PSM II SEMINARPSM II SEMINAR
DEPARTMENT OF AUTOMOTIVE DEPARTMENT OF AUTOMOTIVE AND AERONAUTICAND AERONAUTIC
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DRUM BRAKE SQUEAL NOISE DRUM BRAKE SQUEAL NOISE USING COMPLEX EIGENVALUE USING COMPLEX EIGENVALUE
ANALYSISANALYSIS
BY : AZHAR BIN SHARIFBY : AZHAR BIN SHARIF
SUPERVISOR : DR. ABD RAHIM B. ABU SUPERVISOR : DR. ABD RAHIM B. ABU BAKARBAKAR
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OBJECTIVEOBJECTIVE
1.1. Determine instability of a drum brake Determine instability of a drum brake componentcomponent
2.2. Perform Complex Eigenvalue AnalysisPerform Complex Eigenvalue Analysis
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SCOPESCOPE1.1. Use an existing FE model of a drum Use an existing FE model of a drum
brake.brake.2.2. Carry out modal testing of a real drum Carry out modal testing of a real drum
brake equipments. (Proton Wira model)brake equipments. (Proton Wira model)3.3. Obtain degree of correlation between Obtain degree of correlation between
predicted and measured result.predicted and measured result.
4.4. Perform Complex Eigenvalue Analysis.Perform Complex Eigenvalue Analysis.5.5. Study the effect of various parameter on Study the effect of various parameter on
squeal propensity.squeal propensity.
PSM 1
PSM 2
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INTRODUCTIONINTRODUCTION
Generally, noise have 2 category :Generally, noise have 2 category :--Low frequency, 100Low frequency, 100--1000 Hz1000 HzHigh frequency, ≥ 1000 Hz (Group of High frequency, ≥ 1000 Hz (Group of Squeal Squeal noisenoise))
Types of Squeal noise:Types of Squeal noise:--Low Low squealsqueal frequency, 1000frequency, 1000--5000 Hz5000 HzHigh High squealsqueal frequency, > 5000 Hzfrequency, > 5000 Hz
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INTRODUCTIONINTRODUCTION
Squeal exist during every braking action. This is Squeal exist during every braking action. This is called brake squeal.called brake squeal.Actually, brake squeal is disturbing human ear Actually, brake squeal is disturbing human ear and can cause noise pollutionand can cause noise pollutionBrake squeal can easy to defined as a vibration Brake squeal can easy to defined as a vibration within the range 1within the range 1--5 kHz.5 kHz.
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INTRODUCTIONINTRODUCTIONThere have several perhaps in brake system can There have several perhaps in brake system can produce squeal :produce squeal :--
Change of friction characteristic interfaceChange of friction characteristic interfaceInstability of vibration modeInstability of vibration modeActuation force at drum componentActuation force at drum component
There have several significant characteristics to There have several significant characteristics to affect squeal happens in drum brake system :affect squeal happens in drum brake system :--
Frequency of vibration each brake componentFrequency of vibration each brake componentFriction between surface of drum and liningFriction between surface of drum and liningRange of frequency ≥1000 HzRange of frequency ≥1000 Hz
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METHODOLOGYMETHODOLOGYStart
Basic theory ondrum brake
Literature review
Experimental of real drum brake equipment
Result Correlation
FEM result
Complete 1st Objective
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FE model of Design study
Comparison Result
Complete 2nd objective
USE ABAQUS SOFTWAREComplex Eigenvalue solver
Complex Eigenvalue Analysis
Squeal Propensity at different parameter
PSM I
METHODOLOGYMETHODOLOGYUNIVERSITI TEKNOLOGI
MALAYSIAUNIVERSITI TEKNOLOGI UNIVERSITI TEKNOLOGI
MALAYSIAMALAYSIA
FE model of Design study
Comparison Result
Complete 2nd objective
USE ABAQUS SOFTWAREComplex Eigenvalue solver
Complex Eigenvalue Analysis
Squeal Propensity at different parameter
PSM II
COMPLEX EIGENVALUE ANALYSISCOMPLEX EIGENVALUE ANALYSIS
The existing nonThe existing non--linear structure must be linearised linear structure must be linearised to enable extraction of the complex eigenvalues and to enable extraction of the complex eigenvalues and mode shape.mode shape.
Predicts the instability of any unstable mode, Predicts the instability of any unstable mode, frequency and mode shape adopted by couple frequency and mode shape adopted by couple system.system.
Carried out using ABAQUS which the instability Carried out using ABAQUS which the instability measurement, natural frequency and mode shape measurement, natural frequency and mode shape may be extracted.may be extracted.
The squeal propensity can be evaluated from the The squeal propensity can be evaluated from the magnitude of the instability measurement.magnitude of the instability measurement.
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COMPLEX EIGENVALUE ANALYSISCOMPLEX EIGENVALUE ANALYSIS(Cont)(Cont)
Use the equation of motion :Use the equation of motion :--
Where : [M] = Mass Matrix[C] = Damping Matrix[K] = Stiffness Matrix{Pi} = Normal Force
[ ] [ ] [ ]{ } { }iiii PUKUCUM =+⎭⎬⎫
⎩⎨⎧+
⎭⎬⎫
⎩⎨⎧ ∗∗∗
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COMPLEX EIGENVALUE ANALYSISCOMPLEX EIGENVALUE ANALYSIS(Cont)(Cont)
From this equation can determine the From this equation can determine the eigenvalue, eigenvalue, λλ ::--
λλ = = α α ±± jjωωWhere :Where :-- αα == the real partthe real part
ωω == frequencyfrequencyThis eigenvalue can be extracted the complex This eigenvalue can be extracted the complex mode.mode.
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COMPLEX EIGENVALUE ANALYSISCOMPLEX EIGENVALUE ANALYSIS(Cont)(Cont) Solid modeling
Calculation of unsymmetrical friction stiffness matrix
Friction stabilization
Complex eigenvalue extraction
Adopted from Hi-Kang paper
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COMPLEX EIGENVALUE ANALYSISCOMPLEX EIGENVALUE ANALYSIS(Cont)(Cont)
6 rad/sRotational Speed (ω)
0.35Coefficient friction (µ)
2.5 MPaPressure (P)
VALUEOPERATION DATA
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Assembly FE Model in ABAQUSAssembly FE Model in ABAQUS
Leading Shoe
Drum
Trailing Shoe
RESULTRESULT1. 1. CONTACT PRESSURE
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107
96.3
85.6
74.9
64.2
53.5
42.8
32.1
21.4
10.70
15
30
050000100000150000200000250000300000350000400000450000500000550000600000650000700000
Con
tact
Pre
ssur
e (P
a)
Angular Position (o)
Axial Position
(mm)
CONTACT PRESSURE DISTRIBUTION OF LEADING LINING SURFACE UNDER FRICTIONAL CONDITION (µ=0.35)
650000-700000600000-650000550000-600000500000-550000450000-500000400000-450000350000-400000300000-350000250000-300000200000-250000150000-200000100000-15000050000-1000000-50000
Toe
Heel
RESULTRESULT1. 1. CONTACT PRESSURE (Cont.)
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107
96.8
86.6
76.4
66.2
56
45.8
35.6
25.4
15.25010
20
30
40
050000100000150000200000250000300000350000400000450000500000550000600000650000700000
Cont
act P
ress
ure
(Pa)
Angular Position (o)
Axial Position (mm)
CONTACT PRESSURE DISTRIBUTION OF TRAILING LINING SURFACE UNDER FRICTIONAL CONDITION (µ = 0.35)
650000-700000600000-650000550000-600000500000-550000450000-500000400000-450000350000-400000300000-350000250000-300000200000-250000150000-200000100000-15000050000-1000000-50000
Toe
Heel
RESULTRESULT2. MODE SHAPE2. MODE SHAPE
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185.886th Nodal Diametral for drum3rd torsion trailing shoe7417.23
198.172nd torsion trailing shoe4677.52
131.873rd Nodal Diametral for drum1st bending for leading shoe1st torsion trailing shoe
2127.91
Instability Measurement (s-1)Mode ShapeFrequency
(Hz)Mode No.
RESULTRESULT3. DISTRIBUTION OF INSTABILITY MEASUREMENT3. DISTRIBUTION OF INSTABILITY MEASUREMENT
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SQUEAL PROPENSITY VS FREQUENCY FOR DRUM BRAKE
0
1000
2000
3000
4000
5000
6000
7000
8000
9000
-500 -400 -300 -200 -100 0 100 200 300 400 500
Squeal Propensity (s-1)
Freq
uenc
y (H
z)
Instability Measurement
PARAMETRIC STUDYPARAMETRIC STUDY
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To investigate squeal behavior of instability measurementTo investigate squeal behavior of instability measurementTo predict squeal propensity with difference parametricTo predict squeal propensity with difference parametric2 condition consider about this study :2 condition consider about this study :--
Acceleration condition Acceleration condition
Constant speed conditionConstant speed condition
Both of this condition consider 3 difference parametric :Both of this condition consider 3 difference parametric :--Difference pressureDifference pressure
Difference coefficient frictionDifference coefficient friction
Difference rotational speedDifference rotational speed
RESULT FROM ACCELERATION CONDITIONRESULT FROM ACCELERATION CONDITION
1. DIFFERENCE PRESSURE1. DIFFERENCE PRESSURE
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EFFECT OF DIFFERENT PRESSURE (P) OF INSTABILITY MEASUREMENT FOR DRUM BRAKE
0
1000
2000
3000
4000
5000
6000
7000
8000
9000
10000
11000
12000
000 -5000 -4000 -3000 -2000 -1000 0 1000 2000 3000 4000 5000 6000Squeal Propensity (s-1)
Freq
uenc
y (H
z)
P = 2.5 MPaP = 3.5 MPaP = 4.5 MPaP = 5.5 MPa
The modal instability distribution increase when increase the contribution pressure
RESULT FROM ACCELERATION CONDITIONRESULT FROM ACCELERATION CONDITION
2. DIFFERENCE COEFFICIENT FRICTION2. DIFFERENCE COEFFICIENT FRICTION
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The modal instability distribution decrease when the friction become decrease
Distribution of mode become stable
EFFECT OF COEFFICIENT FRICTION (µ) OF INSTABILITY MEASUREMENT FOR DRUM BRAKE
0
1000
2000
3000
4000
5000
6000
7000
8000
9000
10000
11000
12000
13000
14000
-6000 -5000 -4000 -3000 -2000 -1000 0 1000 2000 3000 4000 5000 6000
Squeal Propensity (s-1)Fr
eque
ncy
(Hz)
u = 0.25u = 0.35u = 0.45u = 0.55
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The distribution of modal instability increase at the highest rotational speed
EFFECT OF DIFFERENT VELOCITY(ω ) OF INSTABILITY MEASUREMENT FOR DRUM BRAKE
0
1000
2000
3000
4000
5000
6000
7000
8000
9000
-1200 -1000 -800 -600 -400 -200 0 200 400 600 800 1000 1200
Squeal Propensity (s-1)Fr
eque
ncy
(Hz)
w = 4 rad/sw = 6 rad/sw = 10 rad/sw = 12 rad/s
RESULT FROM ACCELERATION CONDITIONRESULT FROM ACCELERATION CONDITION
3. DIFFERENCE ROTATIONAL SPEED3. DIFFERENCE ROTATIONAL SPEED
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The distribution of modal instability increase when increase the contribution pressure until P = 3.5 MPa
Mode become stable when pressure continuous increase
RESULT FROM CONSTANT SPEED CONDITIONRESULT FROM CONSTANT SPEED CONDITION
4. DIFFERENCE PRESSURE4. DIFFERENCE PRESSURE
EFFECT OF DIFFERENT PRESSURE (P) OF INSTABILITY MEASUREMENT FOR DRUM BRAKE
0
1000
2000
3000
4000
5000
6000
7000
8000
9000
10000
11000
12000
13000
-15000 -12500 -10000 -7500 -5000 -2500 0 2500 5000 7500 10000 12500 15000
Squeal Propensity (s-1)F
req
ue
nc
y (
Hz)
P = 2.5 MPaP = 3.5 MPaP = 4.5 MPaP = 5.5 MPa
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The maximum modal instability is at µ = 0.35
RESULT FROM CONSTANT SPEED CONDITIONRESULT FROM CONSTANT SPEED CONDITION
5. DIFFERENCE COEFFICIENT FRICTION5. DIFFERENCE COEFFICIENT FRICTION
EFFECT OF DIFFERENT COEFFICIENT FRICTION (µ) OF INSTABILITY MEASUREMENT FOR DRUM BRAKE
0
1000
2000
3000
4000
5000
6000
7000
8000
9000
10000
11000
12000
13000
-15000 -10000 -5000 0 5000 10000 15000
Squeal Propensity (s-1)F
req
uen
cy (H
z)
u = 0.30
u = 0.35
u = 0.40
u = 0.55
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RESULT FROM CONSTANT SPEED CONDITIONRESULT FROM CONSTANT SPEED CONDITION
6. DIFFERENCE ROTATIONAL SPEED6. DIFFERENCE ROTATIONAL SPEED
EFFECT OF DIFFERENT SPEED (ω ) OF INSTABILITY MEASUREMENT FOR DRUM BRAKE
0
1000
2000
3000
4000
5000
6000
7000
8000
9000
10000
11000
12000
13000
-20000 -15000 -10000 -5000 0 5000 10000 15000 20000Squeal Propensity (s-1)
Fre
qu
ency
(Hz)
w = 4 rad/s
w = 6 rad/s
w = 8 rad/s
w = 10 rad/s
The modal instability increasing when a rotational speed increase
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COMPARISON BETWEEN BOTH CONDITIONCOMPARISON BETWEEN BOTH CONDITION
7. PRESSURE7. PRESSURE
COMPARISON MODAL INSTABILITY DISTRIBUTION BETWEEN BOTH CONDITION AT PRESSURE, P = 3.5 MPa
0
10002000
30004000
5000
60007000
8000
900010000
1100012000
13000
-6000 -5000 -4000 -3000 -2000 -1000 0 1000 2000 3000 4000 5000 6000
Squeal Propensity (s-1)
Freq
uenc
y (H
z)
Constant SpeedAcceleration
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COMPARISON BETWEEN BOTH CONDITIONCOMPARISON BETWEEN BOTH CONDITION
8. COEFFICIENT FRICTION8. COEFFICIENT FRICTION
COMPARISON MODAL INSTABILITY DISTRIBUTION BETWEEN BOTH CONDITION AT COEFFICIENT FRICTION, µ = 0.35
0
1000
2000
3000
4000
5000
6000
7000
8000
9000
10000
11000
12000
13000
14000
-14000 -12000 -10000 -8000 -6000 -4000 -2000 0 2000 4000 6000 8000 10000 12000 14000
Squeal Propensity (s-1)
Freq
uenc
y (H
z)
Constant SpeedAcceleration
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COMPARISON BETWEEN BOTH CONDITIONCOMPARISON BETWEEN BOTH CONDITION
9. ROTATIONAL SPEED9. ROTATIONAL SPEED
COMPARISON MODAL INSTABILITY DISTRIBUTION BETWEEN BOTH CONDITION AT ROTATIONAL SPEED, ω = 4 rad/s
0
1000
2000
3000
4000
5000
6000
7000
8000
9000
10000
11000
12000
13000
14000
-8000 -6000 -4000 -2000 0 2000 4000 6000 8000Squeal Propensity (s-1)
Freq
uenc
y (H
z)
Constant SpeedAcceleration
CONCLUSIONCONCLUSION
The result shown that the acceleration condition The result shown that the acceleration condition is more stable mode than constant speed is more stable mode than constant speed condition.condition.The constant speed condition can produce the The constant speed condition can produce the highest modal instability and predict the highest highest modal instability and predict the highest squeal propensity.squeal propensity.
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THE ENDTHE END
THANK YOU
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PROBLEM STATEMENTPROBLEM STATEMENT
Brake system produced noise when the brake is Brake system produced noise when the brake is appliedappliedBrake noise is disturbing a vehicle passengers Brake noise is disturbing a vehicle passengers and the environment. and the environment. Brake noise appearing high on the list of items Brake noise appearing high on the list of items that reduce customer’s satisfaction with their that reduce customer’s satisfaction with their vehicle.vehicle.
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8762 Kg/m3Density of rib
250 GPaModulus Young of rib
2638 Kg/m3Density of lining
3.1 GPaModulus Young of lining
4 mmLining thickness
40 mmLining width
107oLining arc angle
LEADING SHOE & TRAILING SHOE
104 GPaDensity
7673 Kg/m3Modulus YoungDRUM
VALUEPARAMETRICCOMPONENT
COMPLEX EIGENVALUE ANALYSISCOMPLEX EIGENVALUE ANALYSIS
3D MODEL OF DRUM BRAKE3D MODEL OF DRUM BRAKE
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Drum Brake Assembly
3D MODEL OF DRUM BRAKE (Cont.)3D MODEL OF DRUM BRAKE (Cont.)
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Drum component
Trailing ShoeLeading Shoe
Lining
Rib
MODE SHAPE FOR DRUM BRAKEMODE SHAPE FOR DRUM BRAKE
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3rd Nodal Diametral at frequency 2127.9 Hz
6th Nodal Diametral at frequency 7417.2 Hz
MODE SHAPE FOR LEADING SHOEMODE SHAPE FOR LEADING SHOE
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1st bending at frequency 2127.9 Hz
MODE SHAPE FOR TRAILING SHOEMODE SHAPE FOR TRAILING SHOE
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1st torsion at frequency 2127.9 Hz
2nd torsion at frequency 4677.5 Hz
MODE SHAPE FOR TRAILING SHOEMODE SHAPE FOR TRAILING SHOE
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4th torsion at frequency 7417.2 Hz
PSM II PLANNINGPSM II PLANNING
Prepare for PSM 2 presentation and draft submitting5.
Give conclusion and recommendation 4.
Prepare discussion on result obtained3.
FE model of design study2.
Complex Eigenvalue Solver (ABAQUS)1.
16151413121110987654321TaskNo.
weeks
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