CN104102778B - A kind of crankshaft dynamic analysis method - Google Patents
A kind of crankshaft dynamic analysis method Download PDFInfo
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- CN104102778B CN104102778B CN201410338434.2A CN201410338434A CN104102778B CN 104102778 B CN104102778 B CN 104102778B CN 201410338434 A CN201410338434 A CN 201410338434A CN 104102778 B CN104102778 B CN 104102778B
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Abstract
The present invention relates to engine art more particularly to a kind of crankshaft dynamic analysis methods.The present invention provides a kind of crankshaft dynamic analysis method, includes the following steps：A, the finite element model for establishing engine and crankshaft system parts carries out piecemeal to bent axle, row 3D entity finite element mesh generations is tapped into piecemeal crankshaft straight；B, engine structure and crankshaft system component number are subjected to Rigidity Calculation to crank throw respectively according in input finite element model；C, lubricating oil and explosion pressure curve are selected, load solution is carried out；D, crankshaft stress is calculated and safety coefficient solves；E, according to solving result, bent axle is evaluated.The present invention provides the crankshaft dynamic analysis method that a kind of speed is fast, efficient, reliability is high, largely reduces the time；3D mesh generations are carried out rapidly and efficiently to bent axle, analysis model establishes quick, response soon；It is short to calculate the solution time；This method is more accurate than ONE-DIMENSIONAL METHOD, quicker than complete three-dimensional method.
Description
Technical field
The present invention relates to engine art more particularly to a kind of crankshaft dynamic analysis methods.
Background technology
Bent axle is one of most important parts of engine, its dimensional parameters, which largely not only affect, to be started
The overall dimensions and weight of machine, and largely affect the reliable and service life of engine.The malicious event of bent axle can
It can cause the badly damaged of other parts and engine.At the beginning of engine is designed and developed, the structure as early as possible to bent axle is needed
Form, dimensional parameters, material and technique etc. are assessed.Therefore, in the engine concept design phase, to crankshaft stress and safety
The dynamic analysis that coefficient carries out quickly, efficiently and accurately is very important.
In traditional crankshaft dynamic analysis, there is following problem：
1, bent axle is simplified using One Dimension Analysis method, is unable to detailed reaction crankshaft structure information；
2, it using complete three dimensional analysis method, then needs to establish engine complete machine FEM finite element models, complex parts are such as
Time-consuming for the division finite element grid such as gray iron, bent axle and grid assembly；Number of grid is big, and finite element grid quality is also difficult
To ensure；Under huge number of grid, time-consuming for finite element analysis；FEM calculation is difficult to restrain, and analyzes easily failure.
3, when carrying out mesh generation to bent axle, 2D mesh generations first are carried out to bent axle, regenerate 3D grids, 2D grids are drawn
Divide and take, 3D mesh qualities are problematic, also need repeatedly to adjust 2D grids, elapsed time is long.
Invention content
It is in view of the deficiencies in the prior art or insufficient, the technical problem to be solved by the present invention is to：A kind of speed is provided
Spend crankshaft dynamic analysis method fast, efficient, that reliability is high.
The technical solution that the present invention takes is to provide a kind of crankshaft dynamic analysis method, is included the following steps：
A, the finite element model for establishing engine and crankshaft system parts carries out piecemeal to bent axle, direct to piecemeal bent axle
Carry out 3D entity finite element mesh generations；
B, engine structure and crankshaft system component number are subjected to rigidimeter to crank throw respectively according in input finite element model
It calculates；
C, lubricating oil and explosion pressure curve are selected, load solution is carried out；
D, crankshaft stress is calculated and safety coefficient solves；
E, according to solving result, bent axle is evaluated.
As a further improvement on the present invention, the Rigidity Calculation includes torsion, coplanar bending and non-uniplanar bending rigidimeter
It calculates.
As a further improvement on the present invention, the step C include it is following step by step：
C1, static determinacy solution is first carried out；
C2, static indeterminacy solution is carried out again.
As a further improvement on the present invention, the Stress calculation uses Quasi-static Method.
As a further improvement on the present invention, the safety coefficient solution is solved using Goodman figures.
As a further improvement on the present invention, the step D include it is following step by step：
D1, first the crank throw Stress calculation under progress specific loading, the crank throw include 1/2 trunnion, 1/2 connecting rod neck, song
Shaft arm, rod journal fillet, trunnion fillet, oilhole；
D2, crankshaft stress calculating under each operating loading is carried out again.
As a further improvement on the present invention, the solving result includes crank throw stress calculating results, material properties.
As a further improvement on the present invention, there is step F after the step E：It is evaluated as being unsatisfactory for crankshaft material strong
Degree and fatigue safety coefficient requirement need to carry out structure change to bent axle, then re-start calculating.
The beneficial effects of the invention are as follows：After using technical scheme of the present invention, advantageous effect below is achieved：1、
Mesh generation need not be carried out to complex parts such as gray irons, largely reduce the time；2, fast to bent axle progress 3D mesh generations
Fast efficiently avoiding needs first to carry out 2D mesh generations in conventional method, then to carry out the cumbersome of method of 3D mesh generations, efficiency low
Etc. drawbacks；3, analysis model establishes quick, response soon；4, it is short to calculate the solution time；5, this method is more accurate than ONE-DIMENSIONAL METHOD,
It is quicker than complete three-dimensional method.
Description of the drawings
Fig. 1 is the flow chart of crankshaft dynamic analysis method of the present invention；
Fig. 2 is crankshaft dynamic analysis method bent axle cutting whole into sections structural schematic diagram of the present invention；
Fig. 3 is crankshaft dynamic analysis method torsion stiffness schematic diagram of the present invention；
Fig. 4 is the coplanar bending stiffness schematic diagram of crankshaft dynamic analysis method of the present invention；
Fig. 5 is crankshaft dynamic analysis method non-uniplanar bending rigidity schematic diagram of the present invention；
Fig. 6 is crankshaft dynamic analysis method crank throw structure chart of the present invention；
Fig. 7 is crankshaft dynamic analysis method Goodman figures of the present invention.
Digital representation in figure：1, connecting rod neck center line；2, trunnion center line；3, crank throw.
Specific implementation mode
The present invention is further described for explanation and specific implementation mode below in conjunction with the accompanying drawings.
As shown in Figure 1, the present invention provides a kind of crankshaft dynamic analysis method, include the following steps：
A, the finite element model for establishing engine and crankshaft system parts carries out piecemeal to bent axle, direct to piecemeal bent axle
Carry out 3D entity finite element mesh generations；For proof stress computational accuracy, mesh generation needs thinner closeer in radius area；
The mesh generation includes：1, crank-resolved model is imported in Hypermesh, takes the central plane of trunnion and rod journal, such as
Shown in Fig. 2, by bent axle piecemeal.
2, the tetramesh in 3D is selected, selects Volume Tetra directly to carry out 3D physical grids to bent axle piecemeal and draws
Point, the division of 2D grids is first carried out so as to avoid traditional, then carry out the division of 3D grids, 3D mesh qualities are unqualified, also
The cumbersome approaches that need to be repeatedly adjusted between 2D grids and 3D grids.To ensure follow-up crankshaft stress computational accuracy, fillet
Fillet area grids are fine.
As shown in Figures 3 to 6, B, by engine structure and crankshaft system component number according to input finite element model Engdyn
In, crank throw 2 is reversed respectively, it is coplanar bending and non-uniplanar bending Rigidity Calculation, calculate bent axle rigidity, as shown in figure 3, being not required to
Analysis model is built, does not have to grid division, saves the plenty of time so that analytical cycle greatly shortens.
Torsion stiffness:In the plane of connecting rod neck center line 1 and trunnion center line 3, applies torque, calculate
The rigidity come.
Coplanar bending stiffness:By in the plane of connecting rod neck center line 1 and trunnion center line 3, applying torque, calculate
Rigidity out.
Non-uniplanar bending rigidity:It is being formed by plane perpendicular to by connecting rod neck and trunnion center line, and is passing through main shaft
In the plane of neck center line, apply torque, the rigidity calculated.
C, lubricating oil and explosion pressure curve are selected, load solution is carried out；
The step C include it is following step by step：
C1, static determinacy solution is first carried out；
C2, static indeterminacy solution is carried out again.
Load solves：Suitable oil number is selected from the lubricating oil database of Engdyn.It will be quick-fried under each operating mode
It sends out in pressure curve input model.It selects Indeterminate static indeterminacy to solve to calculate, at this moment can first carry out Determinate
Static determinacy solves, and solves the equation of static equilibrium, and the primary condition that its result is solved as Indeterminate static indeterminacy is added
The deformation compatibility condition for ensureing the deformation geometry relationship that structural continuity should meet, obtains the loads on crankshaft under each operating mode.
As shown in fig. 7, D, to crankshaft stress calculate and safety coefficient solve；It is quasi-static using finite element
FE Quasi-Static methods carry out the calculating of specific loading Unit Loads.Based on specific loading Unit
The result of calculation of Load carries out Stress calculation to crank arm, rod journal fillet, trunnion fillet, oilhole etc..It uses
Goodman figures carry out safety coefficient calculating.
The stress coupling is bent and distorting stress.
Define σycFor material compression yield strength,
σytFor material tensile yield strength,
σutFor the ultimate tensile strength of material,
σflFor the fatigue limit intensity of material.
According to above-mentioned parameter, Goodman Safety Factor curve graphs as shown in Figure 4 can be drawn out.According to
Goodman curve graphs can calculate the safety coefficient under each operating mode.
Wherein σmFor mean stress, computational methods are：
σaFor stress amplitude, computational methods are：
Cyclic Overload safety coefficient computational methods are：
General Overload safety coefficient computational methods are:
The step D include it is following step by step：
D1, first the crank throw Stress calculation under progress specific loading, the crank throw include 1/2 trunnion, 1/2 connecting rod neck, song
Shaft arm, rod journal fillet, trunnion fillet, oilhole；
D2, crankshaft stress calculating under each operating loading is carried out again.
E, according to solving result, bent axle is evaluated.
The Stress calculation uses Quasi-static Method.
The safety coefficient solution is solved using Goodman figures.
The solving result includes crank throw stress calculating results, material properties.
There is step F after the step E：It is evaluated as being unsatisfactory for crankshaft material intensity and fatigue safety coefficient requirement, need
Structure change is carried out to bent axle, then re-starts calculating.
The above content is a further detailed description of the present invention in conjunction with specific preferred embodiments, and it cannot be said that
The specific implementation of the present invention is confined to these explanations.For those of ordinary skill in the art to which the present invention belongs, exist
Under the premise of not departing from present inventive concept, a number of simple deductions or replacements can also be made, all shall be regarded as belonging to the present invention's
Protection domain.
Claims (2)
1. a kind of crankshaft dynamic analysis method, it is characterised in that：Include the following steps：
A, the finite element model for establishing engine and crankshaft system parts carries out piecemeal to bent axle, row is tapped into piecemeal crankshaft straight
3D entity finite element mesh generations；
B, engine structure and crankshaft system component number are subjected to Rigidity Calculation to crank throw respectively according in input finite element model；
The Rigidity Calculation includes torsion, coplanar bending and non-uniplanar bending Rigidity Calculation；
C, lubricating oil and explosion pressure curve are selected, load solution is carried out；The step C include it is following step by step：
C1, static determinacy solution is first carried out；
C2, static indeterminacy solution is carried out again；
D, crankshaft stress is calculated and safety coefficient solves；The Stress calculation uses Quasi-static Method；The safety system
Number is solved and is solved using Goodman figures；The step D include it is following step by step：
D1, first carry out specific loading under crank throw Stress calculation, the crank throw include 1/2 trunnion, 1/2 connecting rod neck, crank arm,
Rod journal fillet, trunnion fillet, oilhole；
D2, crankshaft stress calculating under each operating loading is carried out again；
E, according to solving result, bent axle is evaluated；The solving result includes crank throw stress calculating results, material properties.
2. crankshaft dynamic analysis method according to claim 1, it is characterised in that：There is step after the step E
F：It is evaluated as being unsatisfactory for crankshaft material intensity and fatigue safety coefficient requirement, structure change need to be carried out to bent axle, then re-start
It calculates.
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Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105069224B (en) * | 2015-08-06 | 2017-12-08 | 北汽福田汽车股份有限公司 | A kind of crankshaft strength computational methods |
| CN108228936A (en) * | 2016-12-21 | 2018-06-29 | 华晨汽车集团控股有限公司 | A kind of connection rod of automobile engine dynamic analysis method |
| CN107665286A (en) * | 2017-10-31 | 2018-02-06 | 华晨汽车集团控股有限公司 | One kind is on automobile engine bearings dynamic analysis method |
| CN108287957B (en) * | 2018-01-12 | 2021-06-08 | 西华大学 | Safety analysis method for main longitudinal beam of road heavy cargo transportation trailer |
| CN113343508A (en) * | 2020-02-18 | 2021-09-03 | 北京福田康明斯发动机有限公司 | Method for analyzing buckling of connecting rod |
| CN113532817B (en) * | 2021-05-31 | 2022-04-01 | 东风马勒热***有限公司 | Method for measuring and calculating safety coefficient of silicone oil fan |
| CN113343526B (en) * | 2021-06-04 | 2024-01-30 | 南京林业大学 | Fatigue limit load prediction method for quenched steel crankshaft |
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| CN203201995U (en) * | 2013-03-14 | 2013-09-18 | 南车玉柴四川发动机股份有限公司 | High-power marine engine crankshaft |
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| CN101158989A (en) * | 2007-11-02 | 2008-04-09 | 奇瑞汽车有限公司 | Engine crankshaft dynamic analysis method |
| KR20090050855A (en) * | 2007-11-16 | 2009-05-20 | 현대자동차주식회사 | Engine crankshaft fatigue limit stress determination method |
| CN203201995U (en) * | 2013-03-14 | 2013-09-18 | 南车玉柴四川发动机股份有限公司 | High-power marine engine crankshaft |
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