A main drive sealing key parameter matching method based on multi-working condition analysis

Abstract

The application discloses a kind of main drive sealing key parameter matching method based on multi-working condition analysis, comprising the following steps: ① determine the application environment of shield main drive sealing, the key parameters required by parameter matching method are measured;② the finite element model of the cross section of sealing element is established, the geometric structure of the cross section of sealing element after compression is obtained, the initial structure of the deformed sealing element is obtained based on the profile node coordinates of the deformed sealing element reconstruction plane geometric model;③ draw oil cavity flow channel, obtain cavity load by flow field analysis model, obtain the boundary pressure of sealing element in working state by finite volume method solution, and the obtained boundary pressure is discretized;④ mechanical analysis is carried out in pseudo 2D multi-working condition analysis model to obtain the stress of sealing element contact surface node;⑤ carry out friction and wear analysis.The application can reduce the consumption of grease injection amount while ensuring the sealing effect, and reduce the cost of shield construction.

Description

Technical Field

[0001] This invention relates to the field of simulation technology for the main drive seal of tunnel boring machines, and in particular to a method for matching key parameters of the main drive seal based on multi-condition analysis. Background Technology

[0002] A tunnel boring machine (TBM) is a type of mechanical equipment specifically designed for tunnel excavation. It completes the support, cutting, and excavation of the surrounding rock of a tunnel in a mechanized manner, greatly improving construction efficiency and safety. It is widely used in tunnels, subways, highways, water conservancy projects, and other fields, and is one of the most commonly used pieces of equipment in tunnel construction today.

[0003] The main drive system of a tunnel boring machine (TBM) is its core component, responsible for providing power and control. The main drive seal is a crucial part of this system, acting as an isolation barrier between the internal and external environments to prevent damage to the main bearings. Common main drive seal structures include finger seals and lip seals, both of which are annular seals. Finger seals are multi-lip rotating sealing rings, while lip seals are single-lip rotating sealing rings. Polyurethane and nitrile rubber are used as the sealing ring molding materials, respectively.

[0004] Figure 1 This illustrates a common structure for main drive seals. To ensure sealing effectiveness and prevent sediment from entering the main drive bearing, a combined structure containing multiple sealing rings is typically used in the main drive seal structure. Figure 1 Only the first sealing ring is shown (this first sealing ring is the soil-adjacent sealing ring, and this application only studies the first sealing ring). When the soil pressure (i.e., at the location of outlet 5, which leads to the soil chamber) is high, grease needs to be injected between the first sealing elements 3 to provide back pressure and ensure stable sealing chamber pressure. Among them, the sealing element 3 between oil injection hole 1 and oil injection hole 2 is in direct contact with the soil chamber (its outlet 5 leads to the soil chamber), and the working condition is the most severe. Changes in the amount of grease injected on both sides will directly affect the sealing effect. In existing shield tunneling applications, the amount of grease injected into the main drive sealing structure is often determined by empirical formulas. This method is seriously wasteful and cannot achieve the optimal sealing effect. It is necessary to construct a simulation model based on the actual inner and outer pressures of the main drive seal to establish a quantitative relationship between the working area pressure and the amount of grease injected. Summary of the Invention

[0005] The purpose of this invention is to overcome the shortcomings of the prior art and provide a method for matching key parameters of the main drive seal based on multi-condition analysis, which reduces grease consumption and lowers the cost of tunnel boring machine construction while ensuring sealing effect.

[0006] To achieve the above objectives, the present invention adopts the following technical solution:

[0007] A method for matching key parameters of the main drive seal based on multi-condition analysis includes the following steps:

[0008] ① Determine the application environment of the shield tunnel main drive seal and measure the key parameters required for the parameter matching method, including soil chamber pressure, oil injection hole one pressure, oil injection hole two pressure, oil viscosity and density, material parameters, model structure, shield rotation speed, and wear coefficient;

[0009] ②Establish a finite element model of the seal cross section to obtain the geometric structure of the seal cross section after compression. Reconstruct the planar geometric model based on the contour node coordinates of the deformed seal to obtain the initial structure of the deformed seal.

[0010] ③ Based on the initial structure of the deformed seal obtained in step ②, draw the oil cavity flow channel, input the pressure of oil injection hole one, the pressure of oil injection hole two, the pressure of earth chamber, the viscosity and density of oil into the flow field analysis model to obtain the cavity load of the sealing cavity, where the pressure of oil injection hole one and the pressure of oil injection hole two are the input pressure, and the pressure of earth chamber is the output pressure. The boundary pressure of the seal under working conditions is obtained by solving the finite volume method, and the obtained boundary pressure is discretized.

[0011] ④ Input the discretized cavity load, material parameters, model structure, and shield rotation speed into the pseudo-2D multi-condition analysis model for mechanical analysis to obtain the nodal stress of the sealing contact surface;

[0012] ⑤ Conduct friction and wear analysis, using the amount of wear as the criterion. Based on the results of the friction and wear analysis, determine whether the grease injection pressure matches the shield rotation speed. If the wear rate is greater than the maximum value, adjust the grease injection pressure until a matching effect is achieved.

[0013] In step ①, the pressure in the soil chamber is measured by a pressure sensor, the pressure of oil injection hole one and oil injection hole two are fixed set values ​​based on engineering experience, the viscosity and density of the oil are obtained by capillary testing, the material parameters of the seals are measured by a universal tensile and compressive testing machine, the model structure is measured based on its actual product, the shield rotation speed is a fixed set value based on engineering experience, and the wear coefficient is measured by a friction testing machine.

[0014] In step ②, the finite element model includes the model structure, material parameters, and boundary conditions. The model structure adopts a two-dimensional planar model, including the seal, contact surface, and groove. The seal is defined as an elastic body, and its material parameters are defined by the Mooneylin parameters. The boundary conditions include motion control, setting the contact surface position offset by a certain distance to ensure that the seal can be installed in the groove without being compressed. Then, the contact surface is pressed to the installation position to simulate the loading effect and obtain the deformation amount and position of the node after deformation.

[0015] In step ②, the formula for calculating the position of the deformed node is:

[0016] x(i)=x int +Δx

[0017] y(i)=y int +Δy

[0018] In the formula, x int ,y int The initial node coordinates are generated based on the undeformed seal profile. △x and △y are the deformation amounts of the seal profile nodes in the x and y directions obtained through finite element calculation. x(i) and y(i) are the coordinates of the i-th node after deformation.

[0019] In step ③, the oil chamber pressure on the discretized sealing unit:

[0020]

[0021] In the formula, x is the additional coordinate of the bearing boundary of the seal, representing the distance between any load and the origin of the coordinate system, p represents the distributed pressure of the oil cavity on the bearing boundary of the seal, p(i) is the oil cavity pressure on element i, and ξ1 and ξ2 are the coordinates of the start and end points of the computational domain, which are two values ​​on the coordinate x.

[0022] In step ④, a three-dimensional simulation model needs to be constructed for the rotating cavity load. The three-dimensional simulation model includes the seal, contact surface, and groove. The pseudo-2D modeling approach is adopted. The contact surface is a plane. The thickness of one unit is added to the plane seal model, and the groove is also increased with a corresponding thickness to construct a single-layer mesh model.

[0023] The mechanical analysis of the three-dimensional simulation model includes two processes: loading and motion. In the loading process, the boundary pressure obtained in step ③ is applied to the corresponding node of the seal. After the loading is completed, the motion process is initiated, and the contact surface is rotated through a certain angle to obtain the normal stress perpendicular to the contact surface on the element node.

[0024] Wear analysis is performed using the Archard model, the classic Archard model is as follows:

[0025]

[0026] In the formula: K is the wear coefficient, which can be measured experimentally; F is the normal force on the contact surface of the seal; G t H is the sliding distance between the seal and the contact surface; H is the hardness of the seal.

[0027] Differentiation yields the equation for calculating the wear rate in the direction perpendicular to the surface:

[0028]

[0029] In the formula: K is the wear coefficient, which can be measured by test; H is the hardness of the seal; σ is the normal stress on the unit node on the contact surface of the seal. It is the rate of wear change in the direction perpendicular to the surface; V rel It is the rotation speed of the tunnel boring machine.

[0030] In step ⑤, the wear rate is highest at the node where the lip of the seal is located. The lip wear is used as the matching criterion, based on the maximum allowable wear rate in the project. The wear rate, obtained based on the mechanical analysis results, is used as the criterion for judgment. like If the grease injection pressure is too high, repeat steps ③ and ④ until a matching effect is achieved. The matching standard is that the wear amount within the specified stroke is less than the expected engineering result. If the wear amount is too high, adjust the grease injection pressure and repeat the flow field analysis and mechanical analysis until the wear rate result is less than the maximum wear rate allowed by the engineering.

[0031] The specific method for adjusting the grease injection pressure is as follows: while ensuring that the pressure at injection port one is higher than the pressure in the earth chamber, simultaneously reduce the pressure at injection port one and injection port two. Then the parameter matching is completed, and the pressure of oil injection hole one and oil injection hole two at this time are output.

[0032] The beneficial effects of this invention are:

[0033] First, determining the optimal amount of grease based on simulation analysis can reduce grease consumption and lower the cost of tunnel boring machine construction.

[0034] Second, by using a pseudo-2D model to conduct mechanical analysis, the problem that traditional planar sealing research models cannot apply rotational loads is solved.

[0035] Third, this method uses real-time pressure and rotation speed as inputs to determine the amount of grease injected, enabling real-time adjustment of the amount of grease injected. Attached Figure Description

[0036] Figure 1 This is a schematic diagram of the main drive sealing structure of the present invention.

[0037] Figure 2 This is a flowchart of the present invention.

[0038] Figure 3 This is a schematic diagram illustrating the deformation analysis of the sealing element during installation according to the present invention.

[0039] Figure 4 This is a schematic diagram of the flow field analysis results of the present invention.

[0040] Figure 5 This is a schematic diagram of the pseudo-2D mechanical analysis model of the present invention.

[0041] Figure 6 for Figure 5 A partial schematic diagram (with the contact surface removed).

[0042] Figure 7 This is a schematic diagram of the mechanical analysis of the present invention.

[0043] Figure 8 for Figure 7 A magnified schematic diagram of the lip mechanics analysis.

[0044] Figure 9 for Figure 8 Trend chart of lip biomechanics analysis.

[0045] In the diagram: 1. Oil injection hole 1; 2. Oil injection hole 2; 3. Seal; 4. Contact surface; 5. Outlet; 6. Groove; 7. Lip. Detailed Implementation

[0046] The present invention will be further described below with reference to the accompanying drawings and specific embodiments:

[0047] like Figures 1-9 As shown, a method for matching key parameters of the main drive seal based on multi-condition analysis is used to obtain the pressure of oil injection port 1 and oil injection port 2 based on the operating conditions of the main drive. The method includes the following steps:

[0048] ① Determine the application environment of the shield main drive seal and measure the key parameters required for the parameter matching method, including soil chamber pressure, oil injection hole 1 pressure, oil injection hole 2 pressure, oil viscosity and density, material parameters, model structure, shield rotation speed, and wear coefficient.

[0049] The pressure in the earth chamber is measured by a pressure sensor. The pressures of oil injection hole 1 and oil injection hole 2 are fixed values ​​based on engineering experience. The viscosity and density of the oil are obtained by capillary testing. The material parameters of the seal 3 are measured by a universal tensile and compressive testing machine. The model structure is measured based on its actual product. The shield rotation speed is a fixed value based on engineering experience. The wear coefficient is measured by a friction testing machine.

[0050] ② Establish a finite element model of the cross section of seal 3 to obtain the geometric structure of the cross section of seal 3 after compression. In order to construct a more accurate main drive sealing flow channel model, it is necessary to simulate the initial deformation of the sealing cross section during installation and reconstruct the deformed cross section of the seal.

[0051] The finite element model includes the model structure, material parameters, and boundary conditions. Since the sealing system is an axisymmetric structure considering only the deformation state and neglecting the oil cavity pressure and contact surface friction, the model structure adopts a two-dimensional planar model, including the seal 3, contact surface 4, and groove 6. First, the geometry of the model structure is imported into the finite element analysis program, such as... Figure 3As shown in the left figure, the initial geometry is a planar figure composed of the initial cross-section of the seal 3 and the boundary lines of the contact surface 4, the groove 6, etc.

[0052] Next, the material parameters are defined. Seal 3 is defined as an elastomer, which uses a large-strain rubber element, and its material parameters are defined using Mooneyrin parameters. The deformation of the boundary lines such as contact surface 4 and groove 6 during the contact process is very small and can be ignored. Since only the deformed structure of seal 3 is needed, the above boundary lines are defined as rigid bodies, that is, the groove 6 and contact surface 4 are defined using rigid walls.

[0053] Next, boundary conditions are defined, including force loading and motion control. In this embodiment, there is no force loading, only motion control. Specifically, the position of the contact surface 4 is offset by a certain distance to ensure that the seal 3 can be installed in the groove 6 without being compressed (i.e., Figure 3 (Left image), then press (to) the contact surface 4. Figure 3 (for reference) to the installation location (i.e.) Figure 3 (See right figure) The simulation of loading effect yields the deformation amount and position of the deformed nodes.

[0054] Formula for calculating the position of the deformed node:

[0055] x(i)=x int +Δx

[0056] y(i)=y int +Δy

[0057] In the formula, x int ,y int The initial node coordinates are generated based on the undeformed seal profile. △x and △y are the deformation amounts of the seal profile nodes in the x and y directions obtained through finite element calculation. x(i) and y(i) are the coordinates of the i-th node after deformation.

[0058] The planar geometric model is reconstructed based on the contour node coordinates of the deformed seal 3 to obtain the initial structure of the deformed seal 3.

[0059] ③ Based on the initial structure of the deformed seal 3 obtained in step ②, draw as follows: Figure 4 The oil cavity flow channel shown is obtained by inputting the pressure of oil injection hole 1, the pressure of oil injection hole 2, the pressure of earth chamber (i.e., the pressure of outlet 5), the viscosity and density of oil into the flow field analysis model to obtain the cavity load of the sealing cavity. The sealing oil cavity flow channel is constructed based on the structure of the deformed sealing element 3 after installation.

[0060] The oil viscosity and density, the pressure of injection hole 1, the pressure of injection hole 2, and the pressure of the earth chamber are input into the flow field analysis model. The pressures of injection hole 1 and injection hole 2 are used as input pressures, and the pressure of the earth chamber is used as the output pressure. The boundary pressure of the seal under working conditions is obtained by solving the finite volume method, and the obtained boundary pressure is discretized. Since the flow field analysis obtains the continuous oil cavity pressure, it cannot be directly applied to the mechanical analysis unit. It needs to be discretized into forces at the unit level before it can be input into the subsequent mechanical analysis model.

[0061] Oil chamber pressure on the discretized sealing unit:

[0062]

[0063] In the formula, x is the additional coordinate of the bearing boundary of the seal, representing the distance between any load and the origin of the coordinate system, p represents the distributed pressure of the oil cavity on the bearing boundary of the seal, p(i) is the oil cavity pressure on element i, and ξ1 and ξ2 are the coordinates of the start and end points of the computational domain, which are two values ​​on the coordinate x.

[0064] ④ The discretized cavity load, material parameters, model structure, and shield rotation speed are input into the pseudo-2D multi-condition analysis model for mechanical analysis to obtain the stress at the contact surface nodes of the seal. In terms of modeling, since the main drive seal is a rotary seal structure, the two-dimensional cross-section simulation model used in step ② can only be used to simulate the deformation of the seal body 3 generated during the installation process. It cannot apply loads on different planes, such as rotational friction, to the seal structure. Therefore, a three-dimensional simulation model needs to be constructed for the rotational load to improve the accuracy of the model.

[0065] Reference Figure 5 The 3D simulation model includes a seal 3, a contact surface 4, and a groove 6. It adopts a pseudo-2D modeling approach. Specifically, the contact surface 4 is set as a rotating plane. The thickness of one unit is added to the plane seal 3 model, and the groove 6 is also increased with a corresponding thickness. A single-layer mesh model is constructed, and the mesh of the seal body at the contact position is locally refined. It is combined with the rotating disc-shaped contact surface 4 as a plane, and the relative friction between the single-layer mesh and the rotating disc-shaped contact surface 4 is simulated.

[0066] The diameter of the sealing element 3 used in the tunnel boring machine can reach 5-6 meters, while the widest part of the cross-section of the sealing element 3 is only 2-3 centimeters, and the cross-section size is much smaller than the diameter. The friction between the main drive shaft and the sealing body 3 can be approximated as a unidirectional linear friction. Therefore, using a rigid rotating disk (i.e., contact surface 4) instead of the drive shaft structure as the contact surface can significantly improve the calculation speed of the model while meeting the accuracy requirements.

[0067] The mechanical analysis of the 3D simulation model includes two processes: loading and motion. The loading process can be referred to step ②, only extending the planar calculation results to the 3D model. The loading process applies the discretized boundary pressure obtained in step ③ to the corresponding nodes of seal 3 (refer to...). Figure 6 After loading is completed, the motion process begins, and the contact surface 4 is controlled to rotate through a certain angle to obtain the mechanical analysis results, namely the normal stress (i.e., contact stress) perpendicular to the contact surface 4 on the unit node of the sealing component contact surface.

[0068] ⑤ Conduct friction and wear analysis, using wear amount as the judgment standard, and determine whether the grease injection pressure (pressure of injection hole 1 and pressure of injection hole 2) matches the shield rotation speed based on the friction and wear analysis results. If the wear rate is greater than the maximum value, adjust the grease injection pressure until the optimal matching effect is achieved.

[0069] Wear analysis is performed using the Archard model, the classic Archard model is as follows:

[0070]

[0071] In the formula: K is the wear coefficient, which can be measured experimentally; F is the normal force on the contact surface of the seal; G t H is the sliding distance between the seal and the contact surface; H is the hardness of the seal.

[0072] Differentiation yields the equation for calculating the wear rate in the direction perpendicular to the surface:

[0073]

[0074] In the formula: K is the wear coefficient, which can be measured by test; H is the hardness of the seal; σ is the normal stress on the unit node on the contact surface of the seal. It is the rate of wear change in the direction perpendicular to the surface; V rel It is the rotation speed of the tunnel boring machine.

[0075] The wear rate is highest at the center of the contact surface of seal 3, that is, at the node where the lip 7 of seal 3 is located (refer to...). Figures 7-9 The wear amount of lip 7 is used as the matching criterion parameter, and the maximum allowable wear rate in engineering is used as the criterion. The wear rate, obtained based on the mechanical analysis results, is used as the criterion for judgment. like If the grease injection pressure is adjusted, steps ③ and ④ are repeated until the optimal matching effect is achieved. The matching standard is that the wear amount within the specified stroke is less than the engineering expectation. If the wear amount is too large, the grease injection pressure is adjusted, and the flow field analysis and mechanical analysis are repeated until the wear rate result is less than the maximum wear rate allowed by the engineering.

[0076] The specific method for adjusting the grease injection pressure is as follows: while ensuring that the pressure at injection port 1 is higher than the pressure in the earth chamber, simultaneously reduce the pressure at injection port 1 and injection port 2. Then the parameter matching is completed, and the pressure of oil injection hole 1 and oil injection hole 2 at this time are output.

[0077] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A method for matching key parameters of the main drive seal based on multi-condition analysis, characterized in that, Includes the following steps: ① Determine the application environment of the shield main drive seal and measure the key parameters required for the parameter matching method, including soil chamber pressure, oil injection hole one (1) pressure, oil injection hole two (2) pressure, oil viscosity and density, material parameters, model structure, shield rotation speed, and wear coefficient; ②Establish a finite element model of the cross section of the seal (3) to obtain the geometric structure of the cross section of the seal (3) after compression. Reconstruct the plane geometric model based on the contour node coordinates of the deformed seal (3) to obtain the initial structure of the deformed seal (3). ③ Based on the initial structure of the deformed seal (3) obtained in step ②, draw the oil cavity flow channel, input the pressure of oil injection hole 1 (1), the pressure of oil injection hole 2 (2), the pressure of earth chamber, the viscosity and density of oil into the flow field analysis model to obtain the cavity load of the sealing cavity, where the pressure of oil injection hole 1 (1) and the pressure of oil injection hole 2 (2) are the input pressure, and the pressure of earth chamber is the output pressure. The boundary pressure of the seal under working conditions is obtained by solving the finite volume method, and the obtained boundary pressure is discretized. ④ Input the discretized cavity load, material parameters, model structure, and shield rotation speed into the pseudo-2D multi-condition analysis model for mechanical analysis to obtain the nodal stress of the sealing contact surface; ⑤ Conduct friction and wear analysis, using the amount of wear as the criterion. Based on the results of the friction and wear analysis, determine whether the grease injection pressure matches the shield rotation speed. If the wear rate is greater than the maximum value, adjust the grease injection pressure until a matching effect is achieved.

2. The method for matching key parameters of the main drive seal based on multi-condition analysis as described in claim 1, characterized in that, In step ①, the pressure of the soil chamber is measured by a pressure sensor. The pressure of oil injection hole one (1) and oil injection hole two (2) are fixed values ​​based on engineering experience. The viscosity and density of the oil are obtained by capillary testing. The material parameters of the seal (3) are measured by a universal tensile and compressive testing machine. The model structure is measured according to its actual product. The shield rotation speed is a fixed value based on engineering experience. The wear coefficient is measured by a friction testing machine.

3. The method for matching key parameters of the main drive seal based on multi-condition analysis as described in claim 1, characterized in that, In step ②, the finite element model includes model structure, material parameters and boundary conditions. The model structure adopts a two-dimensional planar model, including seal (3), contact surface (4) and groove (6). The seal (3) is defined as an elastic body, and its material parameters are defined by the Munirelli parameters. The boundary conditions include motion control, setting the position of the contact surface (4) to be offset by a certain distance to ensure that the seal (3) can be installed in the groove (6) without being compressed. Then, the contact surface (4) is pressed to the installation position to simulate the loading effect and obtain the deformation amount and position of the node after deformation.

4. The method for matching key parameters of the main drive seal based on multi-condition analysis as described in claim 1, characterized in that, In step ②, the formula for calculating the position of the deformed node is: x(i)=x int +Δx y(i)=y int +Δy In the formula, x int ,y int The initial node coordinates are generated based on the undeformed seal profile. △x and △y are the deformation amounts of the seal profile nodes in the x and y directions obtained through finite element calculation. x(i) and y(i) are the coordinates of the i-th node after deformation.

5. The method for matching key parameters of the main drive seal based on multi-condition analysis as described in claim 1, characterized in that, In step ③, the oil chamber pressure on the discretized sealing unit: In the formula, x is the additional coordinate of the bearing boundary of the seal, representing the distance between any load and the origin of the coordinate system, p represents the distributed pressure of the oil cavity on the bearing boundary of the seal, p(i) is the oil cavity pressure on element i, and ξ1 and ξ2 are the coordinates of the start and end points of the computational domain, which are two values ​​on the coordinate x.

6. The method for matching key parameters of the main drive seal based on multi-condition analysis as described in claim 1, characterized in that, In step ④, a three-dimensional simulation model needs to be constructed for the rotating cavity load. The three-dimensional simulation model includes the seal (3), the contact surface (4), and the groove (6). The pseudo-2D modeling approach is adopted. The contact surface (4) is a plane. The thickness of one unit is added to the plane seal (3) model, and the groove (6) is also increased accordingly to construct a single-layer mesh model.

7. The method for matching key parameters of the main drive seal based on multi-condition analysis as described in claim 6, characterized in that, The mechanical analysis of the three-dimensional simulation model includes two processes: loading and motion. In the loading process, the boundary pressure obtained in step ③ is applied to the corresponding node of the seal (3). After the loading is completed, the motion process is initiated, and the contact surface (4) is rotated through a certain angle to obtain the normal stress perpendicular to the contact surface (4) on the unit node.

8. The method for matching key parameters of the main drive seal based on multi-condition analysis as described in claim 1, characterized in that, Wear analysis is performed using the Archard model, the classic Archard model is as follows: In the formula: K is the wear coefficient, which can be measured experimentally; F is the normal force on the contact surface of the seal; G t H is the sliding distance between the seal and the contact surface; H is the hardness of the seal. Differentiation yields the equation for calculating the wear rate in the direction perpendicular to the surface: In the formula: K is the wear coefficient, which can be measured by test; H is the hardness of the seal; σ is the normal stress on the unit node on the contact surface of the seal. It is the rate of wear change in the direction perpendicular to the surface; V rel It is the rotation speed of the tunnel boring machine.

9. The method for matching key parameters of the main drive seal based on multi-condition analysis as described in claim 8, characterized in that, In step ⑤, the node where the lip (7) of the seal (3) is located has the highest wear rate. The wear amount of the lip (7) is used as the matching judgment parameter, and the maximum wear rate allowed by the project is used as the standard. The wear rate, obtained based on the mechanical analysis results, is used as the criterion for judgment. like If the grease injection pressure is too high, repeat steps ③ and ④ until a matching effect is achieved. The matching standard is that the wear amount within the specified stroke is less than the expected engineering result. If the wear amount is too high, adjust the grease injection pressure and repeat the flow field analysis and mechanical analysis until the wear rate result is less than the maximum wear rate allowed by the engineering.

10. The method for matching key parameters of the main drive seal based on multi-condition analysis as described in claim 9, characterized in that, The specific method for adjusting the grease injection pressure is as follows: while ensuring that the pressure at injection hole one (1) is higher than the pressure at the earth chamber, simultaneously reduce the pressure at injection hole one (1) and injection hole two (2), such as... Then the parameter matching is completed, and the pressure of oil injection hole one (1) and oil injection hole two (2) at this time are output.

Images