發(fā)布時間：2019-06-04 17:24

【摘要】：隨著汽車技術(shù)的發(fā)展與生活水平的提高,人們對汽車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)。車內(nèi)低頻噪聲問題作為整車NVH問題的一個重要組成部分,由其頻率特征造成了其產(chǎn)生和傳播過程相對復(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內(nèi)低頻聲-固耦合噪聲產(chǎn)生的根源、更加準(zhǔn)確確定對噪聲有影響的主要部件、更有針對性的提出控制方案,以及在產(chǎn)品開發(fā)階段如何準(zhǔn)確預(yù)測、分析車內(nèi)低頻聲-固耦合噪聲等NVH問題,成為了各大汽車廠商和研究機構(gòu)的主要研究方向。本文通過對某國產(chǎn)輕型客車低頻聲-固耦合噪聲的傳遞路徑分析及控制方法進行深入研究,建立了一整套能夠快速、準(zhǔn)確地預(yù)測、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。針對車內(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)展趨勢進行了總結(jié)與分析,確定了本文基于傳遞路徑分析理論對聲-固耦合噪聲進行研究的基本思路。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)的理論及其無偏估計;詳細(xì)介紹了三種工作載荷識別方法以及應(yīng)用范圍。重點推導(dǎo)了應(yīng)用奇異值分解方法求解廣義逆矩陣的過程。介紹了單參考傳遞路徑分析和多參考傳遞路徑分析�；谀硣a(chǎn)輕型客車建立了整車低頻聲-固耦合噪聲的TPA模型。該模型包括了以動力總成懸置,前、后懸架以及傳動軸支撐為激勵端,以人耳耳旁噪聲為響應(yīng)點的多條傳遞路徑�；诖四Ｐ蛯φ嚨皖l聲-固耦合噪聲進行了傳遞路徑分析。對以駕駛員、第二排乘客以及第五排乘客位置的耳旁噪聲為響應(yīng)點的多條傳遞路徑進行了結(jié)構(gòu)路徑傳遞函數(shù)的測試;利用逆矩陣法獲取了彈性元件被動端工作載荷。在進行傳遞路徑分析之前,針對工況試驗中的目標(biāo)點數(shù)據(jù)進行了簡要的車內(nèi)NVH水平分析。結(jié)合主觀評價與客觀數(shù)據(jù),確定70km/h時駕駛員耳旁位置以及第五排乘客耳旁位置存在噪聲問題,并詳細(xì)描述了噪聲的主觀感受。針對該工況問題頻率下各主要位置進行傳遞路徑分析,并提出了一種綜合考慮聲壓級、幅值、相位的噪聲傳遞路徑貢獻量評價方法。利用這種方法進一步針對每一個懸置進行了重新分組計算。初步確定了對不同頻率、各個位置有主要影響的路徑。為了深入分析低頻噪聲問題的產(chǎn)生機理及特征,本文建立了包含車身、車架、車門和車窗等在內(nèi)的聲-固耦合有限元模型。逐步建立了車架及白車身的有限元建模,并驗證了仿真與和試驗的模態(tài)頻率基本吻合,模態(tài)振型一致。進一步建立了車窗及車門的有限元模型,并用正確的連接及約束方式連接,得到了門窗緊閉狀態(tài)的整車模型。以整車有限元模型為基礎(chǔ),建立了考慮車內(nèi)座椅的聲腔有限元模型。進一步建立了整車聲-固耦合模型,對耦合前后聲腔和結(jié)構(gòu)模態(tài)的特征進行了對比分析。將通過試驗獲取的材料吸聲特性及結(jié)構(gòu)阻尼施加到耦合模型上。為了驗證低頻聲-固耦合模型,對車內(nèi)噪聲進行了混合傳遞路徑分析并與試驗傳遞路徑分析的結(jié)果進行了對比,得到了較準(zhǔn)確的低頻聲-固耦合模型。為了進一步體現(xiàn)tpa在分析、預(yù)測以及應(yīng)用在研發(fā)初期時的優(yōu)越性,本文建立了包含行駛系及b級路面的整車多體動力學(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)點以及多工況的車內(nèi)噪聲綜合傳遞路徑分析方法,并進行了綜合貢獻量分析,確定了對輕型客車車內(nèi)低頻聲-固耦合噪聲貢獻量較大的傳遞路徑。從理論基礎(chǔ)、分析結(jié)果、以及后續(xù)優(yōu)化等三個方面對三種tpa方法進行分析,證明了虛擬tpa的優(yōu)越性。針對貢獻量最大的路徑進行了單級以及次級傳遞路徑分析。通過單級傳遞路徑分析,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)。針對板件環(huán)節(jié)進行了次級傳遞路徑分析,并提出了一種考慮多頻、多響應(yīng)點、多工況以及相對關(guān)系的改進板件聲學(xué)貢獻量系數(shù)算法�；谠摲椒�,進一步提出了板件聲學(xué)影響系數(shù)的概念,并對其含義進行了說明�；谛碌乃惴ê透拍钸M行了深入的次級傳遞路徑分析,依據(jù)分析結(jié)果最終確定了需要控制的板件,實施了阻尼降噪措施,并通過仿真及試驗的方法驗證了降噪效果。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)位級別】：博士
【學(xué)位授予年份】：2017
【分類號】：U467.493

【相似文獻】

相關(guān)期刊論文 前10條

1 張義民;;頻域內(nèi)振動傳遞路徑的傳遞度排序[J];自然科學(xué)進展;2007年03期

2 趙薇;張義民;;具有直線與搖擺耦合運動的振動傳遞路徑系統(tǒng)的參數(shù)靈敏度分析[J];噪聲與振動控制;2008年06期

3 柳瑞鋒;周璞;王強;;傳遞路徑分析在結(jié)構(gòu)設(shè)計中的應(yīng)用[J];噪聲與振動控制;2012年04期

4 李傳兵;王彬星;李宏成;王月琳;鄭四發(fā);;運行工況傳遞路徑分析識別車內(nèi)聲源[J];噪聲與振動控制;2013年02期

5 張義民;李鶴;聞邦椿;;基于靈敏度的振動傳遞路徑的參數(shù)貢獻度分析[J];機械工程學(xué)報;2008年10期

6 王萬英;靳曉雄;彭為;郭輝;尹燕莉;;輪胎振動噪聲結(jié)構(gòu)傳遞路徑分析[J];振動與沖擊;2010年06期

7 李靜波;王宏偉;王暉;劉瀟;;基于傳遞路徑分析的正時鏈條階次噪聲優(yōu)化[J];內(nèi)燃機;2013年04期

8 張磊;曹躍云;楊自春;何元安;;水下圓柱殼體結(jié)構(gòu)噪聲的工況傳遞路徑分析[J];振動.測試與診斷;2012年06期

9 關(guān)偉;李俊;;傳遞路徑分析的改進方法及實車應(yīng)用[J];農(nóng)業(yè)裝備與車輛工程;2013年11期

10 張義民;;時域內(nèi)振動與噪聲傳遞路徑系統(tǒng)的路徑傳遞度探索[J];航空學(xué)報;2007年04期

相關(guān)會議論文 前3條

1 趙彤航;宋傳學(xué);盧炳武;;基于傳遞路徑分析的車外噪聲源識別[A];2007年APC聯(lián)合學(xué)術(shù)年會論文集[C];2007年

2 王曉峰;韓德寶;門麗杰;;有限元方法在傳遞路徑識別中的應(yīng)用研究[A];第十四屆船舶水下噪聲學(xué)術(shù)討論會論文集[C];2013年

3 金鵬;段傳學(xué);吳群力;;基于運轉(zhuǎn)工況測試條件的噪聲振動傳遞路徑分析方法[A];運輸噪聲的預(yù)測與控制——2009全國環(huán)境聲學(xué)學(xué)術(shù)會議論文集[C];2009年

相關(guān)博士學(xué)位論文 前5條

1 莫愁;傳遞路徑分析方法理論研究及其汽車降噪實踐[D];華南理工大學(xué);2015年

2 徐猛;基于傳遞路徑分析方法的車內(nèi)低頻結(jié)構(gòu)噪聲識別與控制[D];天津大學(xué);2014年

3 祖慶華;輕型客車低頻聲—固耦合噪聲傳遞路徑分析與控制[D];吉林大學(xué);2017年

4 趙薇;機械振動傳遞路徑系統(tǒng)傳遞性的研究與應(yīng)用[D];東北大學(xué);2012年

5 宋海生;基于擴展OPAX傳遞路徑方法的輕型客車振動控制研究[D];吉林大學(xué);2012年

相關(guān)碩士學(xué)位論文 前8條

1 白海飛;動車組噪聲振動傳遞路徑測試與分析[D];北京交通大學(xué);2016年

2 湯毓;基于混合傳遞路徑分析方法的低速載重貨車駕駛室振動控制研究[D];廣西科技大學(xué);2015年

3 雷鵬;地鐵車輛車內(nèi)噪聲源傳遞路徑分析研究[D];北京交通大學(xué);2016年

4 鄭啟明;基于工況傳遞路徑分析的縫紉式訂標(biāo)機振動研究[D];江南大學(xué);2016年

5 張擰;噪聲振動傳遞路徑研究及其應(yīng)用[D];北京交通大學(xué);2015年

6 付俊涵;傳遞路徑中聲源串?dāng)_消除問題研究[D];北京交通大學(xué);2012年

7 劉洪達;復(fù)雜殼體耦合系統(tǒng)載荷提取及振動特性分析[D];哈爾濱工程大學(xué);2013年

8 龐曉柯;基于工況傳遞路徑分析的挖掘機座椅振動研究[D];山東大學(xué);2014年

，

本文編號：2492873