CN104331578A

CN104331578A - Method for designing length of rubber sleeve of external biasing non-coaxial cab stabilizer bar

Info

Publication number: CN104331578A
Application number: CN201410665583.XA
Authority: CN
Inventors: 周长城; 周超
Original assignee: Shandong University of Technology
Current assignee: Shandong University of Technology
Priority date: 2014-11-19
Filing date: 2014-11-19
Publication date: 2015-02-04
Anticipated expiration: 2034-11-19
Also published as: CN104331578B

Abstract

The invention relates to a design method for the length of a rubber sleeve of an external offset non-coaxial cab stabilizer bar, and belongs to the technical field of cab suspension. According to the structure and material characteristic parameters of the cab stabilizer bar system, the present invention utilizes the required value of roll angle stiffness design and the length of the swing arm of the stabilizer bar, the equivalent line stiffness of the torsion tube, the load coefficient of the torsion rubber bushing, the radial stiffness and Based on the relationship between the equivalent combination line stiffness, a mathematical model for the design of the length of the rubber sleeve of the outer offset non-coaxial cab stabilizer bar is established, and the Matlab program is used to solve the design. Through the design example and simulation verification, it can be seen that the method can obtain accurate and reliable design value of the length of the rubber sleeve, which lays a reliable technical foundation for the design of the cab stabilizer bar system and the development of CAD software. Using this method can not only improve the design level and quality of the stabilizer bar system in the cab, improve the ride comfort and safety of the vehicle, but also reduce the design and test costs.

Description

Design method of rubber sleeve length for externally offset non-coaxial cab stabilizer bar

技术领域technical field

本发明涉及车辆驾驶室悬置，特别是外偏置非同轴式驾驶室稳定杆橡胶套长度的设计方法。The invention relates to a vehicle cab suspension, in particular to a design method for the length of a rubber sleeve of an external offset non-coaxial cab stabilizer bar.

背景技术Background technique

在驾驶室实际设计中，经常在保持稳定杆其他结构参数不变的情况下，采用通过调整橡胶套长度，使驾驶室稳定杆系统达到侧倾角刚度的设计要求。对于外偏置非同轴式驾驶室稳定杆系统，尽管只由摆臂、扭管和橡胶衬套所组成，但却是一个由刚体、弹性体及柔性体三者组成的耦合体，而且因扭管外偏置还存在扭转和弯曲的耦合，同时，由于橡胶衬套的刚度计算非常复杂，因此，对于外偏置非同轴式驾驶室稳定杆橡胶套长度的调整设计，一直未能给出可靠的解析设计方法。目前，国内外对于驾驶室稳定杆系统的设计，大都是利用ANSYS仿真软件，通过实体建模对给定结构的驾驶室稳定杆系统的特性进行仿真验证，尽管该方法可得到比较可靠的仿真数值，然而，由于ANSYS仿真分析只能对给定参数的稳定杆特性进行仿真验证，无法提供精确的解析设计式，不能满足解析设计及CAD设计软件开发的要求。因此，必须建立一种精确、可靠的外偏置非同轴式驾驶室稳定杆橡胶套长度的设计方法，在不增加产品成本的前提下，仅通过对橡胶套长度的调整设计，使稳定杆系统侧倾角刚度满足驾驶室悬置的设计要求，提高产品设计水平和质量，提高车辆行驶平顺性和安全性；同时，降低设计及试验费用，加快产品开发速度。In the actual design of the cab, it is often used to adjust the length of the rubber sleeve to make the cab stabilizer bar system meet the design requirements of the roll angle stiffness while keeping other structural parameters of the stabilizer bar unchanged. For the external offset non-coaxial cab stabilizer bar system, although it is only composed of swing arm, torsion tube and rubber bushing, it is a coupling body composed of rigid body, elastic body and flexible body. There is also torsion and bending coupling in the external offset of the torsion tube. At the same time, because the calculation of the stiffness of the rubber bush is very complicated, the adjustment design for the length of the rubber sleeve of the external offset non-coaxial cab stabilizer bar has not been given. A reliable analytical design method is developed. At present, most of the design of cab stabilizer bar system at home and abroad is to use ANSYS simulation software to simulate and verify the characteristics of the cab stabilizer bar system with a given structure through solid modeling, although this method can obtain relatively reliable simulation values However, because ANSYS simulation analysis can only simulate and verify the characteristics of the stabilizer bar with given parameters, it cannot provide accurate analytical design formulas, and cannot meet the requirements of analytical design and CAD design software development. Therefore, it is necessary to establish an accurate and reliable design method for the length of the rubber sleeve of the external offset non-coaxial cab stabilizer bar. On the premise of not increasing the product cost, only by adjusting the length of the rubber sleeve The roll angle stiffness of the system meets the design requirements of the cab suspension, improves product design level and quality, improves vehicle ride comfort and safety; at the same time, reduces design and test costs, and speeds up product development.

发明内容Contents of the invention

针对上述现有技术中存在的缺陷，本发明所要解决的技术问题是提供一种简便、可靠的外偏置非同轴式驾驶室稳定杆橡胶套长度的设计方法，其设计流程图如图1所示；外偏置非同轴式驾驶室稳定杆系统的结构示意图如图2所示；稳定杆橡胶衬套的结构示意图如图3所示；稳定杆系统变形及摆臂位移的几何关系图如图4所示。In view of the above-mentioned defects in the prior art, the technical problem to be solved by the present invention is to provide a simple and reliable method for designing the length of the rubber sleeve of the external offset non-coaxial cab stabilizer bar. The design flow chart is shown in Figure 1 Fig. 2 shows the structural diagram of the external offset non-coaxial cab stabilizer bar system; Fig. 3 shows the structural diagram of the rubber bushing of the stabilizer bar; the geometric relationship diagram of the deformation of the stabilizer bar system and the displacement of the swing arm As shown in Figure 4.

为解决上述技术问题，本发明所提供的外偏置非同轴式驾驶室稳定杆橡胶套长度的设计方法，其特征在于采用以下设计步骤：In order to solve the above-mentioned technical problems, the design method of the length of the rubber sleeve of the external offset non-coaxial cab stabilizer bar provided by the present invention is characterized in that the following design steps are adopted:

(1)驾驶室稳定杆系统的侧倾线刚度K_ws设计要求值的计算：(1) Calculation of the design requirement value _of the roll line stiffness Kws of the cab stabilizer bar system:

根据驾驶室稳定杆系统的侧倾角刚度设计要求值稳定杆的悬置距离L_c，对驾驶室稳定杆系统的侧倾线刚度K_ws设计要求值进行计算，即According to the required value of the roll angle stiffness design of the cab stabilizer bar system The suspension distance L _c of the stabilizer bar is calculated from the design requirement value of the roll line stiffness K _ws of the cab stabilizer bar system, namely

(2)外偏置非同轴式驾驶室扭管的等效线刚度表达式K_T的建立：(2) The establishment of the equivalent linear stiffness expression K _T of the torsion tube of the external offset non-coaxial cab:

根据扭管长度L_w，内径d，外径D，外偏置量T，弹性模量E和泊松比μ，及摆臂长度l₁，对稳定杆的扭管在驾驶室悬置安装位置处的等效线刚度K_T进行计算，即According to the torsion tube length L _w , inner diameter d, outer diameter D, outer offset T, elastic modulus E and Poisson's ratio μ, and swing arm length l ₁ , the torsion tube for the stabilizer bar is at the installation position of the cab suspension The equivalent line stiffness K _T is calculated, that is

${K K}_{T T} = = \frac{πE πE (({D D.}^{44} - - {d d}^{44}))}{3232 ((11 + + μ μ)) {(({l l}_{11} + + T T))}^{22} {L L}_{W W}};;$

(3)外偏置非同轴式稳定杆橡胶衬套的等效组合线刚度表达式K_x(L_x)的建立：(3) Establishment of the equivalent combination linear stiffness expression K _x (L _x ) of the rubber bushing of the external offset non-coaxial stabilizer bar:

①建立橡胶衬套的径向刚度表达式k_x(L_x)① Establish the radial stiffness expression k _x (L _x ) of the rubber bushing

根据橡胶套的内圆半径r_a，外圆半径r_b，弹性模量E_x和泊松比μ_x，以橡胶套长度L_x为待设计参变量，建立橡胶衬套的径向刚度表达式k_x(L_x)，即According to the inner circle radius r _a , outer circle radius r _b , elastic modulus E _x and Poisson's ratio μ _x of the rubber bushing, and the length L _x of the rubber bushing as the parameter to be designed, the radial stiffness expression k of the rubber bushing is established _x (L _x ), that is

${k k}_{x x} (({L L}_{x x})) = = \frac{11}{u u (({L L}_{x x})) + + y the y (({L L}_{x x}))};;$

其中， $u (L_{x}) = (\ln \frac{r_{b}}{r_{a}} - \frac{r_{b}^{2} - r_{a}^{2}}{r_{a}^{2} + r_{b}^{2}}) \frac{1 + μ_{x}}{2 π E_{x}} L_{x},$ in, $u (L_{x}) = (\ln \frac{r_{b}}{r_{a}} - \frac{r_{b}^{2} - r_{a}^{2}}{r_{a}^{2} + r_{b}^{2}}) \frac{1 + μ_{x}}{2 π {E.}_{x}} L_{x},$

$y the y (({L L}_{x x})) = = {a a}_{11} I I ((00,, α α {r r}_{b b})) + + {a a}_{22} K K ((00,, α α {r r}_{b b})) + + {a a}_{33} + + \frac{11 + + {μ μ}_{x x}}{55 π π {E E.}_{x x} {L L}_{x x}} ((ln ln {r r}_{b b} + + \frac{{r r}_{b b}^{22}}{{r r}_{a a}^{22} + + {r r}_{b b}^{22}})),,$

${a a}_{11} = = \frac{((11 + + {μ μ}_{x x})) [[K K ((11,, α α {r r}_{a a})) {r r}_{a a} (({r r}_{a a}^{22} + + 33 {r r}_{b b}^{22})) - - K K ((11,, α α {r r}_{b b})) {r r}_{b b} ((33 {r r}_{a a}^{22} + + {r r}_{b b}^{22}))]]}{55 π π {E E.}_{x x} {L L}_{x x} α α {r r}_{a a} {r r}_{b b} [[I I ((11,, α α {r r}_{a a})) K K ((11,, α α {r r}_{b b})) - - K K ((11,, α α {r r}_{a a})) I I ((11,, α α {r r}_{b b}))]] (({r r}_{a a}^{22} + + {r r}_{b b}^{22}))},,$

${a a}_{22} = = \frac{(({μ μ}_{x x} + + 11)) [[I I ((11,, α α {r r}_{a a})) {r r}_{a a} (({r r}_{a a}^{22} + + 33 {r r}_{b b}^{22})) - - I I ((11,, α α {r r}_{b b})) {r r}_{b b} ((33 {r r}_{a a}^{22} + + {r r}_{b b}^{22}))]]}{55 π π {E E.}_{x x} {L L}_{x x} α α {r r}_{a a} {r r}_{b b} [[I I ((11,, α α {r r}_{a a})) K K ((11,, α α {r r}_{b b})) - - K K ((11,, α α {r r}_{a a})) I I ((11,, α α {r r}_{b b}))]] (({r r}_{a a}^{22} + + {r r}_{b b}^{22}))},,$

${a a}_{33} = = \frac{((11 + + {μ μ}_{x x})) (({b b}_{11} - - {b b}_{22} + + {b b}_{33}))}{55 π π {E E.}_{x x} {L L}_{x x} α α {r r}_{a a} {r r}_{b b} [[I I ((11,, α α {r r}_{a a})) K K ((11,, α α {r r}_{b b})) - - K K ((11,, α α {r r}_{a a})) I I ((11,, α α {r r}_{b b}))]] (({r r}_{a a}^{22} + + {r r}_{b b}^{22}))},,$

${b b}_{11} = = [[I I ((11,, α α {r r}_{a a})) K K ((00,, α α {r r}_{a a})) + + K K ((11,, α α {r r}_{a a})) I I ((00,, α α {r r}_{a a}))]] {r r}_{a a} (({r r}_{a a}^{22} + + 33 {r r}_{b b}^{22})),,$

${b b}_{22} = = [[I I ((11,, α α {r r}_{b b})) K K ((00,, α α {r r}_{a a})) + + K K ((11,, α α {r r}_{b b})) I I ((00,, α α {r r}_{a a}))]] {r r}_{b b} (({r r}_{b b}^{22} + + 33 {r r}_{a a}^{22})),,$

${b b}_{33} = = α α {r r}_{a a} {r r}_{b b} [[I I ((11,, α α {r r}_{a a})) K K ((11,, α α {r r}_{b b})) - - K K ((11,, α α {r r}_{a a})) I I ((11,, α α {r r}_{b b}))]] [[{r r}_{a a}^{22} + + (({r r}_{a a}^{22} + + {r r}_{b b}^{22})) ln ln {r r}_{a a}]],,$

$α α = = 22 \sqrt{1515} / / {L L}_{x x},,$

Bessel修正函数I(0,αr_b)，K(0,αr_b)，I(1,αr_b)，K(1,αr_b)，Bessel correction function I(0,αr _b ), K(0,αr _b ), I(1,αr _b ), K(1,αr _b ),

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

②计算外偏置非同轴式稳定杆系统的扭转橡胶衬套的载荷系数η_F ② Calculation of the load factor η _F of the torsional rubber bushing of the external offset non-coaxial stabilizer bar system

根据扭管长度L_W，泊松比μ，外偏置量T，及摆臂长度l₁，对扭转橡胶衬套的载荷系数η_F进行计算，即According to the length L _W of the torsion tube, Poisson's ratio μ, the external offset T, and the length l ₁ of the swing arm, the load factor η _F of the torsion rubber bushing is calculated, namely

${η η}_{F f} = = \frac{24 twenty four ((11 + + μ μ)) {l l}_{11} T T}{{L L}_{W W}^{22}};;$

③外偏置非同轴式稳定杆橡胶衬套的等效组合线刚度表达式K_x(L_x)的建立③Establishment of the equivalent combined linear stiffness expression K _x (L _x ) of the rubber bushing of the external offset non-coaxial stabilizer bar

根据①步骤中所建立的橡胶衬套的径向刚度表达式k_x(L_x)，及②步骤中计算得到的扭转橡胶衬套的载荷系数η_F，建立外偏置非同轴式稳定杆橡胶衬套的等效组合线刚度表达式K_x(L_x)，即According to the radial stiffness expression k _x (L _x ) of the rubber bush established in step ①, and the load factor η _F of the torsional rubber bush calculated in step ②, an externally offset non-coaxial stabilizer bar is established The equivalent combination line stiffness expression K _x (L _x ) of the rubber bushing, namely

${K K}_{X x} (({L L}_{x x})) = = \frac{{k k}_{x x} (({L L}_{x x}))}{11 + + {η η}_{F f}};;$

(4)外偏置非同轴式驾驶室稳定杆的橡胶套长度L_x设计数学模型的建立及设计：(4) Establishment and design of the rubber sleeve length L _x design mathematical model of the external offset non-coaxial cab stabilizer bar:

根据步骤(1)中计算得到的驾驶室稳定杆系统的侧倾线刚度的设计要求值K_ws，步骤(2)中计算得到的扭管的等效线刚度K_T，及步骤(3)中的③步骤所建立的橡胶衬套的等效组合线刚度表达式K_x(L_x)，建立外偏置非同轴式驾驶室稳定杆的橡胶套长度L_x的设计数学模型，即According to the required design value K _ws of the roll line stiffness of the cab stabilizer bar system calculated in step (1), the equivalent line stiffness K _T of the torsion tube calculated in step (2), and the The equivalent combination linear stiffness expression K _x (L _x ) of the rubber bush established in step ③, establishes the design mathematical model of the length L _x of the rubber bush of the external offset non-coaxial cab stabilizer bar, namely

K_TK_X(L_x)-K_wsK_X(L_x)-K_wsK_T＝0；K _T K _X (L _x )-K _ws K _X (L _x )-K _ws K _T = 0;

利用Matlab程序，求解上述关于L_x的方程，便可得到外偏置非同轴式驾驶室稳定杆橡胶套长度L_x的设计值；Using the Matlab program to solve the above equation about L _x , the design value of the rubber sleeve length L _x of the external offset non-coaxial cab stabilizer bar can be obtained;

(5)外偏置非同轴式驾驶室稳定杆系统侧倾角刚度的ANSYS仿真验证：(5) ANSYS simulation verification of the roll angle stiffness of the external offset non-coaxial cab stabilizer bar system:

I利用ANSYS有限元仿真软件，根据橡胶套长度L_x的设计值，及外偏置非同轴式驾驶室稳定杆系统的其他结构参数和材料特性参数，建立ANSYS仿真模型，划分网格，并在摆臂的悬置安装位置处施加载荷F，对稳定杆系统的变形进行ANSYS仿真，得到外偏置非同轴式稳定杆系统在摆臂最外端的变形位移量f_A；I use ANSYS finite element simulation software, according to the design value of the rubber sleeve length L _x , and other structural parameters and material property parameters of the external offset non-coaxial cab stabilizer bar system, establish an ANSYS simulation model, divide the grid, and Apply a load F at the suspension installation position of the swing arm, carry out ANSYS simulation on the deformation of the stabilizer bar system, and obtain the deformation displacement f _A of the external offset non-coaxial stabilizer bar system at the outermost end of the swing arm;

II根据所设计的橡胶套长度L_x，橡胶衬套的其他结构及材料特性参数，利用步骤(3)中的①步骤所建立的橡胶衬套径向刚度表达式k_x(L_x)，求得所设计橡胶衬套的径向刚度k_x；II According to the designed rubber bushing length L _x , other structural and material characteristic parameters of the rubber bushing, using the rubber bushing radial stiffness expression k _x (L _x ) established in step ① of step (3), find Obtain the radial stiffness k _x of the designed rubber bushing;

III根据ANSYS仿真所得到的摆臂最外端的最大变形位移量f_A，摆臂长度l₁，摆臂的悬置安装位置到最外端的距离Δl₁，稳定杆的悬置距离L_c，在臂的悬置安装位置处施加的载荷F，及II步骤中计算得到的橡胶衬套的径向刚度k_x，利用稳定杆系统变形及摆臂位移的几何关系，对所设计的外偏置非同轴式驾驶室稳定杆系统侧倾角刚度的ANSYS仿真验证值，进行计算，即III According to the maximum deformation displacement f _A of the outermost end of the swing arm obtained by ANSYS simulation, the length l ₁ of the swing arm, the distance Δl ₁ from the suspension installation position of the swing arm to the outermost end, and the suspension distance L _c of the stabilizer bar, in The load F applied at the suspension installation position of the arm, and the radial stiffness k _x of the rubber bush calculated in the second step, using the geometric relationship between the deformation of the stabilizer bar system and the displacement of the swing arm, the designed external bias Coaxial cab stabilizer bar system roll angle stiffness The ANSYS simulation verification value is calculated, namely

${f f}_{C C} = = \frac{{l l}_{11} {f f}_{A A}}{{l l}_{11} + + Δ Δ {l l}_{11}};;$

$f_{ws} = f_{C} + \frac{F}{k_{x}};$ $f_{ws} = f_{C} + \frac{f}{k_{x}};$

将该非同轴式驾驶室稳定杆系统侧倾角刚度的ANSYS仿真验证值与设计要求值进行比较，从而对本发明所提供的外偏置非同轴式驾驶室稳定杆橡胶套长度的设计方法及参数设计值进行验证。The ANSYS simulation verification value of the roll angle stiffness of the non-coaxial cab stabilizer bar system and design requirements By comparison, the design method and parameter design value of the length of the rubber sleeve of the outer offset non-coaxial cab stabilizer bar provided by the present invention are verified.

本发明比现有技术具有的优点Advantages of the present invention over prior art

由于外偏置非同轴式驾驶室稳定杆系统，是一个由刚体、弹性体及柔性体三者组成的耦合体，而且因扭管外偏置还存在扭转和弯曲的耦合，同时，由于橡胶衬套的刚度计算非常复杂，因此，对于外偏置非同轴式驾驶室稳定杆橡胶套长度的设计，一直未能给出可靠的解析设计方法。目前，国内外对于驾驶室稳定杆系统的设计，大都是利用ANSYS仿真软件，通过实体建模对给定结构的驾驶室稳定杆系统的特性进行仿真验证，尽管该方法可得到比较可靠的仿真数值，然而，由于ANSYS仿真分析只能对给定参数的稳定杆特性进行仿真验证，无法提供精确的解析设计式，不能满足解析设计及CAD设计软件开发的要求。Due to the external bias non-coaxial cab stabilizer bar system, it is a coupling body composed of rigid body, elastic body and flexible body, and there is torsion and bending coupling due to the external bias of the torsion tube. At the same time, due to the rubber The calculation of the stiffness of the bushing is very complicated. Therefore, a reliable analytical design method has not been given for the design of the length of the rubber bushing of the external offset non-coaxial cab stabilizer bar. At present, most of the design of cab stabilizer bar system at home and abroad is to use ANSYS simulation software to simulate and verify the characteristics of the cab stabilizer bar system with a given structure through solid modeling, although this method can obtain relatively reliable simulation values. However, because ANSYS simulation analysis can only simulate and verify the characteristics of the stabilizer bar with given parameters, it cannot provide accurate analytical design formulas, and cannot meet the requirements of analytical design and CAD design software development.

本发明根据驾驶室稳定杆系统的结构及材料特性参数，利用侧倾角刚度设计要求值与稳定杆的摆臂长度，扭管的等效线刚度，扭转橡胶衬套的载荷系数，径向刚度及等效组合线刚度之间的关系，建立了外偏置非同轴式驾驶室稳定杆橡胶套长度的设计数学模型，并利用Matlab程序对其进行求解设计。通过设计实例及ANSYS仿真验证可知，该方法可得到准确可靠的橡胶套长度L_x设计值，为驾驶室悬置及稳定杆系统的设计提供了可靠的设计方法，并且为驾驶室稳定杆系统CAD软件开发奠定了可靠的技术基础。利用该方法，可在不增加产品成本，仅通过橡胶套长度的调整设计，提高驾驶室悬置及稳定杆系统的设计水平、质量和性能，满足驾驶室悬置对稳定杆侧倾角刚度的设计要求，进一步提高车辆的行驶平顺性和安全性；同时，还可降低设计及试验费用，加快产品开发速度。According to the structure and material characteristic parameters of the cab stabilizer bar system, the present invention utilizes the required value of roll angle stiffness design and the length of the swing arm of the stabilizer bar, the equivalent line stiffness of the torsion tube, the load coefficient of the torsion rubber bushing, the radial stiffness and Based on the relationship between the equivalent combination line stiffness, a mathematical model for the design of the length of the rubber sleeve of the outer offset non-coaxial cab stabilizer bar is established, and the Matlab program is used to solve the design. Through the design example and ANSYS simulation verification, it can be seen that the method can obtain the accurate and reliable design value of rubber sleeve length L _x , which provides a reliable design method for the design of the cab suspension and stabilizer bar system, and provides a basis for the cab stabilizer bar system CAD Software development lays a solid technical foundation. Using this method, the design level, quality and performance of the cab suspension and stabilizer bar system can be improved without increasing the product cost, and the design level, quality and performance of the cab suspension and stabilizer bar system can be improved, and the design of the cab suspension to the roll angle stiffness of the stabilizer bar can be satisfied. Requirements, further improve the ride comfort and safety of the vehicle; at the same time, it can also reduce design and test costs and speed up product development.

为了更好地理解本发明，下面结合附图做进一步的说明。In order to better understand the present invention, further description will be made below in conjunction with the accompanying drawings.

图1是外偏置非同轴式驾驶室稳定杆橡胶套长度的设计流程图；Figure 1 is a flow chart of the design of the length of the rubber sleeve of the external offset non-coaxial cab stabilizer bar;

图2是外偏置非同轴式驾驶室稳定杆系统的结构示意图；Fig. 2 is a structural schematic diagram of an externally offset non-coaxial cab stabilizer bar system;

图3是橡胶衬套的结构示意图；Fig. 3 is the structural representation of rubber bushing;

图4是外偏置非同轴式稳定杆系统变形及摆臂位移的几何关系图；Fig. 4 is a geometric relationship diagram of the deformation of the external offset non-coaxial stabilizer bar system and the displacement of the swing arm;

图5是实施例一的橡胶衬套的径向刚度k_x随橡胶套长度L_x的变化曲线；Fig. 5 is the change curve of the radial stiffness k _x of the rubber bushing of embodiment one along with the length L _x of the rubber sleeve;

图6是实施例一的稳定杆系统的等效组合线刚度K_x随橡胶套长度L_x的变化曲线；Fig. 6 is the change curve of the equivalent combination line stiffness K _x of the stabilizer bar system of embodiment one along with the length L _x of the rubber sleeve;

图7是实施例一的外偏置非同轴式稳定杆系统侧倾角刚度随橡胶套长度L_x的变化曲线；Figure 7 is the roll angle stiffness of the externally offset non-coaxial stabilizer bar system in Embodiment 1 The change curve with the length L _x of the rubber sleeve;

图8是实施例一的外偏置非同轴式驾驶室稳定杆系统的变形仿真云图；Fig. 8 is a cloud diagram of deformation simulation of the external offset non-coaxial cab stabilizer bar system of the first embodiment;

图9是实施例二的外偏置非同轴式稳定杆系统侧倾角刚度随橡胶套长度L_x的变化曲线；Figure 9 is the roll angle stiffness of the externally offset non-coaxial stabilizer bar system in Embodiment 2 The change curve with the length L _x of the rubber sleeve;

图10是实施例二的外偏置非同轴式驾驶室稳定杆系统的变形仿真云图。Fig. 10 is a deformation simulation cloud diagram of the external offset non-coaxial cab stabilizer bar system of the second embodiment.

具体实施方案specific implementation plan

下面通过实施例对本发明作进一步详细说明。The present invention will be described in further detail below by way of examples.

实施例一：某外偏置非同轴式驾驶室稳定杆系统的结构左右对称，如图2所示，包括：摆臂1，悬置橡胶衬套2，扭转橡胶衬套3，扭管4；其中，扭管4与扭转橡胶衬套3不同轴，扭管4的外偏置量T＝30mm；左右两个摆臂1之间的距离距离L_c＝1550mm，即为稳定杆的悬置距离；悬置橡胶衬套2与扭转橡胶衬套3之间的距离l₁＝380mm，即为摆臂长度；摆臂的悬置安装位置C到最外端A的距离Δl₁＝47.5mm；扭管4的长度L_w＝1500mm，内径d＝35mm，外径D＝50mm，弹性模量E＝200GPa，泊松比μ＝0.3；左右四个橡胶衬套的结构和材料特性完全相同，如图3所示，包括：内圆套筒5，橡胶套6，外圆套筒7，其中，内圆套筒5的内圆直径d_x＝35mm，壁厚δ＝2mm；橡胶套6的内圆半径r_a＝19.5mm，外圆半径r_b＝34.5mm，弹性模量E_x＝7.84MPa，泊松比μ_x＝0.47，橡胶套的长度L_x为待设计参数。该驾驶室稳定杆设计所要求的侧倾角刚度对该外偏置非同轴式驾驶室稳定杆的橡胶套长度L_x进行设计，并在载荷F＝5000N情况下对稳定杆系统的侧倾角刚度进行ANSYS仿真验证。Embodiment 1: The structure of an external offset non-coaxial cab stabilizer bar system is left-right symmetrical, as shown in Figure 2, including: swing arm 1, suspension rubber bushing 2, torsion rubber bushing 3, torsion tube 4 Wherein, the torsion tube 4 is not coaxial with the torsion rubber bushing 3, and the external offset of the torsion tube 4 is T=30mm; the distance between the left and right swing arms 1 is L _c =1550mm, which is the suspension of the stabilizer bar The distance between the suspension rubber bushing 2 and the torsion rubber bushing 3 is l ₁ =380mm, which is the length of the swing arm; the distance from the suspension installation position C of the swing arm to the outermost end A is Δl ₁ =47.5mm ; The length L _w of torsion tube 4=1500mm, inner diameter d=35mm, outer diameter D=50mm, elastic modulus E=200GPa, Poisson's ratio μ=0.3; the structures and material properties of the four rubber bushes on the left and right are exactly the same, As shown in Figure 3, comprise: inner circle sleeve 5, rubber sleeve 6, outer circle sleeve 7, wherein, the inner circle diameter _dx =35mm of inner circle sleeve 5, wall thickness δ=2mm; Rubber sleeve 6 Inner circle radius r _a =19.5mm, outer circle radius r _b =34.5mm, elastic modulus E _x =7.84MPa, Poisson's ratio μ _x =0.47, and the length L _x of the rubber sleeve is a parameter to be designed. The required roll angle stiffness for this cab stabilizer bar design The rubber sleeve length L _x of the external offset non-coaxial cab stabilizer bar is designed, and the roll angle stiffness of the stabilizer bar system is verified by ANSYS simulation under the load F=5000N.

本发明实例所提供的外偏置非同轴式驾驶室稳定杆橡胶套长度的设计方法，其设计流程如图1所示，具体步骤如下：The design method for the length of the rubber sleeve of the external offset non-coaxial cab stabilizer bar provided by the example of the present invention is shown in Figure 1. The specific steps are as follows:

根据稳定杆系统的侧倾角刚度的设计要求值稳定杆的悬置距离L_c＝1550mm，对驾驶室稳定杆系统的侧倾线刚度K_ws的设计要求值进行计算，即According to the design requirement value of the roll angle stiffness of the stabilizer bar system The suspension distance L _c of the stabilizer bar = 1550mm, and the design requirement value of the roll line stiffness K _ws of the cab stabilizer bar system is calculated, namely

根据扭管长度L_w＝1500mm，内径d＝35mm，外径D＝50mm，外偏置量T＝30mm，弹性模量E＝200GPa和泊松比μ＝0.3，及摆臂长度l₁＝380mm，对该外偏置非同轴式稳定杆的扭管在驾驶室悬置安装位置C处的等效线刚度K_T进行计算，即According to the torsion tube length L _w = 1500mm, inner diameter d = 35mm, outer diameter D = 50mm, outer offset T = 30mm, elastic modulus E = 200GPa and Poisson's ratio μ = 0.3, and swing arm length l ₁ = 380mm, Calculate the equivalent line stiffness K _T of the torsion tube of the external offset non-coaxial stabilizer bar at the installation position C of the cab suspension, that is,

${K K}_{T T} = = \frac{πE πE (({D D.}^{44} - - {d d}^{44}))}{3232 ((11 + + μ μ)) {(({l l}_{11} + + T T))}^{22} {L L}_{W W}} = = 2.84488 2.84488 \times \times 1010^{55} N N / / m m;;$

根据橡胶套的内圆半径r_a＝19.5mm，外圆半径r_b＝34.5mm，弹性模量E_x＝7.84MPa和泊松比μ_x＝0.47，以橡胶套长度L_x为待设计参变量，建立该稳定杆橡胶衬套的径向刚度表达式k_x(L_x)，即According to the inner circle radius r _a =19.5mm of the rubber sleeve, the outer circle radius r _b =34.5mm, the elastic modulus E _x =7.84MPa and the Poisson's ratio μ _x =0.47, the length of the rubber sleeve L _x is the parameter to be designed, Establish the radial stiffness expression k _x (L _x ) of the rubber bushing of the stabilizer bar, namely

${a a}_{33} = = \frac{((11 + + {μ μ}_{x x})) (({b b}_{11} - - {b b}_{22} + + {b b}_{33}))}{55 π π {E E.}_{x x} {L L}_{x x} α α {r r}_{a a} {r r}_{b b} [[I I ((11,, α α {r r}_{a a})) K K ((11,, α α {r r}_{b b})) - - K K ((11,, α α {r r}_{a a})) I I ((11,, α α {r r}_{b b}))]] (({r r}_{a a}^{22} + + {r r}_{b b}^{22}))};;$

${b b}_{22} = = [[I I ((11,, α α {r r}_{b b})) K K ((00,, α α {r r}_{a a})) + + K K ((11,, α α {r r}_{b b})) I I ((00,, α α {r r}_{a a}))]] {r r}_{b b} (({r r}_{b b}^{22} + + 33 {r r}_{b b}^{22})),,$

$α α = = 22 \sqrt{1515} / / {L L}_{x x},,$

其中，橡胶衬套的径向刚度k_x随橡胶套长度L_x的变化曲线，如图5所示；Among them, the variation curve of the radial stiffness k _x of the rubber bushing with the length L _x of the rubber bushing is shown in Figure 5;

根据扭管长度L_W＝1500mm，泊松比μ＝0.3，外偏置量T＝30mm，及摆臂长度l₁＝380mm，对扭转橡胶衬套的载荷系数η_F进行计算，即According to the torsion tube length L _W = 1500mm, Poisson's ratio μ = 0.3, external offset T = 30mm, and swing arm length l ₁ = 380mm, the load coefficient η _F of the torsion rubber bushing is calculated, namely

${η η}_{F f} = = \frac{24 twenty four ((11 + + μ μ)) {l l}_{11} T T}{{L L}_{W W}^{22}} = = 0.15808 0.15808;;$

根据①步骤中所建立的k_x(L_x)，及②步骤中计算得到的η_F＝0.15808，建立外偏置非同轴式稳定杆橡胶衬套的等效组合线刚度表达式K_x(L_x)，即According to k _x (L _x ) established in step ① and η _F = 0.15808 calculated in step ②, the equivalent combined linear stiffness expression K _x ( L _x ), that is

${K K}_{X x} (({L L}_{x x})) = = \frac{{k k}_{x x} (({L L}_{x x}))}{11 + + {η η}_{F f}} = = \frac{{k k}_{x x} (({L L}_{x x}))}{1.15808 1.15808};;$

其中，稳定杆橡胶衬套的等效组合线刚度K_x随橡胶套长度L_x的变化曲线，如图6所示；Among them, the change curve of the equivalent combined linear stiffness K _x of the stabilizer bar rubber bushing with the length L _x of the rubber bushing is shown in Figure 6;

根据步骤(1)中计算得到的K_ws＝2.461×10⁵N/m，步骤(2)中计算得到的K_T＝2.84488×10⁵N/m，及步骤(3)中的③步骤所建立的建立外偏置非同轴式驾驶室稳定杆橡胶套长度L_x的设计数学模型，即According to K _ws calculated in step (1) = 2.461×10 ⁵ N/m, K _T calculated in step (2) = 2.84488×10 ⁵ N/m, and established in step ③ in step (3) of Establish the design mathematical model of the length L _x of the rubber sleeve of the external offset non-coaxial cab stabilizer bar, namely

K_TK_X(L_x)-K_X(L_x)+K_wsK_w＝0；K _T K _X (L _x )-K _X (L _x )+K _ws K _w =0;

利用Matlab程序，求解上述关于L_x的方程，可得到该非同轴式驾驶室稳定杆橡胶套长度L_x的设计值，即Using the Matlab program to solve the above equation about _Lx , the design value of the length _Lx of the non-coaxial cab stabilizer bar rubber sleeve can be obtained, namely

L_x＝25mm； _Lx = 25mm;

其中，该稳定杆系统的侧倾角刚度随橡胶套长度L_x的变化曲线，如图7所示；Among them, the roll angle stiffness of the stabilizer bar system With the change curve of rubber sleeve length L _x , as shown in Figure 7;

I利用ANSYS有限元仿真软件，根据设计所得到的橡胶套长度L_x＝25mm，，及外偏置非同轴式驾驶室稳定杆系统的其他结构参数和材料特性参数，建立ANSYS仿真模型，划分网格，并在摆臂的悬置安装位置C处施加载荷F＝5000N，对稳定杆系统的变形进行ANSYS仿真，所得到的变形仿真云图，如图8所示，其中，稳定杆系统在摆臂最外端A处的变形位移量f_A为I utilize ANSYS finite element simulation software, according to the obtained rubber sleeve length L _x =25mm of design, and other structural parameters and material property parameters of the external offset non-coaxial cab stabilizer bar system, set up the ANSYS simulation model, divide Grid, and a load F=5000N is applied at the suspension installation position C of the swing arm, and the deformation of the stabilizer bar system is simulated by ANSYS, and the obtained deformation simulation cloud diagram is shown in Figure 8. The deformation displacement f _A at the outermost end A of the arm is

f_A＝19.984mm； _fA = 19.984mm;

II根据所设计的橡胶套长度L_x＝25mm，橡胶衬套的其他结构及材料特性参数，利用步骤(3)中的①步骤所建立的橡胶衬套径向刚度表达式k_x(L_x)，求得所设计橡胶衬套的径向刚度k_x＝2.1113×10⁶N/m；II According to the designed rubber bushing length L _x = 25mm, other structural and material characteristic parameters of the rubber bushing, use the rubber bushing radial stiffness expression k _x (L _x ) established by step ① in step (3) , obtain the radial stiffness k _x of the designed rubber bushing = 2.1113×10 ⁶ N/m;

III根据ANSYS仿真所得到的摆臂最外端A处的变形位移量f_A＝19.984mm，摆臂长度l₁＝380mm，摆臂的悬置安装位置C到最外端A的距离Δl₁＝47.5mm，稳定杆的悬置距离L_c＝1550mm，在摆臂的悬置安装位置C处所施加的载荷F＝5000N，及II步骤中计算得到的k_x＝2.1113×10⁶N/m，利用稳定杆系统变形及摆臂位移的几何关系，如图4所示，对该外偏置非同轴驾驶室稳定杆系统侧倾角刚度的ANSYS仿真验证值，进行计算，即III According to ANSYS simulation, the deformation displacement at the outermost end A of the swing arm is f _A =19.984mm, the length of the swing arm is l ₁ =380mm, and the distance from the suspension installation position C of the swing arm to the outermost end A is Δl ₁ = 47.5mm, the suspension distance L _c of the stabilizer bar = 1550mm, the load F = 5000N applied at the suspension installation position C of the swing arm, and the k _x calculated in step II = 2.1113×10 ⁶ N/m, using The geometric relationship between the deformation of the stabilizer bar system and the displacement of the swing arm is shown in Figure 4. For the outer offset non-coaxial cab stabilizer bar system, the roll angle stiffness The ANSYS simulation verification value is calculated, namely

${f f}_{C C} = = \frac{{l l}_{11} {f f}_{A A}}{{l l}_{11} + + Δ Δ {l l}_{11}} = = 17.7635 17.7635 mm mm;;$

f_ws＝f_C+F/k_x＝20.1317mm；f _ws =f _C +F/k _x =20.1317mm;

可知，该外偏置非同轴式驾驶室稳定杆的侧倾角刚度的ANSYS仿真验证值与设计要求值相吻合，相对偏差仅为0.916％；结果表明该发明所提供的外偏置非同轴式驾驶室稳定杆橡胶套长度的设计方法是正确的，参数设计值是准确可靠的。It can be seen that the ANSYS simulation verification value of the roll angle stiffness of the external offset non-coaxial cab stabilizer bar and design requirements They coincide, and the relative deviation is only 0.916%. The result shows that the design method of the length of the rubber sleeve of the outer offset non-coaxial cab stabilizer bar provided by the invention is correct, and the parameter design value is accurate and reliable.

实施例二：某外偏置非同轴式驾驶室稳定杆系统的结构形式与实施例一的相同，如图2所示，其中，扭管4与扭转橡胶衬套3不同轴，扭管4的外偏置量T＝50mm；左右两个摆臂1之间的距离L_c＝1400mm，即稳定杆的悬置距离；悬置橡胶衬套2与扭转橡胶衬套3之间的距离l₁＝350mm，即摆臂长度；摆臂的悬置安装位置C到最外端A的距离Δl₁＝52.5mm；扭管4的长度L_w＝1000mm，内径d＝42mm，外径D＝50mm，材料弹性模量E＝200GPa，泊松比μ＝0.3；左右四个橡胶衬套的结构都完全相同，如图3所示，其中，内圆套筒5的内圆直径d_x＝35mm，壁厚δ＝5mm；橡胶套6的内圆半径r_a＝22.5mm，外圆半径r_b＝37.5mm，弹性模量E_x＝7.84MPa，泊松比μ_x＝0.47，橡胶套的长度L_x为待设计参数。该驾驶室稳定杆设计所要求的侧倾角刚度对该外偏置非同轴式驾驶室稳定杆的橡胶套长度L_x进行设计，并在载荷F＝5000N情况下对稳定杆系统的侧倾角刚度进行ANSYS仿真验证。Embodiment 2: The structural form of an externally biased non-coaxial cab stabilizer bar system is the same as that of Embodiment 1, as shown in Figure 2, wherein the torsion tube 4 is not coaxial with the torsion rubber bushing 3, and the torsion tube 4's external offset T = 50mm; the distance L _c between the left and right swing arms 1 = 1400mm, that is, the suspension distance of the stabilizer bar; the distance l between the suspension rubber bush 2 and the torsion rubber bush 3 ₁ = 350mm, that is, the length of the swing arm; the distance from the suspension installation position C of the swing arm to the outermost end A Δl ₁ = 52.5mm; the length L _w of the torsion tube 4 = 1000mm, the inner diameter d = 42mm, and the outer diameter D = 50mm , material modulus of elasticity E=200GPa, Poisson's ratio μ=0.3; The structures of the left and right four rubber bushes are all identical, as shown in Figure 3, wherein, the inner circle diameter d _x of the inner circle sleeve 5=35mm, Wall thickness δ=5mm; inner circle radius r _a =22.5mm of rubber sleeve 6, outer circle radius r _b =37.5mm, elastic modulus E _x =7.84MPa, Poisson’s ratio μ _x =0.47, length L of rubber sleeve _x is the parameter to be designed. The required roll angle stiffness for this cab stabilizer bar design The rubber sleeve length L _x of the external offset non-coaxial cab stabilizer bar is designed, and the roll angle stiffness of the stabilizer bar system is verified by ANSYS simulation under the load F=5000N.

采用与实施例一相同的步骤，对该外偏置非同轴式驾驶室稳定杆的橡胶套长度L_x进行设计，即：Using the same steps as in Embodiment 1, the rubber sleeve length L _x of the external offset non-coaxial cab stabilizer bar is designed, namely:

根据稳定杆系统的侧倾角刚度的设计要求值稳定杆的悬置距离L_c＝1400mm，对该驾驶室稳定杆系统的侧倾线刚度K_ws设计要求值进行计算，即According to the design requirement value of the roll angle stiffness of the stabilizer bar system The suspension distance L _c of the stabilizer bar is 1400mm, and the design requirement value of the roll line stiffness K _ws of the cab stabilizer bar system is calculated, namely

根据扭管长度L_w＝1000mm，内径d＝42mm，外径D＝50mm，外偏置量T＝30mm，弹性模量E＝200GPa和泊松比μ＝0.3，及摆臂长度l₁＝350mm，对该外偏置非同轴式稳定杆的扭管在驾驶室悬置安装位置C处的等效线刚度K_T进行计算，即According to the torsion tube length L _w = 1000mm, inner diameter d = 42mm, outer diameter D = 50mm, outer offset T = 30mm, elastic modulus E = 200GPa and Poisson's ratio μ = 0.3, and swing arm length l ₁ = 350mm, Calculate the equivalent line stiffness K _T of the torsion tube of the external offset non-coaxial stabilizer bar at the installation position C of the cab suspension, that is,

${K K}_{T T} = = \frac{πE πE (({D D.}^{44} - - {d d}^{44}))}{3232 ((11 + + μ μ)) {(({l l}_{11} + + T T))}^{22} {L L}_{W W}} = = 3.28257 3.28257 \times \times 1010^{55} N N / / m m;;$

根据橡胶套的内圆半径r_a＝22.5mm，外圆半径r_b＝37.5mm，弹性模量E_x＝7.84MPa和泊松比μ_x＝0.47，以橡胶套长度L_x为待设计参变量，建立稳定杆橡胶衬套的径向刚度表达式k_x(L_x)，即According to the inner circle radius r _a =22.5mm of the rubber sleeve, the outer circle radius r _b =37.5mm, the elastic modulus E _x =7.84MPa and the Poisson's ratio μ _x =0.47, the length L _x of the rubber sleeve is the parameter to be designed, Establish the radial stiffness expression k _x (L _x ) of the rubber bushing of the stabilizer bar, namely

$α α = = 22 \sqrt{1515} / / {L L}_{x x},,$

根据扭管长度L_W＝1000mm，泊松比μ＝0.3，外偏置量T＝30mm，及摆臂长度l₁＝350mm，对扭转橡胶衬套的载荷系数η_F进行计算，即According to the torsion tube length L _W = 1000mm, Poisson's ratio μ = 0.3, external offset T = 30mm, and swing arm length l ₁ = 350mm, the load coefficient η _F of the torsion rubber bushing is calculated, namely

${η η}_{F f} = = \frac{24 twenty four ((11 + + μ μ)) {l l}_{11} T T}{{L L}_{W W}^{22}} = = 0.3276 0.3276;;$

根据①步骤中所建立的k_x(L_x)，及②步骤中计算得到的η_F＝0.3276，建立稳定杆橡胶衬套的等效组合线刚度表达式K_x(L_x)，即According to k _x (L _x ) established in step ①, and η _F =0.3276 calculated in step ②, the equivalent combination linear stiffness expression K _x (L _x ) of the rubber bushing of the stabilizer bar is established, namely

${K K}_{X x} (({L L}_{x x})) = = \frac{{k k}_{x x} (({L L}_{x x}))}{11 + + {η η}_{F f}} = = \frac{{k k}_{x x} (({L L}_{x x}))}{11 . . 32763276};;$

根据步骤(1)中计算得到的K_ws＝2.97455×10⁵N/m，步骤(2)中计算得到的K_T＝3.28257×10⁵N/m，及步骤(3)中的③步骤所建立的建立外偏置非同轴式驾驶室稳定杆橡胶套长度L_x的设计数学模型，即According to the K _ws calculated in step (1) = 2.97455×10 ⁵ N/m, the K _T calculated in step (2) = 3.28257×10 ⁵ N/m, and the establishment of step ③ in step (3) of Establish the design mathematical model of the length L _x of the rubber sleeve of the external offset non-coaxial cab stabilizer bar, namely

L_x＝40mm；L _x = 40mm;

其中，该驾驶室稳定杆系统的侧倾角刚度随橡胶套长度L_x的变化曲线，如图9所示；Among them, the roll angle stiffness of the cab stabilizer bar system With the change curve of rubber sleeve length L _x , as shown in Figure 9;

I利用ANSYS有限元仿真软件，根据设计所得到的橡胶套长度L_x＝40mm，及外偏置非同轴式驾驶室稳定杆系统的其他结构参数和材料特性参数，建立ANSYS仿真模型，划分网格，在摆臂的悬置安装位置C处施加载荷F＝5000N，对稳定杆系统的变形进行ANSYS仿真，所得到的变形仿真云图，如图10所示，其中，稳定杆系统在摆臂最外端A处的变形位移量f_A为I Utilize ANSYS finite element simulation software, according to the rubber sleeve length L _x =40mm obtained by design, and other structural parameters and material property parameters of the external offset non-coaxial cab stabilizer bar system, establish the ANSYS simulation model, divide the network grid, the load F=5000N is applied at the suspension installation position C of the swing arm, and the deformation of the stabilizer bar system is simulated by ANSYS. The deformation displacement f _A at the outer end A is

f_A＝17.881mm； _fA = 17.881mm;

II根据所设计的橡胶套长度L_x＝40mm，橡胶衬套的其他结构及材料特性参数，利用步骤(3)中的①步骤所建立的橡胶衬套径向刚度表达式k_x(L_x)，求得所设计橡胶衬套的径向刚度k_x＝4.2085×10⁶N/m；II According to the designed rubber sleeve length L _x = 40mm, other structural and material characteristic parameters of the rubber bush, use the rubber bush radial stiffness expression k _x (L _x ) established in step ① in step (3) , obtain the radial stiffness k _x of the designed rubber bushing = 4.2085×10 ⁶ N/m;

III根据ANSYS仿真所得到的摆臂最外端A处的变形位移量f_A＝17.881mm，摆臂长度l₁＝350mm，摆臂的悬置安装位置C到最外端A的距离Δl₁＝52.5mm，稳定杆的悬置距离L_c＝1400mm，在摆臂悬置安装位置C处所施加的载荷F＝5000N，及II步骤中计算得到的k_x＝4.2085×10⁶N/m，利用稳定杆系统变形及摆臂位移的几何关系，如图4所示，对该外偏置非同轴式驾驶室稳定杆系统侧倾角刚度的ANSYS仿真验证值，进行计算，即III According to ANSYS simulation, the deformation displacement at the outermost end A of the swing arm is f _A =17.881mm, the length of the swing arm is l ₁ =350mm, and the distance from the suspension installation position C of the swing arm to the outermost end A is Δl ₁ = 52.5mm, the suspension distance L _c of the stabilizer bar = 1400mm, the load F = 5000N applied at the suspension installation position C of the swing arm, and the k _x calculated in step II = 4.2085×10 ⁶ N/m, using the stabilizer The geometric relationship between the deformation of the rod system and the displacement of the swing arm is shown in Figure 4. The ANSYS simulation verification value is calculated, namely

${f f}_{C C} = = \frac{{l l}_{11} {f f}_{A A}}{{l l}_{11} + + Δ Δ {l l}_{11}} = = 15.5486 15.5486 mm mm;;$

f_ws＝f_C+F/k_x＝16.7367mm；f _ws =f _C +F/k _x =16.7367mm;

可知，该外偏置非同轴式驾驶室稳定杆的侧倾角刚度的ANSYS仿真验证值与设计要求值相吻合，相对偏差仅为0.431％；结果表明该发明所提供的外偏置非同轴式驾驶室稳定杆橡胶套长度的设计方法是正确的，参数设计值是准确可靠的。It can be seen that the ANSYS simulation verification value of the roll angle stiffness of the external offset non-coaxial cab stabilizer bar and design requirements The relative deviation is only 0.431%. The results show that the design method of the length of the rubber sleeve of the outer offset non-coaxial cab stabilizer bar provided by the invention is correct, and the parameter design value is accurate and reliable.

Claims

1. The design method for the length of the rubber sleeve of the externally offset non-coaxial cab stabilizer bar. The specific design steps are as follows:

(1) Calculation of the design requirement value _of the roll line stiffness Kws of the cab stabilizer bar system:

According to the required value of the roll angle stiffness design of the cab stabilizer bar system The suspension distance L _c of the stabilizer bar is calculated from the design requirement value of the roll line stiffness K _ws of the cab stabilizer bar system, namely

(2) The establishment of the equivalent linear stiffness expression K _T of the torsion tube of the external offset non-coaxial cab:

According to the torsion tube length L _w , inner diameter d, outer diameter D, outer offset T, elastic modulus E, Poisson's ratio μ, and swing arm length l ₁ , the torsion tube for the stabilizer bar is at the installation position of the cab suspension The equivalent line stiffness K _T is calculated, that is

{K K}_{T T} = = \frac{πE πE (({D D.}^{44} - - {d d}^{44}))}{3232 ((11 + + μ μ)) {(({l l}_{11} + + T T))}^{22} {L L}_{W W}};;

(3) Establishment of the equivalent combination linear stiffness expression K _x (L _x ) of the rubber bushing of the external offset non-coaxial stabilizer bar:

① Establish the radial stiffness expression k _x (L _x ) of the rubber bushing

According to the inner circle radius r _a , outer circle radius r _b , elastic modulus E _x and Poisson's ratio μ _x of the rubber bushing, and the length L _x of the rubber bushing as the parameter to be designed, the radial stiffness expression k of the rubber bushing is established _x (L _x ), that is

{k k}_{x x} (({L L}_{x x})) = = \frac{11}{u u (({L L}_{x x})) + + y the y (({L L}_{x x}))};;

in,

u = (L_{x}) = (\ln \frac{r_{b}}{r_{a}} - \frac{{r_{b}}^{2} - {r_{a}}^{2}}{{r_{a}}^{2} + {r_{b}}^{2}}) \frac{1 + μ_{x}}{2 π {E.}_{x}} L_{x},

y the y (({L L}_{x x})) = = {a a}_{11} I I ((00,, α α {r r}_{b b})) + + {a a}_{22} K K ((00,, α α {r r}_{b b})) + + {a a}_{33} + + \frac{11 + + {μ μ}_{x x}}{55 π π {E E.}_{x x} {L L}_{x x}} ((ln ln {r r}_{b b} + + \frac{{r r}_{b b}^{22}}{{r r}_{a a}^{22} + + {r r}_{b b}^{22}})),,

{a a}_{11} = = \frac{((11 + + {μ μ}_{x x})) [[K K ((11,, α α {r r}_{a a})) {r r}_{a a} (({r r}_{a a}^{22} + + 33 {r r}_{b b}^{22})) - - K K ((11,, α α {r r}_{b b})) {r r}_{b b} ((33 {r r}_{a a}^{22} + + {r r}_{b b}^{22}))]]}{55 π π {E E.}_{x x} {L L}_{x x} α α {r r}_{a a} {r r}_{b b} [[I I ((11,, α α {r r}_{a a})) K K ((11,, α α {r r}_{b b})) - - K K ((11,, α α {r r}_{a a})) I I ((11,, α α {r r}_{b b}))]] (({r r}_{a a}^{22} + + {r r}_{b b}^{22}))},,

{a a}_{22} = = \frac{(({μ μ}_{x x} + + 11)) [[I I ((11,, α α {r r}_{a a})) {r r}_{a a} (({r r}_{a a}^{22} + + 33 {r r}_{b b}^{22})) - - I I ((11,, α α {r r}_{b b})) {r r}_{b b} ((33 {r r}_{a a}^{22} + + {r r}_{b b}^{22}))]]}{55 π π {E E.}_{x x} {L L}_{x x} α α {r r}_{a a} {r r}_{b b} [[I I ((11,, α α {r r}_{a a})) K K ((11,, α α {r r}_{b b})) - - K K ((11,, α α {r r}_{a a})) I I ((11,, α α {r r}_{b b}))]] (({r r}_{a a}^{22} + + {r r}_{b b}^{22}))},,

{a a}_{33} = = - - \frac{((11 + + {μ μ}_{x x})) (({b b}_{11} - - {b b}_{22} + + {b b}_{33}))}{55 π π {E E.}_{x x} {L L}_{x x} α α {r r}_{a a} {r r}_{b b} [[I I ((11,, α α {r r}_{a a})) K K ((11,, α α {r r}_{b b})) - - K K ((11,, α α {r r}_{a a})) I I ((11,, α α {r r}_{b b}))]] (({r r}_{a a}^{22} + + {r r}_{b b}^{22}))};;

{b b}_{11} = = [[I I ((11,, α α {r r}_{a a})) K K ((00,, α α {r r}_{a a})) + + K K ((11,, α α {r r}_{a a})) I I ((00,, α α {r r}_{a a}))]] {r r}_{a a} (({r r}_{a a}^{22} + + 33 {r r}_{b b}^{22})),,

{b b}_{22} = = [[I I ((11,, α α {r r}_{b b})) K K ((00,, α α {r r}_{a a})) + + K K ((11,, α α {r r}_{b b})) I I ((00,, α α {r r}_{a a}))]] {r r}_{b b} (({r r}_{b b}^{22} + + 33 {r r}_{a a}^{22})),,

{b b}_{33} = = α α {r r}_{a a} {r r}_{b b} [[I I ((11,, α α {r r}_{a a})) K K ((11,, α α {r r}_{b b})) - - K K ((11,, α α {r r}_{a a})) I I ((11,, α α {r r}_{b b}))]] [[{r r}_{a a}^{22} + + (({r r}_{a a}^{22} + + {r r}_{b b}^{22})) ln ln {r r}_{a a}]],,

α α = = 22 \sqrt{1515} / / {L L}_{x x},,

Bessel correction function I(0,αr _b ), K(0,αr _b ), I(1,αr _b ), K(1,αr _b ),

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

② Calculation of the load factor η _F of the torsional rubber bushing of the external offset non-coaxial stabilizer bar system

According to the length L _W of the torsion tube, Poisson's ratio μ, the external offset T, and the length l ₁ of the swing arm, the load factor η _F of the torsion rubber bushing is calculated, namely

{η η}_{F f} = = \frac{24 twenty four ((11 + + {μ μ}_{11})) {l l}_{11} T T}{{L L}_{W W}^{22}};;

③Establishment of the equivalent combined linear stiffness expression K _x (L _x ) of the rubber bushing of the external offset non-coaxial stabilizer bar

According to the radial stiffness expression k _x (L _x ) of the rubber bush established in step ①, and the load factor η _F of the torsional rubber bush calculated in step ②, an externally offset non-coaxial stabilizer bar is established The equivalent combination line stiffness expression K _x (L _x ) of the rubber bushing, namely

{K K}_{X x} (({L L}_{x x})) = = \frac{{k k}_{x x} (({L L}_{x x}))}{11 + + {η η}_{F f}};;

(4) Establishment and design of the rubber sleeve length L _x design mathematical model of the external offset non-coaxial cab stabilizer bar:

According to the required design value K _ws of the roll line stiffness of the cab stabilizer bar system calculated in step (1), the equivalent line stiffness K _T of the torsion tube calculated in step (2), and the The equivalent combination linear stiffness expression K _x (L _x ) of the rubber bush established in step ③, establishes the design mathematical model of the length L _x of the rubber bush of the external offset non-coaxial cab stabilizer bar, namely

K _T K _X (L _x )-K _ws K _X (L _x )-K _ws K _T = 0;

Using the Matlab program to solve the above equation about L _x , the design value of the rubber sleeve length L _x of the external offset non-coaxial cab stabilizer bar can be obtained;

(5) ANSYS simulation verification of the roll angle stiffness of the external offset non-coaxial cab stabilizer bar system:

I use ANSYS finite element simulation software, according to the design value of the rubber sleeve length L _x , and other structural parameters and material property parameters of the external offset non-coaxial cab stabilizer bar system, establish an ANSYS simulation model, divide the grid, and Apply a load F at the suspension installation position of the swing arm, carry out ANSYS simulation on the deformation of the stabilizer bar system, and obtain the deformation displacement f _A of the external offset non-coaxial stabilizer bar system at the outermost end of the swing arm;

II According to the designed rubber bushing length L _x , other structural and material characteristic parameters of the rubber bushing, using the rubber bushing radial stiffness expression k _x (L _x ) established in step ① of step (3), find Obtain the radial stiffness k _x of the designed rubber bushing;

III According to the maximum deformation displacement f _A of the outermost end of the swing arm obtained by ANSYS simulation, the length l ₁ of the swing arm, the distance Δl ₁ from the suspension installation position of the swing arm to the outermost end, and the suspension distance L _c of the stabilizer bar, in The load F applied at the suspension installation position of the arm, and the radial stiffness k _x of the rubber bush calculated in the second step, using the geometric relationship between the deformation of the stabilizer bar system and the displacement of the swing arm, the designed external bias Coaxial cab stabilizer bar system roll angle stiffness The ANSYS simulation verification value is calculated, namely

{f f}_{C C} = = \frac{{l l}_{11} {f f}_{A A}}{{l l}_{11} + + Δ Δ {l l}_{11}};;

{f f}_{ws ws} = = {f f}_{C C} + + \frac{F f}{{k k}_{x x}};;

The ANSYS simulation verification value of the roll angle stiffness of the non-coaxial cab stabilizer bar system and design requirements By comparison, the design method and parameter design value of the length of the rubber sleeve of the outer offset non-coaxial cab stabilizer bar provided by the present invention are verified.