CN114970237A - Method for improving fatigue endurance simulation precision of stabilizer bar system - Google Patents
Method for improving fatigue endurance simulation precision of stabilizer bar system Download PDFInfo
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Abstract
The invention relates to a method for improving fatigue endurance simulation precision of a stabilizer bar system, which comprises finite element modeling; calibrating constitutive parameters of the rubber material; applying bolt pre-tightening load, connecting the cover plate to a local structure of the auxiliary frame in a pressing manner, and pressing the cover plate and the rubber bushing together; carrying out simulation calculation on an external load fatigue working condition, carrying out local structural constraint on the auxiliary frame, adding relative displacement at two ends of the stabilizer bar, and solving to obtain two stress field results; and (4) introducing results of the two stress fields, and finishing calculation of the equal-amplitude fatigue endurance damage value between the two stress fields. According to the invention, accurate load transmission is ensured by establishing contact constraint of the rubber bushing, the stabilizer bar and the cover plate; setting a simulation assembly process through bolt pre-tightening and contact constraint initial interference; the virtual rubber bushing is replaced by the real rubber bushing model, so that the problem that the rigidity test data of the bushing does not meet the finite element simulation requirement is solved; through the measures, three difficult problems in the simulation process of the stabilizer bar system are solved, and the simulation precision is improved.
Description
Technical Field
The invention belongs to the technical field of transverse stabilizer bar systems, and particularly relates to a method for improving fatigue endurance simulation precision of a stabilizer bar system.
Background
The stabilizer bar system is used for preventing the vehicle body from generating overlarge transverse rolling when turning so as to ensure the stability and the smoothness of the vehicle. In the stabilizer bar system, the both ends of stabilizer bar are passed through the connecting rod and are connected on control arm or bumper shock absorber support, and two points pass through the bush to be connected on sub vehicle frame about middle straight section has, and the bush is built-in rubber spare, and coating adhesive and vulcanization become integrative between stabilizer bar and the stabilizer bar bush avoid producing wearing and tearing and abnormal sound in the use. When the automobile turns, the body of the automobile can incline due to the action of centrifugal force, so that the inner wheel is suspended and stretched, the outer wheel is suspended and compressed, the rod body of the stabilizer bar is twisted, and a large torsion force is generated. The stabilizer bar of an automobile can be twisted for 30 ten thousand times in the whole life cycle, so that the design needs to ensure that the stabilizer bar meets the fatigue life of 30 ten thousand times of twisting, and meanwhile, the fatigue life cannot exceed a target value too much, otherwise, the stabilizer bar is over-designed, and material waste and cost increase are caused.
Fatigue durability performance of a stabilizer bar system is an important performance indicator for vehicle development. At present, two methods for predicting the fatigue life of the stabilizer bar are provided, one method is through a bench test, and the other method is through finite element simulation calculation. The former has high precision, but has longer cost and period; the latter has low cost and short period, but the simulation precision can be greatly different due to the difference of simulation methods. The finite element modeling of the prior stabilizer bar system has three difficulties: firstly, the assembly simulation of the bushing needs to consider the interference assembly stress of the bushing, and the assembly process has great influence on the strength of the cover plate of the stabilizer bar; secondly, the connection relation of the position of the bushing is simulated, the contact of the bushing with the stabilizer bar and the cover plate needs to be considered, and the accuracy of local load transmission is ensured; thirdly, the rigidity data of the lining can not meet the requirement of finite element simulation, the nonlinear interval of the rigidity test data of the general lining is shorter, and the problem of poor convergence exists.
At present, when a stabilizer bar system is simulated, the positions of rubber bushings are connected by adopting a virtual bushing unit, one end of each bushing is connected to a stabilizer bar through an rb3 unit, the other end of each bushing is connected to a stabilizer bar cover plate through an rb3 unit, each direction rigidity of the bushing is endowed to simulate a real bushing, when load is transmitted through an rb3, load transmission of each connecting point follows a certain weight coefficient, the weight coefficient is difficult to determine, and therefore the load is transmitted in a local position inaccurately. The method cannot evaluate the connection position of the stabilizer bar, and from past experience, the failure position is often concentrated on the connection position of the bushing, so that the simulation precision is low. Meanwhile, the interference assembly process of the bushing cannot be considered, the assembly stress cannot be substituted into the calculation, and the simulation precision is further reduced. Based on this, a method capable of effectively improving the fatigue endurance simulation accuracy of the stabilizer bar system is urgently needed to be developed.
Disclosure of Invention
The invention aims to provide a method for improving fatigue endurance simulation precision of a stabilizer bar system, which is based on real system modeling and considers the influence of an assembly process so as to solve the problem of low fatigue simulation precision of a finite element of the conventional stabilizer bar system. The method can improve the simulation precision and save the development cost.
The purpose of the invention is realized by the following technical scheme:
a method for improving fatigue endurance simulation accuracy of a stabilizer bar system comprises the following steps:
A. finite element modeling
A1, sequentially drawing grids on stabilizer bar system parts, wherein the stabilizer bar system parts comprise stabilizer bars, a plurality of rubber bushings, a plurality of stabilizer bar cover plates and a plurality of bolts;
a2, establishing material properties;
a3, endowing element attributes, wherein all structures use entity elements;
a4, assembling a model;
a5, establishing constraint and load working conditions; B. rubber material constitutive parameter calibration, calculating initial constitutive parameters of rubber by rubber hardness, and calibrating real constitutive parameters of rubber by a parameter optimization means;
C. assembly process simulation
Applying bolt pre-tightening load, connecting the cover plate to a local structure of the auxiliary frame in a pressing manner, and pressing the cover plate and the rubber bushing together;
D. endurance behavior calculation
On the basis of the step C, performing simulation calculation on an external load fatigue working condition, performing local structural constraint on the auxiliary frame, adding a certain relative displacement to two ends of the stabilizer bar, and solving to obtain two stress field results;
E. endurance damage value calculation
And D, importing the two stress field results calculated in the step D, and finishing the calculation of the equal-amplitude fatigue endurance damage value between the two stress fields.
Further, in step a1, the number of the rubber bushing and the stabilizer bar cover plate is 2, and the number of the bolts is 4.
Further, in step a1, the rubber bushing is divided into hexahedral meshes, so as to ensure that the aspect ratio is greater than or equal to 5, and the meshes of other parts are divided into second-order tetrahedral meshes.
Further, step a2 specifically includes: the rubber body structural material adopts a binomial Mooney-Rivlin model, namely a formula (1), and a rubber constitutive parameter C is calculated by inputting rubber hardness through a material constitutive parameter empirical formula (2) to a formula (4) 10 And C 01 And imparting a density to the material;
W＝C 10 (I 1 -3)+C 01 (I 2 -3) (1)
lgE 0 ＝0.0184H r -0.4575 (2)
G＝E 0 /3＝2(C 10 +C 01 ) (3)
C 01 /C 10 ＝0.05 (4)
wherein, C 10 ，C 01 Is a material constant; e 0 Is the elastic modulus of rubber, H r Rockwell hardness of rubber and G shear modulus.
Further, step a4 specifically includes: connecting bolt holes at two ends of the stabilizer bar by using a rigid unit, wherein a main point is a central point of the bolt hole; tie restraint is made with the stabilizer bar to the bush, and the bush establishes contact restraint with apron, bolt and apron, apron and sub vehicle frame local structure, and wherein there is initial penetration with the apron structure in the bush, and the penetration is the magnitude of interference.
Further, step a5 specifically includes: restraining a local structure of the auxiliary frame, wherein the load working condition comprises two load steps, the first step is an assembly working condition which comprises bolt pre-tightening and interference fit of a bushing and a cover plate; and the second step is an external load working condition, wherein the external load is the relative displacement of two ends of the stabilizer bar, the relative displacement is related to the left and right relative jumping quantity of the wheel center, and the relative displacement is converted into the positions of two ends of the stabilizer bar through a lever ratio.
Further, step B specifically comprises:
b1, through result output and data processing, ensuring that the displacement output interval of the calculated rigidity curve is consistent with that of the tested rigidity curve, and the simulation working condition is the same as that of the rigidity test of the rubber bushing rack, restraining the outer pipe and the inner pipe of the bushing to be loaded, and solving the load and displacement curve;
b2 as C 10 And C 01 Calculating the minimum value of the area S enclosed by the stiffness curve and the test stiffness curve as a variable, and calibrating the constitutive parameters of the rubber;
b3, parameter optimization: firstly preparing a test stiffness curve, then preparing a stiffness calculation finite element model, and carrying out parameterization C 10 And C 01 And setting a target S, building parameter optimization process iterative computation, executing the parameter optimization iterative computation, and finally determining a parameter C 10 And C 01 。
Further, the specific steps of calculating the area S enclosed by the stiffness curve and the test stiffness curve are as follows:
S 1 ＝(a 1 -b 1 ) 2 +(a 2 -b 2 ) 2 +…(a n -b n ) 2 (5)
S 2 ＝(c 1 -d 1 ) 2 +(c 2 -d 2 ) 2 +…(c n -d n ) 2 (6)
S 3 ＝(e 1 -f 1 ) 2 +(e 2 -f 2 ) 2 +…(e n -f n ) 2 (7)
S 4 ＝(g 1 -h 1 ) 2 +(g 2 -h 2 ) 2 +…(g n -h n ) 2 (8)
S 5 ＝(i 1 -j 1 ) 2 +(i 2 -j 2 ) 2 +…(i n -j n ) 2 (9)
S 6 ＝(k 1 -l 1 ) 2 +(k 2 -l 2 ) 2 +…(k n -l n ) 2 (11)
S＝S 1 +S 2 +S 3 +S 4 +S 5 +S 6 (11)
wherein S is 1 、S 2 、S 3 、S 4 、S 5 、S 6 Calculating the area of a wall between the stiffness curve and the test stiffness curve for X, Y, Z three translation directions and three rotation directions respectively, wherein S is the sum of all areas; a is a n 、c n 、e n 、g n 、i n 、k n Calculating the counterforce of the displacement of the stiffness curve at the nth point in X, Y, Z three translation directions and three rotation directions respectively; b n 、d n 、f n 、h n 、j n 、l n The reaction force of the displacement of the stiffness curve at the nth point is tested for X, Y, Z three translation directions and three rotation directions respectively.
Further, step D, one of the two stress field results is a relative displacement plus 50mm stress result, and one is a relative displacement minus 50mm stress result;
and step E, the cycle number is 30 ten thousand, the evaluation index is 1, the damage value result is greater than 1, the requirement on the durability is not met, and the damage value result is less than 1, the requirement on the durability is met.
Compared with the prior art, the invention has the beneficial effects that:
according to the invention, accurate load transmission is ensured by establishing contact constraint of the rubber bushing, the stabilizer bar and the cover plate; setting a simulation assembly process through bolt pre-tightening and contact constraint initial interference; the virtual rubber bushing is replaced by the real rubber bushing model, so that the problem that the rigidity test data of the bushing does not meet the finite element simulation requirement is solved; through the measures, three difficult problems in the simulation process of the stabilizer bar system are solved, and the simulation precision is improved.
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In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings needed to be used in the embodiments will be briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present invention and therefore should not be considered as limiting the scope, and for those skilled in the art, other related drawings can be obtained according to the drawings without inventive efforts.
FIG. 1 is a flow chart of the steps of the method of the present invention for improving fatigue endurance simulation accuracy of a stabilizer bar system;
FIG. 2 is a schematic structural view of a stabilizer bar system;
FIG. 3 is a flow chart for parameter optimization.
Detailed Description
The invention is further illustrated by the following examples:
in order to achieve the purpose of the invention, the process of the invention is elaborated by taking a passenger car stabilizer bar system as an example. The invention adopts hypermesh as pretreatment, abaqus as a solver, isight as a parameter optimization flow building platform, femfat software is used for durable damage value calculation, and a flow chart is shown in figure 1.
Finite element modeling
As shown in fig. 2, the stabilizer bar system part is composed of four types, i.e., a stabilizer bar, a plurality of rubber bushings, a plurality of stabilizer bar cover plates, and a plurality of bolts. In this embodiment, the rubber bush and the stabilizer bar cover plate are 2, and the bolts are 4. The finite element model establishment is divided into 4 steps:
1. grid drawing points
The four parts are sequentially divided into grids, and the rubber bushing is divided into hexahedral grids due to the fact that the rubber elastic modulus is low and the grids are greatly deformed in the deformation process, meanwhile, the length-width ratio is guaranteed to be larger than or equal to 5, and the grids of other parts are divided into second-order tetrahedral grids.
2. Establishing material properties
The rubber body structural material adopts a binomial Mooney-Rivlin model, namely a formula (1), and rubber constitutive parameters C are calculated by inputting rubber hardness through an empirical formula (2) to a formula (4) 10 And C 01 And imparting a density to the material. In this example, the rubber hardness H r 60, according to formula C 10 ＝0.48，C 01 0.12, material density 1.3e-9ton/mm 3 . The other structures are all steel materials, the elastic modulus E is 210000MPa, and the Poisson ratio v is 0.3.
Two-term Mooney-Rivlin model
W＝C 10 (I 1 -3)+C 01 (I 2 -3) (1)
Wherein, C 10 ，C 01 -a material constant;
the model is not only applicable to classical small deformation range, but also applicable to larger deformation range. Due to simplicity and practicality. The model is widely applied to FEA.
The empirical formula of the constitutive parameters of the material is as follows:
lgE 0 ＝0.0184H r -0.4575 (2)
G＝E 0 /3＝2(C 10 +C 01 ) (3)
C 01 /C 10 ＝0.05 (4)
wherein E is 0 Is the elastic modulus of rubber, H r Rockwell hardness of rubber, G shear modulus, C 10 And C 01 To obtainIs determined by the material constant of (1).
3. Attribution to units
All structures use physical units.
4. Model assembly
Connecting bolt holes at two ends of the stabilizer bar by using a rigid unit, wherein a main point is a central point of the bolt hole; tie restraint is made with the stabilizer bar to the bush, and the bush establishes contact restraint with apron, bolt and apron, apron and sub vehicle frame local structure (be used for fixed stabilizer bar), and wherein there is initial penetration with the apron structure in the bush, and the penetration size is the magnitude of interference.
5. Establishing constraint and load conditions
Restraining a local structure of the auxiliary frame, wherein the load working condition comprises two load steps, the first step is an assembly working condition which comprises bolt pre-tightening and interference fit of a bushing and a cover plate; and the second step is an external load working condition, wherein the external load is the relative displacement of two ends of the stabilizer bar, the relative displacement is related to the left and right relative jumping quantity of the wheel center, and the relative displacement is converted into the positions of two ends of the stabilizer bar through a lever ratio.
Second, calibration of constitutive parameters of rubber material
The rubber initial constitutive parameters are calculated through rubber hardness, and have certain difference with real rubber constitutive parameters. The real rubber constitutive parameters need to be calibrated by a parameter optimization means.
With C 10 And C 01 Calculating the area S enclosed by the stiffness curve and the test stiffness curve as a variable, and calibrating the constitutive parameters of the rubber by taking the minimum value of the formula (5) -the formula (11) as a target. Before the test, the displacement output interval of a calculated rigidity curve and a tested rigidity curve is consistent by means of result output and data processing, the simulation working condition is the same as that of a rigidity test of a rubber bushing rack, the outer pipe and the inner pipe of the bushing are restrained to be loaded, and the load and displacement curve is solved. And (3) building an optimization flow by adopting the isight software, calling an abaqus solver to solve, and showing an optimization flow as figure 3. Specifically, a test stiffness curve is prepared, then a stiffness calculation finite element model is prepared, and the stiffness is calculated through parameterization C 10 And C 01 And setting a target S, constructing a parameter optimization process iterative calculation, and executing the parameter optimization iterative calculationFinally, the parameter C is determined 10 And C 01 。
In the present embodiment, the first and second electrodes are,
S 1 ＝(a 1 -b 1 ) 2 +(a 2 -b 2 ) 2 +…(a n -b n ) 2 (5)
S 2 ＝(c 1 -d 1 ) 2 +(c 2 -d 2 ) 2 +…(c n -d n ) 2 (6)
S 3 ＝(e 1 -f 1 ) 2 +(e 2 -f 2 ) 2 +…(e n -f n ) 2 (7)
S 4 ＝(g 1 -h 1 ) 2 +(g 2 -h 2 ) 2 +…(g n -h n ) 2 (8)
S 5 ＝(i 1 -j 1 ) 2 +(i 2 -j 2 ) 2 +…(i n -j n ) 2 (9)
S 6 ＝(k 1 -l 1 ) 2 +(k 2 -l 2 ) 2 +…(k n -l n ) 2 (10)
S＝S 1 +S 2 +S 3 +S 4 +S 5 +S 6 (11)
wherein S is 1 、S 2 、S 3 、S 4 、S 5 、S 6 Calculating the area of a fence of the stiffness curve and the tested stiffness curve respectively for X, Y, Z three translation directions and three rotation directions, wherein S is the sum of all the areas; a is n 、c n 、e n 、g n 、i n 、k n Calculating the counterforce of the displacement of the stiffness curve at the nth point in X, Y, Z three translation directions and three rotation directions respectively; b n 、d n 、f n 、h n 、j n 、l n The counterforce of the displacement of the stiffness curve at the nth point is tested for X, Y, Z three translations and three rotation directions respectively.
Through the parameter optimization process, the constitutive parameter of the rubber is marked as C 10 ＝0.52，,C 01 ＝0.13。
Thirdly, simulation of assembly process
The assembling process is mainly to apply bolt pretension load, connect the apron pressure to sub vehicle frame local structure, and simultaneously with apron and rubber bush pressure equipment together, the initial magnitude of interference of this in-process bush and apron also takes into account together.
Fourth, calculating endurance condition
On the basis of the previous pre-tightening working condition, simulation calculation of an external load fatigue working condition is completed, the auxiliary frame is restrained by a local structure, the plus or minus 50mm relative displacement is added to the two ends of the stabilizing rod, and two stress field results are obtained by using abaqus solution, wherein one stress result is the relative displacement plus or minus 50mm stress result, and the other stress result is the relative displacement minus or 50mm stress result.
Fifthly, durable damage value calculation
And (3) importing the two stress field results calculated in the fourth step into femfat software or other endurance calculation software to finish the calculation of the constant-amplitude fatigue endurance damage value between the two stress fields, wherein the cycle number is 30 ten thousand, the evaluation index is 1, the endurance performance requirement is not met if the damage value result is greater than 1, and the endurance performance requirement is met if the damage value result is less than 1. In the example, the damage value of the stabilizer bar is 0.96, the bench test fails for 34.5 ten thousand times, the failure positions are the same, the simulation precision is over 90 percent, the damage value of the stabilizer bar calculated by the original method is 0.42, and the precision is greatly improved.
Through the five steps, the invention process of improving the fatigue endurance simulation precision of the stabilizer bar is completed, and compared with the traditional simulation method, the simulation precision is greatly improved.
It is to be noted that the foregoing is only illustrative of the preferred embodiments of the present invention and the technical principles employed. It will be understood by those skilled in the art that the present invention is not limited to the particular embodiments described herein, but is capable of various obvious changes, rearrangements and substitutions as will now become apparent to those skilled in the art without departing from the scope of the invention. Therefore, although the present invention has been described in greater detail by the above embodiments, the present invention is not limited to the above embodiments, and may include other equivalent embodiments without departing from the spirit of the present invention, and the scope of the present invention is determined by the scope of the appended claims.
Claims (10)
1. A method for improving fatigue endurance simulation accuracy of a stabilizer bar system is characterized by comprising the following steps:
A. finite element modeling
A1, sequentially drawing grids for stabilizer bar system parts, wherein the stabilizer bar system parts comprise stabilizer bars, a plurality of rubber bushings, a plurality of stabilizer bar cover plates and a plurality of bolts;
a2, establishing material properties;
a3, giving unit attributes, and using entity units for all structures;
a4, assembling a model;
a5, establishing constraint and load working conditions; B. rubber material constitutive parameter calibration, rubber initial constitutive parameters are calculated according to rubber hardness, and then real rubber constitutive parameters are calibrated through parameter optimization means;
C. assembly process simulation
Applying bolt pre-tightening load, connecting the cover plate to a local structure of the auxiliary frame in a pressing manner, and pressing the cover plate and the rubber bushing together;
D. endurance behavior calculation
On the basis of the step C, performing simulation calculation on an external load fatigue working condition, performing local structural constraint on the auxiliary frame, adding a certain relative displacement to two ends of the stabilizer bar, and solving to obtain two stress field results;
E. endurance damage value calculation
And D, importing the two stress field results calculated in the step D, and finishing the calculation of the equal-amplitude fatigue endurance damage value between the two stress fields.
2. The method for improving fatigue endurance simulation accuracy of a stabilizer bar system according to claim 1, wherein: step A1, the rubber bush and stabilizer bar apron are 2, and the bolt is 4.
3. The method for improving fatigue endurance simulation accuracy of a stabilizer bar system according to claim 1, wherein: and step A1, dividing the rubber bushing picture into hexahedral meshes, ensuring that the length-width ratio is greater than or equal to 5, and dividing the meshes of other parts into second-order tetrahedral meshes.
4. The method for improving fatigue endurance simulation accuracy of a stabilizer bar system according to claim 1, wherein step a2 specifically comprises: the rubber body structural material adopts a binomial Mooney-Rivlin model, namely a formula (1), and a rubber constitutive parameter C is calculated by inputting rubber hardness through a material constitutive parameter empirical formula (2) to a formula (4) 10 And C 01 And imparting a density to the material;
W＝C 10 (I 1 -3)+C 01 (I 2 -3) (1)
lgE 0 ＝0.0184H r -0.4575 (2)
G＝E 0 /3＝2(C 10 +C 01 ) (3)
C 01 /C 10 ＝0.05 (4)
wherein, C 10 ，C 01 Is a material constant; e 0 Is the elastic modulus of rubber, H r Rockwell hardness of rubber and G shear modulus.
5. The method for improving fatigue endurance simulation accuracy of a stabilizer bar system according to claim 1, wherein step a4 specifically comprises: connecting bolt holes at two ends of the stabilizer bar by using a rigid unit, wherein a main point is a central point of the bolt hole; tie restraint is made with the stabilizer bar to the bush, and the bush establishes contact restraint with apron, bolt and apron, apron and sub vehicle frame local structure, and wherein there is initial penetration with the apron structure in the bush, and the penetration is the magnitude of interference.
6. The method for improving fatigue endurance simulation accuracy of a stabilizer bar system according to claim 1, wherein step a5 specifically comprises: restraining a local structure of the auxiliary frame, wherein the load working condition comprises two load steps, the first step is an assembly working condition which comprises bolt pre-tightening and interference fit of a bushing and a cover plate; and the second step is an external load working condition, wherein the external load is the relative displacement of two ends of the stabilizer bar, the relative displacement is related to the left and right relative jumping quantity of the wheel center, and the relative displacement is converted into the positions of two ends of the stabilizer bar through a lever ratio.
7. The method for improving fatigue endurance simulation accuracy of a stabilizer bar system according to claim 1, wherein step B specifically comprises:
b1, through result output and data processing, ensuring that the displacement output interval of the calculated rigidity curve is consistent with that of the tested rigidity curve, and the simulation working condition is the same as that of the rigidity test of the rubber bushing rack, restraining the outer pipe and the inner pipe of the bushing to be loaded, and solving the load and displacement curve;
b2, with C 10 And C 01 Calculating the minimum value of the area S enclosed by the stiffness curve and the test stiffness curve as a variable, and calibrating the constitutive parameters of the rubber;
b3, parameter optimization: firstly preparing a test stiffness curve, then preparing a stiffness calculation finite element model, and carrying out parameterization C 10 And C 01 And setting a target S, building parameter optimization process iterative computation, executing the parameter optimization iterative computation, and finally determining a parameter C 10 And C 01 。
8. The method for improving fatigue endurance simulation accuracy of a stabilizer bar system according to claim 7, wherein the specific step of calculating an area S enclosed by the stiffness curve and the test stiffness curve is as follows:
S 1 ＝(a 1 -b 1 ) 2 +(a 2 -b 2 ) 2 +…(a n -b n ) 2 (5)
S 2 ＝(c 1 -d 1 ) 2 +(c 2 -d 2 ) 2 +…(c n -d n ) 2 (6)
S 3 ＝(e 1 -f 1 ) 2 +(e 2 -f 2 ) 2 +…(e n -f n ) 2 (7)
S 4 ＝(g 1 -h 1 ) 2 +(g 2 -h 2 ) 2 +…(g n -h n ) 2 (8)
S 5 ＝(i 1 -j 1 ) 2 +(i 2 -j 2 ) 2 +…(i n -j n ) 2 (9)
S 6 ＝(k 1 -l 1 ) 2 +(k 2 -l 2 ) 2 +…(k n -l n ) 2 (10)
S＝S 1 +S 2 +S 3 +S 4 +S 5 +S 6 (11)
wherein S is 1 、S 2 、S 3 、S 4 、S 5 、S 6 Calculating the area of a fence of the stiffness curve and the tested stiffness curve respectively for X, Y, Z three translation directions and three rotation directions, wherein S is the sum of all the areas; a is n 、c n 、e n 、g n 、i n 、k n Calculating the counterforce of the displacement of the stiffness curve at the nth point in X, Y, Z three translation directions and three rotation directions respectively; b n 、d n 、f n 、h n 、j n 、l n The counterforce of the displacement of the stiffness curve at the nth point is tested for X, Y, Z three translations and three rotation directions respectively.
9. The method for improving fatigue endurance simulation accuracy of a stabilizer bar system according to claim 1, wherein: and D, one of the two stress field results is a relative displacement plus 50mm stress result, and the other is a relative displacement minus 50mm stress result.
10. The method for improving fatigue endurance simulation accuracy of a stabilizer bar system according to claim 1, wherein: and E, cycling for 30 ten thousand times, evaluating the index to be 1, and if the damage value result is greater than 1, the requirement on the durability is not met, and if the damage value result is less than 1, the requirement on the durability is met.
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| CN117634265A (en) * | 2024-01-25 | 2024-03-01 | 潍柴动力股份有限公司 | Cylinder cover unloading groove parameter determination method and related device |
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2022
- 2022-04-21 CN CN202210424742.1A patent/CN114970237A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117634265A (en) * | 2024-01-25 | 2024-03-01 | 潍柴动力股份有限公司 | Cylinder cover unloading groove parameter determination method and related device |
| CN117634265B (en) * | 2024-01-25 | 2024-05-17 | 潍柴动力股份有限公司 | Cylinder cover unloading groove parameter determination method and related device |
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