CN104200040B - The design method of vehicle suspension stabilizer bar Rigidity Matching and diameter - Google Patents
The design method of vehicle suspension stabilizer bar Rigidity Matching and diameter Download PDFInfo
- Publication number
- CN104200040B CN104200040B CN201410475786.2A CN201410475786A CN104200040B CN 104200040 B CN104200040 B CN 104200040B CN 201410475786 A CN201410475786 A CN 201410475786A CN 104200040 B CN104200040 B CN 104200040B
- Authority
- CN
- China
- Prior art keywords
- backward
- suspension
- roll angular
- design
- vehicle
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Landscapes
- Vehicle Body Suspensions (AREA)
Abstract
The present invention relates to vehicle suspension stabilizer bar Rigidity Matching and the design methods of diameter, belong to vehicle suspension technical field.Due to being restricted by stabiliser bar and rubber bushing radial deformation analytical Calculation and the problem of intercoupling, fail to provide the reliable optimum design method for stablizing shank diameter always.The invention it is characterized in that：First according to vehicle parameter and inclination model, matched design is carried out to forward and backward suspension stabilizer bar system roll angular rigidity；Then, according to roll angular rigidity matched design value, the radial rigidity COEFFICIENT K of rubber bushingxWith the deformation coefficient expression formula G of end part of stabilizer rodw, the mathematical model of optimizing design for stablizing shank diameter d is established, the optimization design value of accurate, reliable stable shank diameter d is obtained using Matlab programs.The design level and performance that suspension and stabiliser bar can be improved using the invention improve ride performance and the safety of vehicle；Meanwhile can also accelerate product development and design speed, reduce design and testing expenses.
Description
Technical field
The present invention relates to vehicle suspensions, especially vehicle suspension stabilizer bar Rigidity Matching and the design method of diameter.
Background technology
Lateral stability lever system is one of important composition component of vehicle suspension system, in Vehicular turn when driving to prevent
Vehicle body occurs excessive inclination and rolls angular oscillation.The stabilizer bar that roll stiffness matches is added in vehicle suspension system
System, it is possible to reduce it is this laterally to roll, if the forward and backward suspension roll angle Rigidity Matching of vehicle and diameter design are improper, it will shadow
Ring the steering characteristic of vehicle.Simultaneously as the roll angular rigidity of stabilizer bar system, not only by vehicle parameter and stabilizator rod structure and
The influence of material characteristic parameter is also influenced by the structure and material characterisitic parameter and installation site of rubber bushing.Therefore, how
According to vehicle parameter and suspension stiffness, Rigidity Matching and diameter design are carried out to stabiliser bar, are vehicle suspension system designs
Critical issue.However due to by end part of stabilizer rod deformation and rubber bushing radial deformation analytical Calculation and intercoupling etc. crucial
The restriction of problem, for suspension stabilizer bar Rigidity Matching and diameter design, home and abroad not yet provides reliable parsing at present
Design method is mostly to establish model using ANSYS simulation softwares, by emulation to lateral stability lever system carry out deformation and just
Degree analysis, although reliable analysis numerical value can be obtained, this method can only be steady under structure and load condition to giving
The deformation of fixed pole system and rigidity are verified, and analytical formula cannot be provided, and are set it is thus impossible to meet the parsing of suspension stabiliser bar
The requirement of meter and CAD software exploitation.With the continuous improvement of Vehicle Industry and travel speed, suspension stabiliser bar Rigidity Matching is set
More stringent requirements are proposed for meter, therefore, it is necessary to establish a kind of accurate, reliable vehicle suspension stabilizer bar Rigidity Matching and straight
The design method of diameter improves vehicle suspension and the design level and performance of stabilizer bar system, improves vehicle ride performance；Together
When, design and testing expenses are reduced, product development speed is accelerated.
Invention content
Defect present in for the above-mentioned prior art, technical problem to be solved by the invention is to provide it is a kind of it is easy,
The design method of reliable vehicle suspension stabilizer bar Rigidity Matching and diameter, design flow diagram is as shown in Figure 1, vehicle side
Motion model figure incline as shown in Fig. 2, the structural schematic diagram of stabiliser bar is as shown in Figure 3.
In order to solve the above technical problems, vehicle suspension stabilizer bar Rigidity Matching provided by the present invention and diameter are set
Meter method, it is characterised in that use following steps.
(1) the required total roll angular rigidity of vehicle suspensionCalculating：
According to automobile body quality ms, vehicle body barycenter and roll between centers distance hs, radius of wheel r, side acceleration ay,
And the vehicle body max. roll required by Car designIgnoring unsprung mass muIn the case of, it is required to vehicle suspension total
Roll angular rigidity is calculated, i.e.,：
Wherein, g is acceleration of gravity；
(2) roll angular rigidity of the forward and backward bearing spring of vehicleWithCalculating：
According to the front tread B of vehiclefWith rear tread Br, forward swing arm lengths T1f, rear-swing arm length T1r, forward and backward bearing spring
Installation site is to the distance between swing arm hinge point T2fAnd T2rAnd the Line stiffness k of forward and backward bearing springsfAnd ksr, to forward and backward outstanding
The roll angular rigidity of frame spring, is respectively calculated, i.e.,：
(3) front suspension stabilizer bar system roll angular rigidity Theoretical Design value is determinedDesign License Value and range：
According to the required total roll angular rigidity of obtained vehicle suspension in step (1)And it is determined in step (2)
Bearing spring roll angular rigidityWithDetermine front suspension stabilizer bar system roll angular rigidity Theoretical Design value most
Big License ValueWith minimum License ValueRespectively：
Therefore, front suspension stabilizer bar system roll angular rigidity Theoretical Design valueLicense value range be：
(4) forward and backward suspension stabilizer bar system roll angular rigidity actual design valueWithMatched design：
IfThe then Theoretical Design value of the forward and backward suspension stabilizer bar system roll angular rigidity of vehicleWithIt is equal to zero, i.e.,The namely forward and backward suspension of the vehicle need not add stabilizer bar；
IfMatched design then is carried out to forward and backward suspension stabilizer bar system roll angular rigidity actual design value,
I.e.：A：According to the license value range of identified front suspension stabilizer bar system roll angular rigidity Theoretical Design value in step (3)The theory that an angle of heel rigidity value is chosen as front suspension stabiliser bar roll angular rigidity is set
Evaluation
B：According to the Theoretical Design value of identified front suspension stabilizer bar system roll angular rigidity in step AAnd step
Suddenly in (3)Value, the Theoretical Design value of rear suspension stabilizer bar system roll angular rigidity is calculated, i.e.,：
C：According in step AIn step BIt calculatesThe size of ratio, and according to than
Value size decides whether to install rear suspension stabiliser bar：
If ratioThen identified Theoretical Design value in step AAs front suspension is stablized
Lever system roll angular rigidity actual design valueAnd identified Theoretical Design value in step BAs rear suspension is steady
Fixed pole system roll angular rigidity actual design value
If ratioThen take the actual design value of rear suspension stabilizer bar system roll angular rigidityI.e. rear suspension is not provided with stabiliser bar；The actual design value of front suspension stabiliser bar roll angular rigidityThat is the actual design value of front suspension stabiliser bar roll angular rigidityStablize bar side equal to front suspension
The maximum allowable value of inclination angle rigidity value
(5) calculating of the deformation coefficient of forward and backward suspension end part of stabilizer rod vertical deviation：
According to the total length l of forward and backward suspension stabiliser barcfAnd lcr, the mounting distance l of intermediate two rubber bushings0fAnd l0r,
The brachium l of forward and backward stabilizer bar1fAnd l1r, the transition arc radius R of forward and backward stabilizer barfAnd Rr, the circle of transition arc
Heart angle θfAnd θrAnd elastic properties of materials model E and Poisson's ratio μ, to the deformation coefficient G of forward and backward suspension end part of stabilizer rod vertical deviationwf
And GwrIt is calculated, respectively：
In formula,
Q6f=32 (μ+1) [Rf(cosθf-1)-l1fsinθf]2[2l1fcosθf-lcf+2Rfsinθf]；
Q6r=32 (u+1) [Rr(cosθr-1)-l1rsinθr]2[2l1rcosθr-lcr+2Rrsinθr]；
(6) forward and backward stabiliser bar rubber bushing radial line stiffness K is establishedxfAnd KxrExpression formula：
According to the axial length L of forward and backward rubber bushingfAnd Lr, thickness hfAnd hr, elastic modulus Ex, Poisson's ratio μx, rubber lining
Cover wall thickness of internal cylindrical sleeve Δ lfWith Δ lrIf the value to be designed of forward and backward stable shank diameter is respectively dfAnd dr, therefore, forward and backward rubber
The inner circle radius and exradius of glue bushing, can be expressed as：
So the expression formula of forward and backward rubber bushing radial direction Line stiffness, can be expressed as：
In formula, Kxf(df) and Kxr(dr) it is respectively that forward and backward suspension stablizes shank diameter dfAnd drExpression formula；
b1f=[I (1, αaf)K(0,αaf)+I(0,αaf)K(1,αaf)]Mf,
b2f=-[I (1, αbf)K(0,αaf)+I(0,αaf)K(1,αbf)]Pf,
Bessel correction functions：I(0,αbf), K (0, αbf), I (1, αbf), K (1, αbf)；I(1,αaf), K (1, αaf),
I(0,αaf), K (0, αaf)；
Wherein,
b1r=[I (1, αar)K(0,αar)+I(0,αar)K(1,αar)]Mr,
b2r=-[I (1, αbr)K(0,αar)+I(0,αar)K(1,αbr)]Pr,
Bessel correction functions：I(0,αbr), K (0, αbr), I (1, αbr), K (1, αbr)；
I(1,αar), K (1, αar), I (0, αar), K (0, αar)；
(7) forward and backward suspension stablizes shank diameter dfAnd drThe foundation and design of mathematical model of optimizing design：
According to the wheelspan B of the forward and backward bridge of vehiclefAnd Br, the total length l of forward and backward stabilizer barcfAnd lcr, forward and backward stabiliser bar
The mounting distance l of intermediate two rubber bushings0fAnd l0r, the middle obtained forward and backward suspension stabilizer bar system of design of step (4)
The actual design value of roll angular rigidityWithThe forward and backward stabiliser bar being calculated in step (5) is vertical in end
The deformation coefficient G of displacementwfAnd GwrAnd in step (6) obtained forward and backward rubber bushing radial direction Line stiffness expression formula Kxf
(df) and Kxr(dr), it establishes forward and backward suspension and stablizes shank diameter dfAnd drMathematical model of optimizing design, respectively：
Using Matlab calculation procedures, above-mentioned mathematical model of optimizing design is solved, it is straight that forward and backward suspension stabiliser bar can be obtained
Diameter dfAnd drOptimization design value.
The present invention has the advantage that than the prior art：
Vehicle suspension stabilizer bar Rigidity Matching is designed in home and abroad at present, is mostly to utilize modeling and simulating software,
Analysis and parameter designing are carried out to stabilizer bar by modeling and simulating, or determines and stablizes with repetition test and modification by rule of thumb
Therefore bar design parameter is unsatisfactory for vehicle fast development and travel speed is continuously improved, the design proposed to stabiliser bar is wanted
It asks.The present invention first according to vehicle parameter and roll model, to the forward and backward required roll angular rigidity of suspension stabilizer bar system into
Row matched design；Then, to stablize shank diameter d as parameter to be designed, according to the roll angular rigidity of stabilizer bar system
With design value, the radial rigidity COEFFICIENT K of rubber bushingxWith the deformation coefficient expression formula G of end part of stabilizer rod vertical deviationw, establish steady
The mathematical model of optimizing design of fixed pole diameter d solves the optimization design value for obtaining stablizing shank diameter d using Matlab softwares.It is logical
Example design and ANSYS simulating, verifyings are crossed it is found that the vehicle suspension stabilizer bar Rigidity Matching and the design method of diameter are
Accurately, reliably.The optimization design value that accurate, reliable stable shank diameter d can be obtained using the invention, meet vehicle traveling and
To the design requirement of stabiliser bar roll angular rigidity, the design level and performance of suspension and stabiliser bar are improved, the traveling of vehicle is improved
Ride comfort and safety；Meanwhile design and testing expenses can be also reduced, accelerate product development and design speed, and be stabiliser bar
System CAD software is developed, and reliable design method and technology are provided.
Description of the drawings
Invention is described further below in conjunction with the accompanying drawings in order to better understand.
Fig. 1 is the flow chart of vehicle suspension stabilizer bar Rigidity Matching and diameter design；
Fig. 2 is vehicle roll motion illustraton of model；
Fig. 3 is the structural schematic diagram of lateral stability lever system；
Fig. 4 is the structural schematic diagram of rubber bushing；
Fig. 5 is the roll angular rigidity of the vehicle front suspension stabilizer bar system of embodiment one with stablizing shank diameter dfVariation it is bent
Line；
Fig. 6 is the vehicle roll angle of embodiment oneWith the variation simulation curve of travel speed v；
Fig. 7 is the roll angular rigidity of the forward and backward suspension stabilizer bar system of vehicle of embodiment two with stablizing shank diameter dfChange
Change curve；
Fig. 8 is the vehicle roll angle of embodiment twoWith the variation simulation curve of travel speed v.
Specific implementation mode
Below by embodiment, invention is further described in detail.
Embodiment one：The body quality m of certain vehicles=4690kg, side acceleration ay=0.4g, vehicle body barycenter and inclination
The distance h of between centerss=1069mm, the design requirement value of vehicle roll angleFront suspension pendulum arm length T1f=675mm, bullet
Spring Line stiffness ksf=102.45N/mm, spring center to distance T between swing arm hinge point2f=430mm；Rear suspension pendulum arm length
T1r=650mm, spring wire stiffness Ksr=261N/mm, spring center to distance T between swing arm hinge point2r=400mm；Front tread
Bf=1650mm, rear tread Br=1485mm；The structural schematic diagram of the used stabiliser bar of the forward and backward suspension of the vehicle as shown in figure 3,
Wherein, lcFor the total length of stabiliser bar, lc=lcf=lcr=800mm；l1For brachium, l1=l1f=l1r=150mm；l0For centre
The mounting distance of two rubber bushings, l0=l0f=l0r=400mm；R is transition arc radius, R=Rf=Rr=50mm；θ is
Transition arc central angle, θ=θf=θr=60o；Stablize elastic modulus E=210GPa of bar material, Poisson's ratio μ=0.3.It is forward and backward
The structure and material of stabiliser bar rubber bushing are all identical, the elastic modulus E of rubber bushingx=7.8MPa, Poisson's ratio μx=0.47,
The structural schematic diagram of rubber bushing is as shown in figure 4, stabiliser bar 1, interior round buss 2, rubber bushing 3, outer round buss 4, wherein rubber
Thickness h=h of bushing 1f=hr=10mm, axial length L=Lf=Lr=25mm, the wall thickness Δ l=Δs l of interior round buss 2f=Δ
lr=2.0mm, outer round buss 4 and interior round buss 2 and rubber bushing 3 are matched as one by interior round buss 2 and stabiliser bar 1
Merge and be mounted on stabiliser bar 1, the internal diameter of interior round buss 2 is equal with the diameter d of designed stabiliser bar 1.It is forward and backward to the vehicle outstanding
The Rigidity Matching and diameter d of frame stabilizer bar system are designed.
The design method of vehicle suspension stabilizer bar Rigidity Matching and diameter that present example is provided, design stream
Journey is as shown in Figure 1, be as follows：
(1) the required total roll angular rigidity of vehicle suspensionCalculating：
According to automobile body quality ms=4690kg, side acceleration ay=0.4g, vehicle body barycenter is at a distance from inclination between centers
hs=1069mm, vehicle roll angleIgnoring unsprung mass muIn the case of, total angle of heel required to vehicle suspension
Rigidity is calculated, i.e.,：
(2) roll angular rigidity of the forward and backward bearing spring of vehicleWithCalculating：
According to the front tread B of vehiclef=1650mm and rear tread Br=1485mm, forward swing arm lengths T1f=675mm, it is rear to put
Arm lengths T1r=650mm, forward and backward bearing spring installation site to the distance between swing arm hinge point T2f=430mm and T2r=
The Line stiffness k of 400mm and forward and backward bearing springsf=102.45N/mm and ksr=261N/mm, to the side of forward and backward bearing spring
Inclination angle rigidity is respectively calculated, i.e.,：
(3) front suspension stabilizer bar system roll angular rigidity Theoretical Design value is determinedDesign License Value and range：
According to the required total roll angular rigidity of obtained vehicle suspension in step (1)And
Step
(2) roll angular rigidity of identified bearing spring inWithDetermine front suspension stabilizer bar system roll angular rigidity value Theoretical Design valueMaximum license
ValueWith minimum License ValueRespectively：
Therefore, front suspension stabilizer bar system roll angular rigidity Theoretical Design valueLicense value ranging from：
(4) forward and backward suspension stabilizer bar system roll angular rigidity actual design valueWithMatched design：
A：According to the license value range of front suspension stabilizer bar system roll angular rigidity Theoretical Design value in step (3)
83.329WithChoose certain angle of heel
Theoretical Design value of the rigidity value as front suspension stabiliser bar roll angular rigidity, i.e.,：
B：The Theoretical Design value of rear suspension stabilizer bar system roll angular rigidity is calculated, i.e.,：
Step C：According in step AIn step BMeter
It calculatesThen determine the actual design value of forward and backward suspension stabilizer bar system roll angular rigidity
WithRespectively：
(5) the deformation coefficient G of front suspension end part of stabilizer rodwfCalculating：
According to the total length l of front suspension stabiliser barcf=800mm, the mounting distance l of intermediate two rubber bushings0f=
400mm, the brachium l of preceding stabilizer bar1f=150mm, the transition arc radius R of preceding stabilizer barf=50mm, transition arc
Central angle θf=60。, elastic properties of materials model E=210GPa and Poisson's ratio μ=0.3, to the deformation system of front suspension end part of stabilizer rod
Number is calculated, i.e.,：
In formula,
Q6f=32 (u+1) [Rf(cosθf-1)-l1fsinθf]2[2l1fcosθf-lcf+2Rfsinθf]=- 0.5624m3；；
(6) rubber bushing radial line stiffness K beforexfExpression formula：
According to the axial length L of preceding rubber bushingf=25mm, elastic modulus Ex=7.84MPa, Poisson's ratio μx=0.47, it is preceding
The wall thickness of internal cylindrical sleeve Δ l of rubber bushingf=2.0mm, rubber bushing thickness hf=10mm, if front stabilizer diameter is to be designed
Parameter is df, then the expression formula of preceding rubber bushing radial direction Line stiffness, is represented by：
In formula, variable dfStablize the value to be designed of shank diameter for front suspension；
b1f=[I (1, αaf)K(0,αaf)+I(0,αaf)K(1,αaf)]Mf,
b2f=-[I (1, αbf)K(0,αaf)+I(0,αaf)K(1,αbf)]Pf,
Bessel correction functions：I(0,αbf), K (0, αbf), I (1, αbf), K (1, αbf)；
I(1,αaf), K (1, αaf), I (0, αaf), K (0, αaf)；
(7) front suspension stablizes shank diameter dfDesign：
According to vehicle front tread Bf=1650mm, the total length l of front suspension stabiliser barcf=800mm, two rubber bushings it
Between mounting distance l0f=400mm, the roll angular rigidity of the middle obtained front suspension stabilizer bar system of design of step (4) is practical to be set
EvaluationDeformation coefficient G of the front stabilizer being calculated in step (5) in endwf=
1.5935×10-12m5Obtained preceding rubber bushing radial direction Line stiffness expression formula K in/N and step (6)xf(df), establish front overhang
Frame stablizes shank diameter dfDesign mathematic model, i.e.,：
Calculation procedure is write using Matlab, front suspension can be acquired and stablize shank diameter dfAnalytical design method value be df=
19.8mm, rounding obtain front suspension and stablize shank diameter dfActual design value df=20mm；Wherein, which stablizes leverage
The roll angular rigidity of system is with stablizing shank diameter dfChange curve, as shown in Figure 5.
As stabiliser bar diameter design value df=20mm, the Line stiffness K of the Chinese herbaceous peony stabilizer bar systemw=84.23N/mm stablizes
The roll angular rigidity checking computations value of lever systemWhen vehicle is with speed v=50km/h, radius r=50m
When Turning travel, vehicle roll angleMeetDesign requirement.
To the vehicle at given turning radius 50m, stabilizer bar is matched to the vehicle suspension using Matlab softwares
Vehicle roll angle before and after installationIt is emulated with the variation of speed v, it is as shown in Figure 6 to emulate obtained curve；
By comparing installing the stabilizer bar of Rigidity Matching and not installing stabiliser bar, it is known that vehicle roll angle when speed 60km/h
49.53% is reduced, shows that the design method of the vehicle suspension stabilizer bar Rigidity Matching and diameter is correct, reliable.
Embodiment two：Known certain automobile body quality ms=5000kg, side acceleration ay=0.4g, vehicle body barycenter and side
Incline the distance h of between centerss=1150mm, vehicle roll angleThe spring Line stiffness k of vehicle front suspensionsf=90.761N/mm,
The spring Line stiffness k of rear suspensionsr=176.23N/mm；Front tread Bf=1650mm, rear tread Br=1600mm；Front suspension swing arm
Length T1f=660mm, front suspension spring center to distance T between homonymy swing arm hinge point2f=450mm；Rear-swing arm length T1r=
650mm, rear suspension spring installation center to distance T between homonymy transverse arm hinge joint2r=400mm.The knot of stabiliser bar, rubber bushing
Structure and material property are identical in example one as applying.Stablize shank diameter to fore suspension and rear suspension to be designed.
Using the step of applying example one, the diameter d of the forward and backward suspension stabiliser bar of the vehicle is designed.
(1) the required total roll angular rigidity of vehicle suspensionCalculating：
According to automobile body quality ms=5000kg, side acceleration ay=0.4g, vehicle body barycenter is at a distance from inclination between centers
hs=1150mm, the max. roll required by vehicle body designTotal roll angular rigidity required to vehicle suspension carries out
It calculates, i.e.,：
In formula, g acceleration of gravity, g=9.8m/s2；
(2) roll angular rigidity of the forward and backward bearing spring of vehicleWithCalculating：
According to the front tread B of vehiclef=1650mm and rear tread Br=1600mm, forward swing arm lengths T1f=660mm, it is rear to put
Arm lengths T1r=650mm, forward and backward bearing spring installation site to the distance between swing arm hinge point T2f=450mm and T2r=
The Line stiffness k of 400mm and forward and backward bearing springsf=90.761N/mm and ksr=176.23N/mm, to forward and backward bearing spring
Roll angular rigidity be respectively calculated, i.e.,：
(3) front suspension stabilizer bar system roll angular rigidity Theoretical Design value is determinedDesign License Value and range：
According to obtained total roll angular rigidity in step (1)And it is determined in step (2)
Bearing spring roll angular rigidityWithDetermine front suspension stabiliser bar
The maximum allowable value of system angle of heel rigidity valueWith minimum License ValueRespectively：
Therefore, the license value range of front suspension stabilizer bar system roll angular rigidity Theoretical Design value is：
(4) forward and backward suspension stabilizer bar system roll angular rigidity actual design valueWithMatched design：
A：According to the tolerance band of front suspension stabilizer bar system roll angular rigidity design value in step (3) WithChoose certain roll angular rigidity
It is worth the Theoretical Design value as front suspension stabiliser bar roll angular rigidity, i.e.,：
B：The Theoretical Design value of rear suspension stabilizer bar system roll angular rigidity is calculated, i.e.,：
Step C：According in step AIn step B
It calculatesThen determine the actual design value of forward and backward suspension stabilizer bar system roll angular rigidityWithRespectively：
(5) the deformation coefficient G of forward and backward suspension end part of stabilizer rodwfAnd GwrCalculating：
Due to the structure and material of the forward and backward suspension stabiliser bar of the vehicle, all with apply the identical of example one, therefore, the vehicle
The deformation coefficient of forward and backward suspension end part of stabilizer rod, also with apply the identical of example one, i.e.,：
Gwf=1.5935 × 10-12m5/ N, Gwr=1.5935 × 10-12m5/N；
(6) forward and backward rubber bushing radial line stiffness KxfAnd KxrExpression formula：
Due to the wall thickness h of the forward and backward suspension stabiliser bar rubber bushing of the vehicle, material property ExAnd μxAnd the thickness of interior round buss
Spend Δ l, it is all identical, and with apply the identical of example one, i.e. hf=hr=h, Δ lf=Δ lr=Δ l, only fore suspension and rear suspension stabiliser bar
Diameter dfAnd drDifference, therefore, the forward and backward rubber bushing radial line stiffness K of the vehiclexfAnd KxrExpression formula, can indicate respectively
For：
In formula, variable dfAnd drStablize the value to be designed of shank diameter for forward and backward suspension；
(7) forward and backward suspension stablizes shank diameter dfAnd drDesign：
According to vehicle front and rear wheel away from Bf=1650mm and rear tread Br=1600mm, the total length l of stabiliser barc=800mm,
The mounting distance l of intermediate two rubber bushings0=400mm, the middle obtained forward and backward suspension stabilizer bar system of design of step (4)
Roll angular rigidity actual design valueKN.m/rad andStep (5) is fallen into a trap
Deformation coefficient G of the obtained forward and backward suspension stabiliser bar in endwf=1.5935 × 10-12m5/ N and Gwr=1.5935 × 10- 12m5Obtained forward and backward rubber bushing radial direction Line stiffness expression formula K in/N and step (6)xf(df) and Kxr(dr), it establishes respectively
Forward and backward suspension stablizes shank diameter dfAnd drDesign mathematic model, i.e.,：
Calculation procedure is write using Matlab, forward and backward suspension can be acquired and stablize shank diameter dfAnd drAnalytical design method value,
Respectively df=21.4mm and dr=19.0mm, rounding obtain forward and backward suspension and stablize shank diameter dfAnd drActual design value df=
22.0mm and dr=19mm, wherein the roll angular rigidity of the forward and backward suspension stabilizer bar system of the vehicle is with stablizing shank diameter dfWith
drChange curve, as shown in Figure 7.
Currently, rear stabilizer bar diameter design value df=22mm and dr=19mm, the Line stiffness of the vehicle front stabilizer system
Kwsf=116.21N/mm, the Line stiffness K of rear stabilizer bar systemwsr=70.418N/mm；The roll angular rigidity of front stabilizer system
Checking computations valueThe roll angular rigidity checking computations value of rear stabilizer bar system
When vehicle is with speed v=50km/h, when radius r=50m Turning travels, vehicle roll angleMeetSet
Meter requires.
To the vehicle at given turning radius 50m, stabilizer bar is matched to the vehicle suspension using Matlab softwares
Vehicle roll angle before and after installationIt is emulated with the variation of speed v, it is as shown in Figure 8 to emulate obtained curve；
By comparing installing the stabilizer bar of Rigidity Matching and not installing stabiliser bar, it is known that vehicle roll angle when speed 60km/h
59.348% is reduced, shows that the design method of the vehicle suspension stabilizer bar Rigidity Matching and diameter is correct, reliable.
Claims (1)
1. the design method of vehicle suspension stabilizer bar Rigidity Matching and diameter, is as follows：
(1) the required total roll angular rigidity of vehicle suspensionCalculating：
According to automobile body quality ms, vehicle body barycenter and roll between centers distance hs, radius of wheel r, side acceleration ayAnd vehicle
The required vehicle body max. roll of designIgnoring unsprung mass muIn the case of, total inclination required to vehicle suspension
Angular rigidity is calculated, i.e.,：
Wherein, g is acceleration of gravity；
(2) roll angular rigidity of the forward and backward bearing spring of vehicleWithCalculating：
According to the front tread B of vehiclefWith rear tread Br, forward swing arm lengths T1f, rear-swing arm length T1r, forward and backward bearing spring installation
Position is to the distance between swing arm hinge point T2fAnd T2rAnd the Line stiffness k of forward and backward bearing springsfAnd ksr, to forward and backward suspension bullet
The roll angular rigidity of spring, is respectively calculated, i.e.,：
(3) front suspension stabilizer bar system roll angular rigidity Theoretical Design value is determinedDesign License Value and range：
According to the required total roll angular rigidity of obtained vehicle suspension in step (1)And it is identified outstanding in step (2)
The roll angular rigidity of frame springWithDetermine that the maximum of front suspension stabilizer bar system roll angular rigidity Theoretical Design value is permitted
It can be worthWith minimum License ValueRespectively：
Therefore, front suspension stabilizer bar system roll angular rigidity Theoretical Design valueLicense value range be：
(4) forward and backward suspension stabilizer bar system roll angular rigidity actual design valueWithMatched design：
IfThe then Theoretical Design value of the forward and backward suspension stabilizer bar system roll angular rigidity of vehicleWithAll etc.
In zero, i.e.,The namely forward and backward suspension of the vehicle need not add stabilizer bar；
IfMatched design then is carried out to forward and backward suspension stabilizer bar system roll angular rigidity actual design value, i.e.,：A：
According to the license value range of identified front suspension stabilizer bar system roll angular rigidity Theoretical Design value in step (3)The theory that an angle of heel rigidity value is chosen as front suspension stabiliser bar roll angular rigidity is set
Evaluation
B：According to the Theoretical Design value of identified front suspension stabilizer bar system roll angular rigidity in step AAnd step (3)
InValue, the Theoretical Design value of rear suspension stabilizer bar system roll angular rigidity is calculated, i.e.,：
C：According in step AIn step BIt calculatesThe size of ratio, and it is big according to ratio
It is small to decide whether that rear suspension stabiliser bar is installed：
If ratioThen identified Theoretical Design value in step AAs front suspension stablizes leverage
System roll angular rigidity actual design valueAnd identified Theoretical Design value in step BAs rear suspension stabiliser bar
System roll angular rigidity actual design value
If ratioThen take the actual design value of rear suspension stabilizer bar system roll angular rigidity
I.e. rear suspension is not provided with stabiliser bar；The actual design value of front suspension stabiliser bar roll angular rigidityThat is front overhang
The actual design value of frame stabiliser bar roll angular rigidityEqual to the maximum allowable value of front suspension stabiliser bar roll angular rigidity value
(5) calculating of the deformation coefficient of forward and backward suspension end part of stabilizer rod vertical deviation：
According to the total length l of forward and backward suspension stabiliser barcfAnd lcr, the mounting distance l of intermediate two rubber bushings0fAnd l0r, forward and backward
The brachium l of stabilizer bar1fAnd l1r, the transition arc radius R of forward and backward stabilizer barfAnd Rr, the central angle θ of transition arcf
And θrAnd elastic properties of materials model E and Poisson's ratio μ, to the deformation coefficient G of forward and backward suspension end part of stabilizer rod vertical deviationwfAnd GwrInto
Row calculates, respectively：
In formula,
Q6f=32 (μ+1) [Rf(cosθf-1)-l1fsinθf]2[2l1fcosθf-lcf+2Rfsinθf]；
Q6r=32 (u+1) [Rr(cosθr-1)-l1rsinθr]2[2l1rcosθr-lcr+2Rrsinθr]；
(6) forward and backward stabiliser bar rubber bushing radial line stiffness K is establishedxfAnd KxrExpression formula：
According to the axial length L of forward and backward rubber bushingfAnd Lr, thickness hfAnd hr, elastic modulus Ex, Poisson's ratio μx, in rubber bushing
Round buss wall thickness Δ lfWith Δ lrIf the value to be designed of forward and backward stable shank diameter is respectively dfAnd dr, therefore, forward and backward rubber lining
The inner circle radius and exradius of set, can be expressed as：
So the expression formula of forward and backward rubber bushing radial direction Line stiffness, can be expressed as：
In formula, Kxf(df) and Kxr(dr) it is respectively that forward and backward suspension stablizes shank diameter dfAnd drExpression formula；
b1f=[I (1, αaf)K(0,αaf)+I(0,αaf)K(1,αaf)]Mf,
b2f=-[I (1, αbf)K(0,αaf)+I(0,αaf)K(1,αbf)]Pf,
Bessel correction functions：I(0,αbf), K (0, αbf), I (1, αbf), K (1, αbf)；I(1,αaf), K (1, αaf), I (0, αaf),
K(0,αaf)；
Wherein,
b1r=[I (1, αar)K(0,αar)+I(0,αar)K(1,αar)]Mr,
b2r=-[I (1, αbr)K(0,αar)+I(0,αar)K(1,αbr)]Pr,
Bessel correction functions：I(0,αbr), K (0, αbr), I (1, αbr), K (1, αbr)；
I(1,αar), K (1, αar), I (0, αar), K (0, αar)；
(7) forward and backward suspension stablizes shank diameter dfAnd drThe foundation and design of mathematical model of optimizing design：
According to the wheelspan B of the forward and backward bridge of vehiclefAnd Br, the total length l of forward and backward stabilizer barcfAnd lcr, among forward and backward stabiliser bar
The mounting distance l of two rubber bushings0fAnd l0r, the inclination of the middle obtained forward and backward suspension stabilizer bar system of design of step (4)
The actual design value of angular rigidityWithThe forward and backward stabiliser bar being calculated in step (5) is in end vertical deviation
Deformation coefficient GwfAnd GwrAnd in step (6) obtained forward and backward rubber bushing radial direction Line stiffness expression formula Kxf(df) and
Kxr(dr), it establishes forward and backward suspension and stablizes shank diameter dfAnd drMathematical model of optimizing design, respectively：
Using Matlab calculation procedures, above-mentioned mathematical model of optimizing design is solved, forward and backward suspension can be obtained and stablize shank diameter df
And drOptimization design value.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410475786.2A CN104200040B (en) | 2014-09-18 | 2014-09-18 | The design method of vehicle suspension stabilizer bar Rigidity Matching and diameter |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410475786.2A CN104200040B (en) | 2014-09-18 | 2014-09-18 | The design method of vehicle suspension stabilizer bar Rigidity Matching and diameter |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104200040A CN104200040A (en) | 2014-12-10 |
| CN104200040B true CN104200040B (en) | 2018-08-07 |
Family
ID=52085333
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410475786.2A Expired - Fee Related CN104200040B (en) | 2014-09-18 | 2014-09-18 | The design method of vehicle suspension stabilizer bar Rigidity Matching and diameter |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104200040B (en) |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105718706B (en) * | 2016-04-27 | 2018-12-28 | 山东理工大学 | End contact lacks the design method of the reinforced auxiliary spring root thickness in piece root |
| CN105975656B (en) * | 2016-04-27 | 2019-12-31 | 山东理工大学 | Method for determining endpoint force of non-end contact type few-leaf root-reinforced main and auxiliary springs |
| CN105975686B (en) * | 2016-05-04 | 2019-12-31 | 山东理工大学 | Method for determining end point force of end contact type few-leaf end reinforced main and auxiliary springs |
| CN105956311B (en) * | 2016-05-13 | 2019-12-27 | 山东理工大学 | Design method for root thickness of non-end contact type few-leaf end reinforced auxiliary spring |
| CN106033484B (en) * | 2016-05-13 | 2019-01-25 | 山东理工大学 | End contact lacks the design method of piece parabolic type variable cross-section auxiliary spring length |
| CN107571707B (en) * | 2017-09-21 | 2024-02-06 | 安徽安凯汽车股份有限公司 | Front independent suspension height control valve fixing support assembly and measuring method thereof |
| CN109991023A (en) * | 2017-12-29 | 2019-07-09 | 郑州宇通客车股份有限公司 | Stabilizer bar roll stiffness matching test device |
| CN111651923B (en) * | 2020-06-03 | 2023-03-28 | 北京航宇振控科技有限责任公司 | Multi-degree-of-freedom passive vibration isolation system optimization design method |
| CN112339884B (en) * | 2020-09-25 | 2021-10-29 | 广州汽车集团股份有限公司 | Stabilizer bar arrangement position determining method and device and readable storage medium |
| CN113268811B (en) * | 2021-05-26 | 2022-11-22 | 江西五十铃汽车有限公司 | Method for calculating torsional rigidity of stabilizer bar by utilizing multi-body dynamics |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102320337A (en) * | 2011-06-30 | 2012-01-18 | 三一重工股份有限公司 | A kind of automobile cab front hung holder and heavy motor vehicle |
| CN102923201A (en) * | 2012-11-27 | 2013-02-13 | 东风柳州汽车有限公司 | Front suspension device for heavy-duty truck cab |
-
2014
- 2014-09-18 CN CN201410475786.2A patent/CN104200040B/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102320337A (en) * | 2011-06-30 | 2012-01-18 | 三一重工股份有限公司 | A kind of automobile cab front hung holder and heavy motor vehicle |
| CN102923201A (en) * | 2012-11-27 | 2013-02-13 | 东风柳州汽车有限公司 | Front suspension device for heavy-duty truck cab |
Non-Patent Citations (3)
| Title |
|---|
| Optimal Power System Stabilizer Tuning in Multi-machine System via an Improved Differential Evolution;G. Y. Yang 等;《Proceedings of the 17th World Congress The International Federation of Automatic Control》;20080711;14939-14944 * |
| 前双横臂独立悬架前双横臂独立悬架的建模仿真与改进设计的建模仿真与改进设计;乐升彬;《中国优秀博硕士学位论文全文数据库 (硕士) 工程科技Ⅱ辑》;20041215(第04期);C035-38 * |
| 基于ADAMS的越野车独立悬架仿真研究;程康;《中国优秀硕士学位论文全文数据库 工程科技Ⅱ辑》;20110915(第09期);C035-87 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104200040A (en) | 2014-12-10 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104200040B (en) | The design method of vehicle suspension stabilizer bar Rigidity Matching and diameter | |
| CN104182597B (en) | The check method of vehicle suspension roll angular rigidity | |
| US5723782A (en) | Method of land vehicle suspension evaluation and design through roll angle analysis | |
| CN101826125A (en) | Method for designing McPherson suspension | |
| CN104890461B (en) | A kind of double cross arm independent suspension and knuckle assembly | |
| CN107380336A (en) | A kind of damping balance car | |
| CN104268357B (en) | Coaxial-type driver's cabin stablizes the design method of shank diameter | |
| CN104281759B (en) | The design method of interior biasing non-coaxial driver's cabin stabiliser bar rubber sleeve length | |
| CN104331575B (en) | The design method of the outer amount of bias of torsion tube of outer biasing non-coaxial driver's cabin stabiliser bar | |
| CN104175831B (en) | The design method of the inner circle sleeve thickness of suspension stabiliser bar rubber bushing | |
| CN104239657B (en) | Coaxial-type driver's cabin stabiliser bar suspension clipping room away from design method | |
| CN104268359B (en) | The design method of coaxial-type driver's cabin stabiliser bar rubber sleeve length | |
| CN104268360B (en) | The design method of coaxial-type driver's cabin stabiliser bar rubber sleeve exradius | |
| CN104281758B (en) | The design method of the torsion tube length of interior biasing non-coaxial driver's cabin stabilizer bar system | |
| CN104361164B (en) | The design method of the torsion tube outer diameter of interior biasing non-coaxial driver's cabin stabilizer bar system | |
| CN104200050B (en) | The design method of suspension stabiliser bar rubber bushing thickness | |
| CN104200043B (en) | The design method of suspension stabiliser bar rubber bushing length | |
| CN104200123A (en) | Method for calculating rigidity of transverse stabilizer bar system on basis of radial deformation of rubber bushing | |
| CN206579424U (en) | A kind of double cross arm independent suspension and automobile | |
| CN104281760B (en) | The design method of the torsion tube interior biasing amount of interior biasing non-coaxial driver's cabin stabiliser bar | |
| CN104318018B (en) | The design method of coaxial-type driver's cabin stabiliser bar rubber bushing pin diameter | |
| CN105160180B (en) | High speed railway car two is the Analytic Calculation Method of vertical suspension Optimal damping ratio | |
| CN204452655U (en) | A kind of adjustment structure of stabilizer rod assembly | |
| CN104361163B (en) | The design method of the pendulum arm length of interior biasing non-coaxial driver's cabin stabilizer bar system | |
| CN104268358B (en) | The design method of coaxial-type driver's cabin stabilizer bar system torsion tube length |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20180807 Termination date: 20200918 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |