Patent Publication Number: US-2023160364-A1

Title: Vertical axis wind turbine

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     This application is a continuation-in-part of and is based upon and claims the priority filing date of the previously filed, copending U.S. Nonprovisional patent application entitled “Vertical Axis Wind Turbine” filed Sep. 3, 2019, Ser. No. 16/559,364, the entire disclosure of which is hereby incorporated herein by reference. 
    
    
     FIELD OF THE INVENTION 
     The present invention relates to the field of wind turbines, and more specifically, to a vertical axis wind turbine and methods of operating vertical axis wind turbines. 
     BACKGROUND 
     Wind energy is a fast-growing renewable resource that will play a factor in reducing the world&#39;s reliance on fossil fuels. The wind industry is growing on a global and national level. The United States Department of Energy (DOE) aims for 20% of the nation&#39;s electricity to be produced from wind by 2030. The DOE also states that “greater use of the nation&#39;s abundant wind resources for electric power generation will help the nation reduce emissions of greenhouse gases and other air pollutants, diversify its energy supply, provide cost-competitive electricity to key regions across the country, and reduce water usage for power generation.” Wind energy is a fast-growing renewable resource that will play a factor in reducing the world&#39;s reliance on fossil fuels. 
     Generally speaking, wind turbines are used to convert the kinetic energy of the wind to power by use of turbine blades rotatably arranged on a drive shaft. The wind exerts a force on the turbine blades, which by rotation of the turbine blades is transformed to a torque about the longitudinal axis of the drive shaft driving the drive shaft. The rotating drive shaft is connected to a generator to produce electrical power or any other form of power medium. 
     Numerous designs of wind turbines have been presented. Generally, these designs fall in two categories, i.e. horizontal axis wind turbines or vertical axis wind turbines. Most common are horizontal axis wind turbines, wherein the turbine blades are arranged in a propeller-like manner about the longitudinal axis of the horizontal drive shaft forming a rotor, which is placed at the top of a tower structure. The rotor has to be pointed in the direction of the wind. Usually, the generator and/or a gearbox, which converts the rotation speed of the blades to a rotation speed more convenient for power generation, are placed at the top of the tower. Vertical axis wind turbines have turbine blades arranged in a carousel manner about the longitudinal axis of the drive shaft, which is directed perpendicular to the direction of the wind. Usually, the drive shaft is vertical, although the drive shaft also can be placed horizontally. 
     Moreover, the horizontal axis wind turbine has the highest coefficient of performance currently available and operates by producing lift. Lift is a force that is perpendicular to the fluid motion on the airfoil. In order for the turbine blade to rotate faster, the wind lift force must exceed the drag force. The drag force is parallel to the relative velocity and is present throughout the whole circle of rotation. Lift force, however, is only present when there is a low-pressure zone on one side of the airfoil. This means that there are zones in a full revolution where no lift is produced. 
     The main issue with horizontal wind turbines are the cost and the fact that the power generator and other electrical equipment are located generally at the top of a tower. This makes maintenance difficult, so the operation and maintenance costs of new turbines are 20-25% of the annual profit. Turbine maintenance can take 1 to 7 days of downtime for each repair depending on the part that needs to be replaced. In addition to downtime required for maintenance, the structure that supports the turbine needs to be sturdy enough to hold up the heavy generator equipment as well. For example, a structure of a small turbine that is only eighty feet tall accounts for approximately 30 percent of the total system cost. 
     For the foregoing reasons, there is a need for a wind-powered turbine that can be maintained at a low cost while producing more power than a traditional horizontal wind turbine which provides superior airflow and lift characteristics. 
     SUMMARY 
     In accordance with the invention, a vertical axis wind turbine is provided which efficiently powers a generator for providing electricity, particularly electric to be supplied to a power grid for conducting electrical energy or for storage in high capacity batteries for future use thereof. The vertical axis wind turbine comprises a blade angle adjustment mechanism which precisely and simultaneously adjusts the angle of attack of each of the plurality of blades through a cyclical path of rotation based on the relative wind direction as observed by a wind vane assembly. The angle of attack of each blade throughout the cyclical path of rotation is configured to provide the maximum amount of lift. 
     In certain versions of the application, the wind vane assembly may further comprise a brake release assembly for rotationally locking the wind vane assembly while wind velocity and direction remain unchanged. The brake release assembly is configured to unlock the wind vane assembly, allowing it to rotate, when changes in wind velocity and direction reach a certain threshold, thereby allowing the wind vane assembly to move and relock into a new position based on the currently observed relative wind direction. 
     These and other features of the present invention will become readily apparent upon further review of the following specification and drawings. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       These and other features, aspects, and advantages of the present invention will become better understood with regard to the following description and accompanying figures where: 
         FIG.  1    is a front perspective view of a version of the vertical axis wind turbine; 
         FIG.  2    is a front elevation view of the version shown in  FIG.  1   ; 
         FIG.  3    is a rear elevation view of the version shown in  FIG.  1   ; 
         FIG.  4    is a left side elevation view of the version shown in  FIG.  1   ; 
         FIG.  5    is a right side elevation view of the version show in  FIG.  1   ; 
         FIG.  6    is a top plan view of the version shown in  FIG.  1   ; 
         FIG.  7    is an up-close cross-sectional view taken at Detail “A” in  FIG.  5    of the version shown in  FIG.  1   ; 
         FIG.  8    is an up-close cross-sectional view taken at Detail “B” in  FIG.  5    of the version shown in  FIG.  1   ; 
         FIG.  9    is an exploded perspective view of the version shown in  FIG.  1   ; 
         FIG.  10    is a partially unassembled view of the rotor assembly of the version shown in  FIG.  1   ; 
         FIG.  11    is an unassembled view of the of the support framework of the version shown in  FIG.  1   ; 
         FIG.  12    is an unassembled view of the support framework and fixed central spindle of the version shown in  FIG.  1   ; 
         FIG.  13    is a top plan view of the version shown in  FIG.  1   ; 
         FIG.  14    is an up-close detailed view of the pivot connection assembly taken at Detail “C” in  FIG.  13   ; 
         FIG.  15    is a front perspective view of a second example version of the rotor assembly having multiple tiers of radially positioned blades; 
         FIG.  16    is a perspective view of a third version of an arm assembly and blade having multiple tiers of blades; 
         FIG.  17    is a front perspective view of a fourth version of the vertical axis wind turbine showing multiple tiers of radially spaced blades; 
         FIG.  18    is an illustrative example of a version of the vertical axis wind turbine operably coupled to a housing structure; 
         FIG.  19    is a perspective view of a second version of the wind vane assembly; 
         FIG.  20    is a bottom perspective view of the wind vane assembly shown in  FIG.  19   ; 
         FIG.  21    is a left side elevation view of the wind vane assembly shown in  FIG.  19   ; 
         FIG.  22    is a right side elevation view of the wind vane assembly shown in  FIG.  19   ; 
         FIG.  23    is a front side elevation view of the wind vane assembly shown in  FIG.  19   ; 
         FIG.  24    is a rear side elevation view of the wind vane assembly shown in  FIG.  19   ; 
         FIG.  25    is a top plan view of the wind vane assembly shown in  FIG.  19   ; 
         FIG.  26    is a bottom plan view of the wind vane assembly shown in  FIG.  19   ; 
         FIG.  27    is an exploded view of the wind vane assembly shown in  FIG.  19   ; 
         FIG.  28    is a sectional view taken along Section A-A of  FIG.  22   ; 
         FIG.  29    is a sectional view taken along Section B-B of  FIG.  22   ; 
         FIG.  30   a    is a detailed view of the vertical stabilizer of the version shown in  FIG.  19   ; 
         FIG.  30   b    is a detailed view of the vertical stabilizer of the version shown in  FIG.  19   ; 
         FIG.  31   a    is a top plan view of the brake release assembly of the version shown in  FIG.  19   ; 
         FIG.  31   b    is a top plan view of the brake release assembly of the version shown in  FIG.  19   ; 
         FIG.  32    is an up-close view taken at Detail “C” in  FIG.  31   a    of the version shown in  FIG.  19   ; 
         FIG.  33    is an up-close view taken at Detail “D” in  FIG.  31   b    of the version shown in  FIG.  19   ; 
         FIG.  34    is an up-close view of the rudder and hinge of the version shown in  FIG.  19   ; 
         FIG.  35    is a front elevation view of a guide roller of the version shown in  FIG.  19   ; 
         FIG.  36    is a perspective view of the brake release assembly of the version shown in  FIG.  19   ; and 
         FIG.  37    is a perspective view of a version of the vertical axis wind turbine utilizing the wind vane assembly of the version shown in  FIG.  19   . 
     
    
    
     DETAILED DESCRIPTION 
     In the following description, for purposes of explanation and not limitation, specific details are set forth such as particular architectures, interfaces, techniques, etc. in order to provide a thorough understanding of the present invention. However, it will be apparent to those skilled in the art that the present invention may be practiced in other versions that depart from these specific details. In other instances, detailed descriptions of well-known devices and methods are omitted so as not to obscure the description of the present invention with unnecessary detail. 
     The following detailed description is of the best currently contemplated modes of carrying out exemplary versions of the invention. The description is not to be taken in the limiting sense, but is made merely for the purpose illustrating the general principles of the invention, since the scope of the invention is best defined by the appended claims. Various inventive features are described below that can each be used independently of one another or in combination with other features. 
     Referring now to the figures wherein the showings are for purposes of illustrating a preferred version of the invention only and not for purposes of limiting the same, the present application discloses a vertical axis wind turbine which efficiently powers a generator for providing electricity, particularly electric to be supplied to a power grid for conducting electrical energy or for storage in high capacity batteries for future use thereof. 
     Referring generally to  FIG.  1   —  FIG.  6   , in a version of the application the wind turbine  10  and system generally comprises a rotor assembly  12  having a plurality of blades  36 , a fixed central spindle  14  having a central axis Y for supporting rotation of the rotor assembly  12 , a blade angle adjustment mechanism  15  for adjusting the blade angle of attack throughout rotation of the rotor assembly  12 , and a support framework  16  for supporting the rotor assembly  12  at an elevated position in order to gain access to a sustained source of wind. The wind turbine  10  may be operably coupled with a power electric generator  18  or other device which transfers mechanical energy into electrical energy as a combined system. 
     Generally speaking, the blade angle adjustment mechanism  15  is a fully mechanically and autonomously driven and is configured to change the blade rotating angle or relating angle of attack of each blade  36  at each point through the relative circular motion of the turbine  10  depending on wind direction. In other terms, each of the blades  36  are responsive to rotation throughout the cyclical path of the rotor assembly  12  to vary the blade angle of attack with respect to the direction of the wind impinging on the rotor assembly  12 , without the need of motors, such as a stepper motor. Preferably, each blade  36  angle of attack changes relative to the instant relative wind direction RW ( FIG.  3   ) and is operably configured to provide the maximum instantaneous rotational force applied about the central axis Y causing the rotor assembly to move throughout a cyclical path of motion. 
     In the illustrated version, the electric generator  18  is ideally positioned below the rotor assembly  12  within the support framework  16  in an upright disposition (See  FIG.  1    and  FIG.  9   ). The electric generator  18  can be of any type which converts rotational mechanical energy generated from the wind turbine  10  into electrical energy. For example, a parallel shaft direct current DC gearmotor may be utilized in conjunction with a drive shaft  20  having one or more gears  22  which operate to transfer power from the rotation of the rotor assembly  12  to the drive shaft  20  of the electric generator  18 . 
     With reference to  FIG.  9   - FIG.  12   , the support framework  16  can be constructed in any manner which operably and safely supports the rotor assembly  12  and fixed central spindle  14  among other parts in a vertical operating position. Ideally, the height of the support framework  16  is sufficiently elevated to position the rotor assembly  12  such that it is subjected to a sustained airflow. For example, the support framework  16  may ideally position the rotor assembly  12  a few feet above the respective ground or thousands of feet in the atmosphere in order to gain access to sustained, high-velocity winds. 
     Other variations may be tailored to position the rotor assembly  12  above the roof line of housing or other man-made structures.  FIG.  18    illustrates an example support framework  16  which is operably coupled with a home structure  200  roof  202  which places the rotor assembly  12  above the roof line of the home  200 , which may be operably configured to provide electrical energy for the illustrated home  200  or building structure provided by the electric generator  18 . 
     Ideally, the support framework  16  is constructed of a combination of woven cables  25  and angle iron  26  which form a rectangular frame having a low coefficient of drag, thereby allowing airflow efficiently pass through the structure (See  FIG.  9   ). In the version, the support framework  16  includes a base platform  28  and an elevated platform  30  positioned there above. The base platform  28  provides support for the electrical generator  18 . Preferably, the generator  18  is positioned a sufficient distance from the rotor assembly  12  and other moving parts—mitigating the likelihood of a collision occurring between moving parts and the generator  18  and providing sufficient area for the generator  18  to dissipate heat during operation. 
     As best illustrated in  FIG.  11   , the base platform  28  further provides a seating coupler  32  for receiving and positioning the fixed central spindle  14  in a vertical direction. Moreover, the elevated platform  30  provides a cylindrical hole  34  which allows and contains the fixed central spindle  14  for passing vertically therethrough. 
     Now referring to the figures, particularly  FIG.  1   , the rotor assembly  12  is constructed to freely rotate about the fixed central spindle  14  and central axis Y through a cylindrical path of rotation. The rotor assembly  12  generally comprises a plurality of blades  36  or airfoils which create lift thereby imparting motion to the rotor assembly  12  and in turn provides motive force to the drive shaft  20  of the electric generator  18 . 
     As best illustrated by  FIG.  6    and  FIG.  9   , the rotor assembly  12  is generally configured in a hub and spoke formation—each blade  36  positioned radially from the hub assembly  38  by way of respective arm assemblies  40 . In the illustrated version, the hub assembly  38  comprises a lower hub  42  and an upper hub  44 . Each hub  42 ,  44  is shaped in the form of a circular platform including axially aligned holes  43 ,  45  for receipt of the fixed central spindle  14  resembling the shape of a washer. The hub assembly  38  generally provides radial structural support platform for each arm assemblies  40  to attach with by way of hardware. 
     Referring to  FIG.  10   , the arm assemblies  40  each provide lateral radial positioning and support for each blade  36 . In the version, each arm assembly  40  comprises a lower cantilever arm  46  and an upper cantilever arm  48  positioned parallel above and below each other respectively—each fixedly attached to and extending outward from their respective lower and upper hubs  42 ,  44  forming the radial support of each blade  36 . In the version, as best illustrated by  FIG.  6   , the lower and upper cantilever arms  46 ,  48  are slightly offset when viewed from the plan perspective for operational purposes further described in detail below. 
     As illustrated in DETAIL C of  FIG.  14   , each arm assemblies further includes an angled support lever  60  positioned at the distal end of each of the upper cantilever arms  48 —operably extending to support and rotatably attached to the upper portion of the blade  36  at the blade axis Z. Thus, the lower cantilever arm  46  distal end and the angled support lever  60  provide rotatable axial support of each blade  36  therebetween wherein blade axis Z passes therethrough. 
     Each of the plurality of blades  36  is equally spaced and vertically disposed about the hub assembly  38  at the distal end of the respective arm assembly  40 . Preferably, there are a total of six blades  36  and respective arm assemblies  40 ; however, other variations are certainly considered. Each blade  36  has a vertical blade axis Z of rotation allowing the blade  36  to pivot relative to the arm assembly  40  as the rotor assembly  12  moves through the operable cyclical path of motion. 
     Preferably, as best depicted in  FIG.  10   , generally, each blade  36  is an airfoil having an inner surface  50 , outer surface  52 , leading edge  54 , trailing edge  56 , and a chord line  58  formed between the leading and trailing edges  54 ,  56 . The camber of each blade  36 , which is the asymmetry between the upper and lower surfaces  50 ,  52  can vary depending on the application. Moreover, the blade  36  can be symmetrical between the upper and lower surfaces  50 ,  52  providing an airfoil with no camber as illustrated in the figures. 
     As best illustrated by  FIG.  9   , the wind turbine  10  further comprises the drive gear  24  which is affixed to the bottom of the hub assembly  38  and operably positioned to rotate about the central axis Y in conjunction the operation of the rotor assembly  12 . As depicted in  FIG.  1   , the drive gear  24  is coupled to cooperate with the generator gear  22  located at the end of the drive shaft  20  of the generator  18 . Thus, as the rotor assembly  12  moves through the cyclical path of motion, the rotation of the drive gear  24  provides rotational energy to the drive shaft via the generator gear  22 . Ideally, the gear ratio between the generator gear  22  and the drive gear  24  is 12:1. 
     In the illustrated version best illustrated by  FIG.  5    and  FIG.  8   , the rotor assembly  12  may further include a rotor bearing  62  or angular bearing for supporting and providing rotation of the rotor assembly  12  throughout its cyclical path of motion. In the version, the rotor bearing  62  is positioned at the bottom of the rotor assembly  12  and operably attached to the top surface of the elevated platform  30  of the support frame  16 . The rotor bearing  62  generally comprises an outer race  66 , and inner race  68 , a cage retainer  70 , a plurality of balls  72 , and lubricant  74  (See  FIG.  8   ). The outer race  66  fixedly attached to the elevated platform  30  and the inner race  68  operably affixed to the rotor assembly  12 . Thus, the rotor assembly  12  is rotatably supported by the platform  30  and rotor bearing  62  throughout the path of rotation. Ideally, the rotor bearing  62  is a thrust bearing which permits rotation between parts but are designed to support a predominantly axial load. 
     Now with reference to  FIG.  1   - FIG.  9   , the vertical axis wind turbine  10  further comprises a blade angle adjustment mechanism  15 —which generally functions to control the angle of attack of each blade based on the wind direction and radial position throughout the rotor assembly  12  cyclical path of motion. The angle of attack is defined as is the angle between the chord line of the airfoil and the vector representing the relative motion between the body and the fluid (airflow) through which it is moving. For example, when the blade  36  rotates at different points throughout the rotor assembly  12  cyclical path of rotation, the blade&#39;s  36  angle of attack is automatically adjusted for any position relative to the wind direction for ideal lift and drag characteristics. The preferable angle of attack at each position throughout the rotational path is relatively based on the blade rotating angle which is set between the blade&#39;s  36  chord line and the radius that extends from the central axis Y. See U.S. Pat. No. 7,780,411 and U.S. patent application 2017/0051720 for further clarification. 
     In the illustrated version, the blade angle adjustment mechanism  15  generally comprises a rotationally independent wind vane  78 , a cam  80  operably affixed below the wind vane  78  having a rotational axis R which is axially aligned with the central axis Y, and a plurality of pushrods  82  operable between the cam  80  and the respective blades  36 . 
     As best illustrated by  FIG.  13   , the cam  80  is rotatably positioned about the central axis Y above the upper hub  44  of the rotor assembly  12 . The cam  80  is freely rotatable about the central axis Y and is independent of the rotation of the rotor assembly  12  by way of a cam bearing  84  (See  FIG.  7   ). Specifically, the bearing  84  provides support and rotation of the wind vane  78  and cam  80  throughout a circular path of motion. In the version the bearing  84  operably couples the cam  80  with the distal end of the fixed central spindle  14 . The bearing  84  generally comprises an outer race  86 , an inner race  88 , a cage retainer  90 , a plurality of balls  92 , and lubricant  94 . The outer race  86  fixedly attached to the distal end of the central spindle  14  and the inner race  88  operably affixed to the cam  80  and wind vane  78 . Thus, the cam  80  and wind vane  78  are rotatably supported by the fixed central spindle  14  bearing  84  throughout the path of rotation thereof. The cam bearing  84  is ideally a rotor or angular type bearing. 
       FIG.  10    and  FIG.  13    show a perspective view and a top plan view of the vertical wind turbine  10  and more specifically illustrates how each pushrod  82  connects between the cam  80  and the respective blade  36  via upper cantilever arm  48 . Generally, the pushrod  82  is an elongated linear rod having a proximal end  96  extending away from the central axis Y and—in the version—encased within the respective upper cantilever arm  48  terminating at a distal end  98 . The upper cantilever arm  48  provides dual purposes—supporting for the respective blade  36  and functions as a sleeve for the respective pushrod  82  contained therein. 
     The cam  80  provides an interior track  100  which is disposed in and follows the outer contoured perimeter of the cam  80  perimeter  102 . Positioned at the proximal end  96  of each pushrod  82  is a cam follower  104  which is operably configured to follow the interior track  100  of the cam  80  throughout the rotational path of the rotor assembly  12 . Further, as depicted in  FIG.  14   , the distal end  98  of the pushrod  82  provides a pivot connection assembly  105 . In the version, the pivot connection assembly  105  comprises a linear rack gear  106  which operably engages with a pinion gear  109  which is positioned atop the respective blade  36  configured to impart rotation thereto about the blade axis Z. Thus, generally, as the rotor assembly  12  moves through its cyclical path of motion, the cam followers  104  move through the interior track  100 , thereby moving each pushrod  82  either radially outward or radially inward along their linear path of motion based on the contoured perimeter of the cam  80  and distance the cam follower  104  is with respect to the rotational axis R of the cam  80  (See  FIG.  13   ). Preferably, the interior track  100  is used as opposed to other cam designs to assist with balancing the push and pull effect of each of the pushrods  82  throughout the irregular path of the interior track  100 . Thus, throughout rotation, a portion of the pushrods  82  are actively pulled towards the central axis Y by the interior track  100  while the remaining portion of the pushrods  82  are being actively pushed away from the central axis Y. Thus, significantly reducing the net force applied about the cam  80  throughout operation. 
     As discussed above and referring to  FIG.  3   , the wind vane  78  is affixed above the cam  80 , wherein the wind vane  78  and the cam  80  rotate together about the central axis Y freely depending on the direction of the impinging relative wind RW. The wind vane  78  is vertically disposed and is operably configured to gravitate into the wind determining wind direction. In the version, the wind vane  78  is a thin triangular shaped structure having a heightened rear portion  108  which tapers downward to a front point  110 , wherein as airflow is introduced to the wind vane  78 , the thin triangular profile causes the front point  110  to align and point in the opposite direction of the relative wind RW. Generally speaking, the wind vane  78  can range in size from having a small profile for smaller, low velocity wind applications and larger profiles for larger, high velocity wind applications. 
     With reference to  FIG.  19   - FIG.  37   , an alternative embodiment of the wind vane assembly  300  is disclosed which includes a brake release assembly  400 . The purpose of the brake release assembly  400  is to lock the wind vane assembly  300  in a default, brake engaged position during operation. However, if the relative wind RW direction changes providing a rotational force to the vane assembly  300 , the brake release assembly acts to release the brake allowing the wind vane assembly  300  to rotate into the relative wind RW. In other terms, the brake release assembly  400  provides a means to maintain the wind vane assembly  300  in a constant direction even in view of minimal changes in wind direction; however, when a sustained relative wind RW direction changes exceeding a certain velocity threshold, the brake releases thereby allowing the wind vane assembly  300  to rotate until aligned with the new relative wind RW direction. 
     Generally, as best shown in  FIG.  19   - FIG.  27   , a version of the wind vane assembly  300  generally comprises a cylindrical base plate  304  for supporting rotation about the fixed central spindle  14  via a central aperture  306 , and a horizontal support beam  308  in the form of an elongated rod fixedly attached to the cylindrical base plate  304  and having a forward end  310  and an aft end  312 . The horizontal support beam  308  aft end  312  supports a vertical stabilizer  314  and a rudder  316  positioned aft of and vertically hinged to the vertical stabilizer  314 . The forward end  310  of the horizontal support beam  308  provides support for a balance counterweight  318  in order to counter the weight of the vertical stabilizer  314  and the rudder  316  positioned on the aft end  312 . 
     With reference to  FIG.  27    illustrating an exploded view of the wind vane assembly  300 , a brake housing assembly  320  is provided which generally encapsulates the brake mechanism and central spindle  14  while supporting the horizontal support beam  308  and wind vane assembly  300  above the brake release assembly  302 . In the version, the brake housing assembly  320  comprises a table  322  having a circular top  324  and, preferably, four equally spaced legs  326  provide a height and affixed to the top surface  328  of the cylindrical base plate  304 ; and a cap  330  which is configured to attach over and affix to the circular top  324 . The horizontal support beam  308  is generally affixed to the top of the riser cap  330  at a fulcrum point f, thereby balancing the aft end  312  supported components with the forward end  310  balance counterweight  318  which provides 360 degrees of rotation about the fixed central spindle  14 . 
     In the version, the vertical stabilizer  314  is vertically affixed to the aft end  312  of the horizontal support beam  308 . The vertical stabilizer  314  has a bottom edge  332 , a trailing edge  334 , and a leading edge  336 . In the illustrated version, the leading edge is curved in nature connecting the bottom edge  332  and the trailing edge  334 . The bottom edge  332  of the vertical stabilizer  314  is longitudinally aligned with the longitudinal axis Z of the aft end  312  of the horizontal support beam  308 . The trailing edge  334  is generally perpendicular or angled aftward as compared to bottom edge  332  and the longitudinal axis Z of the horizontal support beam  308  (See  FIG.  22   ). 
     The rudder  316  generally includes a leading edge  338  parallel to the vertical stabilizer trailing edge  334 , a bottom edge  342 , and a rear trailing edge  340 . In the illustrated version, the rear trailing edge  340  is curved connecting the leading edge  338  with the bottom edge  342 . 
     The rudder  316  is rotatably connected to the trailing edge  334  of the vertical stabilizer  314  via a hinge  344 . In the version, the hinge  344  includes a forward hinge plate  346  attached to a length along the trailing edge  334  of the vertical stabilizer  314  and an aft hinge plate  348  attached to the leading edge  338  of the rudder  316 . The vertical stabilizer  314  is fixed in position relative to the horizontal support beam  308  and the rudder  316  is operably configured to rotate about the hinge axis Y through an angular path of motion, thereby providing a rotational force about the central axis R and central spindle  14  depending on shift in wind velocity and direction. [Ratio of surface area here]. 
     Generally, a balance counterweight  318  is affixed to the forward end  310  of the horizontal support beam  308  in order to counter the weight of the aft end  312  components including the vertical stabilizer  314 , rudder  316 , and hinge  344 . 
     As best shown in  FIG.  27   - FIG.  37   , the brake release assembly  400  generally comprises a brake release member  402 , a linear rod  404 , a concentric band  406 , and a first and second lever assemblies  410   a ,  410   b . Collectively, the brake release assembly  400  components counter rotational forces applied to the wind vane assembly  300  due to abrupt changes in wind velocity and direction which will be described in more detail below. Therefore, during these events, slowing down the angular velocity providing a more stable wind vane assembly  300  throughout operation and wind changes. 
     As best shown in  FIG.  19    and  FIG.  20   , the linear rod  404  is configured to be translatable within a longitudinal path between a translated forward, default brake engagement position  FIG.  31   a    and a translated rearward, brake released position  FIG.  31   b   . The linear rod  404  has a length between a proximal end  412  and a distal end  414  and is positioned beneath and in parallel in relation to the horizontal support beam  308 . 
     As best shown in  FIG.  34    and  FIG.  35   , the linear rod  404  translatable path between the default brake engaged position and the brake released position is supported and provided by a forward guide roller  416  and a rear guide roller  418 . The rear guide roller  418  is affixed beneath the horizontal support beam  308  aft end  312  and the forward guide roller  416  is affixed beneath the horizontal support beam  308  aft and near the cylindrical base plate  304 . During operation, the brake engaged position is achieved by translating the linear rod  404  outward within the rear guide roller  418  and the forward guide roller  416 , thereby actuating the concentric band  406 , slowing and locking the wind vane assembly  300 . In the illustrated version of  FIG.  35   , each guide roller  416 ,  418  comprises a plurality of rollers including two parallel vertical axis rollers  420  and a bottom horizontal roller  422 . 
     As best shown in  FIG.  27   , the linear rod  404  distal end  414  terminates at a plate  424  providing a flat contact surface  426  which is perpendicular to its longitudinal path of the linear rod  404 . The proximal end  412  of the linear rod  404  terminates at a junction member  428  for operably connecting to the first and second lever assemblies  410   a ,  410   b.    
     As best shown in  FIG.  31   a    and  FIG.  31   b   , the brake release assembly  400  includes a concentric band  406  adapted to radially clutch the fixed central spindle  14  while in the default, brake engaged position. In the version, the concentric band  406  is positioned such that it partially encircles about the fixed central spindle  14  terminating at opposing first and second ends  430 ,  432 . The first and second ends  430 ,  432  form a gap  434  therebetween which allows the concentric band  406  to expand and contract about the fixed central spindle  14  throughout operation. 
       FIG.  31   a    and  FIG.  31   b    provide up-close top plan views showing the brake assembly while in the default brake engaged position ( FIG.  31   a   ) and the brake released position ( FIG.  31   b   ). Further, the brake release assembly  400  comprises a series of levers that are operably configured to engage or release the braking by pinching or expanding the concentric band  406 . For example, while in the default, brake engaged position, the biasing spring  438  provides an inward force when compressed to the linear rod  404  which causes the series of levers to translate outward and away from the central spindle  14  moving the first and second ends  430 ,  432  of the concentric band  406 , thereby releasing the concentric band  406  from clutching and contacting the central spindle  14 . Oppositely, in order to release the brake, the series of levers  408  translate the outward motion of the linear rod  404  into rotational forces applied to the first and second ends  430 ,  432  of the concentric band  406 , thereby causing the concentric band  406  to radially disengage contact with the fixed central spindle  14  during operation, thereby allowing the wind vane assembly  300  to rotate about the central spindle  14 . 
     As best shown in  FIG.  31   a    and  FIG.  31   b   , the series of levers  408  comprise mirrored first and second lever assemblies  410   a ,  410   b  which operably rotate about opposing first and second hinged axis points  440   a ,  440   b  affixed to the cylindrical base plate  304 . Preferably, the hinged axis points  440   a ,  440   b  are positioned at opposing sides of the central aperture  306  and affixed with the top surface  328  of the cylindrical base plate  304 . Generally, each of the first and second lever assemblies  410   a ,  410   b  comprise a primary rotatable member  442   a ,  442   b , a drive member  444   a ,  444   b , and a tension member  446   a ,  446   b  which operably combine to translate the forward, biased movement of the linear rod  404  into a squeezing or pinching action of the concentric band  406  in order to engage the central spindle  14  while in the default brake engaged position. 
     Each primary rotatable member  442   a ,  442   b  is rotatable about the respective fixed axis point  440   a ,  440   b  having an interior arm  448  and an exterior arm  450  extending outward at an angle. The interior arm  448  terminates at an interior rotatable hinge point  452  and the exterior arm  450  terminates at an exterior rotatable hinge point  454 . Further, each drive member  444   a ,  444   b  in the form of a rod has a length, a first end  456  and a second end  458 . The first end  456  is operably hinged with the exterior arm  450  of the primary rotatable member  442  at the exterior rotatable hinge point  454 . The second end  458  is operably hinged with the junction member  428  of the linear rod  404 . 
     The tension members  446   a ,  446   b  each are generally a shortened rod having a length, an interior end  460  and an exterior end  462  and is for connecting the interior arm  448  of the primary rotatable member  442  with the respective first and second ends  430 ,  432  of the concentric band  406 . The exterior end  462  of the tension member  446  is hingedly connected to the primary rotatable member  442  interior arm  448  interior rotatable hinge point  452 . The interior end  460  of the tension member  446  is hingedly connected to the respective first and second ends  430 ,  432  of the concentric band  406 . 
     As shown, a biasing spring  438  or other elastic means is operably connected between the junction member  428  to a fixed point  464  on the cylindrical base plate  304  which during operation biases the and brake release assembly  400  and linear rod  404  in the default, brake engaged position. Therefore, when the wind direction and velocity remain unchanged, the brake release assembly  400  maintains the wind vane assembly  300  in a static manner respective of the central spindle  14 . 
     Lastly, the brake release assembly  400  further comprises a brake release member  402  which is operably attached to the rudder  316  extending laterally. The brake release member  402  is configured to rotate with the rudder  316  in either the clockwise or counterclockwise direction about the rudder hinge axis Y. When the rudder  316  rotates during a change in wind velocity or direction, the brake release member  402  actively contacts the linear rod  404  distal end  414  plate  424  moving the linear rod  404  rearward. Thus, as the direction of the wind changes, the rudder  316  rotates due to the application of force (See  FIG.  30   b   ) about the hinge axis Y between the vertical stabilizer  314  and the rudder  316 , whereby the brake release member  402  is rotated forward and pushes the linear rod  404  inward which actuates the first and second lever assemblies  410   a ,  410   b  to cause the concentric band  406  to release the fixed central spindle  14 , thereby allowing the wind vane assembly  300  to rotate about the fixed central spindle  14  in accordance with the direction of the relative wind RW. In the version, the brake release member  402  is a horizontal flat member having a triangular plan view having a free edge  468  terminating at lateral contact points  470 ,  472  (see  FIG.  30   a   ). 
     Generally, the vertical axis wind turbine  10  does not require any form of energy aside from wind energy to operate. In order to initiate rotation of the rotor assembly  12 , the vertical axis wind turbine  10  is exposed to wind or other airflow typically provided at a perpendicular direction relative to the central axis Y. As described above, the wind vane  78  automatically moves and aligns itself with the direction of the relative wind RW. Therefore, as the wind vane  78  rotates, the cam  80  affixed therewith rotates which positions the shaped interior track in the ideal arrangement which will simultaneously position each blade  36  angle of attack or attitude to maximize lift and rotational force about the central axis Y. Thus, as the direction of the relative wind changes, the cam  80  and interior track  100  autonomously adjust via the wind vane  78  to accommodate and facilitate the maximum amount of rotational force. By way of the drive gear  24 , the rotational mechanical energy is transferred to the electric generator  18  via the generator gear  22  and drive shaft  20 . Thereafter, the electrical energy generated by the generator  18  can be supplied to an existing electrical grid or be store by way of batteries. 
     As it relates to the brake release assembly  302 , the generally purpose of operation is by default to lock and prevent the wind vane assembly  300  from rotating about the central axis  14 . However, when the relative wind changes providing enough rotational force upon the rudder  316 , the brake release assembly  400  releases the concentric band  406  from clutching the central spindle  14 . In further detail, upon change in the relative wind RW, the rudder  316  rotates about the rudder  316  hinge axis Y causing the brake release member  402  to contact and move rearward the linear rod  404  by way of the plate  424  distal end  414 . The rearward movement of the linear rod  404  causes the first and second lever assemblies  410   a ,  410   b  to rotate about the first and second hinged axis points  440   a ,  440   b  while compressing the biasing spring  438 , thereby simultaneously separating or expanding the first and second ends  430 ,  432  of the concentric band  406  releasing the central spindle  14 . 
     Oppositely, when the relative wind RW direction stabilizes, the rudder  316  aligns with the vertical stabilizer  314  thereby removing the application of force of the brake release member  402  returning to a default, neutral position. Thereafter, the biasing spring  438  under compression pushes the linear rod  404  forward which causes the first and second lever assemblies  410   a ,  410   b  to rotate inward, thereby causing the concentric band to radially clutch the fixed central spindle applying a braking action and locking the wind vane assembly in position relative to the central spindle  14 . 
     Now referring specifically to  FIG.  15   - FIG.  17   , a version of the vertical wind turbine  200  may bolster several tiers of radial blade groupings. For example,  FIG.  17    shows the turbine  200  having a first tier plurality of blades  36   a  and an outer second tier plurality of blades  36   b . Providing multiple tier blade groups provides an option to increase the rotational force or thrust about the central axis Y.  FIG.  16    partially illustrates how a third tier plurality of blades  36   c  may be added. 
     Preferably, the construction of the vertical wind turbine  10  is formed by a combination of materials—namely, carbon fiber, plastics, metals and lightweight, yet strong materials. Preferably, the blades  36  are manufactured of either Stainless Steel, Aluminum, and/or Tungsten. 
     The invention does not require that all the advantageous features and all the advantages need to be incorporated into every version of the invention. 
     Although preferred embodiments of the invention have been described in considerable detail, other versions and embodiments of the invention are certainly possible. Therefore, the present invention should not be limited to the described embodiments herein. 
     All features disclosed in this specification including any claims, abstract, and drawings may be replaced by alternative features serving the same, equivalent or similar purpose unless expressly stated otherwise.