CN109918780A - A kind of small retaining mechanism elastic element optimum design method towards high stability - Google Patents
A kind of small retaining mechanism elastic element optimum design method towards high stability Download PDFInfo
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Abstract
The small retaining mechanism elastic element optimum design method towards high stability that the invention discloses a kind of, method of this method based on linear iteraction optimizing, it carries out seeking optimization design for elastic element geometric structure diamete, the geometric dimension of elastic element is set to meet the working characteristics of bearing capacity and high stable, simultaneously, it is combined formula iteration optimizing for the structure of elastic element, higher stability operation interval is realized by the differentiation structure size combination of elastic element.One kind proposed by the present invention is towards the small retaining mechanism elastic element optimum design method of high stability, based on the parameterized finite element modeling analysis to product, crucial geometric dimension is carried out for structure to extract, the search carried out in feasible zone achievees the purpose that structure optimization, get rid of the dependence to experience, design time has been saved, design optimum value is achieved.
Description
Technical field
The invention belongs to Optimal Structure Designing technical fields, and in particular to a kind of small retaining mechanism towards high stability
Elastic element optimum design method.
Background technique
Mechanical pendulous accelerometer is the Sensitive Apparatus of inertial navigation system, has been widely used in space flight, aviation, navigation
Equal fields, performance directly determine Inertial Navigation and Guidance system accuracy.Small retaining mechanism is mechanical pendulous accelerometer
Core component, locking load reliability directly affects the zero bias long-time stability of pendulous accelerometer, it has also become restricts
One of key technology bottleneck of inertial navigation system precision improvement.
The small retaining mechanism of mechanical pendulous accelerometer is mainly by compressing structure, spring element, upper bottom crown and center
Spare part in accelerometer with certain physical parameter transfer characteristic is assembled into one by applying connection load by bolt composition
It rises, and guarantees to put the rigging position and mechanical state of component.Since the spring element rigidity of structure is weaker, small locking machine is carried
The overwhelming majority deformation of construction system, therefore, the mechanical and physical property of spring element directly decide retaining mechanism connection load
Horizontal and stability, to influence the installation condition and zero offset error of accelerometer pendulum component.It can be seen that how to rationally design
Spring element structure type, so that its mechanical and physical property is met the long-time stability of connection load is elevating mechanism pendulum-type acceleration
Count the key point of military service performance.
Currently, the design of small retaining mechanism spring element often relies on experience handbook, obtained by a large number of experiments trial and error
The structure met the requirements, design efficiency are low；The present invention proposes to utilize finite element technique, establishes elastic element parameterized model, tie
It closes geometric dimension optimization to optimize with structure composition, has freed manpower, saved design time, and design optimum value can be obtained, it is real
The high stability of small retaining mechanism load is showed.
Summary of the invention
The small retaining mechanism elastic element optimum design method towards high stability that the object of the present invention is to provide a kind of,
To realize the purpose of constant force locking；For the aximal deformation value part contained in system, the kernel size factor for influencing rigidity is found,
It is iterated optimizing, higher stability operation interval is realized by the differentiation structure size combination of elastic element.
The present invention adopts the following technical scheme that realize:
A kind of small retaining mechanism elastic element optimum design method towards high stability, this method are based on linear iteraction
The method of optimizing carries out seeking optimization design for elastic element geometric structure diamete, meets the geometric dimension of elastic element and holds
The working characteristics of loading capability and high stable, meanwhile, it is combined formula iteration optimizing for the structure of elastic element, passes through elasticity
The differentiation structure size combination of element realizes higher stability operation interval.
A further improvement of the present invention lies in that specifically includes the following steps:
1) modeling Analysis is carried out for the assembly system containing elastic element, obtains system stiffness characteristic；
2) on the basis of step 1), judge assembly system reduction procedure, according under normal circumstances, the deformation of assembly system
It is relatively small, therefore the stiffness analysis of assembly system is reduced to the analysis of deformation of elastic element；
3) for the elastic element parametric modeling after step 2) reduction procedure, its each geometric dimension is analyzed to loading
The deformation influence degree of journey；
4) in the analytic process of step 3), in the feasible zone of elastic element geometric dimension, linear search optimizing is carried out；
And after to single elastic element optimizing, composite structure is compared, selects bearing capacity and the optimal result of stability.
A further improvement of the present invention lies in that for the assembly system comprising elastic element, carrying out rigidity point in step 1)
Analysis, analysing elastic element is in assembly system deformation process, the effect of elastic element performance.
A further improvement of the present invention lies in that the concrete methods of realizing of step 4) is as follows:
Step 1: it establishes about the mutually independent geometric dimension of single elastic element, meanwhile, provide target axial force F0With
Rigidity stationary value K0:
X=(x1, x2, x3, x4..., xn)T
Wherein, the vector variable that X- is established by independent combination size；
The force value of model, which is extracted, extracts F=F (X, S) by ANSYS software, Rigidity Calculation model
Constraint condition: | Fi-F0|≤ε1, | Ki-K0|≤ε2；
Wherein, S- loads variation for the displacement of part；
F (X, S)-force value function is determined by geometric dimension and displacement load；
FiIt is that certain puts the axial force numerical value got in section；
F1, F2It is axial force at the interval endpoint got in section；
S1, S2It is to take F1, F2When corresponding shift value；
KiRefer to the rigidity value in computation interval；
K0Refer to target call numerical value；
ε1Acceptable force value variation range；
ε2Acceptable stiffness variation range；
Define the array of size factor position:
Define arrays a={ a1, a2, a3, a4}={ 1,2,3,4 }；For indicating the address of size factor storage
Step 2:
Finite element model is established, loading procedure is carried out and is divided into following three parts during loading:
First part is to carry out the load of total travel, i.e., by single elastic element pressure for a certain particular geometric size
It is flat, the F-S curve under this geometric dimension is obtained, comparison is given over to；
F=F (X, S)
Wherein, S=0.01*I, I≤[H0]；
H0- indicates 100 times of distance that flatten single elastic element；
[H0]-bracket function；
Second part is carried out for the geometric dimension in the first step linear after the completion of carrying out total travel load every time
Iteration, in the load for carrying out total travel；
Wherein, A=0,1,2...10, α=constant；That indicate is corresponding aiThe size of position storage；
Part III, completes this size after the iteration in certain gradient, and mobile array position carries out next xi
Iterative calculation:
1≤j, m, n≤4, ai≠aj≠am≠an
It indicates in mutually independent geometric dimension set, mutually independent four geometric dimensions, aiWhat is indicated is corresponding
The storage position of geometric dimension；
Step 3:
For the F-S curve obtained under different dimension combinations, according to constraint condition: | Fi-F0|≤ε1, | Ki-K0|≤ε2, choosing
Select suitably sized scheme；
Step 4:
If under constraint condition, do not find it is suitably sized, then enter fabricated structure design, using different sizes
Mounting means under combination；
Step 5:
Various combination structure iteration then re-starts the iteration optimizing of structure size according to step 1, suitable until finding
Dimension plan meets: | Fi-F0|≤ε1, | Ki-K0|≤ε2。
The present invention has following beneficial technical effect:
1) present invention proposes a kind of new iteration optimization aiming at the problem that bearing capacity under identical structure and insufficient rigidity
Scheme, that is, under the structural condition for not changing part, realize that rigidity is complementary by the change of combination.
2) the constant force locking under limited assembly space may be implemented in the present invention, improves the stability of equipment performance.
3) present invention has found optimum combination dimension plan under boundary condition, improved efficiency by multiple nested circulation.
4) first, it is independent geometric dimension linear iteraction, in certain size range inner iteration optimizing.Second, it terminates
Condition is: | Fi-F0|≤ε1, | Ki-K0|≤ε2, the condition that meets is the dimension combination scheme optimized.
5) first, it is not limited to the geometric dimension of a part.When there is no optimizing result in given range, the design
Scheme can be applicable in the part combination for selecting identical structure difference specific size；Second, the size of component parts determines, still suitable
It is determined with present design.
In conclusion one kind proposed by the present invention is towards high stability small retaining mechanism elastic element optimization design side
Method is carried out crucial geometric dimension for structure and extracted, carried out in feasible zone based on the parameterized finite element modeling analysis to product
Search achieve the purpose that get rid of structure optimization the dependence to experience, saved design time, it is best to achieve design
Value.By taking disc spring as an example, for the unique variation rigidity feature of disc spring part, the iteration optimization of size factor is carried out, is found optimal
Dimension combination；In the size in face of being unsatisfactory for requiring, creativeness carries out stiffness combine optimization, carries out non-equal size to disc spring
Under rigidity it is complementary, realizing can stablize in the carrying in biggish deformation range, fully meet rigidity and bearing capacity
It is required that.
Detailed description of the invention
Fig. 1 is single disc spring thickness change to stress and deformation data curve (partial data).
Fig. 2 is disc spring path change in size to stress and deformation data curve (partial data).
Fig. 3 is single disc spring extreme displacement variation to stress and deformation data curve (partial data).
Fig. 4 is single disc spring spherical radius variation to stress and deformation data curve (partial data).
Fig. 5 is Combination nova structure and original single disc spring to stress and deformation data curve.
Fig. 6 is part size schematic diagram.
Fig. 7 is the cross-sectional view of Fig. 6.
Fig. 8 is structure design core combination schematic diagram.
Fig. 9 is the cross-sectional view of Fig. 8.
Figure 10 is the schematic diagram of original structure, and centre is not bolt, is the flank of axis processing.
Figure 11 is the cross-sectional view of Figure 10.
Figure 12 is the schematic diagram of new construction, and centre is not bolt, is the flank of axis processing.
Figure 13 is the cross-sectional view of Figure 12.
Specific embodiment
The present invention is made further instructions below in conjunction with drawings and examples.
A kind of small retaining mechanism elastic element optimum design method towards high stability provided by the invention is based on certain
Elastic element-spherical surface disc spring in assembly system assembles installation method, comprising the following steps:
Step 1: it establishes about the mutually independent geometric dimension of spherical surface disc spring, meanwhile, provide target axial force F0And rigidity
Stationary value K0:
X=(x1, x2, x3, x4..., xn)T
Wherein,
The vector variable that X- is established by independent combination size.
The force value of model, which is extracted, extracts F=F (X, S) by ANSYS software, Rigidity Calculation model
Constraint condition: | Fi-F0|≤ε1, | Ki-K0|≤ε2
Wherein S- loads variation for the displacement of part
F (X, S)-force value function is determined by geometric dimension and displacement load
ε1Acceptable force value variation range.
ε2Acceptable stiffness variation range.
Define the array of size factor position:
Define arrays a={ a1, a2, a3, a4}={ 1,2,3,4 }
Step 2:
Finite element model is established, loading procedure is carried out.During loading, divide three parts:
First part is to carry out the load of total travel for a certain particular geometric size, obtains under this geometric dimension
F-S curve gives over to comparison.(see attached drawing 1)
F=F (X, S)
Wherein, S=0.01*I, I≤[H0]；
H0- indicates 100 times of distance that flatten disc spring
[H0]-bracket function
Second part is carried out for the geometric dimension in the first step linear after the completion of carrying out total travel load every time
Iteration, in the load for carrying out total travel.(see attached drawing 1)
A=0, α=constant
α-selected growth ratio
Part III, completes this size after the iteration in certain gradient, and mobile array position carries out nextIterative calculation.
1≤j, m, n≤4, ai≠aj≠am≠an
Step 3:
For the F-S curve obtained under different dimension combinations, according to constraint condition: | Fi-F0|≤ε1, | Ki-K0|≤ε2, choosing
Select suitably sized scheme.
Step 4:
If under constraint condition, do not find it is suitably sized, then enter fabricated structure design, using different sizes
Mounting means under combination.
Step 5:
Various combination structure iteration then re-starts the iteration optimizing of structure size according to step 1.It is suitable until finding
Dimension plan.Meet: | Fi-F0|≤ε1, | Ki-K0|≤ε2
Embodiment 2
By taking certain spherical surface disc spring design as an example, which includes the following steps:
(1) by carrying out finite element modeling to certain spherical surface disc spring, force-deflection analysis is carried out.For its structure, four are found
A independent geometric dimension, and establish space constraint relationship.With x1For=DH-T (disc spring thickness), it is iterated optimization and says
It is bright.
(2)x1=x1+A*α.(A=10, α=0.05), x2=DH-H0, x3=DH-R01, x4=DH-SR
Wherein,
x2Represent the extreme displacement (disc spring pressing distance) of disc spring
x3Represent disc spring minor diameter
x4Represent disc spring spherical radius
(3) by x1=x1+ A* α brings finite element model into, obtains corresponding F-S curve (selected part data trace).Number
According to as follows: displacement S unit: mm F unit: N (partial data curve is shown in attached drawing 1)
The data characteristics of other sizes are as follows: (only portion size being taken to do figure)
Disc spring path (DH-R01 is shown in attached drawing 2), disc spring extreme displacement (DH-H0 is shown in attached drawing 3), disc spring spherical radius (DH-SR
See attached drawing 4).
(4) according to Finite element analysis results, the critical size factor for influencing bearing capacity and bearing stability is found, is gone forward side by side
Row refinement interval analysis, it is just unique to grasp disc spring.It was found that not meeting target force values and rigidity value obtains single part ruler simultaneously
Very little factor is combined formula disc spring installation iteration, realizes the significantly promotion of bearing capacity and bearing stability.
(5) combined type disc spring mounting structure is shown in attached drawing 1.Obtained data and curves (see attached drawing 5):
Under same thickness, SEC-H0 represents the extreme displacement size of second disc spring, it is contemplated that actual processing ruler
Very little, second disc spring extreme displacement takes 0.3.
Conclusion:
No matter the organization plan obtained through the invention than former scheme has in bearing capacity or constant force stable region
It is obviously improved, it is shown that the superiority of present design.
Spherical surface disc spring (material: beraloy elasticity modulus: 1.207E5Mpa Poisson's ratio: 0.3).
A case study on implementation of the invention is described in detail above, but the content is only preferable reality of the invention
Example is applied, should not be considered as limiting the scope of the invention.It is all according to equivalent change made by the present patent application range with change
Into etc., it should all still fall within patent covering scope of the invention.
Claims (4)
1. a kind of small retaining mechanism elastic element optimum design method towards high stability, which is characterized in that this method base
In the method for linear iteraction optimizing, carries out seeking optimization design for elastic element geometric structure diamete, make the geometry of elastic element
Size meets the working characteristics of bearing capacity and high stable, meanwhile, it is combined formula iteration for the structure of elastic element and seeks
It is excellent, higher stability operation interval is realized by the differentiation structure size combination of elastic element.
2. a kind of small retaining mechanism elastic element optimum design method towards high stability according to claim 1,
It is characterized in that, specifically includes the following steps:
1) modeling Analysis is carried out for the assembly system containing elastic element, obtains system stiffness characteristic；
2) on the basis of step 1), judge assembly system reduction procedure, according under normal circumstances, the deformation of assembly system is opposite
It is smaller, therefore the stiffness analysis of assembly system is reduced to the analysis of deformation of elastic element；
3) for the elastic element parametric modeling after step 2) reduction procedure, its each geometric dimension is analyzed to loading procedure
Deform influence degree；
4) in the analytic process of step 3), in the feasible zone of elastic element geometric dimension, linear search optimizing is carried out；And
After single elastic element optimizing, composite structure is compared, selects bearing capacity and the optimal result of stability.
3. a kind of small retaining mechanism elastic element optimum design method towards high stability according to claim 2,
It is characterized in that, for the assembly system comprising elastic element, carrying out stiffness analysis, analysing elastic element is filling in step 1)
In match system deformation process, the effect of elastic element performance.
4. a kind of small retaining mechanism elastic element optimum design method towards high stability according to claim 2,
It is characterized in that, the concrete methods of realizing of step 4) is as follows:
Step 1: it establishes about the mutually independent geometric dimension of single elastic element, meanwhile, provide target axial force F0It is steady with rigidity
Definite value K0:
X=(x1,x2,x3,x4,…,xn)T
Wherein, the vector variable that X- is established by independent combination size；
The force value of model, which is extracted, extracts F=F (X, S) by ANSYS software, Rigidity Calculation model
Constraint condition: | Fi-F0|≤ε1, | Ki-K0|≤ε2；
Wherein, S- loads variation for the displacement of part；
F (X, S)-force value function is determined by geometric dimension and displacement load；
FiIt is that certain puts the axial force numerical value got in section；
F1,F2It is axial force at the interval endpoint got in section；
S1,S2It is to take F1,F2When corresponding shift value；
KiRefer to the rigidity value in computation interval；
K0Refer to target call numerical value；
ε1Acceptable force value variation range；
ε2Acceptable stiffness variation range；
Define the array of size factor position:
Define arrays a={ a1,a2,a3,a4}={ 1,2,3,4 }；For indicating the address of size factor storage
Step 2:
Finite element model is established, loading procedure is carried out and is divided into following three parts during loading:
First part is to carry out the load of total travel for a certain particular geometric size, i.e., flatten single elastic element, obtain
The F-S curve under this geometric dimension is taken, comparison is given over to；
F=F (X, S)
Wherein, S=0.01*I, I≤[H0]；
H0- indicates 100 times of distance that flatten single elastic element；
[H0]-bracket function；
Second part is to carry out linear iteraction for the geometric dimension in the first step after the completion of carrying out total travel load every time,
In the load for carrying out total travel；
Wherein, A=0,1,2 ... 10, α=constant；That indicate is corresponding aiThe size of position storage；
Part III, completes this size after the iteration in certain gradient, and mobile array position carries out next xiRepeatedly
In generation, calculates:
1≤j,m,n≤4,ai≠aj≠am≠an
It indicates in mutually independent geometric dimension set, mutually independent four geometric dimensions, aiWhat is indicated is corresponding geometry
The storage position of size；
Step 3:
For the F-S curve obtained under different dimension combinations, according to constraint condition: | Fi-F0|≤ε1,|Ki-K0|≤ε2, selection conjunction
Suitable dimension plan；
Step 4:
If under constraint condition, do not find it is suitably sized, then enter fabricated structure design, using different dimension combinations
Under mounting means；
Step 5:
Various combination structure iteration then re-starts the iteration optimizing of structure size according to step 1, suitably sized until finding
Scheme meets: | Fi-F0|≤ε1,|Ki-K0|≤ε2。
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| CN111062161A (en) * | 2019-12-11 | 2020-04-24 | 浙江大学 | Large-tension high-stability light and small constant force device |
| CN111173873A (en) * | 2020-02-26 | 2020-05-19 | 中国工程物理研究院总体工程研究所 | Spherical net-shaped disc spring |
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