FI56644C - PRESS AV SKIVTYP FOER KONTINUERLIG AVVATTNING - Google Patents

Description

r »l ANNOUNCEMENT.

jst cp 5¾¾ (45) Patc, lt = 'dd-; it ^ V ^ (51) Kv.lk.' / Int.CI. * B 30 E 9/20 B 01 D 33/22 FINLAND —FINLAND (21) P «* nUlhakemuj - Patentansölcnlng 3278/70 (22) HakamlspSivi - Ansöknlngsdag OU. 12.70 (EN) (23) Primary Cloud — Giltighettdag Ol.12.70 (41) Has become public - Bllvlt offantllg 07 · 06.71

National Board of Patents and Registration (44) Date of Nihtivikalpano and KuLJalsals. - 30.11.79

Patents and registration 7 Aruökan utlagd och utl.ikrlften publlcerad - (32) (33) (31) Pyydetty etuoikeus — Begird prloritet 06.12.69

Japan-Japan (JP) 9753 ^ / 69 (71) (72) Ryutaro Yoritomi, 5-17-12, Koishikawa, Bunkyo-ku, Tokyo, ^ Japan-Japan (JP) (7I +) Leitzinger Oy (5 ^) Disc press The present invention relates to a device for the continuous removal of water, comprising oppositely arranged filter plates inside an annular outer shell with a fixed base part, the filter plates being freely rotatable on support shafts connected to each other by a single pin. with the jacket is supported in the middle part of the jacket, and the outer ends of the support shafts are movably supported in the guide openings in the side plates of the base part.

Such a dewatering device is described in Japanese design protection 18395/59.

In such a device, a space is formed between the two filter plates, an annular channel and its cross-section is V-shaped. The opening of this V-shaped channel is largest on one side and smallest on the other side. In this case, the aqueous raw material is fed to the largest part of the opening, and as the filter plates rotate, the aqueous raw material moves from the largest part of the opening to the smallest part of the opening, while the aqueous raw material is pressed between the filter plates. Compression and dewatering are performed as the transition occurs and the extracted 56644 water exits the back of the filter plates through small holes in the filter plates.

When the maximum compressive force is applied to the raw material, at the smaller openings of the filter plates of the device, and the support rods of the rotating filter plates are fixed, the raw material is subjected to an unusually high force if the raw material content is high the device becomes blocked or damaged by the generated counterforce.

To prevent downtime or damage to the device, a large number of rollers can be placed on the backside of the filter plates in such a device, and this large counterforce is applied to the rollers, but the structure itself becomes very complex and difficult to change.

A device for avoiding the above disadvantages is described in Japanese Patent Publication 19805/68. In this device, the substance to be dewatered is continuously pressed in an annular channel, the cross-section of which is adjustable according to the desired dewatering and the characteristics of the feedstock fed. However, the device malfunctions when high compression pressures are used.

Deformations easily occur in the support plate and the surrounding jacket, which interferes with the operation of the filter plates and filter material can leak out around the filter plates. ~

The object of the present invention is to avoid said drawbacks, and the structure is such that the forces generated during compression are directed so as to avoid bending of the support frame plate and wedging of the filter plates. The device according to the invention is characterized by connecting arms attached to respective support shafts near their outer ends passes through intersecting support cassettes, and extends beyond the outer circumference of the sheath, in addition to which the free ends of the arms are adjustably connected to the connecting member.

Some embodiments of the present invention will now be described with reference to the accompanying drawings, in which: $ 3,644

Figure 1 shows a cross-section of a first embodiment.

Figure 2 is a side view of this embodiment.

Figure 3 also shows this embodiment seen from the side with the part cut away.

Figure 4 is a front view of the same embodiment with the right side cut away.

"Figure 5 shows a top view of another embodiment.

Figure 6 shows a substantial part of another embodiment from above.

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

Figures 8a-c schematically illustrate the principle of the present invention.

In the prior art device described in the aforementioned design protection 18395/59 and patent publication 19805/68, the support shafts of the rotating filter plates are arranged in a downwardly oblique position, since such an arrangement is convenient for feeding and removing the raw material.

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Before describing the present invention with reference to embodiments, the principles related to the prior art disclosed in Japanese Patent Publication 19805/68 and the present invention, while referring to the schematic drawings shown in Fig. 8 A-C, will be described.

Each of these drawings has a pin shown by a cross-hatched circle located perpendicular to the plane of the drawing.

This pin is attached to a central circular plate at the tip of the support frame plate, and as a result, the following description can be considered as referring to the same space.

This means, assuming that the support body plate ~ forms an extension of the pin, that one end of the long pin is attached and its other end is free, with the cross-hatched circle corresponding to the free end. The right end of the rod (Fig. 8 A) is rotatably attached to the pin in a freely rotatable manner, and the line perpendicular to the part of the rod is locked, i.e. attached to the rod. In the actual model, part of the rod corresponds to the support axis and the perpendicular line corresponds to the filter plates. A perpendicular line means a round plate.

Both the rod and the round plate are rigid pieces, in which case no bending is required.

Fig. 8A shows a previously known device in which the force "a" is applied to a circular plate in the plane of the figure. In the figure, the force "a" is directed parallel to the rod to a circular plate below the rod.

In the real model, there is a force "a" counterforce caused by the filter plates compressing the raw material. The force "a" develops a force that tends to move the rod in the same direction as the force "a", and at the same time a force pair is formed that tends to rotate the rod.

When looking at the actual model as it performs the compression, the • free end of the rod, i.e. the left end, must be in such a position that the turning movement of the free end stops. To create this space, an additional force is applied to the free end of the rod, for example with a spring provided for this purpose, or also with a stop piece. In the drawings, a crossed-out rectangle means a abutment located above the free end of the rod.

When equilibrium is reached in this state, forces "b" equal to force "a" in direction and magnitude are applied to the pin and in addition other forces "c" are applied which are perpendicular to the rod but opposite to each other and of the same magnitude than the force pair, the counterpart and the pin under the influence of the force pair.

These forces "c" are perpendicular to the force "a". All these forces are located in the plane of the drawing. In the real model, the same force "" develops on the right side symmetrically with respect to the pin, and as a result the force "b" has the opposite direction and they cancel each other out.

The forces "c" are parallel and thus a force equal to "2C" is applied to the free end of the pin and bends the pin with a force twice the force "c".

It appears that the reason for the bending of the pin tip by the force M2C "on the pin depends on the abutment being placed above the free end of the rod, as shown in the drawing, against the rotational movement of the rod, and consequently a force" c "is applied to the abutment and pin due to the effect of the power pair caused by “a”.

Thanks to the present invention, the direction of the force "c" changes to the same as the force "a" and the forces "c" combine into an equal symmetrical force on the right side, and all forces acting on the pin under the influence of force "a" smooth each other and eliminate the force bend the free end of the pin.

First, the present invention will be described in more detail. As described above, the direction of the force "c" in the drawing depends on the force "a" and the position of the abutment on the rod. In the case of Figure 8A, the free end of the rod displaces the abutment under the action of the force "a" and the direction of displacement is perpendicular to the direction of the force "a".

6 56644

Thus the directions of the forces "c" are perpendicular to the direction of the forces "a". If the direction of displacement of the abutment by the force "a" is parallel to the force "a", the direction of the forces "c" will be the same as the force "a". Thus, in Fig. 8B, the free end of the rod is allowed to rotate freely, and the abutment is arranged to limit the rotational movement of the rod, as a result of which the direction of impact of the rod against the rod is made parallel to the force "a".

The rod shown in Fig. 8A is parallel to the direction of the force "a" and in Fig. 8A the rod is shown in the horizontal direction. The abutment / which is placed against the rod does not allow the direction of impact on the rod to be changed parallel to the force "a". As a result, a vertical bar is provided which is the same as the horizontal bar, and a stop piece which limits the rotational movement of the free end of the vertical bar comes to the left side of the free end of the vertical bar, as shown in Fig. 8B.

In Fig. 8B, the force pair which develops under the influence of the force "a" changes into the force under which the vertical bar strikes the abutment and into the force acting on the pin. The direction of impact on the garment is the same as the force "a" and, in addition, a counterforce parallel to the force "a" is applied to the pin.

The force "b" applied to the pin is the same as that shown in Fig. 8A, where the forces applied to the pin in Fig. 8B are indicated by the letters "b" and "c", which are forces in opposite directions. Thus, the pin is subjected to a difference of forces "b" and "c".

If the force is applied symmetrically to the right side of the pin, the opposite force can be applied to the pin, the difference of which is the difference of forces "b" and "c", respectively, depending on the force on the right side, and as a result the forces on the pin can offset each other. This means that the force that tends to bend the pin becomes zero in value.

Naturally, a force of the same magnitude is applied to the pin from the opposite direction and thus the pin is subjected to shear, but there is no force capable of bending the free end of the pin. However, in the actual model shown in Fig. 8B, there is a vertical bar between the filter plates, and the presence of such a vertical bar is detrimental.

As a result, the part (A) between the filter plates is removed from the vertical bar, and the left main part of the horizontal bar is connected in one piece with the remaining part of the lower part of the bar, as shown in Fig. 8c. In such an arrangement, the forces "b" and "c" have the same relationship to the force "a" shown in Figure 8B.

e * '1

If there is a force applied to the right side of the pin symmetrically with the force shown in Fig. 8C, a force in the opposite direction is applied to the opposite side of the pin. As a result, the pin becomes subjected to shear stress due to these forces, and those forces that would be able to bend the pin get a value of zero.

The above description illustrates the principled effect of forces.

In the prior art device described in the above-mentioned design protection application 18395/59 and patent publication 19805/68, the support shafts of the rotating filter plates are arranged in a downwardly oblique position, since such an arrangement is convenient for the supply and removal of raw material.

First, the removal of the raw material will be described.

It is necessary to remove the dewatered material by scraping from the "" point where the v-shaped groove has opened slightly after the raw material has been subjected to the greatest compressive force, and it is further recommended that the scraping be performed in a position close to horizontal level in the center. To this end, it is necessary that the smallest opening point of the V-shaped channel between the filter plates is at a level slightly lower than the horizontal plane of the center. This means that the maximum opening number of the V-shaped groove is correspondingly located at a level slightly higher than the horizontal plane of the center. As a result, the support shafts will be inclined with respect to the line joining the points of the largest aperture of the V-shaped channel and the smallest aperture of $ 6844 8, and is thus in a downwardly inclined direction. However, the description becomes more complicated if it is done using an image in which the support axes are obliquely downward, as a result of which the description uses images in which the support axes are assumed to be horizontal but inclined with respect to the horizontal plane.

Similarly, the V-shaped groove has the largest opening point and the smallest opening point on a horizontal plane in the center, but the raw material discharge section is located slightly above the horizontal plane - in this state, and as a result a special type of discharge system must be used.

Thus, the support shafts of Figure 2 are usually placed in a slightly counterclockwise rotated position. The outer annular sheath 1 is an annular part of suitable width and its lower part is fixed to the bottom part F of the frame. The inner surface of the outer annular sheath 1 is a spherical surface shown as an arc in the cross-section according to Fig. 1. The central circular or circular plate 2 is placed in the center of the outermost annular sheath and the outer surface of the central annular plate 2 is part of the spherical surface, and the thickness of the annular plate is slightly smaller on one side than on the other side. The central annular plate 2 is attached to the end of the support frame plate 3, and the support frame plate is formed in one piece with the outer annular sheath 1 and extends vertically downwards to the center (Fig. 3). ~

A rectangular opening 4 is located in the central part of the central annular ifev 2 (Fig. 3). The ends of the shafts 5 and 6 extend into a rectangular opening 4 on both sides thereof, and one end of the shafts 5 and 6 is fork-shaped and the other end is such a projection as to cause these ends to engage each other. The pin 7 is placed in a vertical position through the interconnected parts. The pin 7 passes through the center of the rectangular opening 4 and both ends of the pin are positioned and secured to the pin openings located in a vertical position in the center of the central annular plate 2 9 66644. The central annular plate 2 has space for the interconnected parts of the shafts 5 and 6 and at the same time they come into contact with the central discharge parts of the filter plates 8 and 9 to seal the free space between them.

Since the ends of the shafts 5 and 6 are connected to each other via a pin 7 within a rectangular opening 4, the positions of the ends of the shafts 5 and 6 become determined by the action of the pin 7, but the shafts are rotatably movable relative to each other in a horizontal plane.

The filter plates 8 and 9 are rotatably attached to the shafts 5 and 6. Each filter plate 8 and 9 has a front surface which is in the shape of a truncated cone and a hollow shaft 10 and 11 which is integral with the plate forming the front surface. Shafts 5 and 6 are connected to hollow shafts 10 and 11, respectively, and radial bearings 12 and 13 and axial bearings 14 and 15, respectively, are connected to interconnected parts. The front surfaces of the filter plates 8 and 9 have pits at the centers of the truncated conical surfaces and the imaginary tips of the truncated conical surfaces are in contact with each other approximately at the center of the pin 7, but the plate portions have pits 16 and 17. and 9 rotate on the shafts 5 and 6, the pit points 16 and 17 also rotate around the outer surface of the central annular plate 2. The outer surfaces of the filter plates 8 and 9 are in contact with the inner spherical surface of the outer annular sheath 1. In addition, the sprockets 18 and 19 are formed integrally with the hollow shafts 10 and 11 of the filter plates 8 and 9, and in addition, a large number of openings 20 are arranged in the truncated conical surfaces of the filter plates 8 and 9.

The side plates 21 and 22 are arranged vertically on both sides of the base part F to which the outer annular sheath 1 is attached and form a frame. Guide holes 23 and 24 are arranged in the horizontal plates in the side plates 21 and 22, as can be seen from Fig. 2, and act as control means for the movement of the outer ends of the shafts 5 and 6 in the horizontal direction. The center line of the guide openings 23 and 24 is a horizontal plane passing through the center of the central annular plate 10 56644 and perpendicular to the pin 7 connecting the shafts 5 and 6. The ends of the shafts 5-6 are movably connected to the respective guide openings 23 and 24, and the center of the ends of the shafts 5 and 6 is in a position which has moved in a horizontal direction from a position corresponding to the center of the central annular plate 2 along the guide openings. This means that the ends of the shafts 5 and 6 are fixedly placed in the rectangular opening 4 of the annular central plate by means of the connection formed by the pin 7, and the shafts 5 and 6 are in a plane inclined with respect to the horizontal direction. The ends of the shafts are movably connected to the horizontal guide openings 23 and 24.

The necessity of the control means is explained below. The degree of opening of the annular groove formed between the filter plates is smallest on the right side of the annular round plate in a plane perpendicular to the pin 7 (see Figure 3), and similarly the strongest compression of the raw material is applied at this point, so major. However, the compression of the raw material is continuously generated from the largest opening point of the V-shaped channel between the filter plates to the smallest opening point by the rotation of the filter plates. As a result, the compressive force gradually increases toward the smallest opening portion, and there is a corresponding point at which a joint resultant force of counter-forces and compressive forces is generated that is slightly lower than the horizontal position where the strongest compression occurs.

Ts. the counter-forces which develop during the pressing of the raw material while handling it not only move the shafts 5 and 6 in the horizontal direction, but also have a force component capable of moving the shafts 5 and 6 upwards. As a result, the extreme ends of the shafts 5 and 6 are forced to move to an upward but inclined position, as a result of which the control openings 23 and 24 acting as guide members are subjected to the effects of upward force components. As a result, the extreme ends of the shafts 5 and 6 can be supported without difficulty in a rotatably movable manner at the ends of the support shafts which are rotatably oriented in a vertical direction from the base plate F at the guide openings 23 and 24. In this case, where the extreme ends of the shafts 5 and 6 bend, these extreme ends move very little up and down, but such movement has almost no effect on the filtration event.

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The chains 25-26 cause the filter plates 8 and 9 to rotate via the sprockets 18 and 19. The chains 25 and 26 are connected to a spring-tensioned wheel 27 and 28, respectively, by a drive shaft 60 located in the space between the legs of the base part F. The feed opening 29 is located above the point corresponding to the largest part of the opening of the V-shaped channel formed by the filter plates, at the top of the upper annular jacket 1 (see Figures 2 and 3). In addition, the device includes an outlet 30 provided with a scraper plate and located at a point above the smallest opening of the V-shaped channel.

The most important parts of the device are described below. The ends of the L-shaped connecting arms 30 and 31 are connected and fixed to the support shafts 5 and 6 near their outermost ends. This means that the support shafts 5 and 6 are formed as a single piece with the connecting arms 30 and 31. The connecting arms 30 and 31 are in the same plane as the intersecting support shafts 5 and 6.

This means that the plane is perpendicular to the pin. The main portions of the connecting arms 30 and 31 extend into the outermost region of the outermost annular sheath 1 and the free ends of its short ends form connecting pieces 32 and 12 56644 33 which form a right angle with the outer annular sheath 1 at its outer circumference. The connecting openings 34 and 35 are attached to the connecting pieces. The rotatable shaft is positioned through the connecting openings 34 and 35 and has a screw thread at both ends of this shaft and the shaft has stop ribs 37 and 33 near the center. The part of the shaft between the stop rings 37 and 38 is connected to the U-shaped projection 40 formed in the bearing part 39 (Fig. 2), and the movement of the rotatable shaft 36 in the axial direction is prevented by the stop rings 37 and 38. The set nuts 41 and 42 are connected to the screw portion of the rotatable shaft 36 by screwing and come into contact with the connectors 32 and 33 so as to prevent the connecting arms 30 and 31 from moving outward, and restrict the positions of the rotatable shaft connectors 32 and 33. The support part is attached to the outer annular sheath 1.

When using the device, the ratio between the largest opening and the smallest opening of the V-shaped groove formed between the filter plates is adjusted, above all, depending on the raw material. For adjustment, the set nuts 41 and 42 of the rotatable shaft 36 are threaded through the free ends of the connecting arms 30 and 31. Since the stop rings 37 and 38, which rest on the bearing part 39 on both sides, prevent the rotating shaft 36 from moving in a horizontal direction, the openings between the V-shaped channel between the two filter plates are individually adjusted and fixed, i.e. locked, one of the two setting nuts 41 and 42. When the raw material is fed to the raw material supply point in the adjusted state and when the filter plates 8 and 9 rotate under the action of the chains, the raw material fed to the largest opening of the V-shaped channel moves to the filter plates 8 and 9. due to the rotational movement with them, whereby they are compressed between the filter plates. The opening of the V-shaped channel between the filter plates then becomes constantly narrower and the raw material gradually becomes more strongly compressed and at the same time water is removed from it, whereby this water flows out through the filter plates to their rear sides. The raw material is subjected to maximum compression and dewatering when the V-groove opening is smallest. The dewatered raw material is then released from the compression, since the opening of the V-shaped groove is constantly increasing, and the raw material leaves the outlet under the action of the scraper plate. The counter forces acting on the filter plates increase as the filter plates compress the raw material and remove water from it, because the opening of the V-groove becomes smaller as the filter plates rotate and because the counter forces are greatest when the opening is at their smallest, and the counter forces then decrease abruptly and reach zero when the raw material has passed the smallest gap. Consistent with this, there is a point which is subjected to the resultant force of all strong counter forces and which acts on the filter plates. This is located at a point slightly lower than the point of the smallest opening of the V-shaped groove and this position is in a plane perpendicular to the axis line of the pin 7. As a result, the large counter-forces acting on the filter plates change into an axial force tending to push the support shafts 5 and 6 outwards, and the force pair tends to rotate the support shafts 5 and 6 from a horizontal direction in a slightly oblique, upward direction. It can be assumed that the force pair can be divided into a strong force pair tending to rotationally move the shaft ends of the support shaft sections 5 and 6 in a plane perpendicular to the axis of the pin 5 and a relatively small force pair tending to rotate the support shafts perpendicular to the plane. Since the smaller of these power pairs is very small compared to the large power pair, this smaller power pair can be disregarded. Similarly, the counter forces acting on the filter plates can be divided into forces capable of pushing the support shafts 5 and 6 outwards and into a pair of forces tending to rotationally move the extreme ends of the support shafts 5 and 6. Since the intersecting support shafts 5 and 6 and the connecting arms 30 and 31 are in a plane perpendicular to the pin 7, the situation is the same as previously described in connection with the description in principle related to Fig. 8. This means that the counter-forces acting on the filter plates are divided into "" forces tending to pull the pin towards the interconnected parts of the tips of the support shafts 5 and G, and forces tending to move the set nuts 41 and 42 on the shaft 36 connecting the connecting pieces 32 and 33 to the connecting arms. 30 and 31 for the free ends into one piece with the support shafts. The smaller pair of forces has a tendency to move the outer ends of the support shafts 5 and 6 upwards in Fig. 4, and to move the upper side of the guide openings. As a result, counter-forces acting on the filter plates act as described above, and compression and dewatering can take place continuously as the filter plates 8 and 9 rotate. As described in detail above, based on the principle, most of the counterforce forces developed in the filter plates 3 and 9 due to the purls- 14 S G 6 4 4 effect of the raw material, i.e. counter forces in a plane perpendicular to the pin 7 only in a cut-like manner on the pin 7, and no force acts on the support frame plate 3 supporting the pin. In addition, the support shafts 5 and 6 move in a horizontal direction in the horizontal guide openings 23 and 24 and move only at the top of the horizontal guide openings. As a result, only a very small upward force is applied to the side plates 21 and 22.

According to the present invention, most of the counter forces acting on the filter plates are reduced during the pressing step and the pressing and dewatering step, as described above. This only results in shear forces acting on the pin and compression forces acting on the adjusting nuts, as a result of which it is not necessary that structural parts such as a support frame plate for supporting the pin, an outer annular sheath supporting the arm plate part, frame, would be particularly strong in structure.

On the other hand, efficient compression and dewatering can be performed, in which case no stresses occur in these parts of the structure. As a result, the method can be applied in a state where no leakage of raw material takes place, due to the tightening of the contact between the filter plates and the outer annular jacket.

This means that no improper contact between the outer annular jacket and the filter plates, etc. takes place in this state, whereby the normal pressing method can be implemented as a waste image process.

In the case where the method is applied so that the ratio between the largest and the smallest opening of the V-shaped groove is constant, which has been described in connection with the above-mentioned embodiment, there will be a high risk of solids leaving a large amount of water due to insufficient compression. at the point where the opening of the V-groove is smallest, for example if the amount of raw material to be fed is reduced.

If, on the other hand, the raw material is fed excessively, there is a risk of excessive compression and unnecessarily large counter-forces.

is 56644 Consequently, an embodiment for the case where the raw material supply is variable will be described below with reference to Fig. 5 et seq. In Figure 5, the screw portions of the rotatable shaft 36 are lengthened and the adjusting nuts 44 and 45 are screwed near the center of the shaft and are in contact with the connecting pieces 32 and 33 of the connecting arms 30 and 31.

In this embodiment, the angle between the support shafts 5 and 6 is changed via the connecting shafts 30 and 31 so that the set nuts 44 and 45 are rotated, as a result of which the size of the smallest opening of the annular groove between the filter plates 8 and 9 also changes.

In addition, the compressive strength of the springs 46 and 47 is adjusted by turning the nuts 41 and 42.

Thus, the raw material is compressed with a force corresponding to the compressive force of the springs 46 and 47 when the device is used. When the supply of raw material is constant, the pressing step takes place in a state in which the connecting pieces 32 and 33 of the connecting arms 30 and 31 compress the springs 46 and 47 more strongly than at the beginning of the working step, i. when the connecting pieces are in the unloaded state on the shaft 36. When the supply of raw material is small, the pressing takes place in a position where the connecting pieces 32 and 33 are in contact with the adjusting nuts 44 and 45, i. to which springs 46 and 47 are adjusted at the beginning of the work phase. When the% feed of the raw material becomes higher, the compression takes place in a state in which the connecting pieces ^ 32 and 33 compress the springs 46 and 47 more strongly than in the stationary or permanent state.

In addition, this embodiment provides the advantage that when the springs 46 and 47 expand or compress, the spring force thus provided does not change at all, as a result of which the compression event can always be performed using a nearly constant compression force.

Since it is necessary to use a constant compressive force of a predetermined amount, the springs are adjusted to a predetermined force so that both adjusting nuts 44 and 45 are rotated as well as both nuts 41 and 42 before starting the work step, as described above, and the raw material as a result, the compressive force acquires a predetermined value. If the device is built to a larger size or if stronger compression and more efficient dewatering is used, the combination of springs and nuts described above makes the method difficult to apply, resulting in the use of hydraulic oil cylinders instead, as shown in Figures 6 and 7. In Figures 6 and 7, the abutment plate 61 is attached to the center of the support frame 49 and the guide opening 50 is located in the abutment plate 61. The hydraulic oil cylinders 53 and 54 are attached to both side plates of the support frame 49. The main portions of the bolts 51 and 52 screwed to the connectors 32 and 33 are in contact on both sides with the abutment plate 61, and the end portions of the bolts are in contact with the pistons of the cylinders 53 and 54. The pin 48 projecting from the support member in the outermost annular shell passes through the guide opening 50 into the abutment plate 61. The minimum opening width of the filter plates 8 and 9 can be adjusted by turning the bolts 51 and 52. The same effect provided by the springs in Figure 5 here the cylinders 53 and 54 and the pistons 55 and 56 when the device is used. The wolves 55 and 56 move back and forth in the cylinders 53 and 54 and the process is carried out using an almost constant compressive force.

Claims (6)

56644 17 A disc press for the continuous removal of water, comprising oppositely arranged filter plates (8, 9) inside an annular outer shell (1) with a fixed base part (F), the filter plates (8, 9) being freely rotatable on support shafts (5, 6) which is connected to each other by a pin (7) supported by a support body plate (3) integral with the casing (1) in the center of the casing, and the outer ends of the support shafts (5, 6) movably supported in guide holes (23, 24) in the bottom part (F ) in side plates (21, 22), characterized by connecting arms (30, 31) attached to the respective support shafts (5, 6) in the vicinity of their outer ends in a plane passing through the intersecting support shafts (5, 6) and extending from the sheath (1) outside the outer circumference, in addition to which the free ends of the arms (30, 31) are adjustably connected to the connecting member (36). Device according to claim 1, characterized in that the arms (30, 31) at the point of attachment to the support shafts (5, 6) are oriented substantially rectangularly against them and that the connecting member (36) is adjustable to adjust the distance between the free ends of the arms (30, 31). the space between the filter plates (8, 9). Device according to Claim 1 or 2, characterized in that the guide openings (23, 24) are oriented substantially horizontally. Device according to one of Claims 1 to 3, characterized in that the connecting element (36) is provided with a flexible support element (46, 47). Device according to one of the preceding claims, characterized in that the connecting arms (30, 31) are L-shaped, the short arms of which are turned against each other and are provided with end pieces (32, 33) substantially at right angles to said short arm, in addition to which a bolt (36) extends through openings in the end piece and is provided with threaded nuts (41, 42) for bringing the arms (30, 31) together when tightened. 18 66644 Device according to Claim 4, characterized in that the resilient support element consists of a helical spring (46, 47) between the bolt (36) and the end piece.