of other coils also increases simultaneously. At this time, the return water temperature of some coils may be too low, causing the supply and return water temperature difference in the horizontal pipe to be less than the design temperature difference. In other words, to meet the heat exchange requirements of a coil with the most unfavorable conditions, the temperature difference between the supply and return water in the horizontal pipe is increased. Below the design temperature difference Since only the supply and return water temperature difference of each floor's horizontal pipe is controlled here, the supply and return water temperature difference of the main supply and return water pipe may be less than [the specified value]. .

[0225] Please see Figure 14 This application also provides a centralized air conditioning terminal metering and control device, which can realize the above-mentioned centralized air conditioning terminal metering and control method. The centralized air conditioning terminal metering and control device includes:

[0226] The first acquisition module 1410 is used to acquire the supply and return water temperature difference and the design supply and return water temperature difference of each floor in the air conditioning chilled water system; wherein, the air conditioning chilled water system includes a horizontal pipe installed on each floor, the horizontal pipe is connected to at least one air conditioning terminal, and the horizontal pipe is equipped with a control valve for controlling the air conditioning terminal.

[0227] The regulating module 1420 is used to regulate the control valve so that the supply and return water temperature difference of the floor is equal to the design supply and return water temperature difference.

[0228] The second acquisition module 1430 is used to acquire the cooling area and hourly cooling load of the air conditioning terminal, and to measure the actual return water temperature of the air conditioning terminal for each household based on the cooling area and hourly cooling load.

[0229] The calculation module 1440 is used to calculate the supply and return water pressure difference of the horizontal pipe when the control valve is in the open state.

[0230] The control module 1450 is used to increase the supply and return water pressure difference or increase the opening of the control valve if the actual return water temperature is greater than the preset return water temperature, so that the actual return water temperature is less than or equal to the preset return water temperature.

[0231] The specific implementation method of the centralized air conditioning terminal metering and control device is basically the same as the specific implementation method of the centralized air conditioning terminal metering and control method described above, and will not be repeated here.

[0232] This application also provides an electronic device, which includes a memory and a processor. The memory stores a computer program, and the processor executes the computer program to implement the above-described centralized air conditioning terminal metering and control method. This electronic device can be any smart terminal, including tablet computers, in-vehicle computers, etc.

[0233] Please see Figure 15 , Figure 15 The hardware structure of an electronic device according to another embodiment is illustrated. The electronic device includes:

[0234] The processor 1510 can be implemented using a general-purpose central processing unit (CPU), microprocessor, application specific integrated circuit (ASIC), or one or more integrated circuits, and is used to execute relevant programs to implement the technical solutions provided in the embodiments of this application.

[0235] The memory 1520 can be implemented as a read-only memory (ROM), static storage device, dynamic storage device, or random access memory (RAM). The memory 1520 can store the operating system and other applications. When the technical solutions provided in the embodiments of this specification are implemented through software or firmware, the relevant program code is stored in the memory 1520 and called and executed by the processor 1510 to execute the centralized air conditioning terminal metering and control method of this application embodiment.

[0236] The input / output interface 1530 is used to implement information input and output;

[0237] The communication interface 1540 is used to enable communication and interaction between this device and other devices. Communication can be achieved through wired means (such as USB, Ethernet cable, etc.) or wireless means (such as mobile network, WIFI, Bluetooth, etc.).

[0238] Bus 1550 transmits information between various components of the device (e.g., processor 1510, memory 1520, input / output interface 1530, and communication interface 1540);

[0239] The processor 1510, memory 1520, input / output interface 1530 and communication interface 1540 are connected to each other within the device via bus 1550.

[0240] This application also provides a computer-readable storage medium storing a computer program that, when executed by a processor, implements the above-described centralized air conditioning terminal metering and control method.

[0241] Memory, as a non-transitory computer-readable storage medium, can be used to store non-transitory software programs and non-transitory computer-executable programs. Furthermore, memory may include high-speed random access memory, and may also include non-transitory memory, such as at least one disk storage device, flash memory device, or other non-transitory solid-state storage device. In some embodiments, memory may optionally include memory remotely located relative to the processor, and these remote memories can be connected to the processor via a network. Examples of such networks include, but are not limited to, the Internet, intranets, local area networks, mobile communication networks, and combinations thereof.

[0242] The embodiments described in this application are for the purpose of more clearly illustrating the technical solutions of the embodiments of this application, and do not constitute a limitation on the technical solutions provided by the embodiments of this application. As those skilled in the art will know, with the evolution of technology and the emergence of new application scenarios, the technical solutions provided by the embodiments of this application are also applicable to similar technical problems.

[0243] Those skilled in the art will understand that the technical solutions shown in the figures do not constitute a limitation on the embodiments of this application, and may include more or fewer steps than shown, or combine certain steps, or different steps.

[0244] Those skilled in the art will understand that all or some of the steps in the methods disclosed above, as well as the functional modules / units in the systems and devices, can be implemented as software, firmware, hardware, or suitable combinations thereof.

[0245] The terms “first,” “second,” “third,” “fourth,” etc. (if present) in the specification and accompanying drawings of this application are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate so that the embodiments of this application described herein can be implemented in orders other than those illustrated or described herein. Furthermore, the terms “comprising” and “having,” and any variations thereof, are intended to cover non-exclusive inclusion; for example, a process, method, system, product, or apparatus that comprises a series of steps or units is not necessarily limited to those steps or units explicitly listed, but may include other steps or units not explicitly listed or inherent to such processes, methods, products, or apparatus.

[0246] It should be understood that in this application, "at least one (item)" means one or more, and "more than" means two or more. "And / or" is used to describe the relationship between related objects, indicating that three relationships can exist. For example, "A and / or B" can represent three cases: only A exists, only B exists, and both A and B exist simultaneously, where A and B can be singular or plural. The character " / " generally indicates that the preceding and following related objects are in an "or" relationship. "At least one (item) of the following" or similar expressions refer to any combination of these items, including any combination of single or plural items. For example, at least one (item) of a, b, or c can represent: a, b, c, "a and b", "a and c", "b and c", or "a and b and c", where a, b, and c can be single or multiple.

[0247] In the several embodiments provided in this application, it should be understood that the disclosed apparatus and methods can be implemented in other ways.

Claims

1. A method for centralized air conditioning terminal metering and control, characterized in that, The method includes: The system obtains the supply and return water temperature difference and the design supply and return water temperature difference for each floor in the air conditioning chilled water system; wherein, the air conditioning chilled water system includes a horizontal pipe installed on each floor, the horizontal pipe is connected to at least one air conditioning terminal, and the horizontal pipe is equipped with a control valve for controlling the air conditioning terminal; wherein, the control valve includes a static balancing valve and a regulating valve, or a differential pressure valve and a regulating valve; Adjust the control valve so that the supply and return water temperature difference of the floor is equal to the design supply and return water temperature difference; The cooling area and hourly cooling load of the air conditioning terminal are obtained, and the actual return water temperature of the air conditioning terminal is measured for each household based on the cooling area and the hourly cooling load. When the control valve is in the open state, calculate the supply and return water pressure difference of the horizontal pipe; If the actual return water temperature is greater than the preset return water temperature, then increase the supply and return water pressure difference or increase the opening of the control valve so that the actual return water temperature is less than or equal to the preset return water temperature; The horizontal pipe is equipped with a cooling capacity meter, and the calculation of the supply and return water pressure difference of the horizontal pipe includes: The chilled water flow rate of the horizontal pipe is obtained through the chilled water meter, or the chilled water flow rate is calculated based on the hourly cooling load; the supply and return water pressure difference is calculated based on the chilled water flow rate and the control valve. The step of calculating the supply and return water pressure difference based on the chilled water flow rate and the control valve includes: If the control valve includes a static balancing valve and a regulating valve, then the first valve differential pressure of the static balancing valve, the fan coil unit differential pressure of the floor, and the second valve differential pressure of the regulating valve are calculated based on the chilled water flow rate; the first valve differential pressure, the fan coil unit differential pressure, and the second valve differential pressure are summed to obtain the supply and return water pressure difference. The step of calculating the supply and return water pressure difference based on the chilled water flow rate and the control valve includes: If the control valve includes a differential pressure valve and a regulating valve, then calculate the working differential pressure of the control valve and the differential pressure of the fan coil unit on the floor based on the chilled water flow rate; obtain the control differential pressure of the control valve; sum the working differential pressure, the control differential pressure, and the differential pressure of the fan coil unit to obtain the supply and return water differential pressure. The step of metering the actual return water temperature of the air conditioning terminal for each household based on the cooling area and the hourly cooling load includes: The fan speed setting of the air conditioning terminal is obtained for each household. The fan speed setting can be any one of high speed, medium speed, low speed, and off. The heat transfer coefficient is determined based on the fan speed setting. The maximum value of the designed room temperature and the panel set temperature is selected for each household to obtain the room temperature of the air conditioning terminal. The actual return water temperature is calculated for each household based on the cooling area, the hourly cooling load, the heat transfer coefficient, and the room temperature. The method dynamically adjusts the hydraulic balance of each floor in real time, adjusts the control valves on floors that are in the open state, and shuts off the chilled water supply to floors that do not require overtime work.

2. The method according to claim 1, characterized in that, After calculating the supply and return water pressure difference of the horizontal pipe when the control valve is in the open state, the process includes: Select the maximum supply and return water pressure difference as the target pressure difference; Calculate the total chilled water flow rate of the air conditioning chilled water system; The pump head of the air conditioning chilled water system is calculated based on the target pressure difference and the total flow rate of the chilled water.

3. The method according to claim 2, characterized in that, After calculating the pump head of the air conditioning chilled water system based on the target pressure difference and the total chilled water flow rate, the method further includes: The pump efficiency is determined based on the total chilled water flow rate, the pump head, the preset pump speed, and the preset number of pumps in operation. Select the preset pump speed and preset number of pumps that maximize the pump efficiency.

4. A centralized air conditioning terminal metering and control device, characterized in that, The apparatus is used to implement the method according to any one of claims 1 to 3, the apparatus comprising: The first acquisition module is used to acquire the supply and return water temperature difference and the design supply and return water temperature difference for each floor in the air conditioning chilled water system; wherein, the air conditioning chilled water system includes a horizontal pipe installed on each floor, the horizontal pipe is connected to at least one air conditioning terminal, and the horizontal pipe is equipped with a control valve for controlling the air conditioning terminal; wherein, the control valve includes a static balancing valve and a regulating valve, or a differential pressure valve and a regulating valve; The adjustment module is used to adjust the control valve so that the supply and return water temperature difference of the floor is equal to the design supply and return water temperature difference; The second acquisition module is used to acquire the cooling area of ​​the air conditioning terminal and the hourly cooling load of the air conditioning terminal, and to measure the actual return water temperature of the air conditioning terminal for each household based on the cooling area and the hourly cooling load. The calculation module is used to calculate the supply and return water pressure difference of the horizontal pipe when the control valve is in the open state. The control module is used to increase the supply and return water pressure difference or increase the opening of the control valve if the actual return water temperature is greater than the preset return water temperature, so that the actual return water temperature is less than or equal to the preset return water temperature. The horizontal pipe is equipped with a cooling capacity meter, and the calculation of the supply and return water pressure difference of the horizontal pipe includes: The chilled water flow rate of the horizontal pipe is obtained through the chilled water meter, or the chilled water flow rate is calculated based on the hourly cooling load; the supply and return water pressure difference is calculated based on the chilled water flow rate and the control valve. The step of calculating the supply and return water pressure difference based on the chilled water flow rate and the control valve includes: If the control valve includes a static balancing valve and a regulating valve, then the first valve differential pressure of the static balancing valve, the fan coil unit differential pressure of the floor, and the second valve differential pressure of the regulating valve are calculated based on the chilled water flow rate; the first valve differential pressure, the fan coil unit differential pressure, and the second valve differential pressure are summed to obtain the supply and return water pressure difference. The step of calculating the supply and return water pressure difference based on the chilled water flow rate and the control valve includes: If the control valve includes a differential pressure valve and a regulating valve, then calculate the working differential pressure of the control valve and the differential pressure of the fan coil unit on the floor based on the chilled water flow rate; obtain the control differential pressure of the control valve; sum the working differential pressure, the control differential pressure, and the differential pressure of the fan coil unit to obtain the supply and return water differential pressure. The step of metering the actual return water temperature of the air conditioning terminal for each household based on the cooling area and the hourly cooling load includes: The fan speed setting of the air conditioning terminal is obtained for each household. The fan speed setting can be any one of high speed, medium speed, low speed, and off. The heat transfer coefficient is determined based on the fan speed setting. The maximum value of the designed room temperature and the panel set temperature is selected for each household to obtain the room temperature of the air conditioning terminal. The actual return water temperature is calculated for each household based on the cooling area, the hourly cooling load, the heat transfer coefficient, and the room temperature. The device dynamically adjusts the hydraulic balance of each floor in real time, regulates the floors where control valves are in the open state, and shuts off the chilled water supply to floors that do not require overtime work.

5. An electronic device, characterized in that, The electronic device includes a memory and a processor, the memory storing a computer program, and the processor executing the computer program to implement the method according to any one of claims 1 to 3.

6. A computer-readable storage medium storing a computer program, characterized in that, When the computer program is executed by a processor, it implements the method described in any one of claims 1 to 3.

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