Slurry pump and coupling dynamics failure simulation method of transmission bearing

Abstract

The present application provides a kind of slurry pump and transmission bearing coupling dynamics fault simulation method.The method comprises: the finite element model of the impeller, volute, mixed fault and transmission bearing inner ring, outer ring, mixed fault of slurry pump is established.Simulation is carried out to slurry pump under each health state using Fluent software, the influence of the axial force generated by fluid on the dynamic characteristics of transmission bearing and stress variation law under different inlet velocities, and the variation law of slurry pump head is analyzed.The axial force generated by pump fluid is coupled to transmission bearing, and then ANSYS LS-DYNA and Fluent are used for axial force coupling simulation, the vibration characteristics of transmission bearing under different health states and the action mechanism of slurry pump axial force are analyzed.Compared with the prior art, the present application provides an effective slurry pump fault simulation analysis method, analyzes the influence of the axial force generated by slurry pump fluid on the vibration characteristics of transmission bearing and stress distribution, and the hydraulic characteristics of slurry pump body, which helps the research of slurry pump fault diagnosis.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of fluid machinery. In particular, it relates to a slurry pump and a method for simulating the coupling dynamics fault of a transmission bearing. BACKGROUND

[0002] The slurry pump is a common mechanical power equipment in fluid machinery. It is often used for sewage operation and other industrial sites. Its main components include a volute, an impeller, front and rear cavity cover plates, and other flow components. In addition, the transmission end bearing plays a supporting and load-carrying role in the transmission system of the slurry pump. Its failure occurs from time to time in complex environments, which can cause great losses to industrial production. In addition, the damage to the key components of the pump, such as the impeller and volute, will also affect the hydraulic performance of the slurry pump, thereby reducing the service life of the pump. Industrial sites generally test the hydraulic performance of the slurry pump, but when the pump fails, they do not know the specific fault type of the pump. The present application simulates slurry pumps in different health states, analyzes the change rule of the head of slurry pumps in different health states under different flow rates, and calculates the pump shaft axial force generated by the fluid medium at the shaft end of the pump. The pump shaft axial force has a certain influence on the dynamic vibration characteristics of the transmission bearing in different health states. It is very important to find the change rule of the hydraulic characteristics of slurry pumps in different health states and the influence rule of the axial force generated by the fluid medium on the dynamic characteristics of the transmission bearing. It can not only analyze the influence rule of the inlet velocity parameter of the slurry pump fluid medium on the hydraulic characteristics of the slurry pump in different health states, but also analyze the influence rule of the axial force generated by different parameter combinations on the dynamic characteristics of the transmission bearing of the slurry pump, so as to play a certain auxiliary role in the fault analysis of the slurry pump.

[0003] Current research on the fluid mechanics of slurry pumps utilizes the discrete element method (DEM) to study the impact of parameters such as the number of blades, blade fracture, and inlet flow rate on the hydraulic characteristics of slurry pumps. Alternatively, it may focus solely on the dynamic vibration characteristics of the pump shaft bearings, or investigate the pressure pulsation characteristics and the influence of slurry concentration on pump vibration. However, it fails to consider the coupling effect of the axial force generated by the fluid medium on the pump bearings. While laboratory hydraulic performance tests using small pumps are reliable, these methods do not account for the influence of the axial force generated by the slurry medium on the pump shaft and its impact on the transmission bearings. Furthermore, most experiments are conducted under optimal pump conditions. In actual production, however, the hydraulic characteristics of a slurry pump differ from those under healthy conditions when the flow components malfunction. Moreover, malfunctions may generate more pump shaft axial movement and forces, which can negatively impact the transmission bearings. Since most of the slurry pumps tested are used for production needs, and the laboratory uses good slurry pumps, the hydraulic characteristics of the pump and the changes in the axial force generated at the pump shaft end are inconsistent when the pump's flow-through components fail. The test pump cannot be damaged in a short time, and the damage cannot be detected and replaced in time. The influence and effect of the axial force generated under the failure of the slurry pump on the transmission end bearing often cannot be verified in real time.

[0004] The above content is only used to help understand the technical solution of the present invention and does not represent an admission that the above content is prior art. Summary of the Invention

[0005] The main objective of this invention is to provide a simulation method for coupled dynamic faults of slurry pumps and drive bearings. It aims to provide a simulation analysis method for fault diagnosis of slurry pumps by considering the influence of the hydraulic characteristics of the slurry pump and the different axial forces generated by the fluid medium on the dynamic characteristics of the drive bearing under different health conditions of the slurry pump and the pump drive bearing.

[0006] To achieve the above objectives, this invention provides a method for simulating coupled dynamic faults in slurry pumps and transmission bearings, the method comprising the following steps:

[0007] Step 1: Based on the parameters and dimensions of the slurry pump and its transmission bearings, three-dimensional models of slurry faults (impeller fault, volute fault, and mixed fault) and three-dimensional solid models of transmission bearings (inner ring fault, outer ring fault, and mixed fault) were established.

[0008] Step 2: Using the ansys-icem module, mesh the transmission bearings of the slurry pump under different health conditions and establish an explicit dynamic finite element model of the bearings.

[0009] Step 3: Extract the fluid domain from the 3D model of the slurry pump under different health conditions and name the fluid domain. Then, mesh the fluid domain model to establish the finite element model of the slurry pump.

[0010] Step 4, explicit dynamic analysis of the transmission end bearing is carried out by using ansys-lsdyna pre-processing module, simulation time and boundary conditions, solid material, load conditions and other simulation parameters are defined, and vibration monitoring points are set.

[0011] Step 5, fluid mechanics analysis of the slag slurry pump finite element model in different health states is carried out by using fluent software, liquid medium and solution algorithm of the slag slurry pump are set, other simulation parameters are defined, and monitoring points on the pump body of the slag slurry pump are set.

[0012] Step 6, step 4 is solved, the vibration characteristic law of the transmission end bearing of the slag slurry pump is analyzed under the conditions of not considering the self-weight of the bearing and considering the radial force generated by the self-weight of the bearing and other factors, and the stress change law is analyzed.

[0013] Step 7, step 5 is solved, only the working condition of the inlet velocity is changed, the head, static pressure, flow velocity and axial force change law of the slag slurry pump finite element model in different health states are analyzed.

[0014] Step 8, the pump shaft axial force generated in step 7 is applied to the transmission end bearing to realize the coupling of the pump body and the transmission shaft bearing, simulation time and simulation parameters, boundary conditions, solid material, load conditions and vibration monitoring points are defined in ansys-lsdyna, and stress extractors of bearing components are set.

[0015] Step 9, step 8 is solved, the vibration characteristic law of the transmission bearing under the coupling action of the pump shaft axial force is analyzed, the transmission bearing with different pump shaft axial forces and different fault types is changed, and the vibration characteristic law and stress change law of the transmission bearing in different health states are analyzed.

[0016] The specific steps of step 1 include that the structure parameters mainly included in the transmission bearing include the detailed structure sizes of the bearing rolling body, inner and outer rings, retainer, etc., the size of the slurry pump impeller, the size of the volute, the diameter of the front and rear cover plates, the number of blades, etc.; the size of the fault model is 2*1.5*1.5 for the outer ring fault size and 0.5mm*0.5mm*2mm for the inner ring fault size, and the faults are established on the 30° slope of the model. The inner and outer rings of the slurry pump bearing are stretched and cut off, the assembled three-dimensional model parts are saved and exported as x-t files. The main flow parts of the slurry pump body are fault cut, the impeller fault size is 0.8mm*3mm*2mm, and the fault point is at the middle end of the third blade. The fault size of the volute is trapezoidal, the upper base is 7mm, the lower base is 10mm, and the other two sides are 11mm and 10mm deep, respectively. Simulate the impeller damage and the volute inner flow channel pitting wear fault, and the fault positions are established on the 30° slope.

[0017] The specific steps of step 2 include that the material of the slurry pump transmission bearing is given, then the three-dimensional grid is divided, the local subdivision is performed on the contact surface, the inner ring of the bearing is set to rotate, the outer ring is fixed, the load condition and the load condition are set, and the simulation time and the number of calculation cores are set.

[0018] The specific steps of step 3 include that the established three-dimensional model of the slurry pump is used to extract the fluid domain of the slurry pump body by using the pre-processing module of space-claim, then the fluid domain of the slurry pump is meshed by using ansys-icem module, the interface and the fluid region are named, the finite element model of the slurry pump body and the finite element model of the transmission bearing are established, and the fluid domain model is exported. In the three-dimensional software, different radial cross-section sketches are drawn, then the point capture function in sw three-dimensional software is used to obtain the coordinates of the volute and each circumferential 0°-270° direction monitoring point. The coordinates of the intersection points of different radial circles and two vertical lines are recorded, the point command is inserted into Geometries in fluent, and the previously recorded monitoring point coordinates are established.

[0019] The specific steps of step 4 include that the materials of each part of the bearing are defined, the outer ring of the bearing is fixed, the inner ring is set to rotate, and the simulation solving parameters including solving time, sampling frequency, solving core number, etc. are set. The extracted grid nodes are set, and the vibration signals of the x, y and z nodes on the nodes and the equivalent stresses of each part of the bearing are extracted.

[0020] The step 5 step includes that the material of the slurry pump fluid medium, the turbulence model, the solving method and the related coefficients of the turbulence equation need to be defined, and the inlet and outlet, each detection report and the head calculation formula, the simulation time and the step size are set.

[0021] The specific steps of the step 4 transmission bearing dynamics simulation include: setting materials of each part of the bearing, fixing the bearing outer ring, setting the inner ring to rotate and applying radial load and bearing gravity parameters in the radial direction of the inner ring, setting the inner ring as a rigid body, setting simulation solving time, sampling frequency and solving core number.

[0022] The specific steps of the step 5 pump body fluid simulation include: defining the pump internal fluid medium, the pump speed, the pump inlet and outlet boundary conditions, establishing the monitoring points recorded in step 2 in the fluent grid model, and setting the simulation solving method, solving time and calculation core number. Report-face report-selection drop-down average pressure is set, monitoring report is set, and is named xxp and xxv. The total pressure in the drop-down option is also selected, and the named inlet and outlet are established to detect the reports and head reports of inp and outp respectively. The head formula is H=(inp-outp) / pg, wherein inp and outp are the total pressures of the inlet and outlet, the monitoring and recording function of the fluent software can be used to monitor the total pressures of the inlet and outlet, p is the density of the fluid medium, the unit is kg / m3, and g=9.81 m / s2. Then the monitoring and recording function of the fluent software is used to edit the head formula, and the head of the slurry pump can be calculated by clicking computer after the simulation is completed. The head of the slurry pump under different health conditions is plotted into a curve, the pressure of the front and rear cover plates along the 180° radial direction is averaged, and the axial force of the fluid medium is calculated. The axial force formula is: D2 is the diameter of the front cover plate, D1 is the diameter of the rear cover plate, and p is the pressure value at the geometric center. In order to more reasonably reflect the size of the axial force, the pressure difference between the average pressure of the front and rear cover plates is taken The pressure value at the geometric center is It is the average value of the instantaneous pressure change of the third layer of the front and rear cover plates in the 180° radial direction), the instantaneous pressure change recorded by the monitoring point is exported to an electronic table, and the pressure difference between the average pressure of the front and rear cover plates in the third layer in the 180° direction is calculated as the pressure value at the geometric center, that is, Δp=p. Finally, the axial force is recorded and plotted into a curve, and the instantaneous pressure collected on the volute in the 0°-270° direction is plotted into a pressure and velocity curve.

[0023] The specific steps of step 6 include: after the step 4 solving is completed, the equivalent stress change of each part of the transmission bearing and the vibration characteristic change rule in different directions under different health conditions are counted and observed.

[0024] The specific steps of step 7 include: after the solution of step 5 is completed, the monitoring report data of each monitoring point is counted, the report data is imported into an electronic form and the axial force generated by the slurry pump fluid on the cover plate is calculated, and the pressure nephogram and the velocity nephogram of the pump flow field can be viewed by using CFD-post.

[0025] The specific steps of step 8 include: the axial force generated by the pump fluid calculated in step 7 is applied to the transmission bearing, the coupling of the pump and the transmission bearing is realized, the load condition of the transmission bearing is changed by using ansys-lsdyna, the simulation time is set, the core number, the material of the inner and outer rings, the boundary condition setting of the fixed outer ring of the rotating inner ring and the vibration monitoring point setting and the stress extractor setting.

[0026] The specific steps of step 9 include: the solution of step 8 is carried out, the vibration characteristic law of the transmission bearing and the stress distribution of different parts of the transmission bearing are analyzed, and the stress distribution of the transmission bearing under different working conditions is counted.

[0027] The present application establishes the finite element models of the transmission bearings in different health states and the finite element models of the pump bodies of the slurry pumps in different health states, analyzes the vibration characteristics and the stress distribution law of the transmission bearings in different health states by using ansys-lsdyna, analyzes the fluid pressure, the velocity variation law and the axial force generated by the fluid medium of the slurry pump body model in different health states by using fluent, calculates the slurry pump lift, the pump shaft axial force generated by the fluid medium and other information under different variables by changing the inlet velocity parameter of the slurry pump, analyzes the axial force generated by the fluid medium of the slurry pump under different fault types under different inlet velocities of the pump by using the fluent fluid simulation, counts the vibration signals and the stress distribution results of the transmission bearing under different axial forces, and obtains the vibration characteristics and the equivalent stress distribution law of the transmission bearing of the slurry pump body under different fault types by the coupling simulation analysis of fluent and ansys-lsdyna. Compared with the prior art, the present application can provide a new method for fault identification and diagnosis of the slurry pump, improve the work efficiency and reduce the production and maintenance cost. BRIEF DESCRIPTION OF DRAWINGS

[0028] Figure 1 It is a flowchart of the slurry pump and transmission bearing coupling dynamics fault simulation method embodiment of the present application;

[0029] Figure 2 It is a health transmission bearing finite element model of the present application;

[0030] Figure 3 It is an inner ring fault transmission bearing finite element model of the present application;

[0031] Figure 4The outer ring fault transmission bearing finite element model of the application;

[0032] Figure 5 The mixed fault transmission bearing finite element model of the application;

[0033] Figure 6 The health slurry pump body finite element model of the application;

[0034] Figure 7 The volute fault slurry pump body finite element model of the application;

[0035] Figure 8 The impeller fault slurry pump body finite element model of the application;

[0036] Figure 9 The mixed fault slurry pump body finite element model of the application. DETAILED DESCRIPTION

[0037] The application will be further clarified by the following figures and embodiments, it should be understood that these embodiments are only used to illustrate the application and not used to limit the scope of the application, after reading the application, the modification of various equivalent forms of the application by those skilled in the art falls within the scope defined by the appended claims of the application.

[0038] Referring to Figure 1 , the application discloses a slurry pump and transmission bearing coupling dynamics fault simulation method, comprising the following steps: step 1: referring to Figures 2-5 , Figures 2-5 The finite element model of the transmission bearing of different health states of the application is shown in the figure. The material parameters of the bearing are defined, and the finite element model of the transmission bearing in different health states is established. The specific steps are: using ansys software, according to the type of bearing parts, actual material parameters, setting the material parameters of the bearing, including the engineering data module of the bearing material, and improving the parameters such as Poisson's ratio, solids density, shear modulus and bulk modulus.

[0039] The Geometries module of ansys-lsdyna is used to set the rolling body, inner and outer rings of the bearing to Gr15, and the cage to Structural steel. The meshsh is opened to set the contact pairs, including the frictional contact between the inner and outer rings and the rolling body, and the contact friction between the rolling body and the cage. In the contacts, the frictional contact coefficient between the inner and outer rings and the rolling body, and the rolling body and the cage is inserted, and the bearing rolling body is set as the contact body, the inner and outer rings as the target body, the rolling body as the contact body, and the cage as the target body. The actual bearing working condition is simulated, including the contact between the inner and outer rings and the rolling body, and the frictional rolling between the rolling body and the cage.

[0040] After setting the frictional contact, other parameters are set. The outer ring is fixed by right-clicking ansys-ls-dyna→insert→fixed support, and then a remote displacement is inserted→remote displacement to simulate the bearing rotation and apply it to the inner surface of the bearing inner ring→application surface. An hourglass control is inserted→hourglass control to prevent grid distortion. A radial force is applied to the center of the inner surface of the bearing inner ring→Force, which simulates the influence of bearing vibration factors and its own gravity on the dynamic characteristics of the bearing. The number of solving cores and the solving time step and total time are set in the analysis settings. The mesh method is inserted in the Mesh as a tetrahedral mesh, and three size adjustments are inserted to locally refine the grid of the bearing rolling body and the bearing inner and outer rings and the cage. Finally, the mesh is generated by clicking generating mesh.

[0041] In the solution information, nine node collection detectors are inserted for directional deformation, directional velocity, and directional acceleration to simulate the sensor collection of the bearing vibration signal. In the solution, four equivalent stresses are inserted by selecting each component, and four equivalent stresses are inserted. In addition, the contact normal stress is inserted to view the contact stress of the inner and outer surfaces. The maximum stress σ of the transmission bearing under the rotating load is compared with the allowable stress [σ] of the transmission bearing. If σ≤[σ], the transmission bearing meets the strength requirement. Then click to solve.

[0042] Refer to the attachedFigures 6-9 The finite element model of different health states of the pump body of the slurry pump established for the present application. The specific steps are: dragging a fluent module in ansys, importing the slurry pump body assembly model in Geometries, then extracting the fluid domain in the pre-processing software space-claim, and the specific steps of extraction are as follows:

[0043] (1) The front and rear cover plates are merged with the volute

[0044] First, merge the front and rear end covers with the volute, hide the impeller model after merging, and select the merge option to merge the front and rear cover plates with the volute respectively. After checking that the merging is complete without error, delete the previously imported front and rear cover plate models.

[0045] (2) Volume extraction

[0046] Select the "volume extraction" option, select the "merged volume" previously merged, extract the model boundary line of the "merged volume", select the boundary line of the front and rear cover plates and the volute outlet boundary line respectively, and then click "face selection type" to select the flow passage surface of a volume, which is the inner surface of the volute outlet here. Then click "finish" to see the preliminary extraction of the slurry pump fluid domain. After extraction, delete the previous "merged volume" model.

[0047] (3) Volume trimming

[0048] After the previous steps, the entire fluid region is now a whole. Now display the previously hidden impeller model, then select the "merge" tab with the fluid domain of (2) as the whole model. With the impeller as the cutter, separate the whole fluid domain model. After separation, you can see that the previous fluid domain model in the model tree is divided into multiple parts, select each part to view and delete the unnecessary fluid domain. Finally, delete the impeller to form a preliminary fluid domain model. At this time, the impeller water body has not been separated from the volute, but only the cavity of the impeller and the front and rear cover plates has been formed. Therefore, it is still necessary to separate the impeller water body from the volute water body.

[0049] (4) Secondary volume separation

[0050] Select the separate body option next to the "merge" tab, select the volute body as the target geometry, and then select the impeller as the cutter. At this time, the impeller and the volute have been separated. Rename the extracted fluid domain model, and delete the previous assembly model.

[0051] (5) Inlet and outlet flow passage extension section

[0052] The extracted import and export section is appropriately extended to extend the import and export end, which is to prevent backflow of fluid and cause errors in numerical calculation. The import and export section of the fluid domain is extended to about 1.5 times the diameter of the import and export. Finally, the three-dimensional fluid domain model of normal, impeller failure, volute failure, and mixed failure of impeller and volute is extracted. Save the extracted fluid domain model as a step file, then assemble it in the three-dimensional software, and then use the sketch function in the three-dimensional software to make five equally spaced circles on the front and rear cover plates of the pump body, and make 90° and 180° vertical lines at the center of the circles. The intersection of the vertical lines and the circles is named 0°, 90°, 180°, and 270° clockwise, respectively. A total of five layers are equally spaced, and a total of ten layers are equally spaced on the front and rear cover plates, which are equally spaced. Similarly, in order to more conveniently detect the pressure fluctuation, four monitoring points in the same direction are set on the volute, and the monitoring point coordinates are recorded. Then, under the mesh module, name the fluid domain model, name the outlet, inlet, impeller, volute, and water body pipeline.

[0053] The tetrahedral mesh is divided for the whole fluid domain, and the local mesh surface is divided for the inlet, outlet, and dynamic static interface. The volume mesh is divided for the impeller, volute, water body, and cover plate. Then click Update to update the mesh. Close the mesh module after the update is successful.

[0054] Double-click setup to open the fluent fluid calculation setting interface, set gravity, solver, and material in Geometries. Click the inlet, right-click to change the inlet type to velocity inlet, and the outlet type to pressure outlet. Before setting the speed, first click unit to change the speed unit to r / min, then click the impeller to set its speed, check Frame Motion and then select the rotation coordinate axis in rotation-Axis. The coefficient of the rotation coordinate axis is 1, and the other coordinate systems are set to zero by default. Set the relative rotation of the impeller wall to 0. Finally, establish the coordinates of the recorded monitoring points on the grid model of fluent in Geometries.

[0055] Click methods to set the solution method and convergence factor, set the turbulence model and wall equation in Models. Set the turbulence intensity and pressure coefficient of the turbulence equation, energy equation, and mass equation in Controls.

[0056] In Run calculation, set the final solution time, solution time sub-step, define the head and import and export pressure, velocity change with time monitoring report, and each monitoring point report. Click Save to initialize the entire flow field, and then click Calculation to solve and simulate the fluid flow field.

[0057] The output of each detection point monitoring report data is solved by the axial force formula described above, and the detected head is calculated and recorded, and then the head changes with the inlet velocity to draw a curve.

[0058] Finally, the calculated pump shaft axial force is equivalent to the load on the transmission bearing, and the dynamic simulation analysis of the transmission bearing of different fault types is carried out, the effect of different axial forces on the bearing is analyzed, and the calculation results are compared. The influence of the size of the axial force of the fluid medium of the pump under different working conditions on the vibration law of the dynamic characteristics of the transmission bearing and the change distribution law of the equivalent stress are analyzed.

Claims

1. A method for simulating the coupling dynamics fault of a slurry pump and a transmission bearing, characterized in that: Step 1, according to the parameters and sizes of the slurry pump and the transmission bearing, a three-dimensional model of the impeller fault, the volute fault and the mixed fault of the slurry pump, and a three-dimensional entity model of the inner ring fault, the outer ring fault and the mixed fault of the transmission bearing are established; Step 2, the transmission bearing of the slurry pump in different health states is meshed by using the ansys-icem module, and a bearing explicit dynamics finite element model is established; Step 3, the three-dimensional model of the slurry pump in different health states is extracted and named, and then the model is meshed, and a slurry pump finite element model is established; Step 4, the transmission end bearing is analyzed by using the ansys-lsdyna pre-processing module, the simulation time and boundary conditions, solid material, load condition simulation parameters, and the vibration monitoring point are defined; Step 5, the fluent software is used to analyze the fluid mechanics of the slurry pump finite element model in different health states, the liquid medium and solution algorithm of the slurry pump are set, and other simulation parameters and the monitoring points on the slurry pump body are set; Step 6, the step 4 is solved, the vibration characteristic law of the transmission end bearing of the slurry pump is analyzed under the conditions of not considering the bearing self-weight and considering the radial force generated by the bearing self-weight and other factors, and the stress change law is analyzed; Step 7, the step 5 is solved, only the working condition of the inlet velocity is changed, the lift, static pressure, flow velocity and the change law of the fluid medium generated pump shaft axial force of the slurry pump finite element model in different health states are analyzed; Step 8, the pump shaft axial force generated in step 7 is applied to the transmission end bearing, the coupling of the pump body and the transmission shaft bearing is realized, the simulation time and simulation parameters, boundary conditions, solid material, load condition and vibration monitoring point and bearing component stress extractor are set in ansys-lsdyna; Step 9, the step 8 is solved, the vibration characteristic law of the transmission bearing under the coupling action of the pump shaft axial force is analyzed, the transmission bearing of different pump shaft axial force and different fault types is changed, and the vibration characteristic law of the transmission bearing in different health states is analyzed.

2. The method of claim 1, wherein, The three-dimensional model of the slurry pump in different health states further comprises: establishing a three-dimensional entity model of the transmission bearing and a three-dimensional entity model of the slurry pump, the transmission bearing comprises structural parameters of bearing rolling body, inner and outer rings, detailed structure size of retainer, size of slurry pump impeller, size of volute, and diameter size of front and rear cover plates, and number of blades.

3. The method of claim 1, wherein, The bearing explicit dynamics finite element model and the slurry pump finite element model further comprise: the physical parameters of the transmission bearing need to be defined, including material, load, bearing inner and outer ring boundary conditions, and simulation parameters of core number, calculation time and sampling frequency; the physical parameters of the slurry pump include fluid medium, liquid viscosity and turbulence intensity; and the motion parameters of the slurry pump include the size of the impeller rotating speed and the coordinate axis required to rotate.

4. The method of claim 1, wherein, The vibration characteristic law and stress variation law of the drive end bearing of the slurry pump further include: setting a monitoring point to extract the vibration signals in x, y and z directions, and setting a stress distribution extractor for each component, analyzing the vibration law of the drive bearing under different load conditions and different health states, and the stress variation law of each component of the bearing.

5. The method of claim 1, wherein, The pressure and flow field distribution law of the finite element model of the slurry pump under different inlet velocity conditions and different health states further includes: using the post-processing module of fluent to establish a display plane in the x-z / y-z plane, and finally displaying the pressure and velocity cloud map according to a certain proportion to observe the fluid flow direction and flow trend in the flow field.

6. The method of claim 1, wherein, The variation law of the pump shaft axial force of the slurry pump fluid medium in different health states under different inlet flow rates further includes that the pump shaft axial force is calculated by setting monitoring points, and the pump shaft axial force is derived from the pressure difference of the front and rear cover plates, so four monitoring points at 0°, 90°, 180° and 270° are arranged on the front and rear cover plates of the slurry pump; and the pump body is divided into five layers along the radial direction of the slurry pump, and the four detection points in the volute direction are not included; the radial circle is equally divided; the pressure value at the geometric center along the radial 180° direction is taken as the fluid pressure of the pump shaft axial force, and the formula is where D2 is the diameter of the front cover plate, D1 is the diameter of the rear cover plate, and p is the pressure value at the geometric center. In order to more reasonably reflect the size of the pump shaft axial force, the pressure difference of the average pressure of the front and rear cover plates is taken The pressure average of the geometric center is the average value of the instantaneous pressure change of the third layer of the front and rear cover plates in the radial 180° direction, and the pressure difference of the average pressure of the front and rear cover plates in the radial 180° direction of the third layer is taken as the pressure value at the geometric center, that is, Δp=p. Finally, the pump shaft axial force is recorded and drawn into a curve to observe the variation law with the flow rate.

7. The method of claim 1, wherein, The step of applying the pump shaft axial force generated in step 7 to the drive end bearing to realize the coupling of the pump body and the drive end bearing further includes: loading the pump shaft axial force calculated in step 7 to the drive end bearing, changing the original load condition, and then setting a node monitoring point to extract the speed, acceleration and displacement information of the drive end bearing and a stress extractor for different components of the drive end bearing.

8. The method of claim 1, wherein, The influence of the fluid medium generated pump shaft axial force on the drive end bearing further includes: performing explicit dynamic analysis on the drive end bearing under different health states, changing the size of the pump shaft axial force, and analyzing the vibration characteristic law and the stress distribution law of each component through the monitoring point extractor and the stress extractor.

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