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Патент USA US2872015

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Feb. 3, 1959
Filed Oct. 29, 1957
2 Sheets-Sheet l
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Feb. 3, 1959
Filed Oct. 29, 1957
2 Sheets—Sheet 2
Thomas Wz'rfz
BY KarF-A’ezivz 1142662164
Kai’! VVézzger
United States
' ate-nt
Patented Feb. 3, 1959
Thomas Wirth, Dachau, Karl-Heinz Nebhuth, Darm
building structure and to adjacent machines may be over
come by providing a foundation for the centrifuge having
as great a mass as possible, and by providing the founda~
tion with an elastic support, for example, of cork or rub
ber, which tends to reduce the amplitude of the alternat
ing stresses transmitted to the building structure. How
ever, such foundations are costly and are not always prac
stadt-Arheilgen, and Karl Wenger, Munich-Allach,
tical, for example, in cases where the centrifuge is to be
installed on the upper ?oors of a building.v Furthermore,
Application October 29, 1957, Serial No. 693,086
10 the vibrations of the centrifuge frame are transmitted to
the drive motors of the centrifuge mounted on the frame
19 Claims. (Cl. 210-370) ‘
thereof, and also to the transmission members, such as,
belts, drive shafts and the like, thereby to increase the
load on the motor bearings, the motor windings and the
This invention relates generally to centrifuges for re
transmission members and to correspondingly reduce their
moving water or other liquids from a granular material,
useful life. In the described existing arrangement the
and more particularly is directed to improvements in
bearings carrying the spindle are also subjected to high
centrifuges of the kind wherein the basket is oscillated in
stresses by reason of the oscillation of the balancing
the direction of-its rotational axis in order to effect the
mass, that is, the frame of the centrifuge, which does not
‘continuous discharge of the dried granular material or 20 rotate with the spindle, and whereon the bearings is
other solids.
thereby increased.
With centrifuges of the kind described above, the axial
Accordingly, it is an object of the present invention to
oscillation of the basket carries the dried solid material provide a centrifuge of the kind described above, and
\over the lip of the conical basket wall for discharge from
wherein the axial oscillations of the centrifuge basket
the basket without damage to the granular structure of 25 for effecting the continuous discharge of the dried solid
‘the dried material, whereas the mechanical discharging
material are isolated fromthe foundation of the centrifuge
‘devices with which other centrifuges are equipped, tend
and also from the drive motors, the transmission mem
to destroy the granular structure of the dried solid
bers and the bearings carrying the spindle.
In accordance with an aspect of this invention, the
In existing centrifuges of the kind wherein the basket 30 oscillations of the basket are isolated from the founda
is axially oscillated in order to effect the continuous dis
tion, drive motors, transmission members and the bearings
charge of dried solid material therefrom, the basket is
elastically connected to the spindle of the centrifuge either
supporting the spindle by elastically connecting both the
mass of the basket and the balancing mass to the frame
by an elastic bottom in the basket or by springs which
of the centrifuge, but in opposite directions, so that the
:are connected between a rigid bottom in the basket and 35 forces transmitted by the resulting dual-mass oscillating
the spindle, thereby freeing the basket for oscillation
system to the frame of the centrifuge always act simul
axially relative to the spindle, while the spindle is axially
taneously upon the latter, but in opposite directions, so
movable in a support which is, in turn, elastically con
that oscillation of the centrifuge frame is essentially
nected to the frame of the centrifuge. In a centrifuge
having the above arrangement, axial oscillations are di
Further, in accordance with the invention, mutual can
rectly imparted to the slidable spindle which forms a bal
cellation of the forces exerted on the ‘centrifuge frame by
ancing mass elastically coupled to the basket to form an
the oscillating basket and balancing mass, respectively, is
oscillating system having dual masses. With such a dual
ensured by providing an oscillation generator operatively
mass oscillating system, the masses of the basket and
connected'to the balancing mass and to the basket in order
spindle, respectively, may oscillate either in the same or
to produce synchronous, inverse or opposed oscillations
in opposite directions, and alternating forces are always
of the basket and of the balancing mass at all frequencies.
transmitted from the‘ support of the centrifuge to the
A further feature of the invention resides in providing
frame or foundation thereof by Way of the elastic‘ con
a drive assembly for rotating the spindle and the basket
nection therebetween. These alternating forces will be 50 which does not participate in the oscillations of the basket
relatively small when the masses of the basket and spindle,
and the balancing mass, so that such oscillations are iso
respectively, oscillate in opposite directions, however,
lated from the elements of the drive assembly, for ex
since the oscillations are directly imparted only to the
ample, drive motors, drive shafts, transmission belts and
mass of the spindle, the masses of the basket and spindle
the like.
will oscillate in opposite directions only within a narrow 55
and other objects, features and advantages
range of frequencies.
of the‘ invention, will be apparent in the following de
In other existing centrifuges of the kind wherein the
tailed description of an illustrative embodiment thereof
dried solid material is discharged from the basket by
which is to be read in connection with the accompanying
effecting axial oscillation of the latter and employing a
drawing-forming a part hereof, and wherein:
dual mass oscillating system, the frame of the centrifuge 60
Fig. 1 is a longitudinal, sectional view of an oscillating
acts as the balancing mass and is elastically connected to
the foundation so that, in such an arrangement, the mo
mentum of the masses is also transmitted to the founda
tion by way of the elastic connection between the latter
centrifuge embodying the present invention, with auxiliary
momentum of the masses are, in turn, transmitted from
Referring to the drawing in detail, and initially to Fig.
devices associated with the centrifuge being shown
Fig. 2 illustrates additional auxiliary devices; and
and the oscillating'mass of the centrifuge frame. The
Fig. 3 is a diagrammatic representation of the operating
alternating forces resulting from the transmission of the
principles of the centrifuge illustrated in Fig. 1.
the foundation of the ?oor of the building structure hous
1 thereof, it will be seen that an oscillating centrifuge em
ing the centrifuge or to adjacent machinery, and fre
bodying the present invention and there generally identi~
quently causes structural damage to the building or inter
?ed by the-reference numeral 10 includes a centrifuge
ference with the mechanical e?iciency, or even operative~ 70 basket 11 having a frusto-conical, perforated side wall 12
ness, of the centrifuge and of adjacent machines. Such
and an end wall 13 closing the relatively small diameter
transmission of the forces ‘from the foundation to the
end ‘of the basket. The basket 11 is arranged with its
12,8 more
central axis extending horizontally and'is mounted within
atv 33a, -is ‘bored and carries a diametrically extending
a centrifuge frame or housing 14, as hereinafter described
in detail, for rotation about its horizontal central axis and
cross-piece 33 extending outwardly through diametrically
opposed pairs of registering, axially elongated slots 34 and
for oscillation or reciprocation ‘inith'e anguish-urinating
of rotation. A stationary feed pipe 15 extends saws
wardly into the frame or housing lli'aiiidiis then bent," as
cross-piece 33 are secured within the balancing mass 31.
35 in the hollow portion 22a of the spindle and in the
hollow shaft 18, respectively, while the outer ends of the
open, relatively large‘di'ameter ‘end of the-'latter'and‘to
terminate adjacent the end wall‘13‘f0r suppiyingmeslan-y
A relatively strong helical compression spring 36 ex
tends around the hollow shaft 18 and abuts, at its opposite
ends, against the sleeve 29 and the balancing mass 31, re
is to be centrifuged, so that ‘such material will not spun‘
and 3S acting as elastic spacers extend around the hollow
shown, to extend axially into the-‘basket 11 through'the ,
of liquids and solid materials which are to 'be‘separaréd 10 spectively,to act as an elastic-coupling between the bal
ancing mass, which is connected by the cross-piece 33 to
to the centrifuge basket. The angle of inclination of the
oscillate with the rod 32, and the sleeve 29 which is con
perforated side wall 12 ‘of the centrifuge basket relative
nected, by the pin '23, to oscillate with the spindle 22
to the central axis of rotation of the latter is selectedQto
and basket 11. Further, helical compression springs 37
be smaller'than the angle of repose vof the'material which
shaft 18 and are axially interposed between the sleeve 29
taneously ?ow out'of the open, large diameter end of the
and a collar 39 abutting against the partition 16, and be
basket 11, and will be'discharged through‘the open end
tween the 'rna'ssiilan'd a collar 44} abutting against the
of the basket only in'response to axial oscillation of the
casing 20 secured in-the end'wall 21, respectively.
latter. Since the amplitude and frequency of the axial
oscillations of’ basket 11 are adjustable, as hereinafter 20 _ ‘In order to effect synchronous oscillations of the basket
11 ‘and balancing mass 31 in opposed directions at all
indicated in detaihthe dwell time of the solid material
in the basket 11 prior to discharge'from the latter can be
varied in order to regulate the operation of the centrifuge
in connection with the properties of the solid material
‘frequencies, the'centrifug‘eltl embodying the presentin~
volition includes a’cylinder 41 which is‘slidable within the
cylindrical casing 20 and axially coupled to the end of
being separated.
In order to‘ mount the basket 11 for rotation and axial
oscillation within the frame or housing '14, the latter is
the ‘spindle '22 remote from the basket‘ll, and a piston
42 which is slidable within the cylinder 41 and connected
to the'end of the rod 32 remote from the cross-piece 33.
Thus, ‘when ?uid under pressure isYadmittcd to the cylinder
“that-the‘ right hand side of the piston 42, as viewed in
one end of an open-ended, hollow shaft‘ 18, and the latter 30 Fig. 1, the piston 42 as well as the balancing mass 31
‘will be' driven’toward the left, while the cylinder 41, the
is also rotatably supported, adjacent its opposite end, in
spindle 22 and the basket 11 will be driven toward the
a bearing'19' fixed in one end of a cylindrical casing 20
which‘ is suitably secured in an end wall 21 of the frame _ right. 'Conversely, when fluid under presusre is admitted
to' the cylinder 41 at‘ the left hand side of the piston 42,
or housing 14. A spindle 22 is rigidly secured, at one
end, to’ the end wall 13 of basket 11 and extends axially 35 as‘vi‘ewed'in‘Fig. l, the balancing mass 31 is driven toward
the: right,‘while the basket 11 is driven toward the left.
from the latter through the hollow shaft 18. In vorder
‘In a modi?ed construction according to our invention,
to coupleithe‘ spindle 22' to the hollow shaft 18 for'rota
the ‘balancing mass 31 is replaced by a second basket
tion with the latter, while permitting axial oscillation of
analogous to‘basket 11, in which case we provide within
the spindle relative to the shaft 18 which is held against
axial displacement with respect to the housing 14, a pin 40 the spindle ‘22 instead of the‘ rod 32 a rod that passes
through‘ they piston 42 and also through the end wall of
or wedge 23 passes through a diametrical‘ bore ‘in the
spindle 22 and extends radially outward through'a pair , the cylinder '41 remote from the'pulley 25. The second
basket is secured, beyond said end wall of the cylinder
of diametrically opposed, axially elongated slots 24'pro
41, to the free end of the rod. With this construction,
vided in the hollow shaft 18 intermediate the ends of the
the second basket acts as a balancing mass since the two
baskets synchronously voscillate ‘in opposite directions at
In order to effect rotation of the hollow shaft 18, and
the same frequency with the same amplitude. The
hence also rotation of the spindle 22 by way of the cou
throughput of this double centrifuge having the balanced
pling provided between the shaft 18 and spindle 22 in the
characteristics described above with reference to the em
form of the pin 23 engaging in slots 24, a pulley 25 is
bodiment illustrated in Fig. l is practically doubled.
suitably secured on the end of hollow shaft 18 remote
According to a modi?cation of the embodiment shown
from the basket 11 and is’ engaged by endless transmission
and described hereinbefore, the springs 36, 37 and 38 are
belts 26 which also run around a pulley 27 secured on the
provided with ‘a partition 16 extending thereacross and
centrally carrying a bearing 17 which rotatably supports
shaft of a drive motor 28.
Since the hollow shaft 18 is
replaced by pneumatic and hydraulic pressure'cylinders.
For instance, 'in such modi?cation a sleevelike piston is
only rotatable and does not participate in they axial oscil
slidably mounted on'the hollow shaft 18 and abuts atone
lations imparted to the spindle‘ 22, as ‘hereinafter de
end against the sleeve 29. The piston is guided in a
scribed in detail, the bearings 17 and 19 supporting ‘the
cylinder, the annular'bottom of which abuts accordingly
shaft 13, the transmission consisting‘of the belts 26 and
against the collar 39. Air enclosed in the cylinder‘space
the pulleys 2S and 27 and the motor‘ 28‘ a‘re'all isolated
is compressed whenhydraulic fluid is admitted to the pis
from the effects of such oscillations and ‘are'th‘ereby pro
tected against the increased we'ar‘that results from the ill) ton 42 at the side of the rod 32, and when hydraulic ?uid
is admitted to the other side of the piston the air expands.
transmission of the oscillations to such operating parts.
This device constitutes an elastic intermediary member
' A sleeve 29 is slidably'mounted upon the‘ hollow shaft 18
analogous‘ to helical spring 37. The elasticity of this
and is provided with bores 30 receiving the opposite ends
intermediate member can be increased by connecting to
of the pin 23 so that the sleeve 29 is thereby coupled to
the air-?lled cylinder space an expansion chamber, such
the spindle 22 for axial oscillation with the latter with
as is customary with piston pumps. An air-holding ex
respect to the hollow shaft 18.
A balancing mass, preferably in the form of ‘an annular
member 31 which is split ‘along a diarhetric plane to pro
vide'two separable parts which can‘ be secured together
around the hollow shaft v18, is slidably mountedon'the 70
shaft 18 between the sleeve 29 and the end wall 21 ‘of
housing 14. The spindle 22 is formed with a‘hollow
portion 22a opening axially in the direction‘ away from
the basket 11 and slidably receiving and‘ 32 which,iat' its
inner end within the hollow/‘portion 22a of the spindle,
pansion chamber is ‘definitely required when the hydraulic
fluid for the cylinder is a liquid and the necessary elas
ticity of the system must be obtained despite the incom
pressibility of the liquid.
It is also‘ possible to place a cylinder and piston analo
'gous to the cylinder 41 and piston 42, respectively, inside
of the hollow shaft‘ 18.
In this case, the hollow shaft
assumes the function of the casing 20, and'the ‘hollow
~portion ‘of‘the spindle 22 am “as ‘the cylinder 41in’ which
the piston slides. The external diameter of the piston
corresponds to the internal diameter of the hollow spindle
As shown in Figs. 1 and 2, a system for supplying
?uid under pressure to the cylinder 41 alternately at the
opposite sides of the piston 42 therein may include con
duits 43 and 44 connected to the casing 20 and opening
into annular grooves 45 and 46, respectively, formed in
the inner surface of the cylindrical casing 20 at axially
52 between the pump 50 and the adjustable throttling
valve 64 in order to absorb any pressure shocks that
may be imparted to the ?uid under pressure during oper
ation of the pump.
Referring to Fig. 3, wherein the operating conditions
achieved with the above described oscillating centrifuge
are diagrammatically represented, it will be apparent that
the masses a and b of the basket 11 and the balancing mass
31, ‘respectively, with the interposed helical spring 36
spaced apart locations and permanently communicating 10 coupling together the two masses created a dual-mass
with radial openings 47 and 48, respectively, in the cyl- ' oscillating system, which, when the masses oscillate in
inder 41 adjacent the opposite ends of the latter. The
opposite directions, does not exert any momentum on the
illustrated system further includes a source of ?uid 49,
frame 14 by reason of the provision of the spacing springs
in the form of a tank or reservoir, a pump 50 having
37 and 38 which space the oscillating system from the
its inlet side connected, as by a pipe 51, to the source 16 transverse walls 16 and 21 of the frame and always exert
49, a supply line 52 for ?uid under pressure extending
equal and opposite forces against the frame 14. Thus,
from the discharge or outlet side of the pump 50, a
the forces exerted by the springs 37 and 38 against the
return line or pipe 53 emptying into the source 49, and
frame 14 cancel each other, and oscillations of the centri
a rotary distributing valve 54 driven by a variable speed
fuge are not transmitted to the foundation supporting the
motor 55 which is independent of the motor 28 for effect 20 latter or to any surrounding structure or adjacent ma
ing rotation of the basket 11. The rotary distributing
chines. Further, since the balancing mass 31 rotates with
valve 54 is operative, when driven by the motor 55, to
the basket 11, no vibrations are transmitted to the bearings
alternately connect or establish communication between
17 ‘and 19 which rotatably support the hollow shaft 18 and
the conduits 43 and 44 and the supply line 52 and return
the bearings are thereby protected against excessive Wear.
line 53.
The ?uid under pressure supplied to the cylinder 41
As shown merely by way of example in Fig. 2, the ‘ ‘for generating the desired oscillations of the basket and
rotary distributing valve 54 may include a cylindrical
balancing mass may be either a gas or a liquid, and such
valve body 56 connected, as at 57, to the motor 55 for
?uid under pressure may be derived from a source of
rotation by the latter within a housing 58. The valve
pressurized ?uid which primarily serves other purposes,
body 56 selected for illustration has four axially spaced .30 thereby to avoid the necessity for providing an individual
apart slot-shaped recesses 59, 60, 59a, and 60a, which
source 49 and pump 50 for each centrifuge.
, .
extend approximately to the axis of the valve body and
Although it is desirable to have the ?uid under pressure
are arranged in pairs on opposite sides. Spacedly pro
supplied to the cylinder 41 alternately at the opposite
vided in the housing 58 are four axially extending pipes
sides of the piston 42, as described above, it is possible to
61, 62, 61a and 62a, each of which comprises two oppo
eliminate one of the conduits 43 or 44 and to employ the
sitely directed branches, as the branches 61' and 61" ‘I
remaining conduit for alternately connecting the related
of the pipe 61, and the branches 62' and 62" of the pipe
62. Altogether there are eight such branches, the end
space in the cylinder 41 to the supply line 52 and the re
portions of which are bent toward the interior of the
turn line 53, respectively. Our oscillating centrifuge will
operate satisfactorily even when the dual-mass oscillating
valve body and open at points along generating lines of 40 system consisting of the mass of the basket 11 and the
the inner wall of the cylindrical housing 58. The width
balancing mass 31, in cooperation with the helical springs
of the recesses 59, 60, 59a, and 60a is such that one
36, 37, 38 as elastic links, is excited in one direction only
branch of each of the two pipes 61 and 62, as 61' and
in the rhythm of its resonant frequency, whereby free os
62',-open into one and the same recess, as 59. Thus,
cillation of the masses is generated. In this modi?cation,
the valve body is adapted to effect communication be 45 the recesses 59a and 60a of the valve body 56 of the
rotary valve 54 (see Fig. 2) may be omitted, so that the
tween two pipes over one of their branches, as between
supply line 52 and the return line 53 and conduit 44 will
register in the area of the recesses 59 and 60. The piston
42 and the cylinder 41 will be driven in opposite axial
lishes communication between two pairs of pipes, as be
tween 61 and 62 and between 61a and 62a‘, that is also 50 directions upon the admission of ?uid under pressure to
the cylinder at one side of the piston.
between each of the conduits 43 and 44 and one of the
In place of the axially movable cylinder 41, it is
lines 52 and 53. In the position of the valve body, as
61 and 62 over 61’ and 62’.
Actually, in any of the
operating positions of the valve body, the latter estab
illustrated, the supply line 52 is shown to communicate
possible to substitute two ?xed cylinders having pistons
slidable therein and connected to the basket 11 and the
over pipes 614: and 6211 With the conduit 43, while the
conduit 44 communicates over pipes 62 and 61 with the 55 balancing mass 31, respectively, while the supplying of
?uid under pressure to such ?xed cylinders is controlled.
return line 53. With the valve body rotationally dis
in order to provide for the desired oscillation of the basket,
placed by approximately one hundred and eighty degrees,
and balancing mass in opposite directions.
the supply line 52 will communicate with the conduit
‘ Furthermore, the single rotary valve 54 described above
44 over the pipe 61a, using the opposite branch of the
latter, and the pipe 62, using the branch 62", and the 60 and employed for controlling the connection of the
conduit 43 will communicate with the return line
using the opposite branches of pipes 62a and 61.
It will be apparent that the variable speed motor
in changing the rotational speed of the valve body
will correspondingly vary the frequency at which
conduits 43 and 44 to the lines 52 and 53 may be ob
viously replaced by cam-controlled valves or by electri
cally or hydraulically-controled valves. It is also apparent
that the rotatabe body 56 of distributing valve 54 may
the 65 be driven by a variable speed transmission from the motor
28, rather than by a separate variable speed motor 55, as
conduits 43 and 44 are alternately communicated with
illustrated in the drawing.
the supply line 52 and the return line 53, thereby to
of the
correspondingly vary the frequency of the oscillations
rotary distributing valve 54, a spring-loaded disc valve
imparted to the basket 11 and the balancing mass 31.
70 similar to those used in internal combustion engines with
In order to permit adjustment of the amplitude of the
a stem sliding by means of a cam follower on eccentric
oscillations imparted to the basket 11 and the balancing
discs is arranged between each pair of coordinated ends
mass 31, an adjustable throttling valve 64 may be inter
of the pipes 61, 62, 61a and 62a. The eccentric discs are
posed in the supply line 52.
Further, a pressure accu
mounted on the shaft 57 driven by the motor 55. There
mulator 65 may also be interposed in the supply line 75 are two pairs of such eccentric discs, but the two pairs are
angularly displaced with respect to eachother by 180°
so that when one pair of thervalves is_ lifted the supply
the frequency of oscillation of said basket and balancing
7. An oscillating centrifuge as in claim 6; wherein
said'means for supplying ?uid under pressure further in
cludes pressure accumulating means interposed in said
supply line and operative to absorb pressure shocks dur
ing operation of said pump means.
rotary valve 54.
8.‘ An oscillating centrifuge as in claim 6; wherein
Although a single illustrativeembodiment- of ‘the in
said means for supplying ?uid under pressure further in
vention has been described herein .with referenceto the
accompanying drawings, and several modi?cations of-the 10 cludes an adjustable throttling valve interposed in said
supply line and operative to control the flow of ?uid
illustrated arrangement have additionally been described,
under pressure through said supply line and, hence, to
it is to be noted that the invention-is. not limited to the
control the amplitude of the oppositely directed oscilla~
precise embodiments illustratedand'descfibed, and. that
tions imparted to said basket and balancing mass.
many other changes and other modi?cations .may'be ef
9. An oscillating centrifuge as in claim 5; further com
fected without departing from the. scope or spirit of the
promising a hollow, open-ended shaft, bearing means ro
invention, except as' defined in theappended'claims.
tatably mounting said hollow shaft in said frame coaxial
3What is claimed is:
with said axis for rotation of said basket, a spindle ex
1. An oscillating centrifuge 'for eifectingi‘the continuous
tending axially from said. basket and slidably received in
discharge of dried solid materials and comprising a ‘frame,
a basket mounted in said frame for rotation and for 20 said hollow. shaft, .means constraining said spindle to
rotate with said hollow shaft while permitting axial os
oscillation along the axis of rotation of ‘the basket, a
cillation of said spindle relative to said hollow shaft,
balancing mass mounted for oscillation along said axis of
said balancing mass being slidably mounted on said h0l—
rotation and being elastically coupled with said basket to
low shaft, means constraining said balancing mass to
form, with the latter, a dual-mass oscillating system, drive
means operatingin opposed axial directions on said basket 25 rotate with said hollow shaft, rotational drive means, and
transmission means connected between said rotational
and balancing mass, respectively, and elastic means cou
line 52 is connected with the conduit 43, whilethe con
duit. 44 is connected with the return line 53. The con
nections are reversed when the other pair of valves is
lifted. Thus, the same effect :is insured as with the
pling said basket and said balancing mass, respectively,
to said frame in opposed-directions so that forces trans
mitted from said dual-mass oscillating system to said
frame act simultaneously in opposite directions to prac
tically eliminate the oscillation of said frame.
2. An oscillating centrifuge as in claim 1; wherein said
drive means includes a single generating device for pro—
ducing oscillations of both-said basket and said balancing
3. An oscillating centrifuge as in claim '2; wherein
said drive means further includes coupling means between
ssiidgeneratihg device and said basket and balancing mass,
respectively, operative to cause said basket ‘and balancing
drive-means and said hollow shaft to rotate the latter and
thereby to effect simultaneous rotation of said basket
with said spindle and of said'balancing mass.
10. An oscillating centrifuge as in claim 9; wherein
said spindle is directly connected to said cylinder and
thereby forms said-coupling means between said cylinder
and said basket.
‘11. An oscillating centrifuge as in claim 10; wherein
said spindle has a hollow portion opening axially in the
direction-toward said cylinder and said hollow shaft and
said hollowportion of the spindle have registering axially
elongated slots; and wherein said coupling means be
tween said piston and said balancing mass includes a rod
- mass to oscillate synchronously in opposite directions at 40 connected to said piston and extending axially out of
all operating frequencies.
4. An oscillating centrifuge as in claim 3; wherein said
generating device is ?uid pressure operated; and said drive
means further includes means for supplying an operating
?uid to said generating device at repeatedly varying pres
sures, and adjustable control :means effective to vary the
frequency of the variation of pressure of the operating
5. An oscillating centrifuge as‘in claim ‘3; wherein said
generating device includes a cylinder slidably mounted in
said frame to move axially relative to the latter in the
direction of said axis of rotation ofthe basket, and a
piston axially movable within said cylinder, said coupling
means connecting said basket to said cylinder and said
balancing mass to said piston; and further comprising
means for supplying ?uid under pressure to said cylinder
alternately at the opposite sides of said piston so that, in
response ‘to the admittance of ?uid under pressure to said
cylinder, said cylinder and‘piston, and hence said basket
and balancing mass, respectively, are displaced in op
posite directions.
6. An oscillating centrifuge as in claim 5; wherein said
means for supplying ?uid under pressure includes conduits
opening into the opposite ends of said cylinder, a source
of ?uid, pump means having an inlet receiving ?uid from
said cylinder into said hollow portion of the spindle,
and a cross-piece on said rod projecting radially through
said registering slots and secured, at its ends, to said bal
ancingrn'ass to transmit the axial displacements of said
rod with the piston to said balancing mass and to de?ne
said means constraining said balancing mass to rotate
with said hollow shaft.
12. An oscillating centrifuge as in claim 10; wherein
said hollow shaft has axially elongated slots therein, and
said means constraining said spindle to rotate with said
hollow shaft includes a pin extending diametrically
through said spindle and having its opposite end por
tions slidably received in said elongated slots.
13. _An oscillating centrifuge as in claim 12; further
comprising a sleeve slidable on said hollow shaft and
connected to said pin to move axially with said spindle
relative to said hollow shaft, and elastic intermediary
means on said hollow shaft between said sleeve and said
balancing mass to provide the elastic coupling between
(if) the latter and said basket.
14. An oscillating centrifuge as in claim 13; wherein
said intermediary elastic means includes a helical com
pression spring extending around said hollow shaft.
15. An oscillating centrifuge as in claim 13; wherein
said intermediary elastic means includes an axially com
said source and a discharge for ?uid under pressure, a
pressible cylinder assembly containing ?uid to yieldably
?uid under pressure supply line extending from said dis
charge of the pump means, a return line extending back
resist axial compression thereof.
to said source, valve means connected to said conduits
and'to said‘ supply and return lines and operative, upon
actuation, to alternately communicate said supply and re
turn lines with said conduits, and independent, variable
speed motor means connected to said valve-means for
driving the latter at an adjustable speed, thereby to vary
16. An oscillating centrifuge as in claim 13; wherein
said frame has spaced apart laterally extending wall por
tions carrying said bearing means mounting the hollow
shaft, with said sleeve and balancing mass being both
disposed between said wall portions; and wherein addi
tionalelastic means includes an elastic element inter
posed between said sleeve and the adjacent wall por
tion and an elastic element interposed between said bal~
ancing mass and other of said wall portions.
17. An oscillating centrifuge as in claim 14; wherein
each of said elastic elements includes a helical compres
sion spring extending around said hollow shaft.
18. An oscillating centrifuge as in claim 14; wherein
19. An oscillating centrifuge as in claim 3; wherein
said balancing mass is .in the form of a second basket
so that, in response to the synchronous oscillation of
said second basket and the ?rst mentioned basket in op
5 posite directions, dried solid materials are simultaneously
and continuously discharged from both baskets.
each of said elastic elements includes an axially compres
sible cylinder assembly containing ?uid to yieldably resist
axial compression thereof.
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