A method of optimizing a cone crusher cavity

Abstract

The application discloses a conical crusher cavity optimization method, comprising the following steps: A) conical crusher material nonlinear hysteresis force model establishment; B) conical crusher dynamics analysis; C) dynamic cone lining finite element analysis; D) conical crusher cavity optimization; compared with the prior art, the cavity wear resistance and the service life of the crusher can be improved, and the use cost is reduced.

Description

[Technical Field]

[0001] This invention relates to the field of engineering machinery, specifically to a method for optimizing the cavity of a cone crusher. [Background Technology]

[0002] Cone crushers are an indispensable key piece of equipment in the crushing process of bulk materials, widely used in core pillar industries such as mining, construction, and metallurgy. They are characterized by low energy consumption, high crushing ratio, adjustable particle size, and overload protection. The crushing cavity, as a critical component of the cone crusher, directly rubs against the material during operation, and its wear performance determines the service life of the crusher. To comprehensively describe the crushing behavior of bulk materials in a layered manner, considering the nonlinear hysteresis characteristics of the material layer within the crusher cavity, a set of dynamic differential equations for the crushing model in three-dimensional space is established to analyze the influence of different parameters on the dynamic characteristics of the moving cone of the crusher. Using the geometric parameters of the liner as design variables and minimizing the force as the objective, the target-driven optimization module in finite element software is used to optimize the structural dimensions of the crusher cavity, which is of great significance for improving the wear resistance of the cavity and the service life of the crusher. [Summary of the Invention]

[0003] The purpose of this invention is to solve the problems in the prior art by proposing a method for optimizing the cavity of a cone crusher, which can improve the wear resistance of the cavity and the service life of the crusher, and reduce the operating cost.

[0004] To achieve the above objectives, this invention proposes a method for optimizing the cavity of a cone crusher, comprising the following steps:

[0005] A) Establishment of nonlinear hysteresis force model for material in cone crusher: The Bouc-Wen model is used to describe the nonlinear hysteresis force generated in the material layer during the crushing process. The model is obtained by equivalent linearization.

[0006] B) Dynamic analysis of cone crusher: Numerical calculation of the dynamic differential equations is performed using Matlab software, and the response curve of the crushing system is plotted to realize the dynamic analysis of the hydraulic cone crusher.

[0007] C) Finite element analysis of the moving cone liner: A 3D model of the moving cone liner is constructed using 3D software and saved in X_T format. The model is then imported into Hypermesh. The equivalent stress cloud map and total deformation cloud map of the moving cone liner are obtained through calculation. If the maximum equivalent stress value is much smaller than the allowable stress of the moving cone liner and the deformation is within an acceptable range, no structural optimization is required. If the maximum equivalent stress value is close to or greater than the allowable stress of the moving cone liner, it is prone to failure during the crushing process, and structural optimization is required.

[0008] D) Cone Crusher Cavity Optimization: The characteristic of the cone crusher cavity is that the fixed cone liner has a nearly straight shape, while the moving cone liner has a curved shape. Usually, the optimization of the cavity focuses on the moving cone liner. Hypermesh software has an optimization module, which requires setting three parts: design variables, constraints, and objective function. The design variables are selected as input parameters, and the maximum equivalent stress value and total deformation value of the liner are selected as output parameters. The calculation of each set of design points is performed to analyze the maximum equivalent stress value and total deformation value of the liner under various design schemes. During the calculation process, the system imports each set of design points into the 3D model of the moving cone liner, regenerates the geometric model, and then the generation of the mesh, constraints, and application of loads are automatically completed according to the initially defined state. After the calculation is completed, the system will generate the corresponding maximum equivalent stress value and total deformation value under various schemes, and select the optimal scheme according to the requirements.

[0009] Preferably, step A) involves performing an equivalent linearization process to obtain the following model:

[0010]

[0011] In the formula:

[0012]

[0013]

[0014] r = Rsin(τ)

[0015]

[0016] A - System amplitude control parameters;

[0017] β and γ-hysteresis loop size and shape control parameters;

[0018] n-Hysteresis loop smoothness control parameters for transition from elastic to inelastic regions;

[0019] - Equivalent linearization coefficient;

[0020] F - System restoring force;

[0021] r - Radial displacement of the moving cone.

[0022] Preferably, step B) includes B1 establishing the dynamic model of the cone crusher: During the crushing process of the cone crusher, its moving cone rigid body moves in three-dimensional space, undergoing axial movement Z, radial movement r, and rotation θ of the moving cone axis centerline. The position of the center of mass of the moving cone when it is at rest is O, thereby establishing the absolute coordinate system (r, θ, z) of the moving cone's motion process. The position of the center of mass of the moving cone when it is in motion is O1, thereby establishing the relative coordinate system (r1, θ1, z1) of the moving cone's motion process. The precession angle α of the moving cone is considered, and the material hysteresis force f acts on the moving cone rigid body during the crushing process. During crushing, the moving cone rigid body realizes yaw motion, and the nonlinear hysteresis force generated by the crushed material on the moving cone rigid body is considered. Since the hydraulic device of the entire system causes the moving cone to move along its axial direction, and considering that the precession angle α of the moving cone is very small, its vertical component is approximated as gravity. Therefore, the dynamic differential equation of the hydraulic cone crusher is as follows:

[0023]

[0024] m - Vibrating mass of the moving cone, kg;

[0025] m0 - Mass of the eccentric block, kg;

[0026] c2 - Radial damping coefficient of the moving cone;

[0027] r - radial displacement of the moving cone, in meters;

[0028] e - the eccentricity distance of the eccentric block, m;

[0029] θ - the angle through which the moving cone rotates, in rad;

[0030] The equivalent linear vibration system amplitude R is obtained by solving the above equation:

[0031]

[0032] In the formula:

[0033]

[0034]

[0035]

[0036] k s k x- Equivalent coefficients; β, γ - Model parameters; Before performing dynamic analysis on a cone crusher, an initial value must be given to the system. The specific parameters can be selected according to different models of cone crushers. Substitute the initial value into the above (4) equation and use Matlab to simulate the equation. The response curves of the radial amplitude R and angular velocity w of the moving cone during the crushing process can be obtained. The numerical results obtained are compared with the results after equivalent linearization. The curve fitting function can be used to obtain the specific parameters of the dynamic equation. At the same time, the response curves between the two when the material in the crushing chamber is excluded are given. According to different initial values ​​of A, m, m0, e, the change of the radial amplitude-frequency curve of the moving cone is observed, and the influence of the parameters on the crushing system is obtained. B2 The influence of system-related parameters on the dynamic characteristics of the crushing system: By changing the values ​​of the system-related parameters, the change of the amplitude-frequency curve of the moving cone during the crushing process is observed, and the influence of the numerical change on the dynamic characteristics of the crushing system is obtained.

[0037] Preferably, step C) includes C1 liner load calculation: During the crushing process, the moving cone liner will be subjected to unit loads from both its vertical and circumferential directions. Considering the hysteresis force of the material layer on the moving cone, the moving cone will generate a large resonance amplitude A. Therefore, it is necessary to take amplitude A into account when solving for the unit load in the vertical direction. Vertical load P v It can be expressed by the following formula:

[0038]

[0039] In the formula:

[0040] The value of k is obtained by conversion based on the actual working conditions of the crusher;

[0041] z i -To handle the distance from a point on the surface to the suspension point;

[0042] e- represents the lowest eccentricity of the working area of ​​the moving cone liner;

[0043] h - is the distance from the suspension point on the center line to the lowest point of the working area of ​​the moving cone liner;

[0044] α- is the engagement angle;

[0045] b - is the width of the ore discharge opening;

[0046] A - represents the amplitude of the moving cone liner when considering the action of materials;

[0047] Based on the principle of layering, the load-bearing area of ​​the moving cone liner is rationally divided into 20 layers. The crushing force of each layer is then calculated, and its variation along the circumference of that layer is studied. Ultimately, the force distribution on the surface of the fixed cone can be obtained.

[0048]

[0049] In the formula:

[0050] P c - The crushing pressure in the i-th material layer;

[0051] P i - The maximum crushing pressure in the i-th material layer;

[0052] R i - is the radius of the fixed conical section;

[0053] e i - is the distance from the center of the fixed cone section to the center of the moving cone section;

[0054] a i - is the radius of the moving cone section;

[0055] θ - is the counterclockwise rotation angle from the starting position.

[0056] Because of P v =P i Therefore, the maximum pressure P in each layer i From the above formula, we can obtain that, e i a i b i R i It can be derived through geometric relationships and practical models;

[0057] C2 Load Application and Solution: Calculate the maximum pressure load applied to each layer of the liner according to formula (8), that is, the maximum unit crushing force corresponding to θ=0. Then, select the function input method in the Hypermesh operating system, input the pressure function corresponding to each layer according to formula (9), and apply the pressure load to the working range of -45~45° of the moving cone liner layer by layer.

[0058] Preferably, step D) includes design variables D1: Since the moving cone liner is a body of revolution and an axisymmetric geometric model, when defining parameters, the geometric parameters of the moving cone liner in the two-dimensional cross-section are selected as design variables for structural optimization, and the resulting design variable column vector is as follows:

[0059] R = [R1, R2, ..., R] 20 ] T (10)

[0060] R i - is the distance from the intersection of the lowest arc of each layer and the outer curve of the two-dimensional cross-section of the liner to the central axis of the liner;

[0061] D2 Constraint Conditions: When selecting constraints for structural optimization, considering that the shape of the liner plate has the most direct impact on its working performance, geometric constraints of the design variables are selected as structural constraints to reduce stress by changing the thickness of each layer of the liner plate.

[0062] D3 Objective Function: When considering the hysteresis effect of the material layer on the moving cone liner, a large stress will be generated on the liner, which is very close to the allowable stress of the liner. This can easily cause damage to the liner during operation. Therefore, in order to improve this situation, the maximum value of the equivalent stress of the moving cone liner is selected as the objective function, in order to reduce the maximum stress value generated by the liner through structural optimization. Since the maximum value of the equivalent stress of the liner is related to the shape of the liner, the objective function is expressed in the following form:

[0063] f max (R) = f(R1, R2, ..., R) 20 (11).

[0064] As a preferred option, the design variable R is selected. i (i = 0 ~ 20) are the input parameters.

[0065] The beneficial effects of this invention are as follows: By considering the nonlinear hysteresis characteristics of the material layer within the crusher cavity, this invention establishes a set of dynamic differential equations for the crushing model in three-dimensional space, and analyzes the influence of different parameters on the dynamic characteristics of the crusher's moving cone. Using the geometric parameters of the liner as design variables and minimizing force as the objective, the target-driven optimization module in finite element software is used to optimize the structural dimensions of the crusher cavity. Compared with existing technologies, this improves the wear resistance of the cavity and the service life of the crusher, while reducing operating costs.

[0066] The features and advantages of the present invention will be described in detail through embodiments and in conjunction with the accompanying drawings. [Attached Image Description]

[0067] Figure 1 This is a flow chart for optimizing the cavity of a cone crusher;

[0068] Figure 2 It is a mesh model of a cone crusher liner;

[0069] Figure 3 It is a mesh model of a liner with a variable load applied to the i-th (i = 1 to 20) layer;

[0070] Figure 4 This is a flowchart of finite element analysis;

[0071] Figure 5 This is a stress-deformation contour map of the lining plate.

Detailed Implementation Methods

[0072] The specific process is as follows: Figure 1 As shown, this invention proposes a method for optimizing the cavity of a cone crusher (the specific process is as follows). Figure 1 (As shown), including the following steps:

[0073] A) Establishment of a Nonlinear Hysteresis Force Model for Cone Crusher Materials: In the initial crushing stage of the cone crusher, the stress between the material and the moving cone gradually increases with crushing time, while the corresponding stress-strain slope continuously accelerates. As the crushing process continues, the particle size of the material in the cavity decreases to a certain extent, resulting in a downward stratification. However, the stress between the material and the moving cone continues to increase, while the corresponding stress-strain slope continuously decreases. When the curve reaches its peak value, the crushed material enters the unloading stage, and the energy stored between the material layers is released, reacting back onto the crushed material layer in the cavity. The Bouc-Wen model is used to describe the nonlinear hysteresis force generated in the material layer during the crushing process. After equivalent linearization, the model is obtained as follows:

[0074]

[0075] In the formula:

[0076]

[0077]

[0078] r = Rsin(τ)

[0079]

[0080] A - System amplitude control parameters;

[0081] β and γ-hysteresis loop size and shape control parameters;

[0082] n-Hysteresis loop smoothness control parameters for transition from elastic to inelastic regions;

[0083] - Equivalent linearization coefficient;

[0084] F - System restoring force;

[0085] r - Radial displacement of the moving cone.

[0086] B) Dynamics analysis of cone crusher: The dynamic differential equations are numerically calculated using Matlab software, and the response curves of the crushing system are plotted to achieve dynamics analysis of the hydraulic cone crusher. The changes in the response curves under different parameter values ​​are compared to determine the degree of influence of different parameters on the crushing system of the hydraulic cone crusher, laying the foundation for the optimized design of the cone crusher.

[0087] C) Finite element analysis of the moving cone liner: A 3D model of the moving cone liner was constructed using 3D software and saved in X_T format. The model was imported into HyperMesh, and the equivalent stress contour plot and total deformation contour plot of the moving cone liner were obtained through calculation, as shown below. Figure 5 As shown, if the maximum equivalent stress is much smaller than the allowable stress of the moving cone liner and the deformation is within an acceptable range, then no structural optimization is required. If the maximum equivalent stress is close to or greater than the allowable stress of the moving cone liner, it is prone to damage during the crushing process, and then structural optimization is required.

[0088] D) Cone Crusher Cavity Optimization: The characteristic of the cone crusher cavity is that the fixed cone liner is close to a straight line, while the moving cone liner is curved. Usually, the focus of cavity optimization is on optimizing the moving cone liner. Appropriate methods are used to reduce the stress distribution on the liner, thereby extending the service life of the crusher and reducing the operating cost.

[0089] Hypermesh software has an optimization module that requires setting three parts: design variables, constraints, and objective function. The design variable R is then selected. i (i = 0 ~ 20) are the input parameters, the maximum equivalent stress value of the liner is the output parameter, and the total deformation value is the output parameter. The system performs calculations on each set of design points and analyzes the maximum equivalent stress value and total deformation value of the liner under various design schemes. During the calculation process, the system imports each set of design points into the 3D model of the moving cone liner, regenerates the geometric model, and then automatically completes the mesh generation, constraint and load application according to the initially defined state. After the calculation is completed, the system will generate the corresponding maximum equivalent stress value and total deformation value under various schemes, and select the optimal scheme according to the requirements.

[0090] Step B) includes B1. Establishing the dynamic model of the cone crusher: During the crushing process, the moving cone rigid body moves in three-dimensional space, undergoing axial movement Z, radial movement r, and rotation θ of the moving cone axis centerline. The center of mass of the moving cone when stationary is O, thus establishing the absolute coordinate system (r, θ, z) for the moving cone's motion. The center of mass of the moving cone when in motion is O1, thus establishing the relative coordinate system (r1, θ1, z1) for the moving cone's motion. The precession angle α of the moving cone is considered, and the material hysteresis force f acts on it during the crushing process. During crushing, the moving cone rigid body experiences yaw motion, considering the nonlinear hysteresis force generated by the crushed material on the moving cone rigid body. Since the hydraulic device of the entire system causes the moving cone to move along its axial direction, and considering that the precession angle α of the moving cone is very small, its vertical component is approximated as gravity. Therefore, the dynamic differential equation of the hydraulic cone crusher is as follows:

[0091]

[0092] m - Vibrating mass of the moving cone, kg;

[0093] m0 - Mass of the eccentric block, kg;

[0094] c2 - Radial damping coefficient of the moving cone;

[0095] r - radial displacement of the moving cone, in meters;

[0096] e - the eccentricity distance of the eccentric block, m;

[0097] θ - the angle through which the moving cone rotates, in rad;

[0098] The equivalent linear vibration system amplitude R is obtained by solving the above equation:

[0099]

[0100] In the formula:

[0101]

[0102]

[0103]

[0104] k s k x - Equivalent coefficients; β, γ - Model parameters; Before performing dynamic analysis on a cone crusher, an initial value must be given to the system. Specific parameters can be selected according to different models of cone crushers. Among them, commonly used parameters can be referred to Table 1. Damping coefficients and stiffness coefficients need to be obtained through experiments.

[0105] Table 1. System structural parameters

[0106]

[0107] Substituting the initial values ​​into equation (4) above, and using Matlab to simulate the equation, the response curves of the radial amplitude R and angular velocity w of the moving cone during the crushing process can be obtained. The numerical results obtained are compared with the results after equivalent linearization. The specific parameters of the dynamic equation can be obtained by using the curve fitting function. At the same time, the response curves between the two are given when the material in the crushing chamber is excluded. Based on different initial values ​​of A, m, m0, and e, the changes in the radial amplitude-frequency curve of the moving cone are observed, thereby obtaining the influence of the parameters on the crushing system.

[0108] The influence of system parameters B2 on the dynamic characteristics of the crushing system: By changing the values ​​of relevant system parameters, the changes in the amplitude-frequency response curve of the moving cone during the crushing process are observed, and the influence of numerical changes on the dynamic characteristics of the crushing system is obtained. It is not difficult to find that the amplitude-frequency response curve of the moving cone is sensitive to the changes of different system parameters during the crushing process to different degrees. The changes in the mass and eccentricity of the eccentric block make the changes in the amplitude-frequency response curve of the moving cone more sensitive. However, the changes in the mass of the moving cone and the value of parameter A in the Bou-Wen model correspond to the less sensitive amplitude-frequency response curve of the moving cone. Furthermore, with the change of parameters, the resonant frequency of the crushing system shifts to different degrees.

[0109] Step C) includes the calculation of the C1 liner load: Applying loads and constraints appropriately to the geometric model can more accurately reflect the stress state of the model and obtain more accurate solution results. During the crushing process, the moving cone liner will be subjected to unit loads from both its vertical and circumferential directions. Considering the hysteresis force of the material layer on the moving cone, a large resonance amplitude A will be generated in the moving cone. Therefore, it is necessary to consider amplitude A when solving for the unit load in the vertical direction. The vertical load P... v It can be expressed by the following formula:

[0110]

[0111] In the formula:

[0112] The value of k is obtained by conversion based on the actual working conditions of the crusher;

[0113] z i -To handle the distance from a point on the surface to the suspension point;

[0114] e- represents the lowest eccentricity of the working area of ​​the moving cone liner;

[0115] h - is the distance from the suspension point on the center line to the lowest point of the working area of ​​the moving cone liner;

[0116] α- is the engagement angle;

[0117] b - is the width of the ore discharge opening;

[0118] A - represents the amplitude of the moving cone liner when considering the action of materials;

[0119] Based on the principle of layering, the load-bearing area of ​​the moving cone liner is rationally divided into 20 layers. The crushing force of each layer is then calculated, and its variation along the circumference of that layer is studied. Ultimately, the force distribution on the surface of the fixed cone can be obtained.

[0120]

[0121] In the formula:

[0122] P c - The crushing pressure in the i-th material layer;

[0123] P i - The maximum crushing pressure in the i-th material layer;

[0124] R i - is the radius of the fixed conical section;

[0125] e i - is the distance from the center of the fixed cone section to the center of the moving cone section;

[0126] a i - is the radius of the moving cone section;

[0127] θ - is the counterclockwise rotation angle from the starting position.

[0128] Because of P v =P i Therefore, the maximum pressure P in each layer i From the above formula, we can obtain that, e i a i b i R i It can be derived through geometric relationships and practical models;

[0129] C2 Load Application and Calculation: Calculate the maximum pressure load applied to each layer of the liner according to formula (8), i.e., the maximum unit crushing force corresponding to θ = 0. Then, select the function input method in the Hypermesh operating system and input the pressure function corresponding to each layer according to formula (9). Apply the pressure load layer by layer to the working range of -45 to 45° of the moving cone liner. Figure 2 As shown.

[0130] The material parameters, including elastic modulus, Poisson's ratio, and material density, are related to the material selection. The moving cone plate is fixed to the contact surface of the moving cone during operation. Therefore, according to the actual situation, a fixed constraint is added to the contact part between the inner surface of the moving cone liner and the liner, and a full displacement constraint is added to the upper and lower end faces of the moving cone liner.

[0131] Considering both computational time and accuracy, and after trial calculations, a mesh size of 2mm is deemed reasonable for the main study area, while a mesh size of 5mm is more appropriate for areas far from stress, contact, and constraint zones. To improve mesh quality and facilitate calculation, some less important features can be simplified during modeling, such as chamfers, sharp corners, threaded decorations, and various small holes. Finite element results are significantly affected by the mesh, and the accuracy of the results needs to be judged in conjunction with actual conditions, requiring extensive knowledge of mechanics and experience. If the results do not change much before and after mesh refinement, the results are considered relatively accurate. However, when refining the mesh for sharp corners that are not circular, the stress will continuously increase, resulting in inaccurate results. To obtain accurate stress results, extrapolation can be used to calculate the stress at this location. This involves refining the mesh at a certain distance from the corner to obtain accurate stress results in the vicinity, and then interpolating based on the distance of these points from the corner to extrapolate the stress at that point. The mesh model of the liner is shown below. Figure 3 As shown

[0132] The entire simulation analysis process is as follows: Figure 4 As shown.

[0133] The equivalent stress contour diagram and total deformation contour diagram of the moving cone liner were obtained through calculation (e.g., Figure 5 (As shown). If the maximum equivalent stress is much smaller than the allowable stress of the moving cone liner and the deformation is within an acceptable range, no structural optimization is required. If the maximum equivalent stress is close to or greater than the allowable stress of the moving cone liner, and is prone to failure during the crushing process, then structural optimization is required.

[0134] Step D) includes design variables D1: Since the moving cone liner is a body of revolution and an axisymmetric geometric model, when defining parameters, the geometric parameters of the moving cone liner in the two-dimensional section are selected as design variables for structural optimization. The resulting design variable column vector is as follows:

[0135] R = [R1, R2, ..., R] 20 ] T (10)

[0136] R i - is the distance from the intersection of the lowest arc of each layer and the outer curve of the two-dimensional cross-section of the liner to the central axis of the liner;

[0137] D2 Constraint Conditions: When selecting constraints for structural optimization, considering that the shape of the liner plate has the most direct impact on its working performance, geometric constraints of the design variables are selected as structural constraints to reduce stress by changing the thickness of each layer of the liner plate.

[0138] D3 Objective Function: When considering the hysteresis effect of the material layer on the moving cone liner, a large stress will be generated on the liner, which is very close to the allowable stress of the liner. This can easily cause damage to the liner during operation. Therefore, in order to improve this situation, the maximum value of the equivalent stress of the moving cone liner is selected as the objective function, in order to reduce the maximum stress value generated by the liner through structural optimization. Since the maximum value of the equivalent stress of the liner is related to the shape of the liner, the objective function is expressed in the following form:

[0139] f max (R)=f(R1,R2,…,R 20 (11)

[0140] The above embodiments are illustrative of the present invention and are not intended to limit the present invention. Any simple modifications to the present invention are within the scope of protection of the present invention.

Claims

1. A method for optimizing the cavity of a cone crusher, characterized in that: Includes the following steps: A) Establishment of nonlinear hysteresis force model for material in cone crusher: The Bouc-Wen model is used to describe the nonlinear hysteresis force generated in the material layer during the crushing process. The model is obtained by equivalent linearization of the model. B) Dynamic analysis of cone crusher: Numerical calculation of the dynamic differential equations is performed using Matlab software, and the response curve of the crushing system is plotted to realize the dynamic analysis of the hydraulic cone crusher. C) Finite element analysis of the moving cone liner: A 3D model of the moving cone liner is constructed using 3D software and saved in X_T format. The model is then imported into Hypermesh. The equivalent stress cloud map and total deformation cloud map of the moving cone liner are obtained through calculation. If the maximum equivalent stress value is much smaller than the allowable stress of the moving cone liner and the deformation is within an acceptable range, no structural optimization is required. If the maximum equivalent stress value is close to or greater than the allowable stress of the moving cone liner, it is prone to failure during the crushing process, and structural optimization is required. D) Cone Crusher Cavity Optimization: The characteristic of the cone crusher cavity is that the fixed cone liner has a nearly straight shape, while the moving cone liner has a curved shape. Usually, the optimization of the cavity focuses on the moving cone liner. Hypermesh software has an optimization module, which requires setting three parts: design variables, constraints, and objective function. The design variables are selected as input parameters, and the maximum equivalent stress value and total deformation value of the liner are selected as output parameters. The calculation of each set of design points is performed to analyze the maximum equivalent stress value and total deformation value of the liner under various design schemes. During the calculation process, the system imports each set of design points into the 3D model of the moving cone liner, regenerates the geometric model, and then the generation of the mesh, constraints, and application of loads are automatically completed according to the initially defined state. After the calculation is completed, the system will generate the corresponding maximum equivalent stress value and total deformation value under various schemes, and select the optimal scheme according to the requirements.

2. The method for optimizing the cavity of a cone crusher as described in claim 1, characterized in that: Step A) involves equivalent linearization to obtain the following model: In the formula: r = Rsin(τ) A - System amplitude control parameters; β and γ-hysteresis loop size and shape control parameters; n-Hysteresis loop smoothness control parameters for transition from elastic to inelastic regions; - Equivalent linearization coefficient; F - System restoring force; r - Radial displacement of the moving cone.

3. The method for optimizing the cavity of a cone crusher as described in claim 1, characterized in that: Step B) includes B1. Establishing the dynamic model of the cone crusher: During the crushing process, the moving cone rigid body moves in three-dimensional space, undergoing axial movement Z, radial movement r, and rotation θ of the moving cone axis centerline. The center of mass of the moving cone when stationary is O, thus establishing the absolute coordinate system (r, θ, z) for the moving cone's motion. The center of mass of the moving cone when in motion is O1, thus establishing the relative coordinate system (r1, θ1, z1) for the moving cone's motion. The precession angle α of the moving cone is considered, and the material hysteresis force f acts on it during the crushing process. During crushing, the moving cone rigid body experiences yaw motion, considering the nonlinear hysteresis force generated by the crushed material on the moving cone rigid body. Since the hydraulic device of the entire system causes the moving cone to move along its axial direction, and considering that the precession angle α of the moving cone is very small, its vertical component is approximated as gravity. Therefore, the dynamic differential equation of the hydraulic cone crusher is as follows: m—mass of the moving cone vibrating in motion, kg; m0—mass of the eccentric block, kg; c2—Radial damping coefficient of the moving cone; r—radial displacement of the moving cone, in meters; e—eccentricity distance of the eccentric block, m; θ — the angle through which the moving cone rotates, in rad; The equivalent linear vibration system amplitude R is obtained by solving the above equation: In the formula: k s k x - Equivalent coefficients; β, γ - Model parameters; Before performing dynamic analysis on a cone crusher, an initial value must be given to the system. The specific parameters can be selected according to different models of cone crushers. Substitute the initial value into the above (4) equation and use Matlab to simulate the equation. The response curves of the radial amplitude R and angular velocity w of the moving cone during the crushing process can be obtained. The numerical results obtained are compared with the results after equivalent linearization. The curve fitting function can be used to obtain the specific parameters of the dynamic equation. At the same time, the response curves between the two when the material in the crushing chamber is excluded are given. According to different initial values ​​of A, m, m0, e, the change of the radial amplitude-frequency curve of the moving cone is observed, and the influence of the parameters on the crushing system is obtained. B2 The influence of system-related parameters on the dynamic characteristics of the crushing system: By changing the values ​​of the system-related parameters, the change of the amplitude-frequency curve of the moving cone during the crushing process is observed, and the influence of the numerical change on the dynamic characteristics of the crushing system is obtained.

4. The method for optimizing the cavity of a cone crusher as described in claim 1, characterized in that: Step C) includes the calculation of the liner load: During the crushing process, the moving cone liner will be subjected to unit loads from both its vertical and circumferential directions. Considering the hysteresis force of the material layer on the moving cone, the moving cone will generate a large resonance amplitude A. Therefore, it is necessary to take amplitude A into account when solving for the unit load in the vertical direction. Vertical load P v It can be expressed by the following formula: In the formula: The value of k is obtained by conversion based on the actual working conditions of the crusher; z i -To handle the distance from a point on the surface to the suspension point; e- represents the lowest eccentricity of the working area of ​​the moving cone liner; h - is the distance from the suspension point on the center line to the lowest point of the working area of ​​the moving cone liner; α- is the engagement angle; b - is the width of the ore discharge opening; A - represents the amplitude of the moving cone liner when considering the action of materials; Based on the principle of layering, the load-bearing area of ​​the moving cone liner is rationally divided into 20 layers. The crushing force of each layer is then calculated, and its variation along the circumference of that layer is studied. Ultimately, the force distribution on the surface of the fixed cone can be obtained. In the formula: P c - The crushing pressure in the i-th material layer; P i - The maximum crushing pressure in the i-th material layer; R i - is the radius of the fixed conical section; e i - is the distance from the center of the fixed cone section to the center of the moving cone section; a i - is the radius of the moving cone section; θ - is the counterclockwise rotation angle from the starting position; Because of P v =P i Therefore, the maximum pressure P in each layer i From the above formula, we can obtain that, e i a i b i R i It can be derived through geometric relationships and practical models; C2 Load Application and Solution: Calculate the maximum pressure load applied to each layer of the liner according to formula (8), that is, the maximum unit crushing force corresponding to θ=0. Then, select the function input method in the Hypermesh operating system, input the pressure function corresponding to each layer according to formula (9), and apply the pressure load to the working range of -45~45° of the moving cone liner layer by layer.

5. The method for optimizing the cavity of a cone crusher as described in claim 1, characterized in that: Step D) includes design variables D1: Since the moving cone liner is a body of revolution and an axisymmetric geometric model, when defining parameters, the geometric parameters of the moving cone liner in the two-dimensional section are selected as design variables for structural optimization. The resulting design variable column vector is as follows: R=[R1,R2,...,R 20 ] T (10) R i - is the distance from the intersection of the lowest arc of each layer and the outer curve of the two-dimensional cross-section of the liner to the central axis of the liner; D2 Constraint Conditions: When selecting constraints for structural optimization, considering that the shape of the liner plate has the most direct impact on its working performance, geometric constraints of the design variables are selected as structural constraints to reduce stress by changing the thickness of each layer of the liner plate. D3 Objective Function: When considering the hysteresis effect of the material layer on the moving cone liner, a large stress will be generated on the liner, which is very close to the allowable stress of the liner. This can easily cause damage to the liner during operation. Therefore, in order to improve this situation, the maximum value of the equivalent stress of the moving cone liner is selected as the objective function, in order to reduce the maximum stress value generated by the liner through structural optimization. Since the maximum value of the equivalent stress of the liner is related to the shape of the liner, the objective function is expressed in the following form: f max (R)=f(R1,R2,...,R 20 ) (11)。 6. A method for optimizing the cavity of a cone crusher as described in any one of claims 1 to 5, characterized in that: The selected design variable R i (i = 0 ~ 20) are the input parameters.

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