CN106777820A - A kind of big part Dynamic performance Optimization method for designing of machine tool basic - Google Patents
A kind of big part Dynamic performance Optimization method for designing of machine tool basic Download PDFInfo
- Publication number
- CN106777820A CN106777820A CN201710047760.1A CN201710047760A CN106777820A CN 106777820 A CN106777820 A CN 106777820A CN 201710047760 A CN201710047760 A CN 201710047760A CN 106777820 A CN106777820 A CN 106777820A
- Authority
- CN
- China
- Prior art keywords
- big part
- lathe
- dynamic performance
- analysis
- machine tool
- 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
-
- 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]
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Theoretical Computer Science (AREA)
- Computer Hardware Design (AREA)
- Evolutionary Computation (AREA)
- Geometry (AREA)
- General Engineering & Computer Science (AREA)
- General Physics & Mathematics (AREA)
- Numerical Control (AREA)
Abstract
A kind of big part Dynamic performance Optimization method for designing of machine tool basic of the present invention, lathe assembly is simplified according to Dynamics Simulation Analysis requirement, assembly after simplification is imported into ANSYS/Workbench carries out mesh generation, material setting, boundary condition setting, completes the model analysis of lathe assembly.In harmonic responding analysis, by simulating cutter actual working state, obtain lathe assembly main spindle box end under the effect of simple harmonic quantity power X to, the peak swing response of Y-direction, Z-direction.Experimental design is finally carried out to basic big part mass property parameter using Parametric Analysis technology, fitting obtains the response surface model between the big part mass property of machine dynamic performance response and basis.It is analyzed by response surface model, not only can qualitatively finds out basic big weak link of the part in machine dynamic performance, can also quantitatively predict the trend that the change of basic big part influences on machine dynamic performance, improves the precision of Machine Tool design.
Description
Technical field
The present invention relates to Digit Control Machine Tool optimization design field, specially a kind of big part Dynamic performance Optimization design of machine tool basic
Method.
Background technology
Static properties and dynamic property that the lathe superperformance requirement big part of machine tool basic has had.At present, Machine Tool design
Method still continues to use experience, the conventional method of analogy design lathe static strength and Static stiffness, does not recognize machine dynamic characteristics
Material impact effect to machine tool capability.Now, Digit Control Machine Tool is produced towards high accuracy, crudy high, high stability and height
Rate direction is developed, and the dynamic property of lathe has become the important indicator for weighing machine tool capability.
Model analysis and harmonic responding analysis are the basic contents of machine dynamic performance analysis.Mould is carried out by finite element method
State is analyzed and harmonic responding analysis, dynamics that can be to the vibration characteristics of lathe and lathe under the effect of certain frequency harmonic model
Response carries out qualitative analysis, but is unable to the sensitivity that the big part in each basis of quantitative analysis lathe influences on machine dynamic performance,
So as to the effect tendency of the change to its dynamic property of the big part of machine tool basic can not be predicted.
The content of the invention
For problems of the prior art, the present invention provides a kind of big part Dynamic performance Optimization design side of machine tool basic
Method, by Parametric Analysis technology and response surface experiments designing technique, not only can qualitatively find out shadow in the big part of machine tool basic
The weak link of machine dynamic performance is rung, the sensitivity that the big part of machine tool basic influences on it can also be quantitatively analyzed, machine is improved
Bed design accuracy and design efficiency.
The present invention is to be achieved through the following technical solutions：
A kind of big part Dynamic performance Optimization method for designing of machine tool basic, comprises the following steps：
1) the dynamic analysis requirement according to lathe, simplifies in CAD software to lathe entire assembly model；
2) the lathe entire assembly model after simplification is imported into finite element analysis software；
3) mesh generation is carried out to lathe entire assembly model in finite element analysis software, and main spindle box to lathe is carried out
Mesh refinement；
4) material properties for carrying out the big part in each basis to lathe entire assembly model in finite element analysis software set, combine
Face attribute is set and boundary condition is set, and on the basis of mesh generation is carried out to lathe entire assembly model, completes lathe assembling
The Modal Analysis analysis of body, obtains the eigenfrequncies and vibration models of lathe assembly, so as to obtain the first natural frequency of lathe；
5) intrinsic frequency according to lathe assembly and the machine spindle speed of setting, complete in finite element analysis software
The harmonic responding analysis of lathe assembly, obtain main spindle box end X under the effect of simple harmonic quantity power and are responded to the peak swing of, Y-direction and Z-direction
Value；
6) first natural frequency in finite element analysis software to lathe, the peak swing response of three-dimensional and setting
The big part mass property parameter of machine tool basic is parameterized, and test sample point is obtained by Central Composite experimental design mode, profit
The corresponding machine dynamic performance response of test sample point is obtained with simulation analysis；
7) according to step 6) the middle response for testing sample point and test sample point, build each machine dynamic performance response
And the quadratic polynomial response surface model between the big part mass property parameter in basis：
Wherein：Y is machine dynamic performance response, and x is a big part mass property parameter in basis, big part based on n
Number, β is undetermined coefficient, big part mass property parameter sequence number based on i and j is equal, and i, j and n are natural number；
8) on the basis of quadratic polynomial response surface model obtained above, the big part mass property parameter in each basis is asked
Partial derivative, obtains the sensitivity that basic big part mass property parameter influences on machine dynamic performance, by between each sensitivity
Compare, big influence of the part to machine dynamic performance in qualitative analysis basis；
9) obtain influenceing the weak link of machine dynamic performance according to sensitivity the qualitative analysis；It is big for machine tool basic
Weak link in part, changes the big part mass property parameter in basis, quantitative forecast basis in quadratic polynomial response surface model
Big part mass property changes the effect tendency and influence amount to machine dynamic performance, carries out quantitative analysis, completes lathe dynamic
Can optimization design.
Preferably, step 1) in, the specific method that lathe entire assembly model simplifies is：
1) the small chamfering of size and fillet in deletion lathe assembly；
2) deleting does not influence the small feature of simulation analysis, and described small feature includes screw hole, bolt hole and oil filler point；
3) transmission system is simplified, reduction box internal structure is simplified using equivalent mass, screw structure uses cylinder generation
Replace；
4) simplify main axle structure, when carrying out assembly simulation analysis, be analyzed main shaft as an entirety, use
Effect physical model and equivalent mass are replaced；
5) simplify supplementary structure, do not produce the supplementary structure of influence, use quality point to carry out generation to assembly structural rigidity
Replace；
6) undersized plane characteristic in assembly is deleted, it is ensured that good element quality.
Preferably, step 5) in, in harmonic responding analysis, the force boundary condition in boundary condition is set as follows：
Apply the equal cutting force of two groups of numerical value in spindle end, size is the cutting force width that lathe is processed under nominal power
Value, 90 ° of phase angle difference, the actual working state for simulating cutter.
Preferably, step 6) in, when carrying out parametrization setting to the big part mass property parameter in lathe assembly basis, use
Central Composite experimental design mode obtains test sample point；The harmonious sound of lathe assembly model analysis is carried out by finite element method
Should analyze, obtain the corresponding machine dynamic performance response of above-mentioned test sample point.
Further, step 6) in machine tool basic big part mass property parametrization is comprised the following steps：
6.1 pairs of big part mass parameter experimental design modes in basis are tested using Central Composite；Part is original sets with basic big
Centered on meter quality, lower limit is the 90% of the big part original design quality of machine tool basic, and the upper limit is the big part original design of machine tool basic
The 110% of quality, obtains the test sample point under Central Composite test method；
6.2 are calculated the machine dynamic performance response under Central Composite test method, including ginseng by simulation analysis
The main spindle box end of the lathe first natural frequency of numberization and parametrization under the effect of simple harmonic quantity power X to, the peak swing of Y-direction, Z-direction
Response.
Preferably, step 7) in, the big part mass property parameter in lathe assembly basis is obtained using least square fitting
With the quadratic polynomial response surface model between machine dynamic performance response.
Further, the step 7) in, fitting quadratic polynomial response surface model is comprised the following steps：
7.1 output variables be respectively lathe first natural frequency and main spindle box end simple harmonic quantity power effect under X to, Y-direction, Z
To peak swing response, design variable for the big part of machine tool basic mass property parameter；
7.2 are fitted using least square method to output variable and design variable, obtain quadratic polynomial response face mould
The fitting coefficient of type.
Preferably, step 8) in, by big to each basis in quadratic polynomial response surface model as design variable
Part mass property parameter seeks local derviation, obtains big sensitivity of the part mass property to dynamic property response in lathe assembly basis,
Wherein, machine dynamic performance is caused to change maximum key element as lathe dynamic during each basic big part mass property Parameters variation
Can weak link.
Preferably, step 9) in, by changing the quality characteristic value of the big part in basis in quadratic polynomial response surface model,
Obtain machine dynamic performance response, can quantitative analysis go out the change of basic big part mass property parameter to machine dynamic performance
The trend and influence amount of influence；According to the trend and influence amount of prediction, the weak link in the original entire assembly model of lathe is changed,
Quantitative analysis is carried out, the optimization design of machine dynamic performance is completed.
Preferably, described finite element analysis software uses ANSYS/Workbench softwares.
Compared with prior art, the present invention has following beneficial technique effect：
The present invention simplifies according to Dynamics Simulation Analysis requirement to lathe assembly, and the assembly after simplification is imported
Mesh generation, material setting, boundary condition setting are carried out in ANSYS/Workbench, the mode point of lathe assembly is completed
Analysis.In harmonic responding analysis, by simulating cutter actual working state, lathe assembly main spindle box end is obtained in simple harmonic quantity masterpiece
With lower X to, the peak swing response of Y-direction, Z-direction.Finally using Parametric Analysis technology to basic big part mass property parameter
Experimental design is carried out, fitting obtains the response surface model between the big part mass property of machine dynamic performance response and basis.It is logical
Cross and response surface model be analyzed, not only can qualitatively find out basic big weak link of the part in machine dynamic performance,
The trend that the change of basic big part influences on machine dynamic performance can also be quantitatively predicted, the precision of Machine Tool design is improved,
And quantitative analysis can directly be carried out to it to similar lathe, based on response surface model, it is to avoid the duplication of labour and
Operation, improves the efficiency of optimization design, the traditional design method offer guidance to continuing to use experience, analogy.
Brief description of the drawings
Fig. 1 is overall flow figure of the present invention.
Fig. 2 is simulation analysis schematic diagram of the present invention in ANSYS/Workbench.
Fig. 3 a are big sensitivity of the part mass property parameter to lathe first natural frequency in each basis.
For the big part mass property parameter in each basis, to main spindle box end, the X under the effect of simple harmonic quantity power is responded Fig. 3 b to peak swing
The sensitivity of value.
Fig. 3 c are the Y-direction peak swing response under the effect of simple harmonic quantity power to main spindle box end of the big part mass property parameter in each basis
The sensitivity of value.
Fig. 3 d are the Z-direction peak swing response under the effect of simple harmonic quantity power to main spindle box end of the big part mass property parameter in each basis
The sensitivity of value.
Specific embodiment
With reference to specific embodiment, the present invention is described in further detail, it is described be explanation of the invention and
It is not to limit.
A kind of big part Dynamic performance Optimization method for designing of machine tool basic of the present invention, based on experimental design, comprising finite element fraction
Analysis software parameters analytical technology and response surface experiments designing technique.Lathe assembly is entered according to Dynamics Simulation Analysis requirement
Row simplifies, and the assembly after simplification is imported into finite element analysis software carries out that mesh generation, material are set, boundary condition sets
Put, complete the model analysis of lathe assembly.In harmonic responding analysis, by simulating cutter actual working state, lathe is obtained
Assembly main spindle box end under the effect of simple harmonic quantity power X to, the peak swing response of Y-direction, Z-direction.Finally use Parametric Analysis
Technology carries out experimental design to basic big part mass property parameter, and fitting obtains the big part matter of machine dynamic performance response and basis
Response surface model between flow characteristic parameter.By to response surface analysis, not only can qualitatively find out basic big part in lathe
Weak link in dynamic property, can also quantitatively predict the change of basic big part to becoming that machine dynamic performance influences
Gesture, so as to improve the precision and efficiency of Machine Tool design.
Specifically, the method for the invention, as depicted in figs. 1 and 2, comprises the following steps.
1. lathe entire assembly model simplifies.
The entire assembly model for setting up lathe is simplified in CAD software, particular content includes：
(1) the small chamfering of size and fillet in deletion lathe assembly；
(2) deleting does not influence the small feature of simulation analysis：Screw hole, bolt hole, oil filler point；
(3) transmission system is simplified：Reduction box internal structure is simplified using equivalent mass, and screw structure uses simple circle
Post replaces；
(4) main axle structure is simplified：When carrying out assembly simulation analysis, it is analyzed main shaft as an entirety, is used
Equivalent entity model and equivalent mass are replaced；
(5) supplementary structure is simplified：Not producing the supplementary structure of influence, use quality point on assembly structural rigidity carries out generation
Replace；
(6) undersized plane characteristic in assembly is deleted, it is ensured that good element quality.
2. in finite element analysis software entire assembly model importing and treatment.
Illustrated by taking ANSYS/Workbench softwares as an example in this preferred embodiment, the lathe assembly mould that will be kept
Type is imported into software by geometry menus in ANSYS/Workbench.In geometry menus, by Boolean calculation
Correlated parts are merged, is made main big comprising the basis such as lathe bed, column, saddle, main spindle box, workbench in entire assembly model
Part, reduces the faying face in assembly, improves computational efficiency.Design of material requirement according to lathe, in Workbench material depots
It is middle set up entire assembly model respectively required for material.In the present embodiment, the faying face of entire assembly model mainly considers two kinds：
A kind of is the bolt fixed combinating surface of lathe bed and column, and another kind is lathe bed and workbench, column and saddle, saddle and main spindle box
The movable faying face of guide rail.In the simulation analysis of lathe assembly, fixed combinating surface is set to Bonded (bonding) mode,
Movable faying face is set to No separation (slip is not separated) mode.
3. mesh generation.
Because entire assembly model physical dimension is larger, complex structure, number of parts it is many, size of mesh opening is set into 50mm, it is right
Thinner grid can be divided into the critical concern such as main spindle box region.
4. lathe assembly model analysis.
The boundary condition of model analysis is set in finite element analysis software, and the main fixed constraint including foundation bolt sets
Put.It is the eigenfrequncies and vibration models that can obtain lathe assembly by model analysis.
5. lathe assembly harmonic responding analysis.
The rank of lathe first and second-order natural frequency value that model analysis is obtained are respectively：48.119Hz and 54.426Hz,
The solution interval for setting harmonic responding analysis is 0Hz to 60Hz, and solution point is 40.Because lathe is during reality processing, cut
Along the circumferential direction it is continually changing to cutting force main axis, extraneous exciting force size is set for lathe is processed under nominal power
Cutting force amplitude, actual working state of 90 ° of the phase angle difference to simulate cutter.Main shaft is obtained by harmonic responding analysis
Case end under the effect of simple harmonic quantity power X to, the peak swing response of Y-direction, Z-direction.
6. quadratic polynomial response surface model fitting.
In order to obtain the rule that basic big part influences on machine dynamic performance, the weak link of machine dynamic performance is found out,
Using the Parameter Function Unit of ANSYS/Workbench, fitting obtains basic big part mass property and machine dynamic performance response
Between response surface model.Response surface model can be represented between response and design variable with dominant function expression
Relation.Response i.e. output valve, have 5 design variables in the present invention, the big part lathe bed in basis, column, saddle, main spindle box,
The quality of workbench.Due to the constancy of volume of the big part in each basis, therefore, to basic big part lathe bed, column, saddle, main spindle box, work
The density for making platform carries out experimental design, composite experiment design centered on test method.Central Composite experimental design can be with minimum
Working cycles provide test sample point.Specific method is：Centered on the corresponding density of basic part original design quality greatly, under
The 90% of the big part original design quality correspondence density of machine tool basic is limited to, the upper limit is the big part original design quality correspondence of machine tool basic
The 110% of density, obtains the test sample point under Central Composite test method；By ANSYS/Workbench Parametric Analysis
Technology, obtains the corresponding dynamic property response of Central Composite test method sample point：Lathe first natural frequency and main spindle box
End under the effect of simple harmonic quantity power X to, the peak swing response of Y-direction, Z-direction.
By least square fitting test sample point and the corresponding response of sample point, you can obtain lathe single order intrinsic
Frequency and main spindle box end under the effect of simple harmonic quantity power X between, the big part quality of the peak swing response of Y-direction, Z-direction and basis
Quadratic polynomial response surface model：
Wherein：Y is output variable, xiIt is design variable, n is design variable number, and β is undetermined coefficient, and β passes through a most young waiter in a wineshop or an inn
Multiplication fitting is obtained.
7. Dynamic performance Optimization design.
Local derviation is asked to can obtain basic big part matter the big part quality in each basis using the above-mentioned quadratic polynomial model tried to achieve
Measure to lathe assembly dynamic property lathe first natural frequency and main spindle box end under the effect of simple harmonic quantity power X to, Y-direction, Z-direction
The sensitivity of peak swing response, as shown in accompanying drawing 3a, accompanying drawing 3b, accompanying drawing 3c, accompanying drawing 3d.Can by sensitivity analysis result
To find, the dynamic property column of lathe assembly, saddle, main spindle box quality change it is very sensitive.It is possible thereby to determine
Column, saddle, main spindle box quality are the weak links of machine dynamic performance.In by changing quadratic polynomial response surface model
The mass value of basic big part, obtain lathe first natural frequency and main spindle box end under the effect of simple harmonic quantity power X to, Y-direction, Z-direction
The functional value of peak swing response, can go out the change of basic big part quality to becoming that machine dynamic performance influences with quantitative analysis
Gesture and influence amount.According to the trend and influence amount of prediction, the weak link in the modification original entire assembly model of lathe, you can complete
The optimization design of machine dynamic performance, so as to improve the design accuracy and efficiency of lathe.
Wherein, as shown in Figure 3 a, the big part mass property in each basis for obtaining is analyzed by quadratic polynomial response surface model
Sensitivity of the parameter to complete machine tool first natural frequency.Each big part quality in basis is to the sensitive of lathe first natural frequency
Angle value is negative, represents as the first rank of increase lathe natural frequency value of basic big part quality reduces, wherein, column, cunning
Saddle, the influence of main spindle box quality are maximum.
As shown in Figure 3 b, the big part mass property parameter pair in each basis for obtaining is analyzed by quadratic polynomial response surface model
Main spindle box end under the effect of simple harmonic quantity power sensitivity from X to peak swing response, column, the influence of main spindle box quality are maximum.Its
In, column quality to main spindle box end simple harmonic quantity power effect under sensitivity from X to peak swing response be negative value, represent with
Column quality increases, and X reduces to peak swing response.Main spindle box quality to main spindle box end simple harmonic quantity power effect under X to most
The sensitivity of large amplitude response is on the occasion of expression increases with main spindle box quality, and X increases to peak swing response.
As shown in Figure 3 c, the big part mass property parameter pair in each basis for obtaining is analyzed by quadratic polynomial response surface model
The sensitivity of main spindle box end Y-direction peak swing response under the effect of simple harmonic quantity power, column, the influence of saddle quality are maximum.Wherein,
Column, saddle quality to main spindle box end simple harmonic quantity power effect under Y-direction peak swing response sensitivity be negative value, represent with
Column, saddle quality increases, and Y-direction peak swing response reduces.
As shown in Figure 3 d, the big part mass property parameter pair in each basis for obtaining is analyzed by quadratic polynomial response surface model
The sensitivity of main spindle box end Z-direction peak swing response under the effect of simple harmonic quantity power, column, the influence of saddle quality are maximum.Wherein,
Column, saddle quality to main spindle box end simple harmonic quantity power effect under Z-direction peak swing response sensitivity be negative value, represent with
Column, saddle quality increases, and Z-direction peak swing response reduces.
Claims (10)
1. the big part Dynamic performance Optimization method for designing of a kind of machine tool basic, it is characterised in that comprise the following steps：
1) the dynamic analysis requirement according to lathe, simplifies in CAD software to lathe entire assembly model；
2) the lathe entire assembly model after simplification is imported into finite element analysis software；
3) mesh generation is carried out to lathe entire assembly model in finite element analysis software, and main spindle box to lathe carries out grid
Refinement；
4) material properties setting, the faying face category of the big part in each basis are carried out to lathe entire assembly model in finite element analysis software
Property set and boundary condition is set, on the basis of mesh generation is carried out to lathe entire assembly model, complete lathe assembly
Modal Analysis are analyzed, and the eigenfrequncies and vibration models of lathe assembly are obtained, so as to obtain the first natural frequency of lathe；
5) intrinsic frequency according to lathe assembly and the machine spindle speed of setting, complete lathe in finite element analysis software
The harmonic responding analysis of assembly, obtain main spindle box end under the effect of simple harmonic quantity power X to, Y-direction and the peak swing response of Z-direction；
6) first natural frequency in finite element analysis software to lathe, the peak swing response of three-dimensional and the lathe of setting
Basic big part mass property parameter is parameterized, and test sample point is obtained by Central Composite experimental design mode, using imitative
True analysis obtains the corresponding machine dynamic performance response of test sample point；
7) according to step 6) the middle response for testing sample point and test sample point, build each machine dynamic performance response and base
Quadratic polynomial response surface model between the big part mass property parameter of plinth：
Wherein：Y be machine dynamic performance response, x be a big part mass property parameter in basis, the number of big part based on n,
β is undetermined coefficient, big part mass property parameter sequence number based on i and j is equal, and i, j and n are natural number；
8) on the basis of quadratic polynomial response surface model obtained above, local derviation is asked to the big part mass property parameter in each basis
Number, obtains the sensitivity that basic big part mass property parameter influences on machine dynamic performance, by the comparing between each sensitivity,
Big influence of the part to machine dynamic performance in qualitative analysis basis；
9) obtain influenceing the weak link of machine dynamic performance according to sensitivity the qualitative analysis；For in the big part of machine tool basic
Weak link, the big part mass property parameter in basis, the big part in quantitative forecast basis are changed in quadratic polynomial response surface model
Mass property changes the effect tendency and influence amount to machine dynamic performance, carries out quantitative analysis, completes machine dynamic performance excellent
Change design.
2. a kind of big part Dynamic performance Optimization method for designing of machine tool basic according to claim 1, it is characterised in that step
1) in, the specific method that lathe entire assembly model simplifies is：
1) the small chamfering of size and fillet in deletion lathe assembly；
2) deleting does not influence the small feature of simulation analysis, and described small feature includes screw hole, bolt hole and oil filler point；
3) transmission system is simplified, reduction box internal structure is simplified using equivalent mass, and screw structure is replaced using cylinder；
4) simplify main axle structure, when carrying out assembly simulation analysis, be analyzed main shaft as an entirety, use equivalent reality
Body Model and equivalent mass are replaced；
5) simplify supplementary structure, do not produce the supplementary structure of influence, use quality point to be replaced on assembly structural rigidity；
6) undersized plane characteristic in assembly is deleted, it is ensured that good element quality.
3. a kind of big part Dynamic performance Optimization method for designing of machine tool basic according to claim 1, it is characterised in that step
5) in, in harmonic responding analysis, the force boundary condition in boundary condition is set as follows：Apply two groups of numerical value in spindle end
Equal cutting force, size is the cutting force amplitude that lathe is processed under nominal power, and 90 ° of phase angle difference is used for
Simulate the actual working state of cutter.
4. a kind of big part Dynamic performance Optimization method for designing of machine tool basic according to claim 1, it is characterised in that step
6) in, when carrying out parametrization setting to the big part mass property parameter in lathe assembly basis, using Central Composite experimental design side
Formula obtains test sample point；The model analysis of lathe assembly and harmonic responding analysis are carried out by finite element method, above-mentioned examination is obtained
Test the corresponding machine dynamic performance response of sample point.
5. a kind of big part Dynamic performance Optimization method for designing of machine tool basic according to claim 4, it is characterised in that step
6) the big part mass property parametrization of machine tool basic is comprised the following steps in：
6.1 pairs of big part mass parameter experimental design modes in basis are tested using Central Composite；With basic big part original design matter
Centered on amount, lower limit is the 90% of the big part original design quality of machine tool basic, and the upper limit is the big part original design quality of machine tool basic
110%, obtain the test sample point under Central Composite test method；
6.2 are calculated the machine dynamic performance response under Central Composite test method, including parametrization by simulation analysis
Lathe first natural frequency and parametrization main spindle box end under the effect of simple harmonic quantity power X responded to, the peak swing of Y-direction, Z-direction
Value.
6. a kind of big part Dynamic performance Optimization method for designing of machine tool basic according to claim 1, it is characterised in that step
7) in, the big part mass property parameter in lathe assembly basis and machine dynamic performance response are obtained using least square fitting
Between quadratic polynomial response surface model.
7. the big part Dynamic performance Optimization method for designing of a kind of machine tool basic according to claim 6, it is characterised in that described
Step 7) in, fitting quadratic polynomial response surface model is comprised the following steps：
7.1 output variables be respectively lathe first natural frequency and main spindle box end under the effect of simple harmonic quantity power X to, Y-direction, Z-direction
Peak swing response, design variable is the mass property parameter of the big part of machine tool basic；
7.2 are fitted using least square method to output variable and design variable, obtain quadratic polynomial response surface model
Fitting coefficient.
8. a kind of big part Dynamic performance Optimization method for designing of machine tool basic according to claim 1, it is characterised in that step
8) in, ask inclined by the big part mass property parameter in each basis in quadratic polynomial response surface model as design variable
Lead, obtain big sensitivity of the part mass property to dynamic property response in lathe assembly basis, wherein, each big part quality in basis
Characterisitic parameter causes machine dynamic performance to change maximum key element as machine dynamic performance weak link when changing.
9. a kind of big part Dynamic performance Optimization method for designing of machine tool basic according to claim 1, it is characterised in that step
9) in, by changing the quality characteristic value of the big part in basis in quadratic polynomial response surface model, machine dynamic performance sound is obtained
Should be worth, can quantitative analysis go out trend and the influence that the change of basic big part mass property parameter influences on machine dynamic performance
Amount；According to the trend and influence amount of prediction, the weak link in the modification original entire assembly model of lathe carries out quantitative analysis, complete
Into the optimization design of machine dynamic performance.
10. a kind of big part Dynamic performance Optimization method for designing of machine tool basic according to claim 1, it is characterised in that institute
The finite element analysis software stated uses ANSYS/Workbench softwares.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710047760.1A CN106777820A (en) | 2017-01-22 | 2017-01-22 | A kind of big part Dynamic performance Optimization method for designing of machine tool basic |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710047760.1A CN106777820A (en) | 2017-01-22 | 2017-01-22 | A kind of big part Dynamic performance Optimization method for designing of machine tool basic |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106777820A true CN106777820A (en) | 2017-05-31 |
Family
ID=58941413
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710047760.1A Pending CN106777820A (en) | 2017-01-22 | 2017-01-22 | A kind of big part Dynamic performance Optimization method for designing of machine tool basic |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106777820A (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108647433A (en) * | 2018-05-10 | 2018-10-12 | 西安交通大学 | A kind of axis system digital prototype fast construction method based on graph theory |
| CN108776746A (en) * | 2018-08-08 | 2018-11-09 | 上海理工大学 | A kind of dynamic stiffness optimization method improving machine dynamic characteristics |
| CN108984951A (en) * | 2018-08-08 | 2018-12-11 | 上海理工大学 | A method of optimization complete machine tool dynamic characteristic |
| CN109190198A (en) * | 2018-08-15 | 2019-01-11 | 国网新疆电力有限公司电力科学研究院 | A kind of erosive wear characteristic analysis method of strong Wind-sandy Area single cylindrical component |
| CN109558690A (en) * | 2018-12-12 | 2019-04-02 | 上海理工大学 | Mass center based on complete machine digital model drives machine tool design method |
| CN109634122A (en) * | 2018-12-28 | 2019-04-16 | 上海理工大学 | A kind of machine dynamic performance method for improving based on optimization sequence |
| CN110210079A (en) * | 2019-05-15 | 2019-09-06 | 大连理工大学 | A kind of lathe supporting member quality matches method towards complete machine dynamic characteristic |
| CN113094869B (en) * | 2021-03-05 | 2024-04-02 | 西安交通大学 | Machine tool large part structure optimization method considering gravity and heat influence |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102063548A (en) * | 2011-01-07 | 2011-05-18 | 西安交通大学 | Method for optimally designing dynamic property of complete machine tool |
| CN103995937A (en) * | 2014-05-27 | 2014-08-20 | 天津大学 | Precision machine tool mass matching design method based on response surface and genetic algorithm |
| CN104156501A (en) * | 2014-07-15 | 2014-11-19 | 天津大学 | Optimized design method of overall static rigidity of machine |
| CN104992038A (en) * | 2015-07-27 | 2015-10-21 | 天津大学 | Dynamic performance optimizing design method for rigid-mechatronic coupled feeding system |
-
2017
- 2017-01-22 CN CN201710047760.1A patent/CN106777820A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102063548A (en) * | 2011-01-07 | 2011-05-18 | 西安交通大学 | Method for optimally designing dynamic property of complete machine tool |
| CN103995937A (en) * | 2014-05-27 | 2014-08-20 | 天津大学 | Precision machine tool mass matching design method based on response surface and genetic algorithm |
| CN104156501A (en) * | 2014-07-15 | 2014-11-19 | 天津大学 | Optimized design method of overall static rigidity of machine |
| CN104992038A (en) * | 2015-07-27 | 2015-10-21 | 天津大学 | Dynamic performance optimizing design method for rigid-mechatronic coupled feeding system |
Non-Patent Citations (4)
| Title |
|---|
| PRAJINA N.V.: "Multi Response Optimization of CNC End Milling Using Response", 《INTERNATIONAL JOURNAL OF ENGINEERING RESEARCH AND TECHNOLOGY》 * |
| 张疆平: "基于自适应响应面法的数控铣床尺寸优化", 《机床与液压》 * |
| 郭俊康: "基于有限元分析的拉刀磨床床身结构优化设计", 《组合机床与自动化加工技术》 * |
| 黄华: "基于灵敏度的机床产品结构多层次集成设计分析方法", 《计算机集成制造***》 * |
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108647433B (en) * | 2018-05-10 | 2020-04-10 | 西安交通大学 | Method for quickly constructing digital prototype of spindle system based on graph theory |
| CN108647433A (en) * | 2018-05-10 | 2018-10-12 | 西安交通大学 | A kind of axis system digital prototype fast construction method based on graph theory |
| CN108776746A (en) * | 2018-08-08 | 2018-11-09 | 上海理工大学 | A kind of dynamic stiffness optimization method improving machine dynamic characteristics |
| CN108984951A (en) * | 2018-08-08 | 2018-12-11 | 上海理工大学 | A method of optimization complete machine tool dynamic characteristic |
| CN108984951B (en) * | 2018-08-08 | 2022-12-27 | 上海理工大学 | Method for optimizing dynamic characteristics of complete machine tool |
| CN108776746B (en) * | 2018-08-08 | 2022-06-21 | 上海理工大学 | Dynamic stiffness optimization method for improving dynamic characteristics of machine tool |
| CN109190198A (en) * | 2018-08-15 | 2019-01-11 | 国网新疆电力有限公司电力科学研究院 | A kind of erosive wear characteristic analysis method of strong Wind-sandy Area single cylindrical component |
| CN109558690A (en) * | 2018-12-12 | 2019-04-02 | 上海理工大学 | Mass center based on complete machine digital model drives machine tool design method |
| CN109558690B (en) * | 2018-12-12 | 2023-04-18 | 上海理工大学 | Centroid driving machine tool design method based on complete machine digital model |
| CN109634122A (en) * | 2018-12-28 | 2019-04-16 | 上海理工大学 | A kind of machine dynamic performance method for improving based on optimization sequence |
| CN110210079A (en) * | 2019-05-15 | 2019-09-06 | 大连理工大学 | A kind of lathe supporting member quality matches method towards complete machine dynamic characteristic |
| CN110210079B (en) * | 2019-05-15 | 2020-11-13 | 大连理工大学 | Machine tool supporting part quality matching method oriented to complete machine dynamic characteristics |
| CN113094869B (en) * | 2021-03-05 | 2024-04-02 | 西安交通大学 | Machine tool large part structure optimization method considering gravity and heat influence |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN106777820A (en) | A kind of big part Dynamic performance Optimization method for designing of machine tool basic | |
| CN104156501A (en) | Optimized design method of overall static rigidity of machine | |
| CN102063548B (en) | Method for optimally designing dynamic property of complete machine tool | |
| US6799081B1 (en) | Fiber placement and fiber steering systems and corresponding software for composite structures | |
| CN109977460B (en) | Multi-objective optimization design method based on vehicle body section parameterization | |
| CN103995937B (en) | Precision machine tool mass matching design method based on response surface and genetic algorithm | |
| CN102592017B (en) | Two-sided locking knife handle/main shaft coupling performance simulating and optimizing method | |
| CN103995914B (en) | Structure optimization design method for gear grinding machine stand column on basis of dynamic characteristic analysis | |
| CN102087670A (en) | Multi-body dynamics-based automotive suspension and simulation test and design platform of vibration reduction system | |
| CN106354955A (en) | Sliding bearing rigidity recognition method based on mill vibration mode parameters | |
| CN104134013B (en) | Wind turbine blade modal analysis method | |
| CN106295015B (en) | A kind of profile modification method of involute spur gear pair and special parameters CAD system matched with its | |
| CN105095583B (en) | A kind of hydrostatic spindle modal analysis method under minute yardstick | |
| CN112100761A (en) | Dynamic response analysis and vibration reduction optimization design method for rocket engine pipeline | |
| CN109684723A (en) | A kind of two-dimensional structure internal acoustic method for analyzing performance | |
| CN105779755A (en) | Quantitative evaluation method for vibration aging effect | |
| CN109614748B (en) | Structure optimization method for improving dynamic characteristics of machine tool by combining test and simulation technology | |
| CN112464401B (en) | Accurate modeling method for metal material welding spot | |
| CN111597742B (en) | Agricultural machinery structure residual deformation prediction method based on linkage effect of welding members | |
| Zou et al. | The modeling method of digital twin models for machining parts | |
| CN101393582A (en) | Non-support grinding and high stiffness principal axis system simulation and analysis method | |
| CN109409021B (en) | Bolt connection method in engine simulation analysis | |
| CN103294866A (en) | Tool-finite-element-analysis-oriented screw nut database creating method | |
| CN103942368B (en) | A kind of construction design method of laser cutting machine tool | |
| Anand et al. | Process automation of simulation using Toolkit/Tool Command Language (TK/TCL) scripting |
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 | ||
| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20170531 |