Field of the Invention The present invention relates to techniques for processing materials to pulverize and extract moisture. Background of the Invention Numerous industries require the labor intensive task of reducing materials to smaller particles and even to a fine powder. For example, the utility industry requires coal to be reduced from nuggets to powder before being burned in power generation furnaces. Limestone, chalk and many other minerals must also, for most uses, be reduced to powder form. Breaking up solids and grinding it into powder is a mechanically demanding process. Ball mills, hammer mills, and other mechanical structures impact on, and crush, the pieces of material. These systems, although functional, are inefficient and relatively slow in processing. Numerous industries further require moisture extraction from a wide range of materials. Food processing, sewage waste treatment, crop harvesting, mining, and many other industries require moisture extraction. In some industries materials are discarded because moisture extraction cannot be performed efficiently. These same materials, if they could be efficiently dried, would otherwise provide a commercial benefit. In other industries, such as waste treatment and processing, water extraction is an ongoing concern and tremendous demand exists for improved methods. Although several techniques exist for dehydrating materials, there is an increasing need for improved moisture extraction efficiency. Thus, it would be an advancement in the art to provide more efficient processes for pulverizing materials and extracting moisture from materials. Such techniques are disclosed and claimed herein. Brief Description of the Drawings A more particular description of the invention briefly described above will be rendered by reference to the appended drawings. Understanding that these drawings only provide information concerning typical embodiments of the invention and are not therefore to be considered limiting of its scope, the invention will be described and explained with additional specificity and detail through the use of the accompanying drawings, in which: Figure 1 is a side view illustrating one embodiment of a pulverizing system of the present invention; Figure 2 is a plan view illustrating the pulverizing system of Figure 1 ; Figure 3 is a cross-sectional side view illustrating a venturi of a pulverizing system as the venturi receives material; Figure 4 is a side view illustrating an alternative embodiment of a pulverizing system of the present invention; Figure 5 is a plan view illustrating a plan view of the pulverizing system of Figure 4; Figure 6 is a perspective view illustrating an air generator housing and outlet restrictors; Figure 7 is a cross-sectional view of one embodiment of an air generator housing; Figure 8 is cross-sectional view of a venturi and a throat resizer; Figure 9 is a block diagram illustrating the components of an alternative embodiment of a pulverizing system; Figure 10 is a block diagram illustrating an alternative embodiment of a pulverizing system of the present invention; Figure 11 is a perspective view of one embodiment of an airflow generator suitable for use with a system of the present invention; Figure 12 is a cross-sectional view of a portion of the airflow generator of Figure 11 ; Figure 13 is a plan view of an interior portion of the airflow generator of Figure 11 ; Figure 14A is a plan view of a trailing edge of a blade of the airflow generator of Figure 11 ; Figure 14B is a plan view of an alternative embodiment of a trailing edge of a blade of the airflow generator of Figure 11 ; Figure 15A is a perspective view of a portion of the airflow generator of Figure 11 ; Figure 15B is a perspective view of a portion of an alternative embodiment of an airflow generator of Figure 11 ; Figure 16 is a side view of a blade of the airflow generator of Figure 11 ; Figure 17 is a cross-sectional view of the blade of Figure 16; Figure 18 is a perspective view of a portion of the airflow generator of Figure 11 ; Figure 19 is a side view of an alternative embodiment of a pulverizing system of the present invention; Figure 20 is a side view illustrating an alternative embodiment of a pulverizing system of the present invention; Figure 21 is a side view illustrating an alternative embodiment of a pulverizing system of the present invention; Figure 22 is a cross-sectional view an alternative embodiment of an air generator housing; Figure 23 is a perspective view of an embodiment of a housing, axle, and balancer; Figure 24A is a diagram illustrating a position of compensating weights relative to a point of imbalance; Figure 24B is another diagram illustrating a position of compensating weights relative to a point of imbalance; Figure 25A is another diagram illustrating a position of compensating weights relative to a point of imbalance; Figure 25B is another diagram illustrating a position of compensating weights relative to a point of imbalance; Figure 26A is a perspective view of a balancer relative to a rotating mass; Figure 26B is another perspective view of a balancer relative to a rotating mass; Figure 27 is a cross-sectional view of one embodiment of an internal balancer disposed within an axle; Figure 28 is a cross-sectional view of one embodiment of compensating weights within the internal balancer of Figure 27; Figure 29 is a perspective view of one embodiment of a ring balancer; and Figure 30 is a cross-sectional view of one embodiment of compensating weights within the ring balancer of Figure 29.

Detailed Description of Preferred Embodiments Referring to Figures 1 and 2, a system 10 for pulverizing and extracting moisture is shown that includes an inlet tube 12. The inlet tube 12 includes a first end 14, communicating with free space and an opposing, second end 16 that couples to a venturi 18. Although reference is made herein to tubes and pipes, one of skill in the art will appreciate that all such elements may have circular, rectangular, hexagonal, and other cross-sectional shapes. Generally, circular cross-sections are desirable to facilitate fabrication and operation, but the invention is not limited to such a specific implementation. The inlet tube 12 provides some distance to the venturi 18 in which material can accelerate to the required velocity. A filter (not shown) may be placed to cover the first end 14 to prevent introduction of foreign particles into the system 10. The inlet tube 12 further includes an elongated opening 20 on an upper part thereof to allow communication with the open lower end of a hopper 22. The hopper 22 is open at its upper end 24 to receive materials. In an alternative embodiment, the system 10 does not include a hopper 10 and material is simply inserted into the elongated opening 20 through various known conventional methods. The venturi 18 includes a converging portion 26 coupled to the inlet tube 12. The converging portion 26 progressively reduces in diameter from that of the inlet tube 12 to a diameter smaller than the inlet tube 12. The venturi 18 further includes a throat 28 that maintains a consistent diameter and is smaller than the diameter of the inlet tube 12. The venturi 18 further includes a diverging portion 30 that couples to the throat 28 and progressively increases in diameter in the direction of airflow. The diverging portion 30 may be coupled to the throat 28 by casting, screw threads, or by other known methods. As illustrated, the converging portion 26 may be longer in longitudinal length than the diverging portion 30. The venturi 18 is in communication with an airflow generator 32 that creates an airflow flowing from the first end 14, through the inlet tube 12, through the venturi 18, and to the airflow generator 32. The velocity of the generated airflow may range from 350 mph to supersonic. The airflow velocity will be greater in the venturi 18 than in the inlet tube 12. The airflow generator 32 may be embodied as a fan, impeller, turbine, a hybrid of a turbine and fan, a pneumatic suction system, or other suitable device for generating a high speed airflow. The airflow generator 32 is driven by a drive motor 34. The drive motor 34 couples to an axle 33 using known methods. The axle 33 engages the airflow generator 32 to power rotation. The horse power of a drive motor 34 will vary significantly, such as from 15 hp to 1000 hp, and depends on material to be treated, material flow rate, and airflow generator dimensions. Thus, this range is for illustrative purposes only as the system 10 can be scaled up or down. An upper scale system 10 may be used at a municipal waste processing facility whereas a smaller scale system 10 may be used to process sewage waste on board an ocean vessel. The airflow generator 32 includes a plurality of radially extending blades that rotate to generate a high speed airflow. The airflow generator 32 is disposed within a housing 35 that includes a housing outlet 36 that provides an exit to incoming air. The housing 35 couples with the venturi 18 and has a housing input aperture (not shown) that allows communication between the venturi 18 and the interior of the housing 35. The blades define radially extending flow passages through which air passes to a housing outlet 36 on its periphery to allow pulverized material to exit. One embodiment of an airflow generator 32 suitable for use with the present invention is discussed in further detail below in reference to Figures 11 to 18. Referring to Figure 3, a diagram is shown illustrating operation of the venturi 18 during a pulverization event. In operation, material 38 is introduced into the inlet tube 12 through any number of conveyance methods. The material 38 may be a solid or a semi-solid. The airflow generator 32 generates an air stream, ranging from 350 mph to supersonic, that flows through the inlet tube 12 and through the venturi 18. In the venturi 18, the airflow velocity substantially accelerates. The material 38 is propelled by the high speed airflow to the venturi 18. The material 38 is smaller in diameter than the interior diameter of the inlet tube 12 and a gap exists between the inner surface of the inlet tube 12 and the material 38. As the material 38 enters the converging portion 26, the gap becomes narrower and eventually the material 38 causes a substantial reduction in the area of the converging portion 26 through which air can flow. A recompression shock wave 40 trails rearwardly from the material and a bow shock wave 42 builds up ahead of the material 38. Where the converging portion 26 merges with the throat 28 there is a standing shock wave 44. The action of these shock waves 40, 42, 44 impacts the material 38 and results in pulverization and moisture extraction from the material. The pulverized material 45 continues through the venturi 18 and exits into the airflow generator 32. The material size reduction depends on the material to be pulverized and the dimensions of the system 10. By increasing the velocity of the airflow, pulverization and particle size reduction increases with certain materials. Thus, the system 10 allows the user to vary desired particle dimensions by varying the velocity of the airflow. The system 10 has particular application in pulverizing solid materials into a fine dust. The system 10 has further application in extracting moisture from semi-solid materials such as municipal waste, paper sludge, animal by-product waste, fruit pulp, and so forth. The system 10 may be used in a wide range of commercial and industrial applications. Referring to Figures 4 and 5, an alternative embodiment of a system 100 of the present invention is shown for extracting moisture from materials. The system 100 may include a blender 102 for blending materials in a preprocessing stage. Raw material may include polymers that tend to lump the material into granules. The granules may be oversized and, due to the polymers, resist breaking down into a desired powder form. The presence of polymers is typical with municipal waste as polymers are introduced during sewage treatment to bring the waste particles together. Waste is processed on a belt press resulting in a material that is mostly semi-solid. In some processes the material may be approximately 15 to 20 percent solid and the remainder moisture. In the preprocessing stage, a drying enhancing agent is mixed with the raw material to break down the polymers and the granulization of the material. Non- polymerized products may be processed without the blending. Raw material is introduced into the blender 102 that blends the material with a certain amount of a drying enhancing agent. The drying enhancing agent may be selected from a wide range of enhancers such as attapulgite, coal, lime, and the like. The drying enhancing agent may also be a pulverized and dried form of the raw material. The blender 102 mixes the material with the drying enhancing agent to produce an appropriate moisture content and granular size. The raw material is transferred from the blender 102 to the hopper 22 in any one of a number of methods including use of a conveyance device 104 such as a belt conveyor, screw conveyor, extruder, or other motorized devices. In the illustrated embodiment, the conveyance device 104 is an inclined track that relies on gravity to deliver raw material to the hopper 22. The conveyance device 104 is positioned below a flow control valve 106 located on the lower portion of the blender 102. In an alternative embodiment, the hopper 22 may be eliminated and material is delivered directly to the elongated opening 20 of the inlet tube 12. The hopper 22 is only one device that may be used to facilitate delivery of material to the inlet tube 12. Any number of other types of conveyance devices may be used as well as manual delivery. One or more sensors 108 may monitor the flow rate of material passing from the blender 102 to the inlet tube 12. A sensor 108 is in communication with a central processor 110 to regulate the flow rate. The sensor 108 may be disposed proximate to the conveyance device 104, proximate to the hopper 22, within the hopper 22, or even between the hopper 22 and the elongated opening 20 to monitor the material flow rate. The central processor 110 is in communication with the flow control valve 106 to increase or decrease the flow rate as needed. Alternative methods for monitoring and controlling the flow rate may also be used including visual inspection and manual adjustment of the flow control valve 106. The hopper 22 receives the material and delivers the material to the elongated opening 20 of the inlet tube 12. The elongated opening 20 may be equal to or less than 4" wide and 5" long to maintain an acceptable feed flow for certain applications. The length of inlet tube 12 from the elongated opening 20 to the venturi 18 may range from 24" (610 mm) to 72" (1830 mm) or more and depends on material to be processed and the flow rate. One of skill in the art will appreciate that the dimension are for illustrated purposes only as the system 10 is scalable. The airflow pulls the material from the inlet tube 12 through the venturi 18. In the illustrated embodiment, the first end 14 is configured as a flange to converge from a diameter greater than the inlet tube 12 to the diameter of the inlet tube. The flange configured first end 14 increases airflow volume into the inlet tube 12. Certain embodiments have the throat diameter of the venturi 18 ranging from approximately 1.5 " (38 mm) to approximately 6" (152 mm). The throat diameter is scalable based on material flow volume and may exceed the previously stated range. The throat diameter of the venturi 18 and the inlet tube 12 are directly proportional. In one embodiment, the throat diameter is 2.75" and operates with an inlet tube diameter of 5.5" (139.33 mm). In an alternative embodiment, the throat diameter may be 2.25" (57 mm) and operates properly with an inlet tube diameter of 4.50" (114 mm). Thus, a 2 to 1 ratio ensures that raw feed material is captured in the incoming airflow. In the illustrated embodiment, the diverging section 30 couples to the housing 35 and communicates directly with the housing 35. The final diameter of the diverging section 30 is not necessarily the same as the inlet tube 12. In an alternative embodiment, the diverging section 30 may couple to an intermediary component, such as a cylinder, tube, or pipe, prior to coupling with the housing 35. One or more flow valves 111 may be disposed on the diverging portion 30 and provide additional air volume into the interior of the housing 35 and the airflow generator 32. The additional air volume increases the airflow generator 32 performance. In one embodiment, two flow valves 111 are disposed on the diverging portion 30. The system 100 may be operated with the flow valves 111 partially or completely opened. If material begins to obstruct the venturi 18, the flow valves 111 may be closed. This results in more airflow through the venturi 18 to provide additional force and drive material through the venturi 18 and the airflow generator 32. The flow valves 111 are adjustable and are shown in electrical communication with the central processor 110 for control. Although manual operation of the flow valves 111 is within the scope of the invention, computer automation greatly facilitates the process. The venturi 18 provides a point of impact between higher velocity shock waves and lower velocity shock waves. The Shockwaves provide a pulverization and moisture extraction event within the venturi 18. In operation, there are no visible signs of moisture on the interior of the venturi 18 or in the housing outlet 36. The amount of moisture removed is substantial although a residual amount may remain. The pulverization event further reduces the size of materials. It has been experienced that certain materials having a diameter of 2" (50 mm) entering the venturi 18 are reduced to a fine powder with a diameter of 20 urn in one pulverization event. Size reduction depends on the material being processed and the number of pulverization events. Separating water from the material has numerous applications such as material dehydration and greatly reducing the number of pathogens. The present invention has particular application in processing municipal waste. The preprocessing step of blending a drying enhancing agent provides a waste material that is readily processed by the system 100. It is believed that the pulverizing and moisture extraction process greatly reduces the amount of illness causing pathogens in the waste material by rupturing their cell wall. A second source of pathogen reduction is moisture extraction which reduces the pathogens. Analytical data from treating municipal waste shows that the present invention eliminates the majority of total colifrom, faecal coliform, escherichia coli, and other pathogens. The present invention has specific application in extracting moisture from fruit and vegetable products. In one application, the system 100 may be used to dehydrate fruit and vegetable products such as apples, oranges, carrots, nectarines, peaches, melons, tomatoes, and so forth. Extracted moisture, which is relatively sanitary, may be condensed and recaptured to provide a pure juice product. In another application, the invention may be used to pulverize and extract water from certain agricultural products such as banana stalk, palm trees, sugar canes, rhubarb, and so forth. In pulverizing banana stalk fibers, the fibers are separated and moisture is extracted. Commercial applications exist in taking agricultural products from their natural state to a dehydrated state. The material, moisture, and air stream proceed through the airflow generator 32 and exit through the housing outlet 36. The housing outlet 36 is coupled to an exhaust pipe 112 which delivers the material to a cyclone 114 for material and air separation. The diameter of the exhaust pipe 112 may range from approximately 4" (100 mm) to 7" (177 mm). It may be necessary to exceed this given range for certain materials such as attapulgite or coal where a 8" (203 mm) exhaust pipe 112 is appropriate. The exhaust pipe 112 may have a cross-section of various shapes, i.e. rectangular, octagonal, etc. and may have various diameters. The exhaust pipe 112 may have a length of approximately 12 feet to 16 feet. The diameter size of the exhaust pipe 112 impacts the amount of drying that further occurs. High air volume is required for further drying of materials. In the exhaust pipe 112, the faster moving air in the exhaust pipe 112 passes the material and removes moisture remaining on the material. The air and vapor travel to a cyclone 114 where air and vapor are separated from the solid material. A pulverization event generates heat that assists in drying the material. In addition to pulverization, rotation of the airflow generator 32 generates heat. The dimensions between the housing 35 and the airflow generator 32 are such that during rotation the friction generates heat. The heat exits through the housing outlet 36 and exhaust pipe 112 and further dehydrates the material as the material travels to the cyclone 114. The generated heat may also be sufficient to partially sterilize the material in certain applications. The diameter of the housing outlet 36 may be increased or decreased to adjust the resistance and the amount of heat traveling through the housing outlet 36 and exhaust pipe 112. The diameter of the exhaust pipe 112 and the housing outlet 36 effects the removal of moisture on pulverized material. Adjusting the outlet diameter is further discussed below. The pulverization and moisture extraction increases as the airflow generated by the airflow generator 32 increases. If airflow is increased or decreased, the diameter of the exhaust pipe 112 and housing outlet 36 may be decreased to provide the same material dehydration. Thus, the airflow and diameters may be adjusted relative to one another to achieve the desired dehydration. Heavier materials with less water, such as rock materials, require less moisture extraction. With such materials, the housing outlet 36 and exhaust pipe 112 diameters may be increased as less drying is required. Consequently, with wetter materials, the housing outlet 36 and the exhaust pipe 112 diameters may be decreased to increase the amount of air and heat to achieve the proper dehydration of the material. The angle of inclination of the exhaust pipe 112 relative to the longitudinal axis of the venturi 18 and airflow generator 32 also effects dehydration performance. The exhaust pipe angle α may be approximately 25 degrees to approximately 90 degrees in order to enhance moisture extraction. Material traveling upward is held back by gravity whereas air is less restricted by gravity. This allows the air to move faster than the material and increase moisture removal. The angle α may be adjusted to increase or decrease the effect on moisture extraction. The exhaust pipe 112 may be straight as illustrated or curved as shown in phantom. The cyclone 114 is a well known apparatus for separating particles from an airflow. The cyclone 114 typically includes a settling chamber in the form of a vertical cylinder 116. Cyclones can be embodied with a tangential inlet, axial inlet, peripheral discharge, or an axial discharge. The airflow and particles enter the cylinder 116 through an inlet 118 and spin in a vortex as the airflow proceeds down the cylinder 116. A cone section 120 causes the vortex diameter to decrease until the gas reverses on itself and spins up the center to an outlet 122. Particles are centrifuged toward the interior wall and collected by inertial impingement. The collected particles flow down in a gas boundary layer to a cone apex 124 where it is discharged through an air lock 126 and into a collection hopper 128. In certain applications, the system 100 may further include a condenser 130 to receive the airflow from the cyclone 114. The condenser 130 condenses the vapor in the airflow into a liquid which is then deposited in a tank 132. An outlet 134 couples to the condenser 130 and provides an exit for air. As can be appreciated, the condenser 130 has particular application with food processing. In an alternative embodiment, the condenser 130 is embodied as an alternative treatment device such as a charcoal filter or the like. As can be appreciated, condensation or filtering will depend on the material and application. The outlet 134 may include or couple to a filter (not shown) to filter residue, particles, vapor, etc. from the outputted air. Passing material through the system 100 multiple times will further dehydrate material and will further reduce particle size. In municipal waste applications, multiple cycles through the system 100 may be required to achieve the desired dehydration results. The present invention contemplates the use of multiple systems 100 in series to provide multiple Venturis 18 and multiple pulverization events. Thus, a single cycle through multiple systems 100 in series achieves the desired results. Alternatively, material may be processed and reprocessed by the same system 100 until the desired particle size and dryness is achieved. In one implementation, the resulting product issuing from a system 100 is analyzed to determine the size of the powder granules and/or the moisture percentage. If the product fails to meet a threshold value for size and/or water percentage the product is directed through one or more cycles until the product meets the desired parameters. The present invention allows homogenization of different materials. In operation different materials enter the inlet tube 12 together, are processed through the venturi 18, and undergo pulverization. The resulting product is blended and homogenized as well as being dehydrated and reduced in size. A particular application of the present invention involves the homogenization of landfill product with coal. After pulverization and water extraction, the combined and homogenized waste and coal product is used in a coal burner to achieve optimum burning rates for creating steam in an electrical generation plant. The waste is used for energy production rather than for routine disposal. If desired, the material may be mixed in the blender 102 prior to pulverization or at an intermediate stage between pulverization events. Mixing materials may enhance homogenization with certain materials. If desired, the material may be mixed in the blender 102 prior to pulverization or at an intermediate stage between pulverization events. Materials blended in a preprocessing stage may be cycled through multiple pulverizing stages to provide the desired homogenization. A first material may be processed through multiple pulverizing stages and then homogenized with a second material. Between pulverizing stages the second material may be blended with the processed material in a preprocessing stage. The first and second materials are then passed through one or more pulverizing stages to produce a homogenized, final product. As an additional example, a first material may cycle through three pulverizing stages. After the third pulverizing stage, a second material may be blended together in a blender 102. Before mixing, the second material may have passed through a venturi 18 for pulverization and reduction to a desired particle size. The first and second materials may then pass together through one or more additional pulverizing stages to provide the desired moisture content, size, and homogenization for industrial use. Referring to Figure 6, a perspective view is shown of a housing 200 that includes a housing outlet 202. The housing 200 encompasses the operational components of an airflow generator 32. The housing 200 is shown with a cut-away section to illustrate the airflow generator 32 within. In order to provide variance in the output flow, a restrictor 204 may be introduced into the housing outlet 202. A restrictor 204 increases the resistance to the airflow and also increases heat. Varying the amount of resistance and airflow is dependent on the material to be processed. A restrictor 204 includes a neck 206 to nest within the housing outlet 202 and a restrictor aperture 208. The restrictor aperture 208 has a cross-section less than that of the housing outlet 202. A restrictor aperture 208 may be rectangular, circular, or have another suitable shape. The neck 206 provides a converging flow path from a cross- section approximating that of the outlet 202 to the final cross-section of the restrictor aperture 208. A number of restrictors 204 with varying aperture sizes may be available to manipulate the output flow and thereby tune the system 100 to suit the material. Referring to Figure 7, a cross-sectional view of an airflow generator 32 within a housing 200 is shown. The airflow generator 32 may not be coaxially aligned within the housing 200. In one implementation, the airflow generator 32 includes a diverter plate 250 that has a cutting edge 252 near the airflow generator 32. The cutting edge 252 of the diverter plate 250 directs pulverized material into the housing outlet 202. The diverter plate 250 is coupled to the interior of the housing 200 and may be coupled to the interior of the housing outlet 202. The diverter plate 250 prevents pulverized material from further rotation within the housing 200. As such, the diverter plate 250 serves as the first separation of pulverized material from air that continues to rotate within the housing 200. Subsequent separation of pulverized material from air is performed by the cyclonei 14. If pulverized materials continue to rotate within the housing 200 the pulverized materials may build up and eventually obstruct the airflow generator 32. The cutting edge 252 varies the airflow volume proceeding through the housing 200. The separation of the cutting edge 252 of the diverter plate 250 from the airflow generator 32 may range from about 20 thousandths of an inch to 100 thousandths of an inch. The position of the diverter plate 250 may also be adjustable to increase or decrease the separation from the airflow generator 32. Adjustment may be required depending on the materials being processed or to manipulate airflow volume. Adjustment may be controlled by the central processor 110 which communicates with an electromechanical or pneumatic device for moving the diverter plate 250. The cutting edge 252 has a bevel that accommodates the shape of the airflow generator 32. Referring to Figure 8, a cross-sectional view of a venturi 18 with an accompanying throat resizer 300 is shown. The throat resizer 300 is a removable component that, when inserted, nests within the throat 28. The throat resizer 300 alters the effective diameter of the throat 28 and increases the air velocity. Variance of the throat diameter is required depending on the material and the desired dehydration and particle reduction. Thus, although the airflow generator 32 may vary the airflow, it is further desirable to manipulate throat diameter of venturi 18. The throat 28 may be configured with a ledge 302 upon which a collar 304 of the throat resizer 300 nests. A crown member 306 is coupled to the collar 304 and conforms to the interior surface of the converging portion 26. The throat resizer 300 includes a sleeve 308 that conforms to the interior surface of the throat 28 and extends within a major portion of the venturi throat length to resize the venturi 18. Referring to Figure 9, an alternative embodiment of a system 400 is shown that incorporates two pulverizing stages 402, 404. Each time material passes through a venturi 18, pulverization occurs, moisture is extracted, and particle reduction occurs. As discussed previously, this process may be repeatedly performed with a single venturi 18 or with multiple Venturis 18 in series until the desired amount of water is extracted and product size is achieved. This process may be continued until nearly 100 percent water extraction is achieved. Although two pulverizing stages are shown with the system 400, one of skill in the art will appreciate that a system may include three, four, five, or more stages. The first pulverizing stage 402 is similar to that previously described in reference to Figures 4 and 5. The first pulverizing stage 402 includes a hopper 22, blender 102, conveyance device 104, flow control valve 106, venturi 18, housing 35 (with an airflow generator 32 within), and an exhaust pipe 112. The system 400 may further include a flow control valve 405 in the exhaust pipe 112 to regulate airflow within. As in the previous embodiments, the exhaust pipe 112 couples to a cyclone 114 to separate the processed product from the air. The system 400 may further include a second cyclone 406 to receive air from the outlet 122 of the first cyclone 114. The second cyclone 406 further separates air from residual particles and delivers the purified air to a condenser 130. A first tank 132 is in communication with the second cyclone 406 to receive condensed liquid from the condenser 130. An outlet 134 provides an exit for air passing from the condenser 130 and the second cyclone 406. A residual hopper 408 is positioned to receive residual particles from the second cyclone 406. Particles separated by the first cyclone 114 are delivered to a hopper 410 using any number of conventional techniques including gravity. Although not shown, particles from both the first and second cyclones 114, 406 may be delivered to the hopper 410. The hopper 410 receives the particles that then undergo the second pulverizing stage 404. The hopper 410 delivers the particles to a second inlet tube 412 that is coupled to a second venturi 414 as with the first pulverizing stage 402. One or more flow valves 416 are located on the second venturi 414 and are in electrical communication with the central processor 110. The flow valves 416 function similar to those previously described and referenced as 111. The second venturi 414 communicates with a second airflow generator (not shown) in a housing 418. The second airflow generator generates a high speed airflow through the venturi 414. The second housing 418 couples to a second exhaust pipe 420 that delivers air and processed material to a third cyclone 422. The second exhaust pipe 420 is inclined at an angle of approximately 25 degrees to approximately 90 degrees relative to the longitudinal axis of the second venturi 414. A second flow control valve 424 is within the second exhaust pipe 420 to regulate airflow within. As with the first flow control valve 404, the second flow control valve 424 is in electrical communication with the central processor 110 for regulation. The third cyclone 422 separates the particles from the air and delivers a product that is delivered to another conveyance device 425. A 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 are deposited in a residual hopper 428. The fourth cyclone 426 delivers air to a second condenser 430 where vapor is condensed into a liquid and received by a second tank 432. An outlet 434 couples to the second condenser 430 to allow air to exit. The system 400 further includes a heat generator 436 to provide heat through the inlet tubes 12, 412 and the Venturis 18, 414 and assist in drying materials. The addition of heat is not required for water extraction and is merely used to further increase the drying potential of the present invention. The heat generator 436 may communicate with the hoppers 22, 438 or with the inlet tubes 12, 412. A heat generator 436 may also be used in a similar manner in the embodiments illustrated in Figures 1 , 2, 4, and 5. In Figure 9, the heat generator 436 is in communication with a first heat control valve 440 to deliver heat to the first hopper 22. The first heat control valve 440 is in electrical communication with the central processor 110 to regulate the heat delivery. Alternatively, the heat control valve 440 may be operated manually. The heat generator 436 is further in communication with a second heat control valve 442 that regulates heat flow to hopper 438. Heating material during the second pulverizing stage 404 may be desired depending on the material or the application. If heating is desired, the hopper 438 receives particles from the first cyclone 114. Otherwise, the material may pass to the hopper 410 as illustrated in Figure 9. The system 400 may include one or more pulverizing stages for further dehydration and particle reduction. The conveyance device 425 may feed back into the blender 102 or the hopper 22 for further cycling of product through the pulverizing stages 402, 404. The second and fourth cyclones 406, 426 provide further purification of air but the added cost may not be justified for certain applications. In certain applications the condensers 130, 430 may be removed or another type of treatment apparatus, such as a filter, be used. Flow control valves may also be introduced or removed throughout the system 400 as warranted and as based on design constraints. Referring to Figure 10 an alternative embodiment of a pulverization and moisture extraction system 450 is shown. The system 450 is similar to that of Figures 4 and 5 and further includes a second cyclone 406 in communication with the first cyclone 114, a residual hopper 408 to collect particles from the second cyclone 406, a condenser 130 in communication with the second cyclone 406, a tank 132 in communication with the condenser 130, and an outlet 134 coupled to the condenser 130. The system 450 further includes a diverter valve 452 coupled to the first cyclone 114. The diverter valve 452 directs particles received from the first cyclone 114 to a first outlet 454 or a second outlet 456. The first outlet 454 is coupled to a collector 458 such as a bag, hopper, tank, or the like. The second outlet 456 is coupled to a recycling tube 460 to introduce the pulverized material through the system 450 again. The recycling tube 460 is coupled at its opposing end to the first end 14. Alternatively, the recycling tube 460 may direct pulverize material into the hopper 22 or directly into the elongated opening 20. In operation, material is pulverized as it passes through the system 450 and is redirected, by control of the diverter valve 452, to pass through the system 450 again for another pulverization event. This may be repeated as desired until a final product results which is then directed by the diverter valve 452 into the collector 458. Referring to Figure 11 , an embodiment of an airflow generator 500 suitable for the present invention is shown. Various metals are suitable for the airflow generator, depending on the material to be processed. For abrasive material, a harder alloy steel may be used. The material selected has to strike a balance between strength and anticipated wear. Casting of the airflow generator 500 is advantageous as fabrication via welding creates inconsistent surfaces and heat effected areas due to heat effected zones. The cast airflow generator 500 may have a variable material thickness to resist rapid structural impacts and accelerated wear resulting from processing various materials. The section thickness and resulting total weight of the airflow generator 500 is directly proportional to the air volume and material flow rate that is to be processed. The airflow generator 500 is received within a housing such as that illustrated in Figure 6. The housing 200 at least partially encircles the airflow generator 500 and preferably completely encircles the airflow generator 500 so that the only egress is the housing outlet 36. The airflow generator 500 may have a close clearance to the housing 200 to generate additional friction and heat. The heat is desired to assist in further drying materials passing through the airflow generator 500 and into the exhaust pipe 112. The airflow generator 500 includes a front plate 502 with a concentrically disposed input aperture 504 to receive incoming materials. The diameter of the input aperture 504 is variable depending on the processed material size and anticipated air volume. A back plate 506 parallels the front plate 502 and includes a concentrically disposed axle aperture 508. As the name suggests, the axle aperture 508 receives and engages an axle or spindle to power rotation. Alternative airflow generators 500 may be used with the present invention and include generators with a single back plate coupled to blades or generators with radially extending blades alone. The back plate 506 may further include bolt apertures 509 that are disposed concentrically around the axle aperture 508. The bolt apertures 509 each receive a corresponding axle bolt (not shown) that are each coupled to an axle. The axle bolts are secured to back plate 506 by nuts or other conventional devices. Although the thickness of the front and back plates 502, 506 may vary considerably, in one design the back plate 506 is approximately 3/8" (8 mm) and the front plate 502 is 3/16" (5 mm). A plurality of blades 510 are disposed between the front and back plates 502, 506 and are coupled to both plates 502, 506. As can be appreciated, the number of blades 510 may vary and depends, in part, on the material to be processed. The thickness of the blades 510 may also vary depending on the material to be processed. In one embodiment, the blades 510 extend through the front and back plates 502, 506 to form blade fins 511 on the exterior face of the front and back plates 502, 506. The blade fins 511 may extend approximately 1/2" (12 mm) from either the front or back plates 502, 506. The blade fins 511 generate a cushion of air between the airflow generator 500 and the interior of the housing 200. The blade fins 511 further act to clean out materials that may enter between the housing 500 and the airflow generator 200. Referring to Figure 12, a cross-sectional view of the axle aperture 508 is shown. The axle aperture 508 receives an axle, shaft, spindle, or other member to rotate the airflow generator 500. The bolt apertures 509 each receive an axle bolt to secure the back plate 506. In this embodiment, an axle transitions from a first diameter, with axle bolts extending, to a second diameter suitable for insertion into the axle aperture 508. The bolt apertures 509 may each provide a well 513 to receive a nut that engages an axle bolt. Referring to Figure 13, a plan view of the interior of the airflow generator 500 is shown with a single blade 510. The single blade 510 is shown to illustrate the unique features of blades 510 incorporated within the airflow generator 500. The remaining blades 510 are similarly embodied. The blade 510 extends from a trailing edge 512 at the perimeter 513 of the back and front plates 502, 506 to a leading edge 514 adjacent the axle aperture 508. The blade 510 includes a wedge portion 516 adjacent the trailing edge 512. The wedge portion 516 has a thicker cross-section to increase pressure and airflow volume. The wedge portion 516 provides increased resistance to wear which is advantageous with some materials. Referring to Figure 14A, a plan view illustrating the wedge portion 516 in greater detail is shown. The shape of the wedge portion 516 affects airflow volume, airflow velocity, and material flow rate through the airflow generator 500. The wedge portion 516 may be altered in the circumferential and longitudinal direction to alter airflow volume, airflow velocity, and material flow rate. Casting techniques advantageously allow variance in three dimensions and allows any number of circumferential and longitudinal profiles in the wedge portion 516. The increased thickness of the wedge portion 516 enhances the life of the airflow generator 500 as this is where the blade 510 typically experiences the most wear. The material used and the hardness of the wedge portion 516 may also differ from the remainder of the blade 510. Referring to Figure 14B, an alternative embodiment of a wedge portion 518 is shown which includes a replaceable wear tip 520. With the airflow generator 500 rotating in a clockwise direction, the replaceable wear tip 520 is subject to the most material contact. Although thickened to increase wear resistance, the wedge portion 518 is subject to more wear than other components of the airflow generator 500 and may wear out sooner. By replacing the replaceable wear tip 520, replacement of the entire airflow generator 500 is deferred. The replaceable wear tip 520 is coupled to the remainder of the wedge portion 518 through any known fastening device including a securing nut and bolt assembly 522. The replaceable wear tip 520 may be a material harder than the remainder of the blade 510. The replaceable wear tip 520 may also be replaced with a replaceable wear tip 520 having a different circumferential and longitudinal profile. In yet another embodiment, the entire wedge portion 518 is replaceable. Referring to Figure 15A, a perspective view of the airflow generator 500 is shown illustrating the wedge portion 516 coupled to the front and back plates 502, 506. The blade fins 511 are further shown extending from the exterior surface of the front and back plates 502, 506. As shown, the wedge portion 516 is substantially thicker than the corresponding blade fins 511. The blade fins 511 are not subject to the same wear as the wedge portion 516 and are not as thick. Referring to Figure 15B a perspective view of the airflow generator 500 is shown with an alternative embodiment of the wedge portion 516. The wedge portion 516 increases its thickness and its circumferential profile as it extends in the longitudinal direction from the front plate 502 to the back plate 506. The wedge portion 516 also increases in thickness as it extends radially towards the perimeter. Pulverized material entering into the airflow generator 500 has a tendency to accumulate proximate to the back plate 506. The longitudinally increasing thickness encourages pulverized material to remain centered between the front and back plates 502, 506 rather than accumulating along the back plate 506. Casting techniques enable production of such a wedge portion 516 as three dimensional variation is possible. The replaceable wear tip 520 may include and define the longitudinally increasing thickness. If another wedge portion 516 shape is desired another replaceable wear tip 520 without a longitudinally increasing thickness or a more pronounced longitudinally increasing thickness may be used. Thus, pulverized material flow direction may be manipulated longitudinally by using wedge portions 516 of different circumferential and longitudinal configurations. Referring again to Figure 13, the blade 510 transitions from a position perpendicular to the back plate 506 to an angled position. The blade 510 transitions as it proceeds from the wedge portion 516 to a location prior to the leading edge 514. The angled position causes the blade 510 to pitch into the direction of the airflow. In the illustrated embodiment, a trailing portion 524 of the blade 510, including the wedge portion 516, extends perpendicular from the back plate 506. The trailing portion 524 may be approximately one fourth to one half of the blade 510 as the blade 510 extends from the trailing edge 512 to the leading edge 514. A leading portion 526 is the remaining amount of the blade 510 from the trailing portion 524 to the leading edge 514. The illustrated leading portion 526 has an angled transition from a perpendicular position relative to the back plate 506 to an angled position. The angled position has an angle that is referred to herein as the attack angle as it allows the leading edge 514 to cut into the incoming airflow. In Figure 13, the final attack angle of the blade 510 at the leading edge 514 is approximately 25 degrees. The transition from a perpendicular position to an angled position may extend over the entire blade 510 or any portion thereof. The attack angle may be selected from a broad range of angles based on anticipated airflow velocity, material flow rate, and material. The angled position may have a range of approximately 20 to 60 degrees. Alternatively, the blade 510 may remain perpendicular along its entire length. The blade 510 may also have an attack angle along its entire length. Although extending along the entire length, the attack angle may still vary as the blade 510 extends from the trailing edge 512 to the leading edge 514. Referring to Figure 16, a profile view of the leading edge 514 is shown. Conventionally, an edge may be relatively straight and proceed on an angle relative to the back plate 506. In one embodiment of the present invention, the leading edge 514 proceeds from the back plate 506 with an outwardly curving portion 528 and then transitions into an inward curve 530. The outwardly curving portion 528 assists in capturing air traveling into the input aperture 504 of the airflow generator 500. The leading edge 514 so profiled is able to cut into air and improve the efficiency of the airflow generator 500. Referring to Figure 17 a cross section of the leading edge 514 taken along section 17-17 is shown. The leading edge 514 has an oval shaped cross-section that assists in slicing into incoming airflow. Referring to Figure 18, a perspective view of the airflow generator 500 is shown without the front plate 502 to illustrate the blades 510. The illustrated embodiment includes nine blades 510 although the number is variable. Each blade 510 includes a wedge portion 516 for added resistance to wear and to increase pressure and airflow. Each blade 510 further transitions from a perpendicular position to an attack angle. The attack angle inclines towards the clockwise position that corresponds to the anticipated rotation of the airflow generator 500. The airflow generator 500 can be operated in the counter-clockwise position and the blades 510 would consequently be inclined in that direction. In operation, the rotating blades 510 generate a high speed airflow ranging from 350 mph or greater and directs air and pulverized material into the input aperture 504. The leading edges 514 of the blades 510 cut into the air and pulverized material and direct both the air and pulverized material into flow paths 532 defined by the blades 510 and extending from the input aperture 504 to the perimeter 513 of the front and back plates 502, 506. The flow paths 532 would have a maximum flow rate for materials passing through. The wedge portions 516 push the air and pulverized material to the housing outlet 202 that is located within the housing 200. Although the airflow generator 500 provides unique features, one of skill in the art will appreciate that any number of devices may be used and are included within the scope of the invention. The present invention provides a pulverizing and dehydrating system that can accommodate various materials and various flow rates. The systems described herein are scalable for the different applications and different sized materials and any specific component dimensions are given only as examples. Thus, a system may be sized as a bench-top model or as a large industrial-sized unit. The systems 10, 100, 400, 450 disclosed herein may be mounted to a ground surface and larger scale embodiments are more likely to be so constructed. Alternatively, a system may be mounted within or on a vehicle such as a truck, trailer, rail car, boat, barge, and so forth. Any vehicle that provides a sufficient planar footprint may be used. Having a mobile system is advantageous in certain applications such as agricultural harvesting, remote site treatments, demonstrations, and so forth. Referring to a Figure 19, a block diagram representing a mobile system 600 is shown. The system 600 includes components previously discussed such as the inlet tube 12, venturi 18, airflow generator 32, housing 35, motor 34, exhaust pipe 112, and first and second cyclones 116, 406. The system 600 may include additional elements such as the blender 102, central processor 110, condenser 130, and so forth. Systems with a plurality of pulverization stages may be mounted on a vehicle in similar manner. The system 600 includes a vehicle genetically represented as 602 and providing a sufficient footprint to support the assembled components. The system 600 further includes a plurality of supports 604 that couple to the vehicle 602 and support any number of assembled components. The system 600 may further include a housing 606 that encompasses components of the system. The housing 606 protects the components and dampens noise during operation. One or more components of the system 600 may be removable to facilitate transportation. For example, the first and second cyclones 116, 406 may extend out of the housing 606 and need to be moved during transportation. The cyclones 116, 406 may be removed entirely or partially dissembled prior to transportation. Similarly a blender 102 may be removable for transportation. The necessity of removing components is based on the size of the system 600, vehicle 602, and other design constraints. The housing 606 may accommodate a control room for a user to operate the system 600. The housing 606 may include windows for viewing the components and access for viewing, operation, repair, and inserting material to be processed. The system 600 may have any number of configurations based on convenience, application, and other design considerations. Referring to Figure 20, a side view of an alternative embodiment 700 of the present invention is shown. The illustrated embodiment 700 is similar to that previously depicted in Figure 4 and also includes an acoustical emission sensor 702 that is coupled to the housing 35. The acoustical emission sensor 702 may be embodied as any number of commercially available products including the acoustical emission monitoring system (AEMS) manufactured by Schmitt Industries, Inc. of Portland, Oregon. In one embodiment, the acoustical emission sensor 702 is a piezo-ceramic sensor capable of monitoring 50 KHz to 950 KHz resonant frequencies. The acoustical emission sensor 702 monitors the high frequency signals generated by material flowing through the inlet tube 12, venturi 18, airflow generator 32, and housing 35. The resonant frequency received by the acoustical emission sensor 702 is indicative of the volumetric flow rate. Changes in the flow rate of material through the system 700 alter the resonant frequency. The acoustical emission sensor 702 is in electrical communication with a sensor controller 703 that receives the resonant frequency and calculates a flow rate. The sensor controller 703 is in electrical communication with the central processor 110 that receives the flow rate and may respond to adjust the flow rate. During normal operation the resonant frequency remains within normal operating parameters. System failure may result when the flow rate exceeds a threshold. Minimum and maximum values may be established for the flow rates during normal operating conditions. If the flow rate is below the minimum value, the flow rate is increased and, likewise, the flow rate is decreased if it exceeds the maximum value. The sensor controller 703 includes a predetermined maximum threshold value for the resonant frequency. The maximum threshold value may be entered by an operator and is based on material to be processed and the constraints of the system 700. The sensor controller 703 may also include a minimum threshold value for performance. If the flow rate exceeds the maximum threshold value, an overload situation is indicated and the sensor controller 703 signals the central processor 110 that the flow rate must be adjusted. Similarly, if the flow rate is below the minimum threshold value, the sensor controller 703 so indicates to the central processor 110. In addition to the flow rate, the acoustical emission sensor 702 receives resonant frequencies that indicate abnormal conditions such as improper balance of the airflow generator 32, dislodged blade 510, or other mechanical failure. An overload situation itself may create a mechanical failure. Such failure may result in significant and even catastrophic damage to the system 700. Mechanical failure may also create flying debris that is a possible danger to an operator. The acoustical emission sensor 702 monitors the resonant frequencies and detects changes indicating failure as it occurs. As soon as an overload situation or failure is indicated, the sensor controller 703 signals the central processor 110 within one millisecond or less. The central processor 110 responds with immediate corrective action. Alternatively, the sensor controller 703 may include visual or audible notification to inform an operator who then responds with manual corrective action. The acoustical emission sensor 702 is shown disposed on a backside 704 of the housing 35. Alternatively, the acoustical emission sensor 702 may be disposed on a frontside 706 of the housing 35 or any other location on the exterior housing surface. The acoustical emission sensor 702 may also be disposed on the venturi 18 or the inlet tube 12. Referring to Figure 21 , a system 800 is shown wherein an acoustical emission sensor 702 is disposed on the diverging portion 30 as well as on the backside 704 of the housing 35. Multiple acoustical emission sensors 702 may be used to improve monitoring of the resonant frequencies. In alternative embodiments, a plurality of acoustical emission sensors 702 may be disposed on the housing 35, venturi 18, and/or inlet tube 12 to monitor the flow rate. A sensor controller 703 is in electrical communication with the acoustical emission sensors 702 to calculate a flow rate. The sensor controller 703 is in electrical communication with the central processor 110 that receives data transfers within one millisecond of the resonant frequency event. If the flow rate approaches an overload condition, the sensor controller 703 signals the central processor 110 to adjust the flow rate. The central processor 110 may adjust the flow rate by partially or completely closing the adjustable flow valves 111. Partial or complete closure of the flow valves 111 increases airflow through the venturi 18 to provide additional force and drive material through the venturi 18 and the airflow generator 32. The central processor 110 may also partially or completely close the flow control valve 106 to reduce material into the system 700. If the resonant frequency indicates a mechanical failure, the central processor 110 may also perform a system shutdown and turn off the motor 34. The sensor controller 703 may also provide a visual or audible response to an operator. Referring to Figure 22, a cross-sectional view of an embodiment of an air generator housing 200 is shown. As previously discussed, the position of the diverter plate 250 may also be adjustable to increase or decrease the separation from the airflow generator 32. The central processor 110 may control the position of the diverter plate 250 by communicating with an actuator device 900 to move the diverter plate 250. The actuator device 900 may be embodied as an electromechanical device, pneumatic device, or other conventional device. The central processor 110 may adjust the flow rate by moving the diverter plate 250 in order to avoid an overload condition. This action may be taken simultaneously with adjustment of the flow valves 111 and/or the flow control valve 106 to increase control of the flow rate. One or more acoustical sensors 702 may also be disposed on systems illustrated in Figures 1 , 2, 9, and 19. Thus, the illustrated system 700 should be considered for exemplary purposes only and not limiting of the present invention. Referring to Figure 23, a perspective view of an alternative embodiment of a system 1000 is shown including the motor 34 and axle 33 adjacent the backside 704 of the housing 35. The motor 34 engages a pulley 1002 that engages the axle 33 to effect high speed rotation of the axle 33. The axle 33, also referred to as a spindle, couples to one or more brackets 1004 to secure the axle 33 and fix its rotation. The brackets 1004 are secured to a mounting plate 1006. The pulley 1002 is shown engaging the axle 33 between two brackets 1004, although the pulley 1002 may engage the axle 33 in other locations as well. The system 1000 further includes an automatic balancer system 1008 that includes a dynamic balancer 1010, a vibration sensor 1012, and a balancer controller 1014. Automatic balancer systems 1008 are easy to mount, highly reliable, fully automatic, and require little operator training. In Figure 23, the balancer 1010 is embodied as an external balancer 1010 although the balancer 1010 may also be embodied as an internal balancer or ring balancer as discussed below. The external balancer 1010 is in electrical communication with a balancer controller 1014 to compensate for unbalance in the axle 33 and the airflow generator 32 as the axle spins at working RPM levels. The balancer controller 1014 includes a processor (not shown) operating an algorithm to control the external balancer 1010. The dynamic compensation reduces the noise and vibration and improves the system's performance and the material flow rate through the airflow generator 32. Dynamic balancing of the airflow generator 32 prevents cavitation and improves the performance of the airflow generator 32. External balancers are commercially available such as those manufactured by Schmitt Industries, Inc. of Portland, Oregon. The external balancer 1010 may receive power through a rotary slip ring power transfer system or through a non-contact power transfer system. In Figure 23, the external balancer 1010 is coupled to a proximate end 1016 of the axle 33. The axle 33 couples at a distal end (not shown) to the airflow generator 32 that is within the housing 35. The external balancer 1010 couples to the axle 33 proximate to the backside 704, also referred to as the pulley side, of the airflow generator 32. In this manner, the external balancer 1010 does not interfere with airflow into the input aperture 508 of the air turbine 32. The external balancer 1010 operates on a principle of mass compensation for axle imbalance. In one embodiment, the external balancer 1010 includes two movable eccentric weights. The external balancer 1010 drives each eccentric weight by micro- electric motors through a precision gear train. Referring to Figure 24A, a diagram is shown illustrating an airflow generator 32 axially aligned with an external balancer 1010. An external balancer 1010 is disposed in a plane remote from a plane in which the airflow generator 32 is disposed, such as in Figure 23. The external balancer 1010 includes weights 1020 shown relative to a position of imbalance 1022. The balancer controller 1014 instructs the external balancer 1010 to reposition the weights 1020 to offset the position of imbalance 1022. This situation is referred to herein as opposite plane balancing, as the weights 1020 in one plane balance a mass, such as the airflow generator 32, in a second plane. Referring to Figure 24B, a dynamic balanced situation is shown with the weights 1020 compensating for the position of imbalance 1022. With opposite plane balancing, the weights 1020 must be in the same semicircle 1024 as the position of imbalance 1022 in order to balance. The semicircle 1024 is defined as having the axle center 1025. The external balancer 1010 is able to maintain precise balance even if the axle 33 is stopped and restarted. Referring to Figure 25A, a diagram is shown illustrating an airflow generator 32 once again aligned with an external balancer 1010. However, in this situation the external balancer 1010 is adjacent the airflow generator 32 and therefore substantially within the same plane. This is referred to herein as same plane balancing. The weights 1020 are shown relative to a position of imbalance 1022 and an unbalanced condition exists. The balancer controller 1014 instructs the external balancer 1010 to reposition the weights 1020 to offset the position of imbalance 1022. Referring to Figure 25B, a dynamic balanced situation is shown with the weights 1020 compensating for the position of imbalance 1022. With same plane balancing, the weights 1020 are disposed in an opposing semicircle 1026 than the position of imbalance 1022 to provide balance. Referring to Figure 26A, a perspective diagram is shown illustrating operation of the opposite plane balancing technique. An external balancer 1010 is coupled to an axle 33 and rotates within a first plane 1030. A mass 1032, such as an airflow generator 32, is coupled to an opposing end of the axle 33 and rotates within a second plane 1034. Accordingly, the external balancer 1010 and mass 1032 are on opposing ends of the axle 33. The weights 1020 within the external balancer 1010 compensate for a position of imbalance 1022 in the mass 1032. The opposite plane balancing technique is applied in the system 1000 of Figure 23 with the mass 1032 being the airflow generator 32. The external balancer 1010 and the airflow generator 32 are mounted on opposing ends of the axle 33 to precisely and dynamically balance the airflow generator 32. The pulley 1002 couples to the axle 33 between the external balancer 1010 and the airflow generator 32 although the pulley 1002 may couple to the axle 33 at other locations as well. The compensating weights 1020 create balance in the same semicircle but in a different plane of the position of imbalance 1022. Referring to Figure 25B, a perspective diagram is shown illustrating operation of the same plane balancing technique. The mass 1032 and external balancer 1010 are disposed adjacent one another so that they are approximately within the same plane 1036. The external balancer 1010 couples to an axle 33 that also couples to the mass 1032. The weights 1020 must be in an opposing semicircle than the position of imbalance 1022 in order to provide balance. The system 1000 shown in Figure 23 can be modified to provide same plane balancing. Referring again to Figure 23, the dynamic balance system 1008 includes the vibration sensor 1012 that accurately monitors vibration levels that indicate imbalance. The sensor 1012 couples to the brackets 1004 or mounting plate 1012 by magnets, stud mounting, or other conventional methods. The vibration sensor 1012 is in electrical communication with a balancer controller 1014, which filters incoming signals by RPM. The balancer controller 1014 is in communication with the external balancer 1010 and drives the weights 1020 in the direction that reduces the amplitude of the vibration signal. When the weights 1020 are positioned so the lowest vibration level is reached, the balance is complete and the dynamic balance system 1008 monitors the vibration levels to assume optimum operations. Referring to Figure 27, a cross-sectional view of an alternative embodiment of a dynamic balancer 1040 is shown. The dynamic balancer 1040 is an internal balancer 1040 that completely or partially nests within a bore of the axle 33. Internal balancers are commercially available such as those manufactured by Schmitt Industries, Inc. of Portland, Oregon. The internal balancer 1040 may include a mounting flange 1042 that bolts to the axle 33 through one or more bolts 1044. Other conventional methods exist for securing the internal balancer 1040 to the axle 33. As with the external balancer 1010, the internal balancer 1040 positions weights to compensate for a position of imbalance in a mass. The internal balancer 1040 may be used with a balance system 1008 shown in Figure 23 and may be used for opposite plane or same plane balancing techniques. Accordingly, the internal balancer 1040 communicates with a balancer controller 1014 to dynamically position the weights. As previously discussed, the balancer controller 1014 communicates with a vibration sensor 1012 to determine a position of imbalance. Referring to Figure 28, a cross-sectional view of one embodiment of compensating weights 1046, 1048 used by the internal balancer 1020 is shown. The compensating weights 1046, 1048 may be embodied as semi-circles and rotate relative to one another in an over and under configuration. As shown, an inner compensating weight 1046 has a thicker cross-section than an outer compensating weight 1048. By precisely positioning the compensating weights 1046, 1048, dynamic balance is achieved. The illustrated compensating weights 1046, 1048 may also be used in an external balancer 1010. Referring to Figure 29, a perspective view of an alternative dynamic balancer 1050 is shown. The dynamic balancer 1050 is a ring balancer 1050 that encircles and couples to an axle 33. Ring balancers are commercially available such as those manufactured by Schmitt Industries, Inc. of Portland, Oregon. As such, the ring balancer 1050 may be disposed at any accessible location along the length of the axle 33. The ring balancer 1050 may be used with a balance system 1008 shown in Figure 23 and may be used for opposite plane or same plane balancing techniques. Referring to Figure 30, a cross-sectional view of one embodiment of a ring balancer 1050 is shown. The ring balancer 1050 includes compensating weights 1052, 1054 that may be disposed axially side-by-side relative to one another. A first compensating weight 1052 may have greater mass than a second compensating weight 1054. Positioning the compensating weights 1052, 1054 creates an overall compensation counterweight to a position of imbalance to achieve dynamic balance. Alternatively, the ring balancer 1050 may incorporate compensating weights similar to those disclosed in the previously described dynamic balancers 1010, 1040. Alternative balancer embodiments are known in the art and can be used. The automatic balancer system 1008 dynamically balances the airflow generator 32 at operational speeds to maintain optimal balance. Balance is maintained after rotation ceases and during subsequent operations. Balancers may couple to the axle 33 on the pulley side to avoid interference with airflow into the airflow generator. The automatic balancer system 1008 eliminates cavitation to improve efficiency and performance of the airflow generator.