Numerical and experimental analyses of intake silencer and its effects on turbocharger compressor performance
|
|
- Hilary Steven Cooper
- 5 years ago
- Views:
Transcription
1 Research Article Numerical and experimental analyses of intake silencer and its effects on turbocharger compressor performance Advances in Mechanical Engineering 2019, Vol. 11(3) 1 15 Ó The Author(s) 2019 DOI: / journals.sagepub.com/home/ade Chen Liu 1,YipengCao 1,YangLiu 2, Wenping Zhang 1, Pingjian Ming 1 and Sihui Ding 1 Abstract Numerical studies of a marine diesel engine intake silencer are conducted to evaluate its performance, and effects of the silencer on the turbocharger compressor performance are also discussed. The results show that the duct acoustic mode method can be used in the silencer transmission loss prediction, and the predicted noise reduction and main frequency range agree with the measurements fairly well. However, it is found that the silencer compromises the compressor performance by shortening its operating range. It is found that the static pressure on the compressor blade surface is decreased, thus the compressor total-to-total pressure ratio and isentropic efficiency are reduced. Pressure fluctuations at compressor rotor and stator inlets enhanced when a silencer is installed, which means the trend of pressure spectrum in the rotor and stator passage is changed. Compared with the results of a compressor in natural aspiration, it is found that the silencer can significantly reduce high-frequency noise. In particular, it is quite effective in tonal noise reduction. In addition, the compressor inlet noise spectrum indicates that noise radiation characteristics are different with a silencer installed. Keywords Intake silencer, turbocharger, noise, compressor, performance Date received: 5 October 2018; accepted: 2 January 2019 Handling Editor: Jose Ramon Serrano Introduction Turbochargers are widely used in marine low-speed diesel engines, and it can improve the in-cylinder combustion, increase the engine output power, and reduce the fuel consumption and exhaust emission. 1 Although the turbocharging technology is necessary in marine diesel engines, it also has some negative effects, for example, high cabin noise. Recently, the requirements of marine cabin noise are becoming more stricter, so the marine diesel engine noise control becomes a trending topic. The existing literature shows that main noise sources of turbocharging diesel engines consist of mechanical noise, combustion noise, and aerodynamic noise. 2 4 The mechanical noise can be reduced by optimal designs of crank train, value train, and other moving components; while the combustion noise has been significantly reduced by the use of electronically controlled injection system. 5,6 As a result, the aerodynamic noise, specifically turbocharger noise, becomes the prominent issue in marine diesel engine noise. 1 College of Power and Energy Engineering, Harbin Engineering University, Harbin, China 2 Chongqing Jiangjin Shipbuilding Industry Co., Ltd., Chongqing, China Corresponding author: Yipeng Cao, College of Power and Energy Engineering, Harbin Engineering University, Harbin , China. yipengcao06@163.com Creative Commons CC BY: This article is distributed under the terms of the Creative Commons Attribution 4.0 License ( which permits any use, reproduction and distribution of the work without further permission provided the original work is attributed as specified on the SAGE and Open Access pages ( open-access-at-sage).
2 2 Advances in Mechanical Engineering Tremendous attention has been paid to turbocharger in the past decades. Li and Liu both studied turbocharger noise characteristics through experiments, and they found that the main noise source of turbocharger is the compressor noise, rather than turbine noise or structural radiation noise. 7,8 Moreover, the applications of the exhaust silencer and the acoustic enclosure significantly reduce the turbine noise and structural radiation noise Raitor and Neise carried out experiments to investigate the compressor noise generation mechanisms. On the compressor inlet side, the compressor noise is dominated by tip clearance noise (TCN) with low rotating speeds, and the main feature is tonal noise (noise peaks occur at shaft rotation frequency, blade passing frequency, and its harmonics) at sonic Mach number. Furthermore, tonal noise and buzz-saw noise (noise peaks occur at shaft rotation frequency and its harmonics) become the main noise sources in supersonic flow conditions. 12 Meanwhile, broadband noise can be obtained within the entire frequency range of interest. Several narrow bands were detected at khz in compression ignition engines and at 5 7 khz in spark-ignition engines In summary, the compressor noise components are complex, and the main noise source varies with operating conditions. Therefore, the effective control of compressor intake noise is difficult. Nowadays, intake silencers are adopted to reduce the compressor intake noise. There are different kinds of silencers for different noise sources, including reactive silencer, dissipative silencer, and their combinations. The sound energy in the reactive silencer is consumed by the reflection, and the interference induced by duct impedance changes. In addition, the sound energy in the dissipative silencer is transformed into heat energy through the friction between the sound wave and sound absorbing materials. Lee et al. 17 designed a multi-chamber silencer, and the experimental and analytical results showed that it is effective in whoosh noise control. Abom and Kabral developed a compact dissipative silencer, which is based on a combination of a micro-perforated tube and a locally reacting cavity. In more than an octave, noise reduction was more than 30 db for its high damping effects. 18,19 Tian et al. 20 introduced a reactive silencer to reduce turbocharger synchronous noise, and the results obtained in a vehicle test indicated that the silencer can reduce noise effectively in the frequency range of Hz. The aforementioned researches obtained many benefits from the compressor intake noise control, but they mainly concentrated on the automotive turbocharger broadband noise. There are only few literatures focusing on the performance of turbocharger compressor intake silencers of marine diesel engines. Many publications assume that the inlet flow field is stable; therefore, the effects of the inlet distortion are neglected However, in a real condition, the intake pipelines or silencers mounted in the compressor inlet would change the uniformity of the intake air, thus the compressor performance is closely related to the impeller inlet flow. It is necessary to study the effects of inlet distortion induced by intake pipelines or silencers on the compressor performance. Galindo et al. 24 investigated the effects of intake pipelines on automotive turbocharger compressor, and the results showed that pressure ratio and isentropic efficiency of a compressor are reduced by increasing the pipeline length or decreasing the pipeline diameter. Serrano compared effects of the straight duct, the elbow, and elbow with guide vanes on turbocharger performance and operation stability. It is found that the air intake uniformity and total pressure loss are two deciding factors of the compressor performance. 25 Yang, Li, and Wang further studied the effects of elbow shapes and their installation positions on a centrifugal compressor. This study gave suggestions for the optimal design of an intake pipeline For turbocharging marine diesel engines, the airflow inlet is located at the cabin, so the intake silencers are necessary for cabin noise control. The compressor performance is influenced by the complex inlet flow that is caused by intake silencer, so it is necessary to study the effects of an intake silencer on the compressor performance. The performance of a marine diesel engine turbocharger intake silencer and the effects of silencer on turbocharger compressor were analyzed in this article. First, the intake noise characteristics of marine diesel engine turbocharger compressor were experimentally investigated, and the intake silencer structure was also designed. Then, the intake silencer performance was studied, such as total pressure loss and transmission loss (TL). Furthermore, the effects of the silencer structure on the compressor global performance, unsteady flow characteristics, and intake noise were numerically analyzed. All analysis methods are shown in Figure 1. Design and numerical analysis of intake silencer Turbocharger intake noise characteristics The turbocharger intake noise characteristics were measured in a turbocharger performance test bench, which is shown in Figure 2. In order to eliminate the influence of other noise sources, the turbine outlet was directly connected to the outside, and all connecting pipelines and turbocharger housing were isolated using acoustic materials. The compressor intake noise was tested under the natural aspiration condition to obtain the original measurement results. The measurement points were also shown in Figure 1. The location of measurement points is higher than 1 m from the floor, which was also isolated by the acoustic material. Therefore,
3 Liu et al. 3 Figure 1. Research flow diagram. Figure 2. Experimental equipment of compressor intake noise measurement. the ground reflection effects were eliminated. Furthermore, the environment correction was conducted in experimental results analysis to take into account the effects of acoustic reflection on measured sound pressure level (SPL). All the five measurement points are arranged in semicircle with counter-clockwise distribution. The microphones manufactured by BSWA TECH (Model MPA401) were used to measure the compressor intake noise. Data were analyzed by the B&K 3560D data acquisition front-end and B&K PULSE 12.6 software analysis system, respectively. The intake noise characteristics at compressor design speed are shown in Figure 3. It can be clearly found that the tonal noise and buzz-saw noise are the main noise sources, and the tonal noise is the dominant spectral component. The compressor intake noise has high SPL in nearly entire frequency range (0 10 khz), especially at high frequencies like blade passing frequency
4 4 Advances in Mechanical Engineering Figure 3. Intake noise characteristics at design speed: linear spectrum and one-third octave spectrum. Figure 4. Cutaway view of intake silencer: vertical section and cross section. (BPF, the definition is shown as in equation (1)) and its harmonics Intake silencer design f BPF = nz 60 ð1þ In this article, the intake silencer structure is shown in Figure 3, and its design is based on previous studies The silencer consists of the front wall, the end wall, 33 sound absorbing blades, 3 ribs, and other additional structures, as shown in Figure 4. The size of the temperature measurement hole, pressure measurement hole, oil gas suction hole, and cleaning water pipe is small. Hence, all of these components are neglected in the silencer calculation model. In order to obtain acoustic cavities with different volumes, the arrangement of ribs is not equidistance. The sound absorbing material used in the silencer is aluminum silicate wool. The airflow direction of the intake silencer is same as the radial direction, which can guarantee noise reduction, increase the airflow passage, and filter the air. Numerical analysis of intake silencer performance Two most important parameters of a silencer are the resistance performance and noise reduction. The former often refers to the total pressure loss between the silencer inlet and the outlet. The latter has different evaluations, including TL and insertion loss (IL). 32 The TL is defined as the difference between the incident sound power level on silencer acoustic inlet plane and the transmission sound power level on the silencer acoustic outlet plane, as shown in equation (2). This parameter is often used in numerical calculations TL = 10 log W i ð2þ W t
5 Liu et al. 5 Figure 5. Flow field model of intake silencer. The IL is defined as the difference between the SPL (or sound power level) obtained at a fixed measurement points before and after the silencer was installed, as shown in equation (3). This parameter is often used in experimental analyses IL = L p(sp) L p(is) ð3þ Pressure loss. The flow field model of the intake silencer is shown in Figure 5, and the structure of sound absorbing blades and ribs is removed to obtain the airflow passage. Because this model is also used in the calculation of compressor performance with silencer installed, the compressor rotor shaft head is considered in the numerical model. The overall mesh consists of 1.18 million structured hexahedral cells, in order to satisfy the requirement of near wall y + value that limits to 1. The three-dimensional steady flow of intake silencer was simulated by ANSYS CFX. K-omega shear stress transport (SST) turbulence model was employed, thus the boundary conditions near the solid walls were not analyzed by the standard wall function that was used for rough meshes. The inlet boundary condition was set as fixed inlet pressure and fixed inlet temperature. The outlet boundary conditions were set as fixed mass flow rate. The air property was set as ideal gas. The solid wall roughness was set as 50 mm. As shown in Figure 6, the total pressure loss induced by intake silencer was calculated under eight different operating conditions, and the volume flow rate covered the entire compressor operating range. The total pressure loss is defined as the total pressure difference between the silencer inlet and the outlet, including the pressure loss caused by the pipeline of the silencer outlet and the sound absorbing structure. The pressure loss caused by the silencer outlet pipeline is eliminated in the corrected pressure loss to show the resistance performance of sound absorbing structure. The total pressure loss increases with the increase in the Figure 6. Total pressure loss caused by silencer. volume flow rate. The results show that the corrected pressure loss is lower than 1000 Pa in nearly the entire flow range, which means the intake silencer design is feasible. TL. The sound absorbing material used in the silencer is aluminum silicate wool. The acoustic characteristics of aluminum silicate wool were experimental measured by B&K-4206T impedance tube, as shown in Figure 7. The experimental method was referred to ISO The complex impedance ratio and complex wavenumber ratio were shown in Figure 7 and (c). The experimental data were treated with curve fitting. The empirical formula of the acoustic characteristics of aluminum silicate wool was obtained as follows z z 0 = :88f 0:75 i 37:89f 0:73 ð4þ k = :81f 0:7 i 26:27f 0:59 ð5þ k 0 In the TL calculation using traditional finite element method (FEM), such as commercial software LMS Virtual.Lab, where the acoustic inlet is defined as unit particle velocity 1 m/s, the acoustic outlet is set as nonreflection boundary. In this situation, single node on the inlet plane and the outlet plane is selected to represent the entire plane, and a good result can be obtained in the frequency range of plane wave. However, the sound wave radiation is affected by the structure, size, and material of the silencer duct. Therefore, the highorder waves in the silencer must be considered. Although these boundary conditions can fully describe the sound field and acoustic model in the silencer, there are still some limitations. The duct acoustic mode method is used in this article to predict the TL of intake silencer, which is also based on FEM. However, this method is able to take into account the high-order waves. The numerical model is shown in Figure 8, in which the acoustic inlet is defined as a sound wave represented by acoustic mode, the
6 6 Advances in Mechanical Engineering (c) Figure 7. Experimental measurement of acoustic characteristics of aluminum silicate wool: impedance tube (B&K-4206T), complex impedance ratio, and (c) complex wavenumber ratio. p m i = pm in + r 0c 2 p n t = pn out Thus, equation (2) can be rewritten as Sp m i TL = 10 log pm i Am 10 Sp n t pn t An ð6þ ð7þ ð8þ The maximum frequency in this article is 10 khz, and the mesh grid size can be calculated using the Nyquist sampling theorem as follows l size ł c 6f max ð9þ Figure 8. Numerical model for silencer TL prediction. acoustic outlet is set as automatically matching layer (AML), and the TL is calculated with equation (2). All simulations were completed using commercial software LMS Virtual.Lab. Based on the definition of TL and the acoustic decomposition theory, the incidence sound pressure of grid cell m on inlet plane and the transmission sound pressure of grid cell n on outlet plane are defined as follows The sound velocity at 298 K is 344 m/s, and thus, the maximum mesh size is 5 mm. In the TL calculation with the duct acoustic mode method, all the modal waves were used to describe the sound wave propagation. If the calculation frequency is higher than the cut-off frequency of a certain order mode, the certain order modal wave can propagate in the silencer. Otherwise, the certain order of mode wave is attenuated rapidly. The cutoff frequency is calculated as follows f cut off = 1 M 2 1=2 k m, n c 2pa ð10þ
7 Liu et al. 7 Table 1. Modal wavenumber of acoustic model (m, n). k m, n m =0 m =1 m =2 m =3 m =4 n = n = n = n = n = Figure 10. Silencer static acoustic test bench. Figure 9. Transmission loss of intake silencer. The k m, n was the modal wavenumber of acoustic model (m, n), which can also be called modal Bessel zeros. Equation (10) is applicable to circular pipelines, and it can be used to set the acoustic inlet boundary in the intake silencer TL calculation because the acoustic inlet of intake silencer was a circular plane. The modal wavenumber of acoustic model was shown in Table 1. The amplitude and the phase of every mode used are set as 1 and 0 W, respectively. Air density is kg/s, and speed of sound is 344 m/s. Multiple high-order acoustic modes were used in the acoustic inlet, which is shown in Table 1. The acoustic outlet is set as AML boundary, and all the other walls were set as rigid wall. The TL calculation result is shown in Figure 9, and the intake silencer can achieve a significant noise reduction. The TL values of octaves are higher than 20 db in the frequency range of 2 10 khz. Limited to the silencer structure size, the noise reduction is lower than 10 db in the frequency range of 0 1 khz. Experimental verification. Silencer static acoustic test was conducted to validate the numerical result, and the test bench is shown in Figure 10. The noise source, connecting pipeline, and intake silencer are arranged in a straight line, which makes the sound wave directly propagates through the connecting pipeline to the intake silencer. The measurement points arrangement is shown in Figure 11, and there were four microphones located at the measurement surface, and the experiments were conducted with intake silencer and substitution pipe, respectively. Figure 12 shows the comparison of the experimental and calculated silencer IL. It can be found that the IL values in high frequency (2 10 khz) are also more than 20 db, which indicates that the silencer can reduce highfrequency noise effectively. Meanwhile, the comparison of calculated IL and measured IL shows that the main noise reduction frequency range and noise reduction values are similar. The total calculated and measured IL is and db, respectively. Effect of the silencer on compressor performance Compressor global performance The intake silencer is mounted to the compressor inlet, as a part of marine diesel engine turbocharger. The original compressor structure is composed of the inlet duct, impeller, diffuser, and volute. The principle geometric structure and parameters of the compressor used in this article are shown in Table 2. A three-dimensional numerical model of the centrifugal compressor was established by ANSYS CFX. The impeller was discretized along with the inlet duct, vane diffuser, and volute, and the tip clearance of the impeller was also considered in the computational fluid dynamics (CFD) model. To better calculate the compressor unsteady flow details, local mesh refinement and boundary layers were applied in the complex flow
8 8 Advances in Mechanical Engineering Figure 11. Positions of noise measurement points: substitution pipe, silencer, and (c) measurement surface (view of section A). (c) area. Three domain interfaces were defined between the inlet duct impeller, impeller diffuser, and diffuser volute, which facilitated the compressor flow calculation. The numerical model of compressor under natural aspiration condition is shown in Figure 13. The grid independence analysis at compressor design operating condition is shown in Table 3. It can be found that the medium mesh is sufficient for numerical simulations. When the silencer is installed, the inlet duct is replaced with the numerical model of silencer, which is shown in Figure 5. The three-dimensional compressor steady flow was simulated using Reynolds-averaged Navier Stokes (RANS) k-omega SST model. The fixed inlet pressure, inlet temperature, and outlet pressure boundary conditions were used, but when the operating conditions moved toward the surge line, the fixed inlet mass flow rate and temperature were applied to ensure the convergence of the numerical computation. 33,34 As shown by the previous studies, heat transfer between the highspeed compressors and their surroundings can be Figure 12. Insertion loss of intake silencer. neglected, 35 thus all wall conditions in the numerical model were set to adiabatic. The variation of compressor performance is shown in Figure 14. Under the natural aspiration condition, the comparison of the experimental measurement and the numerical calculation indicates that the numerical
9 Liu et al. 9 Table 2. Compressor geometric parameters. Parameter Value Main blade number 8 Splitter blade number 8 Diffuser blade number 18 Design speed (r/min) 23,500 Design pressure ratio 4.2 Impeller inlet diameter D1 (mm) 149 Impeller outlet diameter D2 (mm) 410 Diffuser inlet diameter D3 (mm) 450 Volute inlet diameter D4 (mm) 590 results are accurate. The numerical model can be used in the discussion of the effects of the silencer structure on compressor performance. When the intake silencer is installed, the maximum volume flow rate at every speed line (choke line) reduced, the surge line moves to high flow rate, and the reduction in compressor flow range is nearly m 3 /s. Thus, the compressor operating range was shortened. The high-efficiency area also decreases, and the maximum efficiency moves to the surge line, which is not ideal for compressor operations. Meanwhile, compared with the results of compressor natural aspiration, the total-to-total pressure ratio and efficiency at the same speed and flow rate decrease. With the increase in compressor speed, the trends become more obvious. The analysis results above indicate that intake silencer has a great influence on compressor performance. In order to further explain the diminishing compressor performance when the intake silencer is installed, the compressor rotor blade load is discussed. The blade load capacity can be expressed by the static pressure distribution of compressor rotor blade surface. It is shown in Figure 15 that the static pressure decreases when the silencer is installed. Furthermore, with the compressor operating condition moves to the surge line, such downtrend of static pressure is more obvious. Because the airflow at the impeller inlet is approximately one-dimensional flow, the one-dimensional pipe flow formula can be referred m = k p pt ffiffiffiffi qa ð11þ Under the condition of same flow rate and the total temperature, the total pressure at impeller inlet decreases when pressure loss increases, thus the axial flow coefficient q and axial velocity increase. If the rotating speed is the same, high axial velocity makes the attack angle to diverge from the design value, which means the compressor load is reduced. Under a natural aspiration condition, there is only a straight short duct in front of the impeller inlet. The T t Figure 13. Numerical model of compressor natural aspiration. Table 3. Mesh independence analysis (compressor design operating condition). Parameter Coarse mesh Middle mesh Fine mesh Mesh cell account y + limit Pressure ratio Efficiency resultant total pressure loss is much less than that when the silencer is installed. The total pressure loss induced the compressor rotor blade load reduction and decreased the total-to-total pressure ratio and efficiency at the same speed and flow rate, which are shown in Figure 14. The static pressure distribution on compressor rotor blade surface at near-surge conditions in different operating speeds is shown in Figure 16. The total pressure loss increases with the rotating speed, so the trend of static pressure is also more obvious with the rotating speed. Compressor unsteady flow characteristics The three-dimensional unsteady flow of the compressor was simulated under the design operating condition. The total time of every calculation is s, which is more than eight impeller revolutions. The time step size can be calculated by the sensitivity analysis conducted by Navarro, 16 which suggested that the impeller rotates no more than 1 in each time step. The time step size used in this article is 5e-6 s, in order to obtain accurate unsteady flow results. The pressure fluctuation at rotor inlet and stator inlet is monitored, and the results are shown in Figures 17 and 18. The compressor blade rotation caused periodic pressure fluctuation, and every rotating blade leads to a fluctuation peak.
10 10 Advances in Mechanical Engineering Figure 14. Variation of compressor performance: total-to-total pressure ratio and isentropic efficiency. Figure 15. Static pressure distribution of compressor rotor blade surface at 50% span, design speed, natural aspiration (black line), and silencer installed (red line). The pressure fluctuation amplitude peaks appear at BPF and its harmonics, as shown in Figures 17 and 18. The pressure fluctuation at rotor inlet is mainly affected by the main blades. Although the splitter blade has less effects than the main blade, the pressure fluctuation at stator inlet is affected by both main blades and splitter blades. Compared with the numerical results under natural aspiration condition, the pressure fluctuation at both rotor inlet and the stator inlet increases after the intake silencer is installed. The pressure fluctuation increases more than 1500 and 8000 Pa at compressor rotor and Figure 16. Static pressure distribution of compressor rotor blade surface at 50% span, near-surge conditions at different operating speeds, natural aspiration (black line), and silencer installed (red line). stator inlet, respectively. According to equation (7), under the condition of same flow rate and the total temperature, the total pressure at impeller inlet decreases when pressure loss increases after silencer is installed, thus the axial flow velocity increases, and the interaction between the inlet airflow and blades is stronger. Furthermore, the pressure fluctuation was induced by the interaction between inlet flow air and rotating blades, and the total pressure loss at blade inlet plane was nearly uniform, thus the interaction between inlet airflow and different blades was nearly the same and
11 Liu et al. 11 Figure 17. Pressure fluctuation at monitoring point of compressor rotor inlet: time domain and frequency domain. Figure 18. Pressure fluctuation at monitoring point of compressor stator inlet: time domain and frequency domain. the time period was closely related to compressor rotating speed, which would represent a significant pressure amplitude peak at shaft rotation frequency. The above phenomena indicate that the flow structure of the compressor becomes more complex when the intake silencer is installed, and these results can also prove that the effects of intake silencer on compressor performance should not be neglected. Compressor noise reduction In this article, FEM was used to predict the compressor noise. The pressure fluctuation at each grid node on the impeller inlet plane was monitored at each time step in the unsteady flow calculation. The pressure fluctuation was transformed to a simplified dipole source via fast Fourier transform (FFT). According to the theory of aero-acoustics, compressor noise sources can be divided into monopole, dipole, and quadrupole sources. The dimensional analysis of the fluid noise source indicates that the dipole source is the main noise source, and the monopole source and the quadrupole source can be neglected. 36,37 The numerical models for compressor noise prediction are shown in Figure 19, which are referred to the positions of the measurement points displayed in Figure 11 and. The diameter of compressor impeller inlet is m and the maximum diameter of the silencer is 0.96 m; thus, the radius of the spherical measurement surface is set as 1.25 m. All four noise calculation points are arranged as shown in Figure 11(c), and they are placed in the noise calculation domain. The pressure fluctuation on impeller inlet of 2837 time steps are used for noise prediction in all cases, the corresponding total time is s, and the frequency resolution is 69.6 Hz. The dipole source is attached to
12 12 Advances in Mechanical Engineering Figure 19. Numerical model of compressor noise: natural aspiration and silencer installed. Figure 20. Compressor intake noise spectrum: linear spectrum, natural aspiration (solid line), and silencer installed (dash line). One-third octave spectrum, natural aspiration (light gray), and silencer installed (deep gray). the noise source surface (acoustic inlet), the acoustic outlet is defined as AML boundary, the air material property is defined in noise calculation domain, and all solid walls are set as rigid wall. When the silencer is installed, the acoustic property of aluminum silicate wool is defined in the calculation domain of sound absorbing blades. The compressor intake noise spectrums are shown in Figure 20. It is found that the tonal noise and broadband noise are main components of compressor noise spectral. Because only the dipole source is used in the calculation, the buzz-saw noise cannot be found in the spectrum. After the silencer is installed, the SPL of compressor noise reduces in nearly whole frequency range, especially in high frequency like BPF and its harmonics. According to the definition of IL, the difference between the mean SPL of all four noise calculation points before and after silencer is installed can be used as the silencer IL. The numerical result of the silencer IL is obtained from the results shown in Figure 20, and the SPL is the mean value of all four noise calculation points. The comparison of experimental and calculation results is shown in Figure 21, and the experimental result has been smoothed by moving average approach to make a common frequency for the
13 Liu et al. 13 Figure 21. Insertion loss spectrum of silencer. comparison of experimental and numerical results. Although there were errors in Hz, the experimental and calculated IL agrees well in low- and high-frequency range. This indicates that the FEM calculation can also be used in silencer IL prediction, especially within high-frequency range. The total calculated and measured IL is and db, respectively. The SPL distribution of compressor noise at the inlet area is shown in Figure 22. The results under the natural aspiration condition indicates that the compressor noise distribution is not uniform when it transmits outward the compressor inlet, and there exists obvious acoustic directivity. After the silencer is installed, its structure changes the noise radiation characteristics, and the compressor noise distribution is much more uniform when it transmits outward the compressor inlet. Furthermore, the sound power is significantly reduced in the silencer. Conclusion Numerical and experimental studies are conducted to investigate the performance of turbocharger intake silencer. The effects of the silencer structure on the turbocharger compressor performance are also analyzed, including compressor global performance, unsteady flow characteristics, and intake noise. Conclusions are summarized in the following. 1. The duct acoustic mode method can be used to predict the TL and IL of intake silencer, the numerical results are in good agreement with the measurements, and the discrepancy between total calculated IL and measured IL is lower than 2 db. 2. The silencer results in greater total pressure loss than that of the natural aspiration, which is higher than 1000 Pa in high flow range. The total-to-total pressure ratio and efficiency at the same speed and flow rate decrease when silencer is installed, and the reduction of flow range is Figure 22. Sound pressure level distribution of compressor noise at inlet nozzle, BPF: natural aspiration and silencer installed. higher than 0.4 m 3 /s. Meanwhile, the highefficiency area reduces. 3. The pressure fluctuation at compressor rotor and stator inlet increases when the intake silencer is installed, and the increased pressure value is higher than 1500 and 8000 Pa, respectively. The pressure spectrum in the rotor and stator passage changes, and a pressure peak appears at the rotor shaft rotation frequency. 4. The noise spectrum indicates that the silencer structure changes the noise radiation characteristics. Compared with the results under the natural aspiration, the silencer can significantly reduce the high-frequency noise, and it is especially effective in tonal noise reduction. The intake silencer IL can also be predicted with CFD and FEM results; the total calculated and measured IL are and db, respectively. Acknowledgements The authors acknowledge the help of Yuejun Shi, who works in the Department of Mechanical and Aerospace Engineering, University of California, Davis.
14 14 Advances in Mechanical Engineering Declaration of conflicting interests The author(s) declared no potential conflicts of interest with respect to the research, authorship, and/or publication of this article. Funding The author(s) disclosed receipt of the following financial support for the research, authorship, and/or publication of this article: This study received financial supports from Marine Low-Speed Engine Project Phase I. ORCID id Yipeng Cao References 1. Watson N and Janota MS. Introduction to turbocharging and turbochargers. Turbocharging the Internal Combustion Engine. London: Palgrave. 2. Hung NS. Aero and vibroacoustics of automotive turbochargers. Berlin; Heidelberg: Springer, Braun ME, Walsh SJ, Horner JL, et al. Noise source characteristics in the ISO 362 vehicle pass-by noise test: literature review. Appl Acoust 2013; 74: Stoffels H and Schroeer M. NVH aspects of a downsized turbocharged gasoline powertrain with direct injection. SAE technical paper , Badami M, Mallamo F, Millo F, et al. Influence of multiple injection strategies on emissions, combustion noise and BSFC of a DI common rail diesel engine. SAE technical paper , Park SS, Rohani B and Bae C. Effect of injection strategies for noise reduction during low temperature combustion-conventional diesel combustion mode transition in a heavy-duty diesel engine. In: Proceedings of th annual conference of the Society of Instrument and Control Engineers of Japan (SICE), Hangzhou, China, July New York: IEEE. 7. Li HB, Sun ZL and Peng X. Turbocharger noise prediction using broadband noise source model. J Beijing Inst Tech 2010; 19: Liu C, Cao YP, Sun WJ, et al. Experimental analysis of aerodynamic noise characteristics of a marine diesel engine compressor. Trans CSICE 2018; 36: Kruger J, Castor F and Jebasinski R. Active exhaust silencers current perspectives and challenges. SAE technical paper , Brand JF, Fallen M and Kammer HJ. Future technologies against turbocharger noise transferred to exhaust systems. SAE technical paper , Badini J and Brown PA. Guidelines for reducing the noise level of a centrifugal air compressor installation. In: Proceedings of the fortieth turbomachinery symposium, Houston, TX, September Texas: Turbomachinery and Pump Symposia. 12. Raitor T and Neise W. Sound generation in centrifugal compressors. J Sound Vib 2008; 314: Trochon EP. A new type of silencers for turbocharger noise control. SAE technical paper , Gaude G, Lefevre T, Tanna R, et al. Experimental and computational challenges in the quantification of turbocharger vibro-acoustic sources. In: Proceedings of the INTER-NOISE and NOISE-CON congress and conference, Shanghai, China, 26 October 2008, pp Reston, VA: Institute of Noise Control Engineering. 15. Figurella N, Dehner R, Selamet A, et al. Noise at the mid to high flow range of a turbocharger compressor. Noise Control Eng J 2014; 62: Navarro DR. A numerical approach for predicting flowinduced acoustics at near-stall conditions in an automotive turbocharger compressor. PhD Thesis, Universitat Politecnica de Valencia, Valencia, Lee IJ, Selamet A, Kim H, et al. Design of a multichamber silencer for turbocharger noise. SAE technical paper , Abom M and Kabral R. Turbocharger noise generation and control. SAE technical paper , Kabral R, Du L, Abom M, et al. A compact silencer for the control of compressor noise. SAE technical paper , Tian S, Sheng XZ, Yang D, et al. Design of a reactive silencer to reduce turbocharger synchronous noise generated from compressor pressure pulsations. In: Proceedings of the 21st international congress on sound and vibration, Beijing, China, July USA: The international institute if acoustics and vibration (IIAV). 21. Japikse D. Centrifugal compressor design and performance. Wilder, ID: Concepts ETI, Inc., Zemp A, Kammerer A, Abhari RS, et al. Unsteady CFD investigation on inlet distortion in a centrifugal compressor. In: Proceedings of ASME turbo expo 2008: power for land, sea, and air (ASME paper GT ), Berlin, 9 13 June New York: The American Society of Mechanical Engineers (ASME). 23. Zhang J, Ma HW, He H, et al. Numerical simulation of effects on the inlet pipe on the performance of a centrifugal compressor. J Aerosp Power 2009; 24: Galindo J, Tiseira A, Navarro R, et al. Effect of the inlet geometry on performance, surge margin and noise emission of an automotive turbocharger compressor. Appl Therm Eng 2017; 110: Serrano JR, Margot X, Tiseira A, et al. Optimization of the inlet air line of an automotive turbocharger. Int J Engine Res 2013; 14: Yang C, Zhao B, Ma CC, et al. Effect of different geometrical inlet pipes on a high speed centrifugal compressor. In: Proceedings of the ASME turbo expo 2013: turbine technical conference and exposition (ASME paper GT ), San Antonio, TX, 3 7 June New York: The American Society of Mechanical Engineers (ASME). 27. Li D, Yang C, Zhao B, et al. Investigation on centrifugal impeller in an axial-radial combined compressor with inlet distortion. J Therm Sci 2011; 20: Wang LL, Yang C, Zhao B, et al. The change of the inlet geometry of a centrifugal compressor stage and its
15 Liu et al. 15 influence on the compressor performance. J Therm Sci 2013; 22(3): Kerr JD. Air intake silencer. Patent , USA, Jiri K and David J. Filter muffler. Patent E , Germany, Feld H-J, Mrvelj L and Meyer P. Sound attenuator of an exhaust-gas turbocharger. Patent , USA, ISO :1998. Acoustics determination of sound absorption coefficient and impedance in impedance tube part 2: transfer-function method. 33. Broatch A, Galindo J, Navarro R, et al. Numerical and experimental analysis of automotive turbocharger compressor aeroacoustics at different operating conditions. Int J Heat Fluid Fl 2016; 61: Broatch A, Galindo J, Navarro R, et al. Methodology for experimental validation of a CFD model for predicting noise generation in centrifugal compressors. Int J Heat Fluid Fl 2014; 50: Serrano JR, Olmeda P and Arnau F. Importance of heat transfer phenomena in small turbochargers for passenger car applications. SAE Int J Engines 2013; 6: Marburg S and Nolte B. Computational acoustics of noise propagation in fluids finite and boundary element methods. Berlin; Heidelberg: Springer, Howe M. Acoustics and aerodynamic sound. New York: Cambridge University Press, Appendix 1 Notation a A A m A n c f duct radius sectional area area of cell m area of cell n sound velocity frequency f BPF f cut off f max i k k 0 k m, n k l size L p(sp) L p(is) m M n p m i p m i p m in p t p n t p n t p n out q r 0 T t W i W t z 0 z Z blade passing frequency cut-off frequency maximum calculation frequency imaginary unit specific heat ratio wavenumber modal wavenumber of acoustic model (m, n) complex wavenumber mesh cell size SPL obtained with substitution pipe SPL obtained with silencer installed mass flow rate Mach number compressor rotating speed incident sound pressure of grid cell m conjugate incident sound pressure of grid cell m inlet sound pressure of grid cell m total pressure transmission sound pressure of grid cell n conjugate transmission sound pressure of grid cell n outlet sound pressure of grid cell n axial flow coefficient cell radius total pressure incident sound pressure level transmission sound pressure level characteristic impedance complex impedance compressor main blade number
AN INTAKE SILENCER FOR THE CONTROL OF MARINE DIESEL TURBOCHARGER COMPRESSOR NOISE
AN INTAKE SILENCER FOR THE CONTROL OF MARINE DIESEL TURBOCHARGER COMPRESSOR NOISE Liu Chen, Cao Yipeng, Zhang Wenping and Zhao Xiaochen Harbin Engineering University, College of Power and Energy Engineering,
More informationSilencers. Transmission and Insertion Loss
Silencers Practical silencers are complex devices, which operate reducing pressure oscillations before they reach the atmosphere, producing the minimum possible loss of engine performance. However they
More informationInfluence of Cylinder Bore Volume on Pressure Pulsations in a Hermetic Reciprocating Compressor
Purdue University Purdue e-pubs International Compressor Engineering Conference School of Mechanical Engineering 2014 Influence of Cylinder Bore Volume on Pressure Pulsations in a Hermetic Reciprocating
More informationAPPLICATION OF STAR-CCM+ TO TURBOCHARGER MODELING AT BORGWARNER TURBO SYSTEMS
APPLICATION OF STAR-CCM+ TO TURBOCHARGER MODELING AT BORGWARNER TURBO SYSTEMS BorgWarner: David Grabowska 9th November 2010 CD-adapco: Dean Palfreyman Bob Reynolds Introduction This presentation will focus
More informationINVESTIGATION OF HEAT TRANSFER CHARACTERISTICS OF CIRCULAR AND DIAMOND PILLARED VANE DISC BRAKE ROTOR USING CFD
SDRP JOURNAL OF NANOTECHNOLOGY & MATERIAL SCIENCE. INVESTIGATION OF HEAT TRANSFER CHARACTERISTICS OF CIRCULAR AND DIAMOND PILLARED VANE DISC BRAKE ROTOR USING CFD Research AUTHOR: A.RAJESH JUNE 2017 1
More informationDesign and Test of Transonic Compressor Rotor with Tandem Cascade
Proceedings of the International Gas Turbine Congress 2003 Tokyo November 2-7, 2003 IGTC2003Tokyo TS-108 Design and Test of Transonic Compressor Rotor with Tandem Cascade Yusuke SAKAI, Akinori MATSUOKA,
More informationResearch on vibration reduction of multiple parallel gear shafts with ISFD
Research on vibration reduction of multiple parallel gear shafts with ISFD Kaihua Lu 1, Lidong He 2, Wei Yan 3 Beijing Key Laboratory of Health Monitoring and Self-Recovery for High-End Mechanical Equipment,
More informationCOMPUTATIONAL FLUID DYNAMICS ANALYSIS OF THE ACOUSTIC PERFORMANCE OF VARIOUS SIMPLE EXPANSION CHAMBER MUFFLERS
COMPUTATIONAL FLUID DYNAMICS ANALYSIS OF THE ACOUSTIC PERFORMANCE OF VARIOUS SIMPLE EXPANSION CHAMBER MUFFLERS Middelberg, J.M., Barber, T.J., Leong, S. S., Byrne, K.P and Leonardi, E. School of Mechanical
More informationComparing FEM Transfer Matrix Simulated Compressor Plenum Pressure Pulsations to Measured Pressure Pulsations and to CFD Results
Purdue University Purdue e-pubs International Compressor Engineering Conference School of Mechanical Engineering 2012 Comparing FEM Transfer Matrix Simulated Compressor Plenum Pressure Pulsations to Measured
More informationTurbostroje 2015 Návrh spojení vysokotlaké a nízkotlaké turbíny. Turbomachinery 2015, Design of HP and LP turbine connection
Turbostroje 2015 Turbostroje 2015 Návrh spojení vysokotlaké a nízkotlaké turbíny Turbomachinery 2015, Design of HP and LP turbine connection J. Hrabovský 1, J. Klíma 2, V. Prokop 3, M. Komárek 4 Abstract:
More informationDevelopment of Shape of Helmholtz Resonator Cavity for Attenuation of Low Frequency Noise of Pure Reactive Muffler
Development of Shape of Helmholtz Resonator Cavity for Attenuation of Low Frequency Noise of Pure Reactive Muffler Amit Kumar Gupta 1, Nirmal Gupta 2 1 Assistant Professor, 2 M.E. Scholar Mechanical Engineering
More informatione t Performance of Extended Inlet and Extended Outlet Tube on Single Expansion Chamber for Noise Reduction
e t International Journal on Emerging Technologies 7(1): 37-41(2016) ISSN No. (Print) : 0975-8364 ISSN No. (Online) : 2249-3255 Performance of Extended Inlet and Extended Outlet Tube on Single Expansion
More informationA STUDY OF THE CENTRIFUGAL COMPRESSOR DISCHARGE PIPELINE CONSTRAINED OSCILLATION. KIRILL SOLODYANKIN*, JIŘÍ BĚHAL ČKD KOMPRESORY, a.s.
A STUDY OF THE CENTRIFUGAL COMPRESSOR DISCHARGE PIPELINE CONSTRAINED OSCILLATION KIRILL SOLODYANKIN*, JIŘÍ BĚHAL ČKD KOMPRESORY, a.s. Abstract: The paper presents a solution of a pipeline constrained oscillation
More informationISSN (PRINT): ,(ONLINE): ,VOLUME-2,ISSUE-4,2016 1
A STUDY ON THE ACOUSTIC PERFORMANCE OF A REACTIVE MUFFLER Shemin Thomas Varkey 1, Lalu P. P 2, K. Balakrishnan 3 1 Post Graduate Student, Government Engineering College, Thrissur, 2 Assistant Professor,
More informationInfluence of pantograph fixing position on aerodynamic characteristics of high-speed trains
DOI 1.17/s4534-17-125-y Influence of pantograph fixing position on aerodynamic characteristics of high-speed trains Liang Zhang 1 Jiye Zhang 1 Tian Li 1 Weihua Zhang 1 Received: 28 September 216 / Revised:
More informationNUMERICAL STUDY OF TRANSFER FUNCTION OF COM- BUSTION NOISE ON A HEAVY DUTY DIESEL ENGINE
NUMERICAL STUDY OF TRANSFER FUNCTION OF COM- BUSTION NOISE ON A HEAVY DUTY DIESEL ENGINE Ibrahim Ciylez Ford OTOSAN A.Ş., Sancaktepe, Istanbul, Turkey email: iciylez@ford.com.tr Haluk Erol Istanbul Technical
More informationEffect of Stator Shape on the Performance of Torque Converter
16 th International Conference on AEROSPACE SCIENCES & AVIATION TECHNOLOGY, ASAT - 16 May 26-28, 2015, E-Mail: asat@mtc.edu.eg Military Technical College, Kobry Elkobbah, Cairo, Egypt Tel : +(202) 24025292
More informationAERODYNAMIC DESIGN OPTIMIZATION OF A 200 KW-CLASS RADIAL INFLOW SUPERCRITICAL CARBON DIOXIDE TURBINE
Proceedings of Shanghai 2017 Global Power and Propulsion Forum 30 th October 1 st November, 2017 http://www.gpps.global GPPS-2017-0109 AERODYNAMIC DESIGN OPTIMIZATION OF A 200 KW-CLASS RADIAL INFLOW SUPERCRITICAL
More informationScroll Compressor Oil Pump Analysis
IOP Conference Series: Materials Science and Engineering PAPER OPEN ACCESS Scroll Compressor Oil Pump Analysis To cite this article: S Branch 2015 IOP Conf. Ser.: Mater. Sci. Eng. 90 012033 View the article
More informationDESIGN & OPTIMIZATION OF EXHAUST MUFFLER & DESIGN VALIDATION
DESIGN & OPTIMIZATION OF EXHAUST MUFFLER & DESIGN VALIDATION 1 RAHUL D. NAZIRKAR, 2 S.R.MESHRAM, 3 AMOL D. NAMDAS, 4 SURAJ U. NAVAGIRE, 5 SUMIT S. DEVARSHI 1,2,3,4,5 Department of Mechanical Engineering,
More informationStudy on Flow Fields in Variable Area Nozzles for Radial Turbines
Vol. 4 No. 2 August 27 Study on Fields in Variable Area Nozzles for Radial Turbines TAMAKI Hideaki : Doctor of Engineering, P. E. Jp, Manager, Turbo Machinery Department, Product Development Center, Corporate
More information6. Acoustical simulation of straight and side inlet/outlet rectangular plenums using the FEM method
Research Signpost 37/661 (2), Fort P.O. Trivandrum-695 023 Kerala, India Noise Control: Theory, Application and Optimization in Engineering, 2014: 119-144 ISBN: 978-81-308-0552-8 Editors: Min-Chie Chiu
More informationCRITICAL SPEED ANALYSIS FOR DUAL ROTOR SYSTEM USING FINITE ELEMENT METHOD
CRITICAL SPEED ANALYSIS FOR DUAL ROTOR SYSTEM USING FINITE ELEMENT METHOD Kai Sun, Zhao Wan, Huiying Song, Shaohui Wang AVIC Commercial Aircraft Engine Co. Ltd, 3998 South Lianhua Road, 201108 Shanghai,
More informationModal Analysis of Automobile Brake Drum Based on ANSYS Workbench Dan Yang1, 2,Zhen Yu1, 2, Leilei Zhang1, a * and Wentao Cheng2
7th International Conference on Mechatronics, Computer and Education Informationization (MCEI 2017) Modal Analysis of Automobile Brake Drum Based on ANSYS Workbench Dan Yang1, 2,Zhen Yu1, 2, Leilei Zhang1,
More informationAnalysis of Air Flow and Heat Transfer in Ventilated Disc Brake Rotor with Diamond Pillars
International Journal of Current Engineering and Technology E-ISSN 2277 4106, P-ISSN 2347 5161 2016 INPRESSCO, All Rights Reserved Available at http://inpressco.com/category/ijcet Research Article Analysis
More informationInnovative Centrifugal Compressor Design
Innovative Centrifugal Compressor Design L. Tarnowski TURBOMECA groupe SAFRAN INTRODUCTION SP2 : IRA (Intercooled Recuperative Aero-engine) Task 2.2.5 HP Centrifugal Compressor Design The challenge is
More informationMARINE FOUR-STROKE DIESEL ENGINE CRANKSHAFT MAIN BEARING OIL FILM LUBRICATION CHARACTERISTIC ANALYSIS
POLISH MARITIME RESEARCH Special Issue 2018 S2 (98) 2018 Vol. 25; pp. 30-34 10.2478/pomr-2018-0070 MARINE FOUR-STROKE DIESEL ENGINE CRANKSHAFT MAIN BEARING OIL FILM LUBRICATION CHARACTERISTIC ANALYSIS
More informationEffect of concave plug shape of a control valve on the fluid flow characteristics using computational fluid dynamics
Effect of concave plug shape of a control valve on the fluid flow characteristics using computational fluid dynamics Yasser Abdel Mohsen, Ashraf Sharara, Basiouny Elsouhily, Hassan Elgamal Mechanical Engineering
More informationImproving muffler performance using simulation-based design
Improving muffler performance using simulation-based design Fangsen CUI 1 *; Ying WANG 2 ; Richard Chao CAI 3 1 Institute of High Performance Computing, A*STAR, Singapore 2 Jinan Dejia Machine Pte Ltd,
More informationCompressor Noise Control
Purdue University Purdue e-pubs International Compressor Engineering Conference School of Mechanical Engineering 1972 Compressor Noise Control G. M. Diehl Ingersoll-Rand Research Follow this and additional
More informationMuffler size minimization, using attenuation behaviour by acoustic simulation
ISSN 2395-1621 size minimization, using attenuation behaviour by acoustic simulation #1 Sandeep K Kakade, #2 Prof.Dr.F.B.Sayyad #12 G S Moze College of Engineering, Pune, India ABSTRACT ARTICLE INFO Engine
More informationEFFECT OF SURFACE ROUGHNESS ON PERFORMANCE OF WIND TURBINE
Chapter-5 EFFECT OF SURFACE ROUGHNESS ON PERFORMANCE OF WIND TURBINE 5.1 Introduction The development of modern airfoil, for their use in wind turbines was initiated in the year 1980. The requirements
More informationOptimization of Suction Muffler Using Taguchi s DOE Method
Purdue University Purdue e-pubs International Compressor Engineering Conference School of Mechanical Engineering 006 Optimization of Suction Muffler Using Taguchi s DOE Method Sanjay S. Gosavi Kirloskar
More informationStudy of Inlet Guide Vanes for Centrifugal Compressor in Miniature Gas-Turbines
Study of Inlet Guide Vanes for Centrifugal Compressor in Miniature Gas-Turbines Ronald Reagon R 1 Roshan Suhail 2, Shashank N 3, Ganesh Nag 4 Vishnu Tej 5 1 Asst. Professor, Department of Mechanical Engineering,
More informationTHE EFFECT OF BLADE LEAN ON AN AXIAL TURBINE STATOR FLOW HAVING VARIOUS HUB TIP RATIOS. Dr. Edward M Bennett
THE EFFECT OF BLADE LEAN ON AN AXIAL TURBINE STATOR FLOW HAVING VARIOUS HUB TIP RATIOS Dr. Edward M Bennett ABSTRACT The effect of simple lean on an axial turbine stator was examined using a threedimensional
More informationMarc ZELLAT, Driss ABOURI and Stefano DURANTI CD-adapco
17 th International Multidimensional Engine User s Meeting at the SAE Congress 2007,April,15,2007 Detroit, MI RECENT ADVANCES IN DIESEL COMBUSTION MODELING: THE ECFM- CLEH COMBUSTION MODEL: A NEW CAPABILITY
More informationNoise Reduction in a Reciprocating Compressor by Optimizing the Suction Muffler
Noise Reduction in a Reciprocating Compressor by Optimizing the Suction Muffler Katakama Nagarjuna ¹ K.Sreenivas² ¹ M.tech student, ²Professor, dept of mechanical engineering kits, markapur, A.P, INDIA
More informationNUMERICAL INVESTIGATION OF FLUID FLOW AND HEAT TRANSFER CHARACTERISTICS ON THE AERODYNAMICS OF VENTILATED DISC BRAKE ROTOR USING CFD
THERMAL SCIENCE: Year 2014, Vol. 18, No. 2, pp. 667-675 667 NUMERICAL INVESTIGATION OF FLUID FLOW AND HEAT TRANSFER CHARACTERISTICS ON THE AERODYNAMICS OF VENTILATED DISC BRAKE ROTOR USING CFD by Thundil
More informationInternational Journal of Scientific & Engineering Research, Volume 5, Issue 7, July-2014 ISSN
ISSN 9-5518 970 College of Engineering Trivandrum Department of Mechanical Engineering arundanam@gmail.com, arjunjk91@gmail.com Abstract This paper investigates the performance of a shock tube with air
More informationBack pressure analysis of an engine muffler using cfd and experimental validation
Back pressure analysis of an engine muffler using cfd and experimental validation #1 Mr. S.S. Mane, #2 S.Y.Bhosale #1 Mechanical Engineering, PES s Modern College of engineering, Pune, INDIA #2 Mechanical
More informationTheoretical and Experimental Investigation of Compression Loads in Twin Screw Compressor
Purdue University Purdue e-pubs International Compressor Engineering Conference School of Mechanical Engineering 2004 Theoretical and Experimental Investigation of Compression Loads in Twin Screw Compressor
More informationAvailable online at ScienceDirect. Physics Procedia 67 (2015 )
Available online at www.sciencedirect.com ScienceDirect Physics Procedia 67 (2015 ) 518 523 25th International Cryogenic Engineering Conference and the International Cryogenic Materials Conference in 2014,
More informationExperimental Study on Torsional Vibration of Transmission System Under Engine Excitation Xin YANG*, Tie-shan ZHANG and Nan-lin LEI
217 3rd International Conference on Applied Mechanics and Mechanical Automation (AMMA 217) ISBN: 978-1-6595-479- Experimental Study on Torsional Vibration of Transmission System Under Engine Excitation
More informationStudy on Flow Characteristic of Gear Pumps by Gear Tooth Shapes
Journal of Applied Science and Engineering, Vol. 20, No. 3, pp. 367 372 (2017) DOI: 10.6180/jase.2017.20.3.11 Study on Flow Characteristic of Gear Pumps by Gear Tooth Shapes Wen Wang 1, Yan-Mei Yin 1,
More informationExperimental research on dynamic characteristics of gas bearing-rotor with different radial clearances
Experimental research on dynamic characteristics of gas bearing-rotor with different radial clearances Long Hao 1, Jinfu Yang 2, Dongjiang Han 3, Changliang Tang 4 Institute of Engineering Thermophysics,
More informationPulsation dampers for combustion engines
ICLASS 2012, 12 th Triennial International Conference on Liquid Atomization and Spray Systems, Heidelberg, Germany, September 2-6, 2012 Pulsation dampers for combustion engines F.Durst, V. Madila, A.Handtmann,
More informationCFD Investigation of Influence of Tube Bundle Cross-Section over Pressure Drop and Heat Transfer Rate
CFD Investigation of Influence of Tube Bundle Cross-Section over Pressure Drop and Heat Transfer Rate Sandeep M, U Sathishkumar Abstract In this paper, a study of different cross section bundle arrangements
More informationRoot Cause Analysis of a vibration problem in a propylene turbo compressor. Pieter van Beek, Jan Smeulers
Root Cause Analysis of a vibration problem in a propylene turbo compressor Pieter van Beek, Jan Smeulers Problem description A newly installed turbo compressor system for propylene showed vibrations in
More informationNoise Reduction of Accumulators for R410A Rotary Compressors
Purdue University Purdue e-pubs International Compressor Engineering Conference School of Mechanical Engineering 2008 Noise Reduction of Accumulators for R410A Rotary Compressors Ling Li Guangdong Meizhi
More informationIJSRD - International Journal for Scientific Research & Development Vol. 4, Issue 07, 2016 ISSN (online):
IJSRD - International Journal for Scientific Research & Development Vol. 4, Issue 07, 2016 ISSN (online): 2321-0613 Design, Optimization and Analysis of Exhaust Muffler to Reduce Exhaust Noise Level and
More information(1) Keywords: CFD, helicopter fuselage, main rotor, disc actuator
SIMULATION OF FLOW AROUND FUSELAGE OF HELICOPTER USING ACTUATOR DISC THEORY A.S. Batrakov *, A.N. Kusyumov *, G. Barakos ** * Kazan National Research Technical University n.a. A.N.Tupolev, ** School of
More informationin ultra-low NOx lean combustion grid plate
CFD predictions of aerodynamics and mixing in ultra-low NOx lean combustion grid plate flame stabilizer JOSÉ RAMÓN QUIÑONEZ ARCE, DR. ALAN BURNS, PROF. GORDON E. ANDREW S. SCHOOL OF CHEMICAL AND PROCESS
More informationTHE APPLICATION OF WHOLE ENGINE FINITE ELEMENT MODEL ON CRITICAL SPEED ANALYSIS FOR THE COMMERCIAL AERO-ENGINE ROTOR
THE APPLICATION OF WHOLE ENGINE FINITE ELEMENT MODEL ON CRITICAL SPEED ANALYSIS FOR THE COMMERCIAL AERO-ENGINE ROTOR Huiying Song, Shaohui Wang, Kai Sun and Shoufeng Hu AVIC Commercial Aircraft Engine
More informationAerodynamic Characteristics of Sedan with the Rolling Road Ground Effect Simulation System
Vehicle Engineering (VE) Volume 2, 2014 www.seipub.org/ve Aerodynamic Characteristics of Sedan with the Rolling Road Ground Effect Simulation System Yingchao Zhang 1, Linlin Ren 1, Kecheng Pan 2, Zhe Zhang*
More informationResearch on Pressure Loss for the Reverse-Flow Extended-Tube Muffler*
Research on Pressure Loss for the Reverse-Flow Extended-Tube Muffler* Jie Yao 1, Zhao-Xiang Deng 1,2, Pei-Ran Li 1, and Liang Yang 2 1 State Key Laboratory of Mechanical Transmission, Chongqing University,
More informationinter.noise 2000 The 29th International Congress and Exhibition on Noise Control Engineering August 2000, Nice, FRANCE
Copyright SFA - InterNoise 2000 1 inter.noise 2000 The 29th International Congress and Exhibition on Noise Control Engineering 27-30 August 2000, Nice, FRANCE I-INCE Classification: 7.6 ROLLING NOISE FROM
More informationThe Performance Optimization of Rolling Piston Compressors Based on CFD Simulation
Purdue University Purdue e-pubs International Compressor Engineering Conference School of Mechanical Engineering 2004 The Performance Optimization of Rolling Piston Compressors Based on CFD Simulation
More informationAerodynamically induced power loss in hard disk drives
Microsyst Technol (2005) 11: 741 746 DOI 10.1007/s00542-005-0575-8 TECHNICAL PAPER Sung-Oug Cho Æ Seung-Yop Lee Æ Yoon-Chul Rhim Aerodynamically induced power loss in hard disk drives Received: 30 June
More informationADVANCES in NATURAL and APPLIED SCIENCES
ADVANCES in NATURAL and APPLIED SCIENCES ISSN: 1995-0772 Published BYAENSI Publication EISSN: 1998-1090 http://www.aensiweb.com/anas 2017 April 11(4): pages 544-550 Open Access Journal Analysis Of Sliding
More informationABSTRACT I. INTRODUCTION III. GEOMETRIC MODELING II. LITERATURE REVIW
2017 IJSRSET Volume 3 Issue 5 Print ISSN: 2395-1990 Online ISSN : 2394-4099 Themed Section: Engineering and Technology Performance Analysis of Helical Coil Heat Exchanger Using Numerical Technique Abhishek
More informationClearance Loss Analysis in Linear Compressor with CFD Method
Clearance Loss Analysis in Linear Compressor with CFD Method Wenjie Zhou, Zhihua Gan, Xiaobin Zhang, Limin Qiu, Yinzhe Wu Cryogenics Laboratory, Zhejiang University Hangzhou, Zhejiang, China, 310027 ABSTRACT
More informationCFD on Cavitation around Marine Propellers with Energy-Saving Devices
63 CFD on Cavitation around Marine Propellers with Energy-Saving Devices CHIHARU KAWAKITA *1 REIKO TAKASHIMA *2 KEI SATO *2 Mitsubishi Heavy Industries, Ltd. (MHI) has developed energy-saving devices that
More informationFlow and Heat Transfer Analysis of an Inlet Guide Vane with Closed-loop Steam Cooling
International Conference on Intelligent Systems Research and Mechatronics Engineering (ISRME 2015) Flow and Heat Transfer Analysis of an Inlet Guide Vane with Closed-loop Steam Cooling Siping Zhai 1, Chao
More informationChapter 7: Thermal Study of Transmission Gearbox
Chapter 7: Thermal Study of Transmission Gearbox 7.1 Introduction The main objective of this chapter is to investigate the performance of automobile transmission gearbox under the influence of load, rotational
More informationInvestigation for Flow of Cooling Air through the Ventilated Disc Brake Rotor using CFD
International Journal of Thermal Technologies E-ISSN 2277 4114 2015 INPRESSCO, All Rights Reserved Available at http://inpressco.com/category/ijtt/ Research Article Investigation for Flow of Cooling Air
More informationEngineering Success by Application of STAR-CCM+ for Modern Gas Turbine Design
STAR Japanese Conference 2013 December 3, Yokohama, Japan Engineering Success by Application of STAR-CCM+ for Modern Gas Turbine Design Norbert Moritz, Karsten Kusterer, René Braun, Anis Haj Ayed B&B-AGEMA
More informationChina. Keywords: Electronically controled Braking System, Proportional Relay Valve, Simulation, HIL Test
Applied Mechanics and Materials Online: 2013-10-11 ISSN: 1662-7482, Vol. 437, pp 418-422 doi:10.4028/www.scientific.net/amm.437.418 2013 Trans Tech Publications, Switzerland Simulation and HIL Test for
More informationNumerical Study on the Flow Characteristics of a Solenoid Valve for Industrial Applications
Numerical Study on the Flow Characteristics of a Solenoid Valve for Industrial Applications TAEWOO KIM 1, SULMIN YANG 2, SANGMO KANG 3 1,2,4 Mechanical Engineering Dong-A University 840 Hadan 2 Dong, Saha-Gu,
More informationSILENCER SELECTION INSTRUCTIONS
For general information in HVAC Acoustics, consult the following publications: 2013 ASHRAE Fundamentals Handbook, Chapter 8 Sound and Vibration 2011 ASHRAE Applications Handbook, Chapter 48 Noise and Vibration
More informationStudy of intake manifold for Universiti Malaysia Perlis automotive racing team formula student race car
Journal of Physics: Conference Series PAPER OPEN ACCESS Study of intake manifold for Universiti Malaysia Perlis automotive racing team formula student race car To cite this article: A Norizan et al 2017
More informationThe Modeling and Simulation of DC Traction Power Supply Network for Urban Rail Transit Based on Simulink
Journal of Physics: Conference Series PAPER OPEN ACCESS The Modeling and Simulation of DC Traction Power Supply Network for Urban Rail Transit Based on Simulink To cite this article: Fang Mao et al 2018
More information2292. Numerical computation of aerodynamic noises of the high speed train with considering pantographs
2292. Numerical computation of aerodynamic noises of the high speed train with considering pantographs Ya-hui Wang 1, Jian-ting Wang 2, Liu-qiang Fu 3 North China University of Water Resources and Electric
More informationFinite Element Analysis on Thermal Effect of the Vehicle Engine
Proceedings of MUCEET2009 Malaysian Technical Universities Conference on Engineering and Technology June 20~22, 2009, MS Garden, Kuantan, Pahang, Malaysia Finite Element Analysis on Thermal Effect of the
More informationA NOVEL DESIGN METHOD OF VARIABLE GEOMETRY TURBINE NOZZLES FOR HIGH EXPANSION RATIOS
A NOVEL DESIGN METHOD OF VARIABLE GEOMETRY TURBINE NOZZLES FOR HIGH EXPANSION RATIOS Lei Huang 1, Hua Chen 2, * 1. National Laboratory of Engine Turbocharging Technology, North China Engine Research Institute,
More informationAnalysis of aerodynamic and aeroacoustic behaviour of a simplified high-speed train bogie
Analysis of aerodynamic and aeroacoustic behaviour of a simplified high-speed train bogie J.Y. Zhu 1, Z.W. Hu 1, D.J. Thompson 2 1 Aerodynamics and Flight Mechanics Research Group, Faculty of Engineering
More informationOpen Access Calculation for the Heating and Safe Operation Time of YKK Series Highvoltage Motors in Starting Process
Send Orders of Reprints at reprints@benthamscience.net The Open Electrical Electronic Engineering Journal, 213, 7, (Supple 1: M3) 39-45 39 Open Access Calculation for the Heating and Safe Operation Time
More informationOptimization of Hydraulic Retarder Based on CFD Technology
International Conference on Manufacturing Science and Engineering (ICMSE 2015) Optimization of Hydraulic Retarder Based on CFD Technology Li Hao 1, a *, Ren Xiaohui 1,b 1 College of Vehicle and Energy,
More informationEnhanced Heat Transfer Surface Development for Exterior Tube Surfaces
511 A publication of CHEMICAL ENGINEERING TRANSACTIONS VOL. 32, 2013 Chief Editors: Sauro Pierucci, Jiří J. Klemeš Copyright 2013, AIDIC Servizi S.r.l., ISBN 978-88-95608-23-5; ISSN 1974-9791 The Italian
More informationStatic and Dynamic Strength Analysis on Rear Axle of Small Payload Off-highway Dump Trucks
Static and Dynamic Strength Analysis on Rear Axle of Small Payload Off-highway Dump Trucks Ji-xin Wang, Guo-qiang Wang, Shi-kui Luo, Dec-heng Zhou College of Mechanical Science and Engineering, Jilin University,
More informationA Model of Wind Turbine s Flexibility Shaft
Advanced Materials Research Online: 2014-06-18 ISSN: 1662-8985, Vols. 953-954, pp 384-388 doi:10.4028/www.scientific.net/amr.953-954.384 2014 Trans Tech Publications, Switzerland A Model of Wind Turbine
More informationCFD Analysis and Comparison of Fluid Flow Through A Single Hole And Multi Hole Orifice Plate
CFD Analysis and Comparison of Fluid Flow Through A Single Hole And Multi Hole Orifice Plate Malatesh Barki. 1, Ganesha T. 2, Dr. M. C. Math³ 1, 2, 3, Department of Thermal Power Engineering 1, 2, 3 VTU
More informationSubsynchronous Shaft Vibration in an Integrally Geared Expander-Compressor due to Vortex Flow in an Expander
Subsynchronous Shaft Vibration in an Integrally Geared Expander-Compressor due to Vortex Flow in an Expander Daisuke Hirata cting Manager, Engineering & Design Division Mitsubishi Heavy Industries Compressor
More informationVibration Analysis of Gear Transmission System in Electric Vehicle
Advanced Materials Research Online: 0-0- ISSN: 66-8985, Vols. 99-00, pp 89-83 doi:0.408/www.scientific.net/amr.99-00.89 0 Trans Tech Publications, Switzerland Vibration Analysis of Gear Transmission System
More informationDesign and Stress Analysis of Crankshaft for Single Cylinder 4-Stroke Diesel Engine
Design and Stress Analysis of Crankshaft for Single Cylinder 4-Stroke Diesel Engine Amit Solanki #1, Jaydeepsinh Dodiya #2, # Mechanical Engg.Deptt, C.U.Shah University, Wadhwan city, Gujarat, INDIA Abstract
More informationNumerical and Experimental Research on Vibration Mechanism of Rotary Compressor
Purdue University Purdue e-pubs International Compressor Engineering Conference School of Mechanical Engineering 2018 Numerical and Experimental Research on Vibration Mechanism of Rotary Compressor Zhiqiang
More informationAcoustic design of the air transparent soundproofing wall
PROCEEDINGS of the 22 nd International Congress on Acoustics Materials for Noise Control: Paper ICA2016-323 Acoustic design of the air transparent soundproofing wall Seong-Hyun Lee (a), Junghwan Kook (b),
More informationAdvanced Aerodynamic Design Technologies for High Performance Turbochargers
67 Advanced Aerodynamic Design Technologies for High Performance Turbochargers TAKAO YOKOYAMA *1 KENICHIRO IWAKIRI *2 TOYOTAKA YOSHIDA *2 TORU HOSHI *3 TADASHI KANZAKA *2 SEIICHI IBARAKI *1 In recent years,
More informationThe Simulation of Metro Wheel Tread Temperature in Emergency Braking Condition Hong-Guang CUI 1 and Guo HU 2*
2017 3rd International Conference on Computer Science and Mechanical Automation (CSMA 2017) ISBN: 978-1-60595-506-3 The Simulation of Metro Wheel Tread Temperature in Emergency Braking Condition Hong-Guang
More informationNUMERICAL INVESTIGATION OF PISTON COOLING USING SINGLE CIRCULAR OIL JET IMPINGEMENT
NUMERICAL INVESTIGATION OF PISTON COOLING USING SINGLE CIRCULAR OIL JET IMPINGEMENT BALAKRISHNAN RAJU, CFD ANALYSIS ENGINEER, TATA CONSULTANCY SERVICES LTD., BANGALORE ABSTRACT Thermal loading of piston
More informationHighly transient gas engine operation from a turbocharging perspective
HERVÉ MARTIN, ABB TURBO SYSTEMS LTD Highly transient gas engine operation from a turbocharging perspective 10th CIMAC CASCADES, Kobe, 12 th October 2018 Overview Introduction Basics of load pick-up Modeling
More informationPNEUMATIC HIGH SPEED SPINDLE WITH AIR BEARINGS
PNEUMATIC HIGH SPEED SPINDLE WITH AIR BEARINGS Terenziano RAPARELLI, Federico COLOMBO and Rodrigo VILLAVICENCIO Department of Mechanics, Politecnico di Torino Corso Duca degli Abruzzi 24, Torino, 10129
More informationDESIGN AND ANALYSIS OF UNDERTRAY DIFFUSER FOR A FORMULA STYLE RACECAR
DESIGN AND ANALYSIS OF UNDERTRAY DIFFUSER FOR A FORMULA STYLE RACECAR Ali Asgar S. Khokhar 1, Suhas S. Shirolkar 2 1 Graduate in Mechanical Engineering, KJ Somaiya College of Engineering, Mumbai, India.
More informationKey Parameters Investigation on Small Cycle Fuel Injection Quantity for a Diesel Engine Electronic Unit Pump System
Page63 EVS25 Shenzhen, China, Nov 5-9, 21 Key Parameters Investigation on Small Cycle Fuel Injection Quantity for a Diesel Engine Electronic Unit Pump System Abstract Liyun Fan 1, Bingqi Tian 1, and Xiuzhen
More informationFLOW AND HEAT TRANSFER ENHANCEMENT AROUND STAGGERED TUBES USING RECTANGULAR VORTEX GENERATORS
FLOW AND HEAT TRANSFER ENHANCEMENT AROUND STAGGERED TUBES USING RECTANGULAR VORTEX GENERATORS Prabowo, Melvin Emil S., Nanang R. and Rizki Anggiansyah Department of Mechanical Engineering, ITS Surabaya,
More information1874. Effect predictions of star pinion geometry phase adjustments on dynamic load sharing behaviors of differential face gear trains
1874. Effect predictions of star pinion geometry phase adjustments on dynamic load sharing behaviors of differential face gear trains Zhengminqing Li 1, Wei Ye 2, Linlin Zhang 3, Rupeng Zhu 4 Nanjing University
More informationTurbo boost. ACTUS is ABB s new simulation software for large turbocharged combustion engines
Turbo boost ACTUS is ABB s new simulation software for large turbocharged combustion engines THOMAS BÖHME, ROMAN MÖLLER, HERVÉ MARTIN The performance of turbocharged combustion engines depends heavily
More informationImpacts of Short Tube Orifice Flow and Geometrical Parameters on Flow Discharge Coefficient Characteristics
Impacts of Short Tube Orifice Flow and Geometrical Parameters on Flow Discharge Coefficient Characteristics M. Metwally Lecturer, Ph.D., MTC, Cairo, Egypt Abstract Modern offset printing machine, paper
More informationFlow Analysis of Air Intake Duct for Noise. Reduction in Automobile
Contemporary Engineering Sciences, Vol. 9, 2016, no. 20, 989-995 HIKARI Ltd, www.m-hikari.com http://dx.doi.org/10.12988/ces.2016.6699 Flow Analysis of Air Intake Duct for Noise Reduction in Automobile
More informationSILENCER SELECTION INSTRUCTIONS
SILENCER SELECTION INSTRUCTIONS For general information in HVAC Acoustics, consult the following publications: > > 07 ASHRAE Fundamentals Handbook, Chapter 8 Sound and Vibration > > 05 ASHRAE Applications
More information51. Heat transfer characteristic analysis of negative pressure type EGR valve based on CFD
51. Heat transfer characteristic analysis of negative pressure type EGR valve based on CFD Guannan Hao 1, Sen Zhang 2, Yiguang Yin 3 Binzhou University, Binzhou, China 1 Corresponding author E-mail: 1
More information