Perpetual machine patent ref 20081101

US-RE29165 1977 Electromotive device including magnetic shield interacting with permanent . George Fred Bode

US4118637 1978 Integrated energy system Louis Eugene Tackett

US5810141 1998 Driveline clutch with unidirectional apply ball ramp- Organek

US5903069 1999 Synchronous reciprocating electric machines Misha Hitere

US6084322 2000 Amplifying mechanical energy with magnetomotive force Donald E. Rounds

US6356000 2002 Magnetically augmented rotation system Chun-Yuan Ho

US6369180 2002 magnetic force to create force vector to control an object Clarence S. Blakesley

US6851534 2002 Axial setting device with a switching coupling incorporated into the drive Michael Hock et al

US6956300 2005 Gimbal-mounted hydroelectric turbine Andrew Roman Gizara

Application pending

US20060237970 Perpetual motion comptrollers & energy molecule splitters Rudolph Bailey

US20070246939 Perpetual motion machine Macdonald

United States Patent Bode

[ 19]

[54] ELECTROMOTIVE DEVICE INCLUDlNG MAGNETIC SHIELD INTERACTING WITH PERMANENT MAGNET POLE FACES

[76] Inventor: George Fred Bode, Rte. No.1, Middletown, Md. 21769

[22J Filed: Nov. 18, 1975

[21] AppL No.: 633,002

Related U.S. Patent Documents

Reissue of: [64] Patent No.: 3,895,245

Issued: July IS, 1975 App!. No.: 472,909 Filed: May 23, 1974

[52J U.S. CI. .................................. 310/46; 3 JO/l03 [51] Int. CV ........................................ H02K 37/00 [58] Field of Search ............ 310/46, 103,112,114,

310/115,126,83

[56] References Cited

UNITED STATES PATENTS

1,724,446 8/1929 1,889,208 11/1932 1,893,629 1/1933

Worthington ....................... 310/46 Masterson et al. ............ 310/115 X Masterson et al. ............ 31 O/J 15 X

1,963,376 3,703,653 3,721,873 3,811,058 3,814.962

1111 E Re. 29,165 [45] Reissued Mar. 29, 1977

6/1934 J 1/1972 3/l 973 5/1974 6/1974

Papas ............................ 310/l03 X Tracy et al .................... 31 Oil 03 X Vogel .............................. 310/20 X Kiniski ........................... 310/l03 X Bacrmann ............ ........ ..... 310/103

Primary Examiner-Donovan F. Duggan Attorney, ARent, or Firm--Lowe, King, Price & Markva

[57J ABSTRACT

An electric motor is composed of two counter-rotating discs having intermeshing gearing and each carrying a plurality of permanent magnets radially arranged with the same poles at the periphery of both discs. A shield of magnetic material is provided at one side extending partly around the periphery of each of the discs and into substantially the bite of the discs. An electromag­netic is arranged with one pole adjacent the bite of the discs, with means to energize the electromagnet as each of the permanerit magnets reaches the bite of the discs to create a field of such polarity as to make the mag­netic poles of the adjacent permanent magnets move away from the bite of the discs in the direction away from the shield, utilizing the combined forces of the electromagnetic force and the repelling force of the permanent magnets to effect rotation.

13 Claims. 11 Drawing Figures

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2

ELECTROMOTIVE DEVICE INCLUDING MAGNETIC SHIELD INTERACTING WItH

PERMANENT MAGNET POLE FACES

Matter enclosed in heavy brackets [ 1 appears in the original patent but forms no part of this reissue ~pecifi­cation; matter printed in italics indicates the additions made by reissue.

BACKGROUND OF THE INVENTION 1. Field of the Invention The invention relates to an electric motor relying on

permanent magnets and an electromagnet for its opera­tion.

2. The Prior Art Various attempts have been made to create motors

utilizing the power of permanent magnets, but these seem never to have been commerically successful.

SUMMARY OF THE INVENTION

as a basis for defining a term "user efficiency" which will be employed in the following discussion.

Assuming an analogy to a magnetic engine to be described herein, such as one which operates on com-

5 pressed gas and includes a conversion device such as a turbine which converts the energy of the compressed gas to rotary motion. Further assume that there is an endless supply of compressed gas which is released, as required, by means of some control element which

10 demands very little power compared to the output of the compressed gas turbine. Under this condition, the output exceeds the input to the control device and the efficiency is greater than 100 percent. In the end, how­ever, the compressed gas will be dissipated, and the

15 battery discharged, requiring the entire system to be supplied with energy again. It will then be found that the entire sum of energy supplied to the system exceeds the energy removed from it, resulting in overall effi­ciency less than 100 percent.

20 In the present context, magnetic energy is used to replace the compressed. gas concept and offers a method of storing large amounts of energy for long periods of time. Furthermore, the magnetic energy can be released in an orderly manner which does not re­

The invention relates to a new, highly efficient elec- 25 quire excessive amounts of energy from a lead-acid trically operated motor, particularly suited forautomo- battery pack used to control the magnetic energy. tive, truck or other systems requiring a compact, high- In principle, according to the invention, the motor is powered engine which is independent of gasoline or composed oftwo counter-rotating members, preferably similar fuels and operates pollution-free. disc rotors, which are connected by gearing so as to

The invention provides a motor which utilizes the 30 turn at the same speed in opposite directions. Each of power· of permanent magnets aiong with an electro- the rotors carries a plurality, preferably four, equiangu-magnet operating in synchronism with the movement larly spaced permanent magnets extending radially of of the permanent magnets in order to produce turning the discs, the permanent magnets being so positioned of a shaft. It is particularly desirable from the ecologi- that they are opposite each other when passing the bite cal point of view, since the battery can be recharged, at 35 of the rotors. In the preferred form, all of the perma-any point where sufficient electric current is available, nent magnets have the same poles at the peripheries of while the magnets can be renewed or recharged in the the rotors and the opposite pole adjacent the centers of machine, and there is no consumption of gasoline or the rotors. other fuels which will contaminate the atmosphere. There is also provided a magnetic shield, composed

The device provides an arrangement by which, with a 40 of a generally V-shaped member of a magnetic mate-reasonable battery storage capacity, and with adequate rial, such as tin-plated steel, the point of which extends permanent magnets, vehicles can be operated for con- up almost to the bite of the rotors, while its legs are siderable distances and over considerable periods of somewhat curved about a radius of curvature greater time without the necessity for recharging, other than an than that of the rotors. occasional charge of the storage battery. 45 In the vicinity of the bite of the rotors, preferably on

Fundamentally, the concept of rotating electrical the opposite side from the shield there is arranged an machinery follows certain well-established and undis- electromagnet energized by a storage battery or other puted laws governing the actual operation. One such current source. Timing mechanism is provided which, law which is applicable to every machine is the law of when any pair of opposed electromagnets reaches the conservation of energy. This law states that.energy is 50 bite of the rotors, energizes the electromagnet to create given to a body when work is done upon it and in this a pole adjacent the other ends of the permanent mag-process there is merely a transfer of energy from one nets and of opposite polarity, So as to pull the perma-body to another. In such transfer, no energy is created nent magnets past the dead center or aligned position. or destroyed; it merely changes from one form to an- In a modified form, the electromagnet may be placed other. 55 at the point of the V-shaped shield and is then arranged

This statement does not indicate the efficiency with so that its end adjacent the bite of the rotors has the which the transfer takes place. It must be assumed that same plurality as the outer poles of the permanent the transfer takes place with somewhat less than 100 magnets, so as to push or repel them past the dead-cen-percent efficiency, as otherwise the output could be ter position. coupled to the input and the device would sustain itself, 60 Other objects and advantages of the invention will which is not believed possible. In other words, losses appear more fully from the follo~ing description, par-always occur which place an upper limit to the effi- ticularly when taken into conjunction with the accom-ciency and preclude the possibility of perpetual mo- panying drawings which form a part thereof. tion.

However, when the term "efficiency" is applied dis- 65 cretely, under properly defined conditions, it is possible to arrive at apparent efficiencies exceeding 100 per­cent. A simple example will illustrate a point and serve

BRIEF DESCRIPTION OF THE DRAWINGS

In the drawings: FIGS. 1 to 5 are diagrams for explaining the back­

ground of the invention;

3 Re. 29,165

4 FIG. 6 shows in side elevation a motor in accordance

with the invention; FIG. 7 is a side view of the motor of FIG. 6; and FIG. 8 shows a detail of a modified form of the inven-

FIG. 5 shows this condition, along with a modifica­tion of the shape of the ferromagnetic material 6'. A study of the prevailing forces which prevail in this dia­gram will lead to the conclusion that if a short burst of

tion; 5 external energy, of the proper polarity is applied to the FIG. 9 shows in side elevation a part of a further system at this time two of the poles are nearest dead

modification of the invention; center (in this case, south pole), they will be kicked FIG. 10 is a plan view of a part of FIG. 9; past dead center and beyond the influence of the ferro-FIG. 11 shows a further possible modification. magnetic material. The two south poles will now de-

DESCRIPTION OF THE PREFERRED EMBODIMENTS

10 velop a force repelling each other, and the north poles will develop new forces attracting them towards the shield until they reach a point just before dead center

FIG. 1 shows two magnets 2 and 4, of the ordinary where they will stop unless the external energy is ap-bar type placed in close proximity to each other iIIus- plied again in the form of a short burst. It is evident that trating in a simple manner that two poles of like 15 the external energy must be applied in such phase that polarity repel each other. Further, with certain restric- it aids rotation or else a portion of the energy extracted tions, they generally repel each other with a force F from the magnets is cancelled and the system will not that is directly proportional to the product of the indi- work. vidual pole strengths, and inversely proportional to the It is important to note at this point that the energy square of the distance separating them. In addition, the 20 injected into the system in the manner and time sped-force is affected by the permeability of the medium fied will add to any energy extracted from the magnets. through which the force acts. For ordinary air the nu- Therefore, the total output energy is the sum of the merical value of the permeability is very nearly unity external energy injected, plus the energy extracted and is not used in calculation. from the magnetic fields of the permanent magnets,

FIG. 2 shows an identical pair of bar magnets, the 25 minus the energy used to overcome any losses. only difference being that a piece 6 of ferromagnetic Experimentally it has been determined that the losses material has been shown inserted between the poles. do not increase as rapidly as the Dutput, providing a Under this condition an important effect is observed. basis for the assumption that it is possible to control The poles no longer repeal each other; they are, as a substantial amounts of output power with relatively matter of fact in apparent attraction as indicated by F I 30 small amounts of energy derived from a lead-acid bat-and F2• Theoretically, the individual magnets induce a tery control source. The impact of this statement is pole of opposite polarity in the ferromagnetic material apparent as indicating that an engine of this type could and are thereby attracted to it. Suitable arrangements be used to power an automobile for a considerable of air gaps in conjunction with other factors allow this amount of time before it would be necessary to re-apparent attraction to remain throughout a very wide 35 charge the batteries. range of pole strengths, and thicknesses of the ferro- It is equally important to note that it is not necessary magnetic material. to inject external energy continuously. As a matter of

This action actually occurs and the effect can be used fact, the external energy must be injected for a very to recover large amounts of the energy stored in the brief time around dead center or the system will not magnetic fields of permanent magnets. 40 work. Quickly, after the poles at dead center have been

Next, attention is directed to FIG. 3 where similar kicked past the dead center position, the input energy magnets are attached to turn about fixed individual must be turned off and the forces developed by the axes 8 physically geared together at 10. This arrange- permanent magnets left to supply their contribution to ment is intended to confine the rotation of the magnets the output of the system. The advantages of not having to a circular path, each magnet rotating in an opposite 45 to supply energy over the engine cycle are obvious also. direction from the other. With these restrictions, the The instantaneous demand may be high, but if the system will reach a state of equilibrium as shown where energy is only supplied for a short time the average the force F t' is equal and opposite to the force F2 ', energy demand is much lower. rendering the system stationary. Finally, the discussion thus far is based on a system

Now, referring to FIG. 4, visualize this as a plan view 50 employing a single bar magnet in each rotating head. of FIG. 3, without showing the shafts and gears. In This results in having to reverse the polarity of the other words, the right hand bar magnet 4 of FIG. 4 is external energy source because alternately north and considered to rotate clockwise about the center axis 6 south poles appear at the dead center position. This of the magnet in a plane parallel to the plane of the condition is easily taken care of by the arrangement paper. The left hand magnet 2 rotates in the opposite 5S shown in FIGS. 6 to 8. direction. Without the benefit of ferromagnetic mate- Referring to FIGS. 6 to 8, there are two rotors 12 and rial 6 inserted between the south poles of FIG. 4, the 14 mounted on shafts 16 and 18, respectively, from one bar magnets will align themselves paralic I to each other of which power may be taken. The rotors are caused to as shown. If we now restrain the magnets in the parallel turn in opposite directions in the same speed by mesh-position and insert the ferromagnetic material, the 60 ing gears 20 and 22 mounted on the shafts 16 and 18, forces can be illustrated as shown in FIG. 4, where the respectively. sum of the forces F2a and F2b complement the value of Each of the rotors carries a plurality of permanent Fb and the system is no longer in a state of eqUilibrium. magnets 24, which are arranged radially in the rotors If unrestrained, magnets will turn about axes 6 in the with the same poles at the periphery and the opposite directions indicated. It can be seen that the insertion of 6S poles adjacent the center of the rotors. At one side of the ferromagnetic material causes an apparent reversal the rotors there is a magnetic shield 26, which may for of forces imparting rotation to the system in the direc- example be of tin-plated steel, which is of generally tion intended. V -shape and has its point adjacent the bite of the ro-

5 Re.29,165

6 tors. The legs of the V -shape are arcuate, each having As is shown in FIG. 11, it is not essential that the a radius of curvature somewhat greater than the radius electromagnet be at the bite of the rotors. It could be at of curvature of the rotors, so that they gradually di- various places around the periphery of the rotors, and verge from the rotors. The legs of the shield extend one or several such magnets can be used, to impart about 90° around the periphery of the rotors. 5 either attractive or repulsive forces to the rotors.

On the side of the bite of the rotors opposite the I claim: shields, there is an electromagnet 28 which is con- 1. An electric motor comprising a pair of rotors, nected to a storage battery 30 by a make-and break- means for causing the rotors to rotate in opposite direc-switch 32, operated by cam 34 having four projecting tions at the same speed, a plurality of permanent mag-cam portions, corresponding generally in position to 10 nets carried by each rotor and angularly spaced there-the permanent magnets, so as to close the switch 32 as around, the permanent magnets extending radially and each· pair of permanent magnets reaches the aligned being angularly positioned so that a pair of magnets, position at the bite of the rotors. one of each rotor come opposite each other at the bite

In such a device, as the magnets approach the mag- of the rotors, the outer poles of the magnets opposing netic shield 26, they are attracted thereto and cause the 15 each other being of the same polarity, a magnetic shield rotors to turn in the directions shown opposite to each of ferromagnetic material having its edge adjacent the other. When the rotors reach the bite of the rotors, the bite of the rotors and extending away from the bite of electromagnet 28 is energized in such a way as to cre- the rotors for a substantial distance, and electromagnet ate a pole of opposite polarity to the outer poles of the means having one pole adjacent the periphery of at rotors; that is when the permanent magnets have their 20 least one of the rotors, and means responsive to the north poles outwardly the electromagnet pole adjacent rotation of the rotors for energizing the electromagnet the bite of the rotors is a south pole. This will pull the means temporarily as a permanent magnet approaches permanent magnets around in the direction of rotation, said electromagnet means, with the end of the electro-and past the dead-center point, whereupon the electro- magnet adjacerit the periphery of the rotor having a magnet is de-energized and the permanent magnets 25 polarity such as to produce movement ofthe outer ends which have just passed the dead-center point because of the permanent magnets at the bite in the direction of their repulsion continue to cause turning of the ro- away from the electromagnetic shield. tors, while the following magnets approach the ~hield 2. An electric motor as claimed in claim 1, in which and are attracted thereby so as to cause the rotatIOn to th t d f th t ts h th continue. 30 e o~ er en s? e permanen magne. ave e same

.. polanty and Said electromagnet means IS on the oppo-It may be necessary to start the rotors In motIOn at 't'd fth b't fth t f th h' Id d th

the beginning of the operation which can either be SI e Sl e 0 e leo e ro ors rom .e s Ie an e done by hand or by an electric starting motor. Once end of the ~lectrom~gnet nearest the bite of the rotors rotation is started, it continues until the electromagnet has a polanty opposIte to that of the outer ends of the 28 is no longer energized, which can be accomplished 35 pe;m:enlt m~gnetst I' d' I' l' h' h by opening a hand switch 38. • e ectnc mo or as c alme In c aim ,In W IC

In a modification shown in FIG. 8, the electromagnet the o~ter ends of the permanent magnet~ have the same 28 is placed on the same side as the shield 26 with one ~lanty and. the electromagnet mea;ns IS on the same end extending into a gap in the shield adjacent the bite Side of the bite of the rotors as t~e shield and the end of of the rotors. In this case, the electromagnet is ener- 40 the electrOl;nagnet nearest the bIte of the rotors has the gized in such a way that the hole adjacent the bite of same polanty as the outer ends of the permanent mag-the rotors has the same polarity as the outer ends of the nets. . ..... permanent magnets, so as to repel the permanent mag- 4. ~ ele.ctnc moto: as claimed m chum ~, III which net poles which are adjacent the bite of the rotors and the shield IS substantlally V-shaped and sal~ electro-to drive them in rotation. 45 magnet means has one pole adjacent the bite of the

Such an arrangement provides a device which does rotors.. ..... not create fumes or other undesirable vapors, and 5. An electnc .moto~ as claimed In elal.m 1, .m whIch which can operate for considerable periods of time the legs of the shield dlV~rge from the penphenes of the with only an occasional recharging of the storage bat- rotors away from th~ bite ~f the roto:-,: . tery, since a majority ofthe energy is obtained from the 50 6. An electromotlVe devIce comprzsmg a mngnellc permanent magnets. These can be re-magnetized at shield, a pair of rotors, each of said rotors having a plu-considerable intervals, so that operation of a device rality of spaced, permnnent mngnet pole faces on its over long periods of time is practical and effective. periphery, said rotors being mounted for synchronous

While the arrangement shown is of course the most rotation of the pole faces of the pair of rotors relative to convenient to explain the theory, it is practical that the 55 a point of closest proximity between the peripheries of the outer ends of the magnets could be of alternatingly two rotors so that while the rotors are in proximity to said opposite polarity, which would however require two point mngnetic fields extending from the pole faces of the electromagnets, one as shown in FIG. 6 and one as two rotors interact to produce forces on the rotors caus-shown in FIG. 8, which would also be alternately ener- ing rotation of the rotors, said shield being mounted gized to produce the necessary polarity. 60 relative to the periphery of said rotors and said point to

In the arrangement according to FIGS. 9 and 10, prevent substantial interaction of the magnetic pole faces there is arranged adjacent the bite of the rolls an elec- of the two rotors on one side of said point, whereby the tromagnet, possibly ofthe horseshoe type, which has its mngnetic fields of the two rotors interact assymetrically poles on opposite sides of the bite of the rolls. When on the different sides of the point to rotatably drive the this is energized, the north pole will impart a repellent 65 rotors in predetermined directions relative to the point, force to the north poles of the magnets 24 and the and electromngnet means responsive to the rotation of south pole will exert an attracting force, the two forces one of the rotors for supplying a mngnetic field to one of thus reinforcing each other. the rotors to rotatably drive the rotor between the shield

7 Re.29,165

8 and the point in the same direction it rotates in response magnetic shield being positioned on one side of the point to the interaction. and relative to said magnets to prevent substantial inter-

7. The device of claim 6 wherein the shield extends into action of the magnetic fields on said side of the point, proximity with the point so that the magneticfieldsfrom whereby the magnetic fields interact assymetricaliy on only one pole face on each of the rotors interact with each ·5 the different sides of the point to drive the magnets in other on said side of the point. predetermined directions relative to the point, and elec-

8. The device of claim 6 wherein the pole faces of both tromagnet means responsive to movement of at least one rotors have the same polarizations and said rotors are magnet for supplying a magnetic field to at least one mounted to rotate toward said point, said shield being magnet to drive the magnets between the shield and the positioned on the same side of the point as the side from 10 point in the predetermined directions. which the rotors approach the point. 12. The device of claim 11 wherein the magnets are

9. An electromotive device comprising a fixed magnetic mounted for rotation about axes removed from said shield, a pair of permanent magnets, means for mounting point. at least one of said magnets for cyclic movement relative 13. An electromotive device comprising a magnetic to said shield and a point of closest proximity between the 15 shield, a rotor having a plurality of spaced, permanent magnets, said magnets having pole faces with polariza- magnet pole faces on its periphery, another permanent tions that produce interacting magnetic fields tending to magnet pole face displaced from said rotor, said rotor drive the at least one magnet relative to said point, said being mounted for rotation of the pole faces relative to a magnetic shield being positioned on one side of the point point of closest proximity between the path of the periph-and relative to said magnets to prevent substantial inter- 20 ery of the rotor and the another permanent magnet pole action of the magnetic fields on said side of the point, face so that while the rotor is in proximity to said point whereby the magnetic fields interact assymetrically on magnetic fields extending from the pole faces of the rotor the different sides of the point to drive the at least one and another permanent magnet pole face interact to magnet in a predetermined direction relative to the point, produce forces on the rotor causing rotation of the rotor, and electromagnet means responsive to movement of the 25 said shield being mounted relative to the periphery of said at least one magnet for supplying a magnetic field to the rotor, said another permanent magnet pole face, and said at least one magnet to drive the magnet between the point to prevent substantial interac(ion of the magnetic shield and the point in the predetermined direction. pole faces of the rotor and said another permanent mag-

10. The device of claim 9 wherein the at least one net pole face on one side of said point, whereby the mag-magnet is mounted for rotation about an axis removed 30 netic fields of the rotor and another permanent magnet from said point. pole face interact assymetrically on the different sides of

11. An electromotive device comprising a fIXed mag- the point to rotatably drive the rotor in a predetermined netic shield, a pair of permanent magnets, means for direction relative to the point, and electromagnet means mounting said magnets for cyclic movement relative to responsive to the rotation of the rotor for supplying a said shield and a point of closest proximity between the 35 magnetic field to the rotor to rotatably drive the rotor path of the magnets, said magnets having pole faces with between the shield and the point in the predetermined polarizations that produce interacting magnetic fields direction. tending to drive the magnets relative to said point, said * * * * *

40

45

50

55

60

65

United States Patent [19]

Tackett

[54] INTEGRATED ENERGY SYSTEM

[75] Inventor: Louis Eugene Tackett, Grandview, Tex.

[73] Assignee: UNEP3 Energy Systems Inc., Grandview, Tex.

[21] Appl. No.: 728,064

[22] Filed: Sep. 30, 1976

Related U.S. Application Data

[63] Continuation-in-part of Ser. No. 579,131, May 20, 1975, abandoned.

[51] Int. 0.2 ••••••••••••••••••••••••••••••••••••••••••••••• H02P 9/04 [52] U.S. CI. ......................................... 290/55; 60/398 [58] Field of Search ..................... 290/1, 4, 44, 43, 54,

290/55; 60/398, 413, 415; 417/336, 382

[56] References Cited

U.S. PATENT DOCUMENTS

874,140 12/1907 943.000 12/1909

2,539,862 111951 3,996,741 12/1976 4,004,427 1/1977

Valiquet .............. , .................. 60/398 Busby ................................... 417/336 Rushing ................................. 60/398 Herberg ................................. 60/398 Butler, Jr ............................... 60/398

Primary Examiner-Robert K. Schaefer Assistant Examiner-John W. Redman Attorney, Agent, or Firm-James L. Bean

[57] ABSTRACf

This invention is a multiple diverse energy source

r 10.

: '

[11]

[45]

4,118,637 Oct. 3, 1978

driven energy integration and multiple use-point sys­tem: which includes system air pressure compensated variable pressure and volume delivery of compressed air from multiple air compression stations which dis­charge and store compressed air into an included inter­connecting collection storage and distribution conduit multiple module grid system; of largest needed and commercially available size pipe to keep the pressure drop to a minimum, and from which the compressed air is withdrawn at multiple points of need; when and as needed, through synchronized dual-precision-controls to turn, at optimum RPM speed regardless of varying work loads, air motor drives for operation of conven­tional electrical generating equipment with varying customer-use-demand output work loads. The conduit­pipe systems are arranged in interconnecting, but isola­ble, multiple module grids ranging in size from those needed, for example, for a small town or a large individ­ual user of electricity to large metropolitan areas and which may ultimately be interconnected into a large regional, national, or continental system. Natural en­ergy sources including wind, tide, wave, thermal and solar power, as well as conventional fuels, may be uti­lized to provide the energy required to drive compres­sors to supply the air into the system. An improved wind turbine is included for the recovery and use of wind-power for compressing air on a vast scale in multi­ple installations.

21 Claims, 25 Drawing Figures

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FIG 15

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192

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FINISHED GRADE LINE

4,118,637 2 1

stalled at the Grand Coulee Dam, it has been the gen­eral practice to directly couple large water turbines to fixed electrical generators, frequently making it neces­sary to duplicate or provide additional equipment in

INTEGRATED ENERGY SYSTEM

CROSS REFERENCE TO RELATED APPLICATIONS

This is a continuation-in-part of my co-pending appli­cation Ser. No. 579,131, filed May 20, 1975 now aban­doned.

BACKGROUND OF THE INVENTION

5 order to accommodate fluctuating demands. Under this type of development, only the very large water power sites are developed, and smaller sites are not considered economically feasible. Further, other collectively enor­mous sources of non-contaminating energy which have

1. Field of the Invention 10 never been fully exploited due primarily to their inter­

mittent nature: include solar energy, wind energy, and ocean tide and wave energy. This invention relates to systems for providing useful

energy in the form of electrical power, and more partic­ularly to an improved system for utilization mUltiple diverse energy sources in compressing large volumes of 15 air, collecting, storing and distributing the air in a con­duit system including interconnecting multiple module grids constructed of large conduit-pipe, utilizing the air

SUMMARY OF THE INVENTION

The integrated energy system according to the pres-ent invention may be constructed in any needed size, progressively and interconnectively from the size needed, for example, for a small town or a single user to that required to serve a continent. Each said system as and where necessary to operate equipment for gener­

ating electricity near the points of use. 2. Description of the Prior Art

20 includes multiple diverse energy collector-converter­driven system pressure compensated variable volume air-compression facilities, a grid-type compressed air combination collection-storage-transmission-distribu-

The use of compressed air as a means to drive or operate numerous devices is well-known, and com­pressed air was widely used in the early development of modern industry. However, the development of oil and 25 gas powered direct drive universal electrical energy generating and distribution systems have resulted in a virtual abandonment of the development of compressed air as a major industrial motive power. Consequently, air compression, storage, and transmission systems in 30 use today generally include conventional branch and truck type collection and transmission lines of relatively small flow size, with conventional air storage tanks, or accumulators, near the compressors and/or near the points of use. The storage tanks are expressly for the 35 purpose of bridging over short periods of high use where compressor and normal line carrying capacities are normally overtaxed, and are not intended or built for storage pf several days reserve usage of compressed air. Pressure losses in such conventional compressed air 40 systems is a highly limiting factor in transmitting air in large volumes over any substantial distance.

The compressor installations in use today are gener­ally single stage compressors for delivering relatively high volumes of air at low pressures, while two stages 45 are used for medium pressures, and three stages for higher pressure, low volume air. This does not give sufficient volume-pressure automatic demand delivery flexibility in meeting maximum use demands for com­pressed air with minimum compressor equipment for 50 large scale use.

Conventional compressed air controls for air motors which turn multiple electrical generators of power plants cannot adequately control the delivery of the driving air with the precision control required to reach 55 and maintain the ditTerent optimum speeds required for different generators with varying work loads, due to the fact that such known automatic control devices gener­ally regulate only air flow and not a combination of flow and pressure. 60

Electrical generating systems in use today normally make no provisions for storing energy during periods of low use for later utilization during times of peak use. This, generally, has resulted in discouraging the utiliza­tion of natural energy sources for the generation of 65 electricity with the exception of a relatively small num­ber of hydroelectric generating plants. Even in the case of hydroelectric plants such, for example, as that in-

tion network, preferably made of the largest commer­cially available conduit-pipe which may be transported over the existing highway systems; and dual precision controlled air-motor drives primarily for turning con­ventional electric generators. The grid conduit network preferably surrounds each area and region of use with interconnecting grid plumbing lines into which the compressed air is introduced and from which it is with-drawn where and as needed. The grid plumbing system incorporates means for automatically or manually iso­lating individual modules of the entire system to thereby isolate trouble spots, or areas under construc­tion, etc.

A grid module surrounding each predetermined area or region of need is fed from multiple diverse energy source collector-converter driven air compressor sta­tions. Such stations are placed at points throughout the area of need where constant energy output sources are available for use as well as at all other points of need where intermittent energy sources are available.

While it is contemplated that various conventional or known collector-converters of diverse forms of energy will be used to furnish mechanical torque for driving the air compressor stations, an improved wind powered energy collector-converter according to the present invention is particularly well suited for driving the air compressor units, for high capacity production of com­pressed air.

The grid type compressed air system allows the use of the compressed air for driving conventional electrical generators which may be located wherever needed and convenient to population centers.

The compressor stations employed to compress the air are preferably of a three stage capability, with the inlet of the second and third stages being connected so that the various compressor stations can produce high volumes of air at relatively low pressures: and by sys­tem pressure compensating automatic connecting of the inlets of the second and third stages to the discharge of the preceding stage, a lower volume of relatively high pressure air can be delivered as system air-pressure rises. This facilitates high-efficiency start-up of the sys­tem and assures flexibility in meeting maximum use-demands for the compressed air with minimum air com­pressor equipment design requirements.

3 4,118,637

4 While it is contemplated that, under most conditions,

adequate compressed air volume storage capacity can be provided in the multiple grid plumbing system con­structed from large diameter pipe surrounding the major areas of use, it is recognized that in certain instal- 5 lations such as in congested sea shore cities or on is­lands, space requirements on shore may limit installa­tion of such conduit systems. Under these conditions, an offshore floating dock installation according to the present invention and including multiple interconnect- 10 ing layers of piping may be joined together to provide storage for the compressed air. These floating docks are to be provided with a suitable anchorage system to permit self-adjustment, with the docks themselves pro­viding support for the multiple diverse energy collec- 15 tor-converter-driven air-compressor stations.

BRIEF DESCRIPTION OF THE DRAWINGS

The foregoing and other features and advantages of the integrated energy system according to the present 20 invention will become more apparent from the detailed description thereof contained herein below, taken in conjunction with the drawings, in which:

FIG. 19 is a fragmentary plan sectional view taken on line 19-19 of FIG. 17 and showing the linkages for operating the bottom brake shoes for the turbine;

FIG. 20 is a fragmentary sectional view taken on line 20-20 of FIG. 17.

FIG. 21 is a schematic view of a two-way air flow metering apparatus employed in the system;

FIG. 22 is a schematic view showing an automati­cally and manually triggered isolation valve employed in the plumbing system;

FIG. 23 is a sectional view through a manhole and including a typical main grid line condensation blow-off means;

FIG. 24 is a fragmentary plan sectional view showing an expansion-contraction pipe joint for use in the pipe in the conduit system; and

FIG. 25 is a schematic layout plan of a portion of a multiple grid system and illustrating the main isolation cut-off valves and typical modules encompassed within the grids.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

FIG. 1 is a schematic plan view of an integrated Referring now to the drawings in detail, a preferred energy system module for a small consumer of electric- 25 embodiment of the invention will be described in which ity;

FIG. 2 is a view similar to FIG. 1 and showing an integrated energy system module for a large city or metroplitan area;

numerous energy sources are utilized to compress air which is stored under pressure in an interconnected network of transmission pipes of maximum commericial

FIG. 3 is a schematic plan view of an energy recov- 30 size required and available which is haulable on trucks and having sufficient total bulk storage capacity for maintaining a long term reserve storage, and for utiliz-ery farm employed in the system;

FIG. 4 is a schematic plan view of an energy recov­ery farm adapted for off-shore floating use;

FIG. 5 is a schematic side elevation view of the float­ing energy farm shown in FIG. 4;

FIG. 6 is a sectional view of the floating energy farm of FIG. 5 on an enlarged scale with the section taken on line 6-6 of FIG. 7 and FIG. 4;

FIG. 7 is a schematic sectional view taken on line

ing the compressed air for the generation of electricity at or near the points of use and at a rate determined by the requirement for electrical energy. The compressed

35 air is utilized, through automatic, coordinated pressure and volume controls, to drive air motors which, in turn, power conventional electrical generators to supply electrical energy for conventional uses. The coordi-

7-7 of FIG. 6 and FIG. 4; 40 nated pressure and volume controls enable the air motor to drive the generators at a precisely controlled speed throughout the load range capabilities of the generators. FIG. 8 is a schematic plan diagram of a typical com­

pressor facility employed to provide compressed air for the main grid plumbing line system;

FIG. 9 is a schematic plan diagram of a precision RPM control system for air motor drives, for conven- 45 tional electrical generators, employed in the com­pressed air driven power plants;

FIG. 10 is a schematic plan diagram of a typical wind powered, vertical turbine driven air compression facil­

The transmission and storage pipe network employed in the system is designed in a plurality of modules which are interconnected and which may be automatically or manually isolated when desired or necessary, with the individual modules containing sufficient interior vol-ume storage capacity to operate electrical generating equipment to supply electrical energy to the geographi­cal area encompassed by the module for a substantil,tl

ity employed in the system; FIG. 11 is a plan view of a vertical air turbine show­

ing the blade arrangement and support framing thereof; FIG. 12 is a sectional view ofthe wind turbine and air

50 period of time, preferably for several days. Each mod­ule is supplied with compressed air by multiple systems of air compressors described more fully herein below, at least a portion of which are preferably driven by non-

compression facility driven thereby; FIG. 13 is a side elevation view of the frame structure 55

around the periphery of the horizontal revolving verti­cal wind turbine;

FIG. 14 is a fragmentary sectional view, on an en-larged scale, of the central hub and bearing at the base of the revolving turbine;

FIG. 15 is a fragmentary plan sectional view taken on line 15-15 of FIG. 14;

FIG. 16 is a fragmentary sectional view of the central hub and bearing at the top of the revolving turbine;

60

FIG. 17 is a fragmentary sectional view taken on line 65 17-17 of FIG. 12;

FIG. 18 is a fragmentary plan sectional view taken on line 18-18 of FIG. 17;

poluting natural energy sources such as wind, solar, thermal, water, wave, or tide powered energy collec­tors. However, a portion of the compressor installations in each module preferably are capable of employing conventional power sources such as gas or steam en-gines or turbines. .

By providing an interconnecting transmission and storage grid pipe network joining the respective mod­ules, a more complete utilization of natural energy sources may be employed. Thus, in areas where ocean tide and wave energy, or water power from streams is generally not available, wind power turbines according to the present invention may be utilized, along with solar-power converters, as the principal sources of natu­ral energy to be employed to provide the compressed

5 4,118,637

6 air. However, as is well-known, air movements are not uniform and it may be anticipated that wind turbines employed in a particular module will be able to supply an excess of air during the terms of high wind move­ment and be unable to supply sufficient quantity of air 5 during prolonged periods of relative calm. Likewise, solar-power converters will not run at night nor on cloudy days. By interconnecting the respective mod­ules, it is possible to more evenly balance the system, with compressed air flowing out of a particular module 10 during times of high wind, and on bright and sunny days, for example: or drawing from other modules hav­ing an extra energy supply in times of relative calm or during prolonged doudy conditions. Due to check valve special spring loadings, small systems will release 15 excess air pressure to adjoining systems.

Only the module and grid system according to this invention makes it possible to construct the system in steps, gradually expanding same, town by city by re­gion, to a complete integrated national air continental 20 energy system. On such a large scale, the grid network preferably includes a basic grid covering and dividing the entire area into relatively large regions, with the individual towns, cities and metroplitan areas therein each having independently operable grid systems inter- 25 connected with each other and to the main grid system. By use of automatically and/or mariually controlled automatic valves, entire regions as well as individual modules may be isolated. Further, meters are employed at each junction of a module to a region, or region to a 30 national grid to measure the flow of air into or from the over-all system. The meter readings are then employed to compute the net supply and utilization of compressed air by the individual modules. Thus, a module, whether for an individual town or for a large metropolitan area, 35 may be charged for drawing excess air from the system, or may receive a payment or credit for supplying air utilized by other modules connected in the system.

Referring now to FIG. 1, a typical module for a small town or a large individual user of electrical power is 40 designated generally by the reference numeral 10 and includes a plurality of collection-transmission-storage pipes 11 extending in generally parallel relation around the user, indicated generally as a small town. The trans­mission and storage pipes 11 are interconnected as by 45 pipe 12 to permit the free flow of compressed air be­tween the respective pipe. The number, size, and length of the transmission and storage pipes 11 will obviously be determined by the projected requirement of electri­cal power to be generated and utilized within the geo- 50 graphical area serviced by the module. However, it is preferred that the transmission and storage pipes 11 be of the largest needed diameter commercially available and economically feasible, with the length of pipe uti­lized being sufficient to provide a storage capacity suffi- 55 dent to supply compressed air for a substantial length of time, and preferably for several days, to operate a com­pressed air motor driven generator station designated generally by the reference numeral 13.

At spaced points around the module 10 are located a 60 plurality of compressor stations for supplying com­pressed air to the transmission and storage pipes 11. In FIG. 1, where a generally rectangular system of trans­mission and storage pipes are utilized surrounding the area serviced by the modules, there is schematically 65 illustrated two compressor stations located at each cor­ner of the module. Preferably at least one of each of these pairs of compressor stations will be capable of

utilizing a non-polluting, natural energy source, with at least a portion of the compressor stations also being capable of being driven by solar powered or by conven­tional fueled steam or heat differential engines in a rela­tively small module, half of the compressor stations may be wind turbine driven stations, designated generally by the reference numeral 15, and the other half, designated generally by the reference numeral 15, powered by solar power or by conventional fueled steam or heat differential engines.

Initially, a module of the type illustrated in FIG. 1 may operate entirely independently of other modules; however, as more modules are installed, and the re­gional or national grid system developed, the respective modules will be connected, through a pipe 16 and meter 17 to the grid transmission storage line 18.

The larger m9dule shown in FIG. 2 and utilized for a larger consumer of electricity such as a large city or metroplitan area is quite similar in design and construc­tion to that of the small module shown in FIG. 1, with the principal difference being size, and accordingly, similar reference numerals are used to designate similar elements in the two figures. Thus, FIG. 2 illustrates a module, designated generally by the reference numeral 20, in which a typical city or large metropolitan area is generally surrounded by a network of transmission and storage pipes 11 joined together at spaced intervals by connecting pipes 12 which, in turn, are illustrated as supplying compressed air from the system to a plurality of generating stations 13 at various locations around the module, with the generating stations preferably being located near the highest concentrations of electrical consumption to thereby minimize transmission line losses.

Compressed air is supplied to the transmission and storage pipe of the module 20 much in the same manner as that described above with regard to the smaller mod­ule 10. However, for the larger module 20, energy re­covery farms, designated generally by the reference numeral 21 and each consisting of a relatively large number of energy collecting-converting devices such as the wind turbine described more full hereinbelow, are arranged in close proximity to one another in the man­ner illustrated schematically in FIGS. 3 and 4, to supply compressed air for the system.

Referring specifically to FIG. 3, the energy farms indicated generally by the reference numeral 21 may comprise a plurality of individual wind turbine driven compressor stations 14, and/or other diverse energy driven stations 15, each having the compressor dis­charge connected to a collection pipe 22, with the re­spective collection pipes 22 being connected to a header pipe 23. Header pipe 23 is connected, through a one­way check valve 24 and a cut-off valve 25, to one of the transmission and storage pipes 11. Additional cut-off valves, or isolation valves, 26 are mounted in the lines 11. Also, an airflow meter 17 is installed between check valve 24 and cut-off valve 25 to measure the flow of air from the energy farm 21 into the transmission and stor­age pipes 11. It is believed apparent that the respective compressor stations in the farm 21 may be driven by any suitable source. The figures 28° plus 30 minutes indicate preferred-orientation of energy-farm quadrants with reference to prevailing winds in areas of location.

As can also be seen in FIG. 3, the respective needed electrical generating stations 13 are connected to the transmission and storage lines 11 through a cut-off valve 91, a one-way check valve 92, and a meter 93.

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Referring now to FIGS. 4-7, a floating compressed air storage facility for use in coastal regions is illus­trated. These floating installations are preferably con­structed, in the form of floating docks or floating barges, indicated generally by the reference numeral 30, 5 from multiple interconnecting and sealed layers of sec­tions of transmission and storage pipe 11, with alternate layers of pipe extending at right angles to one another, as best seen in FIGS. 6 and 7. The layers of pipe are separated by welding plates 31 at each point of contact 10 to strengthen the welded juncture and provide a rigid barge-like assembly. The individual pipe sections in each layer are interconnected by pipe section extending at 90° thereto along each end of the respective layers of pipe sections, and the layers are interconnected by ver- 15 tically extending pipe sections 32 at spaced intervals around the assembly. Preferably the welded assembly is provided with a deck surface 33 which may be em­ployed to support a plurality of energy collection-con­version stations 34 (see FIGS. 8 and 10) including air 20 compressors run by suitable means such as tide or wave driven energy collecting devices or wind trubines of the type described more fully hereinbelow. Also, the welded assembly is preferably equipped with a bow plate 35 to facilitate towing and positioning of the as- 25 sembly in the open water and, to this end, one or more conventional barge tow couplings 36 may be provided on the assembly.

To anchor the barge assemblies 30 in position, a plu­rality of vertical guide sleeves 37 are rigidly welded to 30 and extend through the barge assembly. The guide sleeves preferably have their inner surfaces lined or coated with a self-lubricating material such as Teflon to minimize frictional contact with vertical, fixed caisson pilings 38. The pilings 38 are preferably positioned by 35 lowering through the guide sleeves 37 and set by con­ventional means which lower the pilings to solid rock or into tough hardpan in accordance with known proce­dure. The caisson pilings preferably will be made of pipe having an external diameter slightly smaller than 40 the internal diameter of the self-lubricating guide sleeves.

When the floating docks or barges 30 are to be posi­tioned in water too deep to make the use of pilings practical, a system of anchors (not shown) may be used 45 to retain the barges in position. This may be accom­plished by using a suitable number of large anchors of conventional design, with the anchors positioned out­wardly from and at spaced intervals around the respec­tive barges. Wire cables from the respective anchors are 50 secured to the barge via cable tensioning winches which maintain a constant tensile load in the cable and thereby automatically compensate for vertical movement of the barge due to tide changes. The wenches may be pow­ered by air motors if desired, with self-operating pres- 55 sure-resistance triggered controls.

Air compressed by the compression stations 34 sup­ported on or carried by the floatation barges 30 and stored in the pipe sections 11 which make up the body of the barges 30 is led from the barges to generating 60 stations on shore through large diameter flexible marine hose which is commerically avialable and indicated as 39 in FIG. 6. The marin hose is connected, through a standard flange coupling 40 to air flow meter 17, a one-way check valve 41 and a cut-off valve 42 to an 65 outlet 43 connected to the storage pipe assembly of the barge. By the use of the heavy-weighted flexible marine hose, which is permitted to lie on the bottom as it is led

8 ashore, vertical movement of the barge can be accom­modated. From the shore, the air is led through rigid piping to generating stations in the module service area as required.

Referring now to FIG. 8, a typical air compressor station and control mechanism will be described in detail. The energy collecting source, whether a wind driven turbine,· solar power collector-converter, or other power source, is indicated generally by the refer­ence numeral 45 and is connected, through a suitable shaft 46 and governor 47 to a hydraulic torque con­verter coupling 48. The coupling 48 is of a minimum speed type control which gives no output rpm until optimum speed is approached or attained. The coupling 48 drives a conventional three stage compressor modi­fied in the manner described hereinbelow or alterna­tively three single stage compressors connected to­gether in the manner described below.

In FIG. 8, the three stage compressor is indicated schematically by three concentric circles, with the ex­ternal circle 49 representing the first stage, the interme­diate circle 50 representing the second stage, and the center circle 51 representing the third stage of the com­pressor. The respective compressor stages each have their inlet connected, through one-way check valves 52 and manifold 53 to atmosphere. The manifold 53 is connected through a three-way, two-position valve 54, operable to alternately connect the inlet to separate but identical air filters 55. The relative spool position of valve 54 is controlled by a manually operated pilot valve 56 which is operated to select the filter to be used and to permit shifting of filters in response to excess pressure drop. Filter drop is measured by a conven­tional vacuum gauge 57 connected in the manifold 53.

The respective compressor stages also have their outlets connected directly to a common discharge line 58, through one-way valves 59, and conventional pro­portionate reduction in piston displacement where each of the compressor stages for higher pressure is followed regardless of whether a single three stage compressor or three interconnected single stage compressors are em­ployed. However, in either case, conventional plumb­ing between compressor stages is modified by the inclu­sions of the two non-return air pressure operated check valves 59 one connected in the outlet of the first stage compressor and the other in the outlet of the second stage compressor, and by the inclusion of two air pres­sure actuated unloading valves 60 and 61 connected one between the outlet of the first stage compressor and the inlet of the second stage compressor, and the other between the outlet of the second stage compressor and the inlet of the third stage compressor. In normal oper­ating conditions, valve 60 is set to unload at approxi­mately 100 psi and valve 61 to unload at approximately 300 psi. These valves, operating in conjunction with the one-way check valves 52 and 59, thus allow all three compressor stages to independently draw and deliver to line 58 maximum volume low pressure compressed air up to the unload pressure setting of valve 60 at initial startup and at all times when system is highly over­loaded. When the pressure in line 58 reaches the setting for valve 60 and prior to the pressure reaching the set­ting for valve 61, the first and second stages will act as a conventional two stage compressor while the third stage will continue to operate as a single stage compres­sor taking its inlet from the atmosphere. Upon the pres­sure in the system reaching the setting for valve 61, the valve spool position will shift to open, thereby connect-

4,118,637 10 9

ing the outlet of the second stage to the inlet of the third stage, causing the three stages to then operate in the manner of a conventional three stage compressor. This operation will thereafter continue during all normal system operating conditions, with all three stages being 5 serviced by the suction inlet of the first stage compres­sor and with all pressure outlets served, in normal suc­cession, by the pressure outlet of the third stage. Thus, the pressure responsive compressor control system, responding to system pressure, automatically controls 10 the compressors to deliver low, intermediate, or high pressure air, at inversely varying flow rates, to the pipe system.

Compressed air flows from the compressor unit through pipe 58 to a two position, three-way selector 15 slave valve 62 which is normally spring loaded to a straight through flow position and operable either man­ually or automatically as described below to the alter­nate position, to direct the compressed air through one or the other of two high pressure air filters 63 and one- 20 way check valve 64, which the discharge from the respective check valves being connected to direct the flow through meter 65. The outlet of meter 65 is con­nected to a two-way slave shut-off valve 66 which is 25 normally spring loaded to the open position and which may be system pressure closed by manual shifting of two position, three-way pilot valve 67 from indicated normal position "an to closing position "b". From main shut-off valve 66, air flows through a one-way check 30 valve 68 and a manually operated shut-off valve 69 to discharge into the transmission and storage pipe n.

In the valve operation just described above, main line pressure is fed, through a shut-off valve 70 and a pres­sure reducer 71 to the two-position, manually actuated 35 pilot valve 67 to supply actuating pressure to the shut­off valve 66. Reduced pressure is also supplied through line 72 to a manually actuated pilot valve 73 for direct­ing operating pressure, through a suitable speed control regulating orifice 74, to the filter selector valve 62. A 40 similar metering orifice is connected in the pressure line between valves 67 and 66.

A pipe 75 is connected in a loop around valve 62, filter 63 and check valves 64, and a differential pressure gauge 76 is connected in line 75 to give a visual indica- 45 tion of the pressure loss across the filter 63 actually in use, and act as an indicator directing the operator when he is to actuate the valve 73 to shift from dirty to clean filter use. A standard system pressure gauge 77 is also preferably connected to line 75, and a pair of shut-off 50 valves 78 in line 75 may be employed to isolate the gauges 76 and 77.

System air pressure is provided in a line 80 connected to compressor discharge line 58 and a spring-loaded safety valve 81, having a discharge vented to atmo- 55 sphere through a silencer 82, in connected in the line 80 to provide safety relief for the system. A second safety valve 83, normally set to actuate at a pressure lower than safety valve 81, is connected to line 80, through a valve 84. The outlet of safety valve 83 is connected, 60 through a pressure reducing valve 85 to line 86 leading to clutch 48 to automatically disengage the clutch in the event of overpressurization of the system. Simulta­neously, pressure in applied, through speed control orifice valves 74, to a brake or damper system 87 for 65 shutting down the power source 45. A speed control ofifice valve 74 is also connected in line 86 between the pressure reducing valve 85 and the clutch 48.

A high pressure line 88 bypasses safety valve 83 and is connected to a pressure reducing valve 89 for supply­ing reduced air pressure to pilot valve 56 for control­ling, through speed control valve 74, the position of low-pressure filter selector valve 54; and to supply pres­sure to a second manually actuated pilot valve 90 con­nected between lines 88 and line 86. Valve 90 may be manually actuated by apply pressure to line 86 to manu­ally control actuation of the brakes and disengagement of the clutch 48. In the normal operating condition, valve 90 is connected, through and adjustable speed control orifice valve 74, to atmosphere through silencer 82 to thereby slowly bleed pressure from line 86 to permit the brakes 87 and clutch 84 to be released and ready for automatic actuation upon return of safety valve 83 to the normal closed operating position.

Referring now to FIG. 9, compressed air from the respective compressor stations described above flows through the transmission and storage lines 11 to electri­cal generating stations located at convenient positions within the module being served. At the respective gen­erating stations, air flows through a normally open motor actuated, automatic or manually controlled shut­off valve 91 and a one-way check valve 92 to a flow meter 93 and into a manifold header 94. A standard sight gauge 95 is connected, through valve 96, to mani­fold 94 to provide a visual indication of manifold pres­sure.

A plurality of electrical generators 97 are operated at the generating station each from a separate air line from the manifold 94. The respective generators, and their control systems, are substantially identical, with four such generators being illustrated in FIG. 9. Accord­ingly, only one will be described in detail, it being un­derstood that the description applies equally to the other generators except for the manual start-up control for the first generator.

Air flows from the manifold 94 through a normally open manually operable shut-off valve 98 in an air line 99 to a two-position normally closed shut-off slave valve 100. Valve 100 is spring loaded to the closed position and opened against spring pressure by system air pressure supplied through valve 101 and line 102 through a flow restricting orifice valve 103 in the valve 100. Connected in line 102 is a normally closed, sole­noid-actuated pilot valve 104 for controlling the flow of air to valve 100 during normal operating conditions. Also, to initially start up the system, a manually actu­ated, two-position, three-way valve 105 provides, in one position, direct communication between the pilot valve 104 and shut-off valve 100, and in the other position gives direct communication between line 102 and the valve 100, bypassing the solenoid-actuated pilot valve 104 for manual start up conditions. The manual valve 105 is provided only for one of the generators at a sta­tion, and in the FIG. 9 embodiment is provided only in the generator at the left side of the drawing.

From the slave valve 100, air flows through a filter 106 to a motor-actuated, variable pressure delivery reducing valve assembly 107. A high pressure gauge 109 and a pressure differential gauge 108 are connected in a line 110 across filter 106.

From the pressure reducer assembly 107, air flows through a line lubricator 110 to a check valve 111. Con­nected in the line between the lubricator and check valve 111 is a pressure relief, or safety valve 112 which vents to atmosphere through a suitable silencer 82. A second sight gauge is preferably connected in the line

11 4,118,637

12 downstream of the lubricator to provide a visual indica­tion of the lowered line pressure.

From the check valve 111, air flows through a motor operated variable flow restriction orifice 113 to an air motor 114 which vents spent air to atmosphere prefera- 5 bly through a suitable silencer 82.

Air motor 114 drives a generator 97 through a shaft coupling 115, and a governor type gravity controlled fully reversing electrical switch, actuated by a geared drive from the air motor drive shaft, senses the motor 10 speed and controls actuation of the one or more electric motor drives of the pressure delivery reducing valve 107 and the variable orifice 113. An insufficient speed reflected on the governor switch 116 will demand addi­tional pressure and volume delivery to the air motor, 15 and will supply current from suitable contacts in the governor switch 116 and in the customary use demand meter 117 to drive the reversible motors in the direction to increase both volume and pressure. An excessive speed sensed by the governor switch 116 will reverse 20 the flow of current to reduce pressure and volume to air motor 114. Preferably, the motors actuating the valve assembly 107 and the variable orifice 113 operate through a low speed reduction gear mechanism to pro- 25 vide precision control of air flow. Governor switch 116 is a conventional item available commercially.

To start up the system, the manual start up valve 105 is placed in the "b" position, thereby pressurizing the slave valve 100 which is shifted to the open position at 30 a slow rate due to the controlled flow of air through the orifice 103 to gradually bring up the speed of air motor 114 and generator 97 to the predetermined optimum speed of rotation. As the customer use demand meter 117 is energized and calls for the generation of more 35 electricity, solenoid valve 104 will be automatically energized and opened by electrical current from contacts in the meter 117. Thereafter, valve 105 may be normally shifted back to the normal, straight through position "a" and further successive operation of the 40 various electrical generator drives will be automatically controlled by the use demand meter. By providing addi­tional sets of contacts in the conventional use demand meter, as the output of the first generator approaches maximum, the second solenoid switch will be energized 45 to bring the second generator up to speed and on line. This procedure will automatically be followed up to the full capacity of all generator sets through the contacts

Selection of the position of valve 54 is controlled by the pilot valve 56 as described above.

Each of the compressors have their outlets con­nected, through one-way check valves 59 to manifold piping 58 which, in turn, is connected to the transmis­sion and storage pipe 11 through the filter selector slave valve 62, filters 63, check valves 64, meter 65, slave shut-off valve 66 and final check valve 68. The respec-. tive compressors are driven by geared shafts 120 which, in turn, are driven by a bull gear 121 rigidly mounted on the base of turbine hub shaft 122 journaled for rotation about a central fixed shaft 123. The hub shaft 122 is driven by the horizontal supports or spokes 124 for the vertical turbine blades 125. Also, suitable clutch means (not shown), are provided between the compressor and the drive shaft 120.

A pilot operated unloading valve 60 is connected between the check valve 59 of compressor 49A and the inlet of compressor SOA between the compressor and its inlet check valve 52, and a similar pilot operated un­loading valve 61 is connected between the outlet of compressor SOA and the inlet of compressor 51A. As described above, valves 60 and 61 are set such that, as the outlet or main system pressure reaches a predeter­mined minimum, valve 60 will be actuated to connect the outlet of compressor 49A to the inlet of compressor 50A. Between this predetermined minimum pressure and a second predetermined pressure setting for valve 61, the outlet of compressor SOA and compressor 51A will each be discharged into the system outlet; how­ever, above this second predetermined pressure, valve 61 will be actuated to connect the discharge of com­pressor 50A to the inlet of compressor 51A so thai the three independent compressors will thereafter operate as a single, conventional three-stage compressor in the manner described above. Controls for the operation of the clutch and braking system are functionally the same as described above with regards to the embodiment of FIG. 8.

Referring now to FIGS. 11 through 20 of the draw­ings, a wind turbine particularly suited to drive the air compressors employed in this invention will be de­scribed in detail. In FIG. 12, the turbine base is set on a fixed foundation 126 which anchors and rigidly sup­ports the fixed vertical shaft 123. Preferably, shaft 123 is in the form of a large-diameter pipe having an access door 127 at its base, and a ladder assembly 128 mounted in the pipe permits maintenance personnel to ascend the structure regardless of rotation of the turbine. A plural-in the use demand meter, and generators will similarly

be dropped from the line as use demand drops. Referring now to FIG. 10, an air compressor installa­

tion similar to that described hereinabove with regard

50 ity of maintenance access openings 129 are also pro­vided in the fixed shaft 123 at the level of the main turbine bearings 138 and 139, illustrated in FIGS. 14 and 16 and described more fully hereinbelow. to FIG. 8, but particularly well adapted for use with a

wind turbine of the type described hereinbelow, will be described in detail. Since many of the components of 55 the compressor installation of FIG. 10 are identical, either actually or functionally, with that described with regard to FIG. 8, similar reference numerals will be used to designate similar parts. Thus, the compressor station is preferably installed beneath the circular base 60 of the air turbine frame structure and is illustrated as employing three separate, single stage compressors 49A, 50A, 51A corresponding to the first, second and third stages, respectively, of the three stage compressor described above. The compressors each have their inlet 65 connected, through check valves 52 to a manifold 53 which, in turn, is connected through the two position filter selector sl?ve valve 54 to one of the two filters 55.

Extending upwardly from foundation 126 is a fixed, annular frame structure 130 having mounted on its top surface and extending around its outer periphery a plu­rality of guide rollers 131 (see FIG. 20) mounted in opposed pairs by horizontal stub shafts 132 supported by brackets 133 which, in tum, are mounted on a sup-port table 134 the top of which is four-way spring loaded vertically about multiple retaining screws 135 and horizontally about multiple retaining screw assem­bly 136 mounted on the fixed frame 130. Additional guide rollers 131A are mounted in opposed pairs by vertical axle shafts 132A supported in brake assemblies 133.

A revolving blade support wheel frame structure indicated generally by the reference numeral 137 in

13 4,118,637

14 FIGS. 11 and 13, is supported on the fixed frame 130 and the fixed shaft 123 for rotation about the vertical axis of the fixed shaft by the upper and lower bearing assemblies 138, 139, respectively, and by an annular, flanged monorail track 140 adapted to engage and be 5 guided and supported by the plurality of pairs of guide rollers 131 and UIA.

The rotating frame 137 includes the vertical rotating hub shaft 122 having the horizontal spokes 124 rigidly mounted thereto, as by brackets 141, at spaced points 10 along the length of the shaft 122, and the outer ends of the spokes, at each level, are connected by horizontal girts 142 extending around the periphery of the rotating frame, and the respective levels of spokes are joined by vertical columns 143, as best seen in FIGS. 11 and 13. 15 As previously indicated, the fixed vertical turbine blades are mounted on the outer ends of the spokes 124 for rotation therewith about the vertical axis of the assembly, with the vertical turbine blades extending, in effect, throughout the heights of the rotating frame 20 assembly 137.

A plurality of adjustable sag rods, or braces 144 pro­vide structural integrity for the rotating frame assem­bly. A fixed catwalk assembly 145 is mounted on the upper end of the fixed shaft 123 which projects above 25 the top of the rotating frame assembly, with the catwalk assembly 145 being supported by a suitable conical truss frame assembly 146. The catwalk and truss assembly provides access for maintenance at the top of the assem­bly, and provides anchorage at the outer periphery of 30 the assembly for a plurality of guide lines 147 which extend to suitable anchors 148 at spaced points around the periphery of the turbine structure.

Referring now to FIGS. 17 through 20, the brake system is illustrated as including a plurality of pneumati- 35 cally actuated opposed action brake assemblies 87 mounted in pairs at spaced intervals around the frame 130 in position to engage the top and bottom flanges 150, 151 respectively, of track 140, with the brake as­semblies in the respective pairs engaging the flanges on 40

opposed sides of the central web 152. The brake assem­blies are identical in structure and operation and ac­cordingly only one will be described in detail, it being understood that the description applies equally to the remaining brake assemblies. 45

As best seen in FIGS. 17 and 18, the bracket assembly 133 includes, in its central portion, a fixed shelf 153 having mounted, on its bottom surface, a spring-biased, pneumatically actuated brake cylinder 154, the rod of which projects upwardly through the shelf to actuate 50 the brakes. Mounted on the top of the brake cylinder rod is a top actuating arm 155 retained in position by a pair of locking nuts 156 on the upper end of the rod. A pair of horizontally extending bolts 157 are mounted, one in each end of the arm 155, with the bolts projecting 55 inwardly through slots in the vertical web of bracket 133. Supported on the distal ends of bolts 157 is a brake shoe mounting bracket 158 for sliding movement along the vertical face of the web of bracket 133. A brake shoe 159 mounted on the top surface of bracket 158 is 60 adapted to engage the undersurface of the top flange 150 to brake the rotating turbine support frame assem­bly.

At the same time, a lower brake shoe 160, mounted on a second mounting bracket 161, is pressed down- 65 wardly into engagement with the top surface of the lower flange 151 by a second pair of the horizontal bolts 157 projecting through a second pair of slots in the web

of the bracket 133. Movement of the lower mounting shoe is effected by a pair of pivoted arms, each having its inner end pivotally connected to the piston rod of the brake cylinder 154 and its outer end pivotally connected to the horizontal bolts 157, and having an intermediate point pivotally connected to an upstanding bracket 162 mounted on the shelf 153. Thus, actuation of the brake cylinder 154 by the application of air, at reduced pres­sure, through the line 86 and the flow restrictors 74 will project the cylinder rod upward to simultaneously urge brake shoes into frictional contact with both the upper and lower flanges of the track 140, on each side thereof, and at spaced points around the periphery of the turbine frame assembly. As described hereinabove, upon leak­age of the air pressure from the line 86, the brakes will automatically be released by the spring biased brake cylinder.

Referring now to FIG. 14, 15 and 16 of the drawings, it is seen that the upper bearing assembly 138 comprises a lower annular ball race 200 supported on the top inner peripheral portion of the rotatable hub shaft 122. The lower bearing race 200 is accurately positioned by an adjusting bracket assembly 201 which is vertically mov­able by nuts 202 which engage a fixed flange 203. Once the race 200 is accurately positioned, it is locked in place by suitable set screws 204. The bottom race and the adjusting bracket assembly is accessible from the interior of the fixed shaft 123 through the door opening 127.

The upper race 205 is mounted on the outer periph­eral surface the fixed shaft 123 in position to roll on spherical ball bearing elements 206 disposed between the upper and lower races. A second adjustable bracket assembly 207 supported from an annular flange 208 on shaft 123 provides means for adjusting the position of the bracket 207, and set screws 209 are provided to firmly anchor the mounting bracket in position.

The lower bearing assembly 139 is preferably posi­toned at the base of the fixed shaft 122 and runs in an oil bath 210 within a sump in the foundation 126. The lower bearing race 211 is mounted on the outer periph­ery of the inner fixed shaft 123 by an adjustable support bracket assembly 212 substantially identical to the sup­port bracket assembly 201 but adapted to be mounted on the outer rather than the inner surface of the support­ing shaft. Positioning of the lower race 211 may be accomplished by the adjustable bracket 212, which is accessible through the oil sump 210.

The upper race 213 of the lower bearing 139 is mounted on the inner periphery of the rotatable shaft 122, adjacent the bottom thereof, by a second adjustable mounting bracket assembly 201 mounted in inverse relation to the mounting bracket 201 supporting the race 200 of bearing 138. Access to the top bearing race 213, and its supporting bracket 201 is through the access openings 127 which, as shown in FIG. 14, may be closed by the movable door assembly 214.

Preferably, the bearing races of both the upper and lower turbine bearings are fabricated in arcuate sections which are mounted in position and welded together, with the welded joint being subsequently ground to provide a continuous smooth race for the balls 206. This enables assembly of the respective races, or sections thereof, as necessary, through the access openings 127, with the welded joints, indicated generally at 216 in FIG. 5, being accomplished in the space between the concentric shafts 122 and 123.

15 4,118,637

16 Referring now to FIG. 25, a section of a national grid

system is schematically illustrated to indicate the isola­tion cut-off valves within the over-all system, and the manner in which these valves are located to isolate sections of the grid in which trouble may develop. Also 5 illustrated schematically on FIG. 25 is the manner in which the individual small or large modules such as those illustrated in greater detail in FIGS. 1 and 2 are tied into the larger regional, national or continental grid system whereby excess air from such a module may 10 flow, via the grid system plumbing, to adjacent mod­ules, or whereby air may be drawn from adjacent mod­ules in times of insufficient air pressure at a particular module. Preferably, two-way meters are connected in the grid lines at the extremities of grid sections such as 15 Section G 192 to measure the flow of air where needed.

As shown in FIG. 21, each module is connected to a pipe 18 of the grid system through a pipe 16 having connected therein a two-way meter assembly 17 for measuring the flow both from the module to the grid 20 and from the grid into the module. The meter assembly consists of a pair of automated cut-off valve assemblies 163 located in the line 16 at each end of the flow mea­suring system. The pipe 16 adjacent each valve 163 is connected to aT-joint, with the open ends of the T 25 being connected by parallel pipe sections 164, 165. Con­nected in the pipe section 165 is a one-way check valve 166 permitting flow from the module to the grid pipe only, through a flow meter 167 which measures the quantity of air flowing into the grid. Check valve 166 is 30 spring biased to require a substantial predetermined pressure differential between the pressure in the module and that in the grid to thereby assure, particularly for smaller modules, an ample reserve supply of air by preventing the larger grid from drawing air from these 35 smaller modules down below a required minimum oper­ation level.

A second one-way check valve 168 is connected in the branch line 164 to permit flow only in the direction from the main grid piping into the module in question. 40 Preferably, check valve 168 is also spring loaded, with the spring loading being relatively small, functioning primarily to assure against reverse flow through a sec­ond meter 169 connected in branch pipe 164 to measure the flow of air from the grid into the module. It is be- 45 lieved apparent that, by integrating the readings from meters 167 and 169, the net air flow from or to a module for any given time period may be determined.

FIG. 22 illustrates schematically the operation of the automated grid isolating shut-off valves 170. These 50 isolation valves are connected in each grid line 18 be­tween the points interconnection with grid lines run­ning in the transverse direction as shown in FIG. 25. The respective valves 170 are located in manholes 171 and are actuated, through a suitable gear drive train 172 55 by a motor 173 which preferably is an air-actuated mo­tor.

Actuation of the motor 173 is controlled by a three position, four-way closed-center slave valve 174. A spring biased damper assembly 175 mounted in the grid 60 pipe 18 adjacent the valve 170 has a cam surface bearing upon one end of a spring-biased push rod assembly 176 extending outwardly through the side wall of the pipe 18 in position to engage an actuating rod for valve 174. The spring biasing pressure on rod 176 is such that a 65 predetermined minimum flow rate of air through pipe 18, in either direction, will be required to tilt the damper and cause the cam to press the push rod upward. Thus,

in the event of a line break, on either side of the particu­lar valve 170, a sudden increase in flow rate through the pipe will push the rod 176 upward to move the valve 174 into position to drive motor 173 in a direction to close the valve 170. At the same time, a detent on the valve actuating rod 176 engages a switch 177A which, through normal electrical circuits (not shown) transmits a signal to a control panel in the manhole and simulta­neously to a regional and a national monitoring center. This enables immediate identification of trouble spots and enables immediate dispatch of maintenance person­nel from each adjacent region in the grid serviced by the line in question.

Main line pressure is supplied to a pipe 177 through a pair of cut-off valves 177B and check valves 178 con­nected one each in line 18 on each side of the valve 170. A pressure reducer 180 in line 177 reduces the main line pressure to that required to operate the motor, and directs the reduced air pressure into a T-joint which directs the air through a conduit 181 through a flow control regUlating orifice 182 to valve 174, and to a three position manual pilot valve 183. From valve 183, air may be directed, depending upon the position of the valve, to a pneumatic operating cylinder 184 through conduit 185 to shift the valve upward to direct air to motor 173 to drive the valve 170 to the closed position, or alternatively to direct air through line 186 to the operating cylinder 187 to shift the valve to the position to drive motor 173 to move the valve to the open posi­tion. In the tird, or null position, of valve 183, air in the lines 185 and 186 are vented to atmosphere.

As shown in FIG. 23, at all low points in the transmis­sion and storage pipe system, condensation drains are provided. These condensation drains include an isola­tion valve 188 in a line from the bottom of the pipe, for example, the main grid pipe 18, leading to a collection chamber 189. A conventional ball float valve is mounted in the collection chamber 189 and operates, when the condensation reaches a predetermined level, to permit main line pressure to blow the condensate, through It check valve 190 and drain line 191, to a con­densate storage tank 192.

Due to the large diameter and heavy wall thickness of the main grid piping conventional expansion loops may not be deemed practical. However, to accommodate inevitable expansion and contraction of the pipe, 0-rings sealed sliding expansion joints are provided at spaced intervals, as required. These expansion joints, illustrated in FIG. 24, comprise mating male and female bolted welding flanges 193, 194 respectively, with spring loaded bolt connections therebetween, welded one to each end of the adjacent pipe sections 18.

The spring loading is provided by opposed springs 195 retained by bolts 196 through outwardly projecting annular flanges. A plurality of O-ring seals 198 are pro­vided within the telescoping overlap portion of the respective well flanges 193, 194. To prevent foreign material from interferring with the telescoping action of the expansion joint, an annular gasket in the form of a soft rubber hose is positioned between the overlying end of well flange 193 and the outwardly projecting bolt flange portion of the element 194.

While I have disclosed and described preferred em­bodiments of my invention, I wish it understood that I do not intend to be restricted solely thereto, but rather that I intend to include all embodiments thereof which would be apparent to one skilled in the art and which come within the spirit and scope of my invention.

17 4,118,637

18 What is claimed is: 1. A system for collecting, storing and distributing

energy comprising a transmission-storage pipe system including an interconnected network of large diameter high pressure conduit for storage and transmission of 5 large volumes of compressed air throughout a predeter­mined wide geographical area, a plurality of energy collector-converters including air compressor means operatively connected to said pipe system and utilizing available energy to compress air and deliver the com- 10 pressed air to said pipe system, said air compressor means including a plurality of separate compressor stages, pressure responsive control means operatively interconnecting said compressor stages for automati­cally delivering low, intermediate or high pressure air at 15 inversely varying flow rates to the pipe system in re­sponse to the pressure in the system, at least one air­actuated generator station, conduit means operatively connecting said at least one generator station to said pipe system for withdrawing compressed air therefrom 20 for operating said at least one generator station, said at least one generator station including air motor means operably connected to said conduit means and operated by the compressed connected to said conduit means and operated by the compressed air for driving an electric 25 generator, and air pressure and air volume control means connected in said conduit means and operable simultaneously to control operations of said air motor means, said air pressure and air volume control means being capable of varying the work output of said air 30 motor means in accordance with a demand signal to thereby accurately control the rate of rotation of said air motor means to drive an electric generator at its optimum speed.

2. The energy collecting, storing and distributing 35 system as defined in claim 1 wherein at least a portion of said plurality of energy collector-converters are non­polluting, natural energy collector-converters operable to collect and convert natural energy to rotational force for driving said ccompressor means. 40

3. The energy collecting, storing and distributing system as defined in claim 1 wherein at least a portion of said plurality of energy collector-converters comprise a wind turbine including a plurality of generally verti­cany extending turbine blades mounted to rotate in a 45 horizontal plane about a fixed vertical axis, said turbine blades being adapted to be driven by wind force.

4. The energy collecting, storing and distributing system as defined in claim 1 wherein each of said at least one generator stations comprise a plurality of air motors 50 each operable to drive a separate electric generator at its optimum speed, and wherein said air pressure and air volume control means include means responsive to the demand for electrical energy for sequentially activating said plurality of air motors to drive an electric generator 55 at its optimum speed to generate electricity in accor­dance with the demand therefor.

5. The energy collecting, storing and distributing system as defined in claim 4 further comprising air flow meter means connected in said conduit means for mea- 60 suring the quantity of compressed air utilized by each said generator station.

6. The energy collecting, storing and distributing system as defined in claim 1 wherein said transmission­storage pipe system comprises a system of large diame- 65 ter high pressure widely spaced pipe disposed in a gen­erally rectangular grid covering said predetermined wide geographic area, and a plurality of area modules

iocated within said wide geographic area, conduit means connecting each said module to said grid, said modules each comprising a plurality of said collector­converters and at least one said generator station, whereby compressed air may flow into said modules from said grid and out of said modules into said grid.

7. The energy collecting, storing and distributing system as defined in claim 6 further comprising an inte­grating meter assembly connecting each said module with said grid, said integrated meter assembly being operable to measure the net flow of air between the grid and the respective associated modules.

8. The energy collecting, storing and distributing system as defined in claim 7 wherein said means con­necting each said module to said grid further comprises valve means preventing air flow from said modules into said grid until a predetermined minimum pressure dif­ferential is established therebetween.

9. The energy collecting, storing and distributing system as defined in claim 8 wherein said valve means includes a spring loaded one-way check valve operable to prevent compressed air from flowing from said mod­ules when the pressure therein is below a predetermined minimum to thereby assure a minimum reserve of com­pressed air in each said module.

10. The energy collecting, storing and distributing system as defined in claim 6 further comprising at least one isolating valve located in each pipe section of said grid which bounds each generally rectangular section encompassed by said grid, and means responsive to the rate of flow of air through the respective pipe sections of said grid for closing said isolating valves therein to thereby isolate predetermined sections of said grid.

11. The energy collecting, storing and distributing system as defined in claim 11 further comprising two­way metering means located in the pipe of said grid at the boundries of predetermined sections thereof, said two-way metering means being operable to measure the net air flow into or out of the respective sections of said grid.

12. The energy collecting, storing and distributing system as defined in claim 1 wherein said air compressor means comprises respective first, second and third stages, an ambient pressure suction source, a first stage discharge line, a second stage discharge line, a third stage discharge line, a discharge sink connected with said pipe system, first suction selector means for con­necting the inlet of said second stage with one of said ambient pressure suction source and said first discharge line; said first suction selector including pressure re­sponsive means for automatically changing the suction of said second stage from said ambient pressure suction source to said first stage discharge line upon the occur­rence of a first predetermined pressure in said discharge sink, second suction selector means for connecting the inlet of said third stage with one of said ambient pres­sure suction source and said second stage discharge line; said second suction selector means being operable to automatically effect change of the inlet of said third stage from said ambient pressure suction source to said second stage discharge line upon the occurrence of a second predetermined pressure higher than said first predetermined pressure in said discharge sink, and first and second stage check valves disposed respectively in said first and second stage discharge lines for preventing air flow from said discharge sink back into said first and second stages when said first and second stage dis-

19 4,118,637

20 charge lines are connected respectively with the suc­tions of said second and third stages.

13. A system for collecting, storing and distributing energy comprising a transmission-storage pipe system including an interconnected network of large diameter 5 high pressure conduit for storage and transmission of large volumes of compressed air throughout a predeter­mined wide geographical area, said system comprising a floating storage means including a plurality of loops of high pressure pipe rigidly joined together in a plurality 10 of superimposed layers and interconnected to form an auxiliary compressed air storage source, said floating storage means including means for anchoring to the bottom of a body of water in which it is floating, and flexible connection means for connecting said floating 15 storage means with high pressure pipe on shore, said flexible connection means being weighted heavily enough to overcome byoyancy and lie along said bot­tom between said floating storage means and said high pressure pipe on shore, said floating storage means con­taining at least one said energy collector-converter 20 supported thereon, a plurality of energy collector-con­verters including air compressor means operatively connected to said pipe system and utilizing available energy to compress air and deliver the compressed air to said pipe system, said air compressor means including 25 a plurality of separate compressor stages, pressure re­sponsive control means operatively interconnecting said compressor stages for automatically delivering low, intermediate or high pressure air at inversely vary­ing flow rates to the pipe system in response to the 30 pressure in the system, at least one air-actuated genera­tor station, conduit means operatively connecting said at least one generator station to said pipe system for withdrawing compressed air therefrom for operating said at least one generator station, said at least one gen- 35 erator station including air motor means operably con­nected to said conduit means and operated by the com­pressed air for driving an electric generator, and air pressure and air volume control means connected in said conduit means and operable simultaneously to con- 40 trol operations of said air motor means, said air pressure and air volume control means being capable of varying the work output of said air motor means in accordance with a demand signal to thereby accurately control the rate of rotation of said air motor means to drive an 45 electric generator at its optimum speed.

14. The energy collecting, storing and distributing system of claim 13 wherein said floating storage means is a shallow water type installation and said anchoring means comprises multiple pilings having vertically dis- .50 posed, slidable sleeves on each said pile, said sleeves being connected with said floating storage means so as to allow said storage means to rise and fall with changes in level of said water.

15. A method for collecting, storing and distributing energy throughout a wide geographical area, said 55 method comprising the steps of constructing a transmis­sion-storage pipe system including an interconnected network of large diameter high pressure conduit for storage and transmission of large volumes of com­pressed air throughout said wide geographical area, 60 providing a plurality of energy collector-converters each including air compressor means operatively con­nected to the pipe system and utilizing available energy to compress air and deliver the compressed air to the pipe system, said air compressor means including a 65 plurality of separate compressor stages, regulating the operation of said compressor means by providing pres­sure responsive controls operatively interconnecting

the compressor stages for automatically delivering low, intermediate or high pressure air at inversely varying flow rates to the pipe system in response to the pressure in the system, providing at least one air-actuated gener­ator station operatively connected to the pipe system through conduit means permitting the withdrawal of compressed air therefrom for operating said at least one generator station, said at least one generator station including air motor means operably connected to the conduit means for operation by the compressed air and driving an electric generator to convert the energy in said compressed air to electrical energy, and providing air pressure and air volume controls connected in the conduit means and operable simultaneously to control the operation of the air motor means, said air pressure and air volume control means being capable of varying the work output of the air motor means in accordance with a demand signal to thereby accurately control the rate of rotation of the air motor means to drive the electric generator at its optimum speed regardless of the load on the generator.

16. The method defined in claim 15 wherein at least a portion of said plurality of energy collector-converters are non-polluting, natural energy collector-converters operable to collect. and convert natural energy to rota­tional force for driving the compressor means for com­pressing air.

17. The method defined in claim 15 wherein at least a portion of said plurality of energy collector-converters are wind turbines each including a plurality of generally vertically extending turbine blades mounted to rotate in a horizontal plane about a fixed vertical axis, said tur­bine blades being adapted to be driven by wind force.

18. The method defined in claim 15 wherein each of the generator stations comprise a plurality of air motors each connected with and operable to drive a separate electric generator at its optimum speed, and wherein the air pressure and air volume control means include means responsive to the demand for electrical energy for sequentially activating said plurality of air motors to drive an electric generator at its optimum speed to gen­erate electricity in accordance with the demand there­for.

19. The method defined in claim 15 wherein transmis­sion-storage pipe system is constructed to include a system of large diameter high pressure widely spaced pipe disposed in a generally rectangular grid covering the predetermined wide geographic area and a plurality of area modules located within the wide geographic area, and conduit means are provided to connect each module to the grid, and wherein each of the modules each include a plurality of collector-converters and at least on said generator station, whereby compressed air may flow into the modules from the grid and out of said modules into the grid.

20. The method defined in claim 19 further compris­ing the steps of connecting an integrating meter assem­bly in the conduit between each module and the grid, and measuring the net flow of air between the grid and the respective associated modules by use of said inte­grating metering assembly.

21. The method defined in claim 20 further compris­ing the steps of monitering the pressure in each module and in the pipe grid, and controlling the flow of com­pressed air therebetween to prevent air flow to the respective modules into the grid until a predetermined minimum pressure differential is established therebe­tween.

... ... .. .. ...

UNITED STATES PATENT OFFICE Page 1 of 2

CERTIFICATE OF CORRECTION

Patent No. 4,118,637 Dated: October 3, 1978

Inventor(s) LOUIS EUGENE TACKETT

It is certified that error appears in the above~identified patent and that said Letters Patent are hereby corrected as shown below:

IN THE DRAWINGS:

FIG. 3, the flow direction of check valve 92 should be reversed.

FIG. 10, the flow direction of check valves 64 and 68 should be reversed.

FIG. 12, reference No. "30" should be -- 130 --.

FIG. 14, reference No. "139" should be 203

IN THE SPECIFICATION AND CLAIMS:

Column 1, line 39, after "storage", "pf" should be -- of

Column 3, line 66, "12"should be 11

Column 5, line 20, "air ll should be or --

Column 6, line 7, "13" should be -- 14 -- . Column 7, line 62, lI avialable" should be -- available

Line 63, "marin" should be marille -- . Column 9, line 21, "which" should be with -- . I

Line 56, aft.er "82, " "in" should be -- is , Line 64, II in" should be -- is -- . and I

Line 67, "ofifice" should be -- orifice

--i

-- . ,

UNITED STATES PATENT OFFICE Page 2 of 2

CERTIFICATE OF CORRECTION

Patent No. 4,118,637 Dated: October 3, 1978

Inventor(s) LOUIS EUGENE TACKETT

It is certified that error appears in the above-identified patent and that said Letters Patent are hereby corrected as shown below:

- for

Column 10, line 8, "by" should 'be -- to -- i '

Line 14, "84" should be -- 48 --1 and Line 5~, after "only", "in" should be'

Column 12; line 65, "brake" should be -- bracket --.

Column 15, line 52, after "points" insert -- of --.

Column 16, line 57, !lwell" should·be -- weld

Column 17, lines 23 and 24, delete "operated by the ompressed connected to said conduit means and"; and

Line 40, correct the spelling of "compressor".

Column 19, line 18, "byoyancy" should be buoyancy

Column 20, line 52, lion II should be -- on.e --: and

[SEAL]

Line 64, II to II (second occurrence) should be ~- of --.

Attest:

RUTH C. MASON Attesti", Officer

eigncd and ecalcd this

Twelfth Day of Ju," 1979

DONALD W. BANNER

United States Patent [19]

Organek et al.

[54] DRIVELlNE CLUTCH WITH UNIDIRECTIONAL APPLY BALL RAMP

[75] Inventors: Gregory J. Organek, Detroit; David M. Preston, Clarkston, both of Mich.

[73] Assignee: Eaton Corporation, Cleveland, Ohio

[21] Appl. No.: 766,838

[22]

[51]

[52]

[58]

[56]

Filed: Dec. 13, 1996

Int. CI.6 ............................ F16D 13/04; F16D 11/00; F16D 19/00

U.S. CI. ........................ 192/35; 192/54.52; 192/84.7; 192/93; 192/40; 475/149

Field of Search ..................................... 475/154, 149,

5,078,248 5,441,137

475/318, 5, 151, 453; 192/54.5, 35, 84.7, 54.52, 93

References Cited

U.S. PATENT DOCUMENTS

1/1992 Yesnik ................................ 192/84.7 X 8/1995 Organek et al. ...................... 192/93 A

4

111111 1111111111111111111111111111111111111111111111111111111111111 US005810141A

[11] Patent Number:

[45] Date of Patent:

5,810,141 Sep. 22, 1998

5,469,948 5,482,512 5,503,602 5,651,437

11/1995 Organek et al. .......................... 192/35 111996 Stevenson ................................... 475/5 4/1996 Dick ...................................... 192/35 X 7/1997 Organek et al. ................... 192/84.7 X

Primary Examiner--Charles A. Marmor Assistant Examiner-Marcus Charles Attorney, Agent, or Firm-I,oren H. Utho/I, Jf.; Howard D. Gordon

[57] ABSTRACT

A ball ramp mechanism having a control ring acting with an actuation ring to apply a clamping force on a driveline clutch during both a vehicle driving mode and a vehicle coast mode using a planetary gearset acting with a one-way clutch between a sun gear and meshing planetary gears to define rotation of the control ring with respect to the actuation ring in a direction tending to further activate the ball ramp mechanism. In the vehicle drive mode the planetary gearset is locked by the one-way clutch and in a vehicle coast mode the one-way clutch releases and the planetary gearset rotates the control ring through a coil pole in a direction to further activate the ball ramp mechanism.

11 Claims, 3 Drawing Sheets

31

32A 44

42

16

u.s. Patent Sep. 22, 1998

lOB

Sheet 1 of 3

CLUTCH CONTROL 101&--"­

UNIT

15

5,810,141

32A 44

42

40 47 ---~.

16

( )

\ )

u.s. Patent Sep. 22, 1998 Sheet 2 of 3 5,810,141

FIG 2

FIG 3

14

64/ 23A

20A FIG 4 /1 22A, /62

\ I 12 I \ -1. 22C

.-L- '\

\ / -,--\ } ) 14

45 64/ 23A

u.s. Patent Sep. 22, 1998 Sheet 3 of 3 5,810,141

FIG 5

5,810,141 1

DRIVELlNE CLUTCH WITH UNIDIRECTIONAL APPLY BALL RAMP

BACKGROUND OF THE INVENTION The present invention relates to a vehicle drive line clutch

and, more particularly, to a driveline clutch where a friction disc is clamped to an engine flywheel using a ball ramp actuator where a one-way clutch and a planetary gearset are used to provide both drive and coast driveline clutch lock­up.

Driveline clutches commonly use a plurality of springs to clamp a friction disc to an engine flywheel. The springs are disposed within a pressure plate assembly which is bolted to the flywheel. A mechanical linkage that controls the pressure plate spring mechanism is displaced by the operator to control the lock-up and release of the clutch.

Efforts to automate the operation of the clutch using electronics are currently underway. It is known to use an electromechanical or hydraulic actuator connected to the mechanical linkage to, in essence, replace the operator for more accurate clutch operation during transmission shifting. Using such an actuator, the mechanical linkage is moved in response to an electrical control signal generated by a central microprocessor used to process a variety of vehicle sensor inputs based on operating conditions to determine when and in what manner the driveline clutch should be activated, or deactivated.

The use of a ball ramp actuator to load a clutch pack in a vehicle driveline differential is known. U.s. Pat. Nos. 4,805, 486 and 5,092,825, the disclosures of which are hereby incorporated by reference, disclose limited slip differentials where a clutch pack is loaded in response to the activation of a ball ramp actuator initiated by rotation of a servo motor or a solenoid driven brake shoe on an activating ring. The advantage of the ball ramp mechanism over other actuators is that it converts rotary motion into axial motion with a very high force amplification, often 100: 1 or greater. A ball ramp actuator has also been utilized in a vehicle transmission to engage and disengage gearsets by loading a gear clutch pack in response to a signal as disclosed in U.s. Pat. No. 5,078, 249, the disclosure of which is hereby incorporated by reference.

2 In other words, this type of ball ramp actuated clutch

using a unidirectional ball ramp having only a single ramp angle, will cause the clutch to disengage when the engine is not supplying rotational energy into the transmission such as

5 when the vehicle is coasting. When coasting, the flywheel is no longer supplying rotational energy to either the transmis­sion or to the ball ramp actuator. In this circumstance, the relative rotation of the actuation ring and control ring has been reversed such that the ball ramp axial displacement is

10 collapsed thereby allowing the pressure plate to pull away from the clutch disc. The result is that the engine is disen­gaged from the transmission and any engine braking effect is eliminated.

A bidirectional ball ramp actuated clutch is disclosed in 15 U.S. Pat. Nos. 2,937,729 and 5,505,285. Using this more

expensive and complicated technology, the ball ramp actua­tor incorporates bidirectional ramps which provide activa­tion when there is relative rotation between the control ring and the actu ation ring in either direction. However, the ball

20 ramp must transition through the nonactivated state which will result in temporary undesirable clutch slippage and the components are more expensive to fabricate than a unidi­rectional unit. Also, a bidirectional ball ramp will have reduced rotational travel between the control ring and the

25 actuation ring in a given package size as compared to a unidirectional ball ramp mechanism. Thus, a unidirectional ball ramp mechanism is preferred if it can be made to activate in both vehicle drive and coast operating modes.

The ball ramp actuator comprises a plurality of roller 30 elements, a control ring and an opposed actuation ring where

the actuation ring and the control ring define at least three opposed single ramp surfaces formed as circumferential semi-circular grooves, each pair of opposed grooves con­taining one roller element. A plurality of thrust rollers (or

35 other type of thrust bearing) are interposed between the control ring and a housing member, rotating with and connected to the input member such as a flywheel. An electromagnetic coil is disposed adjacent to one element of a control clutch so as to induce a magnetic field that loads

40 the control clutch which in turn applies a force on the control ring of the ball ramp actuator. The control clutch can be similar to those commonly used for vehicle air conditioning

In both of these vehicle applications, one side of the ball ramp actuator, commonly called a control ring, reacts against case ground through the force induced by an elec- 45

tromagnetic field generated by a coil or is rotated by an electric motor relative to case ground. To generate greater clamping forces, the electrical current supplied to the coil or motor is increased thereby increasing the reaction of the control ring to case ground which rotates the control ring 50

relative to an actuation ring thereby causing rolling elements

compressors.

SUMMARY OF THE INVENTION

The present invention is characterized by a Hywheel driven by a prime mover and a transmission input shaft coupled through a ball ramp actuated clutch. The ball ramp mechanism has a plurality of unidirectional variable depth grooves (ramps) and an actuation ring having single direc­tion variable depth grooves at least partially opposed and substantially similar in geometry to those of the control ring. Examples of ball ramp actuator clutch systems are shown in U.s. Pat. Nos. 1,974,390; 2,861,225; 2,937,729; 3,000,479; 5,485,904 and 5,505,285. The actuation ring is prevented from counter rotating upon clutch lock-up in the vehicle coast mode through the use of a one-way clutch. A planetary gearset is used to allow the ball ramp actuator to increase the clamping force on the clutch friction disc in the coast mode. Thus, using the present invention, the ball ramp mechanism does not transition through the nonactivated state when the vehicle goes from a drive to a coast mode and clutch slippage is reduced.

to engage ramps in the control and actuation ring which increase the axial movement and clamping force on the clutch pack.

It is also known to use a ball ramp actuator to load a 55

vehicle master clutch as disclosed in u.s. Pat. Nos. 1,974, 390; 2,861,225; 3,000,479; 5,441,137; 5,469,948; 5,485,904 and 5,505,285, the disclosures of which are hereby incor­porated by reference. One problem with the use of a ball ramp actuator to supply the vehicle driveline clutch clamp- 60

ing force is that the mechanics of prior art unidirectional ball ramp mechanisms result in a loss of clamping force when the vehicle is in a coast mode. Once the engine power is reduced and the driveline is actually overrunning the engine (coast mode), the prior art ball ramp actuator with single ramp 65

unidirectional actuation will disengage the clutch thereby eliminating the potential for engine braking of the vehicle.

An electromagnetic coil is used to activate a control clutch which frictionally couples the control ring through the planetary gearset to the transmission input shaft. When

5,810,141 3 4

energized by the coil, the ball ramp mechanism provides a clamping force on the clutch friction disc where the ampli­tude of the clamping force immediately increases whenever there exists a rotational speed differential between the input flywheel and the input shaft of the vehicle transmission. 5

According to the present invention, the amplitude of the clamping force is held at a given level as long as the coil is energized by action of a one-way clutch so that when the vehicle enters a coasting mode where the engine is braking

the embodiment illustrated in the drawings and specific language will be used to describe the same. It will never­theless be understood that no limitation on the scope of the invention is thereby intended, such alterations and further modifications in the illustrated device, and such further applications of the principles of the invention as illustrated therein being contemplated as would normally occur to one skilled in the art to which the invention relates.

Certain terminology will be used in the following descrip­tion for convenience in reference only and will not be limiting. For example, the terms "forward" and "rearward" will refer to directions forward and rearward of the clutch assembly as normally mounted in a vehicle. The terms "rightward" and "leftward" will refer to directions in the

as opposed to driving the vehicle, the ball ramp actuator 10

remains fully activated. Clutch slippage in the drive mode will cause the ball ramp mechanism to increase the clamping force on the clutch disc. Also, in the coasting mode, if for some reason there is clutch slippage, the planetary gearset provides for additional relative rotation between the control 15

ring and the actuation ring in the proper direction to increase the clamping force on the clutch friction plate.

drawings in connection with which the terminology is used. The terms "inwardly" and "outwardly" will refer to direc­tions toward and away from respectively, the geometric center of the apparatus. The terms "upward" and "down­ward" will refer to directions as taken in the drawings in

One provision of the present invention is to prevent a ball ramp actuated clutch from disengaging when the input torque is reversed.

Another provision of the present invention is to prevent a ball ramp actuated clutch having unidirectional ramps from disengaging when the driveline torque is in a coast mode by locking the rotational orientation between a control ring and an actuation ring using a one-way clutch.

Another provision of the present invention is to allow a ball ramp actuated clutch having unidirectional ramps to increase its engagement level when the drive line torque is in a coast mode utilizing a planetary gearset.

Another provision of the present invention is to allow a drive line clutch actuated by a ball ramp actuator having unidirectional ramps to increase its actuation force when the transferred driveline torque reverses direction utilizing a planetary gearset incorporating a one-way clutch acting between the control ring and the transmission input shaft.

Still another provision of the present invention is to allow a driveline clutch actuated by a ball ramp actuator having unidirectional ramps to increase its actuation force when the transferred driveline torque reverses direction utilizing a planetary gearset acting between the control ring and the transmission input shaft where a one-way clutch prevents reverse rotation of the planetary gears relative to the trans­mission input shaft.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a partial cross-sectional view of the ball ramp actuator of the present invention;

FIG. 2 is an axial cross-sectional view of the ball ramp mechanism of the present invention taken along line II-II of FIG. 1;

FIG. 3 is a cross-sectional view of the ball ramp mecha­nism of the present invention taken along line III-III of FIG. 2 with the ball ramp mechanism in a nonenergized state;

FIG. 4 is a cross-sectional view of the ball ramp meclla­nism of the present invention taken along line III-III of FIG. 2 with the ball ramp mechanism in an energized state; and

20 connection with which the terminology is used. All forego­ing terms mentioned above include the normal derivatives and equivalents thereof.

Referring now to the drawings, which are not intended to limit the present invention, FIG. 1 is an axial cross-sectional

25 view of a main drive line clutch assembly 2 of the type in which the present invention may be utilized. The main driveline clutch assembly 2 includes a flywheel 4 rotatably driven by a prime mover (not shown) such as an internal combustion engine by its output crankshaft 3 which is

30 coupled to a transmission 7 by a clutch assembly 2. A bellhousing 6 surrounds the flywheel 4 having a flywheel friction surface 4A and supports the transmission 7 including the transmission input shaft 8 which extends to nonrotatably engage a clutch disc 10 having friction pad lOA and friction

35 pad lOB through splines 10C at the left end of the trans­mission input shaft of where the transmission input shaft 8 then extends rightward to drive the transmission gearing. An actuation ring 12, which also functions as a pressure plate and is rotatably connected to the pressure plate housing 16,

40 is used to clamp the clutch disc 10 through the attached friction pads lOA and lOB to the Hywheel 4 at the flywheel friction surface 4A thereby transferring the rotational power from the prime mover to the transmission 7 through the transmission input shaft 8 and eventually to the rest of the

45 vehicle driveline. In prior art systems, the clutch pressure plate is forced

toward the flywheel using a plurality of loading springs. When the operator wishes to disengage the clutch disc, a mechanical release mechanism is activated by the operator's

50 foot and leg overcoming the force of the springs thereby allowing the clutch disc to slip relative to the flywheel. It should be understood, however, that neither the activation springs nor the mechanical release mechanism are features of the present invention. According to the present invention,

55 a ball ramp mechanism 11 is used to force the actuation ring 12 toward the flywheel 4 which is controlled by the clutch control unit 15 electronically taking the place of an operator during transmission shifting sequences.

FIG. 5 is an axial cross-sectional view of the ball ramp 60

actuator of the present invention taken along line V-V of FIG. 1.

The clutch bellhousing 6 partially encloses the clutch assembly 2 including the ball ramp mechanism 11 of the present invention. Ball ramp actuators that react a control ring to ground are well known in the art and have been used to load transmission gear clutches as disclosed in u.S. Pat. No. 5,078,249, and differential clutch packs as disclosed in DETAILED DESCRIPTION OF ruE

PREFERRED EMBODIMENT

For purposes of promoting the understanding of the principles of the invention, reference will now be made to

65 U.S. Pat. No. 5,092,825 where a ball ramp control ring is reacted against case ground by a coil or motor. In essence, relative rotational motion between the control ring 14 and

5,810,141 5

the actuation ring 12 causes one or more rolling elements 20A, 2013 and 20C, which can be spherical elements or cylindrical rollers, to be moved along a like number of opposed ramps 22A, 22B and 22C formed in the control ring 14 and ramps 23A,23B and 23C formed in the actuation ring 5

12 respectively. Ramps 22A,22B,22C,23A,23B and 23C have variable axial depth which is unidirectional. FIG. 2 illustrates this geometry with more detail and precision, reference to which is made subsequently.

A plurality of thrust elements 27 reacting against the 10

thrust ring 34, which can be any type of suitable thrust bearing, are used to contain the axial forces generated by the ball ramp rolling elements 20A,20B and 20C as they engage the ramps 22A,22B,22C,23A,23B and 23C in the control ring 14 and the actuation ring 12 respectively. The thrust ring

15 34 is connected to the pressure plate housing 16. Rotation of the control ring 14 relative to the actuation ring 12 causes the actuation ring 12 to move axially toward the flywheel 4 thereby clamping the clutch disc 10 between the actuation ring 12 and the flywheel 4. The actuation ring 12 is rotatably connected to the pressure plate housing 16 but can move 20

axially with respect thereto. Attached to the control ring 14 is a somewhat flexible annular ring extension 1413 which supports a primary control friction disc 37 made of a friction material. The ball ramp section 14A of the control ring 14 contains the ramps 22A, 22B and 23C and is rotatably 25

supported by the transmission input shaft 8 by bearing 13. The control friction disc 37 is drawn against the coil pole 32 when the coil 30 is energized by the clutch control unit 15 through connectors 17. The annular electrical coil 30 encircles the transmission input shaft 8 and is supported by 30

the transmission case extension 31 attached to the transmis­sion 7. The electrical coil 30 is positioned in close proximity to the coil pole 32 separated by an air gap from the coil 30 and is rotatably supported on the transmission input shaft 8

6 art, the control ring 14 can be reacted against a ground surface, such as the clutch bellhousing 6, although continu­ous slipping would occur between the control ring 14 through the control friction disc 37 and the coil pole 32 resulting in high parasitic energy losses and no automatic activation of the ball ramp mechanism 11 upon clutch slip. A'S illustrated in the present application, by attaching the control ring 14 to the transmission input shaft 8 through the control friction disc 37 and the planetary gearset 39 con-trolled by action of a one-way clutch 46, very little clutch slip occurs when the ball ramp mechanism 11 is energized thereby minimizing energy losses. Also, the reaction time to even minimal slipping of the clutch disc 10 when in either the vehicle drive or coast mode using the present invention is virtually instantaneous since slippage of the clutch disc 10 results in relative motion between the actuation ring 12, and the control ring 14 through the control clutch 37 and the planetary gearset 39 on the control ring 14 side and through the pressure plate housing 16 to the actuation ring 12. The actuation ring 12 is rotationally coupled to the clutch pres­sure plate housing 16 which is in turn connected to the flywheel 4 all rotating together.

The centering spring 41 functions to control the rotational position of the control ring 14 relative to the actuation ring 12 when the electrical coil 30 is not energized such that very little axial force is applied through the ball ramp mechanism 11, especially when the engine is rapidly accelerated causing inertia forces of the components to come into play and no clutch activation is desired. The centering spring 41 is shown as a torsional spring only on one side of the ball ramp mechanism 11 but actually extends to encircle the control ring 14 and has one end attached to the control ring 14 and a second end attached to the actuation ring 12. Rotation of the control ring 14 relative to the actuation ring 12 causes the centering spring 41 to be stressed and to thereby generate a centering force between the actuation ring 12 and the control ring 14 that tends to return them to a rotational orientation where no axial force is generated by the ball ramp mecha-nism 11.

A plurality of pressure plate springs (not shown) act to pull the actuation ring 12 away from the clutch friction disc 10 and the flywheel 4 by acting as spring elements between the pressure plate housing 16 and the actuation ring 12 thereby biasing the actuation ring 12 away from the flywheel 4. The pressure plate housing 16 is attached to the flywheel 4 such that the actuation ring 12 rotates with the flywheel 4 but can move axially relative to the flywheel 4 as controlled by action of the ball ramp mechanism 11 acting to compress the pressure plate springs.

A planetary gearset 39 is disposed between coil pole 32 and the transmission input shaft 8. The planetary gearset 32

on sun gear 40. The electrical coil 30 is positioned to be partially enclosed by the coil pole 32 and is separated from 35

it by a small air gap. The coil 30 is mounted to the transmission case extension 31 and therefore held stationary while the coil pole 32 rotates according to the action of the planetary gearset 39. The coil 30 generates an electromag­netic Hux 36 shown by arrows in FIG. 1 which travel through 40

the coil pole 32 into the ring extension 14B and back through the coil pole 32 into the coil 30. This electromagnetic flux 36 creates a force tending to draw the ring extension 14B into the coil pole 32 thereby creating a frictional force through contact of the friction disc 37 on coil pole 32 and a resulting 45

torque in the control ring 14 (assuming a rotational speed differential between the flywheel 4 and the transmission input shaft 8) which activates the ball ramp mechanism 11 through the one-way clutch 46 which is loaded in a locking direction. 50 is comprised of a sun gear 40 driven by the transmission

input shaft 8 and meshing with a plurality of planet gears 42 which each rotate on a respective support pin 44. The planet gears 42 then mesh with the coil pole 32 at extension ring 32A The coil pole 32 is rotatably supported on the sun gear 40.

When the clutch disc 10 is unclamped or starts to slip due to excessive torque supplied by the prime mover (engine) through the flywheel 4, there is relative rotation between the control ring 14 and the actuation ring 12 thereby forcing the rings 12 and 14 axially further apart (as described in further

55 detail infra) thereby increasing the clamping force of the actuation ring 12 on the clutch disc 10 at the friction pad lOB and between the friction pad lOA and the flywheel 4. This occurs through a small range of rotational motion of the control ring 14 relative to the actuation ring 12 and provides an automatic, virtually instant, clamping force adjustment 60

should any rotational slipping occur between the flywheel 4 and the transmission input shaft 8.

According to the present invention, once the clutch assembly 2 is locked-up, the coil pole 32 rotates at the same speed as the flywheel 4 and minimal parasitic electrical 65

power is required to be delivered to the coil 30 to maintain lock-up of clutch assembly 2. Using the teaching of the prior

The planet gears 42 are circumferentially spaced from one another by carrier ring 48. A one-way clutch 46 is disposed between the carrier ring 48 and the sun gear 40 and com­prises the carrier ring 48 acting through clutch elements 52 to the inner ring 50. The one-way clutch 46 prevents the control ring 14 from rotating relative to the actuation ring 12 in a direction that would deactivate the ball ramp mechanism 11 as long as the coil 30 is energized by preventing rotation of the carrier ring 48 relative to the sun gear 40 in that direction.

Upon energization of the coil 30, the planetary gearset 39 and the one-way clutch 46 provide for relative rotation of the control ring 14 and the actuation ring 12 only in a direction

5,810,141 7

which results in further activation of the ball ramp mecha­nism 11 and increased clamping force on the clutch disc 10 irregardless of the operational mode of the vehicle and torque flow through the driveline.

A'Cial forces generated by the ball ramp mechanism 11 are transmitted by the thrust elements 27 into the thrust ring 34 which is attached to the flywheel 4 through the pressure plate housing 16. In the opposite direction, the force generated by the ball ramp mechanism 11 is transmitted to the clutch disc 10 and the flywheel 4.

The one-way clutch 46 is positioned to operate between the coil pole extension ring 32A of the coil pole 32 and the sun gear 40 of the planetary gearset 39. The sun gear 40 is driven by the transmission input shaft 8 and then meshes with planet gears 42 which then in turn mesh with the pole extension ring 32A of the coil pole 32 which is electromag­netic ally and frictionally coupled to the control ring 14 of the ball ramp mechanism 11. Acoi130 positioned adjacent to the coil pole 32 creates an electromagnetic field when the coil 30 is energized with an electrical current from the clutch control unit 15 through connecting leads 17. Additional vehicle electronic systems provide inputs via line 16 to the clutch control unit 15.

When the engine is supplying power to the vehicle driveline herein referred to as a drive mode, the coil 30 is energized and the ring extension 14B is electromagnetically coupled to the coil pole 32 thereby rotationally coupling the transmission input shaft 8 to the control ring 14 through the sun gear 40 and planet gears 42 of the planetary gearset 39. Any relative rotation between the transmission input shaft 8 and the flvwheel 4 results in relative rotation between the control ri~g 14 and the actu ation ring 12 in a direction that results in an increase in separation 66 (see FIG. 4) between the control ring 14 and the actuation ring 12. The one-way clutch 46 prevents the planetary gearset 39 from back driving when the engine power is reduced. As long as the coil 30 remains energized, the ball ramp mechanism 11 is not allowed to deactivate since the control ring 14 is held rotationally stationary relative to the actuation ring 12 by the one-way clutch 46 acting on the planet gears 42 and sun gear 40 of the planetary gearset 39.

When the vehicle transitions to the coast mode, the driveline torque transfer reverses to a state where the wheels are driving and the engine is being driven and thus braking the motion of the vehicle. Unless the ball ramp mechanism 11 has dual acting ramps formed in the control ring 14 and the actuation ring 12 (see U.S. Pat. Nos. 2,937,729 and 5,505,285) the unidirectional ball ramp mechanism 11 will normally release and not allow for engine braking when utilizing prior art systems. According to the present invention, a planetary gearset 39 along with the one-way clutch 46 is positioned between the transmission input shaft

8 Referring now to FIGS. 2, 3 and 4 to describe the

operation of the ball ramp mechanism 11, a cross-sectional view of the ball ramp mechanism 11 is shown in FIG. 2 and views taken along line III-III of the actuation ring 12 and

5 the control ring 14 separated by a spherical element 20A are shown in FIGS. 3 and 4. Three spherical rolling elements 20A,20B and 20C are spaced approximately 120° apart rolling in three ramps 22A,22B and 22C having a variable axial depth respectively as the control ring 14 is rotated relative to the actuation ring 12. Any number of spherical

10 rolling elements 20A,20B and 20C and respective ramps 22A,22B,22C,23A,23B and 23C could be utilized depend­ing on the desired rotation and axial motion of the ball ramp mechanism 11. It is mandatory to employ at least three spherical rolling elements 20A,20B and 20C travelling on a

15 like number of identical equally spaced opposed ramps 22A,22B,22C,23A,23B and 23C formed respectively in both the control ring 14 and the actuation ring 12 to provide axial and radial stability to the control ring 14 and the actuation ring 12. As mentioned previously, any type of rolling elements could be utilized such as a ball or a

20 cylindrical roller. The actu ation ring 12 is shown which rotates with the flywheel 4, the pressure plate housing 16 and the thrust ring 34 turning about axis of rotation 47 coincident with the axis of rotation of the transmission input shaft 8.

Three semi-circular, circumferential ramps 23A,23B and 25 23C are shown formed in the face of the actuation ring 12

with corresponding identical opposed ramps 22A,22B and 22C formed in the face of the control ring 14. TIle control ring 14 and the actuation ring 12 are made of a high strength steel and the unidirectional tapered ramps 22A,22B,22C,

30 23A,23B and 23C carburized and hardened, to Rc55-60. The ramps 22A,22B,22C,23A,23B and 23C are tapered in depth as more clearly shown in FIG. 3 by references to ramps 22A and 23A and circumferentially extend for approximately 120° (actually less than 120° to allow for a separation

35 section between the ramps). The separation 66 between the control ring 14 and the actuation ring 12 is determined by the rotational orientation between the two corresponding opposed ramps such as 22A and 23A where the spherical rolling element 20A rolls on both ramps 22A and 23A as the control ring 14 is rotated relative to the actuation ring 12 on

40 the same axis of rotation. In a substantially identical manner, rolling element 2013 rolls on both ramps' 2213 and 2313 and rolling element 20C rolls on both ramps 22C and 23C. The relative rotation forces the two rings 14,12 axially apart or allows them to come closer together as determined by the

45 position of the rolling elements 20A,20B and 20C or their respective ramp pairs 22A,23A and 2213,2313 and 22C, 23C thereby providing an axial movement for clamping and releasing the clutch disc 10 between the actuation ring 12 and the flywheel 4.

8 and the control ring 14 so that when the vehicle is in a 50

coast mode, relative rotation between the transmission input shaft 8 and the flywheel 4 causes the ball ramp mechanism

FIG. 3 illustrates the rotational orientation of the control ring 14 and the actuation ring 12 when the carrier ring 48 is at a minimum when the ramps 22A and 23A are at one extreme in alignment and the spherical element 20A is in the deepest section of the ramps 22A and 23A Assuming there is a rotational speed difference the flywheel 4 and the transmission input shaft 8, upon energizing the coil 30, the

11 to become increasingly activated. In the coast mode the one-way clutch 46 does not lock, and results in rotation of the planet gears 42 relative to the sun gear 40 thereby 55

reversing the rotation of the coil pole relative to the trans­mission input shaft 8 which will further activate the ball ramp mechanism 11. Thus, the present invention provides the feature that whenever the coil 30 is energized and there is relative rotation between the transmission input shaft 8 and the flywheel 4 in either direction, the ball ramp mecha- 60

nism 11 is increasingly activated and the clamping force on the clutch disc 10 is increased when there is any dilTerence in the rotational speed of the flywheel 4 and the transmission input shaft 8. The one-way clutch 46 provides a method to prevent the ball ramp mechanism 11 from deactivating 65

whenever the coil 30 is energized by freezing the planetary gearset 39.

control ring 14 is rotated relative to the actuation ring 12 by application of a rotational torque input through the control friction disc 27 and the ramps 22A and 23A move relative to one another causing the spherical element 20A to roll on each of the ramp surfaces 22A and 23A moving to a different position on both ramps 22A and 23A thereby forcing the control ring 14 and the actuation ring 12 apart to a wider separation 66 as shown in FIG. 4. A similar separation force is generated by rolling element 2013 rolling on ramp surfaces 22B and 2313 and by rolling element 20C rolling on ramp surfaces 22C and 23C. The rotation of the control ring 14 is clearly illustrated by reference to FIGS. 3 and 4 by the

5,810,141 9

relative shift in position of reference points 62 and 64 from directly opposed in FIG. 3 to an offset position in FIG. 4 caused by rotation of the control ring 14 in the direction of the arrow 45. This increase in axial displacement can be used for a variety of applications, and especially drive line 5 clutches, since the force level relative to the torque applied to the control ring 14 is quite high, typically a ratio of 100:1. This can be used as illustrated in this application to load an actuation ring 12 against a clutch disc 10 and flywheel 4 in a vehicle driveline. Additional illustrative details of opera- 10

tion of a ball ramp actuator can be found by reference to U.S. Pat. No. 4,805,486.

If the flywheel 4 is rotating at the same speed as the transmission input shaft 8, even if the coil 30 is energized, the control ring 14 rotates at the same speed as the actuation 15

ring 12 and no additional axial force is generated by the ball ramp mechanism 11 since there is no relative rotation between the control ring 14 and the actuation ring 12. Assuming the coil 30 remains energized thereby electro­magnetically tying the control ring 14 to the transmission input shaft 8 through the friction disc 37, coil pole 32 and the 20

planetary gearset 39, according to the present invention, any relative rotation between the flywheel 4 and the transmission input shaft 8, results in relative rotation between the control ring 14 and the actuation ring 12 in a direction which causes the spherical elements 20A, 20B and 20e to further increase 25

the separation 66 between the control ring 14 and the actuation ring 12 thereby generating additional clamping force by the actuation ring 12 so as to use the power of the flywheel to increase the lock-up force on the clutch disc 10.

Now referring to FIG. 5, a partial cross-sectional view of 30

the present invention taken along line v-v of FIG. 1 is shown. The transmission input shaft 8 is nonrotatably con­nected to the sun gear 40 which meshes with the planet gears 42 which are rotatably supported on support pins 44. The pole extension ring 32A has inward facing gear teeth which 35 mesh with the planet gears 42. The coil 30 (not shown) is contained within the coil ring 32. Any number of planet gears 42 can be utilized.

10 a ball ramp mechanism for generating an axial movement

comprising; an annular control ring having an axis of rotation, said control ring having a plurality of circum­ferential control ramps formed in a first face of said control ring, said control ramps varying in axial depth, an equivalent number of rolling elements one occupy-ing each of said control ramps, an actuation ring having an axis of rotation coaxial with said axis of rotation of said control ring, said actu ation ring having a plurality of actuation ramps substantially identical in number, shape and radial position to said control ramps where said actuation ramps at least partially oppose said control ramps and where each of said rolling elements is contained between one of said actuation ramps and a respective control ramp, said control ring being axially and rotationally moveably disposed relative to said actuation ring;

a planetary gearset having an annulus electromagnetically coupled to said control ring, and a sun gear rotatably driven by said output element where a plurality of planet gears couple said sun gear to said annulus;

a coil for inducing an electromagnetic field in said annu­Ius;

a one-way clutch having an inner ring connected to said output element and an outer ring connected to said planet gears, said inner ring and said outer ring con­nected by a plurality of clutch elements;

where said one-way clutch prevents said control ring from rotating in a first direction relative to said actuation ring and said planetary gearset provides rotation of said control ring relative to said actuation ring in a second direction irrespective of the relative rotation of said input element and said output element.

2. The ball ramp actuator of claim 1, wherein said rolling elements are spherical.

3. The ball ramp actuator of claim 1, wherein said rolling elements are rollers.

The vehicle drive line clutch actuator can be used to couple a rotating input shaft to an output shaft where the input shaft would be analogous to the flywheel and the output shaft would be analogous to the transmission input shaft as shown in FIG. 1. The present invention would prevent the ball ramp mechanism 11 from retracting and disengaging the clutch disc 10 so long as the coil 30 was energized thereby providing a friction coupling between the input shaft (flywheel) and the output shaft (transmission input shaft) irregardless of the direction of the torque transfer.

4. The ball ramp actuator of claim 1, wherein said control ramps and said actuation ramps have a continuously increas­ing axial depth.

40 5. The ball ramp actuator of claim 1, wherein said coil is disposed adjacent to a coil pole.

6. The ball ramp actuator of claim 5, wherein said coil encircles said output element.

7. The ball ramp actuator of claim 6 further comprising a 45 control unit electrically connected to said coil for supplying

electrical energy to said coil.

This invention has been described in great detail, suffi­cient to enable one skilled in the art to make and use the 50

8. The ball ramp actuator of claim 1, wherein said clutch elements are electromagnetically rotationally connected to said control ring.

9. The ball ramp actuator of claim 8, wherein said clutch elements are biased to allow said inner ring to rotate in either direction relative to said outer ring when said coil is non­energized.

same. Various alterations and and understanding of the foregoing specijlcation, and it is intended to include all such alterations and modijlcations as part of the invention, insofar as they come within the scope of the appended claims.

We claim: 1. A ball ramp actuator for rotationally coupling two

rotating elements comprising: an input element driven by a prime mover and rotating

about an axis of rotation;

an output element having an axis of rotation coaxial with said axis of rotation of said input element for rotating an output device;

10. The ball ramp actuator of claim 8, wherein said clutch 55 elements are biased to prevent said control ring from rotat­

ing in a direction relative to said actuation ring tending to deactivate said ball ramp mechanism.

11. The ball ramp actuator of claim 1, wherein said input element is a flywheel and wherein said output element is a transmission input shaft and where said output device is a

60 transmission.

* * * * *

United States Patent [19]

Hiterer

[54] SYNCHRONOUS RECIPROCATING ELECTRIC MACHINES

[75] Inventor: Misha Hiterer, leruslaem, Israel

[73] A'isignee: Medis EI, Ltd., Israel

[21] Appl. No.: 08/933,856

[22] Filed: Sep. 19, 1997

[51] Int. CI.6 ........................... H02K 33/16; H02K 33/00 [52] U.S. CI ............................... 310/15; 310/12; 310/162;

310/156; 310/36 [58] Field of Search ................................ 310/162, 12, 15,

310/13, 156, 36; 290/42, 53

[56] References Cited

3,891,874 4,675,563 4,704,553 4,945,269 4,985,652 5,654,596

u.s. PATENT DOCUMENTS

6/1975 Roters et al. ............................. 310/15 6/1987 Goldowsky ............................... 310/15

11/1987 Resnicow .................................. 310/12 7/1990 Kamm ....................................... 310/15 1/1991 Oudet et al. .............................. 310/15 8/1997 Nasar et al. .............................. 310/12

Primary Examiner---Nestor Ramirez Assistant Examiner----B. Mullins

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111111 1111111111111111111111111111111111111111111111111111111111111 US005903069A

[11] Patent Number:

[45] Date of Patent:

5,903,069 May 11, 1999

Attorney, Agent, or Firm-R. Neil Sudol; Henry D. Coleman

[57] ABSTRACT

A synchronous reciprocating electric machine includes a first magnet system having first and second opposing sur­faces forming between them a gap, and a second magnet system mounted within the gap so as to be displace able relative to the first magnet system along a line of travel through the gap. The the first magnet system is configured for generating a magnetic field, referred to as the "gap field", directed across the gap primarily perpendicular to the first surface. The second magnet system includes two magnetic elements configured to generate equal but opposite magnetic fields primarily perpendicular to the first surface. These magnetic elements are spaced from each other along the line of travel by a distance b, where b>O. One of magnet systems produces a non-alternating magnetic field and the other is a coil assembly for producing an operating magnetic field. The machine also includes electrical connections connecting to the coil assembly so as to allow operation of the electric machine with reciprocation of the second magnet system relative to the nrst magnet system.

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5,903,069 1

SYNCHRONOUS RECIPROCATING ELECTRIC MACHINES

FIELD AND BACKGROUND OF THE INVENTION

The present invention relates to electric machines and, in particular, it concerns synchronous reciprocating electric machines and methods for their design.

Alternating current electric machines excited by perma­nent magnets or field windings are known in the literature as synchronous machines (rotating or linear). A rotating or running field generated by the system of windings attracts the systems of field poles (excited by windings or permanent magnets).

The speed of the movable part of electric machine is equal

2 magnet system includes a first magnetic element configured to generate a magnetic field primarily perpendicular to the J1rst surface in a first direction and further includes a second magnetic element similar to, and mounted in fixed relation

5 to, the first magnetic element. The second magnetic element is configured to generate a magnetic field primarily perpen­dicular to the first surface in a direction opposite to the first direction. One of the J1rst and second magnet systems produces a non-alternating magnetic field, while the other of

10 the first and second magnet systems is a coil assembly for producing an operating magnetic field. Electrical connec­tions connect to the coil assembly so as to allow operation of the electric machine with reciprocation of the second magnet system relative to the first magnet system.

15

to speed of the rotating (running) magnet J1eld. That is why these machines are classified as synchronous. Their speed does not vary with either an applied load or a supplied voltage, being instead fully determined by an external circuit 20

frequency and the pole number. For generators, an induced voltage frequency depends upon the speed and pole number while the voltage depends upon the design of the windings.

The magnet systems of the present invention are movable relative to one another. Generally, one magnet system is stationary, while the other moves to define the line or path of travel. Of course, it is possible for each magnet system to have a degree of motion relative to a fixed reference frame.

Pursuant to a feature of the present invention, the second magnetic element is spaced from the first magnetic element along the line of travel by a distance b, where b>O. Where the second magnet system includes a spacer of thickness b deployed between the first and second magnetic elements, It should be noted that, while the theory and design

methods of rotating synchronous electric machines are well developed in the literature worldwide, the theory, calculation methods and constructions of reciprocating machine are all but absent from the literature.

There is therefore a need for e1Ticient compound-moving­magnet synchronous machines which make maximal use of the available magnetic flux, for linear or arcuate reciprocat­ing movement. It would also be advantageous to provide a method of designing compound-moving-magnet synchro­nous machines which would optimize the design parameters

25 the spacer may include soft magnetic material and/or non­magnetic material.

Where the second magnet system is distanced from the first surface of the first magnet system by a clearance gap of width !J., the second magnet system is preferably configured

30 such that distance b has a magnitude not significantly less than width !J..

for any given application. 35

In one embodiment of the present invention, the second magnet system is mounted relative to the first magnet system by a mechanical coupling, while the mechanical coupling is conJ1gured to deJ1ne a non-linear travel path.

SUMMARY OF THE INVENTION The first magnet system may be formed as a substantially closed magnetic circuit. Also, the second magnet system may be implemented as the coil assembly.

In some embodiments of the present invention, the first and second surfaces of the first magnet system are shaped such that in a plane perpendicular to the line of travel the gap has a closed annular form. In such cases, the second magnet system is implemented as a corresponding hollow cylindri-

The present invention is a compound-moving-magnet­system synchronous reciprocating electric machine with 40

highly efficient use of magnetic Hux and increased opera­tional amplitude, and capable of arcuate reciprocating move­ment or of employing moving electromagnetic systems. The invention also relates to a method of designing compound­moving-magnet system synchronous machines which opti­mizes the design parameters for any given application.

45 cal magnet system. Pursuant to a further feature of the present invention, the

second magnet system includes a magnetically passive sup­port structure for supporting the J1rst and second magnetic elements. The support structure may be made from soft

The electric machines of the present invention may be used in all electric devices, instruments and tooling where reciprocating movement is required. The movement can be provided along a line of any shape. The shape of the movement is determined by suitable mounting of the mov­able part relative to the fixed one and corresponding con­struction design.

The present invention can be used to good effect for design of electric reciprocating generators driven by sea waves or wind, as well as for constructing electric actuators for replacing piston combustion motors.

A synchronous reciprocating electric machine comprises, in accordance with the present invention a first magnet system and a second magnet system. The first magnet system has a J1rst surface and a second surface opposing the first surface so as to define there between a gap. The first magnet system is configured for generating a magnetic field directed across the gap primarily perpendicular to the first surface. The second magnet system is mounted within the gap so as to be displace able relative to the first magnet system along a line of travel through the gap. The second

50 magnetic material and may be implemented as a substan­tiallv continuous laver, the first and second magnetic ele­me~ts being attach~d to at least one surface of the layer.

The present invention is also directed to an associated method for designing a synchronous reciprocating electric

55 machine of the above described type. The method comprises determining a maximum intended amplitude A of relative reciprocal movement, selecting a dimension Wo for the first and second surfaces of the first magnet system as measured parallel to the line of travel such that the relation wi\+b~2A

60 is applicable, and selecting a dimension W k for the second magnet system as measured parallel to the line of travel such that the relation wk~wo+2A holds. Preferably, b is greater than or equal to zero and is chosen to be at least about the spacing between the second magnet system and the first

65 surface of the first magnet system. The second magnet system may be constructed with a magnetically-passive intermediate spacer of width b.

5,903,069 3 4

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic illustration of an electric machine, constructed and operative according to the present invention, having a linear or straight line of relative motion 5

between a first magnet system and a second magnet system;

FIG. 14Ais a schematic longitudinal cross-sectional view of a hexagonal-section implementation of the second magnet system of FIG. 1 employing permanent magnets;

FIGS. 14B is a corresponding schematic transverse cross­sectional view of the implementation of FIG. 14A, taken along line XIV-XIV;

FIG. 2 is a schematic illustration of an electric machine, constructed and operative according to the present invention, having a nonlinear line of relative motion between a first magnet system and a second magnet system; 10

FIGS. 15A and 16A are schematic longitudinal cross­sectional views, respectively, of a cylindrical and a hexagonal-section implementation of the second magnet system of FIG. 1 employing coils;

FIG. 3 is a schematic illustration of an implementation of the electric machine of FIG. 1 in a central position;

FIG. 4 is a schematic illustration of the implementation of FIG. 3 in a displaced position;

FIGS. 15B and 16B are corresponding schematic trans­verse cross-sectional views of the implementations of FIGS. 15A and 16A, respectively;

FIG. 5A is a schematic illustration of an implementation 15

of the electric machine of FIG. 1 with zero spacing between

FIG. 17A is a schematic circuit diagram showing a possible configuration of electrical connections for the implementations of FIGS. 15A and 16A;

magnetic elements of the second magnet system; FIG. 5B is a graphic representation of actuating force as

a function of displacement for the structure of FIG. 5A;

FIG. 5C is a schematic illustration of an implementation of the electric machine of FIG. 1 with non-zero spacing between magnetic elements of the second magnet system;

FIG. 5D is a graphic representation of actuating force as

FIGS. 1713 and 17C are diagrams showing how the connections of FIG. 17A may be connected in parallel or

20 series, respectively;

FIG. 18A is a schematic cut-away side view of a further cylindrical implementation of the second magnet system of FIG. 1 employing coils;

FIG. 18B is a schematic end view of the implementation a function of displacement for the structure of FIG. 5C; 25 of FIG. 18A;

FIGS. 6A-6D are schematic isometric views of a number of implementations of the first magnet system for use in the electric machine of FIG. 1;

FIG. 18C is a schematic side view of the implementation of FIG. 18A;

FIG. 18D is a schematic circuit diagram equivalent of the FIG. 7Ais a schematic cross-sectional view through a first 30 implementation of FIG. 18A;

construction for the magnet system of FIG. 6D;

FIG. 713 is a top view of the construction of FIG. 7A;

FIG. 7C is a schematic cross-sectional view through a second construction for the magnet system of FIG. 6D;

FIG. 7D is a top view of the construction of FIG. 7C;

FIG. 7E is a schematic cross-sectional view through a third construction for the magnet system of FIG. 6D;

FIG. 7F is a top view of the construction of FIG. 7E;

FIG. 19 is a schematic cross-sectional view through a cylindrically symmetric implementation of the electric machine of FIG. 1; and

FIG. 20 is a schematic cross-sectional view of a variant 35 embodiment of the electric machine of the present invention

in which one pole piece of the first magnet system is made integral to the second magnet system.

FIG. 7G is a schematic side view of a lamination layer for 40

use in a fourth construction for the magnet system of FIG. 6D;

DESCRIPTION OF THE PREFERRED EMBODIMENTS

The present invention is a compound-moving-magnet­system synchronous reciprocating electric machine with highly efficient use of magnetic flux and increased opera­tional amplitude, and capable of arcuate reciprocating move-

FIG. 8Ais a schematic cross-sectional view through a first implementation of the second magnet system of FIG. 1 employing permanent magnet elements;

FIG. 8B is a top view of the implementation of FIG. 8A; FIG. 9A is a schematic cross-sectional view through

another implementation of the second magnet system of FIG. 1 employing permanent magnet elements;

FIG. 9B is a top view of the implementation of FIG. 9A; FIG. lOA is a schematic cross-sectional view indicating

the principles of an implementation of the second magnet system of FIG. 1 employing coils;

FIG. lOB is a top view corresponding to FIG. lOA; FIG. HA is a schematic cross-sectional view through an

implementation of the second magnet system of FIG. 1 employing coils;

FIG.HB is a top view of the implementation ofFIG.llA; FIGS. 12A and 13A are schematic longitudinal cross­

sectional views of two cylindrical implementations of the second magnet system of FIG. 1 employing permanent magnets;

45 ment or of employing moving electromagnetic systems. The invention also relates to a method of designing compound­moving-magnet synchronous machines which optimizes the design parameters for any given application.

50 The principles and operation of machines and methods according to the present invention may be better understood with reference to the drawings and the accompanying description.

Referring now to the drawings, FIGS. 1 and 2 show a 55 generalized representation of an electric machine, desig­

nated 10, constructed and operative according to the teach­ings of the present invention.

Electric machine 10 includes a first magnet system 12 having opposing surfaces 14 and 16 defining therebetween

60 a gap 18. First magnet system 12 is configured so as to produce a magnetic field, referred to as the ""gap field", directed across gap 18 primarily perpendicular to first sur­face 14.

FIGS. 12B and 13B are corresponding schematic trans­verse cross sectional views of the implementations of FIGS. 65

12A and 13A, taken along lines XII-XII and XIII-XIII, respectively;

Within gap 18 is positioned a second magnet system 20. Second magnet system 20 is mounted within gap 18 by any suitable mechanism (represented schematically by a drive rod 22) so as to be displaceable relative to first magnet

5,903,069 5 6

With reference specifically to FIG. 2, it is a further particular feature of certain preferred embodiments of the present invention that the line of travel of second magnet system 20 relative to first magnet system 12 is non-linear,

system 12 along a line of travel within gap 18, typically substantially parallel to first surface 14. Second magnet system 20 includes a first magnetic element 24 and a second magnetic element 26. Magnetic elements 24 and 26 are similar and are both configured to generate a magnetic field primarily perpendicular to first surface 14, but in opposite directions. Magnetic elements 24 and 26 are preferably spaced from each other along the line of travel by a distance b as will be described below.

5 typically in the form of an arc of radius R. In this case, surfaces 14 and 16, and hence gap 18, are preferably designed to run parallel to the line of travel. Second magnet system 20 is also preferably designed with a corresponding

The electric machines of the present invention may be 10

either motors or generators. In either case, one of first and second magnet systems 12 and 20 is either a permanent magnet system (represented by N(S) or SeN)) or an electro­magnet system supplied by a source of direct current (represented schematically by a "=" symbol). In the case of 15

a motor, the other magnet system is an electromagnet system supplied by a source of alternating current (represented schematically by a "-" symbol). This results in a recipro­cating motion of second magnet system 20 relative to first magnet system 12, as indicated by arrows 21. In the case of 20

a generator, the other magnet system is a coil arrangement with appropriate electrical connections.

In this context, it should be noted that the power supplies used in the present invention and the corresponding mag­netic fields need not correspond to constant DC or sinusoidal 25

AC. It is sufficient that one magnet system produces a non-alternating, non-zero magnetic field and that the other produces an operating magnetic field. The phrase "operating magnetic field" is used herein in the description and claims to refer to any magnetic field which varies substantially 30

cyclically between a maximum value in one direction and either a maximum value in the reverse direction or zero. Thus, the operating current which generates the operating magnetic field may be any conventional AC supply, a pulsed supply or any other reversing or intermittent cyclic form. For 35

convenience of reference, the following description will refer to the preferred non-limiting example in which stan­dard sinusoidal AC and, where applicable, constant DC are

curvature to match that shape of the gap.

At this stage, it will be useful to define certain terminol­ogy to be employed below in the description and claims to refer to various parameters and dimensions of the electric machines of the present invention. Firstly, the total height of gap 18 measured perpendicular to the line of travel is denoted 0, while the minimum clearance gap between first and second surfaces 14 and 16 and second magnet system 20 is denoted L',.. The width of first and second surfaces 14 and 16 measured parallel to the line of travel is denoted WOo An internal spacing between magnetic elements 24 and 26 of second magnet system 20 as measured along the line of travel is denoted b. The width of second magnet system 20, made up of the combined width of the two magnetic elements and spacing b, measured parallel to the line of travel is denoted Wk. Finally, the maximum intended dis­placement or motion amplitude of second magnet system 20 relative to first magnet system 12 in either direction from its equilibrium position as measured along the line of travel is denoted A.

Particular care must be taken in defining these terms in the case of a non-linear line of travel (FIG. 2). In this case, measurements are preferably made along, or parallel to, the line of travel or along a local perpendicular thereto. Alternatively, widths w'" and wk , amplitude A and spacing b can be expressed in angular units.

Turning now to the features of electric machine 10 in more detail, the principles of operation will be best under­stood with reference to FIGS. 3 and 4.

For convenience of reference, we consider second magnet used.

It should also be noted that the phrases "magnet system" and "magnetic elements" are used herein to refer to systems and elements which either actually produce a magnetic field or would, if connected to an electrical power source, pro­duce a magnetic field. Thus, these terms may relate to permanent magnets, electromagnets provided with either AC or DC, e.g., via coils 23 and 25, and to corresponding coil arrangements used in a generator. Similarly, the structure of coils in a generator will be described as configured to generate a certain magnetic field, meaning that the coil structure used is such that, if a current was supplied to the coil structure, the stated field would be produced. Furthermore, it should be noted that the coils of a generator can also be correctly described as generating a magnetic field whenever a current is drawn from the generator.

40 system 20 to be a moving element excited by a direct current and first magnet system 12 to be fixed and supplied by an alternating current. FIG. 3 shows a first position of the machine in which the instantaneous current in first magnet system 12 is zero. Under these conditions, second magnet

45 system 20 is self-adjusted to occupy a central position where symmetry axes of second magnet system 20 and of J1rst magnet system 12 coincide. This means that the middle of spacer b (or the butt-joint point of pole pieces if b=O) is centrally positioned relative to the width of surfaces 14 and

50 16 of J1rst magnet system 12. This self-centering results from the non-alternating mag­

netic J1eld of second magnet system 20 tending to a lowest energy symmetrical configuration relative to the magnetic circuit of first magnet system 12. For this reason, the

55 machine described here does not require use of springs to return the movable part to its initial position. Although most implementations of electric machine 10

employ a fixed first magnet system 12 and moving second magnet system 20, it should be noted that the invention is not limited to this configuration. Thus, in alternative implementations, second magnet system 20 is fixed and first 60

magnet system 12 moves. For convenience of reference, both of these possibilities are referred to generically as "motion of second magnet system 20 relative to first magnet system 12".

FIG. 4 shows the machine in a second position in which the instantaneous current in J1rst magnet system 12 and its corresponding magnet flux 1> are maximum. Under currents and magnet fluxes as shown, the movable magnet system 20 is maximally displaced to the left by amplitude A (the maximum displacement of the reciprocating movement). As the current decreases and reverses polarity to its maximum reverse voltage, second magnet system 20 reaches its maxi-

It is a particular feature of certain preferred embodiments of the present invention that the second magnet system 20 is the alternating electromagnet system.

65 mum displacement to the right as shown. Thus, the oscil­lating will occur at the frequency of the voltage supplied to first magnet system 12.

5,903,069 7

It should be appreciated that the operation described here is independent of which of magnet systems 12 and 20 generates the alternating or nonalternating field and which of them is fixed or movable. The only necessary conditions are as follows:

one of the systems generates a non-alternating Jleld while the other one generates an alternating or pulsed Jleld; and

5

8 It will be clear that, in the limit as w k--" oo

It is to be noted that efi1ciency of the electric machine rapidly decreases as soon as the borders of two poles of second magnet system 20 reach the ends of surfaces 14 and 16 (magnetic circuit or permanent magnet). In other words, it is not expedient to design the amplitude of reciprocating

system 20 is mounted within the gap of system 12 so as to allow relative motion up to maximum displacement or amplitude A.

Il follows from the above that design of both magnet systems can be of any shape (plane, round, polygon, etc.). At

10 movement to be more than (w,,+b)/2. This means that the maximum value of amplitude A of reciprocating movement is preferably related to width Wo of Jlrst magnet system according to:

the same time it should be noted that: 15

one of the magnet systems is to move free in the other one with maximum desirable amplitude A;

(1)

that is, a sum of width of magnet system 12; and a clearance b is to be not less than double the maximum electric it is expedient to design the structure such that magnetic

fluxes pass through a minimum total air gap. 20 machine. Thus the degree of inHuence of the boundary e1Tect is

directly correlated with values of amplitude A, spacing b, width W k and width WOo It is recommended that width is chosen to satisfy the relation:

The present invention provides a number of preferred relations between the dimensions of parts of the machine so as to optimize the design and construction for a given application. Some of these relations depend upon an intended maximum amplitude of movement A for which 25

electric machine 10 is to be used. In the case of a motor application, the amplitude is limited to this value in use by providing an electrical supply conJlgured to generate a maximum voltage corresponding to this value. In the case of a generator, the mechanical linkage for driving the moving 30

part of the machine is preferably designed to deJlne the maximum intended amplitude.

Once the intended maximum amplitude A has been determined, the dimensions of the components of electric machine 10 are preferably designed such that: 35

(2)

that is, width w k of the pole couple of second magnet system 20 (including clearance or spacing b) is to be not less than the sum of the width of system 12 and double the maximum amplitude of reciprocating movement of electric machine.

It is evident from FIG. 3 that the more each pole of system 20 extends beyond the ends of system 12, the smaller will be the boundary forces Fb(r) and Fb(l) and the corresponding influence of the boundary effect on performance (efi1ciency, outer dimensions, weight, etc.) of the electrical reciprocating machine. On another hand, over-extension of the width wk

of the poles of system 20 results in increase in the weight, cost and dimensions of the electric machine. Design opti-

The common width w" of surfaces 14 and 16 of Jlrst magnet system 12 plus spacing b is chosen to be not less than double the maximum intended amplitude 2A of the reciprocating movement, i.e., wo+b~2A.

The width wk of second magnet system 20 is chosen to be not less than a sum of width w" and double the intended maximum amplitude 2A of the reciprocating movement, i.e., wk~w,,+2A.

40 mization regarding widths w" and wk , i.e., the degree to which they exceed the aforementioned limitations, is to be performed by an engineer at the design stage depending upon each particular project's requirements.

The lengths of magnet systems, i.e., their dimensions

In the case of an open-sided air gap structure, the length of second magnet system 20 is preferably chosen to be greater than a common length of the surfaces 14 and 16 of first magnet system 12 by at least half the size of the gap, i.e., L,,~(Lk+I\;2).

45 perpendicular to both the line of travel and the height of the gap, for the open operating air gap design (FIGS. 6A and 613 below), are determined by minimum magnetic leakage cri­teria for the closed magnet system (preferably system 12). Preferably, the lengths satisfy the relation:

In order to present a treatment of the design consider- 50

ations for electric machines according to the present invention, reference will be made to various forces illus­trated in FIG. 4. Specijlcally, the reference designation FM represents a maximum force produced by a movable magnet system 20 at a time when the current in the winding of 55

system 12 is maximum; reference Fb(r) represents a force caused by the boundary effect produced by system 20 from

(3)

The lengths of magnet systems 12 and 20 for closed operating air gap designs (FIGS. 6C and 6D below) are determined by the dimensions of the electric machine.

Turning now to FIGS. 5A-5D, the signijlcance of spacing b will now be described. The value of spacing b may essentially be chosen anywhere in the range from zero up to the width of surfaces 14 and 16. FIG. SA illustrates the

its right edge at that time; and reference Fb(l) designates a force caused by the boundary effect applied to system 20 from its left edge at that time. 60 structure of electric machine 10 with b=O, i.e., with second

magnet system 20 formed as butt jointed adjacent poles. FIG. 5B shows the corresponding variation of force with dis­placement from the central position. As can be seen here, the

From FIG. 3, it is evident that the currents at the ends of system 20 flow in directions opposite to those that generate the main tracking force FA.,. As a result of interaction between the main flux with these end currents, boundary forces F b(r) and F bel) act to oppose main tracking force F M. 65

The less the sum of Fb(r) and Fb(l) the higher the efi1ciency of the electric machine.

force exerted by the machine is substantially constant at a value designated 2h over a range of movement equal to WOo

Outside this range of movement, the force drops abruptly to zero.

5,903,069 9

In contrast, FIGS. 5C and 5D show a parallel structure and force diagram for a construction with b>O. In this case, a stepped form is introduced into the force diagram such that the maximum value 211 is provided over a smaller range wo-b and a lower value h is provided over additional side 5

regions of width b. As a result, the total operative amplitude for a given width Wo of surfaces 14 and 16 and for a given design of magnetic elements 24 and 26 is increased by width b. In addition, the form of the force diagram becomes a much closer approximation to a sinusoidal form. In genera- 10

tor applications, the output voltage assumes a corresponding form, thereby also approximating better to a sinusoidal form.

The use of a non-zero spacing b also ensures more efficient use of the fiux of magnet system 20. When b=O, significant leakage of magnetic fiux occurs due to closure 15

between the pole pieces of system 20. By increasing spacing b to be at least about equal to, and preferably greater than, the air gap i\ between surfaces 14 and 16 of system 12, leakage of magnetic fiux is substantially reduced.

Increased spacing b also serves to decrease the negative 20

influence of the boundary dIect for otherwise constant parameters by expanding the pole zone of system 20.

Clearance b between butt jointed pole pieces of system 20 can be filled by any material: magnetic or non-magnetic as well as by any combination of those, or the clearance may 25

be maintained by a hollow frame. The use of soft magnetic material for the spacer may be advantageous in the case that system 20 is implemented with permanent magnets. Induced magnetization of the spacer provides magnetic attachment of each of the magnetic elements to the spacer, thereby helping 30

to maintain firm internal mechanical unity of the compo­nents of system 20.

Turning now to the details of first magnet system 12, a number of different implementations will now described with reference to FIGS. 6 and 7. The magnetic circuit of 35

system 12 is produced from laminated electric steel, soft ferrite, solid steel parts or the like. Its windings (or configu­ration of permanent magnets) are chosen depending on the design of the magnetic circuit of this system.

FIG. 6A shows a fiat-surface pole structure for an open 40

magnetic circuit implementation of system 12. FIG. 613 shows an equivalent structure formed as a closed magnetic circuit, thereby decreasing flux leakage and improving effi­ciency. The closed magnetic circuit of FIG. 613 includes a space 27 for coils or windings 23, 25 (see FIGS. 1 and 2). 45

While the structure of FIG. 613 is clearly advantageous, less optimal designs with open magnetic circuits or no magnetic circuit at all may be used according to the conditions imposed by mechanical attachment requirements.

The operating air gap can be of any shape desired. One 50

example shown in FIGS. 6C and 6D is a cylindrical or annular gap. Here too, the structure can be formed either as an open magnetic circuit (FIG. 6C) or, in preferred implementations, as a closed magnetic circuit (FIG. 6D) corresponding to a hollow annular box of soft magnetic 55

material containing coils or windings 23, 25 (see FIG. 2) in an annular space 29.

10 the U-section annular base element 29 is formed with one side wall extended upwards to form one side of a gap. In this case, only one annular cover portion 31 is required.

FIGS. 7C and 7D show an implementation in which the hollow annular box is constructed from two cylindrical portions 34 and 36, and three annular portions 38, 40 and 42 connected together by any known method (welding, brazing, pasting, etc.). All these parts can be made from any magnetic material. Particularly advantageous for this design is the use of reeled steel band or laminated steel sheets, laminated in the directions shown.

The cylindrical and the annular portions preferably have beveled edges for forming oblique-angled buUjoints, pref­erably at about 45°. Particularly in the case of components made from laminated sheet materials, this ensures that a minimum transient magnetic resistance is encountered.

A further possibility is that the hollow annular box may be constructed from a plurality of laminations, each corre­sponding to a radial segment of the hollow annular box. FIG. 7G illustrates a preferred shape of lamination 44 for such an implementation. The laminations may be of a one-piece or composite design.

It should be appreciated that first magnet system 12 may be shaped to form with a wide range of other shapes of the operative air gap including, but not limited to, arcuate and rounded forms, and polygonal gaps.

Turning now to the features of second magnet system 20 in more detail, these will be described with reference to FIGS. 8-18. System 20 includes two butt jointed spaced poles generating parallel but substantially opposite magnetic fields. This system is open in order to be placed in the air gap of the system 12. The mechanical configurations of the two magnet systems are to be formed to make possible mutual movement up to maximum displacement or amplitude A.

The shape of system 20 is chosen to match to the shape of system 12. FIGS. 8-11 illustrate a number of alternative structures for use with a magnet system 12 with fiat pole surfaces (FIGS. 6A and 613). FIGS. 8A and 813 show a basic implementation in which the two magnetic elements are two permanent magnets 46, 48 magnetized in opposite directions parallel to the height of gap 18. The two magnets are preferably spaced apart by a spacer 50 of width b, as described above.

FIGS. 9A and 913 show a variation of this implementation employing a magnetically passive support structure 52 for supporting the first and second magnetic elements. Support structure 52 may be made from either magnetic or non­magnetic material, or a combination thereof. Preferably, soft magnetic material, such as iron, is used. The use of an additional support structure is particularly valuable for pro­viding internal mechanical strength to second magnet sys-tem 20 and for facilitating mechanical connection to the system by conventional techniques such as welding.

Preferably, support structure 52 is implemented as a substantially continuous layer, as shown. The magnetic elements can then be formed by attaching magnets 54, 56 to at least one and preferably both surfaces of the layer. The magnets forming a common pole are magnetized in the same direction while the magnets forming the other pole are

FIGS. 7 A-7G illustrate, by way of example, four possible constructions which can be used to implement the magnet system of FIG. 6D. 60 magnetized in the opposite direction. Spacer 50 may advan­

tageously be integrally formed with support structure 52. The surface portion of spacer 50 may advantageously be implemented as a non-magnetic layer to further reduce

FIGS. 7A and 713 show an implementation in which the hollow annular box is constructed from a unitary U-section annular base element 28 and two annular cover portions 30 and 32. The parts are connected to each other by any known method (pasting, mechanical attachment, etc.). This imple- 65

mentation is most advantageously constructed from ferrite. FIGS. 7E and 7F show a similar implementation in which

internal closure of magnetic fiux within system 20. It should be noted that the support structure can be cast

from an appropriate material either before or after prelimi­nary assembly of poles relating to system 20. Optionally, the

5,903,069 11

support structure can feature one or more holes serving to decrease magnetic flux leakage between poles of system 20, minimize electromagnetic losses, and reduce overheating of windings.

FIGS. lOA and lOB show a schematic representation of an 5

implementation in which the two magnetic elements are two coils 57, 59 wound/connected to produce magnetic fields in opposite directions primarily parallel to the height of gap 18. I! will be clear that for analytical purposes, this arrangement may be considered fully analogous to the permanent magnet 10

implementation of FIGS. 8A and 813. As mentioned earlier, the coils may be supplied with

either the non alternating or the operating current, according to the implementation of first system 12. Here too, the coils are preferably spaced apart by a spacer 50 of width b.

The windings of system 20 may be attached to a base, 15

encapsulated, molded or the like, to form a rigid construc­tion. Alternatively, they may be mounted through any insu­lation on a common part of the magnetic circuit of width Wk.

The windings can be located either on one side or both sides of a base. The base itself can be made from either from 20

electrically and/or magnetically insulating materials or from electrically and/or magnetically conducting materials.

FIGS. HA and HB show a practical coil implementation using hollow core coils 58 and 60. Optionally, coils 58 and 60 may be filled with magnetic pole pieces or other material. 25

FIGS. 12A-18D illustrate a number of implementations of magnet system 20 for use with a first magnet system 12 having an annular or, in the case of FIGS. 14 and 16, a polygonal gap (FIGS. 6C and 6D).

12 FIG. 20 shows a variant embodiment in which part of the

magnetic circuit of first magnet system 12a is formed of a movable part of width approximately W k formed as a core of cylindrical second magnet system 20.

It will be appreciated that the above descriptions are intended only to serve as examples, and that many other embodiments are possible within the spirit and the scope of the present invention.

What is claimed is: 1. Asynchronous reciprocating electric machine compris­

ing: (a) a first magnet system having a first surface and a

second surface opposing said first surface so as to define therebetween a gap, said first magnet system being configured for generating a substantially uniform magnetic field in said gap extending substantially solely perpendicular to said first surface;

(b) a second magnet system mounted within said gap so as to be displace able relative to said first magnet system along a line of travel through said gap, said second magnet system including a first magnetic element con­figured to generate a magnetic field oriented primarily perpendicular to said first surface and extending in said gap in a first direction only, said second magnet system further including a second magnetic element similar to, and mounted in fixed relation to, said first magnetic element, said second magnetic element being config-ured to generate a magnetic field oriented primarily perpendicular to said first surface and extending in said gap in a second direction only, said second direction being opposite to said first direction,

wherein one of said first and second magnet systems pro­duces a non-alternating magnetic field and the other of said first and second magnet systems is a coil assembly for producing an operating magnetic field; and

(c) electrical connections connected to said coil assembly for supplying an electrical current to said coil assembly to produce a reciprocation of said second magnet system relative to said first magnet system.

FIGS. 12A and 12B show a basic permanent magnet 30

implementation employing two cylindrical, oppositely radi­ally magnetized permanent magnets 62 and 64. FIGS. 13A and 13B show a similar implementation employing a cylin­dricallayer support structure 66 with internal and external cylindrical magnets. FIGS. 14A and 14B show a basic 35

implementation of a hexagonal-section magnet system for use with a hexagonally shaped gap. In each of these cases, each of the permanent magnets forming a pole may be unitary or may be composed from several pieces of any shape. The above systems may advantageously be adapted to include a non-zero spacer between the magnetic elements.

2. The electric machine of claim 1, wherein said second 40 magnetic element is spaced from said first magnetic element

along said line of travel by a distance b, where b>O. 3. The electric machine of claim 2, wherein said second

magnet system includes a spacer of thickness b deployed between said first and second magnetic elements, said spacer

45 including soft magnetic material.

FIGS. 15A-18D relate to coil implementations of system 20. It will be clear that a coil extended around the circum­ference of a cylinder 68 (or hexagonal base 69) is essentially equivalent to two sets of circumferential windings carrying current in opposite directions. Thus, two coils 70, 72 for producing opposing radial fields have adjacent windings carrying similarly directed currents either side of a spacer 74. FIG. 17Aillustrates schematically a possible scheme for connecting the windings in which the adjacent windings of 50

the two coils are connected continuously and the outer windings are connected together. FIGS. 17B and 17C illus­trate possible parallel and serial connections, respectively, for such a scheme. In FIGS. 17A-17C, terminals or coil connections bear designations c, k, 1, and m.

FIGS. 18A-18D illustrate an alternative implementation in which each coil is formed as an independent component. In this case, the magnetic elTects of the short sections of each coil running parallel to the direction of motion cancel out.

55

FIGS. 19 and 20 illustrate the constructions of magnetic 60

circuits for two implementations of the electric machine of the present invention having cylindrical symmetry. FIG. 19 corresponds to a first magnet system structure of FIGS. 6C or 6D together with a second magnet system as in one of FIGS. 12, 13, 15 and 18. In this case, first magnet system 12 65

preferably has a constant width W k along the entire gap perimeter.

4. The electric machine of claim 2, wherein said second magnet system includes a spacer of thickness b deployed between said 11rst and second magnetic elements, said spacer including non-magnetic material.

5. The electric machine of claim 2, wherein said second magnet system is distanced from said first surface by a clearance gap of width L',., said second magnet system being configured such that distance b has a magnitude greater than width L',..

6. The electric machine of claim 2, further comprising means for defining a given maximum amplitude A of recip­rocal motion of said second magnet system relative to said 11rst magnet system, wherein said 11rst and second surfaces have a dimension w'" as measured parallel to said line of travel and said second magnet system has a dimension W k as measured parallel to said line of travel, said first and second magnet systems being designed such that w,,+b?::2A and wk?::wo+2A.

7. The electric machine of claim 1, wherein said second magnet system is mounted relative to said first magnet system by a mechanical coupling, said mechanical coupling being configured to de11ne a non-linear line of travel.

5,903,069 13

8. The electric machine of claim 1, wherein said first magnet system is formed as a substantially closed magnetic circuit.

14 said second magnetic element is disposed mostly out­side of said gap while said J1rst magnetic element is disposed mostly within said gap,

9. The electric machine of claim 1, wherein said second magnet system is implemented as said coil assembly.

10. The electric machine of claim 1, wherein said first and second surfaces are shaped such that in a plane perpendicu-

wherein one of said J1rst and second magnet systems pro­S duces a non-alternating magnetic J1eld and the other of said

J1rst and second magnet systems is a coil assembly for producing an operating magnetic J1eld; and

lar to said line of travel said gap has a closed annular form, said second magnet system being implemented as a corre­sponding hollow cylindrical magnet system.

11. The electric machine of claim 10, wherein said first magnet system is implemented as a hollow annular box of soft magnetic material containing windings.

10

12. The electric machine of claim 11, wherein said hollow annular box is constructed from at least two cylindrical 15

portions and an least three annular portions, said cylindrical and said annular portions having beveled edges for forming oblique-angled butt-joints.

13. The electric machine of claim 11, wherein said hollow annular box is constructed from a unitary U-section annular 20

base element and at least one annular cover portion. 14. The electric machine of claim 11, wherein said hollow

annular box is constructed from a plurality of laminations each corresponding to a radial segment of said hollow annular box.

15. The electric machine of claim 10, wherein said second magnet system is implemented as said coil assembly having windings arranged primarily circumferencially in said cylin­drical magnet system.

25

16. The electric machine of claim 1, wherein said second 30

magnet system includes a magnetically passive support structure for supporting said first and second magnetic elements.

17. The electric machine of claim 16, wherein said support structure is made from soft magnetic material. 35

(c) electrical connections connected to said coil assembly for supplying an electrical current to said coil assembly to produce a reciprocation of said second magnet system relative to said first magnet system along said line of travel between said J1rst extreme position and said second extreme position.

21. A synchronous reciprocating electric machine com­prising:

(a) a J1rst magnet system having a J1rst surface and a second surface opposing said J1rst surface so as to define therebetween a gap, said J1rst magnet system being conJ1gured for generating a magnetic J1eld in said gap extending substantially solely perpendicular to said first surface;

(b) a second magnet system mounted within said gap so as to be displace able relative to said J1rst magnet system along a line of travel through said gap, said second magnet system including a first magnetic element con­figured to generate a magnetic field oriented primarily perpendicular to said first surface and extending in said gap in a J1rst direction only, said second magnet system further including a second magnetic element similar to, and mounted in J1xed relation to, said first magnetic element, said second magnetic element being conJ1g­ured to generate a magnetic J1eld oriented primarily perpendicular to said J1rst surface and extending in said gap in a second direction only, said second direction being opposite to said J1rst direction,

wherein one of said J1rst and second magnet systems pro­duces a non-alternating magnetic J1eld and the other of said J1rst and second magnet systems includes a coil for produc-

18. The electric machine of claim 15, wherein said support structure is implemented as a substantially continu­(JUs layer, said J1rst and second magnetic elements being attached to at least one surface of said layer.

19. The electric machine of claim 1, wherein said J1rst surface and said second surface are stationary, said first magnetic element and said second magnetic element moving relative to said first surface and said second surface.

40 ing an operating magnetic J1eld, said coil being wound in a plane extending parallel to said line of travel,

20. A synchronous reciprocating electric machine com­prising: 45

(a) a J1rst magnet system having a J1rst surface and a second surface opposing said J1rst surface so as to deJ1ne therebetween a gap, said first magnet system being conJ1gured for generating a magnetic J1eld in said gap extending substantially solely perpendicular to said 50

first surface; (b) a second magnet system mounted within said gap, said

second magnet system including a first magnetic ele­ment configured to generate a magnetic field primarily perpendicular to said J1rst surface in a J1rst direction and 55

a second magnetic element similar to, and mounted in J1xed relation to, said J1rst magnetic element, said second magnetic element being configured to generate a magnetic J1eld primarily perpendicular to said J1rst surface in a direction opposite to said J1rst direction, 60

said second magnet system being mounted within said gap so as to be displaceable relative to said J1rst magnet system along a line of travel through said gap between a first extreme position wherein said J1rst magnetic element is disposed mostly outside of said gap while 65

said second magnetic element is disposed mostly within said gap and a second extreme position wherein

(c) electrical connections connected to said coil assembly for supplying an electrical current to said coil assembly to produce a reciprocation of said second magnet system relative to said first magnet system.

22. A synchronous reciprocating electric machine com­prising:

(a) a J1rst magnet system having a J1rst surface and a second surface opposing said J1rst surface so as to deJ1ne therebetween a gap, said J1rst magnet system being configured for generating a magnetic field in said gap extending substantially solely perpendicular to said J1rst surface;

(b) a second magnet system mounted within said gap so as to be displace able relative to said J1rst magnet system along a line of travel through said gap, said second magnet system including a J1rst magnetic element con­J1gured to generate a magnetic J1eld oriented primarily perpendicular to said first surface and extending in said gap in a J1rst direction only, said second magnet system further including a second magnetic element similar to, and mounted in J1xed relation to, said J1rst magnetic element, said second magnetic element being config­ured to generate a magnetic J1eld oriented primarily perpendicular to said J1rst surface and extending in said gap in a second direction only, said second direction being opposite to said J1rst direction,

5,903,069 15

wherein one of said first and second magnet systems pro­duces a non-alternating magnetic field and the other of said first and second magnet systems is a coil assembly for producing an operating magnetic field, said gap being free of any magnetic core windings of said first magnet system, 5

thereby minimizing a width of said gap; and

(c) electrical connections connected to said coil assembly for supplying an electrical current to said coil assembly to produce a reciprocation of said second magnet system relative to said first magnet system.

23. A synchronous reciprocating electric machine com­prising:

10

(a) a first magnet system having a J1rst surface and a second surface opposing said first surface so as to define therebetween a gap, said first magnet system 15

being configured for generating a magnetic field in said gap extending substantially solely perpendicular to said first surface;

16 the first direction, the second magnetic element being spaced from the first magnetic element along the line of travel bv a distance b, wherein one of the J1rst and second "magnet systems produces a non-alternating magnetic field and the other of the first and second magnet systems is a coil assembly for producing an operating magnetic field;

determining a maximum intended amplitude A of relative reciprocal movement of said second magnet system relative to said J1rst magnet system;

providing the J1rst and second surfaces of the J1rst magnet system with a dimension We as measured parallel to the line of travel of the second magnet system such that wo+b~2A;

providing the second magnet system with a dimension wk

as measured parallel to the line of travel of the second magnet system such that wk~we+2A; and

coupling electrical connections to the coil assembly for supplying an electrical current to said coil assembly to produce a reciprocation of the second magnet system relative to the J1rst magnet system.

25. The method of claim 24, wherein where b>O. 26. The method of claim 24, wherein where distance b is

chosen to be at least about the spacing between said second 25 magnet system and said first surface.

(b) a second magnet system mounted within said gap so 20

as to be displace able relative to said first magnet system along a line of travel through said gap, said second magnet system including a first magnetic element con­figured to generate a magnetic field oriented primarily perpendicular to said J1rst surface and extending in said gap in a J1rst direction only, said second magnet system further including a second magnetic element similar to, and mounted in fixed relation to, said first magnetic element, said second magnetic element being config­ured to generate a magnetic field oriented primarily perpendicular to said first surface and extending in said gap in a second direction only, said second direction being opposite to said first direction,

27. The method of clam 26, wherein the second magnet system is constructed with a magnetically-passive interme­diate spacer of width b.

28. A synchronous reciprocating electric machine com-30 prising:

wherein one of said first and second magnet systems pro­duces a non-alternating magnetic field and the other of said 35

first and second magnet systems is a coil assembly for producing an operating magnetic J1e1d; and

(c) electrical connections connected to said coil assembly for supplying an electrical current to said coil assembly to produce a reciprocation of said second magnet 40

system relative to said first magnet system, wherein said first and said second magnet systems are configured to provide said second magnet system with a magnetically induced equilibrium position substantially cen­trally located with respect to said gap when said coil 45

assembly is de-energized. 24. A method for building a synchronous reciprocating

electric machine, comprising: providing a first magnet system having a first surface and

(a) a first magnet system having a first surface and a second surface opposing said first surface so as to define therebetween a gap, said J1rst magnet system being configured for generating a substantially uniform magnetic field in said gap extending substantially solely perpendicular to said first surface;

(b) a second magnet system mounted within said gap so as to be displace able relative to said first magnet system along a line of travel through said gap, said second magnet system including a first magnetic element con­figured to generate a first respective magnetic field primarily perpendicular in said gap to said first surface in a first direction and a second magnetic element similar to, and mounted in fixed relation to, said first magnetic element, said second magnetic element being configured to generate a second respective magnetic field primarily perpendicular in said gap to said first surface in a direction opposite to said first direction, said first respective magnetic field and said second respective magnetic field having respective axes of symmetry which are substantially spaced from one another along said line of travel, said second magnet system having exactly two magnetic fields,

a second surface opposing said first surface so as to 50

define therebetween a gap, said first magnet system being conJ1gured for generating a magnetic J1e1d in said gap extending substantially solely perpendicular to said first surface; wherein one of said first and second magnet systems pro­

ss duces a non-alternating magnetic field and the other of said J1rst and second magnet systems is a coil assembly for producing an operating magnetic field; and

disposing a second magnet system within the gap so as to be displaceable relative to the first magnet system along a line of travel through the gap, the second magnet system including a first magnetic element configured to generate a magnetic field oriented primarily perpen­dicular to the first surface and extending in said gap in 60

a first direction only, the second magnet system further including a second magnetic element similar to, and mounted in fixed relation to, the first magnetic element, the second magnetic element being configured to gen­erate a magnetic field oriented primarily perpendicular to the J1rst surface and extending in said gap in a second direction only, said second direction being opposite to

(c) electrical connections connected to said coil assembly for supplying an electrical current to said coil assembly to produce a reciprocation of said second magnet system relative to said J1rst magnet system.

29. The electric machine of claim 28, wherein said second magnet system includes a spacer of thickness b deployed between said first and second magnetic elements, where

65 b>O. 30. The electric machine of claim 29, wherein said second

magnet system is distanced from said first surface by a

5,903,069 17

clearance gap of width t., said second magnet system being configured such that thickness b has a magnitude at least about width t..

31. The electric machine of claim 28, wherein said first and second surfaces are shaped such that in a plane perpen­dicular to said line of travel said gap has a closed annular form, said second magnet system being implemented as a corresponding hollow cylindrical magnet system.

18 said first respective magnetic field and said second respective magnetic J1eld occupying adjacent regions of space essentially without overlap, said second magnet system having exactly two magnetic fields,

5 wherein one of said first and second magnet systems pro­duces a non-alternating magnetic field and the other of said first and second magnet systems is a coil assembly for producing an operating magnetic field; and

32. The electric machine of claim 31, wherein said first magnet system is implemented as a hollow annular box of 10

soft magnetic material containing windings.

(c) electrical connections connected to said coil assembly for supplying an electrical current to said coil assembly to produce a reciprocation of said second magnet system relative to said first magnet system. 33. The electric machine of claim 28, wherein said first

surface and said second surface are stationary, said first magnetic element and said second magnetic element moving relative to said first surface and said second surface.

34. A synchronous reciprocating electric machine com­prising:

(a) a first magnet system having a J1rst surface and a second surface opposing said first surface so as to define therebetween a gap, said first magnet system being configured for generating a substantially uniform magnetic field in said gap extending substantially solely perpendicular to said J1rst surface;

(b) a second magnet system mounted within said gap so as to be displace able relative to said first magnet system along a line of travel through said gap, said second magnet system including a first magnetic element con­figured to generate a first respective magnetic field primarily perpendicular in said gap to said first surface in a first direction and a second magnetic element similar to, and mounted in fixed relation to, said first magnetic element, said second magnetic element being configured to generate a second respective magnetic field primarily perpendicular in said gap to said first surface in a direction opposite to said J1rst direction,

35. The electric machine of claim 34, wherein said second magnet system includes a spacer of thickness b deployed

15 between said first and second magnetic elements, where b>O.

36. The electric machine of claim 35, wherein said second magnet system is distanced from said J1rst surface by a clearance gap of width t., said second magnet system being

20 configured such that thickness b has a magnitude at least about width t..

37. The electric machine of claim 34, wherein said first and second surfaces are shaped such that in a plane perpen­dicular to said line of travel said gap has a closed annular

25 form, said second magnet system being implemented as a corresponding hollow cylindrical magnet system.

38. The electric machine of claim 37, wherein said first magnet system is implemented as a hollow annular box of soft magnetic material containing windings.

30 39. The electric machine of claim 34, wherein said first surface and said second surface are stationary, said first magnetic element and said second magnetic element moving relative to said first surface and said second surface.

* * * * *

United States Patent [19]

Rounds

[54] AMPLIFYING MECHANICAL ENERGY WITH MAGNETOMOTIVE FORCE

[76] Inventor: Donald E. Rounds, 3111 NW. Norwood PI., Corvallis, Oreg. 97330

[21] Appl. No.: 09/294,078

[22]

[51] [52]

Filed: Apr. 19, 1999

Int. CI? ........................... H02K 37/00; H02K 49/00 U.S. CI. ............................ 310/46; 310/103; 310M2;

310/114 [58] Field of Search ..................................... 310/152, 156,

[56]

Re.29,165 2,243,555 2,378,129 3,267,310 3,355,645 3,790,833 4,074,153 4,151,431 4,169,983 4,751,486 4,877,983 5,034,642 5,569,967 5,886,608

310/154, 162, 103, 83, 80, 46, 92, 75 D, 114, 112; 464/29; 74/63, 37

References Cited

U.S. PATENT DOCUMENTS

3/1977 Bode ......................................... 310/46 5/1941 FallS ........................................ 172/284 6/1945 Chamber ................................. 172/284 8/1966 Ireland .................................... 310/103

11/1967 Kawakami et al. . 2/1974 Rasebe.. ... ... ... .... ... ... ... ... ... ...... 310/162 2/1978 Baker . ... ... ... ... .... ... ... ... ... ... ........ 310/12 4/1979 Johnson .................................. 310/152

10/1979 Felder ....................................... 310/46 6/1988 Minalo .................................... 310/156

10/1989 Johnson .................................. 310/152 7/1991 Roemann et al. ...................... 310/156

10/1996 Rode ....................................... 310/103 3/1999 Chabay ................................... 310/103

151~

140 'j

I I I

111111 1111111111111111111111111111111111111111111111111111111111111 US006084322A

[11] Patent Number:

[45] Date of Patent:

6,084,322 .luI. 4, 2000

FOREIGN PATENT DOCUMENTS

62-114466 of 0000 Japan. 62-81972 of 0000 Japan.

OTHER PUBLICATIONS

"Electric Motors & Electronic Motor Techniques" by J. M. Gottlieb; 1st Ed.; 1976 Howard M. Sims & Co., Inc.; The Bobs-Merrill Co., Inc.; Indianapolis, Kansas City, New York.

Primary Examiner-Nestor Ramirez Assistant Examiner--':'Tran N Nguyen Attorney, Agent, or Firm-William W. Haefiiger

[57] ABSTRACT

A magnetically operating device comprises a driven magnet having magnetically opposite poles which are separated, a driver magnet having magnetically opposite poles, and the magnets are mounted for relative movement to maintain one of the driver magnet's poles substantially equidistant from the poles of the driven magnets as the driven magnet moves relative to the driver magnet. A first rotor may mount the driven magnet or magnets for rotation about a first axis, and a second rotor may mount the driver magnet or magnets for rotation about a second axis, and such axes are typically non intersecting and skewed, the rotors being intercoupled. A source of torque such as a motor may be coupled to the second rotor to effect torque input to the second rotor.

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WI Til MAGNETS

WITIlt11J7 MAGNETS

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OPERATING TIME (MINUTES)

6,084,322 1

AMPLIFYING MECHANICAL ENERGY WITH MAGNETOMOTIVE FORCE

FIELD OF THE INVENTION

This invention relates generally to the utilization of the 5

2 c) means for mounting the rotor and wheel for relative

movement, to maintain the single pole of each driver magnet or magnets substantially equidistant from the separated magnetic poles of the driven magnet or magnets as the driven magnet or magnets moves rela­tive to the driver magnet or magnets.

potential energy in magnets, as for example permanent magnets; and more particularly to a device wherein one or more magnets is caused to move unimpeded past a second magnet or magnets, while creating a strong unidirectional movement of the second magnet or magnets.

As will be seen, the rotor typically mounts the driven magnet or magnets for rotation about a first axis; and the wheel typically mounts the driver magnet or magnets for

10 rotation about a second axis. The two axes are typically skewed, as will appear.

BACKGROUND OF THE INVENTION

More than 85% of energy being consumed today is that from fossil fuels. Although this has many advantages, it has 15

been estimated that the world's reserves of both oil and

It is another object of the invention to include the provi­sion of means operatively coupled to the rotor and wheel for synchronizing rotation thereof.

Yet another object is the provision of a train of such driven magnets on the rotor. Typically, the driven magnets in the train have north and south poles located in alternating rotary sequence. Such driven magnets may be generally bar-shaped and elongated, as well as uniformly spaced apart along the

natural gas will be depleted, at the current rate of consumption, by the year 2024 (Science, vol. 245, pp. 1330-1331, 1989). Moreover, the burning of fossil fuel produces both gaseous and particulate pollutants which cause extensive damage to crops and plants, deterioration of paint, rubber and textiles, and contributes signijlcantly to reduced respiratory function and production of cancer in humans. There is also strong evidence that the gaseous byproducts of this energy source are contributing to global warming and acid rain. The magnitude of these economic and environmental problems has become so serious that it is imperative that the use of fossil fuels be reduced without compromising the application of this energy source.

20 periphery of the first rotor, such as a flywheel. The driven magnets can alternatively be mounted radially, like spokes in a wheel, with alternating north and south poles at the periphery of the rotor. Typically, bipoles of driven magnets form force zones consisting of north-south regions followed

25 by south-north regions, each of equal length around the circumference of the rotor.

The invention also basically allows one driver magnet to move unimpeded between bipoles defined by the driven magnets, whereby unidirectional movement of the driven

Permanent magnets have long been known to contain strong potential energy, but this has only been used in motors

30 magnet rotor is magnetically created. In order to maintain a unidirectional rotation, (e.g. clockwise), the north pole of a driver magnet typically drives a north-south bipole of the driven magnets, while a south pole of a driver magnet

or generators, to date, in the form of stators which create or direct electromotive forces, not as a physical supplement to those forces. The present invention has potential for gener­ating greater forces in existing electric or gasoline motors, 35

wind powered generators, human powered bicycles or other such devices without using additional fuel or creating addi­tional environmental pollutants.

typically drives a south-north bipole of the driven magnets. Magnets can be replaced, or re-charged, after energy

depletion, or the device can simply be allowed to "run­down", it having expanded its utility over a useful time interval.

SUMMARY OF THE INVENTION These and other objects and advantages of the invention,

40 as well as the details of an illustrative embodiment, will be more fully understood from the following specification and drawings, in which:

Although the basic principles of magnetic force are well known, it is helpful to briefly summarize these principles as background to describe the method of developing magne­tomotive force in terms of the present invention. Basically, permanent magnets are polar, in that such a magnet always 45

has a north pole and a south pole. Opposite poles strongly attract each other while like poles repel each other. The force of attraction between any two magnets is the result of the force of one magnet (M1) multiplied by the force of the other (M2)' divided by the square of the distance between them 50

(d2). This formula: F=MlxM2/d2, is known as Coulomb's

law for magnetic poles.

DRAWING DESCRIPTION

FIG. 1 is a diagram showing principles of the invention; FIGS. 2A, 213 and 2C are likewise diagrams showing

principles of the invention; FIG. 3 is a diagram showing basic elements of the

invention; FIGS. 4(A)-4(E) are views showing skewed angularity of

driver magnet motion relative to driven magnet motion, where a pole of the driver magnet is always maintained equidistant from bipoles of the rotating train magnets;

FIG. 5 is a graph of torque values generated at each force zone at the time single driver magnets pass between the bipoles of the driven magnets;

It is a major object of the invention to take advantage of this law by providing a permanent magnet rotor which turns 55

in a unidirectional motion by interaction with a driver magnet or magnets, which can be made to rotate with a negligible amount of force from any form of engine, but in doing so, it can cause a significant amount of force in the rotor.

FIG. 6 is a graph of torque values generated at each force zone by two sets of three driver magnets at the time they pass

60 between the bipoles of the driven magnets; Basically the invention is included in a combination of

elements, which includes: a) a rotor incorporating a driven magnet or magnets,

positioned with alternately opposite and separated magnetic poles,

b) a driver wheel incorporating a driver magnet or magnets, each with a single pole facing the rotor, and

65

FIG. 7 is a graph of the amount of rotation counterbalance required at force zones on the driven rotor with a range of torques being applied to the driver magnet when driven magnets are either absent or present;

FIG. 8 is a graph of the battery voltage decay rate for the electric motor which activates the driver wheel when driven magnets are either absent or present.

6,084,322 3

DETAILED DESCRIPTION

Referring to FIG. 1, it shows a driver magnet 10 having opposite, as for example north and south poles lOa and lOb.

4 extending diametrically opposite magnet 10, and having its south pole (S) at the periphery of 15. Bar magnets 10 and lOa extend radially. Maintaining the peripheral pole of the driver magnet in the neutral corridor requires that the two

A second magnet 11 is provided on a rotor 12 mounted by an axle 13 to rotate about an axis 14. Multiple second magnets 11 and 11a are depicted in a "train", i.e. at the periphery of the circular rotor, and they are alike and curved, as shown, and spaced along the circular periphery of 12, which may constitute a flywheel. In this configuration, the bar magnets 11 and 11a create north-south force zones while the air gaps between them create south-north force zones.

5 rotors or wheels 12 and 15 be synchronized as through a chain drive 18 (FIG. 3) or other timed drive (timing belt and sprockets or a set of gears), to produce the following conditions: (1) the turning ratio of the train-to-driver wheels 12 and 15 is typically 1:4; (2) the train magnets must have

When the north pole (N) of a bar magnet (the driver magnet) is brought into close proximity to the middle of one

10 poles uniformly spaced in Nand S sequence on the circum­ference of the train flywheel; (3) the driver wheel must be mounted on an angle (FIG. 4) described by the hypotenuse of a right triangle, where the base is equal to 0.5 times the distance between the bipoles on the train wheel, while the

of the train magnets on the rotor or flywheel, the north pole (N) of the driver magnet repels the north pole of the train magnet and it simultaneously attracts the south pole (S) of that train magnet. When the driver magnet is held stationary, the train magnet 11 moves with respect to the driver, resulting in an angular displacement (or rotary motion) of 20

the flywheel 12 (FIG. 1) until the south pole of the train magnet stops at its closest point to the north pole of the driver magnet. If, however, the driver magnet is moved away before the south pole of the train magnet reaches that position, the square of the distance between the two magnets 25

is sufficiently great to reduce the force between them to a negligible level. At that point the momentum of the flywheel continues to carry the train magnet along its rotary motion for a period of time. FIG. 1 also shows a second driven magnet 11a, like 11, but at the diametrically opposite rim 30

portion of 12. This can also be acted on by driver magnet 10 when it replaces driven magnet 11 during the rotation.

15 altitude of the right triangle is equal to 0.25 times the circumference of the driver wheel; and (4) the driver magnet is carefully positioned within the neutral corridor on one train magnet before starting the motion of the external

If the driver magnet 10 is mounted radially on a second rotor or Hywheel, designated as 15 in FIG. 2(A), the plane of which is approximately perpendicular to that of the first, with the north pole (N) of the driver magnet 10 extending to

35

the margin of the wheel, its rotation will be influenced by the position of the train magnet 11. Again, if the north pole of the driver magnet is in close proximity to the north pole of the train magnet (when the train is held in a stationary 40

position), the driver magnet is repelled (see arrow 40 in FIG. 2A). If the north pole of the driver magnet is in close proximity to the south pole of the train magnet (when the train is held in a stationary position), the driver magnet is attracted (see arrow 41 in FIG. 2B). However, more 45

importantly, if the train magnet 11 is held so that the north pole of the driver magnet is equidistant between the two N-S poles of the train magnet, the attraction and the repulsion of the poles of the train magnet cancel each other and they cannot act to influence the plane of rotation of the vertical 50

wheel holding the driver magnet (FIG. 2C). As a result, the driver wheelIS can rotate freely through a neutral angular corridor (i.e. angle), without being influenced by the lateral forces of the train magnet 11. Thus, when one pole of the driver wheel magnet is always maintained equidistant from 55

the two poles of each train magnet, there is no effect on the motion of the driver magnet's wheel, but under these same conditions the driver magnet exerts a maximum effect on the train magnet's wheel 12. When a small external motor (as at 24 in FIG. 3) is used to rotate the axle 16 of driver wheelIS, 60

the resulting rotary force of the train magnets strongly ampliJles the force of the external motor. This circumstance

motor.

In FIG. 3, the drive 18 is depicted as an endless chain or timing belt 19, entraining small sprocket or pulley 20 on axle 16, large sprocket or pulley 21 on axle 13, and idler pulleys 22 and 23 that turn the direction of the chain or belt. The small sprocket or pulley 20 and the large sprocket or pulley 21 define the turning ratio of the driver wheel 15 and train wheel 12. A driven device 140 may be coupled to driven shaft 13; and all elements are properly sized. Device 140 may comprise the drive train of a vehicle such as an automobile.

It should be noted that since the force of the driver magnet on the train magnet is inversely proportional to the square of the distance between them, the greatest force on the train wheel will occur at the time the driver magnet is close to each train magnet. This was confirmed by Example 1.

EXAMPLE 1

A 6.625 inch diameter train wheel 12 was constructed with eight (8) two inch long driven rod magnets, 0.75 inches in diameter, mounted radially, with approximately 1.875 inches between each pole at the periphery of the wheel. The margin of the wheel was marked at 5 degree increments around its circumference and it was placed vertically in a cradle mounted on the pan of a triple beam balance.

A 10 inch diameter driver wheelIS was constructed with 2 one inch long driver rod magnets, 0.75 inches in diameter, mounted on opposite sides of the wheel. One driver magnet 10 was mounted with its north pole at the periphery of the wheel and the other lOa was mounted with its south pole at the periphery of the wheel. The margin of the driver wheel was marked at 20 degree increments around its circumfer-ence to simulate a 1 :4 turning ratio. The driver wheelIS was mounted horizontally so that the driver magnets 10 and lOa would pass through the neutral corridor of each of the bipoles on the train wheel 12, which was mounted vertically on the pan of the balance. The distance between the two wheels was 0.5 inches. Net vertical forces, in grams, were measured on the triple beam balance at each of the 72 marked increments to indicate the force exerted on the periphery of the train wheel 12.

The results are shown in FIG. 5. The angular rotation forces were recorded as a series of pulses which occurred when a pole of a driver magnet came into position between the bipoles of the train magnets, as in FIG. 4C. In a second

is the basic principle that permits utilizing the potential energy in permanent magnets for this purpose. Motor 24 is energized by a battery 24a.

FIGS. 2(A), (B) and (C) also show axle 16 for rotor 15; axis 17 of rotation of 15; and a second driver bar magnet lOa

65 version of this experiment, six north pole driver magnets and six south pole driver magnets were used instead of one of each. The distance between the two wheels was one inch.

6,084,322 5 6

With all magnets in place, the electric motor 24 moved the driven wheel 12 at 64 rmp and the driver wheel 15 at 256 rpm. At this speed the generator produced an output of 2.9 volts. Although this model was far from being optimized,

FIG. 6 shows that under these conditions the pulse widths of the forces could be broadened in order to smooth the rotation. In other experiments it was observed that increas­ing the number of train magnets could further broaden the pulse widths at the force zones.

EXAMPLE 2

5 this experiment supports the premise that magnetomotive force could amplify the electromotive force to produce work in the form of voltage generation.

A simple working model of the system as shown in FIG. EXAMPLE 5

The same model described in Example 2 was used to compare the rates at which size AA 1.5 volt DC batteries being used to drive the electric motor 24 decayed, with and without the driven magnets in place. The system was oper­ated for one minute intervals for a total of five minutes for

3 was constructed using a system of gears instead of an 10

endless belt with pulleys. The train wheel 12 was a 7 inch diameter rotor with 8 radially positioned rare earth (NdFeB) rod magnets, 0.75 inches long and 0.75 inches in diameter. The driver wheel 15 was 10 inches in diameter and had single NdFeB magnets on opposite sides of the wheel. One driver magnet 10 was mounted with a north pole moving through each neutral corridor of the north-south bipoles while the second magnet lOa was mounted with a south pole moving through the neutral corridor of each of the south­north bipoles of the driven magnets while the driver wheel 20

15 was moving at a 4.1 ratio with respect to the driven wheel 12. The distance between the two wheels was 1.25 inches.

15 each condition, with the DC voltage of the batteries being recorded at the end of each minute. Fresh batteries were used

In order to evaluate the net torque of the force zones, a series of weights were placed on one side of the driver wheel 15 which was positioned with a driver magnet at its closest 25

proximity to the bipoles of a force zone. Counterbalance weights were placed on the driven magnet rotor 12, just sufficient to stop the forward rotation of this rotor. The same measurements were made when the driven magnets were removed, to determine how much of the torque on the driven 30

magnet rotor 12 was due to the magnetomotive force. The data in FIG. 7 show that the increase in torque of the

driven rotor when no magnets were present could be attrib­uted to the 4:1 gear ratio. When the driven magnets were in place, the torque on the driven wheel increased by approxi- 35

mately 120 grams.

EXAMPLE 3

A modified model described in Example 2 was outfitted with a small DC electric motor 24 which was made to 40

operate the wheels using two D size batteries. Instead of single driver magnets on each side of the driver wheel 15, four north pole rare earth (NdFeB) driver magnets and four south pole rare earth (NdFeB) driver magnets were used. The driven rotor 12 was 6.125 inches in diameter and 45

contained 8 sets of 3 magnets with each set uniformly spaced and alternating north and south poles around the circumfer­ence of the rotor. The distance between the two wheels was 1.25 inches.

Rates of rotation of the driver wheel were determined 50

with and without driver magnets in the driver magnet wheel 15. With all other conditions being equal, the rate of rotation produced by the electrical energy source (2.57 volts DC) when driver magnets were present was 65 rpm for the driven 55

rotor 12 and 260 rpm for the driver wheel 15. When the driver magnets were removed, even increasing the voltage from 2.5 to 4.0 volts could not sustain continual rotation of the two wheels. Under this set of conditions, magnetomotive force was required to supplement the electromotive force to 60

produce continual rotation.

EXAMPLE 4

at the beginning of each series.

The data in FIG. 8 show that the battery decay rate when magnetomotive amplijlcation was used was signijlcantly slower than when electromotive force was used alone. 111is principle could be important for applications such as electric automobiles, where batteries need to be recharged at fre­quent intervals.

New magnets can be substituted for any of the magnets on the rotor, as indicated at 150 and 151 in FIG. 3.

Usable magnets consist of a material or materials selected from the group that includes NdFeB, alnico, ceramic, iron­chromium-cobalt (FeerCo), rare earth, samarium cobalt (SmCo), other magnetic material. Of these NdFeB is pre­ferred.

Usable sources of torque comprise one or more of the following:

i) an electric motor

ii) an internal combustion engine

iii) wind

iv) flowing water

v) manual or foot power vi) other power source. I claim: 1. A device comprising, in combination: a) a train of driven magnets on a first rotor, each driven

magnet having magnetically opposite poles which are separated,

b) a circularly spaced sequence of driver magnets on a second rotor, each driver magnet having magnetically opposite poles,

c) means for mounting said first and second rotors to have planes of rotation defined by said magnets, said planes being substantially perpendicular, for relative move­ment of the magnets to maintain driver magnet's poles substantially equidistant from the poles of the driven magnet as the driven magnets move relative to the driver magnets, and as the rotors rotate in synchronism,

d) and a source of torque coupled to said second rotor to effect torque input to the second rotor, as may he needed for driving of the first rotor by the second rotor.

2. The combination of claim 1 wherein at least one of said magnets is a permanent magnet.

3. The combination of claim 1 wherein both of said magnets are permanent magnets.

A small electric generator was added to the model described in Example 3 and the electric motor was energized with three 1.5 volt DC batteries in order to compensate for the increased friction caused by the generator installation.

4. The combination of claim 1 wherein said first rotor is 65 mounted for rotation about a first axis.

5. Ibe combination of claim 4 wherein said second rotor is mounted for rotation about a second axis.

6,084,322 7

6. The combination of claim 5 wherein said first and second axes are non-intersecting and are skewed.

7. The combination of claim 5 wherein said c) means includes means operatively coupled to said first and second rotors for synchronizing rotation thereof. 5

8. The combination of claim 6 wherein said second rotor is a driver rotor, said skewing of said axes characterized in that they form a right triangle having a base and altitude where:

base=O.5 times distance between north-south poles on the 10

driven rotor altitude=O.25 times circumference of the driver rotor. 9. The combination of claim 1 wherein said driver mag­

nets in said train have north and south poles located in rotary sequence. 15

10. The combination of claim 1 wherein said magnets consist of a material or materials selected from the group that includes NdFeB, alnico, ceramic, iron-chromium-cobalt (FeCreo), samarium cobalt (SmCo), other magnetic mate­rial.

11. The combination of claim 1 wherein said rotors define 20

a turning ratio having a value which is about 1:4. 12. The combination of claim 1 wherein there are multiple

driven magnets on said first rotor, said driven magnets having poles that are uniformly spaced apart in north and south pole sequence along the periphery of the train rotor. 25

13. The combination of claim 1 wherein said source of torque comprises one of the following:

i) an electric motor ii) an internal combustion engine iii) wind 30

iv) flowing water v) manual or foot power vi) other power source. 14. The combination of claim 13 wherein said motor is

battery driven. 35

15. The combination of claim 14 including a driven device coupled in driven relation with said driven rotor.

16. The combination of claim 15, wherein said device is the drive train of an automobile.

17. A device comprising. in combination: a) a driven magnet having magnetically opposite poles

which are separated, b) a driver magnet having magnetically opposite poles,

40

c) means for mounting said magnets for relative move­ment to maintain one of the driver magnet's poles 45

substantially equidistant from the poles of the driven magnet as the driven magnet moves relative to the driver magnet,

d) there being a train of said driven magnets, and said c) means including a J1rst rotor mounting said train of 50

driven magnets for rotation abut a J1rst axis, e) there being a circularly spaced sequence of said driver

magnets, and said c) means also including a second rotor mounting the driver magnets for rotation about a 55

second axis, t) and wherein said driven magnets extend circularly on

said J1rst rotor, and said driver magnets extend radially on said second rotor.

18. The combination of claim 17 wherein i) the first rotor has circumference along which said

driven magnets extend, in a train, ii) the driven magnets have equal lengths,

60

iii) said circumference is twice the length of each driven magnet multiplied by the number of said driven 65

magnets, iv) the driven magnets being spaced apart.

8 19. The combination of claim 18 wherein the minimum

distance "d" between driver and driven magnets being rotated on said rotor is MJxM2/d2=O, where

M1 =magnetic force of 10

M2=magnetic force of 1l. 20. A device comprising, in combination:

a) a driven magnet having magnetically opposite poles which are separated,

b) a driver magnet having magnetically opposite pole,

c) means for mounting said magnets for relative move­ment to maintain one of the driver magnet's poles substantially equidistant from the poles of the driven magnet as the driven magnet moves relative to the driver magnet,

d) there being a train of said driven magnets, and said c) means including a J1rst rotor mounting said train of driven magnets for rotation abut a first axis,

e) there being a circularly spaced sequence of said driver magnets, and said c) means also including a second rotor mounting the driver magnets for rotation about a second axis,

1) and wherein said J1rst rotor is a flywheel, and said train of magnets is located at the circumference of the flywheel.

21. A device comprising, in combination:

a) a driven magnet having magnetically opposite poles which are separated,

b) a driver magnet having magnetically opposite poles,

c) means for mounting said magnets for relative move­ment to maintain one of the driver magnet's poles su bstantially equidistant from the poles of the driven magnet as the driven magnet moves relative to the driver magnet,

d) there being a train of said driven magnets, and said c) means including a J1rst rotor mounting said train of driven magnets for rotation abut a J1rst axis,

e) there being a circularly spaced sequence of said driver magnets, and said c) means also including a second rotor mounting the driver magnets for rotation about a second axis,

f) and wherein said driven magnets in the train are relatively narrow bar-shaped permanent magnets.

22. A device comprising, in combination:

a) a driven magnet having magnetically opposite poles which are separated,

b) a driver magnet having magnetically opposite poles,

c) means for mounting said magnets for relative move­ment to maintain one of the driver magnet's poles substantially equidistant from the poles of the driven magnet as the driven magnet moves relative to the driver magnet,

d) there being a train of said driven magnets, and said c) means including a first rotor mounting Raid train of driven magnets for rotation abut a J1rst axis,

e) there being a circularly spaced sequence of said driver magnets, and said c) means also including a second rotor mounting the driver magnets for rotation about a second axis,

f) and wherein the J1rst rotor is a flywheel, and said driven magnets in the train are lengthwise substantially rect­angular permanent magnets.

* * * * *

(12) United States Patent Ho et ai.

(54) MAGNETICALLY AUGMENTED ROTATION SYSTEM

(76) Inventors: Clmn-Yuan Ho; Tien-See Chow, both of 10 Confucius Plz. #5 F, New York, NY (US) 10002

( *) Notice: Subject to any disclaimer, the term of this patent is extended or adjusted under 35 U.S.c. 154(b) by 0 days.

(21) Appl. No.: 09/775,437

(22) Filed: Feb. 2, 2001

(51) Int. cl? ............................ H02K 7/10; H02K 7/09; H02K 1/17; H02K 1/27

(52) U.S. CI ............................. 310/154.01; 3101156.01; 310/90.5; 310180

(58) Field of Search ......................... 310/152, 90, 90.5, 310/1, 154.Q1, 154.04, 154.24, 154.23,

154.22, 154.21, 154.29, 154.28, 156.01; 180/205,220,206,214, 65.1, 65.2,76,

84, 80, 75 E, 75 C, 78

(56) References Cited

U.S. PATENT DOCUMENTS

2,351,424 A 6/1944 Hansen, Jr. 3,734,565 A 5/1973 Mulasmajic 3,768,532 A 10/1973 Arai 4,062,421 A * 12/1977 Weber ........................ 180/205 4,095,663 A * 6/1978 Gaffney ...................... 180/205 4,179,633 A 12/1979 Kelly 4,571,528 A * 2/1986 McGee et al. ......... 310/154.29 D289,512 S 4/1987 Fukuchi 4,833,351 A * 5/1989 Forys et al. .................. 310/12 5,002,296 A 3/1991 Chiu 5,118,977 A * 6/1992 Bertram el al. ........... 310/49 R

23

35----...

111111 1111111111111111111111111111111111111111111111111111111111111

DE DE JP JP JP

US006356000Bl

(10) Patent No.: (45) Date of Patent:

US 6,356,000 BI Mar. 12,2002

5,182,533 A * 1/1993 Ritts .......................... 335/306 5,481,146 A * 1(1996 Davey ................... 310/154.05 5,514,926 A * 5/1996 Bushman .................... 310/105 5,788,007 A * 8/1998 Miekka ...................... 180/205 6,137,194 A * 10/2000 Haugseth ....................... 310/1 6,163,148 A * 12/2000 Takada et al. .............. 180/206 6,274,959 Bl * 8/2001 Uchiyama ................... 310/152

FOREIGN PATENT DOCUMENTS

3422280 A1 * 4/1986 3931611 Al * 3/1990

359117449 A * 7/1984 362247755 A * 10/1987 406245483 A * 9/1994

H02K/53/00 H02K/21/00 H02K/21/00 H02K/53/00 H02K/53/00

* cited by examiner

Primary Examiner---Nestor Ramirez Assistant Examiner--Guillermo Perez

(57) ABSTRACT

A magnetically augmented rotation system for improving the efficiency of drive wheel and prime mover efficiency. The magnetically augmented rotation system includes includes a wheel assembly having a central portion, a first magnetic assembly with a first magnetic polarity, and a second magnetic assembly having a second magnetic polar­ity opposite the polarity of the first magnetic assembly; a bearing assembly for facilitation the rotation of the wheel assembly and comprised of non-magnetic material; a mag­netic biasing assembly positioned such that a torquing force is applied to the wheel assembly by an interaction between the magnetic biasing assembly and the first and second magnetic assemblies; and an anti-reversing gear assembly coupled to the wheel assembly allowing the magnetically augmented rotation system to rotate in a first direction while preventing it from rotating in a second direction.

8 Claims, 2 Drawing Sheets

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US 6,356,000 Bl 1

MAGNETICALLY AUGMENTED ROTATION SYSTEM

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to magnetic drive systems and more particularly pertains to a new magnetically aug­mented rotation system for improving the efficiency of drive wheel and prime mover efficiency.

2. Description of the Prior Art

The use of magnetic drive systems is known in the prior art. More specifically, magnetic drive systems heretofore devised and utilized are known to consist basically of familiar, expected and obvious structural configurations, notwithstanding the myriad of designs encompassed by the crowded prior art which have been developed for the ful­fillment of countless objectives and requirements.

Known prior art includes U.S. Pat. Nos. 4,062,421; 3,768, 532; 4,179,633; 3,734,565; 5,002,296; 2,351,424; and U.S. Pat. No. Des. 289,512.

While these devices fulfill their respective, particular objectives and requirements, the aforementioned patents do not disclose a new magnetically augmented rotation system. The inventive device includes a wheel assembly having a central portion, a first magnetic assembly with a first mag­netic polarity, and a second magnetic assembly having a second magnetic polarity opposite the polarity of the first magnetic assembly; a bearing assembly for facilitation the rotation of the wheel assembly and comprised of non­magnetic material; a magnetic biasing assembly positioned such that a torquing force is applied to the wheel assembly by an interaction between the magnetic biasing assembly and the first and second magnetic assemblies; and an anti­reversing gear assembly coupled to the wheel assembly allowing the magnetically augmented rotation system to rotate in a first direction while preventing it from rotating in a second direction.

In these respects, the magnetically augmented rotation system according to the present invention substantially departs from the conventional concepts and designs of the prior art, and in so doing provides an apparatus primarily developed for the purpose of improving the efficiency of drive wheel and prime mover efficiency.

SUMMARY OF THE INVENTION

In view of the foregoing disadvantages inherent in the known types of magnetic drive systems now present in the prior art, the present invention provides a new magnetically augmented rotation system construction wherein the same can be utilized for improving the efficiency of drive wheel and prime mover efficiency.

The general purpose of the present invention, which will

2 bearing assembly for facilitation the rotation of the wheel assembly and comprised of non-magnetic material; a mag­netic biasing assembly positioned such that a torquing force is applied to the wheel assembly by an interaction between

5 the magnetic biasing assembly and the first and second magnetic assemblies; and an anti-reversing gear assembly coupled to the wheel assembly allowing the magnetically augmented rotation system to rotate in a first direction while preventing it from rotating in a second direction.

10 There has thus been outlined, rather broadly, the more important features of the invention in order that the detailed description thereof that follows may be better understood, and in order that the present contribution to the art may be better appreciated. There are additional features of the invention that will be described hereinafter and which will

15 form the subject matter of the claims appended hereto. In this respect, before explaining at least one embodiment

of the invention in detail, it is to be understood that the invention is not limited in its application to the details of constmction and to the arrangements of the components set

20 forth in the following description or illustrated in the draw­ings. The invention is capable of other embodiments and of being practiced and carried out in various ways. Also, it is to be understood that the phraseology and terminology employed herein are for the purpose of description and

25 should not be regarded as limiting. As such, those skilled in the art will appreciate that the

conception, upon which this disclosure is based, may readily be utilized as a basis for the designing of other structures, methods and systems for carrying out the several purposes

30 of the present invention. It is important, therefore, that the claims be regarded as including such equivalent constmc­tions insofar as they do not depart from the spirit and scope of the present invention.

35 Further, the purpose of the foregoing abstract is to enable the U.S. Patent and Trademark Office and the public generally, and especially the scientists, engineers and prac­titioners in the art who are not familiar with patent or legal terms or phraseology, to determine quickly from a cursory

40 inspection the nature and essence of the technical disclosure of the application. The abstract is neither intended to define the invention of the application, which is measured by the claims, nor is it intended to be limiting as to the scope of the invention in any way.

45 It is therefore an object of the present invention to provide a new magnetically augmented rotation system apparatus and method which has many of the advantages of the magnetic drive systems mentioned heretofore and many novel features that result in a new magnetically augmented

50 rotation system which is not anticipated, rendered obvious, suggested, or even implied by any of the prior art magnetic drive systems, either alone or in any combination thereof.

It is another object of the present invention to provide a new magnetically augmented rotation system which may be

55 easily and efficiently manufactured and marketed. be described subsequently in greater detail, is to provide a new magnetically augmented rotation system apparatus and method which has many of the advantages of the magnetic drive systems mentioned heretofore and many novel features that result in a new magnetically augmented rotation system which is not anticipated, rendered obvious, suggested, or 60

even implied by any of the prior art magnetic drive systems, either alone or in any combination thereof.

It is a further object of the present invention to provide a new magnetically augmented rotation system which is of a durable and reliable constmction.

An even further object of the present invention is to provide a new magnetically augmented rotation system which is susceptible of a low cost of manufacture with regard to both materials and labor, and which accordingly is then susceptible of low prices of sale to the consuming public, thereby making such magnetically augmented rota­tion system economically available to the buying public.

To attain this, the present invention generally comprises includes a wheel assembly having a central portion, a first magnetic assembly with a first magnetic polarity, and a 65

second magnetic assembly having a second magnetic polar-ity opposite the polarity of the first magnetic assembly; a

Still yet another object of the present invention is to provide a new magnetically augmented rotation system

US 6,356,000 Bl 3

which provides in the apparatuses and methods of the prior art some of the advantages thereof, while simultaneously overcoming some of the disadvantages normally associated therewith.

4 26. The first magnetic assembly 25 has a first magnetic polarity. The second magnetic assembly 26 has a magnetic polarity opposite the polarity of the first magnetic assembly 25.

Still another object of the present invention is to provide 5

a new magnetically augmented rotation system for improv­ing the efficiency of drive wheel and prime mover efficiency.

The bearing assembly 30 is used to for facilitate the rotation of the wheel assembly 20. The bearing assembly 30 being comprised of non-magnetic material.

Yet another object of the present invention is to provide a new magnetically augmented rotation system which includes includes a wheel assembly having a central portion, a first magnetic assembly with a first magnetic polarity, and a second magnetic assembly having a second magnetic polarity opposite the polarity of the first magnetic assembly;

The magnetic biasing assembly 40 is positioned such that a torquing force is applied to the wheel assembly 20 by an

10 interaction between the magnetic biasing assembly 40 and the first 25 and second magnetic assemblies 26.

The anti -reversing gear assembly 70 is coupled to the

a bearing assembly for facilitation the rotation of the wheel assembly and comprised of non-magnetic material; a mag- 15

netic biasing assembly positioned such that a torquing force

wheel assembly 20. The anti-reversing gear assembly 70 allows the magnetically augmented rotation system 10 to rotate in a 11rst direction while preventing the magnetically augmented rotation system 10 from rotating in a second

is applied to the wheel assembly by an interaction between the magnetic biasing assembly and the first and second magnetic assemblies; and an anti-reversing gear assembly coupled to the wheel assembly allowing the magnetically 20

augmented rotation system to rotate in a first direction while preventing it from rotating in a second direction.

direction.

In an embodiment the 11rst magnetic assembly 25 is a single magnetic disk coupled to the center portion 22 and is aligned such that a surface 27 of the 11rst magnetic assembly 25 has a first magnetic polarity. The second magnetic assembly 26 is a single magnetic disk coupled to the center portion 22 and is aligned such that a surface 28 of the second Still yet another object of the present invention is to

provide a new magnetically augmented rotation system that 25

improves the rotational efficiency of bicycles. magnetic assembly 26 has a second magnetic polarity.

In another embodiment the first magnetic assembly 25 is a plurality of magnets 75 positioned in a uniformly distrib­uted relationship around a 11rst side of the wheel assembly 20. Each one of the plurality of magnets 75 is positioned

Even still another object of the present invention is to provide a new magnetically augmented rotation system that improves the rotational efficiency of motor-generators.

These together with other objects of the invention, along with the various features of novelty which characterize the invention, are pointed out with particularity in the claims annexed to and forming a part of this disclosure. For a better understanding of the invention, its operating advantages and the specific objects attained by its uses, reference should be made to the accompanying drawings and descriptive matter in which there are illustrated preferred embodiments of the invention.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention will be better understood and objects other than those set forth above will become apparent when consideration is given to the following detailed description thereof. Such description makes reference to the annexed drawings wherein:

FIG. 1 is a schematic perspective view of a new mag­netically augmented rotation system according to the present invention.

FIG. 2 is a schematic front view of an embodiment of the present invention.

FIG. 3 is a schematic side view of multiple embodiments of the present invention in a cascade arrangement.

DESCRIPTION OF THE PREFERRED EMBODIMENT

With reference now to the drawings, and in particular to FIGS. 1 through 3 thereof, a new magnetically augmented rotation system embodying the principles and concepts of the present invention and generally designated by the ref­erence numeral 10 will be described.

As best illustrated in FIGS. 1 through 3, the magnetically augmented rotation system 10 generally comprises a wheel assembly 20, a bearing assembly 30, a magnetic biasing assembly 40, and an anti-reversing gear assembly 70.

The wheel assembly 20 includes a central portion 22, a first magnetic assembly 25, and a second magnetic assembly

30 such that a magnetic polarity of each one of the plurality of magnets 75 is aligned. The second magnetic assembly 26 is also a plurality of magnets 75 positioned in a uniformly distributed relationship around a second side of the wheel assembly 20. Each one of the plurality of magnets 75 is

35 positioned such that a magnetic polarity of each one of the plurality of magnets 75 is aligned and complimentary to the alignment of the first magnetic assembly 25.

40

An annular groove 23 is positioned around a circumfer-ence of the central portion 22 of the wheel assembly 20.

A drive belt 35 delivers a primary rotational force to the wheel assembly 20. The drive belt 35 is positioned in the annular groove 23. The drive belt 35 may be a belt or a chain.

45 The magnetic biasing assembly 40 further comprises a first linear magnet 41, a second linear magnet 50, and a third linear magnet 60.

The 11rst linear magnet 41 is positioned such that a longitudinal axis of the first linear magnet 41 is substantially

50 perpendicular with a plane which extends radially from a focus of the wheel assembly 20. The 11rst linear magnet 41 preferably is positioned in a spaced perpendicular relation­ship with a circumferential edge 21 of the wheel assembly 20.

55 The second linear magnet 50 is positioned such that a 11rst end 52 of the second linear magnet 50 abuts a first end 42 of the first linear magnet 41. The second linear magnet 50 preferably is positioned at an oblique angle such that the second linear magnet 50 rises upwardly towards the first

60 magnetic assembly 25 of the wheel assembly 20 and a second end 54 of the second linear magnet 50 is adjacent to a surface 27 of the first magnetic assembly 25.

The third linear magnet 60 is positioned such that a first end 62 of the third linear magnet 60 abuts a second end 44

65 of the 11rst linear magnet 41. The third linear magnet 60 preferably is positioned at an oblique angle such that the third linear magnet 60 rises upwardly towards the second

US 6,356,000 Bl 5

magnetic assembly 26 of the wheel assembly 20 and a second end 64 of the third linear magnet 60 is adjacent to a surface 28 of the second magnetic assembly 26.

The first linear magnet 41 is magnetically polarized such that the first end 42 of the first linear magnet 41 has a first 5

magnetic polarity and the second end 44 of the first linear magnet 41 has a second magnetic polarity. The second linear magnet 50 is magnetically polarized such that the first end 52 of the second linear magnet 50 includes a second mag­netic polarity and the second end 54 of the second linear 10

magnet 50 includes a first magnetic polarity. The third linear magnet 60 is magnetically polarized such that the first end 62 of the third linear magnet 60 includes a first magnetic polarity and the second end 64 of the third linear magnet 60 includes a second magnetic polarity. 15

The second ends 52,62 of the second 50 and third linear magnets 60 have magnetic polarities corresponding to the first 25 and second magnetic assemblies 26 respectively such that a repelling force occurs between the second linear magnet 50 and the first magnetic assembly 25 and between 20

the third linear magnet 60 and the second magnetic assembly 26.

A'i to a further discussion of the manner of usage and operation of the present invention, the same should be apparent from the above description. Accordingly, no further 25

discussion relating to the manner of usage and operation will be provided.

With respect to the above description then, it is to be realized that the optimum dimensional relationships for the

30 parts of the invention, to include variations in size, materials, shape, form, function and manner of operation, assembly and use, are deemed readily apparent and obvious to one skilled in the art, and all equivalent relationships to those illustrated in the drawings and described in the specification are intended to be encompassed by the present invention. 35

Therefore, the foregoing is considered as illustrative only of the principles of the invention. Further, since numerous modifications and changes will readily occur to those skilled in the art, it is not desired to limit the invention to the exact 40

construction and operation shown and described, and accordingly, all suitable modifications and equivalents may be resorted to, falling within the scope of the invention.

We claim: 1. A magnetically augmented rotation system comprising: 45

a wheel assembly having a central portion, a first mag-netic assembly, and a second magnetic assembly, said first magnetic assembly having a first magnetic polarity, said second magnetic assembly having a mag­netic polarity opposite the polarity of said first mag-

50 netic assembly;

a bearing assembly for facilitation the rotation of said wheel assembly, said bearing assembly being com­prised of non-magnetic material;

a magnetic biasing assembly positioned such that a torqu- 55

ing force is applied to said wheel assembly by an interaction between said magnetic biasing assembly and said first and second magnetic assemblies;

an anti-reversing gear assembly coupled to said wheel assembly, said anti-reversing gear assembly allowing 60

said magnetically augmented rotation system to rotate in a first direction while preventing said magnetically augmented rotation system from rotating in a second direction; and

wherein said magnetic biasing assembly further includes 65

a first linear magnet positioned such that a longitudinal axis of said first linear magnet being substantially

6 perpendicular with a plane extending radially from a focus of said wheel assembly, said linear magnet being positioned in a spaced perpendicular relation­ship with a circumferential edge of said wheel assembly;

a second linear magnet positioned such that a first end of said second linear magnet abuts a first end of said J1rst linear magnet, said second linear magnet being positioned at an oblique angle such that said second linear magnet rises upwardly and inwardly towards said first magnetic assembly of said wheel assembly and a second end of said second linear magnet is adjacent to a surface of said J1rst magnetic assembly;

a third linear magnet positioned such that a first end of said third linear magnet abuts a second end of said first linear magnet, said third linear magnet being positioned at an oblique angle such that said third linear magnet rises upwardly and inwardly towards said second magnetic assembly of said wheel assem­bly and a second end of said third linear magnet is adjacent to a surface of said second magnetic assem­bly.

2. The magnetically augmented rotation system of claim 1 wherein said wheel assembly further comprises:

an annular groove positioned around a circumference of said central portion of said wheel assembly;

a drive belt for delivering a primary rotational force to said wheel assembly, said drive belt being positioned in said annular groove.

3. The magnetically augmented rotation system of claim 1, wherein said magnetic biasing assembly further com­prises:

said first linear magnet being magnetically polarized such that said J1rst end of said first linear magnet has a first magnetic polarity and said second end of said first linear, magnet has a second magnetic polarity;

said second linear magnet being magnetically polarized such that said first end of said second linear magnet having a second magnetic polarity and said second end of said second linear magnet having a first magnetic polarity;

said third linear magnet being magnetically polarized such that said first end of said third linear magnet having a first magnetic polarity and said second end of said third linear magnet having a second magnetic polarity;

said second ends of said second and third linear magnets having magnetic polarities corresponding to said first and second magnetic assemblies respectively such that a repelling force occurs between said second linear magnet and said first magnetic assembly and between said third linear magnet and said second magnetic assembly.

4. The magnetically augmented rotation system of claim 1 wherein said wheel assembly further comprises:

said first magnetic assembly being a plurality of magnets positioned in a uniformly distributed relationship around a first side of said wheel assembly, each one of said plurality of magnets being positioned such that a magnetic polarity of each one of said plurality of magnets is aligned;

said second magnetic assembly being a plurality of mag­nets positioned in a uniformly distributed relationship around a second side of said wheel assembly, each one of said plurality of magnets being positioned such that a magnetic polarity of each one of said plurality of

US 6,356,000 Bl 7

magnets is aligned and complimentary to the alignment of said J1rst magnetic assembly.

5. The magnetically augmented rotation system of claim 4, further comprising:

an annular groove positioned around a circumference of 5

said central portion of said wheel assembly; a drive belt for delivering a primary rotational force to

said wheel assembly, said drive belt being positioned in said annular groove;

wherein said magnetic biasing assembly further com- 10

prises: said J1rst linear magnet being magnetically polarized

such that said J1rst end of said J1rst linear magnet has a J1rst magnetic polarity and said second end of said J1rst linear magnet has a second magnetic polarity; 15

said second linear magnet being magnetically polarized such that said J1rst end of said second linear magnet having a second magnetic polarity and said second end of said second linear magnet having a first magnetic polarity; 20

said third linear magnet being magnetically polarized such that said J1rst end of said third linear magnet having a J1rst magnetic polarity and said second end of said third linear magnet having a second magnetic polarity; 25

said second ends of said second and third linear mag­nets having magnetic polarities corresponding to said J1rst and second magnetic assemblies respec­tively such that a repelling force occurs between said second linear magnet and said J1rst magnetic assem- 30

bly and between said third linear magnet and said second magnetic assembly.

6. The magnetically augmented rotation system of claim 1, wherein said wheel assembly further comprises:

said J1rst magnetic assembly being a single magnetic disk 35

coupled to said center portion and being aligned such that a surface of said J1rst magnetic assembly has a J1rst magnetic polarity;

said second magnetic assembly being a single magnetic disk coupled to said center portion and being aligned 40

such that a surface of said second magnetic assembly has a second magnetic polarity.

7. The magnetically augmented rotation system of claim 6, further comprising:

an annular groove positioned around a circumference of 45

said central portion of said wheel assembly; a drive belt for delivering a primary rotational force to

said wheel assembly, said drive belt being positioned in said annular groove;

wherein said magnetic biasing assembly further com- 50

prises: said J1rst linear magnet being magnetically polarized

such that said J1rst end of said first linear magnet has a J1rst magnetic polarity and said second end of said J1rst linear magnet has a second magnetic polarity; 55

said second linear magnet being magnetically polarized such that said J1rst end of said second linear magnet having a second magnetic polarity and said second end of said second linear magnet having a J1rst magnetic polarity; 60

said third linear magnet being magnetically polarized such that said J1rst end of said third linear magnet having a J1rst magnetic polarity and said second end of said third linear magnet having a second magnetic polarity; 65

said second ends of said second and third linear mag­nets having magnetic polarities corresponding to

8 said J1rst and second magnetic assemblies respec­tively such that a repelling force occurs between said second linear magnet and said J1rst magnetic assem­bly and between said third linear magnet and said second magnetic assembly.

8. A magnetically augmented rotation system comprising: a wheel assembly having a central portion, a J1rst mag­

netic assembly, and a second magnetic assembly, said J1rst magnetic assembly having a J1rst magnetic polarity, said second magnetic assembly having a mag­netic polarity opposite the polarity of said first mag­netic assembly;

a bearing assembly for facilitation the rotation of said wheel assembly, said bearing assembly being com­prised of non-magnetic material;

a magnetic biasing assembly positioned such that a torqu­ing force is applied to said wheel assembly by an interaction between said magnetic biasing assembly and said first and second magnetic assemblies;

an anti-reversing gear assembly coupled to said wheel assembly, said anti-reversing gear assembly allowing said magnetically augmented rotation system to rotate in a J1rst direction while preventing said magnetically augmented rotation system from rotating in a second direction;

said first magnetic assembly being a single magnetic disk coupled to said center portion and being aligned such that a surface of said first magnetic assembly has a J1rst magnetic polarity;

said second magnetic assembly being a single magnetic disk coupled to said center portion and being aligned such that a surface of said second magnetic assembly has a second magnetic polarity;

an annular groove positioned around a circumference of said central portion of said wheel assembly;

a drive belt for delivering a primary rotational force to said wheel assembly, said drive belt being positioned in said annular groove;

said magnetic biasing assembly further comprises: a J1rst linear magnet positioned such that a longitudinal

axis of said J1rst linear magnet being substantially perpendicular with a plane extending radially from a focus of said wheel assembly, said linear magnet being positioned in a spaced perpendicular relation­ship with a circumferential edge of said wheel assembly;

a second linear magnet positioned such that a J1rst end of said second linear magnet abuts a first end of said J1rst linear magnet, said second linear magnet being positioned at an oblique angle such that said second linear magnet rises upwardly and inwardly towards said J1rst magnetic assembly of said wheel assembly and a second end of said second linear magnet is adjacent to a surface of said J1rst magnetic assembly;

a third linear magnet positioned such that a J1rst end of said third linear magnet abuts a second end of said J1rst linear magnet, said third linear magnet being posi tioned at an oblique angle such that said third linear magnet rises upwardly and inwardly towards said second magnetic assembly of said wheel assem­bly and a second end of said third linear magnet is adjacent to a surface of said second magnetic assem­bly;

wherein said magnetic biasing assembly further com­prises: said J1rst linear magnet being magnetically polarized

such that said J1rst end of said first linear magnet

US 6,356,000 Bl 9

has a first magnetic polarity and said second end of said first linear magnet has a second magnetic polarity;

said second linear magnet being magnetically polar­ized such that said first end of said second linear 5

magnet having a second magnetic polarity and said second end of said second linear magnet having a J1rst magnetic polarity;

said third linear magnet being magnetically polar­ized such that said J1rst end of said third linear 10

magnet having a J1rst magnetic polarity and said

10 second end of said third linear magnet having a second magnetic polarity; and

said second ends of said second and third linear magnets having magnetic polarities corresponding to said J1rst and second magnetic assemblies respectively such that a repelling force occurs between said second linear magnet and said J1rst magnetic assembly and between said third linear magnet and said second magnetic assembly.

* * * * *

(12) United States Patent Blakesley

(54) CONTROL DEVICE USING MAGNETIC FORCE TO CREATE FORCE VECTOR TO CONTROL AN OBJECT

(76) Inventor: Clarence S. Blakesley, 1141 E. Brian Rd., Pahrump, NV (US) 89048

( *) Notice: Subject to any disclaimer, the term of this patent is extended or adjusted under 35 U.S.c. 154(b) by 0 days.

(21) Appl. No.: 09/875,193

(22) Filed: Jun. 7, 2001

(51) Int. cl? ................................................ H02K 21/12 (52) U.S. CI ..................... 310/156.08; 310/46; 310/103;

310/112 (58) Field of Search ....................... 310/156.08, 156.12,

310/156.13, 156.28, 156.29, 156.53, 46, 36, 103, 112, 108, 162

(56) References Cited

U.S. PATENT DOCUMENTS

3,790,833 A * 2/1974 Hasebe ....................... 310/162 RE29,165 E * 3/1977 Bode ........................... 310/46 4,169,983 A * 10/1979 Felder ......................... 310/46 4,751,486 A * 6/1988 Minato ....................... 335/272

110A

140

111111 1111111111111111111111111111111111111111111111111111111111111 US006396180Bl

(10) Patent No.: US 6,396,180 Bl May 28, 2002 (45) Date of Patent:

4,877,983 A * 10/1989 Johnson ....................... 310/12 5,289,071 A * 2/1994 Taghezout .................. 310/254 5,569,967 A * 10/1996 Rode .......................... 310/103 6,084,322 A * 7/2000 Rounds ....................... 310/46

* cited by examiner

Primary Examiner--Nestor Ramirez Assistant Examiner-Thanh Lam

(57) ABSTRACT

A control device for an object includes a J1rst wheel and a second wheel that rotate in opposite directions on a shaft affixed to a frame. The J1rst and second wheels have open­ings to accept magnets that are free to slide up and down in the openings. As the wheels rotate, the magnets are urged outwards due to centrifugal force. The wheels have titanium sleeves J1tted around the outer surfaces of the wheels, which have openings smaller in size than the openings of the wheels, so as to maintain the magnets within the openings even as the wheels rotate. Solenoid stations are provided around the wheels, and as a result of magnetic pulses provided from at least one of the solenoid stations, in synchronism with rotation of the wheels, a magnet is urged inwards to a center of the wheel in which it is disposed, to thereby result in a force vector that causes movement of the frame to thereby control the object.

6 Claims, 8 Drawing Sheets

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FIGURE 1

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US 6,396,180 B1 1 2

FIG. 5 is a side view of one of the wheels according to the first embodiment of the invention;

CONTROL DEVICE USING MAGNETIC FORCE TO CREATE FORCE VECTOR TO

CONTROL AN OBJECT

BACKGROUND OF THE INVENTION

FIG. 6 is a front on view of a wheel without the titanium sleeve fitted thereon, according to the first embodiment of

5 the invention;

A. Field of the Invention

The invention relates generally to a control device for controlling and/or for providing propulsion for various devices, such as for controlling an orbit of a satellite in space 10

or for controlling a steering of a vehicle or for providing propulsion for the vehicle.

B. Description of the Related Art

Conventional control devices, such as gyroscopes or 15

steering mechanisms, require precise control to perform their functions. Also, conventional propulsion devices are complex and fairly costly.

There is a need to provide a control device that is fairly 20

simple to construct and operate.

There is also a need to provide a propulsion device that is fairly simple to construct and operate.

SUMMARY OF THE INVENTION 25

The present invention is directed to a control device, which includes a motor that provides power. The motor is coupled to a first wheel and a second wheel by a pinion/gear arrangement, whereby the first wheel is made to rotate in a first direction (e.g., clockwise) while the second wheel is 30

made to rotate in a second direction (e.g., counterclockwise). The first and second wheels are coupled to the motor via first and second ring gears. The first and second wheels and first and second ring gears are coupled to a shaft, which does not rotate. As the wheels rotate in opposite directions, magnetic 35

pulses are provided from at least one location, so as to provide a magnetic force to the wheels at the same time. Each of the wheels has magnets that are 11tted into various locations within the wheels, whereby the magnets are capable of sliding up and down within those locations. As 40

the wheels spin, the magnets are urged outwards due to centrifugal force. The magnetic pulses provided at precise instants in time provide a same-polarity force to the magnets, forcing them inwards to somewhat counteract the centrifugal force due to the spinning of the wheels. This 45

creates an imbalance in the wheels, whereby that imbalance can be used to provide control, such as for repositioning a satellite that has drifted from its proper orbit.

The present invention is also directed to a propulsion device having elements as described above. 50

BRIEF DESCRIPTION OF THE DRAWINGS

The foregoing advantages and features of the invention will become apparent upon reference to the following detailed description and the accompanying drawings, of 55

which: FIG. 1 is a front view of a control device according to a

first embodiment of the invention;

FIG. 2 is a side view of the control device (as viewed from 60

a pulsing station) according to the first embodiment of the invention;

FIG. 7 is a diagram showing the magnetic repelling force provided by way of a pulsing station, according to the first embodiment of the invention;

FIG. 8 is a diagram showing a ceramic magnet that may be utilized in a device according to the first embodiment of the invention;

FIG. 9 is a diagram showing the force provided by the device according to the first embodiment of the invention;

FIG. 10 is a side view of one of the wheels that is included in a control device according to a second embodiment of the invention; and

FIG. 11 is a front on view of a solenoid station according to a fourth embodiment of the invention.

DETAILED DESCRIPTION OF SPECIFIC EMBODIMENTS

The present invention will be described in detail below, with reference to the accompanying figures.

FIG. 1 shows a front view of a control device 100 for controlling an object, according to the invention. The device may also be utilized for propulsion or movement of an object from one location to another location. In FIG. 1, there is provided a motor 105, which is preferably an electric motor that may be powered by a generator, for example. The motor 105 is controlled by a computer, not shown. Such a com­puter may be a conventional personal computer, such as one powered by an Intel Pentium™ IV chip or anAMK7™ chip, for example. The motor 105 may alternatively be powered by batteries, or by AC.

The motor 105 is mounted onto a frame 110, which is made of aluminum alloy in the first embodiment, but which may be made out of any suitable material for holding the various elements making up the control device 100.

Also shown in FIG. 1 is a 11rst pulsing (or solenoid) station 120 and a second pulsing (or solenoid) station 130, which provide magnetic pulses at precise instants in time, under control of the computer. The two pUlsing stations 120, 130 are positioned 180 degrees apart from each other on a top surface of a bottom plate of the frame 110. The frame 110 also includes two vertical portions 110A, 11013, which extend upwards from the top surface of the bottom plate 110C of the frame 110 (see FIG. 2).

A first wheel 140 is shown in FIG. 1, whereby a second wheel (150, see FIG. 2) is hidden from view in FIG. 1, since it is disposed directly behind the first wheel 140 (with respect to the front view of FIG. 1). The two wheels 140, 150 rotate about a shaft 210.

FIG. 2 shows a side view of the control device 100 according to a 11rst embodiment of the invention, whereby the shaft 210 is shown mounted to the frame 110. The two wheels 140, 150 can be seen in FIG. 2, whereby one wheel is caused to rotate in a first direction, e.g., clockwise, while the other wheel is caused to rotate in a second direction, e.g., counterclockwise. The two wheels 140, 150 rotate at the same speed, e.g., 1000 revolutions per minute (rpm), or fixed a value between 500 rpm and 10,000 rpm. FIG. 3 is a view of the elements coupled to the shaft of the

control device according to the first embodiment of the invention;

FIG. 4 is a front on view of a titanium sleeve 11tted onto a wheel, according to the first embodiment of the invention;

The wheels 140,150 rotate due to power supplied by way 65 of the motor 105. The motor 105 is coupled to the two

wheels 140, 150 by a pinion and gear assembly 235, as seen in FIG. 2. FIG. 3 shows the various elements coupled to the

US 6,396,180 B1 3 4

shaft 210. The first wheel 140 is coupled to a pinion (part of the pinion and gear assembly 235) by way of a first ring gear 310, which causes the first wheel 140 to rotate in a first direction (due to the rotational force imparted on the first ring gear 310 by the pinion). The second wheel 150 is 5

coupled to the pinion by way of a second ring gear 320, which causes the second wheel 150 to rotate in a second direction opposite the J1rst direction. Alternatively, hypoid gears or face gears may be utilized instead of ring gears, for translating the power from the motor 105 to cause rotation 10

of the J1rst and second wheels 140, 150. The pinion and the gears 310, 320 should preferably have about 4 to 6 thou­sandths of an inch play, to provide a good J1t between these

the shaft 210. A hole 520 is provided in the middle of the wheel 140 (giving it a somewhat donut shape), which is a region by which the wheel 140 is fitted onto the shaft 210.

Each wheel 140, 150 is preferably made out of aluminum alloy. Alternatively, the wheels 140, 150 may be made out of a hard plastic composition. The size of the wheels 140, 150 may vary, whereby the size of the wheels 140, 150 is determined based on the intended use of the control device 100 and the amount of force required by the control device 100 in order to control or to propel an object (which is coupled to the control device 100 so that the control force is translated to the object so as to control the object). For example, a wheel of a size of from 1 inch up to 12 inches or more may be contemplated for providing attitude control of

elements.

The shaft 210 is coupled to the frame 110 by way of nuts 350, 360, as seen best in FIGS. 2 and 3. The nuts 350, 360 rigidly couple the shaft 210 to the frame 110, whereby the wheels 140, 150 rotate on the shaft 210 and cause little if any vibration as they rotate. To accomplish this, the wheels 140, 150 are symmetrical in shape (center of gravity at the center of the wheels 140, 150), thereby providing a balanced set of wheels 140, 150 that rotate on the shaft 210.

Also shown in FIG. 3 are J1rst and second spacers 370, 380, which are provided on the shaft 210 and which are coupled to outer surfaces of the two wheels 140,150. A third spacer 385 is also provided between the two ring 310, 320, at a location where the pinion couples (by way of a tooth­to-tooth engagement) to the ring gears 310, 320. FIG. 3 also shows mount gaps 392, 394 which are regions on the shaft 210 where the vertical portions 110A 11013 of the frame 11 0 are disposed when the shaft 210 is J1tted onto the frame 210, as seen best in FIG. 2. In the present invention, a hole is provided on each of the vertical portions 11A, 11013 of the frame 110, which is sized to accept the shaft 210 when the shaft 210 is J1Ued therein. Tbe shaft 210 is fitted through the holes on the two vertical portions 110A, 11013 of the frame 110 and is secured to the frame 110 by way of the nuts 350, 360.

In the present invention, each of the elements that rotate on the shaft 210 have bearings, which allow those elements to turn or rotate relative to the shaft 210 on which they are disposed. Preferably, the bearings are made out of a very hard material, such as by utilizing a TACO process to make the bearing of sufficient hardness. Other processes for form­ing bearings made of hard material in the present invention may be utilized, as are known to those skilled in the art.

The shaft 210 is preferably made out of steel, to provide strong support for the control device 100 according to the present invention. Other hard metal compositions may alter­natively be utilized for forming the shaft 210.

An important feature of the invention is the structure of the wheels 140, 150. FIGS. 4, 5 and 6 show various views of the wheels 140, 150, which make up part of the wheel/ sleeve conJ1guration 610. The wheel/sleeve conJ1guration 610 is included in the control device 100 according to the invention so as to provide control of an object, such as control of a satellite or control of an airplane or a vehicle (e.g., steering control). Alternatively or additionally, the control device 100 may be operable as a propulsion device for providing movement of an object. The wheels 140, 150 are preferably made out of an aluminum alloy.

Referring now to FIG. 5, one wheel 140 of the control device 100 is shown, whereby the other wheel 150 of the control device 100 has a similar construction. The wheel 140 has a ring gear portion 510 (with not shown teeth that engage teeth on the pinion), which allows the wheel 140 to rotate on

15 a satellite. In the J1rst embodiment, each wheel 140, 150 has four cylindrical regions 525A, 525B, 525C, 525D provided at 90 degree offset locations, as seen best in FIG. 5. These regions 525A, 52513, 525C, 525D are locations where four cylindrically-shaped magnets are respectively disposed.

20 FIG. 8 shows a magnet 800 that is sized so that it can be slidably disposed within one of the regions 525A, 52513, 525C, 525D of the wheels 140, 150. Preferably, the fit is such that there is some amount of play from allowing the magnets 800 to slide up and down within the regions 525A,

25 52513, 525C, 525D with little if any friction being imparted on the magnets 800 to hamper their movement. Since two wheels 140, 150 are utilized in the J1rst embodiment of the present invention, eight magnets are used-four per wheel. Preferably, the magnets 800 are ceramic magnets, but other

30 types of magnets that are made of a hard material may be utilized while remaining within the scope of the invention as described herein. A hard material magnet is preferably utilized so that it will not wear down due to its sliding up and down within the regions 525A, 52513, 525C, 525D. This

35 allows for a long-lasting control device 100. The magnets 800 are free to slide up and down within the

regions 525A, 52513, 525C, 525D, similar to how a piston moves up and down in a cylinder of an internal combustion engine. The regions 525A, 52513, 525C, 525D extend all the

40 way to the outer peripheral surface of the wheels 140, 150. FIG. 6 shows three of the holes 535A, 53513, 535]) (one hole 535C is not shown since it is blocked from view), which are provided on sleeves 833 (to be described in more detail below). The holes 535A, 53513, 535C, 535]) are sized to be

45 smaller in diameter (e.g., 5% to 50% smaller) than the diameter of the regions 525A, 52513, 525C, 525D and thus smaller than the size of the magnets 800 that are disposed within the regions 525A, 52513, 525C, 525D.

The regions 525A, 52513, 525C, 525D also preferably 50 have titanium or brass sidewalls, which allow the magnets

800 to readily slide up and down within the regions 525A, 52513, 525C, 525D, while not providing any magnetic J1eld. The sidewalls are preferably from 5 to 100 thousandths of an inch in thickness. FIG. 5 shows sidewalls 505 for regions

55 525A, whereby the other regions 52513, 525C, 525D also preferably have titanium or brass sidewalls.

Once the magnets 800 are inserted into the regions 525A, 52513, 525C, 525D of the wheels 140, 150, a sleeve 833 is then fitted onto the outer surface of each of the wheels 140,

60 150, whereby two sleeves 833 as required (one for each wheel). Each sleeve 833 is made out of a hard metal composition, such as titanium, brass or graphite (similar to the composition of the sidewalls 505). The sleeve 833 is formed as a circular band, with a narrow thickness (e.g., Y4

65 to Y2 inch thickness). The sleeve 833 has four holes 535A, 535B, 535C, 535D

provided 90 degrees apart from each other, so as to be

US 6,396,180 B1 5 6

co-located with the cylindrical regions 525A, 525B, 525C, 525D of the wheels 140, 150. FIG. 4 shows a side view of the sleeve 833, and FIG. 6 shows a side view of the sleeve 833 fitted onto the wheel 140. Since the holes 535A, 535B, 535C, 535D of the sleeve 833 are sized to be smaller than 5

the diameter of the magnets 800, the magnets 800 are prevented from exiting from their respective cylindrical regions 525A, 525B, 525C, 5251) in which they are disposed when the wheels 140, 150 rotate. The centrifugal force caused by wheel spinning results in a force vector that urges 10

the magnets 140, 150 outwards to thereby want to exit out

magnets 800, the magnets are maintained within the regions 525A, 525B, 525C, 525D.

When the wheels 140, 150 are rotating and with no pulses being output by the pulsing stations 120, 130, an equilibrium state is achieved, whereby each of the magnets 800 (and their corresponding masses in each wheel 140, 150) move outwards, but in a symmetrical manner (since there are four magnets 800 spaced 90 degrees apart within each of the wheels 140, 150).

In order to provide control of an object, pulses are provided (under control of the computer) to one of the pulsing stations 120, 130, in order to create a desired force vector. For example, magnetic pulses may be provided at the left side station 120 shown in FIG. 1, whereby those pulses

of the regions 525A, 525B, 525C, 525D of the wheels 140, 150.

The titanium or brass sidewalls 505 disposed on the regions 525A, 525B, 525C, 525D of the wheels 140, 1500 are preferably micro-finished, to allow the magnets 800 to move up and down within those regions 525A, 525B, 525C, 5251) with little if any friction counteracting that movement. With the magnets 800 in place within the regions 525A, 525B, 525C, 525D, the sleeves 833 are fitted around the wheels 140, 150, preferably by a press fitting process. Two sleeves are required-one per wheel.

The band-shaped sleeves 833 are sized to be slightly larger in size than the diameter of the wheels 140, 150 (e.g., 1 to 5 thousandths of an inch larger). When the sleeves 833 are fitted around the wheels 140, 150, they are then subjected to heat (e.g., 800 to 1000 degrees C.), and then allowed to cool (to room temperature for 1 to 4 hours), to thereby obtain

15 are of a particular polarity (e.g., that create aN-polarized magnetic field at the pulsing station 120) This results in a force vector urging the magnet 800 facing the solenoid station 120 to move away from the solenoid station 120, since the surface of the magnet 800 facing the solenoid

20 station 120 is of the same polarity as the pulse emitted by the solenoid station 120. The repelling force provided by the N-N magnetic fields is made so as to be slightly stronger than the centrifugal force that is acting to urge the magnets 800 outwards. The centrifugal force is proportional to the

25 rotational rate of the wheels 140, 150, and the magnetic field strength output by the pulses of the pulsing station 120 is determined accordingly. One of ordinary skill in the art can readily determine the necessary magnetic field force needed

30 to accomplish this.

A'isume that the magnets 800 are inserted into the regions 525A, 525B, 525C, 525D of the wheels 140, 150 such that the North pole surface of each of the magnets 800 is facing outwards, and whereby the South pole surface of each of the

a press fit of the sleeve 833 around each wheel 140, 150. That way, the sleeves 833 are firmly fitted in place around the wheels 140, 150, whereby they are placed such that the four holes 535A, 535B, 535C, 535D of the sleeves 833 and the cylindrical regions 525A, 525B, 525C, 525D of the wheels 140, 150 are aligned (see FIG. 5, for example, showing such an alignment). 35

magnets 800 is facing the shaft 210. Now, assume that the wheels 140, 150 are each rotating at a rate of 1000 rpm. In that case, pulses are applied to the left-side pulsing station In the present invention, one wheel 140 rotates clockwise

and one wheel 150 rotates counterclockwise. The wheels 140, 150 rotate in synchronism at the same frequency and in-phase, thereby forming a stable control device 100. The oppositely rotating wheels 140, 150 provides for a stable control device 100, while also allowing for the control device 100 to precisely control an object such as a satellite or a steering mechanism for a motor vehicle. The control device 100 can also be used to propel an object.

Referring back to FIGS. 1 and 2, the control device 100 of the present invention also includes two pulsing or sole­noid stations 120, 130, which are disposed 180 degrees apart from each other on the bottom portion HOC of the frame 100 of the control device 100. The wheels 140, 150 are posi­tioned between the pulsing stations 120, 130. Each pulsing station 120, 130 includes a coil (wire windings) and is capable of outputting pulses that have a magnetic field associated with them. The pulses are outputted at a con­trolled rate, based on control signals provided to the pulsing stations 120, 130 from the computer. Ibe computer also controls the rpm of the motor that is providing the power to cause the wheels 140, 150 to rotate at a precise rate.

120 (with respect to the front view of FIG. 1) at a rate of 4000 rpm, in synchronism with the rotation of the wheels

40 140, 150. As a result, as each pulse is output from the left-side pulsing station 120, that pulse is output at the same time a magnet 800 passes across the left-side pulsing station 120 (e.g., the left-side pulsing station 120 directly faces one of the cylindrical regions 525A, 525B, 525C, 525D of the

45 wheels 140, 150 as shown in FIG. 4 at the instant the pulse is output). Each pulse is output to create a magnetic field having the same polarity as the polarity of the surface of the magnet 800 facing the left-side pulsing station 120. This creates a repelling force between the pUlsing station 120 and

50 the magnet 800. Since the pulsing station 120 is fixed in position on the frame 110, and since the magnet 800 is not fixed but instead can slide within the cylindrical region 525A, the N-N repelling force causes the magnet 800 to move away from the pulsing station 120 and thereby move

55 further in the cylindrical region 525A.

A'S the wheels 140, 150 rotate, the respective magnets 800 within the wheels 140, 150 are urged outwards to the 60

outermost ends of their cylindrical openings 525A, 525B, 525C, 525D due to the centrifugal force caused by the rotation of the wheels 140,150. This causes the magnets 800

Alternatively, if the magnets 800 are disposed within the cylindrical regions 525A, 525B, 525C, 525D such that their surface facing the pulsing stations 120, 130 has South (S) polarity, the pulses emitted by the pulsing stations would create a S polarity magnetic field to achieve the desired repelling force.

As a result of the repelling force, the weight distribution of the wheels 140, 150 with respect to the shaft 210 is no longer symmetric, but is changed such that the weight distribution is more towards the right side of the wheels 140, 150 than to the left side of the wheels 140, 150. This occurs because one of the four magnets 800 on each of the wheels

to impact an inner surface of the sleeves 833 fitted around the wheels, 140, 150. However, since the sleeves 833 are 65

press HUed onto the wheels 140, 150, and since the holes 535A, 535B, 535C, 535D are smaller than the size of the

US 6,396,180 B1 7 8

The magnets 910 are Hxed in position at one end of each of the regions 525A, 525B, 525C, 525D. The magnets 910 have an outer-facing surface with a polarity of opposite polarity to a nearest-facing surface of the magnet 800. This

140, 150 that faces the left-side solenoid 120 has been pushed inwards (towards the shaft 210), while the other three magnets 800 on each of the wheels 140, 150 are at the outermost portions of their respective regions 525A, 525B, 525C, 525D within the wheels 140, 150 (and thereby pushing against the sleeve 833) due to the centrifugal force caused by the rotation of the wheels 140, 150. FIG. 7 shows an arrow 830 which denotes the direction that the magnet 800 moves due to the N-N repelling force.

5 results in an attraction force that helps pull the magnets 800 towards the center of the wheels 140, 150, thereby providing better balance of the wheels 140, 150 as they rotate.

FIG. 9 shows a phantom force rotation path 935 that is 10

obtained due to the North-polarity pulse being incident on the North-polarity surface of the magnet 800, which pushes the magnet 800 away from the pulsing station 120. Since the wheels 140, 150 are rotating on the shaft 210 that is afi1xed

The magnets 910 are locked in place within the regions 525A, 52513, 525C, 5251) by a lockdown element 920, which is preferably made of brass or titanium. The North­South facing adjacent surfaces of the magnets 800, 910 results in a force vector that urges the magnets 800 towards the magnets 910. As the wheels 140, 150 rotate, the cen-trifugal force causes the magnets 800 to want to move away from the magnets 910, and when the pulses from one of the solenoid stations 120, 130 are incident on the magnets 800, the repelling force that results pushes the magnets 800 back towards the magnets 910.

FIG. 10 also shows the sleeves 833 that are Htted around

to the frame 110, this force is translated to the frame 110 to 15

thereby cause movement of the frame 110 (in a direction in which the magnet 800 is repelled), and thus to cause movement of an object coupled to the frame 110 by an amount shown by the dilTerence between the wheel position 140 shown in FIG. 9 and the phantom force rotational path 935. 20 each of the wheels 140, 150, to prevent the magnets 800

from exiting the regions 525A, 525B, 525C, 525D. Also shown in FIG. 10 is a core of the solenoid station 120 that is used to create a magnetic Held, which is imparted onto the

Since the wheel 140 rotates around the shaft 210, the shaft 210 is also urged in the same direction. Since the shaft 210 is Htted onto the frame 110 by way of the vertical portions 110A, 110B of the frame 110, the frame 110 is also urged in 25

that same direction. A weight distribution change occurs on each wheel 140,

150, by way of the pulsing station 120 providing pulses at precise instants in time to thereby affect the magnets 800 disposed in each wheel 140, 150. This causes the frame 110, 30

which may be coupled to a gimbal of a satellite, for example, to move in a precise amount and in a precise direction in order to correct an orbit drift of a satellite that is orbi ting the Earth. In the present invention, the magnets 800 have a mass and the pulsing stations 120, 130 emit a magnetic Held of an 35

amount to cause the magnets 800 to move a few tenths of an inch within the regions 525A, 525B, 525C, 525D. One of ordinary skill in the art would readily be able to determine the needed magnetic Held strength to accomplish this amount of movement, based on the mass of the magnets 800 40

being moved and the rotational rate of the wheels 140, 150 (e.g., 500 to 1000 gauss magnetic Held for 5 ounce magnets 800 that are disposed in wheels 140, 150 rotating at 1500 rpm).

pulses output by the solenoid station 120. In an alternative configuration, the wheels 140, 150 rotate

co-planar with the top surface of the bottom portion 110C of the frame 110 (as opposed to rotating along a plane perpen­dicular with respect to the bottom portion 110C of the frame 100), whereby four pulsing stations ( or more) can be pro­vided around the wheels 140, 150. This allows for control of an object along any radial x,y radial direction, and not just in a forward and backwards direction between the two pulsing stations 120, 130 as in the first embodiment described earlier.

In a third embodiment, the pulsing stations 120, 130 are turned on to emit a continuous magnetic Held as soon as the control device 100 is activated. This results in an equilib­rium state with respect to the wheels 140, 150, since the repelling forces caused by the pulsing stations 120, 130 being on at the same time counteract each other. That is, a magnet 800 on one side of the wheels 140, 150 is pushed inwards from pulsing station 120, while a magnet on the other side of the wheels 140, 150 is also pushed inwards

In the example provided above, the computer controls both the rotation speed of the wheels 140, 150, as well as the pulsing rate and magnetic strength output by the pulsing stations 120, 130. Only one pulsing station 120, 130 at a time would output pulses, to cause control (or movement) of an object in one direction.

45 from pulsing station 130. To cause movement or control of an object in a particular

direction in the third embodiment, one of the pulsing stations 120, 130 is turned off, which results in movement of the frame 110 in the direction of the pulsing station that has been

50 turned off. Due to the use of magnetic force caused by pulsing, there

is no mass (e.g., no piston or other object) directly provided to the wheels 140, 150. In the present invention, by utilizing a magnetic repelling force, a force vector of a particular strength and direction is provided by way of the control 55

device 100 of the present invention. This force vector can be used to control an object, or to propel an object.

FIG. 10 shows a second embodiment of the invention, in which another magnet 910 is disposed within each of the cylindrical regions 525A, 525B, 525C, 525D of the wheels 60

140,150. Unlike the magnet 800, the magnet 910 does not move within the regions 525A, 525B, 525C, 525D, and can be any type of magnet (since wearing out of the magnet is not an issue due to the magnet 910 does not occur due to the magnet 910 being Hxed in position within the bottom 65

portions of the regions 525A, 52513, 525C, 525D of the wheels 140, 150).

Furthermore, instead of turning off a pulsing station to achieve a desired force vector, a pulsing station may be moved away from the wheels 140, 150, such as by pivotably mounting the pulsing stations to the frame 100. With such a pivotable coupling, a pulsing station may be pivoted away from the wheels 140, 150, to thereby remove the repelling force on the wheels 140, 150 for that pulsing station, while maintaining the magnetic field of the pivoted pulsing station in an ON state.

FIG. 11 shows a solenoid station 1100 that is included in a control device (or propulsion device) according to a fourth embodiment of the invention. The solenoid station 1100 according to the fourth embodiment includes a magnetic ring 1120 that surrounds a solenoid 1110. The solenoid 1110 has windings provided around it, similar to the solenoids used in the solenoid stations of the first, second and third embodiments. The solenoid station 1100 according to the

US 6,396,180 B1 9

fourth embodiment requires less power (less current required) to operate than the solenoid stations of the first and second embodiments. In the fourth embodiment, both the magnetic ring 1120 and the solenoid 1110 provide a mag­netic field, which is used to repel magnets 800 disposed 5

within wheels 140, 150 that are rotating adjacent to the solenoid station. The solenoid station 1100 may be used instead of the solenoid stations 120, 130 of the first, second and third embodiments, to thereby provide a control device that requires less power to operate. 10

10 openings of the first and second wheels, to thereby create a weight distribution change in the first and second wheels that is used to provide a force vector that is used to control the object.

2. The control device according to claim 1, wherein the frame has a bottom surface and two vertical surfaces with at least one opening on each of the two vertical surfaces,

the control device further comprising: at least two nuts for coupling the shaft to the frame

when the shaft is fitted within the openings of the frame.

Also, while the present invention has been described as having four magnets per wheel, other numbers of magnets per wheel may be contemplated while remaining within the scope of the invention, such as having as little as two magnets (and corresponding cylindrical regions) per wheel to as much as 16 magnets per wheel (or perhaps more, depending on the device to be controlled and the degree of preciseness of the control needed). The only requirement is that the computer has to provide the proper control signals to the solenoid stations in order to provide the magnetic pulses at the precise instants in time to magnets disposed within the rotating wheels.

3. The control device according to claim 2, wherein the frame moves in a direction of the second pulsing station as a result of the weight distribution change of the first and

15 second wheels, to thereby providing the force vector to the object to be controlled.

4. The control device according to claim 2, wherein the first pulsing station outputs a second pulse at a second instant in time, which creates a magnetic field at the first

20 pulsing station of the same polarity as the polarity of the nearest surface of the second and fourth magnets.

For example, if only back-forth control or propulsion is needed, then only two oppositely-positioned solenoid sta­tions would be required. Also, in that case, wheels having 25

only two magnets (respectively disposed in two cylindrical regions) could be utilized.

Thus, a control device and a propulsion device has been described according to the present invention. Many modi- 30

fications and variations may be made to the techniques and structures described and illustrated herein without departing from the spirit and scope of the invention. Accordingly, it should be understood that the methods and apparatuses described herein are illustrative only and are not limiting

35 upon the scope of the invention. What is claimed is: 1. A control device for controlling an object, comprising: a frame; a shaft mounted to the frame; a first wheel that rotates around the shaft in a first

direction, the first wheel having at least two openings on an outer peripheral surface thereof;

40

a second wheel that rotates around the shaft in a second direction opposite to the first direction, the second 45

wheel having at least two openings on an outer periph­eral surface thereof;

a motor that provides force to cause the first and second wheels to rotate;

first and second magnets respectively provided in the at 50

least two openings of the first wheel; third and fourth magnets respectively provided in the at

least two openings of the second wheel; and first and second pulsing stations that output pulses having 55

magnetic fields associated therewith, wherein the first pulsing station is operative to output a

first pulse at a first instant in time that creates a magnetic field at the first pulsing station of a same polarity as a polarity of a nearest surface of the first and 60

third magnets, wherein the first instant in time is a time when the first

magnet on the first wheel and the third magnet on the second wheel are passing in front of the first pulsing station, and

wherein a repelling force is provided to thereby urge the first and third magnets inwards within the respective

65

5. A control device for an object, comprising: a frame; a shaft mounted on the frame; a first wheel that rotates around the shaft in a first

direction, the first wheel having at least two openings that extend from an outer peripheral surface of the first wheel inwards;

a second wheel that rotates around the shaft in a second direction opposite to the first direction, the second wheel having at least two openings that extend to from an outer peripheral surface of the first wheel inwards;

a motor which provides force to cause the first and second wheels to rotate;

first and second magnets respectively provided in the at least two openings of the first wheel;

third and fourth magnets respective provided in the at least two openings of the second wheel; and

first and second pulsing stations that output pulses having magnetic 11elds associated therewith,

wherein the first pulsing station is operative to output a first pulse at a first instant in time that creates a magnetic field at the first pulsing station of a same polarity as a polarity of a nearest surface of the first and third magnets.

wherein the first instant in time is a time when the first magnet on the first wheel and the third magnet on the second wheel are passing in front of the first pulsing station, and

wherein a repelling force is provided to thereby urge the first and third magnets inwards within the respective openings of the first and second wheels, to thereby create a weight distribution change in the first and second wheels that is used to provide a force vector that is used to control the object.

6. A control device for controlling an object, comprising: a frame having a bottom plate and two vertical plates

extending upwards from the bottom plate; a shaft that is fitted through holes of the two vertical

plates, wherein the shaft is held in place onto the frame as a result;

a first wheel that rotates around the shaft in a first direction, the first wheel having at least two openings;

a second wheel that rotates around the shaft in a second direction opposite to the 11rst direction, the second wheel having at least two openings;

US 6,396,180 B1 11

means for causing the first and second wheels to rotate;

first and second magnets respectively provided in the at least two openings of the first wheel;

third and fourth magnets respectively provided in the at least two openings of the first wheel; and 5

first and second pulsing stations provided on the bottom plate of the frame and oppositely positioned with respect to each other, wherein the first and second wheels are disposed between the first and second 10

pulsing stations,

wherein one of the first and second pulsing stations is operative to output pulses having a magnetic field

12 associated therewith, having a same polarity as a polar­ity of a surface of the first through fourth magnets facing the first and second pulsing stations, and

wherein a repelling force is provided to thereby urge the first through fourth magnets away from the one of the first and second pulsing stations, at different instants in time, to thereby cause a weight distribution change in the first and second wheels that is used to move the frame and thereby create a force vector used to control the object.

* * * * *

(12) United States Patent Hock et ai.

(54) AXIAL SETTING DEVICE WITH A SWITCHING COUPLING INCORPORATED INTO THE DRIVE

(75) Inventors: Michael Hock, Neunkirchen-Seelscheid (DE); Klaus Matzschker, Neunkirchen (DE)

(73) A'isignee: GKN Automotive GmbH (DE)

( *) Notice: Subject to any disclaimer, the term of this patent is extended or adjusted under 35 U.S.c. 154(b) by 161 days.

(21) Appl. No.: 10/273,087

(22) Filed:

(65)

Oct. 17, 2002

Prior Publication Data

US 2003/0089185 A1 May 15,2003

(30) Foreign Application Priority Data

Oct. 20, 2001 (DE) ......................................... 101 51 960

(51) Int. CI? ................................................ F16D 13/04 (52) U.S. CI. ........................ 192/35; 192/84.7; 192/48.2 (58) Field of Search ......................... 192/84.7, 35, 48.2

(56) References Cited

U.S. PATENT DOCUMENTS

5,620,072 A * 4/1997 Engle .......................... 192/35

111111 1111111111111111111111111111111111111111111111111111111111111

AI' DE DE

US006851534B2

(10) Patent No.: (45) Date of Patent:

US 6,851,534 B2 Feb. 8,2005

5,713,445 A * 2/1998 Davis et al. .................. 192/35 5,810,141 A * 9/1998 Organek et al. .............. 192/35 RE36,502 E * 1/2000 Organek et al. .............. 192/35 6,302,251 B1 * 10/2001 Fair ct al. ..................... 192/35 6,666,315 B2 * 12/2003 Organek et al. ........... 192/84.7 6,691,845 B2 * 2/2004 Showalter .................... 192/35

FOREIGN PATENT DOCUMENTS

004939 lJl 3815225 C2 3909112 C2

1/2002 11/1989 9/1990

* cited by examiner

Primary Examiner-David M. Fenstermacher

(57) ABSTRACT

An axial setting device comprising two plates (24, 29) which are relatively rotatable and coaxially supported relative to one another and between which balls are guided in pairs of ball grooves (34, 39) in the plates (24, 29), with the depth of said pairs of ball grooves (34, 39) being circumferentially variable; of the plates (24, 29), one is axially supported and one is axially displaceable against the elastic returning forces of spring means; at least one of the plates (24, 29) is drivable via a driveline by a driving motor (11). Within the driveline, between the driving motor (11) and the drivable plates (24, 29), there is inserted a switching coupling (83).

12 Claims, 6 Drawing Sheets

u.s. Patent Feb. 8,2005 Sheet 1 of 6 US 6,851,534 B2

AI'

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f' i;

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u.s. Patent Feb. 8,2005 Sheet 2 of 6 US 6,851,534 B2

u.s. Patent Feb. 8,2005 Sheet 3 of 6 US 6,851,534 B2

u.s. Patent Feb. 8,2005 Sheet 4 of 6 US 6,851,534 B2

u.s. Patent Feb. 8,2005 Sheet 5 of 6 US 6,851,534 B2

;1A

I

u.s. Patent Feb. 8,2005 Sheet 6 of 6 US 6,851,534 B2

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US 6,851,534 B2 1

AXIAL SETTING DEVICE WITH A SWITCHING COUPLING INCORPORATED

INTO THE DRIVE

TECHNI CAL FIELD

The invention relates to an axial setting device comprising two plates which are relatively rotatable and coaxially supported relative to one another and between which balls are guided in pairs of ball grooves in the plates, with the depth of the pairs of ball grooves being circumferentially variable. One of the plates is axially supported and one is axially displace able against elastic retuming forces of a spring mechanism. At least one of the plates is drivable via a driveline by a driving motor.

BACKGROUND OF THE INVENTION

One rotatingly driven plate can, at the same time, consti­tute the axially displaceable one, but this would be an exception. Normally, the supported plate is rotatingly driven and the axially displaceable plate which, in turn, is sup­ported via the balls on the supported plate is held in a rotationally fast way.

For actuating the axial setting device, the driving motor is driven in a first direction of rotation. The at least one plate coupled to the driving motor via reduction stages of the driveline is rotated, and the displaceable plate, which, in turn, axially supports itself on the axially supported plate is axially displaced against elastic returning forces of the spring mechanism.

The balls which, in pairs of ball grooves, rest against end stops and which, at the same time, are positioned there in the deepest groove portions are caused, by the relative rotation of the plates relative to one another, to move towards flatter groove portions, as a result of which the plates push each other away from one another.

2 also further masses of the drive line, are disconnected from the abutting drivable plate in the sense that the de-energised motor or, optionally, the electrically braked motor can continue to rotate without there being mechanical overloads.

5 In this context, it should be taken into account that, as a rule, the object is to achieve the quickest possible return movement, irrespective of whether such a return movement is effected actively by the driving motor or, if the driving motor is de-energized, merely by the returning force of the

10 spring mechanism and by the ramp effect of the ball grooves. According to a first embodiment, the switching coupling

is effectively incorporated between a motor shaft of the driving motor and a coupling shaft. According to a second embodiment, the switching coupling is effectively inserted between two gearwheels of an intermediate shaft of the

15 driveline, of which one is connected to the intermediate shaft in a rotationally fast way, with the other one being rotatably supported on the intermediate shaft. According to a third embodiment, the switching coupling is inserted between the drivable one of the plates and a gearwheel or tooth segment

20 serving for driving the drivable one of the plates. The reduction in the masses to be braked and thus in the momentum when the balls abut the groove ends becomes more effective from embodiment to embodiment.

According to a first method according to the present 25 invention for returning purposes, the driving motor, from the

start, is disconnected from the device by the switching coupling in accordance with the invention. The rotatable plate is turned back from the axially displaceable plate by the above-mentioned functions of the sprinb<Y mechanism and

30 ball grooves. When the rotatable plate abuts, the discon-nected motor shaft with the rotor mass can continue to rotate freely, and the way in which the motor shaft is eventually braked is not significant. The motor shaft is kept completely

35 free from the delaying momentum of the rotatingly drivable plate.

If the driving motor is driven in the opposite direction or de-energised, the elastic returning force of the spring mecha­nism acting on the displaceable plate causes the latter to be 40

pushed back and the at least one rotatingly drivable plate is rotated backwards, either actively by the driving motor or due to the effect of the spring mechanism by way of the balls

According to a second method, the device is actively returned by the driving motor, in which case the axially displace able plate only axially follows the rotatingly driven plate. When the stops are reached and when the rotatingly drivable plate is stopped, the motor shaft with the rotor mass and, optionally, further parts of rotational masses of the driveline can simultaneously be disconnected by the inven­tive switching coupling. in the ball grooves until the balls in their pairs of ball

grooves simultaneously abut the end stops. As a result of the 45

balls abutting the ends of the ball grooves, the rotating masses of this system, i.e. the rotatable one of the plates, the gears of the drive line and the motor shaft of the driving motor with the rotor mass are stopped abruptly.

The elastic deformation of the motor shaft caused by 50

stopping the rotating masses so abruptly can lead to tooth fracture at the pinion or at the gear set because the force impact points in the too things move outwards due to the bending of the motor shaft, as a result of which the pinion or the gear set are subjected to loads which can exceed the 55

design loads.

SUMMARY OF THE INVENTION

Other advantages and features of the invention will also become apparent upon reading the following detailed description and appended claims, and upon reference to the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

For a more complete understanding of this invention, reference should now be made to the embodiments illus­trated in greater detail in the accompanying drawings and described below by way of examples of the invention.

In the drawings: FIG. 1 shows an inventive device in a first embodiment

with a switching coupling arranged on the shaft of the driving motor.

It is therefore an object of the present invention to provide a design which is capable of accommodating in a damage­free way the momentum generated as a result of the rotating masses being braked when the balls abut the ends of the ball grooves. The objective is achieved in that the present invention provides a switching coupling inserted between the driving motor and the drivable one of the plates.

FIG. 2 shows the driving motor with the switching 60 coupling according to FIG. 1 in the form of a detail.

The switching coupling of the present invention ensures that at least the motor shaft with the rotor mass, and possibly

65

FIG. 3 shows the inventive device in a second embodi­ment with a switching coupling on an intermediate shaft.

FIG. 4 shows the switching coupling on the intermediate shaft in the form of a detail.

FIG. 5 shows an inventive device in a third embodiment with a switching coupling arranged in the drive of the first ramp plate.

US 6,851,534 B2 3

FIG. 6 shows the drive of the first ramp plate in the form of an enlarged detail.

DETAILED DESCRIPTION OF 11m INVENTION

FIGS. 1 and 2 will be described jointly below. They show a first axial setting device in accordance with an embodi­ment of the invention in a mounted condition. A driving motor 11 is shown as provided with a motor shaft 12 and with a motor housing 13 in which the motor shaft 12 is supported twice. A coupling housing 81 in which there is supported a coupling shaft 82 is fixed to the motor housing 13. A first plate 84 of an electro-magnetic switching cou­pling 83 is secured to the motor shaft 12 by way of a feather key 85. A second plate 86 of the electro-magnetic switching coupling 83 is secured to the coupling shaft 82 by way of a feather key 87. On the coupling shaft 82 there is secured by way of a pin 16 a shaft journal 14 which forms a driving pinion 15. The coupling housing 81 is inserted into a centering bore 51 in a housing wall 52. Ibe free end of the shaft journal 14 is supported by a needle bearing 21 in a housing wall 54. A bearing journal 18 is inserted into a further bore 53 in the housing wall 52. On the bearing journal 18, there is rotatably supported a sleeve pinion 19 by way of two needle bearings 41, 42. A larger gearwheel 20 which, by way of its gear rim, engages the pinion 15 is pressed on to the sleeve pinion 19. The sleeve pinion 19, in turn, engages a tooth segment 22 which is firmly connected to a first plate 24 of the setting device. By way of a needle bearing 23, the plate 24 is rotatably supported on a projec­tion of a cover 25 on which it is axially supported by way of an axial bearing 26, a plate 27 and a securing ring 28. The plate 24 cooperates with a further plate 29 which is slidingly supported on a projection of the plate 24 and which is supported on the cover 25 by way of an axial bearing 30 and a plate 31 via pressure springs 33. The plate 31 acts on pressure pins 32 inserted into the pressure springs 33. The pressure pins 32 form the direct setting members of the device. The surfaces of the plates 24, 29, which face one another, are provided with pairs of grooves 34, 39 whose depth varies across the circumference and in which there run balls 35 held in a ball cage 36. The plate 29 comprises a radial projection 37 with a guiding claw 38. The guiding claw 38 slides in a longitudinally displaceable way on a holding pin 40 which is firmly inserted into a bore 55 in a housing wall 56 and which, in this way, holds the axially displace able plate 29 in a rotationally fast way.

FIGS. 3 and 4 will be described jointly below. They show

4 19, in turn, engages the tooth segment 22 which is firmly connected to a first plate 24 of the setting device. By way of a needle bearing 23, the plate 24 is rotatably supported on a projection of a cover 25 on which it is axially supported by

5 way of an axial bearing 26, a plate 27 and a securing ring 28. The plate 24 cooperates with a further plate 29 which is slidingly supported on a projection of the plate 24 and which, by way of an axial bearing 30 and a disc 31, is supported via pressure springs 33 on the cover 25. The plate

10 31 acts on pressure pins 32 which are positioned in the pressure springs 33. The pressure pins 32 form the direct setting members of the device. The surfaces of the plates 24, 29, which face one another, are provided with pairs of grooves 34, 39 whose depth varies across the circumference

15 and in which there rnn balls 35 held in a ball cage 36. The plate 29 comprises a radial projection 37 with a guiding claw 38. The guiding claw 38 slides in a longitudinally displace­able way on a holding pin 40 which is flrmly inserted into a bore 55 in a housing wall 56 and which, in this way, holds

20 the axially displace able plate 29 in a rotationally fast way. FIGS. 5 and 6 will be described jointly below. They show

a third embodiment of an axial setting device in accordance with the invention in a mounted condition. A driving motor 11 is shown to be provided with a motor shaft 12 and with

25 a motor housing 13 in which the motor shaft 12 is supported twice. The motor housing 13 is inserted into a centering bore 51 in a housing wall 52. On the motor shaft 12 there is secured by way of a pin 16 a shaft journal 14 which forms a driving pinion 15. A bearing journal 18 is inserted into a

30 further bore 53 in the housing wall 52. A sleeve pinion 19 is rotatably supported on the bearing journal 18 by way of two needle bearings 41, 42. A larger gearwheel 20 is pressed on to the sleeve pinion 19 and, by way of its rim gear, engages the pinion 15. The sleeve pinion 19, in turn, engages a

35 gearwheel 22 which, via a switching coupling 83, can be connected to a first plate 24 of the setting device. A first plate 84 of the electro-magnetic switching coupling 83 is firmly connected to the gearwheel 22, and a second plate 86 of the electro-magnetic switching coupling 83 is welded to the first

40 plate 24 of the setting device. The first plate 84 of the switching coupling and the plate 24 are rotatably supported via a needle bearing 23, 23' each on a projection of a cover 25 on which they are axially supported by way of an axial bearing 26, a plate 27 and a securing ring 28. The plate 24

45 cooperates with a further plate 29 which is slidingly sup­ported on a projection of the plate 24 and which, by way of an axial bearing 30 and a disc 31, is supported via pressure springs 33 on the cover 25. The plate 31 acts on pressure pins 32 which are positioned in the pressure springs 33. The a second embodiment of an axial setting device in accor­

dance with the invention in a mounted condition. A driving motor 11 is shown to be provided with a motor shaft 12 and with a motor housing 13 in which the motor shaft 12 is supported twice. The motor housing 13 is inserted into a centering bore 51 in a housing wall 52. On the motor shaft 12, there is secured by way of a pin 16, a shaft journal 14 which forms a driving pinion 15. A bearing journal 18 is inserted into a further bore 53 in the housing wall 52. A sleeve pinion 19 is rotatably supported on the bearing journal 18 by way of two needle bearings 41, 42. A larger gearwheel 20 is rotatably supported on the sleeve pinion 19. 60

Furthermore, an electro-magnetic switching coupling 83 is positioned on the sleeve pinion 19. A first plate 84 of an electro-magnetic switching coupling 83 is secured by pins 90, 91 on the gearwheel 20, with a second plate 86 of the electro-magnetic switching coupling 83 being secured by a feather key 87 on the sleeve pinion 19. The gearwheel 20, by way of its gear rim, engages the pinion 15. The sleeve pinion

50 pressure pins 32 form the direct setting members of the device. The surfaces of the plates 24, 29, which face one another, are provided with pairs of grooves 34, 39 whose depth varies across the circumference and in which there run balls 35 held in a ball cage 36. The plate 29 comprises a

55 radial projection 37 with a guiding claw 38. The guiding claw 38 slides in a longitudinally displaceable way on a holding pin 40 which is firmly inserted into a bore 55 in a housing wall 56 and which, in this way, holds the axially displaceable plate 29 in a rotationally fast way.

The following applies to all three embodiments: When the driving motor 11 is driven for the purpose of

positively setting the device, the electric switching coupling 83 is energised and thus closed. Driving the driving motor 11 thus causes the plate 24 to rotate, with the balls 35 moving

65 from deeper ball groove regions to flatter ball groove regions in both plates, the result being that the second plate 29 is axially displaced on the projection of the plate 24 against the

US 6,851,534 B2 5

returning force of the springs 33. The cover 25 normally forms part of the clutch carrier of a locking clutch, such as a locking clutch for locking a differential drive. According to first variant for returning the device, the driving motor 11 is driven in the opposite direction of rotation, so that the 5

plate 24 is rotated in such a way that the balls move from the flatter ball groove regions into the deeper ball groove regions. The plate 29 follows axially under the influence of the pressure springs 33 until the balls reach the end stops in the ball grooves which, at the same time, form the deepest 10

ball groove regions. The abrupt braking of the plate 24 and thus of the gearwheel 20, which happens as a result, can therefore be prevented from affecting the driving motor 11, as the electric switching coupling is opened at the same time,

6 with the depth of said pairs of ball grooves being circunferentially variable, one of the plates being axi­ally supported and one of the plates being axially displaceable against elastic returning forces of a spring mechanism, and at least one of the plates being drivable via a drive line by a driving motor; and

a switching coupling within a driveline between the driving motor and the drivable one of the plates.

2. A device according to claim 1, wherein the switching coupling is incorporated between a motor shaft of the driving motor and a coupling shaft.

3. A device according to claim 1, wherein the switching coupling is elIectively inserted between two gears of an intermediate shaft of the drive line, wherein one of the gears is connected to the intermediate shaft in a rotationally fixed way, and the other of the gears is rotatably supported on the intermediate shaft.

4. A device according to claim 1, wherein the switching coupling is inserted between the drivable one of the plates and a gear or tooth segment for driving the drivable one of the plates.

5. A device according to claim 2 comprising a coupling housing supporting the coupling shaft, the coupling housing being secured to a motor housing containing the drive motor.

6. A device according to claim 2 wherein the switching coupling comprises a 11rst plate secured to the motor shaft and a second plate secured to the coupling shaft.

so that the rotor mass which constitutes the largest percent- 15

age of mass can continue to rotate freely. According to a further variant for returning the device, the electric switch­ing coupling 83 is opened at the very start, in which case the plate 29 is returned entirely under the influence of the pressure springs 33, which plate 29 then forces the plate 24 20

to rotate in the opposite direction of rotation in that the balls run from the flatter ball groove regions into the deeper ball groove regions. When the balls reach the end stops in the ball grooves which, at the same time, form the deepest ball groove regions, the rotor mass of the electric motor 11 has 25

already been disconnected from the rotational masses of the setting device. The driving motor is normally a frequency­modulated electric motor but other types of electric motors are also contemplated by the present invention. In the first embodiment, the rotor mass, during the return movement, 30

continues to rotate freely. In the second embodiment, the motor mass includes the gearwheels 15, 20 and in the third embodiment, it additionally includes the mass of the gear­wheel 22.

7. A device according to claim 6 wherein the first and second plates of the switching coupling are secured to the respective motor shaft and coupling shaft by feather keys.

8. A device according to claim 1 wherein the switching coupling comprises an electro-magnetic switching coupling.

9. A device according to claim 3 wherein the switching coupling comprises a first plate secured to the rotationally fixed gear of the intermediate shaft and second plate secured

35 to the rotatably supported gear of the intermediate shaft. From the foregoing, it can be seen that there has been brought to the art a new and improved axial setting device and switch coupling. While the invention has been described in connection with one or more embodiments, it should be understood that the invention is not limited to those embodi­ments. Thus, the invention covers all alternatives, modifications, and equivalents as may be included in the spirit and scope of the appended claims.

What is claimed is: 1. An axial setting device comprising:

two plates which are relatively rotatable and coaxially supported relative to one another and between which balls are guided in pairs of ball grooves in the plates,

10. A device according to claim 9 wherein the first plate of the switching coupling is secured to the rotationally fixed gear of the intermediate shaft by pins.

11. A device according to claim 9 wherein the second 40 plate of the switching coupling is secured to the rotatably

supported gear of the intermediate shaft by a feather key. 12. A device according to claim 4 wherein the switching

coupling comprises a first plate secured to the gear or tooth segment for driving the driveable one of the plates, and a

45 second plate secured to the drive able one of the plates.

* * * * *

(12) United States Patent Gizara

(54) GIMBAL-MOUNTED HYDROELECTRIC TURBINE

(76) Inventor: Andrew Roman Gizara, 24471 Corta Cresta Dr., Lake Forest, CA (US) 92630-3914

( *) Notice: Subject to any disclaimer, the term of this patent is extended or adjusted under 35 U.S.c. 154(b) by 149 days.

(21) Appl. No.: 10/604,601

(22)

(65)

(51)

(52)

(58)

(56)

Filed: Aug. 4,2003

Prior Publication Data

US 2005/0029817 A1 Feb. 10, 2005

Int. CI.7 .......................... F03B 13/10; F03B 13/12;

H02P 9/04; F03C 5/02 U.S. CI. ............................. 290/43; 290/42; 290/44;

290/53; 290/54; 290/55; 601398 Field of Search ......................... 290/42-44, 53-55;

601398

References Cited

U.S. PATENT DOCUMENTS

3,455,159 A * 7/1969 Gies, Sf. .................. 73/170.16 3,644,052 A * 2/1972 Lininger ........................ 415/7 3,687,567 A * 8/1972 Lininger ........................ 415/7 3,818,703 A * 6/1974 Lapeyre ....................... 60/504 3,818,704 A * 6/1974 Lapeyre ....................... 60(504 3,980,894 A * 9/1976 Vary et al. .................... 290/54 4,034,231 A * 7/1977 Conn et al. ................... 290/53 4,039,847 A * 8/1977 Diggs .......................... 290/42 4,048,512 A * 9/1977 Wood .......................... 290/53 4,060,344 A * 11/1977 Ootsu ......................... 417/330 4,078,382 A * 3/1978 Ricafranca et al. ........... 60/398 4,151,424 A * 4/1979 Bailey ......................... 290/54 4,159,427 A * 6/1979 Wiedemann ................. 290/55 4,170,738 A * 10/1979 Smith .......................... 290/42 4,172,689 A * 10/1979 Thorsheim ..................... 415/7 4,216,655 A * 8/1980 Ghesquiere ... ... ... ... ...... 60/398 4,256,970 A * 3/1981 Tomassini ..... ... ... ... ...... 290/53

111111 1111111111111111111111111111111111111111111111111111111111111 US006956300B2

(10) Patent No.: US 6,956,300 B2 Oct. 18, 2005 (45) Date of Patent:

4,258,270 A * 3/1981 Tornkvist. ... ... ..... ... ... ... 290/53 4,266,403 A * 5/1981 Hirbod ........................ 60/698 4,313,059 A * 1/1982 Howard ....................... 290/54 4,327,296 A * 4/1982 Weyers ........................ 290/53 4,327,297 A * 4/1982 Harrison ...................... 290/53 4,335,319 A * 6/1982 Mettersheimer, Jr. ........ 290/54 4,352,023 A * 9/1982 Sachs et al. .................. 290/42 4,369,375 A * 1/1983 Romano ...................... 290/53

(Continued)

Primary Examiner---narren Schuberg Assistant Examiner--Pedro J. Cuevas

(57) ABSTRACT

A power plant extracts energy from a free flowing motive fluid by means of a turbine mounted on a gimbal. The shroud element of the fluid intake has external rudders, in conjunc­tion with the gimbal mounting, enabling the enclosed tur­bine to instantaneously respond to changes in the direction of the free flowing motive fluid thus ensuring the face area of the intake is always physically orthogonal to the direction of the motive fluid streamlines. The shroud element may also be buoyant so as to optimally extract energy from an upper non-turbulent and higher velocity layer of the free flowing motive fluid. To function within an inherently unsteady source of energy, the preferred embodiment of the turbine is coupled to a DC generator which may further be coupled to a voltage and current regulating circuit which either charges a battery, performs electrolysis of water to produce hydrogen fuel, or is further coupled to a DC motor coupled to an AC generator. Alternatively an AC induction generator may be coupled to the turbine. Other mechanical, electrical, electronic, or electromechanical features may optionally be implemented to perform such tasks as adap­tively locating the turbine in the maximum velocity flow, adapting internal vane and runner blade pitches for various flow rates and loads, keeping the intake free of obstructions, preventing loss of aquatic life, controlling and communi­cating the state of charge of the battery, or gauging and controlling the electrolysis process and communicating the fullness of the hydrogen gas output tanks.

9 Claims, 8 Drawing Sheets

US 6,956,300 B2 Page 2

u.s. PATENT DOCUMENTS 5,105,094 A * 4/1992 Parker .. ... ... ... ..... ... ... ... 290/53

4,384,212 * 5,136,174 A * 8/1992

A 5/1983 Lapeyre ....................... 290/53 5,468,132 A * 11/1995 4,403,475 A * 9/1983 Kondo 60/398 ........................ 4,443,708 A * 4/1984 Lapeyre .......................

5,499,889 A * 3/1996 290/53

4,447,740 A * 5/1984 Heck ........................... 5,507,943 A * 4/1996

290/53 4,453,894 A * 6/1984 Perone et al. 417/332

5,664,418 A * 9/1997 ...............

4,464,080 A * 8/1984 Gorlov 405/76 6,184,590 B1 * 2/2001 ........................

4,468,153 A * 8/1984 Gutierrez Atencio 405178 6,194,791 Bl * 2/2001 ........

4,480,966 A * 11/1984 Smith ......................... 417/332 6,227,803 B1 * 5/2001

4,490,232 A * 12/1984 Lapeyre ...................... 204/278 6,294,844 B1 * 9/2001

4,495,424 A * 1/1985 Jost ............................. 290/53 6,327,994 B1 * 12/2001

4,516,033 A * 5/1985 Olson 290/54 6,534,705 B2 * 3/2003 ..........................

4,599,158 A * 7/1986 Of en loch 204/229.5 6,537,018 B2 * 3/2003 .................

4,622,471 A * 1111986 Schroeder 290/42 6,551,053 B1 * 4/2003 .................... 4,625,124 A * 11/1986 Ching-An 290/42 6,559,552 B1 * 5/2003

.................... 4,661,716 A * 4/1987 Chu 290/53 6,568,878 B2 * 5/2003 ............................ 4,816,697 A * 3/1989 Takada 290/54 6,734,576 B2 * 5/2004

........................ 4,843,249 A * 6/1989 Bussiere 290/53 6,831,373 B1 * 12/2004 ...................... 4,850,190 A * 7/1989 Pitls 60/398 6,849,963 B2 * 2/2005

............................ 5,005,357 A * 4/1991 Pox 60/398 6,877,581 B2 * 4/2005

.............................

Simoni . ... ... ... ..... ... ... ... 290/54 Snell et al. ... ... ... ..... 418/206.4 Yim ............................ 405/76 Labrador .................... 210/136 Walters ....................... 60/398 Lopez .. ... ... ... ..... ... ... ... 290/53 Wells ... ... ... ... ..... ... ... ... 290/53 Shim ........................... 416/44 Lagerwey ... ... ..... ... ... ... 290/55 Labrador .................... 114/382 Berrios et al. ... ... ..... ... 136/243 Streetman ................... 415/3.1 Schuetz ...................... 415/3.1 Ha .............................. 290/54 Woodall et al. ............... 405/25 Pacheco .. ... ... ..... ... ... ... 290/55 Beaston ... ... ... ..... ... ... ... 290/43 Grinsted et al. .............. 290/42 Badr et al. .................. 180/311

5,009,568 A * 4/1991 Bell 415/3.1 ........................... 5,066,867 A * ll/1991 Shim 290/53 * cited by examiner ...........................

u.s. Patent Oct. 18, 2005 Sheet 1 of 8 US 6,956,300 B2

101 > lOS

11------119

FIG. I

u.s. Patent

201/ • • • •

103

V 200

301/

V 300

Oct. 18, 2005 Sheet 2 of 8 US 6,956,300 B2

106

FIG. 2

03

FIG. 3

u.s. Patent Oct. 18, 2005 Sheet 3 of 8 US 6,956,300 B2

40

404

40

)Civ412

412 411

FIG. 4

FIG. 5

u.s. Patent Oct. 18, 2005 Sheet 4 of 8

00

Yes

1Ql Energize DC

Stepper Motor coil 410 corresponding to present position

FIG. 6

706 De-Energize DC

Stepper Motor coil 411, latch new

position in register

702 Energize Solenoid coil 604 to unlock present position

FIG. 7

US 6,956,300 B2

403

404~MI 412 !

705 De-Energize

Solenoid coil 604 for anti-backlash and

position locking

703 Energize DC

Stepper Motor coil 411 corresponding to next position, De-Energize 410

412

u.s. Patent Oct. 18, 2005 Sheet 5 of 8 US 6,956,300 B2

307

FIG. 8

FIG. 9

u.s. Patent Oct. 18, 2005 Sheet 6 of 8

l!m

HOO

116 1001

1106

1005

I I I 111

-1000

FIG. to

11+ 1108

FIG. II

FIG. 12

US 6,956,300 B2

1007

1002

112 1l¥15

1113

)}

1204

1205

u.s. Patent Oct. 18, 2005 Sheet 7 of 8 US 6,956,300 B2

1204

1205

FIG. 13

1404

1405

FIG. 14

L--_08 __ ~ 1300 t --. 1504

1505

FIG. 15

u.s. Patent Oct. 18, 2005 Sheet 8 of 8 US 6,956,300 B2

oncummt

1602 Differentiate with res~t to time the

main generator output, d(lVol)/dt

l@l 1603 Concurrent Sample and store buoy Integrate and Average

accelerometers voltage,t---.. over an interim term and main generator the main generator voltage, Vo, outputs output, (lIn)(I:nIVol)

No

No

Yes

1607

Concurrent 1604

Estimate the location of breaking waves from

accelerometers voltage profile, store, determine breaker procession (FFT)

Throttle up flow velocity by adjusting internal

vanes and runner blades (see Fig. 7)

Throttle down flow velocity by adjusting

internal vanes and runne blades (see Fig. 7)

1610 Update long term power average,com~to

interim term power average

1611 Temporarily close gate to

stop flow, reduce gyroscopic precession (see Fig. 7)

FIG. 16

Clear intake face by changing orientation

using external rudders or auxiliary motor

1617 Optimize for break

location each interim

1618 Optimize location over semidiumal tidal period

US 6,956,300 B2 1

GIMBAL-MOUNTED HYDROELECTRIC TURBINE

BACKGROUND OF INVENTION

1. Field of the Invention

5

2 infrastructure, increasing impingement on human habitats, and for the most part, neglecting the significant kinetic energy recoverable from one or more of various forms of oceanic flow.

Other prior art exists where the motive fluid is ocean water, but still requires significant infrastructure. In one form, dam like structures known as barrages compel tidal flow to affect a turbine. Some turbines exist that operate in free flow, but do not adapt to changes in direction and have

The present invention is generally in the field of power plants. More specifically, the present invention is in the field of hydrokinetic turbines with means to adapt to changes in streamline direction and magnitude of a free flowing motive fluid. ~

2. Description of Prior Art

10 limited capacity, typically less than a kilowatt. In another recently developed form, offshore platform structures behave as pistons on waves at medium depths, in turn pumpin~ a motive fluid through a turbine and then requiring a .long dlstance power cable generally carrying high voltage dlrect current back to shore, to be further processed. This

For over two thousand years mankind has known of harnessing the kinetic energy in flowing water to perform 15

mechanical endeavors. In the past two hundred years the pace in which developments emerged in the practice of hydraulics has accelerated. The advent of the turbine in the first half of the nineteenth century culminated in the present advancements in hydroelectric generation, with this period 20 of innovation and intense interest peaking in the first quarter of the twentieth century. Since then, fossil fuels have domi­~ated as the high net energy, readily available energy source m the production of electricity and other conveyors of power. With known fossil fuel reserves at what presently appears to be arguably half depleted, as well as the envi- 25

ronmental impact of using a polluting energy source, there is a strong need to develop a renewable and sustainable source of energy to support humankind.

Presently the hydroelectric power plant industry earns 30

revenues of approximately thirty billion dollars annually, but unfortunately is in a state of decline mainly due to the environmental and civic costs of implementing the existing technology. Environmental impact of the prior art hydro­electric power plant threatens extinction to aquatic species 35

living downstream from the proposed power plant infrastructure, and also displaces all human inhabitants that live in what would become the flood plane of the infrastruc­ture. It is estimated that over sixty million people have been displaced in the past century due to hydraulic power plant 40

development with no mention of the number of species of plant and animal that have gone extinct. Furthermore, given the prior art technology, there still exists the possibility of life threatening flooding occurring downstream from the site of the hydraulic power plant infrastructure. Overall these 45

costs have weighed heavily in civic planners' decisions in adopting hydroelectric power generation to the point of putting the industry in a state of such decline that leading companies involved in this business are contemplating other areas of endeavor. 50

Inherent problems in the prior implementation of hydro­electric power generation have exacerbated the present state of declining interest in this technology. The earliest imple­mentation of hydrokinetic systems, commonly known as waterwheels, allowed less impact to the natural flow of the 55

body of water from which these systems drew energy. With the greater efficiency gained by enclosing the impeller within the turbine came the need for more sophisticated penstock arrangements, which included greater infrastruc­ture in the form of dams incurring the majority of the civil 60

and environmental costs. The penstock, gate and impeller arrangements for these systems are physically coupled to sustain a given range of flow velocities and pressures over varying head and load so to maintain required synchroniza­tion to the end electrical alternating current output. This 65

requirement imposes on these systems almost exclusive implementation in fresh-water systems with large scale

likely incurs significant maintenance costs for the offshore platforms. Fully implementing this prior technology would likely impede shipping lanes as a farm of these platforms effectively fences the shoreline. This stands as one of several known environmental impacts of this prior technology with others hypothetically existing.

When one amortizes the total amount of energy that goes into building and maintaining a prior art hydroelectric power installation, it becomes obvious that it takes a considerable amount of time before the plant becomes net energy positive, or in other words, the point when the total invest-ment of energy compared to the total recovery of energy is at the break-even point. As a further example, fossil fuel, not being a renewable resource, requires mining or drilling deeper and pumping farther to obtain a lower yield and lower quality of fuel incurring more costly refining to recover the remaining reserves at the end-of-life of a mine or a well. Thus, fossil fuel as an energy source clearly diminishes in net energy as time goes on, until it obviously becomes a sink, no longer a source. This latter example reinforces the inevitability of mankind's undeniable need for ~ sustainable and renewable source of energy. Contemplat­mg the net energy curves of a renewable energy source and fossil fuel indicates a sense of urgency for the development of a renewable source. The timing of the cross-over point of when one source becomes net energy positive as the other becomes net energy negative will dictate the severitv of the ensuing energy crisis and thus the impact on huma~ity. As time goes on it will be less likely an option to expend a great deal of energy as an investment while more mundane needs are no longer being met. Despite this sense of urgency in the need. to develop renewable, s~stainable sources of energy, as prevIOusly stated hydroelectrIc power plant development is actually declining.

Therefore, there exists a fundamental need for developing renewable and sustainable sources of energy including fur­ther exploitation of readily available known resources. More specifically, there exists a need for a novel approach to ensure low impact to environment and low civic infrastrnc­ture costs such that the energy investment return is most quickly realized. Utmost, to optimally exploit oceanic energy, such as that which arrives onshore, adaptability to inherently unsteady flow is prerequisite of any such system. A system that can achieve the above-specified goals would readily attain a relatively high net energy soon after its inception.

SUMMARY OF INVENTION

The present invention achieves the goals of overcoming existing limitations of present day hydroelectric power gen­eration systems by first and foremost having the ability to

US 6,956,300 B2 3

extract power from a free flowing fluid. While prior art exists which functions in free flowing bodies of water, the novelty of this invention lies in its ability to respond and adapt to any change in the magnitude and direction of the streamlines of the free flowing motive fluid. 'Ibis enables this invention to extract energy from breaking ocean waves, presently an untapped but readily available known source of energy.

4 coaxial fluid coupler through the system of gears in FIG. 9 according to one embodiment.

FIG. 14 represents a schematic view of a DC generator directly coupled to the output shaft of the coaxial fluid

5 coupler according to one embodiment.

10

FIG. 15 represents a schematic view of a gear indirectly coupled to the rotor of an auxiliary DC generator through the system of gears in FIG. 9 according to one embodiment.

FIG. 16 illustrates the flowchart for control of the com-plete system according to the preferred embodiment of the present invention.

DETAILED DESCRIPTION

The present invention is directed to a gimbal-mounted hydroelectric turbine for adaptively extracting energy from a free flowing motive fluid that continuously changes direc­tion and magnitude of flow. The following description contains specific information pertaining to various embodi-

Secondly, because adapting to change of both magnitude and direction of the streamlines of a free flowing motive Huid formed the basis of the guiding concepts of the present invention; this also avails the present invention the applica­bility to other bodies of water besides the ocean. Having been conceived for free flowing motive fluid use obviates the prior art's inherent need for large-scale infrastructure and thus eliminates two fundamental disadvantages pres- 15

ently challenging the hydroelectric power industry. The present invention does not require this scale of infrastructure and therefore greatly diminishes the environmental impact while attaining a positive net energy earlier upon implemen­tation. 20 ments and implementations of the present invention. One

skilled in the art will recognize that the present invention may be implemented in a manner dilTerent from that spe­cifically depicted in the present specification. Furthermore, some of the specific details of the invention are not described

Overcoming the conceptual need for synchronization to the electric power grid positions the present invention as desirable for implementation in gathering energy for the emerging power conveyance systems, especially hydrogen fuel and fuel cell technology.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 illustrates a general perspective view of an exem­plary apparatus in accordance with a preferred embodiment of the present invention.

FIG. 2 illustrates a cross-sectional view length-wise along the turbine shroud in FIG. 1 according to a preferred embodiment of the present invention.

FIG.3 illustrates a cross-sectional view length-wise along the turbine shroud in FIG. 1 according to an alternate embodiment of the present invention.

FIG. 4 illustrates a partially exploded perspective view of the pinion and motor mechanism for adjusting the interior How vanes, runner blades, and gate wickets in FIG. 2.

FIG. 5 illustrates an alternate view of the circular rack gear and motor rotor shaft pinion in FIG. 4.

FIG. 6 illustrates the preferred means of bi-directional anti-backlash and position locking mechanism for the cir­cular rack gear in FIG. 4.

FIG. 7 illustrates the flowchart for synchronizing the bi-directional anti-backlash and position locking solenoid in FIG. 6 to the motor in FIG. 4.

25 in order to maintain brevity and to not obscure the invention. The specific details not described in the present specification are within the knowledge of a person of ordinary skills in the art. Obviously, some features of the present invention may be omitted or only partially implemented and remain well

30 within the scope and spirit of the present invention. The following drawings and their accompanying detailed

description are directed as merely exemplary embodiments of the invention. To maintain brevity, some other embodi­ments of the invention that use the principles of the present

35 invention are specifically described but are not specifically illustrated by the present drawings, and are not meant to exhaustively depict all possible embodiments within the scope and spirit of the present invention.

FIG. 1 illustrates a general perspective view of an exem-40 plary apparatus in accordance with one embodiment of the

present invention. Arrow 100 indicates direction of the approaching flow of the free flowing motive fluid, impinging upon the face of the intake of the turbine, shown covered with a screen 103. The fundamental purpose of the screen

45 103 is to prevent loss of life of fish and other aquatic life forms as well as prevent various forms of debris from entering the turbine and obstructing normal operation. Arrow 101 is shown exiting the back of the turbine and is of

FIG. 8 illustrates a partially exploded perspective view of 50

the pinion and motor mechanism for adjusting the external rudders of the alternate embodiment in FIG. 3.

different shape than arrow 100 to indicate a change in velocity through the turbine due to the difference in area of the intake compared to the draft area at the runner blades. This ratio of intake area to draft area, as well known for about four centuries in the science of fluid dynamics for incompressible flow, is equ al to the ratio of draft velocity to

FIG. 9 illustrates a system of gears that increases the rotational velocity of the rotor of a generator compared to directly coupling the rotor to the actuating member.

FIG. 10 illustrates the mounting system affixed to a rail system in accordance to the preferred embodiment.

FIG. 11 illustrates a system of buoys equipped with accelerometers and their respective vector output signal profiles relative to position of breaking waves for one embodiment.

FIG. 12 represents a schematic view of an AC induction generator directly coupled to the output shaft of the coaxial Huid coupler according to one embodiment.

FIG. 13 represents a schematic view of an AC induction generator indirectly coupled to the output shaft of the

55 intake velocity. This difference in area of the draft compared to the intake may obviously be inferred by the physical profile of the turbine shroud 102 in both FIG. 1 and FIG. 2, though the drawings are not necessarily to scale of the preferred embodiment. The factors governing the necessity

60 of increasing the velocity of the flow through the turbine will be addressed subsequently. Note that the circular geometry of the intake and the shroud area implies use of a coaxial fluid coupler and henceforth changing to a rectangular intake and a crossflow impeller does not represent a significant

65 departure from the scope of the present invention. Subse­quent paragraphs in this specification will address the basis for choosing a coaxial impeller.

US 6,956,300 B2 5 6

waterway. Thus the flow impinging the face of the turbine is less likely to be turbulent, more likely to be laminar, permitting more optimal extraction of energy. Clearly any variation in the above assembly including any change to the

5 main shaft 115, the slotted tongue-and-groove arrangement 112, the non-binding washer 113, the sliding main shaft collar 111 or the buoyancy of the shroud 102, that continues to permit the intake of the turbine to extract energy from an upper, non-turbulent layer of the motive fluid does not

A fundamental and significant departure from prior art that provides considerable novelty in this invention is the implementation of the external vanes or rudders 104, 105, and 106 and the circular bearings 107, and 109. The com­bined use of circular bearings 107 and 109 comprise what results in a mechanical apparatus that one could commonly refer to as a two-axis gimbal, providing two degrees of freedom, specifically, freedom to move in any direction that has vector components that are parallel to a horizontal or a vertical plane. As depicted in FIG. 1, circular bearing 107 and its complement not shown but also affixed to the semi -elliptical follower brace 120 on the opposite side, with concentric pins affixed to the turbine shroud 102, forms an axis orthogonal to, and allows the turbine any motion parallel to, the vertical plane, whereas circular bearing 109 15

forms an axis orthogonal to, and allows the turbine any motion parallel to, the horizontal plane. For instance, as the free flowing motive Huid changes direction of its streamlines parallel to the horizontal plane by any arbitrary angle, this change in direction will exert a force on both rudders 104 20

and 106 causing torque about the bearing 109 resulting in motion parallel to the horizontal plane as represented by arrow 110 until arrival at mechanical equilibrium. Likewise,

10 constitute a substantial departure beyond the scope of the present invention.

as the free flowing motive fluid changes direction of its streamlines parallel to the vertical plane by any arbitrary 25

angle, this change in direction will exert a force on rudder 105 and a complementary rudder not shown on the opposite side of the shroud 102, causing torque about the bearing 107 and its complementary bearing not shown on the opposite side of the semi -elliptical follower brace 120, resulting in 30

motion parallel to the vertical plane as represented by the arrow 108 until arrival at mechanical equilibrium. Thus the present invention adapts to any change in direction of the streamlines of a free flowing motive fluid. Obviously, adding or removing either a rudder or an axis to the gimbal 35

employed within the preferred embodiment of the present invention would not constitute a substantial departure beyond the scope of the invention.

Proceeding further with the features depicted in FIG. 1, the semi-elliptic follower brace 120, is affixed to the outer 40

casing of the circular bearing 109, the inner case of the bearing 109 is affixed to the sliding main shaft collar 11I. The sliding main shaft collar 111 is illustrated in FIG. 1 as having a slotted tongue-and-groove arrangement 112, cap­tivated by a non-binding washer 113 affixed through a screw 45

to the main shaft 115. Said sliding assembly comprised of the slotted tongue-and-groove arrangement 112, and non­binding washer 113 permits the sliding main shaft collar 111 freedom of motion in the vertical direction as depicted by arrow 114. Note that the scale of this drawing is somewhat 50

distorted in order to clearly display the sliding main shaft collar 111, the slotted tongue-and-groove arrangement 112, and the non-binding washer 113 sliding assembly whereas in the preferred embodiment the entire turbine and especially the diameter of the screen-covered face of the intake 103 55

The main shaft 115 is shown in FIG. 1 attached to the base 116. Under the base is a system of rollers 117 riding on a set of rails 119 driven from under the base 116 through the drive axle 118. Further detail of the drive system will be depicted in FIG. 10 and in subsequent paragraphs. The primary purpose this rail system serves is to optimally locate the entire turbine system adaptively to an area of flow where maximum energy may be extracted. A secondary purpose could include facilitating maintenance on any part of the system at a more convenient location than its in-service location. A third purpose could be for moving the turbine out of the way of any vessel needing to pass in the present vicinity of the turbine. Clearly any deviation from the above stated system, such as a winch and pulley system, which continues to allow the turbine system to be adaptively positioned, does not constitute a substantial departure beyond the scope of the present invention. Maximum energy extraction location for the unit has been initially considered the onshore side of breaking ocean waves but can be any area of highest velocity of flow in any body of motive fluid. One alternate example of this could be any body of water that has flow patterns that vary diurnally or seasonally.

Let it be known that the aforementioned features that enable the turbine to namely: adapt to any change in the direction of the streamlines of a free flowing motive fluid; extract energy from an upper, non-turbulent layer of water due to buoyancy of its shroud; adaptively position the turbine in an optimal flow location using the rail system; while originally conceived for accommodating use in break­ing ocean waves, obviously are advantageous for use in other bodies of water such as, but not limited to rivers, creeks, inlets, tidal bores, rapids, or waterfalls. Therefore, use of the present invention in any body of water other than breaking ocean waves does not constitute a substantial departure beyond the scope of the present invention.

FIG. 2 illustrates a cross-sectional length-wise view inte-rior to the shroud 102 of the turbine. The broken line deJ1ned by points 200 and 201 indicates the vertical plane is where the section is cut and the arrows proceeding from points 200 and 201indicate the perspective direction of sight. The hatching of shroud 102 indicates it is the only element cut in this cross-sectional view with everything else contained within the shroud 102 remaining unaltered in this view. The hatch line delineates the shroud 102, and its cross-sectional circumference can be seen in FIG. 2 as creating an inner surface and outer surface and the cavity 202 within the inner and outer surfaces of the shroud 102. This cavity 202 is proposed to create the buoyancy of turbine unit itself. The

would be scaled considerably larger than this main shaft assembly. While said assembly allows the freedom of motion in the vertical direction as depicted by arrow 114, the cause of such motion corresponds to variation in the level of the surface of the motive fluid as tracked by buoyancy of the shroud 102. The means of this buoyancy is further depicted in FIG. 2 and will be further addressed in subsequent paragraphs. The buoyancy causes the turbine to track the variation in the level of the surface of the motive fluid and thereby enables the turbine to always extract energy from an upper layer of the motive fluid, which is less susceptible to the effects of friction namely turbulence at the floor of the

60 cavity 202 may be filled with a material such as polystyrene foam that provides both structural support and buoyancy, or if less expensive, left vacant with the shroud 102 constructed or assembled watertight. This shroud 102 may also alterna­tively be constructed in such a manner as to render the cavity

65 202 gas-tight and useful in containing the output fuel­hydrogen gas as the end product if the energy captured by this turbine is used in the process of electrolysis of water.

US 6,956,300 B2 7

Further elaboration on this cavity 202 for use in the pro­duction of hydrogen fuel will follow.

A., discussed previously the contour of the shroud 102 especially its inner surface is seen in FIG. 2 to form a decreasing area orthogonal to the streamlines and thus 5

causes the velocity of flow of the motive fluid to increase proportionally as it approaches the coaxial fluid coupler 210

8 suited for adapting to changes in flow magnitude due to its adjustable flow vanes and runner blades, and is most often implemented in structures of low head, implying low static pressure in the draft characteristic of, and more resembling an impulse turbine and thus most analogous to use in breaking ocean waves. Nevertheless, implementation of a reaction turbine that responds to changes in direction and magnitude of the streamlines of a free flowing motive fluid in any manner similar to that of the present invention does

in the draft area of the turbine from the screen-covered intake 103. This flow velocity as it thrusts upon the runner blades 211 actuates the rotational velocity of the coaxial fluid coupler 210 which affects the rotational velocity of the rotor of the generator contained within the generator housing 206. Ultimately, the choice of generator and particularly its synchronous speed predicates all requirements of flow velocity and will be discussed in more detail subsequently.

10 not constitute a substantial departure beyond the scope of the present invention. Furthermore, it may be advantageous to implement the present invention with a turbine of recent advent that boasts of being bladeless, as it is well known that seawater is particularly corrosive to metals, breaking waves

In general, it may be stated at this point that the operation of the turbine would likely benefit from increasing the average How velocity through the turbine since other means for reducing the effective velocity are readily attained. One such means of reducing the flow velocity includes closing the gate by rotating its wickets 203 as portrayed by arrows 205. Closing the gate in this manner will cut-off flow which serves to reduce the rotational velocity of the coaxial fluid coupler 210 thus reducing the forces of gyroscopic preces­sion so to quicken the response of the gimbal to changes in direction of the streamlines of a free flowing motive fluid as

15 notably high in particulates, and thus a bladed runner highly susceptible to pitting on the blades and perhaps costly in terms of maintenance. In light of the aforementioned, this modification of a Kaplan turbine in the preferred embodi­ment is purely exemplary, illustrative and not restrictive.

20 Thus, regardless of the impulse or reaction classification of such a bladeless turbine, an implementation of such a blade less turbine that responds to changes in direction and magnitude of the streamlines of a free flowing motive fluid in any manner similar to that of the present invention does

25 not constitute a substantial departure beyond the scope of the

it exerts a force on the exterior rudders 104, 105, 106. Continuous adjustment of the How velocity can be achieved through altering the pitch of the interior flow vanes 207 and runner blades 211. FIG. 2 shows the direction of rotation of 30

the interior flow vanes 207 by arrow 208 and the direction of rotation of the runner blades 211 about their bearings 213

present invention. FIG. 3 illustrates a cross-sectional length-wise view inte-

rior to the shroud 102 of an alternate embodiment of the present invention that includes exterior rudders that are rotatable. The points 300 and 301 define the cross-sectional plane and angle of perspective in the same manner as points 200 and 201 in FIG. 2. The fundamental difference of this alternate embodiment of the present invention as depicted in FIG. 3 versus the embodiment shown in FIG. 2 is in the implementation of rotatable rudders 302, 303 versus fixed rudders, 104, 105, 106, respectively. Arrows 306, 308 encir-cling the shafts 305, 307 depict the direction of rotation of these rudders. The purpose of furnishing the turbine with rotatable rudders 302, 303 is, as before while in the same

by arrow 212. While only two interior flow vanes 207 are shown, it should be understood that in the preferred embodi­ment a minimum of at least four interior flow vanes 207 and 35

as many as eight or twelve could be implemented and likewise a plurality of runner blades 211 could be imple­mented. The rotation and fundamental shape of the interior flow vanes 207 can reduce the effective area and thus increase flow velocity while channeling the flow into near vortical circulation as it thrusts upon the runner blades 211

40 position as the fixed rudders 104, 105, 106, to enable the gimbal-mounted turbine to adapt to changes in the direction of the streamlines of the free flowing motive fluid. The additional benefit of rotatable rudders 302, 303 is to affect a change in the orientation of the face of the screen-covered

at an angle optimal for energy extraction. This channeling of the flow could effectively transform turbulent Howat the screen-covered face 103 into laminar or vortical flow through the turbine. While some loss of energy may result from the friction on the sides of the interior flow vanes 207, coherently altering the pitch of the interior flow vanes 207 and the runner blades 211 optimizes the efIiciency of the turbine over a range of flow velocities and generator loads. The algorithm for control of the pitch of the interior flow vanes 207 and the runner blades 211 is illustrated by FIG. 16, the mechanism for this control is illustrated by FIGS. 4,

45 intake 103 by assuming an alternate position with respect to the fixed rudders 104, 105, 106. By rotating the rudders 302, 303, in case over a long period of use the screen-covered intake 103 gets covered with tenacious debris such as seaweed, the turbine changes orientation such that the face

5, 6 and 7 and is discussed in further detail in subsequent paragraphs.

50 is no longer orthogonal to the streamlines of the motive fluid thereby allowing the motive fluid to wash the debris from the screen-covered intake 103. This alternate embodiment exhibits another difference resulting from the aforemen-

One skilled in the art may recognize the turbine in the 55

preferred embodiment of the present invention as a variation of the turbine invented by Viktor Kaplan in the first quarter of the twentieth century. The choice of this type of turbine, particularly a member in the class of impulse turbines originates from the notion that a free flowing motive fluid is 60

inherently impulsive in nature, i.e. energy is optimally extracted by mechanically responding to the forces of a changing flow velocity impinging upon the turbine blades; as opposed to a member in the class of reaction turbines which derives energy in a system where static pressure in the 65

draft area draws the runner into motion, an action similar to that of a siphon. In particular, the Kaplan turbine is well

tioned rotatable rudder feature that can be seen by compari­son of the support columns 209 of FIG. 2 and the support columns 304 of FIG. 3. The modijlcation to include hollow areas in the support columns 304 in which concentrically situated shafts 305, 307 drive the rotatable exterior rudders 302, 303 embodies the conduit for torque to the rotatable rudders 302, 303 originating from a driving motor member contained within the generator housing 206. Conversely, the support columns 209 of FIG. 2 strictly structurally reinforce the generator housing and impart power and control signals through slip rings in the columns 209 in the vicinity of the gimbals on the same axis as bearing 107 and its complement not shown on the opposite side of the turbine shroud 102. Greater detail into how power and control signals are routed

US 6,956,300 B2 9

as well as the mechanism for the rotatable rudders 302, 303 and the control of it follows in FIGS. 6, 7, 8, and 16, and subsequent paragraphs.

FIG. 4 illustrates a partially exploded perspective view of the pinion and motor mechanism for adjusting the interior 5

flow vanes, runner blades and gate wickets in FIG. 2. When an adjustment in any of the set of interior flow vanes 207, runner blades 211, or gate wickets 203 becomes necessary, for each set of interior flow vanes 207, runner blades 211, or gate wickets 203 one instance of the motor in FIG. 4 in the 10

preferred embodiment a DC stepper motor 404, with its stator windings 410, 411 energized in the appropriate sequence, actuates rotational motion in its rotor shaft 403, in this example represented by arrow 413. The DC motor 404 has at the end of its rotor shaft 403 affixed to, forge or cast 15

into a pinion 402 that meshes with the inner gear of a circular rack gear 400. Briefly directing the discussion to FIG. 5, an alternate view of this circular rack gear 400, meshing its inner gear 401 with the pinion 402 affixed, forged, or cast onto rotor shaft 403 is shown. Returning to FIG. 4, one can 20

see the outer gear of the circular rack 400 engages the pinions 405, 406, 407 affixed, forged, or cast to the actuator shafts 408,409. These actuator shafts 408, 409 represent any one of plural instances of the shafts previously alluded to, the shafts that drive the set of interior flow vanes 207, runner 25

blades 211, or gate wickets 203. The mechanism driving the shafts 305, 307 for the rotatable rudders 302, 303 has some minor dilTerences and is portrayed in FIG. 8 and will be addressed subsequently. The gear ratio of the pinion 402 to the inner rack gear 401 multiplied by the gear ratio of the 30

outer rack gear of the circular rack 400 to the actuator shaft pinions 405, 406, 407 defines the translation of torque and angular displacement derived from the rotor shaft 403 resulting in the motion on the actuator shafts 408, 409 depicted by arrows 414, 415, 416 corresponding to each of 35

the interior flow vanes 207, represented by arrows 208; each of the runner blades 211, represented by arrow 212; or each

10 Several fundamental advantages arise from employing a

DC stepper motor 404, in actuating motion in the interior flow vanes 207, runner blades 211, gate wickets 203, or rotatable rudders 302, 303. Ibe stepper motor is inherently a precise means of translating rotational displacement and therefore requires no feedback, or in other words may be implemented in an open-loop configuration affording more circuit complexity devoted to higher-level control of the system. Secondly, given the preferred means of bi-directional anti-backlash and position locking mechanism for the circular rack gear 400 as illustrated in FIG. 6, the stator coils 410, 411 of the DC stepper motor need powering only in the instances of performing an adjustment, serving to improve the overall efficiency of the turbine. Also, because this adjustment period comprises an exceedingly short duty cycle, in the order of tens of milliseconds every second in the most active member, the current for the stator coils 410, 411 is limited by the breakdown voltage of the coil winding insulation, not the thermal wear of the coil itself, as the average power dissipated by its resistive losses are averaged over a much longer period than its duty period. With the use of higher energizing currents, depicted by arrows 412, comes the advantage of greater torque deliverable to the actuated members in a more space efficient sized DC stepper motor.

In more detail, the components of FIG. 6 includes to the right of the circular rack gear 400, all the components previously defined in FIG. 4 and the foregoing paragraphs, with the addition of a solenoid 600 with a plunger 602 that engages between the teeth of either the inner gear 401 or the outer gear of the circular rack gear 400 to stop motion in the actuated members. The actuated members were omitted from FIG. 6 for sake of clarity though it could be presumed that the actuated members are situated as depicted in FIG. 4 or FIG. 8. The torque translated back to the plunger 602 from the actuated members is contained by the mounting of the solenoid core 600 and the stops 603 cast or forged on the inner surface of the generator housing 206, coaxial Huid coupler 210, or fixed gate shaft 204. The solenoid core 600 is shown spring loaded, with the solenoid spring 601 com­pressed by the retracted plunger 602 when the solenoid coil 604 has current flowing as depicted by arrows 605, in accordance to the right-hand rule. The physical positioning of the solenoid 600 core and the DC stepper motor 404 and its shaft 403 is displayed in a collinear orientation to attest the importance of mounting these components along the central axis of the turbine mounted within the gimbal in such a manner as to not disrupt the balance necessary, otherwise mechanical oscillation may occur thereby harming the sys-

50 tem efficiency and possibly causing stress and shortened life of various components.

of the gate wickets 203, represented by the arrows 205. Because a singular instance of the mechanical assembly given in FIG. 4 actuates one set of each of the interior flow 40

vanes 207, runner blades 211, or gate wickets 203, the location of these assemblies may be found in separate locations within the turbine shroud 102. In the preferred embodiment, the location for the assembly of FIG. 4 for the interior flow vanes 207 would optimally be placed within a 45

central location of the generator housing 206; the location for the assembly of FIG. 4 for the runner blades 211 would optimally be placed within a central location of the coaxial fluid coupler 210; while the location for everything to the left of the shaft 403 of the assembly of FIG. 4, if not the entire assembly itself for the gate wickets 203 would opti­mally be placed within a central location of the fixed gate shaft 204. The advantage of using the circular rack gear 400 versus a simple worm gear mechanism is that especially in the instance of the interior flow vanes 207, the circumfer­ence of the inner gear 401, as most visible in FIG. 5, avails maximal clearance for the generator, itself. Obviously, a simple worm gear or single pinion to shaft coupling gear, for example the rack gear 400 directly affixed to the rotor shaft 403, may be implemented where central clearance is not critical. While this means of actuating motion in the interior flow vanes, runner blades, or gate wickets presents a novel departure from prior art, this preferred means is purely discussed in an exemplary manner, illustrative, not restrictive, and therefore any deviation from the above specification does not constitute a significant departure beyond the scope of the present invention.

FIG. 7 illustrates the flowchart for synchronizing the bi-directional anti-backlash and position locking mechanism of FIG. 6 to the pinion and motor mechanism of FIG. 4.

55 From the start, the DC stepper motor stator coils 410, 411 and the bi-directional anti-backlash and position locking solenoid coil 604 is in the de-energized state 700. When any of the aforementioned actuated components requires an adjustment, assuming the present position of one of these

60 components coincides with the position of the DC stepper motor rotor shaft 403 when its stator coil 410 is energized, the stator coil 410 is once again energized, state 701. Upon energizing the stator coil 410, the solenoid coil 604 is energized with a current as depicted by arrows 605, thereby

65 causing the solenoid plunger 602 to retract and to unlock the present position by disengaging the plunger 602 from the teeth of the circular rack gear 400, state 702. Then to affect

US 6,956,300 B2 11

the necessary adjustment, assuming the position of the next step corresponds to energizing stator coil 411, a current depicted in FIG. 6 by the arrows 412 energizes stator coil 411 while stator coil 410 is de-energized. This actuates the motion in the rotor shaft 403 depicted by arrow 413; the 5

direction of this arrow is arbitrary as implied by the term bi-directional anti-backlash and position locking meclla­nism. This completes states 703 and 704 for this example, though the system could continue to step in this manner through an arbitrary number of stator coils on the DC stepper 10

motor 404, by reiterating state 703 as necessary to achieve the desired set point position of the rotor shaft for this adjustment. Upon obtaining the desired position, the sole­noid coil 604 is de-energized by interrupting the current depicted by arrows 605, thereby permitting the solenoid 15

spring 601 to decompress causing the solenoid plunger 602 to re-engage the teeth of the circular rack gear 400 at the new position, performing the operation of anti-backlash and position locking, state 705. Since this circular rack gear 400

12 the actuator shafts 305, 307 depicted by arrows 811, 812, corresponding to the torque and angular displacement of the rotatable rudders 302, 303. As shown in FIG. 3, because the rotatable rudder shafts 305, 307 conjoin within a central location of the generator housing 206, and the circular rack gear 800 is perfectly analogous to the circular rack gear 400, the circumference of the inner gear 801 or as most visible in FIG. 5, the circumference of inner gear 401, avails maximal clearance for the generator, itself. Obviously, a simple worm gear or single pinion to shaft coupling gear, for example the rack gear 800 directly affixed to the rotor shaft 803, may be implemented where central clearance is not critical. While this means of actuating motion in the rotatable rudders presents a novel departure from prior art, this preferred means is purely discussed in an exemplary manner, illustrative, not restrictive, and therefore any deviation from the above specification does not constitute a significant departure beyond the scope of the present invention.

FIG. 9 illustrates a system of gears that decreases rota­tional velocity and displacement from the rotor shaft of a motor to an actuated member, or conversely, increases rotational velocity and displacement from an actuating member to a rotor shaft of a generator. Member 900 may either be an AC induction or a DC generator or motor

is further coupled to plural actuated members through gears 20

405,406,407, and there remains some play in the gears, this results in some motion associated with backlash in the actuated members. But the precision of the rack gear 400 should be fine enough that this resultant motion in the actuated members is negligible for the overall system response. In the final state 706, the stator coil 411 is de-energized and the new position of the actuated member and of the corresponding stator coil is placed in a register, of discrete logic or microprocessor register or memory space,

25 depending on the synchronous speed of the rotor compared to the armature current frequency in the case of the AC induction motor or generator, or in the case of the DC motor or generator, the direction of the armature current depicted by arrows 909, flowing through the armature coil 901.

as DC stepper motors are amenable to digital control due to their discrete means of determining rotational displacement. More detail of the higher-level system control will follow in subsequent paragraphs and FIG. 16.

FIG. 8 illustrates a partially exploded perspective view of the pinion and motor mechanism for adjusting the rotatable rudders 302, 303. Most of the components of FIG. 8 are analogous to FIG. 4 with the exception of the circular rack gear 400 now having two beveled edges for the circular rack gear 800 of FIG. 8. Because the rotatable rudders 302, 303 need to move in the same direction in the horizontal plane to cause the screened face of the intake 103 to assume a non-orthogonal orientation with respect to the streamlines of the free flowing motive fluid, the pinion of one of the rotatable rudder shafts needs to mesh on the opposite side of the circular rack gear 800 compared to the pinion of the other rotatable rudder shafts. FIG. 8 illustrates this require­ment by displaying first the current 809 flowing through the stator winding 808 of the DC stepper motor 804, assuming the current previously flowed in stator winding 807, causing the rotor shaft 803 to rotate in the direction of arrow 810. As before, in the preferred embodiment, because the bi-directional anti-backlash and position locking mechanism in FIGS. 6 and 7 captivates the circular rack gear 800 while

30 Therefore the speed voltage presented across the conductors of the armature coil 901 by the current 909 is proportional to the rotational velocity of the actuator 908 represented by arrow 912 multiplied by the ratio of gear 907 to gear 906 multiplied by the ratio of gear 904 to gear 903. The arrows

35 910, 911, and 912 merely describe the translation of motion through the gears. The physical positioning of the actuator 908 and the motor or generator 900 and its rotor shaft 902 is displayed in a collinear orientation, though as some implementation of these mechanical components of FIG. 9

40 most likely will not occupy a location within the turbine shroud 102, this is purely shown as a means most efficient for space. In some embodiments this mechanical assembly will occupy a space within the generator housing 206 and thus the actuator 908, the motor or generator 900, its rotor

45 shaft 902 and the tertiary shaft 905 is displayed in FIG. 9 in a collinear orientation as previously, to attest the importance of mounting these components along the central axis of the turbine mounted within the gimbal in such a manner as to not disrupt the balance necessary, otherwise mechanical

50 oscillation may occur thereby harming the system efficiency and possibly causing stress and shortened life of various components. This specification will expound upon the pur­pose of this mechanical assembly in FIG. 9 in subsequent

at rest, the direction of rotation depicted by arrow 810 is arbitrary. The motion depicted by arrow 810 causes the 55

circular rack gear 800 to rotate in the same direction due to the meshing of the rotor shaft pinion 802 to the inner gear 801 of the circular rack 800, whose outer gear meshes with the actuator shaft pinions 805, 806 resulting in motion shown by arrows 811, 812. Actuator shafts 305, 307 thus 60

turn the rotatable rudders 302, 303 in the same direction in the horizontal plane. As with the other actuators, the gear ratio of the rotor shaft pinion 802 to the inner rack gear 801 multiplied by the gear ratio of the outer rack gear of the circular rack 800 to the actuator shaft pinions 805, 806, 65

deJ1nes the translation of torque and angular displacement derived from the rotor shaft 803 resulting in the motion on

paragraphs and in FIGS. 13 and 15. FIG. 10 details the base 116 and associated mechanical

components below it. The broken line deJ1ned by points 1000 and 1001 indicate alternate views. The left side of the broken line 1000-1001 views from underneath the center of the base 116 looking outward orthogonal to the rails, while the right hand side of the broken line 1000-1001 views the underneath of the base 116 from a distance parallel to and in between the rails 119. The base 116 rests on the supports 1008 coupled to the axle of the rollers 117. The rollers 117 rotate freely on the rails 119. The rails 119 are secured to a foundation 1002. In the preferred embodiment, this founda­tion 1002 is formed reinforced concrete, though it could consist of the local natural rock formation depending upon

US 6,956,300 B2 13 14

output amplitude profiles 1105, and 1106 are indicative of a small, short duration impulse in the vertical direction with greater amplitude and duration in the horizontal axis as the onshore bore and offshore retreat associated with plunging or surging breakers proceeds. Ideally the optimal placement of the turbine system would be in the vicinity of buoy 1107 or buoy 1110 whose accelerometer's output signal profiles in the horizontal axis 1108 and 1111 respectively indicate greatest magnitude in the likely form of a large impulse with

10 a decay oflong duration in the onshore direction as the wave plunges or surges and a linear ramp-up in the offshore direction as it retreats. The vertical components 1109, 1112 would also likely exhibit an impulse of large amplitude of only short duration while being lifted by the onshore bore.

where the application of this invention occurs. Ideally this foundation 1002 is located on the tip of a headland formation where wave energy is most focused, and is sloped of adequate angle with respect to the true horizon so to elicit breaking waves of the plunging or surging type that transfer 5

wave energy into particle velocity in a most concentrated location and succinct time frame. The rails 119 have cutouts 1003 that permit cross flow and thus prevent sand from drifting to the point of obstructing the movement of the drive gears 1005 that meshes with the rail rack gear 1004. When stationary, the drive gears 1005 lock indirectly by coupling through its axle 118 to an internal drive gear not shown locked by a means such as the previously described bi-directional anti-backlash and position-locking mecha­nism to hold the drive gears 1005 steady in the path along the rail which also create tension to hold the system upright against any lateral tilting force. In the preferred embodiment, the means of driving the gears, again most easily implemented as a DC stepper motor, will likely occupy an area in the lower portion of the main shaft 115 or perhaps a compartment not shown under the base 116. The rotor shaft of this motor therefore occupies a location concentric to the drive shaft housing 1006 and has a worm gear not shown on its end occupying the gear box 1007. Said worm gear meshes with the internal drive gear, not shown inside the gear box 1007, but parallel to the gears 1005 and mounted such that it directly drives the axle 118. The bi-directional anti-backlash and position locking mechanism not shown also occupies the gear box 1007 and mates and locks the internal drive gear not shown inside the gear box 1007. A detailed discussion of exemplary sensor input means and the control algorithm itself for the above rail system follows in subsequent paragraphs describing FIG. 11 and FIG. 16.

FIG. 11 illustrates a system of buoys 1104, 1107, 1110, 1113 mounted in a collinear orientation parallel to the ordinary direction of onshore flow of breaking waves, orthogonal to the tangent of the shoreline 1100. This system

15 Of course the output profiles of buoys 1107, 1110 would vary from that shown to something more resembling the output profiles from the buoys on the ends, as the location within the surf zone of the breaking waves 1102,1103 varies with time. Statistical and frequency domain analysis could

20 serve to determine the optimal location for extracting energy within the surf zone amongst these two buoys 1107, 1110 and will subsequently be expounded upon. While shown in an orientation parallel to the ordinary direction of onshore bore of breaking waves, both this buoy system and particu-

25 larly the rail system is equally suitable for implementation across an inlet, orthogonal to its tidal bore, or across a river orthogonal to its flow. Thus the buoy and especially the rail system exists for adaptively locating the entire turbine system to an area of optimal flow, regardless of body of

30 water wherein implemented or whether the variation of location of optimal flow velocity is diurnal due to tides or seasonal due to weather patterns. Uses other than the afore­mentioned alternate uses including removal of the unit from obstructing waterway traffic or removal for facilitated main-

35 tenance do not constitute a substantial departure beyond the scope of the present invention. The control algorithm of the complete system including the implementation of the buoy and rail system will be delineated in FIG. 16 and subsequent paragraphs.

FIGS. 12, 13, 14, and 15 depict various coupling con-figurations and energy extraction means from the coaxial fluid coupler or other actuator means through to the output conditioning circuitry of the electric generator. FIG. 12 shows the fluid coupler 210 having a shaft 1201 that directly

45 couples to the rotor shaft of an AC generator 1200. TIle fluid coupler 210 physically occupies the space within the draft area of the shroud 102, while the coupler shaft 1201 extends into the generator housing 206. Note that the shaft 1201 in FIG. 12 is a simplified representation of the coaxial fluid

of buoys aids in adapting the gimbal-mounted turbine to maximal flow along the path of the aforementioned rail 40

system. The buoys 1104, 1107, 1110, 1113 are equipped with accelerometers or other means of measuring force or accel­eration and their output signal proJlles 1105, 1106, 1108, 1109, 1111, 1112, 1114, 1115, respectively portray charac­teristics relative to the position of breaking waves. For example, the buoy 1113 shown to the right, or offshore from the breaking wave 1103 has accelerometers or any other means of measuring force or acceleration including but not limited to spring actuated scales. Here the accelerometers mounted on buoy 1113 outputs two unique signals, i.e. voltages, corresponding to physically a horizontal compo­nent and a vertical component of force or acceleration which over time span the range delineated by arrows 1114 and 1115, respectively. Because this buoy 1113 is situated off­shore with respect to the breaking wave, one may expect these signal amplitude proJlles 1114, 1115 to be of moderate amplitude and of sinusoidal waveform, as one would expect from the undulating motion atop shoaling, but non-breaking waves. Note that the output profiles of all the vertical components 1106, 1109, 1112, 1115 of all the accelerometers show a greater extent in the downward direction. This indicates the constant offset produced by the force of gravity, and may be used to determine the relative angle of the buoy accelerometer system to true vertical and horizontal axes.

50 coupler shaft, and in the preferred embodiment would likely also contain slip rings to impart electrical power and control signals to the aforementioned electromechanical means internal to the coupler 210 for adjusting the pitch of the runner blades 211. In one embodiment, the AC generator

55 1200 would preferably be an AC induction generator of adequate number of poles such that its synchronous speed, which determines whether the AC machine is operating in its generator or motor region according to its torque-slip curve and is inversely proportional to the number of poles, is well

60 below the average rotational velocity of coaxial fluid coupler 210, and therefore the AC machine operates with positive slip as a generator. As previously mentioned the ratio of the area of the screen-covered intake 103 to the area orthogonal to flow within the draft section in the shroud 102 that the

On the other end of the line of buoys, the first buoy 1104 65

going from the beach in the offshore direction is located onshore from the last breaking wave 1101. Its accelerometer

fluid coupler 210 occupies is directly proportional to the ratio of velocity of the motive fluid approaching the runner blades 211 to the velocity of flow entering the screen-

US 6,956,300 B2 15 16

self-excited shunt field winding configuration chosen for its combined simplicity and relatively constant voltage inde­pendent of load current. The DC generator 1400 then produces a speed dependent DC voltage on the leads 1401

covered intake 103, and therefore also determines the aver­age rotational velocity of the fluid coupler 210, and thus also affects the calculation of the required synchronous speed of the generator 1200. What makes the AC induction generator preferable is its economical, reliable construction and wide­spread use, rendering this type of generator easily attainable and cost effective. Also, asynchronous AC induction gen­eration requires little additional circuitry in order to apply power directly to the utility power grid. In the case of unavailability of an AC generator of sufficient number of poles for an adequately low synchronous speed to operate with positive slip given the average rotational velocity of the fluid coupler 210, FIG. 13 depicts an AC induction generator 1200 indirectly coupled to the coaxial fluid coupler 210 through the gear system 1300. The gear system represented by block 1300 in its simplest implementation is that of FIG. 9 wherein this implementation the actuator shaft 908 is the coupler shaft 1201 and the rotor shaft 902 is that of the AC induction generator 1200, and the gear system increases the rotational velocity of the rotor shaft with respect to the coupler shaft 1201 as previously described. The gear system would likely occupy space within the generator housing 206

5 and 1402 that feeds the power conditioning circuit block 1403. The power conditioning performed within the circuit block 1403 could include filtering spurs caused by commutation, and regulating voltage and current for opti­mally applying the generated power to output means. Regu­lation would preferably be of the most efficient known

10 variety, in most cases chopped or in other words, switch-mode buck, boost or buck-boost regulation, depending upon the speed voltage of the generator 1400 and the load requirement. A variety of loads may be applied by connec­tion to the leads 1404, 1405 depending upon end user needs.

15 Examples of loads could include charging any variety of available chemistries of batterv; the leads 1404 and 1405 themselves could terminate as the electrodes in the process of electrolysis of water to produce hydrogen fuel; or the leads 1404 and 1405 could further power a DC motor

20 coupled to a synchronous AC generator directly applied to the utility power grid.

In the case of the load being the charging batteries, the circuit block 1403 could occupy the physical location of the generator housing 206, but because the process of battery

25 charging generally requires low-error voltage sensing at the battery terminals and low-error temperature sensing from a thermistor within the cell packaging powered by an accurate reference, it would likely be more feasible and economical to locate the power conditioning circuit block 1403 in

in proximity to the generator 1200. From the generator 1200 comes two leads 1202 representing the power mains off of the armature coil of the generator 1200. Though two leads 1202 imply a single-phase machine, this is purely exemplary, and no pre-determination is placed on the num­ber phases of the machine in the preferred embodiment. In order to directly apply the voltage from the AC induction generator 1200 to the utility power grid through wires 1204, 1205, the electrical circuit represented by block 1203 con­tains a watt-hour meter, and a speed dependent switch that receives an input signal from a velocity transducer sensing the rotation of the coupler shaft 1201 in the generator housing 206. The velocity transducer output signal would therefore also need to be physically routed along the same path as the leads 1202, either on its own conductor or modulated upon the armature coil power current. This speed dependent switch affords highest efficiency and protection such as when the coupler shaft has inadequate velocity for 40

positive slip, or there exists a fault condition on either side

30 proximity of the battery unit to be charged on shore. Therefore the leads 1401, 1402 would likely route uncon­ditioned DC power from the generator 1400, through slip rings in the columns 209 in the vicinity of the gimbals on the same axis as bearing 107, through slip rings near bearing

35 109, down to the base 116, out along the rail system 119 to the onshore location of the circuit block 1403.

of the circuit block 1203, the generator 1200 becomes disconnected from the utility power grid. The circuit block 1203 is likely physically located on land away from the turbine unit, with the leads 1202 routed from the generator 45

1200, through slip rings in the columns 209 in the vicinity of the gimbals on the same axis as bearing 107, through slip rings near bearing 109, down to the base 116, out along the rail system 119 to the onshore location of the circuit block 1203. As with the leads before the circuit block 1203, though 50

only a pair of wires 1204, 1205 are shown implying a single-phase system, this is purely exemplary with no pre­determination of the number of phases that may be applied to the utility power grid.

Another exemplary load could be the current required to perform electrolysis on water to produce hydrogen fuel. This process achieves a high efficiency due to inherent advan­tages in the preferred embodiment of the present invention. Seawater is naturally electrolytic thereby reducing chemical processing costs; and advanced electrolysis methods allow for a voltage as little as one and a half to two volts applied across the electrodes, which the generator 1400 in the self-excited shunt field winding configuration can easily provide over a wide range of rotational velocities of the fluid coupler 1201. In one embodiment, the cavity 202 within the shroud 102, otherwise vacant to provide buoyancy to the turbine, could also provide the physical volume to store the hydrogen fuel output from the process of electrolysis of water. Given the requirements for such a system for electrolysis, the circuit block 1403 could consist of simply a filter capacitor to smooth the spurs caused by the com­mutator of the DC machine, and likely a switch-mode buck or in other words, stepdown DC-to-DC converter, perhaps with some form of current regulation, to provide the appro-priate voltage to the electrodes 1404, 1405 to perform electrolysis. Because this circuit block 1403 is relatively simple and compact, it would most economically occupy an

Alternately, the circuit block 1203 may take the AC 55

voltage produced by the generator 1200 from leads 1202 and full-wave rectify the AC voltage into a DC voltage, then filter and further regulate the voltage and current for optimal power conditioning for application to loads as described in the following paragraphs regarding DC power generation. 60 area adjacent to the generator 1400 within the generator

housing 206, with the leads 1404 and 1405 routing condi­tioned DC power to the electrodes contained within the appropriate sections of the cavity 202 in the shroud 102,

FIG. 14 illustrates an alternate arrangement from the coaxial fluid coupler 210 through to the power output means. Here the simplified representation of the coupler shaft 1201 is shown directly coupled to the rotor of a DC generator 1400. The DC generator 1400 may be any of available forms 65

of DC generator, including but not limited to a com mutated or semiconductor-rectified generator, and preferably with a

producing hydrogen fuel stored in the cavity 202 generated through electrolysis of seawater admitted into the appropri­ate section of the cavity 202 in a controlled manner through a filter membrane.

US 6,956,300 B2 17

A third exemplary load for the DC generator 1400 could exist in the form of the leads 1404, 1405 attached to a DC motor further coupled to an AC synchronous generator directly applied to the utility power grid. In consideration of this application, the circuit block 1403 would necessarily not 5

only require filtering to smooth the spurs caused by commutation, and voltage regulation to maintain constant speed in the DC motor coupled to the synchronous AC generator, but likely would further require high capacity charge storage devices in the form of a very large capacitor 10

or bank of capacitors or possibly a battery, also in order to maintain constant speed in the DC motor coupled to the synchronous AC generator during periods of reduced rota­tional velocity in the axial fluid coupler 210. The complexity and physical volume of such a circuit dictates that the circuit 15

block 1403 is located in the vicinity of the DC motor and AC synchronous generator. As such, the leads 1401, 1402 would likely route unconditioned DC power from the generator 1400, through slip rings in the columns 209 in the vicinity of the gimbals on the same axis as bearing 107, through slip 20

rings near bearing 109, down to the base 116, out along the rail system 119 to the onshore location of the circuit block 1403.

18 such that it then operates as a motor, or to switch-in an AC voltage of amplitude and frequency such that the AC induc­tion machine then operates as a motor to affect this change in orientation.

FI G. 16 illustrates the overall control of all the compo­nents described thus far of the complete gimbal-mounted turbine for adaptively extracting energy from a free flowing motive fluid that continuously changes direction and mag­nitude of flow. While FIG. 16 displays a flowchart, which is ordinarily associated with a computer program running in software, the algorithm delineated may be implemented with any combination of hardware or software such as linear or analog circuits or discrete digital circuits or an integrated central processing unit, or a microprocessor. One advantage a central processing unit or microprocessor affords is con­venient means to gauge, test, and communicate to a central service logging location the state of any part of the system, including functionality, or fullness of charge of batteries, or hydrogen fuel tanks, etc., using means such as well-defined existing serial protocols or wireless standards. From the start 1600, the controller is continuously sampling and storing 1601 such variables as the main generator output voltage, denoted Vo, and the output voltages from the accelerometers affixed to the buoys and from there proceeding in four

25 concurrent paths through the flowchart. While not specifi­cally stated in block 1601, it may be assumed all sampled variables including the signals representing the outputs of the gimbal motion sensors and/or the auxiliary generator are being sampled and stored in a likewise continuous, concur-

FIG. 15 illustrates an auxiliary generator 1500 attached through a system of gears 1300 to an actuator 1506. The proposed primary provider of mechanical torque for this auxiliary generator 1500 is the rotating sections in the vicinity of the bearing 109. Gear 1506 rotates while its teeth mesh with a circular rack gear not shown of greater circum­ference than, and concentric to, the bearing 109, affixed to the follower brace 120 rotating with respect to the main shaft collar 111. In this instance the actuator shaft 908 would be coaxial, but not likely concentric, to the main shaft collar 111, and the gear system 1300 and the auxiliary generator 1500 would also occupy a location affixed within the main shaft collar 111. This axis of the gimbal is chosen given that the onshore bore and offshore retreat of breaking waves acting upon the rudders and the gimbal would give this axis significant periodic motion, though in other implementations, the other axis of the gimbal may prove prolific in extracting power. As before, the block 1300 represents the system of gears described in FIG. 9, the end result is that the auxiliary generator's 1500 rotor shaft exhibits a higher rotational velocity compared to the fol­lower brace 120. In the preferred embodiment, the generator 1500 would likely be either an AC induction generator with external semiconductor rectification and velocity-controlled switching or else a DC generator. This auxiliary DC power generated could then be applied to either a separately excited field winding of the main generator or additively coupled to 50

the output of the main generator through means of switch mode circuitry such as coupling in series a secondary winding of a transformer with rectifiers for voltage boosting

30 rent manner as implied by the looping arrow exiting only to return to the upper right corner of block 1601. In the preferred embodiment, this sampling period would have a time resolution necessary to react to and control mechanical processes, ordinarily sampling at approximately a frequency

35 of about a hundred times a second, or a period of about ten milliseconds, with a small deviation allowable possibly due to the convenience of a local non-integer multiple frequency digital clock from which to derive this sampling clock frequency. These samples would then get averaged over a

40 space of five to ten samples, this average representing a single sample in order to reduce the effects of noise. It is reasonable that no control process or adjustment would need to occur, or could efficiently occur for that matter, more often than ten to twenty times a second. Note that the four

45 concurrent paths through the flowchart as well as some of the processes undergone in those paths are implementation specific. Obviously if certain hardware components were omitted, that would then render the associated process obsolete.

or coupling in parallel a charge pump circuit for current boosting. Circuit block 1503 and leads 1504, 1505 would 55

likely occupy a space within the generator housing 206 in the case of providing current to a separately excited field winding of the main generator, or else the same location as the power conditioning circuitry employed in the above applications. An alternate purpose for this electromechanical 60

assembly exists in case over a long period of use the screen-covered intake 103 gets covered with tenacious debris such as seaweed, the turbine may change orientation such that the face is no longer orthogonal to the streamlines of the motive fluid thereby allowing the motive fluid to wash 65

the debris from the screen-covered intake 103, simply by reversing the current on leads 1501, 1502 of the DC machine

In practically all conceivable embodiments, there would always exist the path that serves to adjust the internal flow vanes 207 and runner blades 211 to optimize internal flow velocity approaching the axial fluid coupler 210 over a range of velocities of the free flowing motive fluid itself external to the turbine shroud 102. Thus in the flowchart of FIG. 16, the path proceeds from the sampling block 1601 to the decision block 1605, where the instantaneous magnitude of the sampled main generator output voltage, IVol, is com­pared to an upper threshold. This upper threshold would likely equal in excess of one hundred percent of, but less than two times, the rated voltage of the generator. Various types of circuits may perform this comparison through either digital sampling followed by numeric comparison or through analog comparators in effect triggering the DC stepper motors that actuate such adjustments through a voltage feedback loop. Hence, the outcome of this compari­son in block 1605 determines whether to throttle up 1608, or

US 6,956,300 B2 19

throttle down 1607, the velocity of the flow through the turbine by adjusting the internal flow vanes 207 and runner blades 211 accordingly. Using means described previously and depicted algorithmically in FIG. 7, to throttle up the internal flow velocity, the controller must tighten the pitch of the runner blades 211 to a larger angle with respect to the center axis of the turbine, and to throttle down, the pitch of the runner blades 211 becomes a smaller angle, closer to parallel to the center axis, all while adjusting the angle of incidence of flow with the internal flow vanes 207 appro­priately. This algorithm allows the generator to produce a maximum voltage throughout the period of usable flow.

A similar path through the flowchart exists for controlling the open or closed state of the gate. The gate in the present invention primarily functions in two states, fully open and shut, as opposed to prior art where the gate continuously controlled flow as a means of maintaining synchronous operation over varying heads and loads. In the present invention, the gate closes to inhibit flow to enable the gimbal to rotate without the mechanical constraint of gyroscopic precession, which would otherwise exist due to the angular momentum of the axial fluid coupler 210. The path through the flowchart that exits block 1601 proceeding to block 1602 portrays the control of the gate. Here the instantaneous magnitude of the voltage output from the main generator IVai, is differentiated over time. From block 1602, the algorithm then proceeds to the decision block 1606 to determine if the derivative with respect to time of Ivol is practically zero. As shown in block 1606, the absolute value of the derivative is evaluated since a negative derivative merely implies the rotor is slowing, the absolute value evaluated to be lower than a threshold to account for some inaccuracy due to noise, if so, then implies a maximum or minimum in instantaneous output voltage magnitude. If the comparison finds the output voltage not at a maximum or minimum, it returns, otherwise the next step proceeds to block 1609, whereby comparing the instantaneous magni­tude of the output voltage Ivol to some threshold determines whether IVai is at a maximum or minimum. There it may also sense motion in the gimbal by directly observing the output of its motion sensor or indirectly by sensing the voltage generated by the auxiliary generator mechanically coupled to the associated axis of the gimbal. If the instantaneous output voltage of the main generator is below a threshold at this point, and/or motion is sensed in the gimbal, then the controller undertakes the process to close the gate 1611. The gate will remain in the closed state 1611 as long as the motion in the gimbal is sensed as depicted by decision block 1613. Upon gimbal motion ceasing, the gate opens 1615, and the algorithm returns to the start state 1600.

Another path exists based on processing the sampled instantaneous magnitude of the output voltage IVai to deter­mine the extent of control processes applied in order to optimally extract energy from a free flowing motive fluid. Proceeding to block 1603, integration over an interim period is performed to determine the energy extracted during that interim. It is then averaged over the number of samples during that interim period to determine the average power during that period. The interim period would best be defined by a number of samples corresponding to a power of two. First, a number of samples, n, where n is a power of two, can be averaged simply by shifting the binary fixed-point integer sum of n samples of IVaI, log 2(n) places to the right. Secondly, block 1614 performs calculations based on this variable and on the corresponding output of a Fast Fourier Transform, FFI~ which by definition of the FFT algorithm, must be calculated over a number of samples equal to a

20 power of two. The output variable of this averaging process 1603 is then input to update a long term average 1610 and then compared to a low threshold 1612 to determine if power is being extracted properly. If not, the controller proceeds to

5 block 1616, where the turbine attempts to remove debris obstructing its intake by means previously described. Oth­erwise if the rail system or the system of accelerometers affixed to buoys is left unimplemented, the algorithm then returns to the start, otherwise it continues in an interaction

10 with the accelerometer system to control the positioning along the rail system as subsequently described.

While the average power over an interim is being calculated, the output profiles of the accelerometers on buoys are sampled and sorted in a pattern matching algo-

15 rithm to determine the location of the most recent breaking wave relative to the nearest buoy based on the foregoing discussion of output profile characteristics, while the statis­tics are gathered to perform a linear spatial frequency analysis to determine the sequence of locations where the

20 waves break 1604. Whereas all previous blocks of the flowchart of FIG. 16 could have been performed without a digital processor, the complexity of the calculations per­formed in block 1604 likely require a digital signal proces­sor. As an example of the linear spatial frequency analysis,

25 much energy at a low frequency at a certain location in time and space indicates many instances of breaking waves are likely to occur in one location or gradually move in one direction, or gradually undulated over a short distance for a given time, where much energy at a high frequency would

30 indicate a large variability in break location for a given time, and thus increased difficulty tracking and diminished returns in energy invested tracking such a sequence of locations of breaking waves. The smallest period of time the frequency domain analysis could be based on is the interim period

35 previously described that preferably spans the minimum time required to identify an instance of a single breaking wave, thus furnishing amplitude data for that breaking wave sample. A number of these periods, or breaking wave samples, can then be accumulated such that the requirement

40 of a power of two samples for performing a Fast Fourier Transform is satisfied, to give a time dependent distribution of location or in other words, a procession, of breaking waves. Here the concern is that the number of sampled breaking waves is great enough that an accurate Fast Fourier

45 Transform may be computed without spanning such a period of time that the natural changes due to tides reduce the repeatability from one procession sequence to the next. While the presumption that over one hour the repeatability of the wave procession provides reasonable tracking, one

50 hour should permit two to four unique sequences of sixty four to two hundred fifty six breaking wave samples com­puted within an FFT.

Depending on the outcome of decision block 1612, if power generation proves greater than a lower limit, the

55 power extracted that correlates to optimal power, or in other words, power extracted during an interim period wherein the buoy accelerometers had identified a plunging or surging breaker occurring in close proximity before the face of the turbine, is compared 1614 to a threshold value, such as the

60 long term power average calculated in block 1610. Theoretically, a turbine of like embodiment of the present invention, with a face area of one square meter, can extract an average of approximately three horse-power or about two and a quarter kilowatts given the aforementioned breaking

65 conditions of a wave of one meter deep-sea height, and ten second period. If this type of wave is considered average for the place of installation, then occasions when the deep-sea

US 6,956,300 B2 21

wave height is doubled yield more than double the power output. Block 1614 attempts to determine such occasions that make close tracking of the procession worth the energy expended to do so. For instance, if the energy in the ocean is low that day, then the turbine should spend as little energy 5

as necessary tracking the procession of breaking waves as depicted in block 1618, just often enough to track the tide, the procession of which could be prerecorded in non-volatile memory as a type of almanac. However, on an occasion where the return on the energy invested makes tracking the 10

procession along the rail system worthwhile, block 1617 suggests as often as every interval, given high amplitudes and high energy in correlated low spatial frequency bins.

The previously described paths through the flowchart of FIG. 16 perform mathematical manipulations on the 15

sampled instantaneous magnitude of the output voltage, IVol in order to determine an appropriate course of action. The manipulations include differentiation and integration, and it should be known that any of the paths could share the outputs of these mathematical functions in order to improve 20

the overall control algorithm. While not explicitly depicted for sake of clarity in the flow diagram of FIG. 16, it may be inferred, and thus any deviation of the algorithm to include the additional use of these function output variables in decision blocks, or for that matter, use of a singular central 25

processor to also concurrently perform these and other control tasks not explicitly depicted, such as, but not limited to: charging batteries; or performing electrolysis; or elec­tronic means of motor speed control; adjusting to changes in load; or stepper displacement; or controlling an array of 30

gimbal-mounted turbines; or logging communications; does not constitute a substantial departure beyond the scope of the present invention.

From the detailed description above it is manifest that 35 various implementations can use the concepts of the present

invention without departing from its scope. Moreover, while the invention has been described with specific reference to certain embodiments, a person of ordinary skill in the art would recognize that significant alterations could be made in form and detail without departing from the spirit and the 40

scope of the invention. The described embodiments are to be considered in all respects as illustrative and not restrictive. It should also be understood that the invention is not limited to the particular embodiments described herein, but is

45 capable of many rearrangements, modifications, omissions, and substitutions without departing from the scope of the invention.

Thus, a gimbal-mounted hydroelectric turbine for adap­tively extracting energy from a free flowing motive fluid that 50

continuously changes direction and magnitude of flow has been described.

What is claimed is: 1. A turbine or other apparatus of power generation using

means responsive to motive fluid wherein the fluid intake is 55

implemented via a gate or penstock which is:

mechanically or electro-mechanically able to instanta­neously adjust its physical orientation in any direction to adapt to changes in the direction of the streamlines of a free flowing motive fluid; 60

wherein said apparatus is physically secured by a mount­ing system comprised of circular bearings in one axis or plural axes commonly implemented as a gimbal, to provide the ability to instantaneously adjust the physi-cal orientation of said fluid intake in any direction, to 65

adapt to changes in the direction of said free Howing motive fluid;

22 wherein the kinetic energy contained in said motive fluid

is converted to electrical potential; wherein said kinetic energy contained in the motive fluid

is converted to electrical potential by means of a coaxial fluid coupler or impeller directly driving the rotor of a DC generator, or, directly driving or indi­rectly driving through a system of gears, an AC induc­tion generator with external voltage rectifiers produc­ing a direct current output;

wherein the voltage output of said DC generator or said AC induction generator with external voltage rectifiers is sensed to control a gate which inhibits flow to reduce the rotational velocity of said coaxial fluid coupler or impeller thus reducing the forces of gyroscopic precession, so to quicken the response to changes in the direction of the streamlines of a free flowing motive fluid.

2. The apparatus of claim 1 wherein said gate is controlled by an electronic microprocessor sensing said voltage output of the DC generator or AC induction generator.

3. A turbine or other apparatus of power generation using means responsive to a motive fluid wherein the fluid intake is implemented via a gate or penstock which is:

mechanically or electro-mechanically able to instanta­neously adjust its physical orientation in any direction to adapt to changes in the direction of the streamlines of a free flowing motive fluid;

wherein said apparatus is physically secured by a mount­ing system comprised of circular bearings in one axis or plural axes commonly implemented as a gimbal, to provide the ability to instantaneously adjust the physi­cal orientation of said fluid intake in any direction, to adapt to changes in the direction of said free flowing motive fluid;

wherein the kinetic energy contained in said motive fluid is converted to electrical potential;

wherein said kinetic energy contained in the motive fluid is converted to electrical potential by means of a coaxial fluid coupler or impeller directly driving the rotor of a DC generator; or, directly driving or indi­rectly driving through a system of gears, an AC induc­tion generator with external voltage rectifiers produc­ing a direct current output;

wherein the voltage output of said DC generator or said AC induction generator with external voltage rectifiers is sensed to control adjustable interior flow vanes and adjustable runner blades of the fluid coupler or impeller by employing a voltage feedback closed loop so as to optimize efficiency over a range of loads and flow velocities.

4. A turbine or other apparatus of power generation using means responsive to a motive fluid wherein the fluid intake is implemented via a gate or penstock which is:

mechanically or electro-mechanically able to instanta­neously adjust its physical orientation in any direction to adapt to changes in the direction of the streamlines of a free flowing motive fluid;

wherein said apparatus is physically secured by a mount­ing system comprised of circular bearings in one axis or plural axes commonly implemented as a gimbal, to provide the ability to instantaneously adjust the physi­cal orientation of said fluid intake in any direction, to adapt to changes in the direction of said free flowing motive fluid;

wherein the kinetic energy contained in said motive Huid is converted to electrical potential;

US 6,956,300 B2 23

wherein said kinetic energy contained in the motive fluid is converted to electrical potential by means of a coaxial fluid coupler or impeller directly driving the rotor of a DC generator; or, directly driving or indi­rectly driving through a system of gears, an AC induc- 5

tion generator with external voltage rectifiers produc­ing a direct current output;

wherein the voltage output of said DC generator or said AC induction generator with external voltage rectifiers is electronically voltage and current regulated for 10

charging any of the presently available varieties of chemistry of battery.

5. The apparatus of claim 4 wherein said charging of a battery, including gauging and communicating the fullness of the battery is controlled by an electronic microprocessor. 15

6. A turbine or other apparatus of power generation using means responsive to a motive fluid wherein the fluid intake is implemented via a gate or penstock which is:

mechanically or electro-mechanically able to instanta­neously adjust its physical orientation in any direction 20

to adapt to changes in the direction of the streamlines of a free Howing motive fluid;

wherein said apparatus is physically secured by a mount­ing system comprised of circular bearings in one axis or 25

plural axes commonly implemented as a gimbal, to provide the ability to instantaneously adjust the physi-cal orientation of said Huid intake in any direction, to adapt to changes in the direction of said free flowing motive fluid;

wherein the kinetic energy contained in said motive fluid is converted to electrical potential;

wherein said kinetic energy contained in the motive Huid

30

24 7. A turbine or other apparatus of power generation using

means responsive to a motive fluid wherein the fluid intake is implemented via a gate or penstock which is:

mechanically or electro-mechanically able to instanta­neously adjust its physical orientation in any direction to adapt to changes in the direction of the streamlines of a free flowing motive fluid;

wherein said apparatus is physically secured by a mount­ing system comprised of circular bearings in one axis or plural axes commonly implemented as a gimbal, to provide the ability to instantaneously adjust the physi­cal orientation of said fluid intake in any direction, to adapt to changes in the direction of said free flowing motive fluid;

wherein the kinetic energy contained in said motive fluid is converted to electrical potential;

wherein said kinetic energy contained in the motive fluid is converted to electrical potential by means of a coaxial fluid coupler or impeller directly driving the rotor of a DC generator, or, directly driving or indi­rectly driving through a system of gears, an AC induc­tion generator with external voltage rectifiers produc-ing a direct current output;

wherein further energy may be extracted by implementing an auxiliary DC generator or AC induction generator with external voltage rectifiers indirectly coupled through a system of gears to one axis or plural axes of said gimbal.

8. The apparatus of claim 7 wherein the armature current of said auxiliary DC generator or AC induction generator with external voltage rectifiers may be reversed temporarily once over a long term period so as: to use the secondary is converted to electrical potential by means of a

coaxial fluid coupler or impeller directly driving the rotor of a DC generator; or, directly driving or indi­rectly driving through a system of gears, an AC induc­tion generator with external voltage rectifiers produc­ing a direct current output;

35 generator as a motor to affect the orientation of the face area of said fluid intake such that it no longer is orthogonal to the direction of the streamlines; thus:

wherein the voltage output of said DC generator is 40

electronically voltage and current regulated for driving a DC motor mechanically coupled to a synchronousAC generator with output armature voltage applied directly to the utility power grid.

causing the motive fluid to remove tenacious debris from the face of the intake during a routine self-maintenance period.

9. The apparatus of claim 8 wherein said intake physical orientation is controlled by an electronic microprocessor.

* * * * *

111111 1111111111111111111111111111111111111111111111111111111111111111111111111111 us 20060237970Al

(19) United States (12) Patent Application Publication

Bailey, SR. (10) Pub. No.: US 2006/0237970 At (43) Pub. Date: Oct. 26, 2006

(54) PERPETUAL MOTION COMPTROLLERS & ENERGY MOLECULE SPLITTERS

(76) Inventor: Rudolph Bailey SR., Manassas Park, VA (US)

Correspondence Address: RUDOLPH BAILEY SR. P.O. Box 221911 Chantilly, VA 20153 (US)

(21) Appl. No.:

(22) Filed:

11/331,474

Jan. 5, 2006

Related U.S. Application Data

(63) Continuation-in-part of application No. 10/811,382, filed on Mar. 27, 2004, now abandoned.

(60) Provisional application No. 60/644,725, filed on Jan. 18, 2005.

I~

/ 25

508

Publication Classification

(51) Int. Cl. 1l02K 7118 (2006.01) F03G 7108 (2006.01) F02B 63104 (2006.01)

(52) U.S. Cl. ...................................................... ....... 29011 R

(57) ABSTRACT

A method to convert a battery operated device into a perpetual motion machines has been disclosed. A method ±(lr splitting an energy molecule in two and making two mol­ecule from the one while recycling the energy has disclosed. The increased energy is used to offset that which will be loss due to friction, and to do useful work. A molecule splitter and comptroller is used to control the refurbishing of said batteries one at a time, and to rest the drive motor, so as to prevent the device from coming to a stop. Since the method used does not create new energy, but generate new energy by splitting the energy molecule, it does not violate the laws of energy conversion, or the laws of thennodynamics.

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PERPETUAL MOTION COMPTROLLERS & ENERGY MOLECULE SPLITTERS

DESCRIPTION OF RELATED APPLICATIONS

[0001] This Application is a continuation-in-part of co­pending application Ser. No. 10/811,382 filled on Mar. 27, 2004. This application also claims the benifit ofPPA Ser. No. 60/644,725, filed on Jan. 18, 2005.

BACKGROUND

[0002] This version of the invention Is concerned with the field of control devices used to control perpetual motion machines, and energy molecule splitters that can be used to increase the energy within a system. More specifically, this version of the invention is concerned with prior art control devices and technology using timing controls, and computer hardware and sotlware including alpha-digital or voice­sound conmlands or instructions, for a new and unintended, and unforeseen use, to produce perpetual motion which is believed to be both scientifically and practically impossible.

PRIOR ART

[0003] An exanlple of said control devices can be seen as is exemplified in U.S. Pat. No. 5,804,948 System for Zero Emission Generation of Electricity, issued to Frost on Sep. 8, 1998. Frost shows a comptroller 501 which switches back and forth between two 12-volt batteries 101 & 102 and an alternator 401. The purpose intended is to keep a generator 301 in operation for an indefmite period, without need for a separate recharging of said batteries.

DISCUSSION OF THE PRIOR ART

[0004] As illustrated by background art, efforts are con­tinuously being made in an attempt to develop control devices to facilitate perpetual motion machines. Frost's invention falls short of its intended goal, as the device is inoperable, and violates the second law ofthermodynanlics, and the laws of energy conversion. The device also makes improper use of component parts, hence the said comptroller would be of no value in facilitating perpetual motion of Frost's device.

[0005] The reasons are as following, Frost is using a 12-volt deep cycle bay to operate a 12-volt-li4HP motor, to operate a 12-volt alternator, to convert 12-volts into the IS-volts it would take to charge a 12-volt battery. The said action will violate the laws of energy conversion. In addition to that their would be friction and heat resulting in the loss of some of the energy from the 12-volt battery, so Frost's invention also violates the second law of thermodynamics. In addition to that Frost would also be using an automobile type alternator to recharge two discharged batteries, said alternators are not designed to charge a discharged battery, such charging must be accomplished by using a AC to DC trickle type battery charger. A.nother problem with Frost's invention is that a %-HP motor is not sufficient to operate a 12-volt Alternator when it is in a charging cycle, plus a 9,50Owatt generator. In addition to all that is mentioned, the said alternator would burn out prematurely as it would be in a charge cycle continuously as it charges one battery for four hours, and then the next battery for four hours, back and forth with no rest period. Additionally when said alternator is in a charging mode the resistance tends to slow down the

1 Oct. 26, 2006

drive motor, if no rest periods are introduced said drive motor will eventually come to a stop. I do not understand why a patent was granted on Frost's invention. As I men­tioned earlier this patent application only covers the comp­trollers and energy molecule splitters used in perpetual motion machines, and not the perpetual motion machine itself, that is covered in co-pending application Ser. No. 10/811,382, filed on Mar. 27, 2004.

[0006] As illustrated by background art, efforts are con­tinuously being made in an attempt to develop control devices in order to make perpetual motion machines become possible. No prior effort, however, provides a means atten­dant with the present invention. As such, it may be appre­ciated that there is a continuing need for the development of control devices to help make the benefits of perpetual motion machines available to hmnan kind. As such the present invention incorporates prior art technology for a new use, that was unforeseen and unintended, which when modi­fied to provide control devices that can facilitate perpetual motion machines. Additionally the prior patent and use of component parts do not suggest the present inventive com­bination of component elements arraigned and configured as disclosed herein.

[0007] The present invention achieves its intended pur­poses, objects, and advantages through a new, useful and unobvious combination of methods steps and component elements, with the use of a minimum number of functioning parts, at a reasonable cost to manufacture, and by employing only readily available materials.

SUMMARY

[0008] The present version of the invention, which will be described in greater detail hereinafter, relates to the field of control devices and energy molecule splitters that are used to help to make perpetual motion machines possible, includ­ing computer hardware and software and programs. More specifically, this version of the invention is concerned with a timing and switching and control component we call an energy molecule splitter, which incorporates prior art tech­nology for a new unintended, and unforeseen use, to help make perpetual motion machines possible.

[0009] In order to be able to described the present inven­tion briefly, according to a typical embodiment. We must first explain what we at JESUS & Bailey call the "Science of Perpetual Motion Machine". In order to develop perpetual motion and do useful work, one must Hrst be able to recycle the energy within a system or device, resulting in no waste or emissions. Next one must be able to split each energy molecule and take one molecule, and make two as one recycle said energy. In so doing one will be able to generate enough new energy within the system, to overcome what will be lost due to friction and heat, and also to do usefi.J1 work. Said new science is possible in a DC battery operated system.

[0010] Let us consider a 24-volt-DC circuit comprising two 12volt deep cycle batteries connected to give 24-volts. Additionally let us consider a 24-volt-DC motor being operated by said batteries. The motor will convert the electrical energy from the battery into turning motion. Said turning motion with the use of mechanical advantage could be used to set in motion a charging component such as an alternator, and the intended work load. Said charging com-

US 2006/0237970 Al

ponent could transfonn said tuming motion back to electri­cal energy. Said electrical energy could be used to refurbish said batteries, which would keep said drive motor in opera­tion indefinitely. This action will take care of the recycling step. However some of the energy from the battery will be lost due to friction and heat loss. If we use a 24-volt alternator as the charging component, we would have to generate 29-30volts to refurbish the said 24-volt batteries. One can easily see why that will not happen. Said example would violate the laws of energy conversion and the second law of thennodynamics. To eliminate the obvious need for outside energy to keep the system in operation, we have devised a way to increase the energy within the system without any energy from an outside source, by splitting the energy molecule, and making two from one.

[0011] Here is how this is accomplished. Suppose you had one telephone line coming into your home, and you needed another phone in another room, what would you do? Run another line? no, you would use a two-way signal splitter and you would have two full phones, not two hall phones although you split the signal in two. Let us apply that analogy to this problem. Instead of using one 24-volt alter­nator, suppose two 12-volt altemators were used instead, then we would be splitting the energy molecules in two. Now we cannot use both altemators at the same time or we will have the same original problem. Ifwe use one at a time we will begin to solve the problem. since we would be using a 24-volt by to convert to the 14.5-15-volts we would need to charge one 12-volt battery at a time. You would now have two full altemators each one capable of refurbishing the batteries. If you add up the volts from both alternators you get 3D-volts. This would be 25% more than we need to operate the system, hens we have enough energy to refurbish the batteries, replace that which will be loss due to friction and do useful work. Said example does not violate the laws of energy conversion. It does not violate the laws of ther­modynamics. since we are not creating new energy within the system, instead we are generating additional energy by splitting the energy molecules. Consider a wife and husband having a child, they do not say we created a new child, but the child is referred to as part of their generations, from the sanle root word. In like manuer the additional energy is not created but generated. The word create means to make something from nothing, and we are not doing that. When you split anything and make two things from the one you automatically have an increase. This is what the Lord Jesus did in the creation of the lUliverse, after He made man he put him to sleep and split him open and took a rib out, and closed him up, and with the rib, He made woman, and when the man and woman got together in the fullness of time, they continue to generate new life perpetually as long as tIlls world will last. When you follow a divine principle it always works.

[0012] Now we need a energy splitter & controller to control the charging process one battery at a time. This is the purpose of this patent application, and not to patent a perpetual motion machine, that is done in co-pending appli­cation Ser. No. 10/811,382 filed on Mar. 27, 2004. The Molecule spiller is a timing and switching comptroller that is comprised of a master control board, and an insulated hot pointer, a modulating motor with cams and collar, and three output terminals and one feed terminal. The comptroller is set to send 24-volts to each altemator's solenoids for one minute intervals, with two Yo minute rest periods per cycle

2 Oct. 26, 2006

for the drive motor, for a total charge cycle time of three minutes. This means that the altemations must operate at a rate, three times above the rate of the drive motor. This faster rate also allows the altemator to generate more anlps than the system takes to operate it. Hens trom calculations we can generate about 25 to 35% more amps than needed to operate the system. thus we can refurbish the batteries. overcome friction and to do useful work.

[0013] Our invention, therefore, resides not in anyone of these features per se, but rather in the particular combination of all of them herein disclosed. It is distinguished from the prior art in this particular combination of all of its structures for the fnuctions specified.

[0014] In order that the detailed description of the inven­tion may be better nuderstood, and that the present contri­bution to the art can be more fully appreciated, additional features of the invention will be described hereinafter. It should be appreciated by those skilled in the art that the conception and the disclosed specific methods and structures may be readily utilized as a basis for modifYing or designing other structures for carrying out the same purposes of the present invention. It should be realized by those skilled in the art that such equivalent methods and structures do not depart trom the spirit and scope of the invention.

[0015] In this respect, before explaining at least one embodiment of the invention in detail, it is to be understood that the invention is not limited in its application to the details of construction and to the arrangements of the components set forth in the following description, or illus­trated in the drawings. The invention is capable of other embodiments and of being practiced and carried out in various ways. Also, it is to be understood that the phrase­ology and tenninology employed herein are for the purpose of description and should not be regarded as limiting.

[0016] As such. those skilled in the art will appreciate that the conception, upon which this disclosure is based, may readily be utilized as a basis for the designing of other structures, methods and systems for carrying out the several purposes of the present invention.

[0017] Further, the purpose of the foregoing abstract is to enable the U.S. Patent and Trademark Office and the public generally, and especially the scientists, engineers and prac­titioners in the art who are not familiar with patent or legal tenns or phraseology, to determine quickly from a cursory inspection the nature and essence of the technical disclosure of the application. The abstract is neither intended to define the invention of the application, nor is it intended to be limiting as to the scope of the invention in any way.

[0018] Accordingly, it is an object of our version of the invention to provide a low-cost, easy-to-manufacture, and easy-to-market perpetual motion comptroller & energy mol­ecule splitter, for helping to make perpetual motion machines possible.

[0019] A further object of our version of the invention is to provide an easy to install and easy to use perpetual motion comptroller & molecule splitter. for perpetual motion machines.

[0020] A significant object of the invention is to provide a light weight and easy to service and easy to replace perpetual motion comptroller & energy molecule splitter.

US 2006/0237970 Al

[0021] A final but significant object of the invention is to provide a trouble free fool-proof control device that will not cause damage to the system it is installed in if it malfunc­tions, but is safe and reliable.

[0022] For a better nnderstanding of the invention, its operating advantages and the specific objects attained by its uses, reference should be made to the accompanying draw­ings and descriptive matter, in which there is illustrated a preferred embodiment of the invention. These objects should be constmed to be merely illustrate of some of the more prominent features and applications of the present invention. Many other beneficial results can be attained by applying the disclosed invention in a different manner, or by modifYing the invention within the scope of the disclosure. Accordingly, other objects and a fuller understanding of the invention may be had by referring to the summary of the invention, and the detailed description of the preierred embodiment, in addition to the scope of the invention illustrated by the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

[0023] The foregoing and other objects, features and advantages of the invention will become more fully under­stood from the following description of The preferred embodiment of the invention as illustrated in the accompa­nying drawings in which like reference characters refer to the same parts throughout different views. The drawings are not necessarily to scale, emphasis instead being placed upon illustrating the principles of the invention.

[0024] FIG. 1 is a perspective view showing a perpetual motion comptroller and molecule splitter in conjunction with other related parts as it would be installed and wired.

[0025] FIG. 1A is a plan view of a perpetual motion comptroller and molecule splitter with top cover removed showing the intemals.

[0026] FIG. III is a perspective arrangement of an alter­nate embodiment showing a tachometer added which is used to control the charging operation.

DRAWING REFERENCE NUMERALS

[0027] 25 Perpetual Motion Comptroller & Energy Mol­ecule Splitter with Intemal 9-volt Battery

[0028] 32 Positive and Negative Wires to 24-volt Circuit

[0029] 34 24-volt Tachometer with High and low set point for tuming Power on and off

[0030] 36 Positive 24-volt Signal Wire from Tachometer

[0031] 38 12-volt Tachometer Sensing Wire

[0032] 70 Main Control Board

[0033] 71 Positive "A" Solenoid Tenninal

[0034] 72 Negative "A" Solenoid Terminal

[0035] 73 Positive Feed Tenninal

[0036] 74 Negative Feed Temlinal

[0037] 75 Positive "C" Solenoid Tenninal

[0038] 76 Negative "C" Solenoid Tenninal

[0039] 78 Modulating Motor

3 Oct. 26, 2006

[0040] 80 Cam Collar

[0041] 82 Insulated Hot Pointer

[0042] 85 & 85 Positive & negative to 24-volt Drive Motor (not shown)

[0043] 86 Exciter Wire to Altemator (2)

[0044] 87 Exciter Wire to Altemator (1)

[0045] 93 On/Off Switch

[0046] 96 Negative Wire to Altemator (AI)

[0047] 97 Positive Wire to Alternator (AI)

[0048] 98 Negative Wire to Alternator (A2)

[0049] 99 Positive Wire to Alternator (A2)

[0050] 114 Remote Communicator/Controller

[0051] 115 Central Processing Unit

[0052] 117 External Speaker

[0053] 122 Touch Monitor

[0054] 500C Solenoid to Battery (Bl) Positive

[0055] 500 Solenoid to Battery (B1) Negative

[0056] 508A Solenoid to Battery (B2) Positive

[0057] 508 Solenoid to Battery (B2) Negative

DESCRIPTION OF THE PREFERRED EMBODIMENT

Description

[0058] Referring now to the drawings and, in particular, to FIG. 1 wherein there is illustrated a typical embodiment of a perpetual motion comptroller & energy molecule splitter 25. The present version of the invention 25 which casing is constmcted non-conductive materials such as plastic or fiber glass, with a removable cover. FIG. 1 shows how comp­troller 25 inter-relates with its associate component parts which are covered in co-pending application Ser. No. 10/811 ,382, and are not part of this application.

[0059] Referring to now to FIG. lA, wherein is illustrated the internals of comptroller 25, with a main control board 70, which controls the timing and switching of the 24-volt power supply to the external alternator solenoids. Pointer 82, is insulated and moves the 24-volts to the output ternlinals A, B, & C. 'Tenninal F, is 24-volt feed intake to main control board 70.

[0060] Referring again to FIG. 1, when switch 93 is closed 24-volts goes to Comptroller 25, via wires 73 & 74, (FIG. 1A). Pointer 82 which is normally at the A terminal when power supply is in the ofT position, sends 24-volts via wires 71 & 72 to alternator Solenoids 508A & 508 for 60 seconds. Said action will cause alternator A2 to refurbish battery B2, for a I-minute interval. Next hot pointer 82, (FIG. 1A) travels to the B, terminal and pauses for 30 seconds, this will allow drive motor to rest for a 'h minute before hot pointer 82 moves to the C, ternlinal, and pauses for 60 seconds. sending 24-volts to alternator solenoids 500C & 500, via wires 75 & 76. Said action will allow alternator Al to charge battery B1. for 1 minute. Next hot pointer 82 will travel back to the B, tenninal and pause for 30 seconds, giving drive motor another 'h rest before it

US 2006/0237970 Al

moves back to the A terminal for 60 seconds, to repeat the continuous charging cycle, back and forth, as long as switch 93 remain in the on position. Said action will facilitate perpetual motion, by increasing energy within the system enough to offset what is lost due to friction, and allow useful work to be done. When switch 93 is tumed oft~ hot pointer 82 will automatically retum to the A terminal. An optional no charging light can be connected to the B terminal.

[0061] Various methods can be employed to accomplish the refurbishing process of batteries B1 & B2, as explained above, and comptroller 25 can be made to operate in different ways. The methods explained does not limit this application to one format, or teclmology in accomplishing the above task. Said comptroller can work together with a computer like central processor 115 with speaker 117, or said process could be performed with the use of sophisti­cated computerized controls which can pedimn other duties such as turning device on and off, and warnings of possible problems or malfunctions, or displaying values and readings on touch monitor 122, or on remote communicator/control­ler 114, which also functions as a mobile phone and two-way radio. Such duties can involve digital, or sounds or voice and verbal conmlands and instmctions. The use of any computer hardware, software, or program or such like use of any and all prior art technology is considered as part of this appli­cation as a new unforeseen and unintended use, to facilitate perpetual motion machines. Furthermore the timing chosen is only for example, and any timing cycle that is proven to work may be used. The present invention is also patentable as an improvement over the sighted prior art, f(lr the reasons sighted in the discussion of the prior art, and the sun1lllary of the invention. Prose applicant request that such patent as explained be granted.

DESCRIPTION OF THE ALTERNATE EMBODIMENT

Description

[0062] Referring now to the drawings and in particular to FIG. III wherein there is illustrated an alternate embodi­ment of a perpetual motion comptroller and energy molecule splitter 25T. The present version of the invention 25T consist of all components as version 25, with the inclusion of a tachometer switch 34, and a double throw normally open, normally close contact switch 93D in place of switch 93. Tach-switch 34 operates on 24-volts, with a 12-volt sensing wire to alternator. and has two set points. One set point is at 5S00-PRM for a 24-volt system and 3100-RPM for a 12-Volt system. The other set point is at 5400-RPM for a 24-volt system and 2700 RPM for a 12-volt system (the exanlple illustrated is a 24-volt system). 'When alternators attain 5S00-RPM Tachometer Switch 34 sends 24-volts to Comp­troller 25. Comptroller 25 will operate as usual, sending 24-volts to alternator solenoids allowing one alternator to commence the charging of the related battery until alternator drops to 5400-RPM. At that point tachometer switch 34 turn

4 Oct. 26, 2006

the power off to comptroller 25 thereby stopping the said charging process. Comptroller 25 pointer will always move to the B rest position when no power is on. \\Then alternator attains 5S00-RPM once more, comptroller pointer will send power to the other alternator solenoids thereby causing said alternator to charge the related battery. \\Then alternator drops to 5400-RPM tach-switch 34 will tum power off to Comptroller 25, thereby stopping the charging process, and pointer will again return to the B rest position and wait for alternators to reach 5S00-RPM once more. At that point the charging of the other battery will take place as previously explained. This process will continue back and forth. as long as the system is in operation. Said process will allow the system to stay in operation indefinitely. Changing the posi­tion of switch 93D will cause comptroller 25 to operate on a timing cycle as was explained in the preferred embodiment of the invention. A second tachometer without a switch could be installed on the other alternator to monitor belt slippage, should both tachometer not have the sanle reading in revolutions per minute.

CONCLUSION AND SCOPE OF INVENTION

[0063] From the foregoing, it will be understood by per­sons skilled in the art that an improved method to make the benefits of perpetual motion machines available to humans has been provided. The invention is relatively simple and easy to manufacture, yet affords a variety of uses. While our description contains many specifications, these should not be constmed as limitations on the scope of the version of the invention, but rather as an exemplification of the preferred embodiment thereof. The foregoing is considered as illus­trative only of the principles of the invention. Further, since numerous modifications and changes will readily occur to those skilled in the art, it is not desired to limit the invention to the exact construction and operation shown and described. Accordingly all suitable modifications and equivalents may be resorted to, falling within the scope of the invention. Although this invention has been described in its preferred form with a certain degree of particularity, it is understood that the present disclosure of the preferred form has been made only by way of example. Accordingly numerous changes in details of construction and combina­tion and arrangement of parts may be resorted to, without departing from the spirit and scope of the invention.

1. What I claim is a method to split energy molecules in a battery operated circuit as said energy is receded in order to increase energy enough to oft'set lost to friction and do useful work whereby facilitating perpetual motion and a method to control the refurbishing of said batteries one at a time and to rest the system equally using prior art teclmology such as computer hardware software programs and timing and switching controls and a remote communicator/control­ler which also acts as mobile phone and two-way radio as a new use to facilitate perpetual motion.

* * * * *

111111 1111111111111111111111111111111111111111111111111111111111111111111111111111 us 20070246939Al

(19) United States (12) Patent Application Publication

McDonald (10) Pub. No.: US 2007/0246939 At (43) Pub. Date: Oct. 25, 2007

(54) PERPETUAL MOTION MACHINE

(76)

(21)

[nventor: Paul Wayne McDonald, Hernando, MS (US)

Correspondence Address: Paul McDonald 7243 Love RD Hernando, MS 38632 (US)

Appl. No.: 111281,660

(22) Filed: Apr. 11, 2006

Publication Classification

(51) Int. Cl. Il02K 7118 (2006.01)

(52) U.S. Cl. ...................................................... ....... 29011 R

(57) ABSTRACT

It is a motor which runs on Prepetual Motion.IT only requires synthetic oil to lubricate metal parts to prevent friction breakdown no Electricity or Fuel required I PAUL WAYNE MCDONALD claim to be the only one who has ever [nvented a Perpetual Motor to the best of my knowl­edge

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PERPETUAL MOTION MACHINE

[0001] B6 IS A Lifter shaft with gears at one end toward the outside of the circle and 2 rollers towards the center of the circle that ride on a clover leaf shaped cam B7 that resembles bunt cake pan B8 main shaft housing for B 20 magnets that bolt in it the B 21 magnets are timed by the B 6 and B 7 the B7 is on the tront end B8 the B21 will move away from B20 just so B2I can get by then it drop back down to magnet pulls the next B20 over and over B6 rides on b7 cam B6 goes up down B82 are timing gear set BI0 is the outer motor block that holds the parts in place.

[0002] B8 has a arrow pointing in the direction it is turning clockwise B20 are bolted to B8 and the B2I move up down just so the B20 can get by just missing each other

[0003] B7 is a bunt shaped cam there is 2 canIS the B6 has 2 rollers that ride on inner and outer rim ofB7 b6 has gears on one end that are for timing

[0004] B8 the front end and how it is shaped with notches on the outer edges so B20 can be bolted in the notches in the center of B8 is 4 more notches so a main shaft that has 4 more notches will 11t in it and B7 be time with B8

[0005] This is a side view of the motor the white dots are bolts that hold the magnets in the main shaft B8

[0006] This is the outer magnet B2I it has a gear set that bolts on it, the white spots are the bolts holes and B21-B is red and it is the gears for timing the B2I on the B8 main shaft

1 Oct. 25, 2007

[0007] B 82 Is a degree gears for the timing on each one of the B2I magnets

COLOR CODE FOR METALS ON DRAWINGS

[0008] I-The green parts 7075-T6 Aluminum

[0009] 2-The yellow parts 9310 Steel Alloy

[0010] 3-The white dots on page 5 are 8740 Steel Alloy

[0011] 4-The Blue parts ARMAX 26 SMCO Magnet Alloy

[0012] 5-The red parts 4130 Chromemoly And on the ends the gears are 9310 Steel Alloy

I claim: 1. I am the only one that knows how to make this

Perpetual Motion Motor and it work! I started on it when I was 8 years old, My Father told me that we are the Caretakers of the Earth, So I Established My Goals to make this Perpetual Motion Motor at age of 8 years old and this is my claim! The Magnets are put in a timed working order that they will push and pull in away that will be in Perpetual Motion I Have Worked on this all Alone no one helped Me with this I did it all by myself in 31 Years of work I Paul Wanes McDonald the End of this claim.

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