WO2024001902A1 - Method and system for calculating maximum stress distribution of parts of vehicle chassis and storage medium - Google Patents

Method and system for calculating maximum stress distribution of parts of vehicle chassis and storage medium Download PDF

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Publication number
WO2024001902A1
WO2024001902A1 PCT/CN2023/101685 CN2023101685W WO2024001902A1 WO 2024001902 A1 WO2024001902 A1 WO 2024001902A1 CN 2023101685 W CN2023101685 W CN 2023101685W WO 2024001902 A1 WO2024001902 A1 WO 2024001902A1
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Prior art keywords
maximum stress
component
chassis
vehicle
stress distribution
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PCT/CN2023/101685
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French (fr)
Chinese (zh)
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WO2024001902A9 (en
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王有智
孙秀兵
程拼拼
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上海合科科技有限公司
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Publication of WO2024001902A1 publication Critical patent/WO2024001902A1/en
Publication of WO2024001902A9 publication Critical patent/WO2024001902A9/en

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    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/15—Vehicle, aircraft or watercraft design
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/20—Design optimisation, verification or simulation
    • G06F30/23—Design optimisation, verification or simulation using finite element methods [FEM] or finite difference methods [FDM]
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
    • G06F2119/02—Reliability analysis or reliability optimisation; Failure analysis, e.g. worst case scenario performance, failure mode and effects analysis [FMEA]
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
    • G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces
    • 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

Definitions

  • the invention relates to the field of transportation, and in particular to a method for calculating the maximum stress distribution of chassis components of various types of vehicles; and a system for calculating the maximum stress distribution of chassis components of various types of vehicles, and a system for performing the above A computer-readable storage medium for each step in the method for calculating maximum stress distribution of vehicle chassis components.
  • Car durability is one of the important indicators of car quality. As an important tool to verify the durability performance of the car, the vehicle durability test is one of the tests that every manufacturer must do during the design verification phase.
  • Automobile reliability tests can be divided into: laboratory reliability tests, proving ground reliability tests, and user road reliability tests. Among them, test sites and user road reliability tests need to collect test data such as six-component force, acceleration, displacement, strain, etc., involving a wide range of working conditions, and the collected test data has a long time history. Fast and accurate analysis of data collected under various working conditions is particularly important to shorten the automotive product development cycle and reduce costs.
  • the automobile chassis As the installation carrier for other vehicle systems, the automobile chassis is subject to loads under various complex working conditions. The performance of the chassis will directly determine the performance of the entire vehicle. In automobile parts design, test plan formulation, parts failure analysis, product improvement and optimization, etc., it is chassis design to clarify the maximum stress and location of each chassis component under various working conditions and the dangerous working conditions of each component. The focus of attention, it can be used as the basis for strength damage, and can also provide reference for the design, optimization and improvement of the chassis.
  • VonMises stress is one of the important criteria for structural failure assessment. It is mostly used for plastic materials and belongs to equivalent stress. It is derived based on the fourth strength theory.
  • the direction of n is called the principal direction of stress at this point.
  • Shear stress is a type of stress, defined as the shear force endured per unit area.
  • the direction of the force is orthogonal to the direction of the force-bearing surface.
  • Hard points generally refer to points in the suspension that determine the kinematic characteristics of the suspension, such as key mounting points, moving hinge center points, bushing center points, etc.
  • the existing technology establishes a multi-body dynamics model of the vehicle, and based on the measured road spectrum data collected under various working conditions, the operation Using the virtual iteration method, the driving load of the multi-body dynamics model of the vehicle is obtained, and dynamic simulation analysis is performed.
  • the load time history of the hard points of the chassis system components is extracted, combined with the stress influence factors of the components under the unit load, and multiplied and summed to calculate the stress time history of the components under the measured road spectrum.
  • the existing technical group In order to solve the problem of long time-consuming dynamic simulation analysis of the full time period of the measured road spectrum load history under various working conditions, the existing technical group generally edits the original load spectrum and compresses the load duration.
  • the more commonly used methods are: starting from the time domain, based on the damage retention editing method, the collected loads are added to windows at equal distances in the time domain, the damage amount of the load in each window is calculated, and the windows with smaller damage contributions are deleted. signal fragments to achieve the purpose of compression; perform time-frequency analysis on the load, identify load cycles with smaller damage from the frequency domain, and delete cycles with smaller damage contribution to achieve the purpose of compression.
  • the technical problem to be solved by the present invention is to provide a method for calculating the maximum stress distribution of chassis components of various types of vehicle chassis that can quickly calculate the maximum stress and maximum stress distribution of chassis components under actual measured road spectrum loads under various working conditions.
  • the present invention also provides a computer-readable storage medium for executing each step in the method for calculating the maximum stress distribution of vehicle chassis components; and a computer-readable storage medium for various types of vehicle chassis that can quickly calculate a variety of tasks.
  • the maximum stress distribution calculation system of vehicle chassis components determines the maximum stress and maximum stress distribution of chassis components under the actual measured road spectrum load.
  • the method for calculating the maximum stress distribution of vehicle chassis components includes the following steps:
  • Step 1 Construct a rigid-flexible coupled multi-body dynamics model of the entire vehicle that does not include tires
  • Step 2 Constrain the motion posture of the vehicle body and benchmark the rigid-flexible coupled multi-body dynamics model of the entire vehicle;
  • Step 3 Conduct sensitivity analysis on the six-component force load to obtain the sensitivity of the maximum stress of each chassis component to each six-component force load component;
  • Step 4 Count the maximum value, minimum value and/or occurrence time of each load component of the six-component road force measured under each working condition;
  • Step 5 Based on the sensitivity calculated in step 3, calculate the maximum stress of each chassis component under the actual measured road spectrum under each working condition;
  • Step 6 Calculate the yield limit of each chassis component material, and calculate the ratio of the maximum stress of each chassis component to the corresponding material yield limit under each working condition;
  • Step 7 Sort the working conditions according to the maximum stress of each component in the chassis system under each working condition
  • Step 8 Sort the working conditions of each component according to the ratio of material yield limit
  • Step 9 Sort the chassis components according to their maximum stress under each working condition
  • Step 10 Sort the components for each working condition according to the ratio of material yield limit
  • Step 11 The maximum stress distribution of each system and subsystem that forms the chassis based on the maximum stress distribution of chassis components.
  • step 4 of the method for calculating the maximum stress distribution of vehicle chassis components the minimum value, the time of occurrence of the maximum value and/or the time of occurrence of the minimum value of each load component of the measured six-component road force under each working condition are also calculated.
  • Benchmarking refers to comparing the signals calculated by simulation (such as shaft head acceleration, damper displacement, etc.) with the signals measured in the test. By adjusting the stiffness and other parameters of the buffer, the simulated signals (such as shaft head acceleration, shock absorber displacement, etc.) Damper displacement, etc.) is consistent with the measured signal in the test or the error is within an acceptable range (the range can be specified according to actual needs), then the benchmarking is completed and the accuracy of the simulation model is ensured.
  • step 5 also calculates the minimum stress, the maximum stress occurrence moment and/or the minimum stress occurrence moment of each chassis component under the measured road spectrum under each working condition.
  • the maximum stress distribution calculation method of vehicle chassis components is described.
  • the components adopt rigid bodies, modal flexible bodies or finite element flexible bodies.
  • the rigid-flexible coupling multi-body dynamics model of the entire vehicle selects at least the first 10 frequencies of the chassis component model.
  • the method for calculating the maximum stress distribution of vehicle chassis components uses a fixed body to constrain the movement posture of the vehicle body;
  • a buffer member is established between the axle head and the ground, and the displacement stiffness range of the buffer member is limited.
  • the displacement stiffness range of the buffer is 0/mm ⁇ 1000N/mm.
  • the displacement stiffness range of the buffer is: the vertical stiffness range is 0N/mm ⁇ 10N/mm, the lateral range is 0N/mm ⁇ 0.5N/mm, and the longitudinal stiffness range is The range is 0N/mm ⁇ 0.5N/mm.
  • the method for calculating the maximum stress distribution of vehicle chassis components and the benchmarking of the multi-body dynamics model include: static balance analysis and adjustment of model axle loads.
  • the method for calculating the maximum stress distribution of vehicle chassis components, and benchmarking the multi-body dynamics model also include: adjusting the stiffness and/or damping parameters of the elastic elements inside the model, adjusting the shock absorber displacement and/or The shaft head acceleration data is benchmarked and the system model is corrected.
  • the maximum stress of chassis components at least includes VonMises stress, each stress component along each coordinate axis direction in the coordinate system, principal stress and/or shear stress.
  • the present invention provides a computer-readable storage medium using the steps in any one of the above methods for calculating the maximum stress distribution of vehicle chassis components.
  • the present invention provides a maximum stress distribution calculation system for vehicle chassis components, including:
  • a model building module which is used to build a rigid-flexible coupled multi-body dynamics model of the entire vehicle that does not include tires;
  • the constraint module is used to constrain the motion posture of the vehicle body and benchmark the rigid-flexible coupled multi-body dynamics model of the entire vehicle;
  • the sensitivity analysis module is used to perform sensitivity analysis on the six-component force load to obtain the sensitivity of the maximum stress of each chassis component to each six-component force load component;
  • the measured statistics module is used to separately count the maximum values of each load component of the six measured road forces under each working condition
  • a calculation module that calculates the maximum stress, occurrence position and/or occurrence time of each chassis component under the measured road spectrum under various working conditions based on sensitivity
  • the statistical module is used to count the yield limits of the materials of each chassis component, and calculate the ratio of the maximum stress of each chassis component to the corresponding material yield limit under each working condition;
  • the sorting module sorts the working conditions according to the maximum stress of each component in the chassis system under each working condition
  • the components are sorted for each working condition according to the ratio of the material yield limit
  • Display module which forms the maximum stress distribution of each system and subsystem of the chassis based on the maximum stress distribution of chassis components.
  • the measured statistics module also counts the minimum value, maximum value occurrence time and/or minimum value occurrence time of each load component of the six-component road force measured under various working conditions.
  • the calculation module of the maximum stress distribution calculation system of vehicle chassis components also calculates the minimum stress, maximum stress occurrence moment and/or minimum stress occurrence moment of each chassis component under the measured road spectrum under various working conditions.
  • the maximum stress distribution calculation system of vehicle chassis components is described.
  • the components adopt rigid bodies, modal flexible bodies or finite element flexible bodies.
  • the maximum stress distribution calculation system of vehicle chassis components is described.
  • the components adopt rigid bodies, modal flexible bodies or finite element flexible bodies.
  • the rigid-flexible coupling multi-body dynamics model of the entire vehicle selects at least the first 10 frequencies of the chassis component model.
  • the maximum stress distribution calculation system of vehicle chassis components uses a fixed body to constrain the movement posture of the vehicle body;
  • a buffer member is established between the axle head and the ground, and the displacement stiffness range of the buffer member is limited.
  • the maximum stress distribution calculation system of vehicle chassis components has a buffer displacement stiffness range of 0/mm to 1000N/mm.
  • the displacement stiffness range of the buffer is: the vertical stiffness range is 0N/mm ⁇ 10N/mm, the lateral range is 0N/mm ⁇ 0.5N/mm, and the longitudinal stiffness range is The range is 0N/mm ⁇ 0.5N/mm.
  • the vehicle chassis components maximum stress distribution calculation system includes: static balance analysis and adjustment of model axle loads.
  • the vehicle chassis components maximum stress distribution calculation system, the multi-body dynamics model benchmarking also includes: adjusting the stiffness and/or damping parameters of the elastic elements inside the model, adjusting the shock absorber displacement and/or The shaft head acceleration data is benchmarked and the system model is corrected.
  • the maximum stress distribution calculation system of vehicle chassis components described above has a maximum stress of at least Including VonMises stress, each stress component along each coordinate axis direction in the coordinate system, principal stress and/or shear stress.
  • the present invention calculates the sensitivity of each chassis component to the six-component load component of each wheel center, which is equivalent to performing a series of unidirectional static calculations on the chassis system, with high calculation efficiency and reliable results.
  • the maximum stress of each component of the automobile chassis under the measured road spectrum under various working conditions can be calculated through simple algebraic operations. There is no need to apply long-term measured road spectrum loads to drive the vehicle multi-body dynamics rigid-flexible coupling model, which reduces calculation costs and time costs.
  • Figure 1 is a schematic flow diagram of the present invention.
  • the invention provides a method for calculating the maximum stress distribution of vehicle chassis components, which includes the following steps:
  • Step 1 Construct a rigid-flexible coupled multi-body dynamics model of the entire vehicle that does not include tires
  • Step 2 Constrain the motion posture of the vehicle body and benchmark the rigid-flexible coupled multi-body dynamics model of the entire vehicle;
  • Step 3 Conduct sensitivity analysis on the six-component force load to obtain the sensitivity of the maximum stress of each chassis component to each six-component force load component;
  • Step 4 Count the maximum values of each load component of the six measured road forces under each working condition
  • Step 5 Based on the sensitivity calculated in step 3, calculate the maximum stress of each chassis component under the actual measured road spectrum under each working condition;
  • Step 6 Calculate the yield limit of each chassis component material, and calculate the ratio of the maximum stress of each chassis component to the corresponding material yield limit under each working condition;
  • Step 7 Sort the working conditions according to the maximum stress of each component in the chassis system under each working condition
  • Step 8 Sort the working conditions of each component according to the ratio of material yield limit
  • Step 9 Sort the chassis components according to their maximum stress under each working condition
  • Step 10 Sort the components for each working condition according to the ratio of material yield limit
  • Step 11 The maximum stress distribution of each system and subsystem that forms the chassis based on the maximum stress distribution of chassis components.
  • step 4 also counts the minimum value, maximum value occurrence time and/or minimum value occurrence time of each load component of the six-component road force measured under each working condition;
  • Step 5 also calculates the minimum stress, maximum stress occurrence moment and/or minimum stress occurrence moment of each chassis component under the measured road spectrum under each working condition.
  • the invention provides a method for calculating the maximum stress distribution of vehicle chassis components, which includes the following steps:
  • Step 1 Construct a rigid-flexible coupled multi-body dynamics model of the entire vehicle that does not include tires.
  • the components are rigid bodies, modal flexible bodies or finite element flexible bodies; the body is reduced to quality point, giving the correct parameters such as mass, center of mass coordinates, and moment of inertia.
  • Automobile chassis components are modeled using modal flexible bodies. At least the first 10 frequencies of the chassis component model are selected. The first 6 frequencies are the rigid body modes of the model, which are not considered in this invention;
  • Step 2 To constrain the movement posture of the vehicle body, a buffer member is established between the axle head and the ground.
  • the buffer member uses a bushing or a spring, and limits the displacement stiffness range of the buffer member.
  • the displacement stiffness range of the buffer member is 0/mm ⁇ 1000N/mm; preferably, The displacement stiffness range of the buffer is: the vertical stiffness range is 0N/mm ⁇ 10N/mm, the lateral stiffness range is 0N/mm ⁇ 0.5N/mm, and the longitudinal stiffness range is 0N/mm ⁇ 0.5N/mm.
  • a fixed body is used to constrain the movement of the body
  • Step 3 Conduct sensitivity analysis on the six-component force load to obtain the sensitivity of the maximum stress of each chassis component to each six-component force load component;
  • the vehicle has 4 axle heads, each axle head has 6 components (3 force components and 3 moment components), and there are a total of 24 load components, recorded as F ij .
  • i 1,2,3,4,5,6.
  • 1, 2, and 3 respectively represent the force components in the X, Y, and Z directions in the vehicle coordinate system
  • 4, 5, and 6 respectively represent the force components in the vehicle coordinate system.
  • the sensitivity matrix is:
  • Step 4 Count the maximum values of each load component of the six measured road forces under each working condition
  • the measured road spectrum collection includes k working conditions, and the working conditions are sequentially numbered 1, 2, 3,...,k. According to the time history curve of the measured road spectrum under various working conditions, the maximum value of the 24 components of the measured force under various working conditions is extracted. minimum value
  • Step 5 Based on the sensitivity calculated in step 3, calculate the maximum stress of each chassis component under the actual measured road spectrum under each working condition;
  • Step 6 Calculate the yield limit of each chassis component material, and calculate the ratio of the maximum stress of each chassis component to the corresponding material yield limit under each working condition;
  • Step 7 Sort the working conditions separately for each component. By sorting the working conditions according to the maximum VonMises stress of each component in the chassis system under each working condition, we can respectively obtain the working conditions in which each component of the chassis has greater stress. We should focus on part design, fault analysis and optimization improvement. These working conditions;
  • Step 8 For each component, sort the working conditions separately based on the yield limit of the materials of each component in the chassis. According to the various parts of the chassis under each working condition, , the working conditions are sorted for each component. The relationship between the safety margins of components under different working conditions can be obtained, providing reference for component design, test plan preparation and failure analysis;
  • Step 9 Sort the components separately for each working condition. According to the maximum VonMises stress of the chassis components under each working condition, the components are sorted for each working condition, and the components with greater stress on the chassis under each working condition can be obtained;
  • Step 10 For each working condition, sort the components separately based on the yield limit of the materials of each component in the chassis. According to the various parts of the chassis under each working condition, , the components are sorted for each working condition. It can be judged whether plastic deformation occurs in each chassis component under each working condition, and the order of safety margin of each component. Provide reference for rapid component failure analysis, lightweight design, optimization and improvement;
  • Step 11 Based on the maximum VonMises stress distribution of chassis components, the maximum VonMises stress distribution of each system and subsystem that makes up the chassis.
  • step 4 also counts the minimum value, maximum value occurrence time and/or minimum value occurrence time of each load component of the six-component road force measured under each working condition;
  • Step 5 also calculates the minimum stress, maximum stress occurrence moment and/or minimum stress occurrence moment of each chassis component under the measured road spectrum under each working condition.
  • the present invention provides a computer-readable storage medium used in the steps of the method for calculating the maximum stress distribution of vehicle chassis components described in the first embodiment or the second embodiment.
  • the present invention provides a maximum stress distribution calculation system for vehicle chassis components, which can be implemented on existing hardware equipment based on computer programming technology, including:
  • a model building module which is used to build a rigid-flexible coupled multi-body dynamics model of the entire vehicle that does not include tires;
  • the constraint module is used to constrain the motion posture of the vehicle body and benchmark the rigid-flexible coupled multi-body dynamics model of the entire vehicle;
  • the sensitivity analysis module is used to perform sensitivity analysis on the six-component force load to obtain the sensitivity of the maximum stress of each chassis component to each six-component force load component;
  • the measured statistics module is used to separately count the maximum values of each load component of the six measured road forces under each working condition
  • the calculation module calculates the maximum stress of each chassis component under the measured road spectrum under various working conditions based on sensitivity
  • the statistical module is used to count the yield limits of the materials of each chassis component, and calculate the ratio of the maximum stress of each chassis component to the corresponding material yield limit under each working condition;
  • the sorting module sorts the working conditions according to the maximum stress of each component in the chassis system under each working condition
  • the components are sorted for each working condition according to the ratio of the material yield limit
  • the display module shows the distribution of the maximum VonMises stress of each system and subsystem that makes up the chassis based on the maximum VonMises stress distribution of the chassis components.
  • the measured statistics module also counts the minimum value, maximum value occurrence time and/or minimum value occurrence time of each load component of the measured six-component road force under each working condition.
  • the calculation module also calculates the minimum stress, the maximum stress occurrence moment and/or the minimum stress occurrence moment of each chassis component under the measured road spectrum under each working condition.
  • the invention provides a maximum stress distribution calculation system for vehicle chassis components, which can be based on computer programming technology.
  • Technical means can be implemented on existing hardware equipment, including:
  • a model building module which is used to construct a rigid-flexible coupled multi-body dynamics model of the entire vehicle that does not include tires.
  • the components are rigid bodies, modal flexible bodies, or finite element flexible bodies.
  • Body simplify the body into a mass point, and assign the correct parameters such as mass, center of mass coordinates, and moment of inertia.
  • Automobile chassis components are modeled using modal flexible bodies. At least the first 10 frequencies of the chassis component model are selected. The first 6 frequencies are the rigid body modes of the model, which are not considered in this invention;
  • the constraint module is used to constrain the movement posture of the vehicle body and uses a buffer member between the axle head and the ground.
  • the buffer member uses a bushing or a spring and limits the displacement stiffness range of the buffer member.
  • the displacement stiffness range of the buffer member is 0/mm ⁇ 1000N/mm;
  • the displacement stiffness range of the buffer is: the vertical stiffness range is 0N/mm ⁇ 10N/mm, the lateral stiffness range is 0N/mm ⁇ 0.5N/mm, and the longitudinal stiffness range is 0N/mm ⁇ 0.5N/mm.
  • a fixed body is used to constrain the movement of the body
  • the sensitivity analysis module is used to perform sensitivity analysis on the six-component force load to obtain the sensitivity of the maximum stress of each chassis component to each six-component force load component;
  • the vehicle has 4 axle heads, each axle head has 6 components (3 force components and 3 moment components), and there are a total of 24 load components, recorded as F ij .
  • i 1,2,3,4,5,6.
  • 1, 2, and 3 respectively represent the force components in the X, Y, and Z directions in the vehicle coordinate system
  • 4, 5, and 6 respectively represent the force components in the vehicle coordinate system.
  • the sensitivity matrix is:
  • the measured statistics module is used to separately count the maximum values of each load component of the six measured road forces under each working condition
  • the measured road spectrum collection includes k working conditions, and the working conditions are sequentially numbered 1, 2, 3,...,k; according to the time history curve of the measured road spectrum under various working conditions, the measured 24 components of the various working conditions are extracted the maximum value of minimum value
  • a calculation module that calculates the maximum stress, occurrence position and/or occurrence time of each chassis component under the measured road spectrum under various working conditions based on sensitivity
  • Step 5 Based on the sensitivity calculated in step 3, calculate the maximum stress of each chassis component under the actual measured road spectrum under each working condition;
  • the statistical module is used to count the yield limits of the materials of each chassis component, and calculate the ratio of the maximum stress of each chassis component to the corresponding material yield limit under each working condition;
  • the sorting module sorts the working conditions for each component separately.
  • the working conditions are sorted according to the maximum VonMises stress of each component in the chassis system under each working condition. The results of the larger stress in each component of the chassis can be obtained.
  • Working conditions, these working conditions should be focused on when designing parts, fault analysis and optimization improvements;
  • the sorting module sorts the working conditions for each component based on the yield limit of the materials of each component in the chassis. According to the various parts of the chassis under each working condition, , the working conditions are sorted for each component. The relationship between the safety margins of components under different working conditions can be obtained, providing reference for component design, test plan preparation and failure analysis;
  • the sorting module sorts the components separately for each working condition. According to the maximum VonMises stress of the chassis components under each working condition, the components are sorted for each working condition, and the components with greater stress on the chassis under each working condition can be obtained;
  • the sorting module sorts the components for each working condition based on the yield limit of the materials of each component in the chassis. According to the various parts of the chassis under each working condition, , the components are sorted for each working condition. It can be judged whether plastic deformation occurs in each chassis component under each working condition, and the order of safety margin of each component. Provide reference for rapid component failure analysis, lightweight design, optimization and improvement;
  • Display module which forms the maximum stress distribution of each system and subsystem of the chassis based on the maximum stress distribution of chassis components.

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Abstract

Disclosed in the present invention are a method and system for calculating maximum stress distribution of parts of a vehicle chassis, comprising: constructing a vehicle rigid-flexible coupling multi-body dynamics model; constraining the motion posture of a vehicle body; obtaining the sensitivity of the maximum stress of each part to each load component of a six-component force; collecting statistics about the maximum value, the minimum value, and occurrence time points of each load component of the six-component force of an actually measured road under each working condition; calculating the maximum stress, an occurrence position, and/or an occurrence time point of each part under an actually measured road spectrum under each working condition; calculating a ratio of the maximum stress of each part under each working condition to the yield limit of a corresponding material; sorting the working conditions according to the maximum stress of the parts; sorting the working conditions for each part according to the ratio of the yield limit of the material; sorting the parts of the chassis according to the maximum stress of the parts of the chassis under each working condition; sorting the parts for each working condition according to the ratio of yield limit of the material; and form maximum stress distribution of systems and subsystems of the chassis according to maximum stress distribution of the parts of the chassis.

Description

车辆底盘零部件最大应力分布计算方法、系统及存储介质Calculation method, system and storage medium for maximum stress distribution of vehicle chassis components 技术领域Technical field
本发明涉及交通运输领域，特别涉及一种用于各类车辆底盘零部件最大应力分布计算方法；以及，一种用于各类车辆底盘零部件最大应力分布计算系统，一种用于执行所述车辆底盘零部件最大应力分布计算方法中各步骤的计算机可读存储介质。The invention relates to the field of transportation, and in particular to a method for calculating the maximum stress distribution of chassis components of various types of vehicles; and a system for calculating the maximum stress distribution of chassis components of various types of vehicles, and a system for performing the above A computer-readable storage medium for each step in the method for calculating maximum stress distribution of vehicle chassis components.
背景技术Background technique
汽车耐久性是汽车质量好坏的重要标志之一，汽车整车耐久性试验作为验证汽车耐久性性能的重要工具，是各个厂商在验证设计阶段必做的试验之一。Car durability is one of the important indicators of car quality. As an important tool to verify the durability performance of the car, the vehicle durability test is one of the tests that every manufacturer must do during the design verification phase.
可将汽车可靠性试验分为：试验室可靠性试验、试验场可靠性试验、用户道路可靠性试验。其中试验场、用户道路可靠性试验均需采集六分力、加速度、位移、应变等试验数据，涉及的工况繁多，采集到的试验数据时间历程长。对多种工况下采集的数据进行快速准确的分析，对缩短汽车产品开发周期、减少成本尤为重要。Automobile reliability tests can be divided into: laboratory reliability tests, proving ground reliability tests, and user road reliability tests. Among them, test sites and user road reliability tests need to collect test data such as six-component force, acceleration, displacement, strain, etc., involving a wide range of working conditions, and the collected test data has a long time history. Fast and accurate analysis of data collected under various working conditions is particularly important to shorten the automotive product development cycle and reduce costs.
汽车底盘作为车辆其他各系统的安装载体，承受着各种复杂工况载荷的作用，底盘性能的好坏将直接决定整车性能的好坏。在汽车零部件设计、试验方案制定、零部件故障分析、产品改进优化等工作中，明确底盘各零部件在各种工况下的最大应力的、位置及各个零部件的危险工况是底盘设计关注的重点，它可以作为强度破坏的依据，也可为底盘的设计、优化改进提供参考。As the installation carrier for other vehicle systems, the automobile chassis is subject to loads under various complex working conditions. The performance of the chassis will directly determine the performance of the entire vehicle. In automobile parts design, test plan formulation, parts failure analysis, product improvement and optimization, etc., it is chassis design to clarify the maximum stress and location of each chassis component under various working conditions and the dangerous working conditions of each component. The focus of attention, it can be used as the basis for strength damage, and can also provide reference for the design, optimization and improvement of the chassis.
VonMises应力是用于结构失效评估的重要判据之一，多用于塑性材料，属于当量应力，是根据第四强度理论得出的。VonMises stress is one of the important criteria for structural failure assessment. It is mostly used for plastic materials and belongs to equivalent stress. It is derived based on the fourth strength theory.
主应力指的是物体内某一点以法向量为n＝(n1,n2,n3)的微面积元上剪应力为零时的法向应力。n的方向称为这一点的应力主方向。The principal stress refers to the normal stress at a certain point in the object when the shear stress is zero on the micro-area element with the normal vector n = (n1, n2, n3). The direction of n is called the principal direction of stress at this point.
剪切应力是应力的一种，定义为单位面积上所承受的剪力，力的方向与受力面的发现方向正交。Shear stress is a type of stress, defined as the shear force endured per unit area. The direction of the force is orthogonal to the direction of the force-bearing surface.
硬点，一般是指悬架中决定悬架运动学特性的点，如关键的安装点、运动铰链中心点、衬套中心点等。Hard points generally refer to points in the suspension that determine the kinematic characteristics of the suspension, such as key mounting points, moving hinge center points, bushing center points, etc.
现有技术建立整车多体动力学模型，根据多种工况下采集的实测道路谱数据，运 用虚拟迭代的方法，得到整车多体动力学模型的驱动载荷，进行动力学仿真分析。提取底盘系统零部件硬点的载荷时间历程，结合零部件单位载荷作用下的应力影响因子，进行相互相乘叠加求和计算，得到零部件在实测道路谱下的应力时间历程。The existing technology establishes a multi-body dynamics model of the vehicle, and based on the measured road spectrum data collected under various working conditions, the operation Using the virtual iteration method, the driving load of the multi-body dynamics model of the vehicle is obtained, and dynamic simulation analysis is performed. The load time history of the hard points of the chassis system components is extracted, combined with the stress influence factors of the components under the unit load, and multiplied and summed to calculate the stress time history of the components under the measured road spectrum.
现有技术组针对多种工况下实测道路谱载荷历程全时间段动力仿真分析耗时长的问题，一般对原始载荷谱进行编辑，压缩载荷时长。比较常用的方法有：从时域出发，基于损伤保留的编辑方法，将采集到的载荷在时域上等距离加窗，计算每个窗口内载荷的损伤量，删除损伤贡献较小的窗口内的信号片段，达到压缩的目的；对载荷进行时频分析，从频域识别出损伤较小的载荷循环，删除损伤贡献较小的循环，达到压缩的目的。In order to solve the problem of long time-consuming dynamic simulation analysis of the full time period of the measured road spectrum load history under various working conditions, the existing technical group generally edits the original load spectrum and compresses the load duration. The more commonly used methods are: starting from the time domain, based on the damage retention editing method, the collected loads are added to windows at equal distances in the time domain, the damage amount of the load in each window is calculated, and the windows with smaller damage contributions are deleted. signal fragments to achieve the purpose of compression; perform time-frequency analysis on the load, identify load cycles with smaller damage from the frequency domain, and delete cycles with smaller damage contribution to achieve the purpose of compression.
发明内容Contents of the invention
在发明内容部分中引入了一系列简化形式的概念,该简化形式的概念均为本领域现有技术简化，这将在具体实施方式部分中进一步详细说明。本发明的发明内容部分并不意味着要试图限定出所要求保护的技术方案的关键特征和必要技术特征，更不意味着试图确定所要求保护的技术方案的保护范围。A series of concepts in simplified form are introduced in the summary of the invention, and the concepts in the simplified form are all simplifications of the prior art in the field, which will be further described in detail in the specific embodiments. The summary of the present invention is not intended to limit the key features and necessary technical features of the claimed technical solution, nor is it intended to determine the protection scope of the claimed technical solution.
本发明要解决的技术问题是提供一种用于各类车辆底盘能快速计算多种工况下，实测道路谱载荷作用下底盘零部件最大应力及最大应力分布的车辆底盘零部件最大应力分布计算方法The technical problem to be solved by the present invention is to provide a method for calculating the maximum stress distribution of chassis components of various types of vehicle chassis that can quickly calculate the maximum stress and maximum stress distribution of chassis components under actual measured road spectrum loads under various working conditions. method
相应的，本发明还提供了一种用于执行所述车辆底盘零部件最大应力分布计算方法中各步骤的计算机可读存储介质；以及，一种用于各类车辆底盘能快速计算多种工况下，实测道路谱载荷作用下底盘零部件最大应力及最大应力分布的车辆底盘零部件最大应力分布计算系统。Correspondingly, the present invention also provides a computer-readable storage medium for executing each step in the method for calculating the maximum stress distribution of vehicle chassis components; and a computer-readable storage medium for various types of vehicle chassis that can quickly calculate a variety of tasks. The maximum stress distribution calculation system of vehicle chassis components determines the maximum stress and maximum stress distribution of chassis components under the actual measured road spectrum load.
为解决上述技术问题，本发明提供的车辆底盘零部件最大应力分布计算方法，包括以下步骤：In order to solve the above technical problems, the method for calculating the maximum stress distribution of vehicle chassis components provided by the present invention includes the following steps:
步骤1：构建不包含轮胎的整车刚柔耦合多体动力学模型；Step 1: Construct a rigid-flexible coupled multi-body dynamics model of the entire vehicle that does not include tires;
步骤2：约束车身运动姿态，对整车刚柔耦合多体动力学模型进行对标；Step 2: Constrain the motion posture of the vehicle body and benchmark the rigid-flexible coupled multi-body dynamics model of the entire vehicle;
步骤3：对六分力载荷进行灵敏度分析，得到底盘各零部件最大应力对各六分力载荷分量的灵敏度；Step 3: Conduct sensitivity analysis on the six-component force load to obtain the sensitivity of the maximum stress of each chassis component to each six-component force load component;
步骤4：分别统计各工况下实测道路六分力各载荷分量的最大值、最小值和/或出现时刻； Step 4: Count the maximum value, minimum value and/or occurrence time of each load component of the six-component road force measured under each working condition;
步骤5：根据步骤3中计算的灵敏度，计算底盘各个零部件在各工况下实测道路谱下的最大应力；Step 5: Based on the sensitivity calculated in step 3, calculate the maximum stress of each chassis component under the actual measured road spectrum under each working condition;
步骤6：统计底盘各零部件材料的屈服极限，分别计算各工况下底盘各零部件的最大应力与对应的材料屈服极限的比值；Step 6: Calculate the yield limit of each chassis component material, and calculate the ratio of the maximum stress of each chassis component to the corresponding material yield limit under each working condition;
步骤7：根据各工况下底盘系统中每个零部件最大应力的对工况进行排序；Step 7: Sort the working conditions according to the maximum stress of each component in the chassis system under each working condition;
步骤8：根据材料屈服极限的比值对每个零部件进行工况的排序；Step 8: Sort the working conditions of each component according to the ratio of material yield limit;
步骤9：根据各工况下底盘零部件的最大应力对底盘各零部件进行排序；Step 9: Sort the chassis components according to their maximum stress under each working condition;
步骤10：根据材料屈服极限的比值，对每个工况都进行零部件的排序；Step 10: Sort the components for each working condition according to the ratio of material yield limit;
步骤11：根据底盘零部件最大应力分布组成底盘的各系统、子系统的最大应力分布。Step 11: The maximum stress distribution of each system and subsystem that forms the chassis based on the maximum stress distribution of chassis components.
其中，所述的车辆底盘零部件最大应力分布计算方法，步骤4还统计各工况下实测道路六分力各载荷分量的最小值、最大值出现时刻和/或最小值出现时刻。Among them, in step 4 of the method for calculating the maximum stress distribution of vehicle chassis components, the minimum value, the time of occurrence of the maximum value and/or the time of occurrence of the minimum value of each load component of the measured six-component road force under each working condition are also calculated.
对标，是指仿真计算得到的信号(如轴头加速度、减振器位移等)与试验实测的信号进行比较，通过调整缓冲件的刚度等参数，使仿真计算的信号(如轴头加速度、减振器位移等)与试验实测的信号一致或误差在可接受范围(该范围可以根据实际需要指定)内，那么就完成了对标，确保了仿真模型的准确性。Benchmarking refers to comparing the signals calculated by simulation (such as shaft head acceleration, damper displacement, etc.) with the signals measured in the test. By adjusting the stiffness and other parameters of the buffer, the simulated signals (such as shaft head acceleration, shock absorber displacement, etc.) Damper displacement, etc.) is consistent with the measured signal in the test or the error is within an acceptable range (the range can be specified according to actual needs), then the benchmarking is completed and the accuracy of the simulation model is ensured.
其中，所述的车辆底盘零部件最大应力分布计算方法，步骤5还计算底盘各个零部件在各工况下实测道路谱下的最小应力、最大应力出现时刻和/或最小应力出现时刻。Among them, in the method for calculating the maximum stress distribution of vehicle chassis components, step 5 also calculates the minimum stress, the maximum stress occurrence moment and/or the minimum stress occurrence moment of each chassis component under the measured road spectrum under each working condition.
其中，所述的车辆底盘零部件最大应力分布计算方法，所述整车刚柔耦合多体动力学模型中，零部件采用刚体、模态柔性体或有限元柔性体。Among them, the maximum stress distribution calculation method of vehicle chassis components is described. In the rigid-flexible coupling multi-body dynamics model of the entire vehicle, the components adopt rigid bodies, modal flexible bodies or finite element flexible bodies.
其中，所述的车辆底盘零部件最大应力分布计算方法，所述整车刚柔耦合多体动力学模型至少选择底盘零部件模型的前10阶频率。Among them, in the method for calculating the maximum stress distribution of vehicle chassis components, the rigid-flexible coupling multi-body dynamics model of the entire vehicle selects at least the first 10 frequencies of the chassis component model.
其中，所述的车辆底盘零部件最大应力分布计算方法，约束车身运动姿态采用固定车身；Among them, the method for calculating the maximum stress distribution of vehicle chassis components uses a fixed body to constrain the movement posture of the vehicle body;
或，约束车身运动姿态采用轴头与地面间建立缓冲件，并限定缓冲件位移刚度范围。Or, to constrain the movement posture of the vehicle body, a buffer member is established between the axle head and the ground, and the displacement stiffness range of the buffer member is limited.
其中，所述的车辆底盘零部件最大应力分布计算方法，缓冲件位移刚度范围为0/mm～1000N/mm。 Among them, according to the maximum stress distribution calculation method of vehicle chassis components, the displacement stiffness range of the buffer is 0/mm ~ 1000N/mm.
其中，所述的车辆底盘零部件最大应力分布计算方法，缓冲件位移刚度范围是，垂向刚度范围为0N/mm～10N/mm，侧向范围为0N/mm～0.5N/mm，纵向刚度范围为0N/mm～0.5N/mm。Among them, according to the maximum stress distribution calculation method of vehicle chassis components, the displacement stiffness range of the buffer is: the vertical stiffness range is 0N/mm ~ 10N/mm, the lateral range is 0N/mm ~ 0.5N/mm, and the longitudinal stiffness range is The range is 0N/mm～0.5N/mm.
其中，所述的车辆底盘零部件最大应力分布计算方法，所述多体动力学模型进行对标包括：静平衡分析和调整模型轴荷。Among them, the method for calculating the maximum stress distribution of vehicle chassis components and the benchmarking of the multi-body dynamics model include: static balance analysis and adjustment of model axle loads.
其中，所述的车辆底盘零部件最大应力分布计算方法，所述多体动力学模型进行对标还包括：调整模型内部的弹性元件的刚度和/或阻尼参数，对减振器位移和/或轴头加速度数据进行对标，以及对系统模型进行修正。Among them, the method for calculating the maximum stress distribution of vehicle chassis components, and benchmarking the multi-body dynamics model also include: adjusting the stiffness and/or damping parameters of the elastic elements inside the model, adjusting the shock absorber displacement and/or The shaft head acceleration data is benchmarked and the system model is corrected.
其中，所述的车辆底盘零部件最大应力分布计算方法，底盘零部件最大应力至少包括VonMises应力、坐标系下沿各坐标轴方向的各个应力分量、主应力和/或剪切应力。Among them, according to the method for calculating the maximum stress distribution of vehicle chassis components, the maximum stress of chassis components at least includes VonMises stress, each stress component along each coordinate axis direction in the coordinate system, principal stress and/or shear stress.
为解决上述技术问题，本发明提供一种用上述任意一项所述车辆底盘零部件最大应力分布计算方法中步骤的计算机可读存储介质。In order to solve the above technical problems, the present invention provides a computer-readable storage medium using the steps in any one of the above methods for calculating the maximum stress distribution of vehicle chassis components.
为解决上述技术问题，本发明提供一种车辆底盘零部件最大应力分布计算系统，包括：In order to solve the above technical problems, the present invention provides a maximum stress distribution calculation system for vehicle chassis components, including:
模型构建模块，其用于构建不包含轮胎的整车刚柔耦合多体动力学模型；A model building module, which is used to build a rigid-flexible coupled multi-body dynamics model of the entire vehicle that does not include tires;
约束模块，其用于约束车身运动姿态，并对整车刚柔耦合多体动力学模型进行对标；The constraint module is used to constrain the motion posture of the vehicle body and benchmark the rigid-flexible coupled multi-body dynamics model of the entire vehicle;
灵敏度分析模块，其用于对六分力载荷进行灵敏度分析，得到底盘各零部件最大应力对各六分力载荷分量的灵敏度；The sensitivity analysis module is used to perform sensitivity analysis on the six-component force load to obtain the sensitivity of the maximum stress of each chassis component to each six-component force load component;
实测统计模块，其用于分别统计各工况下实测道路六分力各载荷分量的最大值；The measured statistics module is used to separately count the maximum values of each load component of the six measured road forces under each working condition;
计算模块，其根据灵敏度，计算底盘各个零部件在各工况下实测道路谱下的最大应力、出现位置和/或出现时刻；A calculation module that calculates the maximum stress, occurrence position and/or occurrence time of each chassis component under the measured road spectrum under various working conditions based on sensitivity;
统计模块，其用于统计底盘各零部件材料的屈服极限，分别计算各工况下底盘各零部件的最大应力与对应的材料屈服极限的比值；The statistical module is used to count the yield limits of the materials of each chassis component, and calculate the ratio of the maximum stress of each chassis component to the corresponding material yield limit under each working condition;
排序模块，其根据各工况下底盘系统中每个零部件最大应力的对工况进行排序；The sorting module sorts the working conditions according to the maximum stress of each component in the chassis system under each working condition;
根据材料屈服极限的比值对每个零部件进行工况的排序；Sort the working conditions of each component according to the ratio of material yield limit;
根据各工况下底盘零部件的最大应力对底盘各零部件进行排序；Sort the chassis components according to their maximum stress under each working condition;
根据材料屈服极限的比值对每个工况都进行零部件的排序； The components are sorted for each working condition according to the ratio of the material yield limit;
展示模块，其根据底盘零部件最大应力分布组成底盘的各系统、子系统的最大应力分布。Display module, which forms the maximum stress distribution of each system and subsystem of the chassis based on the maximum stress distribution of chassis components.
其中，所述的车辆底盘零部件最大应力分布计算系统，实测统计模块还统计各工况下实测道路六分力各载荷分量的最小值、最大值出现时刻和/或最小值出现时刻。Among them, in the vehicle chassis components maximum stress distribution calculation system, the measured statistics module also counts the minimum value, maximum value occurrence time and/or minimum value occurrence time of each load component of the six-component road force measured under various working conditions.
其中，所述的车辆底盘零部件最大应力分布计算系统，计算模块还计算底盘各个零部件在各工况下实测道路谱下的最小应力、最大应力出现时刻和/或最小应力出现时刻。Among them, the calculation module of the maximum stress distribution calculation system of vehicle chassis components also calculates the minimum stress, maximum stress occurrence moment and/or minimum stress occurrence moment of each chassis component under the measured road spectrum under various working conditions.
其中，所述的车辆底盘零部件最大应力分布计算系统，所述整车刚柔耦合多体动力学模型中，零部件采用刚体、模态柔性体或有限元柔性体。Among them, the maximum stress distribution calculation system of vehicle chassis components is described. In the rigid-flexible coupling multi-body dynamics model of the entire vehicle, the components adopt rigid bodies, modal flexible bodies or finite element flexible bodies.
其中，所述的车辆底盘零部件最大应力分布计算系统，所述整车刚柔耦合多体动力学模型中，零部件采用刚体、模态柔性体或有限元柔性体。Among them, the maximum stress distribution calculation system of vehicle chassis components is described. In the rigid-flexible coupling multi-body dynamics model of the entire vehicle, the components adopt rigid bodies, modal flexible bodies or finite element flexible bodies.
其中，所述的车辆底盘零部件最大应力分布计算系统，所述整车刚柔耦合多体动力学模型至少选择底盘零部件模型的前10阶频率。Among them, in the vehicle chassis components maximum stress distribution calculation system, the rigid-flexible coupling multi-body dynamics model of the entire vehicle selects at least the first 10 frequencies of the chassis component model.
其中，所述的车辆底盘零部件最大应力分布计算系统，约束车身运动姿态采用固定车身；Among them, the maximum stress distribution calculation system of vehicle chassis components uses a fixed body to constrain the movement posture of the vehicle body;
或，约束车身运动姿态采用轴头与地面间建立缓冲件，并限定缓冲件位移刚度范围。Or, to constrain the movement posture of the vehicle body, a buffer member is established between the axle head and the ground, and the displacement stiffness range of the buffer member is limited.
其中，所述的车辆底盘零部件最大应力分布计算系统，缓冲件位移刚度范围为0/mm～1000N/mm。Among them, the maximum stress distribution calculation system of vehicle chassis components has a buffer displacement stiffness range of 0/mm to 1000N/mm.
其中，所述的车辆底盘零部件最大应力分布计算系统，缓冲件位移刚度范围是，垂向刚度范围为0N/mm～10N/mm，侧向范围为0N/mm～0.5N/mm，纵向刚度范围为0N/mm～0.5N/mm。Among them, in the maximum stress distribution calculation system of vehicle chassis components, the displacement stiffness range of the buffer is: the vertical stiffness range is 0N/mm ~ 10N/mm, the lateral range is 0N/mm ~ 0.5N/mm, and the longitudinal stiffness range is The range is 0N/mm～0.5N/mm.
其中，所述的车辆底盘零部件最大应力分布计算系统，所述多体动力学模型进行对标包括：静平衡分析和调整模型轴荷。Among them, the vehicle chassis components maximum stress distribution calculation system, the multi-body dynamics model benchmarking includes: static balance analysis and adjustment of model axle loads.
其中，所述的车辆底盘零部件最大应力分布计算系统，所述多体动力学模型进行对标还包括：调整模型内部的弹性元件的刚度和/或阻尼参数，对减振器位移和/或轴头加速度数据进行对标，以及对系统模型进行修正。Among them, the vehicle chassis components maximum stress distribution calculation system, the multi-body dynamics model benchmarking also includes: adjusting the stiffness and/or damping parameters of the elastic elements inside the model, adjusting the shock absorber displacement and/or The shaft head acceleration data is benchmarked and the system model is corrected.
其中，所述的车辆底盘零部件最大应力分布计算系统，底盘零部件最大应力至少 包括VonMises应力、坐标系下沿各坐标轴方向的各个应力分量、主应力和/或剪切应力。Among them, the maximum stress distribution calculation system of vehicle chassis components described above has a maximum stress of at least Including VonMises stress, each stress component along each coordinate axis direction in the coordinate system, principal stress and/or shear stress.
本发明基于底盘系统考虑，计算底盘各零部件对各轮心六分力载荷分力的灵敏度，相当于对底盘系统进行一系列的单方向的静力计算，计算效率高，结果可靠。通过灵敏度，结合实测路谱中六分力载荷的最大值和最小值，通过简单的代数运算即可计算出多种工况下实测道路谱下汽车底盘各零部件的最大应力。不需要施加长时间段的实测路谱载荷驱动整车多体动力学刚柔耦合模型，降低了计算成本和时间成本。计算最大应力与零部件材料的屈服强度的比值，对零部件进行工况排序，对工况进行零部件排序，得到多种工况下底盘零部件、系统及子系统最大应力的分布规律，快速判断汽车底盘零部件各工况下发生危险的位置及安全裕度，对零部件的设计、试验方案编制、故障分析及优化改进提供参考，缩短底盘疲劳耐久开发周期。Based on the consideration of the chassis system, the present invention calculates the sensitivity of each chassis component to the six-component load component of each wheel center, which is equivalent to performing a series of unidirectional static calculations on the chassis system, with high calculation efficiency and reliable results. Through sensitivity, combined with the maximum and minimum values of the six-component force load in the measured road spectrum, the maximum stress of each component of the automobile chassis under the measured road spectrum under various working conditions can be calculated through simple algebraic operations. There is no need to apply long-term measured road spectrum loads to drive the vehicle multi-body dynamics rigid-flexible coupling model, which reduces calculation costs and time costs. Calculate the ratio of the maximum stress to the yield strength of the component material, sort the components under working conditions, sort the components under the working conditions, and obtain the distribution rules of the maximum stress of chassis components, systems and subsystems under various working conditions, quickly Determine the dangerous locations and safety margins of automobile chassis components under various working conditions, provide reference for component design, test plan preparation, fault analysis and optimization improvement, and shorten the chassis fatigue durability development cycle.
附图说明Description of drawings
本发明附图旨在示出根据本发明的特定示例性实施例中所使用的方法、结构和/或材料的一般特性，对说明书中的描述进行补充。然而，本发明附图是未按比例绘制的示意图，因而可能未能够准确反映任何所给出的实施例的精确结构或性能特点，本发明附图不应当被解释为限定或限制由根据本发明的示例性实施例所涵盖的数值或属性的范围。下面根据附图与具体实施方式对本发明作进一步详细的说明：The drawings of the present invention are intended to supplement the description in the specification by illustrating the general characteristics of methods, structures and/or materials used in certain exemplary embodiments of the invention. However, the drawings of the present invention are schematic diagrams not drawn to scale and therefore may not accurately reflect the precise structure or performance characteristics of any given embodiment. The drawings of the present invention should not be construed to limit or limit the scope of use in accordance with the present invention. The range of values or attributes covered by the exemplary embodiments. The present invention will be described in further detail below based on the accompanying drawings and specific embodiments:
图1是本发明流程示意图。Figure 1 is a schematic flow diagram of the present invention.
具体实施方式Detailed ways
以下通过特定的具体实施例说明本发明的实施方式，本领域技术人员可由本说明书所公开的内容充分地了解本发明的其他优点与技术效果。本发明还可以通过不同的具体实施方式加以实施或应用，本说明书中的各项细节也可以基于不同观点加以应用，在没有背离发明总的设计思路下进行各种修饰或改变。需说明的是，在不冲突的情况下，以下实施例及实施例中的特征可以相互组合。本发明下述示例性实施例可以多种不同的形式来实施，并且不应当被解释为只限于这里所阐述的具体实施例。应当理解的是，提供这些实施例是为了使得本发明的公开彻底且完整，并且将这些示例性具体实施例的技术方案充分传达给本领域技术人员。应当理解的是，当元件被称作“连接”或“根据”到另一元件时，该元件可以直接连接或根据到另一元件，或者可以存在中间元件。不同的是，当元件被称作“直接连接”或“直接根据”到另一元件时， 不存在中间元件。在全部附图中，相同的附图标记始终表示相同的元件。如在这里所使用的，术语“和/或”包括一个或多个相关所列项目的任意组合和所有组合。The following describes the implementation of the present invention through specific specific examples. Those skilled in the art can fully understand other advantages and technical effects of the present invention from the content disclosed in this specification. The present invention can also be implemented or applied through different specific embodiments, and various details in this specification can also be applied based on different viewpoints, and various modifications or changes can be made without departing from the general design idea of the invention. It should be noted that, as long as there is no conflict, the following embodiments and the features in the embodiments can be combined with each other. The following exemplary embodiments of the invention may be embodied in many different forms and should not be construed as limited to the specific embodiments set forth herein. It should be understood that these embodiments are provided so that this disclosure will be thorough and complete, and to fully convey the technical solutions of these exemplary specific embodiments to those skilled in the art. It will be understood that when an element is referred to as being "connected" or "connected to" another element, it can be directly connected or attached to the other element or intervening elements may be present. The difference is that when an element is said to be "directly connected" or "directly connected" to another element, There are no intermediate components. Throughout the drawings, the same reference numbers refer to the same elements. As used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items.
第一实施例；First embodiment;
本发明提供一种车辆底盘零部件最大应力分布计算方法，包括以下步骤：The invention provides a method for calculating the maximum stress distribution of vehicle chassis components, which includes the following steps:
步骤1：构建不包含轮胎的整车刚柔耦合多体动力学模型；Step 1: Construct a rigid-flexible coupled multi-body dynamics model of the entire vehicle that does not include tires;
步骤2：约束车身运动姿态，对整车刚柔耦合多体动力学模型进行对标；Step 2: Constrain the motion posture of the vehicle body and benchmark the rigid-flexible coupled multi-body dynamics model of the entire vehicle;
步骤3：对六分力载荷进行灵敏度分析，得到底盘各零部件最大应力对各六分力载荷分量的灵敏度；Step 3: Conduct sensitivity analysis on the six-component force load to obtain the sensitivity of the maximum stress of each chassis component to each six-component force load component;
步骤4：分别统计各工况下实测道路六分力各载荷分量的最大值；Step 4: Count the maximum values of each load component of the six measured road forces under each working condition;
步骤5：根据步骤3中计算的灵敏度，计算底盘各个零部件在各工况下实测道路谱下的最大应力；Step 5: Based on the sensitivity calculated in step 3, calculate the maximum stress of each chassis component under the actual measured road spectrum under each working condition;
步骤6：统计底盘各零部件材料的屈服极限，分别计算各工况下底盘各零部件的最大应力与对应的材料屈服极限的比值；Step 6: Calculate the yield limit of each chassis component material, and calculate the ratio of the maximum stress of each chassis component to the corresponding material yield limit under each working condition;
步骤7：根据各工况下底盘系统中每个零部件最大应力的对工况进行排序；Step 7: Sort the working conditions according to the maximum stress of each component in the chassis system under each working condition;
步骤8：根据材料屈服极限的比值对每个零部件进行工况的排序；Step 8: Sort the working conditions of each component according to the ratio of material yield limit;
步骤9：根据各工况下底盘零部件的最大应力对底盘各零部件进行排序；Step 9: Sort the chassis components according to their maximum stress under each working condition;
步骤10：根据材料屈服极限的比值，对每个工况都进行零部件的排序；Step 10: Sort the components for each working condition according to the ratio of material yield limit;
步骤11：根据底盘零部件最大应力分布组成底盘的各系统、子系统的最大应力分布。Step 11: The maximum stress distribution of each system and subsystem that forms the chassis based on the maximum stress distribution of chassis components.
可选择的，步骤4还统计各工况下实测道路六分力各载荷分量的最小值、最大值出现时刻和/或最小值出现时刻；Optionally, step 4 also counts the minimum value, maximum value occurrence time and/or minimum value occurrence time of each load component of the six-component road force measured under each working condition;
步骤5还计算底盘各个零部件在各工况下实测道路谱下的最小应力、最大应力出现时刻和/或最小应力出现时刻。Step 5 also calculates the minimum stress, maximum stress occurrence moment and/or minimum stress occurrence moment of each chassis component under the measured road spectrum under each working condition.
第二实施例；Second embodiment;
本发明提供一种车辆底盘零部件最大应力分布计算方法，包括以下步骤：The invention provides a method for calculating the maximum stress distribution of vehicle chassis components, which includes the following steps:
步骤1：构建不包含轮胎的整车刚柔耦合多体动力学模型，所述整车刚柔耦合多体动力学模型中，零部件采用刚体、模态柔性体或有限元柔性体；将车身简化为质量 点，赋予正确的质量、质心坐标及转动惯量等参数。汽车底盘零部件采用模态柔性体建模，至少选择底盘零部件模型的前10阶频率，前6阶为模型的刚体模态，本发明不予考虑；Step 1: Construct a rigid-flexible coupled multi-body dynamics model of the entire vehicle that does not include tires. In the rigid-flexible coupled multi-body dynamics model of the entire vehicle, the components are rigid bodies, modal flexible bodies or finite element flexible bodies; the body is reduced to quality point, giving the correct parameters such as mass, center of mass coordinates, and moment of inertia. Automobile chassis components are modeled using modal flexible bodies. At least the first 10 frequencies of the chassis component model are selected. The first 6 frequencies are the rigid body modes of the model, which are not considered in this invention;
步骤2：约束车身运动姿态采用轴头与地面间建立缓冲件，缓冲件采用衬套或弹簧，并限定缓冲件位移刚度范围，缓冲件位移刚度范围为0/mm～1000N/mm；优选的，缓冲件位移刚度范围是，垂向刚度范围为0N/mm～10N/mm，侧向范围为0N/mm～0.5N/mm，纵向刚度范围为0N/mm～0.5N/mm，对多体动力学模型进行静平衡分析，校核轴荷，根据采集的路谱数据，对轴头加速度、减振器位移进行对标，确保多体模型的准确性；Step 2: To constrain the movement posture of the vehicle body, a buffer member is established between the axle head and the ground. The buffer member uses a bushing or a spring, and limits the displacement stiffness range of the buffer member. The displacement stiffness range of the buffer member is 0/mm ~ 1000N/mm; preferably, The displacement stiffness range of the buffer is: the vertical stiffness range is 0N/mm~10N/mm, the lateral stiffness range is 0N/mm~0.5N/mm, and the longitudinal stiffness range is 0N/mm~0.5N/mm. For multi-body dynamic Conduct static balance analysis on the learning model, check the axle load, and benchmark the axle head acceleration and shock absorber displacement based on the collected road spectrum data to ensure the accuracy of the multi-body model;
或，约束车身运动姿态采用固定车身；Or, a fixed body is used to constrain the movement of the body;
步骤3：对六分力载荷进行灵敏度分析，得到底盘各零部件最大应力对各六分力载荷分量的灵敏度；Step 3: Conduct sensitivity analysis on the six-component force load to obtain the sensitivity of the maximum stress of each chassis component to each six-component force load component;
车辆有4个轴头，每个轴头有6个分力(3个力分量和3个力矩分量)，共有24个载荷分量，记为Fij。其中：i＝1,2,3,4,5,6。1、2、3分别表示整车坐标系下X、Y、Z方向的力分量，4、5、6分别表示整车坐标系下X、Y、Z方向的力矩分量；j＝1,2,3,4分别代表左前轮、右前轮、左后轮、右后轮六分力；The vehicle has 4 axle heads, each axle head has 6 components (3 force components and 3 moment components), and there are a total of 24 load components, recorded as F ij . Among them: i=1,2,3,4,5,6. 1, 2, and 3 respectively represent the force components in the X, Y, and Z directions in the vehicle coordinate system, and 4, 5, and 6 respectively represent the force components in the vehicle coordinate system. Moment components in the X, Y, and Z directions; j=1, 2, 3, and 4 respectively represent the six components of the left front wheel, right front wheel, left rear wheel, and right rear wheel;
对轮心六分力载荷进行灵敏度分析。假设底盘共有n个零部件组成，零部件依次编号为1,2,3,…，n。在轴头分别依次施加24个载荷分量，力分量均为F0，力矩分量为M0，对整车多体动力模型进行仿真分析，仿真时间5s，分析步取100步，分析结果稳定后，分别得到底盘各零部件的最大VonMises应力矩阵表示载荷分量Fij单独作用下，编号为m的零部件的最大VonMises。其中：m＝1,2,…,n代表底盘零部件的编号；Sensitivity analysis was performed on the wheel center six-component force load. Assume that the chassis consists of n parts, and the parts are numbered 1, 2, 3,..., n. 24 load components are applied to the axle head in sequence. The force component is F 0 and the moment component is M 0 . The multi-body dynamic model of the vehicle is simulated and analyzed. The simulation time is 5 seconds and the analysis step is 100 steps. After the analysis results are stable, Obtain the maximum VonMises stress matrix of each component of the chassis respectively. Indicates the maximum VonMises of the component numbered m under the action of load component F ij alone. Among them: m=1,2,…,n represents the number of chassis parts;
在轴头分别依次施加24个载荷分量，力分量的均为F1＝F0+ΔF，力矩分量为M1＝M0+ΔM，对整车多体动力模型进行仿真分析，仿真时间5s，分析步取100步，分析结果稳定后，分别得到底盘各零部件的最大VonMises应力矩阵为 24 load components are applied to the shaft head in sequence. The force components are all F 1 =F 0 +ΔF, and the moment components are M 1 =M 0 +ΔM. Simulation analysis is performed on the multi-body dynamic model of the entire vehicle. The simulation time is 5 seconds. The analysis steps are 100. After the analysis results are stable, the maximum VonMises stress matrix of each chassis component is obtained:
计算底盘零部件对六分力载荷的灵敏度，灵敏度矩阵为：
Calculate the sensitivity of chassis components to six-component force loads. The sensitivity matrix is:
步骤4：分别统计各工况下实测道路六分力各载荷分量的最大值；Step 4: Count the maximum values of each load component of the six measured road forces under each working condition;
示例性，实测道路谱采集包含k种工况，工况依次编号为1,2,3,…,k。根据各种工况实测道路谱的时间历程曲线，提取各种工况实测24分力的最大值最小值 For example, the measured road spectrum collection includes k working conditions, and the working conditions are sequentially numbered 1, 2, 3,...,k. According to the time history curve of the measured road spectrum under various working conditions, the maximum value of the 24 components of the measured force under various working conditions is extracted. minimum value
步骤5：根据步骤3中计算的灵敏度，计算底盘各个零部件在各工况下实测道路谱下的最大应力；Step 5: Based on the sensitivity calculated in step 3, calculate the maximum stress of each chassis component under the actual measured road spectrum under each working condition;
根据灵敏度计算底盘零部件在各种工况下实测道路谱下的最大VonMises应力：
Calculate the maximum VonMises stress of chassis components under the measured road spectrum under various working conditions based on the sensitivity:
各工况实测道路谱作用下底盘中编号为m的零部件的最大VonMises应力计算如下：
The maximum VonMises stress of the component numbered m in the chassis under the actual measured road spectrum under each working condition is calculated as follows:
其中m＝1,2,…,n代表底盘零部件的编号,p＝1,2,3,…,k代表工况编号；Among them, m=1,2,…,n represents the number of chassis parts, p=1,2,3,…,k represents the working condition number;
步骤6：统计底盘各零部件材料的屈服极限，分别计算各工况下底盘各零部件的最大应力与对应的材料屈服极限的比值；Step 6: Calculate the yield limit of each chassis component material, and calculate the ratio of the maximum stress of each chassis component to the corresponding material yield limit under each working condition;
统计底盘各零部件材料的屈服极限，记底盘中编号为m的零部件材料的屈服极限为各工况下底盘中编号为m的零部件的最大VonMises应力与屈服极限的比值计算如下：
Calculate the yield limit of each component material of the chassis. Record the yield limit of the component material numbered m in the chassis as The ratio of the maximum VonMises stress to the yield limit of the component numbered m in the chassis under each working condition is calculated as follows:
表示编号为m的零部件在编号为p的工况下处于弹性范围； It means that the component numbered m is in the elastic range under the working condition numbered p;
表示编号为m的零部件在编号为p的工况下最大VonMises应力超过屈服极限，发生塑性变形； It means that the maximum VonMises stress of the component numbered under the working condition numbered exceeds the yield limit and plastic deformation occurs;
步骤7：对每个零部件，分别进行工况的排序。根据各工况下底盘系统中各个零部件的最大VonMises应力的对工况进行排序，可分别得到底盘各个零部件出现较大应力的工况，对零件设计、故障分析及优化改进时应重点关注这些工况；Step 7: Sort the working conditions separately for each component. By sorting the working conditions according to the maximum VonMises stress of each component in the chassis system under each working condition, we can respectively obtain the working conditions in which each component of the chassis has greater stress. We should focus on part design, fault analysis and optimization improvement. These working conditions;
步骤8：对每个零部件，结合底盘中各零部件材料的屈服极限，分别进行工况的排序。根据求出的各工况下底盘各零部件的，对每个零部件都进行工况的排序。可得到零部件不同工况下安全裕度的关系，为零部件的设计、试验方案编制及故障分析提供参考；Step 8: For each component, sort the working conditions separately based on the yield limit of the materials of each component in the chassis. According to the various parts of the chassis under each working condition, , the working conditions are sorted for each component. The relationship between the safety margins of components under different working conditions can be obtained, providing reference for component design, test plan preparation and failure analysis;
步骤9：对每种工况，分别进行零部件的排序。根据各工况下底盘零部件的最大VonMises应力，对每个工况都进行零部件的排序，可得到各个工况下底盘出现较大应力的零部件；Step 9: Sort the components separately for each working condition. According to the maximum VonMises stress of the chassis components under each working condition, the components are sorted for each working condition, and the components with greater stress on the chassis under each working condition can be obtained;
步骤10：对每种工况，结合底盘中各零部件材料的屈服极限，分别进行零部件的排序。根据求出的各工况下底盘各零部件的，对每个工况都进行零部件的排序。可以判断各工况下底盘各零部件是否发生塑性变形，以及各零部件安全裕度的排序。对快速进行零部件故障分析、轻量化设计、优化改进提供参考；Step 10: For each working condition, sort the components separately based on the yield limit of the materials of each component in the chassis. According to the various parts of the chassis under each working condition, , the components are sorted for each working condition. It can be judged whether plastic deformation occurs in each chassis component under each working condition, and the order of safety margin of each component. Provide reference for rapid component failure analysis, lightweight design, optimization and improvement;
步骤11：在底盘零部件最大VonMises应力分布的基础上，组成底盘的各系统及子系统的最大VonMises应力的分布。Step 11: Based on the maximum VonMises stress distribution of chassis components, the maximum VonMises stress distribution of each system and subsystem that makes up the chassis.
可选择的，步骤4还统计各工况下实测道路六分力各载荷分量的最小值、最大值出现时刻和/或最小值出现时刻；Optionally, step 4 also counts the minimum value, maximum value occurrence time and/or minimum value occurrence time of each load component of the six-component road force measured under each working condition;
步骤5还计算底盘各个零部件在各工况下实测道路谱下的最小应力、最大应力出现时刻和/或最小应力出现时刻。Step 5 also calculates the minimum stress, maximum stress occurrence moment and/or minimum stress occurrence moment of each chassis component under the measured road spectrum under each working condition.
第三实施例； Third embodiment;
本发明提供一种用于上述第一实施例或第二实施例所述车辆底盘零部件最大应力分布计算方法中步骤的计算机可读存储介质。The present invention provides a computer-readable storage medium used in the steps of the method for calculating the maximum stress distribution of vehicle chassis components described in the first embodiment or the second embodiment.
第四实施例；Fourth embodiment;
本发明提供一种车辆底盘零部件最大应力分布计算系统，其能基于计算机编程技术手段在现有硬件设备上能实现，包括：The present invention provides a maximum stress distribution calculation system for vehicle chassis components, which can be implemented on existing hardware equipment based on computer programming technology, including:
模型构建模块，其用于构建不包含轮胎的整车刚柔耦合多体动力学模型；A model building module, which is used to build a rigid-flexible coupled multi-body dynamics model of the entire vehicle that does not include tires;
约束模块，其用于约束车身运动姿态，并对整车刚柔耦合多体动力学模型进行对标；The constraint module is used to constrain the motion posture of the vehicle body and benchmark the rigid-flexible coupled multi-body dynamics model of the entire vehicle;
灵敏度分析模块，其用于对六分力载荷进行灵敏度分析，得到底盘各零部件最大应力对各六分力载荷分量的灵敏度；The sensitivity analysis module is used to perform sensitivity analysis on the six-component force load to obtain the sensitivity of the maximum stress of each chassis component to each six-component force load component;
实测统计模块，其用于分别统计各工况下实测道路六分力各载荷分量的最大值；The measured statistics module is used to separately count the maximum values of each load component of the six measured road forces under each working condition;
计算模块，其根据灵敏度，计算底盘各个零部件在各工况下实测道路谱下的最大应力；The calculation module calculates the maximum stress of each chassis component under the measured road spectrum under various working conditions based on sensitivity;
统计模块，其用于统计底盘各零部件材料的屈服极限，分别计算各工况下底盘各零部件的最大应力与对应的材料屈服极限的比值；The statistical module is used to count the yield limits of the materials of each chassis component, and calculate the ratio of the maximum stress of each chassis component to the corresponding material yield limit under each working condition;
排序模块，其根据各工况下底盘系统中每个零部件最大应力的对工况进行排序；The sorting module sorts the working conditions according to the maximum stress of each component in the chassis system under each working condition;
根据材料屈服极限的比值对每个零部件进行工况的排序；Sort the working conditions of each component according to the ratio of material yield limit;
根据各工况下底盘零部件的最大应力对底盘各零部件进行排序；Sort the chassis components according to their maximum stress under each working condition;
根据材料屈服极限的比值对每个工况都进行零部件的排序；The components are sorted for each working condition according to the ratio of the material yield limit;
展示模块，其根据底盘零部件最大VonMises应力分布的基础上，组成底盘的各系统及子系统的最大VonMises应力的分布。The display module shows the distribution of the maximum VonMises stress of each system and subsystem that makes up the chassis based on the maximum VonMises stress distribution of the chassis components.
可选择的，所述的车辆底盘零部件最大应力分布计算系统，实测统计模块还统计各工况下实测道路六分力各载荷分量的最小值、最大值出现时刻和/或最小值出现时刻。Optionally, in the vehicle chassis components maximum stress distribution calculation system, the measured statistics module also counts the minimum value, maximum value occurrence time and/or minimum value occurrence time of each load component of the measured six-component road force under each working condition.
可选择的，所述的车辆底盘零部件最大应力分布计算系统，计算模块还计算底盘各个零部件在各工况下实测道路谱下的最小应力、最大应力出现时刻和/或最小应力出现时刻。Optionally, in the vehicle chassis components maximum stress distribution calculation system, the calculation module also calculates the minimum stress, the maximum stress occurrence moment and/or the minimum stress occurrence moment of each chassis component under the measured road spectrum under each working condition.
第五实施例；Fifth embodiment;
本发明提供一种车辆底盘零部件最大应力分布计算系统，其能基于计算机编程技 术手段在现有硬件设备上能实现，包括：The invention provides a maximum stress distribution calculation system for vehicle chassis components, which can be based on computer programming technology. Technical means can be implemented on existing hardware equipment, including:
模型构建模块，其用于构建不包含轮胎的整车刚柔耦合多体动力学模型，所述整车刚柔耦合多体动力学模型中，零部件采用刚体、模态柔性体或有限元柔性体；将车身简化为质量点，赋予正确的质量、质心坐标及转动惯量等参数。汽车底盘零部件采用模态柔性体建模，至少选择底盘零部件模型的前10阶频率，前6阶为模型的刚体模态，本发明不予考虑；A model building module, which is used to construct a rigid-flexible coupled multi-body dynamics model of the entire vehicle that does not include tires. In the rigid-flexible coupled multi-body dynamics model of the entire vehicle, the components are rigid bodies, modal flexible bodies, or finite element flexible bodies. Body; simplify the body into a mass point, and assign the correct parameters such as mass, center of mass coordinates, and moment of inertia. Automobile chassis components are modeled using modal flexible bodies. At least the first 10 frequencies of the chassis component model are selected. The first 6 frequencies are the rigid body modes of the model, which are not considered in this invention;
约束模块，其用于约束车身运动姿态采用轴头与地面间建立缓冲件，缓冲件采用衬套或弹簧，并限定缓冲件位移刚度范围，缓冲件位移刚度范围为0/mm～1000N/mm；优选的，缓冲件位移刚度范围是，垂向刚度范围为0N/mm～10N/mm，侧向范围为0N/mm～0.5N/mm，纵向刚度范围为0N/mm～0.5N/mm，对多体动力学模型进行静平衡分析，校核轴荷，根据采集的路谱数据，对轴头加速度、减振器位移进行对标，确保多体模型的准确性；The constraint module is used to constrain the movement posture of the vehicle body and uses a buffer member between the axle head and the ground. The buffer member uses a bushing or a spring and limits the displacement stiffness range of the buffer member. The displacement stiffness range of the buffer member is 0/mm ~ 1000N/mm; Preferably, the displacement stiffness range of the buffer is: the vertical stiffness range is 0N/mm~10N/mm, the lateral stiffness range is 0N/mm~0.5N/mm, and the longitudinal stiffness range is 0N/mm~0.5N/mm. Perform static balance analysis on the multi-body dynamic model, check the axle load, and benchmark the axle head acceleration and shock absorber displacement based on the collected road spectrum data to ensure the accuracy of the multi-body model;
或，约束车身运动姿态采用固定车身；Or, a fixed body is used to constrain the movement of the body;
灵敏度分析模块，其用于对六分力载荷进行灵敏度分析，得到底盘各零部件最大应力对各六分力载荷分量的灵敏度；The sensitivity analysis module is used to perform sensitivity analysis on the six-component force load to obtain the sensitivity of the maximum stress of each chassis component to each six-component force load component;
车辆有4个轴头，每个轴头有6个分力(3个力分量和3个力矩分量)，共有24个载荷分量，记为Fij。其中：i＝1,2,3,4,5,6。1、2、3分别表示整车坐标系下X、Y、Z方向的力分量，4、5、6分别表示整车坐标系下X、Y、Z方向的力矩分量；j＝1,2,3,4分别代表左前轮、右前轮、左后轮、右后轮六分力；The vehicle has 4 axle heads, each axle head has 6 components (3 force components and 3 moment components), and there are a total of 24 load components, recorded as F ij . Among them: i=1,2,3,4,5,6. 1, 2, and 3 respectively represent the force components in the X, Y, and Z directions in the vehicle coordinate system, and 4, 5, and 6 respectively represent the force components in the vehicle coordinate system. Moment components in the X, Y, and Z directions; j=1, 2, 3, and 4 respectively represent the six components of the left front wheel, right front wheel, left rear wheel, and right rear wheel;
对轮心六分力载荷进行灵敏度分析。假设底盘共有n个零部件组成，零部件依次编号为1,2,3,…，n。在轴头分别依次施加24个载荷分量，力分量均为F0，力矩分量为M0，对整车多体动力模型进行仿真分析，仿真时间5s，分析步取100步，分析结果稳定后，分别得到底盘各零部件的最大VonMises应力矩阵表示载荷分量Fij单独作用下，编号为m的零部件的最大VonMises。其中：m＝1,2,…,n代表底盘零部件的编号；Sensitivity analysis was performed on the wheel center six-component force load. Assume that the chassis consists of n parts, and the parts are numbered 1, 2, 3,..., n. 24 load components are applied to the axle head in sequence. The force component is F 0 and the moment component is M 0 . The multi-body dynamic model of the vehicle is simulated and analyzed. The simulation time is 5 seconds and the analysis step is 100 steps. After the analysis results are stable, Obtain the maximum VonMises stress matrix of each component of the chassis respectively. Indicates the maximum VonMises of the component numbered m under the action of load component F ij alone. Among them: m=1,2,…,n represents the number of chassis parts;
在轴头分别依次施加24个载荷分量，力分量的均为F1＝F0+ΔF，力矩分量为 M1＝M0+ΔM，对整车多体动力模型进行仿真分析，仿真时间5s，分析步取100步，分析结果稳定后，分别得到底盘各零部件的最大VonMises应力矩阵为 24 load components are applied sequentially to the shaft head. The force components are all F 1 =F 0 +ΔF, and the moment components are M 1 = M 0 + ΔM, conduct simulation analysis on the multi-body dynamic model of the vehicle, the simulation time is 5 seconds, and the analysis steps are 100 steps. After the analysis results are stable, the maximum VonMises stress matrix of each chassis component is obtained:
计算底盘零部件对六分力载荷的灵敏度，灵敏度矩阵为：
Calculate the sensitivity of chassis components to six-component force loads. The sensitivity matrix is:
实测统计模块，其用于分别统计各工况下实测道路六分力各载荷分量的最大值；The measured statistics module is used to separately count the maximum values of each load component of the six measured road forces under each working condition;
示例性，实测道路谱采集包含k种工况，工况依次编号为1,2,3,…,k；根据各种工况实测道路谱的时间历程曲线，提取各种工况实测24分力的最大值最小值 For example, the measured road spectrum collection includes k working conditions, and the working conditions are sequentially numbered 1, 2, 3,...,k; according to the time history curve of the measured road spectrum under various working conditions, the measured 24 components of the various working conditions are extracted the maximum value of minimum value
计算模块，其根据灵敏度，计算底盘各个零部件在各工况下实测道路谱下的最大应力、出现位置和/或出现时刻；A calculation module that calculates the maximum stress, occurrence position and/or occurrence time of each chassis component under the measured road spectrum under various working conditions based on sensitivity;
步骤5：根据步骤3中计算的灵敏度，计算底盘各个零部件在各工况下实测道路谱下的最大应力；Step 5: Based on the sensitivity calculated in step 3, calculate the maximum stress of each chassis component under the actual measured road spectrum under each working condition;
根据灵敏度计算底盘零部件在各种工况下实测道路谱下的最大VonMises应力：
Calculate the maximum VonMises stress of chassis components under the measured road spectrum under various working conditions based on the sensitivity:
各工况实测道路谱作用下底盘中编号为m的零部件的最大VonMises应力计算如下：
The maximum VonMises stress of the component numbered m in the chassis under the measured road spectrum under each working condition is calculated as follows:
其中m＝1,2,…,n代表底盘零部件的编号,p＝1,2,3,…,k代表工况编号；Among them, m=1,2,…,n represents the number of chassis parts, p=1,2,3,…,k represents the working condition number;
统计模块，其用于统计底盘各零部件材料的屈服极限，分别计算各工况下底盘各零部件的最大应力与对应的材料屈服极限的比值；The statistical module is used to count the yield limits of the materials of each chassis component, and calculate the ratio of the maximum stress of each chassis component to the corresponding material yield limit under each working condition;
统计底盘各零部件材料的屈服极限，记底盘中编号为m的零部件材料的屈服极限 为各工况下底盘中编号为m的零部件的最大VonMises应力与屈服极限的比值计算如下：
Calculate the yield limit of each component material of the chassis, and record the yield limit of the component material numbered m in the chassis. for The ratio of the maximum VonMises stress to the yield limit of the component numbered m in the chassis under each working condition is calculated as follows:
表示编号为m的零部件在编号为p的工况下处于弹性范围； It means that the component numbered m is in the elastic range under the working condition numbered p;
表示编号为m的零部件在编号为p的工况下最大VonMises应力超过屈服极限，发生塑性变形； It means that the maximum VonMises stress of the component numbered under the working condition numbered exceeds the yield limit and plastic deformation occurs;
排序模块，对每个零部件，分别进行工况的排序，根据各工况下底盘系统中各个零部件的最大VonMises应力的对工况进行排序，可分别得到底盘各个零部件出现较大应力的工况，对零件设计、故障分析及优化改进时应重点关注这些工况；The sorting module sorts the working conditions for each component separately. The working conditions are sorted according to the maximum VonMises stress of each component in the chassis system under each working condition. The results of the larger stress in each component of the chassis can be obtained. Working conditions, these working conditions should be focused on when designing parts, fault analysis and optimization improvements;
排序模块，对每个零部件，结合底盘中各零部件材料的屈服极限，分别进行工况的排序。根据求出的各工况下底盘各零部件的，对每个零部件都进行工况的排序。可得到零部件不同工况下安全裕度的关系，为零部件的设计、试验方案编制及故障分析提供参考；The sorting module sorts the working conditions for each component based on the yield limit of the materials of each component in the chassis. According to the various parts of the chassis under each working condition, , the working conditions are sorted for each component. The relationship between the safety margins of components under different working conditions can be obtained, providing reference for component design, test plan preparation and failure analysis;
排序模块，对每种工况，分别进行零部件的排序。根据各工况下底盘零部件的最大VonMises应力，对每个工况都进行零部件的排序，可得到各个工况下底盘出现较大应力的零部件；The sorting module sorts the components separately for each working condition. According to the maximum VonMises stress of the chassis components under each working condition, the components are sorted for each working condition, and the components with greater stress on the chassis under each working condition can be obtained;
排序模块，对每种工况，结合底盘中各零部件材料的屈服极限，分别进行零部件的排序。根据求出的各工况下底盘各零部件的，对每个工况都进行零部件的排序。可以判断各工况下底盘各零部件是否发生塑性变形，以及各零部件安全裕度的排序。对快速进行零部件故障分析、轻量化设计、优化改进提供参考；The sorting module sorts the components for each working condition based on the yield limit of the materials of each component in the chassis. According to the various parts of the chassis under each working condition, , the components are sorted for each working condition. It can be judged whether plastic deformation occurs in each chassis component under each working condition, and the order of safety margin of each component. Provide reference for rapid component failure analysis, lightweight design, optimization and improvement;
展示模块，其根据底盘零部件最大应力分布组成底盘的各系统、子系统的最大应力分布。Display module, which forms the maximum stress distribution of each system and subsystem of the chassis based on the maximum stress distribution of chassis components.
除非另有定义，否则这里所使用的全部术语(包括技术术语和科学术语)都具有与本发明所属领域的普通技术人员通常理解的意思相同的意思。还将理解的是，除非这里明确定义，否则诸如在通用字典中定义的术语这类术语应当被解释为具有与它们 在相关领域语境中的意思相一致的意思，而不以理想的或过于正式的含义加以解释。Unless otherwise defined, all terms (including technical and scientific terms) used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. It will also be understood that, unless expressly defined herein, such terms such as those defined in a general dictionary shall be construed to have the same meaning as they do A meaning that is consistent with the meaning in the context of the relevant field and is not interpreted in an ideal or overly formal sense.
以上通过具体实施方式和实施例对本发明进行了详细的说明，但这些并非构成对本发明的限制。在不脱离本发明原理的情况下，本领域的技术人员还可做出许多变形和改进，这些也应视为本发明的保护范围。 The present invention has been described in detail through specific embodiments and examples, but these do not constitute limitations to the present invention. Without departing from the principle of the present invention, those skilled in the art can also make many modifications and improvements, which should also be regarded as the protection scope of the present invention.

Claims (24)

  1. 一种车辆底盘零部件最大应力分布计算方法，其特征在于，包括以下步骤：A method for calculating the maximum stress distribution of vehicle chassis components, which is characterized by including the following steps:
    步骤1：构建不包含轮胎的整车刚柔耦合多体动力学模型；Step 1: Construct a rigid-flexible coupled multi-body dynamics model of the entire vehicle that does not include tires;
    步骤2：约束车身运动姿态，对整车刚柔耦合多体动力学模型进行对标；Step 2: Constrain the motion posture of the vehicle body and benchmark the rigid-flexible coupled multi-body dynamics model of the entire vehicle;
    步骤3：对六分力载荷进行灵敏度分析，得到底盘各零部件最大应力对各六分力载荷分量的灵敏度；Step 3: Conduct sensitivity analysis on the six-component force load to obtain the sensitivity of the maximum stress of each chassis component to each six-component force load component;
    步骤4：分别统计各工况下实测道路六分力各载荷分量的最大值；Step 4: Count the maximum values of each load component of the six measured road forces under each working condition;
    步骤5：根据步骤3中计算的灵敏度，计算底盘各个零部件在各工况下实测道路谱下的最大应力；Step 5: Based on the sensitivity calculated in step 3, calculate the maximum stress of each chassis component under the actual measured road spectrum under each working condition;
    步骤6：统计底盘各零部件材料的屈服极限，分别计算各工况下底盘各零部件的最大应力与对应的材料屈服极限的比值；Step 6: Calculate the yield limit of each chassis component material, and calculate the ratio of the maximum stress of each chassis component to the corresponding material yield limit under each working condition;
    步骤7：根据各工况下底盘系统中每个零部件最大应力的对工况进行排序；Step 7: Sort the working conditions according to the maximum stress of each component in the chassis system under each working condition;
    步骤8：根据材料屈服极限的比值对每个零部件进行工况的排序；Step 8: Sort the working conditions of each component according to the ratio of material yield limit;
    步骤9：根据各工况下底盘零部件的最大应力对底盘各零部件进行排序；Step 9: Sort the chassis components according to their maximum stress under each working condition;
    步骤10：根据材料屈服极限的比值，对每个工况都进行零部件的排序；Step 10: Sort the components for each working condition according to the ratio of material yield limit;
    步骤11：根据底盘零部件最大应力分布组成底盘的各系统、子系统的最大应力分布。Step 11: The maximum stress distribution of each system and subsystem that forms the chassis based on the maximum stress distribution of chassis components.
  2. 如权利要求1所述的车辆底盘零部件最大应力分布计算方法，其特征在于：步骤4还统计各工况下实测道路六分力各载荷分量的最小值、最大值出现时刻和/或最小值出现时刻。The method for calculating the maximum stress distribution of vehicle chassis components according to claim 1, characterized in that step 4 also counts the minimum value, maximum occurrence time and/or minimum value of each load component of the measured six-component road force under each working condition. A moment of emergence.
  3. 如权利要求1所述的车辆底盘零部件最大应力分布计算方法，其特征在于：步骤5还计算底盘各个零部件在各工况下实测道路谱下的最小应力、最大应力出现时刻和/或最小应力出现时刻。The method for calculating the maximum stress distribution of vehicle chassis components according to claim 1, characterized in that step 5 also calculates the minimum stress, maximum stress occurrence time and/or minimum stress of each chassis component under the measured road spectrum under each working condition. moment of stress.
  4. 如权利要求1所述的车辆底盘零部件最大应力分布计算方法，其特征在于：所述整车刚柔耦合多体动力学模型中，零部件采用刚体、模态柔性体或有限元柔性体。The method for calculating the maximum stress distribution of vehicle chassis components according to claim 1, characterized in that in the rigid-flexible coupled multi-body dynamics model of the entire vehicle, the components adopt rigid bodies, modal flexible bodies or finite element flexible bodies.
  5. 如权利要求4所述的车辆底盘零部件最大应力分布计算方法，其特征在于：所述整车刚柔耦合多体动力学模型至少选择底盘零部件模型的前10阶频率。The method for calculating the maximum stress distribution of vehicle chassis components according to claim 4, characterized in that: the rigid-flexible coupled multi-body dynamics model of the entire vehicle selects at least the first 10 frequencies of the chassis component model.
  6. 如权利要求1所述的车辆底盘零部件最大应力分布计算方法，其特征在于：约 束车身运动姿态采用固定车身；The method for calculating the maximum stress distribution of vehicle chassis components according to claim 1, characterized in that: approximately The fixed body is used to bundle the body's movement posture;
    或，约束车身运动姿态采用轴头与地面间建立缓冲件，并限定缓冲件位移刚度范围。Or, to constrain the movement posture of the vehicle body, a buffer member is established between the axle head and the ground, and the displacement stiffness range of the buffer member is limited.
  7. 如权利要求6所述的车辆底盘零部件最大应力分布计算方法，其特征在于：缓冲件位移刚度范围为0/mm～1000N/mm。The method for calculating the maximum stress distribution of vehicle chassis components according to claim 6, wherein the displacement stiffness of the buffer member ranges from 0/mm to 1000N/mm.
  8. 如权利要求7所述的车辆底盘零部件最大应力分布计算方法，其特征在于：缓冲件位移刚度范围是，垂向刚度范围为0N/mm～10N/mm，侧向范围为0N/mm～0.5N/mm，纵向刚度范围为0N/mm～0.5N/mm。The method for calculating the maximum stress distribution of vehicle chassis components according to claim 7, characterized in that: the displacement stiffness range of the buffer is: the vertical stiffness range is 0N/mm～10N/mm, and the lateral stiffness range is 0N/mm～0.5 N/mm, the longitudinal stiffness range is 0N/mm~0.5N/mm.
  9. 如权利要求1所述的车辆底盘零部件最大应力分布计算方法，其特征在于：所述多体动力学模型进行对标包括：静平衡分析和调整模型轴荷。The method for calculating the maximum stress distribution of vehicle chassis components according to claim 1, wherein the benchmarking of the multi-body dynamics model includes static balance analysis and adjustment of model axle loads.
  10. 如权利要求9所述的车辆底盘零部件最大应力分布计算方法，其特征在于：所述多体动力学模型进行对标还包括：调整模型内部的弹性元件的刚度和/或阻尼参数，对减振器位移和/或轴头加速度数据进行对标，以及对系统模型进行修正。The method for calculating maximum stress distribution of vehicle chassis components according to claim 9, characterized in that: benchmarking the multi-body dynamics model further includes: adjusting the stiffness and/or damping parameters of the elastic elements inside the model, and reducing the The vibrator displacement and/or shaft head acceleration data are benchmarked, and the system model is corrected.
  11. 如权利要求1所述的车辆底盘零部件最大应力分布计算方法，其特征在于：底盘零部件最大应力至少包括VonMises应力、坐标系下沿各坐标轴方向的各个应力分量、主应力和/或剪切应力。The method for calculating maximum stress distribution of vehicle chassis components according to claim 1, characterized in that: the maximum stress of chassis components at least includes VonMises stress, each stress component along each coordinate axis direction in the coordinate system, principal stress and/or shear Shear stress.
  12. 一种用于执行权利要求1-11任意一项所述车辆底盘零部件最大应力分布计算方法中步骤的计算机可读存储介质。A computer-readable storage medium for performing the steps in the method for calculating the maximum stress distribution of vehicle chassis components according to any one of claims 1-11.
  13. 一种车辆底盘零部件最大应力分布计算系统，其特征在于，包括：A maximum stress distribution calculation system for vehicle chassis components, which is characterized by including:
    模型构建模块，其用于构建不包含轮胎的整车刚柔耦合多体动力学模型；A model building module, which is used to build a rigid-flexible coupled multi-body dynamics model of the entire vehicle that does not include tires;
    约束模块，其用于约束车身运动姿态，并对整车刚柔耦合多体动力学模型进行对标；The constraint module is used to constrain the motion posture of the vehicle body and benchmark the rigid-flexible coupled multi-body dynamics model of the entire vehicle;
    灵敏度分析模块，其用于对六分力载荷进行灵敏度分析，得到底盘各零部件最大应力对各六分力载荷分量的灵敏度；The sensitivity analysis module is used to perform sensitivity analysis on the six-component force load to obtain the sensitivity of the maximum stress of each chassis component to each six-component force load component;
    实测统计模块，其用于分别统计各工况下实测道路六分力各载荷分量的最大值；The measured statistics module is used to separately count the maximum values of each load component of the six measured road forces under each working condition;
    计算模块，其根据灵敏度，计算底盘各个零部件在各工况下实测道路谱下的最大应力；The calculation module calculates the maximum stress of each chassis component under the measured road spectrum under various working conditions based on sensitivity;
    统计模块，其用于统计底盘各零部件材料的屈服极限，分别计算各工况下底盘各 零部件的最大应力与对应的材料屈服极限的比值；The statistical module is used to calculate the yield limit of each chassis component material, and calculate the yield limit of each chassis component under each working condition. The ratio of the maximum stress of the component to the corresponding material yield limit;
    排序模块，其根据各工况下底盘系统中每个零部件最大应力的对工况进行排序；The sorting module sorts the working conditions according to the maximum stress of each component in the chassis system under each working condition;
    根据材料屈服极限的比值对每个零部件进行工况的排序；Sort the working conditions of each component according to the ratio of material yield limit;
    根据各工况下底盘零部件的最大应力对底盘各零部件进行排序；Sort the chassis components according to their maximum stress under each working condition;
    根据材料屈服极限的比值对每个工况都进行零部件的排序；The components are sorted for each working condition according to the ratio of the material yield limit;
    展示模块，其根据底盘零部件最大应力分布组成底盘的各系统、子系统的最大应力分布。Display module, which forms the maximum stress distribution of each system and subsystem of the chassis based on the maximum stress distribution of chassis components.
  14. 如权利要求13所述的车辆底盘零部件最大应力分布计算系统，其特征在于：实测统计模块还统计各工况下实测道路六分力各载荷分量的最小值、最大值出现时刻和/或最小值出现时刻。The maximum stress distribution calculation system of vehicle chassis components according to claim 13, characterized in that: the measured statistics module also counts the minimum value, maximum occurrence time and/or minimum value of each load component of the six-component road force measured under each working condition. The time when the value appears.
  15. 如权利要求13所述的车辆底盘零部件最大应力分布计算系统，其特征在于：计算模块还计算底盘各个零部件在各工况下实测道路谱下的最小应力、最大应力出现时刻和/或最小应力出现时刻。The maximum stress distribution calculation system of vehicle chassis components according to claim 13, characterized in that: the calculation module also calculates the minimum stress, maximum stress occurrence time and/or minimum stress of each chassis component under the measured road spectrum under each working condition. moment of stress.
  16. 如权利要求13所述的车辆底盘零部件最大应力分布计算系统，其特征在于：所述整车刚柔耦合多体动力学模型中，零部件采用刚体、模态柔性体或有限元柔性体。The maximum stress distribution calculation system of vehicle chassis components according to claim 13, characterized in that in the rigid-flexible coupling multi-body dynamics model of the entire vehicle, the components adopt rigid bodies, modal flexible bodies or finite element flexible bodies.
  17. 如权利要求16所述的车辆底盘零部件最大应力分布计算系统，其特征在于：所述整车刚柔耦合多体动力学模型至少选择底盘零部件模型的前10阶频率。The maximum stress distribution calculation system of vehicle chassis components according to claim 16, wherein the rigid-flexible coupled multi-body dynamics model of the entire vehicle selects at least the first 10 frequencies of the chassis component model.
  18. 如权利要求13所述的车辆底盘零部件最大应力分布计算系统，其特征在于：约束车身运动姿态采用固定车身；The maximum stress distribution calculation system of vehicle chassis components according to claim 13, characterized in that: a fixed body is used to constrain the movement posture of the vehicle body;
    或，约束车身运动姿态采用轴头与地面间建立缓冲件，并限定缓冲件位移刚度范围。Or, to constrain the movement posture of the vehicle body, a buffer member is established between the axle head and the ground, and the displacement stiffness range of the buffer member is limited.
  19. 如权利要求18所述的车辆底盘零部件最大应力分布计算系统，其特征在于：缓冲件位移刚度范围为0/mm～1000N/mm。The maximum stress distribution calculation system of vehicle chassis components according to claim 18, characterized in that: the displacement stiffness of the buffer member ranges from 0/mm to 1000N/mm.
  20. 如权利要求19所述的车辆底盘零部件最大应力分布计算方法，其特征在于：缓冲件位移刚度范围是，垂向刚度范围为0N/mm～10N/mm，侧向范围为0N/mm～0.5N/mm，纵向刚度范围为0N/mm～0.5N/mm。The maximum stress distribution calculation method of vehicle chassis components according to claim 19, characterized in that: the displacement stiffness range of the buffer is: the vertical stiffness range is 0 N/mm ~ 10 N/mm, and the lateral range is 0 N/mm ~ 0.5 N/mm, the longitudinal stiffness range is 0N/mm~0.5N/mm.
  21. 如权利要求13所述的车辆底盘零部件最大应力分布计算系统，其特征在于：约束车身运动姿态采用固定车身方式。 The maximum stress distribution calculation system of vehicle chassis components according to claim 13, characterized in that: a fixed body method is used to constrain the movement posture of the vehicle body.
  22. 如权利要求13所述的车辆底盘零部件最大应力分布计算系统，其特征在于：所述多体动力学模型进行对标包括：静平衡分析和调整模型轴荷。The maximum stress distribution calculation system for vehicle chassis components according to claim 13, wherein the benchmarking of the multi-body dynamics model includes static balance analysis and adjustment of model axle loads.
  23. 如权利要求22所述的车辆底盘零部件最大应力分布计算系统，其特征在于：所述多体动力学模型进行对标还包括：调整模型内部的弹性元件的刚度和/或阻尼参数，对减振器位移和/或轴头加速度数据进行对标，以及对系统模型进行修正。The maximum stress distribution calculation system of vehicle chassis components according to claim 22, characterized in that: benchmarking the multi-body dynamics model further includes: adjusting the stiffness and/or damping parameters of the elastic elements inside the model, and reducing the The vibrator displacement and/or shaft head acceleration data are benchmarked, and the system model is corrected.
  24. 如权利要求13所述的车辆底盘零部件最大应力分布计算方法，其特征在于：底盘零部件最大应力至少包括VonMises应力、坐标系下沿各坐标轴方向的各个应力分量、主应力和/或剪切应力。 The method for calculating maximum stress distribution of vehicle chassis components according to claim 13, characterized in that: the maximum stress of chassis components at least includes VonMises stress, each stress component along each coordinate axis direction in the coordinate system, principal stress and/or shear Shear stress.
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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109426685A (en) * 2017-08-28 2019-03-05 长城汽车股份有限公司 Parts analysis method
WO2020244325A1 (en) * 2019-06-04 2020-12-10 南京依维柯汽车有限公司 Relative sensitivity-based method for lightweighting of non-load bearing body-in-white
CN113190915A (en) * 2021-04-19 2021-07-30 东风柳州汽车有限公司 Vehicle strength evaluation method and system
CN113656943A (en) * 2021-07-15 2021-11-16 桂林电子科技大学 Method for extracting fatigue load spectrum of chassis component of whole commercial vehicle
US20210357544A1 (en) * 2018-10-05 2021-11-18 Jfe Steel Corporation Method and apparatus for analyzing sensitivity of automotive body parts and method for determining material property of automotive body parts
CN115048726A (en) * 2022-06-30 2022-09-13 上海合科科技有限公司 Method and system for calculating maximum stress distribution of vehicle chassis parts and storage medium

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109426685A (en) * 2017-08-28 2019-03-05 长城汽车股份有限公司 Parts analysis method
US20210357544A1 (en) * 2018-10-05 2021-11-18 Jfe Steel Corporation Method and apparatus for analyzing sensitivity of automotive body parts and method for determining material property of automotive body parts
WO2020244325A1 (en) * 2019-06-04 2020-12-10 南京依维柯汽车有限公司 Relative sensitivity-based method for lightweighting of non-load bearing body-in-white
CN113190915A (en) * 2021-04-19 2021-07-30 东风柳州汽车有限公司 Vehicle strength evaluation method and system
CN113656943A (en) * 2021-07-15 2021-11-16 桂林电子科技大学 Method for extracting fatigue load spectrum of chassis component of whole commercial vehicle
CN115048726A (en) * 2022-06-30 2022-09-13 上海合科科技有限公司 Method and system for calculating maximum stress distribution of vehicle chassis parts and storage medium

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
SONG, ZILI; LIU, JUNHONG: "Static Strength Analysis on Automobile Chassis based on Road Spectrum", COMPUTER AIDED ENGINEERING, no. 05, 31 October 2015 (2015-10-31), pages 16 - 21, XP009551575, ISSN: 1006-0871, DOI: 10.13340/j.cae.2015.05.004 *

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