Abstrict A vibrating cone crusher which crushes material between a cone
and a frustoconical ring located therearound. An annular frame supports
the ring and a device for generating circular vibrations in a horizontal
plane. Tie rods connect the frame to a cone holder. Vertical vibration
that disrupts crusher operation is reduced or neutralized by positioning
the center of gravity of the cone, the cone holder, the frame, and
items supported thereon adjacent the plane of vibratory forces.
Claims We claim:
1. A vibrating crusher comprising:
a cone;
a ring surrounding said cone, said cone and said ring each having
a vertical axis;
an annular frame bearing said ring;
a means of generating circular vibrations in a horizontal plane;
a cone support supporting said cone;
a plurality of tie bolts connecting said annular frame to said
cone support, said plurality of tie bolts having respective connections
with said annular frame and said cone support adapted to permit
horizontal relative movements of said annular frame and of said
cone support; and
a plurality of elastic members adapted to support said annular
frame on an underlying surface, said annular frame and said cone
and said cone support each having a center of gravity located in
said horizontal plane of said means of generating circular vibrations
or located within a space defined by two parallel planes at a distance
from said horizontal plane equal to .+-.15% of a maximum diameter
of said cone.
2. The crusher according to claim 1 wherein said centers of gravity
are within a sphere the center of which is located at a point defined
by an intersection of the vertical axis of the cone and of the horizontal
plane when the crusher is idle and a diameter of the sphere is equal
to 15% of the maximum diameter of the cone.
3. The crusher according to claim 1 wherein the annular frame comprises
a skirt surrounding the cone support, said elastic members being
placed between the bottom of the skirt and the underlying surface.
4. The crusher according to claim 1 wherein the annular frame comprises
a skirt surrounding the cone support, said elastic members being
placed between said cone support and the underlying surface.
5. The crusher according to claim 3 wherein other elastic members
connect the cone support to the skirt.
6. The crusher according to claim 1 wherein a weighted cap is
fixed to an apex of the cone.
7. The crusher according to claim 3 wherein the skirt is provided
with weights.
8. The crusher according to claim 1 wherein the cone is mounted
rotatably on a vertical shaft fixed to the cone support, the cone
being mounted via bearings on a shouldered sleeve adapted to slide
along the vertical shaft, the shaft having a shoulder arranged such
that a tight chamber is formed inside the sleeve between the shoulder
of the shaft and of the sleeve, a channel being formed in the shaft
and adapted to supply said chamber with pressurized liquid.
9. The crusher according to claim 1 wherein the annular frame
is constituted by a bottomless vessel, the ring being fixed therein,
said annular frame further comprising:
a base on which is mounted the means for generating; and
a skirt fixed at an upper end thereof on an edge of the base.
10. The crusher according to claim 9 wherein the means for generating
is constituted by unbalanced shafts each having a vertical axis,
each shaft bears two imbalanced weights disposed on either side
of the base in such a way that the vibration forces generated by
a rotation of the unbalanced shafts are located in a horizontal
plane coinciding with or adjacent to a median plane of the base.
11. The crusher according to claim 1 wherein the means for generating
is constituted by imbalance shafts having vertical axes coupled
to one another and to a motor by a mechanical drive system in which
is incorporated a phase shifting device, said phase shifting device
comprising a rotary element coupled directly to one of the imbalance
shafts, at least one other imbalance shaft being coupled to the
rotary element or to the body of the jack, respectively, by a pulley
and belt drive system.
Description VIBRATING CONE CRUSHER
1. Technical Field
The present invention relates to vibrating cone crushers in which
the material is crushed between a cone and a frustoconical ring
surrounding the cone, the axes of the cone and of the ring being
vertical, and which include an annular frame bearing the ring, which
is fixed in the central opening in the frame, and a device suitable
for generating circular vibrations in a horizontal plane, a support
for the cone, and several tie bolts connecting the frame and the
cone support, the links between, on one hand, the ends of the tie
bolts and, on the other hand, the frame and the cone support, respectively,
being designed to allow horizontal relative movements of the frame
and of the support; the assembly constituted by the frame, the members
that it bears, the cone and its support rest on a bedplate or on
the ground via elastic members: springs or rubber shock absorbing
pads.
2. Background Art
It has been found that, in these crushers, the vibrating device,
constituted, for example, by shafts with imbalance masses, or imbalance
shafts, having vertical axes, generates not only horizontal vibrations
of the frame bearing the ring, and of the cone support, when the
crusher is in operation, but also vertical vibrations, the amplitude
of which increases from the center towards the periphery of the
crusher. These vertical vibrations have the harmful effects of changing
the flow of materials in the grinding chamber, and of setting up
stresses that are prejudicial to the mechanical strength of the
crusher components, these stresses, due to the vertical accelerations,
being all the greater the larger the crusher; such vertical vibrations
can also be transmitted to the baseplate or to the foundations,
which is inconvenient, and sometimes even dangerous. These vibrations
also make the process unstable (low-frequency pulsations in the
flow rate and of power consumption) through the effect of coupling
between the flow of the materials into the chamber and the vertical
vibrations.
The object of the present invention is to remove these drawbacks
by suppressing, or at least substantially reducing, the vertical
vibrations that perturb the operation of the crushers.
SUMMARY OF THE INVENTION
The crusher according to the present invention is characterised
in that the center of gravity of the assembly constituted by the
frame and the members that it supports and the center of gravity
of the cone and its support are in the plane of the vibration forces
generated by the vibrating device or in the vicinity thereof, More
precisely, these centers of gravity must remain permanently within
a fictitious sphere centered on the point defined by the intersection
of the vertical axis of the cone with the plane of action of the
vibration forces when the apparatus is idle, and having a diameter
equal to 15% of the maximum diameter of the cone. By satisfying
this condition, it is possible to avoid exerting upon the frame
bearing the ring and upon the cone support tilting torques generating
vertical vibrations.
According to one preferred form of embodiment, the frame comprises
a skirt surrounding the support of the cone and possibly provided
with weights, and a weighted cap is fixed on the apex of the cone.
The elastic members supporting the crusher can be interposed between
the bottom of the skirt and the bedplate or the foundations, the
cone support being suspended from the frame by means of the through
bolts. Other elastic members can be placed between the skirt and
the support of the cone, or between the latter and the bedplate
or the foundations.
Alternatively, the elastic members supporting the crusher can be
placed between the cone support and the bedplate or the foundations,
the other elastic members being placed between the skirt and the
cone support.
The cone is mounted rotatably on a vertical shaft fitted into its
support. To enable the height of the cone to be adjusted, it can
be mounted rotatably, via bearings, on a sleeve mounted on the shaft
in such a way as to be able to slide along it. Preferably, the shaft
and the sleeve will have shoulders, a sealed or tight annular chamber
being provided between the two shoulders and a channel pierced in
the shaft to enable a liquid under pressure to be brought into the
chamber to raise the cone or to be discharged in order to allow
the cone to move back down.
The frame can be constituted by a bottomless tank or vessel in
which the ring is held by suitable means and which is provided with
an annular base on which the vibrating device is mounted, the skirt
being fixed by its upper end to the edge of the base. The vibrating
device will advantageously be constituted by imbalance shafts having
vertical axes mounted on the base, each shaft comprising two imbalance
masses disposed on either side of the base in such a way that the
vibration forces generated by the rotation of the shafts are in
a horizontal plane coinciding with the median plane of the base
or in the vicinity thereof. It can comprise a phase shifting device
constituted by a rotary jack the body or the rotary element of which
will be coupled directly to one of the imbalance shafts, at least
one other imbalance shaft being coupled to the rotary element or
to the body of the jack, respectively, by a pulley and belt drive
system.
BRIEF DESCRIPTION OF THE DRAWINGS
The following description refers to the accompanying drawings which
show, by way of a non-limitative example, a form of embodiment of
the invention, and in which:
FIG. 1 is a vertical cross-sectional view of a vibrating cone type
crusher designed according to the invention; and
FIG. 2 is a cross-sectional view of a rotary jack constituting
the phase shifting device of the vibration generating system.
DETAILED DESCRIPTION OF THE INVENTION
The crusher shown in FIG. 1 has a frame 10 constituted by a bottomless
tank or vessel 12 having a circular cross-section and a vertical
axis, provided with a base 14 and by a skirt 16 fixed underneath
the base, at the edge thereof. The skirt rests on the foundations
via rubber shock absorbing pads 18 which support the crusher. Weights
79 can be fixed beneath the skirt.
A ring 22 is mounted coaxially inside the vessel. It constitutes
an interchangeable wearing part which is held in the vessel by a
flange and bolts.
The so-called cone element, 24 which co-operates with ring 22
is, in fact, constituted by a wearing part 28 having the general
shape of a cone trunk with a variable slope, mounted on a support
30 of the same shape and held thereon by a flange and screws; it
is surmounted by a cap 32.
The cone is mounted on a shouldered sleeve 34 via antifriction
bearings so as to be able to rotate freely about its axis. Sleeve
34 is, itself, mounted slidably on a shouldered shaft 38. The vertical
axis common to the cone, the sleeve and the shaft coincides with
the axis of ring 22 when the crusher is idle.
Seals are placed between the sleeve and the shaft, above and below
the shoulders, so that a tight chamber 40 is formed between the
latter. A channel 42 pierced in the shaft, enables this chamber
to be connected to a source of liquid under pressure. By admitting
liquid into the chamber or by discharging it therefrom, the heightwise
position of the cone in relation to the ring, and, consequently,
the grain size of the crushed product, is modified.
Support 44 of the cone is constituted by a hub 46 into which shaft
38 is fitted and a shell 48 connected to the hub by vertical ribs
50; the space provided between the hub and the shell permits the
discharge of the crushed materials. It is suspended from frame 10
via connecting rods or tie bolts 52 the ends of which are connected
by links to base 14 of the frame and to an annular plate 54 integral
with shell 48. Only one tie bolt has been shown in the drawing but
it is obvious that the crusher has several tie bolts, four for example,
regularly distributed about the crusher axis. Plate 54 is further
connected to skirt 16 by rubber shock absorbing pads 55 which take
up at least a part of the weight of the cone and of its support.
Tightness between frame 10 and cone support 44 is ensured by a metallic
skirt 51 and a deformable seal 53. Tightness between support 44
and sleeve 34 is ensured by a deformable seal 57.
The crusher vibrating device is constituted by several vertical
imbalance shafts 56 mounted on frame 10; only one of them is shown
in the drawing. Each shaft 56 is mounted on base 14 via antifriction
bearings and comprises two imbalance masses 58 disposed on either
side of the base; thanks to this arrangement, the forces exerted
by the imbalance masses on frame 10 when shafts 56 are rotated,
are located in a horizontal plane P--P which is very close to the
median plane of the base and could coincide therewith.
One of the imbalance shafts is coupled, via a double universal
joint type extension, to a drive shaft 60; the other imbalance shafts
are driven from the first one by a mechanical pulley and belt drive
system in which is incorporated a phase shifting device for adjusting
the angular displacement or shift of one group of imbalance shafts
in relation to the others to change the amplitude of the resultant
of the centrifugal forces generated by the rotation of the imbalance
shafts. Such a system is disclosed in documents FR-A-2681080 and
WO-A-9421380.
In one form of embodiment described by way of example, the crusher
comprises four vertical imbalance shafts disposed at the corners
of a square, as described in document WO-A-9421380. The imbalance
shaft diagonally opposed to imbalance shaft 56 directly coupled
to drive shaft 60 is rotated by means of a belt 63 running over
pulleys 64 keyed to these two imbalance shafts, and over return
pulleys mounted idle on the other two imbalance shafts. The latter
are rotated by means of a second belt, 65 running over two pulleys
keyed to these shafts, over a pulley 66 keyed to a sleeve 67 integral
with the body of a rotary jack 68 mounted on shaft 56 and over
a return pulley mounted idle on the fourth imbalance shaft.
The rotary jack shown in FIG. 2 comprises a cylindrical body 69
closed at its ends by end portions 70 and 71. A shaft 72 is disposed
axially in the body of the jack; it passes through end portion 70
in which it is mounted via a bearing which is capable of taking
up the axial stresses to which the shaft may be subjected to prevent
its axial movement in relation to the body of the jack.
A socket 73 is keyed to the shaft. A piston 74 is mounted in the
body of the jack; it comprises a skirt housed between the wall of
the jack body and socket 73. A roller 75 mounted on a pin fixed
on the body of the jack, is received in a helical groove 76 machined
on the piston in such a way that any axial displacement of the piston
in the body of the jack is accompanied by a rotation of the piston
in relation to the latter. Similarly, a roller 77 mounted on a
pin fixed on the skirt of the piston, is housed in a helical groove
78 machined in the socket, in such a way that any axial displacement
of the piston in the body of the jack causes shaft 72 to rotate.
The directions of grooves 76 and 78 are chosen so that the rotations
of the piston and of the shaft add together. By admitting fluid
under pressure into one or the other of the jack chambers, shaft
72 is caused to rotate in one direction or the other in relation
to the body of the jack. Seals are mounted on the piston and on
the shaft at the point where it passes through end portion 70.
Instead of using a roller and a helical groove to transform the
translational movements of the piston into rotational movements,
helical teeth could be machined on the piston and the shaft, these
teeth engaging with toothed wheels fixed to the body of the jack
and the skirt of the piston, respectively.
The body of the jack is fixed to the sleeve 67 and the outer end
of the shaft is fitted into a hole in shaft 56 and keyed thereto.
The jack is supplied with oil under pressure via rotary joint and
through a three-position valve which enables one or the other of
the chambers to be supplied to rotate shaft 72 in one direction
or the other, and to isolate the two chambers by maintaining pressurised
oil therein to prevent any rotation of the shaft in relation to
the jack body and to make it integral with the latter.
In operation, with the valve in locked position (jack chambers
isolated), all the imbalance shafts are rotated at the same speed,
and the amplitude of the resulting vibration force depends on the
relative angular positions of the imbalance shafts. To modify this
amplitude, the valve is actuated to cause shaft 72 of the jack to
rotate, which causes relative rotation of the two shafts of one
group in relation to those of the other; this adjustment can be
made while in operation.
A feed hopper 62 is fixed to vessel 12.
The different parts of the crusher are dimensioned so that the
center of gravity of the assembly formed by frame 10 and the members
that it supports, in particular ring 22 and imbalance shafts 56
and the center of gravity of the cone 24 and of its support 44 are
located in the plane of the vibration forces P--P, or in the immediate
vicinity of the said plane. It is, In particular, by suitably choosing
the dimensions and the weight of skirt 16 weights 79 and cap 32
that this condition is satisfied. More precisely, these centers
of gravity remain within a virtual sphere centered on the 0 point
defined by the intersection of the vertical axis of the cone and
plane P--P when the apparatus is idle, and the diameter of which
is equal to 15% of the maximum diameter D of the cone, for all crusher
operating conditions. As explained earlier, this arrangement makes
it possible to eliminate the tilting torques and, consequently,
the vertical vibrations. It should be noted that the maximum diameter
D is that of the useful part of the cone, that is to say of the
part that is effectively used for crushing purposes. As can be seen
from FIG. 1 the cone can be extended downwards by a part having
a diameter greater than D which must not be taken into consideration.
Other arrangements could be made to support the crusher. The cone
support could, for example, be caused to rest on the ground or the
foundations, via shock absorbing elastic pads, with the frame and
its load resting either directly on the ground or the foundations,
as in the form of embodiment described above, or on the cone support,
via pads analogous to pads 18 or 55.
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