CN109918780B - High-stability-oriented optimal design method for elastic element of micro locking mechanism - Google Patents
High-stability-oriented optimal design method for elastic element of micro locking mechanism Download PDFInfo
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Abstract
The invention discloses a high-stability-oriented optimization design method for an elastic element of a micro locking mechanism, which is based on a linear iterative optimization method and aims at the geometric structural dimension of the elastic element to carry out optimization design so that the geometric dimension of the elastic element meets the bearing capacity and the high-stability working characteristic, meanwhile, the combined iterative optimization is carried out aiming at the structure of the elastic element, and a higher-stability working interval is realized through the combination of the differentiated structural dimension of the elastic element. The invention provides an elastic element optimization design method for a high-stability micro locking mechanism, which is based on finite element parametric modeling analysis of a product, extracts key geometric dimensions of a structure and searches in a feasible domain to achieve the purpose of structure optimization, gets rid of dependence on experience, saves design time and obtains a design optimal value.
Description
Technical Field
The invention belongs to the technical field of structure optimization design, and particularly relates to a high-stability optimization design method for an elastic element of a micro locking mechanism.
Background
The mechanical pendulum accelerometer is a sensitive device of an inertial navigation system, is widely applied to the fields of spaceflight, aviation, navigation and the like, and the performance of the mechanical pendulum accelerometer directly determines the precision of the inertial navigation and guidance system. The micro locking mechanism is a core component of the mechanical pendulum accelerometer, the reliability of locking load of the micro locking mechanism directly influences the zero-offset long-term stability of the pendulum accelerometer, and the micro locking mechanism becomes one of key technical bottlenecks for restricting the improvement of the precision of the inertial navigation system.
The micro locking mechanism of the mechanical pendulum accelerometer mainly comprises a pressing structure, a spring element, an upper polar plate, a lower polar plate and a central bolt, wherein components with certain physical parameter conversion characteristics in the accelerometer are assembled together by applying connection load, and the assembly position and the mechanical state of the pendulum components are ensured. Because the structural rigidity of the spring element is weak, most of deformation of a tiny locking mechanism system is borne, and therefore the mechanical and physical characteristics of the spring element directly determine the level and stability of the connection load of the locking mechanism, the installation state and the zero offset error of the accelerometer pendulum assembly are influenced. Therefore, how to reasonably design the structural form of the spring element and enable the mechanical physical characteristics of the spring element to meet the long-term stability of the connection load is the key point for improving the service performance of the mechanical pendulum type accelerometer.
At present, the design of a spring element of a micro locking mechanism usually depends on an experience manual, a structure meeting the requirement is obtained through a large number of tests and mistakes, and the design efficiency is low; the invention provides a method for building an elastic element parameterized model by utilizing a finite element technology, and combines geometric dimension optimization and structure composition optimization, thereby releasing manpower, saving design time, obtaining a design optimal value and realizing high stability of the load of a micro locking mechanism.
Disclosure of Invention
The invention aims to provide a high-stability optimized design method for an elastic element of a micro locking mechanism to achieve the aim of constant-force locking; and aiming at the large-deformation part contained in the system, the core size factor influencing the rigidity is found, iterative optimization is carried out, and a higher stability working interval is realized through the differentiated structural size combination of the elastic elements.
The invention is realized by adopting the following technical scheme:
a high-stability-oriented optimization design method for an elastic element of a micro locking mechanism is based on a linear iterative optimization method, optimization design is carried out on the geometric structure size of the elastic element, the geometric size of the elastic element meets the bearing capacity and high-stability working characteristics, meanwhile, combined iterative optimization is carried out on the structure of the elastic element, and a higher stability working interval is realized through the combination of the differentiated structure sizes of the elastic element.
The invention is further improved in that the method specifically comprises the following steps:
1) carrying out finite element modeling analysis on an assembly system containing an elastic element to obtain the rigidity characteristic of the system;
2) on the basis of the step 1), judging a simplified scheme of the assembly system, and simplifying the rigidity analysis of the assembly system into the analysis of the deformation of the elastic element according to the fact that the deformation of the assembly system is relatively small under the general condition;
3) aiming at the elastic element parameterized modeling after the simplified scheme in the step 2), analyzing the deformation influence degree of each geometric dimension on the loading process;
4) in the analysis process of the step 3), performing linear search optimization in a feasible domain of the geometric dimension of the elastic element; and after optimizing a single elastic element, comparing the combined structures and selecting the result with the optimal bearing capacity and stability.
A further development of the invention consists in that, in step 1), the assembly system comprising the elastic element is subjected to a stiffness analysis, which analyses the effect exerted by the elastic element during the deformation of the assembly system.
The further improvement of the invention is that the specific implementation method of the step 4) is as follows:
step 1: establishing mutually independent geometrical dimensions with respect to the individual elastic elements, while giving a target axial force F0And a stiffness stability value K0：
X＝(x1，x2，x3，x4，...，xn)T
Wherein X-is a vector variable established by independent binding sizes;
force value extraction of model F ═ F (X, S) is extracted by ANSYS software, and the model is calculated through rigidity
Constraint conditions are as follows: i Fi-F0|≤1，|Ki-K0|≤2；
Wherein S-is directed at displacement loading changes of the part;
the F (X, S) -force value function is determined by the geometric dimension and the displacement loading;
Fi-is the value of the axial force taken at a point in the interval;
F1，F2-is the axial force value at the end of the interval taken within the interval;
S1，S2is taken from F1，F2A corresponding displacement value;
Ki-means stiffness values within a calculation interval;
K0-indicating a target requirement value;
1-an acceptable range of force value variations;
2-an acceptable range of stiffness variations;
array defining the size factor position:
define the array a ═ { a ═ a1，a2，a3，a41, 2, 3, 4; address for indicating storage of size factor
Step 2:
establishing a finite element model, and carrying out a loading process, wherein the loading process comprises the following three parts:
the first part is to load the whole stroke according to a certain specific geometric dimension, namely, a single elastic element is flattened, and an F-S curve under the geometric dimension is obtained and is reserved for comparison;
F＝F(X，S)
wherein, S is 0.01I, and I is less than or equal to [ H0 ];
h0-represents the individual spring element flattened by a distance of 100 times;
[H0] -a rounding function;
the second part is that after the full-stroke loading is finished each time, linear iteration is carried out according to the geometric dimension in the first step, and the full-stroke loading is carried out;
wherein, a is 0, 1, 2.. 10, α is constant;
-represents is the correspondence aiThe size of the site storage;
the third part, after completing the iteration of the cost size within a certain gradient, moves the array position and carries out the next xiThe iterative calculation of (2):
1≤j，m，n≤4，ai≠aj≠am≠an
representing four mutually independent geometries, a, in a mutually independent set of geometriesi-the storage positions are represented in correspondence of the geometrical dimensions;
and step 3:
aiming at F-S curves obtained under different size combinations, according to constraint conditions: i Fi-F0|≤1，|Ki-K0|≤2Selecting a proper size scheme;
and 4, step 4:
if the proper size is not found under the constraint condition, entering a combined structure design and adopting an installation mode under different size combinations;
and 5:
and (3) iterating different combined structures, and then carrying out iteration optimization of the structure size again according to the step 1 until a proper size scheme is found, so that the following requirements are met: i Fi-F0|≤1，|Ki-K0|≤2。
The invention has the following beneficial technical effects:
1) aiming at the problem of insufficient bearing capacity and rigidity under the same structure, the invention provides a new iterative optimization scheme, namely, rigidity complementation is realized through change of a combination mode under the condition of not changing the structure of parts.
2) The invention can realize constant force locking in limited assembly space and improve the stability of equipment performance.
3) According to the invention, through multiple nested loops, an optimal combination size scheme under the boundary condition is found, and the efficiency is improved.
4) First, it is an independent geometric linear iteration, and iterates the optimization within a certain size range. Second, the termination conditions are: i Fi-F0|≤1，|Ki-K0|≤2And the satisfied condition is an optimized size combination scheme.
5) First, there is no constraint on the geometry of a part. When no optimization result exists in a given range, the design scheme can be suitable for selecting the part combination with the same structure and different specific sizes; second, the sizing of the composite part is still determined using the present design.
In summary, the method for optimally designing the elastic element of the high-stability micro locking mechanism provided by the invention extracts the key geometric dimension of the structure based on the finite element parametric modeling analysis of the product, searches in a feasible domain to achieve the purpose of optimizing the structure, gets rid of the dependence on experience, saves the design time and obtains the optimal design value. Taking a disc spring as an example, aiming at the unique variable stiffness characteristic of a disc spring part, carrying out iterative optimization of size factors to find out an optimal size combination; when the dimension which does not meet the requirement is faced, the rigidity combination optimization is creatively carried out, the rigidity complementation is carried out on the disc spring under the condition of different dimensions, the bearing stability in a larger deformation range is realized, and the requirements of rigidity and bearing capacity are completely met.
Drawings
Fig. 1 is a graph of individual disc spring thickness variation versus force and deflection data (partial data).
Fig. 2 is a data curve (partial data) of change of minor diameter size of the disc spring to stress and deformation.
Fig. 3 is a data plot (partial data) of the ultimate displacement change of a single disc spring versus force and deformation.
Fig. 4 is a plot of individual disc spring spherical radius change versus force and deflection data (partial data).
Fig. 5 is a graph of force and deformation data for the new combination structure and the original single disc spring.
Fig. 6 is a schematic drawing of the dimensions of the part.
Fig. 7 is a cross-sectional view of fig. 6.
Fig. 8 is a schematic diagram of a structural design core combination.
Fig. 9 is a cross-sectional view of fig. 8.
Fig. 10 is a schematic view of the original structure, with the bolt in the middle, and the threaded surface of the shaft being machined.
Fig. 11 is a sectional view of fig. 10.
Fig. 12 is a schematic view of the new construction with the bolt in the middle and the machined thread surface of the shaft.
Fig. 13 is a cross-sectional view of fig. 12.
Detailed Description
The invention is further described below with reference to the following figures and examples.
The invention provides a high-stability-oriented elastic element optimization design method for a micro locking mechanism, which is based on an elastic element-spherical disc spring assembly and installation method in a certain assembly system, and comprises the following steps:
step 1: establishing mutually independent geometric dimensions of spherical disc springs and giving a target axial force F0And a stiffness stability value K0：
X＝(x1，x2，x3，x4，...，xn)T
Wherein the content of the first and second substances,
x-a vector variable established by independent binding sizes.
Force value extraction of model F ═ F (X, S) is extracted by ANSYS software, and the model is calculated through rigidity
Constraint conditions are as follows: i Fi-F0|≤1，|Ki-K0|≤2
Wherein S-is varied for displacement loading of the part
The F (X, S) -force function is determined by the geometry and displacement loading
1Acceptable range of variation of force values.
2Acceptable range of stiffness variation.
Array defining the size factor position:
define the array a ═ { a ═ a1，a2，a3，a4}＝{1，2，3，4}
Step 2:
and establishing a finite element model and carrying out a loading process. In the loading process, the method comprises three parts:
the first part is to load the full stroke for a specific geometric dimension, and obtain the F-S curve under the geometric dimension for comparison. (see attached FIG. 1)
F＝F(X，S)
Wherein, S is 0.01I, and I is less than or equal to [ H0 ];
h0-represents the distance to flatten the disc spring 100 times
[H0] -rounding function
And in the second part, after the full-stroke loading is finished each time, performing linear iteration according to the geometric dimension in the first step, and performing the full-stroke loading. (see attached FIG. 1)
A is 0 and α is constant
Alpha-selected growth ratio
The third part, after completing the iteration of the cost size within a certain gradient, moves the array position and carries out the next operation
The iterative computation of (2).
1≤j，m，n≤4，ai≠aj≠am≠an
And step 3:
aiming at F-S curves obtained under different size combinations, according to constraint conditions: i Fi-F0|≤1，|Ki-K0|≤2An appropriate sizing scheme is selected.
And 4, step 4:
if the proper size is not found under the constraint condition, the combined type structure design is entered, and the installation mode under different size combinations is adopted.
And 5:
and (4) iterating different combined structures, and then carrying out iteration optimization on the structure size again according to the step 1. Until a suitable sizing scheme is found. Satisfies the following conditions: i Fi-F0|≤1，|Ki-K0|≤2
Example 2
Taking a certain spherical disc spring design as an example, the design method comprises the following steps:
(1) finite element modeling is carried out on a spherical disc spring, and stress-deformation analysis is carried out. For the structure, four independent geometric dimensions are found, and a space constraint relation is established. With x1An iterative optimization description is performed by taking DH-T (disc spring thickness) as an example.
(2)x1＝x1+A*α。(A＝10，α＝0.05)，x2＝DH-H0，x3＝DH-R01，x4＝DH-SR
Wherein the content of the first and second substances,
x2extreme displacement representing a disc spring (disc spring flattening distance)
x3Representative of the minor diameter of the disc spring
x4-represents the disc spring spherical radius
(3) X is to be1＝x1And substituting the + A x alpha into the finite element model to obtain a corresponding F-S curve (drawing a curve by selecting part of data). The data are as follows: displacement in S units: mm F units: n (partial data curve see attached figure 1)
The data for other sizes are characterized as follows: (drawing only part of the size)
Small disc spring diameter (DH-R01 shown in figure 2), disc spring limit displacement (DH-H0 shown in figure 3), and disc spring spherical radius (DH-SR shown in figure 4).
(4) And according to the finite element analysis result, finding key size factors influencing the bearing capacity and the bearing stability, carrying out detailed interval analysis, and mastering the rigidity and uniqueness of the disc spring. And the size factors of the single part which can not meet the target force value and the rigidity value at the same time are found, the combined disc spring is iteratively installed, and the bearing capacity and the bearing stability are greatly improved.
(5) The combined disc spring mounting structure is shown in figure 1. The data obtained were plotted (see FIG. 5):
at the same thickness, SEC-H0 represents the ultimate displacement dimension of the second disc spring, which is 0.3 in consideration of the actual machining dimension.
And (4) conclusion:
the structural scheme obtained by the invention is obviously improved in the bearing capacity and the constant force stable interval compared with the original scheme, and shows the superiority of the design scheme.
Spherical disc spring (material: beryllium bronze alloy elastic modulus: 1.207E5Mpa Poisson's ratio: 0.3).
While the present invention has been described in detail with reference to the preferred embodiments, the present invention is not limited to the embodiments, but is to be construed as the best mode for carrying out the invention. All equivalent changes and modifications made within the scope of the present invention shall fall within the scope of the present invention.
Claims (2)
1. A high-stability-oriented optimization design method for an elastic element of a micro locking mechanism is characterized in that the optimization design is carried out aiming at the geometric structure size of the elastic element based on a linear iteration optimization searching method, so that the geometric size of the elastic element meets the bearing capacity and the high-stability working characteristic, meanwhile, the combined iteration optimization is carried out aiming at the structure of the elastic element, and a higher stability working interval is realized through the combination of the differentiated structure sizes of the elastic element; the method specifically comprises the following steps:
1) carrying out finite element modeling analysis on an assembly system containing an elastic element to obtain the rigidity characteristic of the system;
2) on the basis of the step 1), judging a simplified scheme of the assembly system, and simplifying the rigidity analysis of the assembly system into the analysis of the deformation of the elastic element according to the fact that the deformation of the assembly system is relatively small under the general condition;
3) aiming at the elastic element parameterized modeling after the simplified scheme in the step 2), analyzing the deformation influence degree of each geometric dimension on the loading process;
4) in the analysis process of the step 3), performing linear search optimization in a feasible domain of the geometric dimension of the elastic element; after optimizing a single elastic element, comparing the combined structures, and selecting the result with the optimal bearing capacity and stability; the specific implementation method comprises the following steps:
step 1: establishing mutually independent geometrical dimensions for the individual spring elements, while giving the spring element target axial force F0And target stiffness K of the elastic element0：
X＝(x1，x2，x3，x4，…，xn)T
Wherein X-is a vector variable established by independent binding sizes;
force value extraction of model F ═ F (X, S) is extracted by ANSYS software, and the model is calculated through rigidity
Constraint conditions are as follows: i Fi-F0|≤1，|Ki-K0|≤2；
Wherein S-is directed at displacement loading changes of the part;
the F (X, S) -force value function is determined by the geometric dimension and the displacement loading;
Fi-is the value of the axial force taken at a point in the interval;
F1，F2-is the axial force value at the end of the interval taken within the interval;
S1，S2is taken from F1，F2A corresponding displacement value;
Ki-means stiffness values within a calculation interval;
1-an acceptable range of force value variations;
2-an acceptable range of stiffness variations;
array defining the size factor position:
define the array a ═ { a ═ a1，a2，a3，a41, 2, 3, 4; address for indicating storage of size factor
Step 2:
establishing a finite element model, and carrying out a loading process, wherein the loading process comprises the following three parts:
the first part is to load the whole stroke according to a certain specific geometric dimension, namely, a single elastic element is flattened, and an F-S curve under the geometric dimension is obtained and is reserved for comparison;
F＝F(X，S)
wherein, S is 0.01I, and I is less than or equal to [ H0 ];
h0-represents the individual spring element flattened by a distance of 100 times;
[H0] -a rounding function;
the second part is that after the full-stroke loading is finished each time, linear iteration is carried out according to the geometric dimension in the first step, and the full-stroke loading is carried out;
wherein, a is 0, 1, 2.. 10, α is constant;
-represents is the correspondence aiThe size of the site storage;
the third part, after completing the iteration of the cost size within a certain gradient, moves the array position and carries out the next xiThe iterative calculation of (2):
1≤j，m，n≤4，ai≠aj≠am≠an
representing four mutually independent geometries, a, in a mutually independent set of geometriesi-the storage positions are represented in correspondence of the geometrical dimensions;
and step 3:
aiming at F-S curves obtained under different size combinations, according to constraint conditions: i Fi-F0|≤1，|Ki-K0|≤2Selecting a proper size scheme;
and 4, step 4:
if the proper size is not found under the constraint condition, entering a combined structure design and adopting an installation mode under different size combinations;
and 5:
different combined structures are iterated according to step 1And carrying out iterative optimization of the structure size until a proper size scheme is found, wherein the following requirements are met: i Fi-F0|≤1，|Ki-K0|≤2。
2. The method for optimally designing the elastic element of the micro locking mechanism facing high stability as claimed in claim 1, wherein in the step 1), the assembling system containing the elastic element is subjected to rigidity analysis, and the function of the elastic element in the deformation process of the assembling system is analyzed.
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| CN104850696A (en) * | 2015-05-15 | 2015-08-19 | 燕山大学 | Large-scale mechanical structure static rigidity optimizing method based on equivalent elastic modulus |
| CN104899400A (en) * | 2015-06-24 | 2015-09-09 | 北京石油化工学院 | Design method of spring piece for repeatable holding-type locking device of magnetic levitation fly wheel |
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