EA008992B1 - System and method for pulverizing and extracting moisture - Google Patents

Abstract

The invention is proposed when a Venturi receives incoming material through an inlet tube and subjects the material to pulverization. The material, as it undergoes pulverization, is further subject to moisture extraction and drying. An airflow generator, coupled to the Venturi, generates a high speed airflow to pull the material through the Venturi and into an inlet aperture in the airflow generator. The airflow generator directs the received pulverized material to an outlet where the material may be subsequently separated from the air. An acoustic emission sensor receives the resonant frequencies generated by material passing through the airflow generator. The resonant frequencies reflect a material flow rate that is adjusted to avoid an overload situation. An automatic system coupled to an axle rotating the airflow generator to provide balance, improve efficiency, and eliminate cavitation.

Description

The scope of the invention

The present invention relates to materials processing technologies for spraying (spraying) and extracting (removing) moisture from them.

BACKGROUND OF THE INVENTION

In various industries, labor-intensive work is required to grind materials into fine particles and even into fine powder. For example, in power plants, it is necessary to grind pieces of coal into powder before burning it in the furnaces to generate electricity. In most applications it is also necessary to grind limestone, chalk and many other minerals into powder. Crushing solid materials and grinding them into powder is a laborious mechanical process. Usually, ball mills, hammer crushers and other mechanical devices are used for this, which crush pieces of material by impact. These systems, although widely used, are inefficient and provide a relatively low processing speed.

In various industries, it is additionally required to carry out the extraction of moisture from a wide variety of materials. When processing food, wastewater, harvesting, mining and many other industries, moisture extraction is required. In some industries, materials have to be sent to waste, since moisture extraction cannot be carried out efficiently. However, these materials, if it were possible to dry them effectively, could bring commercial benefits. In other sectors of the national economy, such as waste management, water removal (dehydration) is a subject of particular concern, and there is an urgent need to develop improved dehydration processes. Although various materials dewatering technologies are known, there is an increasing need to increase the efficiency of moisture extraction.

Thus, progress in this technical field is associated with the creation of more efficient processes for spraying materials and extracting moisture from materials. It is such technologies that are disclosed in the present invention.

Brief Description of the Drawings

In FIG. 1 shows a side view of one embodiment of a spray system in accordance with the present invention;

in FIG. 2 is a top view of the atomization system shown in FIG. one;

in FIG. 3 is a sectional side view of a venturi of a spray system when a venturi receives material;

in FIG. 4 is a side view where an alternative embodiment of the atomization system in accordance with the present invention can be seen;

in FIG. 5 is a plan view of the atomization system shown in FIG. 4;

in FIG. 6 is a perspective view where you can see the casing of the air generator and exhaust restrictors;

in FIG. 7 is a cross section of a first embodiment of an air generator housing;

in FIG. 8 is a cross section of a venturi and a neck calibrator;

in FIG. 9 is a block diagram where components of an alternative embodiment of a spray system can be seen;

in FIG. 10 is a block diagram where an alternative embodiment of a spray system in accordance with the present invention can be seen;

in FIG. 11 is a perspective view of a first embodiment of an airflow generator suitable for use with a system (in a system) in accordance with the present invention;

in FIG. 12 is a cross-sectional view of a portion of the airflow generator shown in FIG. eleven;

in FIG. 13 is a plan view of the inner portion of the airflow generator shown in FIG. eleven;

in FIG. 14A is a plan view of the trailing edge of the blade of the airflow generator shown in FIG. eleven;

in FIG. 14B is a plan view of an alternative trailing edge of a blade of the airflow generator shown in FIG. eleven.

in FIG. 15A is a perspective view of a portion of the airflow generator shown in FIG. eleven;

in FIG. 15B is a perspective view of a portion of an alternative embodiment of the airflow generator shown in FIG. eleven;

in FIG. 16 is a side view of a blade of the airflow generator shown in FIG. eleven;

in FIG. 17 is a sectional view of the blade shown in FIG. sixteen;

in FIG. 18 is a perspective view of a portion of the airflow generator shown in FIG. eleven;

in FIG. 19 is a side view of an alternative embodiment of a spray system in accordance with the present invention;

in FIG. 20 is a side view where an alternative embodiment of the atomization system in accordance with the present invention can be seen;

in FIG. 21 is a side view where you can see an alternative version of the spray system in accordance

- 1 008992 in accordance with the present invention;

in FIG. 22 is a cross section of an alternative embodiment of an air generator housing;

in FIG. 23 is a perspective view of a variant of a casing, an axis, and a balancer;

in FIG. 24A is a diagram for explaining the position of compensating weights with respect to an unbalance point;

in FIG. 24B is another diagram explaining the position of the compensating weights relative to the imbalance point;

in FIG. 25A is another diagram explaining the position of the compensating weights relative to the imbalance point;

in FIG. 25B is another diagram explaining the position of compensating weights relative to an imbalance point;

in FIG. 26A is a perspective view of a balancer relative to a rotating mass;

in FIG. 26B is another perspective view of a balancer relative to a rotating mass;

in FIG. 27 is a cross section of a first embodiment of an internal balancer located inside the axis;

in FIG. 28 is a cross-sectional view of a first embodiment of compensating weights within the internal balancer shown in FIG. 27;

in FIG. 29 is a perspective view of a first embodiment of an annular balancer;

in FIG. 30 is a cross-sectional view of a first embodiment of compensating weights within the annular balancer shown in FIG. 29.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS

Turning now to the consideration of FIG. 1 and 2, which show a system 10 of pulverization (spraying material) and extraction (removal) of moisture, which contains the inlet pipe 12. The inlet pipe 12 has a first end 14 that has a connection with the free space, and the opposite, the second end 16, which connected to the venturi 18. Although the description is made with reference to the pipes, experts will easily understand that all such elements can have a round, rectangular, hexagonal and other cross-sectional shape. As a rule, circular cross sections are desirable in order to facilitate manufacture and operation, however, the present invention is not limited to this type of implementation.

The inlet pipe 12 creates a certain distance to the venturi 18, at which the material can be accelerated to the desired speed. A filter (not shown) can be installed so as to close the first end 14 and to prevent foreign particles from entering the system 10. The inlet pipe 12 further comprises an elongated hole 20 on its upper part, allowing communication with the open lower end of the hopper 22. The hopper 22 is open at its upper end 24 for receiving materials. Alternatively, the systems 10 do not have a hopper 10 and the material is simply introduced into the elongated hole 20 using various known methods.

The venturi 18 contains a converging portion 26 connected to the inlet pipe 12. The converging portion 26 has a gradually decreasing diameter, from the diameter of the inlet pipe 12 to a smaller diameter than the diameter of the inlet pipe 12. The venturi 18 further comprises a neck 28 with a constant diameter that is smaller the diameter of the inlet pipe 12. The venturi 18 also further comprises a diverging portion 30, which is connected to the neck 28 and has a gradually increasing diameter in the direction of air flow. The diverging section 30 may be connected to the neck 28 by co-molding, threaded connection, or other known means of connection. The converging portion 26 may be longer than the diverging portion 30, as shown in FIG. 1 and 2.

The venturi 18 is in communication with an air flow generator 32 that generates air flow from the first end 14 through the inlet pipe 12, through the venturi 18 and into the air flow generator 32. The speed of the created airflow can range from 350 mph to supersonic. The air velocity will be higher in the venturi 18 than in the inlet 12. The air flow generator 32 may be in the form of a fan, a pump, a hybrid turbine and fan, a pneumatic suction system or other suitable device for creating an air flow at high speed.

The airflow generator 32 is driven by an engine 34. The drive motor 34 is connected to the axle 33 by known means. Axis 33 engages with airflow generator 32 to create its rotation. The power of the drive motor 34 can vary within wide limits, for example, from 15 hp up to 1000 hp, and depends on the parameters of the processed material, the flow rate of the material and the size of the air flow generator. Thus, this range is for illustrative purposes only and system 10 may be more powerful or less powerful. The most powerful system 10 can be used to process municipal waste, while the less powerful system 10 can be used to treat wastewater aboard an ocean liner.

The airflow generator 32 comprises a plurality of radially extending vanes that rotate to create airflow at high speed. 32 air generator

- 2 008992 flow is located inside the casing 35, which has an outlet 36 of the casing through which the incoming air. The casing 35 is connected to the venturi 18 and has an inlet (not shown) of the casing, which provides communication between the venturi 18 and the inner part of the casing 35. Between the blades there are radially extending channels through which air passes to the outlet 36 of the casing at its perimeter, allowing leaving pulverized material. One embodiment of an airflow generator 32 suitable for use in accordance with the present invention is discussed below in more detail with reference to FIG. 11-18.

Turning now to the consideration of FIG. 3, which is a cross-sectional side view of a venturi, explaining the operation of the venturi 18 during a spray operation. In working condition, the material 38 is introduced into the inlet pipe 12 by any means of transportation. Material 38 may be solid or semi-solid. The airflow generator 32 generates airflow (at a speed) in the range of 350 mph to a supersonic speed that flows through the inlet pipe 12 and through the venturi 18. In the venturi 18, the air flow increases substantially. Material 38 is driven through a venturi 18 due to a high air flow rate. Material 38 has a smaller diameter than the inner diameter of the inlet pipe 12, and there is a gap between the inner surface of the inlet pipe 12 and the material 38.

When the material 38 enters the converging portion 26, the gap becomes narrower and ultimately the material 38 causes a significant reduction in the area of the converging portion 26 through which air can flow. The shock wave 40 recompression (re-compression) follows the material, and the nasal shock wave 42 arises in front of the material 38. At the point where the converging portion 26 merges with the neck 28, a standing shock wave 44 occurs. These shock waves 40, 42, 44 act on the material 38 and lead to its atomization and to the extraction of moisture from the material. The sprayed material 45 continues through the venturi 18 and exits into the airflow generator 32.

Reducing the particle size of the material depends on the properties of the spray material and the size of the system 10. By increasing the air velocity, it is possible to enhance the atomization and reduction of particle sizes for some materials. Thus, the system 10 allows the user to select the desired particle size due to changes in air velocity.

System 10 is of particular use in the spraying of solid materials into finely dispersed dust. The system 10 is additionally used in the extraction of moisture from semi-solid materials such as municipal waste, paper pulp, animal waste by-products, fruit pulp, etc. System 10 can be used in a wide range of commercial and industrial applications.

Turning now to the consideration of FIG. 4 and 5, an alternate embodiment of a system 100 according to the present invention for extracting moisture from various materials is shown. System 100 may have a mixer 102 for mixing materials in a pre-treatment step. The raw material may contain polymers that tend to form granules of the material. The oversized granules formed by polymers interfere with the grinding of the material into powder form.

The presence of polymers is typical of municipal waste, since polymers are specifically introduced during wastewater treatment to combine waste particles. Waste treatment is carried out on a tape press, as a result of which mainly semi-solid material is obtained. In some processes, the material may be approximately 15-20% solid, and the remainder is moisture.

In the pretreatment step, the drying agent is mixed with the untreated material to break down the polymers and granules of the material. It should be borne in mind that non-polymerized products can be processed without such mixing. The raw material is introduced into a mixer 102, in which the material is mixed with a predetermined amount of a drying agent. The drying agent may be selected from the group consisting of attapulgite, coal, lime, and other similar agents. The drying agent may also be a pulverized and dried starting material. The mixer 102 mixes the material with a drying agent to obtain an appropriate moisture content and an appropriate granule size.

The resulting material is transferred from mixer 102 to hopper 22 by any suitable conveying means 104, such as a conveyor belt, screw conveyor, extruder, or other motorized device. In the shown embodiment, the conveyance means 104 is a slope path (inclined trough) allowing gravity to feed raw material into the hopper 22. The conveyance means 104 is located below the flow regulator 106 installed on the lower portion of the mixer 102.

Alternatively, the hopper 22 may be omitted and the material may flow directly into the elongated hole 20 of the inlet pipe 12. The hopper 22 is only one of the possible devices that can be used to convey material to the inlet pipe 12. Suitable transport means may be used. other types, as well as manual input.

One or more sensors 108 can monitor the flow rate of material passing

- 3 008992 from mixer 102 to intake pipe 12. Sensor 108 is in communication with central processing unit 110 to control flow rate. The sensor 108 may be located in the immediate vicinity of the transport means 104, in the immediate vicinity of the hopper 22, inside the hopper 22, or even between the hopper 22 and the elongated hole 20, in order to control the flow rate of the material. The central processing unit 110 is in communication with a flow controller 106 to increase or decrease the flow rate as necessary. Alternative methods for controlling and adjusting the flow rate may also be used, including visual inspection and manual adjustment of the flow controller 106.

The hopper 22 receives the material and feeds the material into the elongated opening 20 of the inlet pipe 12. The elongated opening 20 may have a width of 4 or less and a length of 5 to maintain an acceptable feed rate for some applications. The length of the inlet pipe 12 from the oblong hole 20 to the venturi 18 can be from 24 (610 mm) to 72 (1830 mm) or more, and depends on the properties of the material being processed and the flow rate. Those skilled in the art will easily understand that the dimensions given are for illustrative purposes only, since system 10 is scalable.

The air flow pushes the material from the inlet pipe 12 through the venturi 18. In the shown embodiment, the first end 14 is made in the form of a flange converging from a diameter larger than the diameter of the inlet pipe 12 to the diameter of the inlet pipe. The flanged first end 14 increases the volume of air flow entering the inlet pipe 12.

Some versions of the system have a venturi neck diameter 18 in the range of approximately 1.5 (38 mm) to 6 (152 mm). The neck diameter is selected based on the volume of the flowing material, and it may exceed the above range. The neck diameter of the venturi 18 and the diameter of the inlet pipe 12 are directly proportional. In one embodiment, to ensure normal operation, the neck diameter is 2.75 and the intake pipe diameter is 5.5 (139.33 mm). Alternatively, to ensure normal operation, the neck diameter is 2.25 (57 mm) and the inlet pipe diameter is 4.50 (114 mm). Thus, a ratio of 2 to 1 ensures that the incoming material is captured by the incoming air stream.

In the shown embodiment, the diverging section 30 is connected to the casing 35 and has a direct connection with it. The final diameter of the diverging section 30 is not necessarily equal to the diameter of the inlet pipe 12. Alternatively, the diverging section 30 may be connected to an intermediate component, such as a cylinder or pipe, previously connected to the casing 35.

One or more valves 111 may be provided in the diverging portion 30 to supply additional air to the interior of the housing 35 and to the air flow generator 32. The additional air volume improves the performance of the airflow generator 32. In one embodiment, the two valves 111 are located on the divergent portion 30. The system 100 may operate with partially or fully open valves 111. If the material begins to clog the venturi 18, the valves 111 may be closed. This leads to the fact that a larger volume of air flow passes through the venturi 18, which creates additional force and pushes the material through the venturi 18 and the generator 32 air flow. Gate valves 111 are adjustable and, as shown in FIG. 4, are in electrical communication with a central processing unit 110 for control. Despite the fact that the manual control of the valves 111 is not beyond the scope of the present invention, computerization greatly simplifies the control process.

The venturi 18 creates a collision point between shock waves having higher velocities and shock waves having lower velocities. Shock waves provide atomization and extraction of moisture inside the venturi 18. In working condition, there are no visible traces of moisture on the inner surface of the venturi 18 or in the outlet 36 of the casing. The amount of moisture removed is sufficient, although a residual amount of moisture may remain. The atomization operation further reduces the particle size of the materials. In the experiment, it was found that some materials having a diameter of 2 (50 mm) at the inlet of the venturi 18 were crushed into a fine powder with a diameter of 20 μm due to a single atomization operation. The reduction in size depends on the properties of the material being processed and the number of spraying operations. The separation of water from the material has various applications, such as dehydration of the material, and significantly reduces the number of pathogens.

The present invention may have particular application in the treatment of municipal waste. The pre-treatment operation using a drying agent makes it possible to obtain waste material that can easily be processed in system 100. It can be assumed that the process of atomization (and extraction of moisture) significantly reduces the number of pathogens (pathogens) in the waste material due to rupture of their wall cells. A second source of pathogen reduction is moisture extraction. Analytical data from the treated urban waste show that the method in accordance with the present invention allows the destruction of most common coliforms (cohogt), fecal coliforms, C5c11spsiaia (Escherichia coli), and other pathogens.

The present invention may also have particular use in the extraction of moisture from fruits and

- 4 008992 products of plant origin (vegetables). In one application, system 100 can be used to dehydrate fruits and vegetables, such as apples, oranges, carrots, nectarines, peaches, melons, tomatoes, and the like. The extracted moisture, which is relatively hygienic, can be condensed and reused to produce pure juice.

In another application, system 100 can be used to spray and extract water from certain agricultural products, such as banana stems, palm wood, sugarcane, rhubarb, etc. The chopped banana stems produce fiber separation and moisture removal. There is a commercial application related to the conversion of agricultural products from their natural state to a dehydrated state.

Material, moisture and air flow pass through the air flow generator 32 and exit through the outlet 36 of the casing. The outlet 36 of the casing is connected to an exhaust pipe 112, which feeds the material into the cyclone 114 to separate the material and air. The diameter of the exhaust pipe 112 lies in the range of approximately from 4 (100 mm) to 7 (177 mm). It may be necessary to increase this range for some materials, such as attapulgite or charcoal, when an 8 (203 mm) exhaust pipe 112 is suitable. The exhaust pipe 112 may have a cross section of various configurations, for example, rectangular, octagonal, etc., wherein pipe 112 may have various sizes.

The exhaust pipe 112 may have a length of approximately 12 to 16 feet. The diameter of the exhaust pipe 112 affects the degree of additional drying. A large amount of air is required for additional drying of materials. The faster the air moves in the exhaust pipe 112, the better it passes through the material and the better removes moisture remaining in the material. Air and steam enter cyclone 114, where air and steam are separated from the solid material.

The atomization operation generates heat, which contributes to the drying of the material. In addition to atomization, rotation of the airflow generator 32 generates heat. The dimensions between the casing 35 and the air flow generator 32 are selected so that friction generates heat during rotation. Heat exits through the outlet 36 of the casing and the exhaust pipe 112 and further dehydrates the material when the material passes into the cyclone 114. The generated heat may also be sufficient to partially sterilize the material in some applications.

The diameter of the outlet 36 of the casing can be increased or decreased to adjust the resistance and the amount of heat passing through the outlet 36 of the casing and the exhaust pipe 112. The diameter of the exhaust pipe 112 and the outlet 36 of the casing affects the removal of moisture from the pulverized material. Outlet diameter adjustment is further discussed below.

The degree of atomization and extraction of moisture increases with increasing air flow generated by the generator 32 of the air flow. If an increase or decrease in air flow is made, the diameter of the exhaust pipe 112 and the exhaust 36 of the casing may be suitably increased or decreased to provide the same dewatering of the material. Thus, the adjustment of the air flow and diameters is carried out in a coordinated manner with respect to each other in order to provide the desired dehydration.

Heavier materials with lower water content, such as rock, require less moisture extraction. For such materials, the diameters of the outlet 36 of the casing and the exhaust pipe 112 can be increased, since a lower degree of drying is required. Conversely, with wetter materials, the diameters of the outlet 36 of the casing and the exhaust pipe 112 can be reduced to increase the amount of air and heat to ensure proper dewatering of the material.

The angle of the exhaust pipe 112 relative to the longitudinal axis of the venturi 18 and the air flow generator 32 also affects the degree of dehydration. The angle of inclination of the exhaust pipe may be approximately 25 to 90 ° in order to enhance the extraction of moisture. Material moving upward is delayed by gravity more than air. This allows air to move faster than the material, which increases moisture removal. This angle can be adjusted to increase or decrease the effect on moisture extraction. The exhaust pipe 112 may be straight, as shown in FIG. 4 by a solid line, or curved, as indicated by a dotted line.

Cyclone 114 is a well-known device for separating particles from an air stream. The cyclone 114 typically comprises a settling chamber in the form of a vertical cylinder 116. The cyclone may be provided with a tangential inlet, axial outlet, peripheral unloading, or axial unloading. Air flow and particles enter cylinder 116 through inlet 118 and rotate in vortices as air flows downward in cylinder 116. The cone section 120 causes the diameter of the vortex to decrease until there is a reversal of gas direction and rotation to the outlet center 122 Particles are centrifuged in the direction of the inner wall and accumulate due to internal collision. The accumulated particles move downward in the gas boundary layer and enter the conical peak 124, from where they are discharged through the air lock 126 and enter the storage hopper 128.

In some applications, the system 100 may further comprise a condenser 130 for receiving air flow from the cyclone 114. The condenser 130 condenses the vapor from the air flow into a liquid, which then accumulates in the tank 132. The outlet 134 is connected to the condenser 130 and

- 5 008992 seals the air outlet. It should be borne in mind that the capacitor 130 is of particular use in food processing. Alternatively, alternative processing means, such as a carbon filter and the like, are used instead of capacitor 130. It is easy to understand that condensation or filtration depends on the type of material and the particular application. The outlet 134 may have a filter or may be connected to a filter (not shown) designed to filter the residue, particles, steam, etc. from the exhaust air.

Passing the material through the system 100 several times allows you to further dehydrate the material and further reduce the particle size. When processing municipal waste, it may take many cycles through the system 100 to achieve the desired degree of dehydration. According to the present invention, it is contemplated to use a plurality of sequentially installed systems 100 having a plurality of venturi 18 and providing a plurality of atomization operations. This allows you to achieve the desired results in a single transmission cycle through many sequentially installed systems 100. Alternatively, the material can be processed several times in the same system 100 until the desired particle size and degree of dehydration are achieved.

In one embodiment, an analysis is made of the resulting product exiting the system 100 to determine the size of the powder granules and / or the percentage of moisture. If the product exceeds the threshold value of the size and / or percentage of moisture, then it is sent to one or more cycles of additional processing until the product meets the desired parameters.

The present invention allows the homogenization of various materials. For this, various materials are co-introduced into the inlet pipe 12, passed through a venturi 18 for processing, and pulverized. The resulting product is mixed and homogenized, and is also dehydrated and has reduced particle sizes.

A particular application of the present invention provides for the homogenization of waste material with coal. After atomization and extraction of water, a combined and homogenized product containing waste and coal is used in a coal furnace at optimal combustion rates to produce steam at power plants. In this case, the waste is used more for energy production, and not for normal disposal.

Optionally, the material may be mixed in a mixer 102 prior to spraying, or may be mixed at an intermediate stage between spraying operations. Mixing the materials allows you to enhance homogenization with some materials.

Materials mixed in the pretreatment step can be passed through a plurality of atomization steps to provide the desired homogenization. The first material may be passed through a plurality of atomization steps and then homogenized with the second material. Between the atomization steps, the second material may be mixed with the material processed in the pretreatment step. The first and second materials are then passed through one or more atomization stages to obtain a homogenized, finished product.

As an additional example, you can specify that the first material can be passed through 3 stages of spraying. After the third atomization step, a second material can be introduced and the materials can be mixed together in mixer 102. Prior to mixing, the second material can be passed through a venturi 18 to atomize and desirably reduce particle size. The first and second materials can then be jointly passed through one or more additional atomization steps to obtain the desired moisture content, the desired particle size, and homogenization for industrial use.

Turning now to the consideration of FIG. 6, which is a perspective view of a casing 200 that includes a casing outlet 202. The casing 200 comprises the operating components of the airflow generator 32. The casing 200 is shown with a break so that you can see the generator 32 of the air flow inside it. In order to create a variation of the effluent, a restrictor 204 can be introduced into the outlet 202 of the casing. Limiter 204 increases resistance to air flow and also increases temperature. The degree of resistance and air flow rate are selected depending on the material being processed.

The limiter 204 includes a neck (neck) 206, installed inside the outlet 202 of the casing, and an aperture (window, hole) 208 of the limiter. The limiter aperture 208 has a cross section smaller than that of the casing outlet 202. The stop aperture 208 may be rectangular, circular, or may have another suitable shape. The neck 206 provides a converging flow from the cross section of the outlet 202 to the final cross section of the stop aperture 208. A number of stoppers 204 with different aperture sizes can be used to vary the output stream and thereby tune the system 100 to work with a particular material.

Turning now to the consideration of FIG. 7, which shows a cross-section of an airflow generator 32 inside a casing 200. An airflow generator 32 does not have to be axially mounted inside the casing 200. In one embodiment, the airflow generator 32

- 6 008992 ka contains a deflection plate 250, which has a cutting edge 252 in the immediate vicinity of the air flow generator 32. The cutting edge 252 of the deflection plate 250 directs the pulverized material into the outlet 202 of the casing. The deflecting plate 250 is connected to the inside of the casing 200 and can be connected to the inside of the outlet 202 of the casing.

The deflecting plate 250 prevents additional rotation of the pulverized material inside the casing 200. By itself, the deflecting plate 250 serves as the first means of separating the pulverized material from the air, which continues to rotate inside the casing 200. Subsequent separation of the pulverized material from the air occurs in cyclone 14. If the pulverized the material continues to rotate inside the casing 200, then the pulverized material can accumulate and ultimately clog the generator 32 in air flow. The cutting edge 252 changes the amount of air flow passing through the casing 200.

The separation distance (gap) of the cutting edge 252 of the deflector plate 250 from the air flow generator 32 may be in the range of approximately 20 thousandths of an inch to 100 thousandths of an inch. The position of the deflection plate 250 can also be adjusted to increase or decrease the separation distance from the air flow generator 32. Adjustment may be required depending on the properties of the materials being processed or to change the volume of the air flow. The adjustment can be controlled by a central processor 110, which is in communication with an electromechanical or pneumatic device to move the deflector plate 250. The cutting edge 252 has an inclination that matches the shape of the airflow generator 32.

Turning now to the consideration of FIG. 8, which shows a cross section of a venturi 18 together with a neck stop 300. The neck stop 300 is an interchangeable component that, when inserted, is installed inside the neck 28. The neck stop 300 changes the effective diameter of the neck 28 and increases the air speed. Changing the diameter of the neck is required depending on the material properties and the desired degree of dehydration and particle size reduction. Thus, despite the fact that the generator 32 of the air flow allows you to vary the air flow, it is additionally desirable to change the diameter of the neck of the venturi 18.

The neck 28 may have a protrusion 302, flush with which a sleeve (neck) 304 of the neck stop 300 is mounted. The castellated element 306 mates with the sleeve 304 and with the inner surface of the converging portion 26. The stop 300 of the neck 300 includes a sleeve 308 corresponding to the inner surface of the neck 28 and extending over most of the length of the neck of the venturi, which allows you to change the cross section of the neck of the venturi 18.

Turning now to the consideration of FIG. 9, an alternate embodiment of a system 400 is shown that includes two atomization stages 402, 404. At each passage of the material through the venturi 18, atomization, moisture extraction and particle size reduction occur. As already mentioned above, this process can be repeated using a single venturi 18 or a plurality of sequentially installed venturi 18 until sufficient water is removed and the desired particle size of the product is achieved. This process can be continued until almost 100% moisture extraction is achieved.

Despite the fact that in FIG. Figure 9 shows a system 400 with two spray stages; specialists will easily understand that a system can have 3, 4, 5, or more stages. The first atomization stage 402 is similar to that previously described with reference to FIG. 4 and 5. The first spraying stage 402 comprises a hopper 22, a mixer 102, transportation means 104, a flow regulator 106, a venturi 18, a casing 35 (with an air flow generator 32 installed inside), and an exhaust pipe 112. The system 400 may further have a regulator 405 of the flow in the exhaust pipe 112 to regulate the air flow therein.

As in previous embodiments, the exhaust pipe 112 is connected to a cyclone 114, designed to separate the processed product from the air. The system 400 may further comprise a second cyclone 406 receiving air from the outlet 122 of the first cyclone 114. The second cyclone 406 further separates the air from the residual particles and supplies the cleaned air to the condenser 130. The first tank 132 is connected to the second cyclone 406 and is used to receive condensed liquid from the condenser 130. The outlet 134 is intended for the exit of air from the condenser 130 and the second cyclone 406. The residue hopper 408 is designed to receive residual particles from the second cyclone 406.

Particles separated by the first cyclone 114 can be fed into the hopper 410 using any suitable means of transportation, including by gravity. Although not shown in FIG. 9, particles from both the first and second cyclones 114, 406 can enter the hopper 410. The particles accumulated in the hopper 410 are then fed to the second atomization stage 404. From the hopper 410, particles enter a second inlet pipe 412, which is connected to a second venturi 414, similar to the connection in the first atomization stage 402.

One or more valves 416 are provided in the second venturi 414, which are in electrical communication with the central processor 110. The valves 416 operate similarly to those previously described with reference to valves 111.

- 7 008992

The second venturi 414 is in communication with a second air flow generator (not shown) mounted in the casing 418. The second air flow generator creates a high velocity air flow through the venturi 414. The second casing 418 is connected to a second exhaust pipe 420 that supplies air and the processed material into the third cyclone 422. The second exhaust pipe 420 has an inclination angle of approximately 25 to 90 ° relative to the longitudinal axis of the second venturi 414. A second flow regulator 424 is provided inside the second exhaust pipe 420 and It is used to adjust the air flow in it. Like the first flow controller 404, the second flow controller 424 is in electrical communication with the central processing unit 110 for regulation.

The third cyclone 422 separates the particles from the air and delivers the resulting product to another transport means 425. The fourth cyclone 426 receives air from the third cyclone 422 and further purifies the air and removes residual particles. Residual particles from the fourth cyclone 426 accumulate in the remainder hopper 428. A fourth cyclone 426 supplies air to a second condenser 430, in which steam condenses into a liquid that enters a second tank 432. An outlet 434 is connected to a second condenser 430 and serves to release air.

System 400 further includes a heat generator 436 that delivers heat through inlet pipes 12, 412 and venturi tubes 18, 414 to facilitate drying of the materials. The addition of heat is not required for water extraction and is simply used in accordance with the present invention to increase the additional drying potential. The heat generator 436 may be in communication with the hoppers 22, 438 or with the inlet pipes 12, 412. The heat generator 436 may also be used in a similar manner in the embodiments shown in FIG. 1, 2, 4 and 5.

In FIG. 9 shows a heat generator 436 that is in communication with a first heat supply control valve 440 that controls the heat supply to the first hopper 22. The first heat supply control valve 440 is in electrical communication with a central processor 110 to control the heat supply. Alternatively, the heat control valve 440 may be manually controlled. The heat generator 436 further communicates with a second heat supply control valve 442, which controls the heat supply to the hopper 438. Heating of the material in the second pulverization stage 404 may be desirable, depending on the type of material or the particular application. If heating is desired, hopper 438 receives particles from the first cyclone 114. Otherwise, material may pass into hopper 410, as shown in FIG. nine.

System 400 may have one or more atomization steps for additional dehydration and particle size reduction. The transport means 425 allows the material to be fed back to the mixer 102 or to the hopper 22 to further pass the product through the pulverization stages 402, 404. The second and fourth cyclones 406, 426 provide additional air purification, however, for some applications, the additional costs associated with this are unjustified. In some applications, capacitors 130, 430 may be omitted or another type of processing device, such as a filter, may be used. Gate valves can also be used or eliminated throughout system 400, if justified and provided for in the design.

Turning now to the consideration of FIG. 10, an alternative embodiment of a moisture spraying and extraction system 450 is shown. The system 450 is similar to the system shown in FIG. 4 and 5, and further comprises a second cyclone 406, which is connected to the first cyclone 114, a residual hopper 408 for collecting particles from the second cyclone 406, a capacitor 130, which is connected to the second cyclone 406, a tank 132, which is connected to a capacitor 130, and an outlet 134 connected to the capacitor 130. The system 450 further comprises a divertor (deviation means, directions) 452 connected to the first cyclone 114.

A diverter 452 directs particles received from the first cyclone 114 to the first outlet 454 or to the second outlet 456. The first outlet 454 is connected to a collector 458, such as a bag, hopper, tank, and the like. The second outlet 456 is connected to a recirculation pipe 460 for re-introducing the pulverized material into the system 450. The recirculation pipe 460 at its opposite end is connected to the first end 14 (inlet pipe). Alternatively, the recirculation pipe 460 may direct the sprayable material to the hopper 22 or directly to the elongated hole 20.

During operation of the system, the material is sprayed when it (for the first time) passes through the system 450, after which the material is diverted again through the system 4502 to pass through the system 450 and undergoes a second spray operation. This can be repeated as desired until a finished product is obtained, which is then sent via diverter 452 to collection 458.

Turning now to the consideration of FIG. 11, an embodiment of an airflow generator 500 is shown suitable for use in accordance with the present invention. Various metals can be used to make an air flow generator, depending on the type of material being processed. For abrasive materials, harder alloy steel may be used. The material selected must strike a balance between strength and predicted wear. The manufacture of an air flow generator 500 using casting technology is

- 8 008992 preferred, and by welding create complex surfaces and areas of influence of heat. The cast airflow generator 500 may have a different thickness of the body material, which allows it to resist impact and accelerated wear when processing various materials. The selected thickness and the total weight obtained of the airflow generator 500 is directly proportional to the air volume and the flow rate of the material being processed.

An air flow generator 500 is installed inside the casing, as shown in FIG. 6. The casing 200 at least partially covers the airflow generator 500, and advantageously completely surrounds the airflow generator 500, so that only the outlet 36 of the casing remains open. The airflow generator 500 may be installed in the casing 200 with small gaps to create additional friction and heat. The presence of heat is desirable to facilitate additional drying of the materials passing through the air flow generator 500 and entering the exhaust pipe 112.

The airflow generator 500 comprises a front plate 502 with a centrally located inlet 504 for receiving incoming materials. The diameter of the inlet 504 depends on the particle size of the material being processed and the predicted air volume. The rear plate 506 is parallel to the front plate 502 and has a centrally located axial hole 508. As its name suggests, the axial hole 508 serves to introduce an axis or shaft into it to allow rotation. Other airflow generators 500 may be used in accordance with the present invention, including generators with a single back plate connected to the vanes, or generators with radially extending vanes only.

The rear plate 506 may further have bolt holes 509 that are concentrically arranged around the axial hole 508. Bolt holes 509 are used to receive corresponding bolts for securing the axle (not shown), each of which is connected to the axle. Axle fastening bolts are attached to the back plate 506 using nuts or other suitable fastening means.

Despite the fact that the thickness of the front and rear plates 502, 506 can vary significantly, as an example, you can specify that in one embodiment, the rear plate 506 has a thickness of about 3/8 (8 mm), and the front plate 502 has a thickness of about 3 / 16 (5 mm).

Many blades 510 are located between the front and rear plates 502, 506 and are connected to both plates 502, 506. It is easy to understand that the number of blades 510 can vary, and this number depends, in part, on the properties of the material being processed. The thickness of the blades 510 may also vary depending on the properties of the material being processed.

In one embodiment, the blades 510 pass through the front and rear plates 502, 506 and form the ribs 511 of the blades on the outer surface of the front and rear plates 502, 506. The ribs 511 of the blades can exit approximately 1/2 (12 mm) from the front and rear plates 502, 506. The ribs 511 of the blades create an air cushion between the air flow generator 500 and the inside of the casing 200. The ribs 511 of the blades further serve to remove material that may be stuck between the casing 500 and the air flow generator 200.

Turning now to the consideration of FIG. 12, which shows a cross section of an axial bore 508. An axial bore 508 is used to receive an axis, shaft, journal or other member for rotating the air flow generator 500. The bolt holes 509 are used to receive the corresponding axis mounting bolts, which are fixed to the rear plate 506. In this embodiment, the axis has a transition from a first diameter that allows screwing in the axis mounting bolts to a second diameter corresponding to the size of the axial hole 508. The holes 509 for the bolts have bores 515 under the nuts, which are screwed onto the bolts to secure the axle.

Turning now to the consideration of FIG. 13, which shows a top view of the inside of the airflow generator 500 with a single blade 510. The single blade 510 is shown only to explain the unique characteristics of the blades 510 mounted inside the airflow generator 500. The remaining blades 510 have a similar design.

The blade 510 extends from the trailing edge 512 at the perimeter 513 of the rear and front plates 502, 506 to the leading edge 514 located in the immediate vicinity of the axial hole 508. The blade 510 comprises a wedge-shaped portion 516 located in close proximity to the trailing edge 512. The wedge-shaped portion 516 has a thicker cross section to increase pressure and flow volume. The wedge-shaped portion 516 gives increased wear resistance, which is preferred when processing certain materials.

Turning now to the consideration of FIG. 14A, a top view is shown where the wedge-shaped portion 516 can be seen in more detail. The shape of the wedge-shaped portion 516 affects the flow volume, air flow rate and material flow rate through the air flow generator 500. The wedge-shaped portion 516 may undergo changes in the circumferential and longitudinal directions in order to change the air flow volume, air flow velocity and material flow velocity. Casting technology mainly allows you to make changes in three directions and create any number of circular and longitudinal profiles in the wedge-shaped section 516.

- 9 008992

The increased thickness of the wedge-shaped portion 516 increases the life of the airflow generator 500, since it is here that the blade 510 typically experiences the greatest wear. The type (grade) of material of the wedge-shaped portion 516 and the strength of this material may also differ from the material of the rest of the blade 510.

Turning now to the consideration of FIG. 14B, an alternate embodiment of a tapered portion 518 is shown that includes a replaceable wear tip 520. If the airflow generator 500 rotates in a clockwise direction, then the replaceable wear tip 520 experiences the most contact with the material being processed. Although the wedge-shaped portion 518 is thickened to increase its wear resistance, it undergoes more severe wear than other components of the airflow generator 500 and can wear out faster. By replacing the replaceable wear tip 520, it is possible to avoid replacing the entire airflow generator 500. The replaceable wear tip 520 may be connected to the rest of the wedge-shaped portion 518 using any suitable fastening means, including using the fastener assembly 522 with a nut and a bolt. The replaceable wear tip 520 can be made of a stronger material than the rest of the blade 510. The replaceable wear tip 520 can also be replaced by another replaceable wear tip 520 having a different circular and longitudinal profile. In accordance with another option, in this case, the entire wedge-shaped portion 518 is replaced.

Turning now to the consideration of FIG. 15A, which shows a perspective view of the airflow generator 500, where you can see the wedge-shaped portion 516 connected to the front and rear plates 502, 506. Additionally, the ribs 511 of the blade protruding from the outer surface of the front and rear plates 502, 506. see that the wedge-shaped portion 516 is significantly thicker than the corresponding ribs 511 of the scapula. This is due to the fact that the ribs 511 of the blade do not undergo the same severe wear as the wedge-shaped portion 516, and therefore they are not so thick.

Turning now to the consideration of FIG. 15B, a perspective view of an airflow generator 500 with an alternative embodiment of a wedge-shaped portion 516. A wedge-shaped portion 516 increases its thickness and its circular profile as it extends longitudinally from the front plate 502 to the rear plate 506. The wedge-shaped portion 516 also increases its thickness as it goes radially in the direction of the perimeter.

The pulverized material entering the airflow generator 500 tends to accumulate in the immediate vicinity of the back plate 506. A longitudinal increase in thickness ensures that the pulverized material remains centered between the front and back plates 502, 506 rather than accumulates along the back plate 506 Casting technologies make it possible to produce such a wedge-shaped section 516, in which dimensional changes along three axes are possible. The replaceable wear tip 520 may have a longitudinally increasing thickness. If a different wedge-shaped portion 516 is desired, another replaceable wear tip 520 may be used without a longitudinal increase in thickness or with a more pronounced longitudinal increase in thickness. Thus, the direction of flow of the pulverized material in the longitudinal direction can be controlled through the use of wedge-shaped sections 516 with different circular and longitudinal configurations.

Referring again to FIG. 13, which shows a blade 510 having a transition from a position perpendicular to the back plate 506 to an angular position. The blade 510 goes with a gradual transition from the wedge-shaped portion 516 to a location in front of the leading edge 514. The angular position allows the blade 510 to have an angle of inclination in the direction of air flow.

In the embodiment shown, the rear portion 524 of the blade 510, including the wedge-shaped portion 516, extends perpendicularly from the rear plate 506. The rear portion 524 may be approximately one fourth to half the length of the blade 510 extending from the trailing edge 512 to the leading edge 514. The front section 526 represents the rest of the blade 510, and extends from the rear section 524 to the leading edge 514. The front section 526 shown has an angular transition from a perpendicular position relative to the rear plate 506 to an angular position.

The angular position has an angle, which is here referred to as the angle of attack, since it allows the leading edge 514 to crash into the incoming air stream. In FIG. 13, the final angle of attack of the blade 510 at the leading edge 514 is approximately 25 °. The transition from a perpendicular position to an angular position may be provided along the entire length of the blade 510 or in any part thereof. The angle of attack can be selected in a wide range of angles, taking into account the predicted air flow rate, material flow rate and material properties. The angular position may have an angle in the range of approximately from 20 to 60 °.

Alternatively, the blade 510 may remain perpendicular along its entire length. The blade 510 may also have an angle of attack along its entire length. Despite the fact that it exists along the entire length of the blade, the angle of attack can still vary along the length of the blade 510 from the trailing edge 512 to the leading edge 514.

- 10 008992

Turning now to the consideration of FIG. 16, which shows a side view (in profile) of the leading edge 514. Typically, the edge is relatively straight and angled toward the back plate 506. In accordance with one embodiment of the present invention, the front edge 514 extends from the back plate 506 with an outward bend section 528 and then transitions to the inwardly curved portion 530. The outwardly curved portion 528 facilitates trapping air entering the inlet 504 of the airflow generator 500. A leading edge 514 having such a profile allows it to crash into the air and increase the efficiency of the airflow generator 500.

Turning now to the consideration of FIG. 17, which shows a section of the leading edge 514 along line 17-17. The leading edge 514 has an oval cross section that facilitates cutting into the incoming air stream.

Turning now to the consideration of FIG. 18, which shows a perspective view of an airflow generator 500 without a front plate 502 to show the blades 510. The shown embodiment contains nine blades 510, but it should be borne in mind that this number may be different. Each blade 510 contains a wedge-shaped portion 516 to increase wear resistance, increase pressure and air flow. Each blade 510 further has a transition from a perpendicular position to an angle of attack. The angle of attack has a clockwise inclination, which corresponds to the predicted direction of rotation of the airflow generator 500. The airflow generator 500 can also operate in a counterclockwise direction, and then the blades 510 will have to be inclined in that direction.

In operation, the rotating blades 510 create a high speed airflow in the range of 350 mph or more, and direct the air and the pulverized material into the inlet 504. The leading edges 514 of the blades 510 cut into the air and the pulverized material and direct the air and pulverized material into the channels 532 bounded by the blades 510 and extending from the inlet 504 to the perimeter 513 of the front and rear plates 502, 506. The channels 532 provide the maximum flow rate for materials passing through them. Wedge-shaped sections 516 push air and pulverized material towards the outlet 202 of the casing, which is located inside the casing 200. Despite the fact that the proposed generator 500 air flow has unique characteristics, experts will easily understand that any other suitable device can be used instead, which not beyond the scope of the present invention.

In accordance with the present invention, there is provided a pulverization and dehydration (dehydration) system which is suitable for various materials and various flow rates. The systems described herein are scalable for various applications and materials with different particle sizes, so the specific component sizes given here are for example purposes only. For example, the system can be small and can be made in the form of a desktop (bench) model, or it can be a large industrial installation.

The systems 10, 100, 400, 450 disclosed herein may be mounted on the surface of the earth (may be stationary), and this is preferred for large systems. Alternatively, the system may be mounted on a vehicle such as a truck, trailer, railroad car, ship, barge, and the like. To install the system, any vehicle that has a flat seat of sufficient size can be used. The use of a mobile system is preferred in some applications, such as harvesting, working in remote areas, demonstrations, etc.

Turning now to the consideration of FIG. 19, which shows a block diagram of a mobile system 600. System 600 includes previously discussed components, such as inlet pipe 12, venturi 18, airflow generator 32, housing 35, engine 34, exhaust pipe 112, and first and second cyclones 116, 406. System 600 may include additional elements such as a mixer 102, central processing unit 110, capacitor 130, and the like. Systems with many atomization stages can be mounted on a vehicle in a similar way.

System 600 comprises a vehicle, generally designated 602, which has a seat of sufficient size to install components and assemble them. The system 600 further comprises a plurality of supports 604 that are coupled to the vehicle 602 and that support the corresponding assembled components. System 600 may further comprise a housing 606 that surrounds system components. Housing 606 protects components and reduces noise during operation.

One or more components of the system 600 may be temporarily removed (removed) to facilitate transportation. For example, the first and second cyclones 116, 406 can be removed from the casing 606 during transportation and can be transported separately. Cyclones 116, 406 can be removed in whole or in part disassembled prior to transport. Similarly, mixer 102 may be removed to facilitate transportation. The need to dismantle the components depends on the size of the system 600 and the type of vehicle 602, as well as other design restrictions.

The casing 606 may have a control room for the user (operator), allowing to control

- 11 008992 system 600. The casing 606 may have windows that allow you to observe the components and provide access for visual inspection, maintenance and repair, as well as for input of the processed material. System 600 may be of any configuration, depending on convenience, type of application, and other design considerations.

Turning now to the consideration of FIG. 20, which shows a side view of an alternative embodiment of a system 700 in accordance with the present invention. The illustrated embodiment of the system 700 is similar to the previously described embodiment shown in FIG. 4, but also contains an acoustic emission sensor (sound emission) 702, which is connected to the casing 35. The acoustic emission sensor 702 can be made in the form of any commercially available product, including in the form of a system for monitoring acoustic emission (AEM8), manufactured by the company 8сшй1 1п6и51пс5. 1ps o £ Rogyapb, Ogedop. In one embodiment, the acoustic emission sensor 702 is a piezoceramic sensor that allows you to control resonant frequencies in the range from 50 to 950 kHz.

The acoustic emission sensor 702 monitors the high frequency signals generated by the material flowing through the inlet pipe 12, the venturi 18, the air flow generator 32, and the housing 35. The resonant frequency obtained by the acoustic emission sensor 702 carries information about the volumetric flow rate. Changes in the material flow rate through system 700 change the resonant frequency.

The acoustic emission sensor 702 is in electrical communication with a sensor control device 703 that receives resonant frequencies and calculates a flow rate. The sensor control device 703 is in electrical communication with a central processor 110, which receives a flow rate and can respond with a flow rate adjustment command. During normal operation, the resonant frequency remains in the normal operating range. A system malfunction can cause the flow rate to exceed a threshold value. A minimum and maximum value can be set for flow rates during normal operation conditions. If the flow rate is below the minimum value, then the flow rate is increased, and, conversely, the flow rate is reduced if it exceeds the maximum value.

The sensor control device 703 stores in memory a predetermined maximum threshold value for the resonant frequency.

The maximum threshold value may be entered by the operator based on the properties of the material being processed and the design limitations of the system 700. The sensor control device 703 may also contain (in memory) a minimum threshold value for the resonant frequency. If the flow rate exceeds the maximum threshold value, an overload situation occurs and the sensor control device 703 sends a signal to the central processor 110 that the flow rate should be adjusted. Similarly, if the flow rate falls below the minimum threshold value, the sensor control device 703 supplies a corresponding signal to the central processing unit 110.

In addition to the flow rate, the acoustic emission sensor 702 receives resonant frequencies that provide information about abnormal conditions, such as poor balance of the air flow generator 32, offset blade 510, or other mechanical malfunction. An overload situation in itself can create a mechanical malfunction. Such a malfunction can lead to substantial and even catastrophic damage to the 700 system. Flying fragments, which can be dangerous for the operator, can also create a mechanical malfunction. The acoustic emission sensor 702 monitors the resonant frequencies and detects changes indicative of damage. As soon as an overload or damage situation has occurred, the sensor control device 703 provides a signal to the CPU 110 for a time of 1 ms or less. The CPU 110 responds immediately with a corrective action. Alternatively, the sensor control device 703 may have a visual or audible alarm for an operator who manually performs a corrective action.

An acoustic emission sensor 702 is shown located on the rear side 704 of the casing 35. Alternatively, an acoustic emission sensor 702 can be located on the front side 706 of the casing 35 or anywhere else on the outer surface of the casing. The acoustic emission sensor 702 may also be located on the venturi 18 or on the inlet pipe 12.

Turning now to the consideration of FIG. 21, a system 800 is shown in which an acoustic emission sensor 702 is located on a divergent portion 30 (venturi), as well as on the rear side 704 of a housing 35. Many acoustic emission sensors 702 can be used to improve control of resonant frequencies. In alternative embodiments, a plurality of acoustic emission sensors 702 may be located on the housing 35, on the venturi 18, and / or on the inlet pipe 12 to control the flow rate. The sensor control device 703 is in electrical communication with the acoustic emission sensors 702 to calculate a flow rate.

The sensor control device 703 is in electrical communication with a central processor 110, which processes the received resonant frequency data for 1 ms. If the flow rate approaches the overload condition, the sensor control device 703 provides a signal to

- 12 008992 central processing unit 110 for adjusting the flow rate. The central processor 110 can control the flow rate by partially or completely closing the adjustable valves 111. Partially or completely closing the valves 111 increases the speed of the air flow through the venturi 18, which creates additional force to push the material through the venturi 18 and the air flow generator 32. The central processor 110 may also partially or completely close the flow regulator 106 to reduce the amount of material in the system 700. If the resonant frequency indicates a mechanical failure, the central processor 110 may also shut down the system and turn off the engine 34. The sensor control device 703 may also provide visual or audible alarm for the operator.

Turning now to the consideration of FIG. 22, which shows a cross section of an embodiment of a casing 200 of an air generator. As already mentioned above, the position of the deflecting plate 250 can be adjusted to increase or decrease the separation (clearance) distance from the air flow generator 32. The central processor 110 may control the position of the deflector plate 250, as it is in communication with the actuator 900 to move the deflector plate 250. The actuator 900 may be in the form of an electromechanical device, a pneumatic device, or other known device. The central processor 110 may adjust the flow rate by moving the deflecting plate 250 to avoid an overload condition. This action can be taken at the same time as the gate valves 111 and / or the flow regulator 106 are adjusted to improve flow rate control.

One or more acoustic sensors 702 may also be used in the systems shown in FIG. 1, 2, 9 and 19. Thus, in accordance with the present invention, the illustrated system 700 should be considered only as an exemplary system that is not restrictive.

Turning now to the consideration of FIG. 23, which shows a perspective view of an alternative embodiment of a system 1000 that includes an engine 34 and an axis 33 in the immediate vicinity of the rear side 704 of the housing 35. The engine 34 has a pulley 1002, which (by a belt) is connected to the axis 33 to rotate the axis 33 with high speed. The axis 33, which can also be called a shaft, passes through one or more brackets 1004, which mount the axis 33 with the possibility of rotation. The brackets 1004 are mounted on the mounting plate 1006. It is shown that the pulley 1002 is connected to the axis 33 between the two brackets 1004, however, it should be borne in mind that the pulley 1002 can be connected to the axis 33 at any other location.

System 1000 further includes an automatic balancing system 1008 that includes a dynamic balancer 1010, a vibration sensor 1012, and a balancer control device 1014. Automatic balancing system 1008 can be easily installed, has high reliability, is fully automatic and requires little operator training. In FIG. 23 shows a balancer 1010 made in the form of an external balancer 1010, however, the balancer 1010 can also be made in the form of an internal balancer or an annular balancer, as discussed in more detail below. The external balancer 1010 is in electrical communication with the balancer control device 1014 to compensate for the imbalance of the axis 33 and the air flow generator 32 when the axis rotates at revolutions in the operating range. The balancer control device 1014 includes a processor (not shown) with an external balancer 1010 control algorithm.

Dynamic compensation can reduce noise and vibration, improve the quality characteristics of the system and increase the flow rate of the material through the generator 32 air flow. Dynamic balancing of the airflow generator 32 eliminates cavitation and improves the performance of the airflow generator 32. External balancers are mass-produced, for example, by the company ΞοΙιιηб Shbiiyez, 1ps. οί Rotyapb, Ogedop. External balancer 1010 may receive power through a rotating current collector of the power transmission system or from a non-contact power transmission system.

In FIG. 23 shows an external balancer 1010 that is connected to the proximal end 1016 of the axis

33. An axis 33 is connected at a distal end (not shown) to an airflow generator 32 that is located inside the housing 35. An external balancer 1010 is connected to an axis 33 in close proximity to the rear side 704, which is also called the pulley side of the airflow generator 32. Due to this, the external balancer 1010 does not create obstacles to the air flow entering the inlet 508 of the air turbine 32 (air flow generator 32).

External balancer 1010 operates on the principle of mass compensation with an imbalance of the axis. In one embodiment, the external balancer 1010 contains two movable eccentric weights. An external balancer 1010 drives each eccentric load by means of electric micromotors through a precision gear train.

Turning now to the consideration of FIG. 24A, which shows a diagram showing an airflow generator 32 aligned axially with an external balancer 1010. The external balancer 1010 is located in a plane remote from the plane in which the airflow generator 32 is located, as shown in FIG. 23. The external balancer 1010 contains loads 1020 shown relative to

- 13 008992 of the unbalance position 1022. The balancer control device 1014 commands the external balancer 1010 to shift the weights 1020 relative to the unbalance position 1022. This situation is called balancing in the opposite plane here, since the weights 1020 are in the mass balancing plane, while airflow generator 32 is in a second plane.

Turning now to the consideration of FIG. 24B, which shows a dynamically balanced situation in which weights 1020 compensate for the position of unbalance 1022. When balancing in the opposite plane, weights 1020 must be in the same plane 1024 as unbalance 1022 in order to balance. The semicircle 1024 has an axial center 1025. The external balancer 1010 is able to maintain accurate balance, even if the axis 33 stops and starts to rotate again.

Turning now to the consideration of FIG. 25A, a diagram is shown where you can see the airflow generator 32 again aligned (axially) with the external balancer 1010. However, in this situation, the external balancer 1010 is in close proximity to the airflow generator 32 and therefore is essentially in the same the plane itself. This situation is called balancing here on the same plane. Weights 1020 are shown relative to the position of the unbalance 1022, and there is an unbalance state. The balancer control device 1014 commands the external balancer 1010 to shift the weights 1020 relative to the position of the unbalance 1022.

Turning now to the consideration of FIG. 25B, which shows a dynamically balanced situation in which weights 1020 compensate for the unbalance position 1022. When balancing in the same plane, weights 1020 must be located in the opposite semicircle 1026 from the unbalance position 1022 in order to balance.

Turning now to the consideration of FIG. 26A, a perspective view showing a balancing technique in the opposite plane is shown. The external balancer 1010 is connected to the axis 33 and rotates in the first plane 1030. A mass 1032, such as an air flow generator 32, is connected to the opposite end of the axis 33 and rotates in the second plane 1034. Thus, the external balancer 1010 and the mass 1032 are at opposite ends axis 33. Weights 1020 inside the external balancer 1010 compensate for the position of the unbalance 1022 of the mass 1032.

The balancing technique in the opposite plane is applied to the system 1000 shown in FIG. 23, in which mass 1032 is an air flow generator 32. An external balancer 1010 and an airflow generator 32 are mounted at opposite ends of the axis 33, which allows accurate and dynamic balancing of the airflow generator 32. The pulley 1002 is connected to the axis 33 between the external balancer 1010 and the air flow generator 32, however, it should be borne in mind that the pulley 1002 can also be connected to the axis 33 at any other location. Compensating weights 1020 create balance in the same semicircle, but in a different plane from the position of imbalance 1022.

Turning now to the consideration of FIG. 25B is a perspective view illustrating balancing techniques in the same plane. Here, the mass 1032 and the external balancer 1010 are located in close proximity to each other, so that they are approximately in the same plane 1036. The external balancer 1010 is connected with the axis 33, which is also connected with the mass 1032. Loads 1020 must be in the opposite semicircle relative to the position of the imbalance 1022 to provide balance. The system 1000 shown in FIG. 23 may be modified to provide balancing in the same plane.

Referring again to FIG. 23, a dynamic balancing system 1008 is shown that includes a vibration sensor 1012 that accurately controls the level of vibration that provides imbalance information. The sensor 1012 is connected to the brackets 1004 or to the mounting plate 1006 by means of magnets, by mounting on racks or by other suitable means. Vibration sensor 1012 is in electrical communication with a balancer control device 1014 that filters incoming signals based on RPM. The balancer control device 1014 is in communication with the external balancer 1010 and allows the weights 1020 to be moved in a direction that reduces the amplitude of the vibration signal. When weights 1020 are positioned so that the smallest vibration level is achieved, balancing is completed and dynamic balancing system 1008 monitors vibration levels to ensure optimal operation.

Turning now to the consideration of FIG. 27, which shows a cross section of an alternative embodiment of the dynamic balancer 1040. The dynamic balancer 1040 is an internal balancer 1040, which is fully or partially located inside the bore of the axis 33. The internal balancers are commercially available, for example, by the company δοϊιιηίΐΐ ΙπάιΐδΙποδ. 1ps o £ RothIalb, Ogedop. The inner balancer 1040 may have a mounting flange 1042, which is connected to the axis 33 using one or more bolts 1044. Other known techniques for fastening the inner balancer 1040 to the axis 33 can be used.

As with the external balancer 1010, the internal balancer 1040 changes the position of the weights to compensate for the mass imbalance. The inner balancer 1040 can be used with the balancing system 1008 shown in FIG. 23, with balancing technique in the opposite plane or in the same plane. In this way, the internal balancer 1040 is in communication with the balancer control device 1014 for dynamically changing the position of the weights. As mentioned here

- 14 008992 above, the balancer control device 1014 is in communication with the vibration sensor 1012 to determine an imbalance position.

Turning now to the consideration of FIG. 28, which shows a cross section of the first embodiment of compensating weights 1046, 1048 used in the internal balancer 1020. Compensating weights 1046, 1048 can be made in the form of semicircles that rotate relative to each other, above and below the structure. It is shown that the internal compensating load 1046 has a thicker cross-section than the external compensating load 1048. By accurately selecting the position of the compensating weights 1046, 1048, a dynamic balance can be ensured. Shown compensating weights 1046, 1048 can also be used in the external balancer 1010.

Turning now to the consideration of FIG. 29, which shows a perspective view of an alternative dynamic balancer 1050. The dynamic balancer 1050 is an annular balancer 1050 that spans the axis 33 and is connected to it. Ring balancers are mass-produced, for example, by the company ΞοΙιιηίΙΙ 1i6i81pe8, 1ps. o £ HornIaib, Ogedop. The ring balancer 1050 itself can be located at any accessible location along the axis 33. The ring balance 1050 can be used with the balancing system 1008 shown in FIG. 23, and it can be used to implement the balancing technique in the opposite plane or in the same plane.

Turning now to the consideration of FIG. 30, which shows a cross-section of the first embodiment of the annular balancer 1050. The annular balancer 1050 contains compensating weights 1052, 1054, which can be axially adjacent to each other. The first compensating load 1052 may have a larger mass than the second compensating load 1054. By selecting the position of the compensating loads 1052, 1054 a centering load is created to completely compensate for the unbalance position, which allows for dynamic balance. Alternatively, the annular balancer 1050 may contain compensating weights similar to those used in the previously described dynamic balancers 1010, 1040.

Other known balancer options may be used. An automatic balancing system 1008 dynamically balances the airflow generator 32 at operating speeds, maintaining an optimal balance. The balance is maintained after the cessation of rotation and during subsequent operation. The balancers can be connected to the axis 33 on the pulley side so as not to interfere with the air flow entering the air flow generator. An automatic balancing system 1008 eliminates cavitation, which improves efficiency and improves the performance of the airflow generator.

Claims (44)

CLAIM 1. A device for atomizing the material and extracting moisture from the material, which includes an inlet pipe; a venturi connected to the inlet pipe; an air flow generator for creating an air flow and comprising an inlet; a casing at least partially covering the air flow generator and comprising an outlet that is in communication with the inlet; an air flow generator that is connected to the venturi to direct the air flow through the venturi and in the direction of the inlet, the material introduced into the air flow passes through the venturi and is subjected to moisture spraying and extraction; and a sound radiation sensor connected to the casing and serving to receive a resonant frequency carrying information about the material passing through the casing. 2. The device according to claim 1, which further comprises a sensor control device that is coupled to a sound emission sensor to receive a resonant frequency and determine a material flow rate. 3. The device according to claim 1, which further comprises a central processor that is in communication with the sensor control device. 4. The device according to claim 3, which further comprises a valve located on the venturi, for adjusting the air volume and air velocity inside the casing and the air flow generator, the valve being connected to a central processor that controls the position of the valve. 5. The device according to claim 3, which further comprises a flow regulator that is connected to the inlet pipe and controls the flow rate of the material in the inlet pipe, the flow regulator being in communication with a central processor controlling the flow regulator. 6. The device according to claim 5, which further comprises a sensor for controlling the flow rate of the material in the inlet pipe. 7. The device according to claim 3, which further comprises a deflecting plate connected to the inner part of the casing in the immediate vicinity of the outlet and having a cutting edge in the immediate vicinity of the air flow generator - 15 008992 ka; and an actuator connected to the deflector plate, setting the deflector plate to a predetermined position, the actuator being in communication with the central processor. 8. The device according to claim 1, in which the sound emission sensor is located on the rear side of the casing. 9. The device according to claim 1, in which the sound emission sensor is located on the front side of the casing. 10. The device according to claim 1, which further comprises a second sound emission sensor located on the venturi, which is used to receive a resonant frequency that carries information about the material passing through the venturi. 11. The device according to claim 1, which further comprises a second sound emission sensor located on the inlet pipe, which is used to receive a resonant frequency carrying information about the material passing through the inlet pipe. 12. The method of atomizing the material and extracting moisture from the material, which includes the following operations: the use of an air flow generator that is connected to the venturi, the air flow generator generating air flow through the venturi and in the direction of the air flow generator; introducing material into the air stream; passing material through a venturi to extract moisture and atomize the material and receiving acoustic emission that carries information about the flow rate of the material through the air flow generator. 13. The method according to item 12, which additionally provides for the installation of an air flow generator inside the casing and in which the reception of acoustic emission involves the installation of a sound emission sensor on the casing. 14. The method according to item 12, in which the sound emission sensor is installed on the rear side of the casing. 15. The method according to item 12, in which the sound emission sensor is installed on the front side of the casing. 16. The method according to item 12, which further provides for the use of a sound emission sensor in communication with the sensor control device to determine a material flow rate. 17. The method according to clause 16, which includes the following operations: using a valve on a diverging portion of the venturi; moreover, the valve is connected to the Central processor to adjust the air volume and air speed inside the casing and inside the air flow generator. 18. The method according to clause 16, which includes the following operations: the use of a deflecting plate connected to the inner part of the casing and having a cutting edge in the immediate vicinity of the air flow generator; the use of an actuator connected to the deflecting plate, and the actuator is in communication with the Central processor to install the deflecting plate in a predetermined position. 19. The method according to item 12, which further provides for the use of an inlet pipe connected to the venturi, the air flow passing through the inlet pipe and in the direction of the venturi. 20. The method according to claim 19, which includes the following operations: the use of a flow controller that controls the flow rate of the material in the inlet pipe; moreover, the flow controller is in communication with the Central processor to adjust the flow rate of the material. 21. The method according to claim 19, in which receiving acoustic emission further comprises installing a second sound emission sensor on the intake pipe. 22. The method according to item 12, in which the reception of acoustic emission further comprises the installation of a second sound emission sensor on the venturi. 23. A device for spraying material and extracting moisture from a material that contains an inlet pipe; a venturi connected to the inlet pipe; an air flow generator for creating an air flow and having an inlet; an axis connected to an air flow generator; a balancer connected to the axis to compensate for the imbalance of the axis during rotation; and a casing at least partially covering the air flow generator and having an outlet that is connected to the inlet, the air flow generator being connected to the venturi to direct the air flow through the venturi and in the direction of the inlet, the material introduced into the air stream, passes through a venturi and is subjected to atomization and extraction of moisture. 24. The device according to item 23, which further comprises a balancer control device, to - 16 008992 which has a connection with the balancer, and the balancer control device controls the imbalance compensation. 25. The device according to paragraph 24, which further comprises a vibration sensor, which is in communication with the balancer control device and receives vibration from the axis, carrying information about the imbalance. 26. The device according to item 23, in which the balancer is an external balancer having compensating loads. 27. The device according to p, in which the external balancer has two compensating weights made with the possibility of rotation around the axis of the balancer. 28. The device according to item 23, in which the axis has an internal bore, and the balancer is an internal balancer at least partially located inside the internal bore and having compensating weights. 29. The device according to p. 28, in which the internal balancer has two compensating weights made with the possibility of rotation around the axis of the internal balancer. 30. The device according to clause 29, in which two compensating weights are located respectively one on top and the other below the structure. 31. The device according to item 23, in which the balancer is an annular balancer having compensating loads. 32. The device according to p, in which the annular balancer has two compensating weights made with the possibility of rotation around the axis of the annular balancer. 33. A method of spraying a material and extracting moisture from a material, which includes the following operations: the use of an air flow generator that is connected to a venturi; use of an axis connected to an air flow generator; the connection of the balancer with the axis, and the balancer compensates for the imbalance of the axis during rotation; using an air flow generator to create air flow through the venturi and in the direction of the air flow generator; introducing material into the air stream and passing the material through a venturi to extract moisture and atomize the material. 34. The method according to claim 33, wherein the external balancer having compensating weights is used as a balancer. 35. The method according to clause 34, which uses an external balancer having two compensating weights made with the possibility of rotation around the axis of the balancer. 36. The method according to p. 33, in which as the balancer use an internal balancer having compensating weights, the method further provides for the use of an internal bore in the axis and at least partial introduction of the internal balancer into the inner bore. 37. The method according to clause 36, in which the internal balancer has two compensating weights made with the possibility of rotation around the axis of the internal balancer. 38. The method according to clause 37, which further provides for the use of two compensating weights, respectively located one on top and the other below the structure. 39. The method according to p, in which the balancer is an annular balancer having compensating loads. 40. The method according to § 39, in which the annular balancer has two compensating weights made with the possibility of rotation around the axis of the annular balancer. 41. The method according to p. 33, which further comprises receiving vibration carrying information about the imbalance of the axis. 42. The method according to paragraph 41, which includes the following operations: the transmission of signals carrying information about the imbalance of the axis to the balancer control device; and using a balancer control device to detect imbalance and control compensation to eliminate imbalance. 43. The method according to clause 33, which provides for the use of a balancer having compensating loads and which additionally includes the following operations: installation of a balancer in the immediate vicinity of the air flow generator; and moving the compensating weights in the opposite semicircle from the imbalance point in the air flow generator to provide imbalance compensation. 44. The method according to p, in which the balancer has compensating loads, and which additionally includes the following operations: installing the balancer at a distance from the air flow generator and moving the compensating weights in the same semicircle where the imbalance point in the air flow generator is located to provide imbalance compensation.