CN104361166A - Design method for suspension space of internal bias non-coaxial cab stabilizer bar system - Google Patents

Abstract

The invention relates to a design method for a suspension space of an internal bias non-coaxial cab stabilizer bar system, and belongs to the technical field of cab suspension. The suspension space is solved and designed by using the rolling angular stiffness, the relationships between the stabilizer bar structure and the suspension space, and between the radial stiffness of a rubber bushing and equivalent combination line stiffness and Matlab through a suspension space design mathematic model according to the structure and material characteristic parameters of the internal bias non-coaxial cab stabilizer bar system. Through example design and ANSYS simulation verification, an accurate and reliable suspension space design value of the internal bias non-coaxial cab stabilizer bar system can be obtained by the method; a reliable design method is provided for design of the cab stabilizer bar system. By virtue of the method, the design level and performance of the stabilizer bar system can be improved by only adjusting and designing the suspension space under the premise that the product cost is not increased; the driving smoothness and safety of a vehicle are improved; meanwhile, the design and testing expenses can also be lowered.

Description

The method for designing of the suspension spacing of interior biased non-coaxial pilothouse stabilizer bar system

Technical field

The present invention relates to vehicle cab suspension, the method for designing of the suspension spacing of biased non-coaxial pilothouse stabilizer bar system particularly.

Background technology

The suspension spacing of interior biased non-coaxial pilothouse stabilizer bar system, has material impact to roll angular rigidity.In pilothouse actual design, often adopting under stabilizer bar system and other structural parameters determination situation, by carrying out adjusted design to stabilizer bar suspension spacing, making pilothouse stabilizer bar system reach the designing requirement of roll angular rigidity.But, because interior biased non-coaxial pilothouse stabilizer bar system is a coupling body be made up of rigid body, elastic body and flexible body three, and due to the Rigidity Calculation of rubber bushing very complicated, meanwhile, because of biased in torsion tube, intercoupling of bending and torsion is also had, cause the analysis and designation of pilothouse stabilizer bar system very complicated and difficult, therefore, for the adjusted design of interior biased non-coaxial pilothouse stabilizer bar suspension spacing, fail to provide reliable resolution design method always.At present, both at home and abroad for the design of pilothouse stabilizer bar system, mostly utilize ANSYS simulation software, simulating, verifying is carried out by the characteristic of solid modelling to the pilothouse stabilizer bar system of giving fixed structure, although the method can obtain reliable simulation numerical, but, because ANSYS simulation analysis can only carry out simulating, verifying to the stabilizer bar characteristic of given parameters, accurate analytical design method formula cannot be provided, can not analytical design method be realized, more can not meet the requirement of pilothouse stabilizer bar system CAD software development.Therefore, a kind of method for designing that is accurate, the suspension spacing of interior biased non-coaxial pilothouse stabilizer bar system reliably must be set up, meet the designing requirement of cab mounting and stabilizer bar system roll angular rigidity, under the prerequisite not increasing cost of products, further raising product design level, quality and performance, improve vehicle ride performance and security; Meanwhile, reduce design and testing expenses, accelerate product development speed.

Summary of the invention

For the defect existed in above-mentioned prior art, technical matters to be solved by this invention is to provide a kind of method for designing that is easy, the suspension spacing of interior biased non-coaxial pilothouse stabilizer bar system reliably, and its calculation flow chart as shown in Figure 1; The structural representation of pilothouse stabilizer bar system as shown in Figure 2; The structural representation of rubber bushing as shown in Figure 3; The geometric relationship figure of stabilizer bar system variant and swing arm displacement as shown in Figure 4.

For solving the problems of the technologies described above, the method for designing of the suspension spacing of interior biased non-coaxial pilothouse stabilizer bar system provided by the present invention, is characterized in that adopting following calculation procedure:

(1) the equivalent line stiffness K of biased non-coaxial pilothouse stabilizer bar in _tcalculating:

According to the length L of torsion tube _w, internal diameter d, outer diameter D, interior amount of bias T, elastic modulus E and Poisson ratio μ, and pendulum arm length l ₁, to the equivalent line stiffness K of stabilizer bar at cab mounting installed position _tcalculate, namely

$K_T=\frac{\mathrm{\πE}(D^4-d^4)}{32(1+\mathrm{\μ}){(l_1-T)}^2{L}_W};$

(2) the equivalent combinations Line stiffness K of rubber bushing _xcalculating:

1. rubber bushing radial rigidity k _xcalculating

According to the inner circle radius r of rubber sleeve _a, exradius r _b, length L _x, elastic modulus E _xwith Poisson ratio μ _x, to the radial rigidity k of pilothouse stabilizer bar rubber bushing _xcalculate, namely

$k_x=\frac{1}{u\left(r_b\right)+y\left(r_b\right)};$

Wherein, $u\left(r_b\right)=\frac{1+{\mathrm{\μ}}_x}{2\mathrm{\π}{E}_x{L}_x}(\ln \frac{r_b}{r_a}-\frac{r_b^2-r_a^2}{r_a^2+r_b^2}),$

$y\left(r_b\right)=a_{1}I(0,\mathrm{\α}{r}_b)+a_{2}K(0,\mathrm{\α}{r}_b)+a_3+\frac{1+{\mathrm{\μ}}_x}{5\mathrm{\π}{E}_x{L}_x}(\ln r_b+\frac{r_b^2}{r_a^2+r_b^2}),$

$a_1=\frac{(1+{\mathrm{\μ}}_x)[K(1,\mathrm{\α}{r}_a)r_a(r_a^2+3r_b^2)-K(1,\mathrm{\α}{r}_b)r_b({3r}_a^2+r_b^2)]}{5\mathrm{\π}{E}_x{L}_x\mathrm{\α}{r}_a{r}_b[I(1,\mathrm{\α}{r}_a)K(1,\mathrm{\α}{r}_b)-K(1,\mathrm{\α}{r}_a)I(1,\mathrm{\α}{r}_b)](r_a^2+r_b^2)},$

$a_2=\frac{({\mathrm{\μ}}_x+1)[I(1,\mathrm{\α}{r}_a)r_a(r_a^2+3r_b^2)-I(1,\mathrm{\α}{r}_b)r_b({3r}_a^2+r_b^2)]}{5\mathrm{\π}{E}_x{L}_x\mathrm{\α}{r}_a{r}_b[I(1,\mathrm{\α}{r}_a)K(1,\mathrm{\α}{r}_b)-K(1,\mathrm{\α}{r}_a)I(1,\mathrm{\α}{r}_b)](r_a^2+r_b^2)},$

$a_3=-\frac{(1+{\mathrm{\μ}}_x)(b_1-b_2+b_3)}{5\mathrm{\π}{E}_x{L}_x\mathrm{\α}{r}_a{r}_b[I(1,\mathrm{\α}{r}_a)K(1,\mathrm{\α}{r}_b)-K(1,\mathrm{\α}{r}_a)I(1,\mathrm{\α}{r}_b)](r_a^2+r_b^2)};$

$b_1=[I(1,\mathrm{\α}{r}_a)K(0,\mathrm{\α}{r}_a)+K(1,\mathrm{\α}{r}_a)I(0,\mathrm{\α}{r}_a)]r_a(r_a^2+3r_b^2),$

$b_2=[I(1,\mathrm{\α}{r}_b)K(0,\mathrm{\α}{r}_a)+K(1,\mathrm{\α}{r}_b)I(0,\mathrm{\α}{r}_a)]r_b(r_b^2+3r_a^2),$

$b_3=\mathrm{\α}{r}_a{r}_b[I(1,\mathrm{\α}{r}_a)K(1,\mathrm{\α}{r}_b)-K(1,\mathrm{\α}{r}_a)I(1,\mathrm{\α}{r}_b)][r_a^2+(r_a^2+r_b^2)\ln r_a],$

$\mathrm{\α}=2\sqrt{15}/L_x,$

Bessel correction function I (0, α r _b), K (0, α r _b), I (1, α r _b), K (1, α r _b),

I(1,αr _a)，K(1,αr _a)，I(0,αr _a)，K(0,αr _a)；

2. the loading factor β of rubber bushing is reversed _fcalculating

According to the length L of torsion tube _w, Poisson ratio μ, interior amount of bias T, and pendulum arm length l ₁, to the loading factor β reversing rubber bushing _fcalculate, namely

${\mathrm{\β}}_F=\frac{24(1+\mathrm{\μ})(l_1-T)T}{L_W^2};$

3. the equivalent combinations Line stiffness K of biased non-coaxial stabilizer bar rubber bushing in _xcalculating

According to pendulum arm length l ₁, the interior amount of bias T of torsion tube, 1. calculates the radial rigidity k of the rubber bushing that gained arrives in step _x, and the loading factor β of the torsion rubber bushing 2. calculated in step _f, to the equivalent combinations Line stiffness K of stabilizer bar rubber bushing _xcalculate, namely

$K_X=\frac{k_{X}T}{{\mathrm{\β}}_F{l}_1+(1+{\mathrm{\β}}_F)T};$

(3) the suspension spacing L of biased non-coaxial pilothouse stabilizer bar system in _cdesign:

According to the roll angular rigidity designing requirement value of pilothouse stabilizer bar system utilize the equivalent line stiffness K of the stabilizer bar calculated in step (1) _t, the equivalent combinations Line stiffness K of the rubber bushing calculated in step (2) _x, set up the suspension spacing L of biased non-coaxial pilothouse stabilizer bar system _cdesign mathematic model, and to L _cdesign, namely

(4) the ANSYS simulating, verifying of biased non-coaxial pilothouse stabilizer bar system roll angular rigidity in:

Utilize ANSYS finite element emulation software, according to the suspension spacing L that the structural parameters of stabilizer bar system, material characteristic parameter and design obtain _c, the realistic model of biased non-coaxial pilothouse stabilizer bar system in setting up, grid division, at the suspension installed position imposed load F of swing arm, carries out ANSYS emulation to the distortion of stabilizer bar system, obtains the deformation displacement amount f of swing arm outermost end _a;

The deformation displacement amount f of the swing arm outermost end obtained is emulated according to ANSYS _a, pendulum arm length l ₁, the suspended position of swing arm is to the distance, delta l of outermost end ₁, the suspension distance L of stabilizer bar _c, at the load F that the suspended position place of swing arm applies, and the rubber bushing radial rigidity k calculated in 1. step in step (2) _x, utilize the geometric relationship of stabilizer bar system variant and swing arm displacement, internally biased non-coaxial pilothouse stabilizer bar system roll angular rigidity aNSYS simulating, verifying value, calculate, namely

$f_C=\frac{l_1{f}_A}{l_1+\mathrm{\Δ}{l}_1};$

f _ws＝f _C+F/k _x；

The ANSYS simulating, verifying value of biased non-coaxial pilothouse stabilizer bar system roll angular rigidity in emulation is obtained compare with designing requirement value, thus the method for designing of the suspension spacing of interior biased non-coaxial pilothouse stabilizer bar system provided by the present invention and parameter designing value are verified.

The advantage that the present invention has than prior art

Because interior biased non-coaxial pilothouse stabilizer bar system is a coupling body be made up of rigid body, elastic body and flexible body three, and due to the Rigidity Calculation of rubber bushing very complicated, and because of biased in torsion tube, stabilizer bar system also has intercoupling of flexural deformation and torsional deflection, cause the analysis and designation of pilothouse stabilizer bar system very complicated and difficult, therefore, for the adjusted design of interior biased non-coaxial pilothouse stabilizer bar suspension spacing, fail to provide reliable resolution design method always.At present, both at home and abroad for the design of pilothouse stabilizer bar system, mostly utilize ANSYS simulation software, simulating, verifying is carried out by the characteristic of solid modelling to the pilothouse stabilizer bar system of giving fixed structure, although the method can obtain reliable simulation numerical, but, because ANSYS simulation analysis can only carry out simulating, verifying to the stabilizer bar characteristic of given parameters, accurate analytical design method formula cannot be provided, the requirement of the design of pilothouse stabilizer bar system analysis and art CAD software exploitation can not be met.

The present invention according to the structural parameters of interior biased non-coaxial pilothouse stabilizer bar and rubber bushing and material characteristic parameter, can utilize the roll stiffness of pilothouse stabilizer bar, with the structural parameters of stabilizer bar and suspend spacing L _c, rubber bushing radial rigidity k _xand combination equivalent line stiffness K _xbetween relation, in setting up, the suspension line space design mathematical model of biased non-coaxial stabilizer bar system, designs it.By example design and ANSYS simulating, verifying known, the method can obtain the suspension line space design value of biased non-coaxial pilothouse stabilizer bar system accurately and reliably, for the design of cab mounting and stabilizer bar system, provide suspension line space design method reliably, and establish technical foundation for interior biased non-coaxial pilothouse stabilizer bar system CAD software development.Utilize the method, under the prerequisite not increasing cost of products, design level, the quality and performance of cab mounting and stabilizer bar system can be improved, reduce pilothouse inclination and float and face upward motion, improve ride performance and the security of vehicle; Meanwhile, utilize the method also can reduce design and testing expenses, accelerate product development speed.

In order to understand the present invention better, be described further below in conjunction with accompanying drawing.

Fig. 1 is the design flow diagram of the suspension spacing of interior biased non-coaxial pilothouse stabilizer bar system;

Fig. 2 is the structural representation of interior biased non-coaxial stabilizer bar system;

Fig. 3 is the structural representation of rubber bushing;

Fig. 4 is the geometric relationship figure of interior biased non-coaxial stabilizer bar system variant and swing arm displacement;

Fig. 5 is the roll angular rigidity of the pilothouse stabilizer bar system of embodiment one with suspension spacing L _cchange curve;

Fig. 6 is the deformation simulation checking cloud atlas of the interior biased non-coaxial pilothouse stabilizer bar system of embodiment one;

Fig. 7 is the roll angular rigidity of the pilothouse stabilizer bar system of embodiment two with suspension spacing L _cchange curve;

Fig. 8 is the deformation simulation checking cloud atlas of the interior biased non-coaxial pilothouse stabilizer bar system of embodiment two.

Specific embodiments

Below by embodiment, the present invention is described in further detail.

Embodiment one: in certain, the structure of biased non-coaxial pilothouse stabilizer bar system is symmetrical, as shown in Figure 2, comprising: swing arm 1, suspended rubber lining 2, reverses rubber bushing 3, torsion tube 4; Wherein, torsion tube 4 and torsion rubber bushing 3 disalignment, the interior amount of bias T=30mm of torsion tube 4; Distance L between two swing arms 1 in left and right _c, i.e. the suspension distance of stabilizer bar is parameter to be designed; Suspended rubber lining 2 and the distance reversed between rubber bushing 3, i.e. pendulum arm length l ₁=380mm; The distance, delta l of swing arm suspended position C to outermost end A ₁=47.5mm; The length L of torsion tube 4 _w=1500mm, internal diameter d=35mm, outer diameter D=50mm, elastic modulus E=200GPa, Poisson ratio μ=0.3.The structure and material characteristic of four rubber bushings in left and right is identical, as shown in Figure 3, comprising: interior round buss 5, rubber sleeve 6, outer round buss 7, wherein, and the inner circle diameter d of interior round buss 5 _x=35mm, wall thickness δ=2mm; The length L of rubber sleeve 6 _x=25mm, inner circle radius r _a=19.5mm, exradius r _b=34.5mm, elastic modulus E _x=7.84MPa, Poisson ratio μ _x=0.47.The designing requirement value of the roll angular rigidity of this pilothouse stabilizer bar system is according to the structure and material characterisitic parameter of stabilizer bar and rubber bushing, to the suspension spacing L of this pilothouse stabilizer bar system _ccalculate, and ANSYS simulating, verifying is carried out to the roll angular rigidity in load F=5000N situation.

The method for designing of the suspension spacing of the interior biased non-coaxial pilothouse stabilizer bar system that example of the present invention provides, as shown in Figure 1, specific design step is as follows for its design cycle:

(1) the equivalent line stiffness K of biased non-coaxial pilothouse stabilizer bar in _tcalculating:

According to the length L of torsion tube _w=1500mm, internal diameter d=35mm, outer diameter D=50mm, interior amount of bias T=30mm, elastic modulus E=200GPa and Poisson ratio μ=0.3, and pendulum arm length l ₁=380mm, to the equivalent line stiffness K of stabilizer bar at cab mounting installed position _tcalculate, namely

$K_T=\frac{\mathrm{\πE}(D^4-d^4)}{32(1+\mathrm{\μ}){(l_1-T)}^2{L}_W}=3.90387\×{10}^{5}N/m;$

(2) the equivalent combinations Line stiffness K of rubber bushing _xcalculating:

1. rubber bushing radial rigidity k _xcalculating:

According to the inner circle radius r of rubber sleeve _a=19.5mm, exradius r _b=34.5mm, length L _x=25mm, elastic modulus E _x=7.84MPa and Poisson ratio μ _x=0.47, to the radial rigidity k of this pilothouse stabilizer bar rubber bushing _xcalculate, namely

$k_x=\frac{1}{u\left(r_b\right)+y\left(r_b\right)}=2.1113\×{10}^{6}N/m;$

Wherein, $u\left(r_b\right)=\frac{1+{\mathrm{\μ}}_x}{2\mathrm{\π}{E}_x{L}_x}(\ln \frac{r_b}{r_a}-\frac{r_b^2-r_a^2}{r_a^2+r_b^2})=6.5395\×{10}^{-8}m/N,$

$y\left(r_b\right)=a_{1}I(0,\mathrm{\α}{r}_b)+a_{2}K(0,\mathrm{\α}{r}_b)+a_3+\frac{1+{\mathrm{\μ}}_x}{5\mathrm{\π}{E}_x{L}_x}(\ln r_b+\frac{r_b^2}{r_a^2+r_b^2})=4.0825\×{10}^{-7}m/N,$

$a_1=\frac{(1+{\mathrm{\μ}}_x)[K(1,\mathrm{\α}{r}_a)r_a(r_a^2+3r_b^2)-K(1,\mathrm{\α}{r}_b)r_b({3r}_a^2+r_b^2)]}{5\mathrm{\π}{E}_x{L}_x\mathrm{\α}{r}_a{r}_b[I(1,\mathrm{\α}{r}_a)K(1,\mathrm{\α}{r}_b)-K(1,\mathrm{\α}{r}_a)I(1,\mathrm{\α}{r}_b)](r_a^2+r_b^2)}=-8.4456\×{10}^{-13},$

$a_2=\frac{({\mathrm{\μ}}_x+1)[I(1,\mathrm{\α}{r}_a)r_a(r_a^2+3r_b^2)-I(1,\mathrm{\α}{r}_b)r_b({3r}_a^2+r_b^2)]}{5\mathrm{\π}{E}_x{L}_x\mathrm{\α}{r}_a{r}_b[I(1,\mathrm{\α}{r}_a)K(1,\mathrm{\α}{r}_b)-K(1,\mathrm{\α}{r}_a)I(1,\mathrm{\α}{r}_b)](r_a^2+r_b^2)}=2.932\×{10}^{-11},$

$a_3=-\frac{(1+{\mathrm{\μ}}_x)(b_1-b_2+b_3)}{5\mathrm{\π}{E}_x{L}_x\mathrm{\α}{r}_a{r}_b[I(1,\mathrm{\α}{r}_a)K(1,\mathrm{\α}{r}_b)-K(1,\mathrm{\α}{r}_a)I(1,\mathrm{\α}{r}_b)](r_a^2+r_b^2)}=1.6585\×{10}^{-6};$

$b_1=[I(1,\mathrm{\α}{r}_a)K(0,\mathrm{\α}{r}_a)+K(1,\mathrm{\α}{r}_a)I(0,\mathrm{\α}{r}_a)]r_a(r_a^2+3r_b^2)=1.2752\×{10}^{-5},$

$b_2=[I(1,\mathrm{\α}{r}_b)K(0,\mathrm{\α}{r}_a)+K(1,\mathrm{\α}{r}_b)I(0,\mathrm{\α}{r}_a)]r_b(r_b^2+3r_a^2)=-4.936\×{10}^{-4},$

$b_3=\mathrm{\α}{r}_a{r}_b[I(1,\mathrm{\α}{r}_a)K(1,\mathrm{\α}{r}_b)-K(1,\mathrm{\α}{r}_a)I(1,\mathrm{\α}{r}_b)][r_a^2+(r_a^2+r_b^2)\ln r_a]=0.008,$

$\mathrm{\α}=2\sqrt{15}/L_x=309.8387,$

Bessel correction function I (0, α r _b)=5.4217 × 10 ^-3, K (0, α r _b)=8.6369 × 10 ^-6;

I(1,αr _b)＝5.1615×10 ³，K(1,αr _b)＝9.0322×10 ^-6；

I(1,αr _a)＝63.7756，K(1,αr _a)＝0.0013，

I(0,αr _a)＝69.8524，K(0,αr _a)＝0.0012；

2. the loading factor β of rubber bushing is reversed _fcalculating:

According to the length L of torsion tube _w=1500mm, Poisson ratio μ=0.3, interior amount of bias T=30mm, and pendulum arm length l ₁=380mm, to the loading factor β reversing rubber bushing _fcalculate, namely

${\mathrm{\β}}_F=\frac{24(1+\mathrm{\μ})(l_1-T)T}{L_W^2}=0.1456;$

3. the equivalent combinations Line stiffness K of biased non-coaxial stabilizer bar rubber bushing in _xcalculating

According to pendulum arm length l ₁=380mm, the interior amount of bias T=30mm of torsion tube, 1. calculate the k that gained arrives in step _x=2.1113 × 10 ⁶n/m, and the β 2. calculated in step _f=0.1456, to the equivalent combinations Line stiffness K of stabilizer bar system rubber bushing _xcalculate, namely

$K_X=\frac{k_{X}T}{{\mathrm{\β}}_F{l}_1+(1+{\mathrm{\β}}_F)T}=6.68034\×{10}^{5}N/m;$

(3) the suspension spacing L of biased non-coaxial pilothouse stabilizer bar system in _cdesign:

According to the roll angular rigidity designing requirement value of pilothouse stabilizer bar system utilize the K calculated in step (1) _t=3.90387 × 10 ⁵n/m, the K calculated in step (2) _x=6.68034 × 10 ⁵n/m, sets up the suspension spacing L of biased non-coaxial pilothouse stabilizer bar system _cdesign mathematic model, and to L _cdesign, namely

Wherein, the roll angular rigidity of stabilizer bar system with suspension spacing L _cchange curve, as shown in Figure 5;

(4) the ANSYS simulating, verifying of biased non-coaxial pilothouse stabilizer bar system roll angular rigidity in:

Utilize ANSYS finite element emulation software, according to the suspension spacing L that the structural parameters of stabilizer bar system, material characteristic parameter and design obtain _c=1550mm, sets up realistic model, grid division, and at the suspended position C place imposed load F=5000N of swing arm, ANSYS emulation is carried out to the distortion of stabilizer bar system, the deformation simulation cloud atlas obtained, as shown in Figure 6, wherein, the deformation displacement amount f at swing arm outermost end A place _afor

f _A＝19.811mm；

The deformation displacement amount f at the swing arm outermost end A place obtained is emulated according to ANSYS _a=19.811mm, pendulum arm length l ₁=380mm, the distance, delta l of the suspended position C to outermost end A of swing arm ₁=47.5mm, the suspension spacing L of stabilizer bar _c=1550mm, at the load F=5000N that the suspended position C place of swing arm applies, and the k calculated in 1. step in step (2) _x=2.1113 × 10 ⁶n/m, utilizes the geometric relationship of stabilizer bar system variant and swing arm displacement, as shown in Figure 4, to this interior biased non-coaxial pilothouse stabilizer bar system roll angular rigidity aNSYS simulating, verifying value, calculate, namely

$f_C=\frac{l_1{f}_A}{l_1+\mathrm{\Δ}{l}_1}=17.443\mathrm{mm};$

$f_{\mathrm{ws}}=f_C+\frac{F}{k_x}=19.812\mathrm{mm};$

$K_{\mathrm{ws}}=\frac{F}{f_{\mathrm{ws}}}=2.52374\×{10}^{5}N/m;$

Known: the ANSYS simulating, verifying value of this pilothouse stabilizer bar system roll angular rigidity with designing requirement value match, relative deviation is only 0.510%; Result shows: the method for designing of the suspension spacing of interior biased non-coaxial pilothouse stabilizer bar system provided by the present invention is correct, and parameter designing value is accurately and reliably.

Embodiment two: the biased version of non-coaxial pilothouse stabilizer bar system and the identical of embodiment one in certain, as shown in Figure 2, torsion tube 4 and torsion rubber bushing 3 disalignment, the interior amount of bias T=30mm of torsion tube 4; Distance L between two swing arms 1 in left and right _c, i.e. the suspension distance of stabilizer bar is parameter to be designed; Suspended rubber lining 2 and the distance reversed between rubber bushing 3, i.e. pendulum arm length l ₁=350mm; The distance, delta l of the suspended position C to swing arm outermost end A of swing arm ₁=52.5mm; The length L of torsion tube 4 _w=1000mm, internal diameter d=42mm, outer diameter D=50mm; The structure of four rubber bushings in left and right is all identical, as shown in Figure 3, wherein, and the inner circle diameter d of interior round buss 5 _x=35mm, wall thickness δ=5mm; The length L of rubber sleeve 6 _x=40mm, inner circle radius r _a=22.5mm, exradius r _b=37.5mm.The material behavior of stabilizer bar and the material behavior of rubber bushing, identical with embodiment one, the i.e. elastic modulus E=200GPa of torsion tube, Poisson ratio μ=0.3; The elastic modulus E of rubber sleeve _x=7.84MPa, Poisson ratio μ _x=0.47.The roll angular rigidity designing requirement value of this pilothouse stabilizer bar system is to the suspension spacing L of this interior biased non-coaxial pilothouse stabilizer bar system _cdesign, and ANSYS simulating, verifying is carried out to the roll angular rigidity under load F=5000N.

Adopt the step identical with embodiment one, the suspension spacing of this interior biased non-coaxial pilothouse stabilizer bar system is designed, that is:

(1) the equivalent line stiffness K of biased non-coaxial pilothouse stabilizer bar in _tcalculating:

According to the length L of torsion tube _w=1400mm, internal diameter d=42mm, outer diameter D=50mm, elastic modulus E=200GPa and Poisson ratio μ=0.3, interior amount of bias T=30mm, and pendulum arm length l ₁=350mm, to the equivalent line stiffness K of stabilizer bar at cab mounting installed position _tcalculate, namely

$K_T=\frac{\mathrm{\πE}(D^4-d^4)}{32(1+\mathrm{\μ}){(l_1-T)}^2{L}_W}=4.6289\×{10}^{5}N/m;$

(2) the equivalent combinations Line stiffness K of rubber bushing _xcalculating:

1. rubber bushing radial rigidity k _xcalculating

According to the inner circle radius r of rubber sleeve _a=22.5mm, exradius r _b=37.5mm, axial length L _x=40mm, elastic modulus E _x=7.84MPa and Poisson ratio μ _x=0.47, to the radial rigidity K of this pilothouse stabilizer bar rubber bushing _xcalculate, namely

$k_x=\frac{1}{u\left(r_b\right)+y\left(r_b\right)}=4.2085\×{10}^{6}N/m;$

Wherein, $u\left(r_b\right)=\frac{1+{\mathrm{\μ}}_x}{2\mathrm{\π}{E}_x{L}_x}(\ln \frac{r_b}{r_a}-\frac{r_b^2-r_a^2}{r_a^2+r_b^2})=3.0019\×{10}^{-8}m/N,$

$y\left(r_b\right)=a_{1}I(0,\mathrm{\α}{r}_b)+a_{2}K(0,\mathrm{\α}{r}_b)+a_3+\frac{1+{\mathrm{\μ}}_x}{5\mathrm{\π}{E}_x{L}_x}(\ln r_b+\frac{r_b^2}{r_a^2+r_b^2})=2.076\×{10}^{-7}m/N,$

$a_1=\frac{(1+{\mathrm{\μ}}_x)[K(1,\mathrm{\α}{r}_a)r_a(r_a^2+3r_b^2)-K(1,\mathrm{\α}{r}_b)r_b({3r}_a^2+r_b^2)]}{5\mathrm{\π}{E}_x{L}_x\mathrm{\α}{r}_a{r}_b[I(1,\mathrm{\α}{r}_a)K(1,\mathrm{\α}{r}_b)-K(1,\mathrm{\α}{r}_a)I(1,\mathrm{\α}{r}_b)](r_a^2+r_b^2)}=-2.0137\×{10}^{-11},$

$a_2=\frac{({\mathrm{\μ}}_x+1)[I(1,\mathrm{\α}{r}_a)r_a(r_a^2+3r_b^2)-I(1,\mathrm{\α}{r}_b)r_b({3r}_a^2+r_b^2)]}{5\mathrm{\π}{E}_x{L}_x\mathrm{\α}{r}_a{r}_b[I(1,\mathrm{\α}{r}_a)K(1,\mathrm{\α}{r}_b)-K(1,\mathrm{\α}{r}_a)I(1,\mathrm{\α}{r}_b)](r_a^2+r_b^2)}=2.3957\×{10}^{-12},$

$a_3=-\frac{(1+{\mathrm{\μ}}_x)(b_1-b_2+b_3)}{5\mathrm{\π}{E}_x{L}_x\mathrm{\α}{r}_a{r}_b[I(1,\mathrm{\α}{r}_a)K(1,\mathrm{\α}{r}_b)-K(1,\mathrm{\α}{r}_a)I(1,\mathrm{\α}{r}_b)](r_a^2+r_b^2)}=9.7232\×{10}^{-7};$

$b_1=[I(1,\mathrm{\α}{r}_a)K(0,\mathrm{\α}{r}_a)+K(1,\mathrm{\α}{r}_a)I(0,\mathrm{\α}{r}_a)]r_a(r_a^2+3r_b^2)=2.44\×{10}^{-5},$

$b_2=[I(1,\mathrm{\α}{r}_b)K(0,\mathrm{\α}{r}_a)+K(1,\mathrm{\α}{r}_b)I(0,\mathrm{\α}{r}_a)]r_b(r_b^2+3r_a^2)=-1.6465\×{10}^{-4},$

$b_3=\mathrm{\α}{r}_a{r}_b[I(1,\mathrm{\α}{r}_a)K(1,\mathrm{\α}{r}_b)-K(1,\mathrm{\α}{r}_a)I(1,\mathrm{\α}{r}_b)][r_a^2+(r_a^2+r_b^2)\ln r_a]=0.0018,$

$\mathrm{\α}=2\sqrt{15}/L_x=193.6492,$

Bessel correction function I (0, α r _b)=214.9082, K (0, α r _b)=3.2117 × 10 ^-4;

I(1,αr _b)＝199.5091，K(1,αr _b)＝3.4261×10 ^-4；

I(1,αr _a)＝13.5072，K(1,αr _a)＝0.0083，

I(0,αr _a)＝15.4196，K(0,αr _a)＝0.0075；

2. the loading factor β of rubber bushing is reversed _fcalculating

According to the length L of torsion tube _w=1000mm, Poisson ratio μ=0.3, interior amount of bias T=30mm, and pendulum arm length l ₁=350mm, to the loading factor β reversing rubber bushing _fcalculate, namely

${\mathrm{\β}}_F=\frac{24(1+\mathrm{\μ})(l_1-T)T}{L_W^2}=0.2995;$

3. the equivalent combinations Line stiffness K of biased non-coaxial stabilizer bar rubber bushing in _xcalculating

According to pendulum arm length l ₁=350mm, the interior amount of bias T=30mm of torsion tube, 1. calculate the k that gained arrives in step _x=4.2085 × 10 ⁶n/m, and the β 2. calculated in step _f=0.2995, to the equivalent combinations Line stiffness K of stabilizer bar system rubber bushing _xcalculate, namely

$K_X=\frac{k_{X}T}{{\mathrm{\β}}_F{l}_1+(1+{\mathrm{\β}}_F)T}=8.7787\×{10}^{5}N/m;$

(3) the suspension spacing L of biased non-coaxial pilothouse stabilizer bar system in _cdesign:

According to the roll angular rigidity designing requirement value of pilothouse stabilizer bar system utilize the K calculated in step (1) _t=4.6289 × 10 ⁵n/m, the K calculated in step (2) _x=8.7787 × 10 ⁵n/m, sets up the suspension spacing L of biased non-coaxial pilothouse stabilizer bar system _cdesign mathematic model, and to L _cdesign, namely

Wherein, the roll angular rigidity of this stabilizer bar system with suspension spacing L _cchange curve, as shown in Figure 7;

(4) the ANSYS simulating, verifying of biased non-coaxial pilothouse stabilizer bar system roll angular rigidity in:

Utilize ANSYS finite element emulation software, according to the suspension spacing L that the structural parameters of stabilizer bar system, material characteristic parameter and design obtain _c=1000mm, sets up realistic model, grid division, and at the suspended position C place imposed load F=5000N of swing arm, ANSYS emulation is carried out to the distortion of stabilizer bar system, the deformation simulation cloud atlas obtained, as shown in Figure 8, wherein, the deformation displacement amount f at swing arm outermost end A place _afor

f _A＝17.637mm；

The deformation displacement amount f at the swing arm outermost end A place obtained is emulated according to ANSYS _a=16.377mm, pendulum arm length l ₁=350mm, the distance, delta l of the suspended position C to outermost end A of swing arm ₁=52.5mm, the suspension spacing L of stabilizer bar _c=1000mm, at the load F=5000N that the suspended position C place of swing arm applies, and the k calculated in 1. step in step (2) _x=4.2085 × 10 ⁶n/m, utilizes the geometric relationship of stabilizer bar system variant and swing arm displacement, as shown in Figure 4, to this interior biased non-coaxial pilothouse stabilizer bar system roll angular rigidity aNSYS simulating, verifying value, calculate, namely

$f_C=\frac{l_1{f}_A}{l_1+\mathrm{\Δ}{l}_1}=15.15\mathrm{mm};$

$f_{\mathrm{ws}}=f_C+\frac{F}{k_x}=16.5246\mathrm{mm};$

$K_{\mathrm{ws}}=\frac{F}{f_{\mathrm{ws}}}=3.02579\×{10}^{5}N/m;$

Known: the ANSYS simulating, verifying value of the roll angular rigidity of this non-coaxial pilothouse stabilizer bar system with designing requirement value match, relative deviation is only 0.2097%; Result shows: the method for designing of the suspension spacing of interior biased non-coaxial pilothouse stabilizer bar system provided by the present invention is correct, and parameter designing value is accurately and reliably.

Claims (1)

1. the method for designing of the suspension spacing of biased non-coaxial pilothouse stabilizer bar system in, its specific design step is as follows:

(1) the equivalent line stiffness K of biased non-coaxial pilothouse stabilizer bar in _tcalculating:

According to the length L of torsion tube _w, internal diameter d, outer diameter D, interior amount of bias T, elastic modulus E and Poisson ratio μ, and pendulum arm length l ₁, to the equivalent line stiffness K of stabilizer bar at cab mounting installed position _tcalculate, namely

$K_T=\frac{\mathrm{\πE}(D^4-d^4)}{32(1+\mathrm{\μ}){(l_1-T)}^2{L}_W};$

(2) the equivalent combinations Line stiffness K of rubber bushing _xcalculating:

1. rubber bushing radial rigidity k _xcalculating

According to the inner circle radius r of rubber sleeve _a, exradius r _b, length L _x, elastic modulus E _xwith Poisson ratio μ _x, to the radial rigidity k of pilothouse stabilizer bar rubber bushing _xcalculate, namely

$k_x=\frac{1}{u\left(r_b\right)+y\left(r_b\right)};$

Wherein, $u\left(r_b\right)=\frac{1+{\mathrm{\μ}}_x}{2\mathrm{\π}{E}_x{L}_x}(1n\frac{r_b}{r_a}-\frac{r_b^2-r_a^2}{r_a^2+r_b^2}),$

$y\left(r_b\right)=a_{1}I(0,{\mathrm{\αr}}_b)+a_{2}K(0,{\mathrm{\αr}}_b)+a_3+\frac{1+{\mathrm{\μ}}_x}{5\mathrm{\π}{E}_x{L}_x}(1n{r}_b+\frac{r_b^2}{r_a^2+r_b^2}),$

$a_1=\frac{(1+{\mathrm{\μ}}_x)[K(1,{\mathrm{\αr}}_a)r_a(r_a^2+{3r}_b^2)-K(1,{\mathrm{\αr}}_b)r_b({3r}_a^2+r_b^2)]}{5\mathrm{\π}{E}_x{L}_x{\mathrm{\αr}}_a{r}_b[I(1,{\mathrm{\αr}}_a)K(1,{\mathrm{\αr}}_b)-K(1,{\mathrm{\αr}}_a)I(1,{\mathrm{\αr}}_b)](r_a^2+r_b^2)},$

$a_2=\frac{({\mathrm{\μ}}_x+1)[I(1,{\mathrm{\αr}}_a)r_a(r_a^2+{3r}_b^2)-I(1,{\mathrm{\αr}}_b)r_b({3r}_a^2+r_b^2)]}{5\mathrm{\π}{E}_x{L}_x{\mathrm{\αr}}_a{r}_b[I(1,{\mathrm{\αr}}_a)K(1,{\mathrm{\αr}}_b)-K(1,{\mathrm{\αr}}_a)I(1,{\mathrm{\αr}}_b)](r_a^2+r_b^2)},$

$a_3=\frac{(1+{\mathrm{\μ}}_x)(b_1-b_2+b_3)}{5\mathrm{\π}{E}_x{L}_x{\mathrm{\αr}}_a{r}_b[I(1,{\mathrm{\αr}}_a)K(1,{\mathrm{\αr}}_b)-K(1,{\mathrm{\αr}}_a)I(1,{\mathrm{\αr}}_b)](r_a^2+r_b^2)};$

$b_1=[I(1,{\mathrm{\αr}}_a)K(0,{\mathrm{\αr}}_a)+K(1,{\mathrm{\αr}}_a)I(0,{\mathrm{\αr}}_a)]r_a(r_a^2+{3r}_b^2),$

$b_2=[I(1,{\mathrm{\αr}}_b)K(0,{\mathrm{\αr}}_a)+K(1,{\mathrm{\αr}}_b)I(0,{\mathrm{\αr}}_a)]r_b(r_b^2+{3r}_a^2),$

$b_3={\mathrm{\αr}}_a{r}_b[I(1,{\mathrm{\αr}}_a)K(1,{\mathrm{\αr}}_b)-K(1,{\mathrm{\αr}}_a)I(1,{\mathrm{\αr}}_b)][r_a^2+(r_a^2+r_b^2)1n{r}_a],$

$\mathrm{\α}=2\sqrt{15}/L_x,$

Bessel correction function I (0, α r _b), K (0, α r _b), I (1, α r _b), K (1, α r _b), I (1, α r _a), K (1, α r _a), I (0, α r _a), K (0, α r _a);

2. the loading factor β of rubber bushing is reversed _fcalculating

According to the length L of torsion tube _w, Poisson ratio μ, interior amount of bias T, and pendulum arm length l ₁, to the loading factor β reversing rubber bushing _fcalculate, namely

${\mathrm{\β}}_F=\frac{24(1+\mathrm{\μ})(l_1-T)T}{L_W^2};$

3. the equivalent combinations Line stiffness K of biased non-coaxial stabilizer bar rubber bushing in _xcalculating

According to the pendulum arm length l of stabilizer bar ₁, the interior amount of bias T of torsion tube, 1. calculates the radial rigidity k of the rubber bushing that gained arrives in step _x, and the loading factor β of the torsion rubber bushing 2. calculated in step _f, to the equivalent combinations Line stiffness K of stabilizer bar rubber bushing _xcalculate, namely

$K_X=\frac{k_{X}T}{{\mathrm{\β}}_F{l}_1+(1+{\mathrm{\β}}_F)T};$

(3) the suspension spacing L of biased non-coaxial pilothouse stabilizer bar system in _cdesign:

According to the roll angular rigidity designing requirement value of pilothouse stabilizer bar system utilize the equivalent line stiffness K of the stabilizer bar calculated in step (1) _t, the equivalent combinations Line stiffness K of the rubber bushing calculated in step (2) _x, set up the suspension spacing L of biased non-coaxial pilothouse stabilizer bar system _cdesign mathematic model, and to L _cdesign, namely

(4) the ANSYS simulating, verifying of biased non-coaxial pilothouse stabilizer bar system roll angular rigidity in:

Utilize ANSYS finite element emulation software, according to the suspension spacing L that the structural parameters of stabilizer bar system, material characteristic parameter and design obtain _c, the realistic model of biased non-coaxial pilothouse stabilizer bar system in setting up, grid division, at the suspension installed position imposed load F of swing arm, carries out ANSYS emulation to the distortion of stabilizer bar system, obtains the deformation displacement amount f of swing arm outermost end _a;

The deformation displacement amount f of the swing arm outermost end obtained is emulated according to ANSYS _a, pendulum arm length l ₁, the suspended position of swing arm is to the distance, delta l of outermost end ₁, the suspension distance L of stabilizer bar _c, at the load F that the suspended position place of swing arm applies, and the rubber bushing radial rigidity k calculated in 1. step in step (2) _x, utilize the geometric relationship of stabilizer bar system variant and swing arm displacement, internally biased non-coaxial pilothouse stabilizer bar system roll angular rigidity aNSYS simulating, verifying value, calculate, namely

$f_C=\frac{l_1{f}_A}{l_1+{\mathrm{\Δl}}_1};$

$f_{\mathrm{ws}}=f_C+F/k_x;$

The ANSYS simulating, verifying value of biased non-coaxial pilothouse stabilizer bar system roll angular rigidity in emulation is obtained compare with designing requirement value, thus the method for designing of the suspension spacing of interior biased non-coaxial pilothouse stabilizer bar system provided by the present invention and parameter designing value are verified.