CN116380387A - Method and system for testing low-frequency vibration dynamic force of vehicle suspension system - Google Patents
Method and system for testing low-frequency vibration dynamic force of vehicle suspension system Download PDFInfo
- Publication number
- CN116380387A CN116380387A CN202310493214.6A CN202310493214A CN116380387A CN 116380387 A CN116380387 A CN 116380387A CN 202310493214 A CN202310493214 A CN 202310493214A CN 116380387 A CN116380387 A CN 116380387A
- Authority
- CN
- China
- Prior art keywords
- suspension system
- vehicle
- force
- frequency
- low
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 239000000725 suspension Substances 0.000 title claims abstract description 234
- 238000012360 testing method Methods 0.000 title claims abstract description 60
- 238000000034 method Methods 0.000 title claims abstract description 55
- 238000005316 response function Methods 0.000 claims abstract description 97
- 230000001133 acceleration Effects 0.000 claims abstract description 85
- 230000005284 excitation Effects 0.000 claims abstract description 85
- 230000004044 response Effects 0.000 claims abstract description 77
- 238000004364 calculation method Methods 0.000 claims description 35
- 230000003068 static effect Effects 0.000 claims description 31
- 238000005259 measurement Methods 0.000 claims description 11
- 238000004891 communication Methods 0.000 claims description 10
- 230000009466 transformation Effects 0.000 claims description 2
- 238000004590 computer program Methods 0.000 description 16
- 230000006870 function Effects 0.000 description 11
- 238000010586 diagram Methods 0.000 description 9
- 238000003860 storage Methods 0.000 description 9
- 238000004458 analytical method Methods 0.000 description 6
- 239000011159 matrix material Substances 0.000 description 6
- 238000012545 processing Methods 0.000 description 6
- 238000004088 simulation Methods 0.000 description 6
- 230000008569 process Effects 0.000 description 4
- 238000005516 engineering process Methods 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 2
- 230000007547 defect Effects 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000003287 optical effect Effects 0.000 description 2
- 241000272470 Circus Species 0.000 description 1
- 238000009825 accumulation Methods 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 230000004075 alteration Effects 0.000 description 1
- 238000003491 array Methods 0.000 description 1
- 239000013256 coordination polymer Substances 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000009795 derivation Methods 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 238000012827 research and development Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 238000010998 test method Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
- 238000012795 verification Methods 0.000 description 1
- 230000000007 visual effect Effects 0.000 description 1
Images
Classifications
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M7/00—Vibration-testing of structures; Shock-testing of structures
- G01M7/02—Vibration-testing by means of a shake table
- G01M7/06—Multidirectional test stands
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M17/00—Testing of vehicles
- G01M17/007—Wheeled or endless-tracked vehicles
- G01M17/04—Suspension or damping
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M7/00—Vibration-testing of structures; Shock-testing of structures
- G01M7/02—Vibration-testing by means of a shake table
- G01M7/022—Vibration control arrangements, e.g. for generating random vibrations
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M7/00—Vibration-testing of structures; Shock-testing of structures
- G01M7/02—Vibration-testing by means of a shake table
- G01M7/025—Measuring arrangements
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T90/00—Enabling technologies or technologies with a potential or indirect contribution to GHG emissions mitigation
Landscapes
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Vehicle Body Suspensions (AREA)
Abstract
The invention discloses a method and a system for testing low-frequency vibration dynamic force of a vehicle suspension system, wherein the method comprises the following steps: acquiring a frequency response function of a plurality of measuring points of a vehicle suspension system in an external excitation mode; acquiring actual acceleration information of multiple measuring points of the suspension system in a low-frequency vibration state of the vehicle, and acquiring dynamic response force of the suspension system in the low-frequency vibration state of the vehicle according to the acquired frequency response function and the actual acceleration information of the multiple measuring points of the suspension system of the vehicle. The method for testing the low-frequency vibration dynamic force of the vehicle suspension system can test and analyze the dynamic response force of the suspension system in the normal working state of the whole vehicle with low cost, convenience and higher precision.
Description
Technical Field
The invention relates to the technical field of vehicle NVH, in particular to a method and a system for testing low-frequency vibration dynamic force of a vehicle suspension system.
Background
Under the working conditions of idling, starting, flameout, acceleration and deceleration and the like, the suspension is not only influenced by the excitation of the engine, but also subjected to the Z-direction and X-direction dynamic load excitation of the road surface, and if the suspension is not reasonably matched, the problem of low-frequency vibration of the whole vehicle is easily caused. The high-precision simulation and test on the dynamic response force of the suspension system in the whole vehicle state are two main methods for acquiring the dynamic response force of the suspension position, and the vibration simulation of the whole vehicle can deeply and comprehensively study the suspension stress in theory, but the problems of long modeling time, more modeling parameter requirements, difficult guarantee of model precision, incapability of studying the suspension position force of a racing vehicle type and the like exist; the dynamic force test of the suspension system in the whole vehicle working state has the advantages of high efficiency, high precision, convenience in scale research on a large number of racing vehicle types, and the like.
The vehicle suspension adopts a direct and visual acquisition method of force sensor measurement; however, the use of such a measurement means is limited by various conditions such as changing the structure, operating state, reliability, etc., and is difficult to implement. Therefore, an indirect method of suspension force acquisition has been developed; the following are two existing methods for indirectly obtaining the suspension force:
the suspension force acquisition method and device for the vehicle suspension system provided by the prior art are characterized in that a strain gauge is arranged on a suspension, and a measurement signal of the strain gauge, a transmission shaft torque measurement signal and a wheel center load measurement signal are processed by using a strain gauge conversion function, and the suspension force is acquired by a simulation method of a preset PID model.
The method is a method for indirectly acquiring the suspension force by combining testing and simulation. The method is characterized in that required measurement parameters are complex (suspension strain, transmission shaft torque and suspension acceleration), simulation calculation is performed with a plurality of models, indirect conversion steps are complex, error accumulation is easy, and the method is inconvenient to widely apply in the field of vehicles. The method is divided into a secondary test, wherein the primary test is an auxiliary test under the static state of the whole vehicle, and the purpose of the method is to obtain FRF by using a force hammer and an acceleration sensor; the second test is a suspension acceleration response test under the whole vehicle working state. Both tests only comprise mechanical structural components, and the functions of the mechanical structural components are directly realized based on the existing test software and hardware systems.
The displacement and stress acquisition method of the power assembly suspension system provided by the prior art is a simulation calculation for acquiring suspension force, the external load of the power assembly is divided into a plurality of parts, suspension deformation is calculated part by part, and superposition suspension stress is calculated according to stiffness curves corresponding to different deformations. The method has the defects that the influence of the inertia and the damping of the suspension on the suspension force in the working state is ignored, and the external load and the suspension rigidity are considered to be in one-to-one correspondence, so that the suspension static force is obtained; it is difficult to calculate the dynamic response force with frequency characteristic of the suspension in the whole vehicle working state.
Disclosure of Invention
The invention aims to overcome the defects of the background technology and provides a method and a system for testing low-frequency vibration dynamic force of a vehicle suspension system.
In a first aspect, a method for testing low frequency vibration dynamic force of a vehicle suspension system is provided, comprising the steps of:
acquiring a frequency response function of a plurality of measuring points of a vehicle suspension system in an external excitation mode;
acquiring actual acceleration information of multiple measuring points of the suspension system in a low-frequency vibration state of the vehicle, and acquiring dynamic response force of the suspension system in the low-frequency vibration state of the vehicle according to the acquired frequency response function and the actual acceleration information of the multiple measuring points of the suspension system of the vehicle.
According to a first aspect, in a first possible implementation manner of the first aspect, the step of acquiring the suspension frequency response function under the actual working state of the vehicle through an external vibration excitation mode specifically includes the following steps:
generating external vibration excitation at the suspension position of the vehicle engine in an external vibration excitation mode, and simultaneously measuring and acquiring acceleration information of multiple measuring points of the suspension system;
and acquiring a frequency response function of the multiple measuring points of the suspension system of the vehicle in an actual low-frequency vibration state according to the acquired acceleration information of the multiple measuring points and the excitation force applied by an external vibration excitation mode.
In a second possible implementation manner of the first aspect, the external vibration excitation is generated at the suspension of the vehicle engine by an external vibration excitation mode, and in the step of obtaining the acceleration information of the multiple measuring points of the suspension system by measurement, the external vibration excitation mode is that the external vibration excitation is generated at the suspension by a force hammer or an additional vibration exciter.
In a third possible implementation manner of the first aspect according to the first possible implementation manner of the first aspect, in the step of simultaneously measuring and acquiring acceleration information of multiple measuring points of the suspension system, the acceleration information includes an acceleration magnitude, phase information and a time synchronization signal.
According to a fourth possible implementation manner of the first aspect, the step of obtaining a frequency response function of the multiple measuring points of the engine according to the obtained acceleration information of the multiple measuring points and an excitation force applied by an external vibration excitation manner specifically includes the following steps:
acquiring a frequency response function calculation formula of a suspension system in a static state of the whole vehicle;
the acceleration of multiple measuring points to be obtained
The information and the excitation force applied by the external vibration excitation mode are input into an acquired frequency response function calculation formula of the suspension system in the static state of the whole vehicle, and the multi-measuring-point frequency response function of the vehicle in the static state is calculated and acquired to serve as the multi-measuring-point frequency response function of the suspension system in the low-frequency vibration state of the vehicle.
In a fourth possible implementation manner of the first aspect, the step of obtaining actual acceleration information of multiple measuring points of the suspension system in the low-frequency vibration state of the vehicle, and obtaining dynamic response force of the suspension system in the low-frequency vibration state of the vehicle according to the obtained frequency response function of the multiple measuring points of the suspension system of the vehicle and the actual acceleration information specifically includes the following steps:
in a fifth possible implementation manner of the first aspect, the step of acquiring actual acceleration information of multiple measuring points of the suspension system in the low-frequency vibration state of the vehicle, and acquiring dynamic response force of the suspension system in the low-frequency vibration state of the vehicle according to the acquired frequency response function and the actual acceleration information of the multiple measuring points of the suspension system of the vehicle specifically includes the following steps:
acquiring actual acceleration information of multiple measuring points of a suspension system in a low-frequency vibration state of a vehicle;
acquiring a dynamic response force calculation formula of the suspension system in a low-frequency vibration state of the vehicle in multiple measuring points in multiple directions on a time domain;
performing Fourier transformation on a dynamic response force calculation formula on a time domain to obtain a dynamic response force calculation formula of the suspension system in a low-frequency vibration state of the vehicle on a frequency domain in multiple measuring points and multiple directions;
and inputting the obtained frequency response function of the multiple measuring points of the suspension system and the actual acceleration information into a dynamic response force calculation formula of the multiple measuring points of the suspension system in a frequency domain in multiple directions under the low-frequency vibration state of the vehicle, and obtaining the dynamic response force of the suspension system under the low-frequency vibration state of the vehicle.
In a sixth possible implementation manner of the first aspect, the acquiring actual acceleration information of multiple measuring points of the suspension system in the low-frequency vibration state of the vehicle;
before the step of obtaining the dynamic response force calculation formula of the suspension system in the low-frequency vibration state in the multiple measuring points in multiple directions on the time domain, the method further comprises the following steps:
assuming that the suspension system is a linear steady system;
the dynamic response force of the suspension system comprises main response force and interference noise generated by superposition of resultant force derived from gas pressure acting on the engine, unbalanced force of a crankshaft and impact force of an intake valve and an exhaust valve in three suspension directions, and the calculation of the dynamic directional stress of the suspension system is simplified.
In a second aspect, the application provides a low-frequency vibration dynamic force testing system of a vehicle suspension system, wherein the frequency response function obtaining module is used for obtaining a frequency response function of a plurality of measuring points of the vehicle suspension system in an external excitation mode;
the dynamic response force acquisition module is in communication connection with the frequency response function acquisition module and is used for acquiring actual acceleration information of multiple measuring points of the suspension system in the low-frequency vibration state of the vehicle, and acquiring dynamic response force of the suspension system in the low-frequency vibration state of the vehicle according to the acquired frequency response function and the actual acceleration information of the multiple measuring points of the suspension system of the vehicle.
In a first possible implementation manner of the second aspect according to the second aspect, the frequency response function obtaining module includes:
the vibration excitation unit is used for generating external vibration excitation at the suspension position of the vehicle engine in an external vibration excitation mode, and simultaneously measuring and acquiring acceleration information of multiple measuring points of the suspension system;
the frequency response function acquisition unit is in communication connection with the excitation unit and is used for acquiring the frequency response function of the multiple measuring points of the suspension system of the vehicle in an actual low-frequency vibration state according to the acquired acceleration information of the multiple measuring points and the excitation force applied by an external vibration excitation mode.
In a second possible implementation manner of the second aspect according to the second aspect, the frequency response function obtaining module includes:
the frequency response function calculation formula obtaining subunit is used for obtaining a frequency response function calculation formula of the suspension system in a static state of the whole vehicle;
the frequency response function obtaining subunit is in communication connection with the frequency response function calculating formula obtaining subunit and is used for inputting the obtained multi-measuring-point acceleration information and the exciting force applied by the external vibration exciting mode into the obtained frequency response function calculating formula of the suspension system in the static state of the whole vehicle, and calculating the multi-measuring-point frequency response function of the suspension system in the static state of the vehicle as the frequency response function of the multi-measuring points of the suspension system in the low-frequency vibration state of the vehicle.
Compared with the prior art, the invention has the following advantages:
according to the vehicle suspension system low-frequency vibration dynamic force testing method, by acquiring the frequency response function of multiple measuring points of the suspension system and combining with common NVH (Noise, vibration, harshness noise, vibration and smoothness) testing equipment, testing and analysis work can be conveniently, rapidly and highly accurately carried out under the whole vehicle working condition, the suspension system dynamic response force under the vehicle low-frequency vibration state is acquired, the operation is simple, manpower and material resources are saved, the suspension system mechanical property testing technology is enriched, and the vehicle suspension system low-frequency vibration dynamic force testing method has the advantages of being high in efficiency and low in investment.
Drawings
FIG. 1 is a flow chart of a method for testing low frequency vibration dynamic force of a vehicle suspension system according to an embodiment of the present application;
FIG. 2 is a flow chart of another method for testing low frequency vibration dynamic force of a vehicle suspension system according to an embodiment of the present application;
FIG. 3 is a schematic diagram of an auxiliary device for testing a frequency response function matrix according to an embodiment of the present application;
fig. 4 is a schematic diagram of a vibration acceleration testing device of a suspension driving end in a whole vehicle working state according to an embodiment of the present application;
fig. 5 is a functional block diagram of a vehicle suspension system low frequency vibration dynamic force testing system according to an embodiment of the present application.
Detailed Description
For better understanding of the present invention, the objects, technical solutions and advantages thereof will be more clearly understood by those skilled in the art, and the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. It will be apparent that the described embodiments are merely some, but not all embodiments of the invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the present invention without making any inventive effort, shall fall within the scope of the present invention. Furthermore, the terms "comprises," "comprising," and "having," and any variations thereof, in the description and claims, are intended to cover a non-exclusive inclusion, such that a process, method, apparatus, article, or device that comprises a list of steps or elements is not necessarily limited to those steps or elements that are expressly listed or inherent to such process, method, article, or device.
The suspension force acquisition method of the suspension system provided by the prior art is mainly used for acquiring suspension static force of the whole vehicle in a static state, and cannot acquire dynamic response force with frequency characteristics of the whole vehicle in a vibration working condition.
Referring to fig. 1, an embodiment of the present invention provides a method for testing low-frequency vibration dynamic force of a vehicle suspension system, including the following steps:
s1, acquiring a frequency response function of a plurality of measuring points of a vehicle suspension system in an external excitation mode;
and S2, acquiring actual acceleration information of multiple measuring points of the suspension system in the low-frequency vibration state of the vehicle, and acquiring dynamic response force of the suspension system in the low-frequency vibration state of the vehicle according to the acquired frequency response function and the actual acceleration information of the multiple measuring points of the suspension system of the vehicle.
The application provides a method for testing low-frequency vibration dynamic force of a vehicle suspension system, which can realize test calculation of suspension dynamic response force with higher precision in a low frequency range (less than or equal to 25 Hz), and enriches suspension dynamic force testing technology;
the test method provided by the application is concise and strong in adaptability, can be well combined with the existing experimental equipment, and does not need to change the existing suspension structure, add a force sensor and a matched test system. The experimental analysis method and the experimental analysis device in the patent have better engineering application prospect.
The test analysis method in the application has the advantages of simple test process, low test time cost and input cost, strong representativeness of test data, convenient analysis and good reference value. In the application, the dynamic response force of the suspension system is defined as the response force of the suspension system in a vibration working condition due to external force such as vibration, and is the resultant force of the stress of a plurality of suspensions.
In an embodiment, the step S1 of obtaining the suspension frequency response function in the actual working state of the vehicle through an external vibration excitation mode specifically includes the following steps:
s11, generating external vibration excitation at a suspension position of a vehicle engine in an external vibration excitation mode, and simultaneously measuring and acquiring acceleration information of multiple measuring points of a suspension system;
and step S12, acquiring a frequency response function of a plurality of measuring points of the suspension system when the vehicle is in an actual low-frequency vibration state according to the acquired acceleration information of the plurality of measuring points and the excitation force applied by an external vibration excitation mode.
The Frequency Response Function (FRF) is defined as the ratio of the dynamic response force or the static response force of the output of the structure to the excitation force, and can also be called as a frequency response coefficient, which is a structural inherent attribute parameter of the suspension system.
In this application, the dynamic force may also be referred to as a dynamic response force, which is one of response forces (the response force includes a static response force and a dynamic response force, which respectively correspond to the static state and the non-static state of the whole vehicle), and is a response generated by the suspension system under the excitation of the excitation force, specifically, a dynamic response force generated by the excitation of the low-frequency vibration under the low-frequency vibration working condition.
In an embodiment, the external vibration excitation is generated at the suspension of the vehicle engine by an external vibration excitation mode, and in the step of measuring and acquiring the acceleration information of multiple measuring points of the suspension system, the external vibration excitation mode is that the external vibration excitation is generated at the suspension by a mode of hammering a force hammer or adding an exciter.
In a more specific embodiment, a vibration exciter or hammering method is used for generating an external vibration excitation mode to measure a frequency response function, a three-point suspension arrangement is taken as an example, a left suspension, a right suspension and a rear suspension are arranged on an engine, a test auxiliary device is formed as shown in fig. 3, the vibration excitation is obtained by applying a hammering force of a hammer to a hammering point at the right suspension of the engine, or an excitation signal is generated through a signal generator, then the external vibration excitation is applied to the suspension through a band-pass filter, a power amplifier and the vibration exciter, the signal conditioner is in communication connection with an acceleration sensor and a phase sensor to obtain acceleration information, the acceleration sensor is respectively arranged at a plurality of measuring points on the engine, the phase sensor is arranged at the plurality of measuring points, the acceleration signal of the plurality of measuring points and the phase signal of the suspension are obtained, the time synchronization signal is obtained by the signal generator or a clock, the data acquisition instrument obtains the acceleration magnitude, the measuring point phase information and the excitation time information, the assumed that the response is related to the suspension force, and the physical characteristics of the system before and after the engine runs are detected, the vibration excitation system is not changed in a large scale, and the vibration response of the system can be calculated according to a vibration response mode of the vibration system is low, and the vibration response of the system can be calculated. The test auxiliary device provided by the application not only can be used for the experimental study of the independent development vehicle type suspension force measurement of enterprises, but also can be widely applied to racing vehicle types, provides a convenient and powerful means for the design and development of suspension systems, and can also reduce the research and development risks.
In one embodiment, the mounting point, hammer point, and response point in this application are defined as follows:
the mounting point mainly refers to an acceleration sensor mounting position arranged on the active end of the suspension bracket when the frequency response function test is carried out in the static state of the whole vehicle or the vibration acceleration test is carried out in the working state of the whole vehicle.
The hammering point mainly refers to a position which is selected to be used for knocking by a hammer near a mounting point of an acceleration sensor arranged on the active end of the suspension bracket when the frequency response function of the whole vehicle in a static state is tested.
The response point mainly refers to the installation position of the acceleration sensor arranged on the active end of the suspension bracket when the frequency response function test of the whole vehicle in a static state or the vibration acceleration test of the whole vehicle in a working state.
In an embodiment, in the step of simultaneously measuring and acquiring acceleration information of multiple measuring points of the suspension system, the acceleration information includes an acceleration magnitude, phase information and a time synchronization signal.
In an embodiment, the step S12 of obtaining the frequency response function of the multiple measuring points of the engine according to the obtained acceleration information of the multiple measuring points and the excitation force applied by the external vibration excitation mode specifically includes the following steps:
step S121, after converting the tested time domain data into the frequency domain, the data is displayed in a complex form C (represented by a real part and an imaginary part or an amplitude and a phase), a frequency response function calculation formula of the suspension system in the static state of the whole vehicle is obtained, and a plurality of measured frequency response function curves are generally shown in a matrix form as follows:
where the subscript may conveniently determine the location of an input-output of a particular FRF, the first subscript in the frequency response function represents the output response location i, specifically the acceleration measurement point location j of the engine, and the second subscript represents the input excitation location, specifically the hammer hammering location or the location where the exciter is attached to the suspension system.
Step S122, assuming that the suspension response and the suspension force are linearly related, and that the physical characteristics of the detection system structure do not change greatly before and after the engine is operated; the static frequency response function obtained by forceful hammer striking can be used for calculating instead of the frequency response function in the actual working state, the obtained multi-measuring-point acceleration information and the excitation force applied by the external vibration excitation mode are input into the frequency response function calculation formula of the suspension system in the static state of the whole vehicle, and the multi-measuring-point frequency response function of the vehicle in the static state is calculated and obtained to serve as the frequency response function of the multi-measuring points of the suspension system in the low-frequency vibration state of the vehicle.
In an embodiment, the step S2 of obtaining actual acceleration information of multiple measuring points of the suspension system in the low-frequency vibration state of the vehicle, and the step of obtaining dynamic response force of the suspension system in the low-frequency vibration state of the vehicle according to the obtained frequency response function and the actual acceleration information of the multiple measuring points of the suspension system of the vehicle specifically includes the following steps:
in step S21, the excitation generated in the actual operation of the engine is complex, mainly the combined action of the gas pressure, the reciprocating inertial force of the piston and the unbalanced force of the crankshaft is interfered by multiple factors such as the seating impact force of the air valve, the resistance of the intake and exhaust air flow and the friction force, and the accurate calculation is difficult. Thus, the actual response sources of the vehicle suspension system are also very complex under engine operating conditions, subject to adverse effects from the vehicle body, as well as disturbances from the external environment, in addition to being directly excited by the engine. In order to accurately and reliably measure and acquire vibration acceleration response signals of a driving end of a suspension system in actual work, a plurality of reference quantities are generally required to be acquired for analysis and judgment, and fig. 4 is a graph of the application, wherein acceleration information is used for calculating dynamic response force of the suspension system in a low-frequency vibration state of a vehicle, and actual acceleration information of multiple measuring points of the suspension system in the low-frequency vibration state of the vehicle is acquired;
s22, acquiring dynamic response force u of the suspension system in the low-frequency vibration state of the vehicle in multiple measuring points in multiple directions on a time domain j The calculation formula is shown as follows:
u j ＝u jfx1 +u jfy1 +u jfz1 +…+u jfxm +u jfym +u jfzm +n(j＝1,2,…3m)
wherein u is jfx1 ，u jfy1 ，u jfz1 Representing the response of the resultant force in the three directions of the first suspension, u jfx1 ，u jfy1 ，u jfz1 The dynamic response force generated by the first suspension in three directions is represented by m, the number of suspension measuring points is represented by m, and the random interference noise is represented by n.
S23, performing Fourier transform on a dynamic response force calculation formula on a time domain to obtain a multi-measuring-point multi-directional dynamic response force U on a frequency domain of a suspension system in a low-frequency vibration state of a vehicle j The calculation formula is as follows:
U j ＝H jX1 ·F X1 +H jY1 ·F Y1 +H jZ1 ·F Z1 +…+H jXm ·F Xm +H jYm ·F Ym +H jZm ·F Zm +N
wherein H is jXm 、H jYm 、H jZm Respectively expressed as that a certain measuring point is in a certain direction caused by excitation in three directions of an m measuring pointN represents the fourier transform of the interference noise.
The above can be expressed as a matrix form
{U}＝[H]·{F}+{N}
In the method, { U } -each measuring point vibration signal Fourier transform vector; [H] -a transfer function matrix; { F } -dynamic response force vector in each direction on suspension; { N } -each station interference noise vector.
Step S23, inputting the obtained frequency response function of the multiple measuring points of the suspension system and the actual acceleration information into a dynamic response force calculation formula of the multiple measuring points of the suspension system in the frequency domain in multiple directions under the low-frequency vibration state of the vehicle, so that { N } = 0, i.e. the disturbance is ignored, a dynamic response force vector F (omega) = H of the suspension system can be calculated -1 And (omega) U (omega) for acquiring dynamic response force of the suspension system in the low-frequency vibration state of the vehicle.
In an embodiment, before the step of obtaining the calculation formula of the dynamic response force of the suspension system in the low-frequency vibration state in multiple measuring points in multiple directions in the time domain, the method further comprises the following steps:
step S2101, presuming that the suspension system is a linear steady system;
step S2102, calculating and simplifying dynamic directional stress of the suspension system by main response force and interference noise generated by superposition and derivation of resultant force of gas pressure acting on the engine, unbalanced force of a crankshaft and impact force of an intake valve and an exhaust valve in three directions of suspension.
Through the assumption and simplification, the suspension system can be represented by a multi-input multi-output system model, and the dynamic directional stress of a certain measuring point at the end of the suspension power assembly in a certain direction can be calculated conveniently, rapidly and highly accurately by applying the least square principle and the relation between the excitation forces through the dynamic response force calculation formula.
According to the method, the static frequency response function of the vehicle in an actual working state is obtained through an external vibration excitation mode to replace the frequency response function of the suspension system of the vehicle in a low-frequency vibration working condition, the dynamic response force of the suspension system is calculated, the dynamic response force of the suspension system can be accurately obtained through verification, the method can be applied to the dynamic response force obtaining of the whole vehicle in a normal running state, only an acceleration sensor is arranged at a plurality of measuring points of an engine, and phase sensors are arranged at each suspension position, and the external vibration excitation is replaced by the vibration excitation of the suspension system caused by the combined action of gas pressure, piston reciprocating inertia force and crankshaft unbalance force in the normal running state of the vehicle, and meanwhile, the vibration excitation is also caused by the air valve seating impact force, intake and exhaust flow resistance, friction force and the like.
The application provides a whole car quiescent condition suspension excitation to each suspension mounting point frequency response function matrix test auxiliary device, as shown in fig. 3, the device has simple structure, characteristics with low costs, and this device has detailed installation position scope, the hammer hammering point of having determined vibration acceleration sensor or vibration exciter excitation point scope, and all the testing arrangement with hammer or vibration exciter measurement frequency response function matrix in this scope is in this patent claim scope.
The vibration acceleration testing device for the suspension driving end of the whole vehicle working state provided by the application has the advantages of judging whether the vibration acceleration signal is credible or not as shown in fig. 4, and the device for simultaneously measuring the vibration acceleration and the rotating speed phase by utilizing the engine time synchronization signal is within the scope of the patent claims.
The vehicle suspension system low-frequency vibration dynamic force test mode is concise and strong in adaptability, and three-way low-frequency vibration dynamic forces of all suspensions of the vehicle power assembly can be indirectly calculated from experimental data through step-by-step test and simple mathematical calculation.
Based on the same inventive concept, please refer to fig. 5, the low-frequency vibration dynamic force testing system for a vehicle suspension system provided by the present application includes a frequency response function obtaining module 100 and a dynamic response force obtaining module 200, where the frequency response function obtaining module 100 is configured to obtain a frequency response function of multiple measuring points of the vehicle suspension system in an external excitation manner; the dynamic response force obtaining module 200 is in communication connection with the frequency response function obtaining module 100, and is configured to obtain actual acceleration information of multiple measuring points of the suspension system in the low-frequency vibration state of the vehicle, and obtain dynamic response force of the suspension system in the low-frequency vibration state of the vehicle according to the obtained frequency response function and the obtained actual acceleration information of the multiple measuring points of the suspension system of the vehicle.
In an embodiment, the frequency response function obtaining module includes:
the vibration excitation unit is used for generating external vibration excitation at the suspension position of the vehicle engine in an external vibration excitation mode, and simultaneously measuring and acquiring acceleration information of multiple measuring points of the suspension system;
the frequency response function acquisition unit is in communication connection with the excitation unit and is used for acquiring the frequency response function of the multiple measuring points of the suspension system of the vehicle in an actual low-frequency vibration state according to the acquired acceleration information of the multiple measuring points and the excitation force applied by an external vibration excitation mode.
In an embodiment, the vehicle suspension system low-frequency vibration dynamic force test system, the frequency response function acquisition unit includes:
the frequency response function calculation formula obtaining subunit is used for obtaining a frequency response function calculation formula of the suspension system in a static state of the whole vehicle;
the frequency response function obtaining subunit is in communication connection with the frequency response function calculating formula obtaining subunit and is used for inputting the obtained multi-measuring-point acceleration information and the exciting force applied by the external vibration exciting mode into the obtained frequency response function calculating formula of the suspension system in the static state of the whole vehicle, and calculating the multi-measuring-point frequency response function of the suspension system in the static state of the vehicle as the frequency response function of the multi-measuring points of the suspension system in the low-frequency vibration state of the vehicle. Based on the same inventive concept, the embodiments of the present application also provide a computer-readable storage medium, on which a computer program is stored, which when executed by a processor implements all or part of the method steps of the above method.
The present invention may be implemented by implementing all or part of the above-described method flow, or by instructing the relevant hardware by a computer program, which may be stored in a computer readable storage medium, and which when executed by a processor, may implement the steps of the above-described method embodiments. Wherein the computer program comprises computer program code, which may be in the form of source code, object code, executable files or in some intermediate form, etc. The computer readable medium may include: any entity or device capable of carrying computer program code, a recording medium, a U disk, a removable hard disk, a magnetic disk, an optical disk, a computer Memory, a Read-Only Memory (ROM), a random access Memory (RAM, ran dom Access Memory), an electrical carrier signal, a telecommunications signal, a software distribution medium, and so forth. It should be noted that the content of the computer readable medium can be appropriately increased or decreased according to the requirements of the jurisdiction's jurisdiction and the patent practice, for example, in some jurisdictions, the computer readable medium does not include electrical carrier signals and telecommunication signals according to the jurisdiction and the patent practice.
Based on the same inventive concept, the embodiments of the present application further provide an electronic device, including a memory and a processor, where the memory stores a computer program running on the processor, and when the processor executes the computer program, the processor implements all or part of the method steps in the above method.
The processor may be a central processing unit (Central Processing Unit, CP U), but may also be other general purpose processors, digital signal processors (Digital Signal Pro cessor, DSP), application specific integrated circuits (Application Specific Integrated Circu it, ASIC), off-the-shelf programmable gate arrays (Field-Programmable Gate Array, FP GA) or other programmable logic devices, discrete gate or transistor logic devices, discrete hardware components, or the like. A general purpose processor may be a microprocessor or the processor may be any conventional processor or the like, the processor being a control center of the computer device, and the various interfaces and lines connecting the various parts of the overall computer device.
The memory may be used to store computer programs and/or modules, and the processor implements various functions of the computer device by running or executing the computer programs and/or modules stored in the memory, and invoking data stored in the memory. The memory may mainly include a storage program area and a storage data area, wherein the storage program area may store an operating system, an application program required for at least one function (e.g., a sound playing function, an image playing function, etc.); the storage data area may store data (e.g., audio data, video data, etc.) created according to the use of the handset. In addition, the memory may include high-speed random access memory, and may also include non-volatile memory, such as a hard disk, memory, plug-in hard disk, smart Media Card (SMC), secure Digital (SD) Card, flash Card (Flash Ca rd), at least one disk storage device, flash memory device, or other volatile solid state storage device.
It will be appreciated by those skilled in the art that embodiments of the present invention may be provided as a method, system, server, or computer program product. Accordingly, the present invention may take the form of an entirely hardware embodiment, an entirely software embodiment or an embodiment combining software and hardware aspects. Furthermore, the present invention may take the form of a computer program product embodied on one or more computer-usable storage media (including, but not limited to, magnetic disk storage, optical storage, and the like) having computer-usable program code embodied therein.
The present invention is described with reference to flowchart illustrations and/or block diagrams of methods, apparatus (systems), servers and computer program products according to embodiments of the invention. It will be understood that each flow and/or block of the flowchart illustrations and/or block diagrams, and combinations of flows and/or blocks in the flowchart illustrations and/or block diagrams, can be implemented by computer program instructions. These computer program instructions may be provided to a processor of a general purpose computer, special purpose computer, embedded processor, or other programmable data processing apparatus to produce a machine, such that the instructions, which execute via the processor of the computer or other programmable data processing apparatus, create means for implementing the functions specified in the flowchart flow or flows and/or block diagram block or blocks.
These computer program instructions may also be stored in a computer-readable memory that can direct a computer or other programmable data processing apparatus to function in a particular manner, such that the instructions stored in the computer-readable memory produce an article of manufacture including instruction means which implement the function specified in the flowchart flow or flows and/or block diagram block or blocks.
These computer program instructions may also be loaded onto a computer or other programmable data processing apparatus to cause a series of operational steps to be performed on the computer or other programmable apparatus to produce a computer implemented process such that the instructions which execute on the computer or other programmable apparatus provide steps for implementing the functions specified in the flowchart flow or flows and/or block diagram block or blocks.
It will be apparent to those skilled in the art that various modifications and variations can be made to the present invention without departing from the spirit or scope of the invention. Thus, it is intended that the present invention also include such modifications and alterations insofar as they come within the scope of the appended claims or the equivalents thereof.
Claims (10)
1. The method for testing the low-frequency vibration dynamic force of the vehicle suspension system is characterized by comprising the following steps of:
acquiring a frequency response function of a plurality of measuring points of a vehicle suspension system in an external excitation mode;
acquiring actual acceleration information of multiple measuring points of the suspension system in a low-frequency vibration state of the vehicle, and acquiring dynamic response force of the suspension system in the low-frequency vibration state of the vehicle according to the acquired frequency response function and the actual acceleration information of the multiple measuring points of the suspension system of the vehicle.
2. The method for testing the dynamic force of low-frequency vibration of the suspension system of the vehicle according to claim 1, wherein the step of obtaining the suspension frequency response function of the vehicle in the actual working state by the external vibration excitation mode comprises the following steps:
generating external vibration excitation at the suspension position of the vehicle engine in an external vibration excitation mode, and simultaneously measuring and acquiring acceleration information of multiple measuring points of the suspension system;
and acquiring a frequency response function of the multiple measuring points of the suspension system of the vehicle in an actual low-frequency vibration state according to the acquired acceleration information of the multiple measuring points and the excitation force applied by an external vibration excitation mode.
3. The method for testing the low-frequency vibration dynamic force of the suspension system of the vehicle according to claim 2, wherein the external vibration excitation is generated at the suspension of the engine of the vehicle by an external vibration excitation mode, and in the step of acquiring the acceleration information of multiple measuring points of the suspension system by measurement, the external vibration excitation mode is the mode of hammering by a force hammer or adding a vibration exciter at the suspension.
4. The method for testing the low-frequency vibration dynamic force of the vehicle suspension system according to claim 2, wherein in the step of simultaneously measuring and acquiring the acceleration information of the plurality of measuring points of the suspension system, the acceleration information comprises acceleration magnitude, phase information and time synchronization signals.
5. The method for testing the dynamic force of the low-frequency vibration of the vehicle suspension system according to claim 2, wherein the step of obtaining the frequency response function of the multiple measuring points of the engine according to the obtained acceleration information of the multiple measuring points and the excitation force applied by the external vibration excitation mode specifically comprises the following steps:
acquiring a frequency response function calculation formula of a suspension system in a static state of the whole vehicle;
and inputting the acquired multi-measuring-point acceleration information and excitation force applied by an external vibration excitation mode into an acquired frequency response function calculation formula of the suspension system in the static state of the whole vehicle, and calculating the multi-measuring-point frequency response function of the suspension system in the static state of the vehicle as the frequency response function of the multi-measuring points of the suspension system in the low-frequency vibration state of the vehicle.
6. The method for testing the dynamic force of the low-frequency vibration of the vehicle suspension system according to claim 1, wherein the step of acquiring the actual acceleration information of the multiple measuring points of the suspension system in the low-frequency vibration state of the vehicle and acquiring the dynamic response force of the suspension system in the low-frequency vibration state of the vehicle according to the acquired frequency response function and the actual acceleration information of the multiple measuring points of the vehicle suspension system specifically comprises the following steps:
acquiring actual acceleration information of multiple measuring points of a suspension system in a low-frequency vibration state of a vehicle;
acquiring a dynamic response force calculation formula of the suspension system in a low-frequency vibration state of the vehicle in multiple measuring points in multiple directions on a time domain;
performing Fourier transformation on a dynamic response force calculation formula on a time domain to obtain a dynamic response force calculation formula of the suspension system in a low-frequency vibration state of the vehicle on a frequency domain in multiple measuring points and multiple directions;
and inputting the obtained frequency response function of the multiple measuring points of the suspension system and the actual acceleration information into a dynamic response force calculation formula of the multiple measuring points of the suspension system in a frequency domain in multiple directions under the low-frequency vibration state of the vehicle, and obtaining the dynamic response force of the suspension system under the low-frequency vibration state of the vehicle.
7. The method for testing the dynamic force of the low-frequency vibration of the vehicle suspension system according to claim 6, wherein before the step of obtaining the dynamic response force calculation formula of the suspension system in the low-frequency vibration state in multiple measuring points in multiple directions in the time domain, the method further comprises the steps of:
assuming that the suspension system is a linear steady system;
the dynamic response force of the suspension system comprises main response force and interference noise generated by superposition of resultant force derived from gas pressure acting on the engine, unbalanced force of a crankshaft and impact force of an intake valve and an exhaust valve in three suspension directions, and the calculation of the dynamic directional stress of the suspension system is simplified.
8. A vehicle suspension system low frequency vibration dynamic force testing system, comprising:
the frequency response function acquisition module is used for acquiring the frequency response function of the plurality of measuring points of the vehicle suspension system in an external excitation mode;
the dynamic response force acquisition module is in communication connection with the frequency response function acquisition module and is used for acquiring actual acceleration information of multiple measuring points of the suspension system in the low-frequency vibration state of the vehicle, and acquiring dynamic response force of the suspension system in the low-frequency vibration state of the vehicle according to the acquired frequency response function and the actual acceleration information of the multiple measuring points of the suspension system of the vehicle.
9. The vehicle suspension system low frequency vibration dynamic force testing system of claim 8 wherein said frequency response function acquisition module comprises:
the vibration excitation unit is used for generating external vibration excitation at the suspension position of the vehicle engine in an external vibration excitation mode, and simultaneously measuring and acquiring acceleration information of multiple measuring points of the suspension system;
the frequency response function acquisition unit is in communication connection with the excitation unit and is used for acquiring the frequency response function of the multiple measuring points of the suspension system of the vehicle in an actual low-frequency vibration state according to the acquired acceleration information of the multiple measuring points and the excitation force applied by an external vibration excitation mode.
10. The vehicle suspension system low frequency vibration dynamic force test system of claim 9, wherein the frequency response function acquisition unit comprises:
the frequency response function calculation formula obtaining subunit is used for obtaining a frequency response function calculation formula of the suspension system in a static state of the whole vehicle;
the frequency response function obtaining subunit is in communication connection with the frequency response function calculating formula obtaining subunit and is used for inputting the obtained multi-measuring-point acceleration information and the exciting force applied by the external vibration exciting mode into the obtained frequency response function calculating formula of the suspension system in the static state of the whole vehicle, and calculating the multi-measuring-point frequency response function of the suspension system in the static state of the vehicle as the frequency response function of the multi-measuring points of the suspension system in the low-frequency vibration state of the vehicle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310493214.6A CN116380387A (en) | 2023-04-25 | 2023-04-25 | Method and system for testing low-frequency vibration dynamic force of vehicle suspension system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310493214.6A CN116380387A (en) | 2023-04-25 | 2023-04-25 | Method and system for testing low-frequency vibration dynamic force of vehicle suspension system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN116380387A true CN116380387A (en) | 2023-07-04 |
Family
ID=86967611
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202310493214.6A Pending CN116380387A (en) | 2023-04-25 | 2023-04-25 | Method and system for testing low-frequency vibration dynamic force of vehicle suspension system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN116380387A (en) |
-
2023
- 2023-04-25 CN CN202310493214.6A patent/CN116380387A/en active Pending
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| Lennström et al. | Validation of the blocked force method for various boundary conditions for automotive source characterization | |
| Janssens et al. | OPAX: A new transfer path analysis method based on parametric load models | |
| CN106991216B (en) | Robustness estimation and optimization method for steering wheel shake caused by automobile cooling module | |
| CN111537170B (en) | Dynamic stiffness testing method for servo actuator | |
| CN110210179B (en) | Method for acquiring dynamic stiffness of elastic element and loads at two ends of elastic element | |
| CN107144435B (en) | A kind of dynamic vibration absorber frequency test method | |
| CN112651354A (en) | Method and device for determining noise source | |
| CN115270296A (en) | Method and system for analyzing fatigue durability of commercial vehicle cab | |
| CN102680214B (en) | Vibration isolation performance test device and method for corrugated pipe | |
| CN112432702B (en) | Vibration source identification method based on superposition of vibration transmission paths of centrifugal pump | |
| CN110096779B (en) | Servo mechanism dynamic characteristic analysis method | |
| CN116380387A (en) | Method and system for testing low-frequency vibration dynamic force of vehicle suspension system | |
| CN113515808A (en) | Noise prediction method for power assembly | |
| JP3145625B2 (en) | Piping system fatigue evaluation device | |
| Ren et al. | Correction of transducers mass effects from the measured frfs in hammer impact testing | |
| JP2020183901A (en) | Correction method for tire uniformity data and tire uniformity machine | |
| CN111062143A (en) | Method for identifying inertial parameters of automobile engine | |
| KR102032491B1 (en) | Method for measuring resistance of model ship using active vibration control technology | |
| Dom et al. | Transfer path analysis: accurate load prediction beyond the traditional mount stiffness and matrix inversion methods | |
| CN113656994B (en) | Suspension force acquisition method and device for automobile suspension system | |
| Gaonkar | Modal analysis of exhaust system to optimize mounting hanger location | |
| CN113155486A (en) | Durability simulation test method and system for power assembly suspension system | |
| CN106096193A (en) | Car load idling, acceleration simulating engine excitation solving system and method | |
| CN112749499A (en) | Simulation method and device for quickly diagnosing NVH performance of motor structure | |
| CN113297907A (en) | Nonlinear damping identification method based on data driving under pulse excitation |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |