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基于雷诺时均方程(RANS)及双方程湍流模型,建立了船用大功率增压器压气机的内部流场计算模型;计算了压气机叶轮流道内的流速分布和湍流流场,得到叶片顶部出口附近的流速分布在1.02马赫和1.1马赫之间;采用基于声比拟的数值积分方法(FW-H方程),得到了压气机叶轮的气动噪声源,并比较了主叶片和分流叶片顶部出口位置的气动噪声频谱特征,发现两者的噪声级及叶频分布存在差异。计算表明:压气机在轴频及其谐波频率处的噪声远小于叶频噪声,主流叶片及分流叶片紊流的噪声成因不同;压气机内部流噪声源的大小主要取决于气流速度;压气机转速由8000r/min增加至16000r/min、由16000r/min增加至22000r/min,流噪声的幅值约增加12dB。
Based on the Reynolds average equation (RANS) and the two-equation turbulence model, the internal flow field model of a marine high-power turbocharger compressor was established. The flow velocity distribution and turbulent flow field in the compressor impeller flow path were calculated. In the vicinity of the flow rate distribution between the Mach 1.0 and Mach Mach 1.0; using numerical simulation based on acoustic integration (FW-H equation), the aerodynamic noise source of the compressor impeller was obtained and compared with the outlet of the main blade and the top of the splitter blade The characteristics of the aerodynamic noise spectrum show that the noise level and the frequency distribution of the two are different. Computation shows that the noise of the compressor at the axial frequency and its harmonic frequency is far less than the leaf frequency noise and the noise causes of the turbulence of the main blades and the splitter blades are different. The size of the noise source inside the compressor depends mainly on the air velocity. Speed from 8000r / min increased to 16000r / min, from 16000r / min increased to 22000r / min, the flow noise amplitude increased by about 12dB.