WO2010031108A9 - An epicyclic transmission - Google Patents

Abstract

A module comprising at least the groupings 11 and 12 which remains the same for all embodiments. Assemblies 11 and 12 are effectively side-by-side unequal co-axial assemblies. Assembly 11 is the first unequal coaxial assembly and comprises of a cam {sun-element} (17), bearing (18) and rollers {planet-element} (20), Assembly 12 is the second unequal coaxial assembly and comprises of a reversible rotor or component (15), cam {sun-element} (16), and rollers {planet- element} (19) being constrained with the planet elements of the assemblies and body (45) being the first element of the second assembly able to enclose the control means and able to be totally within the first rotating element of the first assembly, able to be totally within the body.element (21) of assembly (11).

Description

AN EPICYCLIC TRANSMISSION

eM Dean Gear and said Transmission advanced BY UNDERLINING OR DELETING , Single input only needed can support load from one epd . Or multiple inputs recirculating energy and HYBRIDS can use existi ng Gearbox or no Box at all - or lust a cover, This page 1 Is mostly from a Provisional worded bv a Professprs patent writer applied bv Patent Attorneys In 1995 and later accepted bv them down to line 30 1996/7/8, ,

( NOTE ; PCT FOR "CYCLONE PROOFING AND FREE ENERGY FOR HYBRIDS" 7-05-2008)

. This invention relates to devices for the transmission of mechanical power in the form of rotational motion. In particular, it is directed to transmission of power between a first rotationally movable element and a second rotationally movable element to provide a device which can provide, in a preferred form, continuously variable ratios, of angular velocity at an input to angular velocity at an out ut within the range of ratios - 1 : 1 to 0 to + 1 : 1.

The present Invention finds use in electronic, hydraulic or mechanical applications and, In a preferred form, provides variable input and output speeds; an output angular velocity that varies from 0 to + the gear ratio as the i nput varies from zero to the input angular velocity; torque multiplication ; the ability to vary speed and torque. Furthermore, the present invention provides multiple Inputs and/or outputs and reduction, step up or 1 : 1 gear ratios. This invention includes the use of a planetary drive, that is a drive which includes a set of rollers, bearings or similar moveable parts, arranged in a circle around an axis and configured so that, through their movement in concert, apply torque to a body whose resultant rotation is used as the output of the drive. Examples of similar drives are described in Australian Patents 607822 and 613927 as spin control differentials for vehicles and couplings. A planetary drive based on a sun pear, a ring gear, and a planetary gear carrier is disclosed in Australian Patent number 465202 in the name of Eaton Corporation.

Examples of planetary drives are manufactured by Sumitomo Heavy Industries Ltd, Japan, under the name "Cyclodrive". Although planetary gears are known, the prior art gears have failed to take advantage of certain of their features, in particular, the contra-rotational nature of the input and output shafts being on the same axis.

gee previous Fia 11-Fiq 9 Microcontroller combinino input energies and re-circulating braking providing added power to the Load - or Differential and Fig 2. for High Toroue with optional internal Ring oear components The Roller gearing is optional, can replace existing GearBOX gears with Planetary gears including "Toothed" or Hydraulic or anv suitable Pumps, f Advancing "Wheels Within Wheels" including as stated in page 8). The Variable BELTS are no longer needed on CVT Transmissions, or Hybrid or single ended. 1 Now including added Roller cages for lubrication. fif Eeeentrjc/ cam/sun gear planetary Gearing in chosen) - or optionally without these cages Now with any number of Intermediate rollers on either or both sides of the cage/carrier or one side only or without them.

With any number of cams/sun-gears/eccentrics with Ball Bearing separation if

Eccentric sun gear is chosen OR NOW WITH Bush onl^y can be used.

4 Alternatively cams can be of anv profile shape used now.

5 Thereby advances the previous Patents Titled "Transmission" or "eM Dean" or "Vapable Ratio Multi-Gear".

6 This present Patent Provisional App. advance retains reactive "High Toroue" to "Ground Reference" (Or optionally with oump or generator).

7 On one axis only - or to and from anv other axis.

§ But now has much better "Variability" "regeneration" Compactness and

Automatic Self Governing than the previous Transmission patents) -

3 yvith many designs for the progressive control of the amount of flow of the said

^" suitably formulated fluid or Pas or like storing and redirection of fluid pressure using any number of cams/sun gears/eccentrics, refer Claim 12, 13_f 14, 15.

10 Mv previous patent similarly had High Torque for the first transition, and then drive any load or loads variably.

11 (As confirmed bv these six Reps, from the IAME) - Institute off Automotive Mechanical Engineers ^ supported from one end only when demonstrated.

12 The "Daff type" "variable "belt" reouires two axes. Refer to "CVT Transmissions"

13 on Google to where a "Belt" is shown on Honda and beino "Standard" in the "CVT Encyclopaedia". = "Continuously Variable Transmissions".

14 The Mechanical Engineering Patent Attorneys requested this published on the first oaoe of the previous patent, as according to their understanding.

15 Referred to bv the Patent office by the examiner who confirms as "sighted"

16 placed on the Patent page 1 (Above the ABSTRACT.).

17 (the "Belt" is essential for CV s on the Gooole Encyclopaedia as "Standard

18 The High Tomue for the first transition demonstrated optionally using _ball bearings throwing out centrlfuoallv on a spring loaded designed "tapering part". 19 As the input rotation speed Increases the body to higher speed, the centrifugal force throws the balls centrlfugally out, into recesses. -

20 Recesses eventually lock the input rotation speed to the output rotation speed.

21 UP to a 1 to 1 ratio. -

22 As the load increases past a chosen spring loading tension on the balls, this 23 allows them to return progressively back to a high torque 4 to 1 reduction ratio.

24 Due to the "Taper", sprung loaded part forcing the balls back to the centre.

25 Alternatively much smoother variability from reactive feed back is achieved from regenerated stored energy internal or external - ( 26) instead_of - or as well as optionally ■

(27) Now Changing the number ? (tyio) Cam/Sunqear/Eccentrir rn rotate in the same direction as the main cam/sun - gear and assembly.

(28) flnstead of the opposite direction as in the previous published patent pages). (_.29) Further can have any number of cams/sungears/eccentrics in either direction in the same ring-gear. (30) SEE PAGE 8 "Wheels Within Wheels" β-6-96 INCLUDED. Previous patent wording = "Haying at least one input and one output and being of the epicyclic type involving interaction of three mechanically distinct rotating elements with any suitable form that allows the transfer of torque between input and output, namely a sun element, a ring element and a planet element in each of at least first and second unequal co-axial epicyclic assemblies, a first element of the first assembly and a first element of the second assembly able to rotate independently, the first element of the second assembly able to enclose the control means and able to be totally within the first rotating element of the first assembly, a second rotating element of the first assembly and a second rotating element of the second assembly being constrained to rotate at a common angular velocity, a third element of the First assembly being connected to a motive source, and control means for progressively changing the gear ratio applied to a load fEnd previous original PAGE 1 - 1

Pace 21 connected to the first element of the first assembly of the "Transmission", (referred to as an "eM Dean" or "Variable Ratio Multi-gear" sometimes) characterised in that the first and second assemblies each represent unequal fixed gear ratios respectively between the input and the output of the "Transmission" or "Variable Ratio Multi-gear" the first and second assemblies arranged so that if Individually each assembly has their first element constrained and their thi rd element rotated in a certain direction the second element will try to rotate in the opposite direction relative to the tendency of the other assembly the control means being operative to progressively increase or decrease the output gear ratio in accordance with the demand for an output lower or higher gear stage of operation .

The "roller" gear can be integrated with other planetary gear designs optionally, - is described as follows wherein the first elements are the ring elements of the respective assemblies, the ring elements being outer bodies having spaced endless scallop guides being adapted to receive sets of planet elements being in the form of rollers, the second rotating elements comprising of planet carrier elements and planet elements, the planet carrier elements of the respective assemblies constrained to rotate about an axis collinear with the axes of their respective third elements, the planet carrier elements locating and controlling the motion of integral spaced sets of rollers corresponding to the planet elements of each assembly, the rollers bridging . between the scallop guides of the outer bodies and the third elements of the assemblies, the planet carrier elements being constrained by a rotation controlling means allowing free rotation in one direction and a controlled rotation in the other direction, the third elements of the assemblies being sun elements in the form of respective sungears / cams or eccentrics.

This >ew advancement has an Internal Body able to be totally within another is described below under the relevant wording which refers to it is as follows.

It describes my present older Patent designs with ring-gears being "side by side" as can be seen in the cross section drawing of Fig 2 which more clearly explains the fig X in all these Patent drawings. Fig l shows the variable options with internal - either single electric or double contra- rotation and further, optionally three rotor electrical control variations. The electrical coils were then shown as with multiple hypothetical abilities, with Fig 2 explaining the practical necessities as to how the ring-gears would be physically constructed for the optional external one or more or combined power sources including for Hybrid applications. (WITH MANY OPTIONS DESCRIBED HEREIN ) The Electrical options are described on page 9 from lines 18 In the PCT /02/00305 as follows -The magnetic effects caused by item (25) can drive the cage (22) with the same action as (23) does on item ( 14) The torque caused by items (25) would need to be higher relative to the torque required by the cams (16) and (17) and so the f PREVIOUS PAGE 3V

electric coils afe-WERE an ancillary action NOW ne¾ necessary for SOME OF the central concept of the present invention. Although for some applications to include including "MOTOR WHEELS" or Direct loadina-By electric, mechanical, hydraulic and/or electronic control.- with any type of Fluid Pressure - with internal or external storage of energy is described herein.

With any means of reverse rotation restriction of the carrier being able to implement a first HIGH torque transition to the load. This is when an input rotation Is applied to the cam (sun gear). This third rotor coupled to the double carrier (22) (was drawn long length in Fig 1 thus able to be actuated alternatively by a ground reference one way restriction. Where accumulation of energy is able to be accessed alternatively.

The ground reference WAS/is shown with the shaded area of the housing, in order to more easily see how energy storage is actuated we can refer to the first Patent Windmill experiment. Several alternative methods have been described with some trailed, within the previous pages. In divisional Patent 2003204953 (from AU 93246/98) There was is described how by placing a small wind turbine blade on the Input cam (sun gear), being the First input, say at 6 to l ratio.

There can be a simple HIGH TORQUE and storage of energy provided in a simple three component epicycle configuration of gearing. This was described optionally, by haying another large heavy turbine blade on the reverse rotating cage (carrier). ^' At low wind speed the heavy load coupled to the body (ring-gear optionally ENCLOSING EVERYTHING) would not be able to be turned because of the high torque necessary. Instead the large heavy turbine/blade would be forced to rotate in the opposite direction to its designed pitch, because of the aearino.

optionally - one wav restrictions to around reference only allows it to go in the, same direction as the other b|ade havino the same pitch. Providing oeared torque at ar>y chosen ratio to start the Load. FURTHER THE Rlno oear can enclose the Planetary components.

When forced against the wind it will slow as the wind increases, and change direction due to the designed "pitch" - (on both sides of turbine/blade).

As the wind increases the large blade_r provides added torque from both the first small wind turbine blade together with the large blade returning adding stored reactive energy as well as from the wind..

The load will eventually turn faster than either of them and the load will also turn faster than both - the two input rotation speeds add together on the load.

(Not unlike A "YO YO" ACTION", but now on one axis.1

The "duty cvcle" of the windmill is thereby increased substantially not only because it absorbs recoverable energy, but pyercomino the common problem of the unpredictability of sufficient wind to get a load started.

Sometimes there is not enough- wind for days to start a windmill, whereas this can now make the difference between the viability of wind power even. The other HUGE advantage is that we now can have much smaller blade/turbine diameters

(Previous End Page 3 and Pane 4 starts below Ί

Optionally contra-rotating blades/turbines are known to increase wind pressure bv Fans by 270% In wind Tunnel tests,

Or optionally requiring one single itwpcltor blade only for even the previous compact "Torque Multiplier" as confirmed by the "Institute of Automotive Mechanical Engineers" in 2005. due to the input or out out rotation speed continuing up to a 1 to 1 ratio - (With what has never been successfully achieved so simolv Previously).

Multiple windmills heads can now fit side by side on one tower, due to only needing smaller turbines /blades., (as described herein) .

Similarly, pumps have initial starting friction to overcome - so "Solar energy" systems, are now made Viable - revolutioniseq¹ ·■

By having simple one wav mechanism, which would work similarly restricting carrier/ /cage from reverse rotation to a ground reference (which the large windmill blade could be likened to). Or indeed have integrated with it by including a one way clutch to ground reference. However in this situation a coiled torsion spring or a heavy weight hanging on a cable wound around the shaft of the cage/carrier - could be used instead of the large heavy blade.

By clever design there can be a resetting coiled spring locking onto the cage/carrier shaft which could allow the following to provide even more torque and energy storage: This can be very simple to give a load a kick-off -(or a Pump/s or Generator/s.)- Patent steps a understand this invention -

FIRST "SOLID BODY" fas in n Fin 11 HYBRID multiple In out /outputs- 1995 m Provisional ADD, f 19981

(2) The next ADVANCE was with separate Ringqears = the "Split Body" ->

(3 ISSB « Internally Soilt Solid Bodv! providing a compact High Torque Transmission -with the Centrifugal Frictional Clutch_f with the reverse rotating direction to Input and output rotation · fourth Sungear/Cam/eccentric Demonstrated and Confirmed bv the ΓΑΜΕ as Toroue Multiplying - supported from one end only, (the connecting rollers are also needed offcourse).

(4Y Now this present advance similarly has a double Cage /Carrier! fwith many different caae/carrler options as described with the fourth Planetary Component within (being another cam/sun-gear/eccentrlc). But rotating In the Forward Rotation Direction relative to the Input/output rotation..

(Which now is a huge advance over the previous Patent which had the Frictional Clutch with the Carn 2 rotating in reverse, but now cam/sunoear/eccentric 2 is going in the forward otation direction instead.

This present new Patent Application Epi-cycllc design has now advanced this invention where one Ring gear body can be within another Ringoear not side by side as my first ones were.

Where conveniently providing a wheel hub to drive a wheel or anv load because the output is from the Rlgnoqear Body. And is the outside ring-gear to provide a Hub.

Enclosing the other ring gear, which being a smaller lower power ring gear Is shown within it.

(The output can optionally taken from the Carrier / Cage for INLINE Drives.!

( 5 ) Named VASSTCO = Variable Automatic Self Supporting Transmission Co.

There is NO Gearbox housing required - as it supports itself - A dust cover can be used where only supported from one end or both ends (or discarding ttje gearing in a "BOX^*").

(βΐ Whether Mechanical operation is used, as described using the Ball bearing centrifugal Governing, the Output can be taken from the Carrier/caoe Instead of the

Ring gear body optionally.

f 71 Or as in Claim 12 "the progressive control of the amount of flow of the said suitably formulated fluid or oas or like ip the first and second circuits operable to progressively change the gear ratio applied to a load connected to the first element of the first assembly of the Variable Ratio Multi-gear."

«) When this single axis type of drive is needed It can be fitted between a driveshaft and differential. One option for automatic Transmission is shown and described in the wording on the Fig 2 Drawing which is published in the USA, fas Is around the worlds. (<n As is stated in the wording beside the Drawing in the Published USA Patent as follows. - "Centrifugal Governor Running at Body Speed, coupled to the Body for Body Output. Or Coupled to the carrier which makes th Carrier Output when chosen". "

(10 Allows the Driveshaft of a mobile (or machine) to have NO "BOX" "gear BOX"

Just external bearings support optionally the GEAR mounting in between existing or added Universals for supporting bearings coupled to the body structure.).

(11) Opposite rotation direction of internal Governing is able to be used with anv "Self Governing - with either Body or furri r as output

( 12) More Sunoears or Cams can be added for anv chosen "Steps" and more rinogears for Heavy Duty uses, overdrives, Reversing or Motor bracing OR for storing energy.

13 The Electric Motor Rotor can even be Keyed to e driveshaft. as from the gas engine of any type of engine for Hybrid Operation.

(14 Due to the high cost of running 4 wheel Drives, either the ba k or front differential can be chosen to fit the Mechanics and Electrics to.

(15) Alternatively the standard Gearboxes can have the new parts replacing the old Gears-

(16) Offcourse the inefficient Torque Converter Is replaced with the first Electric motor/generator (For example with Powerful Magnets of any number, their rotor locked to shaft, or input shaft passing through this rotor) With another Electric Motor Generator (If chosep) having for less load. - As there can be the Internal second Ringgear, providing more reduction (Allowing for smaller Electric motors - and the Gas engine can work more gently, ⁽having the spark retarded or backed off if chosen) (When equalised n Hybrid Mode). (Fig 1 is iust as able to provide these Automatic Transmissions as Fla 2.

One Patent Attorney suggested^that we may obtain an even earlier priority date from even this present Patent Application if it is taken that my obsolete fSolrt Body 2) one - PCT/AU02/00305 discloses this somewhat already by showing a body within a body where the heavy output ring-gear (21) is shown within the smaller roller ring-gear in Fig 1. This smaller roller ring-gear was only shown in this position, to show another optional configuration and at the same time so as to accommodate the optional field coils (23,24,25) and further to show the relationship to the double carrier (22) relevant to everything else. Therefore it had to be drawn at the larger diameter, this put it at (26) shown as ground reference, with a small dotted line indicating the second optional rotating ring-gear option.

In order to further describe this invention please refer to page 2 of my Divisional Patent "Converter" AU 35198/01 which provides Polders Eplcyclic calculations. The following applies to this present advancement in appropriate wording and is included so as to understand the present Claims, where any type of epicyclic gearing may be used.

There are some pertinent descriptions made in my prior Patents which can now make this new advance clearer. Some of the earlier description can show unique construction of this new drive now optionally using the replaceable ring gears as especially designed to act like replaceable inserts. This Is to easily change any fixed ratios if thought necessary after manufacturing is completed, or to change the speed of a conveyor belt or similar for example. Some early references are also made and described in the "Wheels Within Wheels" Document &-6-96 which was not available except under strict confidential disclosures. Such as in Item 32 which is available by referring to Divisional Patent AU -2003204953- which was re-applied for in year 2002 which was originally from Patent Application AU 93246/98.

Therefore the original 5 page Document of "Wheals Within Wheels" 6-6-96 is attached to this Patent, with the added words to the Railway Engineer - Item 7B "FRANK NOTE; NEW BATTERIES MAKE POSSIBLE VIABLE HIGH POWERED MOTORS FOR HYBRID AND ELECTRIC" The earlier patents will be allowed to lapse with this present patent advance being far advanced now. Q-here are also small numbers as applied to each Patent on the pages top right!!)

The drawing of Fig 5-showing four wheel steering further becomes viable now with THIS new patent advance. Having the ability to now have the four wheel vehicle with four wheel steering and also four wheel drive being able to Incorporate self contained motors of any type, such as well as Electric, Hydraulic, or Hybrid of any kind.

Constant Velocity Joints can be discarded.

Alternatively there is the ability to Incorporate enormous technological leaps by providing "Three Dimensional" features such the kind of vehicle which can lean into a corner - like a motor-cycle, see fig 30 from this Present Patent Application See Hg 12, Fig 6, and Fig 13.

Some of the unique uses described for this "Ultimate Transmission" invention, which can be providing every conceivable extreme requirement, I have ever required. Able to be self contained or support everything, able to integrate multiple inputs and outputs, single Inputs can deliver and provide, high torque variable speed transmissions, to continuously variable, to Infinitely variable speed, to sequential transmissions to likening it to operating as a type of Yo-Yo action, to linear transmission outputs and further can be performed on one axis, or to and from any other axis. Able to be low cost with low wear, can be designed for short duty cycles because nothing is moving when up to 1 to 1 ratio. As also where there is unlimited speed requirements because there only need be the difference from input to output speed, it may contain its own lubricant which can double to provide automatic governing, and easy maintenance. It is also able to use advanced materials such as ceramics or titanium, yet sizes can be from Micro to Macro.

The great advance is that the Intrinsic nature of this fixed ratio gear design allows the multiple gearing inputs and outputs to become dynamically interrelated, the components of all the relative reference points can be exploited as they are all moving relative to each other. The gear shafts can be massive where required for extremely low ratio leverage enabling the whole structure of the machines to be "alive".

Some hybrid description of this invention given by a highly respected Mechanical Professor, he suggested it as advancement for Toyota and is very appropriate, particularly with reference to their hybrid drives.

Many energy storage and integration of rotational force options are possible. Governor action can further be controlled by the intrinsic dynamic nature of the transmission having fixed ratios, which may centrifugally equalise the Inputs and outputs for optimum operation. (Electronic control for optimum performance together with maximum efficiency is extremely complementary to this transmission and relatively low cost, with manual over-riding being available).

As further understood by the Engineering Professor, a "Pulley" system he further explained how some of the more exciting features of the dynamic component of this invention can b better understood, by labelling Fig 6 (or new Fig 13 B herein, see drawings Page 12) as showing an "Internal View" and labelling Fig 12 as showing an "External View" (the three dimensional view being seen for example by looking at Fig 30, showing the car and passengers tilting into the corner like a motor-cycle instead of throwing out as would normally occur.)

There can be seen the two variable gears positioned between the two front wheels and also between the rear wheels. Continual correction is thereby available to smooth out travel for total passenger comfort. Fig 5 lower drawing can be integrated with Fig 12 for camber and caster. The combined advance of low cost electronic sensors can be input into low cost Miro- processors thereby providing pre programmed reactive correction for any scenario and every obstacle or road irregularity encountered. This is the ultimate result which can be incorporated together wit linear high torque acceleration and smooth braking. Silicone Polymers as used in shock absorbers are very complimentary and optionally able to be used for many of the present advances, These can be actuated again by low cost high voltage, low current electronics. (Or low Voltage offcourse)

Other advanced body shapes and structures may be used such as for strength, low wind resistance ease of manufacture. By using the extremely indestructible structural shape which may be understood as a Three In One structure which provides the minimum surface area to maximum capacity and may be understood to have physical, scientific, chemical and spiritual dimensions and connotations. Three equilateral triangles form the basis of this structure with the ability to view right around in a 360-degree path in any direction in our three dimensional world, it is called a "tetrahedron." However in order to provide substance and capacity, we have to have a fourth side, (which can be positioned anywhere from infinity to infinity) this fourth side is also an equilateral triangle. Einstein postulated that our world is three-dimensional, where a fourth dimension can be understood as being time. This tetrahedron structure further can be extended into as many more of these triangles If required thereby providing extremely strong enclosures.

For our present convenience, rectangular connecting panels for extending for example two of these enclosures together for example for building longer high-speed vehicles and also for water transport would be options. After the previous advanced optional features, the following 18 lines below is the wording direct from this present Provisional Application. Further explaining that the old ring gear bodies had no rotational movement between them except where clearly shown, being always positioned side by side. "The bodies of this transmission may be manufactured by any known method/ being described as "laminated", the scallops or ring-gear may be provided side by side in any known method where there is no rotational movement in between them.

As described previously they can be inside the wheel, the scallops can be machined inside the wheel hub, inside complete with motor, (or contra-rotating motor). Or other epi-cyclic designs could be used where the bodies may be, for example within each other. Or pump combinations may be used without differentiating from the present invention. (There is the exception shown in for example in Fig 11 where there is a flange showing very clearly where such a split would be such as for fans or similar. However the iateet obsolete Patent PCT/AU02/00305 do djd. have a split body, but between the first epicyclic movement's double carrier as an alternative design). Any number of ring gear/scallops could be manufactured in one piece, simply bolted together or slid into rotational restricting cavities, or enclosed, (see inserts to add or change ratios in item 32 page 4≥ or pago-71, lino 21), of Wheels Within Wheels 1996 While the above description deals with the general features involved the following description will enable understanding of the application of the invention to the two specific applications of Figure 1 and Figure 2.

Figure 1 shows a transmission (referred to as an "eM Dean" Gear or "Variable Ratio Multi-Gear" sometimes) input shaft 13 with The previous alternative rotors can now still be duplicated internally concentrically, being shown as options here and also with dotted lines which were In the Fig Α Converter Patent AU 742781 ,or 35198/01 according to This invention as well can apply an input which is a rotor (14) an output (21) and electrical coil and permanent magnet arrangements (23 - 25) that did apply torques respectively to rotors ( 14, 15) and a planet element in the form of a cage (22).

Items 23, 24 and 25 are arrangements of permanent magnets and electrical coils so that with electricity flowing through the coils. Interacting magnetic fields are produced which cause a torque on the rotors (14, 15) and cage (22) respectively. The electricity supply can be adjusted Individually for each of items 23 to 25.

The rotor (14) and input shaft (13) are combined as an integrated part in this module. As an alternative, the rotor (14) could be removed and the input could be solely from an external motive source driving the input shaft (13). The point is the module comprising the groupings 11 and 12 remains the same.

Assembly 11 is the first unequal coaxial assembly and comprises of a cam {sun- element} (17), bearing (18) and rollers {planet-element} (20). The cam (17) is fixed to. the input shaft (13), which is therefore fixed to the input. The bearing (18) has an inner sleeve fitted to the outer diameter of the cam (17). The bearing has an outer sleeve, the outer sleeve of the bearing (18) makes contact with the rollers (20). As the input rotates, the am (17) causes the bearing (18) to move in an eccentric fashion. This causes the rollers (20) to be cyclically displaced away and towards the central axis of the eM Dean Gear the total displacement relative to this central axis, being twice the cam axis offset from this axis. The rollers (20) are located in equally spaced guides in the cage {planet element} (22). The rollers (20) make contact with scallops In the output {ring element}(2l). For both assemblies (11 & 12), the number of scallops relative to the number roller in contact with the scallops, determines the direction of rotation it would rotate the output (21) if the cage (22) was held still. One more scallop than the number of rollers gives an output rotation direction the same as the cam rotation. One less scallop than the number of rollers would give an output rotation the opposite to the cam rotation. The scallops are so shaped that as the rollers are acted on by the cam, the scallops rotate relative to the cage at a constant angular velocity ratio to ^'that of the cam. The action between the cam (17), bearing (18) and rollers (20) against the output (21), causes an equal and opposite reaction on the cage (22), tending to rotate it In the opposite direction to the rotation of the output (21). The cage (22) is constrained by a rotation blocking means in such a way as to allow the cage (22) to only rotate in a direction the same as the output (21). Therefore because of the reactive forces, the cage (22) will be held against the rotation blocking means and will therefore be stationary relative to the frame (26) with Just the actions of assembly 11 alone.

This advance is in order to provide more practical transmissions for better supporting a load and for better sealing even its own lubricant than was possible with the previous "Split Body Patent". It was therefore necessary to advance on the previous one by putting a Body able to be totally within the other, (instead of the external split). This was achieved with this present new ring body Inside the main Body design.

A "Solid Body" now encloses the second body able to be totally within and there is a very compact "Torque Multiplier" design provided as a result.

However the following description can still be related to because either a single power source or contra-rotational and Hybrid qualities are still able to be accessed but now in a more compact and more self supporting advancement. With a *Motor Wheel" now being a reality. The rotors which were in previous Fig l of A Converter are shown with pointer lines to both the new and old inputs, as easier to explain this advancement as follows. However each time there is referred to the three rotors shown, these can be replaced with a new position, but now able to be totally within (or Internal and external power sources can still be combined such combining internal electric or hydraulic with external electric or hydraulic, such for Hybrid, where chosen).

The magnetic effects caused by items 25 can drive the cage (22) (with the same action as 23 does on item 14. This torque caused by items 25 WAS ts-an ancillary action and ARE NOW not-necessary for ONE OF the central concepts of the present invention. )(These components are now inside the ring gear body now with 25 being shown now with one way clutching instead, where two one way clutches are used in sequence fOR CLUTCHED DIRECTLY OR INDIRECTLY to the Caae/carrier) to transfer the first powerful torque to the load from a Ground Reference)

The carrier 22 can now be actuating energy storage internally by being forced into a reversing direction to the load direction, this can provide pumping (or even a coiled torsion spring can absorb energy) The pumping can be integrated with internal accumulation or external accumulation for regeneration. There is alternatively the requirement for two one way clutches to reference the carrier 22 to ground accessed sequentially through the internal Ring Gear 45. Alternatively one wav control/restriction such as concentric extension of Carrier/Caoe 22 from either end, or from 13B Shaft. The one way clutches can be similar to as described in Arthur Woodbridqe's Patent AU 607822 being used for a clever "Spin Control Differential" for vehicles fOR ANY VERY SIMPLE ONE WAY RESTRICTIONS can be used). This Patent is now assigned to me. There is the option of having automatically reversing one way clutches if reverse direction of the load is required and motor braking is needed. However if required a motor brake one way clutch may be fitted between the input shaft and output of the gearing , .The rollers will rotate about there own axis as they move in relation to the scallops. The bearing (18V (OR BUSH), is added to eliminate the sliding action of roller

(20) against cam (17), which would occur (if they were in direct contact) because of the difference in their circumferential speeds. The output (21) is constrained to rotate about the central axis of the input shaft (13). The cyclical movement of the rollers (20) acting on the scallops alone, causes the output (21) to rotate at a. reduced rotational speed depending on the number of rollers and scallops.

For example, if the cage (22) is constrained from being able to rotate, and If assembly 11 has TH EE fear-rollers (20), and there are FOUR five scallops in the output

(21) , the ratio would be one output (21) revolution for every FOUR five revolutions of the cam (17) with the output (21) rotating in the same direction as the cam ( 17).

Assembly 12 is the second unequal coaxial assembly and comprises of a rotor (15), cam (16), and rollers (19). The scallops in the second ring gear 45 make contact with the rollers (19) which make contact with the cam (16). The cam (16) Is fixed to the rotor (15) (shown as an internal clutch drum, now for lower value applications) Alternatively there is now Automatic Variability and Self Governing with internal REDIRECTION OF FLUID pressure, refer Claim 12.

Or another simple option,, which uses Centrlfuoally actuated Ball bearings throwing out on a sprung loaded "taper" locking up to the 1 to 1 ratio. As the load increases returning to 4 to 1 ratio torque on the "Taper"..

To reduce frictional losses, a bearing (pr Bush) would be fitted to the outside diameter of the cam (16). The number of scallops and rollers for assembly 12 are different to the numbers for assembly 11. The rollers are located in equally spaced guides in the cage (22). The cage therefore bridges axially between assemblies 11 and 12 and the rollers (19) are constrained to rotate at the same angular velocity about the central axis of the input shaft (13) as the rollers (20) of assembly 11. The numbers of scallops and rollers are such that if the cage (22) is held relative to the frame (26), the internal ring gear 45 tends to cause the cam (16) to rotate with an angular velocity in the SAME or opposite direction to cam f 17).

For example, ir the cage (22) is constrained from being able to rotate, and if assembly 12 has THREE few rollers (20), and there are FOUR three scallops in the internal ring-gear body 45, the ratio would be one Internal ring gear 45 revolution for every FOUR, revolutions of the cam (16), with the Internal ring gear 45 rotating in the SAME opposite direction to the cam (16). If the assembly 11 cam (17) Is caused to rotate, the output (21) will rotate at another angular velocity, being a fixed ratio to the input angular velocity. The assembly 12 earn (16) will rotate at an angular velocity dependent on the fixed ratio of assembly 12. Ah alternative central concept of the present invention, peing cam ( 7)in the SAME direction in. Assembly 12 is. now changed so that cam f !6) rotates in the same direction as cam (17), the output is thereby reversed as in cam (16}. The cam (16) ill have «e effect on the output angular velocity when tmtH the electrical coils of items 24 are activated. With the electrical coils activated, a torque is transmitted through the rotor (15) to the cam (16). The electrical colls could be activated so that the torque acts in the same or opposite direction as the rotation of the cam (16). If the torque acts In the same direction as the rotation of the cam (16), the output would rotate at the angular velocity determined by the fixed ratio but with an Increased torque dependant on the amount of torque contributed by items 24.

The torque from items 24 act in the opposite direction of rotation of the cam

(16 (ie. the same direction as the input shaft (13)). In this case, assembly 12 will act so as to try and cause the output (21), to rotate in the opposite direction and the cage (22) in the same direction as the input. In simplistic terms, the opposite actions on the output and cage caused by cam (16) tend to Mock' the cage (22) to the input rotation. The cage (22) is free to rotate in the direction of the input (cam (17)). The cage (22) therefore tends to cause the output (21) to rotate as one with the input. The rollers (20) rotation about the central axis of the input shaft (13) due to the action of the cam

(17) , has superimposed on it a rotation about this central axis due to the rotation of the cage (22) in the direction of the input. It is this superimposed rotation that causes the output to increase Its angular velocity relative to the input angular velocity. The amount of rotation of the cage (22) and therefore the amount of superimposed rotation is determined by the relative differences in the output resistive torque (hereafter called the Moad and the input torque from cam (17) and items' 24. (If an internal or external hybrid input Is applied concentrically about the Input shaft 13 to this 15 rotor shown now instead of a motor rotor, is shown as a dutch drum this would have the same effect as 24 being electrically driven, and indeed this is concentrically accessible). When the 'load' lowers relatively and the torque from items 24 is increased, the less the torque required from cam (17). As the proportion of torque from cam (16) relative to cam (17) increases, the more the output (21) tends to be 'locked' to the input and the more the ratio of input to output angular velocity tends to approach l : i. The output gear ratio therefore can be progressively decreased from the fixed ratio of the first assembly to a 1 : 1 ratio by progressively increasing the torque acting on the cam (16) from zero to a value that causes the cage (22) to be ocked' fully to the input. The output torque is inversely proportional to the output angular velocity.

Figure 2 shows another embodiment of a "eM Dean" Gear, in this case there is a combination of a module 10 with extensions (on the right-hand half) that enable further multiple fixed ratios to be obtained from the one eM Dean Gear The module 10 shows the central concept of the present invention. The Input is via a separate motive source (not shown) acting through the input shaft (13). The output is the ring element or body (21). However many new options are available if there is the added extension Fig 2 (For example there is now the option of a second internal body ring -gear with added cam on the right hand side which can be actuated by optionally removing the two bolts and allowing the new second internally shown with arrows. The ring-gear with output 51 can then itself drive another cage with a cam coupled to It so as to provide such as overdrive features. Another cage/cam is shown able to be driven which can provide reversing features by breaking it from being operating in a forward direction of the chosen output. There are also abilities to change ratios or other features by concentrically moving any concentric shafts in and out as shown on SO and 52.

The first unequal coaxial assembly comprises of a cam {suh-gear} (17), and rollers {planet-gears} (20) and the ring element or body (21). The cam (17) is fixed to the input shaft (l3).The outer diameter of the cam (17) makes contact with the rollers (20). As the input rotates, the cam (17) outer diameter moves in an eccentric fashion. This causes the rollers (20) to be cyclically displaced away and towards the central axis of the "eM Dean" Gear as also described in the "A Converter" prior Patent AU 742781 and A 35198/01, explaining the advance here as follows - "the total displacement relative to this central axis, being twice the cam axis offset from this axis. The rollers (20) are located in equally spaced guides in the cage {planet carrier} (22). The rollers

(20) make contact with scallops in the output (21). For both assemblies (11 & 12), the number of scallops relative to the number rollers in contact with the scallops, determines the direction of rotation it would rotate the output (21 if the cage (22) was held still. One more scallop than the number of rollers gives an output rotation direction the same as the cam rotation. One less scallop than the number of rollers would give an output rotation the opposite to the cam rotation. The scallops are s shaped that as the rollers are acted on by the cam, the scallops rotate relative to the cage at a constant angular velocity ratio to that of the cam. The action between the cam (17), bearing (18) and rollers (20) against the output (21), causes an equal and opposite reaction on the cage (22), tending to rotate it In the opposite direction to the rotation of the output

(21) . The cage (22) is constrained by a rotation blocking means in such a way as to allow the cage (22) to only rotate in a direction the same as the output (21). Therefore

( T/AU2009/001187

16 because of the reactive forces, the cage (22) will be held against the rotation blocking means and will therefore be stationary relative to the frame (the structure holding mounting the motor etc.) with just the actions of assembly il alone. The rollers will rotate about there own axis as they move in relation to the scallops. A bearing (OR BUSHO could be fitted to the outside diameter of the cams (16 & 17) to eliminate the sliding action of roller (19 & 20) against cam (16 ¾ 17), which would occur (if they were in direct contact) because of the difference In their circumferential speeds. The output (21) is constrained to rotate about the central axis of the input shaft (13)^'. The cyclical movement of the rollers (20) acting on the scallops alone, causes the output (21) to rotate at a reduced rotational speed depending on the number of rollers and scallops.

For example, if the cage (22) is constrained from being able to rotate, and if assembly 11 has four rollers (20), and there are five scallops in^" the output (21)·, the ratio would be one output (21) revolution for every five revolutions of the cam (17) with the output (21) rotating In the same direction as the cam (17).

The second unequal coaxial assembly comprises of a cam (16), and rollers (19) and inner body (45) The scallops in the body (45) make contact with the rollers (19) which make contact with the am (16). The number of scallops and rollers for the assembly are different to the first assembly 11. The rollers are located in equally spaced guides in the cage (22). The cage therefore bridges axially between assemblies 11 and 12 and the rollers (19) are constrained to rotate at the same angular velocity about the central axis of the Input shaft (13) as the rollers (20) of assembly 11. The numbers of scallops and rollers are such that if the cage (22) is held relative to the frame, the body (45) tends to cause the cam (16) to rotate with an angular velocity in the gAMEopposite direction to cam (17).

For example, if the cage (22) is constrained from being able to rotate, and if assembly 12 has THREE few rollers (20), and there are FOUR thfee scallops in the body (45), the ratio would be one body (45) revolution for every FQIJR_thrce revolutions of the cam (16), with' the body (45) rotating in the SAME oppoitc direction to the cam (16).

If the assembly 11 cam (17) is caused to rotate, the body (45) will rotate at ^another angular velocity, being a fixed ratio to the input angular velocity. The assembly 12 cam (16) will rotate at an angular velocity dependent on the fixed ratio of assembly 12, and for the central concept of the present invention, in the SAME opposite direction to cam (17). If assembly 12 was arranged so that cam (16) rotated in the same direction as cam (17), the output would be reversed if cam (16) was braked. The cam U2009/001187

17

(16) will have no effect on the output angular velocity until a torque is made to act on it. Any torque acting on cam (16) could act in the same or opposite direction as the rotation of the cam (16). If the torque acts in the same direction, the output would rotate at the angular velocity determined by the fixed ratio but with an increased torque. As in the previous embodiment the torque acting on cam (16) is in a direction SAME opposite to that of the rotation of the cam (16) (i.e. the same direction as the input shaft (13)). In this case, assembly 12 will act so as to try and cause the Inner body (45), to rotate in the SAME oppooitc direction and the cage (22) in the same direction as the input. In simplistic terms, the SAME opposite actions on the output and cage caused by cam (16) tend to Mock' the cage (22) to the input rotation. The cage (22) is free to rotate in the direction of the input (cam (17)). The cage (22) therefore tends to cause the output (21) to rotate as one with the input. The rollers (20) rotation about the central axis of the Input shaft (13) due to the action of the am (17), has superimposed on it a rotation about this central axis due to the rotation of the cage (22) in the direction of the Input. It is this superimposed rotation that causes the output to increase Its angular velocity relative to the input angular velocity. The amount of rotation of the cage (22) and therefore the amount of superimposed rotation Is determined by the relative differences in the outpu resistive torque (hereafter called the 'load') and the Input torque from the cams (17 & 16). When the 'load' lowers relatively and the torque acting on cam (16) is increased, the less is the torque required from cam (17). As the proportion of torque from cam (16) relatlve-to cam (17) increases, the more the output (21) tends to be 'locked' to the input and the more the ratio of input to output angular velocity tends to approach 1:1. The output gear ratio therefore can be progressively decreased from the fixed ratio of the first assembly to a 1:1 ratio by progressively increasing the torque acting on the cam (16) from zero to a value that causes the cage (22) to be Mocked' fully to the input. The output torque is inversely proportional to the output angular velocity. The input torque to cam (16) can be through another motive source or a clutch mechanism connecting the input shaft (13) to the extension of cam (16). If a clutch mechanism was used, the control mechanism could be automatic and linked to the output speed through the use of a centrifugal clutch. With a centrifugal clutch arrangement, a the speed of the output increases the clutch engages and tends to turn cam (16) in the same direction as the input, cam (17). So as the output is accelerated at the lower fixed ratio, there will come a stage when the input shaft is spinning at such a speed that the centrifugal clutch starts to engage. As the centrifugal clutch engages, the output gear ratio would progressively decrease to 1: 1. With the addition of other rotation blocking means to this arrangement to constrain other parts to rotate in one direction only, there is the possibility of having sequentially selected multiple ratios with other outputs. For example if the rotation blocking means is connected to cam (16), (or other especially designed cages or ring gears with cams can provide unlimited features) of the transmission the output will be the body (21) or (51), There is also the option of arranging the cage (22) so that it protrudes from the right-hand side of figure 2. The cam (16) can have an extension and Its rotation could be controlled by various external or internal means.

Whilst the above has been given by way of illustrative example of the present invention many variations and modifications thereto will be apparent to those skilled in the art without departing from the broad ambit and scope of the invention as herein set out in the appended claims.

Claims

Claim 1. A transmission having at least one input and one output and being of the epicyclic type involving interaction of three mechanically distinct rotating elements with any suitable form that allows the transfer of torque between input and output, namely a sun element, a ring element and a planet element in each of at least first and second unequal co-axial epicyclic assemblies, a first element of the first assembly and a first element of the second assembly able to rotate independently, the first element of the second assembly able to enclose the control means and able to be totally within the first rotating element of the first assembly, a second rotating element of the first assembly and a second rotating element of the second assembly being constrained to rotate at a common angular velocity, a third element of the first assembly being connected to a motive source, and control means for progressively changing the gear ratio applied to a load connected to the first element of the first assembly of the transmission characterised in that the first and second assemblies each represent unequal fixed gear ratios respectively between the input and the output of the "eM Dean" Gear or said transmission,^' the first and second assemblies arranged so that if individually each assembly has their first element constrained and their third element rotated in a certain direction the second element will try to rotate In an opposite direction relative to the tendency of the other assembly, advanced now with the third element causing the second element to rotate In the same direction of the other assembly, the control means being operative to prog ressively increase or decrease the output gear ratio in accordance with the demand for an output lower or higher gear stage of operation .

Claim 2. A transmission according to claim 1 wherein the first elements are the ring elements of the respective assemblies, the ring elements being outer bodies having spaced endless scallop guides being adapted to receive sets of planet elements being in the form of rollers, the second rotating elements comprising of planet carrier elements and planet elements, the planet carrier elements of the respective assemblies constrained to rotate about an axis collinear with the axes of their respective third elements, the planet carrier elements locating and controlling the motion of integral spaced sets of rollers corresponding to the planet elements of each assembly, the rollers bridging between the scallop guides of the outer bodies and the third elements of the assemblies, the planet carrier elements being constrained by a rotation controlling means allowing free rotation in one direction and a controlled rotation in the other direction, the third elements of the assemblies being sun elements in the form of respective cams.

Claim 3. A transmission according to claim 1 wherein the first elements are the ring elements of the respective assemblies, the second rotating elements comprising of planet carrier elements and planet elements, the planet carrier elements of the respective assemblies constrained to rotate about an axis collinear with the axes of their respective third elements, the planet elements constrained to rotate on their own axes with the axes being constrained to rotate with the planet carrier element, the planet elements with their axes offset from their respective planet carrier element so as to bridge individually or In combination with other planet elements between the ring element and the third element of their respective assembly, the planet carrier elements being constrained by a rotation controlling means allowing free rotation in one direction and a controlled rotation in the other direction, the third elements of the assemblies being sun elements, the ring and planet and sun elements being in a form that will allow the transfer of torque at a fixed ratio between elements.

Claim 4. A transmission according to claim 2 wherein the first elements are the ring elements of the respective assemblies, the ring elements being outer bodies having spaced endless scallop guides being adapted to receive sets of planet elements being in the form of rollers, the second rotating elements comprising of planet carrier elements and planet elements, the planet carrier elements of the respective assemblies constrained to rotate about an axis collinear with the axes of their respective third elements, the planet carrier elements locating and controlling the motion of integral spaced sets of rollers corresponding to the planet elements of each assembly, the rollers bridging between the scallop guides of the outer bodies and the third elements of the assemblies, the planet carrier elements being constrained by a rotation controlling means allowing free rotation in one direction and a controlled rotation in the other direction, the third elements of the assemblies being sun elements In the form of respective cams, the control means being operable to supply a variable rotation to the third element of the second assembly across a continuous range of output gear ratios between low and high angular velocities at respective predetermined low and high output angular velocities.

Claim 5. The transmission according to claim 3 wherein the first elements are the ring elements of the respective assemblies, the second rotating elements comprising of planet carrier elements and planet elements, the planet carrier elements of the respective assemblies constrained to rotate about an axis collinear with the axes of their respective third elements, the planet elements constrained to rotate on their own axes with the axes being constrained to rotate with the planet carrier element, the planet elements with their axes offset from their respective planet carrier element so as to bridge individually or in combination with other planet elements between the ring element and the third element of their respective assembly, the planet carrier elements being constrained by a rotation controlling means allowing free rotation in one direction and a controlled rotation in the other direction, the third elements of the assemblies being sun elements, the ring and planet and sun elements being In a form that will allow the transfer of torque at a fixed ratio between elements, the control means being operable to supply a variable rotation to the third element of the second assembly across a continuous range of output gear ratios between low and high angular velocities at respective predetermined low and high output angular velocities.

Claim 8. A transmission according to claim 2 wherein the first elements are the ring elements of the respective assemblies, the ring elements being outer bodies having spaced endless scallop guides being adapted to receive sets of planet elements being in the form of rollers, the second rotating elements comprising of planet carrier elements and planet elements, the planet carrier elements of the respective assemblies constrained to rotate about an axis collinear with the axes of their respective third elements, the planet carrier elements locating and controlling the motion of integral spaced sets of rollers corresponding to the planet elements of each assembly, the rollers bridging between the scallop guides of the outer bodies and the third elements of the assemblies, the planet carrier elements being constrained by a rotation controlling means allowing free rotation In one direction and a controlled rotation In the other direction, the third elements of the assemblies being sun elements In the form of respective cams, the first element of the second assembly constrained to a fixed frame of reference, a third element of the second assembly rotating at a controlled angular velocity the control means being operative to progressively increase or decrease the output gear ratio in accordance with the demand for an output lower or higher gear stage of operation.

Claim 7. A transmission according to claim 3 wherein tne first elements are the ring elements of the respective assemblies, the second rotating elements comprising of planet carrier elements and planet elements, the planet carrier elements of the respective assemblies constrained to rotate about an axis collinear with the axes of their respective third elements, the planet elements constrained to rotate on their own axes with the axes being constrained to rotate with the planet carrier element, the planet elements with their axes offset from their respective planet carrier element so as to bridge individually or in combination with other planet elements between the ring element and the third element of their respective assembly, the planet carrier elements being constrained by a rotation controlling means allowing free rotation in one direction and a controlled rotation in the other direction, the third elements of the assemblies being sun elements, the ring and planet and sun elements being in a form that will allow the transfer of torque at a fixed ratio between elements, the first element of the second assembly constrained to a fixed frame of reference, a third element of the second assembly rotating at a controlled angular velocity the control means being operative to progressively Increase or decrease the output gear ratio in accordance with the demand for an output lower or higher gear stage of operation.

Claim 8. A transmission according to claim 2 wherein the first elements are the ring elements of the respective assemblies, the ring elements being outer bodies having spaced endless scallop guides being adapted to receive sets of planet elements being In the form of rollers, the second rotating elements comprising of planet earner elements and planet elements, the planet carrier elements of the respective assemblies constrained to rotate about an axis collinear with the axes of their respective third elements, the planet carrier elements locating and controlling the motion of integral spaced sets of rollers corresponding to the planet elements of each assembly, the rollers bridging between the scallop guides of the outer bodies and the third elements of the assemblies, the planet carrier elements being constrained by a rotation controlling means allowing free rotation in one direction and a controlled rotation in the other direction, the third elements of the assemblies being sun elements in the form of respective cams, the first element of the second assembly constrained from rotating in one direction by a fixed frame of reference and free to rotate in the other direction.

Claim 9. A transmission according to claim 3 wherein the first elements are the ring elements of the respective assemblies, the second rotating elements comprising of planet carrier elements and planet elements, the planet carrier elements of the respective assemblies constrained to rotate about an axis collinear with the axes of their respective third elements, the planet elements constrained to rotate on their own axes with the axes being constrained to rotate with the planet carrier element, the planet elements with their axes offset from their respective planet carrier element so as to bridge individually or in combination with other planet elements between the ring element and the third element of their respective assembly, the planet carrier elements being constrained by a rotation controlling means allowing free rotation In one direction and a controlled rotation in the other direction, the third elements of the assemblies being sun elements, the ring and planet and sun elements being In a form that will allow the transfer of torque at a fixed ratio between elements, the first element of the second assembly constrained from rotating in one direction by a fixed frame of reference and free to rotate in the other direction.

Claim 10. A transmission according to claim 2 wherein the first elements are the ring elements of the respective assemblies, the ring elements being outer bodies having°spaced endless scallop guides being adapted to receive sets of planet elements being in the form of rollers, the second rotating elements comprising of planet carrier elements and planet elements, the planet carrier elements of the respective assemblies constrained to rotate about an axis collinear with the axes of their respective third elements, the planet carrier elements locating and controlling the motion of integral spaced sets of rollers corresponding to the planet elements of each assembly, the rollers bridging between the scallop guides of the outer bodies and the third elements of the assemblies, the planet carrier elements being constrained by a rotation controlling means allowing free rotation in one direction and a controlled rotation in the other direction, the third elements of the assemblies being sun elements in the form of respective cams, the third element of the second assembly being constrained to rotate at a respective fixed gear ratio relative to an input to the ^MeM Dean Gear, the control means being operable to supply a variable rotation to the first element of the second assembly across a continuous range of output gear ratios between low and high angular velocities at respective predetermined low and high output angular velocities.

Claim 11. A transmission according to claim 3 wherein the first elements are the ring elements of the respective assemblies, the second rotating elements comprising of planet carrier elements and planet elements, the planet carrier elements of the respective assemblies constrained to rotate about an axis collinear with the axes of their respective third elements, the planet elements constrained to rotate on their own axes with the axes being constrained to rotate with the planet carrier element, the planet elements with their axes offset from their respective planet carrier element so as to bridge individually or in combination with other planet elements between the ring element and the third element of their respective assembly, the planet carrier elements being constrained by a rotation controlling means allowing free rotation in one direction and a controlled rotation in the other direction, the third elements of the assemblies being sun elements, the ring and planet and sun elements being in a form that will allow the transfer of torque at a fixed ratio between elements, the third element of the second assembly being constrained to rotate at a respective fixed gear ratio relative to an Input to the transmission, the control means being operable to supply a variable rotation to the first element of the second assembly across a continuous range of output gear ratios between low and high angular velocities at respective predetermined low and high output angular velocities.

Claim 12. A transmission according to claim 2 wherein the first elements are the ring elements of the respective assemblies, the ring elements being outer bodies having spaced endless scallop guides being adapted to receive sets of planet elements being in the form of rollers, the second rotating elements comprising of planet carrier elements and planet elements, the planet carrier elements of the respective assemblies constrained to rotate about an axis collinear with the axes of their respective third elements, the planet carrier elements locating and controlling the motion of integral spaced sets of rollers corresponding to the planet elements of each assembly, the rollers bridging between the scallop guides of the outer bodies and the third elements of the assemblies, the planet carrier elements being constrained by a rotation . controlling means allowing free rotation in one direction and a controlled rotation in the other direction, the third elements of the assemblies being sun elements in the form of respective cams, the third element of the second assembly being constrained to rotate at a respective fixed gear ratio relative to an input to the transmission, the flow of a suitably formulated fluid or gas or like due to the action of the first element of the second assembly against a fixed frame of reference being directed and controlled in two circuits, the flow of said suitably formulated fluid or gas or like from the said first element of the second assembly in the first circuit being directed and controlled towards the contracting spaces on one side of the rollers of the first assembly so as to tend to restrict the movement of the rollers within the scallops of the first element of the first assembly, the flow of said suitably formulated fluid or gas or like In the second circuit being directed and controlled towards a part of the a transmission that provides a low resistance to flow, the progressive control of the amount of flow of the said suitably formulated fluid or gas or like in the first and second circuits operable to progressively change the gear ratio applied to a load connected to the first element of the first assembly of the Variable Ratio Multi-gear.

Claim 13, A transmission according to claim 10 wherein energy can be transferred to the suitably formulated fluid or gas or like and stored internally or externally so as to enable the return of the energy to the load when required.

Claim 14. A transmission according to claim 2 wherein the first elements are the ring elements of the respective assemblies, the ring elements being outer bodies having spaced endless scallop guides being adapted to receive sets of planet elements being in the form of rollers, the second rotating elements comprising of planet carrier elements and planet elements, the planet carrier elements of the respective assemblies constrained to rotate about an axis coHinear with the axes of their respective third elements, the planet carrier elements locating and controlling the motion of integral spaced sets of rollers corresponding to the planet elements of each assembly, the rollers bridging between the scallop guides of the outer bodies and the third elements of the assemblies, the planet carrier elements being constrained by a rotation controlling means allowing free rotation in one direction and a controlled rotation In the other direction, the third elements of the assemblies being sun elements in the form of respective cams, the rotation of the third elements causing motion of the second rotating elements, the motion of the second and third elements causing contracting and expanding spaces, the contracting spaces in the first assembly displacing a suitably formulated fluid or gas or like, the displaced fluid or gas or like being directed into and controlled in two circuits, the control means proportioning the flow of said suitably formulated fluid or gas or like in the said two circuits in accordance with the demand for an output lower or higher gear stage of operation, the flow of said suitably formulated fluid or gas or (ike in the first circuit being used to rotate the third element of the second assembly, the flow of said suitably formulated fluid or gas or like in the second circuit being directed and controlled towards a part of the transmission that provides a low resistance to flow, the suitably formulated fluid or gas or like being drawn into the expanding spaces of the first assembly in a controlled manner after completing the first or second circuits, the progressive control of the amount of flow of the said suitably formulated fluid or gas or like in the first and second circuits operable to progressively change the gear ratio applied to a load connected to the first element of the first assembly of the Variable Ratio Multi-gear.

Claim S. A transmission according to claim 12 wherein energy can be transferred to the suitably formulated fluid or gas or. like and stored internally or externally so as to enable the return of the energy to the load when required.

Claim 16, A transmission according to claim l wherein the axis of the input or inputs are colllnear with the axis of the third element of the first assembly, the axis of the output or outputs are coHinear with the axis of the third element of the first assembly, the axis of the third elements of the first and second assemblies are colllnear, the elements of both assemblies supported directly or indirectly by the fixed frame of reference, the motive source supported directly or indirectly by the fixed frame of reference, the reactive torque from the motive source acting on the fixed frame of reference.

Claim 17. A transmission according to claim 1 wherein the axis of the inputs are collinear with the axis of the third element of the first assembly, the axis of the output or outputs are collinear with the axis of the third element of the first assembly, the axis of the third elements of the first and second assemblies are collinear, the elements of both assemblies supported directly or Indirectly by the fixed frame of reference, a motive source supported directly or indirectly by the fixed frame of reference and connected to the third element of the first assembly, another motive source supported directly or indirectly by the fixed frame of reference and connected to the third element of the second assembly, the reactive torques from the motive sources acting on the fixed frame of reference.

Claim 18. A transmission according to claim 1 wherein the axis of the inputs are collinear with the axis of the third element of the first assembly, the axis of the output or outputs are collinear with the axis of the third element of the first assembly, the axis of the third elements of the first and second assemblies are collinear, the elements of both assemblies supported directly or indirectly by the fixed frame of reference, an input driven by external Influences Including wind connected to the third element of the first assembly, another input source driven by external influences and connected to the third element of the second assembly.

Cjajm_l9. A transmission having an input and two contra- rotating outputs and being of the epieyclic type involving interaction of three mechanically distinct rotating elements with any suitable form that allows the transfer of torque between input and output, namely a sun element, a ring element and a planet element being In each of at least first, second and third co-axial epieyclic assemblies, a second rotating element of the first assembly and a second rotating element of the second assembly being constrained to rotate at a common angular velocity, the first element of the first assembly and the first element of the third assembly being constrained to rotate at a common angular velocity, and control means for progressively changing the gear ratio applied to a load connected to the first element of the first and third assemblies and another load connected to the second element of the third assembly of the Variable Ratio Multi-gear characterised in that the first and second assemblies each represent unequal fixed gear ratios respectively between the input and the output of the Variable Ratio Multi-gear the first and second assemblies arranged so that If Individually each assembly has their first element constrained and their third element rotated In a certain direction the second element will tend to rotate in an opposite direction relative to the tendency of the other assembly, the third assembly arranged so that if individually it's First element is constrained and the third element rotated in the same certain direction of the first and second assemblies the second element will tend to rotate in the same direction as the second assembly, the control means being operative to progressively increase or decrease the output gear ratios In accordance with the demand for an output lower or higher gear stage of operation.

Claim 20. A transmission according to Claim 1 wherein more elements can be included to provide overdrive speed and directional reversing features to a load coupled to the first element of the first assembly,

Claim 21. A transmission according to Claim 1 wherein the rotation blocking and controlling means required can provide energy storage able to be re used, with mechanical or pressure accumulation.

Claim 22. A transmission according to Claim 1 wherein the rotation blocking and controlling means can provide motor braking by automatically reversible one way clutches working in sequence for internally accessing carrier or ring-gear restricting.

Claim 23. A transmission according to Claim 1 where the compact "Torque Multiplier" action may be accessed by sequentially controlling the storage of energy, internally or externally.

CJairjQ_24. A transmission according to Claim 1 where the control of the load and with internal or external remote control between the first and the second and third elements of the second assembly can be activated by electro-magnetic, magnetic fields, or electro high voltage to activating suitable contents including Liquid Polymers In Silicon oil .

Claim 25. A transmission according to Claim 1 where reactive feedback from the load is used to automatically stabilise mobile transport.

Cjalm 26. A transmission according to Claim 1 where sophisticated electronic sensors are placed in strategic positions including gravitational and tilt Sensors used to incorporate self stabilising to over ride mechanically fed back reaction from tilting of vehicles.

Claim 27. A transmission according to Claim 1 where multiple configurations of this Gearing can be linked together to perform three dimensional manipulation Including to interact and integrate the Camber Control with the Caster control as shown in Fig 5 (lower) and Fig 12 with reference to Fig 30

£jajm_28. A transmission according to Claim 1 where a number of cages able to rotate about the first axis and each cage wholly or partially enclosed by the body, means between the central shaft and any number of the cages, means between the body and any number of the cages, means between the cages In any sets of combinations of any of the cages, wherein each input and each output is applied to or taken from one of the body, the central shaft and any number of the cages, and application of a First torque to the central shaft causing the central shaft to rotate about the axis while torques are applied, about the first axis, to any number of the cages will cause at least one of the cages, cams (sun-gears) and the body to rotate and, furthermore, variation of one of the torques between zero and a maximum value will cause a variation of the ratfo of the angular velocities of the central shaft and the body through the actions of the means.

Claim ¾Oi— A transmission according to cloima 1 to 30 28 substantially os described herein

Cl im 30. A transmission occording to claims 1 30 substantially- as herein describcd-witft reference to any one or more of the accompanying drawings.

MALCOLM LEONARD STEPHEN DEAN