A sliding block and ship hull side suction gap monitoring system

Abstract

The present application provides a kind of sliding block and ship side suction gap monitoring system, it is applied to dredger cabin loading system safety monitoring, including remote computing center, dredger shipborne operation monitoring system;The remote computing center is used as offline end, for each model of in-service dredger respectively generates multiple groups "working condition-side suction gap and mud pump suction vacuum relative difference" quadratic fitting formula, generates the corresponding dredger configuration file of each model dredger, for the in-service dredger shipborne operation monitoring system distributed in field use;The dredger shipborne operation monitoring system calculates target value according to the dredger configuration file and real-time measurement data, i.e.the sliding block and ship side suction gap.The present application solves the problem that the sliding block and ship suction gap can only be measured by entering the ship dock, ensures the ship to run in high efficiency state, has practicality, and application value is great.

Description

Technical Field

[0001] This invention belongs to the technical fields of dredging vessels and fluid mechanics. Background Technology

[0002] As a component of the trailing suction hopper dredger's conveying system, the sliding block's fit with the hull's side suction inlet directly affects the vessel's dredging efficiency. During the sliding motion, uneven wear creates gaps between the sliding block and the hull's side suction inlet, allowing surrounding fluid to enter the loading pipeline. This alters the vessel's operational parameters and directly impacts dredging efficiency; the larger the gap, the lower the efficiency. When dredging efficiency decreases to a certain extent, vulnerable parts should be replaced promptly to adjust the gap value.

[0003] The slider is installed below the waterline, making it impossible to directly measure the gap between the slider and the hull's side suction port during construction. Currently, the timing of maintenance and repair of the slider and hull's side suction port relies solely on experience. Generally, by the time replacement is determined, the wear between the slider and the hull is already very severe, and the gap is already very noticeable. This usually results in the ship operating in an inefficient state for extended periods. Summary of the Invention

[0004] To address the problems of existing technologies, this invention proposes a gap monitoring system between a slider and the hull side suction port. This system can indirectly obtain the gap between the slider and the hull side suction port through numerical simulation calculations combined with measurement data. By adjusting the gap value in a timely manner, the system ensures that the ship operates in a high-efficiency state.

[0005] The technical solution of this invention is as follows:

[0006] A gap monitoring system between a slider and the hull side suction port is applied to the safety monitoring of the dredger's loading and conveying system. The dredger's loading and conveying system includes: a rake arm pipe, a slider, a loading pipe, and a mud pump. The loading pipe includes two sections: one is a suction pipe from the hull side suction port to the mud pump suction port, and the other is an inlet pipe from the mud pump outlet to the mud tank.

[0007] The sliding block and hull side suction port safety clearance monitoring system includes a remote computing center and a dredger onboard operation monitoring system. The remote computing center, as an offline terminal, is used to generate multiple sets of "operating condition-side suction port clearance and mud pump suction port vacuum relative difference" quadratic fitting formulas for each model of in-service dredger, and generate dredger configuration files corresponding to each model of dredger for use by the onboard operation monitoring systems of in-service dredgers distributed on site. The dredger onboard operation monitoring system calculates the target value, i.e., the clearance between the sliding block and the hull side suction port, based on the dredger configuration file and real-time measurement data.

[0008] Details are as follows:

[0009] 1. The remote computing center calculates multiple sets of quadratic fitting formulas for "operating condition - relative difference between side suction port gap and mud pump suction port vacuum" for each type of dredger and saves them to the dredger configuration file; the remote computing center includes a database of in-service ship assets and a simulation system;

[0010] The in-service vessel asset database stores the performance parameters of the mud pumps, boom pipes, and loading pipes of the dredgers in service; specifically:

[0011] The performance parameters of the mud pump include: mud pump speed n and flow-head curve;

[0012] The parameters of the rake arm pipe include: rake arm pipe diameter D1, straight pipe length, bend angle and number of bends, and rubber joints and their quantity;

[0013] The parameters of the loading pipe include the parameters of the suction pipe and the parameters of the inlet pipe. The parameters of the suction pipe include: the diameter of the suction pipe D2, the length of the straight pipe, the angle and number of bends, the number of tees, and the number of gate valves. The parameters of the inlet pipe include: the diameter of the inlet pipe D3, the length of the straight pipe, the height difference in the inlet C, the angle and number of bends, the number of tees, and the number of gate valves.

[0014] The simulation system includes: a parameter input module, a mud pump modeling module, a rake arm pipe modeling module, a suction pipe modeling module, an inlet pipe modeling module, a mud pump suction port vacuum relative difference calculation module, a curve fitting module, and a result saving module;

[0015] The parameter input module reads parameters from the vessel's asset database and simultaneously acquires construction condition parameters from external sources. These parameters are provided to the mud pump modeling module, rake arm pipe modeling module, suction pipe modeling module, and inlet pipe modeling module. The construction condition parameters include: liquid density ρ. 液 1. Drainage depth A and average waterline B;

[0016] The mud pump modeling module establishes a head-flow velocity quadratic fitting formula for the mud pump based on the mud pump performance parameters, and provides it to the mud pump suction port vacuum relative difference calculation module.

[0017] The rake arm pipe modeling module calculates the pipe friction loss and local resistance loss of the rake arm pipe under different flow velocities based on the rake arm pipe parameters, and establishes a pipe resistance-flow velocity quadratic fitting formula for the rake arm pipe, which is then provided to the mud pump suction port vacuum relative difference calculation module.

[0018] The suction pipe modeling module calculates the friction loss and local resistance loss of the suction pipe under different flow rates based on the suction pipe parameters, and establishes a pipe resistance-flow velocity quadratic fitting formula for the suction pipe, which is then provided to the vacuum relative difference calculation module at the mud pump suction port.

[0019] The inlet pipe modeling module calculates the pipe friction loss and local resistance loss of the inlet pipe under different flow velocities based on the inlet pipe parameters, and establishes a pipe resistance-flow velocity quadratic fitting formula for the inlet pipe, which is provided to the mud pump suction port vacuum relative difference calculation module; wherein the flow velocity in the inlet pipe fitting formula refers to the flow velocity converted to the diameter of the hull side suction port.

[0020] The mud pump suction port vacuum relative difference calculation module first establishes a computational fluid dynamics model of the corresponding dredging vessel loading and conveying system, and solves the mud pump suction port vacuum relative difference under different slider and hull side suction port gaps.

[0021] The computational fluid dynamics model is constructed as follows: a geometric solid model is established only for the fluid domain of the slider (excluding fluid domain solid models such as the rake arm pipe, mud pump, and loading pipe). To improve computational stability, straight pipe extension sections are constructed before and after the slider. The model contains two inlet boundaries and one outlet boundary. Inlet 1 boundary is located in the inlet extension section, which is the direction in which mud flows in through the rake arm pipe. Inlet 2 boundary is located at the gap position, which is the direction in which liquid around the rake arm pipe flows into the pipe through the gap between the slider and the hull side suction port. The outlet boundary is located at the inlet position of the suction pipe, which is the direction in which the fluid enters the suction pipe after passing through the slider.

[0022] Furthermore, the computational fluid dynamics model of the dredger loading and conveying system adopts a simplified model, which includes the gap between the slider and the hull side suction port and the straight pipe extension sections before and after the gap, wherein the length of the straight pipe extension sections before and after the gap is 5 to 10 times the diameter D1 of the rake arm pipe suction port;

[0023] In the boundary conditions of this model, the boundary parameters of inlet 1 include construction condition parameters and rake arm pipe parameters, the boundary parameters of inlet 2 include construction condition parameters, and the boundary parameters of outlet include suction pipe, mud pump and loading pipe parameters.

[0024] The boundary condition for inlet 1 is set to total pressure inlet: TP1=P0+(AB-H2)×ρ 液 ×g;

[0025] The boundary condition for inlet 2 is set to total pressure inlet: TP2=P0+(AB)×ρ 液 ×g;

[0026] The outlet boundary condition is set to static pressure outlet: JP=P0+(C+H3+H4-H1)×ρ 液 ×g;

[0027] Where A represents dredging depth, B represents average tank waterline, C represents tank entry elevation difference, H1 is mud pump head, H2 is rake arm pipeline resistance, H3 is suction pipeline resistance, H4 is tank entry pipeline resistance, and ρ 液ρ is the liquid density; TP1 and TP2 are the total pressures at inlet 1 and inlet 2, respectively, in Pa; JP is the static pressure at the outlet, in Pa; P0 is the atmospheric pressure, in Pa; g is the acceleration due to gravity, in m / s². 2 ;

[0028] The mud pump head, rake arm pipe resistance, suction pipe resistance, and inlet pipe resistance obtained from the mud pump modeling module, rake arm pipe modeling module, suction pipe modeling module, and inlet pipe modeling module are substituted into the boundary conditions of the computational fluid dynamics model. The vacuum value of the mud pump suction port is calculated using commercial CFD software (the calculation process is existing technology and can be completed using commercially available software such as Ansys CFX and FLUNET), and the relative difference of the mud pump suction port vacuum compared to the gapless state is obtained. The gap value of the model is transformed, and multiple sets of data on the relative difference of the gap between the slider and the hull side suction port and the mud pump suction port vacuum are calculated and provided to the curve fitting module.

[0029] The suction port vacuum is equal to the absolute pressure minus the atmospheric pressure. The relative difference of suction port vacuum is defined as:

[0030]

[0031] The curve fitting module performs curve fitting based on multiple sets of data on the gap between the slider and the hull side suction port - the vacuum relative difference of the mud pump suction port obtained by the mud pump suction port vacuum relative difference calculation module, and obtains a quadratic fitting formula for the gap between the slider and the hull side suction port - the vacuum relative difference of the mud pump suction port.

[0032] The result saving module is used to save the results as a dredger configuration file; for each type of dredger, multiple sets of quadratic fitting formulas are generated for the relative difference between the working condition-side suction port gap and the mud pump suction port vacuum, and the results are saved as a dredger configuration file for use in the dredger's onboard operation monitoring system.

[0033] 2. The dredging vessel's onboard operation monitoring system includes a suction port vacuum measurement module, a parameter configuration module, a gap calculation module, and a display and alarm module.

[0034] The suction port vacuum measurement module includes a suction port vacuum gauge, which is installed on the mud suction pipe near the mud pump and is used to measure the vacuum value at the mud pump suction port.

[0035] The parameter configuration module includes a working condition information configuration module and an operation parameter configuration module. The working condition information configuration module reads the dredger configuration file (generated by the remote computing center) and generates a quadratic fitting formula mapping table of the relative difference between the working condition-side suction port gap and the mud pump suction port vacuum, which is then provided to the gap calculation module.

[0036] The operation parameter configuration module is used to set the parameters for this dredging operation, determine the current working condition of the dredging vessel based on the parameters, and provide them to the gap calculation module.

[0037] The gap calculation module performs the following functions: based on the dredger working condition determined by the operation parameter configuration module and the mapping table of the quadratic fitting formula for the relative difference between the working condition-side suction port gap and the mud pump suction port vacuum obtained by the working condition information configuration module, it selects the quadratic fitting formula for the relative difference between the side suction port gap and the mud pump suction port vacuum used in this operation; during the operation, it obtains the suction port vacuum value measured by the suction port vacuum measurement module, and calculates the real-time gap between the slider and the hull side suction port according to the quadratic fitting formula for the relative difference between the side suction port gap and the mud pump suction port vacuum.

[0038] The display alarm module is used to display the gap between the slider and the suction port on the side of the hull. When the gap value is greater than a preset threshold, an alarm message is displayed.

[0039] Furthermore, the dredger can operate in the side suction port gap test mode. The operating parameters are adjusted and set according to the operating parameters in the dredger configuration file. Then, the mud pump is started to pump water. By measuring the vacuum value of the mud pump suction port, the gap between the slider and the side suction port of the hull is obtained using the above-mentioned dredger onboard operation monitoring system.

[0040] Beneficial effects

[0041] This invention provides a system for monitoring the gap between a slider and the hull side suction port. By employing a numerical simulation method, the corresponding relationship between the gap and the relative difference in vacuum at the mud pump suction port is obtained. Thus, based on the changes in vacuum at the mud pump suction port under the same construction conditions, the gap value between the slider and the hull side suction port can be indirectly obtained. This solves the problem that the gap between the slider and the hull suction port can only be measured by entering the dry dock. It is practical and has great application value. Attached Figure Description

[0042] Figure 1 Example 1: Diagram of the loading and conveying system for a 4500 cubic meter trailing suction hopper dredger;

[0043] Figure 2 Simplified schematic diagram of the conveying system in Example 1;

[0044] Figure 3 This is a flowchart of a method for indirectly determining the gap between the slider and the suction port on the side of the hull according to the present invention;

[0045] Figure 4 The flow rate-head curve of the mud pump in Example 1;

[0046] Figure 5 Example 1: Schematic diagram of the rake arm tube and its parameters;

[0047] Figure 6Example 1: Schematic diagram of the suction pipe and its parameters;

[0048] Figure 7 Example 1: Schematic diagram of the inlet pipe and its parameters;

[0049] Figure 8 Example 1: Model of the gap between the slider and the hull side suction port;

[0050] Figure 9 The outer side (of the dredger) where the slider connects to the rake arm pipe;

[0051] Figure 10 The slider of the dredger and one side (inside) of the side suction port section;

[0052] Figure 11 Example 2: Schematic diagram of the gap monitoring system between the slider and the hull side suction port;

[0053] Figure 12 Module configuration diagram of the simulation system of this invention;

[0054] Figure 13 Diagram showing the module composition of the dredging vessel onboard operation monitoring system of this invention. Detailed Implementation

[0055] The technical solutions provided in this application will be further described below with reference to specific embodiments and accompanying drawings. The advantages and features of this application will become clearer from the following description.

[0056] It should be noted that the embodiments of this application are preferred for implementation and are not intended to limit the application in any way. The technical features or combinations of technical features described in the embodiments of this application should not be considered isolated; they can be combined with each other to achieve better technical effects. The scope of the preferred embodiments of this application may also include other implementations, and this should be understood by those skilled in the art to which the embodiments of this application pertain.

[0057] Techniques, methods, and apparatus known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and apparatus should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limiting. Therefore, other examples of exemplary embodiments may have different values.

[0058] The accompanying drawings in this application are all in a very simplified form and use non-precise proportions, intended only to facilitate and clarify the illustration of the embodiments of this application, and are not intended to limit the implementation of this application. Any modifications to the structure, changes in the proportional relationships, or adjustments to the size, without affecting the effects and purposes achieved by this application, should fall within the scope of the technical content disclosed in this application. Furthermore, the same reference numerals appearing in the various drawings of this application represent the same features or components, and can be applied to different embodiments.

[0059] Example 1

[0060] This embodiment uses the conveying system of a 4500 cubic meter trailing suction hopper dredger as an example for illustration, but the scope of protection of this invention is not limited to this. Different ship types have different parameters, but the overall model is similar. This method can also be applied to the conveying systems of other different types of trailing suction hopper dredgers.

[0061] Figure 1 This diagram shows the loading and conveying system for a 4500 cubic meter trailing suction hopper dredger. The arrows in the diagram indicate the direction of the conveyed liquid flow.

[0062] Figure 2 This is a simplified schematic diagram of the dredger's loading and conveying system, including the rake arm pipe, slider, suction pipe, mud pump, and inlet pipe. Some components in the conveying system, such as bends, tees, and gate valves, are not shown. A vacuum gauge is installed on the suction pipe near the mud pump. In the diagram, A represents the dredging depth, B represents the average tank waterline, C represents the inlet height difference, and D represents the gap between the slider and the suction port on the hull side.

[0063] The ship's operational parameters include: liquid density ρ 液 =1000kg / m 3 The dredging depth is A = 20m and the average waterline is B = 18m.

[0064] The performance parameters of the mud pump are as follows: mud pump suction diameter 900mm, mud pump speed 214rpm, flow rate-head curve. Figure 4 As shown (the above parameters can be obtained from the mud pump's user manual).

[0065] Based on the above mud pump performance parameters, the head-velocity quadratic fitting formula for the mud pump is obtained: H1 = 0.1167v 2 -2.0459v +31.317;

[0066] Where H1 is the mud pump head in meters; v is the flow velocity at the suction inlet of the rake arm (900 mm in diameter) in meters per second.

[0067] The rake arm tube is composed of, for example Figure 5 As shown, the parameters are as follows: rake arm pipe diameter 900mm, one 90-degree bend, two rubber joints, and straight pipe length 40m.

[0068] Based on the above rake arm pipe parameters, the pipe friction loss and local resistance loss of the rake arm pipe under different flow velocities are calculated, and a quadratic fitting formula for pipe resistance-flow velocity of the rake arm pipe is established: H2 = 8.699 * 10 -2 v 2 +1.1795*10 -15 v-2.0773*10 -15 ;

[0069] Where H2 is the pipe resistance of the rake arm pipeline, in meters;

[0070] The suction pipe is composed of, for example Figure 6 As shown, the parameters are as follows: suction pipe diameter 900mm, straight pipe length 2m, two 90-degree bends, one tee, and one gate valve. Calculate the pipe friction loss and local resistance loss of the suction pipe under different flow velocities, and establish a quadratic fitting formula for the pipe resistance-flow velocity of the suction pipe:

[0071] H3 = 3.5204 * 10 -2 v 2 -9.3507*10 -16 v+1.651*10 -15 ;

[0072] Where H3 is the resistance of the suction pipe, in meters (m);

[0073] The inlet tube is composed of, for example Figure 7 As shown, the parameters are as follows: inlet pipe diameter 850mm, straight pipe length 39m, inlet height difference C = 8m. Figure 2 (As shown), 2 tees, 3 gate valves, and 2 90-degree bends, etc. Calculate the pipe friction loss and local resistance loss of the inlet pipe under different flow velocities, and establish a quadratic fitting formula for the pipe resistance-flow velocity of the inlet pipe:

[0074] H4 = 1.4252 * 10 -1 v 2 -5.1901*10 -16 v-4.3932*10 -16 ;

[0075] Where H4 is the pipe resistance of the inlet pipe, in meters; the flow velocity in the formula refers to the flow velocity converted to the diameter of the hull side suction port.

[0076] The calculation methods for H2, H3, and H4 are similar; let's take H3 as an example:

[0077] Straight pipe, resistance loss type:

[0078]

[0079] Where L represents the pipe length and d represents the pipe diameter;

[0080] Losses at locations such as elbows, rubber short pipes, and gate valves are called local losses, and their types are as follows:

[0081]

[0082] The drag coefficients λ and ξ mentioned above are selected based on engineering experience, as follows:

[0083] The straight pipe resistance coefficient is 0.012. Since the straight pipe is relatively short, its impact on resistance is negligible.

[0084] The resistance coefficient for a 90-degree bend is 0.045.

[0085] The resistance coefficient of the tee is set to 0.55;

[0086] The resistance coefficient of the gate valve is set to 0.05.

[0087] The local resistance loss is calculated according to formula (2), as shown in the table below:

[0088] Flow rate Three-way 90-degree bend gate Main pipe assembly H3 = tee + 90-degree bend + gate valve 2.62 0.19 0.03 0.02 0.24 3.49 0.34 0.06 0.03 0.43 4.15 0.48 0.08 0.04 0.61 4.74 0.63 0.10 0.06 0.79 5.24 0.77 0.13 0.07 0.97

[0089] By performing a second-order fitting on the five sets of data regarding the flow velocity (v) and the main pipe assembly (H3), the fitting formula can be obtained as follows:

[0090] H3 = 3.5204 * 10 -2 v 2 -9.3507*10 -16 v+1.651*10 -15 ;

[0091] Establish a simplified model of the conveying system, such as Figure 8 As shown, the model includes the gap between the slider and the hull-side suction port, as well as the straight pipe extensions before and after the gap. The length of the inlet and outlet extensions is five times the diameter of the suction port. The model contains two inlet boundaries and one outlet boundary. Inlet 1 is located in the inlet extension, representing the direction of slurry flow through the rake arm pipe. Inlet 2 is located at the gap, representing the direction of liquid around the rake arm pipe flowing into the pipe through the gap between the slider and the hull-side suction port. The outlet boundary is located at the inlet of the suction pipe. The boundary conditions include construction condition parameters for inlet 1 and rake arm pipe, construction condition parameters for inlet 2, and parameters for the suction pipe, slurry pump, and loading pipe for the outlet.

[0092] In this calculation, the boundary condition for inlet 1 is set as total pressure inlet: TP1=P0+(AB-H2)×ρ 液 ×g;

[0093] The boundary condition for inlet 2 is set to total pressure inlet: TP2=P0+(AB)×ρ 液 ×g;

[0094] The outlet boundary condition is set to static pressure outlet: JP=P0+(C+H3+H4-H1)×ρ 液 ×g;

[0095] Where TP1 and TP2 are the total pressures at inlet 1 and inlet 2, respectively, in Pa; JP is the static pressure at the outlet, in Pa; P0 is the atmospheric pressure, in Pa; and g is the acceleration due to gravity, in m / s². 2 ;

[0096] The calculation process for JP is as follows:

[0097] The calculation is based on Bernoulli's energy equation:

[0098]

[0099] z represents position height, P represents pressure, and v represents velocity; when a water pump is installed in the pipeline, it is +Hp (i.e., H1 in this example), H 1-2 This represents the head loss of the fluid between position 1 and position 2.

[0100] Taking JP as an example, Bernoulli's equation is applied to the outlet (position 1) and loading pipe outlet (position 2) of the calculation model according to formula (3), where it is assumed that the height of the outlet boundary of the calculation model is 0, and the difference in velocity energy is ignored in the calculation, then:

[0101]

[0102] Thus obtain

[0103] JP=P0+(C+H3+H4-H1)×ρg

[0104] Where P0 is atmospheric pressure.

[0105] By inputting the simplified model and boundary conditions of the above conveying system into Ansys CFX software (a commercial CFD simulation software developed by AEA Technology for solving practical industrial problems), and through iterative solution, the static pressure JP at the outlet with different gaps can be directly obtained, thereby obtaining the vacuum P at the mud pump suction port. v =(JP-H3×ρ 液 ×g-P0) / 1000, P V The unit is kPa. Table 1 shows the calculated vacuum at the mud pump suction port for different gaps, thus enabling the establishment of a quadratic fitting formula for the relative difference between the gap between the slider and the suction port on the hull side and the vacuum at the mud pump suction port: y = -0.0997x 2+2.6083x+0.2623; where y represents the gap between the slider and the suction port on the side of the hull, in mm; and x represents the relative vacuum difference at the suction port.

[0106] Table 1 shows the calculation results of the vacuum at the mud pump suction port for different gaps.

[0107]

[0108] Based on the aforementioned quadratic fitting formula for the relative difference between the gap between the slider and the hull side suction port and the vacuum at the mud pump suction port under the same construction conditions, i.e., y = -0.0997x 2 +2.6083x+0.2623.

[0109] When the dredger is operating under the same conditions, the gap between the slider and the suction port on the side of the hull can be determined by the above formula based on the real-time vacuum value of the mud pump suction port.

[0110] Assuming that the measured vacuum at the mud pump suction port is -48.00 kPa under the above construction conditions, the relative difference between the mud pump suction port and the suction port is (-48.00 - (-49.51)) / 49.51 * 100 = 3.05. Therefore, the gap between the slider and the suction port on the side of the hull is -0.0997 * 3.05 * 3.05 + 2.6083 * 3.05 + 0.2623 = 7.29 mm.

[0111] It should be understood that the computational dynamics model described in this scheme can be obtained by first establishing a geometric solid model, then dividing the geometric model into a mesh that meets the computational accuracy requirements. Based on the actual fluid motion, a suitable solver is selected, appropriate boundary conditions are defined, and a suitable algorithm in the solver is used for discretization. After multiple iterations and convergence, the corresponding computational results can be obtained through post-processing.

[0112] It should be understood that the boundary conditions used in this solution are only one of the solutions of this invention, and those skilled in the art can reselect and combine the boundary conditions.

[0113] Example 2

[0114] A gap monitoring system between a slider and the hull side suction port is applied to the safety monitoring of the dredger's loading and conveying system. The dredger's loading and conveying system includes: a rake arm pipe, a slider, a loading pipe, and a mud pump. The loading pipe includes two sections: one is a suction pipe from the hull side suction port to the mud pump suction port, and the other is an inlet pipe from the mud pump outlet to the mud tank.

[0115] like Figure 11The monitoring system for the safe clearance between the slider and the hull side suction port includes a remote computing center and a dredger onboard operation monitoring system. The remote computing center, as an offline terminal, is used to generate multiple sets of quadratic fitting formulas for "operating condition - relative difference between the clearance of the hull side suction port and the vacuum of the mud pump suction port" for each model of in-service dredger, and to generate dredger configuration files corresponding to each model of dredger for use by the onboard operation monitoring systems of in-service dredgers distributed on site. The dredger onboard operation monitoring system downloads the dredger configuration file from the remote computing center via the Internet, calculates the clearance between the slider and the hull side suction port based on the dredger configuration file and real-time measurement data during operation, and issues an alarm when the clearance value is greater than a preset alarm value, allowing the dredger to return to port for maintenance of the slider and the hull side suction port.

[0116] The remote computing center includes a database of in-service ship assets and a simulation system; the module structure of the simulation system is shown in the diagram below. Figure 12 As shown in the figure. The simulation system includes: a parameter input module, a mud pump modeling module, a rake arm pipe modeling module, a mud suction pipe modeling module, an inlet pipe modeling module, a mud pump suction port vacuum relative difference calculation module, a curve fitting module, and a result saving module.

[0117] The dredging vessel's onboard operation monitoring system includes a suction inlet vacuum measurement module, a parameter configuration module, a gap calculation module, and a display and alarm module. For example... Figure 13 As shown.

[0118] The above description is merely a description of preferred embodiments of this application and is not intended to limit the scope of this application in any way. Any changes or modifications made by those skilled in the art based on the above-disclosed technical content should be considered as equivalent and valid embodiments and fall within the scope of protection of the technical solution of this application.

Claims

1. A gap monitoring system between a slider and a hull side suction port, applied to the safety monitoring of a dredger's loading and conveying system, the dredger's loading and conveying system comprising: The system comprises a rake arm pipe, a slider, a loading pipe, and a mud pump; the loading pipe consists of two sections: a suction pipe from the hull side suction port to the mud pump suction port, and an inlet pipe from the mud pump outlet to the mud tank; its key feature is that: The sliding block and hull side suction port safety clearance monitoring system includes a remote computing center and a dredger onboard operation monitoring system. The remote computing center, as an offline terminal, is used to generate multiple sets of "operating condition - relative difference between hull side suction port clearance and mud pump suction port vacuum" quadratic fitting formulas for each model of in-service dredger, and generate dredger configuration files corresponding to each model of dredger for use by the onboard operation monitoring systems of in-service dredgers distributed on site. The dredger onboard operation monitoring system calculates the target value, i.e., the clearance between the sliding block and the hull side suction port, based on the dredger configuration file and real-time measurement data. The remote computing center calculates multiple sets of quadratic fitting formulas for "operating condition - relative difference between side suction port gap and mud pump suction port vacuum" for each type of dredger and saves them to the dredger configuration file; the remote computing center includes a database of in-service ship assets and a simulation system. The in-service vessel asset database stores the mud pump performance parameters, rake arm pipe parameters, and hopper pipe parameters of the dredgers in service. The performance parameters of the mud pump include: mud pump speed. n Flow rate-head curve; The parameters of the rake arm pipe include: rake arm pipe diameter D1, straight pipe length, bend angle and number of bends, and rubber joints and their quantity; The loading pipe parameters include suction pipe parameters and inlet pipe parameters. The suction pipe parameters include: suction pipe diameter D2, straight pipe length, bend angle and number, number of tees, and number of gate valves. The inlet pipe parameters include: inlet pipe diameter D3, straight pipe length, inlet height difference C, bend angle and number, number of tees, and number of gate valves. The simulation system includes: a parameter input module, a mud pump modeling module, a rake arm pipe modeling module, a suction pipe modeling module, an inlet pipe modeling module, a mud pump suction port vacuum relative difference calculation module, a curve fitting module, and a result saving module; The parameter input module reads parameters from the vessel's asset database and simultaneously acquires construction condition parameters from external sources. These parameters are provided to the mud pump modeling module, rake arm pipe modeling module, suction pipe modeling module, and inlet pipe modeling module. The construction condition parameters include: liquid density. ρ 液 1. Drainage depth A and average waterline B; The mud pump modeling module establishes a head-flow velocity quadratic fitting formula for the mud pump based on the mud pump performance parameters, and provides it to the mud pump suction port vacuum relative difference calculation module. The rake arm pipe modeling module calculates the pipe friction loss and local resistance loss of the rake arm pipe under different flow velocities based on the rake arm pipe parameters, and establishes a pipe resistance-flow velocity quadratic fitting formula for the rake arm pipe, which is then provided to the mud pump suction port vacuum relative difference calculation module. The suction pipe modeling module calculates the friction loss and local resistance loss of the suction pipe under different flow rates based on the suction pipe parameters, and establishes a pipe resistance-flow velocity quadratic fitting formula for the suction pipe, which is then provided to the vacuum relative difference calculation module at the mud pump suction port. The inlet pipe modeling module calculates the pipe friction loss and local resistance loss of the inlet pipe under different flow velocities based on the inlet pipe parameters, and establishes a pipe resistance-flow velocity quadratic fitting formula for the inlet pipe, which is provided to the mud pump suction port vacuum relative difference calculation module; wherein the flow velocity in the inlet pipe fitting formula refers to the flow velocity converted to the diameter of the hull side suction port. The mud pump suction port vacuum relative difference calculation module first establishes a computational fluid dynamics model of the corresponding dredging vessel loading and conveying system, and solves the mud pump suction port vacuum relative difference under different slider and hull side suction port gaps. The curve fitting module performs curve fitting based on multiple sets of data on the gap between the slider and the hull side suction port - the vacuum relative difference of the mud pump suction port obtained by the mud pump suction port vacuum relative difference calculation module, and obtains a quadratic fitting formula for the gap between the slider and the hull side suction port - the vacuum relative difference of the mud pump suction port. The result saving module is used to save the results as a dredger configuration file; for each type of dredger, multiple sets of quadratic fitting formulas are generated based on the relative difference between the side suction port gap and the mud pump suction port vacuum under different operating conditions. ； Where y represents the gap between the slider and the suction port on the side of the hull, in mm; x represents the relative vacuum difference at the suction port; The results are saved as a configuration file for the dredger and provided to the onboard operation monitoring system of the dredger.

2. The gap monitoring system between the slider and the hull side suction port as described in claim 1, characterized in that, The computational fluid dynamics model is constructed as follows: a geometric solid model is established only for the fluid domain of the slider, excluding the fluid domain solid models of the rake arm pipe, mud pump, and loading pipe. To improve computational stability, straight pipe extension sections are constructed before and after the slider. The model contains two inlet boundaries and one outlet boundary. Inlet 1 boundary is located in the inlet extension section, which is the direction in which mud flows in through the rake arm pipe. Inlet 2 boundary is located at the gap position, which is the direction in which liquid around the rake arm pipe flows into the pipe through the gap between the slider and the hull side suction port. The outlet boundary is located at the inlet position of the suction pipe, which is the direction in which the fluid enters the suction pipe after passing through the slider. In the boundary conditions of this model, the boundary parameters of inlet 1 include construction condition parameters and rake arm pipe parameters, the boundary parameters of inlet 2 include construction condition parameters, and the boundary parameters of outlet include suction pipe, mud pump and loading pipe parameters. The boundary condition for inlet 1 is set to total pressure inlet: ; The boundary condition for inlet 2 is set to total pressure inlet: ; The outlet boundary condition is set to static pressure outlet: ; Where A represents the digging depth, B represents the average tank waterline, and C represents the tank elevation difference. H 1 represents the mud pump head. H 2 represents the pipe resistance of the rake arm pipeline. H 3 represents the resistance of the sludge suction pipe. H 4 represents the resistance of the inlet pipe. ρ 液 For the density of the liquid, TP 1、 TP 2 represents the total pressure at inlet 1 and inlet 2, respectively, in Pa; JP This is the static pressure at the outlet, in Pa. P 0 represents atmospheric pressure, measured in Pa. g This is the acceleration due to gravity, measured in m / s². 2 ; The mud pump head, rake arm pipe resistance, suction pipe resistance, and inlet pipe resistance obtained from the mud pump modeling module, rake arm pipe modeling module, suction pipe modeling module, and inlet pipe modeling module are substituted into the boundary conditions of the computational fluid dynamics model. The vacuum value of the mud pump suction port is calculated using commercial CFD software, and the relative difference of the mud pump suction port vacuum compared to the gapless state is obtained. The gap value of the model is transformed, and multiple sets of data on the relative difference of the gap between the slider and the suction port on the hull side and the mud pump suction port are calculated and provided to the curve fitting module. The suction port vacuum is equal to the absolute pressure minus the atmospheric pressure, and the relative difference of the suction port vacuum is defined as: 。 3. The gap monitoring system between the slider and the hull side suction port as described in claim 2, characterized in that, The computational fluid dynamics model of the dredger's loading and conveying system adopts a simplified model. This model includes the gap between the slider and the hull side suction port, as well as the straight pipe extensions before and after the gap. The length of the straight pipe extensions before and after the gap is 5 to 10 times the diameter D1 of the rake arm pipe suction port.

4. The gap monitoring system between the slider and the hull side suction port as described in claim 1, characterized in that, The dredger's onboard operation monitoring system includes a suction port vacuum measurement module, a parameter configuration module, a gap calculation module, and a display and alarm module. The suction port vacuum measurement module includes a suction port vacuum gauge, which is installed on the mud suction pipe near the mud pump and is used to measure the vacuum value at the mud pump suction port. The parameter configuration module includes a working condition information configuration module and an operation parameter configuration module. The working condition information configuration module reads the dredger configuration file and generates a quadratic fitting formula mapping table of the relative difference between the working condition-side suction port gap and the mud pump suction port vacuum, which is provided to the gap calculation module. The operation parameter configuration module is used to set the parameters for this dredging operation, determine the current working condition of the dredger based on the parameters, and provide it to the gap calculation module. The gap calculation module performs the following functions: based on the dredger working condition determined by the operation parameter configuration module and the mapping table of the quadratic fitting formula for the relative difference between the working condition-side suction port gap and the mud pump suction port vacuum obtained by the working condition information configuration module, it selects the quadratic fitting formula for the relative difference between the side suction port gap and the mud pump suction port vacuum used in this operation; during the operation, it obtains the suction port vacuum value measured by the suction port vacuum measurement module, and calculates the real-time gap between the slider and the hull side suction port according to the quadratic fitting formula for the relative difference between the side suction port gap and the mud pump suction port vacuum. The display alarm module is used to display the gap between the slider and the suction port on the side of the hull. When the gap value is greater than a preset threshold, an alarm message is displayed.

5. The gap monitoring system between the slider and the hull side suction port as described in claim 1, characterized in that: The dredger operates in the side suction port gap test mode. The operating parameters are adjusted and set according to the operating condition parameters in the dredger configuration file. Then, the mud pump is started to pump water. By measuring the vacuum value of the mud pump suction port, the gap between the slider and the side suction port of the hull is obtained using the above-mentioned dredger onboard operation monitoring system.

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