CN109684777A - A kind of electronic equation motorcycle race Vehicle Frame Design method - Google Patents
A kind of electronic equation motorcycle race Vehicle Frame Design method Download PDFInfo
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- CN109684777A CN109684777A CN201910092099.5A CN201910092099A CN109684777A CN 109684777 A CN109684777 A CN 109684777A CN 201910092099 A CN201910092099 A CN 201910092099A CN 109684777 A CN109684777 A CN 109684777A
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- G06F30/00—Computer-aided design [CAD]
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- G06F30/23—Design optimisation, verification or simulation using finite element methods [FEM] or finite difference methods [FDM]
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Abstract
Present invention relates particularly to a kind of design methods of electronic equation motorcycle race vehicle frame, build man-machine testing stand at design initial stage, obtain man-machine parameter, determine whole-car parameters according to vehicle general arrangement；Go out suspension hard spot position by suspension kinematical and dynamics simulation, estimates vehicle frame hard spot position；Using vehicle frame parameter and hard spot position, vehicle frame initial model is built；Finite element torsion stiffness analysis is optimized and carried out to vehicle frame model, obtains ideal vehicle frame model；Performance analysis is carried out to determining vehicle frame model, verifies structural strength and security performance under different operating conditions；Constrained mode analysis is carried out to model after performance analysis, obtains the modal parameter of vehicle frame, verifies whether to will appear covibration, and optimize model according to analysis result, obtains final vehicle frame model；Welding clamp of vehicle frame is designed, welding in kind is completed.Present invention substantially reduces the Vehicle Frame Design periods, improve the reasonability of design, and the vehicle frame designed is made to better meet vehicle performance.
Description
Technical field
The invention belongs to Structure Design and Calculation machine ancillary works technical fields, and in particular to a kind of electronic equation motorcycle race
The design method of vehicle frame.
Background technique
Chinese equation electric car contest is started in 2013, is the expansion and supplement of Chinese formula car contest.
According to the technical regulation that contest organizing committee issues, manufactures and designs in year and look after and guide out the single small-sized match of racing
Vehicle, maximum feature are that the design of racing car items has to comply with technical regulation, including main body of vehicle frame structure, battery case with manufacture
The important parameters such as design, mould group electricity, power of motor guarantee the safety of racing car and the justice of race with this.
The max architecture component that equation motorcycle race vehicle frame is manufactured as electronic equation motorcycle race autonomous Design is that vehicle is each total
At carrier, have that arrangement is overall, important function of connecting assembly.The design of vehicle frame is with high intensity, high rigidity, comfort, light
Quantization is used as design object.Equation motorcycle race vehicle frame mostly uses steel pipe truss formula body frame structure for automotive at present, and processing passes through steel-pipe welding
It forms, also there are a small number of schools to design using carbon fiber shell monomer.In the design process, it is lack of standardization that there are design cycles, and theory is answered
With unreasonable problem, be not designed and consider from the overall situation, be mostly it is subjective temporarily conceive a design, cause design and process-cycle length,
Problem is more, it is most important that Vehicle Frame Design is not able to satisfy vehicle performance requirement.
Summary of the invention
In view of the above problems, the present invention proposes a kind of electronic equation motorcycle race Vehicle Frame Design method, to solve electricity
Dynamic equation motorcycle race Vehicle Frame Design unreasonable problem lack of standardization.
To achieve the above object, specific technical solution of the present invention is as follows: a kind of electronic equation motorcycle race Vehicle Frame Design method,
The following steps are included:
1) vehicle frame parameter and vehicle frame hard spot position are determined；
2) man-machine parameter, whole-car parameters, vehicle frame hard spot position are utilized, initial vehicle frame model T is built；
3) increase auxiliary bar, adjustment rod member size, the vehicle frame model after being adjusted on the basis of initial vehicle frame model T
T ', wherein rod size includes caliber size, wall thickness dimension；
4) finite element analysis vehicle frame model T ' torsion stiffness is utilized, ideal vehicle frame model T1 is obtained；
5) performance analysis is carried out to ideal vehicle frame model T1, obtains desired Safety vehicle frame model T2；
6) finite element modal analysis is carried out to desired Safety vehicle frame model T2, obtains final vehicle frame model T3；
7) design of welding jig is carried out to final vehicle frame model T3.
Further, above-mentioned steps 1) in determine that the specific method is as follows for vehicle frame parameter and vehicle frame hard spot position:
1.1) man-machine experiment is carried out at design initial stage, builds man-machine experimental bench, with simulator operation achievement and driver master
Sight is felt as evaluation criterion, with the man-machine database of driver for objective reference, man-machine parameter is obtained, wherein man-machine parameter includes:
The distance between main ring front ring d1, main ring height h1, front ring height h2, braking distance d of the gas pedal away from main ring2, braking throttle
Pedal tilt angle γ, steering wheel hub point height h3And away from main ring distance d2, cabin width l1；
1.2) fore-aft loads ratio k is determined；
1.3) vehicle wheelbase L is calculated；
1.4) wheelspan L is determineds；
1.5) it determines suspension hard spot position, using suspension positional parameter, carries out kinematics, dynamics simulation determines that suspension is hard
Point position, positional parameter includes camber angle α1, leaning angle α2, back rake angle α3, toe-in α4；
1.6) vehicle frame hard spot position is determined, according to suspension hard spot position and vehicle frame hard spot and suspension hard spot position relative quantity
Vehicle frame hard spot position is obtained, the lifting lug size that wherein relative quantity is connect by suspension with vehicle frame determines.
Further, above-mentioned steps 4) in obtain ideal vehicle frame model T1 the specific method is as follows:
4.1) FEM calculation vehicle frame model T ' torsion stiffness value K is utilizedn, calculation formula is as follows:
K in formulanFor the torsion stiffness value that each model calculates, F is support reaction, and d is the distance between two hard spot of suspension, Δ
A, Δ B is the forced displacement of two hard spots；
4.2) the synthesis vehicle frame torsion stiffness K of vehicle frame model T ' is calculated, calculation formula is as follows:
K in formulafFor the torsion stiffness under front overhang torsion, KrFor the torsion stiffness that rear overhang torsion is lower, a for front axle away from, after b is
Wheelbase, L are wheelbase；
4.3) judge whether to meet K > K0And m < m0If 4.4) satisfaction is gone to step, otherwise go to step 3)；
4.4) judge whether to meetIdeal vehicle frame model T1 is obtained if meeting, is otherwise gone to step 3).
Further, above-mentioned steps 5) in ideal vehicle frame model T1 carry out performance analysis include the following steps:
5.1) straight line performance analysis；
5.2) at the uniform velocity excessively curved performance analysis；
5.3) accelerating mode is analyzed；
5.4) damped condition is analyzed.
Further, finite element modal analysis 6) is carried out to desired Safety vehicle frame model T2 in above-mentioned steps, obtained final
The specific method is as follows by vehicle frame model T3:
6.1) 8 hard spots are hanged before and after fixed constraint vehicle frame；
6.2) inertia force load is applied to vehicle frame；
6.3) simulation analysis is carried out, preceding 8 rank modal frequency and the vibration shape are obtained；
6.4) the external drive frequency of the components such as 8 rank modal frequency of gained and motor is compared, sees whether frequency
Coincidence is resonated, if covibration, return step 3 occurs) carry out the variation of size rod piece；Otherwise final vehicle frame model is obtained
T3。
Further, above-mentioned steps 1.3) in calculate vehicle wheelbase L the specific method is as follows:
1.3.1 vehicle front axle load M) is calculatedtf, formula is as follows:
In formula, MiFor the quality of each main component, XiX-axis distance for each main component relative to mass center, L are then wheelbase,
N indicates components number；
1.3.2) axle load M after calculating vehicletr, formula method is as follows:
Mtr=M0-Mtf
In formula, M0For complete vehicle quality (in the case that driver is fully loaded)；
1.3.3 vehicle wheelbase L) is calculated, formula is as follows:
Further, above-mentioned steps 5.1) in straight line performance analysis include the following steps:
5.1.1) 4 hard spots of fixed constraint rear overhang, the front overhang left side hard spot direction y, z constraint, discharge the freedom degree in the direction x,
Right side hard spot y, the direction z constraint, discharges the direction x freedom degree；
5.1.2) to vehicle frame apply load, wherein load position be vehicle frame, driver, motor, battery case, speed reducer respectively
With the position of frame contact, magnitude of load is that respective weight multiplies dynamic load factor；
5.1.3 simulation calculation) is carried out, total deformation cloud atlas, Stress Map and safety coefficient under straight line operating condition is calculated
Figure；
5.1.4) by simulation result and material yield strength σsEqual mechanical attributes compare, and are obtained most by safety coefficient figure
Small safety coefficient ξ, if minimum safety factor ξ is less than ξ0, increase uneasy all positon rod piece wall thickness and caliber, go to step 3), otherwise
Illustrate to meet safety requirements under straight line operating condition, go to step 5.2).
Further, above-mentioned steps 5.2) at the uniform velocity excessively curved performance analysis include the following steps:
5.2.1 whole hard spots) are surveyed in fixed constraint, to the outside direction z restraint of liberty degree, discharge the direction xy freedom degree；
5.2.2 maximum centripetal acceleration a) is calculatedrmax, calculation formula is as follows:
A in formularmaxFor maximum centripetal acceleration, r is turning radius, tminFor the most fast individual pen time；
5.2.3 inertia force load) is applied to vehicle frame, wherein load position is vehicle frame, driver, motor, battery case, deceleration
Machine is respectively with the position of frame contact, and magnitude of load is the product of component inertia power and maximum centripetal acceleration, wherein inertia force
Including vehicle frame self weight, driver's inertia force, electric drive system inertia force, battery case inertia force；
5.2.4) to vehicle frame apply secondary role power, secondary role power respectively from rear overhang triangle rocker arm, rear overhang spring and
Front overhang triangle rocker arm；
5.2.5 simulation calculation) is carried out, total deformation cloud atlas, Stress Map and safety under at the uniform velocity excessively curved operating condition is calculated
Coefficient figure；
5.2.6) by simulation result and material yield strength σsEqual mechanical attributes compare, and are obtained most by safety coefficient figure
Small safety coefficient ξ, if minimum safety factor ξ is less than ξ0, then increase uneasy all positon rod piece wall thickness and caliber, goes to step 3), it is no
Then meet safety requirements under at the uniform velocity excessively curved operating condition, goes to step 5.3).
Further, above-mentioned steps 5.3) in accelerating mode analysis include the following steps:
5.3.1) 4 hard spots of fixed constraint rear overhang, four direction hard spot yz constraints of limitation front overhang, discharge the direction x freedom degree；
5.3.2 peak acceleration a needed for) calculating accelerating modemax, calculation formula is as follows:
S is that linear accelerating travels the distance passed by formula, and t is the acceleration time, and q is classical coefficient, and simplified model is equal to
amax；
5.3.3 inertia force load) is applied to vehicle frame, wherein load position is vehicle frame, driver, motor, battery case, deceleration
Machine is respectively with the position of frame contact, and magnitude of load is the product of component inertia power and peak acceleration, and wherein inertia force includes
Vehicle frame self weight, driver's inertia force, electric drive system inertia force, battery case inertia force；
5.3.4) to vehicle frame apply secondary role power, secondary role power respectively from rear overhang triangle rocker arm, rear overhang spring and
Transmission bracket；
5.3.5 simulation calculation) is carried out, total deformation cloud atlas, Stress Map and safety coefficient under accelerating mode is calculated
Figure；
5.3.6) by simulation result and material yield strength σsEqual mechanical attributes compare, and are obtained most by safety coefficient figure
Small safety coefficient ξ, if minimum safety factor ξ is less than ξ0, then increase uneasy all positon rod piece wall thickness and caliber, goes to step 3), it is no
Then meet safety requirements under accelerating mode, goes to step 5.4).
Further, above-mentioned steps 5.4) in damped condition analysis include the following steps:
5.4.1) all hard spots of fixed constraint, i.e. four-wheel locking state；
5.4.2 braking deceleration a required for damped condition) is calculatedz, calculation formula is as follows:
V in formula0 2To start retro-speed, Z is braking distance；
5.4.3 inertia force load) is applied to vehicle frame, wherein load position is vehicle frame, driver, motor, battery case, deceleration
Machine is respectively with the position of frame contact, and magnitude of load is the product of component inertia power and braking deceleration, and wherein inertia force includes
Vehicle frame self weight, driver's inertia force, electric drive system inertia force, battery case inertia force；
5.4.4) to vehicle frame apply secondary role power, secondary role power respectively from rear overhang triangle rocker arm, rear overhang spring and
Front overhang triangle rocker arm；
5.4.5 simulation calculation) is carried out, total deformation cloud atlas, Stress Map and safety coefficient under damped condition is calculated
Figure；
5.4.6) by simulation result and material yield strength σsEqual mechanical attributes compare, and are obtained most by safety coefficient figure
Small safety coefficient ξ, if minimum safety factor ξ is less than ξ0, increase uneasy all positon rod piece wall thickness and caliber, go to step 3), otherwise
Meet safety requirements under accelerating mode, obtains desired Safety vehicle frame model T2.
Compared with prior art, the present invention is from ergonomics experiment early period, until frame clamp modelling,
A set of rigorous reasonable process and theoretical method are provided for electronic equation motorcycle race Vehicle Frame Design, greatly reduces Vehicle Frame Design week
Phase improves vehicle frame performance, has done supplement and improvement for the theoretical research of current FSEC vehicle frame, has had practicability.
Detailed description of the invention
The electronic equation motorcycle race Vehicle Frame Design method flow diagram of Fig. 1.
Fig. 2 vehicle frame model and hard spot position view.
Specific embodiment
Present invention will be further explained with reference to the attached drawings and specific examples, it should be pointed out that below only
Technical solution of the present invention and design principle are described in detail with a kind of technical solution of optimization, but guarantor of the invention
Shield range is not limited to this.
The embodiment is a preferred embodiment of the present invention, but present invention is not limited to the embodiments described above, not
In the case where substantive content of the invention, any conspicuous improvement that those skilled in the art can make, replacement
Or modification all belongs to the scope of protection of the present invention.
Fig. 1 show electronic equation motorcycle race Vehicle Frame Design method flow diagram；Include the following steps:
1) vehicle frame parameter and vehicle frame hard spot position are determined, vehicle frame parameter includes man-machine parameter and whole-car parameters, wherein people
Machine parameter includes: the distance between main ring front ring d1, main ring height h1, front ring height h2, braking distance of the gas pedal away from main ring
d2, braking gas pedal tilt angle γ, steering wheel hub point height h3And away from main ring distance d2, cabin width l1, whole-car parameters
Including vehicle wheelbase L, wheelspan LsWith fore-aft loads ratio, the specific method is as follows:
1.1) man-machine experiment is carried out at design initial stage, builds man-machine experimental bench, with simulator operation achievement and driver master
Sight is felt as evaluation criterion, with the man-machine database of driver for objective reference, man-machine parameter is obtained, wherein man-machine parameter includes:
The distance between main ring front ring d1, main ring height h1, front ring height h2, braking distance d of the gas pedal away from main ring2, braking throttle
Pedal tilt angle γ, steering wheel hub point height h3And away from main ring distance d2, cabin width l1；
1.2) fore-aft loads ratio k is determined, in the present embodiment, load ratio k value is 48:52, when vehicle fore-aft loads are than protecting
Holding can make vehicle possess good control stability in 48:52.
1.3) vehicle wheelbase L is calculated, wheelbase is depending on carload, with seat lowest point for man-machine H point, that is, it is whole
The direction x position where vehicle mass center, circular are as follows:
1.3.1 vehicle front axle load M) is calculatedtf, the method is as follows:
In formula, MiFor the quality of each main component, XiX-axis distance for each main component relative to mass center, L are then wheelbase,
N indicates components number；
1.3.2) axle load M after calculating vehicletr, the method is as follows:
Mtr=M0-Mtf
In formula, M0For complete vehicle quality (in the case that driver is fully loaded)；
1.3.3 vehicle wheelbase L) is calculated, the method is as follows:
In the present embodiment, it is contemplated that the big tournament rules requirement of FSEC, the racing car at least wheelbase of 1525mm, the wheelbase of racing car
Greatly, vehicle frame quality certainly will also increase, under light-weighted thought, arrangement is compact as far as possible, and first dead axle is away from 1570mm；
1.4) wheelspan L is determineds；Wheelspan according to rule require, lesser wheelspan be no less than large wheel away from 75%, wheelspan pair
Gross mass, overall size, the control stability of racing car have larger impact, and wheelspan increases, and suspension roll angular rigidity is bigger, suspension power
It is better with kinematics performance to learn, also more advantageous for rear deck arrangement, but should not be too large, and otherwise will lead to spatial redundancy, quality without
Therefore increase.Front tread 1210mm, rear tread 1180mm are selected in the present embodiment；
1.5) it determines suspension hard spot position, using suspension positional parameter, carries out kinematics, dynamics simulation determines that suspension is hard
Point position, positional parameter mainly includes camber angle α1, leaning angle α2, back rake angle α3, toe-in α4Deng；
1.6) vehicle frame hard spot position is determined, according to suspension hard spot position and vehicle frame hard spot and suspension hard spot position relative quantity
Obtain vehicle frame hard spot position；In the present embodiment, vehicle frame hard spot and suspension hard spot position relative quantity range are as follows: the direction x (- 10,20),
The direction y (30,40), the direction z (- 5,5), hard spot position is as shown in Figure 2；
2) man-machine parameter, whole-car parameters, vehicle frame hard spot position are utilized, initial vehicle frame model T is built；
According to the distance between main ring front ring d1, main ring height h1, front ring height h2, braking, gas pedal away from main ring away from
From d2, braking gas pedal tilt angle γ, steering wheel hub point height h3And away from main ring distance d2, cabin width l1, wheelbase
L, wheelspan LsAnd vehicle frame hard spot position carries out model buildings, is connected between hard spot with rod piece, and be connected to main ring front ring and
At front baffle position；Vehicle frame model includes leg cabin, sits cabin and rear deck；Frame section before wherein leg cabin structure is front ring is
Driver's legs and feet provide operating space.Specifically there are front baffle, front baffle support rod, front ring, front ring support rod and other are attached
Rod piece, is integrated with braking system, steering system and front suspension system in leg cabin, and leg bilge portion, which is arranged rod piece and carries, turns to assembly,
The fixed brake cylinder of lifting lug is welded in front baffle space is further saved, the bottom of in meeting rule on 915 rule-based approach
Joint welding steel pipe makees back-plate support in two direction x parallel steel tube of portion.In order to keep the vehicle frame stress at damper more preferable, in leg cabin
Top increases cross bar as support.As for front ring, in order to look after driver's driving vision, front ring height is reduced as far as possible, but need to protect
Barrier height meets leg cabin rule plate and when steering wheel is killed is no more than front ring height；It sits cabin and refers to the frame portion between main ring front ring
Point, it sits side crashproof structure in the design of cabin and is designed according to classical three-legged structure required in rule, increase upside side rod top
Rod piece is bonded rod piece as with vehicle body, and driver is allow to go out cabin according to driver two sides vehicle body when escaping, it is desirable that body side case with
Distance is no more than 10mm between upper side edge crash bar upper pole segments；Rear deck is the frame section after main ring, is battery case, motor
Drive assembly and electric-control system provide installation environment.Rear deck needs the moderate direction y distance when designing, and meets battery case
Installation and operating space, rear deck bottom are welded with two 4mm thickness steel bars, support as battery case, by 10 corner braces, by battery case
It is mechanically connected on vehicle frame.Associated rod member structure is arranged in tail portion, for providing welding position for differential mechanism bracket and motor；
3) increase auxiliary bar, the size of adjustment rod member, including caliber, wall thickness on the basis of initial vehicle frame model T, obtain
Vehicle frame model T ' adjusted；
4) finite element analysis vehicle frame model torsion stiffness is utilized, ideal vehicle frame model T1 is obtained；Chassis torsion rigidity is vehicle
Important one in frame evaluation index, the torsion stiffness of vehicle frame refer to vehicle frame when bearing vertical load, the journey of torsional deflection
Degree, can be a simply supported beam by vehicle frame model simplification, and fulcrum is that front and back hangs vehicle frame hard spot.Vehicle frame is matched with suspension, is being transported
During dynamic, if vehicle frame rigidity is lower than suspension roll angular rigidity, it may occur that the case where vehicle frame is by turning round causes to pacify to body frame structure for automotive
Full blast danger, the decline of vehicle control stability it requires that the practical torsion stiffness of vehicle frame is higher than suspension roll angular rigidity, also to there is foot
Enough is more than needed.Method particularly includes:
4.1) FEM calculation vehicle frame model T ' torsion stiffness value K adjusted is utilizedn；Analysis method is in finite element fraction
It analyses in software, the hard spot of the outstanding wherein side in constraint front and back is applied with the forced displacement of lower each 1mm to another party, obtains support reaction
F, and chassis torsion rigidity is thus calculated, the torsion stiffness value calculation formula that each model calculates is as follows:
K in formulanFor the torsion stiffness value that each model calculates, F is support reaction, and d is the distance between two hard spot of suspension, Δ
A, Δ B is the forced displacement of two hard spots.
4.2) synthesis vehicle frame the torsion stiffness K, K for calculating vehicle frame model T ' adjusted are by the torsion under the outstanding constraint in front and back
Rigidity, which is combined, to be obtained, specific formula is as follows:
K in formulafFor the torsion stiffness under front overhang torsion, KrFor the torsion stiffness that rear overhang torsion is lower, a for front axle away from, after b is
Wheelbase, L are wheelbase.
Good material is defined in specific implementation in finite element software, imports model, carries out pipe fitting imparting, applies constraint item
Four hard spots up and down of rear overhang rearward are fixed constraint, limited by part, first the torsion stiffness value under the torsion of calculating front overhang
Freedom degree processed, top two hard spot forward to front overhang are applied with the forced displacement of lower each 1mm, calculate support reaction, bring public affairs into
Formula carries out that K is calculatedf, in the present embodiment, d1=404mm obtains maximum support reaction F=1632.55N by emulation, and calculating can
Obtain Kf=2325.306Nm/deg；The torsion stiffness value under rear overhang torsion is calculated again, by forward four up and down of front overhang
Constraint is fixed in hard spot, limits its freedom degree, and two hard spots up and down of rear overhang rearward are applied with the force bit of lower each 1mm
It moves, calculates support reaction, bring formula into and carry out that K is calculatedr, d in the present embodiment2=506mm obtains maximum branch by emulation
Counter-force F=1269.5N, Kr=2836.5Nm/deg brings formula (4) into and obtains global stiffness K, a=in the present embodiment
753.6mm b=816.4mm,
4.3) judge whether to meet K > K0And m < m0If 4.4) satisfaction is gone to step, otherwise go to step 3), the present embodiment
In, K0=2000Nm/deg, m0=28kg；
4.4) unit of account quality torsion stiffness
4.5) judge whether to meetIf satisfaction obtains ideal vehicle frame model T1,3) this implementation is otherwise gone to step
In example, p0=81Nm/ (kgdeg)；
5) performance analysis is carried out to ideal vehicle frame model T1, obtains desired Safety vehicle frame model T2；Vehicle frame is checked each
Intensity under typical condition optimizes reinforcement to the position of vehicle frame stress weakness, to guarantee to meet racing car in the process of moving
Requirement；Wherein, operating condition includes straight line operating condition, at the uniform velocity excessively curved operating condition, accelerating mode and damped condition.
5.1) straight line operating condition is primary concern is that intensity of the racing car under fully loaded operating condition and by curved situation.Such case
Under, vehicle frame still suffers from the devices such as battery case, motor transmission system, steering system and driver other than bearing the gravity of itself
Gravity, therefore it is required that vehicle frame have high strength and stiffness.It is assumed herein that the quality of other widgets is to this operating condition without too
It is big to influence, it can ignore, straight line operating condition simulating analysis is as follows:
5.1.1) 4 hard spots of fixed constraint rear overhang, hard spot position as shown in Fig. 2, consider racing car approximate straight line motion, it is preceding
The constraint of the outstanding left side hard spot direction y, z, discharges the freedom degree in the direction x, right side hard spot y, and the constraint of the direction z discharges the direction x freedom degree.
5.1.2 load) applied to vehicle frame, load position be vehicle frame, driver, motor, battery case, speed reducer respectively and vehicle
The position of bridge joint touching, magnitude of load are that respective weight multiplies dynamic load factor, and dynamic load factor 2 in specific implementation, in addition to this there are also it
Remaining main component gravity and Motor torque；In the present embodiment, battery case case lining sets 5 mould groups, and each mould group selects 18,650 3
First lithium battery, 7 and 20 strings add various electric elements, conservative estimation battery case gross weight 55Kg, and active force acts on battery
On two 4mm thickness steel bars in bottom portion.Motor selects 228 motors, in addition planetary gear reducing mechanism, sprocket wheel and differential mechanism, electricity
Assembly weight 34Kg is driven, active force is applied on the steel pipe of related lifting lug welding, and driver weight 70Kg is multiplied by dynamic load factor, acts on
On the steel pipe of seat lifting lug welding, there are also vehicle frame self weights for remaining, and with Motor torque, Motor torque takes 240Nm, act on
On electric machine support；
5.1.3 simulation calculation) is carried out, total deformation cloud atlas, Stress Map and safety coefficient under straight line operating condition is calculated
Figure；
5.1.4) by simulation result and material yield strength σsEqual mechanical attributes compare, and are obtained most by safety coefficient figure
Small safety coefficient ξ increases uneasy all positon rod piece wall thickness and caliber if 3) minimum safety factor ξ less than 1.8, is gone to step；Otherwise
Illustrate to meet the requirements under straight line operating condition, go to step 5.2)；
5.2) at the uniform velocity excessively curved operating condition primary concern is that vehicle frame truss structure under the excessively curved operating condition of maximum centripetal acceleration, by
Its transverse direction main function arrived has the centrifugal acceleration inertia force of vehicle frame, the inertia force of each main big quality part, and straight
Line operating condition is identical, and inertia force is realized by way of multiplied by dynamic load factor.It is assumed that the operating condition is to turn to the left, other small portions
Part influence is ignored.The active force of maximum centrifugal acceleration mainly passes through suspension transverse arm and acts on vehicle frame, and horizontal force is
Predominant intermolecular forces, lateral displacement are main constraint.When analyzing simulation calculation, concrete operations are as follows:
5.2.1 whole hard spots) are surveyed in fixed constraint, to the outside namely right side direction z restraint of liberty degree, discharge the direction xy
Freedom degree.
5.2.2 maximum centripetal acceleration a) is calculatedrmax, it is as follows to calculate calculation formula；
A in formularmaxFor maximum centripetal acceleration, r is turning radius, tminFor the most fast individual pen time, by calculating to obtain armax
=18m/s2；
5.2.3 inertia force load) is applied to vehicle frame, load calculation method is that all parts inertia force and maximum laterally accelerate
The product of degree, inertia force have vehicle frame self weight, driver's inertia force, electric drive system inertia force, battery case inertia force, in addition to this
There are also remaining main component gravity and Motor torques；In the present embodiment, driver's inertia force load is 70 × 2 × 1.8g=
2520N, electric drive system inertia force load are 34 × 2 × 1.8g=1224N, and battery case inertia force load is 55 × 2 × 1.8g=
1980N, in addition to this there are also main component gravity 3060N, Motor torque 240Nm；
5.2.4 secondary role power) is applied to vehicle frame, is shaken respectively from rear overhang triangle rocker arm, rear overhang spring and front overhang triangle
Arm；In the present embodiment, rear overhang triangle rocker arm stress condition is Fx=0, Fy=432.54N, Fz=-212.94N；Rear overhang spring by
Power situation is Fx=366.26N, Fy=2168N, Fz=-935.25N；Front overhang triangle rocker arm stress condition is Fx=0, Fy=
600.05N, Fz=1610.2N；
5.2.5 simulation calculation) is carried out, total deformation cloud atlas, Stress Map and safety under at the uniform velocity excessively curved operating condition is calculated
Coefficient figure；
5.2.6) by simulation result and material yield strength σsEqual mechanical attributes compare, and are obtained most by safety coefficient figure
Small safety coefficient ξ increases uneasy all positon rod piece wall thickness and caliber if 3) minimum safety factor ξ less than 1.8, is gone to step；Otherwise
Illustrate to meet the requirements under at the uniform velocity excessively curved operating condition, go to step 5.3)；
5.3) above-mentioned accelerating mode is primary concern is that stress of the vehicle frame under racing car straight line peak acceleration driving cycle
Situation acts on the acceleration inertia force of vehicle frame and the inertia force of each main big quality part on longitudinal direction, most greatly
The speed longitudinal force that the inertia force of vehicle frame and suspension system act on vehicle frame when driving balance each other and in this, as check according to
According to.Assuming that other small quality parts are little to entire effect.The active force of maximum linear acceleration mainly passes through suspension transverse arm and makees
For vehicle frame, longitudinal force is predominant intermolecular forces, and length travel is main constraint.When analyzing simulation calculation, concrete operations are such as
Under:
5.3.1) 4 hard spots of fixed constraint rear overhang, four direction hard spot yz constraints of limitation front overhang, discharge the direction x freedom degree.
5.3.2 peak acceleration a needed for) calculating accelerating modemax, calculation formula is as follows:
amax=qaavg
S is that linear accelerating travels the distance passed by formula, and t is acceleration time, aavgFor the average acceleration in accelerator
Degree, q are classical coefficient, and simplified model is equal to amax；In the present embodiment, q takes 1.5, and the linear accelerating time takes 4.33s, S to take
75m can be calculated amax=1.2g；
5.3.2 inertia force load) is applied to vehicle frame, load calculation method is that all parts inertia force and maximum laterally accelerate
The product of degree, inertia force have vehicle frame self weight, driver's inertia force, electric drive system inertia force, battery case inertia force, in addition to this also
There are remaining main component gravity and Motor torque；In the present embodiment, driver's inertia force load is 70 × 2 × 1.2g=1680N,
Electric drive system inertia force load is 34 × 2 × 1.2g=816N, and battery case inertia force load is 55 × 2 × 1.2g=1320N, is removed
There are also main component gravity 3060N, Motor torque 240Nm except this；
5.3.4 secondary role power) is applied to vehicle frame, respectively from rear overhang triangle rocker arm, rear overhang spring and transmission bracket；This
In embodiment, rear overhang triangle rocker arm stress condition is Fx=0, Fy=324.06N, Fz=-159.54N；Rear overhang spring stress situation
For Fx=274.4N, Fy=1624.2N, Fz=-700.68N；Transmission upper left support force situation is Fx=2784.4N, Fy=0,
Fz=-5071.34N；Transmission right upper bracket stress condition is Fx=-393.8N, Fy=0, Fz=717.23N；It is driven left lower bracket
Stress condition is Fx=-5188.8N, Fy=0, Fz=-6693.5N；Transmission right lower bracket stress condition is Fx=733.8N, Fy=
0, Fz=946.6N；
5.3.5 simulation calculation) is carried out, total deformation cloud atlas, Stress Map and safety coefficient under accelerating mode is calculated
Figure；
5.3.6) by simulation result and material yield strength σsEqual mechanical attributes compare, and are obtained most by safety coefficient figure
Small safety coefficient ξ increases uneasy all positon rod piece wall thickness and caliber if 3) minimum safety factor ξ less than 1.8, is gone to step；Otherwise
Illustrate to meet the requirements under accelerating mode, go to step 5.4)；
5.4) under above-mentioned damped condition, the active force that the inertia force and suspension system of vehicle frame truss act on vehicle frame is in flat
Weighing apparatus state, in this, as the theoretical foundation of check, longitudinal direction act on vehicle frame deceleration inertia force and each main big matter
Measure the inertia force of component, it is assumed that the effect very little of other small quality parts, the inertia force influence of small quality part are little.It is maximum straight
The active force of line deceleration mainly passes through suspension transverse arm and acts on vehicle frame, and longitudinal force is predominant intermolecular forces, and length travel is
Main constraint.When analyzing simulation calculation, concrete operations are as follows:
5.4.1) all hard spots of fixed constraint, i.e. four-wheel locking state；
5.4.2 braking deceleration a required for damped condition) is calculatedz, calculation formula is as follows:
V in formula0 2To start retro-speed, Z is braking distance, by can be calculated az=1.6g.
5.4.3 inertia force load) is applied to vehicle frame, load calculation method is all parts inertia force and braking acceleration
Product, inertia force load have vehicle frame self weight, driver's inertia force, electric drive system inertia force, battery case inertia force, in addition to this also
There are remaining main component gravity and Motor torque；In the present embodiment, driver's inertia force load is 70 × 2 × 1.6g=2240N,
Electric drive system inertia force load is 34 × 2 × 1.6g=1088N, and battery case inertia force load is 55 × 2 × 1.6g=1760N,
In addition to this there are also main component gravity 3060N, Motor torque 240Nm.
5.4.4 secondary role power) is applied to vehicle frame, is shaken respectively from rear overhang triangle rocker arm, rear overhang spring and front overhang triangle
Arm；In the present embodiment, rear overhang triangle rocker arm stress condition is Fx=0, Fy=102.84N, Fz=-50.63N；Rear overhang spring stress
Situation is Fx=87.085N, Fy=-515.47N, Fz=-222.37N；Front overhang triangle rocker arm stress condition is Fx=0, Fy=
527.9N, Fz=1416.6N.
5.4.5 simulation calculation) is carried out, total deformation cloud atlas, Stress Map and safety coefficient under damped condition is calculated
Figure；
5.4.6) by simulation result and material yield strength σsEqual mechanical attributes compare, and are obtained most by safety coefficient figure
Small safety coefficient ξ increases uneasy all positon rod piece wall thickness and caliber if 3) minimum safety factor ξ less than 1.8, is gone to step；Otherwise
Illustrate to meet the requirements under accelerating mode, obtains desired Safety vehicle frame model T2；
6) finite element modal analysis is carried out to desired Safety vehicle frame model T2, obtains final vehicle frame model；
Model analysis is the pith of driving skills dynamic analysis, by analyze available structure modal frequency and
Mode Shape.Racing car travels on racing track, since the vibration of Uneven road and engine can generate exciting to vehicle frame, if exciting
Frequency is identical as a certain intrinsic frequency of driving skills, will generate covibration, and the mechanical performance that may will affect racing car is even broken
Bad body frame structure for automotive.It is therefore desirable to analyze the eigenfrequncies and vibration models of vehicle frame, reference is provided to the structure design of vehicle frame.Mode point
Analysis has Free Modal and two kinds of Constrained mode, in order to preferably be bonded reality, using Constrained mode analysis method, concrete operations
Are as follows:
6.1) 8 hard spots are hanged before and after fixed constraint vehicle frame.
6.2) inertia force load is applied to vehicle frame.Consider the approximate straight line motion of racing car, other than the weight of vehicle frame, also
The weight of driver, the weight of engine, in addition this Work condition analogue is the stress of racing car during the motion, therefore should be multiplied
A upper dynamic load factor, in the present embodiment, taking dynamic load factor is 2.Main stress has driver, battery case, electric drive system, vehicle frame
Self weight, Motor torque, magnitude of load and application position are identical as straight line operating condition.
6.3) simulation analysis is carried out, preceding 8 rank modal frequency and the vibration shape are obtained；
6.4) the external drive frequency of the components such as 8 rank modal frequency of gained and motor is compared, sees whether frequency
Coincidence is resonated, and body frame structure for automotive is caused to destroy, if covibration, return step 3 occurs) carry out the variation of size rod piece；Such as
Covibration does not occur for fruit, then illustrates that vehicle frame meets model analysis requirement, obtains final vehicle frame model T3；
7) design of welding jig is carried out to final vehicle frame model T3；In the present embodiment, using 4040 aluminum profiles as fixture
Material carries out pole stock with corner brace and connects firmly, and in design process, using front baffle, front ring, main ring as three index planes, uses frame
Type structure guarantees globality, reduces influence of the welding stress to steel pipe position in the welding process.Principal security vehicle frame and suspension
The position of relevant 16 hard spots and the position of front and back shock absorber shackle, using aluminum profile and auxiliary clamp to these vital points
Freedom degree limitation is carried out, to guarantee machining accuracy.Vehicle frame model matches observation with welding fixture in three-dimensional software, guarantees fixture
The reasonability of design.
Claims (10)
1. a kind of design method of electronic equation motorcycle race vehicle frame, it is characterised in that include the following steps:
1) vehicle frame parameter and vehicle frame hard spot position are determined；
2) man-machine parameter, whole-car parameters, vehicle frame hard spot position are utilized, initial vehicle frame model T is built；
3) increase auxiliary bar on the basis of initial vehicle frame model T, adjustment rod member size, the vehicle frame model T ' after being adjusted,
Wherein, rod size includes caliber size, wall thickness dimension；
4) finite element analysis vehicle frame model T ' torsion stiffness is utilized, ideal vehicle frame model T1 is obtained；
5) performance analysis is carried out to ideal vehicle frame model T1, obtains desired Safety vehicle frame model T2；
6) finite element modal analysis is carried out to desired Safety vehicle frame model T2, obtains final vehicle frame model T3；
7) design of welding jig is carried out to final vehicle frame model T3.
2. the design method of electronic equation motorcycle race vehicle frame as described in claim 1, it is characterised in that in the step 1) really
Determining vehicle frame parameter and vehicle frame hard spot position, the specific method is as follows:
1.1) man-machine experiment is carried out at design initial stage, builds man-machine experimental bench, with simulator operation achievement and the sense of driver's subjectivity
Man-machine parameter is obtained, wherein man-machine parameter includes: main ring with the man-machine database of driver for objective reference by for evaluation criterion
The distance between front ring d1, main ring height h1, front ring height h2, braking distance d of the gas pedal away from main ring2, braking gas pedal
Tilt angle γ, steering wheel hub point height h3And away from main ring distance d2, cabin width l1；
1.2) fore-aft loads ratio k is determined；
1.3) vehicle wheelbase L is calculated；
1.4) wheelspan L is determineds；
1.5) it determines suspension hard spot position, using suspension positional parameter, carries out kinematics, dynamics simulation determines suspension hard spot position
It sets, positional parameter includes camber angle α1, leaning angle α2, back rake angle α3, toe-in α4；
1.6) it determines vehicle frame hard spot position, is obtained according to suspension hard spot position and vehicle frame hard spot with suspension hard spot position relative quantity
Vehicle frame hard spot position, the lifting lug size that wherein relative quantity is connect by suspension with vehicle frame determine.
3. the design method of electronic equation motorcycle race vehicle frame as described in claim 1, it is characterised in that in the step 4)
To ideal vehicle frame model T1, the specific method is as follows:
4.1) FEM calculation vehicle frame model T ' torsion stiffness value K is utilizedn, calculation formula is as follows:
K in formulanFor the torsion stiffness value that each model calculates, F is support reaction, and d is the distance between two hard spot of suspension, Δ A, Δ B
For the forced displacement of two hard spots；
4.2) the synthesis vehicle frame torsion stiffness K of vehicle frame model T ' is calculated, calculation formula is as follows:
K in formulafFor the torsion stiffness under front overhang torsion, KrFor the torsion stiffness that rear overhang torsion is lower, a for front axle away from, b is rear axle
Away from L is wheelbase；
4.3) judge whether to meet K > K0And m < m0If 4.4) satisfaction is gone to step, otherwise go to step 3)；
4.4) judge whether to meetIdeal vehicle frame model T1 is obtained if meeting, is otherwise gone to step 3).
4. the design method of electronic equation motorcycle race vehicle frame as described in claim 1, it is characterised in that right in the step 5)
Ideal vehicle frame model T1 carries out performance analysis and includes the following steps:
5.1) straight line performance analysis；
5.2) at the uniform velocity excessively curved performance analysis；
5.3) accelerating mode is analyzed；
5.4) damped condition is analyzed.
5. the design method of electronic equation motorcycle race vehicle frame as described in claim 1, it is characterised in that 6) right in the step
Desired Safety vehicle frame model T2 carries out finite element modal analysis, and obtaining final vehicle frame model T3, the specific method is as follows:
6.1) 8 hard spots are hanged before and after fixed constraint vehicle frame；
6.2) inertia force load is applied to vehicle frame；
6.3) simulation analysis is carried out, preceding 8 rank modal frequency and the vibration shape are obtained；
6.4) the external drive frequency of the components such as 8 rank modal frequency of gained and motor is compared, sees whether that frequency is overlapped
Resonate, if covibration, return step 3 occurs) carry out the variation of size rod piece；Otherwise final vehicle frame model T3 is obtained.
6. the design method of electronic equation motorcycle race vehicle frame as claimed in claim 2, it is characterised in that in the step 1.3)
Calculating vehicle wheelbase L, the specific method is as follows:
1.3.1 vehicle front axle load M) is calculatedtf, formula is as follows:
In formula, MiFor the quality of each main component, XiX-axis distance for each main component relative to mass center, L are then wheelbase, N table
Show components number；
1.3.2) axle load M after calculating vehicletr, formula method is as follows:
Mtr=M0-Mtf
In formula, M0For complete vehicle quality (in the case that driver is fully loaded)；
1.3.3 vehicle wheelbase L) is calculated, formula is as follows:
。
7. the design method of electronic equation motorcycle race vehicle frame as claimed in claim 4, it is characterised in that in the step 5.1)
Straight line performance analysis includes the following steps:
5.1.1) 4 hard spots of fixed constraint rear overhang, the front overhang left side hard spot direction y, z constraint, discharge the freedom degree in the direction x, right side
The constraint of the hard spot direction y, z, discharges the direction x freedom degree；
5.1.2 load) is applied to vehicle frame, wherein load position be vehicle frame, driver, motor, battery case, speed reducer respectively and vehicle
The position of bridge joint touching, magnitude of load are that respective weight multiplies dynamic load factor；
5.1.3 simulation calculation) is carried out, total deformation cloud atlas, Stress Map and safety coefficient figure under straight line operating condition is calculated；
5.1.4) by simulation result and material yield strength σsEqual mechanical attributes compare, and obtain minimum peace by safety coefficient figure
Overall coefficient ξ, if minimum safety factor ξ is less than ξ0, increase uneasy all positon rod piece wall thickness and caliber, go to step 3), otherwise illustrate
Meet safety requirements under straight line operating condition, goes to step 5.2).
8. the design method of electronic equation motorcycle race vehicle frame as claimed in claim 4, it is characterised in that in the step 5.2)
Curved performance analysis is at the uniform velocity crossed to include the following steps:
5.2.1 whole hard spots) are surveyed in fixed constraint, to the outside direction z restraint of liberty degree, discharge the direction xy freedom degree；
5.2.2 maximum centripetal acceleration a) is calculatedrmax, calculation formula is as follows:
A in formularmaxFor maximum centripetal acceleration, r is turning radius, tminFor the most fast individual pen time；
5.2.3 inertia force load) is applied to vehicle frame, wherein load position is that vehicle frame, driver, motor, battery case, speed reducer are each
From the position with frame contact, magnitude of load is the product of component inertia power and maximum centripetal acceleration, and wherein inertia force includes
Vehicle frame self weight, driver's inertia force, electric drive system inertia force, battery case inertia force；
5.2.4 secondary role power) is applied to vehicle frame, secondary role power is respectively from rear overhang triangle rocker arm, rear overhang spring and front overhang
Triangle rocker arm；
5.2.5 simulation calculation) is carried out, total deformation cloud atlas, Stress Map and safety coefficient under at the uniform velocity excessively curved operating condition is calculated
Figure；
5.2.6) by simulation result and material yield strength σsEqual mechanical attributes compare, and obtain minimum peace by safety coefficient figure
Overall coefficient ξ, if minimum safety factor ξ is less than ξ0, then increase uneasy all positon rod piece wall thickness and caliber, goes to step 3), it is otherwise even
Meet safety requirements under the excessively curved operating condition of speed, goes to step 5.3).
9. the design method of electronic equation motorcycle race vehicle frame as claimed in claim 4, it is characterised in that in the step 5.3)
Accelerating mode analysis includes the following steps:
5.3.1) 4 hard spots of fixed constraint rear overhang, four direction hard spot yz constraints of limitation front overhang, discharge the direction x freedom degree；
5.3.2 peak acceleration a needed for) calculating accelerating modemax, calculation formula is as follows:
S is that linear accelerating travels the distance passed by formula, and t is the acceleration time, and q is classical coefficient, and simplified model is equal to amax；
5.3.3 inertia force load) is applied to vehicle frame, wherein load position is that vehicle frame, driver, motor, battery case, speed reducer are each
From the position with frame contact, magnitude of load is the product of component inertia power and peak acceleration, and wherein inertia force includes vehicle frame
Self weight, driver's inertia force, electric drive system inertia force, battery case inertia force；
5.3.4 secondary role power) is applied to vehicle frame, secondary role power is respectively from rear overhang triangle rocker arm, rear overhang spring and transmission
Bracket；
5.3.5 simulation calculation) is carried out, total deformation cloud atlas, Stress Map and safety coefficient figure under accelerating mode is calculated；
5.3.6) by simulation result and material yield strength σsEqual mechanical attributes compare, and obtain minimum peace by safety coefficient figure
Overall coefficient ξ, if minimum safety factor ξ is less than ξ0, then increase uneasy all positon rod piece wall thickness and caliber, go to step 3), otherwise plus
Meet safety requirements under fast operating condition, goes to step 5.4).
10. the design method of electronic equation motorcycle race vehicle frame as claimed in claim 4, it is characterised in that in the step 5.4)
Damped condition analysis includes the following steps:
5.4.1) all hard spots of fixed constraint, i.e. four-wheel locking state；
5.4.2 braking deceleration a required for damped condition) is calculatedz, calculation formula is as follows:
V in formula0 2To start retro-speed, Z is braking distance；
5.4.3 inertia force load) is applied to vehicle frame, wherein load position is that vehicle frame, driver, motor, battery case, speed reducer are each
From the position with frame contact, magnitude of load is the product of component inertia power and braking deceleration, and wherein inertia force includes vehicle frame
Self weight, driver's inertia force, electric drive system inertia force, battery case inertia force；
5.4.4 secondary role power) is applied to vehicle frame, secondary role power is respectively from rear overhang triangle rocker arm, rear overhang spring and front overhang
Triangle rocker arm；
5.4.5 simulation calculation) is carried out, total deformation cloud atlas, Stress Map and safety coefficient figure under damped condition is calculated；
5.4.6) by simulation result and material yield strength σsEqual mechanical attributes compare, and obtain minimum peace by safety coefficient figure
Overall coefficient ξ, if minimum safety factor ξ is less than ξ0, increase uneasy all positon rod piece wall thickness and caliber, go to step 3), otherwise speed up
Meet safety requirements under operating condition, obtains desired Safety vehicle frame model T2.
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| CN112035953A (en) * | 2020-08-24 | 2020-12-04 | 山东大学 | Electric tricycle frame lightweight design method and system based on rigid-flexible coupling |
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| CN112613217A (en) * | 2020-12-25 | 2021-04-06 | 中国第一汽车股份有限公司 | Modeling method for shaft tooth performance simulation model of electric drive system speed reducer |
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