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Mechanistic modelling of mineral sizers
R. Heng a, K. Cheng a, D. Tuppurainen b, R.A. Bearman b,*, S. Oswald c
a Department of Mechanical Engineering, University of Western Australia, 35 Stirling Highway, Crawley, WA 6009, Australiab Rio Tinto Technical Services, G.P.O. Box A42, Perth, WA 6837, Australia
c Hamersley Iron, P.O. Box 21, Dampier, WA 6713, Australia
Received 4 March 2003; accepted 13 May 2003
Abstract
Comminution in mineral processing must be tailored to the final product requirements. In many cases the requirement for
comminution is to generate the maximum amount of size reduction in the minimum number of equipment stages. There are howevercertain applications where maximum size reduction, or fines generation, are not desirable.
In such cases, and where the material characteristics allow, the application of twin rolls, toothed mineral sizers is often ad-
vantageous. This paper examines the function of an MMD 625 mineral sizer in terms of its mechanical design parameters and its
interaction with the feed material. Using the understanding developed during the study a mechanistic predictive model of the sizer is
generated that allows analysis of product size distribution, wear and throughput.
2003 Elsevier Ltd. All rights reserved.
Keywords: Comminution; Crushing; Modelling
1. Introduction
Key sectors of the minerals industry require commi-
nution machinery that can crush material to a given size
without over-crushing. These include:
• Coal––due to relatively fragile nature of the material
and the undesirability of fines.
• Iron ore––in cases where fines are of a lower value, or
where ultrafines should be minimized.
In such applications, equipment that is capable of
inputting high energy levels should be avoided. It should
also be noted that in the examples given above the
commodities are those regarded as bulk materials. Asbulk materials command a relatively low price, any
process equipment used in their treatment should be
capable of high throughputs particularly in relation to
the capital cost.
One device capable of high throughputs coupled with
restrained comminution is the mineral sizer. As the
name implies sizers combine a classification (sizing) and
crushing (top size control) function due to their design.
The main feature of mineral sizers is that the crushingtakes place between toothed crushing rolls and/or sta-
tionery surfaces. Other advantages claimed include:
• Ability to deal with high clay content, or sticky feed.
• Design is self-screening, thus removing the require-
ment to pre-screen.
The focus of this paper is the MMD 625 mineral
sizer, where the 625 designation refers to the distance in
millimetres between the centres of the two crushing rolls.
MMD are the original and largest manufacturer of
mineral sizers with their range covering various duties
from a primary sizer (MMD 1500) down to the MMD500. Due to the varying machine duties the design and
configuration of the MMD machines differs.
The machines designed for primary duty are the
largest throughput coarse comminution devices avail-
able. Typically the MMD 1500 machine is capable of
taking a feed size of 2 m down to a produce size of )350
mm at a rate of 10,000 tph. The MMD 625 is regarded
as a secondary machine and can be delivered in a variety
of length with either inward or outward rotation of the
crushing rolls. The main performance control features of
the MMD 625 are:
* Corresponding author. Tel.: +61-8-9327-2920; fax: +61-8-9327-
2999.
E-mail address: [email protected] (R.A. Bearman).
0892-6875/$ - see front matter 2003 Elsevier Ltd. All rights reserved.
doi:10.1016/S0892-6875(03)00178-X
Minerals Engineering 16 (2003) 807–813This article is also available online at:
www.elsevier.com/locate/mineng
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• Length of crushing rolls––throughput;
• Inward/outward rotation––size reduction top size
control and throughput;
• Rolls speed––throughput;
• Rolls separation––top size control, size reduction and
throughput;
• Rolls/stationery surface separation––size reduction
and throughput;
• Tooth configuration––manageable feed top size and
size reduction.
The MMD 625 sizers modelled in this paper are in-
stalled at the Hamersley Iron Yandicoogina operation in
Western Australia. The operation produces a )10 mm
pisolitic iron ore at a rate of 18 million tones per annum
from a three stage crushing and screening circuit. Two
MMD 625 machines act as secondary crushers receiving
an all in feed from a primary jaw crusher. Product from
the sizers is screened using three high ‘‘G’’ force banana
screens, with the undersize reporting to final productand the oversize being crushed using three tertiary
MP1000 cone crushers set at 14 mm closed side setting
in closed circuit with the screens.
The MMD 625 sizer is shown in Fig. 1 and has the
following configuration:
• Outward rotation––crushing between toothed rolls
and stationary fingers;
• Rolls speed: 60 rpm;
• Rolls teeth––stationery teeth gap: 70 mm.
Tooth design comprises five teeth on a segment with48 segments on each roll (96 segments per machine), the
tooth design is shown in Fig. 2.
The machine configuration at the Yandicoogina op-
eration was determined by MMD to meet the process
specification of 1400 tph (per machine) and a product
top size of 80 mm.
2. MMD sizer model
The MMD 625 sizes and crushes material in a variety
of ways due to the geometry of the teeth and the inter-
action with the feed material. The model consists of
eight modules (see Fig. 3), where each module corre-
sponds to a distinct stage within the machine. By having
this design, the modules can be edited or replaced
without affecting the functionality of the whole pro-
gram.
The aim of the modelling is to determine:
• product size distribution,• throughput,
• power consumption,
• rate and pattern of tooth wear.
The rate and pattern of tooth wear being of particular
importance as this in turn impacts the other process
parameters that are being calculated (Fig. 3).
The key information passed between each module is
the percentage weight of feed of a specific particle size at
a particular tooth position. This information can be
represented in a 2D matrix as shown in Fig. 4.
Fig. 1. Plan view of MMD 625 Sizer at Hamersley Iron Yandicoogina.
Fig. 2. Tooth configuration for MMD 625.
FeedDistribution
ParticleMovement
OuterScreening
SpecificEnergyBreakage
Tooth and F ingerWear Profile
Product SizeDistribution
RedistributionFeedDistribution
ParticleMovement
OuterScreening
SpecificEnergyBreakage
Tooth and F ingerWear Profile
Product SizeDistribution
Redistribution
Fig. 3. Flow chart for the fundamental model.
Fig. 4. Matrix of percentage weight, particle size, tooth position.
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For the previous example, particles in the )5000 mm
to +4204 mm size fraction, at the 3rd tooth position
represent 0.05% by weight of the original feed. 5000 mm
has been assigned the value of the maximum feed size
for this model. This is deemed to be in excess of the run-
of-mine feed that a primary crushing device could be
expected to handle. By default the top row of % weights
will always contain zero, as no feed can be in excess of
5000 mm in size.
The size fractions differ by a factor of 1 ffiffi24
p . Compared
to the standard sieve sizes that differ by 1 ffiffi2
p to allow a
greater resolution to be obtained for the particle sizes. In
the matrix, the number of teeth, n, is a parameter that
can be entered into the model by the user.
2.1. Feed distribution module
Given the design of the MMD sizer the feed distri-
bution along the length of the machine and the position
of the falling curtain of feed with respect to the rolls is
particularly important as this controls the maximum
throughput of the machine and the wear pattern of the
teeth.
The feed system into the MMD sizers at Yandicoo-
gina consists of a conveyor belt that empties into a
trouser leg chute that splits the feed to the two parallel
sizers. Due to constraints with the feed system the dis-
tribution along the length of the sizers is biased towards
the centre section of the rolls and the curtain of feed
tends to fall to the outside of the rolls. As these factors
have a major impact on the process performance of the
sizers a method of modelling this feed distribution isrequired. The feed distribution modules aim is to sim-
ulate the way feed enters the sizer. To cater for the va-
riety of feed distributions, the model employs three types
of feed profiles: uniform, triangular or parabolic. The
‘‘a’’ and ‘‘b’’ parameters correspond to the tooth posi-
tion of the feed boundaries. This allows uneven feed to
be modelled, and will enable the user to determine the
effect of different feed arrangements (Fig. 5).
2.2. Particle movement module
Particle motion within the sizer is a critical aspect in
understanding how material is captured and broken.
The action of the machine is that material falls in a
curtain between the two outward rotating rolls and
material that is smaller than the rolls separation falls
through without breakage, but the larger material is
carried by the teeth to the outside where it is broken
between the teeth and the stationary ‘‘fingers’’.
The function of the particle movement module is
twofold:
• To determine the proportion of particles that will
pass through the centre of the sizer, without undergo-
ing breakage and concomitantly the amount report-
ing for breakage.
• Model the movement of particles from the centre of
the sizer to the outer edge.
Trapezoids were selected as having the optimal shape
for calculating the probability of passing easily. The
probability of a particle passing through the gap is de-
termined using the ratio of passable area to total area. In
Fig. 6 below the rock will pass through the light-col-
oured hole if its centroid falls within the darkenedtrapezoid.
Probability of passage
¼ Passable area
Total area
¼ ðAverage length Particle diameterÞ ð? Height Particle diameterÞTotal area
The probability of selection for passage described
above is analogous to the selection function used in
many other types of breakage modelling. In this case the
more mechanistic approach to the issue of selection was
taken due to the action of the MMD and the existence of
a selection function for each tooth. It should also benoted that the selection function will change dramati-
cally with wear and the non-uniform wear rate and
pattern.
Fig. 5. The uniform, triangular, parabolic feed profiles.
Height
Average Length
⊥
Fig. 6. Possible area that a particle may pass.
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Fig. 7 shows the selection function for a single
toothed segment containing five offset teeth (as per Fig.
2). At an instant when a single tooth is at its minimum
setting (70 mm) the last of the five teeth on the segment
will be at 110 mm, this variation is illustrated in Fig. 7
against the particle size reporting for selection.
The variation in selection function along the length of
five toothed segments is shown in Fig. 8.
The particle movement section deals with the change
in position of the rocks as they move from the middle of
the sizer to the breakage side. Since it is assumed that
the sizer is under steady state conditions, any vertical
trajectories can be ignored.
From video footage it was determined that the
movement of the rocks is random. Thus it is appropriate
to use the random normal distribution function to cal-culate the probability of rock trajectories. The only
parameter that is required in such a case is the standard
deviation of normal distribution. From the video, it was
observed that no rock moved more than nine teeth po-
sitions in either direction. Therefore if we assume that 18
teeth positions is equivalent to 3d, the standard devi-
ation for the entire profile is d 3.
2.3. Outer screening module
Just as the gaps in the middle of the sizer will act to
screen undersized material, a similar effect occurs on the
outer edge of the sizer. In this instance the crucial factor
is the geometry of the fingers. Before and after each
breakage event, undersized particles may fall through
the gaps in the stationary fingers.
The action of the outer section where the teeth and
stationary fingers interact is critical in determining the
size reduction behaviour of the sizer. The stationary
fingers are located on ‘‘in-fill’’ boxes so that their posi-
tion relative to the teeth can be adjusted to account for
wear. On the MMD 625 there are five fingers per in-fill
box. The sizing function of this outer area is particularly
important as there is no method of adjusting the gap
between the rolls to account for wear.
As with the particle movement module the selection of
material for breakage is a key element and the calcula-
tion of the function is undertaken in the same manner.
2.4. Specific energy module
Any rock undergoing breakage will have a particular
amount of energy applied to it. This module determines
the amount of energy that will be applied to a rock,
according to the machine geometry. Once the specific
energy is determined, the sizes and proportions of
breakage products can be calculated.
Kicks theory (1885) states that the energy consumed
in size reduction is proportional to the reduction in
volume of the particles undergoing breakage. Hukki(1975) demonstrated that Kicks work is most applicable
for crushing applications where the particles are larger
than 1 cm in diameter. In order to obtain a value for the
constant of proportionality, drop weight tests by Briggs
(1997) have been analysed. By fitting a log curve to the
data, a value of 0.321 kW h/t has been determined.
Thus Kicks law can be used in the following form:
E ¼ 0:321 ln d
gap
where E is the specific energy (kW h/t), d is the initial
particle size (mm), gap is the gap size between the fingers
and the teeth (mm).It is important to note that the geometry of the ma-
chine and the rock strength parameters (captured within
the coefficient) are the sole determining factors for the
specific energy. It must be noted that another advantage
of using the Kick equation is that the coefficient also
takes into account the efficiency of energy transfer.
2.5. Breakage module
Single particle tests to determine the comminution
behaviour of rock can be separated into pendulum and
7090
110
1030
5070
90
0
0.5
1
Gap (mm) Particle Size (mm)
Probability of Selection
for Passage
Fig. 7. Particle passage selection function for single segment con-
taining five offset teeth.
7 0 9
0 1 1 0 8
0 1 0 0 7
0 9 0
1 1 0 8
0
1 0 0 7
0 9 0
1 1 0
1 0
3 0
5 0
7 0
9 0
0
0.5
1
Probability of Selection
for Passage
Gap (mm)Particle
Size
(mm)
Fig. 8. Variation in selection function over five segments.
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drop weight based tests. The twin pendulum test relies
on the particle being broken between an input pendulum
released from a known height and a rebound pendulum.
The drop weight test differs in that the particles are
placed on a hard surface and struck by a falling weight.
Both these approaches have been used extensively in the
field of comminution.
The JKMRC has specialized in the application of
these test methods since the work of Narayanan and
Whiten (1988) highlighted their use in the field of
comminution modelling. Recent developments at the
JKMRC have seen the twin pendulum being replaced by
the drop weight apparatus.
The drop weight apparatus is seen to have several
advantages including:
• extended input energy range compared to the twin
pendulum devices,
• shorter time span of operation compared to the pen-
dulum test,• extended particle size range,
• ability to conduct particle bed breakage studies.
The standard drop weight device is fitted with a 20 kg
mass, which can be extended to 50 kg. The effective
range of drop heights is 0.05–1.0 m, which represents a
wide energy range from 0.01 to 50 kW h/t (based on 10–
50 mm particles).
Following sample preparation the mean mass of each
set of particles to be broken is calculated. Based on the
required specific input energy for each test, the height
from which the drop weight is to be released is deter-mined using the relationship below:
hi ¼ m E is
0:0272 M d
where hi is the initial height of the drop weight above the
anvil (cm), m is the mean mass of each set of particles
(kg), M d is the mass of the drop weight (kg), E is is spe-
cific input energy (kW h/t).
Typically 10 mm is added to the calculated drop
height for each test. This ensures that the required final
specific comminution energy is obtained, since after
breaking a particle the drop weight is brought to rest at
a height above the anvil. The average offset can bemeasured for each sample of particles broken, in which
case the applied energy is
E is ¼ 0:0272 M d ðhi hf Þm
where hf is the average height at which the drop weight
comes to rest above the anvil.
The results from the drop weight tests provide an
energy/input size/product size relationship. This rela-
tionship is analyzed using a set of curves to describe the
size distribution produced from breakage events of in-
creasing size reduction or energy input.
The descriptor employed in this approach is the t
parameter. Each product size distribution curve is nor-
malized with respect to the input size to give percentage
passing figures for various fractions. Therefore t 10 is the
percentage passing 1/10th of the original feed size and t 2
is the percentage passing 1/2 of the original feed size.
The t 10 parameter is the most often quoted parame-ter. Typically in a crusher t 10 is 10–20%, whereas in a
tumbling mill values in the range 20–50% are expected.
To make use of this description of ore breakage the
marker points t 2, t 4, t 25, t 50 and t 75 are stored in a
matrix form against t 10. This same data can be repre-
sented graphically as shown in Fig. 9.
Fig. 9 is a powerful graph as each vertical line (or
value of t 10) represents an entire cumulative percent
passing mass size distribution.
The t 10 value is related to the specific comminution
energy by the equation
t 10 ¼ Að1 eb E csÞwhere t 10 is the percentage passing 1/10th of the initial
mean size, E cs is the specific comminution energy (kW h/
t), A, b are the ore impact breakage parameters.
The A parameter represents the theoretical limiting
value of t 10, whilst ‘‘b’’ is the slope of the t 10 versus E cs
graph.
Using this approach to comminution the key factors
are t 10, E cs, A and b. The relation of these parameters to
other measures of rock strength are examined later.
2.6. Tooth and finger wear
The teeth and fingers of the sizer will wear signifi-
cantly over time causing an increase in the gap size.
The mechanism of wear in the sizer was examined to
determine an appropriate simplification that could be
used in the model. Initial thoughts on the type of wear
that is experienced by the sizer teeth were weighted to-
wards the idea of gouging wear. To investigate this issue
a series of micrographs were taken of the surface.
The results of the examination contradicted the initial
thoughts, in that the percentage of gouging wear seen on
the surface was less than 5–10%, with a majority of the
0
20
40
60
80
100
0 10 20 30 40 50
t10 (%)
C u m u
l a t i v e P e r c e n t P a s s i n g
t75
t50
t25
t10
t4
t2
Fig. 9. Size distribution parameter t versus t 10.
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The model assumes normal feed conditions, uses
machine geometry values derived from the appropriate
engineering drawings.
The model shows good correlation with the measured
data, although it tends to overestimate the size reduction
in the lower end of the size distribution curve. The di-
vergence is minor and well within the measurement ac-
curacy of the sampling. Should the divergence be due to
deficiencies in the model it is suggested that the main
causes could be either the selection function used, or the
shape of the feed material particles.
4. Conclusion
Product size distribution and crushing component
wear are key parameters in determining the performance
of a crushing device. This paper has described the key
modules used in the modelling of the MMD 625 Mineral
Sizer. Using machine geometry, ore breakage charac-teristics and representations of selection and energy
input a model has been derived that successfully predicts
product size distribution and tooth wear. The next stage
of the work is to apply similar techniques to the primary
MMD mineral sizers at the Robe River Pannawonica
operation.
Acknowledgements
The authors would like to thank operations staff at
Hamersley Iron Yandicoogina (John Smoothy), MMD
(Alan Potts, Ali Benbia) and Transmin (Ross Nunn,
Evan Douglas).
References
Briggs, C.A., 1997. A Fundamental Model of a Cone Crusher, Ph.D.
Thesis, University of Queensland.
Hukki, R.T., 1975. The principles of comminution: an analytical
summary. Engineering Minerals Journal.
Kick, F., 1885. Das Gesetz der Proportionalen Widerstande und seine
Anwendung, Leipzig.Narayanan, S.S., Whiten, W.J., 1988. Determination of comminution
characteristics from single particle breakage tests and its applica-
tion to ball mill scale-up. In: Trans. IMM, vol. 97, Section C, pp.
C115–C124.
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