DECANTER CENTRIFUGE

Abstract: The decanter centrifuge (1) comprises a conveyor screw (5) constructed as a hollow body with a lower average density than the lighter liquid phase of the surrounding slurry. The conveyor (5) thus flows in said liquid phase which is utilized in that the one traditional radial bearing of the conveyor is replaced by a radial support bearing (22) which only during starting and stopping of the centrifuge cooperates with the conveyor (5) in order to prevent it from contacting the bowl (2). In operation, the conveyor is thus only supported in the radial direction at the one end, entailing that the flexural rigidity of the conveyor becomes less important to the maximum allowable number of revolutions of the centrifuge which may then be increased for a given centrifuge, thereby obtaining an improved separating effect.

Description: Decanter Centrifuge. This invention relates to a decanter centrifuge comprising an axially symmetrical bowl and a conveyor screw journalled therein. Such a decanter centrifuge is employed for separ- ating a slurry supplied to the interior of the bowl into a solids phase and one or more liquid phases. This is obtained by rotating the entire centrifuge at a high number of revolutions and rotating at the same time the conveyor at a low number of revolutions relative to the bowl. The separating effect of the centrifuge and its capacity or throughput depend, on one hand, on the mag¬ nitude of the field of gravitation generated by the cen¬ trifugal force in the separating space of the bowl, i.e. on the number of revolutions and the inner diameter of the bowl and, on the other hand, on the length of the separating space. A factor of decisive importance for the maximum allowable number of revolutions is the flexural rigidity of the conveyor radially supported at both ends of the bowl because the flexural rigidity determines the cri¬ tical number of revolutions of the conveyor. This fact has hitherto implied that the λ-value of a given centrifuge - the λ-value being defined as the ratio between the length and the inner diameter of the separating space - has not in practice exceeded values of about 5. In cases where a large field of gravitation and a large capacity have been required, the resulting centri- fuges have been excessively large and expensive. This relates to the fact that a straight geometrically en¬ largement of a given decanter centrifuge has caused the costs of manufacture to increase by the cube of the scale ratio, while the capacity only increases by the square of the scale ratio. In view of the fact that, inversely, a capacity increase proportional to the extension is obtained simply by increasing the length of the centrifuge - without a corresponding rise in price - it is obvious to aim at producing decanters having λ-values exceeding said approx. 5. This is now made possible by a decanter centri¬ fuge according to the invention which differs from the prior art centrifuges in that the average density of the conveyor, i.e. the ratio between its total weight and the volume it displaces, is smaller than the density of the lighter liquid phase of the actual slurry, and in that at least one end of the conveyor in operation is unsupported in the radial direction in relation to the bowl. The invention will now be described in more de¬ tail with reference to the drawings in which Fig. 1 is a sche atical longitudinal section through a ' decanter centrifuge according to the inven- tion, in operation, and Fig. 2 is a section as Fig. 1, but through a se¬ cond embodiment of a centrifuge according to the inven¬ tion. The decanter centrifuge 1 illustrated in Fig. 1 consists by and large of a horizontal, axially symme¬ trical bowl 2 with a cylindrical section 3 and a conical section 4. The bowl 2 includes an elongated conveyor screw 5 with a central body portion 6 and surrounded by a continuous screw flight 7. The bowl is at its ends ro- tatably supported in bearings 8 and 9, respectively, and is driven via a gear 10 - for example an epicyclic gear — ensuring in a known manner that bowl 2 and conveyor 5 in operation rotate relative to each other. The suspension to be separated is supplied through an inlet 11 in the form of an inlet tube 12 and extending coaxially with the axis of rotation of the centrifuge through a central passage 13 provided in con¬ veyor body 6. The tube 12 ends in a transverse, radial passage 14 discharging into the separating space 15 of the centrifuge. The liquid level in operation is illu- strated in dotted lines 16 and solid lines 17. After se¬ paration in space 15 solids are discharged through aper¬ tures 18 while liquid is discharged through an annular outlet 19. Conveyor 5 is by and large constructed as a hol- low body with closed cavities 20 and 21 and is so dimen¬ sioned that the average density of the conveyor as a whole is smaller than the density of the ligter liquid phase of the actual suspension. In this context the average density of the conveyor is defined as the ratio between the total weight of the conveyor and the volume it displaces. In other words, the conveyor is able to flow in said light liquid phase which in operation constitutes- the " innermost portion of the "liquid tube" generated by centrifugal forces and positioned along the internal surface of the bowl wall. By adjusting the liquid level in separating space 15 - i.e. the wall thickness of the liquid tube - so that the outer surface of body portion 6 is substantial- ly covered, it is obtained that the conveyor body may be regarded as approximately fully submerged and therefore in possession of a certain positive buoyancy. The result is that the conveyor will constantly seek towards the surface which in operation will mean towards the axis of rotation. The conveyor is in other words self-centering. Said effect has in practice proven to be independent of the degree of overlapping between the outer diameter of the body portion and the inner diameter of the liquid tube, provided a certain overlapping exists. This floating and self-centering ability of the conveyor in operation is in the embodiment illustrated in Fig. 1 utilized for omitting one of the traditional radial bearings of the conveyor (in casu at the large end) . Instead there is, as illustrated, provided a ra- dial support bearing 22 the radial external surface of which is adapted to cooperate periodically with the ra¬ dial internal surface of a circular collar 23 on the conveyor body. There is a certain radial clearance be¬ tween the outer diameter of the supporting bearing and the inner diameter of the collar. Consequently, the bearing and the collar will only cooperate when the ra¬ dial oscillation of the conveyor from the axis of rota¬ tion at the large end exceeds said clearance. This will fσr instance be the case when the centrifuge does not rotate or rotates at such a low number of revolutions that the liquid tube cannot be maintained and thus has no supporting ability. The clearance is so dimensioned that the conveyor in no circumstances can contact the bowl wall. At the small end the conveyor is journalled in an ordinary way by means of a traditional radial bearing 24.. Said bearing may possibly be a spheric bearing in order to allow the slight arigular movements of the con¬ veyor which is a consequence of its radial deflection at the large end. A second possibility of allowing said an¬ gular movement is to make use of a sort of a diaphragm coupling between the drive shaft of the conveyor at the small end and the conveyor body proper. Moreover, the conveyor is, in a manner not shown, controlled in the axial direction. As mentioned in the introduction it is in current centrifuges the conveyor - or rather its flexural rigi¬ dity - which in practice determines the maximum allow¬ able number of revolutions of the centrifuge. This is due to the fact that the conveyor is con¬ stantly supported at both ends in the radial direction. By suspending, in operation, the radial support of the one end of the conveyor, as described above, the deci¬ sive influence of the flexural rigidity is reduced, meaning that the λ-ratio of the centrifuge as well as its maximum allowable number of revolutions can be in¬ creased. The diminished demands on strength makes it pos¬ sible to obtain the weight reduction necessary for con¬ structing the conveyor with an average density not ex- ceeding the density of the lighter liquid phase, inter alia because the conveyor body may now be made from sheet material. As an example of the size of the weight reduction obtained it can be mentioned that the conveyor of a given traditionally constructed centrifuge has a weight of about 400 kg, while the conveyor of a corres¬ ponding centrifuge according to the invention can be manufactured with a weight of only about 100 kg. ' Fig. 2 illustrates a second embodiment of a cen¬ trifuge according to the invention, namely a so-c"alled disc decanter 25, i.e. a centrifuge including a pile of discs as well as a conveyor screw. Centrifuge 25 comprises a double-conical bowl 26 at the one end of which a pile of discs 27 is arranged which rotates with the bowl and at the other end of which a conveyor screw 28 is mounted which in operation rotates relative to bowl 26. The actual slurry is sup¬ plied through an inlet 29 and the separated phases are discharged from the bowl through apertures 30 and outlets 35 and 36, respectively, at the left-hand end of bowl 26 in Fig. 2. The liquid level in operation is designated by 31. The mode of operation of such a centrifuge is known and will therefore not be explained in detail here. As above, conveyor 28 is constructed as a hollow body the radial journalling of which at the one end is effected by means of a periodically active, radial sup- port bearing 32 and an annular collar 33. In this case too, the other end of the conveyor is journalled by me¬ ans of an ordinary radial bearing 34 and the conveyor is likewise controlled in the axial direction in relation 5 to the drum. The radial support bearing is in both specified embodiments arranged at the "large end" of the conveyor, this being advantageous because the conveyor has there a comparatively greater buoyancy than at the small end. 10.This: relates to the fact that the body portion is conically tapered at the small end and thus accommodates less buoyancy promoting cavity volume per unit of length than, is the case at the large end. Moreover, the con¬ veyor; is not fully submerged at the small end. There is, 15 however, nothing to prevent the support bearing from be¬ ing positioned in other embodiments at the small end, and it is also possible to provide the conveyor with support bearings at both ends.

Claims: P A T E N T C L A I M S 1. A decanter centrifuge comprising an axially symmetrical bowl and a conveyor screw journalled there¬ in, characterized in that the average density of the conveyor, i.e. the ratio between its total weight and the volume it displaces, is smaller than the density of the lighter liquid phase of the actual slurry, and in that at least one end of the conveyor in operation is unsupported in the radial direction in relation to the bowl. 2. A centrifuge as claimed in claim 1, characte¬ rized in that the conveyor at the most is supported by one radial bearing and includes at least one radial sup¬ port bearing which is only effective during starting and stopping of the centrifuge with a view to prevent the conveyor from contacting the bowl.

Inventors: MADSEN NIELS FLEMMING, MADSEN, NIELS, FLEMMING
Applicants: ALFA LAVAL SEPARATION AS, ALFA-LAVAL SEPARATION A/S
Application year: 1987
Main classification: B04B1
IPC codes: B04B1