A Novel Double-Notch Passive Hydraulic Mount Design
|
|
- Georgina Montgomery
- 5 years ago
- Views:
Transcription
1 Proceedings of 20 th International Congress on Acoustics, ICA August 2010, Sydney, Australia A Novel Double-Notch Passive Hydraulic Mount Design Reza Tikani (1), Saeed Ziaei-Rad (1), Nader Vahdati (2), Somayeh Heidari (2), Mohsen Esfahanian (1) (1) Department of Mechanical Engineering, Isfahan University of Technology, Isfahan , Iran (2) School of Mechanical and Aerospace Engineering, Nanyang Technological University, 50 Nanyang Avenue, Singapore , Singapore PACS: TM Vibration isolators, attenuators, and dampers ABSTRACT Passive hydraulic engine mounts are broadly applied in automotive and aerospace applications to isolate cabin from engine noise and vibration. The engine mounts are stationed in between engine and fuselage in aerospace applications. In fixed wing turbofan engine applications, notch frequency of each hydraulic engine mount is adjusted to eir N1 frequency (engine low speed shaft imbalance excitation frequency) or to N2 frequency (engine high speed shaft imbalance excitation frequency) at cruise condition. Since most of today's passive hydraulic engine mount designs have only one notch, isolation is only possible at eir N1 or at N2, but not at both. In this paper, a novel double-notch passive hydraulic engine mount design is proposed. The new design consists of two inertia tracks. One inertia track contains a tuned vibration absorber (TVA) where or one does not. This design exhibits two notch frequencies, and refore provide vibration and noise isolation at two different frequencies. The notch frequencies of new design are easily tunable and notches be placed at N1 and N2 with ease. The new passive hydraulic engine mount design concept and its mamatical model are presented in details and some discussions on simulation results are also included. INTRODUCTION Passive hydraulic engine mounts are widely used in automotive and aerospace applications for control of cabin noise and vibration (Singh, Kim and Ravindra, 1992; Kim and Singh, 1993; 1995; Adigunaa et al., 2003; Vahdati, 2005; Christopherson and Jazar, 2006). The hydraulic mount is placed in between engine and fuselage, or car engine and car frame to reduce and control noise and vibration level of cabin. Aircraft engine mounts have two main functions: 1) to connect engine and airframe toger, and 2) to isolate airframe from engine vibration (Swanson, Wu and Ashrafiuon,1993). Vibratory forces are mainly caused by rotational unbalances of engine, and result in increased stress levels in nacelle, as well as high noise levels in cabin (Swanson, Wu and Ashrafiuon,1993). Through careful design and selection of hydraulic engine mount parameters, it is possible to select dynamic stiffness smaller than static stiffness at a certain frequency. This effect is called "notching'' and is referred to as minimum dynamic stiffness over a small frequency range (Yunhe, Nagi G. and Rao V., 2001). The "notch frequency" is frequency at which dynamic stiffness of hydraulic mount is lowest; refore, greatest cabin noise and vibration reduction are obtained. The design location of notch frequency depends on application, but with most applications, notch frequency is designed to coincide with longest period of constant speed. For example, in case of fixed wing applications, notch frequency may be designed to coincide with aircraft cruise speed rar than take-off and landing speeds. Since most of airplane s flight time is spent at cruise speed, it makes most sense to reduce cabin noise and vibration at cruise speed rar than at take-off or landing speeds (Vahdati, 2005). The problem with exisiting hydraulic engine mount designs is that re is only one notch frequency and cabin noise and vibration reduction is only possible at one frequency. Here in this paper, a new hydraulic engine mount design is proposed that has two notch freauencies; refore, cabin noise and vibration reduction is possible at two distinct frequencies. HYDRAULIC ENGINE MOUNT A single-pumper passive fluid mount, as shown in Fig. 1, consists of two fluid chambers that are connected toger through an inertia track. Source: (Vahdati,1998) Figure 1. A typical single pumper Hydraulic mount The notch frequency location depends on inertia track length, diameter, fluid density and viscosity, and rubber stiffness. Fig. 2 shows a typical dynamic stiffness of a passive fluid mount versus frequency. ICA
2 23-27 August 2010, Sydney, Australiaa Proceedings of 20th International Congress on Acoustics, ICA 2010 chamber is connected to bottom fluid chamber via two inertia tracks. In first inertia track, re is a mass and two springs. The fluid, flowing through 1st inertia track, flow in between masss and inertia track walls and dynamically move mass up and down. In bottom fluid chamber a soft rubber diaphragm provides volumetric stiffness and contains fluid. This volumetric stiffnesss also varied by pressuring air behind it, as shown in Fig. 3. The bond graph model of Fig. 3 is shown in Fig. 4. Source: (Vahdati,1998) Figure 2. Dynamic stiffness of a typical hydraulic mount But, at cruise speed, re are many enginee imbalance (disturbance) excitation frequencies and ideally one wants to isolate cabin from all enginee imbalance excitation fremount tech- quencies. However, with current hydraulic nology, hydraulic mount notch frequency only be tuned to one and only one frequency. For example, in most turbofan engines largest imbalance excitation amplitudes normally occur at N1 (engine low-speed shaft imbalance excitation frequency) and at N2 frequencies (engine high- cur- speed shaft imbalance excitation frequency). Since rent hydraulic mount design technology only offers isolation at one frequency, a hydraulic mount designer has no choice but to choose isolation at N1 or at N2 (Vahdati, 2005). Literature and patent review show that only Vahdati (Vahdati, 2005)) has worked on hydraulic engine mounts that provide vibration and noise isolation at two distinct fre- two fluid quencies. In his design, instead of conventional chambers, three fluid chambers and two fluid inertia tracks were used to create a double notch fluid mount. But here, in this paper, a new single-pumper hydraulic mount design will be described, which offer cabin noise and vibration isolation at two frequencies without a need for an additional fluid chamber. The new design concept and its mamatical model, and simulation results will be presented in following sections. DOUBLE-NOTCH PASSIVE HYDRAULIC MOUNT DESIGN Here, in this section, a double-notch passive hydraulic engine mount design concept is described, that filter out two imbalance disturbance inputs from cabin. Fig. 3 shows new double-notch hydraulic engine mount design con- two cept. In this new design, re are two fluid chambers, inertia tracks, and a mass and two springs inside one of inertia tracks. Before deriving state space equations from bond graph model of Fig. 3, it is necessary to obtain flow loss and pressure drop in inertia tracks and especially in gap between mass and 1 st inertia track housing. The inertia track flow resistance, for circular part of 1 st inertia track, is given by (Shaughnessy, Katz and Schaffer 2005) Where μ is fluid viscosity ( Ns/m 2 ), is in- ner diameter of inertia track and L is length of inertia track that is circular. For annular section of inertia track, a different flow resistancee equation needs to be used. The velocity profile between cylindrical mass and inertia track housing could be written as Figure 3. Bond graph model of Figure 3. γ γ (1) (2) Figure 4. Mass in inertia track Where A and B are constants and be obtained by apply- ing appropriate boundary conditions. In this problem, one define boundary conditions 0 (3) Figure 3. Double-notch passive hydraulic mount The top fluid chamber, a costumed designed rubber compocomponent) nent (shown in Fig. 3 as a cone-shaped rubber acts like a spring in axial direction, acts like a piston pumping fluid, and acts like a volumetric spring in volumetric or bulge direction, containing fluid. The top fluid By considering P γh P, constants A and B L will be as follows: b a A 4Lln b P µ a ln b a x (4)
3 B a lnb b lna 4µLln a b P lna ln a x b By using Q 2πrudr, flow in gap will be derived based on pressure gradient and mass velocity. The flow loss in gap depends on fluid flow and mass velocity and be written as, P R 21i QR 21ii x (5) On or hand, force applied to mass by fluid is important in simulations. The shear stress on mass surface is given by τ µ du dr Where must be calculated at r a. By Differentiating u with respect to r, shear stress will be obtained. Where C and C are (6) τ F C 3 P C 4 x (7) A surf b a C 4Lbln b a b 2L µ C bln b a The fluid force acting on mass be written as a function of flow and mass velocity by plugging Eq.(5) into Eq.(7). (8) FC.R.A.QC.R C A.x (9) Now, by considering obtained equations, state space equations, from bond graph model, be derived as q q V (10) q A V P I (11) P q C R P I q C (12) P I A (13) q A q q A C C R C (14) R q (15) q C R q C R (16) q A (17) q C R q C (18) q C R q C (19) q (20) The input force or effort on bond 1, is given by F q C R V A q C (21) In above state space equations, q, q, q, q, q and q are generalized displacement variables, P,,, and are momentum variables. To simulate model of Fig. 4, MATLAB Program and above state space equations with following baseline parameters were used. velocity across mount, m/s effective area of top metal, m2 effective area of mass in inertia track, 2.162e-4 m2 diameter of inertia track, m fluid inertia in upper and below parts of inertia track, same as I and, Ns2/m5 inertia track flow resistance, same as R and R, Ns/m5 inertia of piston, same as, kg loss of inertia around mass, same as, flow loss in gap, Ns/ m5 axial stiffness of rubber in upper chamber (C 1 K ), 2.05e6 N/m damping component of rubber in upper chamber (R B ), 145 Ns/m top chamber volumetric or bulge stiffness (C 1 K ), 1.1e11 N/m5 bottom chamber volumetric or bulge stiffness (C 1 K ) 2.1e9 N/m5 stiffness of springs in inertia track, (C 1 K ), 2*1000 N/m flow loss around piston(r C.R C A ), Ns/m flow loss around piston(r C.R.A ), Ns/m fluid inertia in 2nd inertia track, Ns2/m5 2nd inertia track flow resistance, Ns/m5 The fluid inertia is given by (22) Where ρ is fluid density (1765 kg/m 3 ) and L is length of upper and lower parts of inertia track ( m). Also, be calculated in same manner ( height of piston in inertia track is 25.4e-3 m). The length of second inertia track is m and its diameter is m. ICA
4 MATLAB program, with above baseline parameters, was used to simulate state space Eqs. (10) (21). Fig. 6 shows new hydraulic mount dynamic stiffness (defined as ) versus frequency. The figure clearly shows that indeed that are two notches and two peaks. From figure, one see that first and second notch frequencies occur at and Hz, and peak frequencies at and Hz, respectively. Of course, one place notch and peak frequencies to any desired location by altering hydraulic mount parameters. The first notch location be varied by a change in second inertia track parameters and second notch location by a change in first inertia track parameters and also mass and springs. Fig. 9 shows that if one varies piston material (lead), one alter location of notch and peak frequencies. Figure 9. Dynamic stiffness as piston material changes In this novel design, re is an opportunity to vanish one notch by fixing mass in inertia track. In or words, by using magnets, one change a double notch fluid mount design to a fluid mount design with only one notch. Fig. 10 shows notch location in this situation. Figure 6. Dynamic stiffness of double-notch hydraulic engine mount (MATLAB simulation) For example, Fig. 7 shows that if one varies second inertia track parameters, one alter location of first notch frequency and first and second peak frequencies. In this simulation diameter of second inertia track was altered from m to m. Figure 7. Dynamic stiffness as diameter of second inertia track changes Fig. 8 shows variation in location of notches and peaks as stiffness of springs in inertia track is varied. In this case second notch frequency will vary from Hz to Hz. Figure 10. Dynamic stiffness with and without magnets Often, it is necessary to alter location of notch frequencies after hydraulic mount is manufactured. Also, if notch frequency or frequencies need to be retuned, ideally it be done without a need for any fluid mount redesign. Similar to approach in (Vahdati, 2005), in this new hydraulic engine mount design, volumetric stiffness ; be easily varied if gas pressure behind rubber diaphragm is increased or decreased. This tunability be very useful both to original equipment manufacturer and to customer. The two notch frequencies be fine tuned with help of ; without need for any hydraulic mount redesign. If it is needed to fine tune fluid mount notches in field, one do so by changing gas pressure. Fine tuning notch frequencies in field provide better cabin noise and vibration isolation than tuning fluid mount notches at OEM s manufacturing site. Figs. 11 and 12 show that as volume stiffness is varied, first and second notch frequencies be relocated. Figure 8. Dynamic stiffness as stiffness of springs change Figure 11. First notch frequency as bottom volume stiffness, ; is varied 4 ICA 2010
5 9. Vahdati, N. (2005). "Double-Notch Single-Pumper Fluid Mounts." Journal of Sound and Vibration 285: Yunhe, Y. a., N. a. Nagi G. and D. Rao V. (2001). "A literature review of automotive vehicle engine mounting systems." Mechanism and Machine Theory 36: Figure 12. Second notch frequency as bottom volume stiffness, ; is varied CONCLUSIONS For fixed wing applications, current commercially available passive hydraulic engine mount designs have only one notch frequency; refore, cabin noise and vibration isolation is only possible at N1 or at N2, but not both. Here, in this paper, a new passive hydraulic engine mount design has been presented, which has two notch frequencies. The new design was described and its mamatical model was presented. It was shown that indeed this new design provide vibration and noise isolation at two frequencies and one easily tune notch and peak frequencies by changing gas pressure and appropriate mount parameters. REFERENCES 1. Adigunaa, H., M. Tiwaria, R. Singh, H. E. Tsengb and D. Hrovat (2003). "Transient Response of a Hydraulic Engine Mount." Journal of Sound and Vibration 268: Christopherson, J. and G. N. Jazar (2006). "Dynamic Behavior Comparison of Passive Hydraulic Engine Mounts. Part 1: Mamatical Analysis." Journal of Sound and Vibration 290: Kim, G. and R. Singh (1993). "Nonlinear Analysis of Automotive Hydraulic Engine Mount." Journal of Dynamic Systems, Measurement, and Control 115: Kim, G. and R. Singh (1995). "A Study Of Passive And Adaptive Hydraulic Engine Mount Systems With Emphasis On Non-Linear Characteristics." Journal of Sound and Vibration 179(3): Shaughnessy, E. J., I. M. Katz and J. P. Schaffer (2005). Introduction to fluid mechanics. New York, Oxford University Press. 6. Singh, R., G. Kim and P. V. Ravindra (1992). "Linear Analysis of Automotive Hydro-Mechanical Mount With Emphasis on Decoupler Characteristics." Journal of Sound and Vibration 158(2): Swanson, D. A., H. T. Wu and H. Ashrafiuon (1993). "Optimization of Aircraft Engine Suspension Systems." Journal of Aircraft 30(6): Vahdati, N. (1998). "A Detailed Mechanical Model of a Double Pumper Fluid Mount." Journal of Vibration and Acoustics 120 (2). ICA
VOICE COIL FLUID-TUNED ACTUATOR
VOCE COL FLUD-TUNED ACTUATOR Nader Vahdati etroleum nstitute, O Box 25, Mechanical Engineering, Abu Dhabi, UAE email: nvahdati@pi.ac.ae A new actuator concept is presented here in this paper. This unique
More informationExistence of super-harmonics in quarter-vehicle system responses with nonlinear inertia hydraulic track mount given sinusoidal force excitation
Journal of Sound and Vibration 313 (8) 367 374 Rapid Communication JOURNAL OF SOUND AND VIBRATION Existence of super-harmonics in quarter-vehicle system responses with nonlinear inertia hydraulic track
More informationAnatomy of a Real-Life Non-Linear Device: Hydraulic Engine Mount
Anatomy of a Real-Life Non-Linear Device: Hydraulic Engine Mount Rajendra Singh and Song He Acoustics and Dynamics Laboratory, Department of Mechanical Engineering and
More informationMeasurement Techniques for Engineers. Motion and Vibration Measurement
Measurement Techniques for Engineers Motion and Vibration Measurement Introduction Quantities that may need to be measured are velocity, acceleration and vibration amplitude Quantities useful in predicting
More informationApproximate step response of a nonlinear hydraulic mount using a simplified linear model
Journal of Sound and Vibration 99 (007) 656 663 Short Communication JOURNAL OF SOUND AND VIBRATION Approximate step response of a nonlinear hydraulic mount using a simplified linear model Song He, Rajendra
More informationGrazing Bifurcations and Chaos of a Hydraulic Engine Mount
Grazing Bifurcations and Chaos of a Hydraulic Engine Mount 1Associated Professor, 2MSc. School of Automotive Engineering, Iran University of Science and Technology, Iran * Corresponding Author Abstract
More informationDynamic Analysis on Vibration Isolation of Hypersonic Vehicle Internal Systems
International Journal of Engineering Research and Technology. ISSN 0974-3154 Volume 6, Number 1 (2013), pp. 55-60 International Research Publication House http://www.irphouse.com Dynamic Analysis on Vibration
More informationT1 T e c h n i c a l S e c t i o n
1.5 Principles of Noise Reduction A good vibration isolation system is reducing vibration transmission through structures and thus, radiation of these vibration into air, thereby reducing noise. There
More informationCHAPTER 3 QUARTER AIRCRAFT MODELING
30 CHAPTER 3 QUARTER AIRCRAFT MODELING 3.1 GENERAL In this chapter, the quarter aircraft model is developed and the dynamic equations are derived. The quarter aircraft model is two degrees of freedom model
More informationDynamic design of automotive systems: Engine mounts and structural joints
SaÅdhanaÅ, Vol. 25, Part 3, June 2000, pp. 319±330. # Printed in India Dynamic design of automotive systems: Engine mounts and structural joints R SINGH Department of Mechanical Engineering, Ohio State
More informationVIBRATION ANALYSIS OF E-GLASS FIBRE RESIN MONO LEAF SPRING USED IN LMV
VIBRATION ANALYSIS OF E-GLASS FIBRE RESIN MONO LEAF SPRING USED IN LMV Mohansing R. Pardeshi 1, Dr. (Prof.) P. K. Sharma 2, Prof. Amit Singh 1 M.tech Research Scholar, 2 Guide & Head, 3 Co-guide & Assistant
More informationChapter 23: Principles of Passive Vibration Control: Design of absorber
Chapter 23: Principles of Passive Vibration Control: Design of absorber INTRODUCTION The term 'vibration absorber' is used for passive devices attached to the vibrating structure. Such devices are made
More informationIn this lecture you will learn the following
Module 9 : Forced Vibration with Harmonic Excitation; Undamped Systems and resonance; Viscously Damped Systems; Frequency Response Characteristics and Phase Lag; Systems with Base Excitation; Transmissibility
More informationModule 4: Dynamic Vibration Absorbers and Vibration Isolator Lecture 19: Active DVA. The Lecture Contains: Development of an Active DVA
The Lecture Contains: Development of an Active DVA Proof Mass Actutor Application of Active DVA file:///d /chitra/vibration_upload/lecture19/19_1.htm[6/25/2012 12:35:51 PM] In this section, we will consider
More informationDYNAMIC TUNING OF HYDRAULIC ENGINE MOUNT USING MULTIPLE INERTIA TRACKS. A Thesis
DYNAMIC TUNING OF HYDRAULIC ENGINE MOUNT USING MULTIPLE INERTIA TRACKS A Thesis Presented in Partial Fulfillment of the Requirements for the Degree Master of Science in the Graduate School of The Ohio
More informationAdaptive Electromechanical Tuned Vibration Absorbers and Their Application in Semi-Active Fluid Mounts
roceedgs of th nternational ongress on Acoustics, A 3-7 August, Sydney, Australia Adaptive Electromechanical Tuned Vibration Absorbers and Their Application Semi-Active Fluid Mounts Nader Vahdati (), Somayeh
More informationAn Analysis Technique for Vibration Reduction of Motor Pump
An Analysis Technique for Vibration Reduction of Motor Pump Young Kuen Cho, Seong Guk Kim, Dae Won Lee, Paul Han and Han Sung Kim Abstract The purpose of this study was to examine the efficiency of the
More informationMOOC QP Set 2 Principles of Vibration Control
Section I Section II Section III MOOC QP Set 2 Principles of Vibration Control (TOTAL = 100 marks) : 20 questions x 1 mark/question = 20 marks : 20 questions x 2 marks/question = 40 marks : 8 questions
More informationChapter a. Spring constant, k : The change in the force per unit length change of the spring. b. Coefficient of subgrade reaction, k:
Principles of Soil Dynamics 3rd Edition Das SOLUTIONS MANUAL Full clear download (no formatting errors) at: https://testbankreal.com/download/principles-soil-dynamics-3rd-editiondas-solutions-manual/ Chapter
More informationWEEKS 8-9 Dynamics of Machinery
WEEKS 8-9 Dynamics of Machinery References Theory of Machines and Mechanisms, J.J.Uicker, G.R.Pennock ve J.E. Shigley, 2011 Mechanical Vibrations, Singiresu S. Rao, 2010 Mechanical Vibrations: Theory and
More informationLECTURE 12. STEADY-STATE RESPONSE DUE TO ROTATING IMBALANCE
LECTURE 12. STEADY-STATE RESPONSE DUE TO ROTATING IMBALANCE Figure 3.18 (a) Imbalanced motor with mass supported by a housing mass m, (b) Freebody diagram for, The product is called the imbalance vector.
More informationOn The Finite Element Modeling Of Turbo Machinery Rotors In Rotor Dynamic Analysis
Proceedings of The Canadian Society for Mechanical Engineering International Congress 2018 CSME International Congress 2018 May 27-30, 2018, Toronto, On, Canada On The Finite Element Modeling Of Turbo
More informationSOUND TRANSMISSION LOSS MEASUREMENTS - AN AUTOMOTIVE OVERVIEW
NSA-15 Goa National Symposium on Acoustics Acoustics for Ocean Environment SOUND TRANSMISSION LOSS MEASUREMENTS - AN AUTOMOTIVE OVERVIEW Paresh Shravage Alfa Acoustics Pune, Maharashtra 1133, India e-mail:
More information1859. Forced transverse vibration analysis of a Rayleigh double-beam system with a Pasternak middle layer subjected to compressive axial load
1859. Forced transverse vibration analysis of a Rayleigh double-beam system with a Pasternak middle layer subjected to compressive axial load Nader Mohammadi 1, Mehrdad Nasirshoaibi 2 Department of Mechanical
More informationMOOC QP Set 1 Principles of Vibration Control
Section I Section II Section III MOOC QP Set 1 Principles of Vibration Control (TOTAL = 100 marks : 0 questions x 1 mark/question = 0 marks : 0 questions x marks/question = 40 marks : 8 questions x 5 marks/question
More informationIndex. Index. More information. in this web service Cambridge University Press
A-type elements, 4 7, 18, 31, 168, 198, 202, 219, 220, 222, 225 A-type variables. See Across variable ac current, 172, 251 ac induction motor, 251 Acceleration rotational, 30 translational, 16 Accumulator,
More informationMathematical model of electromechanical system with variable dissipativity
Mathematical model of electromechanical system with variable dissipativity Alexsandr Baykov, Boris Gordeev 2 Nizhny Novgorod State Technical University n. a. R. E. Alexeev, Nizhny Novgorod, Russia 2 Institute
More informationThe student will experimentally determine the parameters to represent the behavior of a damped oscillatory system of one degree of freedom.
Practice 3 NAME STUDENT ID LAB GROUP PROFESSOR INSTRUCTOR Vibrations of systems of one degree of freedom with damping QUIZ 10% PARTICIPATION & PRESENTATION 5% INVESTIGATION 10% DESIGN PROBLEM 15% CALCULATIONS
More informationVibration Analysis of a Horizontal Washing Machine, Part IV: Optimal Damped Vibration Absorber
RESEARCH ARTICLE Vibration Analysis of a Horizontal Washing Machine, Part IV: Optimal Damped Vibration Absorber Galal Ali Hassaan Department of Mechanical Design & Production, Faculty of Engineering, Cairo
More informationMetamaterials with tunable dynamic properties
Metamaterials with tunable dynamic properties Varvara Kouznetsova Marc Geers 6 October 2015 Mechanics of Materials Project aim development of new generation mechanical metamaterials with adaptive, tunable
More informationPorous Materials for Sound Absorption and Transmission Control
Purdue e-pubs Publications of the Ray W. School of Mechanical Engineering 8-2005 Porous Materials for Sound Absorption and Transmission Control J Stuart Bolton, bolton@purdue.edu Follow this and additional
More information19 th INTERNATIONAL CONGRESS ON ACOUSTICS MADRID, 2-7 SEPTEMBER 2007
19 th INTERNATIONAL CONGRESS ON ACOUSTICS MADRID, 2-7 SEPTEMBER 2007 FREQUENCY DEPENDENCY AND ANISOTROPY OF THE ELASTIC CONSTANTS OF (NON-)POROUS MATERIALS AND THEIR INFLUENCE ON THE USAGE IN BUILDING
More informationDSC HW 3: Assigned 6/25/11, Due 7/2/12 Page 1
DSC HW 3: Assigned 6/25/11, Due 7/2/12 Page 1 Problem 1 (Motor-Fan): A motor and fan are to be connected as shown in Figure 1. The torque-speed characteristics of the motor and fan are plotted on the same
More information1820. Selection of torsional vibration damper based on the results of simulation
8. Selection of torsional vibration damper based on the results of simulation Tomasz Matyja, Bogusław Łazarz Silesian University of Technology, Faculty of Transport, Gliwice, Poland Corresponding author
More informationChapter 5 Design. D. J. Inman 1/51 Mechanical Engineering at Virginia Tech
Chapter 5 Design Acceptable vibration levels (ISO) Vibration isolation Vibration absorbers Effects of damping in absorbers Optimization Viscoelastic damping treatments Critical Speeds Design for vibration
More informationFundamentals of noise and Vibration analysis for engineers
Fundamentals of noise and Vibration analysis for engineers M.P.NORTON Department of Mechanical Engineering, University of Western Australia CAMBRIDGE UNIVERSITY PRESS Preface xii Acknowledgements xv Introductory
More information681. Design of elastomeric shock absorbers with a soft stiffness characteristics of type force-settlement
681. Design of elastomeric shock absorbers with a soft stiffness characteristics of type force-settlement V. Gonca 1, J. Shvab Riga Technical University, Ezermalas 6 d, LV-1006, Riga, Latvia E-mail: 1
More informationEnergy balance in self-powered MR damper-based vibration reduction system
BULLETIN OF THE POLISH ACADEMY OF SCIENCES TECHNICAL SCIENCES, Vol. 59, No. 1, 2011 DOI: 10.2478/v10175-011-0011-4 Varia Energy balance in self-powered MR damper-based vibration reduction system J. SNAMINA
More informationAnalysis of powertrain motions given a combination of active and passive isolators
Analysis of powertrain motions given a combination of active and passive isolators Jae-Yeol Park a) and Rajendra Singh b) (Received: 8 September 2008; Revised: 17 February 2009; Accepted: 19 February 2009)
More informationBasic Principle of Strain Gauge Accelerometer. Description of Strain Gauge Accelerometer
Basic Principle of Strain Gauge Accelerometer When a cantilever beam attached with a mass at its free end is subjected to vibration, vibrational displacement of the mass takes place. Depending on the displacement
More informationDEVELOPMENT OF A NOVEL ACTIVE ISOLATION CONCEPT 1
DEVELOPMENT OF A NOVEL ACTIVE ISOLATION CONCEPT 1 Michiel J. Vervoordeldonk, Theo A.M. Ruijl, Rob M.G. Rijs Philips Centre for Industrial Technology, PO Box 518, 5600 MD Eindhoven, The Netherlands 2 1
More informationAircraft Cabin Acoustic Modeling
Penn State 2012 Center for Acoustics and Vibration Workshop Aircraft Cabin Acoustic Modeling 2012 Penn State Center for Acoustics and Vibration Workshop Adam Weston Senior Structural-Acoustics Specialist
More information/ m U) β - r dr/dt=(n β / C) β+ (N r /C) r [8+8] (c) Effective angle of attack. [4+6+6]
Code No: R05322101 Set No. 1 1. (a) Explain the following terms with examples i. Stability ii. Equilibrium. (b) Comment upon the requirements of stability of a i. Military fighter aircraft ii. Commercial
More informationMV Module 5 Solution. Module 5
Module 5 Q68. With a neat diagram explain working principle of a vibrometer. D-14-Q5 (a)-10m Ans: A vibrometer or a seismometer is an instrument that measures the displacement of a vibrating body. It can
More informationA system is defined as a combination of components (elements) that act together to perform a certain objective. System dynamics deal with:
Chapter 1 Introduction to System Dynamics A. Bazoune 1.1 INTRODUCTION A system is defined as a combination of components (elements) that act together to perform a certain objective. System dynamics deal
More informationIntroduction to Continuous Systems. Continuous Systems. Strings, Torsional Rods and Beams.
Outline of Continuous Systems. Introduction to Continuous Systems. Continuous Systems. Strings, Torsional Rods and Beams. Vibrations of Flexible Strings. Torsional Vibration of Rods. Bernoulli-Euler Beams.
More informationLaboratory notes. Torsional Vibration Absorber
Titurus, Marsico & Wagg Torsional Vibration Absorber UoB/1-11, v1. Laboratory notes Torsional Vibration Absorber Contents 1 Objectives... Apparatus... 3 Theory... 3 3.1 Background information... 3 3. Undamped
More informationNonlinear Rolling Element Bearings in MADYN 2000 Version 4.3
- 1 - Nonlinear Rolling Element Bearings in MADYN 2000 Version 4.3 In version 4.3 nonlinear rolling element bearings can be considered for transient analyses. The nonlinear forces are calculated with a
More information2.3 Concept of Active Acoustic Metamaterials
Active Acoustic Metamaterials 23 2.3 Concept of Active Acoustic Metamaterials In order to understand the concept and the structure of an active acoustic metamaterial, consider the structure of the external
More informationVibration Control Prof. Dr. S. P. Harsha Department of Mechanical & Industrial Engineering Indian Institute of Technology, Roorkee
Vibration Control Prof. Dr. S. P. Harsha Department of Mechanical & Industrial Engineering Indian Institute of Technology, Roorkee Module - 1 Review of Basics of Mechanical Vibrations Lecture - 2 Introduction
More informationInfluence of Eccentricity and Angular Velocity on Force Effects on Rotor of Magnetorheological Damper
EPJ Web of Conferences 18, 291 (218) EFM 217 https://doi.org/1.151/epjconf/21818291 Influence of Eccentricity and Angular Velocity on Force Effects on Rotor of Magnetorheological Damper Dominik Šedivý
More informationAcoustics-An An Overview. Lecture 1. Vibro-Acoustics. What? Why? How? Lecture 1
Vibro-Acoustics Acoustics-An An Overview 1 Vibro-Acoustics What? Why? How? 2 Linear Non-Linear Force Motion Arbitrary motion Harmonic Motion Mechanical Vibrations Sound (Acoustics) 3 Our heart beat, our
More informationStudies of Sound Radiation From Beams with Acoustic Black Holes
Studies of Sound Radiation From Beams with Acoustic Black Holes Chenhui Zhao 1, M.G. Prasad 2 Stevens Institute of Technology Abstract: Recently, Acoustic Black Holes (), a new passive structural modification
More informationStep 1: Mathematical Modeling
083 Mechanical Vibrations Lesson Vibration Analysis Procedure The analysis of a vibrating system usually involves four steps: mathematical modeling derivation of the governing uations solution of the uations
More informationInvestigation of a nonlinear dynamic hydraulic system model through the energy analysis approach
Journal of Mechanical Science and Technology 3 (009) 973~979 Journal of Mechanical Science and Technology www.springerlink.com/content/1738-9x DOI.07/s6-009-081- Investigation of a nonlinear dynamic hydraulic
More informationStudy of the influence of the resonance changer on the longitudinal vibration of marine propulsion shafting system
Study of the influence of the resonance changer on the longitudinal vibration of marine propulsion shafting system Zhengmin Li 1, Lin He 2, Hanguo Cui 3, Jiangyang He 4, Wei Xu 5 1, 2, 4, 5 Institute of
More informationIntroduction to Mechanical Vibration
2103433 Introduction to Mechanical Vibration Nopdanai Ajavakom (NAV) 1 Course Topics Introduction to Vibration What is vibration? Basic concepts of vibration Modeling Linearization Single-Degree-of-Freedom
More informationLecture 20. Measuring Pressure and Temperature (Chapter 9) Measuring Pressure Measuring Temperature MECH 373. Instrumentation and Measurements
MECH 373 Instrumentation and Measurements Lecture 20 Measuring Pressure and Temperature (Chapter 9) Measuring Pressure Measuring Temperature 1 Measuring Acceleration and Vibration Accelerometers using
More informationTowards Rotordynamic Analysis with COMSOL Multiphysics
Towards Rotordynamic Analysis with COMSOL Multiphysics Martin Karlsson *1, and Jean-Claude Luneno 1 1 ÅF Sound & Vibration *Corresponding author: SE-169 99 Stockholm, martin.r.karlsson@afconsult.com Abstract:
More information10 Measurement of Acceleration, Vibration and Shock Transducers
Chapter 10: Acceleration, Vibration and Shock Measurement Dr. Lufti Al-Sharif (Revision 1.0, 25/5/2008) 1. Introduction This chapter examines the measurement of acceleration, vibration and shock. It starts
More informationNUMERICAL MODELLING OF RUBBER VIBRATION ISOLATORS
NUMERICAL MODELLING OF RUBBER VIBRATION ISOLATORS Clemens A.J. Beijers and André de Boer University of Twente P.O. Box 7, 75 AE Enschede, The Netherlands email: c.a.j.beijers@utwente.nl Abstract An important
More informationa) Find the equation of motion of the system and write it in matrix form.
.003 Engineering Dynamics Problem Set Problem : Torsional Oscillator Two disks of radius r and r and mass m and m are mounted in series with steel shafts. The shaft between the base and m has length L
More informationFREE VIBRATION ANALYSIS OF THIN CYLINDRICAL SHELLS SUBJECTED TO INTERNAL PRESSURE AND FINITE ELEMENT ANALYSIS
FREE VIBRATION ANALYSIS OF THIN CYLINDRICAL SHELLS SUBJECTED TO INTERNAL PRESSURE AND FINITE ELEMENT ANALYSIS J. Kandasamy 1, M. Madhavi 2, N. Haritha 3 1 Corresponding author Department of Mechanical
More informationApplication of a Helmholtz resonator excited by grazing flow for manipulation of a turbulent boundary layer
Application of a Helmholtz resonator excited by grazing flow for manipulation of a turbulent boundary layer Farzin Ghanadi School of Mechanical Engineering The University of Adelaide South Australia, 5005
More informationDynamics of Rotor Systems with Clearance and Weak Pedestals in Full Contact
Paper ID No: 23 Dynamics of Rotor Systems with Clearance and Weak Pedestals in Full Contact Dr. Magnus Karlberg 1, Dr. Martin Karlsson 2, Prof. Lennart Karlsson 3 and Ass. Prof. Mats Näsström 4 1 Department
More information3.1 Centrifugal Pendulum Vibration Absorbers: Centrifugal pendulum vibration absorbers are a type of tuned dynamic absorber used for the reduction of
3.1 Centrifugal Pendulum Vibration Absorbers: Centrifugal pendulum vibration absorbers are a type of tuned dynamic absorber used for the reduction of torsional vibrations in rotating and reciprocating
More informationAEROSPACE ENGINEERING
AEROSPACE ENGINEERING Subject Code: AE Course Structure Sections/Units Topics Section A Engineering Mathematics Topics (Core) 1 Linear Algebra 2 Calculus 3 Differential Equations 1 Fourier Series Topics
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 Analysis of Vibration Transmissibility on a System using Finite Element Analysis Rajesh
More informationApplication of Neuro Fuzzy Reduced Order Observer in Magnetic Bearing Systems
Application of Neuro Fuzzy Reduced Order Observer in Magnetic Bearing Systems M. A., Eltantawie, Member, IAENG Abstract Adaptive Neuro-Fuzzy Inference System (ANFIS) is used to design fuzzy reduced order
More informationDynamic Analysis of Pelton Turbine and Assembly
Dynamic Analysis of Pelton Turbine and Assembly Aman Rajak, Prateek Shrestha, Manoj Rijal, Bishal Pudasaini, Mahesh Chandra Luintel Department of Mechanical Engineering, Central Campus, Pulchowk, Institute
More informationDesign and Research on Characteristics of a New Vibration Isolator with Quasi-zero-stiffness Shi Peicheng1, a, Nie Gaofa1, b
International Conference on Mechanics, Materials and Structural Engineering (ICMMSE 2016 Design and Research on Characteristics of a New Vibration Isolator with Quasi-zero-stiffness Shi Peicheng1, a, Nie
More informationDynamic characterization of engine mount at different orientation using sine swept frequency test
Dynamic characterization of engine mount at different orientation using sine swept frequency test Zaidi Mohd Ripin and Ooi Lu Ean, School of Mechanical Engineering Universiti Sains Malaysia (USM), 14300
More informationSound diffraction by the splitter in a turbofan rotor-stator gap swirling flow
Nationaal Lucht- en Ruimtevaartlaboratorium National Aerospace Laboratory NLR Sound diffraction by the splitter in a turbofan rotor-stator gap swirling flow R.J. Nijboer This report is based on a presentation
More information226 J. Acoust. Soc. Am. 106 (1), July /99/106(1)/226/7/$ Acoustical Society of America 226
Low frequency passive noise control of a piston structure with a weak radiating cell Bradley W. Ross and Ricardo A. Burdisso Vibration and Acoustic Laboratories, Department of Mechanical Engineering, Virginia
More informationExploiting pattern transformation to tune phononic band gaps in a two-dimensional granular crystal
Exploiting pattern transformation to tune phononic band gaps in a two-dimensional granular crystal The Harvard community has made this article openly available. Please share how this access benefits you.
More informationON THE PREDICTION OF EXPERIMENTAL RESULTS FROM TWO PILE TESTS UNDER FORCED VIBRATIONS
Transactions, SMiRT-24 ON THE PREDICTION OF EXPERIMENTAL RESULTS FROM TWO PILE TESTS UNDER FORCED VIBRATIONS 1 Principal Engineer, MTR & Associates, USA INTRODUCTION Mansour Tabatabaie 1 Dynamic response
More information557. Radial correction controllers of gyroscopic stabilizer
557. Radial correction controllers of gyroscopic stabilizer M. Sivčák 1, J. Škoda, Technical University in Liberec, Studentská, Liberec, Czech Republic e-mail: 1 michal.sivcak@tul.cz; jan.skoda@pevnosti.cz
More informationThe Analysis of Aluminium Cantilever Beam with Piezoelectric Material by changing Position of piezo patch over Length of Beam
The Analysis of Aluminium Cantilever Beam with Piezoelectric Material by changing Position of piezo patch over Length of Beam Mr. Lalit R. Shendre 1, Prof. Bhamare V.G. 2 1PG Student, Department of Mechanical
More information1427. Response and performance of a nonlinear vibration isolator with high-static-low-dynamic-stiffness under shock excitations
1427. Response and performance of a nonlinear vibration isolator with high-static-low-dynamic-stiffness under shock excitations Yong Wang 1, Shunming Li 2, Jiyong Li 3, Xingxing Jiang 4, Chun Cheng 5 College
More informationDamping of materials and members in structures
Journal of Physics: Conference Series Damping of materials and members in structures To cite this article: F Orban 0 J. Phys.: Conf. Ser. 68 00 View the article online for updates and enhancements. Related
More informationA MAGNETORHEOLOGIC SEMI-ACTIVE ISOLATOR TO REDUCE NOISE AND VIBRATION TRANSMISSIBILITY IN AUTOMOBILES
A MAGNETORHEOLOGIC SEMI-ACTIVE ISOLATOR TO REDUCE NOISE AND VIBRATION TRANSMISSIBILITY IN AUTOMOBILES Gregory J. Stelzer Delphi Automotive Systems Chassis Systems Test Center, Dayton, OH 45401-1245 Mark
More informationCar Dynamics using Quarter Model and Passive Suspension; Part V: Frequency Response Considering Driver-seat
357 Car Dynamics using Quarter Model and Passive Suspension; Part V: Frequency Response Considering Driver-seat Galal Ali Hassaan Emeritus Professor, Department of Mechanical Design & Production, Faculty
More informationLANMARK UNIVERSITY OMU-ARAN, KWARA STATE DEPARTMENT OF MECHANICAL ENGINEERING COURSE: MECHANICS OF MACHINE (MCE 322). LECTURER: ENGR.
LANMARK UNIVERSITY OMU-ARAN, KWARA STATE DEPARTMENT OF MECHANICAL ENGINEERING COURSE: MECHANICS OF MACHINE (MCE 322). LECTURER: ENGR. IBIKUNLE ROTIMI ADEDAYO SIMPLE HARMONIC MOTION. Introduction Consider
More informationMODELLING OF A HYDRAULIC ENGINE MOUNT FOCUSING ON RESPONSE TO SINUSOIDAL AND COMPOSITE EXCITATIONS
Journal of Sound and Vibration (1995) 184(3), 503 528 MODELLING OF A HYDRAULIC ENGINE MOUNT FOCUSING ON RESPONSE TO SINUSOIDAL AND COMPOSITE EXCITATIONS J. E. COLGATE, C.-T. CHANG, Y.-C. CHIOU, W. K. LIU
More informationNonlinear effects on the rotor driven by a motor with limited power
Applied and Computational Mechanics 1 (007) 603-61 Nonlinear effects on the rotor driven by a motor with limited power L. Pst Institute of Thermomechanics, Academy of Sciences of CR, Dolejškova 5,18 00
More informationAnalytical Study of Engine Mount to Suit the Damping Requirements of Engine
Analytical Study of Engine Mount to Suit the Damping Requirements of Engine A. S. Sathawane PG student, S.S.G.B.C.O.E. & T; Department of Mechanical Engineering, Bhusawal-425203, NMU A. V. Patil Faculty
More informationANALYSIS OF NATURAL FREQUENCIES OF DISC-LIKE STRUCTURES IN WATER ENVIRONMENT BY COUPLED FLUID-STRUCTURE-INTERACTION SIMULATION
6 th IAHR International Meeting of the Workgroup on Cavitation and Dynamic Problems in Hydraulic Machinery and Systems, September 9-11, 15, Ljubljana, Slovenia ANALYSIS O NATURAL REQUENCIES O DISC-LIKE
More informationIntegration of measured receptance into a time domain simulation of a Multi Body Model using SIMPACK
Fakultät Maschinenwesen Professur für Dynamik und Mechanismentechnik Integration of measured receptance into a time domain simulation of a Multi Body Model using SIMPACK Dipl.-Ing. Johannes Woller Prof.
More informationDynamics of Machinery
Dynamics of Machinery Two Mark Questions & Answers Varun B Page 1 Force Analysis 1. Define inertia force. Inertia force is an imaginary force, which when acts upon a rigid body, brings it to an equilibrium
More informationMODELLING AND TESTING OF AN ERF VIBRATION DAMPER FOR LIGHT ROTORS WITH LARGE AMPLITUDES
MODELLING AND TESTING OF AN ERF VIBRATION DAMPER FOR LIGHT ROTORS WITH LARGE AMPLITUDES Jens Bauer, bauer@sdy.tu-darmstadt.de Institute of Structural Dynamics, Technische Universität Darmstadt, Germany
More informationGraph-theoretic Modeling and Dynamic Simulation of an Automotive Torque Converter
Graph-theoretic Modeling and Dynamic Simulation of an Automotive Torque Converter Joydeep M. Banerjee and John J. McPhee Department of Systems Design Engineering University of Waterloo, Waterloo, Ontario
More informationHysteresis Modelling of an MR Damper Applied to Suspension System
Hysteresis Modelling of an MR Damper Applied to Suspension System Samanwita Roy Department of Mechanical Engineering Shree L. R. Tiwari College of Engineering, Mumbai, Maharashtra, India Abstract- Comfort,
More informationDesign of an Innovative Acoustic Metamaterial
Design of an Innovative Acoustic Metamaterial PAVLOS MAVROMATIDIS a, ANDREAS KANARACHOS b Electrical Engineering Department a, Mechanical Engineering Department b Frederick University 7 Y. Frederickou
More informationFuzzy Logic Control for Half Car Suspension System Using Matlab
Fuzzy Logic Control for Half Car Suspension System Using Matlab Mirji Sairaj Gururaj 1, Arockia Selvakumar A 2 1,2 School of Mechanical and Building Sciences, VIT Chennai, Tamilnadu, India Abstract- To
More informationNV-TECH-Design: Scalable Automatic Modal Hammer (SAM) for structural dynamics testing
NV-TECH-Design: Scalable Automatic Modal Hammer (SAM) for structural dynamics testing NV-TECH-Design Scalable Automatic Modal Hammer (SAM) für structural testing. Patent number: DE 10 2015 110 597.7 Description
More informationModelling and State Dependent Riccati Equation Control of an Active Hydro-Pneumatic Suspension System
Proceedings of the International Conference of Control, Dynamic Systems, and Robotics Ottawa, Ontario, Canada, May 15-16 214 Paper No. 31 Modelling and State Dependent Riccati Equation Control of an Hydro-Pneumatic
More informationDESIGN AND STANDARDIZATION OF BASE FRAME & ANT VIBRATION MOUNTS FOR BALANCED OPPOSED PISTON AIR COMPRESSOR
DESIGN AND STANDARDIZATION OF BASE FRAME & ANT VIBRATION MOUNTS FOR BALANCED OPPOSED PISTON AIR COMPRESSOR KISHOR D. JADHAV & MANEET.R.DHANVIJAY Vishvakarma Institute of Technology, Pune, India E-mail
More informationInvestigation of Passive Control Devices for Potential Application to a Launch Vehicle Structure to Reduce the Interior Noise Levels During Launch
Investigation of Passive Control Devices for Potential Application to a Launch Vehicle Structure to Reduce the Interior Noise Levels During Launch Report for Stage 4 Tasks 1 and 2 July 24 Prepared For:
More informationSound Propagation through Media. Nachiketa Tiwari Indian Institute of Technology Kanpur
Sound Propagation through Media Nachiketa Tiwari Indian Institute of Technology Kanpur LECTURE-13 WAVE PROPAGATION IN SOLIDS Longitudinal Vibrations In Thin Plates Unlike 3-D solids, thin plates have surfaces
More informationA nonlinear dynamic vibration model of defective bearings: The importance of modelling the finite size of rolling elements
A nonlinear dynamic vibration model of defective bearings: The importance of modelling the finite size of rolling elements Alireza Moazenahmadi, Dick Petersen and Carl Howard School of Mechanical Engineering,
More information