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Publication numberUS3769904 A
Publication typeGrant
Publication dateNov 6, 1973
Filing dateJul 16, 1971
Priority dateJul 29, 1970
Also published asCA939192A1, DE2137771A1
Publication numberUS 3769904 A, US 3769904A, US-A-3769904, US3769904 A, US3769904A
InventorsYoritomi R
Original AssigneeYoritomi R
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Continuous press for dehydration
US 3769904 A
Abstract
Two opposed, frustoconical rotary discs define a V-shaped annular channel therebetween in an annular casing of a press. A pair of shafts, each shaft rotatably supporting one of the discs, are pivotally connected together by a supported pin near the apex of the channel. The pin is supported across an opening formed in a plate fixedly disposed centrally in the casing. The shafts extend outwardly through the casing and are fixed to respective supporting yokes, each yoke having two free ends. One of the free ends of one yoke is pivotally connected to a corresponding free end of the other yoke on the axial line of the pin. The remaining two ends of the yokes are adjustably connected together along the plane in which the shafts lie and these ends may be drawn together to selectively vary the shafts' directions to thereby adjust the width of the V-shaped channel.
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Description  (OCR text may contain errors)

United States Patent mi Yoritomi i 1 CONTINUOUS PRESS FOR DEHYDRATION [76] inventor: Ryutaro Yoritomi, 5-17-12 Koishikawa, Bunkyo-ku, Tokyo, Japan [22] Filed: July 16, 1971 [2]] Appl. No.: 163,394

[30] Foreign Application Priority Data 9 [52] US. Cl 100/158 C, 100/121, 100/168 [51] Int. Cl B30b 3/04 [58] Field of Search l0O/l2l, 158 C, 168' 1 Nov. 6, 1973 Primary ExaminerHarvey C. Hornsby Assistant Examiner-Alan l. Cantor Attorney-Robert R. Finch et al.

[57] ABSTRACT Two opposed, frustoconical rotary discs define a V- shaped annular channel therebetween in an annular casing of a press. A pair of shafts, each shaft rotatably supporting one of the discs, are pivotally connected together by a supported pin near the apex of the channel. The pin is supported across an opening formed in a plate fixedly disposed centrally in the casing. The shafts extend outwardly through the casing and are fixed to respective supporting yokes, each yoke having two free ends. One of the free ends of one yoke is pivotally connected to a corresponding free end of the other yoke on the axial line of the pin. The remaining two ends of the yokes are adjustably connected together along the plane in which the shafts lie and these ends may be drawn together to selectively vary the shafts directions to thereby adjust the width of the V-shaped channel.

12 Claims, 6 Drawing Figures 1 con'rmoous PRESS FOR nEn p rIoN BACKGROUND OF THE INVENTION DESCRIPTION OF THE PRIOR ART A V-type squeezing press typically includes an annular casing supported on a stationary frame, a circular plate fixedly disposed concentrically in the casing, supporting shafts extending from opposite sides of the frame to pivotally terminate in the circular plate, and a pair of squeezing discs mounted, one each, on the supporting shafts to be rotatable in the casing. The squeezing discs each have one sloped frustoconical face and are arranged such that the frustoconical faces confront each other; a central, flat (truncated) portion of each disc contacts the circular plate interposed between the discs. The radial peripheries of the discs are closely spaced from the inner surface of the casing. An annular channel of V-shaped cross-section is thereby defined between the discs.

In earlier presses, the shafts supporting the discs extended outwardly with their axes slanted at a predetermined fixed angle relative to' each other, so that the V- shaped channel had a fixed maximum width at one point and a minimum width at a point diametrically p posite.

When the squeezing discs are rotated about the supporting shafts and when feed material is supplied at the widest spaced portion of the V-shaped channel, the feed material is rotated with the discs while being held therebetween and is thereby compacted. Liquid in the feed material is extracted as the width of the V-shaped channel decreases. With fixed-angle supporting shafts the compression ratio (the ratio between the maximum and the minimum channel width) was not changeable.

The earlier presses were not capable of effectively handling a range of materials which differed in liquid content and slippage nature. However, the present inventor proposes a continuous squeezing apparatus with an adjustable compression ratio, as disclosed by the present inventors Japanese Patent No. 536,991.

In that continuous press, the two inner ends of the supporting shafts are pivotally connected together at the center of the circular plate by a pin and the shafts outer ends are fitted in guide grooves provided at both sides of a main frame. The shafts are fixable at selected positions in the guide grooves to adjust the ratio between the maximum and minimum width of the V- shaped channel. Thus, the compression ratio of the apparatus can be preadjusted at a desired value depend.-

ing upon the liquid content of the feed materials. When materials are pressed, counter-forces acting upon the filter discs increase as the clearance between the discs becomes smaller, and the maximum counter-forces are applied at the minimum clearance. After material passes through the minimum clearance,.the counterforces rapidly decrease to nearly zero. Therefore, a counter-force total resultant acts upon the filter discs at a point a little lower than the minimum clearance, in a plane perpendicular to the shaftconnecting pin. In some operations, the resultant is capable of bending the arm supporting the circular plate and, as a result, there is binding between the periphery of the filter discs and the inner surface of the casing. With an increase in the pressing force, the radial peripheries of the filter discs may be so strongly pressed against the casing that the discs stop rotating.

OBJECTS OF THE INVENTION An object of the present invention is to provide an adjustable, continuous V-press which does not bind during operation.

A further object is to provide means and structure distributing counter-forces generated in the operation of a v press.

BRIEF DESCRIPTION OF THE DRAWINGS Further objects and advantages of the invention may be ascertained from the following description and appended illustrations in which:

FIG. 1 is a sectional view taken along line ll of FIG. 2;

FIG. 2 is a side view of a continuous, disc-type press according to the invention:

FIG. 3 is a cut-away view of the press as shown in FIG. 2;

FIG. 4 is an end view of the press of FIG. 2;

FIG. 5 is partially cut-away view of the press as shown in FIG. 4; and

FIG. 6 is a top view of the press shown in FIG. 2.

DETAILED DESCRIPTION OF INVENTION In practice, the shafts supporting the rotating filter discs are arranged in a downward inclined direction for convenience in charging and discharging raw material to the press. Since raw materials are removed where the V-shaped channel is a little opened after the raw materials have been subjected to the maximum pressing force, and because a position near the horizontal level is preferable as the removal position, the minimum clearance of the V-shaped channel of the filter discs is set at a position a little lower than the horizontal. Thus, the supporting shaft axes are in a downward inclined direction. However, to simplify description, explanation is made usingan illustration where the supporting shaft axes are horizontal. Directions described later herein are relative and are utilized for descriptive purposes only. Accordingly, the maximum and minimum opening of the V-shaped channel are horizontal, but the discharge ofthe raw materials is positioned a little above the horizontal. Were such an arrangement utilized in practice, a discharging device of special type would have to be used. In other words, the supporting shafts as shown in FIG. 5, in practice, are inclined slightly downward.

An annular casing l is supported on a frame and has an inner surface defining a circular cavity of certain breadth symmetrical with reference to the casings median plane. In FIG. l,the casings inner surface is defined by opposing arcs. A circular plate 2 is concentri- I cally, fixedly disposed in the cavity by an inwardly directed arm 3 (FIG. 3) extending from the inner surface of the casing. The outer surface of the circular plate 2 defines a truncated sphere which is slantingly sliced symmetrically with reference to the median plane and which is arranged concentrically with the casing so that the width of diametrically opposite edges of the plate differ. A rectangular channel 4 is provided through the plate 2 and the plane of the open ends of the channel slant from normal with the casing axis. The inner ends of supporting shafts 5 and 6 are pivotally connected in the channel 4; shaft 5 has a forked end which receives V the end shaft 6 and these ends are pivotally connected by a pin 7. The pin is located at the center of the channel 4 and extends relatively vertically thereacross and the pin 5 ends are inserted in a bore provided in the circular plate 2.

Filter discs 8 and 9 are concentrically rotated on the shafts 5 and 6, respectively. Each disc has a frustoconical front face, and tubular shafts l0 and 11 are integral with the backs of the respective disc. A number of axially extending perforations are provided through faces of the filter discs 8 and 9. Shaft bearings 12 and 13 and thrust shaft bearings 14 and 15 support the shafts 5 and 6, respectively. The frustoconical faces of the discs 8 and 9 have axial recesses 16 and 17 where the faces are truncated, and the virtual apices of faces would intersect near pin 7. The inner peripheries of the recesses 16 and 17 constitute part-spherical surfaces which loosely engage the outer surface of the circular plate 2 from both sides. In other words, when the discs rotate on the shafts 5 and 6, the recesses 16 and 17 rotate around the outer curved periphery of the circular plate 2. The radial edge surfaces of the filter discs closely clear the inner periphery of the casing l. Sprockets l8 and 19 are fixed outside casing 1, onto the respective tubular shafts l0 and 11.

Rotation of the sprockets 18 and 19 by chains 21 effects rotation of the filter discs 8 and 9, respectively. The chains 21 are coupled with sprockets 23 and 24 on a driving shaft 22 provided across the legs of the frame.

A feed inlet 25 (FIGS. 2 and 3) is provided through the casing 1 above the position corresponding to the maximum width of the V-shaped channel. A discharge outlet 26 having a scraping plate (not shown) is positioned above the minimum width of the V-shaped channel.

A pair of L-shaped horizontal connecting levers 27 and 28 (FIGS. 1, 4 and 6) each have one of their ends fixably engaging the outer ends of the shafts 5 and 6, respectively. That is, the supporting shafts are structurally integrated with the horizontal connecting levers. The horizontal levers 27 and 28 are in the plane of the axes of the shafts 5 and 6 (perpendicular to the center pin 7). Each horizontal lever extends partially around annular casing l, and the levers free ends constitute connecting pieces 29 and 30 bent normal to the outside of easing 1. Openings 31 and 32 are provided through these connecting pieces and a horizontal connecting rod 33 is inserted therethrough. The rod 33 has collars 34 and 35 and the portion of the rod between the collars fits a U-shaped recess 37 formed on a supporting member 36 (FIGS. 2 and 3) extending from casing 1. The connecting rod 33 is prevented from moving in its axial direction by the collars. Adjusting nuts 38 and 39 are threaded onto the rod 33 and contact the connecting pieces 29 and 30 to hold the horizontal levers 27 and 28 onto the rod 33.

If the forces acting upon the outer ends of the shafts 5 and 6 were only in a plane perpendicular to the axis of the center pin 7, it would not be necessary to provide special structure at the outer ends of the shafts; but, in practice, forces act upon the outer ends of the shafts in an inclined direction to the plane perpendicular to the axis of the pin 7. Therefore, it is necessary to prevent the shafts outer ends from moving upwardly. In prior devices, guide openings were provided for the shaft ends; there, however, the shafts deflected the supporting arm 3 causing the press to occasionally bind. Here, vertical connecting levers 40 and 41 are firmly fixed, as by welding, to the horizontal connecting levers 27 and 28, respectively, where the shafts 5 and 6 are supported. The vertical levers, however, may be formed integrally with the corresponding horizontal levers to form a pair of yokes. The vertical connecting levers 40 and 41 are, respectively, in planes including the sup porting shafts 5 and 6 and the axis of the center pin 7. Then, a forked part and a projected part at the free ends of the vertical levers 40 and 41 may intercross on the line of the axis of center pin 7 (see FIG. 5). An outer pin 42, coaxial with the center pin, pivotally joins the intercrossed parts and one end of the pin 42 is fixed to the casing 1.

In operation, the ratio of the maximum opening to the minimum opening of the V-shaped channel is, at first, adjusted according to the raw materials. To make this adjustment, the adjusting nuts 38 and 39 are turned on the rod 33 which is through the free ends 29 and 30 of the horizontal connecting levers 27 and 28. Since the connecting rod 36 is centered on the supporting member 36 by the collars 34, the width of the V-shaped channel between the discs is adjusted and fixed by drawing the nuts 38 and 39.

In a pressing operation, materials are subjected to a maximum pressing action where the width of the V- shaped channel becomes a minimum. The materials are released from pressing as the width of the channel gradually increases. Counter-forces become a maximum where the width is a minimum, and then suddenly approach zero after materials pass the minimum width. Accordingly, the resultant force of all the strong counter-forces acting upon the filter discs is located a little below the minimum opening position of the V-shaped channel. The resultant is a thrust force tending to push the shafts 5 and 6 outwardly and a force couple tending to pivot the supporting shafts 5 and 6 upwardly from the horizontal.

It may be assumed that the force couple may be divided into a strong force couple tending to pivot the shaft ends in a plane perpendicular to the axis of the center pin 7 and into a relatively small force couple tending to pivot the supporting shafts in a direction perpendicular to that plane. As a result, the forces tending to push the supporting shafts 5 and 6 outwardly are opposed to each other at the center pin 7, and offset one another. Further, the small force couple tending to pivot the shafts in a plane perpendicular to the axial line of the center pin 7 is divisable into a set of forces acting through the horizontal connecting levers 27 and 28 to push against the adjusting nuts 38 and 39 on the connecting rod 33 and to a set of forces opposing one another at the center pin 7. These latter forces offset each other and, thus, do not tend to move the center pin 7. Also, the force couples tending to pivot the supporting shafts 5 and 6, respectively, are divisible into forces capable of pushing the outer pin 42 and into forces capable of pulling the center pin 7 through vertical levers 40 and 41. The former forces offset each other and thus no forces tend to move the center pin 7.

In summary, strong counter-forces upon the filter discs, when raw materials are pressed, are converted to forces pulling the connecting rod 33 through the adjusting nuts 38 and 39, forces pushing the outer pin 42, and forces pulling or pushing the center pin7. The

forces act through either the horizontal connecting levers 27 and 28 or the vertical connecting levers 40 and 41. All of the forces at the center pin offset each other. Consequently, no strong forces due to the counterforces act upon the supporting arm 3 that fixes the center pin 7. Accordingly, there are only shearing stresses upon both the center pin 7 and the outer pin 42 and a pulling force acts upon the connecting rod 33. As a re sult. thereis no deflection on the supporting arm 3, and clearance along the radial edges of the filter discs 8 and 9 between the discs and the casing is kept normal. Thus, the pressing operation can be carried out smoothly and continuously.

Furthermore, the supporting arm for the center pin, the annular casing and other structure do not need special strength. Since no strains develop on the supporting arm, annular casing, etc., during pressing operations, there is no leakage of the raw materials and no binding contact of the outer annular casing with the filter discs.

While in the illustrated embodiment, the free ends of the vertical connecting levers 40 and 41 are connected above the casing 1, both the vertical levers may be downwardly directed and connected below or at the bottom of the casing. Such an arrangement adds structural strength to the apparatus and is particularly useful in larger machines or when processing materials which are quite difficult to squeeze. On the other hand, connection of free ends of the vertical connecting levers below the casing causes inconvenience when a fixed casing is utilized. In such cases, the free ends of the vertical connecting levers may be fixed pivotally by two pins, one pin for each lever, at a lower opposed side of the casing in a position as near as possible to the extended axial line of the center pin 7.

I claim:

1. A continuous press which comprises: a pair of filter discs arranged face-to-face within an outer annular casing fixed to a base frame; a pair of shafts for supporting the filter discs in a freely rotatable manner, the inner ends of said shafts pivotally connected with each other by a center pin; the center pin being supported at the center of the outer annular casing by a plate rigidly connected to said outer annular casing by a rigid arm; first connecting levers and second connecting levers fixedly supporting the outer ends of the supporting shafts; the free ends of said first connecting levers being in a plane including the intercrossed supporting shafts; the free ends of said second connecting levers being in planes including the respective supporting shafts and the axial line of the center pin; the free ends of the first connecting levers being fixed on a connecting member at the outside of the outer annular casing in a freely adjustable manner; and the free ends of the second connecting levers being engaged with each other by an outer pin on the axial line of the center pin.

2. A continuous press according to claim 1 wherein said first and second levers are integral with one another adjacent the outer ends of the supporting shafts.

3. A continuous press according to claim 1 wherein said second levers lie in planes including the respective supporting shafts and the axial line of the center pin.

4. A continuous press according to claim 1 wherein said first levers lie in a plane including the intercrossed supporting shafts.

5. A continuous press comprising:

a. A frame-supported annular casing;

b. A circular plate disposed centrally in said casing and having an opening extending transversely therethrough;

c. A center pin positioned in said plate to extend across said opening;

d. A pair of substantially oppositely extending shafts pivotally connected together at their inner ends within said opening by connection to said center pin and extending outwardly of said casing;

e. A pair of filter discs rotatably mounted on said shafts within said casing and. in faceto-face relationship with each other to define an annular channel therebetween;

. A first pair of levers, one end] of each lever of said pair fixedly supporting the outer end of one of said shafts and said levers terminating outside said casing with their respective other ends adjacent to each other and in the same plane with said shafts;

g. Means adjustably connecting said other ends of said first levers to each other to enable movement of said ends toward and away from each other thereby to selectively vary the cross-section of said channel;

h. A second pair of levers, one end of each lever of said second pair fixedly supporting the outer end of one of said shafts, and said levers terminating outside of said casing with their other ends adjacent each other, and means connecting said other ends for pivotal movement about the axial line of said center pin.

6. A continuous press according to claim 5 wherein the ends of said first and second levers fixedly supporting the shafts are integral with each other.

7. A continuous press according to claim 5 wherein said first pair of levers is in the same plane with said shafts.

8. A continuous press according to claim 5 wherein said second levers are respectively arranged to lie in the same plane with one of the shafts and with the axial line of said center pin.

9. A continuous press according to claim 1, wherein the axis of said center pin is generally vertical.

10. A continuous press according to claim 1 wherein said second pair of levers is connected together above said casing.

11. A continuous press according to claim 1 wherein said connecting means includes a member fixedly extending from said casing and a collared rod supported on said member and extending through said other ends of said first levers.

12. A continuous press according to claim 1 where said means connecting the other ends of said second levers for pivotal movement comprise an outer pin secured to said casing to extend along the axial line of said center pin through both of said levers.

Patent Citations
Cited PatentFiling datePublication dateApplicantTitle
US3559567 *Jun 24, 1969Feb 2, 1971Yoritomi RyutaroContinuous squeezing apparatus of a rotary disc type
Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US7166229 *Jul 5, 2002Jan 23, 2007Les Industries Fournier Inc.Method and apparatus for extracting liquid present in a humid mass
US7895943Aug 8, 2005Mar 1, 2011Prime Solution, Inc.Rotary fan press
US7946225Oct 19, 2009May 24, 2011Prime Solution, Inc.Rotary fan press
US7975854Oct 28, 2005Jul 12, 2011Prime Solution, Inc.Rotary fan press
US8091474 *May 23, 2011Jan 10, 2012Prime Solution, Inc.Rotary fan press
US8662315Jul 13, 2009Mar 4, 2014Prime Solution, Inc.Rotary fan press
WO2006020543A2Aug 8, 2005Feb 23, 2006Joseph DendelRotary fan press
Classifications
U.S. Classification100/158.00C, 100/168, 100/121
International ClassificationB30B9/02, B30B9/20
Cooperative ClassificationB30B9/202
European ClassificationB30B9/20B