CN111310377A - Non-probability reliability topological optimization design method for continuum structure under mixed constraint of fundamental frequency and frequency interval - Google Patents
Non-probability reliability topological optimization design method for continuum structure under mixed constraint of fundamental frequency and frequency interval Download PDFInfo
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Abstract
The invention discloses a non-probability reliability topological optimization design method of a continuum structure under mixed constraint of fundamental frequency and frequency interval. Firstly, eliminating the problem of local mode by adopting a modified solid isotropic microstructure/material interpolation model with penalty factors; obtaining upper and lower limits of the natural frequency of the structure by adopting a vertex combination method, and overcoming the problem of modal exchange in the optimization process by adopting a boundary formula, thereby constructing a continuum structure non-probability reliability topological optimization model under mixed constraint of fundamental frequency and frequency interval; the original reliability index is converted by adopting a performance extreme value method so as to overcome the problem of convergence in optimization, and the sensitivity of a target performance extreme value to a design variable is solved by adopting a complex function derivation method; and adjusting parameters in a Mobile Marching Algorithm (MMA), and performing iterative optimization calculation until corresponding convergence conditions are met to obtain an optimization design scheme meeting fundamental frequency and frequency interval reliability constraints.
Description
Technical Field
The invention relates to the field of topological optimization design of a continuum structure under frequency constraint, in particular to a topological optimization design method for non-probability reliability of the continuum structure under mixed constraint of fundamental frequency and frequency interval.
Background
In engineering practice, the structure is subject to not only static loads such as gravity, but also vibration loads. Such as aircraft, are subject to engine vibration and aerodynamic loads; when the machine tool works, the machine tool can be subjected to vibration caused by high-speed rotation of the motor and other factors; the automobile is subjected to vibration loads generated by engine operation and road bumps while running, and the like. The resonance phenomenon easily causes structural damage. Therefore, when the structure is designed, not only the structure needs to be subjected to static analysis, but also the structure needs to be subjected to dynamic characteristic analysis, and optimized design is carried out, so that the aims of avoiding resonance and ensuring the structure safety are fulfilled.
The structure optimization design can be mainly divided into three levels according to different design variables, namely size optimization, shape optimization and topology optimization. For the topology optimization of the continuum structure, the size optimization refers to the numerical optimization design of certain sizes when the structure topology configuration and the shapes of all parts are determined; shape optimization refers to the improved optimization of certain geometries due to manufacturing or other requirements, when the topology of the structure has been determined; the topological optimization is to find the optimal topological configuration for the structure and lay a foundation for subsequent design, and moreover, the topological optimization has higher design freedom, so that higher economic benefit can be obtained. Therefore, the research on the structural topology optimization under the frequency constraint is of great significance.
However, structural analysis and design is generally based on deterministic assumptions, i.e., various parameters are considered to be artificially defined as definite quantities, regardless of errors and uncertainties in the parameters. However, in engineering practice, uncertainties in structural systems are prevalent due to the effects of various factors. Results obtained by neglecting uncertainty analysis and design cannot be convinced, and the method is not consistent with the concept of scientific and technological refinement development. Therefore, while minimizing uncertainty, the uncertainty present in the engineered structure must be studied in order to obtain a highly reliable structure. Due to various uncertainties and insufficient information that can be obtained in engineering practice, probability density functions of uncertain parameters are difficult to obtain, and the variation ranges of the uncertain parameters are easy to obtain. In this case, it is very convenient to describe the uncertain parameters and the reliability of the system by using a non-probability set theory, and the dependency on the initial sample is weak. Therefore, it is necessary to research a non-probabilistic reliability topological optimization design method of a continuum structure under the frequency constraint.
Disclosure of Invention
The technical problem to be solved by the invention is as follows: the method overcomes the defects of the prior art and provides a continuum structure non-probability reliability topological optimization design method under the mixed constraint of fundamental frequency and frequency interval. The invention fully considers the universal uncertain factors in the practical engineering problem, the obtained design result is more in line with the real situation, and the engineering applicability is stronger.
The technical scheme adopted by the invention is as follows: a non-probability reliability topological optimization design method for a continuum structure under mixed constraint of fundamental frequency and frequency interval comprises the following implementation steps:
the method comprises the following steps: aiming at the characteristics of a design structure, a finite element is used for discretizing a design domain, and a Modified Solid isotropic microstructure/Material interpolation model (Modified Solid isotropic microstructure/Material with Penalty, MSIMP) with a Penalty factor is used for describing the elastic modulus and the density of the Material, namely:
M(ρi)=Mmin+ρi(M0-Mmin)
wherein E (ρ)i) And M (ρ)i) Respectively representing the material elastic modulus and the material density of the ith unit, p > 1 is a penalty factor and is set to be 3, E0And M0Respectively the modulus of elasticity and the density of the solid material, EminAnd MminRespectively representing the lower bounds of the modulus of elasticity and the density of the solid material and being set to Emin=10-3E0,Mmin=10-3M0To avoid local modal problems.
Step two: the uncertainty range of the structural material parameters (including the elastic modulus and the density of the material) is described by using an interval model, the result of the structural natural frequency under the influence of uncertainty is calculated by using a vertex combination method, the maximum value of the result is taken as the upper bound of the natural frequency, and the minimum value of the result is taken as the lower bound of the natural frequency, so that the limit range of the structural natural frequency is obtained as follows:
wherein the content of the first and second substances,andω rrespectively an upper bound and a lower bound of the r-th order frequency, a is an uncertain parameter vector, m is the number of uncertain parameters,the calculated order r frequency for the ith vertex combination.
Step three: a boundary formula is adopted to overcome the modal exchange problem in the optimization process, and a non-probability reliability index is used to measure the influence of uncertainty on the structure safety and the front sjAdopting reliability constraint for 1-order frequency, and constructing a continuum structure non-probability reliability topological optimization model under mixed constraint of fundamental frequency and frequency interval:
0≤ρi≤1,i=1,2,…,N
where V denotes the total volume of the structure, and ρ ═ is (ρ1,ρ2,…,ρN)TIs a density design variable, ViIs the solid volume of the ith element, N is the number of elements of the divided finite element, R (-) is the non-probability reliability function,in the interval of the natural frequency of the kth order structure,ω 1for fundamental frequency constraint value, η is target non-probability reliability, for preceding sjThe reliability constraint adopted for the-1 st order frequency is to overcome the mode in the optimization processA problem of state switching, anddenotes the s thj+1 st order and sjThe order frequency spacing constraint, J denotes the order of the mode under consideration.And ω'rIs the natural frequency of the structure under a certain vertex combination, and the vertex combination is taken as the midpoint of the uncertain parameters. Also, constrainAndis also added to overcome the problem of modality exchange during the optimization process;
step four: the performance extremum method is adopted to process the original non-probability reliability index to solve the convergence problem, the original target reliability constraint can be converted into the constraint of the target performance extremum point, and the converted optimization model can be expressed as follows:
0≤ρi≤1,i=1,2,…,N
wherein g (-) is a target performance extremum function;
step five: solving the sensitivity of the upper and lower bounds of the natural frequency of the structure to the design variable, carrying out sensitivity calculation and judging the repetition frequency by adopting the peak combination of the elastic modulus and the density of the material corresponding to the upper and lower bounds of the frequency, considering the two-order frequency as the repetition frequency if the difference of the upper bound (or the lower bound) of the adjacent-order frequency is less than 0.005Hz, and adopting a repetition frequency sensitivity analysis method; otherwise, adopting a single frequency sensitivity analysis method. And further solving the sensitivity of the target performance extreme value to the upper and lower bounds of the natural frequency of the structure, and then solving the sensitivity of the target performance extreme value to the design variable according to a complex function derivation rule.
Step six: adjusting algorithm parameters in a Mobile Marching Algorithm (MMA) to enable the algorithm parameters to become a linear approximation optimization algorithm, further modifying a corresponding program to enable the movement of each step in the linear approximation optimization algorithm to be consistent with the original MMA algorithm, and solving an optimization problem by taking the obtained target performance value and the sensitivity of the target performance value to a design variable as input conditions of the algorithm so as to update the design variable;
and seventhly, repeating the second step to the sixth step, and updating the design variables for multiple times until the current design meets the reliability constraint and the relative change percentage of the objective function is less than a preset value ξ, and stopping the optimization process.
Compared with the prior art, the invention has the advantages that:
(1) the non-probability reliability index adopted by the invention can reasonably consider the influence of uncertain factors on the structural performance, can furthest improve the economic benefit of the structure, gives consideration to the safety, and is very suitable for engineering application;
(2) the MSIMP model provided by the invention can effectively overcome the problem of local modal in the frequency-based topology optimization problem, thereby well realizing the topology optimization design of the continuum structure under the frequency constraint;
(3) the improved mobile progressive optimization algorithm provided by the invention can effectively solve the topological optimization problem of the continuum non-probability reliability structure under the constraints of fundamental frequency and frequency interval, and provides a new algorithm for solving the topological optimization problem of the continuum structure under the constraints of fundamental frequency and frequency interval.
Drawings
FIG. 1 is a flow chart of a non-probabilistic reliability topology optimization design method of a continuum structure under fundamental frequency and frequency interval hybrid constraints according to the present invention;
FIG. 2 is a schematic diagram of the process of deriving the target performance extremum in the present invention, wherein FIG. 2(a) is a schematic diagram of four key slopes of the extreme state plane when deriving the target performance extremum, and FIGS. 2(b) - (e) are schematic diagrams of four cases when deriving the target performance extremum;
FIG. 3 is a schematic diagram of a topology optimization design area and boundary and load conditions in an embodiment of the invention;
fig. 4 is a schematic diagram of an optimization result of topology optimization for a continuum structure according to the present invention, where fig. 4(a) is deterministic optimization, fig. 4(b) is non-probabilistic reliability optimization (R ═ 0.90), fig. 4(c) is non-probabilistic reliability optimization (R ═ 0.95), and fig. 4(d) is non-probabilistic reliability optimization (R ═ 0.999).
Detailed Description
The invention is further described with reference to the following figures and detailed description.
As shown in FIG. 1, the invention provides a non-probabilistic reliability topological optimization design method for a continuum structure under mixed constraints of fundamental frequency and frequency interval, which comprises the following steps:
the method comprises the following steps: aiming at the characteristics of a design structure, a finite element is used for discretizing a design domain, and a Modified Solid isotropic microstructure/Material interpolation model (Modified Solid isotropic microstructure/Material with Penalty, MSIMP) with a Penalty factor is used for describing the elastic modulus and the density of the Material, namely:
M(ρi)=Mmin+ρi(M0-Mmin)
wherein E: (A)ρi) And M (ρ)i) Respectively representing the material elastic modulus and the material density of the ith unit, p > 1 is a penalty factor and is set to be 3, E0And M0Respectively the modulus of elasticity and the density of the solid material, EminAnd MminRespectively representing the lower bounds of the modulus of elasticity and the density of the solid material and being set to Emin=10-3E0,Mmin=10-3M0To avoid local modal problems.
Step two: an interval model is used to describe the uncertainty range of the structural material parameters, including the elastic modulus and density of the material. The mathematical definition of the intervals is described below.
In general, a number of intervals can be defined as:
whereinaAndare respectively referred to as interval number aILower and upper bounds. When in useThe number of intervals aIThe degradation is a real number.
Based on the definition of the number of intervals, the interval matrix can be defined as follows:
interval matrix AICan also be expressed as:
wherein the content of the first and second substances,A=(a ij)m×nandare respectively provided withReferred to as interval matrix AILower and upper bounds of interval matrix AICan be expressed as:
calculating the result of the structure natural frequency under the influence of uncertainty by adopting a vertex combination method for the uncertain parameters, taking the maximum value as the upper bound of the structure natural frequency, and taking the minimum value as the lower bound of the structure natural frequency, thereby obtaining the limit range of the structure natural frequency as follows:
wherein the content of the first and second substances,andω rrespectively an upper bound and a lower bound of the r-th order frequency, a is an uncertain parameter vector, m is the number of uncertain parameters,the calculated order r frequency for the ith vertex combination.
Step three: and the influence of uncertainty on the structure safety is measured by using a non-probability reliability index, and the definition of the non-probability reliability is introduced below.
For the number of intervals xIAnd yIThe non-probabilistic reliability is defined as:
in particular, when only xIThe degradation is a real number x', and the corresponding reliability is calculated as:
when only yIThe degradation is a real number y', and the corresponding reliability is calculated as:
using boundary formula to overcome the problem of modal exchange in optimization process, for previous sjAdopting reliability constraint for 1-order frequency, and constructing a continuum structure non-probability reliability topological optimization model under mixed constraint of fundamental frequency and frequency interval:
0≤ρi≤1,i=1,2,…,N
where V denotes the total volume of the structure, and ρ ═ is (ρ1,ρ2,…,ρN)TIs a density design variable, ViIs the solid volume of the ith element, N is the number of elements of the divided finite element, R (-) is the non-probability reliability function,is an interval of the k-th order natural frequency,ω 1for fundamental frequency constraint value, η is target non-probabilityDegree of leaning, preceding sjThe reliability constraint adopted for the-1 st order frequency is to overcome the modal exchange problem during the optimization process, anddenotes the s thj+1 st order and sjThe order frequency spacing constraint, J denotes the order of the mode under consideration.And ω'rIs the natural frequency of the structure under a certain vertex combination, and the vertex combination is taken as the midpoint of the uncertain parameters. Also, constrainAndis also added to overcome the problem of modality exchange during the optimization process;
step four: the performance extremum method is adopted to process the original non-probability reliability index to solve the convergence problem. Firstly, constructing a reliability-performance extremum function as follows:
F(g)=R(AI+g≥BI)
wherein A isIAnd BIIs the number of intervals, AICan be thatOrCorrespondingly, BICan be thatω 1OrThe original reliability constraint can be written as:
F(0)=R(AI≥BI)≥η
taking inverse transform F for both sides of the above equation-1It is possible to obtain:
F-1(η)≤0
let g (A)I≥BI,η)=F-1(η), the original target reliability constraint can be converted into a constraint of the target performance extreme point, and the converted optimization model can be expressed as:
0≤ρi≤1,i=1,2,…,N
wherein g (-) is a target performance extremum function. How to solve the objective performance function is described below.
The extreme state plane is first constructed as:
M(A,B)=A+g-B=0
wherein A is ∈ AI,B∈BI. The above equation can also be written as:
and
wherein δ a ═ a-ac)/Ar(Ar≠0),δB=(B-Bc)/Br(Br≠0)。
As shown in fig. 2(a), four special cases of the extreme state plane can be derived:
wherein k isiThe slope of the extreme state plane. Thus, g can be found in four cases:
case 1: if k is3<Ar/Br<k1η ≧ 0.5, the extreme state plane intersects the top and left sides of the feasible region, as shown in fig. 2 (B.) to obtain intersection points M1 and N1, substituting δ B-1 and δ a-1 into the extreme state plane yields:
based on the definition of the non-probabilistic reliability, one can obtain:
g can be solved from the above formula to give:
case 2: if A isr/Br≥k1η ≧ 0.5 or Ar/Br≥k2η is less than or equal to 0.5, the two formulas are integrated into Ar/Br≥max{k1,k2And then two intersection points are located at the upper side and the lower side, as shown in fig. 2 (c). Similarly, let δ B ± 1 obtain:
based on the definition of the non-probability reliability, there are:
solving for g from the above formula yields:
g=-Ac+Bc+(2η-1)Ar
case 3: if k is4<Ar/Br<k2η < 0.5, the positional relationship between the extreme state plane and the feasible region is shown in FIG. 2(d), where g can be calculated as:
case 4: if A isr/Br≤k3η ≧ 0.5 or Ar/Br≤k3η is not more than 0.5, both formulae are equivalent to Ar/Br≤min{k3,k4Then g can be solved as:
g=-Ac+Bc+(2η-1)Br
in summary, the target performance extremum function is a piecewise function, as follows:
particularly, when Ar=0,BrNot equal to 0, g can be solved as:
similarly, when Ar≠0,BrWhen 0, we can get:
combining the above several cases, we can get:
where epsilon is a small positive number.
Step five: solving the sensitivity of the upper and lower bounds of the natural frequency of the structure to the design variable, carrying out sensitivity calculation and judging the repetition frequency by adopting the peak combination of the elastic modulus and the density of the material corresponding to the upper and lower bounds of the frequency, considering the two-order frequency as the repetition frequency if the difference of the upper bound (or the lower bound) of the adjacent-order frequency is less than 0.005Hz, and adopting a repetition frequency sensitivity analysis method; otherwise, adopting a single frequency sensitivity analysis method. And further solving the sensitivity of the target performance extreme value to the upper and lower bounds of the natural frequency of the structure, and then solving the sensitivity of the target performance extreme value to the design variable according to a complex function derivation rule. The method for solving the sensitivity of the upper bound of the natural frequency of the structure to the design variable under the condition of single frequency is described firstly. The structural natural frequency characteristic equation under the condition of no damping is considered as follows:
wherein the content of the first and second substances,andthe total rigidity matrix and the mass matrix of the structure, omega, corresponding to the upper bound of the r-th order natural frequencyrAndrespectively, an upper bound of the natural frequency of the r-th order and a corresponding modal vector. Design variable rho is simultaneously paired at two ends of the upper formulajTaking the derivative, one can get:
the formula is simplified and arranged to obtain:
since K and M are symmetric matrices, then:
rigidity matrix of unit j corresponding to upper bound of structure natural frequencyAnd quality matrixOnly the density design variables of the present cell. Then substituting the MSIMP interpolation model into the above equation, there are:
wherein the content of the first and second substances,features corresponding to element j for the upper bound of the r-th order natural frequencyAnd (5) vector quantity.
Similarly, the design variable rho is the lower bound of the natural frequency of the structurejThe sensitivity of (d) is solved as:
wherein the content of the first and second substances,ω rto the lower bound of the structure's order-r natural frequency,the lower bound for the r-th order natural frequency corresponds to the eigenvector of cell j.Andrespectively a rigidity matrix and a mass matrix of the unit j corresponding to the upper bound of the natural frequency of the structure.
For the case of the repetition frequency, since the multiple characteristic frequencies do not have differentiability in the general sense, the corresponding sensitivity information cannot be directly given. For sensitivity analysis of multiple characteristic frequencies, at a repetition frequencySelecting a group of characteristic modal vectors which are continuously changed along with design variables and are independent from each other from a modal space (upper bound of natural frequency)The general form of the set of vectors can be expressed as a linear combination of basis vectors:
wherein, βrkTo determine the coefficients, [ β ] by appropriate processingrk]And r, k is n, …, and n + m-1 forms an m × m orthogonal matrix. To be provided withAndsubstituting the characteristic value equation to obtain:
wherein the content of the first and second substances,andthe derivation of the density design variables from the above equation yields a set of coefficients β for multiple frequency sensitivities and undetermined coefficientsrkThe equation of the sub-eigenvalues of (a) is specifically derived by using a perturbation method.
First, the case of a variation of a single design variable is considered, for which the design variable ρ is givenjA small perturbation Δ ρj. The changes in the frequency, eigenvectors, and stiffness and mass matrices in the eigenvalue equation due to perturbation of a single design variable are as follows (only first order approximations after perturbation are considered here, small terms of second order and above are ignored):
r=n,…,n+m-1
wherein the content of the first and second substances,andrespectively corresponding to multiple characteristic frequenciesAnd feature vectorsThe sensitivity of (2). Substituting the above formula into generalized eigenvalue equation, and respectively multiplying the two ends of the equation by leftMerging of Δ ρjThe same terms are simplified to obtain a first-order approximation result (i.e. let Δ ρjCoefficients of terms are zero):
substituting the linear expression of the basis vector into the formula, and utilizing the orthonormality of the characteristic mode on the quality matrix to obtain:
wherein, deltaskIs a function of Kronecker the above equation gives a set of information about the coefficients βrkN, …, n + m-1, with the condition that the system determinant is zero, i.e.:
the above formula relates to multiple characteristic frequenciesIs sensitive toAlgebraic equation of degree, solution to obtain multiple eigenfrequenciesM sensitivity of
Likewise, the sensitivity of the lower bound of the characteristic frequency to design variables at a repetition frequency can be solved by the following algebraic equation:
wherein the content of the first and second substances,is the lower bound of the characteristic frequencyThe corresponding characteristics of the light-emitting diode are as follows,KandMrespectively a structural overall rigidity matrix and a quality matrix corresponding to the lower boundary of the characteristic frequency,for multiple characteristic frequenciesω rThe sensitivity of (2).
The sensitivity of the target performance extrema function to the upper and lower bounds of the natural frequency of the structure is then introduced. The expression for the target performance limit point g is listed first, as follows:
from the expression of g, one can obtain:
and
and
and
in summary, there are:
wherein the content of the first and second substances,and substituting the sensitivity of the upper and lower boundaries of the prior structure natural frequency to the design variable into the formula to obtain the sensitivity of the target performance extreme value to the design variable. In the above equation, note the reliability constraint for the fundamental frequency, there isThis is because the right-hand term of the fundamental frequency constraint is a constant term. And for the reliability constraint of the frequency interval, thenThis is because the right term of the frequency interval constraint is also the natural frequency of the structure, and therefore the right term of the frequency interval reliability constraint also needs to be derived.
Step six: adjusting algorithm parameters in a Mobile Advance Algorithm (MMA) with U set to 106Set L to-106The linear approximation optimization algorithm is formed, corresponding programs are further modified, the moving limit of each step in the linear approximation optimization algorithm is consistent with that of the original MMA algorithm, the obtained target performance value and the sensitivity of the target performance value to the design variable are used as input conditions of the algorithm, the optimization problem is solved, and therefore the design variable is updated;
and seventhly, repeating the second step to the sixth step, and updating the design variables for multiple times until the current design meets the reliability constraint and the relative change percentage of the objective function is less than a preset value ξ, and stopping the optimization process.
Examples
As shown in FIG. 3, the two-dimensional rectangular flat plate has a fixed support at both left and right ends, a sheet size of 50m × 40m, a plate thickness of 1m, a median value of elastic modulus E of 210GPa, and a median value of density ρ of 7800kg/m3The poisson ratio μ is 0.3. The structure is divided into 50 x 40 cells. Constraining the fundamental frequency of the structure to be greater than ω02Hz, i.e. first order eigenvalues λ0Greater than 4. Let the material parameters and λ0All have a fluctuation of 5%, i.e. EI=[200,220]GPa,ρI=[7410,8190]kg/m3,
In the calculation of the present example, the relative mass is taken as an objective function, and the constraint is that the fundamental frequency of the structure is larger than lambda0For reliability topology optimization, the constraint is that g is less than or equal to 0. And taking the initial value of the relative volume density of each unit as 0.7, and carrying out topological optimization on the structure. Fig. 4 and table 1 are the results of deterministic and reliable topology optimization. It can be seen that the configuration of the structure obtained by deterministic topological optimization and different non-probabilistic reliable topological optimizations has a larger difference, and compared with the deterministic topological optimization result, the reliable topological optimization result is more reasonable. Along with the gradual improvement of the reliability, the connecting parts of the middle area and the left side and the right side become thicker gradually, so that the structural rigidity is higher. Again, as the calculation process tends to reduce the mass, the connection starts to become porous again. As can be seen from table 1, with increasing non-probabilistic reliability,the relative volume fraction of the topology optimization results is also gradually increasing, i.e. the more reliable the structure occupies more volume, i.e. more material is needed to compose the structure.
TABLE 1 volume fraction table of the optimization results of the present invention for continuum structure topology optimization
The invention provides a non-probability reliability topological optimization design method of a continuum structure under mixed constraint of fundamental frequency and frequency interval. The method comprises the steps of firstly, describing the elastic modulus and the density of a Material by adopting a Modified Solid Isotropic Microstructure/Material interpolation model (Modified Solid Isotropic Microstructure/Material with Penalty, MSIMP) with Penalty factors, and selecting a proper elastic modulus and a proper lower density limit to avoid the problem of local mode; describing uncertainty of the elastic modulus and the density of the material by using an interval model, and obtaining upper and lower limits of the natural frequency of the structure by using a vertex combination method; the method comprises the steps of measuring the influence of uncertainty on structural safety by adopting a non-probability reliability index, and overcoming the problem of modal exchange in the optimization process by adopting a boundary formula, so as to construct a non-probability reliability topological optimization model of a continuum structure under mixed constraint of fundamental frequency and frequency interval; the original reliability index is converted by adopting a performance extreme value method so as to overcome the problem of convergence in optimization; solving the sensitivity of the upper and lower boundaries of the natural frequency of the structure to the design variable, and then solving the sensitivity of the target performance extreme value to the design variable according to a complex function derivation rule; and adjusting parameters in a Mobile Marching Algorithm (MMA), and performing iterative optimization calculation until corresponding convergence conditions are met to obtain an optimization design scheme meeting fundamental frequency and frequency interval reliability constraints.
The above are only the specific steps of the present invention, and the protection scope of the present invention is not limited in any way; the non-probability reliability topological optimization design method of the continuum structure under the mixed constraint of fundamental frequency and frequency interval can be expanded and applied, and all technical schemes formed by adopting equivalent transformation or equivalent replacement fall within the protection scope of the invention.
The invention has not been described in detail and is part of the common general knowledge of a person skilled in the art.
Claims (4)
1. A non-probability reliability topological optimization design method for a continuum structure under mixed constraint of fundamental frequency and frequency interval is characterized by comprising the following implementation steps:
the method comprises the following steps: aiming at the characteristics of a design structure, a finite element is used for dispersing a design domain, a Modified Solid Isotropic Microstructure/Material interpolation model (Modified Solid Isotropic Microstructure/Material with Penalty factor, MSIMP) model is used for describing the elastic modulus and the density of the Material, and proper lower limits of the rigidity and the density of the Material are selected to avoid the problem of local modal;
step two: describing an uncertainty range of structural material parameters including the elastic modulus and the density of the material by using an interval model, calculating a result of structural natural frequency under the influence of uncertainty by using a vertex combination method, taking the maximum value as the upper bound of the natural frequency and taking the minimum value as the lower bound of the natural frequency, thereby obtaining a limit range of the structural natural frequency;
step three: the influence of uncertainty on the structure safety is measured by using a non-probability reliability index, and a boundary element formula is adopted to overcome the modal exchange problem in the optimization process, so that a continuum structure non-probability reliability topological optimization model under the mixed constraint of fundamental frequency and frequency interval is constructed:
0≤ρi≤1,i=1,2,…,N
where V denotes the total volume of the structure, and ρ ═ is (ρ1,ρ2,…,ρN)TIs a density design variable, ViIs the solid volume of the ith element, N is the number of elements of the divided finite element, R (-) is the non-probability reliability function,in the interval of the natural frequency of the kth order structure,ω 1for fundamental frequency constraint value, η target non-probability reliability, and for overcoming the modal exchange problem in the optimization process, front s is selectedjThe-1 order frequencies all adopt the reliability constraint, anddenotes the s thj+1 st order and sjThe order frequency spacing constraint, J denotes the order of the mode to be considered,and ω'rIs the natural frequency of the structure under a certain combination of vertices, where the combination of vertices is taken as the midpoint of the uncertain parameter, and similarly, the constraintAndis also added to overcome the problem of modality exchange during the optimization process;
step four: the performance extremum method is adopted to process the original non-probability reliability index to solve the convergence problem, and the original optimization model can be converted into the following model by utilizing the target performance extremum point:
0≤ρi≤1,i=1,2,…,N
wherein g (-) is a target performance extremum function;
step five: solving the sensitivity of the target performance extreme value to the upper and lower bounds of the structure natural frequency and the sensitivity of the upper and lower bounds of the frequency to the design variable, then solving the sensitivity of the target performance extreme value to the design variable by using a complex function derivation method, judging the repetition frequency when solving the sensitivity of the frequency to the design variable, considering the two orders of frequency as the repetition frequency if the difference of the upper bound or the lower bound of the adjacent orders of frequency is less than 0.005Hz, and adopting a repetition frequency sensitivity analysis method; otherwise, adopting a single frequency sensitivity analysis method;
step six: adjusting algorithm parameters in a mobile incremental algorithm (MMA), modifying a corresponding program, taking the obtained target performance value and the sensitivity of the target performance value to a design variable as input conditions of the algorithm, and solving an optimization problem so as to update the design variable;
and seventhly, repeating the second step to the sixth step, and updating the design variables for multiple times until the current design meets the reliability constraint and the relative change percentage of the objective function is less than a preset value ξ, and stopping the optimization process.
2. The non-probabilistic reliability topological optimization design method of continuum structure under fundamental frequency and frequency interval hybrid constraint of claim 1, characterized in that: in the first step, an MSIMP model is adopted to describe the elastic modulus and the density of the material, and proper lower limits of the rigidity and the density of the material are selected to avoid the problem of local mode.
3. The non-probabilistic reliability topological optimization design method of continuum structure under fundamental frequency and frequency interval hybrid constraint of claim 1, characterized in that: in the fourth step, the original non-probability reliability index is processed by adopting a performance extremum method, so that the problem of convergence is well solved.
4. The non-probabilistic reliability topological optimization design method of continuum structure under fundamental frequency and frequency interval hybrid constraint of claim 1, characterized in that: and in the sixth step, the algorithm parameters in the MMA are adjusted, and the corresponding program is modified, so that the algorithm program suitable for solving the frequency constraint topology optimization problem is obtained.
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CN112417692A (en) * | 2020-11-24 | 2021-02-26 | 华东交通大学 | Multi-scale topological optimization design method of material structure based on load uncertainty |
CN113361176A (en) * | 2021-06-21 | 2021-09-07 | 山东大学 | Nonlinear characteristic value topology optimization method and system considering frequency-dependent material |
CN117057038A (en) * | 2023-08-15 | 2023-11-14 | 合肥工业大学 | Wing-oriented single-cycle reliability topology optimization design method |
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