CN104331577B - Design method of external biasing non-coaxial cab stabilizer bar oscillating arm length - Google Patents
Design method of external biasing non-coaxial cab stabilizer bar oscillating arm length Download PDFInfo
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- CN104331577B CN104331577B CN201410665491.1A CN201410665491A CN104331577B CN 104331577 B CN104331577 B CN 104331577B CN 201410665491 A CN201410665491 A CN 201410665491A CN 104331577 B CN104331577 B CN 104331577B
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- 239000003381 stabilizer Substances 0.000 title claims abstract description 99
- 238000013461 design Methods 0.000 title claims abstract description 79
- 238000000034 method Methods 0.000 title claims abstract description 29
- 229920001971 elastomer Polymers 0.000 claims abstract description 66
- 239000000725 suspension Substances 0.000 claims abstract description 32
- 238000006073 displacement reaction Methods 0.000 claims description 14
- 238000009434 installation Methods 0.000 claims description 13
- 239000000463 material Substances 0.000 claims description 9
- 238000012937 correction Methods 0.000 claims description 4
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- 238000004088 simulation Methods 0.000 abstract description 11
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- 238000002474 experimental method Methods 0.000 abstract 1
- 238000012795 verification Methods 0.000 abstract 1
- 230000008878 coupling Effects 0.000 description 4
- 238000010168 coupling process Methods 0.000 description 4
- 238000005859 coupling reaction Methods 0.000 description 4
- 238000010200 validation analysis Methods 0.000 description 3
- 244000079889 Cymbidium pendulum Species 0.000 description 2
- 238000004458 analytical method Methods 0.000 description 2
- 238000004364 calculation method Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000000806 elastomer Substances 0.000 description 2
- 239000003292 glue Substances 0.000 description 2
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- 239000007787 solid Substances 0.000 description 2
- 240000002853 Nelumbo nucifera Species 0.000 description 1
- 235000006508 Nelumbo nucifera Nutrition 0.000 description 1
- 235000006510 Nelumbo pentapetala Nutrition 0.000 description 1
- 244000131316 Panax pseudoginseng Species 0.000 description 1
- 235000005035 Panax pseudoginseng ssp. pseudoginseng Nutrition 0.000 description 1
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Abstract
The invention relates to a design method of an external biasing non-coaxial cab stabilizer bar oscillating arm length, which belongs to the technical field of the suspension of a cab. A design mathematic model of the oscillating arm length can be established by utilizing the relation of roll angle rigidness design required value and the oscillating arm length of a stabilizer bar, equivalent combined linear rigidness of a rubber bushing and equivalent linear rigidness of a torsion pipe and solved by utilizing a Matlab program. By adopting the method, an accurate and reliable oscillating arm length design value can be acquired by virtue of design example and simulation verification, a reliable design method is provided for the suspension of the cab and the design of the stabilizer bar system, and a reliable technical foundation can be set for the development of CAD software. By utilizing the method, not only can the design level and quality of the cab suspension and stabilizer bar system be improved, but also driving smoothness and safety of the vehicle can be improved; meanwhile, the design and experiment expense also can be reduced, and the product development speed can be increased.
Description
Technical field
The present invention relates to vehicle cab suspension, particularly outer to bias setting for non-coaxial driver's cabin stabiliser bar pendulum arm length
Meter method.
Background technology
The pendulum arm length of the stable lever system of driver's cabin, not only affects flexural deformation, the load of reversed rubber bushing of torsion tube
And deformation, and the roll stiffness to stablizing lever system has material impact.For outer biasing non-coaxial driver's cabin stabiliser bar
System, although being only made up of swing arm, torsion tube and rubber bushing, but one by rigid body, elastomer and flexible body three's group
Into coupling body, and because bias outside torsion tube also exist reverse and bend coupling, simultaneously as the Rigidity Calculation of rubber bushing
It is extremely complex, therefore, for the design of outer biasing non-coaxial driver's cabin stabiliser bar pendulum arm length, fail to provide reliable always
Resolution design method.At present, mostly it is, using ANSYS simulation softwares, to lead to both at home and abroad for the design of the stable lever system of driver's cabin
Crossing the characteristic of driver's cabin stable lever system of the solid modelling to giving structure carries out simulating, verifying, although the method can be compared
Reliable simulation numerical, however, because ANSYS simulation analysis can only be verified to the stabiliser bar of given parameters, it is impossible to provide
Accurate analytical design method formula, it is impossible to realize analytical design method, can not meet wanting for the stable lever system CAD software exploitation of driver's cabin
Ask.With the continuous improvement of the fast-developing and Vehicle Speed of Vehicle Industry, cab mounting and stable lever system are set
Meter is put forward higher requirement, and vehicle manufacture producer is in the urgent need to the stable lever system CAD software of driver's cabin.Therefore, it is necessary to set up
A kind of accurate, reliable outer biasing non-coaxial driver's cabin stabiliser bar pendulum arm length method for designing, meet cab mounting and
The requirement of stabiliser bar system design, improves product design level and quality, improves vehicle ride performance and safety；Meanwhile,
Design and testing expenses are reduced, accelerates product development speed.
The content of the invention
For defect present in above-mentioned prior art, the technical problem to be solved be to provide it is a kind of easy,
The method for designing of reliable outer biasing non-coaxial driver's cabin stabiliser bar pendulum arm length, its design flow diagram is as shown in Figure 1；It is outer inclined
The structural representation for putting the stable lever system of non-coaxial driver's cabin is as shown in Figure 2；The structural representation of stabiliser bar rubber bushing is such as
Shown in Fig. 3；Stabiliser bar system variant and the geometrical relationship figure of swing arm displacement are as shown in Figure 4.
To solve above-mentioned technical problem, outer biasing non-coaxial driver's cabin stabiliser bar pendulum arm length provided by the present invention
Method for designing, it is characterised in that using following design procedure：
(1) inclination line stiffness K of the stable lever system of driver's cabinwsThe calculating of design requirement value：
According to the roll angular rigidity design requirement value of the stable lever system of driver's cabinSuspension distance L of stabiliser barc, to this
Inclination line stiffness K of the stable lever system of driver's cabinwsDesign requirement value calculated, i.e.,
(2) equivalent combinations Line stiffness expression formula K of outer biasing non-coaxial driver's cabin stabiliser bar rubber bushing is set upx(l1)：
1. rubber bushing radial rigidity kxCalculating
According to the inner circle radius r of rubber sleevea, exradius rb, length Lx, elastic modulus ExWith Poisson's ratio μx, to driver's cabin
Radial rigidity k of stabiliser bar rubber bushingxCalculated, i.e.,
Wherein,
Bessel correction function I (0, α rb), K (0, α rb), I (1, α rb), K (1, α rb), I (1, α ra), K (1, α ra), I
(0,αra), K (0, α ra)；
2. expression formula η of the reversed rubber bushing loading coefficient of outer biasing non-coaxial driver's cabin stabiliser bar is determinedF(l1)
According to torsion tube length LW, Poisson's ratio μ, outer amount of bias T, with pendulum arm length l1For parameter to be designed, it is determined that reversing rubber
Expression formula η of glue bushing loading coefficientF(l1), i.e.,
3. expression formula K of the equivalent combinations Line stiffness of outer biasing non-coaxial stabiliser bar rubber bushing is set upx(l1)
According to radial rigidity k of the rubber bushing obtained by calculating in 1. stepx, and the torsion rubber 2. set up in step
Loading coefficient expression formula η of glue bushingF(l1), with stabiliser bar pendulum arm length l1For parameter to be designed, outer biasing is set up non-coaxial
The equivalent combinations Line stiffness K of formula driver's cabin stabiliser bar rubber bushingx(l1) expression formula, i.e.,
(3) equivalent Line stiffness expression formula K of outer biasing non-coaxial driver's cabin torsion tube is set upT(l1)：
According to torsion tube length Lw, internal diameter d, outer diameter D, elastic modulus E and Poisson's ratio μ, and outer amount of bias T, with pendulum arm length l1
For parameter to be designed, the equivalent line stiffness K of the torsion tube in suspension installed position of outer biasing non-coaxial stabiliser bar is set upT
(l1) expression formula, i.e.,
(4) outer biasing non-coaxial driver's cabin stabiliser bar pendulum arm length l is set up1Design mathematic model and it is set
Meter：
According to calculated stabiliser bar system inclination line stiffness design requirement value K in step (1)ws, in step (2) 3.
Expression formula K of the equivalent combinations Line stiffness of rubber bushing determined by stepx(l1), and torsion tube determined by step (3) etc.
Expression formula K of effect Line stiffnessT(l1), set up pendulum arm length l of outer biasing non-coaxial driver's cabin stabiliser bar1Design mathematic model,
I.e.
Kws[KT(l1)+KX(l1)]-KT(l1)KX(l1)=0；
Using Matlab programs, solve above-mentioned with regard to l1Equation, pendulum arm length l is just obtained1Design flow；
(5) the ANSYS simulating, verifyings of non-coaxial driver's cabin stabiliser bar system roll angular rigidity are biased outward：
Using ANSYS finite element emulation softwares, according to the pendulum arm length design of outer biasing non-coaxial driver's cabin stabiliser bar
Value l1And other structural parameters and material characteristic parameter, set up ANSYS phantoms, grid division, and the suspension in swing arm and pacify
Imposed load F at holding position, the deformation to stablizing lever system carries out ANSYS emulation, and emulation obtains stablizing lever system in swing arm most
Deformation displacement amount f at the A of outer endA；
According to deformation displacement amount f of the swing arm outermost end obtained by ANSYS emulationA, pendulum arm length l1, the suspension peace of swing arm
Distance, delta l of the holding position to outermost end1, suspension distance L of stabiliser barc, the load applied at the suspension installation site of swing arm
Calculated rubber bushing radial rigidity k in 1. step in F, and step (2)x, using stabiliser bar system variant and swing arm
The geometrical relationship of displacement, imitates the ANSYS of the roll angular rigidity of the stable lever system of designed outer biasing non-coaxial driver's cabin
True validation valueCalculated, i.e.,
By the roll stiffness design requirement value of the stable lever system of the non-coaxial driver's cabinWith the simulating, verifying of ANSYS
ValueIt is compared, so as to method for designing and ginseng to the outer biasing non-coaxial driver's cabin stabiliser bar pendulum arm length for being provided
Number design load is verified.
The present invention has the advantage that than prior art
It it is one by rigid body, elastomer and flexible body three's group due to the stable lever system of outer biasing non-coaxial driver's cabin
Into coupling body, and because bias outside torsion tube also exist reverse and bend coupling, simultaneously as the Rigidity Calculation of rubber bushing
It is extremely complex, therefore, for the design of outer biasing non-coaxial driver's cabin stabiliser bar pendulum arm length, fail to provide reliable always
Resolution design method.At present, mostly it is, using ANSYS simulation softwares, to lead to both at home and abroad for the design of the stable lever system of driver's cabin
Crossing the characteristic of driver's cabin stable lever system of the solid modelling to giving structure carries out simulating, verifying, although the method can be compared
Reliable simulation numerical, however, because ANSYS simulation analysis can only be verified to the stabiliser bar of given parameters, it is impossible to provide
Accurate analytical design method formula, it is impossible to realize analytical design method, can not meet wanting for the stable lever system CAD software exploitation of driver's cabin
Ask.With the continuous improvement of the fast-developing and Vehicle Speed of Vehicle Industry, cab mounting and stable lever system are set
Meter is put forward higher requirement, and vehicle manufacture producer is in the urgent need to the stable lever system CAD software of driver's cabin.
The present invention stablizes the structure and material characteristic parameter of lever system according to driver's cabin, using roll angular rigidity design requirement
The pendulum arm length of value and stabiliser bar, and radial rigidity k with rubber bushingx, equivalent combinations Line stiffness, the load of reversed rubber bushing
Relation between lotus coefficient and the equivalent Line stiffness of torsion tube, establishes outer biasing non-coaxial driver's cabin stabiliser bar pendulum arm length
Design mathematic model, and solution design is carried out to it using Matlab programs.Can by designing example and ANSYS simulating, verifyings
Know, the design load of the available accurately and reliably outer biasing non-coaxial driver's cabin stabiliser bar pendulum arm length of the method, is driver's cabin
Suspension and stabiliser bar system design provide reliable method for designing, and establish for the stable lever system CAD software exploitation of driver's cabin
Reliable technical foundation is determined.Using the method, design level, quality and the property of cab mounting and stable lever system can be improved
Can, meet the design requirement of stabiliser bar roll angular rigidity, improve ride performance and the safety of vehicle；Meanwhile, can also reduce
Design and testing expenses, accelerate product development speed.
For a better understanding of the present invention, it is described further below in conjunction with the accompanying drawings.
Fig. 1 is the design flow diagram of outer biasing non-coaxial driver's cabin stabiliser bar pendulum arm length；
Fig. 2 is the structural representation of the stable lever system of outer biasing non-coaxial driver's cabin；
Fig. 3 is the structural representation of rubber bushing；
Fig. 4 is the geometrical relationship figure of outer biasing non-coaxial driver's cabin stabiliser bar system variant and swing arm displacement；
Fig. 5 is the equivalent line stiffness K of the torsion tube of embodiment oneTWith pendulum arm length l1Change curve；
Fig. 6 is the stabiliser bar system roll angular rigidity of embodiment oneWith pendulum arm length l1Change curve；
Fig. 7 is the deformation simulation cloud atlas of the stable lever system of outer biasing non-coaxial driver's cabin of embodiment one；
Fig. 8 is the equivalent line stiffness K of the torsion tube of embodiment twoTWith pendulum arm length l1Change curve；
Fig. 9 is the stabiliser bar system roll angular rigidity of embodiment twoWith pendulum arm length l1Change curve；；
Figure 10 is the deformation simulation cloud atlas of the stable lever system of outer biasing non-coaxial driver's cabin of embodiment two.
Specific embodiment
The present invention is described in further detail below by embodiment.
Embodiment one：The structure that certain outer biasing non-coaxial driver's cabin stablizes lever system is symmetrical, as shown in Fig. 2 bag
Include：Swing arm 1, suspended rubber bushing 2, reversed rubber bushing 3, torsion tube 4；Wherein, torsion tube 4 is not coaxial with reversed rubber bushing 3, turns round
Outer amount of bias T=30mm of pipe 4；The distance between the swing arm 1 of left and right two LcThe suspension distance of=1550mm, i.e. stabiliser bar；It is outstanding
Put the distance between rubber bushing 2 and reversed rubber bushing 3, i.e. pendulum arm length l1, it is parameter to be designed；The suspension peace of swing arm
Distance, deltas l of the holding position C to outermost end A1=47.5mm；Length L of torsion tube 4w=1500mm, internal diameter d=35mm, outer diameter D=
50mm, elastic modulus E=200GPa, Poisson's ratio μ=0.3；The structure and material characteristic of four rubber bushings 2 and 3 in left and right is complete
It is identical, as shown in figure 3, including：Interior round buss 5, rubber sleeve 6, outer round buss 7, wherein, the interior circular diameter d of interior round buss 5x=
35mm, wall thickness δ=2mm；Length L of rubber sleeve 6x=25mm, inner circle radius ra=19.5mm, exradius rb=34.5mm, bullet
Property modulus Ex=7.84MPa, Poisson's ratio μx=0.47.The required value of the design of the driver's cabin stabiliser bar roll angular rigidityPendulum arm length l of lever system is stablized to the outer biasing non-coaxial driver's cabin1It is designed, and
Roll angular rigidity to stablizing lever system in the case of load F=5000N carries out ANSYS simulating, verifyings.
The method for designing of the outer biasing non-coaxial driver's cabin stabiliser bar pendulum arm length that present example is provided, its design
Flow process is as shown in figure 1, comprise the following steps that：
(1) inclination line stiffness K of the stable lever system of driver's cabinwsThe calculating of design requirement value：
According to the design requirement value of stabiliser bar system roll angular rigidityThe suspension of stabiliser bar
Apart from Lc=1550mm, inclination line stiffness K to the stable lever system of driver's cabinwsDesign requirement value calculated, i.e.,
(2) equivalent combinations Line stiffness expression formula K of outer biasing non-coaxial driver's cabin stabiliser bar rubber bushing is set upx(l1)：
1. rubber bushing radial rigidity kxCalculating
According to the inner circle radius r of rubber sleevea=19.5mm, exradius rb=34.5mm, length Lx=25mm, springform
Amount Ex=7.84MPa and Poisson's ratio μx=0.47, radial rigidity k to driver's cabin stabiliser bar rubber bushingxCalculated, i.e.,
Wherein,
Bessel correction function I (0, α rb)=5.4217 × 10-3, K (0, α rb)=8.6369 × 10-6；
I(1,αrb)=5.1615 × 103, K (1, α rb)=9.0322 × 10-6；
I(1,αra)=63.7756, K (1, α ra)=0.0013,
I(0,αra)=69.8524, K (0, α ra)=0.0012；
2. expression formula η of the reversed rubber bushing loading coefficient of outer biasing non-coaxial driver's cabin stabiliser bar is determinedF(l1)
According to torsion tube length LW=1500mm, Poisson's ratio μ=0.3, and outer amount of bias T=30mm, with pendulum arm length l1To treat
Design parameter, determines loading coefficient expression formula η of reversed rubber bushingF(l1), i.e.,
3. expression formula K of the equivalent combinations Line stiffness of outer biasing non-coaxial stabiliser bar rubber bushing is set upx(l1)
According to the k obtained by calculating in 1. stepx=2.1113 × 106N/m, and the η for 2. being set up in stepF(l1)=
0.416l1, with stabiliser bar pendulum arm length l1For parameter to be designed, set up outer biasing non-coaxial stabiliser bar rubber bushing etc.
Effect combination Line stiffness expression formula Kx(l1), i.e.,
(3) equivalent Line stiffness expression formula K of outer biasing non-coaxial driver's cabin torsion tube is set upT(l1)：
According to torsion tube length Lw=1500mm, internal diameter d=35mm, outer diameter D=50mm, elastic modulus E=200GPa, Poisson
Than μ=0.3, and outer amount of bias T=30mm, with pendulum arm length l1For parameter to be designed, set up outer biasing non-coaxial and stablize
Equivalent line stiffness K of the torsion tube of bar at suspension installation site CT(l1) expression formula, i.e.,
Wherein, the equivalent line stiffness K of the torsion tubeTWith pendulum arm length l1Change curve, as shown in Figure 5；
(4) outer biasing non-coaxial driver's cabin stabiliser bar pendulum arm length l is set up1Design mathematic model and it is set
Meter：
According to calculated K in step (1)ws=2.460867 × 105N/m, determined by the 3. step in step (2) And determined by step (3)Set up outer biasing non-coaxial to drive
Sail pendulum arm length l of room stabiliser bar1Design mathematic model, i.e.,
Kws[KT(l1)+KX(l1)]-KT(l1)KX(l1)=0；
Using Matlab programs, solve above-mentioned with regard to l1Equation, the non-coaxial driver's cabin stabiliser bar swing arm can be obtained
Length l1Design flow, i.e.,
l1=380mm
Wherein, the roll angular rigidity of the stable lever systemWith pendulum arm length l1Change curve, as shown in Figure 6；
(5) the ANSYS simulating, verifyings of non-coaxial driver's cabin stabiliser bar system roll angular rigidity are biased outward：
Using ANSYS finite element emulation softwares, according to the pendulum arm length of the stable lever system of outer biasing non-coaxial driver's cabin
Design load l1=380mm and other structural parameters and material characteristic parameter, set up ANSYS phantoms, grid division, and are putting
Imposed load F=5000N at suspension installation site C of arm, the deformation to the stable lever system carries out ANSYS emulation, emulates institute
The deformation simulation cloud atlas for obtaining, as shown in fig. 7, wherein, deformation displacement amount f of swing arm outermost end AAFor
fA=19.984mm；
According to deformation displacement amount f at swing arm outermost end A obtained by ANSYS emulationA=19.984mm, pendulum arm length l1
=380mm, distance, delta l of suspension installation site C of swing arm to outermost end A1=47.5mm, suspension distance L of stabiliser barc=
1500mm, calculates in the 1. step in load F=5000N applied at suspension installation site C of swing arm, and step (2)
The k for obtainingx=2.1113 × 106N/m, using stabiliser bar system variant and the geometrical relationship of swing arm displacement, as shown in figure 4, to this
The ANSYS validation values of driver's cabin stabiliser bar system roll angular rigidityCalculated, i.e.,
Understand：The ANSYS simulating, verifying values of the roll angular rigidity of the stable lever system of the driver's cabin
With design requirement valueMatch, relative deviation is only 0.916%；As a result show to be provided
The method for designing of outer biasing non-coaxial driver's cabin stabiliser bar pendulum arm length be correct, pendulum arm length l1Parameter design value
It is accurately and reliably.
Embodiment two：Certain outer biasing non-coaxial driver's cabin stablizes the structure of lever system and the version phase of embodiment one
Together, as shown in Fig. 2 wherein, torsion tube 4 is not coaxial with reversed rubber bushing 3, outer amount of bias T=30mm of torsion tube 4；Left and right two
The distance between swing arm 1 LcThe suspension distance of=1400mm, i.e. stabiliser bar；Between suspended rubber bushing 2 and reversed rubber bushing 3
Apart from l1, i.e. pendulum arm length is parameter to be designed；Distance, delta l of suspension installation site C of swing arm to outermost end A1=
52.5mm；Length L of torsion tube 4w=1000mm, internal diameter d=42mm, outer diameter D=50mm；The structure of four rubber bushings in left and right is all
It is identical, as shown in figure 3, wherein, the interior circular diameter d of interior round buss 5x=35mm, wall thickness δ=5mm；Length L of rubber sleeve 6x
=40mm, inner circle radius ra=22.5mm, exradius rb=37.5mm.The material behavior of stabiliser bar and the material of rubber bushing
Characteristic, identical with embodiment one, the i.e. elastic modulus E=200GPa of torsion tube, Poisson's ratio μ=0.3；The elastic modelling quantity of rubber sleeve
Ex=7.84MPa, Poisson's ratio μx=0.47.The required value of the design of the driver's cabin stabiliser bar roll angular rigidityPendulum arm length l to the outer biasing non-coaxial driver's cabin stabiliser bar1It is designed, and
Roll angular rigidity in the case of load F=5000N to stablizing lever system carries out ANSYS simulating, verifyings.
Using the step identical with embodiment one, pendulum arm length l to the outer biasing non-coaxial driver's cabin stabiliser bar1Enter
Row design, i.e.,：
(1) inclination line stiffness K of the stable lever system of driver's cabinwsThe calculating of design requirement value：
According to the design requirement value of stabiliser bar system roll angular rigidityStabiliser bar it is outstanding
Put apart from Lc=1400mm, inclination line stiffness K to the stable lever system of the driver's cabinwsDesign requirement value is calculated, i.e.,
(2) equivalent combinations Line stiffness expression formula K of outer biasing non-coaxial driver's cabin stabiliser bar rubber bushing is set upx(l1)：
1. rubber bushing radial rigidity kxCalculating
According to the inner circle radius r of rubber sleevea=22.5mm, exradius rb=37.5mm, length Lx=40mm, springform
Amount Ex=7.84MPa and Poisson's ratio μx=0.47, radial rigidity k to the driver's cabin stabiliser bar rubber bushingxCalculated, i.e.,
Wherein,
Bessel correction function I (0, α rb)=214.9082, K (0, α rb)=3.2117 × 10-4；
I(1,αrb)=199.5091, K (1, α rb)=3.4261 × 10-4；
I(1,αra)=13.5072, K (1, α ra)=0.0083,
I(0,αra)=15.4196, K (0, α ra)=0.0075；
2. expression formula η of the reversed rubber bushing loading coefficient of outer biasing non-coaxial driver's cabin stabiliser bar is determinedF(l1)
According to torsion tube length LW=1000mm, Poisson's ratio μ=0.3, outer amount of bias T=30mm, with pendulum arm length l1To wait to set
Meter parameter, determines loading coefficient expression formula η of the reversed rubber bushing of the driver's cabin stabiliser barF(l1), i.e.,
3. expression formula K of the equivalent combinations Line stiffness of outer biasing non-coaxial stabiliser bar rubber bushing is set upx(l1)
According to the k obtained by calculating in 1. stepx=4.2085 × 106N/m, and the η for 2. being set up in stepF(l1)=
0.936l1, with stabiliser bar pendulum arm length l1For parameter to be designed, the outer biasing non-coaxial driver's cabin stabiliser bar rubber is set up
Expression formula K of the equivalent combinations Line stiffness of bushingx(l1), i.e.,
(3) equivalent Line stiffness expression formula K of outer biasing non-coaxial driver's cabin torsion tube is set upT(l1)：
According to torsion tube length Lw=1000mm, internal diameter d=42mm, outer diameter D=50mm, elastic modulus E=200GPa, Poisson
Than μ=0.3, and outer amount of bias T=30mm, with pendulum arm length l1For parameter to be designed, set up outer biasing non-coaxial and stablize
Equivalent line stiffness K of the torsion tube of bar at suspension installation site CT(l1) expression formula, i.e.,
Wherein, the equivalent line stiffness K of the torsion tubeTWith pendulum arm length l1Change curve, as shown in Figure 8；
(4) outer biasing non-coaxial driver's cabin stabiliser bar pendulum arm length l is set up1Design mathematic model and it is set
Meter：
According to calculated K in step (1)ws=2.97455 × 105N/m, determined by the 3. step in step (2) And determined by step (3)Set up the outer biasing non-coaxial to drive
Sail pendulum arm length l of room stabiliser bar1Design mathematic model, i.e.,
Kws[KT(l1)+KX(l1)]-KT(l1)KX(l1)=0；
Using Matlab programs, solve above-mentioned with regard to l1Equation, the outer biasing non-coaxial driver's cabin can be obtained and stablized
Bar pendulum arm length l1Design load, i.e.,
l1=350mm；
Wherein, the roll angular rigidity of the stable lever system of the driver's cabinWith pendulum arm length l1Change curve, such as Fig. 9 institutes
Show；
(5) the ANSYS simulating, verifyings of non-coaxial driver's cabin stabiliser bar system roll angular rigidity are biased outward：
Using ANSYS finite element emulation softwares, according to the pendulum arm length of the stable lever system of outer biasing non-coaxial driver's cabin
Design load l1=350mm and other structural parameters and material characteristic parameter, set up ANSYS phantoms, grid division, and are putting
Imposed load F=5000N at suspension installation site C of arm, the deformation to the stable lever system of the driver's cabin carries out ANSYS emulation,
Resulting deformation simulation cloud atlas, as shown in Figure 10, wherein, deformation displacement amount f at swing arm outermost end AAFor
fA=17.881mm；
According to deformation displacement amount f at swing arm outermost end A obtained by ANSYS emulationA=17.881mm, pendulum arm length l1
=350mm, distance, delta l of suspension installation site C of swing arm to outermost end A1=52.5mm, suspension distance L of stabiliser barc=
1400mm, calculates in the 1. step in load F=5000N applied at suspension installation site C of swing arm, and step (2)
The k for obtainingx=4.2085 × 106N/m, using stabiliser bar system variant and the geometrical relationship of swing arm displacement, as shown in figure 4, to this
The ANSYS validation values of outer biasing non-coaxial driver's cabin stabiliser bar system roll angular rigidityCalculated, i.e.,
fws=fC+F/kx=16.7367mm；
Understand：The ANSYS simulating, verifying values of the roll angular rigidity of the stable lever system of the driver's cabin
With design requirement valueMatch, relative deviation is only 0.431%；As a result show to be provided is outer
The method for designing of biasing non-coaxial driver's cabin stabiliser bar pendulum arm length is correct, and parameter design value is accurately and reliably.
Claims (1)
1. the method for designing of biasing non-coaxial driver's cabin stabiliser bar pendulum arm length outside, its specific design step is as follows：
(1) inclination line stiffness K of the stable lever system of driver's cabinwsThe calculating of design requirement value：
According to the roll angular rigidity design requirement value of the stable lever system of driver's cabinSuspension distance L of stabiliser barc, to the driving
Inclination line stiffness K of the stable lever system in roomwsDesign requirement value calculated, i.e.,
(2) equivalent combinations Line stiffness expression formula K of outer biasing non-coaxial driver's cabin stabiliser bar rubber bushing is set upx(l1)：
1. rubber bushing radial rigidity kxCalculating
According to the inner circle radius r of rubber sleevea, exradius rb, length Lx, elastic modulus ExWith Poisson's ratio μx, it is stable to driver's cabin
Radial rigidity k of bar rubber bushingxCalculated, i.e.,
Wherein,
Bessel correction function I (0, α rb), K (0, α rb), I (1, α rb), K (1, α rb),
I(1,αra), K (1, α ra), I (0, α ra), K (0, α ra)；
2. expression formula η of the reversed rubber bushing loading coefficient of outer biasing non-coaxial driver's cabin stabiliser bar is determinedF(l1)
According to torsion tube length LW, Poisson's ratio μ, outer amount of bias T, with pendulum arm length l1For parameter to be designed, it is determined that reversing rubber lining
Expression formula η of set loading coefficientF(l1), i.e.,
3. expression formula K of the equivalent combinations Line stiffness of outer biasing non-coaxial stabiliser bar rubber bushing is set upx(l1)
According to radial rigidity k of the rubber bushing obtained by calculating in 1. stepx, and the torsion rubber lining 2. set up in step
Loading coefficient expression formula η of setF(l1), with stabiliser bar pendulum arm length l1For parameter to be designed, set up outer biasing non-coaxial and drive
Sail the equivalent combinations Line stiffness K of room stabiliser bar rubber bushingx(l1) expression formula, i.e.,
(3) equivalent Line stiffness expression formula K of outer biasing non-coaxial driver's cabin torsion tube is set upT(l1)：
According to torsion tube length Lw, internal diameter d, outer diameter D, elastic modulus E and Poisson's ratio μ, and outer amount of bias T, with pendulum arm length l1To treat
Design parameter, sets up the equivalent line stiffness K of the torsion tube in suspension installed position of outer biasing non-coaxial stabiliser barT(l1) table
Up to formula, i.e.,
(4) outer biasing non-coaxial driver's cabin stabiliser bar pendulum arm length l is set up1Design mathematic model and it is designed：
According to calculated stabiliser bar system inclination line stiffness design requirement value K in step (1)ws, the 3. step in step (2)
Determined by rubber bushing equivalent combinations Line stiffness expression formula Kx(l1), and the equivalent line of torsion tube determined by step (3)
Expression formula K of rigidityT(l1), set up pendulum arm length l of outer biasing non-coaxial driver's cabin stabiliser bar1Design mathematic model, i.e.,
Kws[KT(l1)+KX(l1)]-KT(l1)KX(l1)=0；
Using Matlab programs, solve above-mentioned with regard to l1Equation, pendulum arm length l is just obtained1Design flow；
(5) the ANSYS simulating, verifyings of non-coaxial driver's cabin stabiliser bar system roll angular rigidity are biased outward：
Using ANSYS finite element emulation softwares, according to pendulum arm length design load l of outer biasing non-coaxial driver's cabin stabiliser bar1And
Other structures parameter and material characteristic parameter, set up ANSYS phantoms, grid division, and in the suspension installation site of swing arm
Place imposed load F, the deformation to stablizing lever system carries out ANSYS emulation, and emulation obtains stablizing lever system at swing arm outermost end A
Deformation displacement amount fA；
According to deformation displacement amount f of the swing arm outermost end obtained by ANSYS emulationA, pendulum arm length l1, the suspension installation position of swing arm
Put distance, delta l of outermost end1, suspension distance L of stabiliser barc, load F applied at the suspension installation site of swing arm, and
Calculated rubber bushing radial rigidity k in 1. step in step (2)x, using stabiliser bar system variant and swing arm displacement
Geometrical relationship, the ANSYS emulation to the roll angular rigidity of the stable lever system of designed outer biasing non-coaxial driver's cabin tests
Card valueCalculated, i.e.,
By the roll angular rigidity design requirement value of the stable lever system of the non-coaxial driver's cabinWith the simulating, verifying value of ANSYSIt is compared, so as to method for designing and parameter to the outer biasing non-coaxial driver's cabin stabiliser bar pendulum arm length for being provided
Design load is verified.
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201300692Y (en) * | 2008-10-24 | 2009-09-02 | 奇瑞汽车股份有限公司 | Transverse stabilizer for motor vehicle front wheels |
| CN102514634A (en) * | 2011-12-09 | 2012-06-27 | 三一重工股份有限公司 | Rear suspension component and device of car cab |
| US8262106B1 (en) * | 2009-08-13 | 2012-09-11 | Suszynsky Karol T | Oxygen tank holder |
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|---|---|---|---|---|
| CN201300692Y (en) * | 2008-10-24 | 2009-09-02 | 奇瑞汽车股份有限公司 | Transverse stabilizer for motor vehicle front wheels |
| US8262106B1 (en) * | 2009-08-13 | 2012-09-11 | Suszynsky Karol T | Oxygen tank holder |
| CN102514634A (en) * | 2011-12-09 | 2012-06-27 | 三一重工股份有限公司 | Rear suspension component and device of car cab |
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| Title |
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| 稳定杆橡胶衬套的变形及径向刚度分析;路银行 等;《河南省汽车工程科技学术研讨会》;20141028;第229-230页 * |
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