CN105138806B - The strength check methods of hydro-pneumatic spring not uniform thickness annular valve block - Google Patents
The strength check methods of hydro-pneumatic spring not uniform thickness annular valve block Download PDFInfo
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Abstract
The present invention relates to the strength check methods of hydro-pneumatic spring not uniform thickness annular valve block, belong to hydro pneumatic suspension technical field.The strength check methods of hydro-pneumatic spring provided by the invention not uniform thickness annular valve block, can be according to the structural parameters and material property parameter of hydro-pneumatic spring not uniform thickness annular valve block, accurate Analysis calculating is carried out to the maximum combined stress of not uniform thickness annular valve block, so as to accurately be checked to the stress intensity of hydro-pneumatic spring not uniform thickness annular valve block.By compared with ANSYS simulation results, the strength check methods are accurate, reliable, to realize that hydro-pneumatic spring modernizes CAD design and the stress intensity of uniform thickness annular valve block is not checked, there is provided reliable not stress intensity check method of the uniform thickness annular valve block under well-distributed pressure.Design level, quality and the performance of hydro-pneumatic spring can be improved using this method, reduces the design and testing expenses of hydro-pneumatic spring, on the premise of characteristic design requirement is ensured, meets the requirement of hydro-pneumatic spring projected life.
Description
Technical Field
The invention relates to a hydro-pneumatic spring, in particular to a strength checking method of a hydro-pneumatic spring unequal-thickness annular valve plate.
Background
For the stress intensity check of the hydro-pneumatic spring unequal-thickness annular valve plate, an accurate and reliable method is not available at home and abroad previously, the maximum composite stress is checked by numerical simulation through establishing a solid model for the unequal-thickness annular valve plate under a given pressure by utilizing finite element simulation software, but the solid model needs to be established and an accurate analytic calculation formula and a calculation method cannot be provided, and the method is low in calculation speed and has a certain difference from the actual calculation value. With the rapid development of the automobile industry and the continuous improvement of the driving speed, higher requirements are put forward on the design of the hydro-pneumatic spring and the unequal-thickness annular valve plates, at present, finite element simulation software is utilized to carry out simulation checking calculation on the strength of the unequal-thickness annular valve plates through solid modeling, an accurate analytic calculation formula is lacked, and the requirements of the rapid development of the modern automobile industry and the modern CAD design of the hydro-pneumatic spring cannot be met. Therefore, in order to meet the requirements of modern CAD design and stress intensity check of the hydro-pneumatic spring and the unequal-thickness annular valve plate, an accurate and reliable intensity check method of the hydro-pneumatic spring unequal-thickness annular valve plate must be established.
Disclosure of Invention
Aiming at the defects in the prior art, the technical problem to be solved by the invention is to provide an accurate and reliable strength checking method for the annular valve plates with unequal thicknesses of the hydro-pneumatic spring, and the calculation flow chart is shown in figure 1; the hydro-pneumatic spring unequal-thickness annular valve plate mechanical model is shown in figure 2.
In order to solve the technical problem, the strength checking method of the hydro-pneumatic spring unequal-thickness annular valve plate is characterized by comprising the following calculation steps of:
(1) Determining constant term X formed by maximum composite stress coefficients of annular valve plates with different thicknesses 1 And X 2 ：
According to the elastic modulus E and the Poisson ratio mu of the annular valve plates with different thicknesses, the variable thickness radius r t Effective inner circle radius r a Outer radius r b Establishing a characteristic equation of a constant term formed by the maximum composite stress coefficient of the annular valve plates with different thicknesses, namely:
wherein, Y 1 And Y 2 Constant term X constructed for calculating maximum composite stress coefficient 1 And X 2 The intermediate parameter variable of (1); solving for X as described above using the Matlab program 1 、X 2 、Y 1 And Y 2 The constant term X formed by the maximum composite stress coefficient of the annular valve plates with different thicknesses is obtained 1 And X 2 ；
(2) Determining the maximum composite stress coefficient G of the annular valve plate with different thicknesses Cσmax ：
According to the elastic modulus E of the unequal-thickness annular valve plate of the hydro-pneumatic spring and the effective inner circle radius r a Outer radius r b And (2) obtaining a constant term X consisting of the maximum composite stress coefficient of the annular valve plates with different thicknesses obtained in the step (1) 1 And X 2 Determining the maximum composite stress coefficient G of the annular valve plate with different thicknesses Cσmax Namely:
in the formula (I), the compound is shown in the specification,
(3) Calculating the maximum composite stress sigma of the annular valve plates with different thicknesses Cmax ：
According to the thickness h of the equal-thickness part of the unequal-thickness annular valve plate 0 The uniformly distributed pressure p and G obtained in the step (2) Cσmax Calculating the maximum composite stress sigma of the annular valve plate with different thicknesses Cmax Namely:
(4) Checking the stress intensity of the annular valve plates with different thicknesses:
according to allowable stress [ sigma ] of annular valve plates with different thicknesses]And σ obtained in step (3) Cmax And checking the stress intensity, namely: if σ is Cmax >[σ]If the annular valve plate with different thickness does not meet the requirement of stress intensity; if σ is Cmax <[σ]And the annular valve plates with different thicknesses can meet the requirement of stress strength.
Compared with the prior art, the invention has the advantages that:
for the stress intensity check of the hydro-pneumatic spring unequal-thickness annular valve plate, an inaccurate and reliable calculation method is not available at home and abroad previously, the maximum composite stress is checked by numerical simulation through establishing a solid model for the unequal-thickness annular valve plate under a given pressure by utilizing finite element simulation software, but the solid model needs to be established and an accurate analytic calculation formula and a calculation method cannot be provided.
According to the strength checking method of the hydro-pneumatic spring unequal-thickness annular valve plate, provided by the invention, the maximum composite stress of the unequal-thickness annular valve plate can be quickly and accurately calculated according to the structural parameters and the material performance parameters of the hydro-pneumatic spring unequal-thickness annular valve plate, so that the stress strength of the hydro-pneumatic spring unequal-thickness annular valve plate can be accurately checked. Compared with ANSYS simulation results, the strength checking method is reliable and accurate in calculation results, and provides a stress strength checking method of the unequal-thickness annular valve plate under uniform distribution pressure for realizing modern CAD design of the hydro-pneumatic spring and stress strength checking of the unequal-thickness annular valve plate; the method can improve the design level, quality and performance of the hydro-pneumatic spring, reduce the design and test cost of the hydro-pneumatic spring, and meet the requirement on the design life of the hydro-pneumatic spring on the premise of ensuring the characteristic design requirement of the hydro-pneumatic spring.
Drawings
For a better understanding of the invention, reference is made to the following further description taken in conjunction with the accompanying drawings.
FIG. 1 is a flow chart of a strength checking method of a hydro-pneumatic spring unequal-thickness annular valve plate;
FIG. 2 is a mechanical model diagram of a hydro-pneumatic spring unequal-thickness annular valve plate;
FIG. 3 is a stress simulation cloud picture of the hydro-pneumatic spring unequal-thickness annular valve plate.
Detailed Description
The present invention will be described in further detail below with reference to an example.
The hydro-pneumatic spring of a special vehicle adopts annular valve plates with different thicknesses, the elastic modulus E =200GPa, the Poisson ratio mu =1/3, and the thickness h of the equal-thickness part 0 =0.3mm, variable thickness radius r t =7.3mm, effective inner circle radius r a =5.0mm, radius r of the outer circle b =8.5mm, allowable stress [ σ ]]=2000MPa. At the radius of valve sheet [5.0,8.5 ]]And (3) applying uniform distribution pressure p =3.0MPa to the mm interval, and checking the stress intensity of the annular valve plates with different thicknesses.
The strength checking method of the hydro-pneumatic spring unequal-thickness annular valve plate provided by the embodiment of the invention has the following specific steps that a calculation flow chart is shown in figure 1, a hydro-pneumatic spring unequal-thickness annular valve plate mechanical model is shown in figure 2, and the method comprises the following steps:
(1) Determining constant term X formed by maximum composite stress coefficients of annular valve plates with different thicknesses 1 And X 2 ：
According to the elastic modulus E =200GPa and the Poisson ratio mu =1/3 of the annular valve plate with different thickness, the variable thickness radius r t =7.3mm, effective inner circle radius r a =5.0mm, radius r of the outer circle b And (2) establishing a characteristic equation of a constant term formed by the maximum composite stress coefficient of the annular valve plates with different thicknesses, namely:
solving for X as described above using Matlab program 1 、X 2 、Y 1 And Y 2 The constant term X formed by the maximum composite stress coefficient of the annular valve plates with different thicknesses is obtained 1 ＝5.059×10 -15 And X 2 ＝1.526×10 -20 ；
(2) Determining the maximum composite stress coefficient G of the annular valve plate with different thicknesses Cσmax ：
According to the elastic modulus E =200GPa of the unequal-thickness annular valve plate of the hydro-pneumatic spring, the effective inner circle radius r a =5.0mm, excircle radius r b =8.5mm and constant term X formed by the maximum composite stress coefficient of the annular valve plate with different thickness obtained in the step (1) 1 ＝5.059 -15 And X 2 ＝1.526 -20 Determining the maximum composite stress coefficient G of the annular valve plate with different thicknesses Cσmax Namely:
in the formula (I), the compound is shown in the specification,
(3) Calculating the maximum composite stress sigma of the annular valve plate with different thicknesses Cmax ：
According to the thickness h of the equal-thickness part of the unequal-thickness annular valve plate 0 =0.3mm, uniform distribution pressure p =3.0MPa, and G obtained in step (2) Cσmax ＝4.20459×10 -11 m 2 Calculating the maximum composite stress sigma of the annular valve plate with different thicknesses Cmax Namely:
(4) Checking the stress intensity of the unequal-thickness annular valve plate:
according to allowable stress [ sigma ] of annular valve plates with different thicknesses]=2000MPa, and σ determined in step (3) Cmax =1401.53MPa, and it can be known that Cmax <[σ]Namely, the annular valve plates with different thicknesses can meet the requirement of stress intensity.
According to the unequal-thickness annular valve plate of the hydro-pneumatic spring in the embodiment, the elastic modulus E =200GPa, the Poisson ratio mu =1/3, and the thickness h of the equal-thickness part is equal to that of the valve plate 0 =0.3mm, variable thickness radius r t =7.3mm, effective inner circle radius r a =5.0mm, excircle radius r b =8.5mm, the pressure is p =3.0MPa, the model is established by ANSYS finite element analysis software, the boundary condition is consistent with the mechanical model shown in figure 2, the model is divided into grids by taking 0.1mm as a unit, and the radius [5.0,8.5 ] is measured]The uniform distribution pressure of 3.0MPa is applied to the mm section, the valve plate is subjected to static simulation analysis, and a stress simulation cloud chart of the annular valve plate with different thickness is obtained and is shown in figure 3.
As can be seen from the simulation result of fig. 3, the maximum simulated value of the composite stress of the annular valve plates with different thicknesses is 1390MPa under the uniform distribution pressure p =3.0MPa, and is matched with the maximum composite stress 1401.53MPa calculated by the strength checking method, and the relative deviation is only 0.79%. The result shows that the established strength checking method of the hydro-pneumatic spring unequal-thickness annular valve plate is correct.
Claims (1)
1. The strength checking method of the unequal-thickness annular valve plate of the hydro-pneumatic spring comprises the following specific calculation steps of:
(1) Determining constant term X formed by maximum composite stress coefficient of annular valve plates with different thicknesses 1 And X 2 ：
According to the elastic modulus E and the Poisson ratio mu of the annular valve plates with different thicknesses, the thickness radius r is changed t Effective inner circle radius r a Outer circle radius r b Establishing a characteristic equation of a constant term formed by the maximum composite stress coefficient of the annular valve plates with different thicknesses, namely:
wherein, Y 1 And Y 2 Constant term X constructed for calculating maximum composite stress coefficient 1 And X 2 The intermediate parameter variable of (2); solving for X as described above using Matlab program 1 、X 2 、Y 1 And Y 2 The constant term X formed by the maximum composite stress coefficient of the annular valve plates with different thicknesses is obtained 1 And X 2 ；
(2) Determining the maximum composite stress coefficient G of the annular valve plate with different thicknesses Cσmax ：
According to the elastic modulus E of the unequal-thickness annular valve plate of the hydro-pneumatic spring, the elastic modulus E is effectively withinRadius of circle r a Outer circle radius r b And a constant term X consisting of the maximum composite stress coefficient of the annular valve plates with different thicknesses obtained in the step (1) 1 And X 2 Determining the maximum composite stress coefficient G of the annular valve plate with different thicknesses Cσmax Namely:
in the formula (I), the compound is shown in the specification,
(3) Calculating the maximum composite stress sigma of the annular valve plates with different thicknesses Cmax ：
According to the thickness h of the equal-thickness part of the unequal-thickness annular valve plate 0 The uniform pressure p and G obtained in step (2) Cσmax Calculating the maximum composite stress sigma of the annular valve plates with different thicknesses Cmax Namely:
(4) Checking the stress intensity of the annular valve plates with different thicknesses:
according to allowable stress [ sigma ] of annular valve plates with different thicknesses]And σ obtained in step (3) Cmax And checking the stress intensity, namely: if σ is Cmax >[σ]The annular valve plate with different thicknesses can not meet the requirement of stress intensity; if σ is Cmax <[σ]And the annular valve plates with different thicknesses can meet the requirement of stress strength.
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| CN105912758A (en) * | 2016-04-07 | 2016-08-31 | 周长城 | Method for checking strength of each of end contact type few-leaf root enhanced master and slave springs |
| CN105893684A (en) * | 2016-04-07 | 2016-08-24 | 周长城 | Calibrating method for strengths of non-end contact type few-leaf root-reinforcing main and auxiliary springs |
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