CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims the benefit of U.S. Provisional Application No.

61/249,826, filed on October 8, 2009, the specification of which is incorporated by reference herein in its entirety for all purposes.

BACKGROUND OF THE INVENTION

The present invention relates generally to the field of rotors and more specifically to a self regulating rotor.

Horizontally and vertically oriented rotors for use with windmills and wind turbines to capture energy from the wind are well known in the art. Recently, there has been a great need for such devices that can generate electricity from the energy in the wind. Windmill generated electricity can be stored in batteries. It can replace the need for communities in the third world to purchase kerosene for lighting. Wind generated electricity can also power ultra-violet water disinfection and purification systems which can give third world countries a source of clean drinking water. Windmill generated electricity is a non-polluting source of electricity, and will continue to find greater use through out the world.

Horizontal axis rotor designs have found greater acceptance than vertical axis rotors for use as windmill generators. Horizontal axis rotor wind mills are designed with two or more blades, attached to a rotor hub, similar to the propellers used on propeller driven aircraft. To capture the energy in the wind, horizontal axis rotors need mechanisms to keep their blades facing into the wind, and are generally designed to operate in environments where the wind is constant in direction and wind speed. However, horizontal axis rotor wind mills are not without certain drawbacks. For example, horizontal rotors rotating at high speeds generate strong gyroscopic forces that make them not suitable for use in turbulent winds, where the wind continually changes direction. Thus, horizontal axis wind mills need specific conditions to operate effectively. Specifically, horizontal axis rotor windmills need to be sited where the wind is of a minimum velocity and undisturbed to be practical. Horizontal axis rotor wind mills also need complex control mechanisms to control their speed of rotation as well as to feather their blades in extreme conditions.

Also, horizontal axis rotor wind mills must be placed on high towers where there is an undisturbed air flow. Thus, horizontal axis rotor windmills are not designed to function well in the disturbed air flows that are found around buildings in cities and urban areas. Because of this, there has been resistance to placement of propeller type horizontal axis rotor windmills in some communities because of their appearance and their need to be located on high towers.

Vertical axis rotors differ from horizontal axis rotors in that they are able to function in wind conditions and site locations that are not practical for horizontal axis rotors windmills to operate in. Vertical axis rotors eliminate some of the problems associated with horizontal axis rotor units, making vertical axis rotors a good alternative to horizontal axis rotors. For example, vertical axis rotors do not need to continually orient themselves into the wind since their design allows them to accept wind from any direction. Vertical axis rotors can operate in disturbed, turbulent air flows. Vertical axis rotors will operate in a wider range of wind speeds and more varied wind conditions than horizontal axis rotors. Vertical axis rotor type wind mills have the ability to capture wind energy over a greater period of time, which can amount to the extracting of an equal or greater amount of energy from the wind than is captured with a horizontal axis rotor windmill. Vertical axis rotor windmills have inherent advantages of stability due to gyroscopic action of their rotors and simplicity of design due to the avoidance of yaw mechanisms and blade controls. Vertical axis rotors have been designed to increase the energy that can be captured from the wind. Vertical axis rotors that in cross section have the appearance of an S-shape are seen in prior art and will hereafter be referred to as S- shaped rotors.

An S-shaped rotor is disclosed in U.S. Pat. No. 1,646,673 to Wilson. Wilson discloses a vertical axis, manually adjusted, wind driven turbine windmill that consists of a plural segmented cylindrical shaped construction. The segments of the rotor may be adjusted to provide an enclosed cylinder, or they may be laterally moved to provide vanes having various degrees of extension, allowing its drive shaft to rotate at varying speeds. In a fully opened configuration the segments form an S-shaped rotor.

In U.S. Pat. No. 1,697,574 to Savonius, another vertical axis wind rotor is disclosed. The Savonius device includes a rotor disposed on the vertical axis, which has complementary vertically and longitudinally extending elements rotatable about an individual axis to define an essentially S-shaped configuration in horizontal cross section. This device, known as the S-shaped rotor, resembles the cylindrical rotor of professor Gustav Magnus and is distinguishable in that oppositely arranged complementary vanes overlap to define between them a centrally S-shaped air passage of consistent area, which Savonius found enhanced the speed and torque developed by the rotor. Among its advantages, the Savonius S-shaped rotor would operate in response to any wind movements, regardless of direction.

In U.S. Pat. No. 1,766,765, Savonius provides an improved vertical axis wind turbine wherein he makes provisions for speed control means comprising movable flaps located in transverse relation on the complementary vanes to reduce the speed of rotation of the rotor member during excessive wind movement and velocity.

In U.S. Pat. No. 2,596,726 to Rydell, another vertical axis type wind turbine is shown having telescoping and complementary semicircular elements which are respectively curved and capable of lateral displacement with respect to each other to define the S-shaped rotor in operation. Rydell relies on a rack and pinion linkage for the lateral adjustment of his vanes. U.S. Pat. No. 3,093,194 to Rusconi also relates to a vertically disposed wind motor having a plurality of vertically disposed curved air foils and which are pivotally linked with respect to each other to define in one configuration an approximate S-shaped rotor. Rusconi controls the speed and energy developed by his device by coiled torsion springs for resisting the relative outward movement of the respective vanes during operation of the device. The spring tends to bring the blades into a configuration promoting the S-shape which optimizes operations of the device.

In U.S. Pat No. 3,942,909 to Vengst, a vertical axis wind driven rotor is disclosed. The rotor has hinged vanes which rotate on individual axis to move from the closed position in which they form a cylinder to open position defining the S-shaped rotor similar to Savonius where the movement of fluid is used to control and regulate a rotors speed of rotation.

In U.S. Pat. No. 4,293,274, Gilman discloses a helically shaped vertical axis S- shaped rotor that regulates its speed of rotation by lateral movements of its vanes from a closed cylinder to open S-shaped rotor through the use of extensive linkages.

These prior art rotors all suffer in at least one respect. For example, Wilson's U.S. Pat. No. 1,646,673 wind turbine is not automatically adjustable and uses a design of laterally shifting paired vanes to change exposed area to the wind. The S-shape is only established when the rotor is totally open. In Savonius' first U.S. Pat. No. 1,697,574, the design cannot close into a closed cylinder and in Savonius' second U.S. Pat. No. 1,766,765, fixed vanes with flaps are used to regulate speed of rotation. This design also cannot close into a cylinder or change vane overlap.

U.S. Pat. No. 2,596,726, discloses rotors designed for ship propulsion. The rotor described by Rydell uses a relatively complex rack mechanism to cause lateral movements of its vanes and to change vane overlap. Rusconi U.S. Pat. No. 3,093,194 allows its vanes to swing outwardly to control its speed of rotation, losing the S-shape configuration in the process. Vengst's U.S. Pat. No. 3,942,909 uses fluid to control and regulate a rotors speed of rotation. The mass of the fluid increases the rotors inertia and results in a rotor that will not start turning as easily as a rotor without the mass of fluid. Gilman U.S. Pat. No. 4,293,274 uses extensive linkages to facilitate the lateral movements of vanes from a closed cylinder to an S-shape rotor. Finally all of the foregoing devices have a relatively complex construction, which is expensive to assemble and maintain.

Therefore, vertical axis S-shaped rotor designs should take advantage of their inherent beneficial characteristics over horizontal axis windmills. They should be adaptable to varying weather and wind conditions and be of a simple design. They should take advantage of their high starting torque at low wind speeds, as well as more aerodynamically efficient shapes in higher wind speeds. They should be able to close into a closed shape to protect them from severe conditions. And finally they should take advantage of rotary movements to facilitate any changes to their shape.

With these goals in mind, commonly owned U.S. Patent No. 6,910,873 to Kaliski discloses a machine that is a self regulating rotor including a set of cups or vanes that are pivotally attached about a central axis such that they form a closed three dimensional shape when closed, and when rotated into an open orientation form an S-shaped rotor, when viewed as a horizontal cross section. Each cup is attached to a cup shaft, such that the cup can pivot or rotate from a closed shape to an open S-shaped rotor. A rotational energy connecting element is attached to the cups shafts and a rotational speed sensor measures the speed of rotation of the central shaft and has corresponding controllers to affect rotational changes in rotor cup shafts and cups to suit any specific situation or need. Furthermore, a braking device can be attached to the rotor that will slow the rotation of the rotor or hold the rotor stationary.

While the device disclosed in the Kaliski patent addresses many of the drawbacks of the prior art, it would be further desirable to improve upon the rotor disclosed therein to provide a rotor with additional benefits. For example, it would be desirable to eliminate the cup shafts and related structural components associated with this design in order to reduce the cost and complexity in manufacturing. It would be further desirable to provide a rotor with a simpler clutch mechanism for moving the cups between their open and closed positions. These and other objectives are met by the present invention.

SUMMARY OF THE INVENTION

The present invention is a closable rotor of simple design that generally includes a rotatable main shaft, at least one pair of cups pivotably connected to the main shaft, a clutch mechanism rotatably coupled to the main shaft and a cup linkage connected between the clutch mechanism and the pair of cups. The cup linkage pivots the cups between an open position and a closed position upon rotation of the clutch mechanism with respect to the main shaft.

In a preferred embodiment, the rotor includes a first pair of cups and a second pair of cups, wherein the first pair of cups and the second pair of cups are axially spaced and radially offset from each other by about ninety degrees. In this case, a cup-to-cup linkage is preferably connected between the first pair of cups and the second pair of cups for opening and closing the first and second pair of cups in synchronization.

The rotor further preferably includes a brake for stopping rotation of the clutch mechanism with respect to the main shaft. Also, the clutch mechanism further preferably includes an air-resistance governor for slowing rotation of the clutch mechanism with respect to the main shaft.

Furthermore, a biasing element is preferably connected between the main shaft and the clutch mechanism for biasing the pair of cups into their open position. In this case, the rotor further preferably includes a ratchet disk fixed to the main shaft and a pawl engageable with the ratchet disk for permitting rotation of the main shaft in only one direction.

The clutch mechanism in and of itself is unique in that it includes a rotatable main shaft, a clutch hub rotatably coupled to the main shaft, a linkage connected between the main shaft and the clutch hub and an air-resistance governor attached to said clutch hub. The linkage permits an amount of relative rotation between the main shaft and the clutch hub and the air-resistance governor varies the speed of rotation of the clutch hub based on air-resistance.

A preferred form of the closable rotor, as well as other embodiments, objects, features and advantages of this invention, will be apparent from the following detailed description of illustrative embodiments thereof, which is to be read in conjunction with the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

Figure 1 is a top perspective view of the closable rotor formed in accordance with the present invention.

Figure 2 is a side plan view of the closable rotor shown in Figure 1 in an open position.

Figure 3 is a top plan view of the rotor shown in Figure 2.

Figure 4 is a cross-sectional view of the rotor shown in Figure 2 taken along line

A-A.

Figure 5 is a cross-sectional view of the rotor shown in Figure 2 taken along line

B-B.

Figure 6 is a cross-sectional view of the rotor shown in Figure 2 taken along line

C-C.

Figure 7 is a cross-sectional view of the rotor shown in Figure 2 taken along the line D-D.

Figure 8 is a cross-sectional view of the rotor shown in Figure 2 taken along the line E-E. Figure 9 is a side plan view of the closable rotor shown in Figure 1 in a closed position.

Figure 10 is a top plan view of the rotor shown in Figure 9.

Figure 11 is a cross-sectional view of the rotor shown in Figure 9 taken along line

A-A.

Figure 12 is a cross-sectional view of the rotor shown in Figure 9 taken along line

B-B.

Figure 13 is a cross-sectional view of the rotor shown in Figure 9 taken along line

C-C.

Figure 14 is a cross-sectional view of the rotor shown in Figure 9 taken along the line D-D.

Figure 15 shows various views of a preferred embodiment of the clutch having an air-resistance governor in an open position.

Figure 16 shows various views of the air-resistance governor in a closed position.

Figure 17 shows several views of an alternative embodiment of the air-resistance governor in an idle position.

Figure 18 shows several views of the air-resistance governor in a power position.

Figure 19 is a graphical view of the possible pivot point locations for the rotor cups of the present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

Referring to the drawings, the rotor 10 of the present invention generally includes a main shaft 12, at least one set of closable cups 14 pivotably connected to the main shaft and a clutch mechanism 16 rotatably supported on the main shaft. The rotor 10 is preferably rotatably supported on a base 18 with journals of the main shaft 12 being attached to the base with suitable bearings 20. The main shaft 12 can further be connected to an alternator (not shown) to convert the rotation of the shaft to electricity.

The cups 14 are pivotably attached to the main shaft 12 in a manner that provides a unique S-shape rotor design when the cups are open, as viewed from a horizontal cross section, when as shown in Figures 1-7. Upon actuation of the clutch mechanism 16, as will be discussed in further detail below, the cups 14 pivot to a closed position thereby forming a closed cylinder, as shown in Figures 9-14. In a preferred embodiment, the rotor of the present invention is provided with a lower pair of cups 14 and an upper pair of cups 22. The upper pair of cups 22 is pivotably attached to the main shaft 12 above the lower pair of cups 14 and is radially offset from the lower pair of cups at a ninety degree angle. In other words, the plane defined by the edges forming the opening of the lower cups 14 is preferably generally perpendicular to the plane defined by the edges forming the opening of the upper cups 22. This will allow the rotor 10 to "catch" wind from different directions. Each pair of cups 14, 22 consists of two off-set half cylinders 14a, 14b, 22a, 22b.

Each half cylinder 14a, 14b, 22a, 22b is able to pivot with respect to the main shaft 12 from an open S-shape to a closed cylinder shape. In their open position, the radial centerline of each individual cup is laterally offset from the radial centerline of its mating cup to form the s-shape. As the cups pivot closed, as will be discussed in further detail below, the radial centerlines of the cups come into alignment, thereby causing the cups to form a closed cylinder.

Each pair of cups 14, 22 is attached to the main shaft 12 via a pin and cup support arrangement. Specifically, a lower cup support 24 is fixed to the main shaft 12 below the lower cups 14 for connecting the lower cups to the main shaft. A central cup support 26 is fixed to the main shaft between the lower cups 14 and the upper cups 22 for connecting both the lower cups and the upper cups to the main shaft, and an upper cup support 28 is fixed to the main shaft above the upper cups for connecting the upper cups to the main shaft. Each half cylinder or cup 14a, 14b, 22a, 22b has a hole at the location where the cup pivots and a pin 30 is provided at each hole for rotatably connecting the cup to its respective cup support 24, 26, 28. Thus, the pins 30 are attached to cup supports 24, 26, 28 located above and below each cup. The cup supports 24, 26, 28 are rotatably fixed to the main shaft 12 so that the cups 14, 22 and the main shaft together rotate about the main shaft axis. The pins 30, however, permit the cups 14, 22 to pivot with respect to the main shaft 12 from an open position, as shown in Figures 1-7, to a closed position, as shown in Figures 9-14. The upper and lower cup supports 24 and 28 may simply be in the form of an elongate band having pins 30 fixed at opposite ends thereof. The central cup support 26 is preferably a cross-shaped member having four pins 30 fixed at the four ends thereof for pivotable attachment of the lower and upper cups 14, 22. As will be discussed in further detail below, the cups 14, 22 freely pivot or rotate on these cup supports 24, 26, 28 about the pins 30.

A cup linkage arrangement is provided to open and close the cups 14, 22. In particular, two lower cup linkages 32 are provided below the lower cups 14 and two upper cup-to-cup linkages 34 are provided between the lower cups 14 and the upper cups 22. Each linkage 32, 34 is generally an elongate bar having pins 36 provided at opposite ends thereof. Each lower cup linkage 32 has a pin 36 rotatably attached to the bottom end of a lower cup 14a, 14b. The other lower cup linkage pin 36 is rotatably attached to the clutch mechanism 16. Thus, the lower cups 14 are permitted to pivot about the lower cup linkage pins 36 and the lower cup linkage 32 is permitted to pivot about the clutch mechanism 16. The lower cup linkage 32 is driven by the clutch mechanism 16, as will be discussed in further detail below, to cause the lower cups 14 to open and close.

Similarly, each upper cup 22a, 22b is connected to one of the lower cups 14a, 14b via an upper cup-to-cup linkage 34 that carries two pins 36. One of the cup-to-cup linkage pins 36 travels through a hole in the bottom end of an upper cup 22a, 22b. The other cup-to-cup linkage pin 36 travels through a hole in the upper end of a lower cup 14a, 14b. Again, the lower and upper cups 14, 22 are permitted to pivot about the upper cup-to-cup linkage pins 36. The upper cup-to-cup linkage 34 causes the upper cups 22 and the lower cups 14 to pivot open and closed in unison. The clutch mechanism 16 is located below the lower cup support 24 for driving both cup pairs 14, 22 between their open and closed positions. The clutch mechanism 16 is rotatably coupled to the main shaft 12 meaning that the clutch mechanism and the main shaft rotate about the same axis, but can rotate independently of each other. The clutch mechanism 16 consists of a tube 38 containing a bearing allowing it to rotate freely on the main shaft 12. The clutch mechanism 16 further includes disk plates 40, 42 attached to the opposite top and bottom ends of the tube 38. The upper disk 40 has holes to receive the pins 36 from the lower cup linkage 32 and the bottom second disk 42 is adapted for actuation by an actuator mechanism 44 for stopping or slowing the rotation of the clutch mechanism 16.

In a preferred embodiment, the actuator mechanism 44 is a brake caliper 46 fixed to the base 18 and positioned at the edge of the bottom second disk 42. In this case, the bottom clutch disk 42 is termed a brake disk and the brake caliper 46 allows the brake disk to rotate freely when the caliper is in an open position. When the brake caliper 46 is actuated, the opposite jaws of the caliper close on the brake disk 42, thereby functioning as a brake when the brake caliper is in a closed position. When the brake caliper 46 is closed, the brake disk 42 is prevented from rotating with respect to the main shaft 12, which in turn causes the lower cup linkage 32, attached to the upper clutch disk 40, to pull on the lower cups 14 to close the cups. The relationship of the relative locations between the clutch mechanism 16 and the main shaft 12 defines the amount of closure of the cups 14, 22.

In other words, when the clutch mechanism 16 is stopped from rotation by the action of the brake caliper 46 on the brake disk 42, the main axis 12 will continue to momentarily rotate due to the momentum or rotational inertia of the spinning main shaft 12. However, such continued rotation of the cups 14, 22 on the main axis 12 will act against the force of the lower cup linkage 32 fixed to the clutch mechanism 16, which is now stopped from rotation. As a result, the lower cup linkage 32 will act to close the cups 14 until the cups are completely closed. As the lower cups 14 close, the upper cup- to-cup linkage 34 will cause the upper cups 22 to close in synchronization with the lower cups. When the cups 14, 22 are fully closed, no further rotation is permitted by the stationary clutch mechanism 16 and, therefore, rotation of the main shaft 12 is halted.

The clutch mechanism 16 further preferably includes a coil spring 48 located below the clutch mechanism for restoring the cups 14, 22 to their open position when the brake caliper is released. One end of the spring 48 is attached to the main shaft 12 and the other end is attached to the clutch mechanism 16. The coiled tension of the spring 48 keeps the cups 14, 22 in an open position.

Also in a preferred embodiment, the main shaft 12 is provided with a one way ratchet disk 50 which is engageable with a moveable pawl 52, as shown most clearly in Figure 8. The ratchet disk 50 is fixed to the main shaft 12 and rotates together with the main shaft. The moveable pawl 52 is fixed to the base 18 and is moveable into and out of engagement with the teeth 54 of the ratchet disk 50. Such movement of the pawl 52 can be accomplished electronically or mechanically. Preferably, movement of the pawl 52 is tied to the movement of the brake caliper 46 so that, when the brake caliper is in its open position, the pawl is not in contact with the ratchet disk 50. However, as the brake caliper 46 is closed, the pawl 52 is moved into engagement with the teeth 54 of the ratchet disk 50 to prevent the ratchet disk, and thereby the main shaft 12, from rotating in a reverse direction. This will prevent the cups 14, 22 from opening again while the brake caliper 46 is actuated.

Figure 8 also shows connection of one end 56 of the spring 48 with the ratchet disk 50, while the opposite end 58 (not shown in Figure 8) is attached to the clutch mechanism 16. In this manner, the engaged one way ratchet 50 prevents the main shaft 12 from rotation in reverse, while the spring 48 located below the clutch mechanism 16 is in tension. Without the ratchet disk 50 engaged with the pawl 52, the spring 48 would cause the main shaft 12 to rotate in reverse, thereby opening the cups. Only when the brake caliper 46 is released will the spring 48 allow the cups 14, 22 to return to their open position. The brake caliper 46 is but one form of an actuator mechanism 44 for halting rotation of the clutch mechanism 16. Alternatively, or in addition to the brake caliper 46, the actuator mechanism 44 can take the form of an air-resistance governor 60 attached to the clutch mechanism 16 for slowing down the rotation of the clutch mechanism when subject to wind resistance.

Figures 15 and 16 show a preferred embodiment of an air-resistance governor 60 according to the present invention. The preferred form of the air-resistance governor 60 generally includes at least two curved air chutes 62 pivotably connected to the clutch mechanism 16. The air chutes 62 can be attached at one end to the clutch tube 38, the upper disk 40 or the lower disk 42. In the embodiment shown in Figures 15 and 16, the air chutes 62 are attached between the top disk 40 and the bottom disk 42 of the clutch mechanism 16 with pins 64 that permit pivoting of the chutes about the pins. Chute linkages 66 can also be provided to synchronously move the chutes 62 in and out. These chute linkages 66 are pivotably attached at their ends by pins between the chutes 62.

The chutes 62 are preferably channel shaped and define a pocket 68 for capturing air when the chutes are radially extended. Such radial extension of the chutes 62 will occur by the centrifugal forces acting on the chutes as the clutch mechanism spins.

Springs 70 can be provided between the clutch mechanism and the chutes 62 and/or the chute linkages 66 to bias the chutes in a normally closed position, as shown in Figure 16. These springs 70 can also be specifically selected to allow the chutes 62 to extend only at a specific rotational speed of the clutch mechanism 16.

In use, the centrifugal forces applied by the rotation of the clutch mechanism 16 causes the air chutes 62 to extend in a radial outward direction. With the chutes 62 thus extended, the force of the air-resistance acting on the pockets 68 of the chutes will impede the rotation of the clutch mechanism 16 thereby creating a difference in the speed of rotation between the clutch mechanism and the main shaft 12. As discussed above, such difference in the speed of rotation between the clutch mechanism 16 and the main shaft 12 will cause the lower cup linkage 32 to urge the cups 14 into their closed position. Thus, at a specific rotational speed of the main shaft 12, the air chutes 62 will pivot outward, which will increase the air drag on the rotating governor 60 and the clutch mechanism 16. The drag that is applied to the clutch mechanism 16 is proportional to the rotational speed of the air-resistance governor 60. As the rotational speed increases the clutch mechanism 16 will rotate at a different speed on the main shaft 12, resulting in the progressive closure of the cups 14, 22. The higher rotational speed results in greater drag, thereby closing the cups 14, 22 further.

The partial closing of the cups 14, 22 reduces the S-shaped rotors exposed area to the wind, which reduces the power from the wind entering the S-shaped rotor. This results in the governing of the rotational speed of the S-shaped rotor. At low wind speeds and low rotational speeds of the S-shaped rotor the governor is in a closed cylinder orientation, which adds no air resistance and no additional load to the rotating central shaft.

Figures 17 and 18 show an alternative embodiment of an air-resistance governor 60' for use in the present invention. In this case, the air-resistance governor 60' takes the form of a fan 72 having a plurality of fan blades 74 radially attached to a central hub 76. The central hub 76 is attached to the clutch mechanism 16 so that the blades 74 rotate about the main shaft 12 together with the clutch mechanism. In an idle position, as shown in Figure 17, the fan blades 74 rotate together with the clutch mechanism 16 without any air resistance. However, when the blades 74 are turned into a "power" position, as shown in Figure 18, the blades create a drag against the air, thereby causing a resistance against rotation of the fan 72. Such resistance causes the clutch mechanism 16 to slow down with respect to the main shaft 12, thereby causing the cups 14, 22 to close, as described above.

The fan 72 can be designed to create increasing air resistance with the increase of the rotational speed of the central shaft 12. Alternatively, the fan blades 74 can be made to move between an idle position, as shown in Figure 17, to a power position, as shown in Figure 18. This motion can be accomplished, for example, by a mechanical actuator, or by centrifugal forces.

In any event, at a specific rotational speed the air drag created by the fan blades 74 will slow the clutch mechanism 16 on the main shaft 12, resulting in the partial closing of the cups 14, 22. The greater the rotational speed of the main shaft 12, more air resistance will be experienced, and the clutch mechanism 16 will be rotated more on the main shaft, thereby causing the cups 14, 22 to close.

Having described the various components of the rotor 10 of the present invention, operation of the invention will be further described. In an open orientation, as shown in Figures 1-7, the offset half cylinder cups 14, 22 form an S-shape relationship when viewed as a horizontal cross section. This open relationship catches the wind resulting in rotation of the rotor 10. Wind enters the inside of one cup 14a, 22a and then is redirected to the inside of the other cup 14b, 22b.

The forces created by the wind blowing against the cup surfaces are transmitted to the cup pivot pins 30, through the pivot pins to the cup supports 24, 26, 28, and through the cup supports to the main central shaft 12. As described above, the upper and lower sets of open half cylinder cups 22, 14 are connected by a central cup linkage 34, which causes the cups to open and close in synchronization.

As the wind increases and the S-shaped rotor's rotational speed increases, the air resistant governor 60, 60' is able to impart a progressive drag on the clutch mechanism 16. This progressive drag progressively moves the clutch mechanism 16 with respect to the main shaft 12. When the clutch mechanism 16 moves on the main shaft 12, it exerts a force on the lower clutch linkage 32 connecting the clutch mechanism 16 to the lower set of cups 14 to progressively close these cups.

In turn, the cup linkage 34 connecting the lower cups 14 to the upper set of cups

22 causes the upper set of cups to also progressively close. As the wind decreases and the rotor's rotational speed decreases, the drag created by the air-resistance governor 60, 60' decreases, and the clutch mechanism 16 moves back toward the opening position. Thus, the air-resistance governor 60, 60' allows the S-shaped rotor 10 to self regulate its rotational speed in varying wind speeds and conditions.

To stop the rotation of the S-shaped rotor 10, the brake 44 can be engaged. This closes the brake caliper 46 which clamps down on the brake disk 42 of the clutch mechanism 16. As discussed above, engagement of the brake 44 also preferably actuates the pawl 52 into engagement with the ratchet disk 50 attached to the central shaft 12. The central shaft 12 will continue to momentarily turn while the clutch mechanism 16 is stationary. This will result in the clutch linkages 32, 34 pulling closed the lower and upper set of cups 14, 22. The ratchet disk 50 prevents the spring 48 attached between the clutch mechanism 16 and the main shaft 12 from rotating the main shaft in reverse, which would re-open the cups 14, 22. When the brake 44 is released the pawl 52 is also disengaged from the ratchet 50, whereby the tensioned spring 48 attached between the clutch mechanism 16 and the main shaft 12 opens the cups 14, 22.

An important consideration with respect to the present invention is the location of the cup pivot points such that rotor cups will be able to pivot from an open overlapped configuration into a closed cylinder configuration. Referring now to Figure 19, the cup pivot points 80 must be located on a line of equal distance between the arc of the open cups and the arc of the closed cups. This will allow the open cups to rotate into a closed cylinder.

By carefully selecting the location of the pivot points, the amount of rotation needed for the cups of a Savonius rotor to pivot from fully open (S shaped cross section) to fully closed (closed cylinder position) can be adjusted. Pivot points located on lines with specific angles, for example defined as 0, 22.5, 45, 67.5, and 90 degrees, as drawn from the center of the arch outward to the edge of a cup, where 0 degrees is located at a right angle to the cups base or flat side, and 90 degrees is on the base line will result in the amount of rotation of a cup to go from completely open to completely closed to be equal to twice the angle of the line the pivot point is located on. For example, a pivot point located on the line defined as 22.5 degrees will result in a cup configuration that will require 45 degrees of rotation to go from the open s- shaped position to the fully closed cylinder position. Similarly, for a pivot point located on the line defined as 45 degrees, the cups will require 90 degrees of rotation to go from the open s-shaped position to the fully closed cylinder position. For a pivot point located on the line defined as 67.5 degrees, the cups will require 135 degrees of rotation to go from the open s-shaped position to the fully closed cylinder position. Finally, for a pivot point located on the line defined as 90 degrees, the cups will require 180 degrees of rotation to go from the open s-shaped position to the fully closed cylinder position.

To locate the cup shaft axis of rotation, the two cups are first positioned in a fully open s-shaped position having a specific desired overlap 82. Next, a line 84 is drawn perpendicular to the plane that separates the two cups 14a, 14b such that all points 80a, 80b, 80c on the line are equal distant from the rotor's central axis of rotation when fully open 86a and the location of the cup that becomes the rotor's central axis of rotation when the cups are totally closed 86b. Locating the cup shaft axis of rotation along this defined line will allow the cups to rotate from the fully open S-shaped orientation to a totally closed three dimensional shape. Where the cup shaft axis of rotation is located along this line will determine the angle of rotation needed for the cups shafts to rotate from a fully open S-shaped rotor to a totally closed shape.

To determine the cup shaft angle of rotation needed to go from the fully open s- shape to the closed cylinder, a vertical plane 84 is first drawn that is perpendicular to the plane that separates the two cups 14a, 14b, and that also passes through the point on the cup that becomes the rotor's central axis of rotation when the cups are totally closed. Next a line is drawn from the cup shaft location to the point on the cup that becomes the rotors central axis of rotation when the cups are totally closed. The angle between this line and the vertical plane is measured. The cup shaft angle of rotation needed to rotate the cups from a totally open S-shape to a totally closed shape is equal to twice the angle measured between the vertical plane and the line running through the cup shaft location. As a result of the present invention, a rotor 10 is provided which is simply designed and efficient in use. Previous designed s-shaped rotors with pivoting cups have cup shafts attached to the cup to control the pivoting of their cups. These cup shafts carry the force to end plates that are attached to the main shaft. The cup shafts typically include a pulley and belt arrangement to control the precise positions of the cups relative to each other, as well as to connect the cup shafts to speed controlling devices.

The new design according to the present invention has no cup shafts connected to the cups. This eliminates all the associated engineering and additional parts, such as belts, pulleys, and levers, needed to make the s-shaped rotors to function. Moreover, this new design has no end plates with their associated bearings.

While the present invention has been primarily described in terms of use with a wind turbine, it is also important to note that the rotor described herein will also work in other moving fluids, such as water. Thus, the present invention has applications in tidal currents, river currents, ocean currents, etc.

Similarly, the air-resistance governor of the present invention may find many applications other than use in a vertical axis wind turbine, as described herein. The benefits of the air-resistance governor of the present invention reside in the fact that it is a simple mechanical apparatus for controlling mechanisms and devices that control the rotational speed of a rotating shaft. The air-resistance governor is designed to rotate with a main rotating shaft to which it is mounted on, up until a predetermined RPM. When the shaft reaches a predetermined RPM, the air-resistance governor will start to create more drag as a result of more air passing its blades, scoops, paddles, etc. This increase in drag will cause the main shaft to advance its relative position with respect to the governor. To say it another way, the governor will be slowed with respect to the main shaft's rotation. This rotation of the governor on the shaft will activate a linkage or lever or other mechanism that is connected to the shaft. The force directed through this linkage can be used to control throttles, blade angles and pneumatic, hydraulic and electrical control systems that are used in controlling the rotational speed of a shaft. A spring can be used to hold the air- resistance governor in its starting position on the shaft it is mounted to.

Thus, the air-resistance governor of the present invention can add a mechanical governing system to pre-existing sensing and control systems, as a way of adding redundancy. So if there is a failure in a non-mechanical system the air resistance governor will still operate and can function to control and regulate the rpm of a rotating shaft.

The air-resistance governor of the present invention can be installed on chair lifts, gondolas and trams for an added safety measure. When not activated, the air-resistance governor rides closed, adding no air resistance to the mechanism. When there is a condition of higher than rated rotational speed is sensed, the governor can be activated to slow the rpm to a safe level. An example would be a chair-lift losing its brake and starting to rotate in reverse with the skiers' weight on the chairs becoming the force accelerating the reverse rotation.

Mounting the air-resistance governor of the present invention on the main shaft of a horizontal axis propeller wind mill can be a means of feathering the propeller blades to control the windmills rpm. Connecting the governor via gears or linkages can control the pivoting of the blades and thus the blades pitch corresponding to the speed of rotation of the propeller shaft. Moreover, the governor of the present invention can be provided with a bevel gear that connects to bevel gears at the end of each propeller blade shaft. Thus, when the governor is not activated the propeller blades are in a pitch to the wind for maximum power. When the wind exceeds the safe limit for the wind mill, the air- resistance governor is activated and starts to lag behind the main propeller shaft it is mounted on. The governor's bevel gear moves relative to the main shaft the propellers are connected to causing the propeller blade bevel gears to turn. The result is the blades will start to feather, losing some of their power, progressively as the rpm increases.

Although the illustrative embodiments of the present invention have been described herein with reference to the accompanying drawings, it is to be understood that the invention is not limited to those precise embodiments, and that various other changes and modifications may be effected therein by one skilled in the art without departing from the scope or spirit of the invention.

Various changes to the foregoing described and shown structures will now be evident to those skilled in the art. Accordingly, the particularly disclosed scope of the invention is set forth in the following claims.