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Патент USA US3033486

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May 8, 1962
F. w. BRADWELL
3,033,476
ORE AND STONE JAW CRUSHING MACHINES
Filed Nov. 8, 1960
2 Sheets-Sheet 2
/4A 32 30 29 /8
B
wm?lz, 141M411“Attorneys
WM
nitel Stats
1
1
3,833,476
Fatented May 8, 19%2
2
' centric ratio of 2:1 may be driven at 11/2 times the speed
3,033,476
ORE AND STONE .IAW CRU?HING MACHINES
Frederick W. Bradwell, 91 St. Thomas Road,
Sheffield, England
Filed Nov. 8, 1960, Ser. No. 68,604
Claims priority, application Great Britain Nov. 17, 1959
7 Claims. (Cl. 241—219)
of a conventional machine before choking occurs. Thus,
the output may be increased by up to 50% of that of
a conventional machine of similar dimensions. Although
with this ratio between the eccentrics a slight partial re‘
closing of the jaws will occur, during the open period,
owing to precession of the eccentrics relative to each
other this is not considered detrimental since it will
produce a slight vibration of the movable jaw whilst in
This invention relates to machines for crushing stone,
ore and the like, and more particularly to crushing ma 10 open position, which vibration will assist in discouraging
any tendency to choking during the downward move
chines of the type in which a movable jaw is vibrated
ment of the material undergoing crushing.
with respect to a ?xed jaw by means of an eccentric,
One eccentric may be mounted on the other, the latter
whether the eccentric carries a rocker arm bearing the
rotatable as a shaft, with a common driving shaft con
movable jaw, or the movable jaw is mounted on a rocker
arm connected by toggle plate mechanism to the ec 15 nected to the respective eccentrics by two pairs of pinions
of such respective ratios that'one eccentric is rotated at
centric.
twice the speed of the other. By carryingeccentrically
Although an increase in the frequency of vibration of
on the driving shaft the pinion that serves to drive the
the movable jaw results in an increase in the crushing
eccentric that is mounted on the other eccentric, and with
rate, alirnit to the output of the machine is reached
the pinion equalling the eccentricity of that other eccen
when the jaws are opened for an insufficient time for the
tric, circular pinions may be used for the eccentrically
crushed material to fall under gravity, so that the ma
carried pinion and the pinion with which it meshes, in
chine becomes choked.
spite of the eccentric motion imparted to the driven pin
The object of the present invention is to provide a
ion of the pair. Consequently, with the mere provision
crushing machine in which the time that the jaws are
opening and opened is increased beyond the 50% at 25 of one pinion being carried eccentrically on the driving
shaft, two pairs of circular pinions suiiice for the driving
tainable out of the complete cycle time of a conventional
of the two eccentrics at the required 2:1 difference of
machine of the type referred to.
According to the present invention, a crushing ma
speed.
The eccentric mounted on the other eccentric serves
chine has a jaw movable with respect to a ?xed jaw and
to operate directly a rocker arm bearing the movable
adapted to be driven differentially by two eccentrics, with
jaw, or a rocker arm that moves that jaw through toggle
one of the eccentrics rotatable at twice the speed of the
other and so phased with respect to the other eccentric
mechanism.
The invention will now be further described with ref
that the jaws are maintained substantially fully open for
erence to the accompanying drawings, in whicha period between successive opening and closing move
35 . FIGURES 1 to 8 are diagrams of jaw movements and
ments of the movable jaw.
of eccentric drives by which those movements are pro
This result arises from the phasing causing the throws
duced, the amplitudes of the curves in FIGURES l, 3,
of the two eccentrics to be in conjunction at every other
5 and 7 being shown to a greater scale than the eccen
revolution of the faster eccentric (providing the “fully
closed” position of the moving jaw) and in opposition
tricities in FIGURES 2, 4, 6 and 8 that produce these
at alternate revolutions of the faster eccentric (providing 40 amplitudes,
substantially the “fully opened” position of the movable
FIGURES 1 and 2 relating to the usual form of single
jaw), and because the phasing also causes the throws to
eccentric drive, FIGURES 3 and 4 and FIGURES 5
move rapidly out of conjunction after fully closed posi
and 6 relating to the individual effects of two eccentric
tion, and similarly rapidly into conjunction before the
drives of different throw and frequency, and FIGURES
next fully closed position. Thus, the combined period 45 7 and 8 relating to the combined effect of these two ec
in which the jaws are opening and remain open conside
erably exceeds the 50% attainable out of the complete
cycle of time of a conventional machine driven by a sin
gle eccentric and, therefore the speed of the machine
may be increased proportionally before the machine be
comes choked. Also, as a consequence of the increased
centric drives as combined in carrying out the invention;
FIGURE 9 is a part-sectional side elevation of one
form of crusher using the combined eccentric drive;
FIGURE 10' is a plan of FIGURE 9; and
FIGURE 11 is a part~sectional side elevation of an
other form of crusher using the combined eccentric drive.
In FIGURE 1, the curve 1 shows the amplitude 2 of
movement resulting in the moving jaw of a crusher ac—
tuated by a single eccentric 3 (FiGURE 2) of eccen
speed, in conjunction with the rapid movement of the
eccentric throws in moving the movable jaw to fully
closed position, the closing time is decreased, so that the
impact of the movable jaw on the material to be crushed 55 tricity 4, the movement of this amplitude (or “throw,”
is increased, which makes the machine particularly suit
amounting to twice the eccentricity) taking place once
able for crushing hard materials.
'
in each revolution. The effect through two successive
The eifective amount of ‘movement between “fully
revolutions O—I-—II is shown in FIGURE 1.
closed” and “fully open” positions may be made sub-v
. In FIGURE 3, the curve 5 resembles the curve 1 of
stantially equal to the throw of the slower eccentric, so' 60 FIGURE 1, but has a reduced amplitude (or “throw”)
that in effect the faster eccentric modi?es the time/move
ment curve of the slower eccentric to shorten the time
6 because of its production by an eccentric 7 (FIGURE
4) of correspondingly less eccentricity 8. Again, the
occupied by the closing and opening of the movable jaw.
etfect through two successive revolutions O—I--II is
Preferably the throw of the slower eccentric is so much
shown in FIGURE 3.
greater than the throw of the faster eccentric, e.g. twice 65
In FIGURE 5, the curve 9 of amplitude (or “throw”)
that the combined opening and open period occupies sub
10 is produced by an eccentric 11 (FIGURE 6) of eccen
stantially 75% of the cycle time between successive
tricity 12 approximately twice the eccentricity of 8 of the
closed positions.
eccentric 7 and rotating at one-half thevspeed of the ec
There being one opening movement in a complete cycle
which in duration is equivalent to two complete cycles 70 centric 7. Consequently, when the eccentric 7 has made
one revolution, the eccentric 11 has made one-half revolu
of the simple eccentric drive of a conventional machine,
tion only, O—-I--II in FIGURE 5 now representing one
a machine according to the invention and having an ec
essence
1%
pulley 20 on a shaft ‘21 journalled in and extending be
full revolution or “cycle” of the eccentric 11 whilst the
eccentric 7 is making two successive revolutions or “cy
tween the side plates 22 (one only shown) of the frame
serves to drive two gears 23, 24 secured to the shaft and
cles.” In consequence, the throws of the eccentrics 7,
meshing respectively with gears 25, 26, such that the gear
11 are sometimes in conjunction and sometimes in op
position, with the result that, as shown by the curve 13 91 ratio 23:25 is twice the gear ratio of 24:26, the ratio be
tween the gears 23, 25 being 121. The gear 25 is thus
in FIGURE 7, some 75% of the duration of two complete
driven at twice the speed of the gear 26. The gear 25
cycles of the eccentric 7 of smaller eccentricity is oc
'rotates ‘a shaft 28 journalled on the side plate '22, this
cupied by ?rst a resultant rapid opening movement A-—B,
shaft being eccentric over its length 29 extending across
and second a substantial maintenance of the resultant
opening B—vC, C-D, leaving some 25% only for the 10 the frame, to constitute one of the eccentrics participating
in the drive of the movable jaw 14. The eccentric length
resultant rapid closing movement D——E. The total am
29 carries an eccentric sleeve 30‘ connected to the gear 26.
plitude 10A between “open” and “closed” remains much
This sleeve 30 constitutes the other eccentric for driving
the same as the amplitude 10" due to the eccentric 11
the jaw 14. The gear 24 that meshes with the gear 26
(FIGURES 5 and 6).
is mounted, as shown at 31, on the drive shaft 21, with
FIGURE 8 shows at (a) . . . (e) the relative posi
an eccentricity equal to and in phase with the eccentric
tions of the eccentrics 7, 11 corresponding to the posi
length 29 of the shaft 28, such that as the maximum throw
tions A . . . E of FIGURE 7, from which it will be
of the gear 24 is towards the shaft 28, the throw of the
seen that at C, i.e., halfway through the complete cycle
eccentric length 29 has moved the gear 26 corresponding
A——E of the operation of the two eccentrics, the eccen
ly awayfrom the shaft 21. The axes of the gears 24,
trics are in opposition, with the result that at 13A there
26 thus remain separated by a constant horizontal dis
is a partial re~closing movement between positions 135
tance, so that the gears always remain in mesh.‘ The
of mam'mum opening movement that arise just before and
‘actual distance between these two axes varies slightly at
just after the eccentrics occupy the relative positions of
FIGUlsES 8(1)) and 8((1’) respectively.
different positions in the relative rotations of the gears 24,
As compared, therefore, with the operation of a con 25 126, because of the vertical components of the eccentric
movements, but not sufficiently to affect materially the
ventional single eccentric, as FIGURES l and 2, with the
meshing ofthe gears, which thus can be truly circular
crusher jaws opening and open for only 50% of each
gears. However, the pro?les of either or both of the
cycle, O-—I, I—II, the combined use of eccentrics as in
gears 24, 26 could depart suf?ciently from the circular to
FIGURES 3 to 6 results in the jaws undergoing opening
and remaining open for 75% of each cycle O—Il. Each 30 compensate fully for the slight variation that occurs in
the distance between the axes.
cycle O-II may thus be performed some 50% faster
The eccentric sleeve 30 carries a sheave 32, which
‘than each cycle O-l or L411, i.e. the larger throw ec
forms with the movable jaw 14 a pitman or rocker arm
centric 11 of the combination 7, 11 may be driven some
by which that jaw is moved relatively to the ?xed jaw 15
50% faster than the conventional single eccentric 3, the
smaller throw eccentric '7 of the combination being of 35 about an end of the toggle plate 18 as a pivot. The ec
centric length 29 of the shaft 28 corresponds to the ec
course driven at twice the speed of the eccentric 11. (It
centric 7 of FIGURES 3 and 4 performing t-wo revolu
is to be noted that the longitudinal scales of FIGURE 1
tions for each revolution of the eccentric sleeve 30, come
and of FIGURES 3, 5, and 7 do not attempt to relate the
sponding to the eccentric 11 of FIGURES 5 and 6. The
the relative rates of operation of the conventional single
eccentric and of the combined eccentrics according to the 40 movable jaw 14 thus performs a movement correspond
ing to the curve 13 of FIGURE 7.
invention: to do this, the dimension O—-II in FIGURES
The combined maximum throws of the eccentric length
3, 5, and 7 would have to be reduced to two-thirds of
29 and the eccentric sleeve 30 are in a plane that includes
either dimension O—I or I——II in FIGURE 1).
the axes of the parallel shafts 21, 28, i.e., in the approxi
The movement imparted to the movable jaw of a
mately horizontal direction of movement of any part of
crusher by the combined eccentrics 7, 11 is such that,
the jaw plate 14A with respect to the jaw plate 15A.
after the crushing blow has been strucl; by the closing
In FIGURE 11, a movable jaw 33, suspended at 34-, is
movement ending at A in FIGURE 7, the jaw rapidly opens
moved with respect to a ?xed jaw 35 by a rocker ‘arm ‘36
to 13B, and crushed material descends by gravity in the
operating between two toggle plates 37 and integral with
space between the jaws. The movable jaw then effects
the partial closing movement at 13A before receding to 50 an eccentric sheave 38 corresponding to the sheave 32 of
FIGURES 9 and 10. Similar ?xed shafts, gears, and
the second fully open position 1313, the result of this be
ing to discourage choking by displacing the crushed pieces
from any interlocking positions they may assume during
their descent by gravity. Thus, the combined eccentrics
not only make available a bigger proportion of the faster
cycle O——II during which the proportionately greater
eccentric shaft are used (the same reference numerals as
in FIGURES 9 and 10 being employed), but the com
bined maximum throw of the eccentric length 29‘ of the
shaft 28 and the eccentric sleeve 30 are in a vertical plane
through the axis of the shaft 28, this movement being
transferred by the rocker arm 36 and the toggle plates 37
throughput of material may descend between the jaws:
into ‘the desired generally horizontal movement of the
they also impart a vibration to encourage that descent.
jaw 33.
'
I
FIGURES 9 and 10 and FIGURE 11 show respectively
What I claim is:
two applications of the above-described combination of 60
1. Ore and stone crushing machine comprising a ?xed
eccentrics to the two well-known types of machine in,
jaw and a movable jaw, together with a pivot suspension
which the movable jaw is directly driven at the pivot from
for the movable jaw and jaw-moving means in operative
which it depends, and in which the movable jaw simply
connection with the movable jaw to swing it about the
‘depends from a pivot and is indirectly driven from a
pivot suspension towards and away from the ?xed jaw,
rocker arm or pitman that is driven at the pivot from which
the jaw-moving means including an inner eccentric and
it itself depends, the rocker arm operating two toggle
an outer eccentric mounted on and rotatable about the
plates, one of which bears on the frame of the machine
inner eccentric, means for driving the second eccentric,
and the other on the movable jaw.
and means for driving the inner eccentric at twice the
In FIGURES 9 and 10, a movable jaw 14, with jaw 70 speed of the outer eccentric.
plate 14A, is urged away from a frame plate 15, with
2. Ore and stone crushing machine comprising a ?xed
a plate 15A forming a ?xed jaw, by a tension rod 16 and
jaw and a movable jaw, a pivot suspension for the movable
spring 17 to keep the jaw 14 in bearing with one end of
jaw, an inner eccentric in the pivot suspension, an outer
a toggle plate 18, the other end of which bears on a
eccentric mounted on and rotatable about the inner eccen
rear plate 19‘ of the frame of the crusher. A driving
tric, means for driving the second eccentric, and means
3,033,476
5
6
for driving the inner eccentric at twice the speed of the
jaw, a movable jaw, a transverse pivot suspension for the
outer eccentric.
3. Ore and stone crushing machine comprising a ?xed
movable jaw, a second transverse pivot connection, a
rocker arm mounted to rock about the second suspen
sion, ‘an inner eccentric in the second suspension, a ?rst
pinion secured to the inner eccentric, an outer eccentric
mounted on and rotatable about the inner eccentric, a
second pinion secured to the outer eccentric, a transverse
jaw and a movable jaw, together with a pivot suspension
for the movable jaw, a rocker ‘arm in operative connec
tion with the movable jaw to swing it towards and away
from the ?xed jaw, va pivot suspension for the rocker
arm, a ?rst eccentric in the pivot suspension for the rocker
driving shaft, and two pinions secured to the driving shaft
and meshing constantly with the pinions secured to the
the inner eccentric, means for driving the second eccen 10 inner and outer eccentrics respectively, the driving ratio
between the pinion meshing with the ?rst pinion and that
tric, and means for driving the inner eccentric at twice
?rst pinion being twice the driving ratio between the
the speed of the outer eccentric.
pinion meshing with the second pinion and that second
4. Ore and stone crushing machine comprising a ?xed
arm, an outer eccentric mounted on and rotatable about
pinion, and connecting means between the rocker arm
jaw, ‘a movable jaw, a transverse pivot suspension for the
movable jaw, an inner eccentric in the pivot suspension, 15 and the movable jaw.
a ?rst pinion secured to the inner eccentric, an outer eccen
7. Ore and stone crushing machine as in claim 6, com
tric mounted on and rotatable about the inner eccentric,
a second pinion secured to the outer eccentric, ‘a trans~
verse driving shaft, and two pinions secured to the driv
prising an eccentric mounting on the driving shaft of the
to the inner and outer eccentrics respectively, the driving
lar and maintained in constant mesh by the equal eccen
pinion that meshes with the ?rst pinion, the eccentricity
of that mounting being equal to ‘and in phase with that of
ing shaft and meshing constantly with the pinions secured 20 the inner eccentric ‘and the two pinions each being circu
tricity and the phasing of the pinion mounting on the
ratio between the pinion meshing with the ?rst pin-ion
driving shaft and of the inner eccentric.
and that ?rst pinion being twice the driving ratio between
the pinion meshing with the second pinion and that sec
References Cited in the ?le of this patent
25
ond pinion.
5. Ore and stone crushing machine as in claim 4, com
prising an eccentric mounting on the driving shaft of the
pinion that meshes with the ?rst pinion, the eccentricity
of that mounting being equal to and in phase with that of
the inner eccentric and the two pinions each being circu 30
UNITED STATES PATENTS
tricity and the phasing of the pinion mounting on the
driving shaft and of the inner eccentric.
393,440
548,179
578,357
962,998
965,830
2,257,388
Low _________________ __ Nov. 27,
Bunnell ______________ __ Oct. 22,
Pfouts _______________ __ Mar. 9,
Christ et a1 ____________ __ June 28,
Mitchell _____________ __ July 26,
Krider _______________ __ Sept. 30,
6. Ore and stone crushing machine comprising a ?xed
2,605,051
Bogie ________________ .._ July 29, 1952
lar and maintained in constant mesh by the equal eccen
1888
1895
1897
1910
1910
1941
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