US3698311A

US3698311A - Apparatus for continuous dehydration

Info

Publication number: US3698311A
Application number: US93562A
Authority: US
Inventors: Ryutaro Yoritomi
Original assignee: Individual
Current assignee: Individual
Priority date: 1969-12-06
Filing date: 1970-11-30
Publication date: 1972-10-17
Anticipated expiration: 1989-10-17
Also published as: FI56644C; FR2072971A5; GB1286948A; JPS5027629B1; SE362212B; DE2059856A1; SU955848A3; FI56644B; CA938563A

Abstract

A dehydrating apparatus having facially opposed filter discs mounted angularly for rotation on the inner ends of two fixed supporting shafts. The inner tip ends of the supporting shafts are joined for pivotal movement by a pin assembly which is supported by an arm plate integrated with the apparatus'' outer annular casing. The outer ends of the shaft are supported for movement in a horizontal plane by guides carried by the apparatus'' side plates. Connecting levers integrally formed with the outer ends of the supporting shafts extend to the outer periphery of the outer annular casing. The free ends of the connecting levers connected by an adjustable connecting rod which permits the space between the filter discs to be varied. In one embodiment the adjustable connecting rod is provided with a resilient member to permit the space between the filter discs to be increased if the pressing force therebetween becomes too great.

Description

United States Patent [151 3,698,311 Yoritomi 1 Oct. 17, 1972 [54] APPARATUS FOR CONTINUOUS [57] ABSTRACT DEHYDRATION A dehydrating apparatus having facially opposed filter lnventol'i YT FO Yfll'ltflllll, 547-12 discs mounted angularly for rotation on the inner ends KQlshlkawa, Bunkyo-ku, Tokyo, of two fixed supporting shafts. The inner tip ends of Japan the supporting shafts are joined for pivotal movement [22] Filed; No 30, 1970 by a pin assembly which is supported by an arm plate integrated with the apparatus outer annular casing. [2]] Appl- 93,562 The outer ends of the shaft are supported for movement in a horizontal plane by guides carried by the ap- 30 Foreign Application priority Data paratus side plates. Connecting levers integrally formed with the outer ends of the supporting shafts 1969 Japan "44/975 34 extend to ,the outer periphery of the outer annular casing. The free ends of the connecting levers connected 2% (gr. ..100/158 cfiaioobogll (1): by an adjustable connecting rod which permits the d l l 6 12] space between the filter discs to be varied. ln one em- I l u bodiment the adjustable connecting rod is provided with a resilient member to permit the space between [56] References the filter discs to be increased if the pressing force UNITED STATES PATENTS therebetween becomes too great. 3,559,567 2/1971 Yoritomi ..l00/l58 Primary ExaminerFrank A. Spear, Jr. Attorney-Robert R. Finch and Richard F. Bojanowski 10 Claims, 8 Drawing Figures PATENTEDnm 11 m2 sum 1 or a FIG.

FIG. 2,

INVENTOR. RYUTARO YORITOMI PATENTEUHBT 11 1912 I 3.698.311

sum 3 0r 3 FIG.6 54

FIG? 50 5| 32 INVENTOR.

RYUTARO YORITOMI 1 APPARATUS FOR CONTINUOUS DEI-IYDRATION BACKGROUND OF INVENTION This invention relates generally to an apparatus for continuous dehydration and in particular to a type of pressing apparatus comprising rotatable filter discs and supporting shafts wherein the shafts are supported in a manner such that increased pressing force is achieved while reducing stress applied to surrounding structures.

DESCRIPTION OF PRIOR ART Continuous dehydration apparatus comprising rotatable filter discs and supporting shafts in which the filter discs are counterposed so that their frusto-conical front sides face each other, and the supporting shafts are capable of pivotally supporting the filter discs fixed in an intercrossed state are well known. Such apparatus is disclosedQfor example, in Japanese utility model publication No. 18395/59.

In such a type of apparatus, a space is formed between two filter discs to provide an annular channel wherein its cross-section is in a V-shape.

An opening of the V-shape channel is a maximum at one side and a minimum at other side. Therefore, a water-containing raw material is charged into the maximum opening part and, when the filter discs are allowed to rotate, the water-containing raw material is transferred from the maximum opening part to the minimum opening part while the water-containing raw material is sandwiched between the filter discs.

Squeezing and dehydration are carried out with the transfer, and squeezed water is discharged to the back of the filter disc through small perforations on the filter disc.

When a maximum pressing force is applied to the raw material at the position of the minimum opening of the filter discs in the apparatus where the supporting shafts for the rotating filter discs are fixed, the raw material is pressed with an abnormally strong force if the solid content of the raw material is excessive, as compared with the width of the minimum opening of the filter discs, and sometimes the apparatus is stopped or damaged by the resulting counterforce.

To prevent stoppage or damage of the apparatus, a large number of rollers are provided at the back of the filter discs in such a type of the apparatus and said strong counterforce is supported by the rollers, but the structure itself becomes very complicated, and further it is difficult to change a ratio of the maximum opening to the minimum opening of the annular groove between the filter discs.

. An apparatus for overcoming the above disadvantages are disclosed in Japanese Patent Publication No. 19805/68.

In the above improved continuous squeezer, a ratio of the maximum opening to the minimum opening of the v-shaped annular channel can be changed at option, and a pressing degree of the raw material can be adjusted according to the necessary dehydration percentage of the raw material. Therefore, the supporting shafts of the rotatable filter discs are engaged with each other by means of a pin at the tip ends of the supporting shafts and are allowed to move pivotally around the pin to a slight degree. That is, the intercrossing state of the supporting shafts, which rotatably support the filter discs, can be adjusted at option, and the outer ends of the supporting shafts can be fixed :in said adjusted state. In the improved continuous squeezer, the position at which the tip ends of the supporting shafts are engaged with each other must be fixed, and therefore a supporting arm plate is provided at a center of an outer annular casing arranged around the filter discs integrally with the outer annular casing, and a center circular plate is arranged at the tip end of the supporting arm plate. The engaging parts at the tip ends of said two supporting shafts are positioned at a center hole of the center circular plate, and these supporting shafts are engaged with each other by means of the pin.

In this improved continuous squeezer, the ratio of the maximum opening to the minimum opening of the V-shaped annular channel can be adjusted at option according to the raw material, and therefore operation can be effectively carried out at the necessary pressing ratio according to the raw material. The raw material can be pressed and dehydrated with a strong pressing force by sufficiently increasing the pressing ratio, that is, by sufficiently reducing a width of the V-shaped channel of the filter discs at the maximum pressing part, when a powerful de-hydration is required for the raw material. However, a strong counterforce is developed with an increase in the pressing force. To support the counterforce, a frame body, to which the shaft ends of the supporting shafts of the filter discs are fixed and which is extended to the sides of the outer annular casing, must be more rigid. However, a strong force is also consequently applied to the center circular plate, which supports the engaging part of said two supporting shafts, and therefore a deflection develops on the supporting arm plate of the center circular plate and the outer annular casing integrated with the center circular plate.

As a result, a contact between the outer peripheries of the filter discs and the inner periphery of the outer annular casing is brought into an abnormal state, and there is a fear to make the operation impossible. The refore, it is necessary to make more rigid the outer annular casing and the supporting arm plate, or increase a clearance between the outer annular casing and the filter discs. However, in the latter case, there will occur a leakage of the raw material.

OBJECTS OF INVENTION Accordingly, it is an object of the present invention to prevent the supporting arm plate of the center circular plate from a deflection due to a strong counterforce developed by the pressing of the raw material and at the same time to prevent the outer peripheries of the filter discs from poor contact with the inner periphery of the outer annular casing.

Another object of the present invention is to provide an apparatus, where the supporting shafts for the counterposed filter discs are pivotally connected with each other by a pin and a supporting arm plate which is provided to fix the pin to the predetermined position, characterized by reducing a force applied to the supporting arm plate, particularly the force to bend the supporting arm plate and finally effecting a powerful dehydrating operation while reducing strengths of the outer annular casing, frame and other structures.

BRIEF DESCRIPTION OF DRAWINGS FIG. 1 shows a top cross-sectional view of one embodiment of this invention.

FIG. 2 is a side view of the embodiment of FIG. 1.

FIG. 3 is a side view of the embodiment of FIG. 2 with a part thereof cut away.

FIG. 4 is a front view wherein the right half is cut away.

FIG. 5 is a plan view of a lever arrangement which can be used in the embodiments shown in FIGS. 1-4.

FIG. 6 is a plan view of another lever arrangement which can be used.

FIG. 7 is a front view of the embodiment shown in FIG. 6.

FIG. 8 is a schematic view for illustrating the principle upon which this invention is based.

DESCRIPTION OF PREFERRED EMBODIMENT Before the present invention is explained, an explanation is made about the principles between the prior art Japanese Patent Publication No. 19805/68 and the present invention with reference to FIG. 8.

In each drawing, a black circle represents a pin and is arranged in a direction perpendicular to the drawing.

The position of the actual pin is fixed in the center circular disc at the tip end of the supporting arm plate, and therefore the following assumption can be regarded as an expression of the same state.

That is, according to the assumption the supporting arm plate constitutes a portion of the pin, one end of a long pin is fixed, whereas the other end is in a free state; and the black circle represents its free end. There is a plate member as represented by the full line, whose end is pivotally supported by the pin in a freely pivotally movable state, and the full line in a direction perpendicular to the plate member is fixed. In the actual model, the plate member corresponds to the supporting shaft, and the perpendicular full line corresponds to the filter discs.

The perpendicular full line may be regarded as a circular plate. Both the plate member and the circular plate are rigid bodies, and it is assumed not necessary to take any bending into consideration. FIG. 8(a) shows a well-known example, where a force a is applied to the circular plate along the surface of the drawing. In the drawing, a force a in parallel with the plate member is applied to the circular plate under the plate member.

In the actual model, the force a is a counterforce appearing when the filter discs press the raw material.

The force a applied to the circular plate develops a force capable of moving the plate member toward the same direction as that of the force a, and at the same time a couple of forces capable of rotating the plate member.

To take a state of the actual model during the pressing operation into consideration, the free end of the plate member must be in a state where the pivotal movement of the free end is stopped.

To attain this state, the free end of the plate member is subject to an external force, for example, a spring may be arranged for that purpose, or a stop piece may be provided.

In the drawing, a stop piece as represented as a black rectangular shape is provided above the free end of the plate member.

When an equilibrium is established in that state, forces b, which are equal to the force a in direction and magnitude are applied to the pin by pin by the force a, and further another force 0, which are in a direction perpendicular to the plate member but are opposite to each other and are equal to the couple of forces in magnitude, are applied to the stop piece and the pin by the couple of forces.

Said forces c are in a direction perpendicular to the force a. All of these forces appear along the surface of the drawing. In the actual model, the same force develops at the right side in a symmetrical relation to the pin, and therefore the force b are in a direction opposite to each other and are offset.

The forces 0 are in the same direction and therefore the force in a magnitude of 2C is applied to the free end of the pin to bend the pin by the force in the double magnitude of c.

It seems that the cause for bending the tip end of the pin by applying a force 2C to the pin is due to the fact that, in case that the free end of the plate member is made in a freely swinging state, and a force a is applied thereto, the pivotal movement of the free end of the plate member is restricted and thus the stop piece is provided above the free end of the plate member, as shown in the drawing, against the pivotal movement of the plate member, and as a result, force 0 in a direction perpendicular to a are applied to the stop piece and the pin by a couple of forces developed by a.

According to the present invention, the direction of the force 0 is changed to that of the force a to offset the forces 0 with an equal symmetrical force at the right side, bring all the forces applied to the pin by the force a into an offsetting relation and eliminate the force capable of bending the free end of the pin.

First of all, explanation will be made of the present invention in more detail. As explained above, the direction of the force c depends upon the direction of the force a and the position of the stop piece to the plate member. In the case of FIG. 8(a), the free end of the plate member pushed the stop piece by the force a, and the pushing direction is at a right angle to the direction of the force a.

Therefore, the direction of forces c is at right angle to the direction of the force a. If the pushing direction of the stop piece by the force a is in the same direction as that of the force a, the direction of the forces c will be in the same direction as that of the force a.

Therefore, in FIG. 8(b), the free end of the plate member is allowed to freely swing and a stop piece is provided to restrict the pivotal movement of theplate member, whereby the pushing direction of the stop piece by the plate member is brought into the same direction as that of the force a.

The plate member of FIG. 8(a) is in parallel with the direction of the force a, and in FIG. 8(a) the plate member is shown horizontally.

A stop piece is provided against the plate member, and thus it is impossible to bring the pushing direction of the stop piece by the plate member into the same direction of the force a.

As a result, a vertical plate member is supplemented, which is integral with the horizontal plate member, and a stop piece capable of restricting the pivotal movement of the free end of the vertical plate member is provided at the left side of the free end of the vertical plate member as shown in FIG. 8(b).

In FIG. 8(b), a couple of forces developed by the force a is converted to a force capable of allowing the vertical plate member to push the stop piece and a force capable of acting upon the pin.

The pushing direction of the stop piece is the same as that of the force a, and therefore a reverse force, which is in the same direction as that of the force a, is applied to the pin.

The force b applied to the pin are the same as shown in FIG. 8(a), the forces applied to the pin in FIG. 8(b) are represented by b and c, which are reverse forces in the same direction.

As a result, a force in difference between b and c is applied to the pin.

If a force is provided at the right side in a relation symmetrical to the pin, a force in a reversed direction can be applied to the pin in difference between b and 0, depending upon the force at the right side, and consequently the force applied to the pin can be offset with one another. That is, the force capable of bending the pin is made to zero.

Of course a force in the same magnitude is applied to the pin in a reversed direction, and thus the pin is subject to shearing, but there is no force at all, which is capable of bending the free end of the pin. However, in the actual model as shown in FIG. 8( b), there is the vertical plate member between the filter discs, and such a presence of the vertical plate member is very inconvenient. Therefore, a portion (a) of the vertical plate member positioned between the filter discs is eliminated, and the left end part of the horizontal plate member is integrally connected to the remaining portion of the lower end of the vertical plate member, as shown in FIG. 8(C).

In such an arrangement, the forces b and 0 against the force a are in the same relation as shown in FIG. 8( b).

If there is a force at the right side of the pin in a rela tion symmetrical to the force at the left side in FIG. 8(0), a reverse force will be applied, in a reverse direction to the pin.

The pin is therefore subject to shearing by these forces and the force capable of bending the pin is made to zero.

In the foregoing explanation, the principle of the action of forces has been illustrated.

Now, the embodiment of the present invention will be explained, referring to the accompanying drawings.

In the prior art embodiments as disclosed in Utility Model Publication No. 18395/59 and Patent Publication No. 19805/68 as mentioned above, the supporting shafts for the rotating filter discs are arranged in a downward-inclined direction, since such an arrangement is convenient for the charging and discharging of the raw material.

That is, explanation is made, first of all, of the discharging of the raw material.

It is necessary to discharge the dehydrated materials by scraping at a position where the V-shaped channel is a little opened after the raw materials have been subjected to the maximum pressing force, and further it is preferable that the scraping is carried out at a position near to the horizontal level at the center. Therefore, it is necessary that the minimum degree of opening of the V-shaped channel of the filter discs be positioned at a level a little lower than the horizontal level at the center.

That is, the maximum degree of opening of the V- shaped channel is correspondingly positioned at a level a little higher than the horizontal level at the center. As a result, the supporting shafts are inclined in a direction of a line connecting the maximum opening position to the minimum opening position of the V-shaped channel, and therefore are in a downward-inclined direction. However, explanation will be more complicated if the explanation is made using an illustration where the supporting shafts are in a downward-inclined direction, and therefore the explanation is made using an illustration where the supporting shafts are assumed to be in a horizontal direction but in an inclined state within the horizontal level.

Accordingly, the maximum opening part and the minimum opening part of the V-shaped channel are at a horizontal level at the center, but the discharging part of the raw materials are positioned a little above the horizontal level in that state, and therefore a discharging device of special type must be used.

Therefore, the supporting shafts as shown in FIG. 2 are usually used in a little rotated state towards the clock-wise direction. The outer annular casing l is an annular member having a proper width, and its bottom part is fixed to a base plate F of the frame. An inside periphery of the outer annular casing l constitutes a position of a spherical surface which is represented as a position of the arc in the crosssectional view of FIG. 1.

A center circular plate 2 is arranged at the center of the outer annular casing and the outer periphery of the center circular plate 2 constitutes a portion of the spherical surface, and the thickness at one side of the circular plate is a little smaller than that at the other side. The center circular plate 2 is fixed to the tip end of the supporting arm plate 3, and the supporting arm plate is integrally formed with the outer annular casing 1, and extended vertically downward to the center (FIG. 3).

A rectangular opening 4 is provided at the center part of the center circular plate 2 (FIG. 3). Tip ends of the shafts 5 and 6 enter into the rectangular opening 4 from both sides thereof, and one of the tip ends of the shafts 5 and 6 is a forked end, and other tip end is a projection whereby these tip ends are engaged with each other. A pin 7 is inserted through the engaged parts in a vertical state. The pin 7 passes through the center of the rectangular opening 4 and both ends of the pin are inserted and fixed to pin openings vertically provided at the center part of the center circular plate 2. The center circular plate 2 provides a space for the engaged parts of the tip ends of the shafts 5 and 6 and at the same time comes in contact with the center recess parts of the filter discs 8 and 9 to seal a clearance therebetween.

Since the tip ends of the shafts 5 and 6 are engaged with each other by the pin 7 within the rectangular opening 4, the position of the tip ends of the shafts 5 and 6 is fixed by the pin 7, but the shafts are pivotally movable, relative to each other in a horizontal level around the pin 7.

The filter discs 8 and 9 are rotatably supported on the shafts 5 and 6. Each of the filter discs 8 and 9 has a frusto-conical front disc and a hollow back shaft 10 or 11 integrated with the front disc. The shafts and 6 are engaged with the hollow back shafts 10 and l 1, respectively, and journal bearings 12 and 13 and thrust bearings 14 and 15 are provided at the engaging parts thereof, respectively. The front faces of the filter discs 8 and 9 have recesses at the center of the frusto-conical surfaces, and imaginary top ends of frusto-conical faces are in contact with each other almost at the center of said pin 7, but the tip parts of the discs are recesses 16 and 17. The recesses 16 and 17 are loosely engaged with the outer periphery of the center circular plate 2 from both ends, and when the filter discs 8 and 9 rotate on the shafts 5 and 6 the recesses 16 and 17 rotate around the outer periphery of the center circular plate 2. The outer peripheries of the filter discs 8 and 9 are in contact with the inner spherical periphery of the outer annular casing 1. Further, sprockets 18 and 19 are integrally formed on the hollow shafts 10 and 11 of the filter discs 8 and 9, and furthermore a large number of perforations 20 are provided on the frusto-conical faces of the filter discs 8 and 9.

Side plates

21 and 22 are vertically provided at both sides of the base plate F to which the outer annular casing 1 is fixed, and form a frame. On the

side plates

21 and 22, guide

openings

23 and 24 are provided in a horizontal direction, as shown in FIG. 2, and serve as guides for the movement of the outer end parts of the shafts 5 and 6 in a horizontal direction. The center line of the

guide openings

23 and 24 is in a horizontal level which passes through the center of the center circular plate 2 and is perpendicular to the pin 7 engaging the shafts 5 and 6. The outer ends of the shafts 5 and 6 are engaged with the

corresponding guide openings

23 and 24 in a movable manner, and the centers of the outer ends of the shafts 5 and 6 are in a position horizontally moved from the position corresponding to the center of the center circular plate 2 along the guide openings. That is to say, the tip ends of the shafts 5 and 6 are fixedly positioned within the rectangular opening 4 of the center circular plate by engagement by the pin 7, and the shafts 5 and 6 extend horizontally in an inclined direction. The outer ends of the shafts are engaged with the

horizontal guide openings

23 and 24 in a movable manner. Necessity for the guides is explained hereunder:

' The degree of opening of the annular channel formed by the filter discs is a minimum at the right side of the center circular plate in a plane perpendicular to the pin 7 (see FIG. 3), and accordingly the maximum pressing of the raw materials is carried out at that point, and its counterforce is the maximum. However, the pressing of the raw materials is continuously carried out from the maximum opening part to the minimum opening part of the V-shaped channel formed by the filter discs by rotation of the filter discs. Therefore, the pressing force gradually increases towards the minimum opening part, and accordingly a point to which a resultant force the counter-forces to the pressing force is applied is positioned a little lower than the horizontal position where the maximum pressing is carried out. In other words, the counterforces developed by the pressing of the raw materials during the operation not only moves, strictly speaking, the shafts 5 and 6 in a horizontal direction but also has a component of a force capable of moving the shafts 5 and 6 upward. As a result, the outer ends of the shafts 5 and 6 are forced to move in an upward, but inclined direction, and thus the

guide openings

23 and 24 are provided as guides for repressing the upward component of the force. Therefore, the outer ends of the shafts 5 and 6 can be supported without any trouble, in a pivotably movable manner at the tip ends of supporting levers projected in a vertical direction in a pivotally movable manner from the base plate F in place of the

guide openings

23 and 24. In that case, when the outer ends of the shafts 5 and 6 swing, the outer ends very slightly move up and down, but such a movement has almost no influence upon the filtering operation.

Rotation of the sprockets 18 and 19 on the filter discs 8 and 9 is given by chains 25 and 26. The chains 25 and 26 are coupled with

sprockets

27 and 28 on a driving shaft 60 provided in a bottom space formed by the legs of the base plate F, respectively. A charge inlet 29 is provided above the position corresponding to the maximum opening part of the V-shaped channel formed by the filter discs at the outer periphery of the outer annular casing 1 (see FIGS. 2 and 3).

Further, a discharge outlet 30 having a scraping plate is provided at a position above the minimum opening part of the V-shaped channel. Now, explanation is made of the important parts. Tip ends of L-shaped connecting

levers

30 and 31 are engaged and fixed to the supporting shafts 5 and 6 near the outer ends thereof. That is, the supporting shafts 5 and 6 are in an integrated structure with the connecting

levers

30 and 31. The connecting levers 30 and 31 are in a plane including the inter-crossed supporting shafts 5 and 6. That is, the plane is perpendicular to the pin. The end parts of the connecting

levers

30 and 31 extend to the outer periphery of the outer annular casing l, and the free ends at the tip ends thereof constitute connecting

pieces

32 and 33 formed at a right angle to the outer annular casing 1 at the outer periphery thereof. Connecting

openings

34 and 35 are provided on the connecting pieces. A connecting rod is inserted through the connecting

openings

34 and 35, and both end parts of the connecting rod are in a screw structure, and the rod has

collars

37 and 38 near the center. The portion of the rod between the

collars

37 and 38 are engaged with a U-shaped recess 40 formed on a supporting member 39, FIG. 2, and the connecting rod 36 is prevented from a movement in the axial direction by the

collars

37 and 38. Adjusting

nuts

41 and 42 are engaged with the screw parts of the connecting rod 36 through screwing and come in contact with the connecting

pieces

32 and 33 to prevent the connecting

levers

30 and 31 from the outward movement and restrict the positions of the connecting

pieces

32 and 33 on the connecting rod 36. The supporting member is fixed to the outer annular casing 1.

In the operation, a ratio of the degree of the maximum opening to that of the minimum opening of the V-shaped channel formed by the filter discs is, at first, adjusted according to the raw materials. To make the adjustment, the adjusting

nuts

41 and 42 of the connecting rod 36 are inserted through the free ends of the connecting

levers

30 and 31 and are turned. Since the connecting rod 36 is prevented from the horizontal movement owing to the

collars

37 and 38 pinching the supporting member 39 at both sides, the opening of the V-shaped channel between these two filter discs is individually adjusted and fixed by turning the

individual adjusting nuts

41 and 42. When the raw materials are charged into a raw material inlet in the adjusted state and the filter discs 8 and 9 are allowed to rotate by revolving movement of the chains, the raw materials charged at the maximum opening of the V-shaped channel are transferred by rotation of the filter discs 8 and 9 while being pinched by the filter discs. Theopening of the V-shaped channel of the filter discs is gradually narrowed and the raw materials are gradually strongly pressed and dehydrated, while water flows through the filter discs to their backsides. The raw materials undergo maximum pressing and dehydrating action, where the opening of the V-shaped channel becomes a minimum. Then, the dehydrated raw materials are released from the pressing, because the opening of the V-shaped channel is gradually increased, and the raw materials are discharged from the discharge outlet by the scraping plate. The counter-forces acting upon the filter discs when the filter discs press and dehydrate the raw materials, increase, since the opening of the V- shaped channel becomes smaller with the rotation of the filter discs, and the counterforces become a maximum where the opening is a minimum, and then are suddenly decreased and become zero after having passed the minimum opening. Accordingly, a point to which a resultant force of all the strong counterforces acting upon the filter discs is applied, is located at a position a little below the minimum opening position of the V-shaped channel, and said position is in a plane perpendicular to the axial line of the pin 7. As a result, the strong counterforces acting on the filter discs are converted to a thrust force capable of pushing the supporting shafts and 6 outwards, and a couple of forces capable of pivotally moving the supporting shafts 5 and 6 from the horizontal direction towards a little inclined, upward direction. It is assumable that the couple of forces can be divided to a strong couple of forces capable of pivotally moving the shaft ends of the supporting shafts 5 and 6 in a plane perpendicular to the axial line of the pin 7 and a relatively small couple of forces capable of pivotally moving the supporting shafts in a direction perpendicular to the plane. Since the small couple of forces is very small, as compared with the strong couple of forces, the small couple of forces can be disregarded. Accordingly, the counterforces acting upon the filter discs can be divided to forces capable of pushing the supporting shafts 5 and 6 outwards and a couple of forces capable of pivotally moving the outer end parts of the supporting shafts 5 and 6. Since the intercrossed supporting shafts 5 and 6 and the connecting

levers

30 and 31 are in a plane perpendicular to the pin 7, the state is the same as explained before as to the principle, referring to FIG. 8. That is, the counterforces on the filter discs are divided to forces capable of pulling the pin towards each other at the engaging parts of the tip ends of the supporting shafts 5 and 6, and forces capable of pushing the adjusting

nuts

41 and 42 of the connecting rod 36 which connects the connecting

pieces

32 and 33 at the free ends of the connecting

levers

30 and 31 integrated with the supporting shafts. The small couple of forces tends to move the outer ends of the supporting shafts 5 and 6 upward in FIG. 4, and pushes the upper side of the guide openings. As a result, the counterforces acting upon the filter discs are supported in the manner explained above and the pressing and dehydrating can be continuously carried out while rotating the filter discs 8 and 9. As has been explained in detail before as to the principle, most of the counterforces developed upon the filter discs 8 and 9 by the pressing of the raw materials, that is the counterforces in the plane perpendicular to the pin 7, is reduced only to a shearing force upon the pin 7, and no force is applied at all to the supporting arm plate 3 which supports the pin. Further, the supporting shafts 5 and 6 move in a horizontal direction within the

horizontal guide openings

23 and 24 and only slightly push the upper side of the horizontal guide openings. Therefore, only a very small upward force is applied to the

side plates

21 and 22. According to the present invention, most of the counterforces upon the filter discs due to the pressing during the pressing and dehydrating operation is reduced, as explained above, only to forces to shear the pin and press the adjusting nuts, and accordingly it is not necessary that the structures, such as the supporting arm plate for supporting the pin, the outer annular casing for integrally supporting the arm plate, the frame guiding the outer ends of the supporting shafts, etc. have a special strength.

On the other hand, a powerful pressing and dehydrating operation can be carried out and there occurs no strain in said structures during the powerful pressing and dehydrating operation. Therefore, the operation can be carried out in a state where no leakage of the raw materials takes place, by making tighter the contact between the filter discs and the outer annular casing. That is, no improper contact between the outer annular casing and the filter discs, etc. occur in that state, and the normal pressing operation can be continuously carried out.

In case that the operation is continued at a fixed ratio of the maximum degree to the minimum degree of the opening of the V-shaped channel as it is, as explained in the above embodiment, there are a lot of chances for discharging solid materials containing a large amount of water without sufficient pressing at the minimum opening position of the V-shaped channel, for example, if the amount of raw materials to be charged is decreased.

On the contrary, if the raw materials are supplied in excess, there is a chance for carrying out excessive pressing and developing excessive large counterforces. Therefore, explanation is made of an embodiment for a case where the supply of the raw materials is unstable, referring to FIG. 5 et seq. In FIG. 5, the screw parts of the connecting rod 36 are made longer, and adjusting

nuts

44 and 45 are screwed onto the rod near the center of the rod and are in contact. with the inside surfaces of the connecting

pieces

32 and 33 of the connecting

levers

30 and 31.

Nuts

41 and 42 are screwed at both outer ends of the connecting rod 36 and springs 46 and 47 are inserted between the nuts 41 and 42 and the connecting

pieces

32 and 33.

In this embodiment, an intercrossing angle of the supporting shafts 5 and 6 is changed through the connecting

levers

30 and 31 by turning the adjusting

nuts

44 and 45 and therefore the width of the minimum opening part of the annular channel formed by the filter discs 8 and 9 is adjusted thereby.

Further, the degree of compression of the

springs

46 and 47 is adjusted by turning the nuts 41 and 42. Accordingly, the raw materials are pressed by the force corresponding to the degree of compression of the

springs

46 and 47 during the operation. In case that the supply of raw materials is stationary, the pressing operation is carried out in a state where the connecting

pieces

32 and 33 of the connecting

levers

30 and 31 rather compress the

springs

46 and 47 then at the start of the operation, that is, where the connecting pieces are in a floated state on the connecting rod 36. In case that the supply of raw materials is short, the pressing is carried out in a state where the connecting

pieces

32 and 33 are in contact with the adjusting

nuts

44 and 45, that is, where the

springs

46 and 47 were adjusted at the start of the operation. Further, in case that the supply of raw materials is increased, the pressing is carried out in a state where the connecting

pieces

32 and 33 further compress the

springs

46 and 47 than at the stationary state. However, even if the

springs

46 and 47 are expanded or contracted, the exerting force is not changed almost at all, and therefore, the pressing operation can be always carried out with an almost constant pressing force.

Since it is necessary to make a constant pressing force to a predetermined force, the springs are adjusted to the predetermined force by turning both adjusting

nuts

44 and 45 as well as both

nuts

41 and 42 before the start of the operation, as explained above, and the force for pressing the raw materials is thereby made to the predetermined force. In case that the apparatus is scaled up or more powerful pressing and the dehydration are carried out, a combination of the springs and nuts as mentioned above makes the operation difficult, and consequently oil hydraulic cylinders are used, as shown in FIGS. 6 and 7.

In FIGS. 6 and 7, a supporting plate 61 is fixed to the center of a supporting frame 49, and a guide opening 50 is provided on the supporting plate 61. Oil

hydraulic cylinders

53 and 54 are fixed to both side plates of the supporting frame 49. Head parts of

bolts

51 and 52 screwed to the connecting

pieces

32 and 33 are in contact with both sides of the supporting plate 61 and the end parts of the bolts are in contact with rams of the

cylinders

53 and 54. The pin 48 projected from the supporting element of the outer annular casing is penetrated through the guide opening 50 of the sup porting plate 61. The width of the minimum opening part of the filter discs 8 and 9 can be adjusted by tuming the

bolts

51 and 52. The action as done by the springs in said FIG. is carried out by the

cylinders

53 and 54, and rams 55 and 56 during the operation. The

rams

55 and 56 go into or out of the

cylinders

53 and 54 and the operation is carried out with an almost constant pressing force.

What is claimed is:

1. An apparatus for continuous dehydration, which comprises filter discs arranged face-to-face within an outer annular casing whose bottom part is fixed, tip ends of supporting shafts for supporting the filter discs in a freely rotatable manner being engaged with each other by a pin, the pin being supported at the center of the outer annular casing by a supporting arm plate integrated with the outer annular casing, outer ends of the supporting shafts being supported in a movable manner b uides on a base late conne tin levers integrally f n ned with the sutiporting shafts a positions near the outer ends thereof being in a plane including the intercrossed supporting shafts and being extended to the outer periphery of the outer annular casing, and their free ends being adjustably fixed on a connecting element.

2. A dehydrating apparatus comprising facially opposed discs mounted for rotation about the inner ends of supporting shafts, a support structure for loosely supporting the outer ends of said supporting shafts, the inner tips of said supporting shafts being fixed to each other by a pivotal point which is held in fixed position by an arm extending to said support structure, a lever arm angularly connected to each of the outer ends of said supporting shafts and an adjustable connecting member joining the free ends of each of said lever arms so that on adjustment thereof the space between said facially opposed discs can be varied.

3. The apparatus of claim 2, including an enclosure for said facially opposed discs, said enclosure having inlet and outlet ports.

4. The apparatus of claim 3 wherein said facially opposed discs are perforated.

5. The apparatus of claim 4, including guide means carried by said support structure for providing support and movement of said supporting shafts in a substantially horizontal plane.

6. The apparatus of claim 5 wherein said adjustable connecting member includes a yieldable resilient means.

7. The apparatus of claim 6 wherein the lever arms are L-shaped, the short legs of which oppose each other, said legs having end pieces substantially perpendicular thereto, a rod passing through openings in said end pieces has its ends threaded to receive bolts which urge the lever arms together when tightened.

8. The apparatus of claim 7 wherein a coiled spring is interposed between the bolt and end pieces.

9. The apparatus of claim 8 wherein said facially op posed discs oppose each other on an angle and includes a means for rotating said facially opposed discs in the same direction and at constant speed to provide a constantly increasing pressing action therebetween.

10. A continuous disc-type press comprising: a substantially annular casing; a pair of supporting shafts pivotally connected at their inner ends within said casing and extending through openings in said casing; a pair of frusto-conical expressing discs rotatably mounted .on said supporting shafts; a pin supported at the center of said casing upon which said supporting shafts are pivoted; an arm extending from said casing to support said pin; guide means formed on said casing to guide the outer ends of said shafts; and lever members fixed to the outer ends of said shafts, said levers being extended around said casing in a plane generally including said supporting shafts, the free ends of said levers being adjustably fixed to a connecting element attached to said casing.

Claims

1. An apparatus for continuous dehydration, which comprises filter discs arranged face-to-face within an outer annular casing whose bottom part is fixed, tip ends of supporting shafts for supporting the filter discs in a freely rotatable manner being engaged with each other by a pin, the pin being supported at the center of the outer annular casing by a supporting arm plate integrated with the outer annular casing, outer ends of the supporting shafts being supported in a movable manner by guides on a base plate, connecting levers integrally formed with the supporting shafts at positions near the outer ends thereof being in a plane including the intercrossed supporting shafts and being extended to the outer periphery of the outer annular casing, and their free ends being adjustably fixed on a connecting element.

4. The apparatus of claim 3 wherein said facially opposed discs are perforated.

7. The apparatus of claim 6 wherein the lever arms are ''''L''''-shaped, the short legs of which oppose each other, said legs having end pieces substantially perpendicular thereto, a rod passing through openings in said end pieces has its ends threaded to receive bolts which urge the lever arms together when tightened.

9. The apparatus of claim 8 wherein said facially opposed discs oppose each other on an angle and includes a means for rotating said facially opposed discs in the same direction and at constant speed to provide a constantly increasing pressing action therebetween.

10. A continuous disc-type press comprising: a substantially annular casing; a pair of supporting shafts pivotally connected at their inner ends within said casing and extending through openings in said casing; a pair of frusto-conical expressing discs rotatably mounted on said supporting shafts; a pin supported at the center of said casing upon which said supporting shafts are pivoted; an arm extending from said casing to support said pin; guide means formed on said casing to guide the outer ends of said shafts; and lever members fixed to the outer ends of said shafts, said levers being extended around said casing in a plane generally including said supporting shafts, the free ends of said levers being adjustably fixed to a connecting element attached to said casing.