WO2014138964A1

WO2014138964A1 - Apparatus and method for conversion of water waves energy to electrical energy

Info

Publication number: WO2014138964A1
Application number: PCT/CA2014/050206
Authority: WO
Inventors: Charles C. Haynes
Original assignee: Haynes Charles C
Priority date: 2013-03-11
Filing date: 2014-03-10
Publication date: 2014-09-18
Also published as: CA2808614A1; CA2808614C; CA2911978A1; CA2839176A1; CA2839172A1

Abstract

A tidal compensation apparatus is provided comprising a pile anchored to the seabed with a wave energy point absorber system connected to a sliding mechanism that is slidably connected to the pile and being operative to cause the slidable connection to jamb against the sliding mechanism, and, a float connected to the sliding mechanism, acting to track the tidal height of the surface of the water. A wave energy point absorbing system is provided comprising a framework attached to a tidal compensating frame or platform, with top and bottom plates defining a space with the top plate of the framework located out of and above calm water and the bottom plate of the framework located in and under calm water, with a float contained within the framework with at least two guide rails extending through the float, each guide rail slidably mounted through two linear bearings to the float, one linear bearing located near the top of the float and the other located near the bottom, allowing the float to move up and down due to wave action.

Description

TITLE OF INVENTION

APPARATUS AND METHOD FOR CONVERSION OF WATER WAVES ENERGY TO

ELECTRICAL ENERGY

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is related and claims priority to Canadian Patent Application No. 2,808,614 filed March 1 1 , 2013, which is hereby incorporated herein by reference in its entirety.

FIELD OF THE INVENTION

The invention generally relates to the field of energy and more particularly to apparatus and method for conversion of water waves energy to electrical energy.

BACKGROUND OF THE INVENTION

Water waves and swells are a vast source of clean and renewable energy. Their generation by the transfer and concentrating of wind energy depends on the wind speed, the length of time for which the wind blows and the distance over which it blows. Waves are generated by wind passing over the surface of the sea. As long as the waves propagate slower than the wind speed just above the waves, there is an energy transfer from the wind to the waves. A wave is a transfer of energy, in the form of disturbance through some medium, without translocation of the medium. A wave having a short duration is called a pulse. Waves that vibrate in repeating cycles illustrate periodic motion or harmonic motion. One complete oscillation is called a cycle.

Wind water waves will continue to travel in the direction of their formation even after the wind dies down and they lose energy only slowly (mainly by interacting with the atmosphere), so they can travel with minimal loss of energy as regular, smooth waves or swell. These can persist at great distances from the point of origin. For example, most of the energy in a tsunami can be transferred by waves across the Pacific Ocean, a distance of approximately 10,000 miles with little loss of energy. The total wave power incident on all of the world's coastlines has been estimated at approximately 1 -10 terawatts per year, by Isaacs and Seymour in a paper titled "The ocean as a power resource", International Journal of Environmental Studies, vol. 4(3), 201-205, 1973, which was the same order of magnitude as the world's total current energy demand at that time. The near shore wind water wave energy resource (i.e. at 20 m water depth) has been reported to have an energy density of 25-40 kW/ linear meter of wave front by T.W. Thorpe in his "A Brief Review of Wave Energy", ETSU-R120, May 1999. Recently a paper titled "Assessing the Global Wave Energy Potential", Proceedings of OMAE 2010 29th International Conference on Ocean, Offshore Mechanics and Arctic Engineering, June 6-11, 2010, Shanghai, China OMAE 2010 - 20473 reported:

"In this paper the evaluation of the global wave energy potential is presented based on data from a global wind-wave model (validated and calibrated against satellite altimeter data) and buoy data (the WorldWaves database)... The work presented in this paper constitutes a first step towards the assessment of more detailed global and regional wave energy resources. Based on possibly the highest quality global database available at present, we have estimated that the global gross resource is about 3.7 TW, which lies in the range of earlier evaluations (1 -10 TW). However the exclusion of areas with very low energy (P<5kW/m) and in particular areas impacted by sea ice decreases this resource by about 20%... With the existing global database of known accuracy, the results of this study can potentially lead to more detailed comparative assessments of the theoretical and technical resources for any area worldwide, particularly useful for companies looking for most suitable areas for technology introduction."

Fig. 24 herein shows average worldwide wave energy density to be approximately 37.25 kW/linear meter mostly along coastal areas.

One challenge facing wave energy generation systems in tidal waters, and particularly systems having at least one part of a generator fixed with respect to the sea floor is how to provide for tidal compensation: (A) how to accommodate the changes in the surface water level, where the prime mover waves are located, relative to the sea bed due to tidal action, a viable, economical, reliable, repairable and sustainable method and apparatus is required because the buoyant force which the waves exert on the point absorber must react against an opposing body to facilitate the conversion of the floating body's kinetic energy into commercially useful energy. Another challenge facing wave energy systems in tidal water relates to achieving "public uptake acceptance", or how to have an acceptable looking design and operation that will achieve public uptake acceptance of deployment. It is noteworthy, by way of background, that this aspect is almost always overlooked in the general field of wave energy conversion patents. It is a fact that for near shore devices the public's acceptance of the visual impact is a critical factor as is a deployed wave systems general hidden and imagined impacts. In some cases, these perceived impacts become barriers to obtaining a permit for deployment and thus public information and education is an important part of wave energy converters. Such barriers have been a critical factor in wind energy deployment as public outcry has stopped some wind energy deployments. It is no longer reasonable to assume that the public will accept a system just because it is a "green" renewable energy system and wave energy system engineers and designers need to make this challenge a part of their system, the offshore oil rig platform look is not a sustainable look. The public demands that not only should renewal energy systems work efficiently but that they be unobtrusive and not disturbing to their views and perception of the how the natural seascape should be used, in some case, if at all.

Some point absorber wave energy converters may have the advantages of: (1 ) having relatively small dimensions, in fact they must be smaller than the incident wave length acting on them; (2) having the utility to harvest energy from wave of all directions at one point in the ocean; and, (3) having the potential for a low visual profile.

There remains a need therefore to overcome certain of the shortcomings and problems associated with existing wave energy generation systems and methods.

BRIEF SUMMARY OF THE INVENTION

An apparatus and method is provided according to several embodiments of the present invention for the conversion of water waves energy to electrical energy for near shore or off shore locations using a tidal compensator, a point absorber motive float, a reciprocating wave surge converter, a power conversion means to run a relatively high speed rotary generator efficiently and a covering suitable for the challenges of the environment. According to another embodiment, a tidal compensation system is provided for maintaining a wave energy point absorber at the surface of the water comprising a pile anchored to the seabed which has a sliding mechanism slidably connected to the pile, and has, a float acting to track the tidal height of the surface of the water connected to the sliding mechanism and secondly, due to wave action on the float and the wave energy point absorber, the sliding mechanism jambs against the pile and thereby makes a connection through the pile to the seabed to provide a sufficient reactive force against which the point absorber moves.

In one embodiment, a tidal compensation system is provided which includes a spring, which is interposed between the tidal compensator float and sliding mechanism wherein the spring dampens the movement of the tidal compensator float due to wave action.

In another embodiment, a point absorbing float system is provided comprising a framework defining a space wherein a float is contained within this space and at least two slider rods which are rigidly secured to the framework structure and which extend through the float in such a manner that the float is slidably mounted on the slider rods.

In a further embodiment, a wave energy conversion system is provided which has a point absorbing float system comprising a framework defining a space wherein a float is contained within this space and at least two slider rods which are rigidly secured to the framework structure and which extend through the float in such a manner that the float is slidably mounted on the slider rods; and which has, a tidal compensation system secured to the seabed, that supports the point absorbing float system in such a way that the tidal compensation system tracks the tides so as to maintain the point absorbing float system at a substantially constant sea level; and which has, at least two straight elongated members attached to the point absorbing float and extending vertically from the space within the framework such that the elongated members are associated with an energy converter for converting reciprocal motion of the elongated members to rotational motion.

In a further embodiment, a wave energy converter comprising at least two motion converters, each for converting linear motion of at least one respective reciprocating member, which are configured to reciprocate up and down in unison under wave action, to rotational motion; and each motion converter is configured to actuate rotation of a respective rotating member; where one of the respective rotating members actuates rotation of a shaft in one direction during an up cycle of said reciprocal motion; and, the other one of the respective rotating members actuates rotation of its shaft in one direction during a down cycle of said reciprocal motion.

In another embodiment, a energy converter is provided comprising the converter previously described in summary immediately above wherein each of the respective rotating members comprises an overrunning clutch for controlling the direction of rotation of each respective rotating member.

In a further embodiment, a further energy converter is provided comprising the energy converter previously described in summary immediately above wherein each of the respective rotating members actuates a common main drive shaft.

In further embodiments according to the present invention, the energy converter previously described in summary immediately above may be provided, additionally comprising one or more of the following features:

wherein each of the motion converters comprises a chain attached to one of the respective reciprocating members;

wherein each of at least one of the respective reciprocating members comprises one or more rods positioned between the common main drive shaft and the chain attached to the respective reciprocating members;

wherein each of the respective reciprocating members comprises one or two connecting rods positioned on a distal side of the chain, attached to the respective reciprocating members, in relation to the common main drive shaft;

wherein a flywheel is mounted on the common main drive shaft;

wherein a flywheel acts as a sprocket for actuating a shaft of a generator;

wherein the generator shaft is associated with a generator sprocket and the diameter of this generator sprocket is less than the diameter of the flywheel;

wherein a flywheel is mounted on said common main drive shaft and this flywheel acts as a sprocket to actuate rotation of a second shaft and this second shaft is associated with a sprocket that actuates rotation of a generator shaft and the size of the sprocket on the generator shaft is less than the diameter of the sprocket associated with the second shaft;

further comprising a cover connected to the framework which covers energy converter; and wherein the cover comprises a regular octagonal base having a diameter measured between opposed vertices, with eight octagonal lower sides each rising upwards and outwards from the base at an angle between 120 and 140 degrees measured from the base for a distance of between .3 and .7 of the diameter, with eight octagonal upper sides each rising upwards and inwards from said lower side at an angle between 60 and 80 degrees measured from the base for a distance of between .7 and 1.1 of the diameter, with a semicircular domed top connected to top edges of the eight upper sides.

BRIEF DESCRIPTION OF THE OF THE DRAWINGS

For a more complete understanding of the present invention and the advantages thereof, reference is now made to the following description taken in conjunction with the accompanying Drawings in which:

Fig. 1 A is an elevation view of preferred embodiment of the invention;

Fig. 1 B is a perspective detail view of Fig. 1A;

Fig. 2A is an elevation view of an embodiment of the invention using two piles; Fig. 2B is a perspective detail view of Fig. 2A;

Fig. 3A is an elevation view of an embodiment of the invention using one pile and one tidal compensator float;

Fig. 3B is a perspective detail view of Fig. 3A;

Fig. 3C is an elevation view of another embodiment of the invention using one pile and one tidal compensator float;

Fig. 3D is a perspective detail view of FIG. 3C as viewed from the bottom;

Fig. 3E is a perspective detail of the complete pile in FIG. 3C;

Fig. 3F is a perspective detail of the top of the pile in FIG. 3C;

Fig. 3G is a cross section plan view along line AA of Fig. 3C;

Fig. 3H is a perspective detail of the inside of the slider pipe in Fig. 3C;

Fig. 4A is an elevation view of an embodiment of the invention using one pile and two tidal compensator floats;

Fig. 4B is a perspective detail view of Fig. 4A;

Fig. 5A is an elevation view of an embodiment of the invention using two piles and one tidal compensator float; Fig. 5B is a perspective detail view of Fig. 5A;

Fig. 6A is an elevation view of an embodiment of the invention using two piles and two tidal compensator floats;

Fig. 6B is a perspective detail view of Fig. 6A;

Fig. 7 is a perspective view of double unidirectional rotation system according to a two rod embodiment of the invention;

Fig. 8A is a perspective view of double unidirectional rotation system according to a four rod embodiment of the invention;

Fig. 8B and Fig. 8C are cross sectional views along line BB and CC of Fig. 8A.

Fig. 8D is a perspective view of force springs located on an embodiment of the invention showing two rods on one side;

Fig. 8E is a perspective view looking to top plate of framework showing force springs and spring alignment-receiver attached to top plate located on an embodiment of the invention showing two rods on one side;

Fig. 8F is a detail perspective view of the spring alignment-receiver;

Fig. 9A is a schematic drawing of double unidirectional rotation according to an embodiment of the invention where rods are located inside and clutches grabbing clockwise;

Fig. 9B is a schematic drawing of double unidirectional rotation according to an embodiment of the invention where rods are located inside and clutches grabbing counter clockwise;

Fig. 9C is a schematic drawing of double unidirectional rotation according to an embodiment of the invention where rods are located outside and clutches grabbing clockwise;

Fig. 9D is a schematic drawing of double unidirectional rotation according to an embodiment of the invention where rods are located inside and clutches grabbing counter clockwise;

Fig. 10A is an end perspective view of an embodiment of the invention using a flywheel;

Fig. 10B is a side perspective view of Fig. 10A;

Fig. 1 1A is an end perspective view of an embodiment of the invention using a flywheel and increaser gears; Fig. 1 1 B is a side perspective view of Fig. 1 1 A;

Fig. 12A is a perspective view of an embodiment of the invention using rectilinear point absorber framework with two rods and guide strips;

Fig. 12B is a perspective view showing Fig. 12A from a different angle;

Fig. 12C is a perspective detail of the point absorber of Fig.12A;

Fig. 13A is a perspective view of an embodiment of the invention using rectilinear point absorber framework with four rods and guide strips;

Fig. 13B is a perspective view showing Fig. 13A from a different angle;

Fig. 14A is a perspective view of an embodiment of the invention using rectilinear point absorber framework with two rods and two guide rails;

Fig. 14B is a perspective view showing Fig. 14A from a different angle;

Fig. 15A is a perspective view of an embodiment of the invention using cylindrical point absorber framework with four rods and four guide rails;

Fig. 15B is a perspective view showing Fig. 15A from a different angle;

Fig. 16A is a perspective view of an embodiment of the invention using rectilinear point absorber showing the interior arrangement;

Fig. 16B is a dual perspective view showing Fig. 16A from a different angle;

Fig. 16C is a perspective view of the exterior arrangement of Fig.16A;

Fig. 17A is a perspective view of an embodiment of the invention using cylindrical point absorber showing the interior arrangement;

Fig. 17B is a perspective view showing Fig. 17A from a different angle;

Fig. 17C is a dual perspective view of the exterior arrangement of Fig.17A;

Fig. 18 is a perspective and schematic drawing of different embodiments of the invention using rectangular point absorber with guide strips with respect to four bottom types each with two and four connecting rods;

Fig. 19 is a perspective and schematic drawing of different embodiments of the invention using rectangular point absorber with two and four guide rails with respect to four bottom types each with two and four connecting rods;

Fig. 20 is a perspective and schematic drawing of different embodiments of the invention using cylinder point absorber with two and four guide rails with respect to four bottom types each with two and four connecting rods; Fig. 21A is a perspective drawing with shading of view of WEC embodiment per Fig. 1 A as seen from shore or from a kayak;

Fig. 21 B is a perspective drawing with shading of view of WEC embodiment per Fig. 3A as seen from shore or from a kayak;

Fig. 22A is a perspective view of tidal compensation dampening spring;

Fig. 22B is a sectional perspective view of tidal compensation dampening spring;

Fig. 22C is a perspective view of connector that connects spring to tidal compensator base;

Fig. 22D is a perspective view of connector that connects spring to tidal compensator float;

Fig. 22E is a perspective view of spring details;

Fig. 23A is a side view of energy converter covering showing layout details;

Fig. 23B is a perspective view of energy converter covering;

Fig. 24 is a wave energy density map of the World;

Fig. 25 is a tidal water level map of Diurnal (Mixed) Tide Change Levels North America.

Fig. 26 is a chart showing the distribution of tidal phases with differences between Tidal Day and Tidal Period times shown for diurnal, semidiurnal and mixed tides.

DETAIL DESCRIPTION OF SEVERAL EMBODIMENTS

In the following description of several embodiments of the present invention, the following definitions and abbreviations are used: (a) the phrase Wave Energy Conversion Apparatus and Method herein referred to as "WEC" refers to the overall general description of the apparatus and method of the present invention; (b) a Tidal Compensation Apparatus and Method, or Tidal Compensator refers to the method and apparatus which accommodates the changes in the surface water level, where the prime mover waves are located, relative to the sea bed due to tidal action, herein referred to as "Tidal Compensator" or "TC"; (c) in each embodiment of the TC in the present invention one or more floats are shown as a part, these floats are not the same as the motive float or point absorber, described below, and are thus distinguished and referred to as "Tidal Compensator Float(s)" or "TC Float(s)"; (d) the reciprocating wave surge converter is referred to as a Wave Energy Converter or as an Energy Converter and specifically refers to the method and apparatus to drive relatively high speed rotary generators efficiently from the prime mover of slow moving reciprocating wave motion; (e) a first sub system in the Energy Converter is the conversion of the energy in water waves into reciprocating motion utilizing a motive float point absorber which is the receiver of the kinetic energy transferred to it by the prime mover waves interacting with its buoyancy and mass, herein referred to as "Motive Float", or as "Point Absorber" which terms are used interchangeably; (f) a second sub system in the Energy Converter is the conversion of reciprocating motion into rotational motion is referred to as "Motion Converter" and also as "UDR" which is an abbreviation of Uni-Directional Rotation; (g) a third sub system in the Energy Converter is the conversion of the slow wave produced rotational motion into rotation motion of a speed sufficient to run an electric generator efficiently is referred to as "Power Conversion Means" or "PCM".

Fig. 1A and Fig.l B illustrates a particular embodiment of the invention showing a complete WEC in general and parts concerning the Tidal Compensator, the "TC", are described in detail herein: 111 shows the TC part and 112 shows the energy converter part and 113 shows the cover which is the most noticeable part of the WEC from persons viewing it from onshore or in passing vessels, including kayaks. 114 shows the water level line at high tide, 115 shows the water line at the tide level for this instance of the drawing, 116 shows the water level line at low tide and 117 shows the seabed line. The pile noted as 118-1 and 118-2 is a single metal pile, it may or may not have a protective coating; and, is sunk into the seabed as shown by the 118-1 portion and extends above the seabed by the 118-2 portion. A TC float 119 surrounds slider 128 with sufficient buoyancy to keep the energy converter above the water level and provide enough extra buoyancy to ensure that the energy converter has a stable base sufficient to act as an opposing body for it to react against to facilitate the conversion of the motive float's 140 kinetic energy, from the buoyant force which the waves exert on the motive float into commercially useful energy. For example, for greater clarity and not limited to the specifics, the general factors to include for the calculation of the buoyancy required in the tidal compensator float would include: the weight of the entire tidal compensation apparatus that slides up and down the pile, an additional factor in the 15% range to allow for sliding friction and fouling debris, the weight of the energy converter including the covering, the upthrust of the waves on the motive float determined by its buoyancy, mass and area in contact with the waves with respect to the height of the waves and their period.

TC slider 128 slides up and down the pile on strips 127 of a slippery material to reduce friction, for example but not limited to, 8 strips equally spaced around the pile and screwed into tapped holes in the pile. The slippery material of the strips 127 may be for example typically Polyethylene Acrylonitrile Butadiene Styrene (PE/ABS) or Polycarbonate/Acrylonitrile Butadiene Styrene (PC/ABS) or Melamine formaldehyde (MF) or Polyetheretherketone (PEEK) or Polytetrafluoroethylene (PTFE) aka Teflon or Polymethyl methacrylate (PMMA) or Ultra high molecular weight (UHMW) polyethylene or Polyoxymethylene (POM), in the present embodiment ultra high molecular weight (UHMW) polyethylene is used for these strips. The strips begin a small distance down from the top of the pile, for example but not limited to 4 inches to facilitate mounting the slider and TC framework on the pile and extends continuously to below the lowest point the slider can go, which in the preferred embodiment is, to the seabed but for various reason may be less.

120 and 121 show the framework of the TC which supports the base of the energy converter at a point always below the current water level 115 so that the motive float, which resides inside the framework of the energy converter is always in a position to be affected by the waves, as the water level, relative to the seabed, changes due to tides. The length of the pile 118-1 and 118-2 is determined firstly by the conditions of the seabed, for example but not limited to, whether it be rock or sand or mud, in the embodiment shown a rock base is assumed and the pile would then be grouted into a hole drilled in the rock and the corresponding length of the 118-1 portion of the pile would be shortest when compared to other seabed types; and secondly by the difference in length between the spring low tide and the spring high tide levels for a particular location where the WEC is being deployed with additional allowance made for weather extremes at these times, such that the slider part of the TC, 119,120 and 121 is arranged so that the bottom of the tidal compensator float will not hit the seabed and the tidal compensator float will not rise up beyond the top of the pile. This pile is located at a depth in the water so that the top of the pile, is below the water level at low tide. For example but not limited to, in the embodiment shown here with respect to the wave heights of the location where this WEC is deployed, the distance from the bottom of the energy converter frame to the bottom of the motive float when it is floating in still water is 5 feet, thus the top of the tidal compensator 121 is always 5 feet below the water level during the changes of this level due to tides; and, as the tidal compensator slider shown in Figs 3-6 is 3 feet long, and the top of the pile is positioned 2 feet below the surface of the water at low tide, this then, allows for the tidal compensator slider(s) to bounce up 2 feet before the top of the tidal compensator slider(s) reaches the top of the pile and another 3 feet before the tidal compensator slider(s) can be removed from the pile.

A method of controlling the movement of the tidal compensator is by: transducer sensor 122 reporting the distance from the sensor to the sea level to a computer, not shown, which on a timely basis, for example but not limited to every 5 minutes, assesses the sensor distance information, takes an average over the previous 30 seconds, compares this distance to the set distance and determines if the tidal compensator needs to be adjusted and if so which direction, either up or down, and sends a signal to rotate the winch 123 to pull or release the wire rope cable or chain 124 the amount required to make the adjustment. The cable or chain 124 runs through a pulley 125 of the side of the TC frame 120 and is pivoted via pulley 126 which is fixed to the top of the pile. As the tidal compensator float is in positive buoyancy when the winch pulls the cable or chain up the tidal compensator goes down and when the winch is released the tidal compensator rises. Fig. 2A and Fig. 2B Illustrates complete WEC in general and another embodiment of the invention showing parts of the TC that are described in detail herein. With reference to Fig. 1A and Fig. 1 B this illustration shows similar conditions and parts as follows: 211 shows the TC part and 212 shows the energy converter part and 213 shows the cover, 114 shows the water level line at high tide, 115 shows the water line at the tide level for this instance of the drawing, 116 shows the water level line at low tide and 117 shows the seabed line. The single pile in Figs. 1 A & 1 B is shown here with 2 piles 218-1 and 218-2, as described in 118-1 and 118-2 they are the same size and length and both have slippery strips 227 similar to 127. In this embodiment 2 sliders 228 inter-connect the TC float into the framework between the piles which supports vertical framework 220 and top framework 221. The operation of moving the TC with respect to changing water levels due to tides is the same as in Figs. 1A & B or it may utilize the illustrated double pulley system which shows the cable or chain 224 running around side pulley 225 and pivoting via pulley 226A fixed to the top of one pile then pivoting via another pulley 229 fixed to the bottom of the TC top framework 221 , then pivoting via another pulley 226B fixed to the top of the other pile and then fixed to the base of the TC top platform 221 which will give a mechanical advantage to the load and center the loading on both piles and the TC framework which load is moved by the winch 223 controlled by a computer, not shown, with respect to data received from transducer sensor 222. The result of the movement of the TC is that the motive float 240 is maintained in a position to be affected by the wave as the water surface changes height relative to the seabed due to tides.

Fig. 3A and Fig. 3B illustrates complete WEC in general and another embodiment of the invention showing parts of the TC that are described in detail herein: 311 shows the TC part and 312 shows the energy converter part and 313 shows the cover, 314 shows the water level line at high tide, 316 shows the water level line at low tide and 317 shows the seabed line. In these illustrations the water level is assumed to be at the low tide level shown as 316. The pile noted as 318-1 and 318-2 is a single metal pile which may or may not have a protective coating is sunk into the seabed as shown by the 318-1 portion and extends above the seabed by the 318-2 portion. A slider 328 is integrated with the vertical framework 320 and the horizontal beam framework 329 such that it slides up and down the pile on slider strips 327 as described above 127. The TC float 332 is connected to the TC float rod 330 via a spring shock absorber 331. The TC Float has sufficient buoyancy to maintain the base of the energy converter, which is fixed to the TC top frame 321, at the depth required to maintain the motive float 340 at the correct height with respect to the water level as it changes with the tides as described in the buoyancy description above Figs. 1A and 1 B. The spring shock absorber 331 is an extension and contraction spring made to buffer the load of the waves on the TC float both with regards to spring strength and to spring travel distance in either the expansion direction and the contraction direction. In this embodiment the spring and its casing is made of salt water resistant stainless steel. The spring 331 may be covered with a dual direction accommodating shock absorber type casing or not.

What you need to know about the method of operation of this TC embodiment is that the TC float firstly maintains a buoyancy balance to keep the energy converter in the correct position with respect to the water level changes due to tides and secondly the TC float does not ride the wave(s) with the same frequency and amplitude as does the motive float, in fact it must not. This is accomplished by a combination of the following: the mass of the TC float, which is approximately, but not limited to, 10 times the mass of the motive float and hence does not move the same way in the same wave; the shape of the TC float bottom, which is designed to be the most stable; the spring which is designed to absorb the energy moving the TC float in both upward, spring extension, and downward, spring contraction, directions for, in this embodiment, but not limited to, most of the average wave amplitude for the deployed location; and, the tolerance of the slider 328 on the slippery strips which is, for example, but not limited to, .125 to .25 inches, and is such that as the TC float moves the TC framework 330, 329, 320 and 321 the slider jams against the slippery strips with such force that it adds an additional drag to the movement of the TC and thereby also helps to reduce the movement translated to the TC top framework from wave action on the TC float. This additional drag on the movement of the TC occurs due to wave action unbalancing the TC and preventing it from sliding to compensate for changes in water level due to tides which is a slow moving change in water level as described in FIG. 26 where Tidal Periods, which is the length of time between successive high or low tides and which is either 24 hours and 50 minutes or 12 hours and 2 minutes for all locations of earth, are shown; however the wave action also enables the TC to be in balance sufficiently long enough for it to slide and accommodate the changes in water level due to tides, and, during the periods of unbalance the additional drag, the jamming, enhanced by the length of the horizontal beam framework 329, 429, 529 and 629 acting as a lever with the slider 328 as fulcrum, is sufficient on to itself to provide, through the pile embedded in the seabed a reactive force against which the point absorber WEC moves. Fig. 3C, 3D, 3E, 3F, 3G and Fig. 3H illustrates a complete WEC in general and another embodiment of the invention utilizing a single pile and showing parts of the TC that are described in detail herein: with reference to Fig. 3A and Fig. 3B the illustration in Fig. 3C shows 311 shows the TC part, 312 shows the energy converter part, 313 shows the cover, 314 shows the water level line at high tide, 316 shows the water level line at low tide and 317 shows the seabed line. In these illustrations the water level is assumed to be at the low tide level shown as 316. The pile noted as 318-1 and 318-2 is a single metal pile which may or may not have a protective coating is sunk into the seabed as shown by the 318-1 portion and extends above the seabed by the 318-2 portion. A slider 339 is integrated with the vertical framework 337 and 338 and with the horizontal beam framework 341 and 342 such that it slides up and down the 318-2 part of the pile on slider strips 346, described in Figs. 3G and 3H below. The two metal strips 334, shown in more detail in Figs. 3F and 3G, are welded to either side of the pile 318-2 to prevent the slider 339 from turning around the pile by the method shown in Figs. 3G and 3H. The individual TC floats 335 and 336 are made up of a series of removable and interchangeable floats which are directly and stiffly connected to the vertical framework 338 and 337. The TC Floats 335 and 336 have sufficient buoyancy, the "total buoyancy" to maintain the base of the energy converter, which is fixed to the top of framework 337, at the depth required to maintain the motive float 340 at the correct height with respect to the water level as it changes with the tides as described in the buoyancy description above Figs. 1A and 1 B, this total buoyancy required is proportioned between TC floats 335 and 336 in a ratio of approximately between two thirds at 335 and one third at 336 and three quarters at 335 and one quarter at 336. The horizontal frameworks 341 and 342 are stiffly fixed to the slider 339 and the vertical frameworks 338 and 337; and, the length of the frameworks 341 and 342 may be equal or not equal in length. The vertical frameworks 338 and 337 are not equal in length. Heave plates 343 and 344 are attached to the bottom of the horizontal frameworks 341 and 342. The illustration in Fig. 3D shows a perspective detail view of the TC part of Fig. 3C, the TC slider 339 is shown positioned around the upper part 318-2 of the pile with one of the metal strips 334 attached. The individual TC floats 335 and 336 which are made up of a series of removable and interchangeable floats are fixed in the frameworks 335A and 336A to accommodate removing and adding individual floats to adjust buoyancy as required and the heave plates 343 and 344 are shown attached to the bottom horizontal frameworks. Fig. 3E shows the complete pile, in perspective view, made up of the 318-1 and the 318-2 parts with one of the metal strips 334 attached along the entire length of the 318-2 part and the TC slider 339 positioned around the pile and located near the upper end of the pile. Fig. 3F shows a perspective detail of the top end of the 318-2 part of the pile where the two metal strips 334 are shown attached to the pile opposing each other. Fig. 3G shows the section AA of Fig. 3C, in plan view, to illustrate the relationship between the TC slider 339 and the upper 318-2 portion of the pile. The two metal strips 334 are shown attached to the outside of the 318-2 pile and the 339 slider is shown positioned around the 318-2 pile such that the two metal strips on the 318-2 pile are located between the two pair of metal strips 345 which are welded to the inside of the slider pile 339. Four slippery material strips 346 of a material as described by 127 in Figs. 1A and 1 B are located approximately equal distance from each other around the inside of the slider 339 and fastened with countersunk screws to the inside surface and run the entire length of the 339 slider. Fig. 3H is a perspective detail view of the slider 339 that shows the positions of the two pairs of metal strips 345 and the four slippery strips 346 attached to the inside of the slider 339.

Fig. 4A and Fig. 4B illustrates complete WEC in general and another embodiment of the invention showing parts of the TC that are described in detail herein: with reference to Fig. 3A and Fig. 3B this illustration 411 shows the TC part and 412 shows the energy converter part and 413 shows the cover, 414 shows the water level line at high tide, 415 shows the water level for the tide level in this instance of the drawing, 416 shows the water level line at low tide and 417 shows the seabed line. The single pile 418-1 for the portion embedded in the ground and 418-2 for the portion of the pile extending upward into the water with slippery sliders attached 427 as previously described 127. The TC consists of a slider 428 and a vertical framework 420 and 421. In this exemplary embodiment 2 TC opposable floats 432 are shown on either side of the slider held in place by the horizontal beams 429, 2 vertical rods 430, and the 2 springs 431 as previously described 331. The operation of the TC keeps the motive float 440 consistently in the waves as the water level changes due to tides.

Fig. 5A and Fig. 5B illustrate a complete WEC according to one embodiment in general and another embodiment of the invention showing parts of the TC that are described in detail herein: with reference to Fig. 2A and Fig. 2B which shows a 2 pile embodiment, 511 shows the TC part and 512 shows the energy converter part and 513 shows the cover, 514 shows the water level line at high tide, 515 shows the water level for the tide level in this instance of the drawing, 516 shows the water level line at low tide and 517 shows the seabed line. The 2 piles 518-1 for the portion embedded in the ground and 518-2 for the portion of the pile extending upward into the water are the same size and length both have slippery sliders attached 527 as previously described 127. The TC consists of 2 sliders 528 and a vertical framework 520 and 521 with 1 horizontal beam 529 supporting rod 530 with spring 531 and TC float 532 all as previously described. The operation of the TC keeps the motive float 540 consistently in the waves as the water level changes due to tides.

Fig. 6A and Fig. 6B illustrates complete WEC in general and another embodiment of the invention showing parts of the TC that are described in detail herein: with reference to Fig. 2A and Fig. 2B which shows a 2 pile embodiment, 611 shows the TC part and 612 shows the energy converter part and 613 shows the cover, 614 shows the water level line at high tide, which for these illustrations is the level the water is assumed to be at, 616 shows the water level line at low tide and 617 shows the seabed line. The 2 piles 618-1 for the portion embedded in the ground and 618-2 for the portion of the pile extending upward into the water are the same size and length both have slippery sliders attached 627 as previously described 127. The TC consists of 2 sliders 628 and a vertical framework 620 and 621 with 2 horizontal beams 629 supporting 2 rods 630 with 2 springs 631 and 2 TC floats 632 all as previously described. The operation of the TC keeps the motive float 640 consistently in the waves as the water level changes due to tides.

Fig. 7 illustrates three sections of an embodiment of the invention: grouping A is the Up UDR (Uni Directional Rotation) or, motion converter, which utilizes upward vertical motion, grouping B is the Down UDR or, motion converter, which utilizes downward vertical motion, and grouping C is the main drive shaft which rotates in a uni-direction from the method and apparatus of the Up UDR and the Down UDR. The Up UDR wherein connecting rod 711 transfers prime mover force from movement of motive float, for example 140 shown on Fig.lA and 1 B, due to water wave action in an up and down motion, is connected by connector 712 to an endless chain 713, which in another embodiment is a plain link chain, a poly link belt or a ribbed non-stretch timing-type belt, which runs over upper 714 and lower 715 sprockets, the upper sprocket is attached to clutch drive shaft 716 that has an overrunning clutch 718 mounted on it and a chain or belt clutch sprocket 719 is mounted on the output side of the overrunning clutch, the lower sprocket runs freely or drives another shaft 717, when connecting rod 711 moves upward 721 the clutch drive shaft 716 moves in a clockwise direction and the overrunning clutch engages and the clutch sprocket also rotates in a clockwise direction and moves chain or belt 720 in a clockwise direction 722. When connecting rod 711 moves downward the overrunning clutch does not engage and its clutch sprocket does not rotate. 0001) The Down UDR or, motion converter, wherein connecting rod 731 similarly connected to motive float for example 140, is connected by connector 732 to an endless chain 733 which runs over upper 734 and lower 735 sprockets, the upper sprocket is attached to clutch drive shaft 736 that has an overrunning clutch 738 mounted on it and a chain or belt clutch drive sprocket 739 mounted on the output side of the overrunning clutch, the lower sprocket runs freely or drives another shaft 737, when connecting rod 731 moves upward the clutch drive shaft 736 moves in a counter clockwise direction and the overrunning clutch is oriented so as to not engage in this direction and the attached clutch sprocket also does not rotate. When connecting rod 731 moves downward 741 the clutch drive shaft moves in a clockwise direction and the overrunning clutch engages and the attached clutch sprocket also rotates in a clockwise direction and moves chain or belt 740 in a clockwise direction 742. In this embodiment one connecting rod, 711 and 731 , is connected to each UDR unit, however more connecting rods may be utilized.

Fig. 8A illustrates an embodiment where: two connecting rods 811 A and 811 B are connected to the Up UDR or, motion converter, which operates as a motion converter when these connecting rods move upwards as indicated by arrows 821 A and 821 B; and two connecting rods 831 A and 831 B are connected to the Down URD or, motion converter, which operates as a motion converter when these connecting rods move downwards as indicated by arrows 841 A and 841 B. Each pair of said connecting rods causing their respective chain connectors 812A & 812B and 832A & 832B to move their respective endless chains 813A & 813B and 833A & 833B to move their respective chain sprockets 814A & 814B and 834A & 834B where clutch sprockets 819 and 839 are moved as described for the clutch sprockets 719 and 739 via their respective clutches 818 and 839.

Connected to the clutch sprockets 819 and 839 are chains or belts 820 and 840 which move in the direction indicated by arrows 822 and 842 and cause corresponding chain or belt sprockets 852 and 853 to rotate the main drive shaft 851. Main drive sprockets 852 and 853 may be the same diameter as clutch sprockets 819 and 839, for example typically about three inches to twenty four inches in diameter, however the main drive sprockets may be smaller in diameter than the clutch sprockets so as the create an increaser gear ratio, in the present embodiment these sprockets 852 and 853 are about five inches in diameter and the clutch sprockets 819 and 839 are about 8 inches in diameter, hence the increaser ratio is about 1.6 times so, for example typically the useful RPM of the clutch drive shaft ranges between about 20 and 100 RPM, then with this increaser ratio, the speed of the main drive shaft would be increased to about 32 to 160 RPM, in other embodiments this range could be larger or smaller depending on the ratio between the corresponding sprockets 819 and 852 for the Up UDR and 839 and 853 for the Down UDR.

In this embodiment the Up UDR and the Down UDR units face each other such that connecting rods 811 A and 811 B are positioned between the up chain sprocket shaft 817 and the main drive shaft 851 or, main drive shaft support frame 861 , and, connecting rods 831 A and 831 B are positioned between the down chain sprocket shaft 837 and the main drive shaft 851 or, main drive shaft support frame 861 , which is referred to in Figs. 9A and 9B as the inside position, and, in Figs. 9C and 9D as the outside position when the connecting rod or rods are located on the other side of their respective chain sprocket shafts 817 and 837. These inside and outside embodiment positions for the connecting rods are shown in Fig. 9A, 9B, 9C and 9D. Also in this embodiment Fig. 8A, the overrunning clutch in the Up UDR unit 818 is shown oriented to engage when its shaft turns clockwise and in the Down UDR unit the overrunning clutch 838 is shown also oriented to engage when its shaft turns clockwise. Other embodiment orientations for the overrunning clutches are shown in Fig. 9A, 9B, 9C and 9D.

Fig. 8B shows section BB of Fig. 8A wherein for the Up UDR, connecting rods 811 A and 811 B are shown between shaft 817 and the framework for the main drive shaft 851 , framework 860 is shown as well as lower chain sprockets 815A and 815B with chains 813A and 813B attached. For the Down UDR connecting rods 831A and 831B are shown between shaft 837 and the framework for the main drive shaft 851 , corresponding framework 860 is shown as well as chain sprockets 835A and 835B with chains 833A and 833B attached.

Fig. 8C shows section CC of Fig. 8A wherein for the Up UDR, connecting rods 811 A and 811 B are shown with connectors 821 A and 821 B and upper chain sprockets 814A and 814B as well as upper shaft 816 with overrunning clutch 818 and clutch sprocket 819 with belt 820 which connects to sprocket 852 on main drive shaft 851. For the Down UDR, the same parts as for the UP UDR are shown and specifically upper shaft 836 with overrunning clutch 838 and clutch sprocket 839 with belt 840 which connects to sprocket 853 on main drive shaft 851 are detailed.

Fig. 8D shows the lower force springs 870A positioned around the two rods 811 A and 811 B where force springs 870A are located such that they can rest on the bottom plate of the framework 860 and when the movement of motive float, for example 140 shown on Fig.lA and 1 B moves the rods 811 A and 811 B downwards then: when, more than the expected nominal design distance, due to, for example, storm waves or other excessive waves, the adjustment nut 871A would begin to collapse the force spring 870A and thereby mainly buffer the bottom framework from being impacted with damaging force but also provide an enhanced upward force to the rods 811 A and 811B as the springs release the stored energy as the waves move the rods upwards; or, when, the force springs 870A are installed so that the impact from the adjustment nut occurs when nominal waves move the rods 811 A under normal conditions the force springs act mainly as a force absorber and force enhancer to move the rods upwards and thereby move the chain connectors 812A and 812B and the endless chains 813A and 813B with the addition of the stored force in the force spring as well as act to buffer the bottom framework from being impacted with damaging force from excessive waves. FIG 8D also shows upper force springs 870B which are attached around the top end of the rods 811 A and 811 B which protrude past the upper adjustment nut 871 B for a distance less than the collapsed distance of the springs 870B, force springs 870B rest on the top of nut 871 B and when the rods 811 A and 811 B are driven upwards by the wave action on the motive float then the upper force springs are guided to contact the bottom of the top framework plate 860 by the spring alignment- receiver 872 and the behavior of the upper force springs is the same as described for the lower force springs 870A with respect to buffering and providing enhanced force to the energy conversion system. Fig. 8E shows the location of the spring alignment-receivers 872 on the bottom side of the top framework plate 860T whereby the center of the opening in the spring alignment-receiver is exactly in line with the center of the hole for the rods 811 A and 811B in the bottom framework plate 860B. Fig. 8F shows the spring alignment- receiver plate 872 attached to the bottom 877 of the top framework plate 860T with the following particulars: the thickness of the plate 876 is approximately between 0.25 inch and 1.5 inches, the inner diameter 874 of the bottom cutout in the plate 872 which faces the bottom side 877 of the top framework plate is approximately equal to or not more that 10 percent larger than the outside diameter of the upper spring 870B, the diameter of the top cutout edge 873 in the plate 872 is not less than 10 percent larger than the inner cutout diameter 874 and not more than 40 percent larger than the inner cutout diameter 874, and the transition surface between the inner 874 and the outer 873 diameters is a straight line 875 and not convex or concave.

Figs. 9A, 9B, 9C and 9D illustrate the four possible embodiments of the various alternative positions of the connecting rods and the orientation of the overrunning clutches on the clutch drive shafts for both the Up UDR and the Down UDR units to enable the transfer of power in a unidirectional rotational motion to the main drive shaft from the up and down wave reciprocations on the motive float.

Fig. 9A shows connecting rods 911 and 931 both located between clutch shafts 914, 934 and main drive shaft 921 respectively, and, overrunning clutch 915 and overrunning clutch 935 both oriented so that the clutches grab when their respective clutch shaft moves in a clockwise direction as shown by the arrows 916 and 936; alternatively both clutches 915 and 935 would then freewheel when their respective clutch shafts move in a counter clockwise direction.

In an embodiment of the present embodiment shown as Fig.9A the UP UDR is designated as 941 : when connecting rod 911 moves upward the endless chain or belt 912 would move sprocket 913 and consequently would move clutch shaft 914 in a clockwise rotation direction which would move clutch sprocket 917 in a clockwise direction because overrunning clutch 915 grabs when the clutch shaft moves in a clockwise direction, and, the chain or belt 918 would move in a clockwise direction and move the main drive sprocket 919 such that it would cause main drive shaft 921 to move in a clockwise direction; and, when connecting rod 911 moves downward chain 912 moves sprocket 913 which moves shaft 914 in a counter clockwise motion and sprocket 917 does not move because clutch 915 does not grab when its shaft turns in a counter clockwise direction. The Down UDR is designated as 942: when connecting rod 931 moves downward the endless chain or belt 932 would move sprocket 933 and consequently would move clutch shaft 934 in a clockwise rotation direction which would move clutch sprocket 937 in a clockwise direction because overrunning clutch 935 grabs when the clutch shaft moves in a clockwise direction, and chain or belt 938 would move in a clockwise direction and move main drive sprocket 939 such that it would cause main drive shaft 921 to move in a clockwise direction; and, when connecting rod 931 moves upward chain 932 moves sprocket 933 which moves shaft 934 in a counter clockwise motion and sprocket 937 does not move because clutch 935 does not grab when its shaft turns in a counter clockwise direction.

Fig. 9B shows connecting rods 911 and 931 both located between clutch shafts 914, 934 respectively, and main drive shaft 921 and overrunning clutch 915 and overrunning clutch 935 both oriented so that the clutches grab when their respective clutch shaft moves in a counter clockwise direction and alternatively both clutches 915 and 935 would then freewheel when their respective clutch shafts move in a clockwise direction.

In the present embodiment shown as Fig. 9B the Down UDR is designated as 941: when connecting rod 911 moves downward the endless chain or belt 912 would move sprocket 913 and consequently would move clutch shaft 914 in a counter clockwise rotation direction which would move clutch sprocket 917 in a counter clockwise direction because overrunning clutch 915 grabs when the clutch shaft moves in a counter clockwise direction, and, chain or belt 918 would move in a counter clockwise direction and move main drive sprocket 919 such that it would cause main drive shaft 921 to move in a counter clockwise direction; and, when connecting rod 911 moves upward chain 912 moves sprocket 913 which moves shaft 914 in a clockwise motion and sprocket 917 does not move because clutch 915 does not grab when its shaft turns in a clockwise direction. The UP UDR is designated as 942: when connecting rod 931 moves upward the endless chain or belt 932 would move sprocket 933 and consequently would move clutch shaft 934 in a counter clockwise rotation direction which would move clutch sprocket 937 in a counter clockwise direction because overrunning clutch 935 grabs when the clutch shaft moves in a counter clockwise direction, and chain or belt 938 would move in a counter clockwise direction and move main drive sprocket 939 such that it would cause main drive shaft 921 to move in a counter clockwise direction; and, when connecting rod 931 moves downward chain 932 moves sprocket 933 which moves shaft 934 in a clockwise motion and sprocket 937 does not move because clutch 935 does not grab when its shaft turns in a clockwise direction.

Fig. 9C shows connecting rods 911 and 931 both located on the outside of clutch shafts 914, 934 and overrunning clutch 915 and overrunning clutch 935 both oriented so that the clutches grab when their respective clutch shaft moves in a clockwise direction and alternatively both clutches 915 and 935 would then freewheel when their respective clutch shafts move in a counter clockwise direction.

In the present embodiment shown as Fig. 9C the Down UDR is designated as 941: when connecting rod 911 moves downward the endless chain or belt 912 would move sprocket 913 and consequently would move clutch shaft 914 in a clockwise rotation direction which would move clutch sprocket 917 in a clockwise direction because overrunning clutch 915 grabs when the clutch shaft moves in a clockwise direction, and chain or belt 918 would move in a clockwise direction and move main drive sprocket 919 such that it would cause main drive shaft 921 to move in a clockwise direction; and, when connecting rod 911 moves upward chain 912 moves sprocket 913 which moves shaft 914 in a counter clockwise motion and sprocket 917 does not move because clutch 915 does not grab when its shaft turns in a counter clockwise direction.

The UP UDR is designated as 942: when connecting rod 931 moves upward the endless chain or belt 932 would move sprocket 933 and consequently would move clutch shaft 934 in a clockwise rotation direction which would move clutch sprocket 937 in a clockwise direction because overrunning clutch 935 grabs when the clutch shaft moves in a clockwise direction, and chain or belt 938 would move in a clockwise direction and move main drive sprocket 939 such that it would cause main drive shaft 921 to move in a clockwise direction; and, when connecting rod 931 moves downward chain 932 moves sprocket 933 which moves shaft 934 in a counter clockwise motion and sprocket 937 does not move because clutch 935 does not grab when its shaft turns in a counter clockwise direction.

Fig. 9D shows connecting rods 911 and 931 both located on the outside of clutch shafts 914, 934 and overrunning clutch 915 and overrunning clutch 935 both oriented so that the clutches grab when their respective clutch shaft moves in a counter clockwise direction and alternatively both clutches 915 and 935 would then freewheel when their respective clutch shafts move in a clockwise direction.

In the present embodiment shown as Fig. 9D the UP UDR is designated as 941: when connecting rod 911 moves upward the endless chain or belt 912 would move sprocket 913 and consequently would move clutch shaft 914 in a counter clockwise rotation direction which would move clutch sprocket 917 in a counter clockwise direction because overrunning clutch 915 grabs when the clutch shaft moves in a counter clockwise direction, and chain or belt 918 would move in a counter clockwise direction and move main drive sprocket 919 such that it would cause main drive shaft 921 to move in a counter clockwise direction; and, when connecting rod 911 moves downward chain 912 moves sprocket 913 which moves shaft 914 in a clockwise motion and sprocket 917 does not move because clutch 915 does not grab when its shaft turns in a clockwise direction. The Down UDR is designated as 942: when connecting rod 931 moves downward the endless chain or belt 932 would move sprocket 933 and consequently would move clutch shaft 934 in a counter clockwise rotation direction which would move clutch sprocket 937 in a counter clockwise direction because overrunning clutch 935 grabs when the clutch shaft moves in a counter clockwise direction, and chain or belt 938 would move in a counter clockwise direction and move main drive sprocket 939 such that it would cause main drive shaft 921 to move in a counter clockwise direction; and, when connecting rod 931 moves upward chain 932 moves sprocket 933 which moves shaft 934 in a clockwise motion and sprocket 937 does not move because clutch 935 does not grab when its shaft turns in a clockwise direction.

Figs. 10A and 10B illustrates an embodiment of the invention showing energy converter with a flywheel 1011 mounted on the main drive shaft 1020, same as 851, with a flywheel sprocket 1013 attached to it, a chain or belt 1014 is shown around the flywheel sprocket 1013 driving upper main drive sprocket 1015 which is mounted on upper main drive shaft 1016 which drives 2 generators, 1017 and 1018 which may be activated separately.

Flywheel 1011 is of a weight and diameter commensurate with the loads transferred from a motive float of various sizes, for example typically the weight of the flywheel ranges from about 500 lbs. to about 10,000 lbs. and ranges in diameter from about twenty-four inches to about one hundred and twenty inches, in the present embodiment, the flywheel is about forty-eight inches in diameter and weighs about 1600 lbs., and is mounted on the main drive shaft 1020 and in this embodiment turns in a clockwise direction 1012 which is the same as 851. For clarity the following parts are shown to illustrate the connectivity of the main drive shaft 1020 with a UDR: connecting rod moves downward 1023 and hence chain or belt 1022 is shown moving main drive shaft sprocket 1021 and hence the main drive shaft in a clockwise direction by arrow 1019.

In one embodiment, a "flywheel effect", is only part of the reason for using a flywheel in a WEC. It is here used primarily to act as an energy accumulator and concentrator: as from a calm water situation where the flywheel is not moving, the first wave moves the motive float and the up and down reciprocations are converted to rotational motion in the UDRs and this rotational motion is transferred to the flywheel. At first the flywheel moves a very small amount, in fact if the wave is small there may not be enough energy present to overcome the flywheel and the system's inertia and another larger wave is required just to overcome inertia. When a wave with more than enough energy to overcome the flywheel's inertia and the system's friction then the flywheel will start to move, and then if the next wave comes before the flywheel stops the energy from this next wave is available to be added to the existing rotational energy, and so on and so forth, the energy from successive waves is thereby accumulated and concentrated in the flywheel by adding to the speed of the flywheel which will continue until natural forces cause the flywheel to slow or until some, or all of the available energy is used to do work, such as generate electricity.

Flywheel Sprocket 1013 is attached to the flywheel, for example typically the flywheel sprocket is part of the outer edge of the flywheel or attached so as to protrude beyond the outer edge or it can be attached to the side of the flywheel and be of a lesser diameter than the outer edge of the flywheel, in the present embodiment the flywheel chain sprocket is made as an "A" plate sprocket ring with about 200 teeth and is about 50 inches in outside diameter and about 42 inches inside diameter and is mounted on the side of the flywheel 1011 such that the teeth on the sprocket protrude beyond the outer edge of the flywheel.

Flywheel chain 1014 connects the flywheel to upper main drive sprocket 1015 which has a diameter smaller than the flywheel sprocket to create an increaser gear ratio, for example but not limited to, sprocket 1015 is typically about 3 inches to 18 inches in diameter, in the present embodiment the upper main drive sprocket 1015 is about 6 inches in diameter so the increaser ratio is about 8.3 times, so, for example in this embodiment typically the main drive shaft RPM, and consequently of the flywheel, ranges between about 32 and 160 RPM, then, the speed of the upper main drive shaft 1016, would be in the range about 265 to 1328 RPM, in other embodiments this range could be larger or smaller. Generators 1017 and 1018 are connected or driven, either one or both, by the upper main drive sprocket shaft 1016 and thus electricity may be generated when the upper main drive sprocket shaft is rotating at minimum speed required by either one or both the generators. In the illustrated embodiment of Figs. 11 A and 11 B Flywheel chain 1114 connects from flywheel sprocket 1113 on flywheel 1111 to upper main drive sprocket 1115, which is attached to upper main drive shaft 1116, similar to the embodiment described in Figs. 10A and 10B, however in this embodiment upper main drive shaft 1116 has two increaser gears, 1117 and 1118 driven from it, for example in this embodiment, similar to Figs. 10A and 10B, the speed of the upper main drive shaft 1116 would be in the range about 265 to 1328 RPM, in other embodiments this range could be larger or smaller.

Increaser gear sprocket 1117 rotates in the same direction 1119 as the flywheel 1112 and is driven from the upper main drive shaft 1116 and is of a diameter sized to suit the range of speed desired at the generator drive sprocket 1123, which by chain or belt 1121, for example typically the increaser gear sprocket 1117 is about 4 inches to 24 inches in diameter and its corresponding generator drive sprocket 1123 is about 3 inches to 8 inches in diameter, in the present embodiment the increaser gear sprocket 1117 is about 18 inches in diameter and the generator drive sprocket 1123 is about 4 inches, hence the increaser ratio is about 4.5 times, so, for example in this embodiment typically the resulting RPM of the generator drive sprocket 1123, would be in the range about 1 , 150 to 5,975 RPM, in other embodiments this range could be larger or smaller. Generators 1125 and 1126 are connected, either one or both, to the generator drive shaft 1124 and thus electricity may be generated when the generator 19 shaft is rotating at minimum speed required by the generator or generators. Increaser drive sprocket 1118 rotating in the direction of arrow 1120, in this embodiment, similarly drives chain 1122 and sprocket 1127 and generator drive shaft 1128 and generators 1129 and 1130.

Figs. 12A, 12B and 12C are three perspective drawings of framework 1211 encompassing and containing rectangular motive float or point absorber 1214 which also provides a stable frame, which in one embodiment of this invention is connected to the seabed via one of the described embodiments of the TC, for the motive float to react against. The encompassing aspect of the framework 1211 provides protection for the motive float from people and from debris, it also enables the motive float to slide up and down, in alignment with the UDR units mounted above, on slippery guides, for example typically Polyethylene /Acrylonitrile Butadiene Styrene (PE/ABS) or Polycarbonate/Acrylonitrile Butadiene Styrene (PC/ABS) or Melamine formaldehyde (MF) or Polyetheretherketone (PEEK) or Polytetrafluoroethylene (PTFE) aka Teflon or Polymethyl methacrylate (PMMA) or Ultra high molecular weight (UHMW) polyethylene or Polyoxymethylene (POM), in the present embodiment ultra-high molecular weight (UHMW) polyethylene is used for these guides, which are attached to only the motive float 1215 or to the framework 1212 or to both the point absorber and the framework so that they glide against each other.

Two connecting rods 1216A and 1216B are attached to point absorber in this embodiment through nuts 1218 welded to point absorber and held also in alignment with the UDR units above by linear bearings 1217 attached to the top plate of framework 1211. Bumper safety buffers 1213 are located on the inside of the bottom and top framework plates to buffer point absorber from damage from contact with framework on occasions when high waves cause point absorber to reciprocate beyond the limit of the space inside the framework.

Figs. 13A and 13B are two perspective views of apparatus and method according to aspects of the invention, showing rectangular point absorber 1314 inside framework 1311 with bumpers 1313 attached to the top and bottom, guide strips attached to the edges of the framework 1312 and guide strips on the edges of the point absorber 1315, similar to Fig. 8A, 8B and 8C, but with four connecting rods 1316, to match with the four connection rods illustrated in Figs. 8A, 8B and 8C, are attached to the point absorber through four nuts 1318 and held in alignment with the UDR units above by linear bearings 1317 mounted on the top plate of framework.

Figs. 14A and 14B are two perspective views of apparatus and method showing rectangular point absorber framework similar to Figs. 12A and 12B and but here utilizing guide rails with bumpers attached to top and bottom of point absorber. In this embodiment two guide rails 1412A and 1412B, rather than the guide strips in Figs. 12A and 12B enable the point absorber 1414 to slide up and down in alignment with the UDR units mounted on the framework above, are depicted with the corresponding four guide rail linear bearings 1419 mounted through the top and bottom plates of the point absorber and four guide rail nuts 1418A and 1418B for attachment of guide rails to top and bottom plates of framework 1411. In this embodiment two bumper safety buffers 1413 are located on the top and bottom each of the point absorber to buffer the point absorber from damage from contact with the framework. Also shown are two connecting rods 1416A and 1416B and their respective linear bearings 1417 mounted in the framework 1411 and the connecting rod nuts 1420 connected to the top of the point absorber 1414.

Figs. 15A and 15B are two perspective views of apparatus and method according to aspects of the invention, showing cylindrical point absorber framework 1511 similar to Figs. 14A and 14B but with cylindrical point absorber 1514 shown in this embodiment rather than the rectangular point absorber, and four guide rails 1512A, 1512B, 1512C and 1512D rather than two guide rails in Figs. 14A and 14B , as well eight guide rail linear bearings 1519 are depicted mounted through the top and bottom plates of the point absorber and eight guide rail nuts 1518A, 1518B, 1518C and 1518D securing the guide rails to the top and bottom plates of the framework. In this embodiment two bumper safety buffers 1513 are located on the top and bottom each of the point absorber to buffer the point absorber from damage from contact with the framework. Also shown are four connecting rods 1516A, 1516B, 1516C and 1516D and their respective linear bearings 1517 mounted in the framework 1511 and the connecting rod nuts 1520 connected to the top of the point absorber 1514.

Figs. 16A, 16B and 16C are four perspective views of apparatus and method according to aspects of the invention, showing the internal structure 1611 of rectangle point absorber which includes top and bottom plates, vertical edge members, in this embodiment shown as angle pieces 1611 welded to top and bottom plates, and guide rail protectors 1612, also in this embodiment shown as pipe pieces and also welded to the top and bottom plates and of such a diameter as to allow the guide rail linear bearings 1613 to fit inside, which are used to protect the guide rails from entanglement with ballast and or closed cellular buoyancy foam deployed inside the point absorber structure. Horizontal structural members are shown adjacent to top and bottom plates and ballast mass 1618 is attached to bottom plate. Two bumper safety buffers 1616 are located on the top and bottom each of the point absorber to buffer the point absorber from damage from contact with the framework. Four connecting rods 1615 are attached to top plate by nuts 1614 welded to the top plate. Side cover plates 1617 are attached to vertical edge members to contain the ballast and buoyancy foam filling.

Figs. 17A, 17B and 17C are four perspective views of apparatus and method according to aspects of the invention, showing the internal structure 1711 of cylinder point absorber similar to Figs. 16A, 16B, 16C and 16D which in this embodiment includes top and bottom plates held apart by 4 pipe guide rail protectors 1712 welded to the top and bottom plates with 8 guide rail linear bearings 1713 shown inside guide rail protectors with horizontal structural members 1711 as angle pieces welded to guide rail protectors. Ballast 1718 is attached to bottom plate. Two bumper safety buffers 1716 are located on the top and bottom each of the point absorber to buffer the point absorber from damage from contact with the framework. Four connecting rods 1715 are attached to top plate by 4 nuts 1714. Covering 1717 is an open ended cylinder attached to the top and bottom plates to contain the ballast and buoyancy foam filling.

Fig. 18 is a perspective and a schematic drawing of the different embodiments of the rectangular point absorber using guide strips with respect to: four bottom types, flat 1811 , convex 1812, concave 1813 and pyramid 1814 with two and four connecting rods, eight embodiments shown as follows: flat bottom, two connecting rods 1815; flat bottom, four connecting rods 1816; convex bottom two, connecting rods 1817; convex bottom, four connecting rods 1818; concave bottom, two connecting rods 1819; concave bottom, four connecting rods 1820; pyramid bottom, two connecting rods 1821; pyramid bottom, four connecting rods 1822.

Fig. 19 is a perspective and a schematic drawing of the different embodiments of the rectangular point absorber using guide rails with respect to: four bottom types, flat 1911 , convex 1912, concave 1913 and pyramid 1914 with two and four connecting rods and two and four guide rails, sixteen embodiments shown as follows: flat bottom, two guide rails, two connecting rods 1915; flat bottom, two guide rails, four connecting rods 1916; flat bottom, four guide rails, two connecting rods 1917; flat bottom, four guide rails, four connecting rods 1918; convex bottom, two guide rails, two connecting rods 1919; convex bottom, two guide rails, four connecting rods 1920; convex bottom, four guide rails, two connecting rods 1921 ; convex bottom, four guide rails, four connecting rods 1922; concave bottom, two guide rails, two connecting rods 1923; concave bottom, two guide rails, four connecting rods 1924; concave bottom, four guide rails, two connecting rods 1925; concave bottom, four guide rails, four connecting rods 1926; pyramid bottom, two guide rails, two connecting rods 1927; pyramid bottom, two guide rails, four connecting rods 1928; pyramid bottom, four guide rails, two connecting rods 1929; pyramid bottom, four guide rails, four connecting rods 1930; Fig. 20 is a perspective and a schematic drawing of different embodiments of the cylindrical point absorber using guide rails with respect to: four bottom types, flat 2011 , convex 2012, concave 2013 and cone 2014, two and four connecting rods and two and four guide rails, sixteen embodiments shown as follows: flat bottom, two guide rails, two connecting rods 2015; flat bottom, two guide rails, four connecting rods 2016; flat bottom, four guide rails, two connecting rods 2017; flat bottom, four guide rails, four connecting rods 2018; convex bottom, two guide rails, two connecting rods 2019; convex bottom, two guide rails, four connecting rods 2020; convex bottom, four guide rails, two connecting rods 2021 ; convex bottom, four guide rails, four connecting rods 2022; concave bottom, two guide rails, two connecting rods 2023; concave bottom, two guide rails, four connecting rods 2024; concave bottom, four guide rails, two connecting rods 2025; concave bottom, four guide rails, four connecting rods 2026; pyramid bottom, two guide rails, two connecting rods 2027; pyramid bottom, two guide rails, four connecting rods 2028; pyramid bottom, four guide rails, two connecting rods 2029; pyramid bottom, four guide rails, four connecting rods 2030.

Figs. 21 A, and 21 B are two perspective views with shading of view of WECs embodiments per Fig. 1A and Fig. 3A as seen from shore or from a kayak wherein the WEC 2111 and the WEC 2113 with its tidal compensator float 2114 are shown as they appear relative to the water wave lines 2112 and 2115 at all tide levels, such as at low tide or at mid tide or at high tide. Thereby the visual impact of the WEC is minimized.

Fig. 22A is a perspective view of tidal compensation dampening spring showing the general parts: 2211 is the pipe encasing the spring itself, spring pipe, 2212 is the connector that holds the spring in a vertical position relative to the tidal compensator float, and 2213 is the connector that connects the spring to the tidal compensator framework as shown in FIGS. 3A, 4A, 5A and 6A.

Fig. 22B is a sectional perspective view of tidal compensation dampening spring according to an aspect of the invention, wherein 2211 shows the pipe in section, 2212 indicates the float connector which connects the spring to the tidal compensator float and 2213 indicates the base connector which connects the spring to the tidal compensator framework. The expansion - contraction spring, 2221 is shown in resting position, neither expanded nor contracted. The bottom end of the spring is shown extending through plate 2222 and welded to it, this bottom plate is welded to the bottom of spring pipe 2211; and the upper end of the spring is shown extending through plate 2223 which is free floating in the pipe and connected to slider bushing 2224 which in turn is connected to push rod 2225 which is fixed to the tidal compensator float, all of which as described in detail in Fig. 22E. Fig. 22C is a perspective view of connector 2213 that connects spring to the tidal compensator base, base connector. Four metal tubes 2231 are welded to the tidal compensator framework such that the ring 2232 extends above the top of the framework for about half the length the pipe

Fig. 22D is a perspective view of connector that connects spring to tidal compensator float, float connector. Circular metal plate 2241 provides the base for the connecting this float connector to the tidal compensator float and hole 2242 provides the connection means for connecting the spring push rod to the float connector. Four metal tubes 2243 are welded to the circular metal plate 2241 at the top end and are welded to circular metal ring 2244 at the bottom end, this ring has an inside diameter larger than the outside diameter of the spring pipe and plastic bushing ring 2245 is attached to circular metal ring and fits snuggly around spring pipe with inside edges cut with regular indentations to facilitate a linear bearing action as this bushing slides along the outside of the spring pipe. Fig. 22E is a perspective view of spring details, 2221 is the expansion - contraction spring the bottom end of which is attached to bottom spring plate 2222 and the upper end of the spring extends through plate 2223. Nut 2226C is welded to washer 2227 which is welded to upper spring plate 2223. Push rod 2225 is screwed into nut 2226C and bottom inside bushing support metal plate 2228 with hole in center for push rod and with a diameter less than the inside diameter of spring pipe 2211 rests on top of nut 2226C, inside plastic bushing 2224 rests on support plate 2228 and fits snuggly against the inside of spring pipe with inside edges cut with regular indentations to facilitate a linear bearing action as this bushing slides along the inside of the spring pipe. Upper inside bushing support metal plate 2229 with hole in center for push rod and with a diameter less than the inside diameter of spring pipe 2211 rests on top of inside plastic bushing 2224 and is held in place with nut 2226B tightened down on push rod. Nut 2226A connects push rod 2225 to bottom of float connector circular plate 2241.

The purpose of this spring system described in Figs 22A to D in one embodiment is to dampen the movement of the tidal compensator float, per Figs 3A to 6B, when it moves up and down due to wave forces, so that this up and down movement is not translated through the tidal compensator framework to the point absorber. When the waves cause the tidal compensator float to rise up it pulls the push rod with it and pulls the top of the spring up the pipe and thereby expands the spring, and, when the tidal compensator float moves downward due to wave forces, the TC float pushes the push rod downward and thereby compresses the spring, thus the forces moving the TC float are expended by causing the spring to expand and compress. This is enabled by 4 things; (1 ) the pipe encasing the spring extends past the upper end of the spring by an amount greater than the maximum expansion of the spring; (2) the inside slider bushing allows the spring to slide up and down inside the pipe while keeping the spring from distorting; (3) a base connector holds the spring pipe fixedly to the tidal compensator framework; (4) a float connector hold the spring pipe slideably connected to the TC float.

Fig. 23A is a side view of energy converter according to an aspect of the invention, covering showing layout details. Regular octagonal base 231 1 is shown with a diameter

2312 measured between opposed vertices of said base. Eight regular octagonal lower sides 2313 are attached to the base at an angle 2314 which is between 120 and 140 degrees measured from said base, with a side length 2315 of between 0.3 and 0.7 of diameter 2312. Eight regular octagonal upper sides 2316 are attached to the top of sides

2313 at an angle 2317 which is between 60 and 80 degrees measured from said base, with a side length of between 0.7 and 1.1 of diameter 2312. A semicircular domed top 2319 is fixed to the top edges of sides 2316.

Fig. 23B is a perspective view of energy converter covering according to one embodiment showing the hollow inside 2341 , in this embodiment the covering shown in Fig. 23B is made of double walled fiberglass of marine grade with a marine grade foam spacer between the fiberglass layers of a construction typical to double walled fiberglass boats. Aluminum angle 2331 with holes 2332 for attachment to aluminum motive float point absorber framework shown variously herein as 1211 , 1311 , 1411 and 1511 is fiberglass bonded to the bottom of the cover. Lower octagonal side 2313 rises outwards and upwards from base edge to provide an angled surface to deflect waves, particularly storm waves, away from the device, and secondarily, to provide protection from kayakers and other people as well as from seals, otters and other wild life from being able to attach themselves to the structure. Upper octagonal side 2316 rises upwards and inwards to provide and angled surface to deflect wind, particularly storm winds downward upon the device to help force it into itself, and secondarily, to provide a surface for the natural removal of bird feces by rain. Semicircular domed top 2319 firstly, provides a surface for winds to pass over with little resistance, provides a non-graspable surface and edges for humans to grab onto and otherwise attach themselves to the device and secondarily, deters the nesting, congregating and nesting of birds on top of the device and provides a surface for the natural removal of bird feces by rain.

Fig. 24 is a map of the world showing approximate wave energy density 2411 for various, mainly coastal, locations the source of this map is EPRI - California Ocean Wave Energy Assessment Report, 2007 available from

[http://www1.eere.energy.gov/water/pdfs/mappingandassessment.pdfl. Energy density shown is in kilowatts per linear meter of wave front. Number of data points = 96, total value all data points 3,576, average wave energy density (from this map) = 37.25 kW/lm worldwide. Energy density is the total raw energy available and power density is the actual energy output from a device or system. In addition to waves being more energy dense than wind, Muetze and Vining at the engineering department of the University of Wisconsin-Madison report that: "The utilization factor for wave power - the ratio of yearly energy production to the installed power of the equipment - is typically 2 times higher than that of wind power. That is whereas for example a wind power plant only delivers energy corresponding to full power during 25% of the time (i. e. 2, 190 hours out of 8,760 hours per year) a wave power plant is expected to deliver 50% (4,380 hours of full power per year)." Given that average wave energy density is 37.25kW/lm, worldwide, from the map 2411 , then on a yearly basis it is reasonable to assume that wave energy available for WEC power is = 18.625 kW/ Im yearly average on a worldwide basis.

Fig. 25 shows annual maximum changes in sea level between low tide and high tide for selected locations around North America on a map 2511. Average sea level change for USA = 8 feet, for Canada = 14 feet. This map was compiled by Neptune Equipment Ltd. 06/2012 based on the following data:

USA:

- Alaska and Pan Handle - 10-20+ feet (Anchorage to 40 feet)

- Seattle (Puget Sound) - 10-15 feet

- Wash, Oregon, Northern California Pacific Coast - 8-10 feet

- San Francisco Bay - 8-10 feet - Monterey Bay, Los Angeles, San Diego - 6-8 feet

- Gulf of Mexico -2-4 feet

- Florida west coast -3-5 feet

- Florida East coast north 4-6 feet

- North and South Carolina -4-7 feet

- Virginia -3-5 feet

- New Jersey, New York -6-10 feet

- Massachusetts 8-12 feet

- Main 10-20 feet

- Great Lakes are considered non-tidal

Canada:

- Haida Gwaii (Queen Charlotte Islands) and North - over 20-24 feet

- Pacific Coast of Vancouver Island - over 10 feet

- Georgia Straight (Between Vancouver Island and Mainland) - over 16 feet

- Nova Scotia - 7-10 feet (Bay of Fundy to 53 feet)

- New Brunswick, Prince Edward Island - 4-7 feet

- Newfoundland - 4-8 feet

- Labrador - 8-12 feet

- Quebec (upper St Lawrence Basin) - 8 -14 feet

- Quebec (lower St Lawrence Basin) - 14 -20 feet (Quebec City 18 feet)

- Montreal City - 6+ feet

The exemplary embodiments herein described are not intended to be exhaustive or to limit the scope of the invention to the precise forms disclosed. They are chosen and described to explain the principles of the invention and its application and practical use to allow others skilled in the art to comprehend its teachings.

As will be apparent to those skilled in the art in light of the foregoing disclosure, many alterations and modifications are possible in the practice of this invention without departing from the scope thereof.

Claims

1. A tidal compensation apparatus for maintaining a wave energy point absorber system at the surface of the water comprising:

a pile anchored to the seabed;

said wave energy point absorber system being connected to a sliding mechanism that is slidably connected to said pile;

said sliding mechanism being operative to cause the slidable connection to jamb against the sliding mechanism, and,

a float connected to said sliding mechanism, said float acting to track the tidal height of the surface of the water.

2. A tidal compensation system for maintaining a wave energy point absorber at the surface of the water comprising:

a pile anchored to the seabed;

said wave energy point absorber being connected to a sliding mechanism that is slidably connected to said pile;

a float connected to said sliding mechanism, said float acting to track the tidal height of the surface of the water: and,

a spring, said spring being interposed between said float and said sliding mechanism.

3. The system of claim 2 wherein said spring dampens the movement of said float due to wave action.

4. A tidal compensation system for maintaining a wave energy point absorber system at the surface of the water comprising:

a pile anchored to the seabed;

said wave energy point absorber system being connected to a sliding mechanism that is slidably connected to said pile; said sliding mechanism includes a float part to support the said wave energy point absorber system;

a transducer sensor, a computer, an electric motor, a cable or chain moved by the said electric motor, all acting to track the tidal height of the surface of the water and move the said wave energy point absorber system.

5. A wave energy point absorbing system comprising:

a framework attached to a tidal compensating frame or platform, with top and bottom plates defining a space with the top plate of the framework located out of and above calm water, the bottom plate of the framework located in and under calm water, wherein said framework;

a point absorber float contained within said space which moves up and down due to wave action; and

at least two guide rails extending through said float, said guide rails being rigidly secured to the top plate and to the bottom plate of said framework, and each said guide rail is slidably mounted through two linear bearings to said float, one linear bearing located near the top of said float and the other linear bearing located near the bottom of said float.

6. The system of claim 5 additionally comprising at least two connecting rods located on opposing sides of the center axis of the said float, with one end of each connecting rod rigidly connected to the top of said float and slidably connected through a linear bearing located in the top plate of said framework and the distal end of each connecting rod connected to a drive roller chain located above the top plate of said framework.

7. The system of claim 6 wherein each of the opposable drive roller chains, connected to said reciprocating connecting rods, is configured as an endless roller chain running over an upper and a lower sprocket which is connected to upper and lower shaft units which are located opposing and parallel to each other; the said opposing shaft units being driven by the opposable said chains in opposite directions to each other: when the float moves said connecting rods upwards and in counter opposite directions when said connecting rods move downwards; and one way clutches with roller chain clutch sprocket attached to the drive side is attached to either both the opposing upper shaft units or both the lower shaft units and is oriented so that on one of the opposing shaft units one of said clutch engages on the up stroke of the said connecting rod and on the opposing shaft unit second of said clutch engages on the down stroke of said connecting rod.

8. The system of claim 7 wherein an endless roller chain is connected between the clutch sprocket on one clutch and a drive sprocket on main drive shaft which is positioned at 90 degrees to the axis of said float and parallel to said shaft units and a second endless roller chain is connected between the second clutch sprocket on the second clutch and a second drive sprocket on said drive shaft, the diameter of these sprockets being that said clutch sprockets are larger than the diameter of said drive sprockets.

9. A wave energy point adsorbing system according to claim 5 further comprising a cover connected to said top plate of said framework, wherein said cover comprises: a regular octagonal base having a diameter measured between opposed vertices; eight octagonal lower sides each rising upwards and outwards from said base at an angle between 120 and 140 degrees measured from said base for a distance of between .3 and .7 of said diameter;

eight octagonal upper sides each rising upwards and inwards from said lower side at an angle between 60 and 80 degrees measured from said base for a distance of between .7 and 1.1 of said diameter;

a semicircular domed top connected to top edges of said upper sides.