CN107292057A - Stress simulation analysis method in gear drive - Google Patents
Stress simulation analysis method in gear drive Download PDFInfo
- Publication number
- CN107292057A CN107292057A CN201710616848.0A CN201710616848A CN107292057A CN 107292057 A CN107292057 A CN 107292057A CN 201710616848 A CN201710616848 A CN 201710616848A CN 107292057 A CN107292057 A CN 107292057A
- Authority
- CN
- China
- Prior art keywords
- gear
- stress
- model
- involute
- teeth
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
- G06F30/23—Design optimisation, verification or simulation using finite element methods [FEM] or finite difference methods [FDM]
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/10—Geometric CAD
- G06F30/17—Mechanical parametric or variational design
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Theoretical Computer Science (AREA)
- Geometry (AREA)
- General Physics & Mathematics (AREA)
- Evolutionary Computation (AREA)
- General Engineering & Computer Science (AREA)
- Computer Hardware Design (AREA)
- Computational Mathematics (AREA)
- Mathematical Analysis (AREA)
- Mathematical Optimization (AREA)
- Pure & Applied Mathematics (AREA)
- Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
- Gears, Cams (AREA)
Abstract
A kind of stress simulation analysis method in gear drive, parametric modeling is carried out to gear by UG, and simulation analysis are carried out to pitch point stress in ANSYS softwares, calculate the Max.contact stress of gear, FEM calculation the data obtained and theoretical analysis result are relatively, error illustrates that model sets up correct, finite element analysis process is reasonable in engineering allowed band.Pass through the parametric modeling and design of gear, it is to avoid the modification repeatedly of the major design size of gear.According to design requirement, as long as changing major parameter just can obtain the required model of gear, making the CAE of gear becomes easy, makes the design process of gear and becomes more easy.
Description
Technical field
The present invention relates to a kind of stress simulation analysis method in gear technique field, more particularly to gear drive.
Background technology
The features such as gear drive of compact conformation has gearratio and the efficiency high of stabilization, using wide in machine driving
General, the power of transmission is up to hundreds thousand of kilowatts, and these are all the advantages that other kinds of drive can not replace.Gear drive has a variety of
Device type, gear material, which has firmly, crisp, and its material mechanical performance and Technology for Heating Processing are also differed, therefore gear had been driven
Failure mode has gear teeth fatigue break, flank of tooth abrasive wear, plastic deformation etc. in journey.Generally directed to appearance during design gear in engineering
The failure mode being also easy to produce, takes two kinds of conventional criterions, for the gear based on generation rippling or gluing etc., is mainly
Because basic part intensity is weaker, based on the design formula of tooth face contact fatigue strength.When the gear teeth are loaded, stress distribution compared with
For complexity, the contact strength of tooth surface numerical value calculated with above-mentioned algorithm is more more than needed.
The content of the invention
The invention solves the problems that there is provided the stress simulation analysis side in a kind of gear drive for the problem of above-mentioned prior art is present
Method, the calculating that exists is complicated, follow-up the problem of be difficult to optimization when solving current design gear, meets the demand of design of gears.
The present invention solves the technical scheme that its technical problem is used：Stress simulation analysis method in this gear drive,
Comprise the following steps：
The first step, creates the model of gear, and a pair of involute spur gears of selection are stress simulation object, Ran Hou
In UGNX softwares, involute equation is set up using the modeling method of feature and parameter, it is then defeated in Expression dialog boxes
Enter expression formula, involute is drawn using NX Law Curve functions, according to parameters such as modulus, the numbers of teeth, fitting gear is gradually opened
Line, draws out whole profile, it is then determined that the other structures such as the key dimension such as outside circle, reference circle and wheel rim, spoke and wheel hub
Size, generate involute gear model, then gear is cut, the part number of teeth is left and is analyzed；
Need model being separated into grid model after second step, definition material attribute, cell type, solid modelling, pass through
Definition unit attribute and mess generation are controlled, first definition material attribute Elastic Modulus E and Poisson's ratio, then selecting unit class
Type and order；
3rd step, grid division, to Element Size using giving tacit consent to, obtains rough segmentation grid, Element Size is adjusted
To 0.2mm, subdivided meshes are obtained；
4th step, defines boundary condition, loading, applies identical side to rough segmentation grid model, subdivided meshes model respectively
Boundary's condition and load, compare the result of calculation of two kinds of mesh generations, using Joints functions to gear apply boundary condition, to from
Driving wheel apply radially, circumferentially, axial freedom constraint, to driving wheel apply except Z-direction rotate other revolutes constrain, retain
Rotate in a circumferential direction the free degree, and applies the torque that size is 105kNmm；
5th step, does analyzing static structural, and contact analysis is carried out using finite element method, obtains stress distribution, and pickup should
After Max.contact stress under variate, the model of gear engagement of rough segmentation grid is 182Mpa, subdivided meshes, obtains maximum and connect
It is 232.3Mpa to touch stress value；
The curvature of every bit is different in 6th step, simulation analysis, flank profil, therefore flank profil everywhere subjects different loads
Lotus, the contact stress of the meshing point of active, the node of driven two-wheeled and single pair of gear is larger in theory, it should enter in these positions
Row FEM calculation of contact strength, but be difficult in view of the Stress calculation of monodentate meshing point, and when the little gear number of teeth is more than 20, press
The stress that monodentate engagement minimum point is calculated is closer to engaging the stress calculated by node, therefore the face of coupling gear
Stress can by the gear of pitch diameter two of HERZ formula Superposition degree modulus loading coefficient pinion drive torque little gears the number of teeth
Than the major parameter for substituting into gear, the Max.contact stress 271Mpa of two gear teeth is obtained, it can be seen that mesh refinement is directly affected
Simulation result.
Further, the computing capability that cutting allows for computer is carried out in the first step to gear.
The invention has the advantages that：Stress simulation analysis method in the gear drive of the present invention, by UG to gear
Parametric modeling is carried out, and simulation analysis are carried out to pitch point stress in ANSYS softwares, the Maximum Contact of gear is calculated
Stress, relatively, error illustrates that model is set up in engineering allowed band for FEM calculation the data obtained and theoretical analysis result
Correctly, finite element analysis process is reasonable.Pass through the parametric modeling and design of gear, it is to avoid the major design size of gear
Change repeatedly.According to design requirement, as long as changing major parameter just can obtain the required model of gear, the CAE of gear is set to become to hold
Easily, making the design process of gear becomes more easy.
Brief description of the drawings
Fig. 1 is the theory diagram of the embodiment of the present invention；
Fig. 2 is the principle of forming involute figure of the embodiment of the present invention；
Fig. 3 is the gear solid modelling figure of the embodiment of the present invention；
Fig. 4 is the rough segmentation grid chart of the embodiment of the present invention；
Fig. 5 is the subdivided meshes figure of the embodiment of the present invention；
Fig. 6 is loading result figure on the driving wheel of the embodiment of the present invention；
Fig. 7 is rough segmentation grid meshing gear contact stress of the embodiment of the present invention；
Fig. 8 is subdivided meshes meshing gear contact stress of the embodiment of the present invention；
Embodiment
The invention will be further described below in conjunction with the accompanying drawings：
Moment of torsion is loaded into little gear by the embodiment of the present invention using a pair of involute spur gears as research object,
Two gear materials are structural steel, and given spur gear basic parameter and material property are shown in Table 1：
| Modulus | Pressure angle | The number of teeth 1 | The number of teeth 2 |
| 2.5mm | 20° | 34 | 115 |
| The facewidth | Modulus of elasticity | Poisson's ratio | |
| 85mm | 210GPa | 0.3 |
In UG NX softwares, involute equation is set up using the modeling method of feature and parameter, the key correctly modeled is
Tooth curve is drawn, Involute gear formation basic theory figure as shown in Figure 2 draws the parametric polar equation formula of formula 1：
rk=rb/cosαk
θk=tan αk-αk
In order to which in the proper use of equation in NX, the equation of wushu 1 is changed shown in an accepted way of doing sth 2：
X=rb sin v-rb v cos v
Y=rb cos v+rb v sin v
Expression formula is inputted in Expression dialog boxes, involute is drawn using NX Law Curve functions, according to
The parameters such as modulus, the number of teeth of table 1, are fitted Involute gear, draw out whole profile, it is then determined that outside circle, reference circle etc. are main
The size of the other structures such as size and wheel rim, spoke and wheel hub is wanted, involute gear model is generated.In view of computer computing capability
The problem of, gear is cut, the part number of teeth is left and is analyzed, the threedimensional model of gear is as shown in Figure 3.
Need model being separated into grid model after solid modelling, controlled by definition unit attribute and mess generation, it is first
First definition material attribute Elastic Modulus E and Poisson's ratio are shown in Table described in 1, then selecting unit type and order, FEM model
The number of times of middle calculate node length is directly related with nodes, and the size influence computational accuracy of mesh-density, grid number density is got over
Greatly, solve the time longer, it is therefore desirable to this quantity is controlled in accuracy rating, the amount is reduced, calculate time-consuming to reduce.For
Structural analysis, the density of key point is big.Two gear intermeshings, contact zone is higher pair contact, and its contact portion grid is close
Degree needs higher requirement.The embodiment of the present invention starts to set Element Size using acquiescence, and obtained grid is thicker, such as
Shown in Fig. 4, by the way that Element Size are constantly changed into small, Element Size are finally transferred to 0.2mm, obtained by constantly experiment
Relatively regular thinner grid, subdivision result is shown in Fig. 5.
Identical boundary condition and load are applied to the model shown in Fig. 4 and Fig. 5 respectively, compare the meter of two kinds of mesh generations
Calculate result.Boundary condition is applied to gear using Joints functions.To driven pulley apply radially, circumferentially, axial freedom constraint,
Apply other revolutes constraint rotated except Z-direction to driving wheel, reservation rotates in a circumferential direction the free degree, and apply size and be
105kNmm torque.The boundary condition and load applied is as shown in Figure 6.
The curvature of every bit is different in flank profil, therefore flank profil everywhere subjects different load.In theory actively, it is driven
The node of two-wheeled and the contact stress of the meshing point of single pair of gear are larger, it should carry out FEM calculation of contact strength [1] in these positions.
But the Stress calculation in view of monodentate meshing point is difficult, and when the little gear number of teeth is more than 20, minimum point is engaged by monodentate
The stress of calculating is closer to engaging the stress calculated by node, therefore the Contact Stress of Gear of coupling gear can be public by HERZ
Formula is calculated：
Every symbol description such as table 2 in formula：
The major parameter of the gear of table 1 is substituted into, the Max.contact stress 271MPa of two gear teeth is obtained, with Fig. 7 conclusions
Error is 32.8%, and the error with Fig. 8 conclusions is 14%, it can be seen that mesh refinement directly affects simulation result.In tooth
In the actual engagement of wheel, the rotation of location following gear of load is born on the gear teeth in change, the contact position of between cog is taken turns also not
Disconnected change.What the contact zone shape in Hertz theory calculating was assumed that, calculation formula tends to safe consideration, and value is partial to guarantor
Keep, and obtained result of calculation is emulated by finite element modeling and more tallied with the actual situation.
The characteristics of embodiment of the present invention is：The design of gear is a complexity and rigorous process, master of the embodiment of the present invention
Parametric modeling is carried out to gear by UG, and simulation analysis are carried out to pitch point stress in ANSYS softwares, is calculated
The Max.contact stress of gear, relatively, error allows model in engineering for FEM calculation the data obtained and theoretical analysis result
Enclose, illustrate that model sets up correct, finite element analysis process is reasonable.Pass through the parametric modeling and design of gear, it is to avoid gear
Major design size modification repeatedly.According to design requirement, as long as changing major parameter with regard to the required model of gear can be obtained, make
The CAE of gear becomes easy, makes the design process of gear and becomes more easy.
Although the present invention is shown and described by reference to preferred embodiment, this professional ordinary skill
Personnel are it is to be appreciated that in the range of claims, can make various change in form and details.
Claims (2)
1. a kind of stress simulation analysis method in gear drive, it is characterised in that comprise the following steps：
(1) model of gear is created, a pair of involute spur gears of selection are stress simulation object, then in UGNX softwares
In, involute equation is set up using the modeling method of feature and parameter, then expression formula is inputted in Expression dialog boxes,
Involute is drawn using NX Law Curve functions, according to parameters such as modulus, the numbers of teeth, Involute gear is fitted, has drawn out
Whole flank profil, it is then determined that the size of the other structures such as the key dimension such as outside circle, reference circle and wheel rim, spoke and wheel hub, generation
Involute gear model, then cuts to gear, leaves the part number of teeth and is analyzed；
(2) need model being separated into grid model after definition material attribute, cell type, solid modelling, pass through definition unit
Attribute and mess generation are controlled, first definition material attribute Elastic Modulus E and Poisson's ratio, then selecting unit type and rank
It is secondary；
(3) grid division, to Element Size using giving tacit consent to, obtains rough segmentation grid, Element Size is transferred into 0.2mm,
Obtain subdivided meshes；
(4) define boundary condition, loading, respectively to rough segmentation grid model, subdivided meshes model apply identical boundary condition and
Load, compares the result of calculation of two kinds of mesh generations, applies boundary condition to gear using Joints functions, driven pulley is applied
Radially, circumferentially, axial freedom is constrained, and is applied other revolutes rotated except Z-direction to driving wheel and is constrained, reservation rotates in a circumferential direction
The free degree, and apply the torque that size is 105kNmm；
(5) analyzing static structural is done, contact analysis is carried out using finite element method, stress distribution is obtained, strain value, rough segmentation is picked up
After Max.contact stress under the model of gear engagement of grid is 182Mpa, subdivided meshes, Max.contact stress value is obtained
For 232.3Mpa；
(6) curvature of every bit is different in simulation analysis, flank profil, therefore flank profil everywhere subjects different load, in theory
Actively, the contact stress of the meshing point of the node of driven two-wheeled and single pair of gear is larger, it should carry out contacting strong in these positions
Degree is calculated, but is difficult in view of the Stress calculation of monodentate meshing point, and when the little gear number of teeth is more than 20, is engaged by monodentate
The stress that minimum point is calculated is closer to engaging the stress of calculating by node, therefore the Contact Stress of Gear of coupling gear can be by
The gear ratio of the gear of pitch diameter two of HERZ formula Superposition degree modulus loading coefficient pinion drive torque little gears substitutes into tooth
The major parameter of wheel, obtains the Max.contact stress 271Mpa of two gear teeth, it can be seen that mesh refinement directly affects emulation knot
Really.
2. the stress simulation analysis method in gear drive according to claim 1, it is characterised in that：The step (1)
In cutting carried out to gear allow for the computing capability of computer.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710616848.0A CN107292057A (en) | 2017-07-26 | 2017-07-26 | Stress simulation analysis method in gear drive |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710616848.0A CN107292057A (en) | 2017-07-26 | 2017-07-26 | Stress simulation analysis method in gear drive |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN107292057A true CN107292057A (en) | 2017-10-24 |
Family
ID=60102674
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710616848.0A Pending CN107292057A (en) | 2017-07-26 | 2017-07-26 | Stress simulation analysis method in gear drive |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN107292057A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109241697A (en) * | 2018-11-19 | 2019-01-18 | 徐工集团工程机械有限公司 | The design method and design device of thrust wheel rim size |
| CN110889215A (en) * | 2019-11-20 | 2020-03-17 | 常州大学 | ADAMS-based elliptic gear clearance simulation analysis method |
| CN111339678A (en) * | 2020-03-12 | 2020-06-26 | 广州机械科学研究院有限公司 | Method and device for analyzing and determining collision characteristics of multi-level face gear |
| CN111950178A (en) * | 2020-07-22 | 2020-11-17 | 中国第一汽车股份有限公司 | Gear automatic loading method based on HyperWorks software |
| CN114818181A (en) * | 2022-04-21 | 2022-07-29 | 哈尔滨工程大学 | Tooth profile based straight toothed spur gear finite element mesh automatic generation method and computer equipment |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105843985A (en) * | 2016-03-11 | 2016-08-10 | 武汉理工大学 | Involute bevel gear tooth end relief and parametric modeling method |
-
2017
- 2017-07-26 CN CN201710616848.0A patent/CN107292057A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105843985A (en) * | 2016-03-11 | 2016-08-10 | 武汉理工大学 | Involute bevel gear tooth end relief and parametric modeling method |
Non-Patent Citations (1)
| Title |
|---|
| NTWDQ: "《基于ANSYS的齿轮应力有限元分析》", 《HTTPS://WENKU.BAIDU.COM/VIEW/84405757E53A580217FCFE31.HTML》 * |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109241697A (en) * | 2018-11-19 | 2019-01-18 | 徐工集团工程机械有限公司 | The design method and design device of thrust wheel rim size |
| CN109241697B (en) * | 2018-11-19 | 2023-09-05 | 江苏徐工工程机械研究院有限公司 | Design method and design device for rim size of thrust wheel |
| CN110889215A (en) * | 2019-11-20 | 2020-03-17 | 常州大学 | ADAMS-based elliptic gear clearance simulation analysis method |
| CN110889215B (en) * | 2019-11-20 | 2023-05-23 | 常州大学 | ADAMS-based elliptic gear gap simulation analysis method |
| CN111339678A (en) * | 2020-03-12 | 2020-06-26 | 广州机械科学研究院有限公司 | Method and device for analyzing and determining collision characteristics of multi-level face gear |
| CN111950178A (en) * | 2020-07-22 | 2020-11-17 | 中国第一汽车股份有限公司 | Gear automatic loading method based on HyperWorks software |
| CN111950178B (en) * | 2020-07-22 | 2022-08-16 | 中国第一汽车股份有限公司 | Gear automatic loading method based on Hyperworks software |
| CN114818181A (en) * | 2022-04-21 | 2022-07-29 | 哈尔滨工程大学 | Tooth profile based straight toothed spur gear finite element mesh automatic generation method and computer equipment |
| CN114818181B (en) * | 2022-04-21 | 2023-08-25 | 哈尔滨工程大学 | Method and equipment for automatically generating finite element grid based on tooth profile straight-tooth cylindrical gear |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN107292057A (en) | Stress simulation analysis method in gear drive | |
| Hwang et al. | Contact stress analysis for a pair of mating gears | |
| Gupta et al. | Contact stress analysis of spur gear | |
| Fan | Tooth surface error correction for face-hobbed hypoid gears | |
| Barone et al. | Evaluation of the effect of misalignment and profile modification in face gear drive by a finite element meshing simulation | |
| Mermoz et al. | A new methodology to optimize spiral bevel gear topography | |
| Simon | Design and manufacture of spiral bevel gears with reduced transmission errors | |
| Feng et al. | Geometric design and analysis of face-gear drive with involute helical pinion | |
| Barbieri et al. | Adaptive grid-size finite element modeling of helical gear pairs | |
| CN105122248A (en) | Method for modelling a part, in particular a turbine blade | |
| CN110321655B (en) | Tooth surface dynamic load distribution calculation method | |
| Venkatesh et al. | Design and structural analysis of high speed helical gear using Ansys | |
| Kamouneh et al. | Diagnosis of involutometric issues in flat rolling of external helical gears through the use of finite-element models | |
| Aziz et al. | Comparative analysis of tooth-root strength using stress–strength interference (SSI) theory with FEM-based verification | |
| Guilbault et al. | Helical gears, effects of tooth deviations and tooth modifications on load sharing and fillet stresses | |
| Mao | An approach for powertrain gear transmission error prediction using the non-linear finite element method | |
| Sarkar et al. | Stress analysis of helical gear by finite element method | |
| Gonzalez-Perez et al. | Analytical determination of basic machine-tool settings for generation of spiral bevel gears from blank data | |
| Zhang et al. | Design, meshing characteristics and stress analysis of cylindrical gears with curvilinear tooth profile | |
| CN104008286A (en) | Space flexible mechanism dynamic reliability analysis method based on PSO | |
| CN112651092A (en) | Worm and gear design analysis method | |
| Kalay et al. | Effects of tooth root cracks on vibration and dynamic transmission error responses of asymmetric gears: A comparative study | |
| Khodaee et al. | A study of the effects of reversal cycles in the gear rolling process by using finite element simulations | |
| Bair et al. | Mathematical model and characteristic analysis of elliptical gears manufactured by circular-arc shaper cutters | |
| Reddy et al. | Developing a basic CAD model of a spur gear using an automated approach |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20171024 |
|
| WD01 | Invention patent application deemed withdrawn after publication |