Design method of automobile dynamic vibration absorber

Abstract

The invention relates to the technical field of automobile vibration control, in particular to a design method of an automobile dynamic vibration absorber. Comprising the following steps: identifying a part generating resonance on a main vibration system of a real vehicle, and selecting a mode of the dynamic vibration absorber as a first mode of combining rubber and a mass block or a second mode of an independent mass block based on a resonance frequency value of the resonance part; if it is judged that the mode is the first mode, the mass, the rubber rigidity value and the rubber damping ratio of the dynamic vibration absorber are designed; if it is judged that the mode is the second mode, the mass of the dynamic vibration absorber is designed; a sample piece is manufactured based on the obtained design parameters, the manufactured sample piece is assembled on a real vehicle to be verified and tested, and the sample with the best effect is selected as the final design scheme. The automobile dynamic vibration absorber is a forward design calculation and development process, does not depend on a test value and debugging experience, provides a clear direction for the design of the dynamic vibration absorber, and carries out corresponding parameter design on the dynamic vibration absorber.

Description

Technical Field

[0001] The invention relates to the technical field of automobile vibration control, and in particular to a design method for an automobile dynamic vibration absorber. Background Art

[0002] In automobile R&D and design, NVH performance (Noise Vibration and Harshness) usually refers to performance parameters such as noise, vibration and harshness related to automobiles. As people's requirements for vehicle riding comfort continue to increase, NVH performance has gradually become an important performance indicator for automobile design.

[0003] Among the excitation sources that affect the NVH performance of the vehicle, the powertrain is the main and most important excitation source in the vehicle. Since the powertrain suspension system is the only system that supports, limits and isolates the powertrain, the design and debugging of the powertrain suspension system is crucial to the NVH performance of the vehicle.

[0004] The dynamic vibration absorber is the main vibration isolation structure in the powertrain suspension system. It is mainly composed of mass, spring and damping. It is a passive vibration absorber that can effectively suppress resonance, so it is widely used in the suspension system. When the suspension support or bracket has resonance or insufficient vibration isolation rate, causing NVH problems of the whole vehicle, it can be solved by installing a dynamic vibration absorber on the suspension.

[0005] During the current trial production and testing phase of automobile R&D, when a resonance problem is discovered in the powertrain suspension system, the power absorber is usually designed directly according to the resonance frequency value. After the sample is developed, the actual vehicle is debugged and finally the absorber status is locked.

[0006] The development of existing dynamic vibration absorbers lacks forward design calculations and development processes, and most of them rely on test values ​​and debugging experience. Although they can solve the NVH problem of the entire vehicle during actual vehicle development, due to the inaccurate setting of dynamic vibration absorber parameters, they usually deviate from the optimal state and it is difficult to maximize the vibration damping effect of the dynamic vibration absorber. Summary of the invention

[0007] The purpose of this application is to solve the deficiencies of the above-mentioned background technology and provide a design method for a vehicle dynamic vibration absorber.

[0008] The technical solution of the present application is: a method for designing a dynamic vibration absorber for an automobile, comprising:

[0009] Identify the resonant components on the main vibration system of the actual vehicle, and select the mode of the vehicle dynamic vibration absorber as the first mode of the combination of rubber and mass block or the second mode of the single mass block based on the resonant frequency value of the resonant components;

[0010] If it is determined to be the first mode, the mass, rubber stiffness value and rubber damping ratio of the dynamic vibration absorber are designed;

[0011] If it is determined to be the second mode, the mass of the dynamic vibration absorber is designed;

[0012] The structure of the dynamic vibration absorber is designed, and samples are made based on the obtained design parameters. The samples are assembled on the actual vehicle for verification and testing, and the sample with the best effect is selected as the final design solution.

[0013] According to a method for designing a dynamic vibration absorber for an automobile provided by the present application, the method for selecting a mode of the dynamic vibration absorber for an automobile based on the resonance frequency value of a resonance component includes: if the resonance frequency value of the resonance component is less than a set frequency, the mode of the dynamic vibration absorber for the automobile is selected as a first mode in which rubber and a mass block are combined; if the resonance frequency value of the resonance component is not less than the set frequency, the mode of the dynamic vibration absorber for the automobile is selected as a second mode in which a single mass block is used.

[0014] According to a method for designing a dynamic vibration absorber for an automobile provided by the present application, the method for designing the mass of the dynamic vibration absorber includes: calculating the mass of a mass block of the dynamic vibration absorber in a first mode according to the following formula:

[0015] m 1 =μM

[0016] Where: M is the mass of the main vibration system;

[0017] m 1 - the mass of the mass of the dynamic vibration absorber in the first mode;

[0018] μ——mass ratio, μ≤0.2.

[0019] According to a method for designing a dynamic vibration absorber for an automobile provided by the present application, the method for designing the rubber stiffness value of the dynamic vibration absorber includes: calculating the angular frequency of the main vibration system based on the resonant frequency value of the resonant component; calculating the natural angular frequency of the dynamic vibration absorber in a first mode according to the angular frequency of the main vibration system; and calculating the rubber stiffness value of the dynamic vibration absorber in the first mode according to the following formula:

[0020]

[0021] Where: k 1 ——Rubber stiffness value of the dynamic vibration absorber in the first mode;

[0022] m 1 - the mass of the mass of the dynamic vibration absorber in the first mode;

[0023] ω 1——The natural angular frequency of the dynamic vibration absorber in the first mode.

[0024] According to a method for designing a dynamic vibration absorber for an automobile provided by the present application, the method for designing the rubber damping ratio of the dynamic vibration absorber includes: calculating the rubber damping ratio of the dynamic vibration absorber in a first mode according to the following formula:

[0025]

[0026] Where: ζ——rubber damping ratio of the dynamic vibration absorber in the first mode;

[0027] μ——mass ratio, μ≤0.2.

[0028] According to a method for designing a dynamic vibration absorber for an automobile provided by the present application, the method for designing the mass of the dynamic vibration absorber includes: calculating the angular frequency of the main vibration system based on the resonant frequency value of the resonant component; calculating the natural angular frequency of the dynamic vibration absorber in the second mode according to the angular frequency of the main vibration system; and calculating the mass of the mass block of the dynamic vibration absorber in the second mode according to the following formula:

[0029]

[0030] Where: m 2 - the mass of the mass of the dynamic vibration absorber in the second mode;

[0031] ω 2 ——the natural angular frequency of the dynamic vibration absorber in the second mode;

[0032] k 2 ——Dynamic stiffness value of the dynamic vibration absorber installation point.

[0033] According to a method for designing a dynamic vibration absorber for an automobile provided by the present application, the method for making samples based on the obtained design parameters includes: calculating a preset natural frequency of the dynamic vibration absorber in the first mode based on the mass of the dynamic vibration absorber and the rubber stiffness value of the dynamic vibration absorber in the first mode, and making samples equal to the preset natural frequency and samples exceeding the preset natural frequency and less than the preset natural frequency.

[0034] According to a method for designing a dynamic vibration absorber for an automobile provided in the present application, a preset natural frequency of the dynamic vibration absorber in a first mode is calculated, a sample with a natural frequency being the preset natural frequency is manufactured, a sample with a natural frequency being (1-a) the preset natural frequency, and a sample with a natural frequency being (1+a) the preset natural frequency are manufactured; wherein a is less than 1.

[0035] According to a method for designing a dynamic vibration absorber for an automobile provided by the present application, the method for making samples based on the obtained design parameters includes: making samples according to the calculated mass of the mass block of the dynamic vibration absorber in the second mode, and making samples with a mass greater than that of the mass block of the dynamic vibration absorber in the second mode and samples with a mass less than that of the mass block of the dynamic vibration absorber in the second mode.

[0036] According to a method for designing a dynamic vibration absorber for an automobile provided by the present application, a sample is manufactured whose mass is equal to the mass of the mass block of the dynamic vibration absorber in the second mode calculated, a sample is manufactured whose mass is equal to b times the mass of the mass block of the dynamic vibration absorber in the second mode calculated, and a sample is manufactured whose mass is equal to c times the mass of the mass block of the dynamic vibration absorber in the second mode calculated; wherein b is less than 1 and c is greater than 1.

[0037] The advantages of this application are as follows: 1. This application selects a suitable mode of a dynamic vibration absorber according to the resonance frequency value measured by the actual vehicle, provides a clear direction for the design of the dynamic vibration absorber, and performs corresponding parameter design for dynamic vibration absorbers of different modes, constructs a complete and clear design idea and design method, and can quickly design a dynamic vibration absorber that solves the resonance problem of the actual vehicle, providing a scientific, reasonable and fast design specification for the parameter design of the dynamic vibration absorber;

[0038] 2. This application determines the design direction of the dynamic vibration absorber by the resonant frequency value of the resonant component, and determines the mode of the dynamic vibration absorber according to different resonance situations. The design method is clear, the design idea is reasonable and scientific, and it is convenient to accurately obtain the dynamic vibration absorber that can solve the resonance problem of the current main vibration system in the future;

[0039] 3. The method for determining the mass of the mass block of the dynamic vibration absorber in the first mode in the present application is very simple. The mass of the mass block can be quickly determined through the main vibration system and the mass ratio. The overall calculation is simple, and the mass of the mass block obtained can meet the requirements;

[0040] 4. The rubber stiffness value of the dynamic vibration absorber in the first mode is calculated based on the angular frequency of the main vibration system and the natural angular frequency of the dynamic vibration absorber in the first mode. By obtaining the stiffness value of the rubber part of the dynamic vibration absorber in this way, the rubber design parameters that meet the current main vibration system can be quickly obtained, and the calculation method is simple;

[0041] 5. The present application calculates the rubber damping ratio of the dynamic vibration absorber in the first mode by mass ratio. The calculation method is simple and can quickly obtain the design parameters of the rubber part of the dynamic vibration absorber in the first mode, which can facilitate the selection and design of the rubber part.

[0042] 6. The method for calculating the mass of the mass block of the dynamic vibration absorber in the second mode of the present application is very simple, and can quickly obtain the required mass of the dynamic vibration absorber, which facilitates the subsequent construction of a mass block that meets the requirements and improves the design efficiency of the dynamic vibration absorber;

[0043] 7. This application will produce samples of the dynamic vibration absorber in the first mode for actual vehicle verification, and increase or decrease the number of samples according to possible calculation errors to produce multiple samples. Through actual vehicle tests of multiple samples, the dynamic vibration absorber with the best effect can be quickly obtained, thereby improving the accuracy and matching of the entire dynamic vibration absorber design;

[0044] 8. This application floats above and below the preset fixed frequency, and the floating amplitude is equivalent. The corresponding real vehicle verification can be carried out through three groups of samples, which is convenient for producing samples that can be quickly verified and can also improve the accuracy of real vehicle sample verification;

[0045] 9. The present application will produce samples of the dynamic vibration absorber in the second mode for actual vehicle verification, and increase or decrease the samples according to possible calculation errors to produce multiple samples. Through actual vehicle tests of multiple samples, the best quality block can be quickly obtained, which facilitates the acquisition of the best dynamic vibration absorber;

[0046] 10. The present application produces a plurality of samples for actual vehicle test verification by adjusting the mass of the mass block of the dynamic vibration absorber in the second mode up and down. This not only facilitates the production of verification samples, but also facilitates the rapid acquisition of the dynamic vibration absorber with the best effect.

[0047] The automotive dynamic vibration absorber of the present application is a forward design calculation and development process, which does not rely on test values ​​and debugging experience. It provides a clear direction for the design of the dynamic vibration absorber, and carries out corresponding parameter design for dynamic vibration absorbers of different modes, constructing a complete and clear design idea and design method, which can quickly design a dynamic vibration absorber that solves the resonance problem of the actual vehicle. BRIEF DESCRIPTION OF THE DRAWINGS

[0048] Figure 1 : Flowchart of the design of the automotive dynamic vibration absorber of the present application. DETAILED DESCRIPTION

[0049] The embodiments of the present application are described in detail below, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended to be used to explain the present application, and should not be construed as limiting the present application.

[0050] In the description of the present application, it should be understood that the terms "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present application.

[0051] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of this application, the meaning of "plurality" is at least two, such as two, three, etc., unless otherwise clearly and specifically defined.

[0052] The present application is further described in detail below in conjunction with the accompanying drawings and specific embodiments.

[0053] The present application relates to a method for designing a dynamic vibration absorber for an automobile. The present application detects the main vibration system of an actual vehicle (the main vibration system described in the present application includes a support arm, a bracket or a cantilever support in a suspension system) to obtain the resonance frequency of the components that resonate in the main vibration system, and then designs the dynamic vibration absorber based on the resonance frequency of the resonant components. According to the resonance frequency of the resonant components, dynamic vibration absorbers of different modes are selected. After the corresponding mode is selected, the parameters of the dynamic vibration absorber of the mode are accurately calculated and determined, and finally the required design parameters of the dynamic vibration absorber are obtained. Samples are made based on the design parameters of the dynamic vibration absorber, and the samples are installed on the main vibration system for testing. According to the test results, the required dynamic vibration absorber can be determined. The present application selects a suitable mode of the dynamic vibration absorber according to the resonance frequency value measured by the actual vehicle, provides a clear direction for the design of the dynamic vibration absorber, and performs corresponding parameter design for dynamic vibration absorbers of different modes, constructs a complete and clear design idea and design method, can quickly design a dynamic vibration absorber that solves the resonance problem of the actual vehicle, and provides a scientific, reasonable and fast design specification for the parameter design of the dynamic vibration absorber.

[0054] Specifically, Figure 1 As shown, the automotive dynamic vibration absorber design method of the present application is carried out according to the following steps:

[0055] S1. Identify the resonant components on the main vibration system of the actual vehicle, and select the mode of the vehicle dynamic vibration absorber as the first mode of the combination of rubber and mass block or the second mode of the single mass block based on the resonant frequency value of the resonant components;

[0056] The resonant frequency of the resonant component is the main parameter for determining the mode of the dynamic vibration absorber. Dynamic vibration absorbers of different modes can solve the problem of different resonant frequencies. Determining the mode of the dynamic vibration absorber by the resonant frequency can quickly determine the design direction of the dynamic vibration absorber, which is convenient for the subsequent design of the parameters of the dynamic vibration absorber.

[0057] The first mode dynamic vibration absorber is composed of a rubber body and a mass block (metal block). The rubber body can act as a spring and a damper, and the mass block provides the mass required for matching. Since the stiffness of rubber has a wide range of variation, but the ultimate stiffness is limited, this type of dynamic vibration absorber is mainly used to deal with resonances with lower frequencies. The second mode dynamic vibration absorber only has a mass block, whose damping can be ignored, and the stiffness of the system is mainly affected by the stiffness of the mounting point. Since the stiffness of the mounting point is usually much greater than that of the rubber body, this type of dynamic vibration absorber can deal with resonances with higher frequencies.

[0058] S2. If it is determined to be the first mode, the mass, rubber stiffness value and rubber damping ratio of the dynamic vibration absorber are designed;

[0059] If it is determined to be the second mode, the mass of the dynamic vibration absorber is designed;

[0060] The first mode of dynamic vibration absorber involves a rubber body and a mass block, so the parameters of the rubber body and the mass block need to be designed accordingly, while the second mode of dynamic vibration absorber only has a mass block, so only the parameters of the mass block need to be designed accordingly;

[0061] S3. Design the structure of the dynamic vibration absorber, make samples based on the obtained design parameters, assemble the samples on the actual vehicle for verification testing, and select the sample with the best effect as the final design solution;

[0062] After the design parameters of the dynamic vibration absorber are determined, the structure of the dynamic vibration absorber can be designed. The structural design of the dynamic vibration absorber takes into account two aspects: one is to consider the design parameters obtained above, and the other is to consider the boundary environment of the installation position of the dynamic vibration absorber to ensure that the dynamic vibration absorber of this size does not interfere with the surrounding environment of the installation position, and the designed dynamic vibration absorber structure can be installed at the designed installation position;

[0063] Then, according to the design parameters and design structure, corresponding samples are made and installed on the actual vehicle for verification and actual vehicle matching. Finally, the sample with the best effect can be determined as the final design solution. The sample with the best effect refers to the sample that can eliminate the resonance of the main vibration system to the greatest extent.

[0064] In some embodiments of the present application, this embodiment optimizes the above-mentioned step S1. Specifically, the method for selecting the mode of the automobile dynamic vibration absorber based on the resonance frequency value of the resonance component is: if the resonance frequency value of the resonance component is less than the set frequency, the mode of the automobile dynamic vibration absorber is selected as the first mode of the combination of rubber and mass block; if the resonance frequency value of the resonance component is not less than the set frequency, the mode of the automobile dynamic vibration absorber is selected as the second mode of the single mass block.

[0065] The set frequency of this embodiment is 650Hz, but it is not limited to this value in actual application. The corresponding value can be selected according to actual needs as long as the corresponding requirements are met. The first mode dynamic vibration absorber is mainly used to eliminate the resonance of lower frequency, and the second mode dynamic vibration absorber is used to eliminate the resonance of higher frequency. Different resonance frequencies correspond to different modes of dynamic vibration absorbers.

[0066] In some other embodiments of the present application, this embodiment optimizes the above step S2. Specifically, the method for designing the mass of the dynamic vibration absorber in this embodiment is: the mass of the mass block of the dynamic vibration absorber in the first mode is calculated according to the following formula:

[0067] m 1 =μM

[0068] Where: M is the mass of the main vibration system;

[0069] m 1 - the mass of the mass of the dynamic vibration absorber in the first mode;

[0070] μ——mass ratio, μ≤0.2.

[0071] The mass M of the main vibration system is known. After the actual vehicle is determined, the main vibration system is also determined, and the mass of the main vibration system is also determined. The mass ratio μ≤0.2, and the general value of μ is 0.1. It can be selected according to needs in actual application. After the mass and mass ratio of the main vibration system are determined, the mass of the mass block of the dynamic vibration absorber in the first mode can be calculated.

[0072] Increasing the mass of the mass block of the power system in the first mode can improve the vibration suppression effect of the main vibration system, but the total mass of the main vibration system will also increase accordingly. This embodiment limits the mass ratio to ≤0.2, so that the mass block of the designed power system is within a suitable mass range.

[0073] The design of the dynamic vibration absorber in the first mode also includes the design of the rubber body. The design of the rubber body mainly determines the rubber stiffness value and the rubber damping ratio of the rubber body. The method for designing the rubber stiffness value of the dynamic vibration absorber is: based on the resonant frequency value of the resonant component, the angular frequency of the main vibration system is calculated. The calculation formula is as follows:

[0074] Ω 0 =2πf 0

[0075] Where: Ω 0 ——angular frequency of the master oscillation system;

[0076] f 0 ——resonant frequency value of resonant components;

[0077] The natural angular frequency of the dynamic vibration absorber in the first mode is calculated according to the angular frequency of the main vibration system. The calculation formula is as follows:

[0078]

[0079] Where: 1 ——the natural angular frequency of the dynamic vibration absorber in the first mode;

[0080] Ω 0 ——angular frequency of the master oscillation system;

[0081] f 0 ——resonant frequency value of resonant components;

[0082] μ——mass ratio, μ≤0.2;

[0083] γ——frequency ratio;

[0084] The rubber stiffness value of the dynamic vibration absorber in the first mode is calculated according to the following formula:

[0085]

[0086] Where: k 1 ——Rubber stiffness value of the dynamic vibration absorber in the first mode;

[0087] m 1 - the mass of the mass of the dynamic vibration absorber in the first mode;

[0088] ω 1 ——The natural angular frequency of the dynamic vibration absorber in the first mode.

[0089] The rubber damping ratio of the dynamic vibration absorber in the first mode is calculated according to the following formula:

[0090]

[0091] Where: ζ——rubber damping ratio of the dynamic vibration absorber in the first mode;

[0092] μ——mass ratio, μ≤0.2.

[0093] At this point, the mass of the mass block of the dynamic vibration absorber of the first mode, the rubber stiffness value of the rubber body and the rubber damping ratio can be obtained, and the design operation of the dynamic vibration absorber of the second mode is completed.

[0094] In a further embodiment of the present application, the present embodiment further optimizes the above step S2. Specifically, if it is determined that the dynamic vibration absorber to be designed is the second mode, the angular frequency of the main vibration system is calculated based on the resonant frequency value of the resonant component. The specific calculation formula is as follows:

[0095] Ω 0 =2πf 0

[0096] Where: Ω 0 ——angular frequency of the master oscillation system;

[0097] f 0 ——resonant frequency value of resonant components;

[0098] The natural angular frequency of the dynamic vibration absorber in the second mode is calculated according to the angular frequency of the main vibration system. The specific calculation formula is as follows:

[0099]

[0100] Where: 2 ——the natural angular frequency of the dynamic vibration absorber in the second mode;

[0101] Ω 0 ——angular frequency of the master oscillation system;

[0102] f 0 ——resonant frequency value of resonant components;

[0103] μ——mass ratio, μ≤0.2;

[0104] γ——frequency ratio;

[0105] The mass of the mass block of the dynamic vibration absorber in the second mode is calculated according to the following formula:

[0106]

[0107] Where: m 2 - the mass of the mass of the dynamic vibration absorber in the second mode;

[0108] ω 2 ——the natural angular frequency of the dynamic vibration absorber in the second mode;

[0109] k 2 ——Dynamic stiffness value of the dynamic vibration absorber installation point.

[0110] At this point, the mass of the mass block of the second mode dynamic vibration absorber can be obtained, and the design operation of the second mode dynamic vibration absorber is completed.

[0111] In a further embodiment of the present application, the present embodiment optimizes the above step S3. Specifically, the method for making a sample based on the obtained design parameters is as follows: if the designed dynamic vibration absorber is a first mode, based on the mass of the dynamic vibration absorber and the rubber stiffness value of the dynamic vibration absorber in the first mode, the preset natural frequency of the dynamic vibration absorber in the first mode is calculated. The specific calculation formula is as follows:

[0112]

[0113] Where: f g - the preset natural frequency of the dynamic vibration absorber in the first mode;

[0114] k 1 ——Rubber stiffness value of the dynamic vibration absorber in the first mode;

[0115] m 1 - the mass of the mass of the dynamic vibration absorber in the first mode;

[0116] Then, samples are made based on the preset natural frequency of the dynamic vibration absorber in the first mode, and samples with natural frequencies of (1-a) and (1+a) are made; a is less than 1. The value of a in this embodiment is 0.2, that is, three groups of samples are made in this embodiment, including 0.8f g The sample, f g Samples and 1.2f g of samples.

[0117] If the designed dynamic vibration absorber is of the second mode, samples are made according to the calculated mass of the mass block of the dynamic vibration absorber in the second mode, and samples with a mass greater than that of the mass block of the dynamic vibration absorber in the second mode and samples with a mass less than that of the mass block of the dynamic vibration absorber in the second mode are made. Specifically, samples with a mass equal to the calculated mass of the mass block of the dynamic vibration absorber in the second mode are made, samples with a mass equal to b times the calculated mass of the mass block of the dynamic vibration absorber in the second mode are made, and samples with a mass equal to c times the calculated mass of the mass block of the dynamic vibration absorber in the second mode are made; b is less than 1, and c is greater than 1. In this embodiment, b takes a value of 0.5, and c takes a value of 2. That is to say, the samples of the second mode dynamic vibration absorber in this embodiment include 0.5m 2 Samples, m 2 Samples and 2m 2 of samples.

[0118] Finally, the manufactured samples are installed on the actual vehicle for actual vehicle matching, and the sample with the best effect is selected as the final design solution.

[0119] The automotive dynamic vibration absorber design method of the present application is specifically as follows Figure 1 As shown, the following method is used: the components that resonate on the main vibration system of the actual vehicle are identified. If the resonant frequency value of the resonant component is less than 650 Hz, the mode of the automobile dynamic vibration absorber is selected as the first mode of the combination of rubber and mass block; if the resonant frequency value of the resonant component is not less than 650 Hz, the mode of the automobile dynamic vibration absorber is selected as the second mode of the single mass block;

[0120] If it is determined to be the first mode, the mass of the mass block of the dynamic vibration absorber in the first mode is determined according to the mass and mass ratio of the main vibration system, the angular frequency of the main vibration system is calculated based on the resonant frequency value of the resonance component, the natural angular frequency of the dynamic vibration absorber in the first mode is calculated according to the angular frequency of the main vibration system, and the rubber stiffness value of the dynamic vibration absorber in the first mode is calculated; the rubber damping ratio of the dynamic vibration absorber in the first mode is calculated according to the mass ratio;

[0121] If it is determined to be the second mode, the angular frequency of the main vibration system is calculated based on the resonant frequency value of the resonant component, the natural angular frequency of the dynamic vibration absorber in the second mode is calculated according to the angular frequency of the main vibration system, and the mass of the mass block of the dynamic vibration absorber in the second mode is calculated;

[0122] The structure of the dynamic vibration absorber is designed according to the design parameters calculated above. In the process of structural design, in addition to considering the above design parameters, the boundary environment of the installation position of the dynamic vibration absorber also needs to be considered to ensure that the dynamic vibration absorber can be installed at the set installation position. The first mode of the dynamic vibration absorber needs to ensure that its geometric dimensions meet the requirements of the peripheral clearance, and there must be no risks such as interference or insufficient clearance. The second mode of the dynamic vibration absorber is a mass block, and the mass block is generally made of metal materials such as cast steel and iron, and its geometric dimensions also need to meet the requirements of the peripheral clearance.

[0123] Calculate the preset natural frequency of the dynamic vibration absorber in the first mode based on the mass of the dynamic vibration absorber and the rubber stiffness value of the dynamic vibration absorber in the first mode, and prepare samples based on the preset natural frequency of the dynamic vibration absorber in the first mode, and prepare samples with a natural frequency of (1-a) the preset natural frequency and samples with a natural frequency of (1+a) the preset natural frequency;

[0124] making a sample based on the calculated mass of the mass of the dynamic vibration absorber in the second mode, making a sample having a mass equal to the calculated mass of the mass of the dynamic vibration absorber in the second mode, making a sample having a mass equal to b times the calculated mass of the mass of the dynamic vibration absorber in the second mode, and making a sample having a mass equal to c times the calculated mass of the mass of the dynamic vibration absorber in the second mode;

[0125] Install the manufactured samples on the actual vehicle for actual vehicle matching, and select the sample with the best effect as the final design solution.

[0126] The above shows and describes the basic principles, main features and advantages of the present application. Those skilled in the art should understand that the present application is not limited by the above embodiments, and the above embodiments and descriptions are only for explaining the principles of the present application. The present application may have various changes and improvements without departing from the spirit and scope of the present application, and these changes and improvements fall within the scope of the present application to be protected. The scope of protection claimed in the present application is defined by the attached claims and their equivalents.

Claims

1. A method for designing a dynamic vibration absorber for an automobile, characterized in that: include, Identify the resonant components on the main vibration system of the actual vehicle, and select the mode of the vehicle dynamic vibration absorber as the first mode of the combination of rubber and mass block or the second mode of the single mass block based on the resonant frequency value of the resonant components; If it is determined to be the first mode, the mass, rubber stiffness value and rubber damping ratio of the dynamic vibration absorber are designed; If it is determined to be the second mode, the mass of the dynamic vibration absorber is designed; The structure of the dynamic vibration absorber is designed, and samples are made based on the obtained design parameters. The samples are assembled on the actual vehicle for verification and testing, and the sample with the best effect is selected as the final design solution.

2. The method for designing a dynamic vibration absorber for an automobile according to claim 1, characterized in that: The method for selecting a mode of a vehicle dynamic vibration absorber based on a resonance frequency value of a resonance component comprises: if the resonance frequency value of the resonance component is less than a set frequency, the mode of the vehicle dynamic vibration absorber is selected as a first mode combining rubber and a mass block; if the resonance frequency value of the resonance component is not less than the set frequency, the mode of the vehicle dynamic vibration absorber is selected as a second mode of a single mass block.

3. The method for designing a dynamic vibration absorber for an automobile according to claim 1, characterized in that: The method for designing the mass of the dynamic vibration absorber includes: calculating the mass of the mass block of the dynamic vibration absorber in the first mode according to the following formula: m1=μM Where: M is the mass of the main vibration system; m1——the mass of the mass block of the dynamic vibration absorber in the first mode; μ——mass ratio, μ≤0.

2.

4. The method for designing a dynamic vibration absorber for an automobile according to claim 1, characterized in that: The method for designing the rubber stiffness value of the dynamic vibration absorber includes: calculating the angular frequency of the main vibration system based on the resonant frequency value of the resonance component; calculating the natural angular frequency of the dynamic vibration absorber in the first mode according to the angular frequency of the main vibration system; and calculating the rubber stiffness value of the dynamic vibration absorber in the first mode according to the following formula: Where: k1——rubber stiffness value of the dynamic vibration absorber in the first mode; m1——the mass of the mass block of the dynamic vibration absorber in the first mode; ω1——The natural angular frequency of the dynamic vibration absorber in the first mode.

5. The method for designing a dynamic vibration absorber for an automobile according to claim 1, characterized in that: The method for designing the rubber damping ratio of the dynamic vibration absorber includes: calculating the rubber damping ratio of the dynamic vibration absorber in the first mode according to the following formula: Where: ζ——rubber damping ratio of the dynamic vibration absorber in the first mode; μ——mass ratio, μ≤0.

2.

6. The method for designing a dynamic vibration absorber for an automobile according to claim 1, characterized in that: The method for designing the mass of the dynamic vibration absorber includes: calculating the angular frequency of the main vibration system based on the resonant frequency value of the resonant component; calculating the natural angular frequency of the dynamic vibration absorber in the second mode according to the angular frequency of the main vibration system; and calculating the mass of the mass block of the dynamic vibration absorber in the second mode according to the following formula: Where: m2 is the mass of the mass block of the dynamic vibration absorber in the second mode; ω2——natural angular frequency of the dynamic vibration absorber in the second mode; k2——dynamic stiffness value of the dynamic vibration absorber installation point.

7. The method for designing a dynamic vibration absorber for an automobile as claimed in claim 1, characterized in that: The method for making samples based on the obtained design parameters includes: calculating a preset natural frequency of the dynamic vibration absorber in the first mode based on the mass of the dynamic vibration absorber and the rubber stiffness value of the dynamic vibration absorber in the first mode, and making samples equal to the preset natural frequency and samples exceeding the preset natural frequency and less than the preset natural frequency.

8. A method for designing a dynamic vibration absorber for an automobile as claimed in claim 7, characterized in that: Calculate the preset natural frequency of the dynamic vibration absorber in the first mode, make a sample with a natural frequency equal to the preset natural frequency, make a sample with a natural frequency equal to (1-a) the preset natural frequency, and make a sample with a natural frequency equal to (1+a) the preset natural frequency; wherein a is less than 1.

9. The method for designing a dynamic vibration absorber for an automobile as claimed in claim 1, characterized in that: The method for making samples based on the obtained design parameters includes: making samples according to the calculated mass of the mass block of the dynamic vibration absorber in the second mode, and making samples with a mass greater than that of the mass block of the dynamic vibration absorber in the second mode and samples with a mass less than that of the mass block of the dynamic vibration absorber in the second mode.

10. A method for designing a dynamic vibration absorber for an automobile as claimed in claim 9, characterized in that: Make a sample with a mass equal to the calculated mass of the mass block of the dynamic vibration absorber in the second mode, make a sample with a mass equal to b times the calculated mass of the mass block of the dynamic vibration absorber in the second mode, and make a sample with a mass equal to c times the calculated mass of the mass block of the dynamic vibration absorber in the second mode; wherein b is less than 1 and c is greater than 1.

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