FIELD OF THE INVENTION
[0001] The present invention generally relates to the field of mineral ore processing, and
more particularly, to a mixing apparatus and to uses thereof in the separation of
minerals from mineral-bearing ores.
BACKGROUND OF THE INTENTION
[0002] Processes are known in the prior art which provide for the separation of minerals
from mineral-bearing ores.
[0003] For example, in known processes used for the separation of copper from copper-bearing
ores, illustrated diagrammatically in Figure 1, non-oxidized ores 20 (which might
contain as little as 0.5% copper, and typically contain iron sulfides) are processed
in a crusher 22, with water 24, to form a slurry 26. The slurry 26 is then transferred
to a flotation cell 28, and subjected to physical action, specifically, air sparging
and mixing. As a result of the physical action, a substantial portion of the copper
value in the slurry 26 rises to the surface of the flotation cell 28 as a froth 30,
and is skimmed therefrom by a paddle mechanism 32, while the waste rock 33 ("gangue")
remains in the bulk, and is ultimately passed from the cell 28 to a dryer 34 and discharged
as tailings 36. This process of "froth separation" results from differences in wettability
of copper as compared to other minerals, and is typically aided by chemical frothing
and collector agents 38 added to the slurry 26, such that the froth 30 from such flotation
contains 27% to 36% copper. Methylisobutyl carbonal (MIBC) is a typical frothing agent,
and sodium xanthate, fuel oil, and VS M8 (a proprietary formulation) are typical collector
agents.
[0004] The froth 30 is then fed to an oxygen smelter 40, and the copper and iron sulfides
are oxidized at high temperature resulting in impure molten metal 42 (97% - 99%, copper,
with significant amounts of iron oxide) and gaseous sulfur dioxide 44. The impure
metal 42 is then transferred to an electrolytic purification unit 46, which separates
the impure metal 42 into 99.99% purity copper material 48 and slag 50.
[0005] The gaseous sulfur dioxide 44 is collected in a reactor 52 wherein it is scrubbed
and mixed with water 24 to form sulphuric acid 54. The sulphuric acid 54 is suitably
blended with water 24 and used to leach oxidized ores, typically by "heap leaching"
an ore pile 56. The resultant copper-bearing acid 58 is known as "pregnant leach solution".
Pregnant leach solution 58 is also obtained by mixing solutions of sulphuric acid
54, in vats 60, with the tailings 36 discharged from flotation operations, to dissolve
the trace amounts of copper remaining therein.
[0006] The copper is "extracted" from the pregnant leachate 58 by mixing therewith, in a
primary extraction step 62, organic solvent 64 (often kerosene) in which copper metal
preferentially dissolves. Organic chemical chelators 66, which bind solubilized copper
but not impurity metals, such as iron, are also often provided with the organic solvent,
to further drive the migration of copper. Hydroxyoximes are exemplary in this regard.
[0007] In the primary extraction step 62, the copper is preferentially extracted into the
organic phase according to the formula:
[CuSO
4]
aqueous + [2 HR]
organic → [CuR
2]
organic + [H
2SO
4]
aqueous
where HR = copper extractant (chelator)
[0008] The mixed phases are permitted to separate; into a copper-laden organic solvent 68
and a depleted leachate 70.
[0009] The depleted leachate 70 is then contacted with additional organic solvent 72 in
a secondary extraction step 74, in the manner previously discussed, and allowed to
settle, whereupon the phases separate into a lightly-loaded organic (which is recycled
as solvent 64 in the primary extraction step) and a barren leachate or raffinate 76.
[0010] The barren leachate 76 is delivered to a coalescer 78 to remove therefrom entrained
organics 80, which are recycled into the system; the thus-conditioned leachate 82
is then suitable for recycling into the leaching system.
[0011] The pregnant organic mixture 68 (produced in the primary extraction step 62) is stripped
of its copper in a stripping operation 84 by the addition of an aqueous stripping
solution of higher acidity 86 (to reverse the previous equation); after phase separation,
a loaded electrolytic solution 88 ("rich electrolyte") remains, as well as an organic
solvent, the latter being recycled as solvent 72 in the secondary extraction 74.
[0012] The rich electrolyte 88 is directed to an electrowinning unit 90. Electrowinning
consists of the plating of solubilized copper onto the cathode and the evolution of
oxygen at the anode. The chemical reactions involved with these processes are shown
below
Cathode: CuSO
4 + 2e
1- → Cu + SO
42-
Anode: H
2O → 2H
+ + 0.5 O
2 + 2 e
1-
[0013] This process results in copper metal 92, and a lean (copper-poor) electrolyte, which
is recycled as stripping solution 86.
[0014] The combination of leaching, combined with extraction and electrowinning, is commonly
known in the art as solvent extraction electrowinning, hereinafter referred to in
this specification and in the claims as "SXEW".
[0015] In a known application of the described SXEW process, in both the primary 62 and
secondary 74 extraction steps, the combined organic and aqueous phases are delivered
through a series of mixing vessels (primary P, second S and tertiary T), and then
to a settling tank ST, the primary mixing vessel P being about 2, 44 meters (8 feet)
in diameter and 3, 66 meters (12 feet) in height, and stirred by a rotary mixer driven
by a 14920 watts (20 horsepower) motor, and each of the secondary S and tertiary T
mixing vessels being about 3,66 meters (12 feet) in diameter and height, and stirred
by a rotary mixer driven by a 5595 watts (7.5. horsepower) motor. (The system of primary
P, secondary S and tertiary T mixers, and settling tank ST, is replicated to meet
volume flow requirements, with each system' processing about 0.63 cubic meters per
second (10,000 gpm)). This provides a mixing regime wherein the organic and aqueous
phases are intimately mixed for a period of time sufficient to allow copper exchange
(to maximize copper recovery), yet relatively quickly separate substantially into
organic and aqueous phases.
[0016] In a known application of the froth flotation process, a plurality of flotation cells
28, each being approximately 1,52 meters square (5 feet square) and 1,22 meter (4
feet) high, are utilized, with pairs of cells sharing a 37300 watts (50 horsepower)
motor driving respecting rotary mixers (not shown). This provides a mixing regime
sufficient to allow the air bubbles to carry the copper value to the surface.
[0017] Various modifications can be made to the rotary mixers in the extractors and in the
flotation tanks of the foregoing process. However, the general configurations noted
above have been found to provide relatively economical results, and significant variations
therefrom can impact adversely upon economies. For example, an attempt to reduce energy
costs by scaling-down the motors for the mixers would have consequent impacts either
upon the copper recovery efficiency, or upon available process throughputs. Specifically,
the relatively large motors employed are required to drive the sturdy (and therefore
heavy) rotary mixers and shafts that are needed to withstand the torques caused by
rotation; lower power motors would demand either lower blade speed or smaller blades,
with consequent impacts upon mixing and transfer efficiency.
[0018] Further, in
WO 02/083280 an apparatus is proposed for mixing fluids within a vessel having a contiguous sidewall
centered about and defining a longitudinal axis, the mixing apparatus comprising:
a mixing head having a blade body for immersion in the fluids, the blade body having
a first end, an opposed second end disposed in spaced relation thereto along a blade
body axis, and a passageway extending therealong between the first and second ends;
the passageway tapering from the first end to the second end; the blade body further
having an inner surface and an outer surface, the outer surface of the blade body
defining an inside blade diameter ID at the second end, and an outside blade diameter
OD at the first end ;
means for mounting the mixing head within the vessel; and
means for imparting reciprocating longitudinal movement to the mixing head, the reciprocating
longitudinal movement being defined by a stroke length S, with a duration T for each
cycle,
the mixing apparatus being operable within a set of operational parameters defined
by the equation:
where:
OD is the outside diameter of the blade body at the first end thereof measured in
meters;
ID is the inside diameter of the blade body at the second end thereof measured in
meters;
S is the stroke length measured in meters; and
T is the duration of each cycle measured in seconds
where OD, ID and S are each expressed in inches, and
T is expressed in minutes); and
a portion of the fluids is urged by virtue of the reciprocating longitudinal movement
imparted to the mixing head to flow through the passageway defined in the blade body
to thereby encourage efficient mixing of the fluids in the vessel.
[0019] However the apparatus according
WO 02/083280 does not provide any positive answer to the above mentioned drawbacks. A solution
is defined in the characterizing part of claim 1.
[0020] According to the invention, there is provided an apparatus for mixing fluids within
a vessel having a contiguous sidewall centered about and defining a longitudinal axis.
The mixing apparatus includes a mixing head, means for mounting the mixing head within
the vessel, and means for imparting reciprocating longitudinal movement to the mixing
head. The mixing head has a blade body for immersion in the fluids. The blade body
has a first end, an opposed second end disposed in spaced relation thereto along a
blade body axis, and a passageway extending therealong between the first and second
ends. The passageway tapers from the first end to the second end. The blade body further
has an inner surface and an outer surface. The outer surface of the blade body defines
an inside blade diameter ID at the second end, and an outside blade diameter OD at
the first end. The reciprocating longitudinal movement imparted to the mixing head
is defined by a stroke length S, with a duration T for each cycle. The mixing apparatus
is operable within a set of operational parameters defined by the equation:
where OD, ID and S are each expressed in meters, and T is expressed in seconds
where OD, ID and S are each expressed in inches, and T is expressed in minutes) .
By virtue of the reciprocating longitudinal movement imparted to the mixing head,
a portion of the fluids is urged to flow through the passageway defined in the blade
body to thereby encourage efficient mixing of the fluids in the vessel. According
to the invention, the OD:ID is between 1.5 and 1.7.
[0021] In an additional feature, the stroke length S is between 0,05 meter (2 inches) and
0,61 meter (24 inches). Preferably, the stroke length S is between meter 0,10 (4 inches)
and 0,41 meter (16 inches). More preferably, the stroke length S is between 0,20 meter
(8 inches) and 0,30 meter (12 inches).
[0022] In a further additional feature, the OD:ID is greater than 1.0 and less than or equal
to 1.7. In yet another feature, the stroke length S is between 0,20 and 0, 30 meter
(8 and 12 inches) ; and the OD:ID is between 1.5 and 1.7.
[0023] The novel features which are believed to be characteristic of the present invention,
as to its structure, organization, use and method of operation, together with further
objectives and advantages thereof, will be better understood from the following drawings
in which a presently preferred embodiment of the invention will now be illustrated
by way of example. It is expressly understood, however, that the drawings are for
the purpose of illustration and description only, and are not intended as a definition
of the limits of the invention. In the accompanying drawings:
[0024] Figure 1 is a diagrammatic representation of conventional SXEW processes for copper
extraction.
[0025] Figure 2 is a front, top, right side perspective view of a fluid mixing apparatus
according to a preferred embodiment of the present invention, shown operatively mounted
on a vessel.
[0026] Figure 3 is a right side cross-sectional view of the fluid mixing apparatus and vessel
shown in Figure 2.
[0027] Figure 4 is a front, top left side perspective view of the fluid mixing apparatus
of Figure 2, showing,
inter alia, a reciprocating drive assembly and mounting means.
[0028] Figure 5 is an exploded perspective view of a portion of the structure shown in Figure
4.
[0029] Figure 6A is a front elevational view of the structure of Figure 4, with the mixer
shaft and shaft gripping means removed for clarity.
[0030] Figure 6B is a view similar to Figure 6A, with, inter alia, the flywheel displaced
90° counter-clockwise relative to its position in Figure 6A.
[0031] Figure 6C is a view similar to Figure 6A, with, inter alia, the flywheel displaced
90° counter clockwise relative to its position in Figure 6B.
[0032] Figure 6D is a view similar to Figure 6A, with, inter alia, the flywheel displaced
90° counter-clockwise relative to its position in Figure 6C.
[0033] Figure 7 is a front, top, right side perspective view of the mixing head of the fluid
mixing apparatus shown in Figure 2.
[0034] Figure 8 is a rear, bottom, left side perspective view of the mixing head of the
fluid mixing apparatus shown in Figure 2.
[0035] Figure 9 is a bottom plan view of the mixing head of the fluid mixing apparatus shown
in Figure 2.
[0036] Figure 10 is a right side elevational view of the mixing head of the fluid mixing
apparatus shown in Figure 2.
[0037] Figure 11 is an enlarged detail view of an alternate embodiment of the support webs
to that shown in Figure 7, which view corresponds to the area circumscribed by circle
11 in Figure 7.
[0038] Figure 12 is an enlarged detail view of an alternate embodiment of the blade body
shown in Figure 7, which view corresponds to the area circumscribed by circle 12 in
Figure 7.
[0039] Figure 13 is a view similar to that of Figure 12, showing a further alternate embodiment
of the blade body.
[0040] Figure 14 is a front, top, left side perspective view of a fluid mixing apparatus
according to the preferred embodiment of the invention in use in a froth flotation
cell.
[0041] Figure 15 is a left side cross-sectional view of the structure of Figure 14.
[0042] Figure 16a is a side cross-sectional view of an alternate fluid mixing apparatus
to that shown in Figure 3, showing the fluid mixing apparatus mounted within a vessel
having baffles disposed therein.
[0043] Figure 16b is a top left perspective view of the alternate mixing head shown in Figure
16a.
[0044] Figure 16c is a bottom plan view of the alternate mixing head shown in Figure 16a.
[0045] Figure 17 is a partially exploded view showing an alternate mounting means and an
alternate shaft gripping means to those shown in Figure 4.
[0046] Figure 18 is a sectional view, along sight line 18-18 of Figure 17, with the apparatus
shown fully assembled.
[0047] Figure 19 is a perspective view of yet another alternate mounting means and an alternate
reciprocating drive assembly to those shown in Figure 4.
[0048] Figure 20 is a partially exploded perspective view of the mounting means and the
reciprocating drive assembly of Figure 19.
[0049] Figure 21 is a top, right perspective view of an alternate reciprocating drive assembly
to that shown in Figure 19.
[0050] Figure 22 is an partially exploded perspective view of the reciprocating drive assembly
of Figure 21.
[0051] Figure 23 is a top, right perspective view of an alternate reciprocating drive assembly
to that shown in Figure 19.
[0052] Figure 24 is a partially exploded perspective view of the reciprocating drive assembly
of Figure 23.
DETAILED DESCRIPTION OF A PREFERRED EMBODIMENT
[0053] Referring now to Figure 2 of the drawings, a fluid mixing apparatus, according to
a preferred embodiment of the present invention and designated with general reference
numeral 100, is shown in use with a fluid containing vessel 102 having a contiguous
sidewall 104 centered about and defining a longitudinal axis A-A. The fluid mixing
apparatus 100 is mounted to a frame 140 which spans over the vessel 102.
[0054] The fluid mixing apparatus 100 includes a mixing head 106 for immersion in the fluids
to be mixed; means 108 for mounting the mixing head 106 within the vessel 102; and
reciprocating means 110 for imparting reciprocating longitudinal (i.e. vertical) movement
to the mixing head 106.
[0055] Referring to Figure 7, the mixing head 106 includes: a blade body 112 formed about
a head axis H-H; a generally tubular hub member 114; and a plurality of support webs
116 for connecting the blade body 112 to the hub member 114.
[0056] As shown in Figure 8, the blade body 112 has a first end 120, an opposed second end
122 disposed in spaced relation thereto along the head axis H-H, and a passageway
123 extending longitudinally between the first and second ends 120 and 122. In the
preferred embodiment, the passageway 123 tapers uniformly from the first end 120 to
the second end 122 to impart a substantially frustoconical shape to the blade body
112.
[0057] The blade body 112 also has an inner surface 126 and an outer surface 128. The outer
surface 128 defines an inside blade diameter ID at the second end 122 of the blade
body 112, and an outside blade diameter OD at the first end 120 thereof. The actual
outside diameter OD may be between 25 and 40 percent of the internal diameter D of
the vessel.
[0058] The taper in the passageway 123 can be expressed as an angle α, where angle α is
the angle formed between a pair of axes X,X and Y,Y defined by, and coincident with,
the intersections of the outer surface 128 of the blade body 112 and a plane P-P coincident
with the head axis H-H, as shown in as indicated in Figures 9 and 10. The angle α
is greater than or equal to 90° and less than 180°. Preferably, the angle α is between
90° and 120°.
[0059] Whereas in the preferred embodiment, the passageway 123 tapers uniformly along its
length from the first end 120 to the second end 122 to define a substantially frustoconical
blade body 112, the passageway may be configured to define other blade body shapes.
For instance, the passageway can be configured to have different rates of taper therealong.
In an alternate embodiment shown in Figures 16a, 16b and 16c, there is shown a mixing
head 400 having a blade body 402. The blade body 402 includes a first end 404, a second
end 406 and a passageway 408 defined therebetween. The passageway 408 tapers in a
non-uniform fashion between the first end 404 and the second end 406. More specifically,
the blade body 402 is formed with a point of inflection 410 therein located between
the first end 404 and the second end 406. The passageway 408 tapers at first rate
from the first end 404 to the point of inflection 410, and at a second rate from the
point of inflection 410 to the second end 406. In the alternate embodiment shown,
the first rate of taper is less than the second rate of taper. However, this need
not be the case in all instances. In some applications, it may be desirable for the
first rate of taper to be greater than the second rate of taper.
[0060] In the preferred embodiment, the blade body 112 is constructed from six arcuate segments
118 arranged end-to-end. The segments are secured to one another by bolts (not shown)
fastened through flanges 124 provided at the ends of each segment 118 for this purpose
(see Figures 7, 8 and 9).
[0061] The hub member 114 is disposed generally coincident with the head axis H-H. Extending
substantially radially in a downwardly canted fashion from the hub member 114 is the
plurality of support webs 116. The support webs 116 connect the arcuate segments 118
of the blade body 112 to the hub member 114. Such connection is effected by rivets
or bolts (not shown).
[0062] Whereas in the preferred embodiment the blade body 112 and support webs 116 are substantially
smooth, in an alternative embodiment, one or both of the blade body and the support
webs could be formed with perforations or dimples. For instance, referring to Figure
12, there is shown an alternate blade body 412 having formed therein a plurality of
perforations 414 each extending between an inner surface 416 and an outer surface
418 thereof.
[0063] Figure 13 shows a blade portion 420 provided with a plurality of dimples 422 projecting
outwardly from an outer surface 424 of the blade portion 420 and inwardly from an
inner surface 426 of the blade portion 420. This allows fine tuning of the mixing
device in a manner not taught by the prior art.
[0064] In yet another alternate embodiment shown in Figure 11, a support web 430 is provided
with a plurality of perforations 432, as well as a plurality of tabs 434 each substantially
overlying a respective perforation 432. The tabs 434 are connected to the support
web 430 at one edge of said respective perforation 432 to form a gill. In this manner,
the characteristics of the mixing currents produced by the blade body in motion can
be finely tuned to control the droplet size of the dispersion, and hence the, mixing
efficiency of the device, which feature is not available in prior art mixers.
[0065] Referring now to Figure 3, the preferred mounting means 108 will be seen to include
a mixer shaft 130 for carrying the mixing head 106 and a linear bearing 132 adapted
to slidingly engage the mixer shaft 130.
[0066] The mixer shaft 130 has a bottom end 134 releasably mounted to the mixing head 106,
and a top end 136 operatively connected to the reciprocating means 110. The releasable
connection of the mixer shaft 130 to the mixing head 106 may be effected by threadingly
engaging the bottom end 134 of the mixer shaft 130 with the threaded interior of the
hub member 114. When mounted to the mixing head 106, the mixer shaft 130 extends substantially
coincident with the head axis H-H.
[0067] In the preferred embodiment shown in Figures 2 and 3, the mixing head 106 is mounted
to the mixer shaft 130 with the second end 122 of the blade body 112 being carried
below the first end 120 thereof. In an alternate embodiment, the orientation of the
mixing head could be reversed such that the first end of the blade body is carried
below the second tube end thereof.
[0068] As best shown in Figure 5, the mixer shaft 130 is preferably hollow and is constructed
of a plurality of tube segments 170, threaded at their ends and joined to one-another
in end-to-end relation by threaded couplings 172, so that segments 170 can be added
or removed as desired to accommodate for different depths of the vessel. The use of
a hollow mixer shaft leads to reduced energy consumption by the fluid mixing apparatus
during use. In contrast, conventional rotary-type mixers use heavy, solid shafts requiring
greater energy input.
[0069] The linear bearing 132 is a sleeve-type bearing mounted in surrounding relation to
the mixer shaft 130 for sliding engagement therewith during its reciprocating longitudinal
movement. The linear bearing 132 is securely fixed to a housing 138 supporting the
reciprocating means 110.
[0070] As best illustrated in Figure 4, the reciprocating means 110 includes a shaft gripping
means 142 for gripping the mixer shaft 130 adjacent its top end 136 and a reciprocating
drive assembly 144 operatively connected to the mixing shaft 130 to impart reciprocating
longitudinal movement to the mixing head 106.
[0071] With reference to Figures 4 and 5, the shaft gripping means 142 preferably includes
a clamp 163 formed by a pair of mating clamping blocks 164a and 164b. Each clamping
block 164a, 164b has a groove 166 formed therein which is sized and adapted for receiving
the shaft 130 in close fitting relation thereto. In the preferred embodiment, the
groove 166 is generally concave and has a semi-circular cross-section. When the clamping
blocks 164a and 164b are mated, the grooves 166 thereof are disposed in opposed relation
to each other to grippingly receive the mixer shaft 130 and captively retain the mixer
shaft 130 therebetween. Bolts 168 rigidly fasten the clamping blocks 164a and 164b
to each other and to the reciprocating drive assembly 144. Thus fastened, the clamping
blocks 164a and 164b transfer the reciprocating longitudinal movement of the reciprocating
drive assembly 144 to the mixer shaft 130 when the fluid mixing apparatus 100 is in
use.
[0072] This clamp arrangement permits the relative depth of the mixing head 106 in the vessel
102 to be conveniently adjusted from above; the clamp 163 need only be loosed, by
disengaging the associated bolts 168, whereupon mixer shaft 130 can be raised or lowered
as desired, and bolts 168 re-engaged.
[0073] As shown in Figures 4 and 5, the reciprocating drive assembly 144 includes: a flywheel
146; a drive 148 for driving rotation of the flywheel 146; a crank member 150 projecting
from the flywheel; a yoke 152 adapted and configured to receive the crank member 150
therewithin; and guide means 156 for guiding the yoke 152 along a yoke axis 153 for
reciprocating longitudinal movement. The flywheel 146, the drive 148, the crank member
150, the yoke 152 and the guide means 156 are operatively connected to, and co-operate
with, each other to form a scotch yoke assembly 143.
[0074] The flywheel 146 is mounted to the housing 138 for rotation about a rotational axis
R-R which is substantially normal to the longitudinal axis A-A. The drive 148 in the
nature of an electric motor, is operatively connected by its drive shaft (not shown)
to the flywheel 146 for driving rotation.
[0075] Projecting from the flywheel in a direction parallel to the rotational axis, is the
crank member 150. The crank member 150 is removeably attached to the flywheel 146
for rotation therewith. For the purpose of minimizing friction, the crank member 150
includes an inner axle portion 182 which is fixedly connected to the flywheel 146
and an outer roller portion 184 which is rotatably mounted by bearings (not shown)
on the inner axle portion 182 (see Figure 5).
[0076] The yoke 152 is mounted within the housing 138 for movement along a yoke axis 153
disposed substantially parallel to the longitudinal axis A-A. The yoke 152 is displaced
from the flywheel 146 in the direction of the crank member 150 and has formed therein
a substantially linear race 154 for receiving the crank member 150. The race 154 is
disposed within the yoke 152, substantially normal to both the rotational axis R-R
and the yoke axis 153. The race 154 is adapted and configured to allow translational
movement of the crank member 150 relative to the yoke 152 as the flywheel 146 rotates.
[0077] The guide means 156 includes upper and lower threaded guide shafts 158a and 158b
which are received in threaded, coaxial bores 156 disposed on upper and lower surfaces
of the yoke 152. Corresponding upper and lower guide bearings 160a and 160b are provided
on the housing 138 for slidingly engaging the upper and lower guide shafts 158a and
158b, respectively. During the reciprocating longitudinal movement, the upper guide
shaft 158a extends protrudes through an aperture (not shown) formed in the housing
about which the upper guide bearing 160a is mounted.
[0078] To counter stresses created on the yoke 152 by virtue of its carriage of the shaft
gripping means 142, the guide means 156 additionally include a balancing or stabilizing
shaft 174 and a pair of mating linear bearing blocks 176a and 176b fixed to the yoke
for sliding engagement with the stabilizing shaft 174. The stabilizing shaft 174 is
rigidly connected to the housing 138 and extends substantially parallel to yoke axis
153. Each linear bearing block 176a and 176b has a groove 178 of semi-circular cross-section
formed therein which is sheathed with a self-lubricating material such as polytetrafluorethylene.
When the linear bearing blocks 176a and 176b are mated, the grooves 178 thereof are
mounted in opposed relation one with the other with the stabilizing shaft 174 extending
longitudinally therebetween. Bolts 180 fasten the linear bearing blocks 176a and 176b
to the yoke 152.
[0079] The workings of the reciprocating drive assembly 144 are now explained in greater
detail below. With the yoke 152 operatively mounted with the upper and lower guide
shafts 158a and 158b disposed within the guide bearings 160a and 160b, the yoke 152
is mounted to the housing 138 in a manner which constrains movement of yoke 152 otherwise
than along the yoke axis 153 and normal to the rotational axis R-R. When the flywheel
is rotatively driven by the drive 148, the crank member 150 is caused to translate
linearly within the race 154 thereby urging the yoke 152 to move along the yoke axis
153 to effect longitudinal reciprocating movement of the mixer shaft 130, as indicated
by the sequence of Figures 6A-6D. In the result, the mixing head 106 carried by the
mixer shaft 130 is longitudinally displaced through a stroke length "S" with a duration
"T" for each cycle (where "S" is expressed in meters (inches) and "T" is expressed
in seconds (minutes)). For the sake clarity, a cycle consists of the upstroke and
downstroke movement of the mixing head 106. In Figure 3, the mixing head 106 is shown
in blackline in a starting position, and in phantom outline, at a position longitudinally
displaced from the starting position through the stroke length "S".
[0080] The length of the resultant stroke may be selected by suitable adjustment to the
radial position of the crank member 150 (that is, the distance between the crank member
150 and the rotation axis R-R). Accordingly, the flywheel 146 is provided with a plurality
of threaded sockets 162 disposed in a radial array on the face of the flywheel 146
(s. ee Figure 5). Each threaded socket 162 is sized and adapted to receive the crank
member 150 therein.
Each crank member and socket combination corresponds to a predetermined stroke length
"S". The duration "T" of each cycle may be selected by suitable adjustment of the
rotational speed of the drive 148.
[0081] By virtue of the reciprocating longitudinal movement imparted to the mixing head
106, a portion of the fluids in the vessel 102 is urged to flow through the passageway
123 defined in the blade body 112 thereby encouraging efficient mixing of the fluids
in the vessel 102. It has been found that mixing efficiencies tend to be improved
when the fluid mixing apparatus 100 is operated within a set of operational parameters
defined by the equation:
where:
OD is the outside diameter of the blade body 112 at the first end 120 thereof measured
in meters;
ID is the inside diameter of the blade body 112 at the second end 122 thereof measured
in meters;
S is the stroke length measured in meters; and
T is the duration of each cycle measured in seconds
where:
OD is the outside diameter of the blade body 112 at the first end 120 thereof measured
in inches;
ID is the inside diameter of the blade body 112 at the second end 122 thereof measured
in inches;
S is the stroke length measured in inches; and
T is the duration of each cycle measured in minutes) .
[0082] While the stroke length "S" can measure between 0,05 meter (2 inches) and 0,61 meter
(24 inches), it is preferred that the stroke length "S" be between 0,10 meter (4 inches)
and 0,41 meter (16 inches). More preferably, the stroke length "S" is between 0,20
meter (8 inches) and 0,30 meter (12 inches).
[0083] Moreover, while it has been found that improved mixing efficiencies may be obtained
where the value for OD:ID is greater than 1.0 and less than or equal to 1.7, preferably,
the value for OD:ID lies between 1.5 and 1.7.
[0084] When operated within the set of operational parameters defined above, it has been
found that the present invention can be used to great advantage as a mixer for a vessel
in a solvent extractor unit, as shown in Figures 2 and 3 and illustrated in Examples
1 and 2 below.
EXAMPLE 1
[0085] In the known application of the SXEW process previously described, samples were taken
from the outfall of each of the primary vessel; secondary vessel; tertiary vessel
and settling tank of a respective secondary extraction unit (A) and permitted to separate.
[0086] In a parallel secondary extraction unit (B) (ie processing a pregnant leachate of
substantially identical composition), a mixing apparatus in accordance with the present
invention (OD= 1,52 meter (60 inches); ID= 1,02 meter (40 inches); α=120 ; S= 0,25
meter (10 inches); T= 1,998 seconds (0.0333 minutes), driven by a 1492 watts (2hp)
motor) was substituted for the rotary mixer in the secondary mixing vessel, and samples
were again taken from the outfall from each of the primary, second and tertiary mixing
vessels, and from the settling tank, and permitted to separate.
[0087] Copper concentration (g/l) was measured in the organic component of each sample,
as follows:
|
(A) |
(B) |
|
|
0,014 cubic meters per second (30 cpm) |
|
Cu (g/l) |
Cu (g/l) |
Primary mixing vessel |
2.01 |
2.01 |
Secondary mixing vessel |
2.06 |
2.06 |
Tertiary mixing vessel |
2.12 |
2.13 |
Settling tank |
2.14 |
2.13 |
[0088] As would be expected, copper concentration from the primary mixing vessel in each
of the A and B lines is similar (because to that point in the process, mixing is provided
by identical rotary mixers). However, unexpectedly, copper concentrations in the outfall
from the secondary mixers also remained identical, and copper concentration in the
outfall from the settling tanks remained quite similar, despite the almost 70% reduction
in energy input (932,5 watts (1.25 hp) drawn from a 1492 watts (2 hp) drive motor
for the reciprocating mixer, as compared to 3730 watts (5.0 hp) drawn from the 5595
watts (7.5 hp) motor drive for the rotary mixer).
EXAMPLE 2
[0089] In a second test, the B line of Example 1 was modified by altering the motor speed
of the mixer of the present invention, such that it operated at 0,75 cycles/second,
i.e. T = 1,333 second (45 cycles/minute (T=0, 0222 minute)).
[0090] Copper concentration (g/l) was again measured, as follows:
|
(B) 0,021 cubic meters per second [45cpm] |
|
Cu (g/l) |
Primary mixing vessel |
2.00 |
Secondary mixing vessel |
2.08 |
Tertiary mixing vessel |
2.11 |
Settling tank |
2.16 |
[0091] Again, as would be expected, copper concentration from the primary mixing vessel
in the B line remained similar to that obtained in the A line (because to that point
in the process, mixing is provided by identical rotary mixers). However, unexpectedly,
copper concentrations in the outfall from the settling tank from the modified B line
showed significant improvement over the A line results (copper recovery improved from
2.14 g/l to 2.16 g/l).
[0092] Without intending to be bound by theory, it is believed the fluid mixing apparatus
of the present invention provides mixing currents which [at least in the context of
the liquids utilized in SXEW copper extraction] create a dispersion characterized
by consistent-sized droplets, uniformly distributed throughout the mixing vessel,
whereas in a rotary mixer, there is a wide variation in drop sizes, and in the distribution
of said drops, (perhaps due to the fact that the blade in a rotary mixer moves at
different speeds along its length). This uniform dispersion is believed to provide
an environment amenable to efficient mass transfer between phases, while at the same
time providing for substantial disengagement of the mixed phases within a relatively
short time frame.
[0093] Whereas the illustrations depict an embodiment of the present invention which is
preferred, various modifications are contemplated and described below.
[0094] In the preferred embodiment, the shaft gripping means 142 is adapted to allow the
clamping blocks 164a and 164b to be uncoupled from each other and detached from the
yoke 152 by merely removing the bolts 168. It will be appreciated, however, that in
some instances it may not be desirable to completely detach the clamp from the yoke
when releasing the mixer shaft. In such instances, it would be preferable to uncouple
the clamping blocks while still maintaining a rigid connection between one of the
clamping blocks and the yoke. In the alternate embodiment shown in Figures 17 and
18, this is achieved by replacing clamp 163 with a modified clamp 186. While the clamp
186 is generally similar to the clamp 163 in that it has a pair of mating clamping
blocks 188a and 188b formed with concave grooves 190 therein, it differs in one material
respect, that is, the clamping block 188a is fastened to the yoke 152 by bolts 192,
independently of clamping block 186. Mating of the clamping blocks 188a and 188b is
achieved by fastening bolts 194.
[0095] While in the preferred embodiment the mounting means 108 includes a single linear
bearing 132 which slidingly engages the mixer shaft 130 at a single location, in an
alternate embodiment a linear bearing assembly could be provided for sliding engagement
with the mixer shaft at more than one location. One such alternate embodiment is shown
in Figures 17 and 18, where a mixer shaft designated with reference numeral 196 and
a linear bearing assembly is designated with reference numeral 200. The linear bearing
assembly 200 includes an upper bearing subassembly 202 and a lower bearing subassembly
204 for engagement with the mixer shaft 196 at respective upper and lower, longitudinally
spaced, locations 206 and 208, respectively.
[0096] The upper bearing subassembly 202 is adapted and configured for sliding engagement
with the mixer shaft 196. More specifically, it has a bushing 210 formed of mating
bushing blocks 212a and 212b disposed in surrounding relation to the mixer shaft 196.
Each bushing block 212a, 212b has a concave groove 214 of semi-circular cross-section
formed therein for receiving the mixer shaft 196. Each groove 214 is sheathed or lined
with an arcuate pad 216 of self-lubricating material such as polytetrafluorethylene.
Preferably, each pad 216 is ribbed. When the bushing blocks 212a and 212b are mated,
the grooves 214 thereof are mounted in opposed relation one with the other with the
mixer shaft 196 extending longitudinally therebetween. The bushing blocks 212a and
212b are securely attached to each other by bolts 218. The bushing 210 is operatively
connected to the housing 138 by securely mounting bushing block 212a to a base 207
of the housing 138.
[0097] The lower bearing subassembly 204 is adapted and configured for rolling engagement
with the mixer shaft 196. The lower bearing subassembly 204 includes at least two
roller assemblies identified generally as 220, carried below the base 207 of the housing
138 at the lower location 208. However, preferably, the lower bearing subassembly
204 has first, second and third roller assemblies respectively, 222, 224 and 226,
mounted in surrounding relation to the mixer shaft 196. A first mounting member in
the nature of tubular support 228 attaches the first and second roller assemblies
222 and 224 to the base 207 of the housing 138. The tubular support 228 depends downwardly
from the base 207 and terminates at its distal end with a flange member 230. The flange
member 230 has a pair of upstanding brackets 232 to which are fastened the first and
second roller assemblies 222 and 224 by bolts 234.
[0098] The lower bearing subassembly 204 also includes a second mounting member in the nature
of a pair of removable supports 236. The removable supports 236 are securely attached
to the bushing block 212a and depend downwardly therefrom to a terminus 238. The terminus
has a bracket 240 which extends downwardly therefrom. The third roller assembly is
secured to the bracket 240 by bolts 242.
[0099] In the preferred embodiment, each roller assembly 222, 224 and 226 includes a single
roller 239 rotatively mounted to a roller housing 241. It will be appreciated that
in alternate embodiments multiple rollers may be employed.
[0100] When the bushing blocks 212a and 212b are operably secured to each other, the first,
second and third roller assemblies 222, 224 and 226 circumferentially surround the
mixer shaft 196, as shown in Figure 18, at a position beneath and longitudinally spaced
from bushing 210. The support provided by the first, second and third roller assemblies
222, 224 and 226 at the lower location 208 tends to limit flexure of the mixer shaft
196, while permitting reciprocating longitudinal movement thereof.
[0101] As best shown in Figure 17, the mixer shaft 196 can be removed from the housing 138
for servicing, maintenance, repair or replacement by first disassembling the upper
bearing subassembly 202 and then by disengaging the clamp 186. The removal of bolts
218 in bushing 210 allows the bushing block 212b and the third roller assembly 226
attached thereto, to be removed from sliding engagement with the mixer shaft 196.
Bolts 194 can then be removed from clamp 186 thereby releasing the mixer shaft 196.
An open-ended rebate or slot 244 formed along an outermost edge of the base 207 permits
the mixer shaft 196 to be displaced laterally from the base for ease of removal. To
further facilitate handling of the mixer shaft 196 once released, the mixer shaft
196 is formed with an upper enlarged end portion 246, in which is provided a threaded
bore 248, to receive a threaded lifting lug (not shown).
[0102] With reference to Figures 19 and 20, there is shown an alternate mounting means 250
and an alternate reciprocating drive assembly 252. The mounting means 250 generally
resembles the mounting 108 in that it includes a mixer shaft 254 and a linear bearing
256. The mixer shaft 254 is generally similar to mixer shaft 130, but differs in that
it has an enlarged shaft head 258 provided with a support flange 259. When operatively
connected to the shaft gripping clamp 260, the support flange 259 of the mixer shaft
254 abuts clamping blocks 262 and 264 thereby providing an additional mechanical connection
to the frictional connection effected by the clamping blocks 262 and 264.
[0103] The linear bearing assembly 256 includes a sleeve-type linear plain bearing 266 mounted
in surrounding relation to the mixer shaft 254. The plain bearing 266 is secured to
the base 207 of the housing 138 by fasteners 268. A keyhole-shaped slot 270 formed
along an outermost edge of the base 207 permits the mixer shaft 254 to be displaced
laterally from the base 207 during removal thereof. By virtue of the use of the plain
bearing 266, it will however be evident that, in order to remove the mixer shaft 244,
the plain bearing 266 must first be detached from the housing 138, by removing fasteners
268.
[0104] The reciprocating drive assembly 252 is generally similar to the reciprocating drive
assembly 144 described above in that it has a flywheel 272, a drive 274, a crank member
276, a yoke 278 and guide means 280 operatively connected to form a scotch yoke assembly
282. However, whereas guide means 156 of reciprocating drive assembly 144 includes
upper and lower guide shafts 158a and 158b, corresponding upper and lower guide bearings
160a and 160b and a single stabilizing shaft 174 with mating linear bearing blocks
176a and 176b, the guide means 280 employs a pair of parallel left and right guide
assemblies in the nature of first and second linear slide assemblies 284 and 286.
The first and second linear slide assemblies 284 and 286 are operatively connected
to the housing 138 and to the yoke 278 for sliding engagement therewith along a pair
of guide axes 288 and 290 extending substantially parallel to a yoke axis designated
as 292. The first and second linear slide assemblies 284 and 286 are laterally spaced
from each other with the yoke 278 substantially disposed therebetween.
[0105] Each linear slide assembly 284, 286 includes a guide rail member in the nature of
a track 294 associated with at least one corresponding guide rail following member
in the nature of a saddle member 296. Each track 294 is fixedly secured to a support
member 298 of the housing 138 coincident with a respective guide axis 288 or 290,
as the case may be. Each saddle member 296 is adapted and configured for sliding motion
along its corresponding track 294.
[0106] The linear slide assemblies 284 and 286 are additionally provided with saddle mounting
members 300 for attaching the saddle members 296 to the yoke 278. The saddle mounting
members 300 are generally T-shaped members mounted between a pair of transverse yoke
beams 301 and 303 to define a race 306 formed in the yoke 278. The saddle members
296 are in turn mounted to the back of the saddle mounting members 300 in opposed
relation to the track 294. Thus attached, the saddle members 296 bound on either side
the race 306. Looking into the direction of arrow 307 (shown in Figure 19), it can
be seen that the linear bearing assemblies 284 and 286 are located aft of the yoke
278.
[0107] In the alternate embodiment shown and described above, each linear slide assembly
284, 286 is provided with two, longitudinally-spaced, saddle members 296 for improved
stability; an upper saddle member 308 and a lower saddle member 310.
[0108] It will be appreciated that other alternative track and saddle member arrangements
may be constructed. Referring to Figures 21 and 22, there is shown an alternative
reciprocating drive assembly 350 generally similar to reciprocating drive assembly
252. The reciprocating drive assembly 350 has,
inter alia, a yoke 352 and track-and-saddle type, linear slide assemblies 354 and 356. The linear
slide assemblies 354 and 356 are generally similar to the linear slide assemblies
284 and 286 in that each assembly 354, 356 includes a track 358 associated with at
least one corresponding saddle member 360. However, the assemblies 354 and 356 differ
in that they are fabricated with the saddle members 360 already captively retained
on the tracks 358 for sliding engagement therewith. The yoke 352 differs from yoke
278 shown in Figure 19 and 20 in that it is of unitary construction and has saddle
mounting portions 362 incorporated therein.
[0109] Alternate configurations of a reciprocating drive assembly having dual linear slide
assemblies, are also possible. Referring now to Figures 23 and 24, there is shown
a reciprocating drive assembly 312 generally similar to the reciprocating drive assembly
252 described above. The reciprocating drive assembly 312 includes a flywheel 314,
a drive 316, a crank member 318, a yoke 320 and guide means 322 operatively connected
to form a scotch yoke assembly 324. The guide means 322 is similar to the guide means
280 in that it also uses a pair of parallel, longitudinally extending, left and right
guide assemblies. However, whereas the guide means 280 employs a pair of tracks 294
each associated with at least one saddle member 296, the guide means 322 uses a Thompson
shaft arrangement, that is, a pair of guide posts 326 each associated with at least
one linear sliding block 328.
[0110] Each guide post 326 is mounted within the housing 138 to extend upwardly between
the base 207 and a top plate 332 thereof. The guide posts 326 are secured to the base
207 by collar members 330 and fasteners (not shown). Each linear sliding block 328
is mounted in surrounding relation to its associated guide post 326 for sliding engagement
therewith. As with the linear assemblies 284 and 286, the mounting members 333 attach
the linear sliding blocks 328 with the yoke 320. However, in this embodiment, the
linear slide assemblies (consisting of guide posts 326 and linear sliding blocks 328)
are located fore of the yoke 320.
[0111] While the reciprocating drive assembly 318 operates in a generally similar fashion
to the reciprocating drive assembly 252, the manner in which the flywheel 314, the
crank member 318 and the yoke 320 co-operate with each other differs. Unlike crank
member 276, the crank member 318 does not have an inner axle fixedly connected to
the flywheel with an outer roller portion rotatably mounted thereon. The crank member
318 is embodied in a cam follower block 334 adapted and configured for sliding movement
within the race 335 defined in the yoke 320. The cam follower block 334 is preferably
made of steel and houses therein a roller bearing 336 and an axle 338 rotatively mounted
to the roller bearing 336. The axle 338 is received in socket 340 formed in the flywheel
314. Brass wear plates 342 are fastened to the top and bottom surfaces of the cam
follower block 334 for improved wear resistance. When the cam follower 334 is mounted
within the race 336, the brass wear plates 342 bear against hard steel wear plates
(not shown) lining the race 335.
[0112] While in the preferred embodiment, a scotch yoke apparatus is utilized to provide
linear reciprocating movement, it will be evident that other mechanisms, such as crank
shafts, cam and cam follower mechanisms, and swash plates are possible substituents
therefor.
[0113] Of course, whereas the detailed description herein pertains specifically to the recovery
of copper from copper bearing ores, it should also be understood that the present
invention may be utilized in other applications wherein SXEW processes are utilized,
such as, for example, in the recovery of zinc, nickel, platinum, uranium and gold.
[0114] Moreover, it will be evident that the invention may have advantageous utility even
outside the SXEW process, in other mixing applications, such as in the context of
a froth flotation cell, illustrated in Figures 14 and 15, wherein the fluid mixing
apparatus is used to agitate a slurry to form a froth, and a paddle mechanism 32 is
operatively mounted to the vessel 102 to scour froths produced thereby.
[0115] As shown in Figure 16a, the fluid mixing apparatus can also be employed in a vessel
having baffles 500 disposed therein.
[0116] It will, of course, also be understood that various other modifications and alterations
may be used in the design and manufacture of the mixing apparatus according to the
present invention without departing from its spirit and scope. Accordingly, the scope
of the present invention should be understood as limited only by the accompanying
claims, purposively construed