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WO1982001668A1 - Centrifugeuse avec fond deplacable pour l'evacuation de la matiere solide - Google Patents

Centrifugeuse avec fond deplacable pour l'evacuation de la matiere solide Download PDF

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Publication number
WO1982001668A1
WO1982001668A1 PCT/DE1981/000196 DE8100196W WO8201668A1 WO 1982001668 A1 WO1982001668 A1 WO 1982001668A1 DE 8100196 W DE8100196 W DE 8100196W WO 8201668 A1 WO8201668 A1 WO 8201668A1
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WO
WIPO (PCT)
Prior art keywords
floor
push
drive shaft
drum
axis
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/DE1981/000196
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German (de)
English (en)
Inventor
Georg Schilp
Reinhold Schilp
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Individual
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Individual
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Filing date
Publication date
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Publication of WO1982001668A1 publication Critical patent/WO1982001668A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B3/00—Centrifuges with rotary bowls in which solid particles or bodies become separated by centrifugal force and simultaneous sifting or filtering
    • B04B3/02—Centrifuges with rotary bowls in which solid particles or bodies become separated by centrifugal force and simultaneous sifting or filtering discharging solid particles from the bowl by means coaxial with the bowl axis and moving to and fro, i.e. push-type centrifuges

Definitions

  • the invention relates to a pusher centrifuge with a sieve drum and a rotatable push floor for the axially directed transport of the solid separated by a feed from a suspended suspension to the discharge end of the sieve drum, the push floor having an axis of inclination with respect to the axis of rotation of the sieve drum.
  • Such pusher centrifuges are used for the mechanical dewatering of granular solids or for the mechanical separation of suspensions into their constituents, solid and liquid.
  • Shear centrifuges are also used to spin-dry granular solids, wash solid layers and for extraction purposes in the chemical, mining, food and processing industries as well as in other branches of industry.
  • the push centrifuge differs in its design from other centrifuges in that the separated solids at the discharge end of the sieve drum, which is usually closed with an axially normal bottom, is conveyed by means of the push floor, which is axially displaceably mounted in front of the sieve drum bottom to the axis of rotation of the drive shaft. It extends close to the inner wall of the screen covering of the screening drum and leaves only a small radial gap.
  • the suspension to be separated is fed through a feed pipe in front of the moving floor.
  • the solid which is mostly held back by the usually cylindrical sieve drum, is pushed forwards over its entire circumference through the sliding floor, which reciprocates in the axial direction at a frequency of 0.5 - 2 Hz, towards the discharge end of the sieve drum.
  • the released ring gap between the retracting moving floor and the solid is continuously over the feed tube, which is usually connected to a rotating acceleration funnel, filled with suspension.
  • a rotating acceleration funnel filled with suspension.
  • a thrust centrifuge is known in US Pat. No. 2,350,041, in which the solid is transported in the sieve drum through a tumbling push floor. The wobbling movement of the moving floor is generated by a gear unit flanged to the sieve drum axis.
  • a rotating eccentric drive moves the moving floor shaft at a constant angle of inclination to the sieve drum hollow shaft, the solids flow being regulated via the variable eccentric speed.
  • DE-A 1 966 155 and 1 482 709 have proposed a filter belt centrifuge with mutually inclined axes for the dry centrifuging of fine-grained solids, in which endless filter belts are moved along the inside of the sieve drum and the filtered solids thereon are disposed of at the discharge end of the sieve drum carry there.
  • an inclined swashplate on the axis of rotation is provided for solids discharge, which is intended to push the solid inwards against the centrifugal force to discharge openings.
  • Vibrating centrifuges Vibrating centrifuges.
  • the transport impulses for the solid cake are, however, generated by a rapid wobble movement of the drum axis, causing parts of the solid cake in the conical drum to slide to the largest drum diameter and to be thrown off at a circumferential point of the discharge end.
  • the solids discharge is therefore more constant.
  • the separation performance and the possible area of use of the tumble centrifuges corresponds approximately to that of the vibratory centrifuges.
  • Another principle of solids transport is used in the worm screen centrifuges, in which the solids retained by the screen are transported from a small to a large screen drum diameter by a screw driven at a differential speed to the conical screen drum. Due to this forced transport, these centrifuges are for under various products can be used.
  • Electricity dryer often has an adverse effect. Due to pulsating forces and material flows at the discharge end, the noise level is relatively high. The thrust forces become very high at high speeds or with long sieve drums and are not always distributed exactly in a rotationally symmetrical manner, which means that push centrifuges often fail because the push rods bend for the axial movement of the push floor.
  • the object of the invention is to improve a thrust centrifuge of the type mentioned at the outset in such a way that a controllable continuous flow of solids is achieved at the screen drum discharge.
  • the invention provides in the above-mentioned push centrifuge that the push floor is rotatably mounted about an axis inclined to the axis of rotation of the drive shaft of the sieve drum, the inclination of which is adjustable.
  • the invention is based on the principle of the thrust required for the axial transport of solids to be continuously applied to the solid ring built up in front of the moving floor. So only one segment of the circumference is recorded. A loosening of the solid cake can thereby be achieved, which leads to lower residual moisture.
  • the lower conveying forces are applied continuously (all around)
  • only a lower drive power for driving the push floor for solids transport has to be made available. On the one hand, this leads to a continuous flow of solids and thus a quieter and quieter operation of the push centrifuge, and on the other hand to a lower investment and ultimately to reduced operating costs.
  • the continuous axial pushing out of the solid cake enables the half-sided filling of the gap that is released in front of the moving floor when it moves back.
  • this gap opened evenly over the entire circumference, so that the suspension had to be supplied evenly distributed over the circumference. Since in the push centrifuge according to the invention a gap only opens over a partial area of the circumference, the suspension need only be added in this part. If, in the known centrifuge, a pulsating task is to be aimed at in the cycle of the opening gap, the invention enables a constant addition of suspension in a gap that is always present.
  • the sliding floor axis which is slightly inclined to the axis of rotation of the screening drum, creates a sinusoidal sliding movement in the axial direction at every circumferential position of the moving floor.
  • the path of the moving and retracting moving floor can be increased or decreased by changing the angle of inclination of the moving floor axis relative to the axis of rotation of the screening drum. This allows control of the material throughput between a maximum value with the greatest inclination reach zero angle.
  • the inclined axis of rotation of the moving floor can be fixed in space or can also rotate about the axis of rotation of the screening drum, which also allows the solids throughput to be controlled.
  • the moving floor is generally rotated synchronously with the sieve drum, so that the wear on the moving floor is kept low, in particular in the case of abrasive solids. If the moving floor is mounted on a moving floor shaft without rotation, its drive can be achieved due to the frictional engagement with the solid ring built up in front of it. A synchronous drive of the moving floor can take place through the drive shaft of the screening drum in that a rotationally fixed connection is provided between the inclined moving floor or its shaft and the screening drum or its shaft. If the inclined moving floor rotates synchronously with the sieve drum in terms of speed and direction of rotation, then the solid is constantly displaced in a spatially stationary circumferential area in the sieve drum. This has advantages when it comes to dropping cakes.
  • the cake is dropped in a narrow angular range that does not change in the spatially stationary coordinate system.
  • the direction of the solids discharge can be changed by changing the direction of the moving floor axis through radial and tangential adjustment. This has great advantages for abrasive goods or solids that tend to stick to the housing, as well as for feeding the discharged solid into a downstream device, such as a dryer, a silo, a pneumatic conveyor line or the like.
  • the inclined moving floor can also be connected to the sieve drum in a rotationally fixed manner and then rotates synchronously with it. If, on the other hand, the push floor is rotatably mounted with respect to the sieve drum and is slightly inclined, the cake is also transported axially due to the frictional connection between it and the push floor.
  • the inclined pusher floor axis is rotated around the drum axis in the case of the rotatably mounted moving floor, there are different conditions for cake transport or cake ejection at the end of the drum.
  • Rotates the. inclined moving floor axis in the direction and speed exactly with the sieve drum no cake is transported and thrown off.
  • the speed of the moving floor axis decreases compared to the speed of the screening drum, the shifting or ejection frequency increases with the difference in speed.
  • the direction of the solids discharge then also rotates with the differential speed. If the moving floor axis is stationary in the room, the shift frequency of the Ku chens in the rotating sieve drum equal to the drum speed and the direction of the solids discharge also stands still.
  • the shift frequency in the sieve drum increases further and the discharge jet then rotates in the opposite direction of the drum rotation. This makes it possible to achieve a large product throughput flow with a slight inclination of the sliding floor axis and a low drum speed.
  • the dwell time of the solid in the drum decreases continuously with increasing differential speed.
  • the solids throughput can be influenced by two mechanisms, namely on the one hand by the angle of inclination of the moving floor axis relative to the sieve drum axis of rotation and on the other hand by a differential speed between the sieve drum and moving floor.
  • a feed tube that rotates with the rotation of the moving floor shaft is expedient in order to constantly fill the crescent-shaped gap between the retracted moving floor and the solid cake ring that has been released with suspension at an optimal point.
  • the suspension can also be applied via a pre-acceleration cone, which is connected to the drum screen floor in front of the push floor and opens near the inner surface of the screening drum.
  • the pre-acceleration cone only releases an opening gap in the zone where the walking floor has receded.
  • More than a single moving floor can be provided for the axial transport of the solid.
  • the walking floors are mounted on an inclined walking floor shaft.
  • a mechanical pressing action can also be exerted on the cake in the sieve drum if the sieve drum has a section which narrows conically in the conveying direction in the region of the moving floor and which creates a jamming effect.
  • the solids transport can be promoted by loosening blades on the walking floor shaft.
  • a conveyor edge inclined forward at the edge of the moving floor is also expedient.
  • the solid cake ring has a radial side that faces the drum sieve bottom and becomes free when the pushing floor retracts, which can slide under the influence of the high centrifugal acceleration at a flat slope angle of the solid and thus partially fill the gap.
  • an inclination of the conveying surface or even a step-like gradation is expedient, a design which is also advantageous for the known axially normal moving floors.
  • the outer region of the sieve plate can also be divided into segments which can be moved axially back and forth by means of individual actuators. Appropriate control of the actuators, for example pressure cylinders acted upon by pressure medium, also allows a segment-wise transport of solids moving along the circumference of the moving floor.
  • the pusher centrifuge can be designed as a double pusher centrifuge, in which two sieve drums are mounted on the drive shaft facing or facing away from one another and in which one or more push floors are rotatably mounted about an inclined axis. This training is characterized by high dynamic stability with very large screen areas.
  • FIG. 1 shows a cross section of a pusher centrifuge with a cylindrical screen drum and inclination adjustment of the pusher shaft on the side of the discharge end of the screen drum
  • FIG. 2 shows an end view of the screening drum of the pusher centrifuge according to FIG. 1, 3 shows a cross section, a pusher centrifuge with a sieve drum made of conical sections and inclination adjustment of the sliding floor shaft within the drive shaft of the sieve drum designed as a hollow shaft,
  • FIG. 4 shows a cross section of a pusher centrifuge with a wobble pusher floor and differential speed drive
  • Fig. 5 shows a cross section of a pusher centrifuge
  • Fig. 6 shows a cross section of a pusher centrifuge with a screen press ring, screen pusher bottom and loosening of the
  • Fig. 7 shows a cross section of a two-stage pusher centrifuge with a conical pusher plate and mechanical inclination adjustment of the pusher shaft on the
  • FIG. 8 shows a cross section of a two-stage pusher centrifuge with hydraulic inclination adjustment of a conical pusher floor by means of bellows provided at the end of the drive shaft and distributed around its circumference, and with a conical sieve drum,
  • Fig. 9 shows a cross section of a symmetrical double pusher centrifuge with facing sieve drum bottoms
  • FIG. 1 the basic structure of a push centrifuge is shown schematically.
  • Your sieve drum 1 is rotatably connected to a drive shaft 2 and rotatably supported in bearings 3, 4 of a bearing block.
  • a circular disk-shaped flat or conical sliding floor 5 in the manner of a swash plate is fastened on a sliding floor shaft 7, which is connected to the drive shaft 2 via a joint bearing 6 and is guided and driven radially by the latter.
  • the push floor 5 can also have a polygonal circumference.
  • the sliding floor 5 or its axis 25 is held spatially in an inclined position relative to the screening drum 1 via the sliding floor shaft 7 and a self-aligning bearing 8 which can be adjusted radially and / or tangentially to the axis of rotation of the drive shaft 2.
  • the push floor 5 and push floor shaft 7 also rotate.
  • the edge of the inclined sliding floor 5 executes a sinusoidal displacement movement in the axial direction with each revolution relative to the sieve drum 1 covered with a sieve 9. If the gap 10 that is released with each drum revolution is filled with suspension through a fixed feed or supply pipe 11, the solid retained by the sieve 9 is turned up to a part of a solid ring 12 during rotation and the like! of the solid ring 12 in the drum pushed a bit forward to the discharge end 13.
  • the stroke of the circumferential sinusoidal displacement movement can also be changed during operation by adjusting the position of the self-aligning bearing 8 towards or away from the axis of rotation of the screening drum 1, as a result of which the inclination of the moving floor 5 or its axis 25 is changed.
  • the position of the drive shaft 2 could be shifted together in the same or different planes by kinematic reversal.
  • the spherical bearing 6 can leads as a bend-elastic connection (rubber joint), cardan shaft, homokinetic joint, ball joint, pendulum tip bearing with and without elastic torque coupling, since the moving floor is rotated by the sieve drum 1 due to friction on the solid.
  • the pendulum bearing 8 can be adjusted by any mechanical, hydraulic, pneumatic or electrical actuators by hand or automatically once or periodically with and without overload protection.
  • the push centrifuge can be operated horizontally, vertically or at an angle in any direction of the drive shaft 2. It can be listed in all variants in one or more stages.
  • the push floor 5 can be designed as a rigid, flat or conical disk and can be attached to the push floor shaft 2 in a rotationally fixed or rotatable manner. It can also consist of individual radial segments which are elastically connected to the thrust base 7 and which spring in the axial direction and can be adjusted in succession in the conveying direction with individual actuators, so that the discharge is not carried out all around the circumference of the sieve drum at the same time, but rather all around one place.
  • FIG. 2 shows a view from the front and the processes in the screening drum during the rotation.
  • the push floor 5, like the push floor shaft 7, is inclined with respect to the screening drum 1 towards the off-axis self-aligning bearing 8, as shown in FIG.
  • a free gap between the solid ring 12 and the sliding floor 5 opens from the radius 19, which has the greatest width in the radius 17.
  • the suspension is continuously injected through the feed pipe 11 and filtered on. From the radius 17 on, the gap narrows again and the solid which has been filtered on is compressed until the thickness of the solid ring 12 formed is reached, for example at radius 18. From then on the moving floor pushes the entire solid in the drum zone from radius 18 to radius 19 a little forward so that it is thrown off at the discharge end 13.
  • the push centrifuge according to FIG. 3 has an inclination adjustment of the push floor shaft 7 from the rear and a sieve drum made of a further conical section 21 which narrows in the conveying direction and a front (outlet side) which widens in the conveying direction.
  • the push floor shaft 7 is through the outside the screen drum 5 in the area of the bearing 4 provided articulated bearings 6 and a rear adjustable self-aligning bearing 8 in its axial position to the screen drum.
  • the axial thrust forces are preferably absorbed by the spherical bearing 6.
  • the position of the spherical bearing 6 is to be placed such that it lies on the intersection of the vertical from the center of the two extreme points of the moving floor movement and the sieve drum axis 2 .
  • the sieve drum section 21 can also be designed as a section of a spherical surface.
  • the changes in the gap widths are preferably small angular displacements between the drive shaft 2 and the thrust Bodenwelle 7 only a fraction of a millimeter.
  • the gap that is released between the solid and the sliding floor 5 has a larger filling volume, so that more suspension to be filtered can be filled into the filling zone through the feed pipe 11, so that the centrifuge's ability to swallow increases.
  • the suspension can be injected directly through the feed pipe 11 in the circumferential direction into the opening crescent-shaped gap or, as shown in FIG. 3, via an inner pre-attachment cone 20, which is connected in a rotationally fixed manner to the sieve drum, the preferred - Wise connected to the drive shaft 2 of the screening drum. So that the suspension only exits in the peripheral region of the screening drum, in which the gap for filling is open, the pre-acceleration cone 20 is set against the push floor 5 as far as possible.
  • the pre-acceleration cone is provided on the inner edge facing the moving floor with an elastically resilient sealing lip 24.
  • a pre-acceleration cone for the supplied suspension with an outlet gap open on one side can in principle be attached to all single and multi-stage centrifuges shown in FIGS. 1 to 8 if this appears to be advantageous, for example, for reasons of wear.
  • the solid ring 1 2 is replaced by the solids in the
  • Figure 4 shows a variant in which the inclined moving floor axis 25 is rotatable in space.
  • the direction of the solids discharge zone, the filling zone and preferably also the direction of the feed pipe 11 then also rotates with the speed difference.
  • the walking floor axis 25 tumbles here.
  • Figure 5 shows a further embodiment of the pusher centrifuge, in which the inclined position of the push floor 5 is not achieved by an inclined position of the push floor shaft relative to the sieve bottom shaft, but rather by the actuating drives articulated on the push floor 5 in the form of axially acting working or adjusting cylinders 30 which have a Control head 31 can be acted upon by a pressure medium via a pressure medium line 32.
  • the displacement process for solids 23 in the cylindrical sieve drum section and in the front conical section 22 is the same as in the embodiments according to FIGS. 1 and 3.
  • the control head 31 has the task of allowing the liquid or gaseous pressure medium to flow into or out of the respective actuating cylinders 30 . It can be carried out in a known manner.
  • the pressure medium is preferably supplied and removed via known rotary unions.
  • the speed at which the control head rotates can be regulated via the solids flow.
  • the pressure of the pressure medium can also be used for control purposes. If an axial or radial piston pump is used as the pressure medium generator, the control head can be omitted.
  • the articulated bearing 6 can be designed as a traction means or, as shown in FIG. 1. Instead of the axial actuating cylinder 30, compressed air bellows or the like can also be used.
  • FIG. 6 shows how, in addition to the centrifugal force, the solid can also be dewatered by mechanical pressing forces.
  • the sieve drum shaft 2 is at an angle to the moving floor shaft 7, which is guided through the joints 6 and 8.
  • the push floor 5 is provided on its outer circumference with a conical sieve 33 inclined to the rear, through which the filtrate can flow off, just as in the cylindrical section, axially normal section 34, conical section 35 and conical front section 22 of the sieve drum.
  • a conical sieve 33 inclined to the rear
  • the joint bearing 6 is designed, for example, as an elastic joint.
  • the push floor is preferably in the outer area, where the sieve 33 is provided, in the form of a cone with an angle of inclination similar to the side or pouring angle as the pent-up solid has.
  • a protruding scraping edge 38 is advantageous in order not to pinch individual solid particles between the push floor edge and sieve drum 1 and to reduce the frictional pressure of the solid on the sieve 1.
  • the suspension is fed for example by a hollow shaft, for example the sieve drum shaft 2 or the sliding floor shaft 1. or in the free one
  • Figure 7 shows schematically the basic structure of a two-stage pusher centrifuge.
  • Sieve drum 1 which represents the second sieve stage, is fastened to the outer sieve bottom shaft 2 above the sieve drum bottom 40 and is rotatably supported in the bearings 3 and 4.
  • the moving floor 5 is also rigidly connected to the outer sieve floor shaft 7.
  • the front, inner sieve drum section 22 is fixedly connected via a hub 42 to a pivotable inner sieve bottom shaft 41 and is guided in its spatial position by the spherical bearing 6 and the height-adjustable self-aligning bearing 8.
  • the hub 42 penetrates the push floor 5 in the region of a plurality of openings 43 and is itself interrupted at the webs of the push floor 5.
  • the openings 43 ensure sufficient mobility of the front, inner screen drum section 22 to enable its inclination.
  • the position of the spherical bearing 6 on the outer sieve drum shaft 2 is coordinated with the inclination of the inner sieve drum section 22 and the outer cylindrical sieve drum 1 and with the position of a moving floor ring 44 which extends radially outward from the inner sieve drum section 22 such that at. Inclination results in the smallest possible change in the gap widths between the edges of the moving floor and sieving the sieve drum.
  • the suspension is fed through the feed tube 11 or a acceleration cone in the free gap 10 of the rotating drum, the filtered solid is pushed forward through the sliding floor 5 together with the inner solid 12 of the first stage around the drawer and at the front edge 47 of the front, inner sieve drum section 22 thrown onto the outer cylindrical sieve drum 1.
  • the moving floor ring 44 connected to the conical front, inner sieve drum section 22 compresses the thrown off solid in an annular manner to the outer solid 23 and pushes it forward to the front discharge end 13.
  • the filtrate of the suspension is thrown off by the inner sieve drum section 22 and flows through openings 48 of the sieve drum 1 from.
  • An intensive washing of the solid material by supplied washing liquid 45 is possible in particular on the transfer parts 47 of the solid matter from the inner sieve drum section 22 to the outer sieve drum 1.
  • the outflowing liquids can be discharged separately from one another by partition walls 46 in the housing.
  • FIG. 8 shows the schematic structure of a two-stage pusher centrifuge with hydraulic adjustment of the inner hub 42.
  • the inclined position of the inner hub 42 could also be achieved by a mechanical adjustment of the sieve drum base 40 of the outer sieve drum.
  • the outer screening drum is fastened to the hollow drive shaft 2 and is again guided through the bearings 3 and 4.
  • the inner sieve drum is connected to the outer drive shaft 2 by the spherical bearing 6 and is guided into an inclined position by means of actuators which can be extended on one side and are distributed over the circumference in the form of hydraulic actuating cylinders or bellows 30 '.
  • the control of the individual bellows 30 'on the circumference of the hub 42 takes place via lines 32 in the hollow drive shaft 2, which are fed differently in the flow quantity and direction.
  • each bellows 30 is moved from there via its line 32 with connected pump pistons filled with pressure medium or emptied by it.
  • the hydraulic arrangement corresponds to a mechanical linkage.
  • Each bellows 30 is alternately filled and emptied with each revolution of the outer drive shaft 2.
  • the size of the eccentricity of the radial pump unit 51 is a measure of the inclination of the hub 42 with the front, inner sieve drum section 22. It is also possible for the inner sieve drum section 22 to be inclined out of synchronization with the drive shaft 2, as described with reference to FIG. 5 has been.
  • the inclination of the sieve drum 1 and the inner sieve drum section 22 is matched to the position of the articulation point of the articulated bearing 6.
  • the filling, filtering, washing and pushing out of the solid takes place as described with reference to FIG. 7.
  • the large inclination of the drum sieve 1 and the inner sieve drum section 22 also allows the continuous filtering of very fine-grained solids through fine-meshed fabrics in thin layers, as a result of which the filtration and displacement resistance is low.
  • FIG. 9 schematically shows the basic structure of a symmetrical double-pusher centrifuge with two identical sieve drums 1, the open sides of which point outwards and the bottoms of which face one another.
  • the common drive shaft 2 of the two screening drums 1 is again supported in outer bearings 3 and 4.
  • the two push floors 5 are inclined by several axially parallel push rods 54 articulated on the circumference.
  • the push rods 54 become horizontal by a thrust bearing 53 fixed obliquely in space moved back and forth.
  • the push rods 54 are connected to the thrust bearing in a thrust-resistant manner.
  • the hinge connections can be designed as elastic or other hinge elements.
  • a change in the stroke of the sliding floors 5 can, for example, by Change in the inclination of the thrust bearing 53 happen. All of the special features listed in FIGS. 1 to 8 can also be carried out with a double arrangement of the screening drums 1.
  • FIG. 10 schematically shows a symmetrical double thrust centrifuge, in which the suspension is fed through the feed pipes 11 and the solids are discharged via the discharge ends 13 from the center.
  • the sieve drums 1 facing each other with the open sides are fastened on the common drive shaft 2 and stored in outer bearings 3 and 4.
  • the sliding floors are articulated on the drive shaft 2 and, for example in the articulated bearings 6, are connected to it in a rotationally fixed manner.
  • the sieve drum bottoms 40 have a plurality of openings on the circumference, through which a plurality of adjustment arms 58 for the sloping floor sloping position are passed.
  • the inclined position and spatial fixation of the sliding floors during rotation is carried out by guide bearings 57 connected to the adjusting arms 58, which are adjustably radially displaced and fixed.
  • the adjustment arms 53 can also be tangential to the joint bearing 6, which results in smaller guide bearings 57.
  • the guide bearings can also be arranged within the adjustment arms 58.
  • the openings in the sieve drum bottoms 40 and the space between them and the push bottoms can be sealed off from the separation space by simple bellows seals. This arrangement is advantageous. Great dynamic stability, which allows very large screen areas, and easy access to both separation areas with a sufficiently large screen drum distance.

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Abstract

Avec la centrifugeuse pourvue d'un tambour perfore (1) et d'un fond d'evacuation (5), on obtient, de maniere simple et avec des couts reduits, une humidite residuelle de la matiere solide reduite avec un debit et une acceleration eleves. Dans ce but le fond (5), tournant autour d'un axe (25) incline par rapport a celui du tambour, est aussi dispose obliquement par rapport a l'axe (2) du tambour (1). Le debit est controle en changeant ledit angle d'inclinaison. Le fond (5), dispose incline, peut tourner de maniere synchrone avec le tambour (1) ou peut etre monte de maniere a pouvoir tourner par rapport a celui-ci, enfin la difference entre le nombre de tours influence egalement le debit.
PCT/DE1981/000196 1980-11-12 1981-11-10 Centrifugeuse avec fond deplacable pour l'evacuation de la matiere solide Ceased WO1982001668A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3042674801112 1980-11-12
DE19803042674 DE3042674A1 (de) 1980-11-12 1980-11-12 Schubzentrifuge

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WO1982001668A1 true WO1982001668A1 (fr) 1982-05-27

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WO (1) WO1982001668A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0062576B1 (fr) * 1981-03-31 1985-06-19 S.A. DAREGAL Société: Essoreuse en continu
EP1057533A1 (fr) * 1999-05-27 2000-12-06 Ferrum AG Centrifugeuse

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH660695A5 (de) * 1982-09-06 1987-06-15 Escher Wyss Ag Doppel-schubzentrifuge.

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE221961C (fr) *
DE939259C (de) * 1953-07-14 1956-02-16 Krauss Maffei Ag Austragvorrichtung fuer eine Schubzentrifuge
DE1065333B (de) * 1959-09-10 Gebr. Heine, Viersen (RhId.) Kontinuierlich arbeitende Siebzentrifuge mit einem gegenüber der Siebtrommel vor- oder nacheilend umlaufenden Boden

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE221961C (fr) *
DE1065333B (de) * 1959-09-10 Gebr. Heine, Viersen (RhId.) Kontinuierlich arbeitende Siebzentrifuge mit einem gegenüber der Siebtrommel vor- oder nacheilend umlaufenden Boden
DE939259C (de) * 1953-07-14 1956-02-16 Krauss Maffei Ag Austragvorrichtung fuer eine Schubzentrifuge

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0062576B1 (fr) * 1981-03-31 1985-06-19 S.A. DAREGAL Société: Essoreuse en continu
EP1057533A1 (fr) * 1999-05-27 2000-12-06 Ferrum AG Centrifugeuse
WO2000072974A1 (fr) * 1999-05-27 2000-12-07 Ferrum Ag Centrifugeuse
US6547972B1 (en) 1999-05-27 2003-04-15 Ferrum Ag Centrifuge with ejector for solids

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Publication number Publication date
EP0064544A1 (fr) 1982-11-17
DE3042674A1 (de) 1982-06-09

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