CN112347593A - Non-circular gear dynamic contact characteristic analysis method based on tooth surface topological structure - Google Patents
Non-circular gear dynamic contact characteristic analysis method based on tooth surface topological structure Download PDFInfo
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Abstract
The invention discloses a dynamic contact characteristic analysis method of a non-circular gear based on a tooth surface topological structure, and belongs to the field of gear meshing. Firstly, generating an accurate two-dimensional model of the non-circular gear by using KISSsoft software, generating a three-dimensional model of the non-circular gear in Creo three-dimensional software, and establishing a tooth surface topological structure and a corresponding coordinate identifier; introducing Hypermesh software to divide gear meshes so that tooth surface mesh nodes are matched with the topological structure; and finally, defining boundary conditions in LS-DYAN software, simulating one rotation under the condition of gear bearing, and finally solving the model. The variation trend of tooth surface stress, strain, pressure, displacement and speed of the gear teeth in the meshing process is obtained. The invention reduces and avoids the writing and solving of complex programs in the analysis process of the dynamic contact characteristics of the non-circular gear, saves the workload and resources and provides a basis for the dynamic contact analysis of the non-circular gear.
Description
Technical Field
The invention belongs to the technical field of gear meshing analysis, and particularly relates to a dynamic contact characteristic analysis method for a non-circular gear based on a tooth surface topological structure.
Background
The non-circular gear belongs to a special cylindrical gear and is distinguished from the cylindrical gear by the fact that the non-circular gear has a non-circular pitch curve; the non-circular gear mainly comprises a non-cylindrical gear, a non-circular helical gear, a non-circular face gear, a non-conical gear and the like. The non-circular gear has compact structure, can realize variable ratio transmission, and is mainly applied to low-speed and large-torque occasions, such as: hydraulic pumps, hydraulic motors, flow meters, etc. The time-varying curvature radius of the pitch curve and the curvature radius of the tooth profile of the non-circular gear cause the tooth profiles of the gear teeth at different positions on the pitch curve to be inconsistent, and the left tooth profile and the right tooth profile of each gear tooth to be different. In the practical application process, the contact stress on each tooth surface is greatly different due to the fact that tooth profiles are not consistent, and therefore, the dynamic analysis of the meshing process of the non-circular gear is of great significance for further improving the dynamic design and application occasions of the gear.
LS-DYNA is the most widely applied gear dynamic meshing simulation software at present, can realize bearing contact of gears, and is relatively accordant with actual working conditions. The research of gear meshing simulation by using LS-DYNA is numerous, but most of the researches aim at common cylindrical gear pairs and helical gear pairs, the research on non-circular gears is few, and in the document of ANSYS/LS-DYNA-based gear line external meshing impact research, the problem of meshing impact of the linear gear pairs is researched by using LS-DYNA software; in the article LS-DYNA straight gear dynamic meshing characteristic analysis, LS-DYAN software is used for simulating the dynamic meshing process of a gear pair; in the article of dynamic contact characteristic analysis of the elliptic cylindrical gear under different load conditions, the Ls-Prest software is used for simulating the dynamic meshing process of the elliptic cylindrical gear, which lays a foundation for the meshing simulation of the non-circular gear.
Disclosure of Invention
The invention provides a method for analyzing dynamic contact characteristics of a non-circular gear based on a tooth surface topological structure. The invention reduces and avoids the writing and solving of complex programs in the analysis process of the dynamic contact characteristics of the non-circular gear, saves the workload and resources and provides a basis for the dynamic contact of the non-circular gear.
The invention is realized by the following technical scheme:
a non-circular gear dynamic contact characteristic analysis method based on a tooth surface topological structure comprises the following steps:
step 1: determining parameters of the non-circular gear, and generating a two-dimensional model of the non-circular gear pair by using KISSsoft software according to the parameters;
step 2: importing the two-dimensional model in the step 1 into Creo software to generate a non-circular gear pair three-dimensional model, and setting a tooth surface topological structure;
and step 3: importing the three-dimensional model in the step 2 into Hypermesh software, dividing gear meshes, and establishing a finite element meshing model to enable the tooth surface meshes to correspond to the tooth surface topological structure in the step 2;
and 4, step 4: leading the model generated in the step 3 into LS-DYNA, setting initial conditions and boundary conditions of the three-dimensional model, and solving by using a solver LS-PREPOST MANAGER in the LS-DYNA to generate a solving file;
and 5: opening the solution file in the step 4 by using LS-DYNA, selecting gear teeth at different positions on a non-circular gear pitch curve as objects of data acquisition points, and acquiring stress, strain, pressure, rotating speed and displacement of topological coordinate points in a tooth surface contact area in the dynamic meshing process of the gear;
step 6: and (5) analyzing the stress, the strain, the pressure, the rotating speed and the displacement obtained in the step (5) to obtain the variation trend of the stress, the strain, the pressure, the speed and the displacement along with the position of the gear on the pitch curve in the gear tooth meshing process.
Establishing a topological structure: and establishing a tooth profile topological structure by taking the intersection point of the tooth profile and the tooth trace as the origin of tooth profile topological coordinates, taking the direction of the tooth trace and the direction of the tooth profile as the X axis and the Y axis of a topological coordinate system and analyzing the normal vector of the tooth profile and the curvature identification function in a module in Cero software.
The topological structure is set as a rectangular unit, and the coordinate of the topological structure is marked as the rectangular unit.
In the step 3, the non-circular gear shaft hole is divided into surface grids by using automesh in a 2D unit in Hypermesh software, and the whole gear is divided into body grids by using solid map in a 3D unit in the Hypermesh software.
After the grid division is completed, the face and edge commands in the Tool unit in the Hypermesh software are used for checking the model.
The step 2 further comprises that the model generated by Creo is subjected to motion verification through a Simulation module in Creo.
The parameters in step 1 include modulus, tooth number, pressure angle, tooth width, center distance and pitch curve equation.
By adopting the technical scheme, the invention has the following advantages:
1. the invention reduces and avoids the writing and solving of complex programs in the analysis process of the dynamic contact characteristics of the non-circular gear, saves the workload and resources and provides a basis for the dynamic contact of the non-circular gear.
2. According to the invention, the non-circular gear pair is generated through KISSsoft software, and the modulus, the tooth number, the pressure angle, the tooth width and the pitch curve equation are input, so that the accurate two-dimensional tooth profile model of the non-circular gear can be obtained. In the process, tooth top and tooth root fillet transition curves are dynamically generated, and the change of the rotating angle and the transmission ratio can be dynamically displayed in the meshing simulation process, so that compared with a common non-circular gear design method, the method avoids writing a complex program and has higher precision.
3. The establishment of the tooth surface topological structure can ensure accurate positioning of the coordinate data of any point of the tooth profile. The method comprises the steps of establishing a tooth profile topological structure by taking the intersection point of a tooth profile and a tooth trace as the origin of tooth profile topological coordinates and taking the tooth trace direction and the tooth profile direction as the X axis and the Y axis of a topological coordinate system respectively through the normal vector of the tooth profile and the curvature identification function in an analysis module in Cero software, and ensuring that the established topological coordinates can be accurately positioned to a point on the tooth surface; hexahedral mesh units divided in Hypermesh software can be dynamically matched with the tooth surface topological structure, and the data extraction points are guaranteed to be mesh points under the topological structure.
4. According to the invention, the non-circular gear dynamic meshing model established by the LS-DYAN can be used for simulating the meshing of the gear under the bearing condition, and each gear tooth can be ensured to participate in the meshing in the process of rotating for one circle, so that the stress, strain, pressure, displacement and speed change rules corresponding to each unit in the gear meshing process can be obtained more intuitively.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings needed to be used in the embodiments of the present invention or in the description of the prior art will be briefly described below, and it is obvious that the drawings described below are only some embodiments of the present invention, and it is obvious for those skilled in the art that other drawings can be obtained according to the drawings without creative efforts.
FIG. 1 is a flow chart of the present invention;
FIG. 2 is a two-dimensional graph of a non-circular gear generated in the KISSsoft software of the present invention;
FIG. 3 is a three-dimensional model of a non-circular gear generated in Creo according to the present invention;
FIG. 4 is a non-circular gear tooth profile topology and coordinate identification designed in Creo by the present invention;
FIG. 5 is a non-circular gear finite element model built in Hypermesh software according to the present invention;
FIG. 6 is a cloud of contact stress distribution of a gear in the present invention at a meshing time of 0.002 s;
FIG. 7 is the distribution of the elliptical contact area of the tooth surface of the non-circular gear when the meshing time is 0.0049 s;
FIG. 8 is a view showing the distribution of elliptical contact areas of the tooth surfaces of the non-circular gears at a meshing time of 0.028s in the present invention;
FIG. 9 is the distribution of the elliptical contact area of the tooth surface of the non-circular gear when the meshing time is 0.046 s;
FIG. 10 is a tooth surface contact stress distribution rule of the present invention with topological coordinate points 1(5,5), 1(15,5) and 1(25, 5);
fig. 11 is a tooth surface contact stress distribution rule of topological coordinate points 24(5,5), 24(15,5) and 24(25,5) in the present invention;
FIG. 12 is a graph showing the variation trend of the ratio of stress applied to X, Y, Z in three directions with topological coordinate points of 1(5,4), 1(15,4) and 1(25,4) according to the present invention;
FIG. 13 is a graph showing the variation trend of X, Y, Z displacement in three directions with topological coordinate points 1(5,4), 1(15,4) and 1(25,4) according to the present invention;
FIG. 14 is a graph showing the variation trend of X, Y, Z directional velocities at topological coordinate points 1(5,4), 1(15,4) and 1(25,4) in the present invention;
FIG. 15 is a graph showing the variation tendency of the tooth surface contact force during the gear meshing process according to the present invention;
FIG. 16 is a graph showing the trend of the torque applied during the engagement of the gears in the present invention;
in the drawings: 1. tooth number 1, and tooth numbers 24 and 24.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is described in further detail below with reference to the accompanying drawings and embodiments.
The embodiment provides a non-circular gear dynamic contact characteristic analysis method based on a tooth surface topological structure, which comprises the following steps:
step 1: a non-circular gear pair is designed in KISSsoft, and parameters are input: after the parameters are set, a two-dimensional model of the non-circular gear pair shown in fig. 2 is generated, wherein the modulus m is 3, the tooth number z1 is z2 is 47, the pressure angle α is 20 °, the tooth width b is 30, and the pitch curve equation r is 64.667/1-0.3287cos (θ); and saving the two-dimensional model of the non-circular gear pair into an iges format.
Step 2: importing the files in the iges format generated in the step 1 into Creo, newly building a part, and stretching the graph of the imported two-dimensional model of the non-circular gear pair, wherein the stretching height is 30mm, and the diameter of a shaft hole is 30mm, so as to generate a three-dimensional model of the non-circular gear pair as shown in figure 3; then, a Simulation module is used for motion verification to ensure the motion accuracy; establishing a tooth profile topological structure by using a medium tooth profile vector and curvature identification function of an analysis module in Creo, selecting corresponding transverse and longitudinal direction grid numbers in the establishing process, establishing a tooth profile topological structure coordinate system by using an intersection point of a non-circular gear tooth profile direction and a tooth trace direction as a coordinate origin, the tooth trace direction as an x-axis and the tooth profile direction as a y-axis, and positioning each unit on the gear tooth profile, wherein the tooth profile topological structure coordinate identification is shown in figure 4; and finally storing the data in an iges format.
And step 3: importing the files in the iges format generated in the step 2 into hypermesh software for grid division; when the mesh division is carried out on the tooth profile of the non-circular gear, the number of the nodes of the unit needs to be automatically adjusted, the automatically generated mesh nodes cannot correspond to the tooth surface topological data points designed in the step 2 one by one, and in order to ensure that each topological unit on the tooth profile can be completely and accurately positioned, the number of the meshes needs to be strictly adjusted according to the tooth surface topological structure designed in the early stage when the tooth profile mesh division is carried out. The hexahedron units are adopted when the network is divided, the setting of the tooth surface topological structure of the gear and the coordinate identification of the tooth surface topological structure of the gear are all rectangular units which correspond to the hexahedron grids, and the divided grids and the tooth surface topological structure can be ensured to be in one-to-one correspondence;
the non-circular gear shaft hole is divided into surface meshes by using automesh in a 2D unit in Hypermesh software, the whole gear is divided into body meshes by using solidmap in a 3D unit in the Hypermesh software, and the divided meshes correspond to a tooth surface topological structure; after the grid division is finished, checking the model by using face and edge commands in the Tool unit in Hypermesh software, and ensuring that the model has no T-shaped edges and redundant nodes; and finally saving as a k file.
And 4, step 4: importing the k file generated in the step 3 into LS-DYNA software, as shown in FIG. 5; setting model initial conditions and boundary conditions in LS-DYNA software:
respectively defining a rotating speed curve of a driving wheel and a load curve of a driven wheel in a DEFINE-CURVES module, wherein the rotating speed is defined as 600 r/min;
material properties are defined inside the MAT module, the gear shaft hole is defined as MAT-PIECEWISE-LINEAR-PLASTICITY, and the other part is defined as MAT-RIGID. Poisson ratio PR of 0.3 and density RO of 7.85x10-9 t/mm3Elastic modulus E1＝E2＝2.1x105N/mm2The yield limit SIGY is 355 Mpa;
defining a Shell unit and a Solid unit in a SECTION module, setting ELFORM to be 1 and setting a Shear factor to be 0.8333;
materials are respectively added to the shaft hole and the gear body in the Part unit, the shaft holes of the driving wheel and the driven wheel are set to Solid, and the gear body is partially set to Shell. Defining rigid-flexible coupling, and ensuring that the rigid inner ring drives the flexible body gear to rotate;
ASCII _ OPTIONBINARY _ D3PLOT, BINARY _ D3THDH and EXTENT _ BINARY are arranged in the DATABASE module;
defining the CONTACT of a driving wheel and a driven wheel in the CONTACT module, wherein the static friction coefficient FS is 0.2, and the dynamic friction coefficient FD is 0.1;
defining the application speed of the inner ring of the driving wheel in the BOUNDARY module, and limiting the X, Y, Z-direction movement freedom degree and X, Y-direction rotation freedom degree of the driving wheel and the driven wheel;
defining BULK _ VISCOSITY, CONTACT, CPU, ENGERY, HOURGLASS, OUTPUT, SHELL, SOLID, TERMINATION, TIMETEP in the CONTROL module; the termination time is set to 0.1s, and the driving wheel and the driven wheel rotate by one rotation under the condition of ensuring that the rotating speed is 600 r/min;
after the definition is good, a solver LS-PREPOST MANAGER of LS-DYNA is used for solving; and then generating a solution file in a d3plot format.
And 5: opening the solution file in the step 4 by using LS-DYNA, selecting gear teeth at different positions on a non-circular gear pitch curve as objects of data acquisition points, and acquiring stress, strain, pressure, rotating speed and displacement of topological coordinate points in a tooth surface contact area in the dynamic meshing process of the gear;
FIG. 6 is a cloud chart of the contact stress distribution of the gear with the meshing time of 0.002 s; as shown in fig. 7, 8 and 9, the distribution of the elliptical contact areas of the tooth surfaces of the non-circular gears is 0.0049, 0.028 and 0.046, and the elliptical contact areas are all symmetrically distributed along the middle section of the gear;
selecting No. 1 teeth and No. 24 teeth to obtain stress, strain, pressure, rotating speed and displacement of the topological coordinate points;
step 6: analyzing the stress, strain, pressure, rotating speed and displacement obtained in the step (5) to obtain the variation trend of the stress, strain, pressure, speed and displacement along with the position of the gear on the pitch curve in the gear tooth meshing process;
the tooth surface contact stress distribution law with topological coordinate points 1(5,5), 1(15,5) and 1(25,5) is shown in fig. 10. As shown in fig. 11, the distribution rule of tooth surface contact stress at topological coordinate points 24(5,5), 24(15,5) and 24(25,5) is shown; since the tooth mesh time of the No. 24 tooth is later than that of the No. 1 tooth, the meshing impact occurs at about 0.047 s.
The topological coordinate points shown in fig. 12 are the specific change trend of stress borne by X, Y, Z in three directions, namely 1(5,4), 1(15,4) and 1(25, 4); the trend of the change of X, Y, Z directional displacements with topological coordinate points 1(5,4), 1(15,4) and 1(25,4) is shown in fig. 13; fig. 14 shows the trend of the X, Y, Z directional velocities with topological coordinate points 1(5,4)1(15,4) and 1(25, 4);
FIG. 15 shows a trend of a tooth surface contact force during gear meshing; fig. 16 shows the trend of the torque applied during the gear meshing.
It should be noted that the software used in the above is the prior art.
The change trend of stress, strain, pressure, speed and displacement along with the position of the gear on a pitch curve, which is obtained by analyzing the dynamic contact characteristics of the non-circular gear with the tooth surface topological structure, can be used for guiding the modification of the gear tooth profile; and whether the established three-dimensional model of the non-circular gear is reasonable or not can be verified through the symmetrical distribution trend of the tooth surface contact area along the middle section.
The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
Claims (7)
1. A non-circular gear dynamic contact characteristic analysis method based on a tooth surface topological structure is characterized by comprising the following steps:
step 1: determining parameters of the non-circular gear, and generating a two-dimensional model of the non-circular gear pair by using KISSsoft software according to the parameters;
step 2: importing the two-dimensional model in the step 1 into Creo software to generate a non-circular gear pair three-dimensional model, and setting a tooth surface topological structure;
and step 3: importing the three-dimensional model in the step 2 into Hypermesh software, dividing gear meshes, and establishing a finite element meshing model to enable the tooth surface meshes to correspond to the tooth surface topological structure in the step 2;
and 4, step 4: leading the model generated in the step 3 into LS-DYNA, and setting initial conditions and boundary conditions of the three-dimensional model; solving by using a solver LS-PREPOST MANAGER in LS-DYNA and generating a solving file;
and 5: opening the solution file in the step 4 by using LS-DYNA, selecting gear teeth at different positions on a non-circular gear pitch curve as objects of data acquisition points, and acquiring stress, strain, pressure, rotating speed and displacement of topological coordinate points in a tooth surface contact area in the dynamic meshing process of the gear;
step 6: and (5) analyzing the stress, the strain, the pressure, the rotating speed and the displacement obtained in the step (5) to obtain the variation trend of the stress, the strain, the pressure, the speed and the displacement along with the position of the gear on the pitch curve in the gear tooth meshing process.
2. The method for analyzing the dynamic contact characteristics of the non-circular gear based on the tooth surface topological structure as claimed in claim 1, wherein: establishing a topological structure: and establishing a tooth profile topological structure by taking the intersection point of the tooth profile and the tooth trace as the origin of tooth profile topological coordinates, taking the direction of the tooth trace and the direction of the tooth profile as the X axis and the Y axis of a topological coordinate system and analyzing the normal vector of the tooth profile and the curvature identification function in a module in Cero software.
3. The method for analyzing the dynamic contact characteristics of the non-circular gear based on the tooth surface topological structure as claimed in claim 1, wherein: the topological structure is set as a rectangular unit, and the coordinate of the topological structure is marked as the rectangular unit.
4. The method for analyzing the dynamic contact characteristics of the non-circular gear based on the tooth surface topological structure as claimed in claim 1, wherein: in the step 3, the non-circular gear shaft hole is divided into surface grids by using automesh in a 2D unit in Hypermesh software, and the whole gear is divided into body grids by using solid map in a 3D unit in the Hypermesh software.
5. The method for analyzing the dynamic contact characteristics of the non-circular gear based on the tooth surface topological structure as claimed in claim 3, wherein: after the grid division is completed, the face and edge commands in the Tool unit in the Hypermesh software are used for checking the model.
6. The method for analyzing the dynamic contact characteristics of the non-circular gear based on the tooth surface topological structure as claimed in claim 1, wherein: the step 2 further comprises that the model generated by Creo is subjected to motion verification through a Simulation module in Creo.
7. The method for analyzing the dynamic contact characteristics of the non-circular gear based on the tooth surface topological structure as claimed in claim 1, wherein: the parameters in step 1 include modulus, tooth number, pressure angle, tooth width, center distance and pitch curve equation.
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| CN114818183A (en) * | 2022-04-26 | 2022-07-29 | 兰州理工大学 | Design method of non-circular helical gear |
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| CN112347593B (en) | 2021-06-04 |
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