CN104239734A - Load analysis method for four-wheel six-component road spectrum of finished automobile - Google Patents
Load analysis method for four-wheel six-component road spectrum of finished automobile Download PDFInfo
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Abstract
The invention relates to a load analysis method for a four-wheel six-component road spectrum of a finished automobile. The method comprises the following steps: 1 testing a four-wheel six-component road spectrum of a finished automobile; 2 collecting the design data of the finished automobile; 3 building and adjusting a dynamic model of the finished automobile; 4 carrying out virtual iteration; 5 obtaining Z-direction displacement of a wheel center; 6 decomposing the load of the finished automobile; 7 processing the load result. The six components of four wheel centers of the finished automobile are directly measured as external road excitation input; the actual stress condition of each wheel center under the typical characteristic road excitation of test site reliability is reflected; the technical effect of obtaining the load of the finished automobile system and spare parts is realized by a virtual iteration technique and a dynamics simulation technique; the anti-fatigue performance of the finished automobile structure can be accurately predicted and optimized at the earlier stage; problem rectification of the sample automobile stage is reduced; the research and development cycle is shortened; the research and development cost is also reduced.
Description
Technical field
The present invention relates to a kind of loading analysis method, be specifically related to car load four-wheel six square phase road spectrum loading analysis method.
Background technology
Reliability is very important product quality in automobile research and development, and automobile reliability design matter of utmost importance obtains each system of vehicle structure and the load environment of parts in user uses.Load needed for the complete vehicle structure analysis of fatigue of current most domestic auto vendor mainly adopts traditional stand experience load, with user's road and testing field load dependence poor.Lack real road load, cause the blindness that automobile product designs, occur that complete vehicle structure fatigue endurance performance crosses design, increase panel beating thickness, increase complete vehicle weight, thus increase cost of products; Or the design of complete vehicle structure fatigue endurance performance is not enough, occurs various structure crack phenomenon in reliability compliance test, extends the R&D cycle, causes product to put on market in time, the critical period of even missing the market competition.More seriously, in user uses, occur safety member structural break, serious threat to life, affects brand effect.
Road load is time dependent dynamic random load, is the important sources of vehicle structure fatigue failure external drive load, so must pay close attention to the size of punishing road load.In " car body dynamic intensity analysis method " (patent No.: ZL200810141691.1), emulate using the wheel heart acceleration tested as excitation, the load accuracy of acquisition is not high, truly can not reflect each system of car load and parts stressing conditions.Current most of producers adopt six square phase wheel detector to measure car load travel load, if but the core wheel six square phase recorded is applied directly on multi-body dynamics automobile model emulates, car load can be caused to drift about to disperse and do not restrain and cannot solve.So each system and parts load obtain usually adopt two kinds of methods: method one is that fixing vehicle body carries out car load emulation, method two carries out car load emulation with spring constraint vehicle body, car load road spectrum fatigue load is obtained although can emulate, but in fact vehicle body is in free state in the process of moving, make that car load fatigue load spectrum is very inaccurate, precision is low owing to being applied with the constraint of extra vehicle body, be unfavorable for the quantitative evaluation of car load analysis of fatigue result, even risk of error occurring assessment.
Summary of the invention
In order to overcome above-mentioned the deficiencies in the prior art, the invention provides a kind of car load four-wheel six square phase road spectrum loading analysis method, with the punishing road loading spectrum of each Iarge-scale system of Obtaining Accurate car load and parts.
Technical scheme of the present invention is as follows:
A kind of car load four-wheel six square phase road spectrum loading analysis method, comprises the following steps:
Step 1, car load four-wheel six square phase road spectrum is tested: the six square phase not only measuring four wheel disk places, also comprises the signals such as measuring spring displacement, vibration damper power and spindle nose acceleration, with proof load precision of analysis.
Step 2: entire vehicle design Data Collection: data comprise car load axle load wheel load and distribute, design hard spot, chassis part mass property, chassis lining rigidity, power assembly mass property and suspension bushing rigidity, spring rate, vibration damper drag characteristic, wheelbase wheelspan, axle load;
Step 3: Full Vehicle Dynamics model is set up and adjustment: according to annexation between the entire vehicle design data of collecting and parts, set up suspension, power assembly, vehicle body, turn to, the subsystem model such as stabilizer bar, assembled by above-mentioned subsystem model and set up Full Vehicle Dynamics model;
Step 4: virtual iteration: this step is the core link of invention.Object obtains core wheel Z-direction displacement drive signal by virtual iteration, and using the displacement constraint that the displacement of core wheel Z-direction is decomposed as carload, prevent from car load from drifting about to disperse, this displacement simultaneously also reflects the unevenness of testing field reliability road, and the vertical deviation excitation size to car load core wheel.
(1) whole vehicle model transport function generates
The drive singal input emulated using u (noise signal) as multi-body dynamics automobile model, simulation data response signal y (comprising spring displacement, spindle nose acceleration and core wheel Z-direction power), is calculated the transport function F of whole vehicle model by formula [1]
F＝y/u 【1】
(2) initial driving signal and for the first time simulation calculation
By the inverse function F of transport function F
-1with the spring displacement tested, spindle nose acceleration and core wheel Z-direction power echo signal y
desired, try to achieve one group of initial drive singal U by formula [2]
0
u
0＝F
-1*y
Desired 【2】
Wherein: F
-1the inverse function of-transport function; y
desiredthe echo signal of-test, as spring displacement, core wheel Z-direction force, spindle nose acceleration; u
0-initial displacement drive signal;
Then carry out car load emulation, the response signals such as delivery spring displacement, spindle nose acceleration and core wheel Z-direction power, carry out time domain, frequency domain and relative damage value three aspect comparative assessment respectively by this result and test result.
(3) virtual iteration
By the result u of first time simulation calculation
0initial driving signal as system core wheel inputs, and emulation obtains the response signal y of output channel
0, by y
0with y
desiredrelatively, if meet target control condition, u
0it is exactly the drive singal of reverse; If do not met, then press formula [3] and revise Z-direction displacement drive signal, then carry out the calculating that iterates,
u
n＝u
n-1+F
-1*(y
Desied-y
n-1) 【3】
Wherein, u
nit is the drive singal after n iteration;
Until the comparative result of above-mentioned iteration passage meets target control condition, namely time domain and frequency-region signal coincide respectively, and relative damage value reaches desired value 1, and iteration terminates.
Step 5, the displacement of core wheel Z-direction obtain:
When virtual iteration meets target control condition, now corresponding core wheel Z-direction displacement is required core wheel displacement drive signal, as the constraint condition that carload is decomposed;
Step 6, carload are decomposed:
The core wheel Z-direction displacement that the wheel mental and physical efforts (except Z-direction power) of testing with step 1 and the virtual iteration of step 5 obtain is added four core wheel positions respectively to and is driven car load to carry out load decomposition;
Step 7, load results process:
After carload decomposition terminates, carry out simulation result aftertreatment, obtain each system of car load and Parts loading spectrum.
The present invention is owing to adopting the six square phase at the car load four-wheel core wheel place directly measured as outside road excitation input, reflect the core wheel actual loading situation under the reliability characteristic feature road excitation of testing field, not only objective but also directly, avoid the tire parameter characteristic that is difficult to obtain to the impact of car load dummy load result.The technical bottleneck of Full Vehicle System and the acquisition of parts load is solved by virtual iterative technique and dynamics simulation technology, just can forecast and promote complete vehicle structure fatigue endurance performance accurately in early stage, reduce the problem rectification of sample car stage, shorten the R&D cycle, reduce R&D costs.By setting up platform vehicle type load data storehouse, being the new car R & D design of same platform and later stage system and parts DV verification experimental verification, cae analysis load and bench test proof load are provided.
The present invention has very strong engineering practicability, solving traditional stand experience load can not the deficiency of accurate evaluation complete vehicle structure fatigue endurance performance, solving the spindle nose core wheel six square phase directly adding test causes car load drift to disperse the defect do not restrained, solving prior art is that vehicle body adds additional constraint condition and carries out the inaccuracy that emulates, avoids the tire parameter characteristic that is difficult to obtain to the impact of car load simulation result.
Accompanying drawing explanation
Fig. 1 car load four-wheel six square phase road spectrum loading analysis process flow diagram;
The virtual iterative technique schematic diagram of Fig. 2;
Fig. 3 transport function schematic diagram;
Fig. 4 spring displacement time domain compares schematic diagram;
Fig. 5 spring displacement frequency domain compares schematic diagram.
Embodiment
Below in conjunction with accompanying drawing, the present invention is described further.
See Fig. 1, car load four-wheel six square phase road spectrum loading analysis method step is as follows:
1, car load four-wheel six square phase road spectrum test
Car load four-wheel six square phase road spectrum is tested, and not only tests the six square phase at four-wheel core wheel place, also comprises test spring displacement, signal such as wheel heart acceleration, vibration damper power etc.
2, entire vehicle design Data Collection
Obtaining authentic and valid entire vehicle design data, is the prerequisite setting up Full Vehicle Dynamics model.Entire vehicle design data, comprise car load axle load wheel load and distribute, design hard spot, chassis part mass property, chassis lining rigidity, power assembly mass property and suspension bushing rigidity, spring rate, vibration damper drag characteristic, wheelbase wheelspan, axle load etc.
3, Full Vehicle Dynamics model is set up and adjustment
According to annexation between the entire vehicle design data of collecting and parts, set up suspension, power assembly, vehicle body, turn to, the subsystem model such as stabilizer bar, assembled by above-mentioned subsystem model and set up Full Vehicle Dynamics model.
The object of model adjustment is exactly the precision controlling and ensure Full Vehicle Dynamics model, the accuracy that lifting load is analyzed.Adjusting process is as follows:
(1) suspension K & C adjustment
K & C adjustment carries out K & C by suspension system to emulate, carry out emulating the K index that draws and C index and car load K & C test findings mark respectively, if both results misfit, must amendment model parameter again emulate, until simulation result is consistent with test findings, thus demonstrate the accuracy of Suspension Model.
(2) whole vehicle model adjustment
Whole vehicle model adjustment ensures that the whole vehicle model of emulation is consistent with test vehicle test mode.Whole vehicle model adjustment comprises: static characteristics adjustment and dynamic perfromance adjustment.
Static characteristics adjustment is undertaken by static equilibrium emulation.The axle load obtained after static equilibrium emulation and wheel load, buffer clearance, the spring change result such as displacement, car load centroid position and test vehicle static test come to the same thing.
Dynamic perfromance adjustment emulates mainly through core wheel input random signal, the kinematic relation checked vehicles between parts, and inspection model freedom of motion checks vibration-damper characterist.
4, virtual iteration, the principle of virtual iteration is see Fig. 2:
1) whole vehicle model transport function generates
The drive singal input emulated using u as multi-body dynamics automobile model, simulation data response signal y, is calculated the transport function F of whole vehicle model by formula [1].
F＝y/u 【1】
Wherein: F-transport function; The response signals such as y-displacement, power, acceleration; The drive singal such as u-displacement, power, acceleration.
As shown in Figure 3, wherein: 8 is spring displacement transfer curves, 9 is vibration damper power transfer curves, and 10 is spindle nose acceleration transfer curves, and 11 is core wheel Z-direction power transfer curves.
(2) initial driving signal and for the first time simulation calculation
Calculate the Z-direction displacement initial driving signal of core wheel according to echo signals such as formula [2] and the spring displacement tested, spindle nose acceleration and core wheel Z-direction power, (2) are by the inverse function F of transport function F
-1with the spring displacement tested, spindle nose acceleration and core wheel Z-direction power echo signal y
desired, try to achieve one group of initial drive singal U by formula [2]
0
u
0＝F
-1*y
Desired 【2】
Wherein: F
-1the inverse function of-transport function; y
desiredthe echo signal of-test, as displacement, power, acceleration; u
0-initial the drive singal such as displacement, power, acceleration;
Then car load emulation is carried out, the response signals such as delivery spring displacement, spindle nose acceleration and core wheel Z-direction power, carry out time domain (as shown in Figure 4), frequency domain (as shown in Figure 5) and relative damage value (according to target value 1 is evaluated) three aspect comparative assessments respectively by this result and test result.
(3) virtual iteration
By the result u of first time simulation calculation
0initial driving signal as system core wheel inputs, and emulation obtains the response signal y of output channel
0, by y
0with y
desiredrelatively, if meet target control condition, u
0it is exactly the drive singal of reverse; If do not met, then press formula [3] and revise Z-direction displacement drive signal, then carry out the calculating that iterates,
u
n＝u
n-1+F
-1*(y
Desied-y
n-1) 【3】
Wherein, u
nit is the drive singal after n iteration;
Until the comparative result of above-mentioned iteration passage meets target control condition, namely time domain and frequency-region signal coincide respectively, and relative damage value reaches desired value 1, and iteration terminates.
5, the displacement of core wheel Z-direction obtains
When virtual iteration meets target control condition, now corresponding core wheel Z-direction displacement is required core wheel displacement drive signal, as the constraint condition that carload is decomposed, drifts about disperse to prevent car load.
6, carload is decomposed
The core wheel Z-direction displacement that the wheel mental and physical efforts (except Z-direction power) of testing with step 1 and the virtual iteration of step 5 obtain is added four core wheel positions respectively to and is driven car load to carry out load decomposition.
7, load results process
After carload decomposition terminates, carry out simulation result aftertreatment, obtain each system of car load and Parts loading spectrum.
The present invention can the high fatigue load spectrum needed for complete vehicle structure analysis of fatigue of Obtaining Accurate precision.This not only can carry out effective control and prediction to complete vehicle structure fatigue endurance performance in research and development of products early stage, and greatly reduces later stage sample car production quantity and test round, shortens the test period, reduces R&D costs, improving product reliability qualifications.Simultaneously, by setting up each platform vehicle type dynamic load database, prediction and the management and control of complete vehicle structure fatigue endurance performance is carried out in the load data storehouse that just can make full use of same platform during new car research and development in early stage, evade the risk occurring structure crack in later stage sample car test.
Claims (2)
1. a car load four-wheel six square phase road spectrum loading analysis method, comprises the following steps:
Step 1, car load four-wheel six square phase road spectrum is tested: the six square phase comprising test four-wheel core wheel place, test spring displacement, wheel heart acceleration, vibration damper force signal;
Step 2: entire vehicle design Data Collection: data comprise car load axle load wheel load and distribute, design hard spot, chassis part mass property, chassis lining rigidity, power assembly mass property and suspension bushing rigidity, spring rate, vibration damper drag characteristic, wheelbase wheelspan, axle load;
Step 3: Full Vehicle Dynamics model is set up and adjustment: according to annexation between the entire vehicle design data of collecting and parts, set up suspension, power assembly, vehicle body, turn to, the subsystem model such as stabilizer bar, assembled by above-mentioned subsystem model and set up Full Vehicle Dynamics model;
Step 4: virtual iteration: (following content adjusts, and please audit whether there is any discrepancy)
(1) whole vehicle model transport function generates
The drive singal input emulated using noise signal u as multi-body dynamics automobile model, simulation data response signal y, comprises spring displacement, spindle nose acceleration and core wheel Z-direction power, is calculated the transport function F of whole vehicle model by formula [1]
F＝y/u 【1】
(2) initial driving signal and for the first time simulation calculation
By the inverse function F of transport function F
-1with the spring displacement tested, spindle nose acceleration and core wheel Z-direction power echo signal y
desired, try to achieve one group of initial drive singal U by formula [2]
0
u
0＝F
-1*y
Desired 【2】
Wherein: F
-1the inverse function of-transport function; y
desiredthe echo signal of-test, as spring displacement, core wheel Z-direction force, spindle nose acceleration; u
0-initial displacement drive signal;
Then carry out car load emulation, the response signals such as delivery spring displacement, spindle nose acceleration and core wheel Z-direction power, carry out time domain, frequency domain and relative damage value three aspect comparative assessment respectively by this result and test result;
(3) virtual iteration
By the result u of first time simulation calculation
0initial driving signal as system core wheel inputs, and emulation obtains the response signal y of output channel
0, by y
0with y
desiredrelatively, if meet target control condition, u
0it is exactly the drive singal of reverse; If do not met, then press formula [3] and revise Z-direction displacement drive signal, then carry out the calculating that iterates,
u
n＝u
n-1+F
-1*(y
Desied-y
n-1) 【3】
Wherein, u
nit is the drive singal after n iteration;
Until the comparative result of above-mentioned iteration passage meets target control condition, namely time domain and frequency-region signal coincide respectively, and relative damage value reaches desired value 1, and iteration terminates;
Step 5, the displacement of core wheel Z-direction obtain:
When virtual iteration meets target control condition, now corresponding core wheel Z-direction displacement is required core wheel displacement drive signal, as the constraint condition that carload is decomposed;
Step 6, carload are decomposed:
With the wheel mental and physical efforts that step 1 is tested, except Z-direction power, and the core wheel Z-direction displacement that obtains of the virtual iteration of step 5 is added four core wheel positions respectively to and is driven car loads to carry out load decomposition;
Step 7, load results process:
After carload decomposition terminates, carry out simulation result aftertreatment, obtain each system of car load and Parts loading spectrum.
2. car load four-wheel six square phase road spectrum loading analysis method according to claim 1, it is characterized in that, the method for model adjustment is as follows:
(1) suspension K & C adjustment
Carry out K & C by suspension system to emulate, carry out emulating the K index that draws and C index and car load K & C test findings mark respectively, if both results misfit, then revise model parameter again to emulate, until simulation result is consistent with test findings, the accuracy of checking Suspension Model;
(2) whole vehicle model adjustment: comprise static characteristics adjustment and dynamic perfromance adjustment;
Static characteristics adjustment is undertaken by static equilibrium emulation, and the axle load obtained after static equilibrium emulation and wheel load, buffer clearance, spring change displacement, car load centroid position result and test vehicle static test come to the same thing;
Dynamic perfromance adjustment is emulated by core wheel input random signal, the kinematic relation checked vehicles between parts, and inspection model freedom of motion checks vibration-damper characterist.
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