INFLUENCES OF BRAKE SHOE THICKNESS AGAINTS DISC BRAKE VIBRATION SYSTEM ON Influences Of Brake Pad Thickness Againts Disc Brake System Vibration On Various Braking Condition.
INFLUENCES OF BRAKE SHOE THICKNESS
AGAINTS DISC BRAKE VIBRATION SYSTEM ON
VARIOUS BRAKING CONDITION
PUBLICATION ARTICLE
Submitted as a Partial Fulfillment of the Requirements for GettingBachelor
Degree of Engineering in Automotive Department
Arranged by :
Dwi Aji Saputra
NIM : D 200 102 012
MECHANICAL ENGINEERING PROGRAM STUDY
ENGINEERING FACULTY
MUHAMMADIYAH UNIVERSITY OF SURAKARTA
NOVEMBER 2014
INFLUENCES OF BRAKE SHOE THICKNESS AGAINTS DISC BRAKE VIBRATION
SYSTEM ON VARIOUS BRAKING CONDITION
Dwi Aji Saputra
Automotive Department of Muhammadiyah University of Surakarta
Jln. A. Yani Pabelan-Kartasura. Tromol Pos I Telp. (0271) 715448 Kartasura
Email: [email protected]
ABSTRACT
Abstract :
The aim of this study is to determine the condition of the brake vibration and analyze the
parameters that affect the vibration response occurring. Test was carried out by varying the
thickness of the brake lining. Data taken for thickness of the brake lining (7,5 and 3)mm, with
a variation of the braking pressure 0.6bar and 1bar, shaftrotation (425,
637, 850, and
1061)rpm, the axial and radial direction, vibration measurement used Lutron VB_8202
vibration meter.
Vibration on acceleration measurements show that vibration acceleration in the
radial direction which seems higher when compared to the axial direction, can be in the know
in the axial direction 425 RPM vibration acceleration value is not more than 8.2m / s while the
radial direction up to 11.6m/s .
Increasing the value of amplitude 2-4.7 m/s2 in dictateLessing of Brake pad
worn.The increase in vibration owing to the reduced value of brake lining.
Keywords :Brake, Brake lining thickness, Brake pressure, Damping.
discs (disc brake) with brake pads. These
Background
Brakes are an important component
friction
causes
vibration,
noise. Disc
stopping or slowing down. In general, the
factorstringer the vibration of brake pad and
vehicle uses hydraulic brake system. The
caliper.
caliper (cylinder
and
and
of motor vehicle. Brake function is to
Components of hydraulic brake are master
roughness
heat
friction
Vibration in the brake components
body).
during operation can cause noise. It comes
braking
from the friction between brake pads that
pressure from the pedal tocalipers (cylinder
have been worn by the disc brakes. One of
body) through
factors which cause the vibration when
cylinder
and
Cylinder
Master
distributes
the
brake
a
hose.
The
caliper (cylinder body) is usedto forward a
braking
hydraulic pressure to brake pad.
pad. The effects of excessive vibration will
operation
is
worn
thin
brake
using
cause inconvenience driving. In addition,
pressureprinciple to slow down the rotation
the vibration at brake pads has worn also
Brake
works
by
so that it reveals a friction between the
the performance or the operation of the
d. At the same braking pressure, the
frictional force is assumed to be the
braking was not optimal.
Brake pad is so extremely important
when braking. It needs special attention to
same
for
all
variations
in
the
thickness of the brake lining.
the condition of the brake pad. Therefore,
there should be a study to determine the
effect of thebrake pads thickness against
the brake disc vibration in the system.
The friction coefficient is assumed to be
the same on this test.
LITERATURE REVIEW
Oura (2009), conducted a research on
PROBLEM LIMITATION
From above explanation, it can be
taken a problem formulations, namely: how
to influence the thickness of the brake pads
the mechanism of the appearance of disc
brake squeal vibration.
Carried out research on testing squeal
on a range of braking conditions on the
vibration
vibration of the disc brake system.
thicknesses. The experiment was done with
using
Pads
with
different
testing equipment squeal by using brake
OBJECTIVE
pieces with size 20x20 mm with a thickness
The
purpose
of
this
study
is
determining the effect of the brake lining
thickness at various braking conditions on
the vibration disc brake system in the form
of changes in the value of the vibration
amplitude.
variation of the brake lining as testing
material.The experiment was conducted
with dynamic stiffness test apparatus which
was providing a constant pressure. The test
results showed the dynamic stiffness of
Pads became stiff when braking pressure
was increasing, and the stiffness increased
FORMULATION
with the thin Pads. Results of the testing
To determine the direction of research,
given the extent of the problem as follows:
a. All components of the braking device
is
assumed
to
be
at
calipers, discs and brake hoses).
conditions
are
considered
constant.
c. Data Display is only in the form of
vibration amplitude value.
when the stiffness of Pads became hard.
BASIC THEORY
normal
conditions (80% for the master,
b. Load
showed the frequency squeal was high
A. Brake Work System
In general, the brake discs are currently
working
to
apply
the
principles
of
hydraulics. The hydraulic system consists
of a master cylinder, brake calipers, brake
oil reservoir to place and other supporting
components. When we press
the handle
on brake master so piston inside brake
Brake is also a major component of the
master push fluid brake to fluid path, and
brake as it serves as a grappling discs so
then entering to piston chamber brake
that the rate of the vehicle can be reduced
caliper. At Outer Piston, brake pad is
and eventually stopped completely, usually
installed, this brake pad clamps disc brake
made of composite materials or pasta.
by using piston pressure to outer direction
Brake commonly used in today's modern
which is caused by the pressure of brake
vehicles is appropriate types of brakes,
fluid so that the friction effect among dsisc
whether wearing drum brake or disc brake.
and brake pad are generated braking
To canvass brake used in generally disc
process. Frictional forces that occur in the
brake pad or brake disc called a pad, while
disc braking system can be explained in the
used on drum brakes are often called brake
following figure:
shoe.
Figure 2. Brake Pad
Figure 1. How Disc Brakes Work
(Anonim, 2012)
b. Disc
In general, disc brake or disc made of
cast iron and holes for ventilation and
B. Disc Brake Components
In general, disc brake components
cooling function. Given the age of the brake
ventilation and longer lasting.
are as follows:
a. Brake Pad
Brake consists of a mixture of fiber and
little metallic iron powder. Generally brake
pad is given lining brake to show the thicks
of brake pad.Thus, the worn of the brake
can be checked easierwhen unloading
Figure 4. Disc
brake components. In some brake pads,
the use of metallic plate attached to the
side of the brake piston whose function is to
prevent noise when braking.
c. Caliper
Caliper is also called a cylinder body,
which
functions
holds-piston
and
the
channel where the brake fluid channeled to
the brake master cylinder of the caliper.
Vibration
Vibration is a back and forth motion
The components contained in the circuit
within
calipers as follows:
a
certain
Vibration
1. Piston
associated with the oscillatory motion of
2. Piston Ring
objects and force associated with these
3. Rubber Protector
objects. All objects that have mass and
4. Torque plate
elasticity is able to vibrate, so most
machines
The cause of the vibration on the brake
disc (brake pad)
and
Disk disc is not smooth
Disc Thickness
Unbalance disc
Worn disc Brake and Brake pad
Dust and dirt.
structural
and
consideration
of
design
the
friction between Brake pad and disc.
The magnitude of
vibration where the system generates a
that
of
the
we can see the
equation:
2
operation is vibration excited or self-excited
excitation
nature
2
Vibration happens on the brake during
of
requires
oscillation.
Brake force this optained from the
number
engineering
(engineering) experience some degree of
vibration
1.
2.
3.
4.
5.
interval.
Displacement deviation
can write
as:
produces
oscillatory motion in the system itself.
Harmonic motion velocity and acceleration
Numbers fnis one of the most important in
can
the amount of vibration analysis and is
equation
called the natural frequency. With the
derivatives, then ;
be
obtained
by
by
using
differentiation
dot
notation
equation to find the natural frequency of the
brake lining is:
/
With a record of angular frequency ω, with
units of radians per second, often used in
equations
because
it
simplifies
the
a. Free Vibration without damping
equations, but the amount is usually
converted into a frequency "standard"
(units of Hz) when stating the frequency of
the system.
Where :
0
of
for
deflection. The more rigid a structure
greater rigidity values.
k
b. Friction force
m
Friction is the force that is generated
x(t)
by two objects rub against each other and
the direction opposite to the motion of
F
objects. Here is the friction on the beam.
Figure 2.7. Vibration without dampers
With the equation to calculate the friction
force is:
b. Free Vibration with Dampig
Fg = .N
Where :
/
k
c
x(t)Figure 2.11 Friction on the beam
m
c. Damping
F
Damping is the absorption of incident
energy (energy dissipation) by a structure
Figure 2.8 Vibration with damping
Factors affecting the value of the
vibration on the brake
essential.
of
the
Restrictions
structure
are
is
an
useful
for
maintaining the rigidity of construction so
as not sagged more than the required
deflection. Stiffness is defined as the force
required
to
causes include the release of energy by
movement between molecules within the
a. Stiffness
Stiffness
due to various reasons. Some of the
obtain
one
unit
of
displacement. Stiffness value is the slope
angle of the relationship between load and
material, the release of energy by friction
linking devices and systems support, the
release of energy by friction in the air. The
energy release is also the result of plastic
joints. Since the damping function of
energy release then this will reduce the
structural response.
Therefore greatly affect the vibration
damping. Where the damping is strongly
influenced by the critical damping value
........................
(critical damping), the point at which the
RESEARCH METHODOLOGY
system no longer oscillates. The amount of
Flow chart diagram
attenuation is usually expressed in damping
START
ratio. The coefficient of damping required to
Making tool vibrations test
reach the point of critical damping is:
disc thickness brake Pad
2
2√
2
MAKING OF DATA
If the value of the damping coefficient to
Thickness Variation (A = 7, B = 5, C = 3) mm
reach the point of critical damping, then the
Braking Pressure Variation (0,6, and 1) Bar
system will be difficult muffled. So it is
Variations Rpm (425, 637, 850 and 1061)
difficult
to
stop
oscillating
system,
Acceleration value of
consequently a large vibration.
data vibrations
·
·
∆
Analysis
·∆
Conclusion
·
END
k
F
F
Material and Tools
Tools wich used in this research are as
∆
F
F
c
Page 2.12 Deflection axial
Where :
∆
/
follows :
a. Brake pad vibration test equipment
(with electric motor 3 phase 5,5 HP)
b. 3 couple Brake pad with different
thickness (7mm, 5mm, 3mm).
c. Piezoelectric Accelerometer.
d. Vibration meter markLutronVB_8202
e. Tachometer.
f. Inverter.
g. Pulley dan bel
Data processing
p
s
step
Th
he first ste
ep of data
a processin
ng
begins with recorrd measurem
ment data in
on accelera
ation data into
the forrm of vibratio
a displlay table in the excel program. We
W
show the excel pro
ogram into a graph whicch
onnect betw
ween the brake linin
ng
we co
Figure 6. Vibration meter
thickne
ess variatio
on with rottation of th
he
motor and also brraking press
sure variatio
on
e rotation off the motor. Measurement
with the
of the natural
n
frequ
uency of the
e system eacch
brake lining thickkness variattion with th
he
ach
approa
we
c
calculate
the
t
continu
uous cantilevver beam rods.
A
er
Figure 7. Acceleromete
Figure8. Brake Pad
Affter the test is complete assembled
test, then performed the data collection,
which can be seen in
n the followin
ng
sccheme:
Figure 9.Test da
ata making schema
s
stiffnesss
Data And Analysis
Then, the data above are analized to
16
425
Thickness
7mm
8.2
Thickness
5mm
9.5
Thickness
3mm
10.2
637
10.8
12
12.8
850
12.8
13.7
15.3
1061
13
14.2
15.6
14
12
13.1
Vibration Velocity (m/s²)
16.2
15.4
15.2
14.8
13.2
11.1
Rotation
(RPM)
16.1
18
measurment shown at following figure :
RMS VALUE (m/s2)
pressure and shaft rotation speed. Data
17.1
Vibration Graphs on axial
direction for pressure 1 bar
knowing the vibration at different brake
11.2
10.7
10
8
Pad 7
8.9
Pad 5
6
Pad 3
4
2
0
Vibration Graphs on axial
direction for pressure 0.6 bar
425 637 850 1061 RPM
18
8
15.6
14.2
13
15.3
13.7
12.8
12
10.2
rotations of the vibration amplitude in the
axial direction, the braking pressure of 1bar
10.8
10
9.5
12
12.8
14
Figure 11. Relationship between the axis
Pad 7
Pad 5
8.2
RMS VALUE (m/s2)
16
Rotation
(RPM)
4
425
Thickness
7mm
7
2
637
9
11.2
12.7
0
850
11.8
12.9
14.5
1061
13.5
14.6
16.1
6
Pad 3
425 637 850 1061
Thickness
5mm
9.5
Thickness
3mm
11.6
RPM
Vibration Graphs on Radial
direction for pressure 0.6 bar
Figure 10. Relationship between the
the axial direction, the braking pressure of
0.6bar
Vibration Velocity (m/s²)
425
Thickness
7mm
8.9
Thickness
5mm
10.7
Thickness
3mm
11.1
637
11.2
13.2
13.1
850
14.8
15.4
16.1
1061
15.2
16.2
17.1
RMS VALUE (m/s2)
rotation axes of the vibration amplitude in
Rotation
(RPM)
Vibration Velocity (m/s²)
20
18
16
14
12
10
8
6
4
2
0
18.1
16.5
14.7
13.6
13.2
14.9
16.6
15.5
13.8
11.5
Pad 7
11
Pad 5
9
Pad 3
425 637 850 1061
RPM
Figure 12. The relationship between the
the processing vibration indication that the
rotation axis of the vibration amplitude in
brake pads are still good or still thick
the radial direction at a pressure of 0.6bar
Rotation
(RPM)
produces low vibration acceleration value.
From vibration value measurment, we
Vibration velocity (m/s²)
Thickness
Thickness
Thickness
can find the value of brake pad natural
7mm
5mm
3mm
frequency and critical damping coeficient
425
9.6
12.5
14.3
which will get result as table below:
637
12.2
15.7
16
850
16.5
17.2
17.5
Table 1. Values of natural frequencies and
1061
17.3
18.3
19.2
critical damping coefficient value of each
brake pad.
Vibration Graphs on Radial
direction for pressure 1 bar
Thick Brake
Pad (mm)
RMS VALUE (m/s2)
25
20
(Ns/m)
7
493,63
184,61
5
1111,94
373,27
3
4447,92
1352,16
19.2
17.5
16
15
(Hz)
14.3
12.5
17.2
18.3
17.3
16.5
15.7
Pad 7
12.2
Pad 5
10
9.6
Based on the results of these calculations
with a critical damping coefficient is greater,
Pad 3
and the system will easily vibrate because
5
of small damping ratio.
0
425
637
850
On
1061 RPM
the
axial
direction
of
the
measurement pressure of 1 bar (Figure 4.2)
Figure 13. Relationship between the axis
and the measurement of radial pressure of
rotations of the vibration amplitude in the
1 bar (Figure 4.4) it can be seen that the
radial direction at a pressure of 1bar
thickness of the lining 5mm shaft speed
637 rpm surge approaching the vibration
Discussion
amplitude values even exceed the value of
The results of processing the vibration
the amplitude of vibration in the lining
an
thickness of 3mm.On the measurement of
increase in the value of the acceleration of
vibration velocity shows that the vibration of
vibration generated each variation of the
velocity
thickness of the brake lining. This increase
appears larger when compared to the axial
is indicated by the value of the acceleration
direction, as shown in the graph measuring
of vibration that occurs in brake that has
the axial direction for the braking pressure
experienced wear and worn. The results of
0.6 bar (Figure 10) and radial graphs for
acceleration
values
indicate
that
in
the
radial
direction
which
braking pressure 0.6 bar (Figure 12) it can
Untuk selanjutnya dapat di lakukan
be seen the difference value of the
penelitian untuk mendeteksi tingkat
resonance. 425 rpm for shaft rotation in the
keasuan
direction of axial value does not exceed 8.2
dengan bahan atau merk yang
m/s2, while in the radial direction vibration
reaches the value of 11.6 m/s2. This occurs
due to the effect of centrifugal force on the
rotation axis to the radial direction, so that
the force that occurs on the radial direction
is greater than the axial direction.
Conclusion
From data analysing and discusion can be
of tained conclusion as follow :
1. Increasing the value of aplitude2-4,7
m/s2in dicate lessing of Brake pad
worn.The increasing of aplitude value is
cause by the lessing of pad mass, that
affect the decreasing of damping value
to vibration, then Increasing of braking
pressure and shaft rotation will increase
exitation force that cause the value of
amplitude greater.
Sugesstion
1. Next, we can do research to detect the
level of brake pad worn using other
brand.
2. Before take the data, it is better to know
the brake resonansi frequency.
Sugegestion
kampas
rem
cakram
berbeda.
Sebelum
henaknya
pengambilan
mengetahui
resonansi sistem.
data
frekuensi
References
Aji, K., 2007, Deteksi Kerusakan Bantalan Gelinding Pada Pompa Sentrifugal Dengan
Analisa Sinyal Getaran. Jurusan Teknik Mesin, Fakultas Teknik Universitas
Sebelas Maret, Surakarta.
Anonim., 2012, Automotif Diagnostic & Repair Help for Cars and Trucks.
Hidayat, L.L.R. G., 2009,Perawatan prediktif Penerapan Getaran Mekanis.LPP UNS dan
UNS Press,Surakarta.
http: //yefrican.files.wordpress.com, 20thFebruary 2014
http://www.sensotec.com/accelerometer_fag.asp?category=A11#,20thFebruary 2014
http: // id.wikipedia.org/wiki/Rem, 20thFebruary 2014
Jaya, S.M., 2009, Analisis Getaran dan Suara Pada Rem Cakram Saat Beroperasi.Jurusan
Teknik Mesin, Fakultas Teknik Universitas Andalas.Sugiharto,A., 2007,Cara Kerja
dan Perbaikan Rem Disc Brake,Lembaga Penelitian-UNES,Semarang.Oura, Y.,
Kurita, Y., and Matsumura, Y., 2009,Influence of dynamic stiffness in contact
region on disk brake squeal.Department of Mechanical Engineering, The
University of Shiga Prefecture, 2500 Hassaka-cho, Hicone-shi, Shiga, 522-8533,
Japan.
Oura, Y., Kurita, Y., and Matsumura, Y., 2009,Influence of dynamic stiffness in contact
region on disk brake squeal.Department of Mechanical Engineering, The
University of Shiga Prefecture, 2500 Hassaka-cho, Hicone-shi, Shiga, 522-8533,
Japan.
Oura, Y., Kurita, Y., Nishizawa, Y., and Kosaka, K., 2010,Influence of brake pad thickness
on disk brake squeal.Department of Mechanical Engineering, The University of
Shiga Prefecture, 2500 Hassaka-cho, Hicone-shi, Shiga, 522-8533, Japan.
Rao, S., Singeresu, Mechanical Vibration.
Sawczuk,W.,2011,Application of
Vibroacoustic Signal to Diagnose Disck Braking
System,Journal of KONES Powertrain and Transport, vol. 18,No. 1 2011.
Wiliam T., 1986, Teori Getaran Dengan Penerapan Edisi Kedua, Penerbit Erlangga,
Jakarta.
AGAINTS DISC BRAKE VIBRATION SYSTEM ON
VARIOUS BRAKING CONDITION
PUBLICATION ARTICLE
Submitted as a Partial Fulfillment of the Requirements for GettingBachelor
Degree of Engineering in Automotive Department
Arranged by :
Dwi Aji Saputra
NIM : D 200 102 012
MECHANICAL ENGINEERING PROGRAM STUDY
ENGINEERING FACULTY
MUHAMMADIYAH UNIVERSITY OF SURAKARTA
NOVEMBER 2014
INFLUENCES OF BRAKE SHOE THICKNESS AGAINTS DISC BRAKE VIBRATION
SYSTEM ON VARIOUS BRAKING CONDITION
Dwi Aji Saputra
Automotive Department of Muhammadiyah University of Surakarta
Jln. A. Yani Pabelan-Kartasura. Tromol Pos I Telp. (0271) 715448 Kartasura
Email: [email protected]
ABSTRACT
Abstract :
The aim of this study is to determine the condition of the brake vibration and analyze the
parameters that affect the vibration response occurring. Test was carried out by varying the
thickness of the brake lining. Data taken for thickness of the brake lining (7,5 and 3)mm, with
a variation of the braking pressure 0.6bar and 1bar, shaftrotation (425,
637, 850, and
1061)rpm, the axial and radial direction, vibration measurement used Lutron VB_8202
vibration meter.
Vibration on acceleration measurements show that vibration acceleration in the
radial direction which seems higher when compared to the axial direction, can be in the know
in the axial direction 425 RPM vibration acceleration value is not more than 8.2m / s while the
radial direction up to 11.6m/s .
Increasing the value of amplitude 2-4.7 m/s2 in dictateLessing of Brake pad
worn.The increase in vibration owing to the reduced value of brake lining.
Keywords :Brake, Brake lining thickness, Brake pressure, Damping.
discs (disc brake) with brake pads. These
Background
Brakes are an important component
friction
causes
vibration,
noise. Disc
stopping or slowing down. In general, the
factorstringer the vibration of brake pad and
vehicle uses hydraulic brake system. The
caliper.
caliper (cylinder
and
and
of motor vehicle. Brake function is to
Components of hydraulic brake are master
roughness
heat
friction
Vibration in the brake components
body).
during operation can cause noise. It comes
braking
from the friction between brake pads that
pressure from the pedal tocalipers (cylinder
have been worn by the disc brakes. One of
body) through
factors which cause the vibration when
cylinder
and
Cylinder
Master
distributes
the
brake
a
hose.
The
caliper (cylinder body) is usedto forward a
braking
hydraulic pressure to brake pad.
pad. The effects of excessive vibration will
operation
is
worn
thin
brake
using
cause inconvenience driving. In addition,
pressureprinciple to slow down the rotation
the vibration at brake pads has worn also
Brake
works
by
so that it reveals a friction between the
the performance or the operation of the
d. At the same braking pressure, the
frictional force is assumed to be the
braking was not optimal.
Brake pad is so extremely important
when braking. It needs special attention to
same
for
all
variations
in
the
thickness of the brake lining.
the condition of the brake pad. Therefore,
there should be a study to determine the
effect of thebrake pads thickness against
the brake disc vibration in the system.
The friction coefficient is assumed to be
the same on this test.
LITERATURE REVIEW
Oura (2009), conducted a research on
PROBLEM LIMITATION
From above explanation, it can be
taken a problem formulations, namely: how
to influence the thickness of the brake pads
the mechanism of the appearance of disc
brake squeal vibration.
Carried out research on testing squeal
on a range of braking conditions on the
vibration
vibration of the disc brake system.
thicknesses. The experiment was done with
using
Pads
with
different
testing equipment squeal by using brake
OBJECTIVE
pieces with size 20x20 mm with a thickness
The
purpose
of
this
study
is
determining the effect of the brake lining
thickness at various braking conditions on
the vibration disc brake system in the form
of changes in the value of the vibration
amplitude.
variation of the brake lining as testing
material.The experiment was conducted
with dynamic stiffness test apparatus which
was providing a constant pressure. The test
results showed the dynamic stiffness of
Pads became stiff when braking pressure
was increasing, and the stiffness increased
FORMULATION
with the thin Pads. Results of the testing
To determine the direction of research,
given the extent of the problem as follows:
a. All components of the braking device
is
assumed
to
be
at
calipers, discs and brake hoses).
conditions
are
considered
constant.
c. Data Display is only in the form of
vibration amplitude value.
when the stiffness of Pads became hard.
BASIC THEORY
normal
conditions (80% for the master,
b. Load
showed the frequency squeal was high
A. Brake Work System
In general, the brake discs are currently
working
to
apply
the
principles
of
hydraulics. The hydraulic system consists
of a master cylinder, brake calipers, brake
oil reservoir to place and other supporting
components. When we press
the handle
on brake master so piston inside brake
Brake is also a major component of the
master push fluid brake to fluid path, and
brake as it serves as a grappling discs so
then entering to piston chamber brake
that the rate of the vehicle can be reduced
caliper. At Outer Piston, brake pad is
and eventually stopped completely, usually
installed, this brake pad clamps disc brake
made of composite materials or pasta.
by using piston pressure to outer direction
Brake commonly used in today's modern
which is caused by the pressure of brake
vehicles is appropriate types of brakes,
fluid so that the friction effect among dsisc
whether wearing drum brake or disc brake.
and brake pad are generated braking
To canvass brake used in generally disc
process. Frictional forces that occur in the
brake pad or brake disc called a pad, while
disc braking system can be explained in the
used on drum brakes are often called brake
following figure:
shoe.
Figure 2. Brake Pad
Figure 1. How Disc Brakes Work
(Anonim, 2012)
b. Disc
In general, disc brake or disc made of
cast iron and holes for ventilation and
B. Disc Brake Components
In general, disc brake components
cooling function. Given the age of the brake
ventilation and longer lasting.
are as follows:
a. Brake Pad
Brake consists of a mixture of fiber and
little metallic iron powder. Generally brake
pad is given lining brake to show the thicks
of brake pad.Thus, the worn of the brake
can be checked easierwhen unloading
Figure 4. Disc
brake components. In some brake pads,
the use of metallic plate attached to the
side of the brake piston whose function is to
prevent noise when braking.
c. Caliper
Caliper is also called a cylinder body,
which
functions
holds-piston
and
the
channel where the brake fluid channeled to
the brake master cylinder of the caliper.
Vibration
Vibration is a back and forth motion
The components contained in the circuit
within
calipers as follows:
a
certain
Vibration
1. Piston
associated with the oscillatory motion of
2. Piston Ring
objects and force associated with these
3. Rubber Protector
objects. All objects that have mass and
4. Torque plate
elasticity is able to vibrate, so most
machines
The cause of the vibration on the brake
disc (brake pad)
and
Disk disc is not smooth
Disc Thickness
Unbalance disc
Worn disc Brake and Brake pad
Dust and dirt.
structural
and
consideration
of
design
the
friction between Brake pad and disc.
The magnitude of
vibration where the system generates a
that
of
the
we can see the
equation:
2
operation is vibration excited or self-excited
excitation
nature
2
Vibration happens on the brake during
of
requires
oscillation.
Brake force this optained from the
number
engineering
(engineering) experience some degree of
vibration
1.
2.
3.
4.
5.
interval.
Displacement deviation
can write
as:
produces
oscillatory motion in the system itself.
Harmonic motion velocity and acceleration
Numbers fnis one of the most important in
can
the amount of vibration analysis and is
equation
called the natural frequency. With the
derivatives, then ;
be
obtained
by
by
using
differentiation
dot
notation
equation to find the natural frequency of the
brake lining is:
/
With a record of angular frequency ω, with
units of radians per second, often used in
equations
because
it
simplifies
the
a. Free Vibration without damping
equations, but the amount is usually
converted into a frequency "standard"
(units of Hz) when stating the frequency of
the system.
Where :
0
of
for
deflection. The more rigid a structure
greater rigidity values.
k
b. Friction force
m
Friction is the force that is generated
x(t)
by two objects rub against each other and
the direction opposite to the motion of
F
objects. Here is the friction on the beam.
Figure 2.7. Vibration without dampers
With the equation to calculate the friction
force is:
b. Free Vibration with Dampig
Fg = .N
Where :
/
k
c
x(t)Figure 2.11 Friction on the beam
m
c. Damping
F
Damping is the absorption of incident
energy (energy dissipation) by a structure
Figure 2.8 Vibration with damping
Factors affecting the value of the
vibration on the brake
essential.
of
the
Restrictions
structure
are
is
an
useful
for
maintaining the rigidity of construction so
as not sagged more than the required
deflection. Stiffness is defined as the force
required
to
causes include the release of energy by
movement between molecules within the
a. Stiffness
Stiffness
due to various reasons. Some of the
obtain
one
unit
of
displacement. Stiffness value is the slope
angle of the relationship between load and
material, the release of energy by friction
linking devices and systems support, the
release of energy by friction in the air. The
energy release is also the result of plastic
joints. Since the damping function of
energy release then this will reduce the
structural response.
Therefore greatly affect the vibration
damping. Where the damping is strongly
influenced by the critical damping value
........................
(critical damping), the point at which the
RESEARCH METHODOLOGY
system no longer oscillates. The amount of
Flow chart diagram
attenuation is usually expressed in damping
START
ratio. The coefficient of damping required to
Making tool vibrations test
reach the point of critical damping is:
disc thickness brake Pad
2
2√
2
MAKING OF DATA
If the value of the damping coefficient to
Thickness Variation (A = 7, B = 5, C = 3) mm
reach the point of critical damping, then the
Braking Pressure Variation (0,6, and 1) Bar
system will be difficult muffled. So it is
Variations Rpm (425, 637, 850 and 1061)
difficult
to
stop
oscillating
system,
Acceleration value of
consequently a large vibration.
data vibrations
·
·
∆
Analysis
·∆
Conclusion
·
END
k
F
F
Material and Tools
Tools wich used in this research are as
∆
F
F
c
Page 2.12 Deflection axial
Where :
∆
/
follows :
a. Brake pad vibration test equipment
(with electric motor 3 phase 5,5 HP)
b. 3 couple Brake pad with different
thickness (7mm, 5mm, 3mm).
c. Piezoelectric Accelerometer.
d. Vibration meter markLutronVB_8202
e. Tachometer.
f. Inverter.
g. Pulley dan bel
Data processing
p
s
step
Th
he first ste
ep of data
a processin
ng
begins with recorrd measurem
ment data in
on accelera
ation data into
the forrm of vibratio
a displlay table in the excel program. We
W
show the excel pro
ogram into a graph whicch
onnect betw
ween the brake linin
ng
we co
Figure 6. Vibration meter
thickne
ess variatio
on with rottation of th
he
motor and also brraking press
sure variatio
on
e rotation off the motor. Measurement
with the
of the natural
n
frequ
uency of the
e system eacch
brake lining thickkness variattion with th
he
ach
approa
we
c
calculate
the
t
continu
uous cantilevver beam rods.
A
er
Figure 7. Acceleromete
Figure8. Brake Pad
Affter the test is complete assembled
test, then performed the data collection,
which can be seen in
n the followin
ng
sccheme:
Figure 9.Test da
ata making schema
s
stiffnesss
Data And Analysis
Then, the data above are analized to
16
425
Thickness
7mm
8.2
Thickness
5mm
9.5
Thickness
3mm
10.2
637
10.8
12
12.8
850
12.8
13.7
15.3
1061
13
14.2
15.6
14
12
13.1
Vibration Velocity (m/s²)
16.2
15.4
15.2
14.8
13.2
11.1
Rotation
(RPM)
16.1
18
measurment shown at following figure :
RMS VALUE (m/s2)
pressure and shaft rotation speed. Data
17.1
Vibration Graphs on axial
direction for pressure 1 bar
knowing the vibration at different brake
11.2
10.7
10
8
Pad 7
8.9
Pad 5
6
Pad 3
4
2
0
Vibration Graphs on axial
direction for pressure 0.6 bar
425 637 850 1061 RPM
18
8
15.6
14.2
13
15.3
13.7
12.8
12
10.2
rotations of the vibration amplitude in the
axial direction, the braking pressure of 1bar
10.8
10
9.5
12
12.8
14
Figure 11. Relationship between the axis
Pad 7
Pad 5
8.2
RMS VALUE (m/s2)
16
Rotation
(RPM)
4
425
Thickness
7mm
7
2
637
9
11.2
12.7
0
850
11.8
12.9
14.5
1061
13.5
14.6
16.1
6
Pad 3
425 637 850 1061
Thickness
5mm
9.5
Thickness
3mm
11.6
RPM
Vibration Graphs on Radial
direction for pressure 0.6 bar
Figure 10. Relationship between the
the axial direction, the braking pressure of
0.6bar
Vibration Velocity (m/s²)
425
Thickness
7mm
8.9
Thickness
5mm
10.7
Thickness
3mm
11.1
637
11.2
13.2
13.1
850
14.8
15.4
16.1
1061
15.2
16.2
17.1
RMS VALUE (m/s2)
rotation axes of the vibration amplitude in
Rotation
(RPM)
Vibration Velocity (m/s²)
20
18
16
14
12
10
8
6
4
2
0
18.1
16.5
14.7
13.6
13.2
14.9
16.6
15.5
13.8
11.5
Pad 7
11
Pad 5
9
Pad 3
425 637 850 1061
RPM
Figure 12. The relationship between the
the processing vibration indication that the
rotation axis of the vibration amplitude in
brake pads are still good or still thick
the radial direction at a pressure of 0.6bar
Rotation
(RPM)
produces low vibration acceleration value.
From vibration value measurment, we
Vibration velocity (m/s²)
Thickness
Thickness
Thickness
can find the value of brake pad natural
7mm
5mm
3mm
frequency and critical damping coeficient
425
9.6
12.5
14.3
which will get result as table below:
637
12.2
15.7
16
850
16.5
17.2
17.5
Table 1. Values of natural frequencies and
1061
17.3
18.3
19.2
critical damping coefficient value of each
brake pad.
Vibration Graphs on Radial
direction for pressure 1 bar
Thick Brake
Pad (mm)
RMS VALUE (m/s2)
25
20
(Ns/m)
7
493,63
184,61
5
1111,94
373,27
3
4447,92
1352,16
19.2
17.5
16
15
(Hz)
14.3
12.5
17.2
18.3
17.3
16.5
15.7
Pad 7
12.2
Pad 5
10
9.6
Based on the results of these calculations
with a critical damping coefficient is greater,
Pad 3
and the system will easily vibrate because
5
of small damping ratio.
0
425
637
850
On
1061 RPM
the
axial
direction
of
the
measurement pressure of 1 bar (Figure 4.2)
Figure 13. Relationship between the axis
and the measurement of radial pressure of
rotations of the vibration amplitude in the
1 bar (Figure 4.4) it can be seen that the
radial direction at a pressure of 1bar
thickness of the lining 5mm shaft speed
637 rpm surge approaching the vibration
Discussion
amplitude values even exceed the value of
The results of processing the vibration
the amplitude of vibration in the lining
an
thickness of 3mm.On the measurement of
increase in the value of the acceleration of
vibration velocity shows that the vibration of
vibration generated each variation of the
velocity
thickness of the brake lining. This increase
appears larger when compared to the axial
is indicated by the value of the acceleration
direction, as shown in the graph measuring
of vibration that occurs in brake that has
the axial direction for the braking pressure
experienced wear and worn. The results of
0.6 bar (Figure 10) and radial graphs for
acceleration
values
indicate
that
in
the
radial
direction
which
braking pressure 0.6 bar (Figure 12) it can
Untuk selanjutnya dapat di lakukan
be seen the difference value of the
penelitian untuk mendeteksi tingkat
resonance. 425 rpm for shaft rotation in the
keasuan
direction of axial value does not exceed 8.2
dengan bahan atau merk yang
m/s2, while in the radial direction vibration
reaches the value of 11.6 m/s2. This occurs
due to the effect of centrifugal force on the
rotation axis to the radial direction, so that
the force that occurs on the radial direction
is greater than the axial direction.
Conclusion
From data analysing and discusion can be
of tained conclusion as follow :
1. Increasing the value of aplitude2-4,7
m/s2in dicate lessing of Brake pad
worn.The increasing of aplitude value is
cause by the lessing of pad mass, that
affect the decreasing of damping value
to vibration, then Increasing of braking
pressure and shaft rotation will increase
exitation force that cause the value of
amplitude greater.
Sugesstion
1. Next, we can do research to detect the
level of brake pad worn using other
brand.
2. Before take the data, it is better to know
the brake resonansi frequency.
Sugegestion
kampas
rem
cakram
berbeda.
Sebelum
henaknya
pengambilan
mengetahui
resonansi sistem.
data
frekuensi
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