CN106777605A - A kind of suspension side regards geometry motion analysis method and system - Google Patents
A kind of suspension side regards geometry motion analysis method and system Download PDFInfo
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Abstract
A kind of suspension side be the embodiment of the invention provides regarding geometry motion analysis method and system.Suspension is simplified to two dimensional surface and is analyzed calculating by the suspension side depending on geometry motion analysis method and system from three-dimensional space, is simplified calculating process and is shortened the calculating time, and is easy to practical implementation.The suspension side meets the computational accuracy demand of general side-looking geometrical performance parameter depending on geometry motion analysis method and system, can be used for the design and parameter optimization of this type suspension early stage.
Description
Technical field
Analysis and survey control technology field the present invention relates to automobile, particularly relate to a kind of suspension side regarding geometry motion point
Analysis method and system.
Background technology
In the initial stage development process of vehicle product, the geometry motion analysis of suspension is the most important theories of suspension system designs
Foundation.The geometry motion analysis of suspension can solve the kinematics model of suspension, while may further determine that the geometry of suspension fork mechanism
Parameter and its Changing Pattern.The geometry motion analysis of suspension is to carry out suspension geometry arrangement and suspension system parameter to automotive performance
The basis of impact analysis.Due to the complexity of automotive suspension structure, it is entered using mathematical methods such as many-body dynamicses typically
Row analysis, the analysis method difficulty in computation is big and to calculate the time for spending long, is not easy to the practical application of engineering.
The content of the invention
In order to solve the above-mentioned technical problem, the embodiment of the invention provides a kind of suspension side regarding geometry motion analysis method and
System.Suspension is simplified to two dimensional surface and is divided by the suspension side depending on geometry motion analysis method and system from three-dimensional space
Analysis is calculated, and is simplified calculating process and is shortened the calculating time, and is easy to practical implementation.The suspension side is analyzed regarding geometry motion
Method and system meet the computational accuracy demand of general side-looking geometrical performance parameter, can be used for the design of this type suspension early stage with
Parameter optimization.
According to the one side of the embodiment of the present invention, the embodiment of the invention provides a kind of suspension side and analyzed regarding geometry motion
Method, including：
The hard spot information of suspension is read, wherein the hard spot information of the suspension includes：Front axle hard spot information and rear axle hard spot
Information；
The hard spot information of three-dimensional system of coordinate lower suspension is converted into the leverage coordinate value on two dimensional surface；The bar of the suspension
It is that coordinate value includes：Front axle leverage coordinate value and rear axle leverage coordinate value；
According to front axle leverage coordinate value and rear axle leverage coordinate value, antero posterior axis IC calculating is carried out, calculating respectively obtains front axle
Virtual be hinged center ICFVirtual with rear axle is hinged center ICR；
Selection analysis type, the analysis type is damped condition or accelerating mode；
Center IC is hinged according to the virtual of front axle is obtainedFVirtual with rear axle is hinged center ICRSuspension side is carried out to be transported regarding geometry
Dynamic analysis.
Alternatively, center IC is hinged according to obtaining the virtual of front axleFVirtual with rear axle is hinged center ICRCarry out suspension side
Depending on geometry motion analysis, including：
If analysis type be the damped condition, select braking model, wherein the braking model be internal detent or
Outer brake；
When braking model is the outer brake, virtual according to front axle is hinged center ICFGeometry calculating is carried out, before obtaining
Axle side-looking void brachium lsvsa,FEmpty arm included angle is regarded with the first front isometricF；Virtual according to rear axle is hinged center ICRCarry out geometry meter
Calculate, obtain rear isometric and regard empty brachium lsvsa,REmpty arm included angle is regarded with the second rear isometricR；And then it is calculated performance parameter：Front axle
Antidive rate and the anti-enhancing rate of rear axle；
When braking model is the internal detent, virtual according to front axle is hinged center ICFIt is calculated front isometric and regards void
Brachium lsvsa,FEmpty arm angle theta is regarded with the second front isometricF；Virtual according to rear axle is hinged center ICRRear isometric is calculated respectively
Depending on empty brachium lsvsa,REmpty arm angle theta is regarded with the second rear isometricR；And then it is calculated performance parameter：Front axle antidive rate and rear axle
Anti- enhancing rate；
If analysis type is the accelerating mode, rear axle form is selected；Wherein described rear axle form is stiff shaft or only
Vertical suspension；
When rear axle form is the stiff shaft, virtual according to front axle is hinged center ICFIt is calculated front isometric and regards empty arm
L longsvsa,FEmpty arm angle theta is regarded with the second front isometricF；Virtual according to rear axle is hinged center ICRIt is calculated rear isometric and regards empty arm
L longsvsa,REmpty arm included angle is regarded with the second rear isometricR；And then it is calculated performance parameter：Faced upward before front axle is anti-rate and rear axle it is anti-after
Crouching rate；
When rear axle form is independent suspension, virtual according to front axle is hinged center ICFIt is calculated front isometric and regards empty brachium
lsvsa,FEmpty arm angle theta is regarded with the second front isometricF；Virtual according to rear axle is hinged center ICRRear isometric is calculated respectively regards void
Brachium lsvsa,REmpty arm angle theta is regarded with the second rear isometricR；And then it is calculated performance parameter：Faced upward before front axle is anti-rate and rear axle it is anti-after
Crouching rate.
Alternatively, the front axle leverage coordinate value includes the point of top link first U1F, top link second point U2F, lower swing arm
First point L1F, lower swing arm second point L2F, front axle core wheel W1With front axle wheel rim and the point of contact P on ground1Leverage coordinate value；Front axle
Virtual be hinged center ICFIt is front axle top link U1FU2FWith front axle lower swing arm L1FL2FIntersection point.
Alternatively, the rear axle leverage coordinate value includes top link thirdly U1R, the point U of top link the 4th2R, lower swing arm
Thirdly L1R, lower swing arm the 4th point L2RWith rear axle core wheel W2With rear axle wheel rim and the point of contact P on ground2Leverage coordinate value；Afterwards
The virtual of axle is hinged center ICRIt is rear axle top link U1R U2RWith rear axle lower swing arm L1RL2RIntersection point.
Alternatively, first front isometric regards empty arm included angleFVirtual with front axle is hinged center ICFWith front axle wheel rim with
The point of contact P1 on ground is relevant；First rear isometric regards empty arm included angleRVirtual with rear axle is hinged center ICRWith rear axle wheel rim
Point of contact P2 with ground is relevant.
Alternatively, when braking model is outer brake, the brake-power balance coefficient p of front axle antidive rate and front axleb,F, it is preceding
The first side-looking void arm included angle of axleF, wheelbase l it is relevant with height of center of mass h；The braking force distribution system of the anti-enhancing rate of rear axle and rear axle
Number pb,R, the first rear isometric regard empty arm included angleR, wheelbase l it is relevant with height of center of mass h.
Alternatively, second front isometric regards empty arm angle thetaFVirtual with front axle is hinged center ICFWith core wheel W1Hard spot
It is information-related；Second rear isometric regards empty arm angle thetaRVirtual with rear axle is hinged center ICRWith core wheel W2Hard spot information have
Close.
Alternatively, when braking model is internal detent, the brake-power balance coefficient p of front axle antidive rate and front axleb,F,
Two front isometrics regard empty arm angle thetaF, wheelbase l it is relevant with height of center of mass h；The brake-power balance coefficient of the anti-enhancing rate of rear axle and rear axle
pb,R, the second rear isometric regard empty arm angle thetaR, wheelbase l it is relevant with height of center of mass h.
When alternatively, under accelerating mode, rate is faced upward before the front axle is anti-and regards empty arm angle theta with the second front isometricF, wheelbase l
It is relevant with height of center of mass h；Under accelerating mode and when rear axle is stiff shaft, crouching rate regards void with the first rear isometric after the rear axle is anti-
Arm included angleR, wheelbase l it is relevant with height of center of mass h.
Alternatively, under accelerating mode and when rear axle is independent suspension, crouching rate is regarded with the second rear isometric after the rear axle is anti-
Empty arm angle thetaR, wheelbase l it is relevant with height of center of mass h.
On the other hand, a kind of suspension side is additionally provided regarding geometry motion analysis system, including：
Read module, the hard spot information for reading suspension, wherein the hard spot information of the suspension includes：Front axle hard spot is believed
Breath and rear axle hard spot information；
Modular converter, for the leverage coordinate being converted into the hard spot information of three-dimensional system of coordinate lower suspension on two dimensional surface
Value；The leverage coordinate value of the suspension includes：Front axle leverage coordinate value and rear axle leverage coordinate value；
Computing module, for according to front axle leverage coordinate value, carrying out antero posterior axis IC calculating, calculating respectively obtains the void of front axle
Plan is hinged center ICFVirtual with rear axle is hinged center ICR；
Selecting module, for selection analysis type, the analysis type is damped condition or accelerating mode；
Analysis module, obtains the virtual of front axle and is hinged center IC for basisFVirtual with rear axle is hinged center ICRCarry out
Suspension side is analyzed regarding geometry motion.
Alternatively, the analysis module is further used for：
Under the damped condition, when braking model is outer brake, virtual according to front axle is hinged center ICFCarry out several
What is calculated, and is obtained front isometric and is regarded empty brachium lsvsa,FEmpty arm included angle is regarded with the first front isometricF；Virtual according to rear axle is hinged
Heart ICRGeometry calculating is carried out, rear isometric is obtained and is regarded empty brachium lsvsa,REmpty arm included angle is regarded with the second rear isometricR；And then calculate
To performance parameter：Front axle antidive rate and the anti-enhancing rate of rear axle；
Under the damped condition, when braking model is internal detent, virtual according to front axle is hinged center ICFAnd rear axle
Virtual be hinged center ICRThe second front isometric is calculated respectively regards empty arm angle thetaFEmpty arm angle theta is regarded with the second rear isometricR；Enter
And it is calculated performance parameter：Front axle antidive rate and the anti-enhancing rate of rear axle；
Under the accelerating mode, when rear axle form is stiff shaft, virtual according to front axle is hinged center ICFIt is calculated
Front isometric regards empty brachium lsvsa,FEmpty arm angle theta is regarded with the second front isometricF；Virtual according to rear axle is hinged center ICRIt is calculated
Rear isometric regards empty brachium lsvsa,REmpty arm included angle is regarded with the second rear isometricR；And then it is calculated performance parameter：Faced upward before front axle is anti-
Crouching rate after rate and rear axle are anti-；
Under the accelerating mode, when rear axle form is independent suspension, virtual according to front axle is hinged center ICFCalculate
Empty brachium l is regarded to front isometricsvsa,FEmpty arm angle theta is regarded with the second front isometricF；Virtual according to rear axle is hinged center ICRCount respectively
Calculation obtains rear isometric and regards empty brachium lsvsa,REmpty arm angle theta is regarded with the second rear isometricR；And then it is calculated performance parameter：Front axle resists
Before face upward rate and rear axle it is anti-after crouching rate.
Above-mentioned technical proposal of the invention has the beneficial effect that：
In such scheme, from three-dimensional space be simplified to suspension depending on geometry motion analysis method and system by the suspension side
Two dimensional surface is analyzed calculating, simplifies calculating process and shortens the calculating time, and is easy to practical implementation.The suspension side
Meet the computational accuracy demand of general side-looking geometrical performance parameter depending on geometry motion analysis method and system, can be used for this type and hang
The design and parameter optimization of frame early stage.
Brief description of the drawings
Technical scheme in order to illustrate more clearly the embodiments of the present invention, below will be to needed for embodiment of the present invention description
The accompanying drawing to be used is briefly described, it should be apparent that, drawings in the following description are only some embodiments of the present invention,
For those of ordinary skill in the art, on the premise of not paying creative work, can also be obtained according to these accompanying drawings
Other accompanying drawings.
Fig. 1 is the schematic flow sheet that a kind of suspension side provided in an embodiment of the present invention regards geometry motion analysis method；
Fig. 2 is a kind of double wishbone suspension model schematic provided in an embodiment of the present invention；
Fig. 3 is the simplified model schematic diagram that a kind of side-looking geometry provided in an embodiment of the present invention is calculated；
Fig. 4 is a kind of virtual diagram method for being hinged center IC provided in an embodiment of the present invention；
Side-looking geometric representation when Fig. 5 is outer brake provided in an embodiment of the present invention；
Side-looking geometric representation when Fig. 6 is internal detent provided in an embodiment of the present invention；
Fig. 7 is the side-looking geometric representation that the rear axle under accelerating mode provided in an embodiment of the present invention is stiff shaft；
Fig. 8 is the side-looking geometric representation that the rear axle under accelerating mode provided in an embodiment of the present invention is independent suspension；
Fig. 9 is the schematic flow sheet that a kind of suspension side provided in an embodiment of the present invention regards geometry motion analysis system；
Figure 10 is that suspension side provided in an embodiment of the present invention regards geometrical analysis FB(flow block).
Specific embodiment
To make the technical problem to be solved in the present invention, technical scheme and advantage clearer, below in conjunction with accompanying drawing and tool
Body embodiment is described in detail.
Fig. 1 is the flow chart that a kind of suspension side provided in an embodiment of the present invention regards geometry motion analysis method.
As shown in figure 1, the suspension side is comprised the following steps depending on geometry motion analysis method：
Step 101, the hard spot information for reading suspension, wherein the hard spot information of the suspension includes：Front axle hard spot information and
Rear axle hard spot information.
Hard spot is that three-dimensional coordinate position has been fixed during vehicle configuration, it is impossible to mobile point.The hard spot of the suspension
Information refers to the coordinate in vehicle body coordinate system lower suspension significant points.The significant points are front axle with after in the present embodiment
Axle.
Fig. 2 is a kind of double wishbone suspension model provided in an embodiment of the present invention.As shown in Fig. 2 a kind of double wishbone suspension mould
Type includes：Top Crossbeam 1, lower cross arm 2 and wheel 3.
The front axle and rear axle of suspension can be simplified to the double wishbone suspension model, including：The double wishbone suspension of front axle
Model and rear axle double wishbone suspension model.
Step 102, the leverage coordinate value being converted into the hard spot information of three-dimensional system of coordinate lower suspension on two dimensional surface；It is described
The leverage coordinate value of suspension includes：Front axle leverage coordinate value and rear axle leverage coordinate value.
Fig. 3 is the simplified model that side-looking geometry is calculated, double wishbone suspension three-dimensional stereo model conversion that will be shown in Fig. 2
The leverage simplified model calculated for side-looking geometry shown in Fig. 3.By the front axle of suspension and the double wishbone suspension model of rear axle
The leverage simplified model of front axle and rear axle is changed into respectively, and then obtains the leverage coordinate value of front axle and rear axle.
Wherein, the front axle leverage coordinate value includes the point of top link first U1F, top link second point U2F, lower swing arm
One point L1F, lower swing arm second point L2F, front axle core wheel W1With front axle wheel rim and the point of contact P on ground1Leverage coordinate value.
The rear axle leverage coordinate value includes top link thirdly U1R, the point U of top link the 4th2R, lower swing arm thirdly
L1R, lower swing arm the 4th point L2RWith rear axle core wheel W2With rear axle wheel rim and the point of contact P on ground2Leverage coordinate value.
Step 103, according to front axle leverage coordinate value and rear axle leverage coordinate value, carry out antero posterior axis be virtually hinged center IC meter
Calculate, calculating respectively obtains the virtual of front axle and is hinged center ICFVirtual with rear axle is hinged center ICR。
Fig. 4 is the diagram method for being virtually hinged center IC, by top link U1U2With lower swing arm L1L2Extend to intersecting, intersection point is
To be virtually hinged center IC.
Can be obtained by above theory, the virtual of front axle is hinged center ICFIt is front axle top link U1FU2FWith front axle lower swing arm L1FL2F
Intersection point；
The virtual of rear axle is hinged center ICRIt is rear axle top link U1R U2RWith rear axle lower swing arm L1R L2RIntersection point.
Step 104, selection analysis type, the analysis type are damped condition or accelerating mode.
Step 105, basis obtain the virtual of front axle and are hinged center ICFVirtual with rear axle is hinged center ICRCarry out suspension side
Depending on geometry motion analysis.
1) if analysis type is the damped condition, braking model is selected, wherein the braking model is internal detent
Or outer brake.
When braking model is the outer brake, virtual according to front axle is hinged center ICFGeometry calculating is carried out, before obtaining
Axle side-looking void brachium lsvsa,FEmpty arm included angle is regarded with the first front isometricF；
Wherein, first front isometric regards empty arm included angleFVirtual with front axle is hinged center ICFWith front axle wheel rim and ground
The point of contact P in face1It is relevant.
Referring to Fig. 5, virtual by front axle is hinged center ICFWith front axle wheel rim and the point of contact P on ground1Draw a straight line, should
Straight line is the first front isometric and regards empty arm included angle with the angle on groundF；Front isometric regards empty brachium lsvsa,FAs front axle is virtual
It is hinged center ICFTo by core wheel W1Axis between distance.
Virtual according to rear axle is hinged center ICR and carries out geometry calculating, obtains rear isometric and regards empty brachium lsvsa,RAfter second
Axle side-looking void arm included angleR。
First rear isometric regards empty arm included angleRVirtual with rear axle is hinged center ICRWith cutting for rear axle wheel rim and ground
Point P2It is relevant.
Referring to Fig. 5, virtual by rear axle is hinged center ICRWith rear axle wheel rim and the point of contact P on ground2Draw a straight line, should
Straight line is the first rear isometric and regards empty arm included angle with the angle on groundR；Rear isometric regards empty brachium lsvsa,RAs rear axle is virtual
It is hinged center ICRTo by core wheel W2Axis between distance.
And then it is calculated performance parameter：Front axle antidive rate and the anti-enhancing rate of rear axle；
Wherein, the brake-power balance coefficient p of the front axle antidive rate and front axleb,F, front axle the first side-looking void arm angle
φF, wheelbase l it is relevant with height of center of mass h；Wherein, wheelbase l is distance between front axle and rear axle, and height of center of mass h is arrived for suspension barycenter
The height on ground, wheelbase l and height of center of mass h are constant.
Front axle antidive rate relational expression is
anti-diveF=pb,F·tan(φF)·l/h (1)
Wherein, anti-diveFRepresent front axle antidive rate.
The brake-power balance coefficient p of the anti-enhancing rate of rear axle and rear axleb,R, the first rear isometric regard empty arm included angleR, axle
It is relevant with height of center of mass h away from l.
The anti-enhancing rate relational expression of rear axle is
anti-liftR=pb,R·tan(φR)·l/h (2)
Wherein, anti-liftRRepresent the anti-enhancing rate of rear axle.
Front axle antidive rate when by formula (1) can be the outer brake in the hope of braking model；
The anti-enhancing rate of rear axle when by formula (2) can be the outer brake in the hope of braking model.
If braking model is the internal detent, virtual according to front axle is hinged center ICFFront isometric is calculated to regard
Empty brachium lsvsa,FEmpty arm angle theta is regarded with the second front isometricF；Virtual according to rear axle is hinged center ICRRear axle is calculated respectively
Side-looking void brachium lsvsa,REmpty arm angle theta is regarded with the second rear isometricR；To avoid repeating, front isometric regards empty brachium lsvsa,FAnd rear axle
Side-looking void brachium lsvsa,RMethod of specifically asking just repeat no more.
Wherein, second front isometric regards empty arm angle thetaFVirtual with front axle is hinged center ICFWith core wheel W1Hard spot letter
Breath is relevant.
Referring to Fig. 6, virtual by front axle is hinged center ICFWith core wheel W1Draw a straight line, by core wheel W1Do ground
Parallel lines, the parallel lines and straight line ICFW1Between angle be that the second front isometric regards empty arm angle thetaF。
Second rear isometric regards empty arm angle thetaRVirtual with rear axle is hinged center ICRWith core wheel W2Hard spot information have
Close.
Referring to Fig. 6, virtual by rear axle is hinged center ICRWith core wheel W2Draw a straight line, by core wheel W2Do ground
Parallel lines, the parallel lines and straight line ICRW2Between angle be that the second rear isometric regards empty arm angle thetaR。
Empty arm angle theta is regarded according to the second front isometric tried to achieveFEmpty arm angle theta is regarded with the second rear isometricRIt is calculated performance ginseng
Number：Front axle antidive rate and the anti-enhancing rate of rear axle.
When braking model is the internal detent, the brake-power balance coefficient p of front axle antidive rate and front axleb,F, before second
Axle side-looking void arm angle thetaF, wheelbase l it is relevant with height of center of mass h.
The relational expression of front axle antidive rate is
When braking model is the internal detent, the brake-power balance coefficient p of the anti-enhancing rate of rear axle and rear axleb,R, after second
Axle side-looking void arm angle thetaR, wheelbase l it is relevant with height of center of mass h.
The relational expression of the anti-enhancing rate of rear axle is
Front axle antidive rate when by formula (3) can be the internal detent in the hope of braking model；
The anti-enhancing rate of rear axle when by formula (4) can be the internal detent in the hope of braking model.
2) if analysis type is the accelerating mode, rear axle form is selected；Wherein described rear axle form be stiff shaft or
Independent suspension.
When rear axle form is the stiff shaft, referring to Fig. 7, virtual according to front axle is hinged center ICFIt is calculated front axle
Side-looking void brachium lsvsa,FEmpty arm angle theta is regarded with the second front isometricF；To avoid repeating, method is specifically asked just to repeat no more.
When rear axle form is the stiff shaft, referring to Fig. 7, virtual according to rear axle is hinged center ICRIt is calculated rear axle
Side-looking void brachium lsvsa,REmpty arm included angle is regarded with the second rear isometricR；To avoid repeating, method is specifically asked just to repeat no more.
And then it is calculated performance parameter：Faced upward before front axle is anti-rate and rear axle it is anti-after crouching rate.
When under accelerating mode, rate is faced upward before the front axle is anti-and regards empty arm angle theta with the second front isometricF, wheelbase l and barycenter it is high
H is relevant for degree.
The relational expression that rate is faced upward before front axle is anti-is
anti-liftF=tan (θF)·l/h (5)
Wherein, anti-liftFRepresent that front axle faces upward rate before anti-.
Under accelerating mode and when rear axle is stiff shaft, crouching rate regards empty arm angle with the first rear isometric after the rear axle is anti-
φR, wheelbase l it is relevant with height of center of mass h.
The relational expression of crouching rate is after rear axle is anti-
anti-squatR=tan (φR)·l/h (6)
Wherein, anti-squatRCrouching rate after expression rear axle is anti-.
Rate is faced upward before front axle when by formula (5) can be stiff shaft in the hope of rear axle is anti-；
Crouching rate after rear axle when by formula (6) can be stiff shaft in the hope of rear axle is anti-.
When rear axle form is independent suspension, referring to Fig. 8, virtual according to front axle is hinged center ICFIt is calculated front isometric
Depending on empty brachium lSvsa, FEmpty arm angle theta is regarded with the second front isometricF；To avoid repeating, method is specifically asked just to repeat no more.
When rear axle form is independent suspension, referring to Fig. 8, virtual according to rear axle is hinged center ICRAfter being calculated respectively
Axle side-looking void brachium lsvsa,REmpty arm angle theta is regarded with the second rear isometricR；To avoid repeating, method is specifically asked just to repeat no more.
And then it is calculated performance parameter：Faced upward before front axle is anti-rate and rear axle it is anti-after crouching rate.
Under accelerating mode and when rear axle is independent suspension, crouching rate regards empty arm angle with the second rear isometric after the rear axle is anti-
θR, wheelbase l it is relevant with height of center of mass h.
The relational expression of crouching rate is after rear axle is anti-
anti-squatR=tan (θR)·l/h (7)
Rate is faced upward before front axle when by formula (5) can be independent suspension in the hope of rear axle is anti-；
Crouching rate after rear axle when by formula (7) can be independent suspension in the hope of rear axle is anti-.
The performance parameter being calculated can as suspension arrangement when the adjustment of corresponding hard spot foundation.The design of suspension system
Crouching amount reaches most after the amount of facing upward and rear axle before the front axle amount of nodding that should try one's best when making braking and rear axle lifting capacity, front axle when driving
It is small.Rate and drive are faced upward before the anti-enhancing rate of rear axle when front axle antidive rate when namely making braking, braking, front axle when driving are anti-
Crouching rate reaches maximum after rear axle when dynamic resists.The ideal value of each performance parameter is 1=100% above, now the longitudinal direction fortune of suspension
Dynamic characteristic is best.Yet with many reasons, ideal value is extremely difficult in practice, therefore is rarely employed this ideal value conduct
With reference to.By taking antidive rate as an example, 50% is commonly reached.
On the other hand, a kind of suspension side is additionally provided in the embodiment of the present invention regarding geometry motion analysis system.Fig. 9 is this hair
A kind of bright suspension side for implementing to provide regards the structure chart of geometry motion analysis system.
As shown in figure 9, the suspension side includes depending on geometry motion analysis system：
Read module 901, the hard spot information for reading suspension, wherein the hard spot information of the suspension includes：Front axle is hard
Point information and rear axle hard spot information；
Modular converter 902, the leverage for being converted into the hard spot information of three-dimensional system of coordinate lower suspension on two dimensional surface is sat
Scale value；The leverage coordinate value of the suspension includes：Front axle leverage coordinate value and rear axle leverage coordinate value；
Computing module 903, for according to front axle leverage coordinate value, carrying out antero posterior axis IC calculating, calculating respectively obtains front axle
Virtual be hinged center ICFVirtual with rear axle is hinged center ICR；
Selecting module 904, for selection analysis type, the analysis type is damped condition or accelerating mode；
Analysis module 905, obtains the virtual of front axle and is hinged center IC for basisFVirtual with rear axle is hinged center ICREnter
Row suspension side is analyzed regarding geometry motion.
Optionally, the analysis module 905 is further used for：
Under the damped condition, when braking model is outer brake, virtual according to front axle is hinged center ICFCarry out several
What is calculated, and is obtained front isometric and is regarded empty brachium lsvsa,FEmpty arm included angle is regarded with the first front isometricF；Virtual according to rear axle is hinged
Heart ICRGeometry calculating is carried out, rear isometric is obtained and is regarded empty brachium lsvsa,REmpty arm included angle is regarded with the second rear isometricR；And then calculate
To performance parameter：Front axle antidive rate and the anti-enhancing rate of rear axle.
Under the damped condition, when braking model is internal detent, virtual according to front axle is hinged center ICFAnd rear axle
Virtual be hinged center ICRThe second front isometric is calculated respectively regards empty arm angle thetaFEmpty arm angle theta is regarded with the second rear isometricR；Enter
And it is calculated performance parameter：Front axle antidive rate and the anti-enhancing rate of rear axle.
Under the accelerating mode, when rear axle form is stiff shaft, virtual according to front axle is hinged center ICFIt is calculated
Front isometric regards empty brachium lsvsa,FEmpty arm angle theta is regarded with the second front isometricF；Under the accelerating mode, rear axle form is stiff shaft
When, virtual according to rear axle is hinged center ICRIt is calculated rear isometric and regards empty brachium lsvsa,REmpty arm angle is regarded with the second rear isometric
φR；And then it is calculated performance parameter：Faced upward before front axle is anti-rate and rear axle it is anti-after crouching rate.
Under the accelerating mode, when rear axle form is independent suspension, virtual according to front axle is hinged center ICFCalculate
Empty brachium l is regarded to front isometricsvsa,FEmpty arm angle theta is regarded with the second front isometricF；Virtual according to rear axle is hinged center ICRCount respectively
Calculation obtains rear isometric and regards empty brachium lsvsa,REmpty arm angle theta is regarded with the second rear isometricR；And then it is calculated performance parameter：Front axle resists
Before face upward rate and rear axle it is anti-after crouching rate.
A kind of suspension side be the embodiment of the invention provides regarding geometry motion analysis method and system.With reference to Figure 10, the suspension
Suspension is simplified to two dimensional surface and is analyzed calculating by side-looking geometry motion analysis method and system from three-dimensional space, is simplified
Calculating process and the calculating time is shortened, and be easy to practical implementation.The suspension side regards geometry motion analysis method and system
Meet the computational accuracy demand of general side-looking geometrical performance parameter, can be used for the design and parameter optimization of this type suspension early stage.
The above is the preferred embodiment of the present invention, it is noted that for those skilled in the art
For, on the premise of principle of the present invention is not departed from, some improvements and modifications can also be made, these improvements and modifications
Should be regarded as protection scope of the present invention.
Claims (12)
1. a kind of suspension side regards geometry motion analysis method, it is characterised in that including：
The hard spot information of suspension is read, wherein the hard spot information of the suspension includes：Front axle hard spot information and rear axle hard spot information；
The hard spot information of three-dimensional system of coordinate lower suspension is converted into the leverage coordinate value on two dimensional surface；The leverage of the suspension is sat
Scale value includes：Front axle leverage coordinate value and rear axle leverage coordinate value；
According to front axle leverage coordinate value and rear axle leverage coordinate value, antero posterior axis IC calculating is carried out, calculating respectively obtains the void of front axle
Plan is hinged center ICFVirtual with rear axle is hinged center ICR；
Selection analysis type, the analysis type is damped condition or accelerating mode；
Center IC is hinged according to the virtual of front axle is obtainedFVirtual with rear axle is hinged center ICRSuspension side is carried out regarding geometry motion point
Analysis.
2. suspension side according to claim 1 regards geometry motion analysis method, it is characterised in that according to the void for obtaining front axle
Plan is hinged center ICFVirtual with rear axle is hinged center ICRSuspension side is carried out to be analyzed regarding geometry motion, including：
If analysis type is the damped condition, braking model is selected, wherein the braking model is internal detent or outside
Braking；
When braking model is the outer brake, virtual according to front axle is hinged center ICFGeometry calculating is carried out, front isometric is obtained
Depending on empty brachium lsvsa,FEmpty arm included angle is regarded with the first front isometricF；Virtual according to rear axle is hinged center ICRGeometry calculating is carried out,
Obtain rear isometric and regard empty brachium lsvsa,REmpty arm included angle is regarded with the second rear isometricR；And then it is calculated performance parameter：Front axle resists
Rate of nodding and the anti-enhancing rate of rear axle；
When braking model is the internal detent, virtual according to front axle is hinged center ICFIt is calculated front isometric and regards empty brachium
lsvsa,FEmpty arm angle theta is regarded with the second front isometricF；Virtual according to rear axle is hinged center ICRRear isometric is calculated respectively regards void
Brachium lsvsa,REmpty arm angle theta is regarded with the second rear isometricR；And then it is calculated performance parameter：Front axle antidive rate and rear axle are anti-to be carried
The rate of liter；
If analysis type is the accelerating mode, rear axle form is selected；Wherein described rear axle form is stiff shaft or independent outstanding
Frame；
When rear axle form is the stiff shaft, virtual according to front axle is hinged center ICFIt is calculated front isometric and regards empty brachium
lsvsa,FEmpty arm angle theta is regarded with the second front isometricF；Virtual according to rear axle is hinged center ICRIt is calculated rear isometric and regards empty brachium
lsvsa,REmpty arm included angle is regarded with the second rear isometricR；And then it is calculated performance parameter：Faced upward before front axle is anti-rate and rear axle it is anti-after squat
Rate；
When rear axle form is independent suspension, virtual according to front axle is hinged center ICFIt is calculated front isometric and regards empty brachium lsvsa,F
Empty arm angle theta is regarded with the second front isometricF；Virtual according to rear axle is hinged center ICRIt is calculated rear isometric and regards empty brachium lsvsa,R
Empty arm angle theta is regarded with the second rear isometricR；And then it is calculated performance parameter：Faced upward before front axle is anti-rate and rear axle it is anti-after crouching rate.
3. suspension side according to claim 1 regards geometry motion analysis method, it is characterised in that the front axle leverage coordinate
Value includes the point of top link first U1F, top link second point U2F, lower swing arm the first point L1F, lower swing arm second point L2F, front axle wheel
Heart W1With front axle wheel rim and the point of contact P on ground1Leverage coordinate value；The virtual of front axle is hinged center ICFIt is front axle top link
U1FU2FWith front axle lower swing arm L1FL2FIntersection point.
4. suspension side according to claim 1 regards geometry motion analysis method, it is characterised in that the rear axle leverage coordinate
Value includes top link thirdly U1R, the point U of top link the 4th2R, lower swing arm thirdly L1R, lower swing arm the 4th point L2RAnd rear axle
Core wheel W2With rear axle wheel rim and the point of contact P on ground2Leverage coordinate value；The virtual of rear axle is hinged center ICRIt is rear axle top link U1R
U2RWith rear axle lower swing arm L1RL2RIntersection point.
5. suspension side according to claim 1 regards geometry motion analysis method, it is characterised in that first front isometric is regarded
Empty arm included angleFVirtual with front axle is hinged center ICFIt is relevant with the point of contact P1 on ground with front axle wheel rim；First rear isometric
Depending on empty arm included angleRVirtual with rear axle is hinged center ICRIt is relevant with the point of contact P2 on ground with rear axle wheel rim.
6. suspension side regards geometry motion analysis method according to claim 1 or 5, it is characterised in that braking model is outer
When portion brakes, the brake-power balance coefficient p of front axle antidive rate and front axleb,F, front axle the first side-looking void arm included angleF, wheelbase
L is relevant with height of center of mass h；The brake-power balance coefficient p of the anti-enhancing rate of rear axle and rear axleb,R, the first rear isometric regard empty arm angle
φR, wheelbase l it is relevant with height of center of mass h.
7. suspension side according to claim 1 regards geometry motion analysis method, it is characterised in that second front isometric is regarded
Empty arm angle thetaFVirtual with front axle is hinged center ICFWith core wheel W1Hard spot it is information-related；Second rear isometric regards empty arm folder
Angle θRVirtual with rear axle is hinged center ICRWith core wheel W2Hard spot it is information-related.
8. the suspension side according to claim 1 or 7 regards geometry motion analysis method, it is characterised in that braking model is interior
When portion brakes, the brake-power balance coefficient p of front axle antidive rate and front axleb,F, the second front isometric regard empty arm angle thetaF, wheelbase l and
Height of center of mass h is relevant；The brake-power balance coefficient p of the anti-enhancing rate of rear axle and rear axleb,R, the second rear isometric regard empty arm angle thetaR, axle
It is relevant with height of center of mass h away from l.
9. suspension side according to claim 1 regards geometry motion analysis method, it is characterised in that when under accelerating mode,
Rate is faced upward before the front axle is anti-and regards empty arm angle theta with the second front isometricF, wheelbase l it is relevant with height of center of mass h；Under accelerating mode and
When rear axle is stiff shaft, crouching rate regards empty arm included angle with the first rear isometric after the rear axle is anti-R, wheelbase l and height of center of mass h has
Close.
10. suspension side according to claim 1 regard geometry motion analysis method, it is characterised in that under accelerating mode and
When rear axle is independent suspension, crouching rate regards empty arm angle theta with the second rear isometric after the rear axle is anti-R, wheelbase l and height of center of mass h has
Close.
A kind of 11. suspension sides regard geometry motion analysis system, it is characterised in that including：
Read module, the hard spot information for reading suspension, wherein the hard spot information of the suspension includes：Front axle hard spot information and
Rear axle hard spot information；
Modular converter, for the leverage coordinate value being converted into the hard spot information of three-dimensional system of coordinate lower suspension on two dimensional surface；Institute
The leverage coordinate value for stating suspension includes：Front axle leverage coordinate value and rear axle leverage coordinate value；
Computing module, for according to front axle leverage coordinate value, carrying out antero posterior axis IC calculating, calculating respectively obtains the virtual hinge of front axle
Meet center ICFVirtual with rear axle is hinged center ICR；
Selecting module, for selection analysis type, the analysis type is damped condition or accelerating mode；
Analysis module, obtains the virtual of front axle and is hinged center IC for basisFVirtual with rear axle is hinged center ICRCarry out suspension
Side-looking geometry motion is analyzed.
12. suspension sides according to claim 11 regard geometry motion analysis system, it is characterised in that the analysis module is entered
One step is used for：
Under the damped condition, when braking model is outer brake, virtual according to front axle is hinged center ICFCarry out geometry meter
Calculate, obtain front isometric and regard empty brachium lsvsa,FEmpty arm included angle is regarded with the first front isometricF；Virtual according to rear axle is hinged center ICR
Geometry calculating is carried out, rear isometric is obtained and is regarded empty brachium lsvsa,REmpty arm included angle is regarded with the second rear isometricR；And then being calculated property
Can parameter：Front axle antidive rate and the anti-enhancing rate of rear axle；
Under the damped condition, when braking model is internal detent, virtual according to front axle is hinged center ICFWith the void of rear axle
Plan is hinged center ICRThe second front isometric is calculated respectively regards empty arm angle thetaFEmpty arm angle theta is regarded with the second rear isometricR；And then count
Calculation obtains performance parameter：Front axle antidive rate and the anti-enhancing rate of rear axle；
Under the accelerating mode, when rear axle form is stiff shaft, virtual according to front axle is hinged center ICFIt is calculated front axle
Side-looking void brachium lsvsa,FEmpty arm angle theta is regarded with the second front isometricF；Virtual according to rear axle is hinged center ICRIt is calculated rear axle
Side-looking void brachium lsvsa,REmpty arm included angle is regarded with the second rear isometricR；And then it is calculated performance parameter：Faced upward before front axle is anti-rate and
Crouching rate after rear axle is anti-；
Under the accelerating mode, when rear axle form is independent suspension, virtual according to front axle is hinged center ICFBefore being calculated
Axle side-looking void brachium lsvsa,FEmpty arm angle theta is regarded with the second front isometricF；Virtual according to rear axle is hinged center ICRCalculate respectively
Empty brachium l is regarded to rear isometricsvsa,REmpty arm angle theta is regarded with the second rear isometricR；And then it is calculated performance parameter：Faced upward before front axle is anti-
Crouching rate after rate and rear axle are anti-.
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| CN103226628A (en) * | 2013-03-22 | 2013-07-31 | 北京汽车股份有限公司 | Method and device for rapidly generating tire enveloping surfaces of front and rear automobile suspensions |
| CN103921638A (en) * | 2014-04-24 | 2014-07-16 | 安徽江淮汽车股份有限公司 | Automobile with dual-transverse-arm type front independent suspension |
| CN104573162A (en) * | 2013-10-29 | 2015-04-29 | 广州汽车集团股份有限公司 | Automobile suspension DMU (diesel multiple unit) model parameterization design method |
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|---|---|---|---|---|
| JP2010092225A (en) * | 2008-10-07 | 2010-04-22 | Fuji Heavy Ind Ltd | Modeling method for buffer member |
| CN103226628A (en) * | 2013-03-22 | 2013-07-31 | 北京汽车股份有限公司 | Method and device for rapidly generating tire enveloping surfaces of front and rear automobile suspensions |
| CN104573162A (en) * | 2013-10-29 | 2015-04-29 | 广州汽车集团股份有限公司 | Automobile suspension DMU (diesel multiple unit) model parameterization design method |
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