EP3875180A1 - Dispositif crible, en particulier dispositif crible à effet trampoline - Google Patents

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

Info

Publication number
EP3875180A1
EP3875180A1 EP21159880.0A EP21159880A EP3875180A1 EP 3875180 A1 EP3875180 A1 EP 3875180A1 EP 21159880 A EP21159880 A EP 21159880A EP 3875180 A1 EP3875180 A1 EP 3875180A1
Authority
EP
European Patent Office
Prior art keywords
eccentric
axis
cross member
sieve
drive
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP21159880.0A
Other languages
German (de)
English (en)
Other versions
EP3875180B1 (fr
Inventor
Felix Matheisl
Jörg Thomas
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
WIMA Wilsdruffer Maschinen und Anlagenbau GmbH
Original Assignee
WIMA Wilsdruffer Maschinen und Anlagenbau GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by WIMA Wilsdruffer Maschinen und Anlagenbau GmbH filed Critical WIMA Wilsdruffer Maschinen und Anlagenbau GmbH
Publication of EP3875180A1 publication Critical patent/EP3875180A1/fr
Application granted granted Critical
Publication of EP3875180B1 publication Critical patent/EP3875180B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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-flop screening device, with a screen box having at least two opposite side walls, with at least one first cross member arranged between the side walls, and with at least one second cross member pivotable about a pivot axis A, at least one screen element having at least one first cross member and at least one second cross member is connected, that when the second cross member is pivoted, tensioning and / or relaxation of the screen element results.
  • the present invention also relates to the use of a gear device for a screening device, in particular a flip-flop screening device of the aforementioned type.
  • a screening device of the aforementioned type difficult-to-screen feed materials, such as moist, sticky, clumping and / or sticking materials, can be separated and / or screened.
  • vibrations of components are used to separate the feed material.
  • the particularly flat screen element connected to at least two cross members is elastically deformed by regular movement of the cross members, for example the cross members swinging towards one another, and thus made to vibrate with respect to the screen box.
  • an oscillation or main oscillation of the screen box is usually provided in relation to the subsurface.
  • a sieve box which has at least two side walls and rigid cross members connecting the side walls.
  • a further movable crossbeam is arranged adjacent to each rigid crossbeam, in principle, in such a way that rigid and movable crossbeams are arranged alternately in the screen box.
  • elastic screen elements are typically arranged one behind the other on the cross members.
  • the sieve box of the known sieve device can be excited to vibrate in the form of a main vibration. It is then usual - based on the main oscillation - in a first alternative that the movable cross members are excited indirectly and vibrate, that is, are resonance excited 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 with one another.
  • the movable cross members are mechanically coupled to the main vibration, that is to say to the vibration of the screen box, forcibly excited and / or forcibly guided.
  • the basic disadvantage of the known screening device is that the relative movement between the cross members has to be implemented using a complex mechanical structure.
  • the known screening device also has a large number of components susceptible to wear.
  • the oscillation frequencies and oscillation amplitudes can only be varied to a very limited extent in the prior art and are partly, mostly completely, in mutual interaction.
  • the operation of the known screening device is also associated with high maintenance costs.
  • the resonance-excited oscillation in the known sieve device is particularly disadvantageous because its amplitude and / or frequency depends heavily on the properties and the amount of feed material located on the sieve element at a time, so it is ultimately load-dependent. This means that an increasing mass of feed material on the sieve element leads to the damping of the oscillation and thus, if necessary, sufficient tensioning and relaxation of the sieve linings is no longer achieved. Furthermore, the frequency and amplitude of the resonance-induced oscillation are directly dependent on the frequency and the amplitude of the sieve box oscillation, with a higher frequency not being achievable if required. The amplitude of the expansion of the screen linings cannot be predicted exactly, as it results from various, almost indeterminable dynamic factors of the relative vibration.
  • the leaf springs or rubber buffers which are often used to couple the vibrations between the screen box and the movable cross members, are also subject to high cyclical loads, which have a negative impact on their service life and can even lead to sudden failure.
  • the aforementioned disadvantages are difficult to achieve dominant interaction with a constant result of the sieving and a constant sieving quality.
  • the forcibly excited oscillation in the prior art in which the two oscillations are mechanically coupled to one another, is particularly disadvantageous because the oscillation frequencies are not mutually variable, but are coupled in the same direction to the main drive of the screening device.
  • the object of the present invention is therefore to avoid or at least substantially reduce the disadvantages of the prior art.
  • the aforementioned object is at least essentially achieved in that at least one circumferentially rotationally driven gear device for generating an exclusively oscillating pivoting movement of the second cross member about the pivot axis A is assigned to the second cross member.
  • the second cross member can preferably be pivoted about the pivot axis A at least essentially without translation.
  • the second cross member can thus be positively guided around the pivot axis A on a segment of a circular arc.
  • a pivoting or also a pivoting movement preferably has no - or at least essentially no - translational movement component.
  • the operator does not necessarily have to change the screening device according to the invention Readjust the feed material, since the amplitude and / or frequency of the oscillating pivoting movement are generally independent of the feed material.
  • a kinematic coupling and / or forced guidance of the at least one second cross member with respect to the at least one first cross member can be achieved.
  • the kinematic coupling means that the amplitude, the frequency and / or the exact swivel path of the swivel movement present can be load-independent and / or independent of the oscillation frequency of the sieve box, i.e. independent of the main oscillation of the sieve device.
  • both small and large quantities of feed material can be sieved in the device with at least essentially the same sieving result.
  • properties of the swivel movement can even be changed depending on the properties of the feed item. This significantly increases the flexibility of the screening device.
  • the sieve box can be mounted and / or arranged to vibrate, preferably with respect to the subsurface, the sieve box preferably being designed to be vibratable 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 screen 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 screen box, that is, a relative movement between the first and the second cross member.
  • the frequency and amplitude of the relative movement between the first and the second cross member are not influenced by the vibration of the screen 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 such that it can vibrate, 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 subsurface.
  • a spring-damper arrangement or at least one suspension and / or at least one damping element can be provided between the screen box and the subsurface.
  • the screen box should have a relative mobility within defined limits with respect to the subsurface, so that it can, for example, be set into a main vibration.
  • the invention also makes it possible that a main vibration of the screen box with respect to the oscillating pivoting movement and / or vibration of the second cross member can be carried out at least essentially independently of one another.
  • a simple, ultimately non-superimposed oscillating movement can be used for screening, in which either only the screen box is made to vibrate or only the at least one second cross member is made to vibrate.
  • This is advantageous if less difficult to screen feed material has to be processed in the screening device and a superimposed vibratory movement would cause throwing accelerations that are too high. This can save resources.
  • This can also be advantageous if very difficult to screen feed material is to be processed and several screening passes have to be made, of which only some require a superimposed oscillating movement. In this way, resources for operation and even machine costs can be saved, since this sieve device can in particular take over the tasks of simple and complex sieve devices.
  • the at least one and / or at least one screen element is connected to the first cross member and the, preferably adjacent, second cross member in such a way that the screen element is tensioned and / or relaxed when the second cross member is pivoted in an oscillating manner.
  • a sieve element can rest on at least two, preferably adjacent, cross members and can be connected to the cross members in the area of the support and / or that a screen element can be connected to the cross members.
  • Tensioning and / or relaxation of a sieve element is preferably characterized in that the sieve element is stretched and / or compressed.
  • tensioning and / or releasing the sieve element it can happen that feed materials are separated and / or sieved.
  • the alignment, position and / or shape of the sieve element within the sieve box can change quickly and repeatedly. For example, an up-and-down movement of the alternately tensioned and / or relaxed sieve element within the sieve box with the feed material lying on it leads to the feed material being accelerated or thrown accelerated and consequently moving within the sieve box and even being thrown.
  • a preferably at least regionally flat screen element is typically arranged obliquely at a predetermined angle with respect to the substrate.
  • connection between a sieve element and a cross member can be made non-positively and / or positively and / or with connecting means and / or materially in order to withstand the forces and moments that occur in particular.
  • one point of a sieve element in the upper region of a cross member is connected to this and that a further point of the sieve element in the upper region of another or further cross member is connected to this, so that a pivoting of at least one cross member causes a movement and / or can cause 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 cross members, so that it has a concave and / or convex surface when relieved, starting from its originally flat or curved surface .
  • the screen element can be deformed at least substantially vertically, for example in the direction of the subsurface, during compression and / or relaxation in the area between two cross members. Elastic and / or reversible deformations of a sieve element preferably occur.
  • the strain of the sieve lining which is preferably defined as the maximum spatial deviation from a fixed point on the surface of a sieve element in the tensioned and / or relaxed state compared to the initial state of a sieve element in a flat rest position, can be changed, in particular by 3% + / - 2%.
  • the screen lining stretch can be changed upwards and / or downwards as desired 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 set the screen box, which preferably has the cross members, in vibration.
  • a main drive motor which can set the screen box, which preferably has the cross members, in vibration.
  • an imbalance is arranged on a main drive shaft on the screen box, which can set the screen box in an oscillating vibratory movement, in particular in the main vibration, depending on the speed of the main drive shaft.
  • the oscillating pivoting movement of the second cross member can then be present independently of the main oscillation, but this can also be superimposed if necessary or ultimately not occur.
  • the frequency and / or amplitude of the oscillating pivoting movement of the second cross member can be set independently of a frequency and / or an amplitude of an oscillation of the screen box generated by a main drive.
  • the gear device is designed as an eccentric gear device.
  • the features and advantages of the invention relate to one or the transmission device, according to the invention relate in particular to one or the eccentric transmission device.
  • a very space-saving gear or a very space-saving gear device with a very high degree of efficiency is used through the gear device, in particular designed as an eccentric gear device, 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 due to its very compact design.
  • the transmission device is therefore very maintenance-friendly to handle and, moreover, can be operated with very little wear.
  • the transmission device preferably has at least a first eccentric and / or a second eccentric and / or an eccentric housing.
  • this enables at least essentially eccentric components or components having an eccentricity to be used as components which can be effectively connected in a very space-saving manner.
  • eccentric components such as the first eccentric and the second eccentric can be manufactured inexpensively, with little friction and low maintenance, preferably compared to toothed gear components.
  • the structure according to the invention can make it possible for the drive side and the output side to be arranged in at least approximately the same area and / or in the vicinity of 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 to ensure that the transmission device is easy to access.
  • the transmission devices also makes it possible for the transmission devices to face away from the contaminated area, in particular the inner area of the sieve device within the sieve box and / or the area between the side walls, and can thus be operated at least substantially in a fail-safe and low-maintenance manner and can also be designed more cost-effectively.
  • complex encapsulation of the transmission can be dispensed with.
  • the transmission device and / or the second cross member is preferably decoupled from the screen box, in particular via at least one coupling.
  • first eccentric is connected to a connecting section, in particular through the side wall, and is preferably connected non-rotatably to the second cross member.
  • the connecting section can be a central shaft of the second crossbeam, which can also be used for pivotable mounting of the second crossbeam on both sides.
  • the first eccentric can pivot non-rotatably on the pivot axis A of the second cross member.
  • 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 indirectly and / or directly. 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 advantageously be 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 full body, but can have a space-saving usable passage 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 be.
  • the first eccentric and / or the second eccentric and / or the eccentric housing has at least one bore, wherein the bore can be provided for an axis of another eccentric, for example, to be arranged compactly with one another and / or with one another.
  • the bore and / or the circular outer shape can thus be provided on an eccentric for, in particular, a rotatable mounting, wherein, for example, a bearing means such as a roller bearing and / or a plain bearing can be inserted into the bore.
  • the bearing means can be provided to enable a relative mobility of components of the transmission device with low friction.
  • 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 connected to one another in a rotatable manner.
  • the transmission device and / or the eccentric transmission device can have a lever mechanism.
  • a lever mechanism is to be understood as an assembly with at least two mutually arranged, interacting, operatively connected, supported, sliding and / or coupled components that are designed in particular to transmit and / or transform forces and / or movements .
  • a lever mechanism can, in particular, record, transmit and / or convert translational and / or rotary movements.
  • a lever mechanism typically has 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 transmission device - an incoming, circumferentially rotating input movement or rotation can be transformed into an outgoing, exclusively oscillating pivoting movement or an 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, from a rotational input movement, is a oscillating pivoting movement generated or geared as an output movement.
  • 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 also be provided which has, for example, components, in particular levers, with axes or eccentric axes or housing axes that are spaced apart from one another.
  • the first eccentric is mounted on and / or in the screen box and / or on and / or in the second eccentric and / or inserted on and / or in the second eccentric. It is further preferably provided that the eccentric housing is designed to receive and / or support the second eccentric. It is also possible that the second eccentric is mounted on and / or in the eccentric housing and / or is inserted on and / or in the eccentric housing.
  • 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.
  • the embodiment of the invention is therefore particularly preferred in which - in each case at least regionally - the first eccentric is mounted on the screen box so as to be pivotable in particular about the pivot axis A and rotatable in the second eccentric, in which the second eccentric is rotatably mounted in the eccentric housing and in which the eccentric housing is pivotably mounted on the sieve box.
  • this can advantageously result in a full rotation of the second eccentric in a very tight installation space necessitating at least one full back and forth pivoting of the first eccentric, with the size of the deflection of the pivoting movement being freely determinable in terms of design or structure.
  • the first eccentric has a first eccentric axis A 'and a first further eccentric axis B and / or that the second eccentric has a second eccentric axis B' and a second further eccentric axis C and / or that the eccentric housing has a housing axis C 'and a has 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 the transmission device to be extremely compact.
  • the components of the transmission device can be designed to be highly torsion-free in terms of reduced mass and the associated reduced manufacturing costs, since the power transmission and / or torque transmission can take place at least essentially on one plane or at least between two planes that are very close to one another.
  • 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 preferred at a fixed distance from one another.
  • the fixed spacing means that the position of the relevant axis (s) does not change during the operation of the eccentric device, that is to say preferably in relation to the side walls and / or the screen box.
  • the distances between the further axes and the aforementioned fixed axes can - at least partially - change during the operation of the transmission device, in particular so that the oscillating pivoting movement according to the invention can take place.
  • the fixedly spaced axes also correlate with the fact that the distance between at least two axes that belong to and / or are assigned to an individual component of the transmission device, i. H. at least of the first eccentric, of the second eccentric and / or of the eccentric housing, preferably of all three aforementioned components, is fixed to one another.
  • the eccentricities of the eccentrics are fixed and / or the center distances of the axes of the eccentric housing are fixed.
  • the eccentricity of at least one component of the transmission device is adjustable. It is accordingly also possible for the distance from the axes of the eccentric housing to be adjustable. It can also be provided that the spacing of the axes of the transmission device, which are preferably mounted in the sieve box, is adjustable.
  • Mobility and / or the resulting kinematics between the drive and output of the transmission device results from all selected and / or set center distances of the in particular at least three components (first eccentric, second eccentric, eccentric housing) to one another and preferably leads to the translation of a rotating 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 choice 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, in particular, the strain of the screen lining, at least essentially independently of the load.
  • the first eccentric with the first further eccentric axis B is preferably mounted pivotably and / or rotatably at least partially on and / or in the second eccentric, preferably coaxially and / or concentrically with the second eccentric axis B '. More preferably, the second eccentric with the second further eccentric axis C is at least partially rotatably mounted on and / or in the eccentric housing, preferably coaxially and / or concentrically with the housing axis C '. It is also preferred that the eccentric housing with the further housing axis D is at least partially pivoted 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 rotatably and / or pivotably 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 the coaxiality and / or the concentricity of two axes which ultimately share an at least almost identical local positioning.
  • the transmission device causes a pivoting of a further eccentric, preferably the first eccentric, 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 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 from one another in such a way that the continuous rotation of the second eccentric about the second further eccentric axis C and / or about the housing axis C 'the oscillating pivoting of the eccentric housing about the housing axis D is superimposed.
  • the fixed spacing from the aforementioned axes is advantageous since the mode of operation of the gear is predetermined and also predictable.
  • the kinematics of movement to be achieved can be predetermined and / or monitored in the form of the size of the swivel amplitude as a function of a full incoming rotation.
  • the gear ratio of the transmission device is at least essentially freely selectable, which results in a variety of purposes.
  • the strainer can advantageously be defined, at least essentially independent of the load.
  • the distance between the housing axis C 'and the further housing axis D is greater than the distance between the first eccentric axis A' and the first further eccentric axis B and / or greater than the distance between the second eccentric axis B 'and the second further eccentric axis C. It is also preferred that the distance between the first eccentric axis A 'and the first further eccentric axis B is greater than the distance between the second eccentric axis B' and the second further eccentric axis C.
  • the distance between the axes B' to C is the smallest and / or the distance between the axes C 'to D is the largest. It is thus possible that of the eccentricities present (i.e. of the eccentric housing, the first eccentric and the second eccentric) the eccentricity of the eccentric housing is the greatest 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 transmission ratio of the transmission device can advantageously be provided in order to react flexibly to variable input material.
  • the change in distance can in principle be made by means of adjustment means provided on the respective eccentrics and / or on the eccentric housing take place or, as already explained above, via an exchange of at least one corresponding eccentric part, in which a different axis arrangement results, that is to say the axis distances are different.
  • a change in a distance between two axes can advantageously be used to change the swivel amplitude of an eccentric and / or of the eccentric housing. This can be useful when different feed items have to be processed on one screening device. Ultimately, a large number of swivel amplitudes can be "covered” very easily and / or can be used quickly by adapting the transmission device. To this end, the transmission device does not have to be replaced by a further transmission device. There is also no need to keep an additional screening device in reserve. 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 to compensate for the oscillating swiveling of the eccentric housing and / or the oscillating swiveling of the second eccentric, in particular about the axis D or about the further housing axis D, preferably at least one, for example cardanic, coupling element and / or compensating element and / or universal joint 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 oscillatory movements and / or main vibrations of the sieve box and thus has 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 that the drive device is arranged on the screen box. In addition, it is also possible that the drive device is not arranged on the sieve box, namely, for example, indirectly or directly on the ground, while the gear device, however, can be arranged on the sieve box. Ultimately, it is advantageous that the drive device can be decoupled from the vibratory movements of the screen 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 the latter can be designed more cost-effectively. Sensitive components of the drive device can be arranged at least essentially free of vibrations.
  • the transmission device it is also possible for the transmission device to be designed so that it can be decoupled and / or decoupled from the screen box and / or from the second cross member with the aid of a coupling.
  • the or all of the second crossbeams, but at least one second crossbeam, is decoupled from the screen box.
  • a coupling, preferably by means of a belt drive, of the transmission device, in particular the second eccentric, can be possible 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.
  • 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 adaptable translation of the coupling, in particular the belt drive, and / or, for example, also through 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 drive of the transmission device can take place 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 changed in a simple manner via an adaptable translation of the belt drive and / or, for example, also via the speed.
  • vibration-sensitive components of the drive are at least substantially decoupled from vibrations which are essential for the screening of feed material, in particular on the sieve box.
  • the vibration-sensitive If necessary, 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 cross member coupled to the transmission device is preferably operatively connected to at least one further, second cross member not coupled to the transmission device via a coupling rod.
  • a preferably second cross member, to which no transmission device is assigned is 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 enables the operatively connected second cross members to always have at least essentially the same pivot position.
  • a coupling rod and / or a connecting rod also avoids the use of a large amount of material, since only one gear mechanism has to be provided, but if a large number of movable and / or pivotable second cross members are preferably present.
  • the use of a coupling rod and / or a connecting rod avoids a high mass, in particular on the screen box, which can, for example, adversely affect a vibratory movement of the screen box.
  • cross members preferably second cross members
  • a majority, in particular all, cross members, preferably second cross members are driven, preferably by means of at least one gear device, and / or can be set in a pivoting movement. Accordingly, it is an advantageous embodiment of the invention if a predominant number of cross members and / or all cross members of the screening device are movable and / or pivotable second cross members so that throwing accelerations can be increased.
  • both cross members move in different directions and it is also possible and preferred per se that one cross member is fixedly mounted while the other cross member is pivoted in an oscillating manner. It is also possible that both cross members oscillate in the same direction, in which case it can be decisive that the The deflection path of one cross member is greater than the deflection path of the other cross member, so that the sieve element is tensioned.
  • pivotable cross members can be pivoted synchronously, asynchronously, out of phase, with different amplitudes and / or frequencies in an oscillating manner.
  • a synchronization by means of a synchronization device can also be provided, 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 additionally or alternatively also be implemented in the form of a mechanical coupling, for example by means of a coupling rod and / or a connecting rod.
  • second cross members are driven by means of a transmission device, further second cross members being driven by at least one further transmission device and / or being able to be set in pivoting movement.
  • At least one transmission device is assigned to at least one second cross member and / or that it is coupled to this.
  • 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.
  • connecting rods and / or coupling rods and / or at least one synchronization device can be used in order to enable a co-directional and / or synchronous and / or asynchronous movement of a plurality of second cross members on a transmission device.
  • any desired combination of a number of transmission devices and a number of movable and / or pivotable second cross members that are assigned to and / or coupled to a transmission device in each case can be possible.
  • a transmission device is assigned to every second cross member. In order to generate a uniform oscillation vibration, all driven second cross members should be synchronized.
  • a resource-saving application results when only a single transmission device is used. It is also advantageous in this case that a space-saving and comparatively light structure is implemented.
  • a further embodiment of the invention provides that a plurality of first and second cross members are arranged adjacent and at least substantially parallel and / or spaced from one another, preferably in the screen box.
  • First and second cross members are particularly preferably arranged alternately in the screen box, so that at least one second cross member is adjacent to each first cross member and at least one first cross member is adjacent to every second cross member.
  • first cross members and then one or more second cross members are arranged alternately.
  • This also enables a novel multitude of oscillating movements and / or forms of movement which are advantageous for separating the feed material, in particular when achieving optimized and / or maximized throwing accelerations.
  • the number of first cross members corresponds at least approximately, that is to say with a deviation of less than +/- 10 cross members, preferably less than +/- 1 cross member, to the number of second cross members.
  • This achieves a cost-effective compromise between the rigidity of the structure, the structural complexity for the rotary and / or swivel mounting of second cross members and the level of the achievable throwing accelerations.
  • exclusively or at least essentially exclusively - taking into account the necessary stability of the screen box - one or more pivotable cross members are provided. So it is also possible that there is no rigid and / or non-pivotable cross member and / or no first cross member and only pivotable cross member and / or second cross member.
  • pivotable cross members and / or second cross members can pivot at least essentially in opposite directions and / or in the same direction in order to cause the tensioning and / or relaxation of the at least one screen element in the smallest possible installation space with high throwing 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 cross members rigidly connect the at least two side walls, since they can nevertheless be pivoted.
  • a further embodiment of the invention provides that at least two, in particular plane-shaped, rows of first and / or second cross members between the side walls are preferably arranged one above the other. At least one screen element can also be arranged on and / or on a series of cross members. The stringing together of cross members with at least one at least essentially resting screen element is an essential part of a so-called screen deck in the screen box and / or the screen device.
  • Sieve decks are preferably arranged obliquely or also horizontally with respect to the subsurface at a predetermined angle and have, in particular, planar or flat strings with sieve elements that are preferably at least substantially resting on them.
  • Sieve decks can also have banana-shaped, that is to say in some areas convex and / or concave and / or differently inclined, rows next to one another.
  • Sieve decks differ, for example, in the different opening widths of the associated sieve elements in order to be able to sieve different grain sizes.
  • the transmission device according to the invention be provided. However, the invention is not restricted to this.
  • One or more transmission devices can be arranged in or on the further screen decks.
  • the lowest sieve deck is assigned at least one gear device according to the invention for exclusively oscillating pivoting movement of at least one second cross member, while the sieve decks arranged above can ultimately be rigid in the sieve box. Only the possible main oscillation of the main oscillation 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 oscillation can be superimposed on the lower screen deck.
  • all screen decks can be provided with a transmission device according to the invention, it being possible in particular for movable second cross members to be arranged in each screen deck.
  • the exclusively oscillating pivoting movement which is generated by the transmission device, in particular as a result of an incoming revolving rotation, has the same frequency as the frequency of the main vibration acting on the screen box.
  • the frequencies of the two vibration systems can also be different.
  • the oscillation frequency of the oscillation drive can be smaller, but also greater 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 cross member is selected independently of the frequency of the main drive of the sieve box and / or the sieve device.
  • a sieve device with a sieve box having at least two opposing side walls, at least one first cross member arranged between the side walls and at least one second cross member pivotable about a pivot axis. It is provided according to the invention that at least one screen element is connected to the first cross member and the second cross member in such a way that the screen element is tensioned and / or relaxed when the second cross member is pivoted. In addition, it is provided according to the invention that the second cross member is assigned at least one circumferentially rotationally driven gear device for generating an exclusively oscillating pivoting movement of the second cross member about the pivot axis.
  • the alternative embodiment of the transmission device used in the screening device according to the invention can, however, differ from the embodiment described above with regard to the concrete structure. This applies in particular to the design of the eccentrics of the transmission device, as will be described below.
  • the gear device is particularly preferably 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 in particular be used for the 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 can have a drive shaft which is driven in a rotary manner (i.e. with a rotary movement).
  • a transmission means is particularly preferably arranged eccentrically on the drive shaft. Due to the eccentric arrangement of the transmission means, in particular an eccentric gear device can be provided. Ultimately, the eccentric arrangement makes it possible to convert a rotary movement into a pivoting movement.
  • 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 safe, 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 for the rotary drive of the transmission means. Accordingly, a rotary 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, in particular, a 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 can withstand high stresses can be made possible.
  • the transmission device can have an eccentric housing.
  • the eccentric housing does not have to surround and / or enclose the entire transmission device, but rather is intended in particular to be arranged 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 can be designed for receiving and / or mounting the transmission means.
  • the transmission means can be arranged at least partially on and / or in the eccentric housing.
  • the transmission means can be designed for the rotary drive of the eccentric housing and / or 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 rotatably arranged on the transmission means, preferably via a transmission means bearing, in particular via a preferably angularly movable roller bearing and / or an angularly movable sliding 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 rotary drive of the eccentric housing.
  • the angularly movable bearing makes it possible for 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 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 the pivot angle of the exclusively oscillating pivot movement and / or the amplitude of a pivot means or a pivot shaft can be influenced and / or the aforementioned pivot angle or the aforementioned amplitude can be set can.
  • the bearing for mounting 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 in particular 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 received in it.
  • a coupling element is provided, preferably for converting the rotary movement of the transmission means and / or the eccentric housing into a, preferably exclusively, oscillating pivoting movement.
  • the coupling element in particular has such a shape and is in particular arranged at least indirectly on the eccentric housing and / or the transmission means so that the aforementioned conversion of the rotary movement can be ensured.
  • the coupling element preferably has a coupling side.
  • a coupling side is understood to mean, in particular, a side, an area, a section and / or a coupling end of the coupling element.
  • the coupling side is that region, preferably an outer end region, of the coupling element which 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 some areas by the eccentric housing and / or adjoin the eccentric housing.
  • the coupling element can in particular be designed as a lever for generating the, preferably exclusively, oscillating movement.
  • a mechanical force converter which can be designed as a rigid body, is understood as a lever in particular.
  • the lever can be mounted rotatably 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 displaceably transversely to the eccentric axis of the transmission means, in particular on the coupling side.
  • the rotational movement of the eccentric housing or the transmission means can in particular be converted into a preferably translational movement on or in the area 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 preferably spaced apart from one another and / or arranged parallel to one another, are provided.
  • the connecting means is particularly preferably designed as a bearing pin. Via the operative connection with the connecting means, the conversion of the rotary movement can preferably be ensured initially into the translational movement on the coupling side and then into the preferably exclusively oscillating pivoting movement.
  • the connecting means can accordingly 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 substantially 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 fixedly arranged and / or inserted and / or mounted on the eccentric housing.
  • the at least one connecting means is preferably fastened and / or fixed on the eccentric housing at each end by a bearing block.
  • the bearing block can have an opening for at least regionally receiving the connecting means, in particular an end region of the connecting means.
  • the bearing block can be in one piece or preferably be formed in several parts. With a plurality of connecting means it can be provided that two bearing blocks are assigned to each connecting means.
  • the bearing block can in particular be arranged on and / or connected to a base plate of the eccentric housing.
  • the base plate is preferably cuboid.
  • the coupling element is preferably connected, in particular non-rotatably, to a pivoting means on a pivot side.
  • the pivot side can in particular be arranged on the side opposite the coupling side.
  • the pivoting side of the coupling element is that area, section and / or outer end side or area which is provided for connection and / or for coupling to the pivoting means.
  • the pivot means can also preferably be designed as a pivot shaft.
  • the pivot means is at least partially inserted and / or supported on the pivot 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, so as to be pivotable in an oscillating manner about a pivoting means pivot axis.
  • the pivoting center pivot axis is in particular stationary. Alternatively or additionally, it can be provided that the pivoting center pivot axis forms the longitudinal axis of the pivoting means.
  • the pivoting center pivot axis can in particular coincide with the pivot axis of the second cross member, whereby 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 passage opening on the pivoting side for the arrangement and / or receiving of 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.
  • the pivoting means through-opening can be designed for inserting part of the pivoting means, in particular wherein the pivoting means is 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. Accordingly, as explained above, the pivoting means 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 pivot means in particular represents the link between the coupling element and the second cross member.
  • the pivoting means is connected to the second cross member in a rotationally fixed manner and / or is arranged in a rotationally fixed manner on the second cross member. It goes without saying, however, that further components can be arranged between the second cross member and the pivoting means, so that the pivoting means does not have to directly adjoin the second cross member.
  • the coupling element can be designed as a block-like coupling part, in particular in the area of the coupling side.
  • the coupling element is preferably designed at least essentially in the shape of an eyelet in the area of the pivoting side.
  • the coupling element can be formed in one piece and / or composed of several parts 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 cross member and the pivoting means.
  • the coupling device serves in particular to decouple vibrations and thus preferably enables a reduction in wear.
  • the vibration decoupling can reduce malfunctions that would otherwise be caused in particular due to vibrations.
  • the eccentric housing can have a base plate.
  • the base plate can be used to arrange the bearing blocks.
  • the base plate also has a transmission means bearing opening.
  • the transmission means bearing opening is provided in particular for receiving 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 forces.
  • the base plate is preferably at least substantially cuboid.
  • a central 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 extension 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 substantially parallel to the drive axis. Accordingly, in particular, 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 pivoting center pivot axis is arranged obliquely, in particular at least substantially orthogonally, to the drive axis.
  • the pivoting center 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 connecting central longitudinal axis can in particular be arranged at least substantially parallel to the pivoting central pivoting axis and / or inclined, preferably at least substantially 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 wherein the outer housing is designed to accommodate the transmission device or 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 designed to be open or closed at the top.
  • the outer housing has a floor facing the subsurface and side walls that are fixedly arranged on the floor.
  • 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 end regions.
  • the outer housing can preferably be provided for mounting the pivoting means and / or the drive shaft.
  • protection against 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 are ensured.
  • At least one shaft bearing which is preferably arranged outside the outer housing, is provided for mounting the pivot shaft and / or the drive shaft.
  • the drive shaft is preferably arranged at least in some areas in a shaft bearing, in particular wherein the drive shaft can also protrude from the shaft bearing.
  • the pivoting means can be arranged, preferably with both end regions or end regions, at least in regions in a respective shaft bearing.
  • an arrangement can be provided that the pivoting means protrudes beyond the shaft bearing.
  • the end region of the pivoting means is completely received in the shaft bearing and preferably does not protrude beyond the shaft bearing.
  • a second cross member coupled to the transmission device is preferably operatively connected to at least one further, second cross member not coupled to the transmission device via a coupling rod.
  • a preferably second cross member, to which no transmission device is assigned is 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 enables the operatively connected second cross members to always have at least essentially the same pivot position.
  • a coupling rod and / or a connecting rod also avoids the use of a large amount of material, since only one gear mechanism has to be provided, but if a large number of movable and / or pivotable second cross members are preferably present.
  • the use of a coupling rod and / or a connecting rod avoids a high mass, in particular on the screen box, which can, for example, adversely affect a vibratory movement of the screen box.
  • cross members preferably second cross members
  • a majority, in particular all, cross members, preferably second cross members are driven, preferably by means of at least one gear device, and / or can be set in a pivoting movement. Accordingly, it is an advantageous embodiment of the invention if a predominant number of cross members and / or all cross members of the screening device are movable and / or pivotable second cross members so that throwing accelerations can be increased.
  • both cross members move in different directions and it is also possible and preferred per se that one cross member is fixedly mounted while the other cross member is pivoted in an oscillating manner. It is also possible for both cross members to oscillate in the same direction, in which case it can be decisive that the deflection path of one cross member is greater than the deflection path of the other cross member, so that the sieve element is tensioned.
  • pivotable cross members can be pivoted synchronously, asynchronously, out of phase, with different amplitudes and / or frequencies in an oscillating manner.
  • the sieve box can be mounted and / or arranged to vibrate, preferably with respect to the subsurface, the sieve box preferably being designed to be vibratable 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 screen 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 screen box, that is, a relative movement between the first and the second cross member.
  • the frequency and amplitude of the relative movement between the first and second cross member is not influenced by the vibration of the screen 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 such that it can vibrate, 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 subsurface.
  • a spring-damper arrangement or at least a suspension and / or at least one damping can be provided between the screen box and the subsurface.
  • the screen box should have a relative mobility within defined limits with respect to the subsurface, so that it can, for example, be set into a main vibration.
  • the invention also makes it possible that a main vibration of the screen box with respect to the oscillating pivoting movement and / or vibration of the second cross member can be carried out at least essentially independently of one another.
  • a simple, ultimately non-superimposed oscillating movement can be used for screening, in which either only the screen box is made to vibrate or only the at least one second cross member is made to vibrate.
  • This is advantageous if less difficult to screen feed material has to be processed in the screening device and a superimposed vibratory movement would cause throwing accelerations that are too high. This can save resources.
  • This can also be advantageous if very difficult to screen feed material is to be processed and several screening passes have to be made, of which only some require a superimposed oscillating movement. In this way, resources for operation and even machine costs can be saved, since this sieve device can in particular take over the tasks of simple and complex sieve devices.
  • the present invention relates to the use of a revolving rotationally driven gear device for generating an exclusively oscillating pivoting movement of at least one second cross member of a screening device, in particular a flip-flop 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 they have been described in connection with the screening device according to the invention.
  • a sieve device 1 which is in particular a flip-flop sieve device, which has a sieve box 3 with two outer, opposite side walls 2.
  • the side walls 2 of the sieve box 3 are arranged in parallel in the present case.
  • the screen box 3 can be made to vibrate with a main vibration by means of a main drive (not shown).
  • the sieve box 3 can be mounted so as to oscillate and preferably be decoupled from the subsurface.
  • a spring-damper arrangement or at least one suspension and / or at least one damping device can be arranged between the screen box 3 and the subsurface.
  • each case partially shown screening device 1 has a plurality of first cross members 4 arranged between the two side walls 2, in the present case rigidly connecting the side walls 2, wherein in the Fig. 4 a side wall 2 is hidden for reasons of visibility.
  • FIG. 1 to 5 Embodiments in which a plurality of second cross members 5, which can be pivoted about a pivot axis A, are provided.
  • the second cross members 5 are arranged parallel to and adjacent to the first cross members 4.
  • the second cross members 5 are mounted in the side walls 2, but not it is shown that the first cross members 4 can also be pivotably mounted in the side walls 2, for example.
  • the sieve device 1 of Fig. 1 and 2 has a screen 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 screen element 6 is tensioned and / or relaxed when the second cross member 5 is pivoted.
  • a sieve element 6 is connected to all of the cross members 4, 5 shown. It is not shown that a plurality of screen elements 6 can be provided, each of which is arranged at least substantially between and / or on at least two cross members 4, 5.
  • the sieve element 6 spans at least essentially the entire space between the side walls 6 and as a result - at least essentially - forms a sieve plane or a sieve deck.
  • the Fig. 2 shows a state of the second cross member 5 pivoted to the left compared to the starting position, in which the screen element 6 lying on top of it is tensioned and / or relaxed at least in some areas, in particular in the area between the cross members 4, 5.
  • the sieve element In the relaxed state during operation, the sieve 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 hurls and loosens the material to be sieved on the sieve element 6 upwards, so that better sieving can then take place.
  • a sieve element 6 for example in the upper region of a cross member 4, 5, is connected to the cross member 4, 5 and that another point of the same sieve element 6, for example, in the upper region of a further cross member 4, 5 is connected to the further cross member 4, 5.
  • the sieve element 6 can also be inserted and / or clamped into a cross member 4, 5 and / or firmly connected to a cross member 4, 5.
  • Two sieve elements 6, for example lined up next to one another, 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, the / which between two sieve elements 6 and / or through a sieve element 6 can be inserted and / or driven through into a gap and / or an insertion opening, in particular into a cross member 4, 5.
  • a gear device 7 which is driven in a rotating manner and designed as an eccentric gear device, for generating an exclusively oscillating pivoting movement of a second cross member 5 about the pivot axis A is assigned.
  • a screen box 3 with cross members 4, 5 can be set into a main oscillation and / or oscillation movement by a main drive.
  • the oscillating pivoting movement of the second cross member 5 can then be possible independently of the main oscillation of the screen box 3 by the main drive of the screening device 1 and can take place independently, be superimposed on the main oscillation or even be omitted when the main oscillation takes place.
  • the sieve box 3 can be mounted such 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 such that they can vibrate.
  • the sieve box 3 is in particular mounted at least essentially decoupled from the subsurface, preferably damped against vibrations.
  • a main drive preferably drives the screen box 3 in order to put it into the main oscillation.
  • the screening device 1 in particular the embodiments of Figs. 1 to 5 , is ultimately characterized by the fact that the second cross members 5 are positively guided on a circular path around a pivot point about the pivot axis A. This means that the amplitude and also the frequency of the oscillating pivoting movement are 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 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 shape of a shaft section and also of a disk shape.
  • Fig. 7 an exemplary embodiment, in particular a mechanical analogy model or a sketch that is not necessarily to scale, in which the first eccentric 8, the second eccentric 9 and the eccentric housing are at least substantially lever-shaped and / or rod-shaped.
  • the first eccentric 8, the second eccentric 9 and the eccentric housing 10 are components of a lever mechanism.
  • the lever mechanism can cause a pivoting of both another lever or the first eccentric 8 and a further 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 screen box 3 and is mounted in the second eccentric 9 and inserted into it.
  • the eccentric housing 10 is designed to receive and support the second eccentric 9, the second eccentric 9 being supported in the eccentric housing 10 and inserted into it.
  • Rolling bearings and / or plain bearings can be used for the bearings in order to enable pivotability and / or rotatability with low friction.
  • 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 a rotating manner, and the pivotable eccentric housing 10 are possibly exposed.
  • the second eccentric 9 has a second eccentric axis B ′ and a second further 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 also the pivot axis A and the housing axis D due to the coaxiality and concentricity of the pivot axis A and the first eccentric axis A ' - Are firmly spaced from each other.
  • first eccentric 8 with its first further eccentric axis B is mounted in the second eccentric 9 coaxially with the second eccentric axis B 'so as to be pivotable.
  • second eccentric 9 with the second further eccentric axis C is rotatably mounted in the eccentric housing 10 coaxially with the housing axis C '.
  • the eccentric housing 10 with its further housing axis D is in turn pivotably mounted on the sieve box 3.
  • the Fig. 7 shows a mechanical analogy model of a transmission device 7, which with the same mechanical functionality 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, i.e. ultimately the eccentricities, are decisive for the sizes of the swivel amplitudes of the components of the first eccentric 8 and eccentric housing 10 when the second eccentric 9 is rotated.
  • the distance between the axes C 'and D is several times greater than the distance between the axes A' and B and also several times greater than the distance between the axes B 'and C'.
  • the distance between axes B' to C is preferably the smallest and the distance between axes C 'to D is the largest.
  • the distance between the housing axis C 'and the further housing axis D is here several times greater 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 again greater than the distance between the second eccentric axis B 'and the second further eccentric axis C.
  • the eccentricity of the eccentric housing 10 (or the distances between the housing axes C 'and D from one another) is basically the largest of three eccentricities of the first eccentric 8, the second eccentric 9 and the eccentric housing 10, 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 essentially the same dimensioned as the eccentricity of the first eccentric 8. At least essentially the same dimension means here that the eccentricities are at most 25%, preferably 10%, particularly preferably 5%, differ or are also the same.
  • the second eccentric 9 is driven in rotation by a preferably stationary drive device 12, it being possible for two cardanic compensating elements 13 and / or universal joints to be provided in the drive train.
  • the drive device 12 is mounted and / or arranged independently of the gear device 7 or the eccentric housing 10. It can be provided that the drive device 12 is arranged on the sieve box 3, but it is also possible that the drive device 12 is not arranged on the sieve box 3, namely, for example, indirectly or directly on the ground, 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 screen box 3 and / or from the second cross member 5 via a coupling. It is also possible for the second cross member 5 to be decoupled from the screen box 3. It can be advantageous here that the drive device 12 can be decoupled from the vibrations via a compensating element 13 and / or a universal joint.
  • FIG. 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, which is not directly coupled to the transmission device 7, via at least one coupling rod 14.
  • a plurality of second cross members 5 can be driven by just a single transmission device 7, the cross members 5 being operatively connected to one another by means of a connecting rod 15 and a coupling rod 14.
  • second cross members 5 are driven, it being possible for a synchronization device 16 to synchronize the pivoting and / or the drive devices 12. It is also not shown that several second cross members 5 can be driven by several, in particular synchronized with one another, transmission devices 7.
  • coupled and / or uncoupled second cross members 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 cross members 4, 5 are arranged one above the other between the side walls 2, each of which forms a screen deck 17 in the screen box 3. For each screen deck 17, a plurality of screen elements 6 are in the present case arranged on the rows of cross members 4, 5.
  • Sieve decks 17 are typically flat, inclined and / or arranged at a fixed angle with respect to the ground. It is also possible for screen decks 17 to be arranged or designed in a sloping, rising and / or banana shape. 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 Fig. 5 has several movable, pivotable and several rigid cross members 4, 5.
  • the upper screen deck 17 located above it has exclusively rigid cross members 4, 5.
  • the screen box 3 can be set in a main vibration by a main drive, not shown, whereby the pivotable cross members 4, 5 of the upper screen deck 17 can be set in an additional, oscillating pivoting movement by a drive device 12, not shown, in order to tension the screen elements 6 on top and / or relax.
  • a preferably finest separating fraction can be discharged below the lower screen deck 17.
  • a separation fraction which has not passed through its screen elements 6 can be discharged from the feed material.
  • a circumferentially 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 pivot axis A.
  • the sieve device 1 can have at least two outer side walls 2 and oscillate sieve box 3, with at least one arranged between the two side walls 2, in particular the two side walls 2 preferably rigidly connecting, first cross member 4, and the at least one about the pivot axis A. have 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 further connected to the at least two cross members 4 during use in such a way that when the second cross member 5 is pivoted, the screen element 6 is tensioned and / or relaxed.
  • FIGS Figures 9 to 18 show a further preferred embodiment of the transmission device 7.
  • the preceding statements on the in FIGS Figures 1 to 8 The illustrated and preferred embodiments also apply to the in the Figures 9 to 18 Another preferred embodiment of the sieve device 1 shown.
  • Fig. 9 shows a schematic perspective illustration of a sieve device 1 - but without a sieve element 6.
  • the sieve device 1 is designed in particular as a flip-flop sieve device and has a sieve box 3 having at least two opposite side walls 2.
  • the screening device 1 comprises at least one first cross member 4, which can be arranged between the side walls 2.
  • the screening device 1 has at least one second cross member 5, which is arranged to be pivotable about a pivot axis A.
  • a sieve element 6 is connected to the first and second crossbeams 4, 5 in such a way that the sieve element 6 is tensioned and / or relaxed when the second crossbeam 5 is pivoted.
  • the transmission device 7 can be surrounded at least in some areas by an outer housing 36.
  • the outer housing 36 can also be referred to as a transmission housing and can be provided in particular for mounting 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 “transparently”, so that in particular the components of the transmission device 7 inserted in the outer housing 36 can be seen.
  • the Fig. 10 represents a side view of the in Fig. 9 Sieve device 1 shown. From Fig. 10 the connection of the second cross member 5 via the coupling rods 14 and the connecting rod 15 can be seen. This arrangement or (operative) connection of the second cross members 5 to one another is already in connection with the in the Figures 1 to 8 illustrated embodiments have been explained. Reference is hereby made to these statements.
  • Fig. 11 shows a gear device 7 designed as an eccentric gear device, which differs from that in the Figures 1 to 8
  • the transmission device 7 shown differs in terms of its specific design.
  • the illustrated transmission device 7 can convert a rotary drive movement into an exclusively oscillating pivoting movement. This is shown schematically using the Fig. 14 evident.
  • the Fig. 14 shows the in Fig. 13 illustrated transmission device 7 without outer housing 36.
  • the movement or the direction of movement of the individual components is shown schematically by arrows.
  • 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 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 shown in the sectional views of FIG Fig. 16 and 18th evident.
  • FIG. 16 shows Fig. 16 the section XVI-XVI Fig. 15 , whereby Fig. 15 a top view of the in Fig. 13 illustrated transmission device 7 is.
  • Fig. 18 again shows the section XVIII-XVIII from Fig. 17 , whereby Fig. 17 a side view of the in Fig. 13 transmission device 7 shown is.
  • the Figures 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 for the rotary drive of the transmission means 20.
  • the drive shaft 19 and the transmission means 20 can be connected to one another in a rotationally fixed manner.
  • the fact that the transmission means 20 is rotationally driven by the drive unit 18 or via the drive shaft 19 is shown in FIG Fig. 14 shown schematically via the "movement arrows".
  • Fig. 18 it is also shown that the drive shaft 19 is connected to the transmission means 20 via a flange or a flange connection 37.
  • the flange connection 37 enables eccentric shafts or transmission means 20 with different eccentricity to be changed. Accordingly, it can be made possible that by exchanging and / or adapting the transmission means 20, the pivoting angle and thus the amplitude of the tensioning shaft or of a pivoting means 31 can be set. 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. In Fig. 18 it is shown that the transmission means 20 is firmly connected to the drive shaft.
  • the eccentric housing 10 is in operative connection with the transmission means 20, preferably in such a way that the eccentric housing 10 via the transmission means 20 is rotationally drivable. Accordingly, the eccentric housing 10 can be articulated and / or rotatably arranged on the transmission means 20, in particular via a transmission means bearing 22, preferably a roller bearing and / or a sliding bearing, in particular the transmission means bearing 22 is designed as a self-aligning ball bearing.
  • the transmission medium bearing 22 is closer to FIG Fig. 16 and 18th shown.
  • the transmission medium bearing 22 is designed as a self-aligning ball bearing.
  • the transmission means bearing 22 can allow misalignments of the transmission means 20.
  • Fig. 16 shows Fig. 16 that the transmission means 20 is at least partially received in the eccentric housing 10 and partially protrudes from the eccentric housing 10.
  • the eccentric housing 10 can have a base plate 23.
  • the base plate 23 is at least substantially cuboid.
  • a coupling element 25 is shown as a further element of the gear unit 7, which can be designed as a lever.
  • the coupling element 25 can be designed to convert the rotary 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 revolving drive shaft 19 is shown schematically in FIG Fig. 14 shown.
  • the coupling element 25 can have a coupling side 26.
  • the coupling side 26 is in the in Fig. 14
  • the illustrated embodiment is that area which is coupled to the eccentric housing 10.
  • a pivot side 27 of the coupling element 25 can lie opposite the coupling side 26.
  • the coupling element 25 can be at least substantially block-like 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 pivot side 27 in particular form the outer ends or end sides and / or areas of the coupling element 25 or have them.
  • the coupling element 25 can be mounted on the eccentric housing 10, at least indirectly, 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 Fig. 15 shown.
  • the linear axis Q can run obliquely to the drive axis X, in particular at least substantially orthogonally.
  • the joint axis Q can intersect the drive axis X (but does not have to).
  • At least one connecting means 28 is provided in the illustrated embodiment.
  • 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 journals are rigidly connected to the eccentric housing 10, but allow the sliding 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 inner diameter of which corresponds to the outer diameter of the connecting means 28 exceeds. This is schematically illustrated, for example, using the in Fig. 16 shown sectional view can be seen.
  • the connecting means 28 is arranged with play in the bearing opening 29.
  • the bearing opening 29 is formed in the area of the coupling side 26.
  • the bearing opening 29 is preferably designed as a breakthrough, the connecting means 28 being able to protrude on both sides beyond the bearing opening 29, as shown in FIG Fig. 15 becomes apparent.
  • the connecting means 28 is fixedly arranged at the end or face on a bearing block 30, which in turn is on the one facing away from the drive unit 18
  • the bearing block 30 serves to support or 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, especially when the drive shaft 19 is rotationally driven, they do not transfer this rotary movement to the coupling side 26 of the coupling element 25 the stop or the stop of the connecting means 28 on the inner wall of the bearing opening 29 is used 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 in particular be viewed as a linear bearing or linear guide that can be fastened to the eccentric housing 10.
  • Fig. 14 shows that the coupling element 25 on the pivot side 27 can be connected to a pivot means 31, in particular non-rotatably.
  • the pivot 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 the transmission of the exclusively oscillating pivoting movement.
  • the pivoting means 31 pivots about an, in particular, stationary, pivoting means pivoting axis R, which in particular coincides with the pivoting axis A.
  • the pivoting center pivot axis R can in particular form the longitudinal axis of the pivoting means 31.
  • the Fig. 12 shows that the pivoting center pivot axis R can coincide with the pivot axis A. Also shows Fig. 12 that the pivoting means 31 is only arranged indirectly on the second cross member 5, in particular with further machine parts, preferably for vibration damping, being arranged between the pivot means 31 and the second cross member 5.
  • the pivot means 31 can in particular be at least partially inserted into the pivot side 27 of the coupling element 25.
  • the coupling element 25 can have a pivot means through-opening 32 on the pivot side 27, which is shown in FIG the in Fig. 14 illustrated embodiment is designed as a breakthrough.
  • the pivoting means 31 can be passed through the pivoting means passage opening 32 and preferably protrude over the pivoting means passage opening 32 on both sides.
  • Fig. 16 shows that a shaft-hub connection 33 for fastening the pivoting means 31 is arranged in the pivoting means through-opening 32.
  • the shaft-hub connection 33 can be designed as a shaft-hub clamping set.
  • a coupling device 34 is arranged between the second cross member 5 and the pivoting means 31.
  • the coupling device 34 serves to decouple the vibrations for the second cross member 5.
  • the base plate 23 has a transmission means bearing opening 35 in a central region of the base plate 23.
  • the transmission means bearing opening 35 is used in particular to arrange the transmission means bearing 22, as shown schematically Fig. 18 emerges.
  • Fig. 16 shows that a central axis Y of the transmission means bearing opening 35 preferably at least substantially 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 Fig. 16 shown.
  • Fig. 18 shows that the pivoting center 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 are in particular arranged at least substantially parallel to the pivoting center pivot axis R or to the pivot axis A.
  • the connecting center longitudinal axes K1, K2 are shown schematically in FIG Fig. 14 shown.
  • the connecting central 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 substantially 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 at each end on or in a shaft bearing 38.
  • a shaft bearing 38 is assigned to the end of the drive shaft 19, in particular the drive shaft 19 being received or arranged in the shaft bearing 38 at least in some areas.

Landscapes

  • Combined Means For Separation Of Solids (AREA)
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

Publications (2)

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

Family

ID=73264626

Family Applications (1)

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

Country Status (2)

Country Link
EP (1) EP3875180B1 (fr)
DE (1) DE102020002308B3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116060288A (zh) * 2022-12-16 2023-05-05 内蒙古双欣矿业有限公司 选煤厂煤泥减量装置

Families Citing this family (1)

* 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

Citations (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
EP0099528A2 (fr) * 1982-07-16 1984-02-01 Hein, Lehmann Aktiengesellschaft Appareil à tamiser
EP0208221A2 (fr) * 1985-07-12 1987-01-14 Hein, Lehmann Aktiengesellschaft Appareil à tamiser
DE3823896A1 (de) * 1988-07-14 1990-01-18 Hein Lehmann Ag Siebmaschine
CN104549980A (zh) * 2015-01-12 2015-04-29 黑龙江恒益电气股份有限公司 往复式振荡电机

Patent Citations (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
EP0099528A2 (fr) * 1982-07-16 1984-02-01 Hein, Lehmann Aktiengesellschaft Appareil à tamiser
EP0208221A2 (fr) * 1985-07-12 1987-01-14 Hein, Lehmann Aktiengesellschaft Appareil à tamiser
DE3823896A1 (de) * 1988-07-14 1990-01-18 Hein Lehmann Ag Siebmaschine
CN104549980A (zh) * 2015-01-12 2015-04-29 黑龙江恒益电气股份有限公司 往复式振荡电机

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116060288A (zh) * 2022-12-16 2023-05-05 内蒙古双欣矿业有限公司 选煤厂煤泥减量装置

Also Published As

Publication number Publication date
DE102020002308B3 (de) 2020-12-03
EP3875180B1 (fr) 2023-06-14

Similar Documents

Publication Publication Date Title
EP3875180B1 (fr) Dispositif crible, en particulier dispositif crible à effet trampoline
DE2521348B2 (de) Mahlgut
DE69820920T2 (de) Abgestimmter Schwingungsdämpfer mit doppelten Biegeelementen
DE2051626B2 (de) Schwingungsdämpfer
DE2553800A1 (de) Unwuchtantriebseinrichtung
EP0637559A1 (fr) Convoyeur linéaire à vibrations
EP2258488A2 (fr) Agencement d'entraînement pour un corps d'oscillation longitudinal
DE102012009984A1 (de) Laborkugelmühle
EP3579983B1 (fr) Dispositif de criblage de produit à trier
DE19983670B3 (de) Vibratoranordnung
EP1142651B1 (fr) Dispositif de tamisage
EP2363212B1 (fr) Générateur des vibrations réglable en continu
EP2208693B1 (fr) Convoyeur linéaire de vibrations
DE10312706B4 (de) Vibrations-Linearförderer
DD202400A5 (de) Siebmaschine
DE753502C (de) Antriebsvorrichtung zur Erregung mechanischer, technische Arbeit leistender, schwingungsfaehiger Systeme
EP2625970B1 (fr) Transporteur longitudinal pour produits en forme de tige de l'industrie de traitement du tabac
DE19846328A1 (de) Doppelseitige Drehmomentstütze
DE102007023963B4 (de) Vorrichtung für einen Schwingungserreger
DE102019105867A1 (de) Füllvorrichtung für eine Steinformmaschine
DE102015104041B4 (de) Siebmaschine
DE9216239U1 (de) Vibrationssiebmaschine
DE102021101421B3 (de) Ernteeinrichtung
DE2135323A1 (de) Schwingsieb, insbesondere schwingsieb fuer die feinabsiebung
DE3006762C2 (fr)

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN PUBLISHED

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20211111

RBV Designated contracting states (corrected)

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20220808

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

RIC1 Information provided on ipc code assigned before grant

Ipc: B07B 1/28 20060101ALI20221213BHEP

Ipc: B07B 1/42 20060101ALI20221213BHEP

Ipc: B07B 1/48 20060101AFI20221213BHEP

INTG Intention to grant announced

Effective date: 20230111

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502021000862

Country of ref document: DE

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1578848

Country of ref document: AT

Kind code of ref document: T

Effective date: 20230715

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG9D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20230614

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230614

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230914

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230614

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230614

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230915

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230614

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230614

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230614

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230614

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230614

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230614

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20231014

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230614

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230614

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230614

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20231016

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20231014

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230614

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230614

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230614

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502021000862

Country of ref document: DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230614

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230614

26N No opposition filed

Effective date: 20240315

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230614

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230614