輕型客車(chē)低頻聲—固耦合噪聲傳遞路徑分析與控制
發(fā)布時(shí)間：2019-06-04 17:24
【摘要】：隨著汽車(chē)技術(shù)的發(fā)展與生活水平的提高,人們對(duì)汽車(chē)的乘坐舒適性要求逐日增高,而NVH性能是決定乘坐舒適性的重要指標(biāo)。車(chē)內(nèi)低頻噪聲問(wèn)題作為整車(chē)NVH問(wèn)題的一個(gè)重要組成部分,由其頻率特征造成了其產(chǎn)生和傳播過(guò)程相對(duì)復(fù)雜,較難分析噪聲源及影響因素。因此,如何更加快速判斷車(chē)內(nèi)低頻聲-固耦合噪聲產(chǎn)生的根源、更加準(zhǔn)確確定對(duì)噪聲有影響的主要部件、更有針對(duì)性的提出控制方案,以及在產(chǎn)品開(kāi)發(fā)階段如何準(zhǔn)確預(yù)測(cè)、分析車(chē)內(nèi)低頻聲-固耦合噪聲等NVH問(wèn)題,成為了各大汽車(chē)廠商和研究機(jī)構(gòu)的主要研究方向。本文通過(guò)對(duì)某國(guó)產(chǎn)輕型客車(chē)低頻聲-固耦合噪聲的傳遞路徑分析及控制方法進(jìn)行深入研究,建立了一整套能夠快速、準(zhǔn)確地預(yù)測(cè)、分析及控制低頻聲-固耦合噪聲的理論方法與技術(shù)流程,豐富了TPA的分析理論與方法。針對(duì)車(chē)內(nèi)低頻聲-固耦合噪聲的研究和控制方法,以及傳遞路徑分析的研究發(fā)展趨勢(shì)進(jìn)行了總結(jié)與分析,確定了本文基于傳遞路徑分析理論對(duì)聲-固耦合噪聲進(jìn)行研究的基本思路。本文系統(tǒng)地闡述了低頻聲-固耦合噪聲傳遞路徑分析的理論基礎(chǔ):推導(dǎo)了傳遞函數(shù)的理論及其無(wú)偏估計(jì);詳細(xì)介紹了三種工作載荷識(shí)別方法以及應(yīng)用范圍。重點(diǎn)推導(dǎo)了應(yīng)用奇異值分解方法求解廣義逆矩陣的過(guò)程。介紹了單參考傳遞路徑分析和多參考傳遞路徑分析�；谀硣�(guó)產(chǎn)輕型客車(chē)建立了整車(chē)低頻聲-固耦合噪聲的TPA模型。該模型包括了以動(dòng)力總成懸置,前、后懸架以及傳動(dòng)軸支撐為激勵(lì)端,以人耳耳旁噪聲為響應(yīng)點(diǎn)的多條傳遞路徑�；诖四Ｐ蛯�(duì)整車(chē)低頻聲-固耦合噪聲進(jìn)行了傳遞路徑分析。對(duì)以駕駛員、第二排乘客以及第五排乘客位置的耳旁噪聲為響應(yīng)點(diǎn)的多條傳遞路徑進(jìn)行了結(jié)構(gòu)路徑傳遞函數(shù)的測(cè)試;利用逆矩陣法獲取了彈性元件被動(dòng)端工作載荷。在進(jìn)行傳遞路徑分析之前,針對(duì)工況試驗(yàn)中的目標(biāo)點(diǎn)數(shù)據(jù)進(jìn)行了簡(jiǎn)要的車(chē)內(nèi)NVH水平分析。結(jié)合主觀評(píng)價(jià)與客觀數(shù)據(jù),確定70km/h時(shí)駕駛員耳旁位置以及第五排乘客耳旁位置存在噪聲問(wèn)題,并詳細(xì)描述了噪聲的主觀感受。針對(duì)該工況問(wèn)題頻率下各主要位置進(jìn)行傳遞路徑分析,并提出了一種綜合考慮聲壓級(jí)、幅值、相位的噪聲傳遞路徑貢獻(xiàn)量評(píng)價(jià)方法。利用這種方法進(jìn)一步針對(duì)每一個(gè)懸置進(jìn)行了重新分組計(jì)算。初步確定了對(duì)不同頻率、各個(gè)位置有主要影響的路徑。為了深入分析低頻噪聲問(wèn)題的產(chǎn)生機(jī)理及特征,本文建立了包含車(chē)身、車(chē)架、車(chē)門(mén)和車(chē)窗等在內(nèi)的聲-固耦合有限元模型。逐步建立了車(chē)架及白車(chē)身的有限元建模,并驗(yàn)證了仿真與和試驗(yàn)的模態(tài)頻率基本吻合,模態(tài)振型一致。進(jìn)一步建立了車(chē)窗及車(chē)門(mén)的有限元模型,并用正確的連接及約束方式連接,得到了門(mén)窗緊閉狀態(tài)的整車(chē)模型。以整車(chē)有限元模型為基礎(chǔ),建立了考慮車(chē)內(nèi)座椅的聲腔有限元模型。進(jìn)一步建立了整車(chē)聲-固耦合模型,對(duì)耦合前后聲腔和結(jié)構(gòu)模態(tài)的特征進(jìn)行了對(duì)比分析。將通過(guò)試驗(yàn)獲取的材料吸聲特性及結(jié)構(gòu)阻尼施加到耦合模型上。為了驗(yàn)證低頻聲-固耦合模型,對(duì)車(chē)內(nèi)噪聲進(jìn)行了混合傳遞路徑分析并與試驗(yàn)傳遞路徑分析的結(jié)果進(jìn)行了對(duì)比,得到了較準(zhǔn)確的低頻聲-固耦合模型。為了進(jìn)一步體現(xiàn)tpa在分析、預(yù)測(cè)以及應(yīng)用在研發(fā)初期時(shí)的優(yōu)越性,本文建立了包含行駛系及b級(jí)路面的整車(chē)多體動(dòng)力學(xué)模型,并將該模型與聲-固耦合模型聯(lián)合建立了整車(chē)聲-固耦合噪聲的虛擬tpa模型�；诘皖l聲-固耦合噪聲虛擬傳遞路徑分析的結(jié)果,提出了綜合考慮多頻率、多響應(yīng)點(diǎn)以及多工況的車(chē)內(nèi)噪聲綜合傳遞路徑分析方法,并進(jìn)行了綜合貢獻(xiàn)量分析,確定了對(duì)輕型客車(chē)車(chē)內(nèi)低頻聲-固耦合噪聲貢獻(xiàn)量較大的傳遞路徑。從理論基礎(chǔ)、分析結(jié)果、以及后續(xù)優(yōu)化等三個(gè)方面對(duì)三種tpa方法進(jìn)行分析,證明了虛擬tpa的優(yōu)越性。針對(duì)貢獻(xiàn)量最大的路徑進(jìn)行了單級(jí)以及次級(jí)傳遞路徑分析。通過(guò)單級(jí)傳遞路徑分析,確定了傳遞特性為需要優(yōu)化的因素,并確定板件為需要優(yōu)化的主要環(huán)節(jié)。針對(duì)板件環(huán)節(jié)進(jìn)行了次級(jí)傳遞路徑分析,并提出了一種考慮多頻、多響應(yīng)點(diǎn)、多工況以及相對(duì)關(guān)系的改進(jìn)板件聲學(xué)貢獻(xiàn)量系數(shù)算法�；谠摲椒�,進(jìn)一步提出了板件聲學(xué)影響系數(shù)的概念,并對(duì)其含義進(jìn)行了說(shuō)明�；谛碌乃惴ê透拍钸M(jìn)行了深入的次級(jí)傳遞路徑分析,依據(jù)分析結(jié)果最終確定了需要控制的板件,實(shí)施了阻尼降噪措施,并通過(guò)仿真及試驗(yàn)的方法驗(yàn)證了降噪效果。由此證明了本文所提出的一系列理論及方法可以準(zhǔn)確、有效、快捷地分析、控制、預(yù)測(cè)低頻結(jié)構(gòu)噪聲。
[Abstract]:With the development of automobile technology and the improvement of living standard, people's riding comfort demand is increasing day by day, and the NVH performance is an important index to determine the ride comfort. The low-frequency noise in the vehicle is an important part of the NVH problem of the whole vehicle. The frequency characteristics of the vehicle are relatively complicated, and it is difficult to analyze the noise source and the influencing factors. Therefore, how to judge the root cause of the low-frequency sound-solid coupling noise in the vehicle more quickly and accurately determine the main components that have an effect on the noise, and to provide the control scheme more specifically, and how to accurately predict the noise in the product development stage, The NVH problem such as low-frequency sound-solid coupling noise in the vehicle is analyzed, and the main research direction of the major automobile manufacturers and research institutes has been made. In this paper, a set of theoretical methods and technical processes for fast and accurate prediction, analysis and control of low-frequency sound-solid coupling noise are established through the deep research on the transmission and analysis of low-frequency sound-solid coupling noise of a domestic light bus, and a set of theoretical methods and technical processes that can quickly and accurately predict, analyze and control the low-frequency sound-solid coupling noise are established. The analysis theory and method of TPA are enriched. In this paper, the research and control methods of low-frequency sound-solid coupling noise in the vehicle are summarized and analyzed, and the basic thinking of this paper is to study the acoustic-solid coupling noise based on the theory of transmission and analysis. In this paper, the theoretical basis of low-frequency sound-solid-coupled noise transmission and analysis is presented in this paper. The theory of transfer function and its unbiased estimation are derived, and three methods of working load identification and application range are introduced in detail. The process of using singular value decomposition method to solve the generalized inverse matrix is mainly derived. The analysis of single-reference transfer and the analysis of multi-reference transfer are introduced. The model of the low-frequency sound-solid coupling noise of the whole vehicle is established based on a domestic light bus. The model comprises a plurality of transmission paths which are supported by a power assembly, a front suspension, a rear suspension and a transmission shaft as an excitation end, and the human ear-ear-side noise is a response point. The low-frequency sound-solid coupling noise of the whole vehicle is analyzed based on this model. And the passive end working load of the elastic element is obtained by using the inverse matrix method. The vehicle NVH level analysis is briefly introduced for the target point data in the working condition test before the transfer analysis is carried out. By combining the subjective and objective data, the problem of noise in the position of the driver's ear and the position of the fifth row of passengers at 70 km/ h is determined, and the subjective feeling of the noise is described in detail. In view of the transmission and analysis of the main positions at the frequency of the working condition, a method for evaluating the contribution of the noise transmission path considering the sound pressure level, the amplitude and the phase is presented. The re-packet calculation is further performed for each suspension using this method. A preliminary determination is made of the paths that have a major impact on the different frequencies and the various locations. In order to analyze the mechanism and characteristics of low-frequency noise, an acoustic-solid-coupled finite element model, including vehicle body, frame, door and window, is established. The finite element modeling of the frame and the white body is established, and the modal frequencies of the simulation and the test are basically consistent and the mode shape is consistent. The finite element model of the window and the door is set up, and the whole vehicle model of the closed state of the door and window is obtained by using the correct connection and restraint. Based on the finite element model of the whole vehicle, the finite element model of the acoustic cavity of the seat in the vehicle is established. The acoustic-solid coupling model of the whole vehicle is further established, and the characteristics of the acoustic and structural modes before and after coupling are compared and analyzed. The material sound absorption characteristics and structural damping obtained by the test are applied to the coupling model. In order to verify the low-frequency sound-solid coupling model, the noise in the vehicle is mixed and transmitted and analyzed and compared with the results of the test transmission and analysis, and a more accurate low-frequency sound-solid coupling model is obtained. In order to further reflect the superiority of tpa in the analysis, prediction and application in the initial stage of R & D, the multi-body dynamics model of the whole vehicle with the running system and the b-level road surface is established, and the virtual tpa model of the vehicle sound-solid coupling noise is established by combining the model with the acoustic-solid coupling model. Based on the results of the analysis of the low-frequency sound-solid coupling noise, a comprehensive analysis method of the noise in the vehicle with multi-frequency, multi-response points and multi-working conditions is presented, and the comprehensive contribution is analyzed. The transmission path of low-frequency sound-solid coupling noise contribution to light passenger car is determined. Three tpa methods are analyzed from the three aspects of the theoretical basis, the analysis result, the following optimization and the like, and the superiority of the virtual tpa is proved. The single-stage and secondary transfer-level analysis is carried out for the path with the largest contribution. Through the analysis of single-stage transfer, it is determined that the transmission characteristic is the factor that needs to be optimized, and it is determined that the plate is the main link that needs to be optimized. In this paper, the secondary transmission and analysis of the plate link are carried out, and an algorithm for improving the acoustic contribution coefficient of the plate is proposed, which takes into account the multi-frequency, multi-response points, multi-working conditions and relative relation. Based on this method, the concept of the acoustic effect coefficient of the plate is further put forward, and its meaning is described. Based on the new algorithm and concept, an in-depth secondary transmission and noise reduction analysis is carried out. Based on the results of the analysis, the plate which needs to be controlled is finally determined, the damping noise reduction measures are implemented, and the noise reduction effect is verified by the method of simulation and test. It is proved that the series of theories and methods presented in this paper can be used to analyze, control and predict the low-frequency structure noise.
【學(xué)位授予單位】：吉林大學(xué)
【學(xué)位級(jí)別】：博士
【學(xué)位授予年份】：2017
【分類(lèi)號(hào)】：U467.493
本文編號(hào)：2492873
[Abstract]:With the development of automobile technology and the improvement of living standard, people's riding comfort demand is increasing day by day, and the NVH performance is an important index to determine the ride comfort. The low-frequency noise in the vehicle is an important part of the NVH problem of the whole vehicle. The frequency characteristics of the vehicle are relatively complicated, and it is difficult to analyze the noise source and the influencing factors. Therefore, how to judge the root cause of the low-frequency sound-solid coupling noise in the vehicle more quickly and accurately determine the main components that have an effect on the noise, and to provide the control scheme more specifically, and how to accurately predict the noise in the product development stage, The NVH problem such as low-frequency sound-solid coupling noise in the vehicle is analyzed, and the main research direction of the major automobile manufacturers and research institutes has been made. In this paper, a set of theoretical methods and technical processes for fast and accurate prediction, analysis and control of low-frequency sound-solid coupling noise are established through the deep research on the transmission and analysis of low-frequency sound-solid coupling noise of a domestic light bus, and a set of theoretical methods and technical processes that can quickly and accurately predict, analyze and control the low-frequency sound-solid coupling noise are established. The analysis theory and method of TPA are enriched. In this paper, the research and control methods of low-frequency sound-solid coupling noise in the vehicle are summarized and analyzed, and the basic thinking of this paper is to study the acoustic-solid coupling noise based on the theory of transmission and analysis. In this paper, the theoretical basis of low-frequency sound-solid-coupled noise transmission and analysis is presented in this paper. The theory of transfer function and its unbiased estimation are derived, and three methods of working load identification and application range are introduced in detail. The process of using singular value decomposition method to solve the generalized inverse matrix is mainly derived. The analysis of single-reference transfer and the analysis of multi-reference transfer are introduced. The model of the low-frequency sound-solid coupling noise of the whole vehicle is established based on a domestic light bus. The model comprises a plurality of transmission paths which are supported by a power assembly, a front suspension, a rear suspension and a transmission shaft as an excitation end, and the human ear-ear-side noise is a response point. The low-frequency sound-solid coupling noise of the whole vehicle is analyzed based on this model. And the passive end working load of the elastic element is obtained by using the inverse matrix method. The vehicle NVH level analysis is briefly introduced for the target point data in the working condition test before the transfer analysis is carried out. By combining the subjective and objective data, the problem of noise in the position of the driver's ear and the position of the fifth row of passengers at 70 km/ h is determined, and the subjective feeling of the noise is described in detail. In view of the transmission and analysis of the main positions at the frequency of the working condition, a method for evaluating the contribution of the noise transmission path considering the sound pressure level, the amplitude and the phase is presented. The re-packet calculation is further performed for each suspension using this method. A preliminary determination is made of the paths that have a major impact on the different frequencies and the various locations. In order to analyze the mechanism and characteristics of low-frequency noise, an acoustic-solid-coupled finite element model, including vehicle body, frame, door and window, is established. The finite element modeling of the frame and the white body is established, and the modal frequencies of the simulation and the test are basically consistent and the mode shape is consistent. The finite element model of the window and the door is set up, and the whole vehicle model of the closed state of the door and window is obtained by using the correct connection and restraint. Based on the finite element model of the whole vehicle, the finite element model of the acoustic cavity of the seat in the vehicle is established. The acoustic-solid coupling model of the whole vehicle is further established, and the characteristics of the acoustic and structural modes before and after coupling are compared and analyzed. The material sound absorption characteristics and structural damping obtained by the test are applied to the coupling model. In order to verify the low-frequency sound-solid coupling model, the noise in the vehicle is mixed and transmitted and analyzed and compared with the results of the test transmission and analysis, and a more accurate low-frequency sound-solid coupling model is obtained. In order to further reflect the superiority of tpa in the analysis, prediction and application in the initial stage of R & D, the multi-body dynamics model of the whole vehicle with the running system and the b-level road surface is established, and the virtual tpa model of the vehicle sound-solid coupling noise is established by combining the model with the acoustic-solid coupling model. Based on the results of the analysis of the low-frequency sound-solid coupling noise, a comprehensive analysis method of the noise in the vehicle with multi-frequency, multi-response points and multi-working conditions is presented, and the comprehensive contribution is analyzed. The transmission path of low-frequency sound-solid coupling noise contribution to light passenger car is determined. Three tpa methods are analyzed from the three aspects of the theoretical basis, the analysis result, the following optimization and the like, and the superiority of the virtual tpa is proved. The single-stage and secondary transfer-level analysis is carried out for the path with the largest contribution. Through the analysis of single-stage transfer, it is determined that the transmission characteristic is the factor that needs to be optimized, and it is determined that the plate is the main link that needs to be optimized. In this paper, the secondary transmission and analysis of the plate link are carried out, and an algorithm for improving the acoustic contribution coefficient of the plate is proposed, which takes into account the multi-frequency, multi-response points, multi-working conditions and relative relation. Based on this method, the concept of the acoustic effect coefficient of the plate is further put forward, and its meaning is described. Based on the new algorithm and concept, an in-depth secondary transmission and noise reduction analysis is carried out. Based on the results of the analysis, the plate which needs to be controlled is finally determined, the damping noise reduction measures are implemented, and the noise reduction effect is verified by the method of simulation and test. It is proved that the series of theories and methods presented in this paper can be used to analyze, control and predict the low-frequency structure noise.
【學(xué)位授予單位】：吉林大學(xué)
【學(xué)位級(jí)別】：博士
【學(xué)位授予年份】：2017
【分類(lèi)號(hào)】：U467.493
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3 金鵬;段傳學(xué);吳群力;;基于運(yùn)轉(zhuǎn)工況測(cè)試條件的噪聲振動(dòng)傳遞路徑分析方法[A];運(yùn)輸噪聲的預(yù)測(cè)與控制——2009全國(guó)環(huán)境聲學(xué)學(xué)術(shù)會(huì)議論文集[C];2009年
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