EP3875180B1 - Dispositif crible, en particulier dispositif crible à effet trampoline - Google Patents

Dispositif crible, en particulier dispositif crible à effet trampoline Download PDF

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Publication number
EP3875180B1
EP3875180B1 EP21159880.0A EP21159880A EP3875180B1 EP 3875180 B1 EP3875180 B1 EP 3875180B1 EP 21159880 A EP21159880 A EP 21159880A EP 3875180 B1 EP3875180 B1 EP 3875180B1
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EP
European Patent Office
Prior art keywords
eccentric
axis
transmission
drive
screening device
Prior art date
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EP21159880.0A
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German (de)
English (en)
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EP3875180A1 (fr
Inventor
Felix Matheisl
Jörg Thomas
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Wima Wilsdruffer Maschinen und Anlagenbau GmbH
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Wima Wilsdruffer Maschinen und Anlagenbau GmbH
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Publication of EP3875180A1 publication Critical patent/EP3875180A1/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B07—SEPARATING SOLIDS FROM SOLIDS; SORTING
    • B07B—SEPARATING SOLIDS FROM SOLIDS BY SIEVING, SCREENING, SIFTING OR BY USING GAS CURRENTS; SEPARATING BY OTHER DRY METHODS APPLICABLE TO BULK MATERIAL, e.g. LOOSE ARTICLES FIT TO BE HANDLED LIKE BULK MATERIAL
    • B07B1/00—Sieving, screening, sifting, or sorting solid materials using networks, gratings, grids, or the like
    • B07B1/28—Moving screens not otherwise provided for, e.g. swinging, reciprocating, rocking, tilting or wobbling screens
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B07—SEPARATING SOLIDS FROM SOLIDS; SORTING
    • B07B—SEPARATING SOLIDS FROM SOLIDS BY SIEVING, SCREENING, SIFTING OR BY USING GAS CURRENTS; SEPARATING BY OTHER DRY METHODS APPLICABLE TO BULK MATERIAL, e.g. LOOSE ARTICLES FIT TO BE HANDLED LIKE BULK MATERIAL
    • B07B1/00—Sieving, screening, sifting, or sorting solid materials using networks, gratings, grids, or the like
    • B07B1/46—Constructional details of screens in general; Cleaning or heating of screens
    • B07B1/48—Stretching devices for screens
    • B07B1/485—Devices for alternately stretching and sagging screening surfaces
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B07—SEPARATING SOLIDS FROM SOLIDS; SORTING
    • B07B—SEPARATING SOLIDS FROM SOLIDS BY SIEVING, SCREENING, SIFTING OR BY USING GAS CURRENTS; SEPARATING BY OTHER DRY METHODS APPLICABLE TO BULK MATERIAL, e.g. LOOSE ARTICLES FIT TO BE HANDLED LIKE BULK MATERIAL
    • B07B1/00—Sieving, screening, sifting, or sorting solid materials using networks, gratings, grids, or the like
    • B07B1/42—Drive mechanisms, regulating or controlling devices, or balancing devices, specially adapted for screens

Definitions

  • the present invention relates to a screening device, in particular a flip-flow screening device, with a screen box having at least two opposite side walls, with at least one first crossbeam arranged between the side walls, and with at least one second crossbeam pivotable about a pivot axis A, with at least one screen element having at least one first crossbeam and at least one second crossbeam is connected so that when the second crossbeam is pivoted, the screen element is tensioned and/or relaxed.
  • the present invention also relates to the use of a transmission device for a screening device, in particular a flip-flow screening device, of the aforementioned type.
  • feed materials that are difficult to screen such as moist, sticky, clumping and/or caking materials
  • vibrations of components are used to separate feed material.
  • the particularly flat screen element connected to at least two crossbeams is elastically deformed by a regular movement of the crossbeams, for example a swinging of the crossbeams relative to one another, and thus made to oscillate relative to the screen box.
  • a vibration or main vibration of the sieve box is usually provided in relation to the subsoil.
  • a screen box which has at least two side walls and rigid crossbeams connecting the side walls.
  • a further movable crossbeam is arranged adjacent to, in principle, each rigid crossbeam in such a way that rigid and movable crossbeams are arranged alternately in the sieve box.
  • elastic screen elements are typically arranged one behind the other on the crossbeams. The ability of the screening device to oscillate, particularly in the area of the screen elements, is made possible by relative mobility between the rigid and movable crossbeams. A regular movement of the cross members relatively to each other, i.e. ultimately a vibration, can be caused by resonance or forced excitation.
  • the screen box of the known screening device can be excited to oscillate in the form of a main oscillation.
  • the movable crossbeams based on the main oscillation, it is then customary for the movable crossbeams to be excited indirectly and to oscillate, ie to be excited by resonance due to the design.
  • This excited resonance can be influenced at least essentially by mass inertia as well as damping and rigidity of the components.
  • the movable crossbeams are mechanically coupled to the main vibration, ie to the vibration of the sieve box, forcibly excited and/or forcibly guided.
  • the basic disadvantage of the known screening device is that the relative movement between the crossbeams has to be implemented by a complex mechanical structure.
  • the known screening device also has a large number of components that are susceptible to wear.
  • the oscillation frequencies and oscillation amplitudes can only be varied to a very limited extent and partially, mostly completely, interact with one another.
  • the operation of the known screening device is also associated with high maintenance costs.
  • the resonance-excited vibration in the known screening device is particularly disadvantageous because its amplitude and/or frequency depends heavily on the properties and the amount of feed material on the screening element at a given time, so it is ultimately load-dependent. This means that an increasing mass of feed material on the screen element leads to damping of the vibration and thus, if necessary, adequate tensioning and relaxation of the screen linings is no longer achieved. Furthermore, the frequency and amplitude of the resonance-excited vibration are directly dependent on the frequency and amplitude of the screen box vibration, with a higher frequency not being achievable if required. The amplitude of the elongation of the screen linings cannot be precisely predicted either, since it results from various almost indeterminable dynamic factors of the relative vibration.
  • the leaf springs or rubber buffers that are often used for the vibration coupling between the sieve box and the movable crossbeams are also subject to high cyclic stress, which has a negative impact on their service life and can even lead to a sudden failure.
  • the aforesaid disadvantages are hard to come by dominant interaction with a constant screening result and a constant screening quality.
  • the forcibly excited vibration in the prior art in which the two vibrations are mechanically coupled to one another, is particularly disadvantageous because the vibration frequencies are not variable with respect to one another, but are coupled in the same direction to the main drive of the screening device.
  • the DE 38 23 896 A1 relates to a screening machine having a plurality of parallel side-by-side and spaced-apart crossbeams between which flexible screen decks are fixed and of which every second crossbeam moves relative to the remaining crossbeams therebetween to alternately stretch and compress the screen decks, the second crossbeams therebetween be put into circular vibrations by an imbalance.
  • the EP 0 208 221 A2 relates to a screening machine with two movement systems that execute circular oscillations using at least one eccentric shaft, consisting of frames that are separate from one another or two side walls each with transverse beams that are fastened parallel to one another at regular intervals between the frames or side walls of each system, with the transverse beams located in one screening plane being arranged alternately in both systems and through
  • the systems are driven in such a way that the elastic screen cloth panels located between the crossbeams and attached to them are alternately stretched and compressed.
  • the EP 0 099 528 A2 relates to a screening machine with mutually parallel crossbeams arranged transversely to the direction of transport of the screenings, on or between which a flexible screen lining is attached and of which every second crossbeam can be moved alternately and forms a first group.
  • the CN 104 549 980 A also relates to a screening device with crossbeams.
  • the DE 12 75 339 relates to a screening machine with a screening machine frame and a flexible screen bottom which is fastened in zones on screen bottom supports which are arranged parallel to one another and are movably driven, and under the action of the screen bottom supports which alternately move towards and away from one another, screen zones of constantly changing width, each with an alternating sagging depth of different depths, arc-shaped bulging or different tension of the sieve bottom zones.
  • the above-mentioned object is at least essentially achieved in that the second crossbeam is assigned at least one revolving, rotationally driven transmission device for generating an exclusively oscillating pivoting movement of the second crossbeam about the pivot axis A.
  • the second cross member can preferably be pivoted about the pivot axis A at least essentially without translation. In this way, the second cross member can be positively guided around the pivot axis A on a circular arc section.
  • Pivoting or also a pivoting movement preferably has no—or at least essentially no—translational movement component.
  • a kinematic coupling and/or forced guidance of the at least one second crossbeam relative to the at least one first crossbeam can be achieved be obtained.
  • the kinematic coupling means that the amplitude, the frequency and/or the precise pivoting path of the present pivoting movement can be load-independent and/or independent of the vibration frequency of the screen box, ie independent of the main vibration of the screening device.
  • both small and large amounts of feed material can be screened in the device with at least essentially the same screening result.
  • properties of the pivoting movement (including form, amplitude, frequency and/or speed) can even be changed depending on the properties of the feed material. This significantly increases the flexibility of the screening device.
  • the sieve box can be mounted and/or arranged such that it can vibrate, preferably relative to the subsoil, with the sieve box preferably being designed so that it can vibrate with a main vibration.
  • a main drive of the screening device can be provided for generating the main vibration of the screen box.
  • a regular movement of the sieve box to apply a main vibration can be carried out at least approximately independently of a pivoting movement of a second cross member in the sieve box, ie a relative movement between the first and the second cross member.
  • the frequency and amplitude of the relative movement between the first and second crossbeams is unaffected by the vibration of the sieve box and/or the main vibration, which significantly improves the monitoring and detection of the condition in the screening device, since there are fewer unknown conditions compared to the known screening device.
  • the invention achieves a high screening quality, since the quantity and/or components of the feed material, due to the forced excitation of the second cross member that is now possible, at least essentially neither the oscillation amplitude nor the oscillation frequency of the pivoting movement of the second cross member in relation to the sieve box and/or in relation to the first can affect cross members.
  • the screen box can be mounted so that it can oscillate, in particular together with at least one first and/or second cross member and/or the at least one screen element.
  • the sieve box is preferably decoupled from the subsoil.
  • a spring-damper assembly or at least one suspension and/or at least one damping element can be provided between the sieve box and the subsoil.
  • the sieve box should be able to move within defined limits relative to the subsoil, so that it can be caused to vibrate, for example.
  • the invention also makes it possible for a main oscillation of the sieve box to be carried out at least essentially independently of the oscillating pivoting movement and/or oscillation of the second cross member.
  • a simple, ultimately non-superimposed oscillating movement can be used for sieving, in which either only the sieve box is made to vibrate or only the at least one second cross member is made to vibrate.
  • feed material that is less difficult to screen is to be processed in the screening device and a superimposed vibration movement would cause throwing accelerations that are too high.
  • This allows resources to be saved.
  • feed material that is very difficult to screen is to be processed and several screen passes have to be run through, only some of which require a superimposed vibratory movement.
  • resources for operation and even machine costs can be saved, since this screening device can in particular take over the tasks of simple and complex screening devices.
  • the at least one and/or at least one screen element is connected to the first crossbeam and the preferably adjacent second crossbeam in such a way that the screen element is tensioned and/or relaxed when the second crossbeam pivots in an oscillating manner.
  • a screen element can rest on at least two, preferably adjacent, crossbeams and can be connected to the crossbeams in the area of the support and/or that a screen element can be connected to the crossbeams.
  • Tensioning and/or relaxation of a screen element is preferably characterized in that the screen element is stretched and/or compressed.
  • the tensioning and/or slackening of the screen element it can happen that feed materials are separated and/or screened.
  • the orientation, position and/or shape of the sieve element can change within the Change the screen box quickly and repeatedly. For example, an up and down movement of the alternately tensioned and/or relaxed screen element within the screen box with feed material lying on it leads to the feed material being accelerated or thrown accelerated and consequently moving within the screen box and even being thrown.
  • a sieve element that is preferably at least partially flat is typically arranged at an angle with respect to the subsoil at a predetermined angle. As a result, it can happen that when the sieve element is tensioned and/or relaxed, the feed material lying on it is at least partially thrown and sieved and gradually follows gravity and moves down on the sieve element. A screened fraction or sub-fraction can ultimately be removed below the screen element, while at the end of the downwardly inclined part of the screen element a non-screened fraction or top fraction is ejected from the screen element.
  • connection between a sieve element and a crossbeam can be made in a non-positive and/or positive manner and/or with connecting means and/or in a materially bonded manner, in order in particular to withstand the forces and moments that occur.
  • one point of a screen element in the upper area of a cross member is connected to this and that a further point of the screen element in the upper area of another or further cross member is connected to this, so that pivoting at least one cross member causes a movement and/or deformation and/or tensioning and/or relaxation of the sieve element.
  • a sieve element can have or consist of an elastic material, such as plastic and/or rubber. Furthermore, a sieve element typically has a perforation, which is designed for sieving a sieve fraction. The perforation has a large number of openings.
  • a screen element can be deformed and/or tensioned and/or relaxed in the area between two crossbeams, so that it has a concave and/or convex surface, at least temporarily and/or in certain areas, starting from its originally flat or also curved surface when relaxed .
  • the screen element when compressing and / or when relaxing in Area between two cross members are at least substantially vertically, for example in the direction of the ground, deformed. Elastic and/or reversible deformations of a sieve element preferably occur.
  • the screen cloth elongation which is preferably defined as the maximum spatial deviation from a stationary point on the surface of a screen element in the tensioned and/or relaxed state compared to the initial state of a screen element in a flat rest position, can be changed, in particular by 3% +/- - 2%.
  • the strain of the screen cloth can be varied upwards and/or downwards in order to improve and/or change the screening quality and/or the screening result .
  • the screening device is typically operated with a main drive motor which can cause the screen box, which preferably has the crossbeams, to oscillate.
  • a main drive motor which can cause the screen box, which preferably has the crossbeams, to oscillate.
  • an unbalance is arranged, for example, on a main drive shaft on the sieve box, which can set the sieve box into an oscillating vibrational movement, in particular into the main vibration, depending on the speed on the main drive shaft.
  • the oscillating pivoting movement of the second crossbeam can then be present independently of the main vibration, but can also be superimposed on it if necessary, or ultimately not occur.
  • the frequency and/or amplitude of the oscillating pivoting movement of the second cross member can be adjusted independently of a frequency and/or an amplitude of an oscillation of the sieve box generated by a main drive.
  • the gear device is designed as an eccentric gear device. Accordingly, the transmission device can in particular convert and/or convert a rotary drive movement (rotary movement) into a preferably exclusively oscillating pivoting movement.
  • the pivoting movement can be used in particular for exclusively oscillating drive of the second cross member.
  • the transmission device has a drive unit for driving the transmission device.
  • the drive unit is preferably arranged in a stationary manner.
  • the drive unit has a drive shaft which is driven in rotation (i.e. with a rotary movement).
  • a transmission means is arranged eccentrically on the drive shaft. Due to the eccentric arrangement of the transmission means, an eccentric gear device can be provided in particular. Ultimately, the conversion of a rotary movement into a pivoting movement (with) can be made possible by the eccentric arrangement.
  • the drive unit preferably has a motor for driving the drive shaft.
  • the transmission means is preferably designed as a drive pin.
  • the drive pin enables a secure, robust and/or low-friction arrangement of the transmission means on the drive shaft.
  • the transmission means is arranged on the drive shaft in such a way that the drive shaft is designed to drive the transmission means in rotation. Accordingly, a rotational movement can be applied to the transmission means.
  • the transmission means can be connected to the drive shaft in a rotationally fixed manner, as a result of which permanent transmission of the drive movement can take place.
  • the drive shaft and the transmission means are formed in one piece with one another and/or are firmly connected to one another. Accordingly, an arrangement of the transmission means on the drive shaft that withstands high stresses can be made possible.
  • the transmission device has an eccentric housing.
  • the eccentric housing does not have to surround and/or enclose the entire transmission device, but is intended in particular for arrangement on some components of the transmission device.
  • the eccentric housing is preferably also used to convert the rotary movement into a pivoting movement and is operatively connected to the transmission means.
  • the eccentric housing is designed to accommodate and/or support the transmission means.
  • the transmission means can at least partially be arranged on and / or in the eccentric housing.
  • the transmission means can be designed to drive the eccentric housing in rotation and/or be connected to the eccentric housing in such a way that the eccentric housing is driven in rotation by the transmission means.
  • the eccentric housing is particularly preferably articulated and/or rotatable on the transmission means, preferably via a transmission means bearing, in particular via a preferably angularly movable roller bearing and/or an angularly movable plain bearing, particularly preferably a self-aligning ball bearing and/or self-aligning roller bearing.
  • the bearing acting and/or arranged between the transmission means and the eccentric housing preferably enables the articulated and/or rotatable arrangement of the eccentric housing and also preferably the rotational drive of the eccentric housing.
  • the angularly movable bearing allows the eccentric housing to be misaligned.
  • the drive shaft is preferably arranged on the transmission means via a flange connection.
  • the flange connection is particularly advantageous in that a change or an exchange of the transmission means—which can also be referred to as an eccentric shaft—can be made possible in a comparatively simple manner.
  • Such an exchange makes it possible, in particular, to provide different eccentricities, whereby in particular the pivoting angle of the exclusively oscillating pivoting movement and/or the amplitude of a pivoting means or a pivoting shaft can be influenced and/or the aforementioned pivoting angle or the aforementioned amplitude can be adjusted can.
  • the bearing for supporting the eccentric housing which is preferably designed as a self-aligning ball bearing, can in particular have two rows of balls.
  • the self-aligning ball bearing can compensate for misalignments and/or deflections caused by the transmission means and/or misalignments of the eccentric housing.
  • the transmission means is at least partially arranged on and/or in the eccentric housing and/or is accommodated in it.
  • a coupling element for converting the rotational movement of the transmission means and / or the eccentric housing in a oscillating pivoting movement is provided.
  • the coupling element has in particular such a shape and is in particular arranged at least indirectly on the eccentric housing and/or the transmission means in such a way that the aforementioned implementation of the rotary movement can be ensured.
  • the coupling element preferably has a coupling side.
  • a side, an area, a section and/or a coupling end of the coupling element is understood as a coupling side.
  • the coupling side is that area, preferably an outer end area, of the coupling element that is provided for mounting and/or arrangement on and/or in the eccentric housing and/or transmission means.
  • the coupling element can be mounted and/or inserted on the coupling side on and/or in the eccentric housing.
  • the coupling side and/or the coupling element can be surrounded at least in regions by the eccentric housing and/or border on the eccentric housing.
  • the coupling element can be designed in particular as a lever for generating the, preferably exclusively, oscillating movement.
  • a lever is understood to mean, in particular, a mechanical force converter which can be designed as a rigid body. The lever can be pivoted about a pivot point.
  • the coupling element preferably on the coupling side, is mounted in a linearly displaceable manner on and/or in the eccentric housing.
  • the coupling element is mounted so that it can be displaced linearly transversely to the eccentric axis of the transmission means, in particular on the coupling side.
  • the rotational movement of the eccentric housing or of the transmission means can be converted in particular into a preferably translatory movement on or in the region of the coupling side.
  • the linearly displaceable mounting of the coupling element on and/or in the eccentric housing is implemented via at least one connecting means.
  • two connecting means are provided, preferably spaced apart from one another and/or arranged parallel to one another.
  • the connecting means is particularly preferably designed as a bearing journal.
  • the connecting means can connect the coupling element, in particular the coupling side of the coupling element, to the eccentric housing in a linearly displaceable manner.
  • the connecting means is preferably arranged and/or inserted and/or supported in a corresponding bearing opening of the coupling element, in particular on the coupling side.
  • the connecting means is arranged transversely and/or obliquely, particularly preferably at least essentially orthogonally, to the drive axis in the bearing opening.
  • the bearing opening has, in particular, an opening width and/or an inner diameter that exceeds the diameter of the connecting means. If two connecting means are used, in particular two corresponding bearing openings are provided on the coupling side of the coupling element.
  • the at least one connecting means is arranged and/or inserted and/or mounted firmly on the eccentric housing.
  • the at least one connecting means is fastened and/or fixed to the eccentric housing at each end by a bearing block.
  • the bearing block can have an opening for at least partially accommodating the connecting means, in particular an end region of the connecting means.
  • the bearing block can be designed in one piece or preferably in several parts. In the case of a plurality of connecting means, it can be provided that each connecting means is assigned two bearing blocks.
  • the bearing block can in particular be arranged on a base plate of the eccentric housing and/or connected to it.
  • the base plate is preferably cuboid.
  • the coupling element is preferably connected to a pivoting means on a pivoting side, in particular in a rotationally fixed manner.
  • the pivoting side can be arranged on the side opposite the coupling side.
  • the pivoting side of the coupling element is the area Section and/or outer end face or area provided for connection and/or for coupling to the pivoting means.
  • the pivoting means can also preferably be designed as a pivot shaft.
  • the pivoting means is at least partially inserted and/or mounted on the pivoting side and/or in the coupling element. Accordingly, power can be transmitted from the coupling element to the pivoting means.
  • the pivoting means is particularly preferably arranged, preferably exclusively, in an oscillatingly pivotable manner about a pivoting center pivot axis.
  • the pivot center pivot axis is in particular stationary. Alternatively or additionally, it can be provided that the pivoting means pivoting axis forms the longitudinal axis of the pivoting means.
  • the central pivot axis can in particular coincide with the pivot axis of the second cross member, as a result of which a compact design of the transmission device can preferably be achieved.
  • the pivoting means is designed in particular to transmit the pivoting movement, which is in particular exclusively oscillating, to the second cross member.
  • the coupling element has a pivoting means through-opening on the pivoting side for arranging and/or receiving the pivoting means.
  • a shaft-hub connection in particular a shaft-hub clamping set, is preferably arranged for receiving and/or fastening the pivoting means in and/or on the coupling element, in particular on the pivoting side.
  • the shaft-hub connection is preferably arranged in the pivoting means through-opening.
  • pivoting means through-opening can be designed for the use of a part of the pivoting means, in particular with the pivoting means being connected to the coupling element via the pivoting means through-opening.
  • the pivoting means for transmitting the oscillating pivoting movement can be at least indirectly connected to the second cross member. Therefore the pivoting means, as explained above, can transmit the preferably exclusively oscillating pivoting movement to the second cross member and thus ultimately ensure that the advantages associated with the preferably exclusively oscillating pivoting movement can be achieved.
  • the pivoting means represents in particular the link between the coupling element and the second cross member.
  • the pivoting means is particularly preferably connected to the second crossbeam in a torsionally fixed manner and/or arranged on the second crossbeam in a torsionally fixed manner.
  • further components can be arranged between the second crossbeam and the pivoting means, so that the pivoting means does not have to be directly adjacent to the second crossbeam.
  • the coupling element can be designed as a block-like coupling part, particularly in the area of the coupling side.
  • the coupling element is preferably designed at least essentially in the form of an eyelet in the region of the pivoting side.
  • the coupling element can be designed in one piece and/or be composed of several parts that are firmly connected to one another and, in particular, ensure the conversion of the rotational movement of the drive shaft into the exclusively oscillating pivoting movement according to the invention.
  • a coupling device is arranged between the second crossbeam and the pivoting means.
  • the clutch device is used in particular for vibration decoupling and thus preferably enables a reduction in wear.
  • the vibration decoupling can achieve a reduction in malfunctions that would otherwise be caused, in particular, by vibrations.
  • the eccentric housing can have a base plate.
  • the base plate can be used for arranging the bearing blocks.
  • the base plate also has a transmission medium bearing opening.
  • the transmission means bearing opening is provided in particular for accommodating the transmission means in certain areas and/or for arranging the self-aligning ball bearing.
  • the transmission means bearing opening is arranged in particular in the central area of the base plate. Ultimately, this can serve to improve the absorption and/or transmission of force.
  • the base plate is preferably at least essentially cuboid.
  • a center axis of the transmission means bearing opening coincides with the eccentric axis.
  • the eccentric axis is formed by the longitudinal axis of the transmission means.
  • a longitudinal axis is understood to mean in particular that body axis which runs in the direction of the greatest longitudinal extent and/or expansion or corresponds to this direction.
  • the longitudinal axis preferably forms the, in particular approximate, axis of symmetry of the respective body.
  • the bearing block is particularly preferably arranged on the rear side of the base plate facing away from the drive unit, preferably outside the central area.
  • the drive shaft can have a drive axle.
  • the drive axle is stationary.
  • the drive axis can in particular form the longitudinal axis of the drive shaft.
  • the eccentric axis and/or the central axis can be arranged at least essentially parallel to the drive axis. Accordingly, in particular an effective transmission of the rotational movement from the drive shaft to the transmission means and/or the eccentric housing can be achieved.
  • the transmission device is preferably designed in such a way that the central pivot axis is arranged obliquely, in particular at least essentially orthogonally, to the drive axis.
  • the central pivot axis can intersect the drive axis, the eccentric axis and/or the central axis.
  • the at least one connecting means can have a connecting means longitudinal axis.
  • the longitudinal axis of the connecting means can in particular be arranged at least essentially parallel to the pivoting center pivot axis and/or at an angle, preferably at least essentially orthogonally, to the drive axis and/or the eccentric axis and/or the central axis.
  • an outer housing is provided for the transmission device, in particular the outer housing being designed to accommodate the transmission device or to at least partially accommodate components of the transmission device, in particular the complete accommodation of the coupling element and the eccentric housing .
  • the outer housing can be open or closed at the top.
  • the outer housing has a base facing the ground and side walls fixed to the base.
  • the drive shaft can protrude from the outer housing, in particular from a side wall of the outer housing.
  • pivoting means can protrude from the outer housing, preferably with both front end areas.
  • the outer housing can preferably be provided for mounting the pivoting means and/or the drive shaft.
  • protection from contamination for the transmission device can be made possible via the outer housing, which in particular can lead to a longer, preferably maintenance-free, operating time of the transmission device.
  • an oil bath lubrication of the transmission device or components of the transmission device can be ensured with the transmission housing.
  • At least one shaft bearing which is preferably arranged outside of the outer housing, is preferably provided for mounting the pivot shaft and/or the drive shaft.
  • the drive shaft is preferably arranged at least in regions in a shaft bearing, in particular with the drive shaft also being able to protrude from the shaft bearing.
  • the pivoting means can preferably be arranged with both end regions or front end regions, at least in regions, in a respective shaft bearing.
  • a be provided at the shaft bearing facing the second cross member such an arrangement that the pivoting means projects beyond the shaft bearing.
  • the end region of the pivoting means is completely accommodated in the shaft bearing and preferably does not protrude beyond the shaft bearing.
  • a second crossbeam coupled to the transmission device is preferably operatively connected to at least one further second crossbeam not coupled to the transmission device via a coupling rod.
  • a preferably second crossbeam which is not assigned a transmission device, to be operatively connected to the transmission device via at least one coupling rod and/or at least one connecting rod, preferably with the coupling rod and/or the connecting rod being arranged on the outside of the sieve box is. This makes it possible for the operatively connected second crossbeams to always have at least essentially the same pivot position.
  • the use of a coupling rod and/or a connecting rod avoids a high use of material, since only one transmission device has to be provided, although preferably a large number of movable and/or pivotable second crossbeams are present.
  • the use of a coupling rod and/or a connecting rod avoids a high mass, in particular on the sieve box, which, for example, can adversely affect an oscillating movement of the sieve box.
  • cross members preferably second cross members
  • a majority, in particular all, cross members, preferably second cross members are driven and/or can be set in pivoting motion, preferably by means of at least one transmission device. Accordingly, it is an advantageous embodiment of the invention if a predominant number of crossbeams and/or all crossbeams of the screening device are movable and/or pivotable second crossbeams, so that throwing accelerations can be increased.
  • the sieve box can be mounted and/or arranged such that it can vibrate, preferably relative to the subsoil, with the sieve box preferably being designed so that it can vibrate with a main vibration.
  • a main drive of the screening device can be provided for generating the main vibration of the screen box.
  • a regular movement of the sieve box to apply a main vibration can be carried out at least approximately independently of a pivoting movement of a second cross member in the sieve box, ie a relative movement between the first and the second cross member.
  • the frequency and amplitude of the relative movement between the first and second crossbeams is unaffected by the vibration of the sieve box and/or the main vibration, which significantly improves the monitoring and detection of the condition in the screening device, since there are fewer unknown conditions compared to the known screening device.
  • the screen box can be mounted so that it can oscillate, in particular together with at least one first and/or second cross member and/or the at least one screen element.
  • the sieve box is preferably decoupled from the subsoil.
  • a spring-damper arrangement or at least one spring system and/or at least one damper can be provided between the sieve box and the ground.
  • the sieve box should be able to move within defined limits relative to the subsoil, so that it can be caused to vibrate, for example.
  • the invention also makes it possible for a main oscillation of the sieve box to be carried out at least essentially independently of the oscillating pivoting movement and/or oscillation of the second cross member.
  • a simple, ultimately non-superimposed vibratory movement can be used for sieving, in which either only the sieve box is made to vibrate, or at least only the sieve box a second cross member is made to oscillate. This is advantageous if feed material that is less difficult to screen is to be processed in the screening device and a superimposed vibration movement would cause throwing accelerations that are too high. This allows resources to be saved.
  • the gear device designed in particular as an eccentric gear device means that a very space-saving gear or a very space-saving gear device with a very high degree of efficiency is used in order to set the second cross member in an exclusively oscillating pivoting movement about the pivot axis A.
  • the transmission device according to the invention is easy to protect against external influences such as dirt. The transmission device is therefore very easy to maintain and can also be operated with very little wear.
  • the transmission device preferably has at least one first eccentric and/or a second eccentric and/or an eccentric housing.
  • this makes it possible for at least essentially eccentric components or components having an eccentricity to be able to be used as components which can be operatively connected in a very space-saving manner.
  • eccentric components such as the first eccentric and the second eccentric are inexpensive to produce, low in friction and low in maintenance, preferably compared to geared gear components.
  • the construction according to the invention can enable the drive side and the driven side to be arranged in at least approximately the same area and/or to be close to one another.
  • the transmission device is provided and/or mounted on the outside, in particular on a side wall of the sieve box.
  • this makes it possible for easy accessibility of the transmission device to be ensured.
  • This can also make it possible for the transmission devices to be turned away from the dirt-loaded area, in particular the inner area of the screening device within the screen box and/or the area between the side walls, and thus to be operated at least essentially in a fail-safe and low-maintenance manner and also to be designed more cost-effectively.
  • this also means that there is no need for complex encapsulation of the transmission.
  • the transmission device and/or the second crossbeam is preferably decoupled from the sieve box, in particular via at least one clutch.
  • first eccentric is guided with a connecting section, in particular through the side wall, and is preferably connected in a rotationally fixed manner to the second cross member.
  • the connecting section can be a central shaft of the second cross member, which can also be used for the pivotable mounting of the second cross member on both sides.
  • the first eccentric can pivot in a rotationally fixed manner on the pivot axis A of the second cross member. This results in a space-saving connection that is as short as possible between the output side of the transmission device, in particular the first eccentric, and the drive side of the transmission device, in particular the second eccentric.
  • An arrangement is preferred in which the axis of the output on the transmission device and the pivot axis A of the second cross member are arranged coaxially and/or concentrically and in which the second cross member is driven directly and/or indirectly. This enables a low-loss and/or low-friction transmission of a drive power, in particular starting from a drive device.
  • first eccentric and/or the second eccentric has a circular and/or round outer shape, the center of which coincides with an axis of another eccentric. It can thus be advantageously realized that the first eccentric and/or the second eccentric has a compact design. This is due in particular to the fact that an eccentric does not have to be designed as a solid body, but can have a passage that can be used to save space and/or a bore in which, for example, further components, in particular the first and/or second eccentric, are arranged at least in sections can become.
  • first eccentric and/or the second eccentric and/or the eccentric housing can have at least one bore, wherein the bore can be provided for an axis of another eccentric, for example to be arranged compactly relative to one another and/or to one another.
  • the bore and/or the circular outer shape can be provided on an eccentric for, in particular, rotatable mounting, it being possible, for example, for a bearing means such as a roller bearing and/or a plain bearing to be used in the bore.
  • the bearing means can be provided to enable low-friction relative mobility of components of the transmission device.
  • first eccentric and/or the second eccentric and/or the eccentric housing is at least partially lever-shaped and/or rod-shaped.
  • Such components are preferably arranged next to one another and/or rotatably connected to one another.
  • the gear mechanism and/or the eccentric gear mechanism can have a lever mechanism.
  • a lever mechanism is to be understood as meaning an assembly with at least two components which are arranged on one another, interact with one another, are operatively connected with one another, are supported on one another, slide on one another and/or are coupled to one another and are designed in particular to transmit and/or transform forces and/or movements .
  • a lever mechanism can, in particular, absorb, transmit and/or convert translational and/or rotational movements.
  • a lever mechanism points typically at least one input side and at least one output side, it being possible for the input side and the output side to be kinematically coupled to one another.
  • a lever mechanism can also have lever-shaped and/or rod-shaped components. In particular, with the aid of a lever mechanism—but ultimately also with the aid of a gear mechanism—an incoming, rotationally executed input movement or rotation can be transformed into an outgoing, exclusively oscillating pivoting movement or outgoing pivoting.
  • a gear, a gear device, an eccentric gear and/or an eccentric gear device can be understood to mean a mechanical device which generates an oscillating pivoting movement as an output movement from a rotary input movement or gearedly translates it.
  • the components used in a transmission device have, in particular, defined eccentricities.
  • An eccentricity preferably indicates the distance between two axes within a component.
  • a lever mechanism can thus also be provided which, for example, has components, in particular levers, with axes or eccentric axes or housing axes spaced apart from one another.
  • the first eccentric is mounted on and/or in the sieve box and/or on and/or in the second eccentric and/or is inserted on and/or in the second eccentric.
  • At least one roller bearing and/or slide bearing can be provided in the transmission device.
  • the first and/or second eccentric and/or the eccentric housing can then be provided with at least one bearing means. It can thus advantageously be made possible for the second eccentric to be arranged in particular in a rotatable manner on and/or in the eccentric housing, so that it can be at least essentially accommodated by it and ultimately the compact structure is made possible.
  • the embodiment of the invention is therefore particularly preferred in which - in each case at least in certain areas - the first eccentric is mounted on the sieve box so that it can swivel in particular about the pivot axis A and is rotatable in the second eccentric, in which the second eccentric is rotatably mounted in the eccentric housing and in which the eccentric housing pivoted on the sieve box.
  • This can result in an overall advantageous result in that a full rotation of the second eccentric in a very small space requires at least a full back and forth pivoting of the first eccentric, with the size of the deflection of the pivoting movement being freely determinable due to the design or structure.
  • first eccentric has a first eccentric axis A' and a first additional eccentric axis B and/or that the second eccentric has a second eccentric axis B' and a second additional eccentric axis C and/or that the eccentric housing has a housing axis C' and a further housing axis D and/or that the individual axes of the first eccentric 8, the second eccentric 9 and/or the eccentric housing 10, namely the axes A, A', B, B', C, C' and/or D, are parallel and/or are arranged concentrically and/or coaxially.
  • a parallel arrangement of the axes enables a high degree of compactness of the transmission device.
  • the components of the transmission device can be designed to be extremely torsion-free in terms of reduced masses and the associated reduced production costs, since the power transmission and/or torque transmission can take place at least essentially on one level or at least between two levels that are very close together.
  • An axis of an eccentric in particular the first eccentric axis A′ of the first eccentric, and a further axis of a further eccentric and/or the further axis D of the eccentric housing are particularly preferably at a fixed distance from one another.
  • the fixed spacing means that the position of the axle(s) in question does not change during operation of the eccentric device, ie preferably in relation to the side walls and/or the sieve box.
  • the distances between the other axes and the aforementioned fixed axes can change—at least partially—during operation of the transmission device, in particular so that the oscillating pivoting movement according to the invention can take place.
  • the spacing of at least two axes belonging to and/or associated with an individual component of the transmission device i. H. at least the first eccentric, the second eccentric and/or the eccentric housing, preferably all three of the aforementioned components, are fixed to one another.
  • the eccentricities of the eccentrics are each fixed and/or the center distances of the axes of the eccentric housing are fixed.
  • the adjustment is made by replacing individual or all eccentric parts with the same external dimensions by other corresponding eccentric parts, in which the axes that are fixedly spaced apart from one another - in particular, these are the first eccentric axis A' and the further housing axis D - are at least partially still the same are spaced apart, but the other axes have different distances from each other, resulting in different gear ratios.
  • the pivoting amplitude can be changed.
  • Mobility and/or the resulting kinematics between the input and output of the transmission device result from all selected and/or set center distances of the at least three components in particular (first eccentric, second eccentric, eccentric housing) to one another and preferably leads to the translation of a circumferential and/or continuous rotation of the second eccentric into a pivoting movement of the first eccentric and/or a pivoting movement of the eccentric housing.
  • the selection of the distances between the axes (i.e. axes of rotation or pivot axes) of the components of the transmission device can be used to define the strain of the screen cloth, in particular, at least essentially independently of the load.
  • the first eccentric with the first additional eccentric axis B is at least partially on and/or in the second eccentric, preferably coaxial and/or concentric with the second eccentric axis B ', pivoted and / or rotatably mounted.
  • the second eccentric with the second further eccentric axis C is rotatably mounted at least partially on and/or in the eccentric housing, preferably coaxially and/or concentrically with the housing axis C'.
  • the eccentric housing with the further housing axis D is at least partially pivotably mounted on and/or in the sieve box.
  • the axes A and A' - preferably the pivot axis of the second cross member A and the first eccentric axis A' -
  • the axes B and B' - preferably the first further eccentric axis B and the second eccentric axis B' - and/or the axes C and C' - preferably the second further eccentric axis C and the housing axis C' - each arranged coaxially and/or concentrically.
  • the first eccentric is preferably mounted and/or inserted at least partially in a rotatable and/or pivotable manner on and/or in the second eccentric.
  • two axes of the two eccentrics coincide, particularly preferably axes B and B′.
  • the second further axis C of the second eccentric and the axis C' of the eccentric housing preferably also coincide.
  • Coincidence is to be understood as meaning the coaxiality and/or the concentricity of two axes which ultimately share an at least almost identical spatial positioning.
  • coaxiality and/or concentricity can make it possible for the transmission device to cause a further eccentric, preferably the first eccentric, to pivot from a rotation of an eccentric, preferably the second eccentric, in a very compact installation space.
  • a particularly preferred embodiment provides that the axes of the first eccentric, the second eccentric and/or the eccentric housing, namely the axes A, A', B, B', C, C' and/or D, are spaced apart from one another in such a way that that a continuous rotation of the second eccentric about the second further eccentric axis C and/or about the housing axis C' causes an oscillating pivoting movement of the first eccentric about the pivot axis A and/or about the first eccentric axis A' and/or are spaced apart from each other in such a way that the oscillating pivoting of the eccentric housing around the housing axis D is superimposed on the continuous rotation of the second eccentric around the second further eccentric axis C and/or around the housing axis C'.
  • the fixed spacing from the aforesaid axes is advantageous because the operation of the transmission becomes predetermined and also predictable.
  • the movement kinematics to be achieved can hereby be predetermined and/or monitored in the form of the size of the pivoting amplitude as a function of a full incoming revolution.
  • the distance between the axes results in the gear ratio of the transmission device being at least essentially freely selectable, resulting in a variety of applications.
  • the screen cloth expansion can be advantageously defined, at least essentially load-independent.
  • the distance between the axes B′ to C is the smallest and/or the distance between the axes C' to D is the largest.
  • the eccentricity of the eccentric housing is the largest and the eccentricity of the second eccentric is the smallest.
  • At least one distance between two axes can be variable and/or adjustable.
  • a variable translation of the transmission device can advantageously be provided in order to react flexibly to variable feed material.
  • the distance can be changed by means of adjustment means provided on the respective eccentrics and/or on the eccentric housing or, as already explained above, by exchanging at least one corresponding eccentric part, which results in a different axis arrangement, i.e. the axis distances are different.
  • a change in a distance between two axes can advantageously be used to change the pivoting amplitude of an eccentric and/or of the eccentric housing. This can be useful when different feed materials are to be processed on one screening device. Ultimately, a large number of pivoting amplitudes can be "covered” very easily and/or can be used quickly by adapting the transmission device. Finally, the transmission device does not have to be replaced by another transmission device for this purpose. Also, no further screening device has to be kept available. This would result in high costs, which, however, can be avoided with a preferred embodiment.
  • the second eccentric is driven in rotation by a preferably stationary drive device.
  • a preferably stationary drive device preferably at least one, for example cardanic, coupling element and/or compensation element and/or universal joint can be installed in the drive train and /or be provided on the drive side of the screening device.
  • the drive device does not have to be arranged on the sieve box and thus ultimately does not have to be exposed to the preferably provided vibratory movements and/or main vibrations of the sieve box and thus have a longer service life and can be designed more cost-effectively.
  • the drive device can, for example, be mounted and/or arranged independently of the transmission device. It is possible for the drive device to be arranged on the sieve box. In addition, it is also possible for the drive device not to be arranged on the sieve box, namely, for example, directly or indirectly on the ground, while the transmission device can, however, be arranged on the sieve box. Ultimately, it is advantageous that the drive device can be decoupled from the vibratory movements of the sieve box and/or the transmission device via a compensating element and/or a universal joint, so that less mechanical stress acts on the drive device and it can be designed more cost-effectively. Sensitive components of the drive device can be arranged at least essentially without vibration.
  • the transmission device is decoupled and/or decoupled from the sieve box and/or from the second cross member with the aid of a clutch.
  • the or all second crossbeam(s), but at least one second crossbeam, is decoupled from the sieve box.
  • a coupling, preferably by means of a belt drive, of the transmission device, in particular of the second eccentric, in the area of the main drive motor and/or to the main drive motor of the screening device and/or to the drive device can be possible.
  • the transmission device, in particular the second eccentric can be driven by a separate drive device.
  • the oscillation frequency of the relative movement can thus advantageously be changed in a simple manner via an adjustable translation of the coupling, in particular of the belt drive, and/or, for example, also by the speed of the main drive motor and/or the drive and/or the separate drive device.
  • the transmission device in particular the second eccentric, can also be driven, for example, via a belt drive and/or via a shaft drive.
  • the transmission device can be driven via coupling elements, for example on the drive side of the screening machine. These coupling elements can be driven, for example, by a belt drive coupling to the main drive motor of the screening device and/or a separate drive device.
  • the oscillation frequency of the relative movement can advantageously be determined change an adjustable translation of the belt drive and / or, for example, by the speed in a simple manner.
  • the drive it is also advantageously possible for the drive to be able to choose between different drive variants.
  • the use of a coupling element and/or universal joint for the drive can make it possible for all vibration-sensitive components of the drive to be at least essentially decoupled from vibrations, which are mandatory for screening feed material, in particular on the screen box.
  • the vibration-sensitive components can be arranged on a common frame, for example together with or at least essentially independently of the main drive motor of the screening device.
  • a second crossbeam coupled to the transmission device is preferably operatively connected to at least one further second crossbeam not coupled to the transmission device via a coupling rod.
  • a preferably second crossbeam which is not assigned a transmission device, to be operatively connected to the transmission device via at least one coupling rod and/or at least one connecting rod, preferably with the coupling rod and/or the connecting rod being arranged on the outside of the sieve box is. This makes it possible for the operatively connected second crossbeams to always have at least essentially the same pivot position.
  • the use of a coupling rod and/or a connecting rod avoids a high use of material, since only one transmission device has to be provided, although preferably a large number of movable and/or pivotable second crossbeams are present.
  • the use of a coupling rod and/or a connecting rod avoids a high mass, in particular on the sieve box, which, for example, can adversely affect an oscillating movement of the sieve box.
  • cross members preferably second cross members
  • a majority, in particular all, cross members, preferably second cross members are driven and/or can be set in pivoting motion, preferably by means of at least one transmission device. Accordingly, it is an advantageous embodiment of the invention if a predominant number of crossbeams and/or all crossbeams of the screening device are movable and/or pivotable second crossbeams, so that throwing accelerations can be increased.
  • Synchronization can also be provided by means of a synchronization device which is designed to synchronize transmission devices and/or drive devices and/or drives, in particular with one another.
  • the synchronization can take place, for example, via a control device to which at least two drive devices, drive motors and/or drives are connected.
  • the synchronization can also be realized in the form of a mechanical coupling, for example by means of a coupling rod and/or a connecting rod.
  • At least one transmission device is assigned to at least one second cross member and/or that it is coupled to it.
  • at least one further transmission device can be provided, which is assigned to at least one further second cross member and/or is coupled to it.
  • additional connecting rods and/or coupling rods and/or at least one synchronization device can be used in order to enable a number of second crossbeams to move in the same direction and/or synchronously and/or asynchronously on a transmission device.
  • any combination of a number of gear devices and a number of movable and/or pivotable second crossbeams assigned to and/or coupled to a gear device can be possible.
  • a transmission device is assigned to each second cross member. In this case, in order to generate a uniform oscillating vibration, synchronization of all driven second crossbeams should take place.
  • resource-saving use results if only a single transmission device is used. In this case, it is also advantageous that a space-saving and comparatively light construction is implemented.
  • a further embodiment of the invention provides that a large number of first and second crossbeams are arranged adjacent and at least essentially parallel and/or spaced apart from one another, preferably in the sieve box.
  • First and second crossbeams are particularly preferably arranged alternately in the sieve box, so that at least one second crossbeam is adjacent to each first crossbeam and at least one first crossbeam is adjacent to each second crossbeam.
  • first crossbeams and then one or more second crossbeams are arranged alternately.
  • This also allows a new variety of oscillating movements and / or forms of movement are made possible, which are advantageous for separating feed material, especially when optimized and/or maximized throw accelerations are achieved.
  • the number of first crossbeams corresponds at least approximately, ie with a deviation of less than +/-10 crossbeams, preferably less than +/-1 crossbeam, to the number of second crossbeams. In this way, a cost-effective compromise is achieved between the rigidity of the structure, the design effort for the rotary and/or pivot mounting of the second crossbeam and the level of the throwing accelerations that can be achieved.
  • one or more pivotable crossbeams are provided exclusively or at least essentially exclusively—taking into account the necessary stability of the sieve box. So it is also possible that there is no rigid and/or non-pivotable crossbeam and/or no first crossbeam and only pivotable crossbeams and/or second crossbeams.
  • a plurality of pivotable crossbeams and/or second crossbeams to be able to pivot at least essentially in opposite directions and/or in the same direction in order to cause the tensioning and/or relieving of the at least one screen element in the smallest possible installation space at high throw accelerations.
  • At least one first cross member is designed to be pivotable about an axis, for example a pivot axis A.
  • this first cross member can be structurally identical to the second cross member and/or be functionally connected in the same way as the second cross member. It is also irrelevant whether the first crossbeams rigidly connect the at least two side walls, since they can still be pivoted.
  • a further embodiment of the invention provides that at least two in particular planar rows of first and/or second cross members are preferably arranged one above the other between the side walls. At least one screen element can also be arranged on and/or on a row of crossbeams. The juxtaposition of crossbeams with at least one at least substantially resting screen element is included essential part of a so-called screen deck in the screen box and/or the screening device.
  • Screen decks are preferably arranged at a predetermined angle obliquely or horizontally with respect to the subsoil and in particular have planar or planar rows with preferably at least substantially overlying screen elements. Screen decks can also have banana-shaped rows, ie, convex and/or concave and/or inclined in some areas. Screen decks differ, for example, in the different opening widths of the associated screen elements in order to be able to screen different grain sizes.
  • the transmission device according to the invention can be provided in or on at least one screen deck. However, the invention is not limited to this.
  • One or more gear mechanism(s) can be arranged in or on the other screen decks.
  • At least one transmission device according to the invention for the exclusively oscillating pivoting movement of at least one second cross member is assigned to the bottom screen deck, while the screen decks arranged above it can ultimately be rigid in the screen box. Only the possible main vibration of the main vibration drive of the screening device according to the invention is then assigned to this upper screen deck, whereas the oscillating pivoting movement of the main vibration can be superimposed on the lower screen deck.
  • all screen decks can be provided with a gear device according to the invention, in which case, in particular, movable second crossbeams can be arranged in each screen deck.
  • the exclusively oscillating pivoting movement produced by the gear mechanism has the same frequency as the frequency of the action on the screen box acting main vibration.
  • the invention is not limited to this.
  • the frequencies of the two vibration systems can also be different.
  • the oscillation frequency of the oscillation drive can be lower but also higher than the frequency of the main oscillation drive. In particular, it is a multiple of the frequency of the main drive. It goes without saying that the aforementioned features are ultimately only relevant if a main drive is actually provided, which is certainly advantageous but not absolutely necessary.
  • a frequency of the movement of the second crossbeam is selected independently of the frequency of the main drive of the sieve box and/or the sieve device.
  • the present invention relates to the use of a revolving rotationally driven transmission device for generating an exclusively oscillating pivoting movement of at least one second crossbeam of a screening device, in particular a flip-flow screening device.
  • the screening device is designed in particular according to at least one of the aforementioned embodiments.
  • the gear device is preferably designed as an eccentric gear device and more preferably in particular according to the aforementioned preferred embodiments, as have been described in connection with the screening device according to the invention.
  • Figures 1 to 5 each shows parts of a screening device 1 according to the invention, which is in particular a flip-flow screening device, which has a screen box 3 with two outer, opposite side walls 2 .
  • the side walls 2 of the sieve box 3 are arranged in parallel.
  • the sieve box 3 can be made to oscillate with a main oscillation by means of a main drive (not shown).
  • the sieve box 3 can be mounted so that it can oscillate and can preferably be decoupled from the subsoil.
  • a spring-damper arrangement or at least one spring system and/or at least one damper can be arranged between the sieve box 3 and the ground.
  • FIGS. 1 to 5 each partially shown screening device 1 arranged between the two side walls 2, in this case the side walls 2 rigidly connecting, first cross member 4, wherein in the 4 a side wall 2 is hidden for reasons of visibility.
  • the second crossbeams 5 are mounted in the side walls 2, it not being shown that the first crossbeams 4 can also be pivoted in the side walls 2, for example.
  • the screening device 1 of 1 and 2 has a sieve element 6 made of an elastic material, which is connected to the first cross member 4 and the second cross member 5 in such a way that the sieve element 6 is tensioned and/or relaxed when the second cross member 5 is pivoted.
  • a screen element 6 is connected to all of the crossbeams 4, 5 shown. It is not shown that several screen elements 6 can be provided, which are each arranged at least essentially between and/or on at least two crossbeams 4, 5.
  • the screen element 6 spans at least substantially the entire Space between the side walls 6 and forms as a result - at least essentially - a screen level or a screen deck.
  • the 2 shows a state of the second crossbeams 5 pivoted to the left compared to the starting position, in which the sieve element 6 lying on it is tensioned and/or relaxed at least in regions, in particular in the area between the crossbeams 4, 5.
  • the screen element In the relaxed state during operation, the screen element is usually bent downwards.
  • the tension of the sieve element 6 during the oscillation or during the oscillating pivoting movement then results in a movement impulse, which throws the material to be sieved on the sieve element 6 upwards and loosens it up, so that better sieving can then take place.
  • a screen element 6 is connected to the cross member 4, 5, for example in the upper area of a cross member 4, 5, and that another point of the same screen element 6 is connected, for example in the upper area of another cross member 4, 5 with the other cross member 4, 5 is connected.
  • the screen element 6 can also be inserted into a cross member 4, 5 and/or clamped and/or firmly connected to a cross member 4, 5.
  • Two screen elements 6 arranged in a row, for example, are preferably fastened to a cross member 4, 5.
  • the sieve elements 6 can also be secured by a securing element.
  • the securing element is, for example, a wedge and/or a bar that can be inserted and/or driven between two screen elements 6 and/or through a screen element 6 into a gap and/or an insertion opening, in particular in a cross member 4, 5.
  • a single second cross member 5 is in the embodiments of the Figures 1 to 5 a revolving rotationally driven gear device 7 designed as an eccentric gear device for generating an exclusively oscillating pivoting movement of a second cross member 5 about the pivot axis A.
  • a sieve box 3 with crossbeams 4, 5 can be set into a main oscillation and/or oscillation movement by a main drive.
  • the oscillating pivotal movement of the second cross member 5 can then be possible independently of the main vibration of the sieve box 3 by the main drive of the screening device 1 and can take place independently, be superimposed on the main vibration or be omitted when the main vibration takes place.
  • the sieve box 3 can be mounted so that it can oscillate.
  • the side walls 2, the first cross member 4, the second cross member 5 and/or the screen element 6 can be mounted so as to be able to oscillate.
  • the sieve box 3 is in particular mounted at least essentially decoupled from the subsoil, preferably vibration-damped.
  • a main drive preferably drives the sieve box 3 in order to put it into the main oscillation.
  • the screening device 1 in particular the embodiments of Figures 1 to 5 , is ultimately distinguished by the fact that the second crossbeams 5 are positively guided on a circular path about a pivot point about the pivot axis A. This means that the amplitude and also the frequency of the oscillating pivoting movement is independent of the feed material to be screened.
  • the transmission device 7 has a first eccentric 8, a second eccentric 9 and an eccentric housing 10, as shown in FIG 6 is shown.
  • the transmission device 7 is provided and mounted on the outside of a side wall 2 of the sieve box 3, in particular pivotably mounted.
  • the first eccentric 8 is guided through the side wall 2 with a connecting section 11 and is connected to the second cross member 5 in a rotationally fixed manner.
  • the connecting section 11 is part of a central shaft of the second cross member 5.
  • first eccentric 8 and the second eccentric 9 can be in the form of a shaft section and also in the form of a disk.
  • first eccentric 8, the second eccentric 9 and the eccentric housing are at least essentially lever-shaped and/or rod-shaped.
  • first Eccentric 8, the second eccentric 9 and the eccentric housing 10 components of a lever mechanism On the basis of an incoming rotation on a lever or on the second eccentric 9, the lever mechanism can cause a pivoting of both another lever or the first eccentric 8 and another lever or the eccentric housing 10, in particular if the center distances, ie in particular the lengths the lever, are chosen appropriately.
  • the first eccentric 8 is mounted on the sieve box 3 and mounted in the second eccentric 9 and used in this.
  • the eccentric housing 10 is designed to receive and mount the second eccentric 9, the second eccentric 9 being mounted in the eccentric housing 10 and being inserted into it.
  • Roller bearings and/or sliding bearings can be used for the bearings in order to enable low-friction pivoting and/or rotating capability.
  • the transmission device 7 is protected against external influences such as dirt, in that the first eccentric 8 is arranged on the inside and encapsulated in the transmission device 7 . Only the second eccentric 9, which is preferably driven in rotation, and the pivotable eccentric housing 10 may be exposed.
  • the second eccentric 9 has a second eccentric axis B′ and a second additional eccentric axis C.
  • the eccentric housing 10 has a housing axis C' and a further housing axis D.
  • the axes A' and D i.e. the first eccentric axis A' and the further housing axis D - but ultimately due to the existing coaxiality and concentricity of the pivot axis A and the first eccentric axis A' also the pivot axis A and the housing axis D - are fixedly spaced apart.
  • first eccentric 8 is pivotally mounted with its first further eccentric axis B in the second eccentric 9 coaxially with the second eccentric axis B'.
  • second eccentric 9 is rotatably mounted with the second further eccentric axis C in the eccentric housing 10 coaxially with the housing axis C'.
  • the eccentric housing 10 is in turn mounted pivotably with its further housing axis D on the sieve box 3 .
  • the 7 shows a mechanical analogy model of a transmission device 7, with the same mechanical operation in the Figures 1 to 6 is used, the eccentrics 8, 9 and the eccentric housing 10 being represented by simple rods with bearings at the respective two ends.
  • the model shows that the length of the rods, ie ultimately the eccentricities, are decisive for the sizes of the pivoting amplitudes of the first eccentric 8 and eccentric housing 10 components when the second eccentric 9 is rotated.
  • the distance between axes C' and D is several times greater than the distance between axes A' and B and also several times greater than the distance between axes B' and C'.
  • the distance of the axes B' to C is the smallest and the distance of the axes C' to D is the greatest.
  • the distance between the housing axis C' and the further housing axis D is several times larger than the distance between the first eccentric axis A' and the first further eccentric axis B.
  • the distance between the first eccentric axis A' and the first further eccentric axis B is in turn greater than the distance between the second eccentric axis B' and the second additional eccentric axis C.
  • the eccentricity of the eccentric housing 10 (or the distances between the housing axes C' and D from each other) is the largest of three eccentricities of the first eccentric 8, the second eccentric 9 and the eccentric housing 10, with the eccentricity of the second eccentric 9 (or the distances between the eccentric axes B' and C) is the smallest of the three eccentricities.
  • the eccentricity of the second eccentric 9 is smaller than or at least dimensioned essentially the same as the eccentricity of the first eccentric 8. At least dimensioned essentially the same means that the eccentricities differ by at most 25%, preferably 10%, particularly preferably 5%, differ or are the same.
  • the second eccentric 9 is driven in rotation by a preferably stationary drive device 12, with two gimbal compensating elements 13 and/or universal joints being able to be provided in the drive train.
  • the drive device 12 is mounted and/or arranged independently of the transmission device 7 or the eccentric housing 10 . Provision can be made for the drive device 12 to be arranged on the sieve box 3, although it is also possible for the drive device 12 not to be arranged on the sieve box 3, namely, for example, directly or indirectly on the subsoil, while the transmission device 7 is however on the sieve box 3 can be arranged. It is also possible that the transmission device 7 is decoupled from the sieve box 3 and/or from the second cross member 5 via a clutch. It is also possible for the second crossbeam 5 to be decoupled from the sieve box 3 . It can be advantageous that the Drive device 12 can be decoupled from the vibrations via a compensating element 13 and/or a universal joint.
  • the 2 and 3 show that a second cross member 5 coupled to the transmission device 7 is operatively connected to a further second cross member 5 that is not directly coupled to the transmission device 7 via at least one coupling rod 14 .
  • a plurality of second crossbeams 5 can be driven by only a single transmission device 7, with the crossbeams 5 being operatively connected to one another by means of a connecting rod 15 and a coupling rod 14 in each case.
  • second crossbeams 5 are driven, it being possible for a synchronization device 16 to be provided for synchronizing the pivoting and/or the drive devices 12 . It is also not shown that a number of second cross members 5 can be driven by a number of transmission devices 7, which are in particular synchronized with one another.
  • coupled and/or uncoupled second crossbeams 5 are designed to be moved out of phase and/or asynchronously.
  • FIG 5 shows a screening device 1 according to the invention, in which two planar rows of first and second crossbeams 4 , 5 are arranged one above the other between the side walls 2 , each forming a screen deck 17 in the screen box 3 .
  • several screen elements 6 are arranged on the rows of crossbeams 4, 5 for each screen deck 17.
  • Screen decks 17 are typically level, inclined and/or arranged at a fixed angle to the ground. It is also possible for the screen decks 17 to be arranged or designed to fall obliquely, rise obliquely and/or in the shape of a banana. In this case, banana-shaped means in particular that a different or variable inclination of a screen deck 17 can be present in sections.
  • the lower screen deck 17 of the screening device 1 in figure 5 has several movable, pivotable and several rigid cross members 4, 5.
  • the upper screen deck 17 located above it has only rigid crossbeams 4, 5.
  • the sieve box 3 can be set into a main vibration by a main drive, not shown
  • the pivotable crossbeams 4, 5 of the upper screen deck 17 can be set into an additional, oscillating pivoting movement by a drive device 12 (not shown) in order to tension and/or relax the screen elements 6 lying thereon.
  • a revolving rotationally driven gear device 7 which is designed in particular as an eccentric gear device, is used to generate an exclusively oscillating pivoting movement of at least one second cross member 5 of a screening device 1 about the pivot axis A.
  • the screening device 1 can have a vibrating screen box 3 that has at least two outer side walls 2, with at least one first cross member 4 that is arranged between the two side walls 2 and, in particular, preferably rigidly connects the two side walls 2, and the at least one cross member about the pivot axis A pivotable second cross member 5, in particular wherein the second cross member 5 is arranged at least substantially parallel and/or adjacent to the first cross member 4 and/or is mounted in the two side walls 2.
  • At least one screen element 6 is also connected to the at least two crossbeams 4 during use in such a way that when the second crossbeam 5 is pivoted, the screen element 6 is tensioned and/or released.
  • FIGS 9 to 18 show a further preferred embodiment of the transmission device 7.
  • the previous statements on in the Figures 1 to 8 illustrated and preferred embodiments apply - as far as transferable from a technical point of view - also for in the Figures 9 to 18 illustrated further preferred embodiment of the screening device 1.
  • the screening device 1 is designed in particular as a flip-flow screening device and has a screen box 3 having at least two opposite side walls 2.
  • the screening device 1 comprises at least one first crossbeam 4 which can be arranged between the side walls 2 .
  • the screening device 1 has at least one second crossbeam 5 which is pivotable about a pivot axis A. What is not shown is that a screen element 6 is connected to the first and second crossbeams 4, 5 in such a way that when the second crossbeam 5 is pivoted, the screen element 6 is tensioned and/or released.
  • the second cross member 5 is assigned at least one revolving rotationally driven transmission device 7 for generating an exclusively oscillating pivoting movement of the second cross member 5 about the pivot axis A.
  • the transmission device 7 can be surrounded by an outer housing 36 at least in certain areas.
  • the outer housing 36 can also be referred to as a transmission housing and can be provided in particular for supporting the shafts of the transmission device 7 and/or for protection against contamination. Furthermore, the outer housing 36 can ensure oil bath lubrication.
  • the outer housing 36 is shown schematically as "transparent", so that in particular the components of the transmission device 7 that are used in the outer housing 36 can be seen.
  • the 10 represents a side view of the in 9 illustrated screening device 1.
  • the connection of the second cross member 5 via the coupling rods 14 and the connecting rods 15 can be seen.
  • This arrangement or (active) connection of the second cross member 5 with each other is already in connection with in the Figures 1 to 8 illustrated embodiments have been explained. Reference is hereby made to these statements.
  • FIGS Figures 1 to 8 shows a designed as an eccentric gear device gear device 7, which differs from that in FIGS Figures 1 to 8 shown transmission device 7 differs in terms of their specific training.
  • the gear device 7 shown can convert a rotary drive movement into an exclusively oscillating pivoting movement. This is shown schematically using the 14 evident.
  • the 14 shows the in 13 shown transmission device 7 without outer housing 36.
  • the movement or the direction of movement of the individual components is shown schematically by arrows. In particular, it can be seen that a rotary drive or output movement is converted into an exclusively oscillating pivoting movement via a linear movement.
  • the transmission device 7 has a drive unit 18, as shown schematically in FIG 11 is shown.
  • the drive unit 18 is stationary and has a drive shaft 19 .
  • a transmission means 20 is provided, which is designed in particular as a drive pin.
  • the transmission means 20 is also in the sectional views of 16 and 18 apparent.
  • the 17 and 18 show that the transmission means 20 is arranged eccentrically on the drive shaft 19, in particular in such a way that the drive shaft 19 is designed to drive the transmission means 20 in rotation.
  • the drive shaft 19 and the transmission means 20 can be connected to one another in a torque-proof manner.
  • the drive shaft 19 is connected to the transmission means 20 via a flange or a flange connection 37 .
  • the flange connection 37 makes it possible to change eccentric shafts or transmission means 20 with different eccentricities. Accordingly, it can be made possible that by replacing and / or adjusting the transmission means 20 of Pivoting angle and thus the amplitude of the expansion shaft or a pivoting means 31 can be adjusted. Ultimately, the pivoting angle of the pivoting movement of the pivoting means 31 is influenced.
  • the pivoting means 31 is explained in more detail below.
  • the transmission means 20 can be designed in one piece with the drive shaft 19 .
  • the transmission means 20 is firmly connected to the drive shaft.
  • a drive motor 21 is connected to the drive shaft 19 , which can ultimately be designed to drive the drive shaft 19 in rotation and is preferably arranged in a stationary manner and is supported in particular indirectly on the side wall 2 .
  • the drive motor 21 is in the Figures 10 to 18 not shown in detail.
  • the transmission device 7 has an eccentric housing 10 .
  • the eccentric housing 10 does not enclose the entire transmission device 7, but at least in some areas only a part of the components of the transmission device 7.
  • the eccentric housing 10 serves to accommodate and/or support the transmission means 20 at least in some areas.
  • the transmission means 20 engages in the eccentric housing 10 at least with at least one end side and/or front side.
  • the eccentric housing 10 is in operative connection with the transmission means 20, preferably such that the eccentric housing 10 via the transmission means 20 can be driven in rotation. Accordingly, the eccentric housing 10 can be articulated and/or rotatable on the transmission means 20, in particular via a transmission means bearing 22, preferably a roller bearing and/or a plain bearing, in particular the transmission means bearing 22 is designed as a self-aligning ball bearing.
  • the transfer medium bearing 22 is closer to the 16 and 18 shown.
  • the transmission medium bearing 22 is designed as a self-aligning ball bearing.
  • the transmission medium bearing 22 can allow the transmission medium 20 to be skewed.
  • the transmission means 20 is at least partially accommodated in the eccentric housing 10 and partially relative to the eccentric housing 10 protrudes.
  • the eccentric housing 10 can have a base plate 23 .
  • the base plate 23 is formed at least substantially cuboid.
  • a coupling element 25 which can be designed as a lever.
  • the coupling element 25 can be designed to convert the rotational movement of the drive shaft 19 into the preferably exclusively oscillating pivoting movement of the second cross member 5 .
  • This implementation or transfer of the rotary drive movement of the rotary driven drive shaft 19 is shown schematically in 14 shown.
  • the coupling element 25 can have a coupling side 26 .
  • the coupling side 26 is in the in 14 illustrated embodiment, the area that is coupled to the eccentric housing 10.
  • a pivoting side 27 of the coupling element 25 can be opposite the coupling side 26 .
  • the coupling element 25 can be configured at least essentially as a block and/or compact.
  • the coupling element 25 is preferably designed as an eyelet and/or as a bearing bush.
  • the coupling side 26 and the pivoting side 27 form in particular the outer ends or end sides and/or end areas of the coupling element 25 or have them.
  • the coupling element 25 can be mounted at least indirectly on the eccentric housing 10 so as to be linearly displaceable in relation to the eccentric axis Z of the transmission means 20.
  • the linear axis Q is shown schematically in 15 shown.
  • the linear axis Q can run obliquely to the drive axis X, in particular at least essentially orthogonally.
  • the joint axis Q can (but does not have to) intersect the drive axis X.
  • the coupling element 25 For storage of the coupling element 25 is in the 14 illustrated embodiment, at least one connecting means 28 is provided.
  • the coupling element is mounted on the coupling side 26 by means of a linear guide or by means of a linear bearing.
  • two connecting means 28 are used, which are designed as bearing journals.
  • the bearing pins are rigidly connected to the eccentric housing 10, but allow the displaceable arrangement of the coupling element 25 on the coupling side 26 via an operative connection with the coupling element 25.
  • the connecting means 28 is arranged in a corresponding bearing opening 29, the bore or the inner diameter of which corresponds to the outer diameter of the connecting means 28 exceeds. This is shown schematically, for example, using the in 16 sectional view shown.
  • the connecting means 28 is arranged in the bearing opening 29 with play.
  • the bearing opening 29 is formed in the area of the coupling side 26 .
  • the bearing opening 29 is preferably designed as an opening, with the connecting means 28 being able to protrude beyond the bearing opening 29 on both sides, as shown in FIG 15 becomes evident.
  • the connecting means 28 is arranged fixedly at the end or front side on a bearing block 30 , which in turn can be arranged on the side of the base plate 23 facing away from the drive unit 18 .
  • the bearing block 30 serves to mount or to support the connecting means 28 on the eccentric housing 10.
  • the connecting means 28 is/are also driven in rotation by the fixed arrangement on the eccentric housing 10, particularly when the drive shaft 19 is driven in rotation, they do not transfer this rotary movement to the coupling side 26 of the coupling element 25 Stop or the striking of the connecting means 28 used on the inner wall of the bearing opening 29 for power transmission. Accordingly, the coupling side 26 can be converted into a preferably linear movement or into an "up and down"/"up and down” movement.
  • the combination of the connecting means 28 and the bearing blocks 30 in connection with the bearing opening 29 on the coupling side 26 of the coupling element 25 can be viewed in particular as a linear bearing or linear guide which can be attached to the eccentric housing 10 .
  • the coupling element 25 can be connected to a pivoting means 31 on the pivoting side 27, in particular in a rotationally fixed manner.
  • the pivoting means 31 is designed as a pivot shaft.
  • the pivoting means 31 can be formed at least indirectly with the second cross member 5 for transmitting the exclusively oscillating pivoting movement.
  • the pivoting means 31 pivots about an in particular stationary pivoting center pivot axis R, which in particular coincides with the pivot axis A.
  • the pivoting center pivoting axis R can in particular form the longitudinal axis of the pivoting means 31 .
  • the 12 shows that the pivot center pivot axis R can coincide with the pivot axis A. Also shows 12 that the pivoting means 31 is arranged only indirectly on the second cross member 5, in particular wherein further machine parts, preferably for vibration damping, are arranged between the pivoting means 31 and the second cross member 5.
  • the pivoting means 31 can in particular be at least partially inserted into the pivoting side 27 of the coupling element 25 .
  • the coupling element 25 can have a pivoting means through-opening 32 on the pivoting side 27, which in 14 illustrated embodiment is designed as a breakthrough.
  • the pivoting means 31 can be guided through the pivoting means through-opening 32 and preferably protrude beyond the pivoting means through-opening 32 on both sides.
  • the 16 shows that a shaft-hub connection 33 for fastening the pivoting means 31 is arranged in the pivoting means passage opening 32 .
  • the shaft-hub connection 33 can be designed as a shaft-hub clamping set.
  • the coupling device 34 is used for vibration decoupling for the second cross member 5.
  • the base plate 23 has a transmission medium bearing hole 35 in a central portion of the base plate 23.
  • the transmission medium bearing opening 35 is used in particular for arranging the transmission medium bearing 22, as shown schematically in FIG 18 emerges.
  • a central axis Y of the transmission means bearing opening 35 preferably at least essentially coincides with the eccentric axis Z of the transmission means 20.
  • the eccentric axis Z forms the longitudinal axis of the transmission means 20.
  • the central axis Y and/or the eccentric axis Z can be arranged at least essentially parallel to the drive axis X, which in particular forms the longitudinal axis of the drive shaft 19 .
  • the drive axis X is in 16 shown.
  • central pivot axis R is arranged obliquely to the eccentric axis Z, to the drive axis X and to the central axis Y, in particular at least substantially orthogonally (at an angle of approximately 90°).
  • the connecting means 28 can have connecting means longitudinal axes K1, K2, which in particular are arranged at least essentially parallel to the pivoting center pivoting axis R or to the pivoting axis A.
  • the longitudinal axes of the connecting means K1, K2 are shown schematically in 14 shown.
  • the connecting center longitudinal axes K1, K2 can be arranged obliquely to the eccentric axis Z, to the drive axis X and the central axis Y, in particular at least essentially orthogonally (at an angle of approximately 90°).
  • shaft bearings 38 are provided for mounting the shafts or for mounting the pivoting means 31 and the drive shaft 19 .
  • the pivoting means 31 is arranged on or in a shaft bearing 38 at each end.
  • the drive shaft 19 is assigned a shaft bearing 38 at the end, in particular the drive shaft 19 being accommodated or arranged in the shaft bearing 38 at least in certain areas.

Landscapes

  • Combined Means For Separation Of Solids (AREA)

Claims (12)

  1. Dispositif de tamisage (1) avec un caisson de tamisage (3) présentant au moins deux parois latérales (2) opposées, avec au moins une première traverse (4) disposée entre les parois latérales (2), et avec au moins une deuxième traverse (5) pouvant pivoter autour d'un axe de pivotement (A), au moins un élément de tamisage (6) étant relié à au moins une première traverse (4) et à au moins une deuxième traverse (5) de telle sorte que, lors du pivotement de la deuxième traverse (5), il en résulte une tension et/ou une détente de l'élément de tamisage (6),
    au moins un dispositif de transmission (7) entraîné en rotation de manière circulaire étant associé à la deuxième traverse (5) pour générer un mouvement de pivotement exclusivement oscillant de la deuxième traverse (5) autour de l'axe de pivotement (A), et
    le dispositif de transmission (7) étant conçu comme un dispositif de transmission à excentrique,
    dans lequel le dispositif de transmission (7) comprend une unité d'entraînement (18) avec un arbre d'entraînement (19), un moyen de transmission (20) étant disposé de manière excentrique sur l'arbre d'entraînement (19) et
    dans lequel le dispositif de transmission (7) présente un carter d'excentrique (10) pour recevoir et/ou loger le moyen de transmission (20),
    dans lequel un élément de couplage (25) est prévu pour convertir le mouvement de rotation du moyen de transmission (20) et/ou du carter d'excentrique (10) en un mouvement de pivotement oscillant,
    dans lequel l'élément de couplage (25) est monté sur et/ou dans le carter d'excentrique (10) de manière à pouvoir se déplacer linéairement transversalement à l'axe d'excentrique (Z) du moyen de transmission (20).
  2. Dispositif de tamisage selon la revendication 1, caractérisé en ce que le moyen de transmission (20) est disposé de manière excentrique sur l'arbre d'entraînement (19) de telle sorte que l'arbre d'entraînement (19) est conçu pour l'entraînement en rotation du moyen de transmission (20), en particulier le moyen de transmission (20) et l'arbre d'entraînement (19) étant reliés entre eux de manière solidaire en rotation.
  3. Dispositif de tamisage selon la revendication 1 ou 2, caractérisé en ce que le moyen de transmission (20) est conçu pour l'entraînement en rotation du carter d'excentrique (10) et/ou en ce que le carter d'excentrique (10) est disposé de manière articulée et/ou rotative sur le moyen de transmission (20) et/ou en ce que le moyen de transmission (20) est disposé au moins partiellement sur et/ou dans le carter d'excentrique (10) et/ou est logé dans celui-ci.
  4. Dispositif de tamisage selon l'une des revendications précédentes, caractérisé en ce que l'élément de couplage (25) est relié à un moyen de pivotement (31) sur un côté de pivotement (27).
  5. Dispositif de tamisage selon l'une des revendications précédentes, caractérisé en ce que l'élément de couplage (25) présente, sur le côté de pivotement (27), une ouverture de passage du moyen de pivotement (32) pour l'agencement et/ou la réception du moyen de pivotement (31) et/ou en ce qu'une liaison arbre-moyeu (33) est agencée pour la liaison du moyen de pivotement (31) avec et/ou sur l'élément de couplage (25).
  6. Dispositif de tamisage selon l'une des revendications précédentes, caractérisé en ce que le moyen de pivotement (31) est relié au moins indirectement à la deuxième traverse (5) pour la transmission du mouvement de pivotement oscillant.
  7. Dispositif de tamisage selon l'une des revendications précédentes, caractérisé en ce que le carter d'excentrique (10) présente une plaque de base (23) de préférence parallélépipédique avec une ouverture de palier de moyen de transmission (35).
  8. Dispositif de tamisage selon l'une des revendications précédentes, caractérisé en ce que l'arbre d'entraînement (19) présente un axe d'entraînement (X), l'axe d'excentrique (Z) et/ou l'axe central (Y) étant disposé(s) parallèlement à l'axe d'entraînement (X).
  9. Dispositif de tamisage selon l'une des revendications précédentes, caractérisé en ce que l'axe de pivotement du moyen de pivotement (R) est disposé obliquement par rapport à l'axe d'entraînement (X) et/ou en ce que le au moins un moyen de liaison (28) présente un axe longitudinal de moyen de liaison (K1, K2), l'axe longitudinal de moyen de liaison (K1, K2) étant disposé au moins sensiblement parallèlement à l'axe de pivotement du moyen de pivotement (R) et/ou obliquement par rapport à l'axe d'entraînement (X) et/ou à l'axe d'excentrique (Z) et/ou à l'axe central (Y).
  10. Dispositif de tamisage selon l'une des revendications précédentes, caractérisé en ce qu'une deuxième traverse (5) couplée au dispositif de transmission (7) est en liaison active avec une autre deuxième traverse (5) non couplée au dispositif de transmission (7) par l'intermédiaire d'une barre d'accouplement (14).
  11. Dispositif de tamisage selon l'une des revendications précédentes, caractérisé en ce que le caisson de tamisage (3) est monté et/ou disposé de manière à pouvoir osciller.
  12. Utilisation d'un dispositif de transmission (7) entraîné en rotation de manière rotative, qui est conçu comme un dispositif de transmission excentrique, pour générer un mouvement de pivotement exclusivement oscillant d'au moins une deuxième traverse (5) du dispositif de tamisage (1) selon l'une des revendications précédentes.
EP21159880.0A 2020-03-06 2021-03-01 Dispositif crible, en particulier dispositif crible à effet trampoline Active EP3875180B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020001461 2020-03-06
DE102020002308.8A DE102020002308B3 (de) 2020-03-06 2020-04-16 Siebvorrichtung, insbesondere Spannwellensiebvorrichtung

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EP3875180A1 EP3875180A1 (fr) 2021-09-08
EP3875180B1 true EP3875180B1 (fr) 2023-06-14

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EP21159880.0A Active EP3875180B1 (fr) 2020-03-06 2021-03-01 Dispositif crible, en particulier dispositif crible à effet trampoline

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DE (1) DE102020002308B3 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021001207A1 (de) 2021-03-08 2022-09-08 WlMA Wilsdruffer Maschinen- und Anlagenbau GmbH Siebvorrichtung insbesondere Spannwellensiebvorrichtung

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1275339B (de) * 1967-07-13 1968-08-14 Albert Wehner Siebmaschine
DE3226574C1 (de) * 1982-07-16 1984-01-19 Hein, Lehmann AG, 4000 Düsseldorf Siebmaschine
DE3524895C1 (de) * 1985-07-12 1986-12-18 Hein, Lehmann AG, 4000 Düsseldorf Siebmaschine
DE3823896A1 (de) * 1988-07-14 1990-01-18 Hein Lehmann Ag Siebmaschine
CN104549980B (zh) * 2015-01-12 2017-02-01 黑龙江恒益电气股份有限公司 往复式振动输送机

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EP3875180A1 (fr) 2021-09-08
DE102020002308B3 (de) 2020-12-03

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