Hydraulic balance artificial adjusting method and device based on mechanical differential pressure measuring instrument

Abstract

The application discloses a kind of based on mechanical pressure difference measuring instrument's hydraulic balance artificial regulation method and device, belong to central heating technical field.Mechanical pressure difference measuring instrument includes transparent tubular body with scale, both ends are equipped with end sealing assembly, inside is equipped with piston assembly and elastic piece, piston assembly separates internal chamber into high-pressure area and low-pressure area, end sealing assembly is equipped with pressure guide pipe interface and exhaust valve interface.Hydraulic balance regulating device includes manual regulating valve and the pressure difference measuring instrument in each regulating unit heat inlet.Hydraulic balance artificial regulation: adjust circulating water pump to target working condition and determine required pressure difference;Measure actual pressure difference;Calculate pressure difference deviation rate and preset control interval as regulation precision evaluation basis;According to the comparison result of deviation rate and control interval, adjust manual regulating valve.The application significantly improves the pressure difference measurement precision, can effectively solve the problem of heating system hydraulic imbalance, with the advantages of investment and regulation precision high.

Description

Technical Field

[0001] This invention relates to the field of centralized heating technology, and in particular to a method for manual hydraulic balance adjustment based on a mechanical differential pressure measuring instrument, as well as a mechanical differential pressure measuring instrument and a hydraulic balance adjustment device for use in this method. Background Technology

[0002] Hydraulic imbalance is a common problem in centralized heating systems. This imbalance results in excessive flow to users near the heat source or heat exchange station and insufficient flow to users further away, leading to uneven heating and cooling, high complaint rates, increased heat and electricity consumption, and reduced economic efficiency.

[0003] The main methods for solving hydraulic imbalance problems are the return water temperature method and the flow rate method.

[0004] The return water temperature method involves installing a temperature measuring device on the return water pipe of the regulating unit to determine the imbalance of the regulating unit by measuring the return water temperature. Its main drawback is that the return water temperature has a significant lag compared to the regulating process, and during the regulation process, different regulating units may couple with each other, requiring repeated adjustments to reach the set return water temperature. This results in a long adjustment time and poor balancing effect. The flow rate method typically involves installing a fixed electromagnetic flow meter or a portable ultrasonic flow meter at the thermal inlet of the regulating unit to determine the imbalance of the regulating unit by measuring the flow rate. Its main drawbacks are that fixed electromagnetic flow meters have high water quality requirements, cannot meet the requirements of heating network circulating water, and have high installation requirements, making them difficult to adapt to the complex inlet conditions of the regulating unit. Portable ultrasonic flow measurement devices have high installation requirements, low measurement accuracy, are cumbersome to operate, and require highly skilled operators.

[0005] To address the aforementioned issues, the applicant previously proposed a static hydraulic balance intelligent regulation method based on differential pressure control (application number 2025107077163). This method involves setting up a centralized control platform at the monitoring center, on which hydraulic balancing software is installed. At the thermal inlet of each regulating unit in the centralized heating system network, electric balancing valves, valve opening signal monitoring devices, valve opening signal conversion and transmission devices, supply and return water differential pressure signal monitoring devices, and differential pressure signal conversion and transmission devices are respectively installed. The static hydraulic balancing software, based on the real-time differential pressure and differential pressure setpoint of each regulating unit, analyzes and processes the data, sending valve opening control commands to the corresponding static electric balancing valves of the regulating units, so that the real-time differential pressure values ​​of all regulating units approach the differential pressure setpoint. The advantages of this intelligent regulation system are that it achieves automation and intelligence in the regulation process. However, the system has a large investment, high operation and maintenance costs, a high failure rate, and low usage frequency—only once per heating season or even several heating seasons—resulting in low cost-effectiveness and limiting the widespread application of this system and method. Meanwhile, although pressure gauges can be used to measure differential pressure in existing heating systems, they have insurmountable accuracy defects in hydraulic balance regulation applications: because centralized heating systems need to be adapted to high-rise building conditions, there is a large static pressure in the system, and the range of conventional pressure gauges is limited by this and cannot be reduced. This is an unavoidable measure under the adaptation of operating conditions. The large range of pressure gauges directly leads to a large error in the measurement of the small differential pressure required for hydraulic balance regulation, which cannot meet the core requirement of differential pressure regulation for measurement accuracy. This has become a key bottleneck restricting the application of differential pressure regulation methods in manual regulation scenarios. Summary of the Invention

[0006] To overcome the problems of existing pressure gauges having large ranges and low accuracy, which cannot meet the requirements of small differential pressure measurement and differential pressure method for artificial hydraulic balance adjustment, this invention provides a mechanical differential pressure measuring instrument, a hydraulic balance adjustment device including the measuring instrument, and a corresponding differential pressure hydraulic balance adjustment method.

[0007] To achieve the above objectives, the technical solution adopted by the present invention is as follows: A mechanical differential pressure measuring instrument is characterized by comprising a transparent tubular body with an indicating scale, wherein end sealing assemblies are provided at both ends of the tubular body; a piston assembly is provided inside the tubular body, the piston assembly being tightly fitted with the inner wall of the tubular body and being able to slide freely along the axial direction, dividing the chamber formed by the tubular body and the end sealing assemblies at both ends into a high-pressure zone and a low-pressure zone; an elastic element is provided in the high-pressure zone or the low-pressure zone, the two ends of the elastic element being respectively connected to the piston assembly and the corresponding end sealing assembly; and a pressure guiding pipe interface and an exhaust valve interface are provided on both end sealing assemblies.

[0008] Furthermore, the end sealing assembly is assembled to the end of the tubular body using a flange connection or a sleeve connection.

[0009] Furthermore, when the sleeve is connected, the end sealing assembly and the tubular body are sealed using threads, sealing gaskets, sealant, etc.

[0010] Furthermore, the elastic element is a spring; a tension spring is used when it is located in a high-pressure area, and a compression spring is used when it is located in a low-pressure area.

[0011] Furthermore, an axial limiting structure is provided in the tubular body near the sealing components at both ends to limit the axial travel of the piston assembly and prevent the piston assembly from coming out of the tubular body.

[0012] Furthermore, the axial limiting structure is an inner liner sleeve; the inner liner sleeve is a section of tube whose outer diameter is adapted to the inner diameter of the transparent tubular body, and the inner liner sleeve is inserted into the end of the transparent tubular body and tightly fitted with its inner wall.

[0013] Furthermore, the end sealing assembly is a cylindrical body with one open end. The open end of the cylinder is sealed and fitted onto the end of the tubular body to achieve a seal. The closed end of the cylinder is set in a drum shape to improve the pressure-bearing capacity of the end sealing assembly.

[0014] Furthermore, the indicating scale is either a differential pressure scale or a displacement scale. When a displacement scale is used, the differential pressure is calculated through the correspondence between displacement and differential pressure. When a differential pressure scale is used, the differential pressure scale needs to be calibrated and set accordingly based on the actual force-displacement characteristics of the elastic element, so that the displacement position of the piston assembly under the action of differential pressure directly indicates the corresponding differential pressure value.

[0015] Furthermore, a protective sleeve is provided outside the transparent tubular body, and a window is opened on the protective sleeve for observing the pressure difference scale value.

[0016] The transparent tubular body of this invention is preferably made of plexiglass.

[0017] The mechanical differential pressure measuring instrument provided by this invention is applicable to artificial hydraulic balance adjustment based on differential pressure method.

[0018] The hydraulic balance regulating device for achieving this regulation includes a manual regulating valve installed at the thermal inlet of each regulating unit in the centralized heating system network and the aforementioned mechanical differential pressure measuring instrument. The mechanical differential pressure measuring instrument is used to measure the differential pressure of the differential pressure control loop of the regulating unit. The high-pressure zone pressure guide pipe interface and the low-pressure zone pressure guide pipe interface of the mechanical differential pressure measuring instrument are respectively connected to the high-pressure end and the low-pressure end of the differential pressure control loop through pressure guide pipes. The high-pressure end of the differential pressure control loop should be located at the starting point of the differential pressure control loop of the regulating unit, and the low-pressure end of the differential pressure control loop should be located at the ending point of the differential pressure control loop. The aforementioned mechanical differential pressure measuring instrument can significantly improve the speed and accuracy of hydraulic balance adjustment in heating pipe networks. The manual hydraulic balance adjustment method includes the following steps: S1: Adjust the circulating water pump to the target operating condition, and determine the required differential pressure of each regulating unit's differential pressure control loop under this operating condition through hydraulic calculation; S2: Measure the actual differential pressure in the differential pressure control loop of each regulating unit; S3: Based on the required differential pressure and the actual differential pressure, calculate the differential pressure deviation rate of the differential pressure control loop of each regulating unit, and preset the control range of the differential pressure deviation rate as the basis for evaluating the regulating accuracy. S4: Compare the differential pressure deviation rate of the differential pressure control loop of each regulating unit with the preset differential pressure deviation rate control range, and adjust the manual regulating valve of each regulating unit according to the comparison result.

[0019] Furthermore, the required differential pressure calculation method is as follows: based on the total circulating flow and actual supply area of ​​the system under the target operating condition, determine the average flow rate per unit actual supply area; then, combined with the pipeline configuration of the differential pressure control loop of the regulating unit and the actual supply area of ​​the differential pressure control loop, determine the required differential pressure of each regulating unit control loop through hydraulic calculation.

[0020] Further: The differential pressure deviation rate is expressed by the following formula: ; In the formula, Differential pressure deviation rate of the differential pressure control loop of the regulating unit, % The actual pressure difference in the differential pressure control loop of the regulating unit. kPa ; The required differential pressure in the differential pressure control loop of the regulating unit. kPa .

[0021] Further: The procedure for adjusting the manual regulating valve is as follows: S4.1: Identify the regulating units whose differential pressure deviation rate is less than the lower limit of the control range, and adjust their manual regulating valve opening to the maximum opening. S4.2: Identify all regulating units whose differential pressure deviation rate is greater than the upper limit of the control range, and slowly adjust the opening of their manual regulating valves to gradually reduce their differential pressure deviation rate to near the lower limit of the control range; S4.3: Determine whether there are still regulating units with differential pressure deviation rates less than the lower limit of the control range. If they still exist, further reduce the manual regulating valve of the regulating unit whose differential pressure deviation rate is within the control range but greater than a certain preset value (a certain value between the lower and upper limits). Repeat step S4.3 until the differential pressure deviation rate of all differential pressure control loops of the regulating units falls within the control range.

[0022] The advantages of this invention are explained below based on the adjustment principle: (1) The present invention uses a differential pressure measuring instrument based on the axial deformation of a spring. Compared with the current method of measuring differential pressure using two pressure gauges commonly used in heating systems, the measurement accuracy is improved by more than 10 times, which can significantly improve the accuracy of hydraulic balance adjustment.

[0023] For example, a pressure gauge commonly used in heating systems with a range of 1.6 MPa typically has 80 pressure graduations, with each smallest graduation representing a pressure difference of 20 kPa. However, the invented differential pressure measuring instrument, with a range of 50 kPa and 50 pressure graduations, has each smallest graduation representing a pressure difference of 0.5 kPa. The measurement accuracy of the two differs by a factor of 40.

[0024] (2) The present invention uses the degree of pressure difference deviation as the balance judgment index of the adjustment unit. Compared with the traditional method of using flow deviation as the balance index, it can achieve more precise adjustment requirements.

[0025] For example, when using ultrasonic flow measurement for hydraulic balancing, the flow measurement instrument has low accuracy and large error, and the flow deviation rate is generally set to ±10%. However, the pressure difference deviation rate used in this invention can be controlled more accurately within ±10%, and the corresponding flow deviation rate is within ±5%.

[0026] (3) This invention is a mechanical hydraulic balance manual adjustment device. Compared with intelligent control system, it has the advantages of low investment, low failure rate, low operating cost, high cost performance and long service life. Attached Figure Description

[0027] To more clearly illustrate the technical solutions of the embodiments of the present invention, the accompanying drawings used in the description of the embodiments will be briefly introduced below. The accompanying drawings described below are merely schematic diagrams of one embodiment of the present invention. For those skilled in the art, other similar drawings can be obtained based on these drawings.

[0028] Figure 1 This is a schematic diagram of one embodiment of the mechanical differential pressure measuring instrument of the present invention.

[0029] Figure 2 This is a schematic diagram of the structure of the second embodiment of the mechanical differential pressure measuring instrument of the present invention.

[0030] Figure 3 This is a schematic diagram of the third embodiment of the mechanical differential pressure measuring instrument of the present invention.

[0031] Figure 4 This is a schematic diagram of the arrangement of an embodiment of the hydraulic balance adjustment device of the present invention.

[0032] In the diagram: 1-Stainless steel end; 2-Acrylic glass tube; 3-High pressure end pressure guide pipe interface; 4-Exhaust valve interface; 5-Low pressure end pressure guide pipe interface; 6-Piston; 7-Limiting inner sleeve; 8-Spring; 9-First switching valve; 10-Filter; 11-Differential pressure measuring instrument; 12-Manual regulating valve; 13-Pressure gauge; 14-Exhaust valve; 15-Second switching valve; 16-Drum shape. Detailed Implementation

[0033] The embodiments of the present invention will now be described in detail with reference to the accompanying drawings and one example, so that the advantages and features of the present invention can be more easily understood by those skilled in the art, thereby making a clearer and more explicit definition of the scope of protection of the present invention. Example 1

[0034] Referring to Figure 1, the mechanical differential pressure measuring instrument embodiment of the present invention generally includes: a transparent plexiglass tube 2, a piston 6, a spring 8, and stainless steel end caps 1 located at both ends of the plexiglass tube 2; the plexiglass tube 2 has differential pressure scales on its body, the differential pressure scales corresponding to the axial displacement of the spring; the stainless steel end cap 1 is a cylindrical body with one open end, the open end of the cylinder being sealed and fitted onto the end of the plexiglass tube 2 to achieve a seal; the piston 6 is tightly assembled inside the plexiglass tube 2 and can slide freely along the axial direction of the tube body, thereby... The cavity formed by the plexiglass tube 2 and the stainless steel ends 1 at both ends is divided into a high-pressure zone and a low-pressure zone. The spring 8 is axially arranged in the high-pressure zone or the low-pressure zone. In this embodiment, the spring 8 is located in the low-pressure zone. At this time, the spring is a compression spring. One end of the spring 8 is fixedly connected to the piston 6, and the other end is fixedly connected to the corresponding stainless steel end 1 in the low-pressure zone. The stainless steel end 1 in the low-pressure zone is provided with a low-pressure end pressure guide pipe interface 5 and an exhaust valve interface 4. The stainless steel end 1 in the high-pressure zone is provided with a high-pressure end pressure guide pipe interface 3 and an exhaust valve interface 4.

[0035] In this invention, the stainless steel end cap 1 can be fitted to the end of the acrylic tube 2 using a flange connection or a sleeve connection to achieve a seal. Sleeve connections include, but are not limited to, threaded connections, sealant, and sealing gaskets. This embodiment uses a threaded connection, meaning the stainless steel end cap 1 has internal threads, and the outer wall of the acrylic tube 2 has external threads. The stainless steel end cap 1 is screwed onto the acrylic tube 2 through these internal and external threads. Of course, to prevent leakage, sealant is also used for sealing. Figure 1 It can also be seen that piston limiting structures are respectively provided inside the plexiglass tube 2 near the stainless steel ends 1 at both ends; in this embodiment, both piston limiting structures adopt a section of inner liner tube 7, which is embedded in the inner wall of both ends of the plexiglass tube 2 to limit the axial movement stroke of the piston 6 and prevent the piston 6 from moving out of the tube body.

[0036] It should be noted that the aforementioned inner sleeve 7 is only a preferred embodiment of the axial limiting structure of the present invention. In practical applications, this limiting structure can also be implemented using other conventional structures known in the art, such as providing an integrally formed limiting boss on the inner wall of the tube, or providing a limiting step on the end sealing assembly. These simple substitutions or modifications that are obvious to those skilled in the art are all within the scope of protection of the present invention. In addition, to facilitate intuitive reading or calculation of pressure difference, the initial position of the piston in the present invention preferably coincides with the 0 mark, at which time the spring is in a free state. Example 2

[0037] Referring to Figure 2, this embodiment is an alternative to Embodiment 1, except that the spring 8 is placed in the high-pressure zone. In this case, the spring 8 is a tension spring, with one end connected to the piston 6 and the other end connected to the stainless steel end 1 corresponding to the high-pressure chamber. The rest of the structure is the same as in Embodiment 1. Example 3

[0038] See Figure 3 This embodiment is based on embodiment one, but the closed ends of the two stainless steel ends are designed as drum-shaped 16 to improve the pressure bearing capacity of the end sealing assembly.

[0039] Figure 4 This is a schematic diagram of an embodiment of the hydraulic balance regulating device of the present invention. Taking one regulating unit as an example, the diagram shows that the hydraulic balance regulating device includes a manual regulating valve 12 and a differential pressure measuring instrument 11 located at the thermal inlet of the regulating unit. The high-pressure zone pressure guide pipe interface 3 of the differential pressure measuring instrument 11 is connected to the high-pressure end of the differential pressure control loop via a pressure guide pipe, and the low-pressure zone pressure guide pipe interface 5 of the differential pressure measuring instrument 11 is connected to the low-pressure end of the differential pressure control loop via a pressure guide pipe. The high and low zone exhaust valve interfaces 14 of the differential pressure measuring instrument 11 are respectively connected to the high and low zone exhaust valves. A first switching valve 9, a pressure gauge 13, and a filter 10 are provided on both the supply and return water pipelines at the thermal inlet of the regulating unit to facilitate normal heating for heat users and component maintenance. A second switching valve 15 is provided on both pressure guide pipes.

[0040] In this embodiment, the manual regulating valve 12 is installed on the return water pipe of the differential pressure control circuit of the regulating unit. The high-pressure end of the differential pressure control circuit is located on the outlet side of the thermal inlet on the water supply pipe of the regulating unit, and the low-pressure end of the differential pressure control circuit is located on the inlet side of the manual regulating valve on the return water pipe of the regulating unit.

[0041] The following describes in detail the steps of hydraulic balance adjustment using the hydraulic balance adjustment device of the present invention, taking a secondary pipe network centralized heating system as an example.

[0042] Before operation, first open the two vent valves 14 and the two second switch valves 15 to fill the high-pressure and low-pressure zones of the differential pressure measuring instrument 11 with water; after filling with water, close the two vent valves 14, and then perform hydraulic balance adjustment on the heating system.

[0043] Step 1: Adjust the operating conditions of the circulating water pump: Before operation, adjust the operating conditions of the circulating water pump to a target condition. Based on the total circulating flow rate and the actual area supplied by the system under this condition, determine the average flow rate per unit area supplied. If the total circulating flow rate is 200 tons / hour and the total area supplied is 50,000 square meters under this condition, then the average flow rate per unit area supplied is 4 kg / (h∙m³). 2 ).

[0044] Step 2: Determine the required differential pressure for each regulating unit's differential pressure control loop: Based on the system's average flow rate of 4 kg / (h∙m) per unit actual supply area under this operating condition. 2 The required differential pressure for each regulating unit's differential pressure control loop is determined through hydraulic calculations, taking into account the pipeline layout within each regulating unit's differential pressure control loop and the actual supply area of ​​each pipe section.

[0045] Step 3: Based on the required differential pressure and the actual differential pressure, calculate the differential pressure deviation rate of each regulating unit's differential pressure control loop, and set the differential pressure deviation rate control range. Use the differential pressure deviation rate control range as an evaluation index for differential pressure regulation accuracy. The differential pressure deviation rate is expressed by the following formula: ; In the formula: Differential pressure deviation rate, % The actual pressure difference in the control loop of the regulating unit. kPa ; The required differential pressure in the control loop of the regulating unit. kPa; The control range of the differential pressure deviation rate of the differential pressure control loop of the preset regulating unit is: That is, after the adjustment is completed, the minimum value of the differential pressure deviation rate of the differential pressure control loop of each adjustment unit shall not be lower than -20%, and the maximum value shall not be higher than 20%.

[0046] Step 4: Compare the differential pressure deviation rate of each regulating unit's differential pressure control loop with the preset differential pressure deviation rate control range. Based on the comparison results, manually adjust the manual regulating valve of each regulating unit. The specific method is as follows: 4.1: Control units whose differential pressure deviation rate is less than the lower limit of their control range (i.e., -20%): Identify the regulating units with a differential pressure deviation rate of less than -20%, and adjust their manual regulating valve opening to the maximum opening.

[0047] 4.2: Control units whose differential pressure deviation rate exceeds the upper limit of their control range (i.e., 20%): Identify all regulating units whose differential pressure deviation rate exceeds the upper limit of the control range (i.e., 20%), and slowly adjust the opening of their manual regulating valves until their differential pressure deviation rate gradually decreases to near the lower limit of the control range (i.e., -20%). This measure aims to proactively reduce the flow of users with excessive flow, providing adjustment space for users with insufficient flow.

[0048] 4.3: Determine whether it is necessary to further reduce the opening of the manual regulating valve of a portion of the regulating unit: Determine if there are still control units with a differential pressure deviation rate less than the lower limit of the control range (i.e., -20%). If so, further reduce the manual control valve of the control unit whose differential pressure deviation rate is within the control range but greater than a certain preset value (e.g., greater than 10% or 15%). Repeat step 4.3 until the differential pressure deviation rate of all differential pressure control loops of the regulating units falls within the control range.

[0049] The above is merely one embodiment of the present invention and is not intended to limit the technical solution. In practice, the centralized heating system can be a primary or secondary pipe network system. When it is a primary pipe network system, each regulating unit refers to the regional heating station corresponding to the primary pipe network, the manual regulating valve of each regulating unit refers to the manual regulating valve installed on the primary pipe network of each regional heating station, and the differential pressure measuring instrument is a differential pressure measuring instrument installed on the primary pipe network of each regional heat exchange station. Furthermore, in this embodiment, the exhaust valve interface and the pressure guide pipe interface are located at the upper and lower parts of the stainless steel end cap, which is only for layout illustration and not a limitation on their installation position. In practice, they can also be located on the side of the stainless steel end cap. In short, any technical solution obtained without departing from the design concept of the present invention is within the scope of protection, and the specific scope of protection is determined by the scope described in the claims.

Claims

1. A mechanical differential pressure measuring instrument, characterized in that, The device includes a transparent tubular body with indicator scales, and end sealing assemblies at both ends of the tubular body. A piston assembly is located inside the tubular body, which is tightly fitted to the inner wall of the tubular body and can slide freely along the axial direction, dividing the chamber formed by the tubular body and the end sealing assemblies into a high-pressure zone and a low-pressure zone. An elastic element is located within the high-pressure zone or low-pressure zone, with its two ends connected to the piston assembly and the corresponding end sealing assembly, respectively. Both end sealing assemblies are equipped with a pressure-conducting pipe interface and an exhaust valve interface.

2. The mechanical differential pressure measuring instrument as described in claim 1, characterized in that, The end sealing assembly is connected to the end of the tubular body by a flange.

3. The mechanical differential pressure measuring instrument as described in claim 1, characterized in that, The end sealing assembly is a cylindrical body with one open end. The open end of the cylinder is sealed and fitted onto the end of the tubular body to achieve a seal. The closed end of the cylinder is preferably set to a drum shape to improve the pressure-bearing capacity of the end sealing assembly.

4. The mechanical differential pressure measuring instrument as described in claim 1, characterized in that, The transparent tubular body is made of plexiglass; the end sealing assembly is made of stainless steel; the elastic element is a spring, with a tension spring used in high-pressure areas and a compression spring used in low-pressure areas.

5. The mechanical differential pressure measuring instrument as described in claim 1, characterized in that, An axial limiting structure is provided in the tubular body near the sealing components at both ends.

6. The mechanical differential pressure measuring instrument as described in claim 5, characterized in that, The axial limiting structure is an inner liner sleeve; the inner liner sleeve is a section of tube whose outer diameter is adapted to the inner diameter of the transparent tubular body, and the inner liner sleeve is inserted into the end of the transparent tubular body and fits tightly with its inner wall.

7. The mechanical differential pressure measuring instrument as described in claim 1, characterized in that, The indicating scale is either a differential pressure scale or a displacement scale. When a displacement scale is used, the differential pressure is calculated by the correspondence between displacement and differential pressure. When a differential pressure scale is used, the differential pressure scale needs to be set according to the actual force-displacement characteristics of the elastic element after calibration, so that the displacement position of the piston assembly under the action of differential pressure directly indicates the corresponding differential pressure value.

8. A hydraulic balance regulating device, characterized in that, The system includes a manually operated regulating valve installed at the heat inlet of each regulating unit in the centralized heating system network and a mechanical differential pressure measuring instrument as described in any one of claims 1-7; the mechanical differential pressure measuring instrument is used to measure the differential pressure of the differential pressure control loop of the regulating unit, and the high-pressure zone pressure guide pipe interface and the low-pressure zone pressure guide pipe interface of the mechanical differential pressure measuring instrument are respectively connected to the high-pressure end and the low-pressure end of the differential pressure control loop through pressure guide pipes; the high-pressure end of the differential pressure control loop should be located at the starting point of the differential pressure control loop of the regulating unit, and the low-pressure end of the differential pressure control loop should be located at the ending point of the differential pressure control loop.

9. A method for manually adjusting hydraulic balance based on a mechanical differential pressure measuring instrument, characterized in that, Includes the following steps: S1: Adjust the circulating water pump to the target operating condition, and determine the required differential pressure of each regulating unit's differential pressure control loop under this operating condition through hydraulic calculation; S2: Measure the actual differential pressure in the differential pressure control loop of each regulating unit; S3: Based on the required differential pressure and the actual differential pressure, calculate the differential pressure deviation rate of the differential pressure control loop of each regulating unit, and preset the control range of the differential pressure deviation rate as the basis for evaluating the regulating accuracy. S4: Compare the differential pressure deviation rate of the differential pressure control loop of each regulating unit with the preset differential pressure deviation rate control range, and adjust the manual regulating valve of each regulating unit according to the comparison result.

10. The method for manual adjustment of hydraulic balance based on a mechanical differential pressure measuring instrument as described in claim 9, characterized in that, The procedure for adjusting the manual regulating valve is as follows: S4.1: Identify the regulating units whose differential pressure deviation rate is less than the lower limit of the control range, and adjust their manual regulating valve opening to the maximum opening. S4.2: Identify all regulating units whose differential pressure deviation rate is greater than the upper limit of the control range, and slowly adjust the opening of their manual regulating valves to gradually reduce their differential pressure deviation rate to near the lower limit of the control range; S4.3: Determine whether there are still regulating units with differential pressure deviation rates less than the lower limit of the control range. If they still exist, further reduce the manual regulating valve of the regulating unit whose differential pressure deviation rate is within the control range but greater than a certain preset value. Repeat step S4.3 until the differential pressure deviation rate of all differential pressure control loops of the regulating units falls within the control range.

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