EA043305B1 - ECCENTRIC VIBRATION DEVICE AND METHOD FOR CONTROLLING SUCH DEVICE - Google Patents

Description

Cross reference to related applications

This application claims benefit from U.S. Provisional Patent Application No. 62/632,348, filed February 19, 2018, the entire contents of which are incorporated herein by reference in their entirety.

List of drawings

The accompanying drawings are an integral part of the invention and are included in the present description. The drawings illustrate exemplary embodiments of the invention and, together with the description and claims, serve to explain, at least in part, various principles, features or aspects of the disclosure. Certain embodiments of the invention are described in more detail below with reference to the accompanying drawings. However, various aspects of the invention can be implemented in many different forms and should not be construed as limited to the implementations set forth herein. Like numbers refer to all similar, but not necessarily the same or identical, items.

In fig. 1 is a transparent perspective view of an eccentric vibrating device in accordance with one or more embodiments of the invention.

In fig. 2 is a transparent side view of an eccentric vibrating device in accordance with one or more embodiments of the invention.

In fig. 3A is a perspective top view of an eccentric vibrating device in accordance with one or more embodiments of the invention.

In fig. 3B is a perspective view from below of the eccentric vibrating device shown in FIG. 3A, in accordance with one or more embodiments of the invention.

In fig. 4 is an exploded view of an eccentric vibrating device in accordance with one or more embodiments of the present invention.

In fig. 5 is a sectional view of the eccentric vibrating device shown in FIG. 3A and 3B, in accordance with one or more embodiments of the disclosure.

In fig. 6A is a side view of a vibration system in accordance with one or more embodiments of the present invention.

In fig. 6B is a side view of a vibration system in accordance with one or more embodiments of the present invention.

In fig. 7A is a perspective view of a vibration system in accordance with one or more embodiments of the invention.

In fig. 7B is a perspective view of a vibration system in accordance with one or more embodiments of the present invention.

In fig. 8 is a diagram of a vibration system in accordance with one or more embodiments of the present invention.

In fig. 9 is a schematic diagram of an eccentric vibration device associated with a control system in accordance with one or more embodiments of the invention.

In fig. 10A is a schematic diagram of an eccentric vibrating device associated with a control system in accordance with one or more embodiments of the invention.

In fig. 10B schematically illustrates a vibration device coupled to a control system in accordance with one or more embodiments of the invention.

In fig. 11 illustrates time-dependent forces between mass elements of an eccentric vibration device in accordance with one or more embodiments of the invention.

In fig. 12 illustrates time-dependent forces between mass elements of an eccentric vibration device in accordance with one or more embodiments of the invention.

In fig. 13 illustrates time-dependent forces between mass elements of an eccentric vibration device in accordance with one or more embodiments of the present invention.

In fig. 14 illustrates time-dependent forces between mass elements of an eccentric vibration device in accordance with one or more embodiments of the invention.

In fig. 15 is a block diagram of an exemplary computer system on which the disclosed embodiments may be implemented, according to an embodiment of the present disclosure.

The essence of the invention and information confirming the possibility of its implementation

The invention provides systems and methods for generating vibration forces to control the motion of vibrating industrial equipment or other types of equipment, including consumer equipment and consumer electronics.

Disclosed embodiments include eccentric vibration systems that can produce substantially linear, elliptical and/or circular vibrations. Disclosed embodiments include vibration systems that may use such

- 1 043305 systems. The disclosed systems can produce corresponding substantially linear sinusoidal forces that cause substantially linear oscillations. In some embodiments, the vibration system may be mounted on the equipment and may apply a substantially linear sinusoidal force to thereby vibrate the equipment.

The disclosed control system can change the angle of motion and acceleration in the rumble. In one example, a slurry (eg, a semi-liquid mixture) may be dewatered and moved through a vibrating screen by vibrating motion. The suspension can be converted from a liquid-solid mixture to a dehydrated solid. To increase the dryness of the material, the disclosed embodiments allow the conveying angle of the system to be adjusted, which increases the removal of liquid from the mixture. For example, the transport angle can be increased from 45° to 60°. The increased angle can reduce the flow rate of material moving up the screening surface, allowing more time for liquid to be displaced from the mixture. Likewise, the vibrational acceleration of the system can be increased to increase fluid removal. Alternatively, vibration acceleration can be reduced, resulting in less liquid being removed if a wetter output is required. In dry screening applications, vibration of the material can also be increased to reduce the occurrence of stuck particles in the vibrating surface (ie, to reduce screen clogging).

In one embodiment, the device may include a first motor assembly and a second motor assembly that are located within the housing assembly. The first motor assembly may include a first shaft, and the second motor assembly may include a second shaft substantially collinear with the first shaft. The first shaft and the second shaft may be separate elements. The first motor assembly may also include a first mass group attached at a location proximate the first end of the first shaft, and a second, counterbalance mass group attached proximate to the second end of the first shaft, the second end of the first shaft being opposite the first end of the first shaft. The second engine assembly may include a third mass group. This third mass group may be attached in close proximity to the first end of the second shaft, adjacent to the first mass group of the first engine. The second motor assembly may further include a fourth mass group that serves as a balancing mass group for the second motor assembly and is attached proximate to the second end of the second shaft, opposite the first end of the second shaft.

The first shaft and the second shaft can rotate at a given frequency and in opposite directions, as a result of which the masses included in the device create an essentially linear sinusoidal force. Alternatively, the first and second shafts may rotate in the same direction to create an elliptical or circular motion. In some embodiments, the control system may be operably coupled to the device. The control system may control the rotation of the first and second shafts, the speed and/or the position of the mass elements to create forces having predetermined amplitudes and directions.

Although some embodiments of the invention are shown in connection with industrial equipment, the invention is not limited thereto. The eccentric vibration systems of the present invention may also be used in any other device where vibration is required, such as consumer equipment, consumer electronics, and other types of electronic devices.

In fig. 1 is a transparent perspective view of an eccentric vibrating device 100 in accordance with one or more embodiments of the invention. The eccentric vibrating device 100 includes a housing assembly 150, which may have an elongated shape defining an axis 102 (eg, designated z in FIG. 1). The eccentric vibration device 100 may also include a first motor assembly 110a and a second motor assembly 110b, each located within the housing assembly 150. In some embodiments, the first motor assembly 110a may include a first shaft 105a oriented substantially along axis 102, a first mass element 120a mounted eccentrically on the first shaft 105a, and a first balance mass element 130a mounted eccentrically on the first shaft 105a. .

As shown in FIG. 1, the first mass element 120a may be attached in close proximity to the first end of the first shaft 105a. The first balancing mass element 130a may be attached in close proximity to the second end of the first shaft 105a. Each of the first mass element 120a and the first balancing mass element 130a may include a group of elements. In one embodiment, the first element of the first mass element 120a and the first element of the first balancing mass element 130a may be configured to be substantially parallel and may be mounted at a predetermined angle about the circumference of the first shaft 105a relative to each other. In one example, the predetermined angle may be approximately 180 degrees (eg, as shown in FIG. 2 and discussed in more detail below).

The second motor assembly 110b may include a corresponding second shaft 105b oriented substantially along the axis 102, a second mass element 120b mounted eccentrically on the second shaft 105b, and a second balance mass element 130b mounted eccentrically on the second shaft. 105b. The second mass element 120b may be attached in close proximity to the first end of the second shaft 105b, with the first end of the second shaft 105b adjacent to the first end of the first shaft 105a. The second balancing mass element 130b may be attached adjacent the second end of the second shaft 105b, opposite the first end of the second shaft 105b. Each second mass element 120b and second balancing mass element 130b may include a group of elements. The first element of the second mass element 120b and the first element of the second balancing mass element 130b may be substantially parallel and may be mounted at a predetermined circumferential angle of the second shaft 105b relative to each other. In one example, the predetermined angle may be approximately 180 degrees (eg, as shown in FIG. 2 and discussed in more detail below).

Each first mass element 120a and second mass element 120b may have a first net mass. Likewise, the first mass balance element 130a and the second mass balance element 130b may have a second net mass. Various combinations of the first net mass and the second net mass may be selected, the amount of the second net mass depending on the amount of the first net mass, as explained in more detail below. For example, the first net weight may be approximately 24.0 kg, and the second net weight may be approximately 3.0 kg. In some embodiments, each element of the first mass element 120a may have a substantially circular sector shape with a radius of approximately 14.0 cm. Likewise, each element of the second mass element 120b may have a substantially circular sector shape with a radius of approximately 14.0 cm. In addition, each element of the first balancing mass element 130a may have a substantially circular sector shape with a radius of approximately 9.4 cm. Likewise, each element of the second balancing mass element 130b may also have a substantially circular sector shape with a radius approximately 9.4 cm. Other embodiments may include mass elements having other shapes, sizes and masses.

The eccentric vibrating device 100 can produce a substantially sinusoidal force with a controlled magnitude and orientation in a direction substantially perpendicular to the axis 102 (eg, in the x-y plane). In this regard, the first shaft 105a is rotatable about an axis 102 in a first direction with an angular frequency ω (real number in units of rad/s), and the second shaft 105b is rotatable about an axis 102 with an angular frequency ω in a second direction. In some embodiments, the second direction may be opposite to the first direction, while in other embodiments, the first and second directions may be the same. The angular frequency ω can be up to approximately 377 rad/s. Rotation in a first direction causes the first mass element 120a to produce a first radial force _Fa that is substantially perpendicular to the circular motion path (i.e., perpendicular to the velocity) of the first mass element 120a (as discussed in more detail below in consideration of FIGS. 11-14 ). Likewise, rotation in the second direction causes the second mass element 120b to produce a second radial force F _b that is substantially perpendicular to the path (ie, perpendicular to the speed) of the circular motion of the second mass element 120b. Rotation of the first shaft 105a and the second shaft 105b about the axis 102 may produce a resultant force that is substantially in a plane perpendicular to the axis 102 (eg, the x-y plane). A linearly oscillating force may be generated when the first shaft 105a and the second shaft 105b rotate in opposite directions. Alternatively, a force corresponding to a circular or elliptical motion may be generated when the first shaft 105a and the second shaft 105b rotate together, as discussed in more detail below.

The magnitude of the first force F _a may be determined in part by the angular frequency ω and the moment of inertia of the first mass element 120a. In addition, the magnitude of the second force F _b may be determined in part by the angular frequency ω and the moment of inertia of the second mass element 120b. Each element of the first mass element 120a may have a different mass or may have a common first mass, and each element of the second mass element 120b may have a different mass or may have a common mass. In one embodiment, the first and second masses may be approximately equal. In this case, the force F _a will have the same magnitude as the force F _b , regardless of the corresponding angular positions of the first and second mass elements. Counter-rotation of the first shaft 105a and the second shaft 105b with an angular frequency ω can produce a net force F=F _a +F _b that is maximum at an angular position in which the tangential velocity of the first mass element 120a and the tangential velocity of the second mass element 120b are substantially collinear and oriented in the same direction. Moreover, the resultant force F may disappear at an angular position in which the tangential velocity of the first mass element 120a and the tangential velocity of the second mass element 120b are substantially collinear and oriented in substantially opposite directions. In one embodiment, the amplitude of the time-dependent resultant force F may have a value of approximately 89,000 N for an angular frequency ω of approximately

- 3 043305 exactly 183 rad/s.

In some embodiments, the mass elements in the first mass element 120a may be configured as corresponding first plates disposed substantially perpendicular to the axis 102. Each of these first plates may be elongated and mounted substantially parallel to one another. In addition, each of these first plates can be mounted eccentrically on the first shaft 105a. Likewise, the mass elements in the second mass element 120b may also be configured as corresponding second plates, also located substantially perpendicular to the axis 102. Each of the second plates may also be elongated and mounted substantially parallel to one another. In addition, the second plates may be mounted eccentrically on the second shaft 105b.

Each of the first plates may have a given first mass and a given first size, and the second plates may also all have a given first mass and a given first size. Accordingly, the magnitude of the force _Fa and the magnitude of the force Fb may be substantially equal regardless of the respective angular positions of the first plates and the second plates. As mentioned, counter-rotation of the first shaft 105a and the second shaft 105b with an angular frequency ω can produce a net force F=F _a +F _b which is maximum at an angular position in which the tangential speed of the first plates and the tangential speed of the second plates are substantially collinear and oriented in the same directions. Likewise, the net force F may be substantially zero (or otherwise negligible) at an angular position in which the tangential velocity of the first plates and the tangential velocity of the second plates are substantially collinear and oriented in substantially opposite directions.

In some embodiments, as shown in FIG. 1, the first mass element 120a is mounted adjacent to and spatially separated from the second mass element 120b along axis 102. At an angular position in which the tangential velocity of the first mass element 120a and the tangential velocity of the second mass element 120b are substantially collinear and oriented in substantially opposite directions, the forces F _a and F _b disclosed herein cannot fully compensate each other due to imperfect alignment between the first mass element 120a and the second mass element 120b, as discussed in more detail below.

Incomplete force compensation may result in residual resultant forces that are oriented in a direction transverse to longitudinal axis 102. For example, residual resultant forces may be oriented along the x-direction of the Cartesian coordinate system shown in FIG. 1. The spatial alignment between the mass elements 120a and 120b and the residual resulting forces form a force pair that can distort the linear vibration generated by the eccentric vibration device 100. To eliminate or reduce such a force pair, a first balancing mass element 130a is added to the eccentric vibration device 100 and the second balancing mass element 130b, as disclosed above. As shown in FIG. 1 and 2, for example, the first balancing mass element 130a and the second balancing mass element 130b are also offset relative to each other along the longitudinal axis 102. Therefore, due to this spatial displacement, the balancing mass elements 130a and 130b also create an additional pair of forces as a result of incomplete mutual compensation of the forces created by these mass elements. By aligning the balancing mass elements 130a and 130b in a transverse direction opposite to the transverse direction along which the mass elements 120a and 120b are oriented, as shown in FIG. 2, for example, a pair of forces resulting from the counter-rotation of the balancing mass elements 130a and 130b may compensate for the pair of forces created by the mass elements 120a and 120b.

In some embodiments, the mass elements in the first balancing mass element 130a may share a common first mass, and the mass elements in the second balancing mass element 130b may share a common second mass. Thus, the magnitude of the masses 130a and 130b may be substantially the same. The magnitude of the first and second masses of the balancing mass elements 130a and 130b may be designed to be less than the net mass of the mass elements 120a and 120b due to differences in spatial displacements, which is necessary to compensate for the unwanted residual force couple from the interaction of the mass elements 120a and 120b.

As shown in FIG. 1, the first mass element 120a and the first balancing mass element 130a may be positioned to be in relative angular alignment with the offset. In addition, the second mass element 120b and the second balancing mass element 130b can also be installed with the same relative alignment offset. The relative alignment offset may be indicated by an angle θ (a real number in suitable units such as radians or degrees) between a line representing the orientation of the first mass element 120a and another line representing the orientation of the first balancing mass element 130a.

In one embodiment, for example, in which θ is substantially equal to π (or 180 degrees

- 4 043305 itself), as shown in Fig. 2, the net force F due to masses 120a and 120b may be oriented substantially opposite to the net force F' due to masses 130a and 130b. Thus, the resulting residual force couple is essentially zero when masses 120a and 120b are not aligned. Thus, the first balance mass element 130a and/or the second balance mass element 130b can be used to maintain the linearity of the oscillatory motion produced by the eccentric vibration device 100 when the shafts 105a and 105b rotate in opposite directions, as discussed in more detail below with reference to FIGS. 11-14.

As also shown in FIG. 1, the eccentric vibrating device 100 includes a first rotor mechanism 140a that generates rotation of the first shaft 105a. The vibration device 100 also includes a second rotor mechanism 140b that generates rotation of the second shaft 105b. In some embodiments, the first rotor mechanism 140a may include a first rotor assembly (not shown) mechanically coupled to the first shaft 105a and a first stator assembly (not shown) electromagnetically coupled to the first rotor assembly. The first rotor mechanism 140a may also include a first bearing assembly (not shown) mechanically coupled to the first shaft 105a adjacent the first mass member 120a, and may further include a second bearing assembly (not shown) mechanically coupled to the first shaft 105a. next to the first balancing element 130a. In addition, the second rotor mechanism 140b may include a second rotor assembly (not shown) mechanically coupled to the second shaft 105b and a second stator assembly (not shown) electromagnetically coupled to the second rotor assembly. The second rotor mechanism 140b may also include a first bearing assembly (not shown) mechanically coupled to the second shaft 105b adjacent the second mass member 120b, and may further include a second bearing assembly (not shown) mechanically coupled to the second shaft 105b. next to the second balancing mass elements 130b.

In some embodiments, the first rotor mechanism 140a may include a first feedback device, such as an encoder device (not shown), attached to the first shaft 105a. The first feedback device may provide one or more of first information indicating the corresponding position of at least one mass element of the first mass element 120a; second information indicating the angular velocity ω of the first shaft 105a; or third information indicating the rotation direction (eg, clockwise direction or counterclockwise direction) of the first shaft 105a. The position of the first mass element 120a is represented by an angle between 0 and 2π per revolution of the first shaft 105a relative to a predetermined origin corresponding to the particular installation of the first shaft 105a. The rotor mechanism 140b may further include a second feedback device, such as an encoder device (not shown), attached to the second shaft 105b.

The second feedback device may provide one or more of the first information indicating the corresponding position of the second mass element 120b; second information indicating the angular speed ω of the second shaft 105b; or third information indicating the rotation direction of the second shaft 105b. The position of the second mass element 120b is represented by an angle between 0 and 2π per revolution of the second shaft 105b relative to a predetermined origin corresponding to the specific installation of the first shaft 105b.

The first feedback device and the second feedback device may be implemented as respective encoder devices. Each of the respective encoder devices may be implemented as or may include, for example, a rotary encoder device. The rotary encoder device may include, for example, a 1024 pulses per revolution rotary encoder device. The encoder device may include a substantially circular plate that rotates with a shaft (either a first shaft 105a or a second shaft 105b).

The substantially circular plate may have holes interspersed with solid portions. The holes and the solid portion divide the plate into a plurality of arcs of substantially equal length forming a predetermined angle Δγ. The greater the number of holes in the encoder device, the smaller the Δγ value, and, therefore, the greater the resolution of the angular position of the encoder device. Each hole can represent a shaft angular position value. The encoder device may also include, for example, a light source device, a first sensor, and a second sensor. The light source device may illuminate a substantially circular plate, causing the first light sensor to output an electrical signal in response to the illumination and further causing the second light sensor to output another electrical signal in response to being covered by the solid portion. As the shaft rotates, the first sensor and the second sensor output corresponding pulse trains that can be used to determine the angular velocity of the shaft, the angular position of the shaft, and/or the direction of rotation of the shaft. The invention is not limited to rotary encoder devices, and other types of encoder devices may be used in various embodiments.

- 5 043305

By controlling the respective initial rotation angles of the first shaft 105a and the rotation of the second shaft 105b—and thus controlling the relative angular displacement between these shafts—the direction of the resultant force generated by the first mass element 120a and the second mass element 120b can be controlled. Thus, a net force directed in a desired or intended direction perpendicular to axis 102 can be achieved by configuring and maintaining initial angles and corresponding relative angular displacement between the respective substantially circular movements of the first shaft 105a and the second shaft 105b. Configuration of such initial angles can be performed during operation (with the mass element moving) or during startup (with the mass elements stationary) of the eccentric vibration device.

In fig. 3A and 3B show isometric views of an eccentric vibrating device 300 in accordance with one embodiment of the invention. The vibration device 300 of FIG. 3A includes a housing assembly that extends along an axis 302. The housing assembly includes a first assembly 330 and a second assembly 360. The first assembly 330 may accommodate a first motor assembly (e.g., engine assembly 110a of FIG. 1) and a second assembly 360 may accommodate a second motor assembly (eg, motor assembly 110b of FIG. 1). The first assembly 330 may include a first motor housing 335, a first cover plate 340 (which may be a junction box cover in some embodiments), and a first cover assembly 345. The first motor assembly (eg, the engine assembly 110a of FIG. 1) may be housed within the first motor housing 335. The second assembly 360 includes a second motor housing 365, a second cover plate 370 (eg, a junction box cover), and a second cover assembly 375. A second motor assembly (eg, motor assembly 110b of FIG. 2) may be housed in a second motor housing 365. Various materials may be used to manufacture the first assembly 330 and the second assembly 360. For example, any rigid material may be used, such as a metal (for example, and without limitation, aluminum), an iron-based alloy (for example, and without limitation, stainless steel), a non-ferrous alloy, another type of metal alloy, etc. In other embodiments, plastic may be used depending on the application (eg, for consumer electronics).

As shown in FIG. 3A, the first motor housing 335 includes a flange member 350 that has a plurality of holes configured to receive respective first fasteners. Likewise, the second motor housing 365 also includes a flange member 380 that also has a plurality of openings configured to receive corresponding second fasteners. The first fasteners and the second fasteners may respectively mate to enable the first motor housing 335 and the second motor housing 365 to be assembled into a single unit by the flange member 350 and the flange member 380.

The first engine housing 335 may also include second flange members 355 having one or more openings configured to receive a corresponding one or more fasteners. The second motor housing 365 may also include second flange members 385 having one or more openings configured to receive a corresponding one or more fasteners. The second flange members 355 and 385, along with one or more fasteners in each of the first motor housing 335 and the second motor housing 365 may be configured to couple the eccentric vibration device 300 to the equipment. As already mentioned, the vibration device 300 can be attached to industrial equipment, consumer equipment, consumer electronics, etc., to generate an oscillating motion in the equipment.

In fig. 4 is an exploded view of the eccentric vibrating device 300 of FIG. 3A and 3B, in accordance with one or more embodiments of the invention. As discussed above in connection with FIG. 3A and 3B, the eccentric vibrating device 300 includes a first housing assembly with a first motor housing 335, a first cover plate 340, and a first cover assembly 345. The eccentric vibrating device 300 also includes a second housing assembly with a second motor housing 365, a second cover plate 370, and a second cover assembly 375. The eccentric vibration device 300 also includes a first motor assembly and a second motor assembly, such as the first motor assembly 110a and the second motor assembly 110b of FIG. 1 and 2. The components included in these assemblies may form a structure having inversion symmetry about a plane that substantially bisects the eccentric vibrator 300, which plane is perpendicular to the longitudinal axis along which the eccentric vibrator is aligned.

In this example, the first motor assembly of the eccentric vibrating device 300 may include a fan 408a; engine end cover 410a; encoder mounting ring 412a; encoder 414a; and a first group of (balance or external) mass elements 415a. The first motor assembly may also include a first bearing assembly having a seal housing 416a, a shaft seal 418a, a shaft seal ring 420a, a first (outer) bearing 422a, and a first (outer) bearing housing assembly 424a. The first motor assembly may further include a seal housing 426a; additional shaft seal 428a; stator assembly 430a; and node

432a rotor.

The first motor assembly may further include a second bearing assembly having a seal housing 434a, an additional shaft seal 436a, a second (inner) bearing housing assembly 438a, a second (inner) bearing 440a, a seal housing 442a, a shaft o-ring 444a, and an additional seal 446a. shaft The first motor assembly may also include a second mass element including a mass element 448a and a second mass element 450a. Although the second mass element is illustrated as containing two mass elements, the invention is not limited to this. In additional embodiments, more than two mass elements or less than two mass elements may be installed. The first motor assembly may further include a first shaft 460a oriented along the longitudinal axis 302 of the eccentric vibrating device 300.

The second motor assembly of the eccentric vibration device 300 may include a fan 408b; engine end cover 410b; encoder mounting ring 412b; encoder 414b; and a first group of (balance or external) mass elements 415b. The second motor assembly may also include a first bearing assembly having a seal housing 416b, a shaft seal 418b, a shaft seal ring 420b, a first (outer) bearing 422b, and a first (outer) bearing housing assembly 424b. The second motor assembly may further include a seal housing 426b; additional shaft seal 428b; stator assembly 430b; and rotor assembly 432b. The second motor assembly may further include a second bearing assembly having a seal housing 434b, an additional shaft seal 436b, a second (inner) bearing housing assembly 438b, a second (inner) bearing 440b, a seal housing 442b, a shaft o-ring 444b, and a shaft seal 446b . The second motor assembly may also include a second mass element including a mass element 448b and a mass element 450b. Although the second mass element is illustrated as having two mass elements, the invention is not limited to this. In additional embodiments, more than two mass elements or less than two mass elements may be installed. The second motor assembly may further include a second shaft 460b oriented along the longitudinal axis 302 of the eccentric vibrating device 300.

In fig. 5 is a cross-sectional view of the eccentric vibrating device 300 of FIG. 3A, 3B and 4, in accordance with one or more embodiments of the invention. As shown, the first group of (balance or outer) mass elements 415a is mounted to have an alignment offset of approximately L relative to the mass elements 448a and 450a. The first group of (balance) mass elements 415b is set to have an alignment offset θ' of approximately -π relative to 448b and 450b. In addition, the alignment offset θ' between (i) the second mass element, which includes mass elements 448a and 450a, and (ii) the second mass element, which includes mass elements 448b and 450b, can be adjusted. Thus, the alignment offset θ' of approximately π, which is shown in FIG. 5 is exemplary, and other offsets may be made.

In fig. 6A is a side view of a vibration system 600 that utilizes an eccentric vibration device 300 in accordance with one or more embodiments of the invention. The vibration system 600 includes a deck assembly 610 that is mechanically coupled to the eccentric vibration device 300, for example, through matched flange members and fasteners (eg, flange members 355 and 385 of FIGS. 3A and 3B). During operation, the eccentric vibration device 300 can produce a time-dependent force f(t). Thus, during operation, the eccentric vibrating device 300 can apply a time-dependent oscillatory force f(t) to the deck assembly 610, causing a time-dependent oscillatory mechanical movement of the deck assembly 610. The intensity and period of oscillation of the mechanical movement can be determined by the angular frequency ω of rotation of the shafts in the eccentric vibration device 300 and other mechanical parameters, including moments of inertia.

The amplitude of the time-dependent force f(t) may be determined in part by the angular velocity ω of the shafts in the eccentric vibrating device 300, the respective resulting moments of inertia of the first mass element and the second mass element in the eccentric vibrating device 300, and the corresponding moments of inertia of the first balancing mass element and the second balancing mass element element in the eccentric vibrating device 300. The time-dependent force f(t) may be oriented in a direction substantially perpendicular to the longitudinal axis of the eccentric vibrating device 300 (eg, axis 102 in FIG. 1). Thus, the time-dependent force f(t) can be represented as a three-dimensional vector (f _x (t), f _y (t), f _z (t)), where the vector component f _z (t) can be essentially , zero, whereby the time-dependent force f(t) can be essentially equal to (f _x (t), f _y (t), 0). In an approximate scenario in which deck assembly 610 is started from rest and eccentric vibrating device 300 is energized from off, f(t) may self-level after a transient period (e.g., approximately 500 ms) in the direction passing through the position center of gravity (CG) 620 of the deck node in the x-y plane.

Such self-alignment may occur based on the conservation of angular momentum in the vibration system 600 after the eccentric vibrating device 300 is energized. Such alignment may be accomplished by selecting a motor assembly, such as an assembly that includes an induction motor (e.g., an induction motor) that allows sliding between input frequency and shaft speed. Thus, such a motor can produce torque without relying on physical electrical connections to the rotor. Accordingly, the angle φ indicating the orientation of the time-dependent force f(t) relative to the base side of the deck assembly 610 may be determined by the position of the eccentric vibrating device 300 on the deck assembly 610 along the x-direction in the coordinate system shown in FIG. 6A.

Although f(t) is shown to be strictly collinear with the line having the orientation φ, the actual f(t) produced by the eccentric vibrating device 300 eventually follows an ellipse with a semi-major axis parallel to the line having the orientation φ and a semi-minor axis that is much smaller (e.g., one, two, or three orders of magnitude) than the semimajor axis. Such an ellipse can be called a narrow ellipse. Specifically, angle φ decreases as the x-coordinate of the eccentric vibrator 300 increases (or, more simply put, as the eccentric vibrator moves forward along the deck assembly), and increases as the x-coordinate of the eccentric vibrator 300 decreases (or when the eccentric vibrator the vibrator moves backwards). Angle φ and value |f(t)| can determine the corresponding values of the vector components f _x (t) and f _y (t). For example, a small φ (i.e., a few degrees) can produce a large f _x (t) and a small f _y (t), while a large φ (i.e., several tens of degrees) can produce a small f _x (t) and a large f _y ( t). Thus, the angle φ can be adjusted to control the transport speed or residence time of solids or other types of solids in the xz plane of deck assembly 610.

Various mechanisms may be used to secure the eccentric vibrating device 300 to the deck assembly 610. For example, as shown in FIG. 6B, the mounting mechanism 650 may include a rail or other type of guide mechanism that can cause the eccentric vibrating device to move along the x-axis. Fasteners such as clamps, bolts, etc. may be used to secure the eccentric vibrating device 300 in the proper x-axis position. The mounting mechanism 650 may allow the eccentric vibrating device 300 to be positioned at various positions along the deck assembly 610. The fastening mechanism 650 may include another type of rail or guide mechanism that includes a plurality of locking mechanisms for securing the eccentric vibrating device 300 at predetermined positions along the x-axis. For example, as shown in FIG. 6B, the predetermined positions may include positions x1, _x2 , _x3 , _x4 , _x5 , _x6 , _x7 , _x8 and _x9 , where corresponding locking mechanisms are provided. The invention is, of course, not limited to nine predetermined provisions, and more than nine predetermined provisions or less than nine predetermined provisions can be implemented. In some embodiments, the plurality of locking mechanisms may include one or more gear members configured to engage other locking mechanisms that are contained in the bottom surface of the eccentric vibrating device 300. In other embodiments, the plurality of locking mechanisms may include corresponding openings (threaded or otherwise) which may receive corresponding bolts which may mate with corresponding nuts to secure the eccentric vibrating device in predetermined positions.

In fig. 7A and 7B are perspective views of an exemplary vibration system that utilizes an eccentric vibration device 710 in accordance with one or more embodiments of the invention. As shown, an eccentric vibrating device 710 is installed in the separation equipment deck assembly 720.

In some embodiments, the vibration orientation and the amount of resulting force exerted by the eccentric vibrating device can be adjusted without depending on changes in the position in which the eccentric vibrating device is mounted. In this regard, the control system may be operatively coupled to the eccentric vibrating device 710 to control the movement of the mass elements and shafts included in the eccentric vibrating device 710.

In fig. 8 is a diagram of a vibration system 800 that includes a control system operably coupled to an eccentric vibration device 300 in accordance with one or more embodiments of the invention. The control system includes one or more operator interface devices 830 and one or more motion controller devices 810. The vibration system 800 also includes one or more power supplies 820 that can power the motor assemblies included in the eccentric vibration device

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300, and/or at least one control system device. Power supply(s) 820 may include one or more power supplies and/or an AC power supply. Operator interface device(s) 830 may include input/output (I/O) interface device(s), such as a human machine interface (HMI), which may provide selection of a desired vibration mode (eg , an essentially linear disturbance or an essentially elliptical or circular disturbance).

Operator interface device(s) 830 may further provide real-time tracking or periodic tracking at specified times. The vibration mode may include a predetermined orientation and a predetermined amount of time-dependent force f(t) applied by the eccentric vibration device 300. The predetermined orientation is represented by an angle α in FIG. 8. As shown, α=0 will correspond to a time-dependent force f||(t) essentially oriented along the x-direction. In other words, fj|(t) is substantially parallel to the base side of the deck assembly 610. As also shown, α=π/2 will correspond to a time-dependent force f/(t), which is substantially vertical, oriented along the y direction, where f।(t) is substantially perpendicular to the base side of the deck assembly 610 .

Adjusting the operating mode may include adjusting a predetermined angular rotation speed of the shaft of the eccentric vibration device 300 and/or adjusting a predetermined angular displacement between the first eccentric mass element of the first motor assembly and the second eccentric mass element of the second motor assembly. Operator interface device 830 may receive input information indicating a desired angle α, angular frequency ω, and/or angular displacement. The input information may be used to configure the motion controller device 810 to control the vibrating motion of the eccentric vibrating device 300. Although the resulting f(t) produced by the eccentric vibrating device 300 is shown to be linear with orientation a, the actual f(t) produced by the eccentric vibrating device 300 eventually intersects an ellipse having a semi-major axis parallel to a line having slope α, and a semi-minor axis that is much smaller (e.g., one, two, or three orders of magnitude smaller) than the semi-major axis.

Depending on the required screening capacity, the α angle (which may also be referred to as the narrow ellipse angle) can be adjusted to cause the material to be screened to be conveyed slowly, thereby maximizing output dryness. Alternatively, the angle α can be adjusted to cause rapid movement of the material to be screened, thereby increasing the throughput of the machine, or can be adjusted to instantly reverse the transport of material, thereby shaking out stuck particles (i.e., eliminating clogging).

In addition, the angle α can be adjusted during operation, as disclosed herein, to an angle α' of approximately 90° over a predetermined period of time to ensure ongoing elimination of screen clogging in the screening device. After a predetermined period of time, the angle α', which is approximately 90°, can be reset to α. In various embodiments, other ongoing operating mode changes may be implemented. In one example, a transition may be made from an angle α ₀ of approximately 45° to an angle α' of approximately 60° to slow down transport and provide a drier output from the slurry supplied to the eccentric linear vibrator deck assembly 300. Then a transition from an α' angle of approximately 60° to an α ₀ angle of approximately 45° can be realized to resume faster transport. In another example, an angle α of approximately 45° can be adjusted during operation, as disclosed herein, to an angle α' of approximately 30° over a predetermined period of time to remove accumulated material on the screen. After a predetermined period of time, the angle α', which is approximately 30°, can be reset to α.

Such adjustment may be required when operating the screen to screen slurry. During screening, the slurry changes from a liquid-solid mixture to a dewatered solid. The α angle can be adjusted to increase dryness. For example, if the angle α increases from about 45° to about 60°, as disclosed above, the screening material flow rate decreases. This reduction in flow rate allows more time for liquid to be displaced from the slurry as the material moves more slowly towards the discharge end of the screen.

In fig. 9 schematically illustrates a system that may include motion controller device(s) 810, controller device 920, and drive devices 930. Control device 920 may be implemented as or include a programmable logic controller (PLC). ), a microcontroller, etc., and the drive devices 930 may be implemented as or include electronically controlled electric drives, variable frequency drives (VFDs), etc. Controller mouth

The device 920 may receive information indicating the position, speed of the eccentric mass elements, and/or the direction of rotation of the eccentric vibration device 300. The controller device 920 may control the drive devices 930 to create a predetermined operating mode. In this regard, feedback devices 910 may be coupled to the respective shafts of the eccentric vibrating device 300 and may provide first information indicating the respective positions of the mass elements.

The feedback devices 910 may also provide second information indicating the respective angular velocities of the shafts. The feedback devices 910 may provide third information indicating the direction of rotation of the shaft of the eccentric vibrating device 300. In one embodiment, the first information, the second information, and the third information may be provided directly to the controller device 920. In another embodiment, the first information, the second information and the third information may be indirectly provided to the controller device 920, wherein such information is provided to the corresponding drive devices 930 and transmitted by the drive drive devices 930 to the controller device 920. The controller device 920 may control the drive devices 930 to produce rotational motion of at least one of the collinear eccentric vibration device shafts 300.

The feedback devices 910 may include a first feedback device (such as a first encoder device) attached to a first shaft of the eccentric vibrating device 300. The first feedback device may send one or more of (a) first information indicating an appropriate a position of at least one of the first mass elements of the eccentric vibration device 300, (b) second information indicating the angular velocity of the first shaft, or (c) third information indicating the direction of rotation of the first shaft. Feedback devices 910 may also include a second feedback device (such as a second encoder device) attached to a second shaft of vibrating device 300. The second feedback device may send one or more of (a) fourth information indicating the corresponding a position of at least one of the second mass elements of the eccentric vibration device 300, (b) fifth information indicating the angular velocity of the second shaft, or (c) sixth information indicating the direction of rotation of the second shaft.

The controller device 920 may further receive first information, second information, third information, fourth information, fifth information, sixth information, and information from the operator interface device 830, and may instruct the drive devices 930 to adjust the rotational movements of the first shaft and the second shaft based on at least the received information. In one embodiment, controller device 920 may receive such information directly from the first feedback device and the second feedback device. In another embodiment, controller device 920 may receive first information, second information, third information, fourth information, fifth information, and/or sixth information indirectly, which information is provided to drive devices 930 and transmitted by drive devices 930 to controller device 920.

The drive devices 930 may include a first drive device coupled to a first motor assembly including a first shaft of the eccentric vibrating device 300. The control device 920 may instruct the first drive device to generate rotational motion of the first shaft based on one or more of the first portions. information; parts of the second information; portions of the third information and information of the operator interface device 830. The drive devices 930 may also include a second drive device coupled to a second motor assembly including a second shaft of the eccentric vibrating device 300. The controller device 920 may direct the second drive device to configure rotational motion a second shaft based on one or more of the fourth portion of information; parts of the fifth information; part six information and information of the operator interface device 830.

In fig. 10A schematically illustrates an eccentric vibrating device 1000 coupled to a control system in accordance with one or more embodiments of the invention. As shown in FIG. 10A, system 1000 may include a controller device 1010, which may be implemented as, or may include, a programmable logic controller. In addition, drive devices 930 may be provided (eg, see FIG. 9), which may be implemented as, or may include, a first electronically controlled electric drive 1020A and a second electronically controlled electric drive 1020B. The invention is not limited to electronically controlled electric drives having a common architecture. The first electronically controlled electric drive 1020A and the second electronically controlled electric drive 1020B may drive respective motor assemblies in the eccentric vibrating device 300. In this regard, the first electronically controlled electric drive 1020A may include an electronic converter or other type of power source associated with ( for example, electromechanically coupled) to the first motor assembly, for example, through power line assembly 1060A. The second electronically controlled electric drive 1020B may include an electronic converter or other type of power source coupled to the second motor assembly via a second power line assembly 1060B.

The first and second power line assemblies 1060A and 1060B may include, for example, electrical conductor, power connectors, insulating covers, etc. The first electronically controlled electric drive 1020A and the second electronically controlled electric drive 1020B may be connected to respective power lines 1030A and 1030B that are connected to an AC power source (eg, a 50 Hz AC power source or a 60 Hz AC power source). In addition, the first electronically controlled motor 1020A may be coupled (electrically or electromechanically) to the first feedback device of the eccentric vibrating device 300 via a first bus 1070A. The second electronically controlled electric drive 1020V may also be coupled (electrically or electromechanically) to the second bus 1070V. The first and second bus structures 1070A and 1070B provide transmission of information (analog and/or digital) that may represent the angular position, angular velocity, and/or direction of rotation of the shaft of the eccentric vibrating device 300. The invention is not limited to buses that share a common architecture.

As also shown in FIG. 10A, system 1000 may further include operator interface device(s) 830 and remote operator interface device(s) 1080. Operator interface device(s), programmable logic controller 1010, first electronically controlled drive 1020A, and second electronically controlled drive(s) 1020B control may be connected by network devices 1050 (such as a high-speed network device or bus). Network devices 1050 may exchange information (eg, data and/or signaling) between operator interface device(s) 830, programmable logic controller 1010, first electronically controlled drive 1020A, and second electronically controlled drive 1020B. One or more remote operator interface devices 1080 may be coupled to network device 1050 via wireless communications links and/or wired communications links 1085. The device(s) 1080 may provide adjustment and/or monitoring of the operation of the eccentric vibration device 300.

In fig. 10B schematically illustrates a vibration system 1090 having a control system that is operably coupled to other types of eccentric motors to thereby control the type of motion generated by the eccentric motor. For example, the control system may be operatively coupled to conventional eccentric motors 1095a and 1095b, such as eccentric motors that do not include collinear shafts. According to one embodiment, the rotational mode (eg, angular velocity and direction of rotation) of each of the conventional motors 1095a and 1095b can be controlled independently. For example, to generate a substantially linear mechanical disturbance, the PLC 1010 may control the first electronically controlled motor 1020A so that the eccentric motor 1095a rotates in the first direction at an angular velocity ω. The PLC 1010 may further control the second electronic motor drive 1020B so that the eccentric motor 1095b rotates in a second direction opposite to the first direction at an angular velocity ω. In another example, to generate a substantially circular mechanical disturbance, the PLC 1010 may control the first electronically controlled motor 1020A to cause the eccentric motor 1095a to rotate in a first direction at an angular velocity ω. The PLC 1010 may further control the second electronically controlled motor 1020B so that the eccentric motor 1095b also rotates in the first direction at an angular velocity ω.

As discussed above, a control system that includes motion controller(s) 810 (eg, see FIG. 8) can create a predetermined operating mode of the inventive eccentric vibrating device. The control system may adjust and/or control appropriate movements—such as appropriate angular velocities and angular positions of collinear shafts present in the eccentric vibrating device—independently and continuously, nearly continuously, or at specified times (e.g., periodically, nearly periodically, or on a schedule) . For example, the mode of operation can be monitored and/or adjusted as needed in near real time (or essentially periodically, at time intervals that are significantly shorter than, for example, hundredths, thousandths, millionths, etc. rotation period 1/ω of the device shaft) without turning off the power to the eccentric vibrator. In this regard, the motion controller device(s) 810 may use various methods, including electronic speed switching, to adjust the angular velocity and/or angular position of the shaft during operation of the eccentric vibrating device, without the need to turn off power to the eccentric vibrating device to perform the operation reconfiguration.

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As disclosed above, the control system may be configured to set and maintain a relative angular displacement between respective rotational movements of the collinear shafts of the eccentric vibrating device. In this case, the control system can set the corresponding initial angles of the corresponding rotational movements of the collinear shafts. The corresponding starting angles can be determined relative to the reference coordinate system, and can determine the oscillation orientation of the resultant force f(t) (essentially a sinusoidal force) generated by the eccentric vibrating device. Orientation can be represented by an angle relative to a given direction in a reference coordinate system. For example, the reference coordinate system may be a Cartesian system having an axis (eg, the z-axis as shown in FIG. 8) substantially parallel to the longitudinal axis of the eccentric vibrating device. The direction representing the oscillation orientation of the resultant force f(t) may lie in a plane (eg, the x-y plane in FIG. 8) that is perpendicular to the z-axis.

In fig. 11-14 show schematic force plots for four corresponding starting angle configurations and corresponding relative angular displacements at nine different instants during operation of the eccentric vibrating device 1100 in accordance with the embodiments disclosed herein.

In fig. 11 shows the force configurations at times t ₀ , t 1 , t ₂ , t ₃ , t ₄ , t ₅ , t ₆ , t ₇ and t ₀ +T for initial angles equal to 0 for both collinear shafts in the eccentric vibrating device 1100 , causing the relative angular displacement to be essentially 0. At any given time, the forces are indicated by arrows inside the circle, and the shaded areas indicate the positions of the corresponding masses. The arrows located outside the circle indicate speeds. The forces corresponding to the corresponding groups of mass elements are shown by thin arrows, and the resulting forces F are represented by thick arrows. In this example, the angles are defined relative to the Cartesian coordinate system shown in FIG. 11, and T represents the period of rotation of the collinear shafts. For the initial angular configuration and its corresponding relative angular displacement in this example, the first mass element of the eccentric vibrating device 1100 can be substantially aligned with the second mass element at angles 0 and π, as shown by the graphs corresponding to t ₀ and t ₄ .

At any given time, the force exerted by a given mass (eg, shown by the thin arrow inside the circle) is essentially perpendicular to the velocity (eg, shown by the arrow outside the circle) of the mass elements. Masses create forces of equal magnitude. For example, the first mass element and the second mass element may apply a force F _a and a force F _b , respectively, where |F _a | = |F _b |. As shown in FIG. 11, for initial angles substantially equal to 0, the resulting force f(t) may be oriented along the x direction or parallel to the base of the eccentric vibrating device 1100. In addition, the forces cancel out at times t ₂ and t ₆ and point toward a negative x direction at time t4. The configuration in Fig. 11 thus causes horizontal transverse vibration (oscillation) of the equipment (such as the deck assembly or screen basket) on which the force is applied. For example, the screen frame or deck assembly may vibrate in a plane that is substantially horizontal.

In fig. 12 shows a second vibration mode in which the linear vibrations are oriented at an angle relative to the horizontal, in accordance with one embodiment of the invention. In this example, the control system can instantaneously retard the first shaft and instantaneously increase the speed of the second shaft of the eccentric vibrating device, thereby adjusting the respective initial angles of the first shaft and the second shaft, which give a relative angular displacement approximately equal to π/4 (given t ₂ is t ₀ in Fig. 12). In fig. 12, one of the mass elements may be advanced, for example, by π/4, and the other of the mass elements may be lagging behind, for example, by π/4. Thus, the first mass element can be substantially aligned with the second mass element at angles π/4 and 5π/4, as shown in the graphs corresponding to t ₀ and t ₄ . For such initial angles and the associated relative angular displacement, the resulting force f(t) may be oriented at an angle of approximately π/4 relative to the base of the eccentric vibrating device 1100.

In fig. 13 shows a third vibration mode in which the linear vibrations are oriented at an angle relative to the horizontal, in accordance with one embodiment of the invention. By setting the initial rotation angles of the first shaft and the second shaft to be approximately 3π/4, a relative angular displacement of approximately 3π/4 can be obtained, as shown in FIG. 13 (the given t ₂ is equal to t ₀ in Fig. 13). In this example, the first mass element may be substantially aligned with the second mass element at angles of 3π/4 and 7π/4, as shown by the graphs corresponding to times t ₀ and t ₄ in FIG. 13. Thus, rotating the oscillation orientation of the resultant force f(t) by an angle π/2 relative to the orientation for a relative angular displacement of π/4 (see FIG. 12) provides a force that will be substantially aligned with another diagonal of the x-y plane of the Cartesian coordinate system relative to the movement in Fig. 12.

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In fig. 14 shows a fourth vibration mode in which the linear vibrations are oriented at an angle relative to the horizontal, in accordance with one embodiment of the invention. The control system may set the initial angles of the respective rotations of the first shaft and the second shaft to be π/2, providing a relative angular displacement of approximately π/2, as shown in FIG. 14. In this example, the first mass element may be advanced by, for example, π/2, while the second mass element may be advanced by π/2. Thus, the first mass element can be substantially aligned with the second mass element at angles π/2 and 3π/2, as shown in the graphs corresponding to t ₀ and t ₄ in FIG. 14 (set t ₁ is equal to to in Fig. 14). Thus, the oscillations of the resulting force f(t) can be oriented substantially perpendicular to the horizontal (ie, aligned with the y direction). Thus, the movement is a vertical vibration (vertical oscillation) up and down. In this vibration mode, the screen frame or deck assembly can vibrate with a linear oscillatory motion that is substantially perpendicular to the ground.

The control systems disclosed herein may provide changes in the angles of the respective rotations of the collinear shafts during operation of the eccentric vibrating device. In this case, the plane of oscillatory motion can change during operation of the eccentric vibration device. In another operating mode, the oscillatory motion can be changed from linear oscillation to circular or elliptical oscillation. For example, the control system may cause the collinear shafts of the eccentric vibrating device to rotate in the same direction and at the same angular velocity to produce a substantially circular mechanical disturbance. For example, while the system produces linear motion with counter-rotating masses, the control system may reverse the direction of rotation of a first shaft (or, in some cases, a second shaft) of substantially collinear shafts to be reversed. With such reversal, the control system can also ensure that the first shaft and the second shaft are angularly aligned, i.e. neither the first shaft nor the second shaft is ahead or behind in angle from the other shaft. Thus, the substantially collinear shafts are configured to rotate in one direction at one angular frequency ω, without angular displacement between the shafts, resulting in substantially circular motion of the eccentric vibrating device. In additional embodiments, elliptical, as well as circular, oscillations can be implemented with masses rotating in the same direction, but with relative displacements.

In some embodiments, adjustment of a substantially circular or elliptical motion may be implemented in response to a button press on a human-machine interface (HMI) or to the selection of a selectable visual element displayed on a display device (which is may be part of the HMI in some embodiments). Controlling the initial angles and subsequent relative angular displacements during operation of the eccentric vibrating device may allow the orientation of the vibrating vibrations to be adjusted without the need to dismantle and reassemble the eccentric vibrating device, as would be the case with a conventional vibrating device. Thus, the disclosed systems and methods provide increased efficiency and/or versatility of the vibration system.

In additional embodiments, the eccentric vibrating device can generate a substantially circular mechanical disturbance without relying on a control system to adjust the circular motion and energy delivery. In such embodiments, the direction of rotation of the shaft of the eccentric vibrating device can be reversed by changing the polarity of two of the three input power terminals of the three-phase induction motor that produces rotation of the shaft. For example, a three-phase system may include (i) a first power supply line L1, a second power supply line L2, and a third power supply line L3, and (ii) a first motor terminal T1, a second motor terminal T2, and a third motor terminal T3. Clockwise rotation of the shaft can be achieved by connecting L1 to T1, L2 to T2 and L3 to T3. Alternatively, counterclockwise rotation of the shaft can be achieved by reconnecting L1 to T3, maintaining the connection of L2 to T2, and reconnecting L3 to T1.

The control system may provide control of the speed of the motor assembly and/or the direction of the vibration force in real time or near real time. The speed at which solids move from the feed end to the discharge end of the separation system can in turn be controlled by controlling the parameters of an eccentric vibrating device that is coupled to the separation system. In addition to shaking systems, the eccentric vibrating device can be coupled with feeders such as vibrating feeders, where the feed rate of the material can be precisely controlled. For example, in high-volume applications, the conveying speed may be increased to move solids or other types of solids away from the screening surface and/or to open the screening surface area to incoming material flow. In another example, the conveying speed may be reduced to increase the dryness of the screened material by increasing the residence time of the material on the screening surface.

In fig. 15 illustrates a block diagram of an exemplary computer system 1500, in which the disclosed embodiments or portions thereof may be implemented as machine-readable code (i.e., machine-readable computer program instructions) that is executed by one or more processors and causes one or more processors to perform operations of the disclosed embodiments according to one embodiment.

The disclosed systems may include components implemented in a computer system 1500 using hardware, software, firmware, tangible computer-readable (i.e., machine-readable) media on which computer program instructions are stored, or combinations thereof, and may be implemented in one or more computer systems or other processing systems.

If programmable logic is used, the logic may be executed on a commercially available processing platform or on a special purpose device. One of ordinary skill in the art will appreciate that embodiments of the disclosed subject matter may be practiced with a variety of computer system configurations, including multi-core multiprocessor systems, minicomputers, mainframes, computers coupled or grouped with distributed functions, and all-pervasive or miniature computers. computers that can be built into almost any device.

The various disclosed embodiments are described in relation to such an exemplary computer system 1500. After reading this description, those skilled in the art will be aware of how to implement the disclosed embodiments using other computer systems and/or computer architectures. Although operations may be described as a sequential process, some of the operations may actually be performed in parallel, simultaneously and/or in a distributed environment, with program code stored locally or remotely for access by single or multiprocessor machines. Moreover, in some embodiments, the order of operations may be changed without departing from the spirit of the disclosed subject matter.

As will be appreciated by those skilled in the art, a computing device for implementing the disclosed embodiments has at least one processor, such as processor 1502, which processor may be a single processor, a group of processors, a processor in a multi-core/multi-processor system, such a system operating alone, or in a cluster of computing devices running in a cluster or server farm.

The processor 1502 may be connected to a communications infrastructure 1504, such as a bus, a message queue, a network, or a multi-core messaging circuit.

The computer system 1500 may also include a primary memory 1506, such as random access memory (RAM), and may also include a secondary memory 1508. The secondary memory 1508 may include, for example, a hard disk drive 1510, removable drive 1512. Removable drive 1512 may include a floppy disk drive, a magnetic tape drive, an optical disk drive, flash memory, and the like. Removable storage device 1512 may be configured to read and/or write data to removable storage device 1514 in a known manner. Removable storage device 1514 may include a floppy disk, magnetic tape, optical disk, etc., which is written to and read from removable storage device 1512. As will be appreciated by those skilled in the art, removable storage device 1514 may include includes a machine-readable medium containing computer software (i.e., computer program instructions) and/or data stored thereon.

In alternative implementations, the secondary memory 1508 may include other similar devices that enable loading of computer programs or other instructions into the computer system 1500. Such devices may include, for example, a removable storage device 1516 and an interface 1518. Examples of such devices may include a software cartridge and cartridge interface (such as those found in video game devices), a removable memory chip (such as an EPROM or PROM) and associated connector, and other removable storage devices 1516 and interfaces 1518 that enable transfer of software and data from removable storage device 1516 to computer system 1500.

Computer system 1500 may also include a communications interface 1520. Communication interface 1520 allows for the transfer of software and data between computer system 1500 and external devices. Communication interfaces 1520 may include a modem, a network interface (eg, an Ethernet card), a communications port, a PCMCIA slot and card, or the like. Software and data transmitted through communication interface 1520 may be in the form of signals 1522, which may be electronic, electromagnetic, optical, or other signals that can be received by communication interface 1520. These signals may be provided to communication interface 1520 via communication channel 1524.

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In this document, the terms computer program storage medium and computer-usable storage medium are generally used to refer to storage media such as removable storage device 1514, removable storage device 1516, and a hard disk installed on the hard disk drive 1510. The storage medium for computer programs and the storage medium used by the computer may also refer to memory, such as main memory 1506 and secondary memory 1508, which may be semiconductor memory (eg, DRAMS, etc.). The computer system 1500 may further include a display unit 1526 that interacts with the communications infrastructure 1504 via a display interface 1528. The computer system 1500 may further include a user input device 1530 that interacts with the communications infrastructure 1504 via an input interface 1532. User input device 1530 may include a mouse, trackball, touch screen, or the like.

Computer programs (also referred to as computer control logic or computer program instructions) are stored in main memory 1506 and/or secondary memory 1508. Computer programs may also be received via communications interface 1520. Such computer programs, when executed, enable the computer system to implement the 1500 embodiments disclosed herein. In particular, the computer programs, when executed, cause the processor 1502 to implement processes of the disclosed embodiments, such as various steps of the disclosed methods, as described in more detail above. Accordingly, such computer programs represent controllers of the computer system 1500. When an embodiment is implemented using software, the software may be stored in a computer program product and loaded into the computer system 1500 using removable storage 1512, interface 1518, and hard disk drive 1510, or 1520 communication interface. The computer program product may include any suitable non-volatile computer-readable (ie, computer-readable) storage device on which computer program instructions are stored.

Embodiments may be implemented using software, hardware, and/or operating system implementations other than those disclosed herein. Any software, hardware, or operating system implementations suitable to perform the functions described in this document may be used. Embodiments apply to both a client and a server, or a combination of both.

The disclosure is exemplary embodiments and, therefore, is not intended to limit in any way the scope of the embodiments of the present invention and the appended claims. The above embodiments have been disclosed using functional building blocks illustrating the implementation of given functions and their relationships. The boundaries of these functional building blocks have been defined here arbitrarily for ease of description. Alternative boundaries may be defined to the extent that the specified functions and their relationships are adequately fulfilled.

The breadth and scope of the embodiments of the invention should not be limited by any of the exemplary embodiments described above, but should be defined only in accordance with the following claims and their equivalents.

Conventional language, including terms such as may/may, can, and others expressing possibility, unless specifically stated otherwise or otherwise understood in the context used, is generally intended to indicate what given implementations may include, then as other implementations do not include these features, elements and/or operations. Thus, such conventional language is not generally intended to indicate that features, elements, and/or operations are necessarily required by one or more implementations, or that one or more implementations necessarily include logic for making a decision, with or without user input or prompting. them, whether these features, elements and/or operations are included or must be performed in any particular implementation.

The description and accompanying drawings disclose examples of systems and systems that can provide tunable, substantially eccentric mechanical disturbances and/or substantially linear circular mechanical disturbances. Of course, it is not possible to describe every conceivable combination of elements and/or methods for purposes of disclosing various aspects of the invention, but it will be recognized that many additional combinations and permutations of the disclosed elements are possible. Accordingly, various modifications may be made to the invention without departing from its scope or spirit. Additionally or alternatively, other embodiments of the invention and practice thereof may be apparent from consideration of the description and accompanying drawings disclosed herein. It is intended that the examples set forth in the specification and accompanying drawings are to be considered in all respects as illustrative and not restrictive. Although specific terms are used herein, they are used only in a general and descriptive sense and not for limitation purposes.

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Claims (23)

CLAIM 1. An eccentric vibration device containing: a first shaft having a first end and a second end; a second shaft having a third end and a fourth end, the first and second shafts having a common axis and the first end and the third end being adjacent to each other; a first mass eccentrically mounted on the first shaft and rotatable about the first shaft; a second mass eccentrically mounted on the second shaft and rotatable about the second shaft; a third mass eccentrically mounted on the first shaft at a first angle relative to the first mass and rotatable about the first shaft; a fourth mass eccentrically mounted on the second shaft at a second angle relative to the second mass and rotatable about the second shaft; wherein the third and fourth masses are spatially separated from, respectively, the first and second masses and are configured to act as partially counterbalancing masses to the first and second masses, respectively; a drive system configured to selectively generate elliptical, circular and linear oscillatory motion such that: in the first selectable setting, the drive system imparts rotational motion to the first and second shafts to cause the first and second masses to rotate in a common direction, thereby creating an elliptical or circular oscillatory motion of the device; and in a second selectable setting, the drive system imparts rotational motion to the first and second shafts to cause the first and second masses to rotate in opposite directions, thereby producing a linear oscillatory motion of the device. 2. The apparatus of claim 1, wherein the drive system further comprises: a first motor assembly attached to the first shaft and configured to impart rotational motion to the first shaft; and a second motor assembly attached to the second shaft and configured to impart rotational motion to the second shaft. 3. The device of claim 1, further comprising a control system configured to control the rotational speeds, directions and relative angular positions of the first and second masses, thereby controlling the linear, elliptical and circular oscillatory motion of the device. 4. The device according to claim 3, wherein the control system is further configured to control the angle of linear motion by controlling the relative angular positions of the first and second masses. 5. The device according to claim 4, wherein the control system is further configured to change the angle of linear motion from the first angle to the second angle during operation of the device. 6. The device according to claim 3, wherein the control system is further configured to transition from linear motion to elliptical or circular motion during operation of the device. 7. The apparatus of claim 3, wherein the control system is further configured to control the first and second shafts so that they rotate in opposite directions at the same frequency to produce linear oscillations. 8. The apparatus of claim 3, wherein the control system is further configured to control the first and second shafts so that they rotate in the same direction at the same frequency to produce circular vibrations. 9. Device according to claim 1, in which: a first mass is mounted on or adjacent to a first end of the first shaft, and a third mass is mounted on or adjacent to a second end of the first shaft; and a second mass is mounted on or adjacent to a third end of the second shaft, and a fourth mass is mounted on or adjacent to a fourth end of the second shaft. 10. The device according to claim 1, wherein the first and third masses are substantially parallel; and the second and fourth masses are substantially parallel. 11. The apparatus of claim 1, wherein the first and second angles are each approximately 180 degrees. 12. The device according to claim 3, further comprising a measuring device configured to measure the angular position and/or speed of the first and second masses. 13. The apparatus of claim 12, wherein the control system is further configured to control one or more of the rotational speeds, directions, and relative angular positions of the first and second masses based on measurements made by the measuring device. 14. The device according to claim 3, in which the control system is configured to control the wheel - 16 043305 battal movement so that it is a linear movement along a line oriented at an angle ranging from approximately 0 radians to approximately π radians with respect to a fixed direction. 15. A processor-implemented method for controlling an eccentric vibration device according to claim 1, including a first shaft having a first end and a second end; a second shaft having a third end and a fourth end, the first and second shafts having a common axis and the first end and the third end being adjacent to each other; a first mass eccentrically mounted on the first shaft and rotatable about the first shaft; a second mass eccentrically mounted on the second shaft and rotatable about the second shaft; a third mass eccentrically mounted on the first shaft at a first angle relative to the first mass and rotatable about the first shaft; a fourth mass eccentrically mounted on the second shaft at a second angle relative to the second mass and rotatable about the second shaft; wherein the third and fourth masses are spatially separated from, respectively, the first and second masses and are configured to act as partially counterbalancing masses to the first and second masses, respectively; and a drive system configured to selectively generate elliptical, circular and linear oscillatory motion such that: in a first selectable setting, the drive system imparts a rotational motion to the first and second shafts to cause the first and second masses to rotate in a common direction, thereby creating an elliptical or circular oscillatory motion of the device; and in a second selectable setting, the drive system imparts rotational motion to the first and second shafts to cause the first and second masses to rotate in opposite directions, thereby creating a linear oscillatory motion of the device, the method comprising: controlling, by the processor circuit, the drive system to select the first selectable setting or the second selectable setting. 16. The method of claim 15, further comprising controlling, through the processor circuit, the drive system to control the angle of linear motion by controlling the relative angular positions of the first and second masses. 17. The method of claim 16, further comprising controlling, by the processor circuit, the drive system to change the angle of linear motion from the first angle to the second angle during operation of the device. 18. The method of claim 15, further comprising controlling, through the processor circuit, the drive system to transition from linear motion to elliptical or circular motion during operation of the device. 19. The method of claim 15, further comprising controlling, through the processor circuit, the drive system to cause the first and second shafts to rotate in opposite directions at a common frequency to produce linear oscillations. 20. The method of claim 15, further comprising controlling, through the processor circuit, the drive system to cause the first and second shafts to rotate in the same direction at the same frequency to produce circular vibrations. 21. The method according to claim 15, additionally containing: monitoring, by means of a processor circuit, a measuring device for measuring the angular position and/or velocity of the first and second masses; and based on the measurements made by the measuring device, controlling, through the processor circuit, the drive system to control one or more of the rotational speeds, directions, and relative angular positions of the first and second masses. 22. The method of claim 15, further comprising controlling, by the processor circuitry, the drive system to control the oscillatory motion so that it is linear motion along a line oriented at an angle ranging from about 0 radians to about π radians with respect to a fixed direction. 23. A method for controlling an eccentric vibrator, comprising: a first shaft having a first end and a second end; a second shaft having a third end and a fourth end, the first and second shafts having a common axis and the first end and the third end being adjacent to each other; a first mass eccentrically mounted on the first shaft and rotatable about the first shaft; a second mass eccentrically mounted on the second shaft and rotatable about the second shaft; a third mass eccentrically mounted on the first shaft at a first angle relative to the first mass and rotatable about the first shaft; a fourth mass eccentrically mounted on the second shaft at a second angle relative to the second mass and rotatable about the second shaft; wherein the third and fourth masses are spatially separated from, respectively, the first and second masses and are configured to act as partially counterbalancing masses to the first and second masses, respectively; and a drive system configured to selectively generate elliptical, circular and linear -