psm ii seminar - universiti teknologi malaysiaarahim/presentation psm ii_azhar.pdf ·...

PSM II SEMINARPSM II SEMINAR

DEPARTMENT OF AUTOMOTIVE DEPARTMENT OF AUTOMOTIVE AND AERONAUTICAND AERONAUTIC

UNIVERSITI TEKNOLOGI MALAYSIA

UNIVERSITI TEKNOLOGI UNIVERSITI TEKNOLOGI MALAYSIAMALAYSIA

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



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



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



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



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.



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



METHODOLOGYMETHODOLOGYStart

Basic theory ondrum brake

Literature review

Experimental of real drum brake equipment

Result Correlation

FEM result

Complete 1st Objective



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.





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 =+⎭⎬⎫

⎩⎨⎧+

⎭⎬⎫

⎩⎨⎧ ∗∗∗




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.



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




6 rad/sRotational Speed (ω)

0.35Coefficient friction (µ)

2.5 MPaPressure (P)

VALUEOPERATION DATA



Assembly FE Model in ABAQUSAssembly FE Model in ABAQUS

Leading Shoe

Drum

Trailing Shoe

RESULTRESULT1. 1. CONTACT PRESSURE



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.)



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



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



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



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



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


2. DIFFERENCE COEFFICIENT FRICTION2. DIFFERENCE COEFFICIENT FRICTION



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



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


3. DIFFERENCE ROTATIONAL SPEED3. DIFFERENCE ROTATIONAL SPEED



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



The maximum modal instability is at µ = 0.35


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




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



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


Freq

uenc

y (H

z)

Constant SpeedAcceleration




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


Freq

uenc

y (H

z)





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)


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.



THE ENDTHE END

THANK YOU



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.





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



Drum Brake Assembly

3D MODEL OF DRUM BRAKE (Cont.)3D MODEL OF DRUM BRAKE (Cont.)



Drum component

Trailing ShoeLeading Shoe

Lining

Rib

MODE SHAPE FOR DRUM BRAKEMODE SHAPE FOR DRUM BRAKE



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



1st bending at frequency 2127.9 Hz

MODE SHAPE FOR TRAILING SHOEMODE SHAPE FOR TRAILING SHOE



1st torsion at frequency 2127.9 Hz

2nd torsion at frequency 4677.5 Hz

MODE SHAPE FOR TRAILING SHOEMODE SHAPE FOR TRAILING SHOE



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



psm ii seminar - universiti teknologi malaysiaarahim/presentation psm ii_azhar.pdf ·...

Documents