CN107862152A - The nonlinear Design of Structural parameters method for resisting snakelike shock absorber - Google Patents
The nonlinear Design of Structural parameters method for resisting snakelike shock absorber Download PDFInfo
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Abstract
The invention discloses a kind of nonlinear Design of Structural parameters method for resisting snakelike shock absorber, to resist the fluid mechanics principle of snakelike shock absorber internal structure to establish non-linear fluid-percussion model of isolated, non-linear fluid-percussion model of isolated and vehicle dynamic model are combined into associative simulation model, influence of the internal structure parameter of snakelike shock absorber to intact stability is resisted with associative simulation model analysis, so as to realize the optimization design of anti-snakelike damper structure parameter.By technical scheme, efficiency when simplifying model, improving the reasonability of parameter selection, improve emulation, the accuracy of model is improved so that the parameter gone out more optimizes.
Description
Technical field
The present invention relates to vibration absorber technical field, more particularly to a kind of nonlinear structural parameters for resisting snakelike shock absorber
Optimization Design.
Background technology
At present, the overall trip speed of present High Speed Railway Vehicle has reached 350km/h, but this can also cause operating condition
More severe during than low speed, vibratory impulse is also bigger.It is higher in order to obtain under conditions of dynamics of vehicle performance is ensured
Speed, many New technical uses are in high-speed railway, such as vehicle Lightweight Technology, and height smooth-going and high stability are without tiny fragments of stone, coal, etc. rail
Road.The application of these technologies all can cause vehicle suspension component working condition to change：First, between suspension parts and vehicle
The reduction of relative displacement amplitude；Second, between suspension parts and vehicle relative motion frequency increase.For support vehicles safety
And even running, this just proposes requirements at the higher level to vehicle hanging performance.The suspension of rail truck can absorb and relax
Vibrate and impact caused by road irregularity etc., the quality of its performance will directly affect the stationarity, comfortableness, vehicle part of vehicle
Service life and travel safety.
The working characteristics of each element of suspension has very strong nonlinear characteristic, and the stability that they run to vehicle has
Important function.The nonlinear characteristic of vehicle suspension system refers to air spring, hydraulic buffer, anti-hunting damper holder, pivoted arm
The nonlinear characteristic of the hanging elements such as locating stiffness.Anti-hunting damper holder characterisitic parameter in the nonlinear characteristic of suspension, turn
Influence of the arm locating stiffness to iron nitride films is relatively large.In vehicle normal operation in most cases, they
Working characteristics can be with linear come approximate description.Certainly the section in rail truck by switch area or other complex working conditions, production
When giving birth to more violent motion, the nonlinear characteristic of suspension influences whether the dynamics of rail truck system.Wherein
The work of nonlinear anti-hunting damper holder can cause Hopf bifurcateds to change, after selecting suitable anti-hunting damper holder, band
The vibration for having amplitude can be suppressed and reach higher critical speed.
The damping characteristic of hydraulic buffer is described with the relation between damping force and piston speed, therefore the liquid established
Pressure damper numerical model should give expression to this relation as precisely as possible.Now with three kinds of modeling methods：
1. establishing numerical model based on lot of experimental data, this method is also referred to as non-parametric model.It does not have to examine
Consider shock absorber internal structure and operation principle, become only with figure description damping force and displacement, speed, acceleration, frequency etc. state
The relation of amount, in the calculating of reality, figure or simple interpolations only need to be looked into, arithmetic speed is quickly.Non-parametric model emphasis
Study shock absorber under the various excitation methods such as random, simple harmonic quantity, constant speed and high frequency, its restoring force curved surface operating speed displacement or
It is the accuracy for using acceleration-speed as state variable, it is therefore an objective to want more accurately describe under the conditions of limited experimentation
Damping characteristic of the shock absorber in broadband.
2. model, the volume of such as pressure chamber, the characteristic of valve, piston cross-section are established based on shock absorber physical arrangement parameter.
The advantages of this method is that model can apply to different shock absorbers, can change different physical arrangement parameters.Result is to adjust
Test number (TN) needed for section model can be preferably minimized.
3. equivalent parametersization models.It by shock absorber be abstracted into some as damping element, flexible member, friction element,
Gap element etc. has the combined system of the typical physical element of certain mechanical characteristic, generally only includes (but being not limited only to) 1-10
Parameter, very high efficiency is can guarantee that in the calculating of reality.
In order to improve the performance of shock absorber, this just needs to carry out more in-depth study, vibration damping to shock absorber dynamics
The influence of device structural parameters is exactly an important direction.One important means of shock absorber performance design is exactly by adjustment
Portion structural parameters are realized.Although hydraulic buffer structure is different, elementary structure parameter is mainly choke valve correlation
Initial throttle orifice, variable orifice, the rigidity of spring and pre-pressure of the spring, the diameter of piston rod, the both ends rigidity of shock absorber
Deng.
In the prior art, establishing non-parametric model needs to carry out substantial amounts of experiment to obtain an accurate model.
These experiments have to that all opereating specifications when shock absorber is possible to work can be described.And usually occur in this case and subtract
Damping force caused by device of shaking is not only relevant with current speed and position, also relevant with the speed of previous instant and position.
For some shock absorbers, when different pressures intracavitary pressure differential do not reach certain numerical value when fluid be will not
Flowing, and this when, it from nought state when zero velocity and displacement is different that power caused by shock absorber, which is,.This phenomenon is just
It can not be described using this model.The model based on result of the test is also required to substantial amounts of interpretation of result simultaneously, and this
It is difficult to repeat to obtain, because model of damper can produce change with the change of structural parameters.
The model based on shock absorber physical arrangement parameter is established, this model is too complicated, and if model is excessively multiple
Miscellaneous efficiency when can allow to carry out dynamics simulation declines, or even the phenomenon of result diverging occurs.
Equivalent parameter model is established, shock absorber can be abstracted into some such as damping element, flexible member, friction member
Part, clearance component etc. have the combined system of the typical physical element of certain mechanical characteristic, can guarantee that very in the calculating of reality
High efficiency, but its drawback is that the physical attribute of parameter is difficult to determine, analysis result may not apply to the excellent of shock absorber
Change in design.
The content of the invention
At least one of regarding to the issue above, the invention provides a kind of nonlinear structure ginseng for resisting snakelike shock absorber
Number Optimization Design, by starting with from the internal structure of anti-hunting damper holder, to the element foundation such as various valves, piston, oil pocket
Hydromechanical principle establishes description accurately and calculates the efficient non-linear fluid-percussion model of isolated of anti-hunting damper holder.The model can be with
Applied to different shock absorbers, different physical arrangement parameters can be changed.Test number (TN) needed for regulation model can be preferably minimized,
The shortcomings that efficiency is low when also solving complicated model, dynamics simulation simultaneously or even result diverging occurs.In addition, by anti-
Damping hole of the relevant parameter of each element as optimized variable, including choke valve is chosen in the structural detail of hunting Damper
Footpath, through-flow aperture, spring rate, initial tension of spring, the unidirectional clear valve diameter of piston, the unidirectional clear valve diameter of bottom valve, diameter of piston rod, node
Rigidity etc., the non-linear hydraulic pressure numerical model of anti-hunting damper holder is combined with vehicle dynamic model, uses associative simulation
Method analyzes influence of these structural parameters to High Speed Railway Vehicle nonlinear stability, so as to obtain optimized parameter.
To achieve the above object, the invention provides a kind of nonlinear Design of Structural parameters for resisting snakelike shock absorber
Method, including：Resist the non-linear of snakelike shock absorber to resist the damping regulating valve of snakelike shock absorber, piston check valve and bottom valve to establish
Fluid-percussion model of isolated；Dynamic simulation and experiment are carried out to non-linear fluid-percussion model of isolated using multigroup different piston speed respectively, according to dynamic
The damping force data that state is emulated and experiment is drawn, judges whether the accuracy of non-linear fluid-percussion model of isolated meets the requirements；By vehicle
Anti- snakelike shock absorber in kinetic model replaces with the damping force element that can set active force and state variable；By kinetic simulation
State variable in type establishes dynamic link with the active force in non-linear fluid-percussion model of isolated, forms associative simulation model；To vehicle
Tested, the emulation data of the test data of experiment and associative simulation model are subjected to time domain scale and frequency domain respectively
Contrast；According to the comparing result of test data and emulation data, judge whether associative simulation model meets the requirements；If it is determined that joint
Simulation model meets the requirements, then the structure that regulating valve, piston check valve and bottom valve are damped in non-linear fluid-percussion model of isolated is joined respectively
Number is adjusted, and determines influence curve of the different structural parameters to the nonlinear stability of joint simulation model；According to structure
Parameter and the influence curve of associative simulation model, determine the optimal value of the parameter of each structural parameters.
In the above-mentioned technical solutions, it is preferable that the damping force data drawn according to dynamic simulation and experiment, judge institute
Whether the accuracy for stating non-linear fluid-percussion model of isolated meets the requirements and specifically includes：Adjusted respectively to being damped in non-linear fluid-percussion model of isolated
The structural parameters of valve, piston check valve and bottom valve are adjusted, and obtain resistance of the different structural parameters to non-linear fluid-percussion model of isolated
The influence curve of damping characteristics, and determine influencing characterisitic of the structural parameters to non-linear fluid-percussion model of isolated；To damp regulating valve and piston
The structural parameters of check valve are influence factor, to resist the damping force maximum of snakelike shock absorber as test index, in experiment model
Enclose interior three kinds of factors of selection and carry out orthogonal tests；The result of the test of orthogonal test is analyzed, determines the water of each influence factor
Flat variation tendency, and determine the preference data of each influence factor；
In the above-mentioned technical solutions, it is preferable that the damping regulating valve includes choke valve, normal open hole, spring, the anti-snake
Shape shock absorber also includes piston；The structural parameters of the damping regulating valve, the piston check valve and the bottom valve include：It is described
Damping aperture, the spring rate of the spring, the pretightning force of the spring, the through-flow aperture in the normal open hole of choke valve, institute
State aperture, the unidirectional clear valve diameter of the bottom valve of the bottom valve, the diameter of piston rod of the piston and the anti-snake of piston check valve
The connection stiffness of the connected node of shape shock absorber and carbody.
In the above-mentioned technical solutions, it is preferable that the influence factor of the orthogonal test includes the damping hole of the choke valve
Footpath, the through-flow aperture in the normal open hole, the spring rate of the spring, the pretightning force of the spring and the piston check valve
Aperture.
In the above-mentioned technical solutions, it is preferable that the result of the test to the orthogonal test is analyzed, and determines each shadow
The horizontal variation tendency of the factor of sound, and determine that the preference data of each influence factor specifically includes：By each influence factor according to not
Same level determines test group；Calculate the damping force maximum for resisting snakelike shock absorber of different tests group under each influence factor
Sum, and the summation of the damping force maximum of all test groups；Calculate under each influence factor damping force in different tests group
Extreme difference between maximum sum, and the influence primary and secondary of each influence factor is determined sequentially according to the extreme difference value；According to described every
Damping force maximum sum in the different tests group of individual influence factor, determine the preference data of each influence factor.
In the above-mentioned technical solutions, it is preferable that the anti-snakelike shock absorber in the kinetic model by vehicle replaces with
Active force and the damping force element of state variable can be set, by the state variable in the kinetic model with it is described non-thread
Property fluid-percussion model of isolated in the active force establish dynamic link, form associative simulation model and specifically include：By Adams simulation softwares
The described of middle vehicle dynamic model resists snakelike shock absorber to replace with damping force element, adds the anti-snakelike shock absorber both ends
Displacement and the relative velocity for resisting snakelike shock absorber both ends add the work for resisting snakelike shock absorber as system state variables
Firmly；By the system state variables of the vehicle dynamic model and active force with it is described non-linear in Easy5 simulation softwares
Anti- snakelike shock absorber displacement, speed and the damping force of fluid-percussion model of isolated carry out dynamic link, form associative simulation model；Will be described
Close simulation model generation dynamic link library file.
In the above-mentioned technical solutions, it is preferable that it is described that the vehicle is tested, by the test data of the experiment with
The emulation data of the associative simulation model carry out time domain scale respectively and the contrast of frequency domain specifically includes：Gather the car
Test data and the associative simulation model emulation data；By the test data and the car body in the emulation data
Contrasted with the vibration acceleration of framework in time domain scale；Calculate and contrast the root-mean-square value of the test data with it is described
Emulate the root-mean-square value of data；The test data is subjected to PSD with the emulation data and transforms to frequency domain；By the examination
Test data and the vibration acceleration of car body in the emulation data is contrasted in frequency domain.
Compared with prior art, beneficial effects of the present invention are：It is right by starting with from the internal structure of anti-hunting damper holder
The elements such as various valves, piston, oil pocket establish description accurately according to hydromechanical principle and calculate efficient anti-snake vibration damping
The non-linear fluid-percussion model of isolated of device.The model can apply to different shock absorbers, can change different physical arrangement parameters.Adjust mould
Test number (TN) needed for type can be preferably minimized, while efficiency is low when also solving model complicated, dynamics simulation or even occurs
As a result the shortcomings that dissipating.In addition, it is used as by the relevant parameter that each element is chosen in the structural detail of anti-hunting damper holder
Optimized variable, including the damping aperture of choke valve, through-flow aperture, spring rate, initial tension of spring, the unidirectional clear valve diameter of piston, bottom
The unidirectional clear valve diameter of valve, diameter of piston rod, connection stiffness etc., the non-linear hydraulic pressure numerical model of anti-hunting damper holder is moved with vehicle
Mechanical model is combined, and these structural parameters are analyzed to High Speed Railway Vehicle nonlinear stability using the method for associative simulation
Influence, so as to obtain optimized parameter.
Brief description of the drawings
Fig. 1 is the nonlinear Design of Structural parameters method for resisting snakelike shock absorber disclosed in an embodiment of the present invention
Schematic flow sheet；
Fig. 2 is the fundamental diagram of typical non-linear hydraulic buffer disclosed in an embodiment of the present invention；
Fig. 3 is the disclosed damping regulating valve operation principle schematic diagram of an embodiment of the present invention；
Fig. 4 is the structural representation of valve block disclosed in an embodiment of the present invention；
Fig. 5 is the FEM model schematic diagram of valve block disclosed in an embodiment of the present invention；
Fig. 6 is shock absorber numerical value fluid-percussion model of isolated schematic diagram disclosed in an embodiment of the present invention；
Fig. 7 is the emulation indicator card of friction speed disclosed in an embodiment of the present invention；
Fig. 8 is the experiment indicator card of friction speed disclosed in an embodiment of the present invention；
Fig. 9 is that choke valve disclosed in an embodiment of the present invention damps the horizontal changing trend diagram in aperture；
Figure 10 is the horizontal changing trend diagram in normal open aperture disclosed in an embodiment of the present invention；
Figure 11 is the horizontal changing trend diagram of the unidirectional clear valve diameter of piston disclosed in an embodiment of the present invention；
Figure 12 is the horizontal changing trend diagram of spring rate disclosed in an embodiment of the present invention；
Figure 13 is the horizontal changing trend diagram of pretightning force of spring disclosed in an embodiment of the present invention；
Figure 14 is amended vehicle dynamic model schematic diagram disclosed in an embodiment of the present invention；
Figure 15 is that the dynamics of vehicle of anti-hunting damper holder numerical value fluid-percussion model of isolated disclosed in an embodiment of the present invention is combined
Simulation model schematic diagram；
Figure 16 is the vibration acceleration time domain scale contrast schematic diagram of car body disclosed in an embodiment of the present invention；
Figure 17 is the vibration acceleration time domain scale contrast schematic diagram of framework disclosed in an embodiment of the present invention；
Figure 18 is the vibration acceleration frequency domain contrast schematic diagram of car body disclosed in an embodiment of the present invention；
Figure 19 is that choke valve disclosed in an embodiment of the present invention damps influence schematic diagram of the aperture to dynamic antivibration rate；
Figure 20 is that choke valve disclosed in an embodiment of the present invention damps influence schematic diagram of the aperture to vehicle critical speed；
Figure 21 is that choke valve disclosed in an embodiment of the present invention damps influence signal of the aperture to vehicle stability index
Figure；
Figure 22 is influence schematic diagram of the choke valve normal open aperture disclosed in an embodiment of the present invention to dynamic antivibration rate；
Figure 23 is influence schematic diagram of the choke valve normal open aperture disclosed in an embodiment of the present invention to vehicle critical speed；
Figure 24 is influence signal of the choke valve normal open aperture disclosed in an embodiment of the present invention to vehicle stability index
Figure；
Figure 25 is influence schematic diagram of the throttle valve spring rigidity disclosed in an embodiment of the present invention to dynamic antivibration rate；
Figure 26 is influence schematic diagram of the throttle valve spring rigidity disclosed in an embodiment of the present invention to vehicle critical speed；
Figure 27 is influence signal of the throttle valve spring rigidity disclosed in an embodiment of the present invention to vehicle stability index
Figure；
Figure 28 is influence schematic diagram of the initial tension of spring disclosed in an embodiment of the present invention to dynamic antivibration rate；
Figure 29 is influence schematic diagram of the spring rate disclosed in an embodiment of the present invention to vehicle critical speed；
Figure 30 is influence schematic diagram of the spring rate disclosed in an embodiment of the present invention to vehicle stability；
Figure 31 is influence schematic diagram of the unidirectional clear valve diameter of piston disclosed in an embodiment of the present invention to dynamic antivibration rate；
Figure 32 is influence schematic diagram of the unidirectional clear valve diameter of piston disclosed in an embodiment of the present invention to vehicle critical speed；
Figure 33 is influence signal of the unidirectional clear valve diameter of piston disclosed in an embodiment of the present invention to vehicle stability index
Figure；
Figure 34 is influence schematic diagram of the bottom valve aperture disclosed in an embodiment of the present invention to vehicle critical speed；
Figure 35 is influence schematic diagram of the bottom valve aperture disclosed in an embodiment of the present invention to vehicle stability index；
Figure 36 is influence schematic diagram of the connection stiffness disclosed in an embodiment of the present invention to dynamic antivibration rate；
Figure 37 is influence schematic diagram of the connection stiffness disclosed in an embodiment of the present invention to dynamic rate；
Figure 38 is influence schematic diagram of the connection stiffness disclosed in an embodiment of the present invention to vehicle critical speed；
Figure 39 is influence schematic diagram of the connection stiffness disclosed in an embodiment of the present invention to vehicle stability index.
Embodiment
To make the purpose, technical scheme and advantage of the embodiment of the present invention clearer, below in conjunction with the embodiment of the present invention
In accompanying drawing, the technical scheme in the embodiment of the present invention is clearly and completely described, it is clear that described embodiment is
The part of the embodiment of the present invention, rather than whole embodiments.Based on the embodiment in the present invention, ordinary skill people
The every other embodiment that member is obtained on the premise of creative work is not made, belongs to the scope of protection of the invention.
The present invention is described in further detail below in conjunction with the accompanying drawings：
As shown in figure 1, according to a kind of nonlinear Design of Structural parameters for resisting snakelike shock absorber provided by the invention
Method, including：Step S101, resist snakelike vibration damping to resist the damping regulating valve of snakelike shock absorber, piston check valve and bottom valve to establish
The non-linear fluid-percussion model of isolated of device；Step S102, action is entered to non-linear fluid-percussion model of isolated using multigroup different piston speed respectively
State emulates and experiment, and the damping force data drawn according to dynamic simulation and experiment, judging the accuracy of non-linear fluid-percussion model of isolated is
It is no to meet the requirements；Step S103, the anti-snakelike shock absorber in the kinetic model of vehicle, which is replaced with, can set active force and shape
The damping force element of state variable；Step S104, by the effect in the state variable in kinetic model and non-linear fluid-percussion model of isolated
Power establishes dynamic link, forms associative simulation model；Step S105, is tested vehicle, by the test data and connection of experiment
The emulation data for closing simulation model carry out the contrast of time domain scale and frequency domain respectively；Step S106, according to test data with
The comparing result of data is emulated, judges whether associative simulation model meets the requirements；Step S107, if it is determined that associative simulation model accords with
Close and require, then the structural parameters that regulating valve, piston check valve and bottom valve are damped in non-linear fluid-percussion model of isolated are adjusted respectively,
Determine influence curve of the different structural parameters to the nonlinear stability of joint simulation model；Step S108, joins according to structure
The influence curve of number and associative simulation model, determine the optimal value of the parameter of each structural parameters.
In the above embodiment, it is preferable that damping regulating valve includes choke valve, normal open hole, spring, resist snakelike shock absorber also
Including piston；The structural parameters of damping regulating valve, piston check valve and bottom valve include：The damping aperture of choke valve, the bullet of spring
Spring rigidity, the pretightning force of spring, the through-flow aperture in normal open hole, the aperture of piston check valve, the unidirectional clear valve diameter of the bottom valve of bottom valve, work
The connection stiffness of the connected node of the diameter of piston rod of plug and anti-snakelike shock absorber and carbody.
In the above embodiment, it is preferable that the influence factor of orthogonal test includes damping aperture, the normal open hole of choke valve
Through-flow aperture, the spring rate of spring, the aperture of the pretightning force of spring and piston check valve.
In the above embodiment, it is preferable that the above-mentioned result of the test to orthogonal test is analyzed, each influence factor is determined
Horizontal variation tendency, and determine that the preference data of each influence factor specifically includes：By each influence factor according to varying level
Determine test group；The damping force maximum sum of the anti-snakelike shock absorber of different tests group under each influence factor is calculated, and
The summation of the damping force maximum of all test groups；Calculate under each influence factor damping force maximum sum in different tests group
Between extreme difference, and according to extreme difference value determine each influence factor influence primary and secondary order；Tried according to the difference of each influence factor
Damping force maximum sum in group is tested, determines the preference data of each influence factor.
In the above embodiment, it is preferable that replace with can for the anti-snakelike shock absorber in the above-mentioned kinetic model by vehicle
Active force and the damping force element of state variable are set, by the state variable in kinetic model and non-linear fluid-percussion model of isolated
Active force establishes dynamic link, forms associative simulation model and specifically includes：By vehicle dynamic model in Adams simulation softwares
Resist snakelike shock absorber to replace with damping force element, add the displacement for resisting snakelike shock absorber both ends and the phase for resisting snakelike shock absorber both ends
To speed as system state variables, the active force for resisting snakelike shock absorber is added；The system mode of vehicle dynamic model is become
Amount and anti-snakelike shock absorber displacement, speed and the damping force of active force and the non-linear fluid-percussion model of isolated in Easy5 simulation softwares are entered
Mobile state links, and forms associative simulation model；Associative simulation model is generated into dynamic link library file.
In the above embodiment, it is preferable that above-mentioned test vehicle, by the test data of experiment and associative simulation mould
The emulation data of type carry out time domain scale respectively and the contrast of frequency domain specifically includes：The test data and joint of collection vehicle
The emulation data of simulation model；By the car body in test data and emulation data and the vibration acceleration of framework in time domain scale
Contrasted；Calculate the simultaneously root-mean-square value of contrast test data and the root-mean-square value of emulation data；By test data and emulation number
Frequency domain is transformed to according to PSD is carried out；Test data and the vibration acceleration of car body in emulation data are entered in frequency domain
Row contrast.
In the above-described embodiments, the method for building up for resisting the non-linear fluid-percussion model of isolated of snakelike shock absorber is specific as follows：
It is illustrated in figure 2 the operation principle schematic diagram of typical non linear hydraulic buffer.When shock absorber stretches, on piston
Closed check valve, the check valve on bottom valve opens, and upper piston area elongated cavity flows to equivalent to the fluid that volume is A through throttle orifice
Oil storage cylinder, while the fluid in oil storage cylinder equivalent to (A+B) is flowed in piston lower portion compression chamber through bottom valve.Work as shock absorbers compression
When, the closed check valve on bottom valve, the check valve on piston is opened, compression chamber equivalent to volume (A+B) fluid through check valve
Elongated cavity is flowed to, wherein volume A fluid stays in elongated cavity, and the fluid that volume is B is flowed in oil storage cylinder through damping hole.
When establishing the non-linear fluid-percussion model of isolated of shock absorber, in order that model is simple not to influence computational accuracy again, to carry out
Some assume to simplify：Ignore the small hole of some structure via holes, throttling capacity；Ignore the system rigidity because of caused by pressure change
The deformation of the component of a system caused by the elastic deformation and temperature change of component；Ignore the elastic deformation feelings of system rigidity component
Condition；Ignore the deadweight of fluid；Ignore the oil liquid leakage between piston and working cylinder, between piston rod and guide holder；Ignore vibration damping
Device causes the change of work oil liquid temperature at work.
There are three main elements in the numerical value fluid-percussion model of isolated of hydraulic buffer, it is unidirectional respectively to damp regulating valve, piston
Valve and bottom valve, their modeling is introduced separately below.
(1) regulating valve modeling is damped
It is illustrated in figure 3 the operation principle schematic diagram of damping regulating valve.Damp in regulating valve, initial tension of spring can change and subtract
Shake the size and characteristic of resistance.A points communicate with elongated cavity in Fig. 3, and B points communicate with shoe cream room, when elongated cavity and shoe cream room
When pressure differential is not enough to promote preloading spring, fluid flows (Q1) from normal open aperture；When the pressure differential of elongated cavity and shoe cream room
When can promote preloading spring, fluid flows (Q2) from normal open aperture (Q1) and sideshake.Using normal in EASY5 simulation softwares
The function of damping regulating valve is realized in through hole, check valve and choke valve combination, and the rigidity of wherein spring is taken as 8.1 × 104N/m。
(2) piston check valve and bottom valve
It is illustrated in figure 4 the structural representation of valve block.Piston check valve is similar with the structure of bottom valve, is all to utilize during work
Valve block blocks liquid stream, produces resistance.
It is illustrated in figure 5 the schematic diagram of valve block FEM model.FEM model is established according to the size of valve block, by having
First force analysis is limited, obtains equivalent stiffness, wherein piston one-way valve plate rigidity is 4.63 × 103N/m, bottom valve valve block rigidity are
1.65×103N/m。
Table 1 is Parameters of Dampers.
The Parameters of Dampers of table 1
Such as the numerical value fluid-percussion model of isolated schematic diagram that Fig. 6 is shock absorber.According to damping regulating valve, work in EASY5 simulation softwares
The operation principle of check valve and bottom valve is filled in, establishes the fluid-percussion model of isolated of shock absorber.
In EASY5 simulation softwares, for piston different speed (5mm/s, 10mm/s, 20mm/s, 30mm/s, 40mm/
S, 50mm/s, 60mm/s) under carry out dynamic simulation, its emulate indicator card line it is as shown in Figure 7.The experiment indicator card of shock absorber simultaneously
As shown in Figure 8.
Test data compares as shown in table 2 with shock absorber emulation data.
The shock absorber of table 2 is tested and emulation data comparison table
It can be drawn by table 2, emulation damping force and experiment damping force relative error very little, be up to 6.67%, minimum is only
For 0.70%, the EASY5 models that this explanation is established are more accurate, meet modeling demand.
In the above-described embodiments, for resisting the analysis method of influence of the snakelike damper structure parameter to vibration-damper characterist such as
Under：
In the structural detail of anti-hunting damper holder, relevant parameter, diameter of piston rod, the node of each element of shock absorber are firm
Degree all has important influence to the working characteristics of shock absorber.Although the structure of each element differs, their major parameter
All include initial throttle diameter, variable restrictor aperture, the rigidity of spring and the pretightning force of spring etc..The present invention chooses choke valve
Aperture D1, through-flow aperture D2, spring rate K1, pretightning force F1, the unidirectional clear valve diameter D3 of piston, the unidirectional clear valve diameter D4 of bottom valve are damped,
Diameter of piston rod D, connection stiffness K2 are research object, and their influences to shock absorber working characteristics are discussed.
During experiment, using same speed and displacement excitation, the choosing method of parameter value be original parameter value or so compared with
A small range value, parameter designing experiment table such as table 3,0 initial value for representing built model of damper in table, "+", " " distinguish
Represent to add on initial value, subtract.
The shock absorber numerical experiment parameter value of table 3
In the above-described embodiments, the orthogonal test analysis method for resisting the working characteristics of snakelike shock absorber is specific as follows：
(1) orthogonal test table is set
When orthogonal test is carried out, choke valve damping aperture, normal open aperture, spring rate, the pretension of spring are selected
The unidirectional clear valve diameter of power, piston is as influence factor.Three kinds of factors are respectively selected in trial stretch, factor level is as shown in table 4, and incite somebody to action
Absorber damping force maximum is as test index.
4 factors of table-water-glass
| 1 | 0.75 | 0.05 | 1.1 | 800 | 100 |
| 2 | 0.95 | 0.1 | 1.5 | 2000 | 200 |
| 3 | 1.15 | 0.15 | 1.9 | 3200 | 300 |
This experiment is that five factor three is horizontal, therefore selects L18 (37) orthogonal arrage to be tested.According to the above-listed water of factor order
It is flat to sit in the right seat, determine that testing program is as shown in table 5.
The testing program table of table 5
| 1 | 1(0.75) | 1(0.05) | 1(1.1) | 1(800) | 1(100) |
| 2 | 1(0.75) | 2(0.1) | 2(1.5) | 2(2000) | 2(200) |
| 3 | 1(0.75) | 3(0.15) | 3(1.9) | 3(3200) | 3(300) |
| 4 | 2(0.95) | 1(0.05) | 1(1.1) | 2(2000) | 2(200) |
| 5 | 2(0.95) | 2(0.1) | 2(1.5) | 3(3200) | 3(300) |
| 6 | 2(0.95) | 3(0.15) | 3(1.9) | 1(800) | 1(100) |
| 7 | 3(1.15) | 1(0.05) | 2(1.5) | 1(800) | 3(300) |
| 8 | 3(1.15) | 2(0.1) | 3(1.9) | 2(2000) | 1(100) |
| 9 | 3(1.15) | 3(0.15) | 1(1.1) | 3(3200) | 2(200) |
| 10 | 1(0.75) | 1(0.05) | 3(1.9) | 3(3200) | 2(200) |
| 11 | 1(0.75) | 2(0.1) | 1(1.1) | 1(800) | 3(300) |
| 12 | 1(0.75) | 3(0.15) | 2(1.5) | 2(2000) | 1(100) |
| 13 | 2(0.95) | 1(0.05) | 2(1.5) | 3(3200) | 1(100) |
| 14 | 2(0.95) | 2(0.1) | 3(1.9) | 1(800) | 2(200) |
| 15 | 2(0.95) | 3(0.15) | 1(1.1) | 2(2000) | 3(300) |
| 16 | 3(1.15) | 1(0.05) | 3(1.9) | 2(2000) | 3(300) |
| 17 | 3(1.15) | 2(0.1) | 1(1.1) | 3(3200) | 1(100) |
| 18 | 3(1.15) | 3(0.15) | 2(1.5) | 1(800) | 2(200) |
(2) orthogonal experiments are analyzed
A) I, II, III and summation T of each factor is calculated
In order to become apparent from reflecting the difference of each factor level, in this result of the test each factor it is each level corresponding to finger
Mark adds up, and fills out in table 6.Desired value sum in row where wherein I=factor corresponding to digital " 1 "；II=factor institute
Row in desired value sum corresponding to digital " 2 "；Desired value in row where III=factor corresponding to digital " 3 " it
With.Finally by total Test data accumulation, T is designated as, can check that I, II, the III of same factor calculates zero defect by it.
B) the extreme difference R of factor is calculated
The primary and secondary order of factor influence can be determined by calculating extreme difference.The each extreme difference R=of factor factors I, II,
Maximum and minimum difference in III.From each factor extreme difference value R of calculating, it is known that the master that each structural parameters influence on damping force
Secondary order can be arranged as choke valve damping aperture, spring rate, the pretightning force of spring, the unidirectional clear valve diameter of piston, normal open aperture (from
It is main to arrive secondary order).
C) more excellent working condition is chosen
According to I, II, III result, the maximum is as corresponding horizontal i.e. for each of maximum damping force in choosing I, II, III
Factor optimum combination is choke valve damping aperture (experiment 1), spring rate (experiment 3), the pretightning force (experiment 3) of spring, piston
Unidirectional clear valve diameter (experiment 1), normal open aperture (experiment 2).
The result of the test table of table 6
D) tendency chart
For each factor, with horizontal position abscissa, corresponding I, II, III is ordinate, the described point in coordinate diagram, is just obtained
The tendency chart of the factor.Choke valve damping aperture, normal open aperture, the unidirectional clear valve diameter of piston, spring rate, the pretightning force of spring institute
Corresponding tendency chart is respectively shown in Fig. 9, Figure 10, Figure 11, Figure 12, Figure 13.
In the above-described embodiments, the internal structure parameter of snakelike shock absorber is resisted to car speed with associative simulation model analysis
With the influence of stability, so as to realize that the Optimization Design of anti-snakelike damper structure parameter is specific as follows：
(1) associative simulation model
A) foundation of vehicle dynamic model
Certain type CRH EMUs vehicle dynamic models are established in Adams/Rail.While in order to establish associative simulation mould
Type, anti-hunting damper holder is removed for forecarriage, add two active forces Damper_force_left and Damper_
Force_right and 6 system state variables, wherein Damper_xx_act_extension represent the position at shock absorber both ends
Move, Damper_xx_act_rate represents the relative velocity at shock absorber both ends, and Damper_force_xx represents the effect of shock absorber
Power, set as shown in table 7, amended department pattern is as shown in figure 14.Identical processing, setting are similarly carried out to trailing bogie
Good various variables.Finally utilize the plant files of Adams/Control modules export control.
The state variable of table 7
B) foundation of associative simulation model
An associative simulation model is established for the input/output Variable Control plant of each shock absorber.Now with forward
On the left of to frame exemplified by the input/output control variable Pout_left_1/Pin_left_1 of anti-hunting damper holder, how introduction builds
Vertical associative simulation model.Extensions expanding libraries are selected in Easy5 component library, are selected in MSC.Software component libraries
Select and " ADAMS Mechanism " elements, element is dragged in model area.The attribute of setting member is derived from Adams/View
Plant files, " Co.simulation " mode is selected, and as connected the element in Easy5 models in Figure 15 so that Damper_
The displacement with CD elements and speed are connected respectively by left_act_extension_1, Damper_left_act_rate_1,
Damper_Force_mag_1 is connected with the damping force of CD elements.Associative simulation model is finally exported as Adams External
System Library, system generation dynamic link library file, are called for Adams/Control.
C) checking of associative simulation model
The track used during the checking of associative simulation model is Chinese high speed rail CHN60, and track irregularity uses military wide
High-speed railway combined test measures irregularity, and total length 7000m, middle 1960m to 3560 are curve, and the specific operating mode of curve is shown in Table
8。
Table 8 verifies the orbital curve operating mode of model
| Sweep R (m) | Circular curve superelevation of outer rail h (mm) | Balancing speed (km/h) | It is actual to pass through speed (km/h) |
| 9000 | 128 | 312km/h | 345km/h |
The model checking of time domain scale：
In time domain scale, the test data of car body and framework vibration acceleration and emulation data are compared, compared
As a result as shown in Figure 16, Figure 17.
Car body is can be seen that from Figure 16, Figure 17 and is framed in the horizontal and vertical test data of time domain scale and emulation meter
The acceleration vibration for the evidence that counts is substantially coincident, and the maximum of vibration is also coincide substantially.
Table 9 is result of the test and the contrast of Adams/Rail simulation results, and RMS (Root Mean Square) is equal here
Root value, as shown in Equation 1.
The measured data of table 9 and simulation result RMS compare
| Compare item | Survey RMS | Simulation calculation RMS | Error |
| Framework transverse acceleration (m/s^2) | 1.079 | 1.290 | 19.5% |
| Framework vertical acceleration (m/s^2) | 1.198 | 1.023 | 14.6% |
| Values of lateral (m/s^2) | 0.08726 | 0.07120 | 18.4% |
| Car body vertical acceleration (m/s^2) | 0.1278 | 0.1158 | 9.39% |
As can be seen from Table 9, the simulation result of dynamics of vehicle associative simulation model is in time domain scale with result of the test
Basically identical (error range is less than 20%).The associative simulation model for illustrating to establish is reliable in the simulation result of time domain scale
, can be in the use of engineering practice.
The model checking of frequency domain：
Figure 18 show the test data of car body and framework and emulation data carry out the comparison that PSD transforms to frequency domain.
As can be seen from Figure 18, the result and the result of experiment calculated with associative simulation approximate trend one in frequency domain
Cause.Wherein body oscillating acceleration PSD compares as can be seen that the dominant frequency of experiment car body oscillation crosswise vibration acceleration is in 2.3Hz
Left and right, Vertical Acceleration dominant frequency is in 0.8Hz or so；Car body lateral vibration acceleration dominant frequency is emulated in 2.7Hz or so, it is vertical
Vibration acceleration dominant frequency is in 0.75Hz or so.The cross-car of experiment and emulation, vertical vibration dominant frequency are relatively, it is believed that
In rational error range.The vibration acceleration PSD of framework compares as can be seen that result of the test and simulation result are in 0-20HZ
Frequency distribution in frequency range is essentially identical.
In summary, the results contrast of time domain and frequency is analyzed, this Dynamic Co-Simulation model is to substantially conform to reality
It is required that it can be studied using this model.
(2) structural parameters are preferred
A) choke valve damping hole
Aperture, normal open aperture, spring rate and initial tension of spring are damped by the choke valve for changing anti-hunting damper holder, point
The stability and stationarity of vehicle operation are analysed, as a result as shown in Figure 19 to Figure 21.
In Figure 19 it can be seen that with the dynamic antivibration rate dullness of choke valve damping aperture increase anti-hunting damper holder
Drop, aperture increase to 1.15cm from 0.75cm, and dynamic antivibration rate reduces 34%.
With the decline of dynamic antivibration rate, the critical speed of vehicle also constantly reduces.In fig. 20, when choke valve damping hole
When footpath is less than, with choke valve damping aperture increase, the critical speed of vehicle varies less, but when the diameter of damping hole is more than
Afterwards, the critical speed of vehicle starts rapid decrease.In figure 21, the vertical riding index W of vehiclezzChange is gentle, and laterally flat
Stability index WzyIt can be varied from, but the W after diameter of damping hole is more than 0.9cmzyIt can quickly become big, under lateral stability
Drop.
B) choke valve normal open hole
By changing the choke valve normal open aperture of anti-hunting damper holder, the stability and stationarity of analysis vehicle operation, knot
Fruit is as shown in Figure 22 to Figure 24.
In fig. 22 it can be seen that with the dynamic antivibration rate dullness of choke valve damping aperture increase anti-hunting damper holder
Drop, aperture increase to 0.22cm from 0.02cm, and dynamic antivibration rate reduces 22%, after choke valve normal open aperture is more than, dynamic
Ratio of damping rapid decrease.
In Figure 23 and Figure 24, after choke valve normal open aperture is less than 0.1cm, the critical speed dramatic decrease of vehicle, and
Choke valve normal open aperture riding index W vertical to vehiclezzInfluence less, and ordinary through hole footpath increases, lateral stability index
WzyIt can be increased monotonically, lateral stability declines.
C) throttle valve spring rigidity
By changing the throttle valve spring rigidity of anti-hunting damper holder, the stability and stationarity of analysis vehicle operation, knot
Fruit is as shown in Figure 25 to Figure 27.
In fig. 25 it can be seen that as throttle valve spring rigidity increases, in the dynamic antivibration rate dullness of anti-hunting damper holder
Rise, but after spring rate is more than 2000N/cm, the change of dynamic antivibration rate tends towards stability.From Figure 26 and Figure 27 it can be seen that this
Kind change, after throttle valve spring rigidity is more than 2000N/cm, the critical speed of vehicle varies less, lateral stability index Wzy
Also it can change and ease up.Throttle valve spring rigidity riding index W vertical to vehiclezzInfluence little.
D) pretightning force of throttle valve spring
By changing the throttle valve spring pretightning force of anti-hunting damper holder, the stability and stationarity of vehicle operation are analyzed,
As a result as shown in Figure 28 to Figure 30.
It can be seen that increasing the dynamic antivibration rate list of anti-hunting damper holder with the pretightning force of throttle valve spring in Figure 28
Increase is adjusted, dynamic antivibration rate adds 40% from 9452Ns/m to 13216.58Ns/m.
It can be seen that increasing with the pretightning force of throttle valve spring, in vehicle critical speed dullness in Figure 29 and Figure 30
Rise, but after the pretightning force of spring is more than 200N, its change tends towards stability, lateral stability index WzyAlso it can change and ease up.
The pretightning force of throttle valve spring riding index W vertical to vehiclezzInfluence little.
E) piston check valve
The unidirectional clear valve diameter of piston by changing anti-hunting damper holder, the stability and stationarity of analysis vehicle operation, knot
Fruit is as shown in Figure 31 to Figure 33.
In Figure 31 it can be seen that as the unidirectional clear valve diameter of piston increases, under the dynamic antivibration rate dullness of anti-hunting damper holder
Drop, but after aperture is more than 1.5cm, the change of dynamic antivibration rate tends towards stability.
In Figure 32, with the unidirectional clear valve diameter increase of piston, the critical speed of vehicle reduces, but works as the unidirectional valve opening of piston
After footpath is more than 1.5cm, the critical speed change of vehicle is gentle；In fig. 33, the vertical riding index W of vehiclezzIt is steady with transverse direction
Property index WzyChange is gentle.
F) bottom valve
By changing the bottom valve aperture of anti-hunting damper holder, the stability and stationarity of analysis vehicle operation, as a result as schemed
Shown in 34 and Figure 35.
In Figure 34, when bottom valve aperture is too small, distortion, Jin Erying occurs in the damping characteristic of anti-hunting damper holder
Ring the critical speed of vehicle.The critical speed of vehicle can be improved by improving bottom valve aperture, but when bottom valve aperture is more than 2.5cm
Afterwards, the critical speed of vehicle no longer improves；In Figure 35, the vertical riding index W of vehiclezzChange is gentle, and lateral stability
Index WzyIt can diminish with the increase of bottom valve aperture, after bottom valve aperture is more than 2.5cm, WzyNo longer reduce.
G) endpoint node rigidity
When simulation calculation, regard anti-hunting damper holder endpoint node rigidity as linear gradually increase, other ginsengs of shock absorber
Number keeps constant, and anti-hunting damper holder endpoint node rigidity influences very big on the dynamic antivibration rate and dynamic rate of shock absorber.Such as
Shown in Figure 36 and Figure 37.From Figure 36, Figure 37 it can be found that when endpoint node rigidity is less than 18MN/m, the dynamic resistance of shock absorber
Buddhist nun leads with the increase of endpoint node rigidity and reduced, and dynamic rate is then opposite；But it is more than 18MN/m in endpoint node rigidity
Afterwards, this variation tendency slows down, in the state for being slowly increased and reducing.This variation tendency also has in vehicle critical speed
Similar embodiment, as shown in figure 38.Simulation result in Figure 38 shows, with the increase of endpoint node rigidity, vehicle
Critical speed substantially rises, and increased very fast when rigidity is less than 18MN/m, and increases after connection stiffness is more than 20MN/m
Rate of acceleration starts to reduce, and has a declining tendency.And show that influence of the end connection stiffness for stationarity is main in Figure 39
It is to lateral stability WzyHave a certain impact, the index of lateral stability has been reduced with the increase of connection stiffness, is said
Bright lateral stability improves, but after connection stiffness increases to certain value, lateral stability index change is little.Connection stiffness
To vertical stationarity WzzInfluence less, with the increase of connection stiffness, vertical stationarity is almost unchanged.From the point of view of simulation result,
Improve anti-snake vibration damping connection stiffness has effect to vehicle critical speed and stability, it should firm from larger axial direction as far as possible
Degree, but the process condition for being also contemplated that rubber metal pad selects suitable rigidity with practice situation.
Described above is embodiments of the present invention, it is contemplated that model complexity is unstable in the prior art, simulation efficiency is low,
The uncertain technical problem of parameter attribute, the present invention propose a kind of nonlinear structure parameter optimizing for resisting snakelike shock absorber and set
Meter method, to resist the fluid mechanics principle of snakelike shock absorber internal structure to establish non-linear fluid-percussion model of isolated, by non-linear fluid die
Type is combined into associative simulation model with vehicle dynamic model, and the internal structure of snakelike shock absorber is resisted with associative simulation model analysis
Influence of the parameter to car speed and stability, so as to realize the optimization design of anti-snakelike damper structure parameter.By this hair
Bright technical scheme, efficiency when simplifying model, improving the reasonability of parameter selection, improve emulation, improves model
Accuracy so that the parameter gone out more optimizes.
The preferred embodiments of the present invention are the foregoing is only, are not intended to limit the invention, for the skill of this area
For art personnel, the present invention can have various modifications and variations.Within the spirit and principles of the invention, that is made any repaiies
Change, equivalent substitution, improvement etc., should be included in the scope of the protection.
Claims (7)
- A kind of 1. nonlinear Design of Structural parameters method for resisting snakelike shock absorber, it is characterised in that including：To resist damping regulating valve, piston check valve and the bottom valve of snakelike shock absorber to establish the non-linear liquid for resisting snakelike shock absorber Pressing mold type；Dynamic simulation and experiment are carried out to the non-linear fluid-percussion model of isolated using multigroup different piston speed respectively, according to dynamic The damping force data that emulation and experiment are drawn, judges whether the accuracy of the non-linear fluid-percussion model of isolated meets the requirements；Anti- snakelike shock absorber in the kinetic model of vehicle, which is replaced with, can set the damping force member of active force and state variable Part；The active force in the state variable in the kinetic model and the non-linear fluid-percussion model of isolated is established dynamic State links, and forms associative simulation model；The vehicle is tested, the test data of the experiment and the emulation data of the associative simulation model are entered respectively The contrast of row time domain scale and frequency domain；According to the comparing result of test data and emulation data, judge whether the associative simulation model meets the requirements；If it is determined that the associative simulation model meets the requirements, then adjusted respectively to being damped described in the non-linear fluid-percussion model of isolated The structural parameters of valve, the piston check valve and the bottom valve are adjusted, and determine that different structural parameters are imitative to the joint The influence curve of the nonlinear stability of true mode；According to the influence curve of the structural parameters and the associative simulation model, the optimal ginseng of each structural parameters is determined Numerical value.
- 2. the nonlinear Design of Structural parameters method for resisting snakelike shock absorber according to claim 1, its feature exist In, it is described according to dynamic simulation and the damping force data that draws of experiment, judge the non-linear fluid-percussion model of isolated accuracy whether Meet the requirements and specifically include：The structure that regulating valve, the piston check valve and the bottom valve are damped described in the non-linear fluid-percussion model of isolated is joined respectively Number is adjusted, and obtains influence curve of the different structural parameters to the damping characteristic of the non-linear fluid-percussion model of isolated, and determine Influencing characterisitic of the structural parameters to the non-linear fluid-percussion model of isolated；Using the structural parameters of the damping regulating valve and the piston check valve as influence factor, with the anti-snakelike shock absorber Damping force maximum chooses three kinds of factors progress orthogonal tests as test index in trial stretch；The result of the test of the orthogonal test is analyzed, determines the horizontal variation tendency of each influence factor, and determines each shadow The preference data of the factor of sound.
- 3. the nonlinear Design of Structural parameters method for resisting snakelike shock absorber according to claim 1, its feature exist In：The damping regulating valve includes choke valve, normal open hole, spring, described to resist snakelike shock absorber also to include piston；The structural parameters of the damping regulating valve, the piston check valve and the bottom valve include：The damping hole of the choke valve Footpath, the spring rate of the spring, the pretightning force of the spring, the through-flow aperture in the normal open hole, the piston check valve Aperture, the unidirectional clear valve diameter of the bottom valve of the bottom valve, the diameter of piston rod of the piston and the anti-snakelike shock absorber and vehicle The connection stiffness of the connected node of car body.
- 4. the nonlinear Design of Structural parameters method for resisting snakelike shock absorber according to claim 1, its feature exist In：The influence factor of the orthogonal test includes the damping aperture, the through-flow aperture in the normal open hole, the bullet of the choke valve The aperture of the spring rate of spring, the pretightning force of the spring and the piston check valve.
- 5. the nonlinear Design of Structural parameters method for resisting snakelike shock absorber according to claim 1, its feature exist In the result of the test to the orthogonal test is analyzed, and determines the horizontal variation tendency of each influence factor, and is determined each The preference data of influence factor specifically includes：Each influence factor is determined into test group according to varying level；The damping force maximum sum for resisting snakelike shock absorber of different tests group under each influence factor is calculated, and it is all The summation of the damping force maximum of test group；The extreme difference in different tests group between damping force maximum sum under each influence factor is calculated, and according to the extreme difference value Determine the influence primary and secondary order of each influence factor；According to damping force maximum sum in the different tests group of each influence factor, the preferred number of each influence factor is determined According to.
- 6. the nonlinear Design of Structural parameters method for resisting snakelike shock absorber according to claim 1, its feature exist In the anti-snakelike shock absorber in the kinetic model by vehicle replaces with the damping force that can set active force and state variable Element, the active force in the state variable in the kinetic model and the non-linear fluid-percussion model of isolated is established dynamic State links, and forms associative simulation model and specifically includes：Resist snakelike shock absorber to replace with damping force element the described of vehicle dynamic model in Adams simulation softwares, add institute The displacement at anti-snakelike shock absorber both ends and the relative velocity at the anti-snakelike shock absorber both ends are stated as system state variables, addition The active force for resisting snakelike shock absorber；By the system state variables of the vehicle dynamic model and active force and the non-linear liquid in Easy5 simulation softwares Anti- snakelike shock absorber displacement, speed and the damping force of pressing mold type carry out dynamic link, form associative simulation model；The associative simulation model is generated into dynamic link library file.
- 7. the nonlinear Design of Structural parameters method for resisting snakelike shock absorber according to claim 1, its feature exist In, it is described that the vehicle is tested, by the test data of the experiment and the emulation data point of the associative simulation model Not carry out the contrast of time domain scale and frequency domain specifically include：Gather the test data of the vehicle and the emulation data of the associative simulation model；The test data and the car body in the emulation data and the vibration acceleration of framework are carried out pair in time domain scale Than；Calculate and contrast the root-mean-square value and the root-mean-square value of the emulation data of the test data；The test data is subjected to PSD with the emulation data and transforms to frequency domain；The test data and the vibration acceleration of car body in the emulation data are contrasted in frequency domain.
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