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HUNGARIAN JOURNAL
OF INDUSTRY AND CHEMISTRY

VESZPRÉM
Vol. 40 (2) pp. 113-119 (2012)

MAGNETORHEOLOGICAL FLUID BRAKE –
BASIC PERFORMANCES TESTING

WITH MAGNETIC FIELD EFFICIENCY IMPROVEMENT PROPOSAL

A. POZNIĆ1 , A. ZELIĆ1, L. SZABÓ2

1University of Novi Sad, 6 Trg Dositeja Obradovića, 21 000 Novi Sad, SERBIA
E-mail: alpoznic@uns.ac.rs

2University of Pannonia, 18 Zrínyi Str., 8800 Nagykanizsa, HUNGARY

A review of all magnetorheological brake types was presented. Based on overall braking torque analytical comparison for
all magnetorheological brake types and other relevant parameters, the most promising design was selected. A test rig,
utilizing selected brake type filled with magnetorheological fluid – Basonetic 5030 was manufactured and then tested. To
analyze the effect produced by magnetic field on magnetorheological fluid and hence at overall braking torque, the
authors used amplification factor. Results were discussed and the magnetic field efficiency improvements were proposed.

Keywords: magnetorheological brake, Basonetic 5030, test rig, amplification factor, efficiency improvements

Introduction

The convectional friction brake (FB) is the most
commonly used brake type in almost any mechanical
system today. However, it is characterized by
drawbacks such as periodic replacement due to wear,
large mechanical time-delay, bulky size etc. [13, 29],
partially altered. Electromechanical brakes (EMBs)
have potential to overcome some of these drawbacks
and are a suitable FB replacement. Today EMBs are
applicable in almost any mechanical system.
Application of intelligent materials is the next step in
the development of EMB.

Magnetorheological (MR) fluids belong to a class of
intelligent materials that respond to applied magnetic
field with fast, continuous, and reversible change in its
rheological behaviour [3, 7, 28], partially altered. MR
fluids are a type of suspensions, with carrier fluid
usually mineral or synthetic oil, water, kerosene and
micro size magnetizable particles dispersed in it. When
exposed to external magnetic field particles form a
chain-like structures thus changing the viscosity of the
fluid. In this study, authors used BASF’s
magnetorheological fluid, Basonetic 5030.

MR fluids have attracted extensive research interest
in recent years since they can provide simple, quiet and
fast response interface between electronic control and
mechanical system [11, 20, 22]. A lot of work was done
on MR fluid brakes modelling, properties investigation
and control [3, 6, 11]. A wide range of MR fluid devices
have also been investigated for their potential
applications in different systems, such as: clutch system,
vibration control, seismic response reduction, etc. [9,
10, 26].

MR fluid brakes have also been used in actuators
due to their distinguished force control and power
transmission features [5, 15]. By applying a proper
control effort, viscosity with large varying range is
achievable with the MR fluid brake. Currently, there are
many solutions for MR fluid brake design. Some MR
fluid brakes with attractive properties, such as high
yield stress and stable behavior, have been developed
and commercialized [4, 16].

The objective of this work was to compare overall
braking torque analytical expressions and design
complexity for all MR fluid brake types. Based on
results obtained from these comparisons, MR fluid
brake type with the most promising properties was
manufactured and tested on a specially designed test rig.
Results were discussed and a proposal for new MR
brake design with higher magnetic efficiency was
presented.

Magnetorheological effect

MR fluids are suspensions composed out of three major
components: carrier fluid - usually mineral or synthetic
oil, magnetizable particles - carbonyl iron powder and
set of additives [2, 17], partially altered. When exposed
to an external magnetic field (ON state), change in MR
fluid’s viscosity occurs. In the absence of an external
magnetic field (OFF state), MR fluid acts as Newtonian
fluid [7, 11] and can be described as:

τ η γ= ⋅ & (1)

In (1) τ represents shear stress, η the viscosity of the
fluid and γ& shear rate. Often, for MR fluid brakes,

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denoted as r / gγ ω= ⋅& , where r is rotor radius, ω and g
are angular speed and MR fluid gap length, respectively.

When in ON state, MR the rheological properties of
MR fluid change. Magnetizable particles induce
polarization and form chain-like structures in magnetic
flux path direction, thus changing apparent viscosity of
the fluid. ON state behavior of MR fluid is often
represented as a non-Newtonian [1, 3, 5], having a
variable yield strength. The usage of Bingham’s model
(2), in this situation, gives reasonably good results, [1,
11, 20, 22]:

Bτ τ η γ= + ⋅ & , (2)

where τB is the yield stress, developed in response to the
applied magnetic field. Its value is a function of the
magnetic field induction B.

When used in a device, MR fluid can be in one of
four modes: shear, flow (pressure), squeeze and pinch,
[8, 18, 28]. In brake i.e. torque transfer applications,
MR fluid operates in shear mode [1]. Braking torque
values are adjusted continuously by changing the
external magnetic field strength.

Magnetorheological brakes

MR brake consists out of four main parts: rotor, housing
i.e. stator, coil and MR fluid, Figure 1. The shape of the
rotor is what differentiates MR brake types from each
other. One needs the quantitative parameters of MR
brake, to be able to determine its specific application
suitability.

MR brake types, mechanical model, quantitative
parameters comparison for all MR brake types are
presented in next section.

Magnetorheological brake types

Through literature research [9, 14, 22, 23, 24], authors
of this paper have identified five major MR fluid brake
designs: drum brake, inverted drum brake, disk brake,
T-shape rotor brake and multiple disks brake, Fig. 1.

Drum brake along with the disk brake is the easiest
designs to manufacture. However, large inertia is its
major drawback compared to disk brake design [1].

The disk brake design is the most common MR
brake design found in literature today and was the first
one to be investigated [25]. It is the easiest one to
manufacture and gives reasonably good results in terms
of weight and compactness [14]. There are some
variations in MR disk brake design such as: the use of
two coils instead of one in order to increase the
magnetic pole area and/or relocation of the coil on top
of the disk in order to reduce its external diameter [22],
but the basics remain the same. It is also interesting to
note that the MR disk brake design is currently the only
one commercially available as a standard product,
manufactured by Lord Corporation [16] and that it was
used in several studies [7, 19, 21].

In order to increase compactness of the MR disk
brake design, several disk-shape rotors can be used
instead of one, with segments of stator located in
between each rotor disk, Fig. 1.d. This multiple disk
design is very popular in literature and was used in
several applications that required high torque in limited
space and weight [13, 22, 23]. The equations describing
this particular design are very similar to those of the
single disk brake, presented paper’s sequel.

The T-shape rotor brake design (Fig. 1.e), is more
compact than all other designs but is also more complex
to manufacture. Despite its advantages, this design is
not so common in literature [22].

Figure 1: Types of MR brakes: a) drum, b) inverted

drum, c) disk, d) multiple disks, e) T-shaped rotor, [28]

For all aforementioned MR brake types, the rotor
has a cylindrical shape and the magnetic flux lines run
in the radial direction, Fig. 1.

To author’s knowledge, an in-depth comparison of
all these architectures is not yet available.

Mechanical model

The key objective in MR fluid brake design is to
establish the relationship between the overall braking
torque, magnetic field strength and design parameters.
Interaction of MR fluid and inner surfaces of the brake
will generate the braking torque. Based on Eq. (2) and
the specific geometrical configuration of MR brake, for
all MR brake types, it applies:

2d 2 dT N r rπ τ= , (3)

where:
N – number of surfaces of the rotor, perpendicular to
the magnetic flux lines and in contact with MR fluid,
r – the radius of the rotor.

The overall braking torque TOverall, consists of three
components:
- the magnetic field induced component TB, due to the

field-dependent yield stress,
- the fluid viscosity dependent component Tvis and
- the friction induced component Tfric..

Thus, the overall brake torque:

115

Overall B vis fricT T T T= + + (4)

The sum of the first two components TB and Tvis i.e.
the braking torque can be obtained by the following
integral:

22 d
O

R
B vis

R
T T N r rπ τ+ = ∫ , (5)

where RO and Ri are the brake’s rotor outer and inner
radii respectively. Considering practical conditions, for
all MR brake types, the value of the Ri can be ignored
because the RO is several order of magnitude of the Ri
(Figure 2).

Figure 2: MR fluid disk brake simplified representation

Based on Eq. (5), the authors formed the final

analytical expressions for all five MR brake designs.
Expressions were adopted from several different
literature sources [1, 6, 12, 13, 21, 27, 29] and were
partially altered in order to make the comparison easier.
The last part of torque, Tfric can be precisely obtained
only by torque gauge.

3 4
4

( )
3Overall O O fric

T R R T
g
ω

π τ η= + + , (6)

3 4
4

( )
3Overall O O fric

T N R R T
g
ω

π τ η= + + , (7)

2 34 ( )Overall O O fricT h R R Tg
ω

π τ η= + + , (8)

2 38 ( )Overall O O fricT h R R Tg
ω

π τ η= + + . (9)

Variable h is the height of the rotor.
It is now easy to distinguish components of overall

braking torque in Eq. (6–9), for disk, multiple disks,
drums and T-shaped rotor, respectively. The yield stress
τB given in Eq. (2), varies with magnetic induction, but
can reasonably be fitted with the third-order polynomial
[12], as follows:

2 31 2 3B K B K B K Bτ = + + , (10)

where Ki represents coefficients of regression.

Performances comparison

MR brakes can be compared on several different aspects
e.g. overall braking torque, dynamic range, mechanical
simplicity, inertia, electric power consumption, torque
to volume ratio, compactness, etc. Authors of this paper
compared level of mechanical simplicity for all five MR
brake types and the overall braking torque based on
analytical expressions, given in Eq. (6–9), Table 1. In
addition, the dynamic range and inertia were consider
and presented in the same table.

Table 1: Characteristics of various MR brake designs

B
ra

ke
ty

T O
ve

ra
ll

ev
el

o
f

m
ec

ha
ni

ca
l

si
m

pl
ic

ity

D
yn

am
ic

ng
e

T B
/T

vi
s

In
er

tia

(1) M H B
i

g
R

τ
ηγ

⋅
&

21
2 O

mR *

(2) M L
4
3

g
R

τ
ηγ
⋅ ⋅
&

21
2 O

(3) H L
4
3

g
R

τ
ηγ
⋅ ⋅
&

21
2 O D

mR N

(4) H H B
O

g
R

τ
ηγ

⋅
&

2
2
i i

O
m R

mR −

Explanations:
Brake types: (1)drum and inverted drum, (2) disk, (3)
multiple disks, (4) T-shaped rotor.
Level of mech. simplicity: H – high, M - medium,
L – low.
* For inverted drum brake design, expression is the same as
for the T-shape rotor design.
ND – the number of rotor disks, mi – missing inner mass of
the disk.

Dynamic range represents ratio of field induced

component TB and viscous component Tvis (friction
torque component not considered).

T-shaped rotor brake performs best dynamic and can
offer biggest overall braking torque, however it has a
large inertia, and is considered difficult to manufacture.
The other four designs are globally less compact than
the T-shaped rotor design. The two drum based designs
have comparable performances but are burdened with
even larger inertia for same rotor radius. Finally, the
disk and multiple disks designs offer a good alternative,
being mechanically the simplest, with smaller inertia
and giving reasonable dynamic range and the overall
braking torque.

Test rig

Based on test rigs literature research [10, 15, 20, 27] and
MR brake properties comparison (Eq. (6–9) and Tab. 1),

116

the authors of this paper selected the most promising
MR brake design and manufactured it. With lowest
inertia, good dynamic range and the highest mechanical
simplicity, the disk type promised the biggest potential.

For performance evaluating of the selected MR
brake type a rig was set up. The test rig was designed
and manufactured at Faculty of technical sciences, Novi
Sad – Serbia, and is presently at its Laboratory for
engines and vehicles. The test rig with its parts is depict
in Figure 3 and 4, and consists of four main parts:

- drive,
- power supply,
- MR brake and
- measuring and data acquisition equipment.

An 8-pole AC squirrel cage motor with 0.75 kW and
nominal speed of 700 rpm, model 5 AZ 100 LA – 8
(Končar) was placed at one end of the support-frame, of
the test rig. The inverter - Micro Master (Siemens),
Fig. 4, position 2, controls the direction and variable-
speed of the AC motor. Speed range was from 150 rpm
to 750 rpm with 50 rpm increment. These two elements
form a drive part of the test rig. The flexible coupling
connects AC motor and the shaft of the MR brake. MR
brake rests on two self-aligning ball bearings into
housings P203 (FK Bearing group). To avoid leakage of
MR fluid, Nitrile Rubber lip seals, suitable for MR type
application, have been used.

Torque transfer from the MR brake to a
measurement device was done indirectly. A load arm,
connected to the MR brake housing at one end, rests on
top of the load cell on the other end, Fig. 3. Thus, by
measuring the force on the load cell, the value of
transmitted torque was obtained. Load cell was
internally calibrated by calibration weights. The
capacity of the load cell, 1030 (Tedea), was 15 kg.

Figure 3: Demonstrating the test rig for MR brake

1. drive, 2. coupling, 3. self-aligning ball bearing, 4. MR
fluid brake, 5. self-aligning ball bearing, 6. optical

encoder, 7. load arm, 8. load cell, 9. data acquisition
card

The optical encoder, model AMT102-V-REV-C
(CUI Inc.), was connected to the shaft of the MR brake,
at the opposite side of the AC motor and rotated at the
same speed sample rate was 2048 per rotation. The
signals were processed by universal amplifier, KWS

673.A2 (HBM), Fig. 4, position 3. The DC power
supply, EA PS 2016-100 (Elektro-automatik), was
connected to the leads of the coil to provide flux
generation. This was the control current, with range of 0
A to 2 A and 0.2 A increment. The coil, made of copper
wire with diameter of 1 mm (18 gauges) has been coiled
on outer radius of the MR brake housing.
The MR fluid used in this experiment was Basonetic®
5030, from BASF® [17]. It is a carbonyl iron powder
based MR fluid.

Figure 4: Measurement and data acquisition equipment:

1. stabilized power supply, 2. inverter, 3. universal
amplifier

A typical testing procedure was as follows. First, the

MR brakes shaft was set to a certain speed for 1 min as
an initial condition, which stirred the MR fluid in the
brake to distribute it uniformly. The desired magnetic
field was then applied by setting the coil current i.e.
control current and waiting for 1 min. This ensured
stable structure forming of the MR fluid. The load cell
detected transmitted torque. Finally, the signal from the
load cell was processed and recorded.

Experimental results and improvement proposal

The goal of this experiment was to determine overall
braking torque capabilities of selected MR brake design.
The experiment was conducted on a specially designed
test rig, with different control currents and speed sets.
To eliminate the effects of previous observations,
different combinations of control current and rotational
speed were set for each reading. To bring repeatability
in the reading, every speed set was carried out twice at
different instance of time. For every reading,
approximately 1 min time, before torque data recording,
has been allotted to distribute the carbonyl iron particles
uniformly in the MR fluid and form a stable structure.

Experimental results

The experiment itself consisted out of tree parts. The
first part was to determine the influence of the
supporting ball bearings and seals, without MR fluid
inside the brake and no control current applied. This
was a friction braking torque component. Second part of
the experiment had the same setup but it included MR
fluid inside the brake. Viscous torque data was then

117

recorded, assuming that bearings and seals did not
change their friction characteristics in time.

Aforementioned recordings were needed in order to
get clear and precise information about field induced
component. This was the third part of the experiment
and it included MR fluid inside the brake and
application of the control current.

The same speed sets were used for the friction and
the viscous torque component measurements were
repeated. For each speed set, a 2 minute recording time
was used. Some field induced component results are
depict in Figure 5. Magnetic field influence is apparent.

Figure 5: Samples of overall braking torque results:

a) 0,2 A at 150 rpm, b) 1,6 A at 300 rpm

Because of the large number of data obtained in this

experiment, authors decided to use amplification factor
to determine the effect produced by magnetic field.
Amplification factor (AF) represents relation between
overall braking torque and sum of friction and viscous
torque, i.e. relation between the ON and OFF state of
the MR fluid.

at current
at zero current

Overall

T I
AF

T
= (11)

Amplification factor curves for all 13 speed sets are
plotted in Figure 6. This figure shows linearity in
amplification factor with increase in control current.
This was expected, since the higher the current, the
higher the field induced torque should be. Results are
presented with rotational speed variation as well.

Figure 6 indicates that the amplification factors for
speeds 150, 200, 250, 300 and 350 were much larger than
the ones for 450, 500, 550, 600, 650, 700 and 750 rpm.

Transition rpm value for this MR brake was 400
rpm. This was somewhat opposite to the torque
predicted by Eq. (6) where the TOverall should increase
with angular speed. This was not the case here.
However, other authors have also reported the same
trend – reduction of amplification factor with increment
of speed [20, 27]. This may be due to the possible shear
thinning effect of the MR fluid at high shear rates. This
reduces the effectiveness of MR brake at higher speeds.
Therefore, to make MR brake effective at higher speed
operation, one needs to think of „Shear stable MR
fluid“.

Figure 6: Variation in amplification factor with control

current

MR brake improvement proposal

In order to increase the overall braking torque of any
MR brake type its geometry needs to be optimized [14].
State of the art MR brake designs base their torque
generation on the inner section of the coil [4, 10, 13].
These designs are rather inefficient, because the
magnetic field is not used to its full potential and active
MR area is small. Flux mostly travels through the
housing of the MR brake. In this configuration,
magnetic field is concentrated on small area of the MR
fluid.

Figure 7: Novel MR brake design with enhanced

magnetic field efficiency

By altering earlier MR brake designs, it is possible
to concentrate magnetic field effect. One such design
has been presented in Figure 7.

Compared to the dimensions of the tested MR disk
brake, radius of the coil was reduced so that it could be
placed in a more suitable position inside new MR brake
design. New coil position allows for magnetic flux to be

118

used more efficiently. Now, the magnetic flux inside
MR brake passes through MR fluid several times.

Based on analytical comparison, presented in Eq.
(6–9) and Tab. 1, new design features two disks in order
to create more MR fluid active area. Greater number of
disks creates more MR fluid gaps thus the volume of
MR fluid can be increased.

Conclusion

Authors compared all MR brake types on several
different aspects. Based on this information, the most
promising MR brake type was selected, manufactured
and tested on a specially designed test rig.

The MR brake produced desirable results, which
coincide with literature sources. Approximately linear
relation between the overall braking torque and the
control current intensity was observed. To present
results in more readable manner, the amplification
factor was introduced.

The experiment showed that the tested MR brake
has potential for practical applications due to easiness
and accuracy of control. However, the value of the
overall braking torque is still small. To increase it,
better utilization of the existing magnetic field is
needed. The authors suggested different approach in
comparison to the conventional MR brake design that
would increase the overall braking torque by increasing
the magnetic field efficiency and the contact area of the
MR brake fluid. By multiplying the number of the disks
in contact with MR fluid, value of the overall braking
torque will multiply as well, Eq. (7).

In order to maximize the potential of the proposed
MR brake, further investigations on magnetic field
propagation is needed as well as design optimization.
Finite element method model of the novel MR brake is
the next step in this process.

Acknowledgments

This research was done as a part of project TR31046
“Improvement of the quality of tractors and mobile
systems with the aim of increasing competitiveness and
preserving soil and environment”, supported by Serbian
Ministry of Science and Technological Development.

MR fluid used in this experiment was provided by
BASF® company, under commercial name Basonetic®
5030. The authors of this paper would like to express
their sincere gratitude to BASF Company as well as to
the project manager Dr. Christoffer Kieburg for all the
supports.

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