AU739831B2 - Improvements to hyperbolic fuel turbines - Google Patents

Description

1 This specification associated with improvements to hyperbolic fuel gas-turbines following P01344 31/7/96(Lapsed) and P05132,P08422, P09352 and PP0855 all in 1997. This invention details four sizes of hyperbolic gas turbine previously disclosed in application 42,173/93 with improvements and extensions which run on a multiplicity of liquid fuels with.a heat release capacity from 3 ,000watts to 1,200,000 watts. The main liquid fuels for consumption in the four sizes of turbine are ethanol,methanol,petrol (specifically unleaded),Diesil and Kerosine plus Kerosine or diesil as a thinner in distilled oil mixes and also a broad range of coal tar distillates and coal tar that has been thinned. One important option for the turbines is the use of high temperature sintered alloy in the rear blade section as slits in a disc sintered on a high temperature alloy base with the base welded to hollow shaft through which cooling water passes. This 15 high temperature material Pneans fiel tan almost be stoiciometrically burnt in air which means combustion temperatures can reach 2,500°K with rear blade outer tip temperatures sustaining 14000C or greater at up to 150 meters/second outer tip speeds. This greatly enhances efficiency of turbine to convert energy to rotational energy.

There are four sizes of turbine under development,each made of conical sheath segments of each having five segments. The sizes are as follows: Number 1,60mm. long conical segment,diameters tapering from 120mm. to 82.2mm. to 55.6mm. to 39.8mm. to 36.0mm. to 34.5mm.

S" with the turbine being 300mm. long. Number 2,80mm. long conical segment,diameters tapering from 160mm. to 123mm. to 93mm. to to 54mm. to 45mm. with the turbine being 400mm. long. Number 3,100 mm. long segment,diameters tapering from 200mm. to 161mm. to 127mm.

to 98mm. to 74mm. to 55mm. with the turbine being 500mm. long.

Number 4,120mm. long conical segment,diameters tapering from 250mm.

2 to 190mm. to 141.5mm. to 104.5mm. to 79mm. to 65mm. with the turbine being 600mm. long. The key aspect to turbine performance is combustion speed and combustion speeds over 100m/s'are achieved by a droplet size of less than 50 microns in diameter. The two main ways of achieving this are by adding surfactant to the fuel which helps the spread of liquid fuels on intermediate blade surfaces which have spiral grooves machined in flat surface in a lathe with a low angle pointed tool of very low ti.p radius with greater than 4x grooves per millimeter and preferably 32x per millimeter and tool angle less than 60 So as jet of fuel emerges from less than .3mm. hole at high speed and high pressure contact on misting surface blades with grooves and edge serations helps the formation of droplets which can be blown down turbine sheath in low density air stream.

Propellant gases such as ethylene or acetylene can be injected into fuel as fuel is loaded and pressurized for high speed release through less than .3mm. holes pointing down turbine sheath with jet reaching up to 100m/s and the propellant gas and surfactant loaded into fuel by fuel pump helps droplet formation in the low density, low pressure air stream at front of turbine. Ethylene and acetylene are choosen because they come in bottles at over 2 Mpa. (megapascal) and they have limited solubility in most liquid fuels that are economically acceptable.

The blade positions for the four sizes of turbine are as follows and are a indication of what is required for each turbine although other combinations can be developed and used. Each blade plate has preferably 8x or more blades protruding and in the case of sintered tungsten alloy discs as rear blade plates again 24x or more slits of divergent angle which are angled as normal blades are. If the turbine is adapted for lower temperature operation then plates 3 instead of discs with slits are used with the plates being made of high temperature material that can sustain operation at up to 1,100 C. The final combustion temperature being governed by the number of holes of less than 2.00mm. diameter in a 3mm. thick front plate. This plate with a certain number of holes in it governs the final temperature and volume of exhaust gas and the final torque generated on the rear blades. If the number of holes in front plate are limited the temperature climbs to over 2,000 0 C and the slits are of a certain width to restrict pressure drop. The other option is a lot more holes in front plate means the blade plates at rear allow faster flow and torque is lower. This however is not prefered as combustion speed goes over 300m/s and this requires speciallized misting of fuel,so exit speeds in rear of turbine whether very high temperature (greater than 2,0000C) or at moderate temperatures of less than 1,1000C are less than 300m/s by the use of discs as rear blades with slits that restrict the pressure drop and keep the torque high even at low power outputs from turbine making the turbine system economical with fuel. In the case of moderate temperature regions (less than 1,100 C) the rear discs can be of high 0 temperature alloy such as Inconel 600 and not sintered tungsten alloy. For the Number 1 size turbine the positions for blades are as follows: Blade plate No.l at 30mm. into sheath,blade plate No.2 at 90mm. into sheath with these front blades being responsible for thinning and speeding up air stream past fuel injection points which are pointed towards the intermediate blade plates or misting surface blade plates with grooves at 120mm. and 150mm. into sheath with these misting surface or intermediate blade plates followed by the sparking points after which the 5x rear blade plates or discs are located at 180mm. and 2 10mm. and 240mm. and 270mm. and finally 4 300mm. down sheath. For Number 2 size turbine the 4x front blade plates at 40mm. and 80mm. and 120mm. and 160mm. into sheath with 3x misting surface or intermediate blade plates at 200mm. and 230mm.

and 260mm. followed by 7x rear blade plates or discs at 280mm., 30 0 mm., 3 2 0mm.,340mm.,360mm.,380mm., and 400mm.. Fuel is introduced after set of front blade plates with ignition points after set of misting surface blade plates in all sizes of turbines. For Number 3 size turbine the front blade plates are at 2 5mm.,50mm.,75mm.,100mm., 125mm.,150mm.,175mm., and 200mm., followed by 4x misting surface blade plates at 2 2 5mm.,250mm.,275mm., and 300mm., followed by rear blade plates or discs at 8x points at 3 2 5 mm.,350mm.,375mm.,400mm., 4 2 5 mm.,450mm.,475mm., and 500mm.. For Number 4 size turbine 8x front blade plates are at 3 0mm., 6 0mm.,90m.mm.,120mm.,mm.,180mm.,210mm., and 240mm., followed by 5x misting surface blade plates at 270mm., 30 0mm.,330mm.,360mm., and 390mm., followed by 10x rear blade plates or discs at 4 10mm., 4 3 0mm., 4 50mm.,470mm.,490mm.,510mm.,530mm.,550mm., 570mm.,590mm.. For Number 1 size turbine up to 200x less than 2 .00mm.

holes are drilled in front plate (3mm. thick) infront of turbine to regulate air intake and final combustion temperature limit. For

S

:20 Number 2 size turbine has up to 400x less than 2.00mm. holes with Number 4 size turbine having up to 1,600x less than 2.00mm. holes.

For all sizes of turbine there are three spark gaps (at least) having a 1.6mm. wire tungsten point (electroplated with Ruthenium) 25 pointing down sheath so electtons pass through Tungsten ring (electroplated with Ruthenium) which is a anode and excess charge electrons flow through spark gap by a 7,000 volt pilot supply of about 3 0 0 watts shared over the 3x spark points. A additional supply of 500watts plus, is superimposed at each spark point over high 5 voltage supply from about 24 volts in Turbine size I to about 48 volts in Turbine size 4 accross spark gap in turbine. All supply to spark gaps being from high speed D.C. (direct current) generators with the 7,000 volt supplies being set through transformers from 24 volt in turbine sizes 1 and 2 and from 48 volt in turbine sizes 3 and 4 with the alternating current generators of 24 volt and 48 volt running off the turbines through a geared down ratio of up to lOx times in the case of the Number 1 size turbine and this charges the lead acid batteries that run the 12 volts .18 Kilowatt D.C. motor that pumps and pressure loads fuel,propellant and surfactant and runs the 7,000V. transformers. So 2x ordinary 12 volt car batteries are needed for turbine sizes 1 and 2 with 4x ordinary 12 volt car batteries for turbine sizes 3 and 4 and to start turbines through a 24 volt high speed D.C. motor for turbine sizes 1 and 2 and 48 volt high speed D.C. motor starts turbine sizes 3 and 4. The key advantage of this type of turbine is the high torque produced by the flow restrictive slits in the rear blade section which is aided by the magnetic coil around the turbine sheath which acts on excess electrons ejected and electrons produced by spark gap down sheath go and the magnetic field strength close to the outer diameter of rear S blade plates or discs with slits to give a high magnetic torque affect by electrons circulating in hot gas at up to 200,000m/s so that hot gas in magnetic field acts as a electron membrane along with the aspect that a multiplicity of fuels can be burnt in the turbine with particular interest being coal tar at up to volume to volume in principally methanol and wood or dry plant matter that hasundergone destructive distillation with distillates thinned with principally methanol. Efficiency is markedly higher at operating temperatures in rear blade section of over 2,000°C.

6 The following 17x figures are the turbine system and components and sections of the turbine with the following description giving details of size and mode of operation and construction of turbine and components. Figure 1 is a simplified overview of all of the components of the turbine and support components in a cylindrical housing 65 which is hinged about its vertical mid-point and cylindrical housing lies on its side so as to fit into vehicle etc., with large diameter reduced R.P.M. fan 33 at front of cylindrical housing in enclosure 67 so when top half of cylindrical enclosure opens on top side for access to turbine and accompanying components there is no risk to person checking turbine system. Item 1 is the turbine with the front blade plates 2 that speed up low density air stream and regulate final R.P.M. level to 60,000R.P.M. in turbine size 1, 50,000R.P.M. in turbine size Number 2 ,40,000R.P.M. in turbine size 3, 30,000R.P.M. in turbine size 4 all being regulated by crease in front blades that builds a pressure zone under blades contact surface with air as in patent application 60,658/96 by this inventor. The thermal limit in the Number 1 size turbine is 200,000 watts,Size 2 turbine limit is 4 0 0 ,000watts (thermal),size 3 turbine limit is 75 0,000watts and size 4 turbine limit is 1, 200 ,000watts (thermal).

The misting surface blades 68 of greater than 16x grooves per millimeter are between fuel injection hole sites and sparking points.

The rear discs that have slits ground into them at blade angle configurations are shown by 3 and can be high temperaure alloy or a disc of high temperature alloy with sintered tungsten alloy powder pressed and sintered in a vacuum of than 10-3 atmospheric density at over 1,0000C with divergent slits then ground in and the final disc with slits electroplated with Ruthenium and mounted on turbine shaft by welding. (mounting of disc and blade plates will be described 7 later) The initial composition of the tungsten sintered alloy when pressed and before sintering in hydrogen at low pressure and high temperature varies within the following limits in terms of weight percent: Tungsten powder of less than 5 microns of from 50% to (weight percent) is added to Tantalum oxide 15% to 25% (wt. and to 15% Hafnium Oxide and 3% to 8% of Thorium oxide with carbon with the powder pressed and infiltrated with Ruthenium Nitrosylnitrate to make the Ruthenium binder up to 1.5% when heated back to metal. All oxide powders are ball milled and all powders are significantly less than 5 microns in size. Windings 4 are wound over glass or alumina wool on outside of sheath and grit spaced to greater than .5mm. and the following windings schedules for each size turbine are used. All winding strip for windings is Silver exchange coated and heated to 500 C to sinter Silver coating before winding coated copper strip. Winding starts from large diameter end of sheath and each layer is shortened at narrow end of turbine sheath. For Number 1 size turbine 4x layers of 50x windings of 6x3mm.

copper strip is layed with broad end over sheath followed by layer of 42x windings,then 34x windings, then 26x windings, then 18x windings so that the coil is tapered from large diameter front end with up to 300 amps at 24 volts D.C. being delivered to coil from a high speed generator 47 running parallel to turbine. The construction and design of generator will be discussed later. For Number 1 size turbine the coil can reach up to 4 tesla field strength by 25 virtue of the fact that at a certain spacing each winding is additive to total field strength for that spacing but this multiplicative affect is about 99.9% efficient so the coil is stronger at large diameter end where most of the windings are and weaker at the lower diameter end of fewer windings so at distance in turbine close to 8 outer most winding of coil field strength drops linearly with distance from coil edge and can be as high as 4 tesla accross most of the surface of the slits in rear blade discs and due to the reduction of diameter of the sheath which causes electrons to spiral.

down turbine thus assisting torque to rear blades or slit surfaces by the gas acting as a electron membrane and electrons spiralling down turbine sheath at up to 2 0 0 ,000m/s. On number 2 size turbine winding layers are 55x,55x,55x,55x,55x,47x,39x,31x,23x, 1 5 x with the windings being out of 4x7mm. copper strip layed with broad end over sheath and subsequent windings being also grit spaced to over with the achievable field strength being up to 6 tesla with up to 500 amps through coil and 30 volts D.C. from high speed generator 47. For Number 3 size turbine 3x6mm. strip is used with broad side over sheath with the layers being as follows: 8 0x,80x,80x,80x,80x, 8 0x,72x,64x,56x,48x,40x,32x with taper towards narrow end and grit spaced to greater than .5mm. with achievable field strength being S up to 8 tesla with 800 amps at 40 volts flowing though coil from high speed generator 47. For Number 4 size turbine 4 x7mm. strip is used with broad side over sheath with the layers being as follows: i'0 8 0x,80x,80x,80x,80x,80x,72x,64x,56x,4 8 x, 4 0 x, 32 x with taper towards narrow end and grit spaced to greater than .5mm. with achievable field strength being up to 10 tesla with 1300 amps at 48 volts flowing through coil from high speed generator 47. The less than 2.00mm. holes in 3mm. thick stainless steel front plate 10 to turbine 7 with greater than 3 .00mm. holes for 3 0 0m/s air flow down outer corridor 5 with up to 250 holes for No.l size turbine,500x holes for No.2 size turbine, 1000x holes for No.3 size turbine,2000x holes for No. 4 size turbine denoted by 8. The corridor 5 for 300m/s.flow is a single cone to half way down turbine sheath to a cylinder with 9 serations machined on internal surface for better forced flow turbulent convection as heat from turbine that has not been converted to rotational energy and withdrawn from turbine transfers to cooling air stream in this expansion zone of cylinder with serations with flows going over 600m/s. The holes in front plate are less than 2.00mm. holes for the greater than 2 0 0 m/s air flow for cooling water spiral 69 from hollow water cooled turbine shaft The holes to greater than 200m/s flow corridor 6 are shown by 9 and are less than 2 .00mm. in diameter with up to 500x holes for number 1 size turbine,1000x for number 2 size turbine,1700x holes for number 3 size turbine,3000x holes for number 4 size turbine. The outer cone for number 1 size turbine tapers from 250mm. to 155mm.

half way down turbine sheath with inner corridor for 300m/s air flow tapering from 200mm. to 105mm. with the cylinder section being serated on internal surface for enhanced air convection. For Number 2 size turbine outer cone tapers from 300mm. to 2 55mm. with inner cone tapering from 240mm. to 165mm.. Again inside cylindrical surface of inner surface is serated for enhanced air convection for this size and all turbine sizes. For Number 3 size turbine outer 0O cone tapers from 360mm. to 2 60mm. with inner cone tapering from S 300mm. to 200mm.. For Number 4 size turbine outer cone tapers from 500mm. to 360mm. with inner cone tapering from 380mm. to 2 All cone dimensions on sheaths and corridors are internal diameters.

All of above cones and turbine sheath are welded to 3mm. plate with holes 10. The large stainless steel fan 11 in front of turbine front plate is sealed in 5mm. thick stainless steel compartment 12 by welding as with cones for air cooling corridors and turbine sheath. A 400# mesh stainless steel cloth 13 is over front of compartment for dust extraction. openings per inch) This front 10 cover with 400# gauze at front has up to 500x holes for Number 1 size turbine of 6mm. diameter and up to 000x holes for Number 2 size turbine and up to 1700x holes for Number 3 size turbine and up to 3000x holes for Number 4 size turbine. All hole sizes are 6mm.

diameter in 5mm. stainless steel plate. A flange joint in turbine exists at front of turbine 14 and rear of turbine 40 with brass bolts which have been soldered with lead solder to fix flanges with other mount being to front compartment of large fan. Two concave surface pulleys 15a and 15b are on connection to turbine shaft for greater than 250m/s plastic belt transmission to paralleled shafts 71a and 71b with 71a also hollow and water cooled through centre with second concave curved pulley 4 3a on shaft 71a being driven by pulley 15a on shaft 70 and concave curved pulley 43b on shaft 71b for power transmission between concave curved pulley 15b on shaft and concave curved pulley 43b on shaft 71b. The plastic belt material for high speed power transmission is 4 0mm. wide for Number 1 size turbine and can transmitt up to 8 Kilowatts of high speed energy and for Number 2 size turbine plastic belt is 50mm. wide on S concave pulleys and can transmitt up to 16 kilowatts with Number 3 size turbine plastic belt 60mm. wide and can transmitt up to 32 kilowatts 6f high speed energy with Number 4 size turbine 80mm. wide plastic belt which can transmitt up to 64 kilowatts of high speed energy between shafts 70 and 71a. The turbine bearing housing at 16 is supported by one of 5x ribs 2 0c which are bolted together through at least 6x rods 18 spaced by bushes 19. Rib 20d supports external cover 12 which supports turbine sheath and external corridors by plate 10. Water bush 17 is stationary and water is injected through hollow shaft through this stationary P.T.F.E. bush. Cylindrical housings 65 are attached to rib sections 20 that are bolted together 11 by rods and bushes 18 and 19 with internal sizes being 500mm.

diameter for No.1 turbine and 700mm. long and 600mm. diameter for No.2 size turbine and 800mm. long and 800mm. in diameter and 1200mm.

long for No.3 turbine and 9 00mm. in diameter and 1 4 00mm. long for No.4 turbine with all cylindrical housings being out of 1.6mm.

stainless steel. The sheaths and outer corridors for No.1 and No.2, .9mm. except for cylindrical section of 300m/s corridor which has serations machined in and this is 2 .00mm.. The sheaths and corridors of turbine sizes 3 and 4 are 1.6mm. stainless steel or high temperature alloy except for cylindrical section of 300m/s corridor which is 3.00mm. and has serations machined in. The first gear reduction unit 21 with bearings for high R.P.M. central gear being 22 with intermediate gears bearings 23 with central gear being 26 with stationary cover 24 and rotating internal cover 25. Shaft from first reduction unit goes to second central gear 32 supported by bearings 28 to intermediate gears supported by bearings 29. The rotating S cover 31 of second reduction unit 27 has stationary cover supported by rib 20a and large fan at front 33 for bulk cooling air motion of about 8m /s in No.l turbine,16m 3 /s in No.2 turbine,30m 3 /s in No.3 i.i 0 turbine and 50m 3 /s in No.4 turbine. With large front fan in a full screen enclosure for safety-enclosure 67. A rear tungsten sleeve that has been electroplated with Ruthenium 34 is bolted on end of turbine sheath and is about 2mm. thick for all sizes of turbines and about 100mm. long for No.l size turbine and 150mm. long for No.2 size turbine,200mm. long for No.3 size turbine and 250mm. long for No.4 size turbine with about 50% of thermal energy going into 3 0 0m/s air stream through coil and tungsten sleeve and other 50% of thermal energy pouring into shaft water line and cooled through copper tube at high energy idle with over-speed of turbine blowing more air down 12 corridors and resistance in coil windings increasing and power dropping in coil and subsequent torque failure with system failure at prolonged high energy idle when energy i-s not withdrawn as usefull work and unburnt fuel escaping into cooling air streams and mixing there. This protection is vital for high energy idle with blade drag from frdnt blades of turbine preventing very high over-speed of turbine which bearing cannot stand for long. A expansion cone to help mixing of emerging air from coil corridor where 300m/s air stream flows and also exit gas from turbine emerges with gauge of material being the same as other conical sections.

This expansion cone section bolted on end of tungsten sleeve is and of stainless steel or high temperature alloy. A second expansion cone of stainless steel of the same gauge as the sheath and other conical sections is bolted on end on cylindrical section that has a serated internal surface for enhanced convection of air over coil windings and section that separates 200m/s air flow corridor where copper water spiral is supported end flared cone segment 36. The serations on the internal surface of cylindrical section are 38. The external corridor wall has a expansion cone bolted on end 37 and is of the same gauge as other conical segments of sheath and corridors.

A rear conical deflector 39 goes on shaft and is welded to shaft

C

and has been filled with copper so that prior to welding it slides on shaft with copper forming a close tolerance for good heat conduction and deflects exhaust gas from turbine to away from flange joint 40 and rear bearing housing 41 which is supported by rib A stationary P.T.F.E. water bush 42 supported by 20e is on the end of shaft and exiting hot water from shaft goes to water spiral 69 in 200 m/s corridor. The concave pulley 4 3a on parallel shaft 71a to which turbine shaft 70 transmitts high R.P.M. rotation by a plastic 13 belt driven by concave pulley 15a with a bearing housing at each of shaft 71a with bearing housing 44a supported by rib 20d and bearing housing at other end being supported by rib 20e (bearing housing 51a). Shaft 71a drives a conical reducing fan 45 with at least five sets of blade plates which supplies a compressed air stream with two points on fan supplying a pressure differential of at points 46a and 46b to water reservoir 72 and oil reservoir 54 which drives water into centripetal pump for water pressurization 49, also on shaft 71a and oil from reservoir into centripetal pump (also on shaft 71a) for oil circulation- centripetal oil pump 50. A high speed D.C. motor 48 starts turbine of about 24 volts for turbine sizes 1 and 2 and is about 3.5 kilowatt at high speed (10,600 and about 24v. and about a 5.0 kilowatt motor for turbine sizes 3 and 4 (7,600 R.P.M.) at about 48V.. A second concave pulley 15b on Turbine shaft transmitts torque to second parallel shaft 71b by concave pulley 43b by plastic belt as with 43a and is supported by bearing housing 44b on rib 20d and bearing housing 51b supported by rib 20e for D.C.

*c.o motor 48. (Shaft 71b on other side of turbine housing to that of shaft 71a for fan 45, generator 47 and centripetal pumps 49 and '20 The stationary P.T.F.E. bush supported by rib 20e is for water output from parallel high speed shaft 71a is 52 with 53 being the stationary P.T.F.E. bush for input into parallel high speed shaft 71a. Water from the centripetal water pump 49 that flows through hollow turbine shaft 70 and through copper tube water spiral 69 and back to water reservoir 72. The copper tube spiral for cooling water from central turbine shaft is 40 meters long of copper tube being 1/4 inch copper flattened tube for No..1 size turbine and 5/16 inch flattened copper tube for No.2 size turbine and 3/8 inch flattened copper tube for No.3 size turbine and 1/2 inch flattened copper tube 14 for No.4 size turbine. The water reservoir 72 has impressed air pressure differential 46a and 46b from conical air fan 45 which forces water to turbine shaft through centripetal water pump 49 through outline 56a then to turbine shaft and'is returned from copper spiral to water reservoir through line 56b with water from water reservoir going directly to bearing housings and parallel shaft 71a from 56a and not passing through centripetal water pump and then returning directly through water return line 56b. Oil from oil reservoir 54 has impressed air pressure differential 4 6a and 46b from conical air fan 45 to push out oil through oil output line from reservoir 54 which goes to bearing housings of turbine and parallel shafts as well as bearing housings in the two in-line reduction units on turbine drive and bearings of generators 47 and D.C. motor 48 and 7000V. motor. Oil from centripetal pump 50 being injected to sites in gear reduction unit 21 between meshing gears.

Oil on line 55a from 54 also goes to reduction gear box 58 on fuel oi loading 12 volt D.C. motor 57. The impressed air pressure forces 99** 9. 9* lubricating oil to bearings and gear sites and then oil is forced by S• same air pressure differential through return passages to return oil .0 line 55b to oil reservoir 54. Oil from the reservoir first goes to oil centripetal pump 50 which pressurizes oil for injection to high speed mesh sites for gears in gear reduction unit 21. For bearings and lower speed sites oil can come directly from oil reservoir along line 55a. Fuel pump 59 which is driven by .18Kilowatt, 12 volt D.C.

motor through gear reduction box 58 with gear reduction box having s ee oil injected directly from oil output line 55a from reservoir 54.

Pressured fuel to about 2.5Mpa. fills a spring loaded piston with a position switch which activates fuel pump when spring loaded piston 60 is near empty. A compressed gas bottle of preferably 15 ethylene 63 feeds into fuel pump and is released into fuel through a solenoid valve when fuel pump is active. The 7,000 volt full wave rectified D.C. pilot arc supply for the spark gap in the turbine is a incredible nuisance and 99% of this high voltage energy is consumed through D.C. motor which has very many fine wire windings (discussed later) and although back E.M.F. is very small and final speed can never be reached this motor 61 compresses air by fans in motor thus limiting speed and consuming energy. Any excess high voltage energy charges a capacitor with Barium Titanate between charged surfaces and this capacitor 62 can Store over 5 seconds of direct charge from high voltage supply itself (without motor). A surfactant tank 64 holds surfactant and a fuel mix for suction into fuel pump. Figure 2 is of the fuel pump system with Figure 2a a plan view of the fin pump with 2b showing the overlapping fins with the reducing drive,synchronized screw mount shafts with P.T.F.E. seals for each level with 2c showing the four levels of the fuel pump and 2d being a flow diagram of fuel through the fuel pump system and 2e being a diagram of the 6x reduction gear box. In Figure 2a the s plain view of fuel entering and leaving by arrows 88 is shown with :o .20 over-lapping fins which pressurize and move fuel through cavity 73.

Over-lapping fins 74 are shown in plate 75 with allignment holes 76 g for bolting plates of the 4x levels in the pump together. Item 77 is 0 the reducing diameter shaft through the four levels of the pump.

In Figure 2b two discs are shown with overlapping fins in cavity plate 75 sandwiched between spacing plates which are about 0 thick (item 80). Item 79 are the P.T.F.E. bushes for sealing each level and allowing significant reduced friction resistance that shaft and over-lapping fin discs turn in. The reducing shaft 77 is shown with a cylindrically smooth surface through spacer plates and 16 a screw thread which tightens in the direction of rotation of finned disc and locks on ledge with the next spacing plate's smooth cylindrical surface being reduced further in diameter. The bolt that bolts the four levels of the pump together 78 through allignment holes 76.is shown. In Figure 2c the four levels of the pump is shown with the lowest level where fuel is sucked in through pump 81 and then moved to next level where fuel is pressurized and propellant ethylene is injected along with pressurized surfactant from level 3 through 83 to injection point at level 2 at 82. The surfactant-fuel mix is sucked into system through level 4 at 84 which that goes to level 3 for surfactant pressurization. Module 1.5 gears of equal size synchronize over-lapping fin disc motion with gears at base of pump 85 with level 1 and 2 discs being about 70mm. in diameter and 8mm. thick with fins protruding about 5mm. with about 5mm. over-lap.

The discs for level 3 and 4 are 1mm. thick with about a 1mm.

protrusion and over-lap. All discs with fins are brass while shaft 77 is steel being 24mm. in diameter reducing to 20mm. with pitch thread for gears reducing to 16mm. through spacing plate then 12mm. with 1mm. pitch thread for first level of discs then through spacing plate to 8mm. with 1mm. pitch thread through discs reducing to 6mm. through spacing plate then 5mm. with .5mm. pitch S:s through level 3 discs and then 4mm. through spacing plate then 3.7fm.

with .35mm. pitch reducing to 3mm. through spacing plate. In Figure 2d the overview of fuel loading and supply to turbine is shown with 57 being the 12 volt D.C. motor through 6x reduction box 58 and four level disc/fin pump 87 with the compressed ethylene gas bottle 63 released through a on/off switch to solenoid release when motor 57 is going, through needle valve/solenoid 96 at various settings for various fuels. Ethylene goes into 4x level fin/disc pump 87 17 along line 97 with surfactant and fuel mix from tank 64 into pump 87 along 89 with input through 90 for fuel with the pressurized loaded fuel pushing up a spring loaded piston which activates a switch 93 when cylindrical cavity 91 empties of fuel with spring 92 maintaining the neccessary 2.5MPa. for high speed fuel injection into turbine through variable position solenoid needle valve 94 which regulates the amount of fuel flowing to turbine by making the solenoid coil work against a spring and adjusting the field strength in the solenoid by a in-line variable resistor and governing the amount of fuel to turbine through line 95. In Figure 2e the 6x reduction gear unit is shown for the 12 volt fuel pump motor with 6x oil injection points 98 and 2x sets of module 1.5 gears 101 and 102 and the bearing pair of oppositely faced bearings 99a for input coupling from motor 104 and bearing 100a and 100b for through shaft through first reducing gear to second reducing gear both screwed to shaft between lock nuts 105 and also oil supply to bearing pair 99b for output shaft 103 to fuel pump 87. Oil drains to bottom of gear box and is forced back to oil reservoir through return line being injected through 6x points by supply line 55a. Impressed air pressure from high speed fan 45 along lines 46a and 46b force the return of oil.

Figure 3 is of the spring loaded cylindrical cavity for loaded pressurized fuel and the variable position needle solenoid valve and with a 1/8 inch stainless steel tube that goes into turbine for injection of high speed fuel as jets through holes less than .3mm.

in diameter. Figure 3a is the spring loaded cylindrical cavity with switch. Figure 3b is position switch for spring loaded cavity.

Figure 3c is variable position solenoid for fuel release to turbine.

Figure 3d is the 1/8 inch stainless steel tube with less than .3mm.

18 holes for high speed fuel jets. In Figure 3a 91 is the cylindrical cavity with 92 being the 400mm. long tapering spring that maintains the required 2.5Mpa. fuel pressure for high speed injection down turbine and being tapered allows uniformity of pressure for small travels of about 40mm. before fuel pump is switched off by switch 93. Item 106 is P.T.F.E. bush that forms seal ih 50mm. Internal Diameter cylindrical cavity which is bolted between two discs with discs welded to shaft along length of cylindrical cavity 111. In Figure 3b a double spring arrangement 107a and 107b means that base 110 that contacts piston of two discs with P.T.F.E. seal and pushes up compressing spring 107b and allowing shaft to slip through P.T.F.E. locating bush 121 thus disengaging electrical contact at lugs on shaft at 109 to switch contact at 93 on fixed ring to side of cylinder. The ring 108 holds re-compression spring 107a which means that when travel of piston is complete and switch disconnects and cylindrical cavity empties of fuel spring 92 forces piston down and 107b forces ring 108 down on piston and lug 109 makes electrical .:o o contact with switch 93. Figure 3c is the variable position needle valve for fuel release to turbine 94 which is a cylinder with tube I ::0ZO shaft filled with permanent magnets with a spring 113 pushing to close valve through tube shaft 117 through locating bushes and a lock nut on end of tube shaft being 120 with solenoid 112 opening needle valve 114 with a in-line resistor supplying power to solenoid to vary the extent to which needle moves back in cavity in brass socket on end of spring loaded shaft with a P.T.F.E. seal 115 in tapering cavity of brass cavity 116. The variable resistor varies S. power supply to solenoid which opens needle valve cavity to let more fuel through line 95 to turbine. In Figure 3d the 1/8 inch stainless steel tube is flattened on end with a weld seam to seal 19 119 with tube 117 having about .15mm. diameter holes with about 3x tube sites per turbine with a multiplicity of holes extending different diameters into turbine with about a total of 9x holes for No.1 size turbine,18x holes for No.2 size turbine-,24x holes. for No.3 size turbine,42x holes for No.4 size turbine with methanol which has about 17.7 Mega-joules per litre being injected down turbine at about 80m/s at 2.5Mpa. and other fuels of higher energy densities such as petrol or kerosine being injected at greater than 100m/s down turbine at 2.5Mpa. impressed pressure from pump and cylinder.

The .15mm. holes are item 118.

Figure 4 is of the 4x major bearing pairs in the turbine system with Figure 4a the housing itself and Figure 4b a copper ring for the two directional flow of cooling water to bearings and lubricating oil to bearings. In Figue 4a of the bearing housing for the high R.P.M. precision bearing pair 126 of preferably single row angular contact ball bearings with the turbine sets 16 for front with bearing housing being mounted to rib 20c and rear set 41 being mounted to rib 20e. The parallel high R.P.M. shaft next to turbine can have smaller bearings in pairs with the front set 44a being 30 mounted to 20d and rear set or pair 51a in mounting mounted to rib 20e. The hollow turbine shaft 70 goes through the bearing housing 122 (shaft 71a as hollow parallel shaft to turbine) which is bolted to ribs 20c,d or e depending on which bearing housing it is with bolts 125. Oil input injection from oil reservoir 54 along line by impressed air pressure differential in oil reservoir by 46a and 46b from conical fan 45 which sprays onto bearings with impressed air pressure differential 46a and 46b from conical fan forcing accumulated oil in bearing housing out through holes in copper ring 134 that are radial holes to groove in bearing housing 122 for 20 return along oil return line 55b. The groove from oil collection and return is 123. A split copper bush for circulating cooling water around bearings outer cover exist inside housing and is 127 and is silver soldered together and accurately machined and has support rings with grooves cut in for the passage of water also silver soldered so that they give strength to the copper bush structure for cooling water. The copper support rings with grooves and slits are 128. A P.T.F.E. bush is mounted on inside of bearing housing and this oil seal 129 is screwed into bearing housing 122 by counter sunk screws 130. Threaded section of shaft behind bearing pair at 131 pre-loads bearing pair by lock screw ring 132. A water cover ring goes over dual direction copper ring 134 for oil exit and water supply to split copper bush 127 for water cooling of bearings with copper covering ring with groove 133 having water supplied directly from water reservoir 72 by impressed air pressure differential 46a and 46b from conical fan 45. The cover ring is pressed by spacing ring in bearing housing which is item 135 which in turn is pressed by cover plate 136 which is tightened by lock ring 139 in threaded rear internal section of bearing housing 122. On cover plate 139 a P.T.F.E. bush seal on inside of plate is bolted to plate by screws 138. The P.T.F.E. sealing bush is 137. The water from water reservoir 72 pushed in water reservoir by air pressure differential 46a o and 46b from conical fan 45 and enters split copper bush through water line 56a through cover ring 133 and water leaves system '.25 throtigh groove in housing 122 which is 124 and returns to water reservoir by line 56b.

Figure 5 shows the flange arrangement whereby the turbine shaft and rotors and turbine sheath with per" eral covers and corridors are positioned and alligned and held securely in position. The 21 hollow turbine shaft 70 is shown with turbine assembly held by flange position 14 at front and 40 at rear and this holds turbine rotor accurately in positions with flange plates being alligned by cover 140a at front of turbine and 140b at rear of turbine. A P.T.F.E. gasket between flange surfaces seal flange arrangement from high pressure cooling water that flows through hollow turbine shaft 70. Brass bolts through flange plates and allignment covers 140a and b and P.T.F.E. gaskets 142 and are tightened and can be lead soldered to fix turbine rotor. The other aspect of fixing the turbine is 5mm. stainless cover 12 which houses large stainless steel fan 11 to which turbine sheath and external covers of turbine assembly are weld attached. These stationary covers of the turbine are held by large fan cover 12 to accurately machined surfaces on supporting rib 20d of external support for turbine covers. Flange plates are about 6mm. stainless steel which can be diameter for No.1 size turbine,60mm. diameter plates for No.2 size diameter plates for No.3 size turbine, and diameter plates for No.4 size turbine.

Figure 6 is of the rear stationary sections of turbine covers with .30 34 being the rear tungsten sintered alloy which extends the length for forced flow convection of greater than 300m/s air cooling stream on outside of turbine sheath which supports copper coil for magnetic field which connects to end of turbine sheath by flange to thick ridge 143 of tungsten alloy(sintered) with counter-sunk :i "25 holes for high temperature alloy bolts with nut of bolt 144 being 144a and outside high temperature flow of exiting turbine gases that means that high energy idle which is the main reason for significant heat withdrawal by air stream of greater than 600m/s air flow in corridor between sheath with coil and and cylinder with 22 serations 38 that supports water cooling spiral from turbine shaft with ridge 143 and counter-sunk holes not obstructing turbine exiting gas flow. Similarly ridge 146 on outer part on Tungsten alloy sleeve with counter-sunk holes does not restrict or obstruct significantly the greater than 600m/s cooling air stream for turbine sheath with coil 145 and exiting turbine gases. Bolts 148 in ridge 146 bolt conical flaring end 35 for gas disapation and mixing through flange held by nut 1 4 8a. A external ridge 147 on end of cylindrical outer section 38 of high air speed cooling corridor for turbine with serations for enhanced convection transfer has counter-sunk holes for attaching conical disapator 36 for greater than 200m/s air flow in outer corridor for water spiral from hollow shaft 70 joined by flange with bolts 149 and nut 149a behind flange so as not to obstruct significantly the greater than 200m/s air flow from outer corridor.

Figure 7 is of the two stage gear reduction units and drive transmission form the turbine to drives outside the turbine cylindrical housing 65 with large fan 33 at front and its housing or enclosure 67. Items 150a and 151a are support shafts for rotating parts on parallel shaft 71a to turbine's shaft that hold the S external casings of these high speed components between rib 20d and 20e with end of shaft 71a being spun in water injection bush 53 of P.T.F.E. which is mounted on rib 20c. The first gear reduction unit 21 has a high speed bearing housing 152 bolted to stationary cover 24 for bearings 22 for central gear 26. The high speed bearing housings are the same as Figure 4 with air pressure impression lines 46a and 46b with water cooling 56a and 56b and oil lines 55a and The intermediate gears of which there are 3x sets are mounted through bearing housings 154 through bearings 23 which has water 23 and oil supply lines to these housings 55a,55b and 56a,56b with air impression differential 46a and 46b which forces oil to housing and back from housing. The water injection 'site 17 to hollow shaft is mounted on outside bearing housing cover 122 as in Figure 4 and is stationary with P.T.F.E. bush inside which injects water to high R.P.M. turbine shaft through holes in shaft that spin in P.T.F.E. bush with high pressure water 56c being loaded through from centripetal water pump 49. The intermediate gear sets 153b (x3) mesh with outer gear ring 153c which is part of rotating internal section of gear reduction unit. The hollow shaft that central high speed gear is on 26 or 153a ends in a bearing in rotating section of unit with a P.T.F.E. seal 156a with a small hole going into a split copper pad 155a supported by rings through which water from hollow shaft flows and is extracted through grooves in a plate bolted to rotating section of unit 25 with flange plate with shaft (solid) being 157 and groove for water collection being 158 with bolts 160 and the solid shaft on flange plate being 161. A stationary cover plate 162 is bolted to rib 20b with P.T.F.E. sealing ring 163 bolted to cover plate 162 by counter-sunk screw 164a with external P.T.F.E.

20 rings 165a for replacement of worn rings with cover plate being bolted by bolt 166a. Oil comes from centripetal oil pump and is injected to 6x mesh sites (x3 on central gear and 3x on outer ring) from 1 9 2a along line 55c from centripetal oil pump. A P.T.F.E.

bush in a cover plate 159a that is stationary and is bolted to cover plate bolt site 162 where seal 163 is with this bush 193a over shaft and over grooves in flange plate 157 and 158 for water collection and return along line 56b. A coupling 167 joins solid shaft 161 to hollow shaft for central gear 32 to second in-line gear reduction unit 27 with a P.T.F.E. mounted water bush 168 bolted to bearing 24 housing 169 of central gear 32 of second unit with bearing pair 28 only requiring impressed air pressure differential 4 6a and 46b to push oil out of bearing housing with oil inserted along line The intermediate gears (3x sets) are mounted to stationary cover which is bolted to rib 20a with bearings for intermediate gears 29 being housed in housing 170 being bolted to stationary cover for unit 30 with only oil supplied to housings along 55a and oil forced back from housings along 55b by impressed air pressure differential 46a and 46b through oil groove in housing as discussed for Figure 4.

The hollow shaft 171a for central gear 32 has water flowing through it from stationary water bush 168 from water line 56a with end of hollow shaft having a small hole for water to enter a split copper disc or pad 155b with support rings brazed or soldered in with holes that allow radial water flow with a P.T.F.E. seal 156b at end of hollow shaft with central hole with this end of shaft being mounted in bearing 194 that is mounted on rotating internal section 31 of gear reduction unit 194 (bearing) with intermediate gears being threaded to shaft 171b that goes into intermediate gear bearing housing 170 with intermediate gears meshing with external 10O ring gear 171c in internal rotating section 31 with a flange plate 172 being bolted to rotating section 31 with solid shaft on flange 172 being 175 with grooves in flange plate 173 for water collection with flange plate being bolted to 31 by bolts 180. A cover plate 176 is bolted to rib 20a and is stationary with P.T.F.E. seal 177 is bolted to cover plate 176 through counter-sunk screw head 164b with external extra P.T.F.E. rings 165b also being bolted for when one wears out with these extra P.T.F.E. seals 165b are bolted with counter-sunk screw head and bolt 166b through cover plate 176. The main drive gear 181 on shaft from flange plate 172 is threaded to 25 shaft and held between threaded collars 182. A equal size gear 183 to main drive gear 181 is mounted on shaft and drives shaft 184 at bottom of cylindrical housing 65 with drive gear 18.3 threaded on shaft 184 between threaded collars 185 with a housing for main drive gears 181 and 183 with oil feeding into cover along oil feed line with impressed air pressure differential supplied to cover 186 which is supported by rib 2 0a with P.T.F.E. seals around shafts to seal cover for drive gears making the cover fairly air tight for air impressed differential lines 46a and 46b which forces oil back to oil reservoir along line 55b when oil reaches oil fill level 187 at base of cover which side gear drags through. Oil input site to cover for drive gears 181 and 183 for line 55a is site 188 where oil then drains to base of cover. The drive shaft from the drive gear 183 runs through a series of bearing housings each of a pair of oppositely faced bearings in a housing like Figure 4 but without the water cooling around bearing but still with the oil supply and retrieval through impressed air pressure differential 46a and 46b acting on oil reservoir through 55a and grooves in housing 122 as 123 back along line 55b. The three bearing housings for drive shaft are 189a I.O for rib 20a and 189b for rib 20c and 189c for rib 20e all at base of cylindrical housing 65. All gears in drive system and reduction unit are module 2.5 and only a variation in gear width is needed for larger size turbines (Nos. 1 to Oil to second reduction unit 6x mesh sites 192b are from oil reservoir and not centripetal pump 25 as unit is much slower than first unit with 3x to central gear 32 and to outer ring gear on internal surface of rotating internal section 31. Oil from unit one reduction unit is forced out through holes in rotating internal section 25 through point 191a in stationary cover 24 by impressed air pressure differential with oil in 26 Second in-line reduction unit forced out through holes in internal rotating cover 31 through point 191b by impressed air pressure differential lines 4 6a and 46b to second gear reduction unit. The air fan at front of turbine 33 that runs off secdnd gear reduction unit is in.enclosure 67 which is nothing more than wire mesh of greater than 1.6mm. wire and mesh size of less than 10mm. square with fan screw threaded to shaft between threaded collars 190a and 190b. Water extraction from second gear reduction unit is through flange plate 172 with grooves and bolted to rotating internal section 31 with a stationary cover plate 159b with P.T.F.E. bush bolted to stationary cover plate 176 at bolt point 174 with water from hollow shaft flowing through split copper plate 155b with grooves 173 in flange plate 172 which then flows into stationary P.T.F.E. bush 193b supported by plate 159b and stationary cover plate 176 with water returning to water reservoir 72 by line 56b.

The drive gears 181 and 183 and cover 186 only obstruct about of frontal intake air from large fan 33 in all turbine sizes.

Figure 8a is of the flange mount for water and oil centripetal pumps and Air fan for air pressure differential as well as high 20 speed generator and starter motor. With Figure 8b and c being of .2 central rotor of centripetal oil and water pump with fabrication details. In Figure 8a a plate is cut in the form of a ring with a larger amount at two opposite sides of ring for holes for support of parallel bars 150a and 151a to go through to support flanges or ribs 195 with holes 196 in rib. The support bars 150a with 151a are bolted in parallel between 20d and 20e and support the external non-moving parts of air fan 4 5 ,centripetal water pump 49 and oil pump 50 as well as external casing of high speed generator and high speed starter motor 48. In Figure 8b the rotor of the centripetal 27 pump consists of a circular disc with off-angle slits 197 made in circular disc so with the insertion of at least 8x fins, the fins are angled off radial direction with direction of rotation to throw fluid against circumferential wall or radial.lly outwards with fins still perpendicular to plane of disc. The fins 198 are weld tacked at outside circumferential edge 199 and machined back to a circular surface. A central bush 200 is welded to centre of disc with a hole for location on a shaft. Figure 8c is the finished fin rotor with fins 198 weld tacked to cylindrical cover 201 at sites 202 on both sides of cylindrical cover. In Figure 9 the centripetal pump is shown which can be for water or oil with fin rotor welded on hollow shaft 71a and lugs through which support ring is held by parallel shafts 150a and 151a with support ring or rib 195a being for water pump 49 and support rib 195b being for oil pump 50 and support rib 195c being for air fan 45. About 4x holes in rib 196 support cover plate 206 and base plate 205 with P.T.F.E. seal 207 between them.

The fin disc is shown assembled in pump housing on shaft 71a with slits 197, fins 198 that slide into disc and weld tacks for fins in :o slits of disc as 199 (weld tacks). The central bush we/ded to disc is 200 and mounted on shaft with cylindrical cover over fins on disc at 201 with weld tacks of fins to cylindrical cover as 202.

The fin disc on shaft 7 1a is spun at high R.P.M. with fluid thrown outwards with disc in cylindrical cover 201 about central shaft and holes in cylindrical cover or disc that mounts fins so fluid can 25 run to either side of pump and not be impeded in exit from pump at 211 which is line 56c for water pump and 55c for oil pump with S. exiting fluid at a high pressure. The inlet to pump is line 55a for oil pump from oil reservoir with oil forced to pump by impressed air pressure differential 46a and 46b and similarly for water 28 along line 56a from water reservoir by impressed air pressure differential. A P.T.F.E. bush 203a is located by housing 2 10a of base plate 205 with another P.T.F.E. bush located in housing of cover plate 206. (bush 203b, housing 210b) Screw in covers to P.T.F.E.

bushes or fluid seals 203a in housing 210a is 204a and bush 203b in housing 210b is screw in cover 204b with lock nut 2 09a over 204a and lock nut 209b over 204b. Brass bolts 208 bolt base plate 205 to cover plate 206 with P.T.F.E. seal 207 through holes 196 and thus support stationary housing of centripetal pump. Welds 212 on bushes that support fin disc at 200 secure fin disc to shaft 7 1a at fin disc which turns at high R.P.M. inside stationary housing supported by shaft 150a and 151a. With P.T.F.E. bushes or fluid seals 203a and 203b the problem of wear can be overcome in a hard to get at aspect of being replaced over shaft by having split P.T.F.E. half bushes that go into housings 210a and 210b which are accurately matching half surfaces that still give adequate fluid and air seal.

The R.P.M. rating of the centripetal pump is about the same as the turbine rotor through near equal diameter pulleys of concave surface 15a and 4 3a with the water centripetal pump being all of 2 .0mm.

stainless steel with fins in No.1 turbine being 8mm. high by and cylindrical cover being 20mm. long and having a Internal diameter of 60mm. with fins of No.2 turbine being 10mm. high and wide with cylindrical cover being 2 5mm. long and having a internal diameter of 80mm.,No.3 turbine fin pump having fins 12mm. high and 32mm. wide with cylindrical cover being 32mm. long and having a internal diameter of 100mm.,No.4 turbine water fin pump having fins 16mm. high and 40mm. wide with cylindrical cover being 40mm. long and having a internal diameter of 150mm.. The oil centripetal pumps are all made of 1.6mm. stainless steel with fin pump of No.l turbine 29 having 5mm. high fins being 15mm. wide with cylindrical cover being wide and having a internal diameter of 50mm., fin pump of No.2 size turbine having 8mm. high fins that are 20mm. wide with cylindrical cover being 20mm. long and internal diameter of cylindrical cover being 60mm., oil fin pump of No.3 size turbine having high fins that are 25mm. wide with cylindrical cover being long and internal diameter of cylindrical cover being 8 0mm.,oil fin pump of No.4 size turbine having 12mm. high fins that are 30mm. wide with cylindrical cover being 30mm. long and internal diameter of cylindrical cover being 100mm.. In Figure 10 the air pressure differential lines 4 6a and 46b for conically reducing high speed fan 45 has conical cover 219 with flange 218 to this conical reducing section and front plate with holes 217 bolted to support rib on ring 195c with parallel support shafts 150a and 151a through lug and flange .218 and front plate 217 bolted through holes in rib 196.

There are about lOOx holes in front plate 217 for air intake. Welds to both ends of shaft of fan which is a tube with 5x sets of blade plates with at least 8x blades and plates being mounted between 9*9* collars with blade plates 215 welded to collars and collars 214 20 welded to tube shaft with tube shaft welded at each end 213 to hollow parallel shaft 71a. Air increases in speed as pressure drops towards narrow end of conical reducing fan and emerges at end 216 .9 with the air pressure differential 46a and 46b at different points along length with lower pressure point 46b being further down 25 conical reducing section and the high pressure point being further back towards larger diameter intake end. Brass bolts 220 are used to bolt fan's stationary sections together 217,218 and 219 through holes in rib 195c at 196 with double lock nuts or tightened nuts that have been lead soldered. The 4 x sizes of fans for the 4x 30 turbine sizes are as follows: No.1 turbine fan 45 all out of 1.6mm.

stainless...steel with the 100x holes in plate 217 being 1.6mm. diameter holes and internal diamensions of conical section being reducing to 30mm. with the length of conical section 219 being 80mm.. No.2 turbine fan 45 all out of 2 .00mm. stainless steel with the 100x holes in plate 217 being 2 .00mm. in diameter and internal diamensions of conical section being 90mm. reducing to 4 0mm. with the length of conical section being 100mm.. No.3 turbine fan 45 all out of 2 .5mm. stainless steel with the lOOx holes in plate 217 being 2 .5mm. diameter holes and internal diamensions of conical section being 110mm. reducing to 50mm. with length of conical section being 120mm.. No.4 turbine 45 all out of 3 .00mm. stainless steel with the 100x holes in plate 217 being 3 .00mm. diameter holes and internal diamensions of conical section being 140mm. reducing to 60mm. with the length of conical section being 150mm..

Figure 11 is of the high speed generator with Figure 12 of the high speed D.C. starter electric motor. A flange joint as in Figure 5 exists for generator at 221 and behind generator at 222 and for S motor at 2 2 3a and behind D.C. motor at 223b making generator and '20 motor distachable from hollow shafts 71a and 71b (respectively).

Figure lla is of a cylindrical tube as the inner part of stationary casing of generator with tube section 224 and two slots milled along length of tube all the way around tube circumference with a larger diameter slot only partially into tube wall and a central smaller diameter slot 226 through the tube wall so that a ledge is formed by the larger slot 225 that only is partially into tube wall so rectanguloid magnets can be inserted with magnet pole which is on large flat face of rectanguloid facing into generator casing or into generator's interior. These permanent magnets can be glued into 31 slots. The typical size for these magnets is 2 5mm. by llmm. by with the pole on the 25x 11mm. face. Figure lib is of the tube as part of the stationary casing for generator with the tube 224 with slots 225 and 226 shown with the rectanguloid magnets 227 mounted in slots within rings of 10mm. thickness 228 made of mild steel through which 3mm. diameter holes 229 run through the rings adjacent to'each other over tube 224 that houses rectanguloid magnets. Generator for No.l size turbine requires 13x rows of magnets with 6x per row with 25x 11mm. side facing inwards with No.2 turbine generator having 15 rows of 7x magnets with pole side facing inwards, No.3 turbine generator having 20 rows of 8x magnets with pole side facing inwards, No.4 turbine generator having 27 rows of magnets with pole side facing inwards. The rings 228 have 3mm.

holes for air cooling with 16x rings of 15mm. radial thickness with 10x cooling holes for No.1 turbine generator,No.2 turbine generator having 1 4 x rows of 3mm. holes and 18x 10mm. thick rings with radial thicknesses of 20mm.,No.3 turbine generator having 21x rings 10mm. thick with 2 4x rows of 3mm. holes with a radial thickness of 25mm.,No.4 turbine generator having 26x rings 10mm. thick 20 with 38x rows of 3mm. holes with a radial thickness of FFigure 11c is longtitudinal section of casing with 224 the tube with slots that holds magnets, 228 the 10mm. ring with 3mm. hole rows 229 for cooling air with rings 228 held by threaded ledges 2 32a and 232b with locking nuts at both ends in Aluminium casing 230 25 with tube for magnets 224 held by threaded ledges at both ends in rings at 2 3 1a and 231b with lock nuts to fasten. Figure lid is. of the hollow dynamo of generator with 10mm. thick rings 233 with 3mm.

holes for cooling air through rings 234 with a 5mm. thick Aluminium sleeve inside rings for magnetic shielding of- return loop of 18x 32 windings 236. Aluminium sleeve is 235. The length of the dynamo and diameter is in terms of the 10mm. thick rings. For No.1 turbine generator the diameter is .05m. and length-is .15m.,No.2 turbine generator the diameter is .064m. and length is 1 7m.,No.3 turbine generator the diameter is .09m. and length is .2m.,No.4 turbine generator the diameter is .12m. and length is .25m.. The radial thickness of 10mm. thick rings for No.1. turbine generator is .,No.2 turbine generator 20mm.,No.3 turbine generator is No.4 turbine generator is 30mm.. The copper wire diameter for windings in turbine generators is 2 .00mm.,2.5mm.,3.00mm., 4 .00mm., for Nos.1,2,3 The number of 3mm. cooling hole rows in rings 233 for turbine generators 1,2,3 4 are 4 0 x,70x,120x,190x respectively. Figure lie shows the dynamo assembled with 233 the rings,234 the 3mm. hole rows and 235 the 5mm. thick Aluminium sleeve. The 18x winding loops are 236 with dynamo held together by cover plate of stainless steel 237 on each end with slits 238 for windings to go through so cover plate sits on accurate machined surfaces with a stainless steel tube welded in each recess of the cover plate thus holding and sealing dynamo. All copper windings

S

are of bare wire with cotton thread or .3mm. P.T.F.E. round extro: uded strand wrapped around wire in a spiral of less than 3.00mm.

pitch with some high temperature epoxy resin glue applied in some 6S 6 cases. A allignment surface on cover plates 237 at 243 is adjacent to threaded section of left and right hand thread 239 so rotation 25 in one direction tighens attachments to cover plates 237 that supports dynamo. Weld on left side to tube 241 that holds dynamo together is done first at 24 2a so wire terminal from windings can go through holes in left cover plate at 240 after which the dynamo is securely assembled with final weld in tube through centre 33 for water passage at weld site 242b. Figure llf is of the turbine generator in a assembled form. Items 195dl and 195d2 are the flange plate attachment sites through parallel support shafts 150a and 151a at both ends of generator. The flange attachment sites 221 and 222 at both ends of generator allow attachment to hollow shaft 71a. The stationary outer 10mm. thick rings 228 are shown inside Aluminium casing 230 with 3mm. hole rows through rings 229. The 18x winding loops 236 of the dynamo are shown going through stainless steel covers 237 at each end of dynamo (grooves can exist for windings on outside of dynamo) with slits and internal Aluminium sleeve 235 is shown that supports rings 233 with 3mm. cooling hole rows 234. The rectanguloid magnets 227 inside tube 224 are shown. The allignment surface 243 on cover plate 237 is shown with attachment to cover bush and hollow shaft section 244 with threaded section of left bush 244 at 245 for blade plate 246 with 8x or more blades for blowing greater than 200m/s air flow down 3mm.

cooling hole rows with blade plate being attached to threaded surface 245 by lock nuts or rings 247 that can also be weld tacked. Threaded section of cover plates 237 have left and right hand S :20 thread so on rotation cover bush and shaft segments 244 tighten.

Item 248 is the P.T.F.E. bush assembly that holds brass commutator rings with contact bushes or in this case rollers being held by support section 249a and 249b for positive and negative terminals with support section held in housing on Aluminium casing of gener- 25 ator. Points 2 50a and 250b are joins in the hollow shaft segments 244 on the left and right side respectively. Bearing support plate 251 with support lug 195dl holds bearing on left side which is preferably a single groove angular ball bearing 252 which is the same for right hand side bearing. Air intake into generator is 34 through 253 in bearing support plate 251 or end cover for generator with gauze filter 254 over these 6mm. diameter holes 253 with end cover 251 bolted to aluminium casing 230 by bolts 255. Figure llg is of the end cover and bearing housing with 195d. the support lug and 256 and 257 being the different depth grooves in bearing recess for water circulation with the deeper groove 257 being for water return along line 56b with the shallower groove 256 being for water input from line 56a into split copper bush for water cooling with support ring being brazed and split copper bush 295 with holes in outer circumference to grooves 256 and 257. Grooves 258 and 259 are for oil input and recovery with the lower diameter groove 259 being for oil input along line 55a and the larger diameter groove being 258 working by impressed air pressure differential 46a and 46b as oil is flug out from centre. A internal cover plate holds bearing in recess and is bolted to cover plate 251 with oil seal for bearing 252 being with P.T.F.E. ring 260 held by backing ring (i.e.

steel) 261 and bolted to internal cover plate at bolt 262. Air intake 253 is 6mm. diameter holes with gauze 254 held between end plate 251 and Aluminium casing 230 by bolts 255. The left internal shaft joint 2 50a is with bush 2 65a welded at 263 with the internal threads of 266a and 266b (of right join on the other side of dynamo) being left and right hand threads so as to tighten join on S rotation. The internal P.T.F.E. bush of bush 265a makes a water tight seal when tightened for hollow shaft that allows water to flow through it. This P.T.F.E. bush is item 264. Figure l1h is of the cover bush and shaft threaded to cover plate 237. The cover bush 244 over cover plate 237 has holes for electricalterminal 268 and 269 to P.T.F.E. bush assembly for commutator rings 248 through water tight P.T.F.E. seal 270 that spaces and alligns holes between 35 237 and 244 as well as making water seal. This allignment and assembly is achieved by screw allignment of 237 and 244 with spacing seal 270 alligning holes for terminal 268 and 269 to commutator bush 248 with cover plate 237 welded to holding tube 241 at 242a first and when holes are alligned terminal wires 268 and 269 are pushed through with final assembly of dynamo being made by tube 241 at weld site 242b after this is achieved. The commutator bush 248 is held on shaft by threaded sections 271 and lock rings (threaded) 272. Threaded section of cover bush 244 holds blade plate 246 with lock rings 247. A threaded male bush 266al which screws into female threaded bush 265a is welded to shaft of 244 at 267.

Figure 11i is of the P.T.F.E. commutator bush 248 with the bulk of the bush 273 or base holding first brass ring 274 by wire hole in shaft 244 which locates bush 248 and then holes in brass ring 274 and base 273 locates first brass ring with wire and holes locating spacing P.T.F.E. intermediate bush 276 to first brass ring 274 with second thicked brass ring 275 located to P.T.F.E. bush 276 by wire segment and accurately alligned holes with P.T.F.E. bush on end of bush assembly 248 being also located or fixed in this manner by wire and holes 277. The electrical terminals 268 and 269 comes through base of P.T.F.E. bush 273 and are connected to brass rings 274 and 275 and are connected to terminals by counter sunk allen screws in brass rings with allen screw 275a connecting terminal to brass ring 275 and allen screw 274a connecting other terminal to brass ring 274. The wires and holes 277 do not make contact between the two brass rings and for turbines 1,2,3 4 wire segments for matching generators can be 1.6mm.,2.5mm.,3.00mm., and respectively. A threaded section 271 on cover bush and shaft segment 244 tightens commutator bush 248 segments by screw lock rings 36 272. The commutator brush or ring contact assembly and housing fixture is described in Figure 11j. Figure 11jl is the square section commutator roller assembly of square gection 249 with terminal lead through centre with cotton thread spiralled around or: P.T.F.E. strand of greater than .3mm. of less than 3mm. spiral pitch for insulation with the option of some high temperature epoxy resin on terminal lead with a lug 289 on end of square section commutator roller assembly 249. The end near lug 289 is machined round at 279 with thread for screw cap 278 that holds P.T.F.E.

ferrell 288 around terminal to allign electrical wire. The assembly is cut in 2x with a round insertion into other part 281 with a spring 280 to push bronze roller 287 against brass rings 274 and 275. The square section of 249 is alligned by 4x wire pieces in holes at corners of square section 282. The wire terminal 283 is soldered to brass bolt 284 with brass cover plates 285 which connect to stainless steel bolt 286 which holds commutator bronze contact roller 287. The square sections for commutator assemblies for No.1,2,3,4 turbine generators are 10mm.xl0mm.,12mm.xl2mm.,16mm.x 16mm.,20mm.x20mm. respectively. The terminal wire 283 for No.1,2 ,3,4 turbine generator commutator assemblies is 1.6mm.,2.5mm.,3.0 mm.,4.0mm. respectively. The smooth contact surface diameters of No.1,2,3,4 turbine generators is 3mm.,4mm.,5mm. and 6mm. respectively. The broze rollers for No.1,2,3,4 turbine generators are in diameter by 6mm. wide,12mm. in diameter by 8mm.wide, *25 16mm. in diameter by 10mm. wide, and 20mm. in diameter by 12mm.

wide respectively. The brass ring contact surface diameter of No.1 ,2,3,4 turbine generators is 30mm.,40mm.,50mm.,60mm. respectively making internal contact speed of stainless steel cylindrical surface 286 with bronze roller about lm/s at maximum speed which 37 is minimal wear. In Figure 11j2 the aluminium housing (square) 292 is bolted to casing 230 by bolts 293. A brass square cover 290 over 292 fixes 249 assembly to housing 292 and brass cover 290 by bolts 291. The internal diamensions of housing 292 for'turbine generator No.1,2,3,4 are 15mm.x15mm., 2 0mm.x20mm.,25mm.x25mm.,30mm.x30mm.

respectively. In Figure 11j3 292 is Aluminium housing bolted to casing 230 by bolts 293 with rounded corners from milling: 2 9 4ai internal,294b external, with 290 going over 294b. This makes fitting easier. Figure 12 is of 'the high speed starter motors that start the turbine. Two sizes are needed with about 3.5Kw. running off 24 volt D.C. or 2x car batteries which starts turbines No.1 and 2 with back E.M.F. exceeding input voltage at 10,600 R.P.M. with ignition only being on momentarily till turbine starts up and then current supply is turned off in the same way as a car engine and starter motor. The second size is about 5.0Kw. running off 48 volt D.C. or 4x car batteries with back E.M.F. exceeded at 7600 R.P.M.

for No. 3 4 turbines. Figure 12a is of a tube 296 with slots that .i houses the permanent magnet rectanguloids 2 5mm.xllmm.x5mm.) with large slots that do not go fully through tube wall 297 with smaller diameter slots central to this that go'fully through tube wall 298 with slots running the length of the tube. The dynamo for the 24V., motor is .12m. in diameter and .2m. long having about 1mm.

clearance from permanent magnet housing tube with 27 slots of 7x magnets. The dynamo for the 48V.,5.0Kw motor is .15m. in diameter and .25m. long having greater than 2mm. clearance from permanent magnet housing tube with 34 slots of 9x magnets. Figure 12b is of the outer aluminium casing 300 with magnet tube 296 held between threaded sections of casing 29 9 a and 299b with lock nuts at each ledge. Figure 12cl is of 4x fin Aluminium holder or support 38 302 for windings of dynamo over brass sleeve 301 which is part of the shaft assembly for motor. The attachment of 4x fin support 302 to brass sleeve shaft is made in the angled corners of the 4x fins of support by about 8x holes to brass sleeve (holes 303) for brass screws to brass sleeve 301. Position 304 is for P.T.F.E. electrically isolating bush with locating holes 305 for P.T.F.E. electrically isolating bush 304. Figure 12c2 is the screw (brass) 307 over and through brass sleeve 306 that go into holes 303 of 4x fin support 302 which fix 4x fin support to brass sleeve 301 with screws lead soldered to sleeve 306 and shaft sleeve 301. Figure 12c3 is a longtitudinal section of dynamo and shaft section of motor. Tubular stainless steel shaft 309 is welded to hollow stainless steel shaft 71b and goes through bearing housing 44b and 51b. Weld sites of 309 to 71b at 316. The brass sleeve 301 that runs through motor is attached to tubular shaft 309 by brass locking ring 317 on threaded section 318 of 309 with brass screws 319 through 317 locking ring S lead soldered to shaft sleeve 309. The 4x fin Aluminium support 302 holds P.T.F.E. bush 304 with brass connector ring 308 fixed to P.T.F.E. bush 304 by brass screws 310 lead soldered to brass conn- 20 ector ring 308 with brass screw fixed to P.T.F.E. bush in countersunk hole for nut 310b thus making ring 308 electrically isolated from 4x fin support 302. Brass screw 311 holds P.T.F.E. bush 304 to 4x fin Aluminium holder 302. Allen screw 312 fixes one of the 36x leads of 36x coils to brass connector ring 308. Lead 313 is fixed by screw 312. The single power lead for the 36x coils,item 314 is fixed to ring 308 by allen screw 315. This arrangement of P.T.F.E. bush and connector ring for 36x coils and other terminal power lead similarly at other end of 4x fin support 302. Figure 12c4 is a cross-section of 4x fin support and 1/4x Aluminium sleeve 39 supports 320 for the 36x coils with 9x coils for each 1/4x sleeve.

Windings of the 36x coils in the 24V. 3.5Kw. motor are .5mm. copper wire windings with ordinary polyester enamel insulation coating and for the 48V. 5Kw. motor are .6mm. diameter wire with enamel coating.

A brass strip holds each adjacent pair of 1/4 sleeves 320 in recess and brass strip 321 has at least 6x counter-sunk brass screws taped into 4x fin Aluminium support with each screw lead soldered to brass strip 321 with brass screws being 322. There are 30x windings in each of the 9x recesses if the 1/4x Aluminium sleeves with a recess of 8mm. wide and 1mm. deep for 24V. motor and 80x windings around sleeve for 48V. motor with recess 323 being 12mm. wide by 3mm. deep. The sleeve 320 is thick enough to shield top surface wires from opposite magnetic field affects from underside and is 8mm. thick in 24V. motor and 10mm. thick in 48V. motor. Lead 313 from each of the 36x coils is fastened to connector ring 308 by S allen screw 312. Main power input lead 314 is fastened to connector ring by allen screw 315. Brass screw 311 fastens P.T.F.E. bush 304 to 4x fin Aluminium support. Brass screws 310 attaches connector ring to P.T.F.E. bush 403 and is isolated electrically from rest of motor. Brass sleeve that forms part of shaft 301 is connected to stainless steel tubular shaft 309 which is connected to hollow stainless steel shaft 71b. The torque of 24 volt motor at 10,600 R.P.M. is about 2.1Nm. and the 48V. motor is 6.6Nm. at about 7,600 Figure 12d is of the motor assembly with 300 the Aluminium casing with 3 2 4a the 6mm. diameter holes for cooling air intake and 324b the 6mm. holes for cooling air output. Items 325a and 325b are the location holes in end plates for motor (Aluminium) for support shafts 150b and 151b between ribs 20d and 20e. The Aluminium end plates.are 326. The bearings 327 at each end and oppositely 40 faced are held in by cover plates 328. The commutator roller assembly 330 (steel) at each end for each terminal is held in Aluminium assembly housing in round hole. Commutator assembly housing is 329. A brass bush 331 is at each end of dynamo to hold commutator brass ring and fan or blade plate (stainless steel) 332 with brass bush held to brass sleeve 301. The leads from the 36x coils 313 on dynamo goes to brass connector ring 308. Power lead from brass bush 331 that holds brass commutator ring goes to brass connector ring 308. (Power lead 314). Figure 12e is the bearing housing end plate 326. The 6mm. air input holes 324a have a gauze filter over inside of hole at 334 with bolt 333 bolting end plate 326 to casing 300.

Flange holes 325a and 325b hold motor to shafts 150b and 151b. The brass shaft sleeve 301 is over stainless steel tubular shaft 309.

The bearing 327 is held in housing by cover plate 328 (Aluminium) with P.T,F.E. sealing ring 339 held by cover (steel) 340 and bolt 341. Radial grooves are around split copper hollow bush for water circulation around outside diameter edge of bearing with shallow groove 337 being for water out along line 56b (normal flow from water reservoir 72). The oil is forced in from line 55a from oil reservoir 54 through low diameter groove 335 and flung outwards

S

and recovered from larger diameter groove 336 along oil line with impressed air pressure differential 46a and 46b acting on oil in bearing. Bearing pre-load and fixing for generator is achieved by having steps in the shaft or in the case of the motor (D.C.

""25 starter) accurately positioned steps in the brass sleeve shaft 301.

Figure 12f is of brass bush 331 that supports commutator ring 360 and blade plate 332 (stainless steel) for forced air flow through motor with power lead 314 from brass connector ring 308 with power lead wire having cotton thread or P.T.F.E. strand (greater than 41 .3mm. in diameter) wound in a less than 3mm. pitch spiral around wire with some epoxy resin on this for electrical insulation. The brass bush 331 is fixed to brass sleeve shaft 301 by brass screws 359 (counter-sunk) that are lead soldered with P.T.F.E. split bush 363 bolted to brass bush 331 by brass bolts 362 and lead soldered.

The brass commutator rings 360 are fixed to split P.T.F.E. bush 363 by wire segments in alligned holes 361 in bush 363 and brass commutator ring 360. These wire segments are of 2.0mm. wire for 24V.

and 48V. motors. For both size motors the commutator rings are 60mm. outside diameter. The power lead 314 is soldered to commutator ring 360 at 364 and machined back for a accurate circular surface. Brass screw 358 fixes blade plate fan 332 to brass bush 331 and screw is lead soldered to brass bush 331. Brass sleeve shaft 301 is attached to stainless steel tube shaft 309 which in turn is welded to hollow stainless steel shaft through motor and bearing housing as item 71b (shaft). The hollow shaft 71b can have water running through it to cool shaft and bearing but at and 5.0Kw. this is not neccessary but the motor is mounted between o flange joints 223a and 223b so motor can be taken out of housing.

Figure 12g is of the commutator roller assembly 330 in commutator a roller assembly housing 329 (of Aluminium) which is attached to casing 300. The steel round section that is the commutator roller support is supported in a insulating (electrical) nylon tube 346 by flange on steel round section 345 by nylon nut 344 (glued if required) with wire lead through centre of steel round roller support with wire insulated by cotton thread spiralled around or greater than .3mm. P.T.F.E. strand spiralled around with wire lead sliding through P.T.F.E. bush 349 at top which has a brass nut 342 to hold P.T.F.E. bush 349 with lug on end'which connects to junct- 42 ion box on side of motor (lug343). The wire lead 350 or connector wire is soldered to brass screw 354 at base of round roller support with brass screw holding brass plates together (brass plates 355) which connects to stainless steel bolt 356 of 5mm. diameter that bronze roller 357 runs on at less than .6m/s contact speed (maximum). The connector wire 350 runs through a circular slide 351 with spring 352 that ensures contact of roller 357 with brass commutator ring 360 with steel round section at midpoint circular slide joint 351 being alligned by 4 x wire segments with holes 353 with 2 diameter wire segments. The nylon tube that fixes steel round commutator roller support is fixed in Aluminium housing 329 by Aluminium nut 348 and copper ferrell 347. The outside diameter of brass commutator rings for both motors is 60mm. (rings 360). The bronze rollers are 12mm. in diameter and 8mm. wide for both sizes of motors. Figure 13 is a cross-section of the dynamo of the 7000 volts D.C. motor. The 7000 volt D.C. motor is very similar to 24V.

and 48V. motors in that there is a peripheral tube with permanent magnets of the same size as the 24V. and 48V. motors with slots 9 with the dynamo .1m. diameter and .15m. long with 2 2x slots of magnets. The 1/4x sleeves 320 (Aluminium) have single windings of 2 500x windings in a groove 2mm. deep by 70mm. circumferential length of .17mm. diameter polyester enamel wire with .5mm. all around windings in groove in 1/4 sleeve 320 of epoxy resin that has a resistivity of greater than 10 9 ohm.m.. The rest is basically the '25 same with 1/4 sleeve 320 being:of 8mm. thick Aluminium with no stainless steel internal shafts as 309 and 71b only the brass sleeve shaft 301. Air is blown through motor to absorb its 3 00w about as in 24V. and 48V. motors with 7000V. reaching 60,000R.P.M.

if not retarded by air flow or motion with the motor having .045Nm.

43 torque at 60,000R.P.M.. A step on brass sleeve shaft means that bearings can be pre-loaded and shaft fixed. Water cooling and oil lubrication of bearings is done in the same way as 24V.,48V.

motors. As in figure,301 is the brass sleeve shaft with 312 the allen screw that fixes coil lead 313 to brass connector ring 308 with main power lead 314 fixed to brass connector 308 by allen screw 315. With brass screw 310 holding P.T.F.E. bush 304 (lead soldered and electrically isolated from 4x fin Aluminium support 302 for 1/4x sleeves 320) to brass connector 308. Brass screw 311 is taped in to 4x fin Aluminium sleeve (320) support and screw are glued to Aluminium threads in 4x fin support and holds P.T.F.E.

bush 304 to 4x fin Aluminium support 302. Recess in 1/4x Aluminium sleeves has a brass strip 321 with deep taped brass screws 322 lead soldered to brass strip 321. The 2 500x windings 323 are on each 1/4x sleeve. The commutator rings 360 are 50mm. in outside diameter. Bronze rollers 357 are 6mm. wide and 10mm. in diameter on S stainless steel bolt 356 of 3mm. diameter and a contact speed of about .6m/s between bronze roller and stainless steel bolt 356 is not exceeded. Holes 3 2 4a and 324b through motor of about diameter allow enough air to retard speed of motor so the full 60,000R.P.M. rotation speed is never reached and high voltage energy is completely consumed.

Figure 14 is of the 7,000 volt connectors and high voltage components and circuitry. Figure 14al is of a single line male 7,000V.

connection with exposed conductive surfaces not being active. The heavy wall flex 371 is held by plastic nut 365 and soft plastic ferrell 367. A tapered brass bush 369 is the connector with a copper wire 370 through 369 that is lead soldered and filed back with lead connection from 371 soldered to wire 370 at 372. The 44 external nut 366 of plastic housing screws into female socket by turning flex in counter direction to turn of thread 368 then tightening sockets. The single line female socket Figure 14a2 with 373 the plastic nut and 374 being the internal thread in plastic socket.

The internally tapered brass bush 375 that is the live internal connection is suspended on a spring 376 with wire from flex 379 being soldered to brass bush (wire from flex 380). A plastic nut 377 tigh(ens ferrel 378 around flex. Figure 14b1 is a double connection of two terminals to a single male plastic socket. Everything is the same as Figure 14al but there are two brass bushes 369a and 369b with two separate wires through each 370a and 370b and female socket going over thread 368. For positive and negative terminals wire from flex at 372a and 372b are separated by at least .5mm. and cavity wires are in is filled with epoxy resin. Figure 14b2 is the female socket with everything the same as Fig.14a2 with 375a and S* 375b the internally tapered brass bushes and wire from flex on larger bush 375a closer to opening being through plastic wall 380a.

Wire from flex of other terminal comes through centre 380b with nut tightening ferrell 378 around flex 379a. Figure 14c is of male inert connection to commutator assembly 329 being tightened on top of 329 with plastic socket pushing down on P.T.F.E. slide bush 349 with lug on end of wire through 349 (lug 343) with wire to wire 370 through externally tapered bush 369 and soldered join of wire to 370 being 372. The nut 366 (plastic) tightens male socket by '25 thread 368. Wire from lug to 370 is 382. The plastic top of socket 381 goes on top of 329 (commutator roller assembly) at 383. Figure 14d1 is of Alumina slug that gives the spark gap inside turbine and the housing of this Alumina slug or rod that carries the 7,000V. pilot arc and the 24V. power from high speed generator for 45 Turbine sizes 1 and 2 and 48V. power from high speed generator for turbines 3 and 4 size. The tungsten wire through Alumina slug 394 is 1.6mm. diameter and Ruthenium electroplated with ring in end 3 95a being anode for electrons from point cathode' 395b that point down turbine. A stainless steel screw socket 385 is on turbine sheath 384 in 300m/s corridor with windings around. A stainless steel tube 387 that goes into socket 385 with a stainless steel nut 388 on end of tube 387 with copper (soft metal) ferrell 389 that holds Alumina slug 394. A stainless steel tube 386 is around 387 in 200m/s corridor. The Alumina slug has the two 1.6mm. tungsten electrodes with the powder prior to sintering being infiltrated with Aluminium Nitrate and Sodium Silicate solution and sintered or fired to give glazed smooth surface finish of slug 394. A threaded section on top of nut 388 is for plastic 7,000V. connector. (threaded section on 388 is 390). A copper sleeve 392 is silver soldered onto tungsten electrodes outside turbine and to copper wire exiting S slug at 393 (copper exiting wire 393). For adequate resistance and 9 9 approximate spark gap for electron ejection 391 not to draw too much power the spark gap is 2mm. with Internal diameter of tung- 20 sten wire loop being 3mm. for No.l turbine with other sizes as follows:No.2 a 3mm. gap 4mm. I.D. loop,No.3 a 3.5mm. gap and I.D. loop,No.4 a 4mm. gap and 5mm. I.D. loop. Figure 14d2 is of double terminal 7,000V. connection to Alumina slug 394 and power connections also (24V. and 48V) from high speed generator. Item *"25 387 is stainless steel tube that holds Alumina slug 394 with stainless steel nut 388 that presses copper ferrell 389 with thread 390 on top of nut 388 for holding power and high voltage connections. The two connections on side are 7,000V. connections that join to main power connections (24V. and 48V.) with 370 being the 46 wire through tapered brass bushes 369 in 7,000V. connections. Item 372 is the lead connection to wire 370(toldered). The Thread 368 is for male socket connection of 7,000V. connectors. The sleeve 392 join tungsten electrodes to exit wire 393 for both terminals.

Brass rings 366a and 396b connect to adjacent brass bushes 397a and 397b respectively with exiting wires to soldered joints 396al and 396b1 from 393 and incoming flex power leads to 3 96a2 and 396b2 rings. Wires and alligned holes 400 locate rings 396 to brass bushes 397 with 3 99a and 399b being the two separating P.T.F.E.

bushes from brass bushes. Item 398 are the power leads 398a and 398b to 396a2 and 396b2 respectively. Power lead flex 402 is held by ferrell 401 which is tightened by plastic nut 403. Leads. 395a and 395b connect 7,000V. inputs from wires 370 at join 372 to two inputs with wire connection cavity to wires 393 filled with epoxy resin for electrical isolation of 7,000V. potential (cavity 455).

Figure 14e is of a 2x double junction 7,000V. connector with 4x single outputs with 374 the internal threads and 375 the internally tapered brass bush with 375a being outer large diameter bush and 375b being inner tapered bush and springs 376 with lead 380a through plastic wall and isolated electrically and 380b through o9 hollow centre with cavity 4 55a filled with epoxy resin and cavity 455b filled with epoxy resin to electrically isolate two leads. The :circuit diagram Figure 14fl is of transformer that is 24V. A.C. to 7,000V..A.C. at 40 Milliamps for turbine sizes 1 and 2 and 48V.

A.C. at 40 Milliamps for turbine sizes 3 and 4 being rectified by low power high voltage diodes in parallel 404 through the 3x spark gaps 406 (3x or more) in turbine with return line going through the 7,000V. motor 407 and 1500watt/7000V. capacitor bank (408). (Transformer is 405). Figure 14f2 is a junction diagram of male, female 47 connectors for 3x spark gap for turbine with 411 the positive terminal and 412 the negative terminal with a junction style connection at 410 of two live female connections and one inert male input connection. A simple connection join at 409 with inert male and live female connection. Item 410 is a junction. The junction at the spark gap 413 is by 2x separate female connectors.

Figure 15 is of the 1500W/7,000V. capacitor bank. The capacitor consist:s oE .6mmi. thick Alumi.nium platie pai.rs of 250mm. by 250mm.

separated by Barium Titanate paste mixed with epoxy resin spaced by strands of nylon fishing line running in parallel accross plate width which give a separation of plates of about .5mm. with a total of 48x plate pairs. Figure 15a is the capacitor bank housing with 4 15a and 415b being the two male connectors for 7,000V. input described in Figure 14al with spiral wire lead 416 to allow lid to be lifted. Bolts 456 bolt Polyester fibre-glass lid 419 (10mm. thick) to 10mm. thick polyester fibre-glass box 420 that houses capacitor bank 418 or plate assembly. Two Alumina bolts 417 run through S capacitor plate assembly for electrical connection. Figure 15b is of the plate sequencing with 422a and 422b being the two opposite charge Aluminium plates (.6mm. thick) separated by Barium Titanate Paste with epoxy resin 421 with strands of .5mm. nylon fishing line running parallel through plate gap for spacing. A 4mm. thick section of polyester fibre-glass is between each plate pair (423) and Sbolt 417 with the second plate 422b not connected to bolt by having 25 a gap around bolt 424 which is filled with epoxy resin. Plates are laid flat and put over each other while lying flat up so as to fill gap 424 with epoxy resin in every second plate. Figure 15c details connection (electrical) through plate assembly with the two adjacent bolt 4 17a in Figure 15ci and bolt 417b in Figure 15c2. In 48 Figure 15cl Aluminium bolt 417a connects to alulinium plate 4 2 2a with Barium Titanate 421 between plates 4 2 2a and 422b with the gap 424 around second plate 422b which is filled with epoxy resin followed by 4mm. of Polyester fibre-glass with a '.2mm. step in Aluminium shaft or bolt 425,for each plate pair with 4mm. polyester spacing plate 423. This sequence repeats for each plate pair with .2mm. step for contact (electrical) at each .2mm. diameter reduction 425 in bolt 4 17a and in Figure 1.5c2 the bolt 417b is isolated from first plate 4 22a by nylon bush 426 and gap around shaft 424 electrically isolates first plate. This dual system allows for connection of the two terminal bolts 4 17a and 417b with Figure 15c2 shows connection of last plate isolated from bolt 4 1 7 a by nylon bush 426 in the sequence of plate pairs for each connection bolt.

The boring of accurate holes in plates 422 is achieved by a simple boring bar in vertical milling machine as shown in Figure 15d for steps for connection interfaces to bolts 417 with 427 being the S Morse taper that goes into milling machine turrent and round allignment slides 4 28a and 428b fixed in enlarged end with boring tool 430 on slides 4 2 8a and b moved by screw feed adjustment 429. The boring tool assembly is spun in milling machine turrent to bore holes in capacitor plates 422 of increments in diameter of about .4mm.. Figure 16 is of the baffles for slowing exhaust and cooling air streams from the turbine to less than 2 0m/s. In Figure 16a 2x baffles of two sides are at each side of the turbine housing 65. A conical reducing duct 66 inside cylindrical housing 65 directs exiting gas into exit duct 431 from which two rectangular passages 433 on either side of 431 direct gas to baffles on either side of turbine housing 65. Flange connection 432 is next to exit duct 431 and joins rectangular passage to exit duct 431 and flange 434 conn- 49 ects rectangular passage to baffle. The baffle 435 is rectangular with 3x plates 436 of a increasing number of 1 2 7 mm. holes on either side of the central input column of-baffle with a gauze on each side over last plate with 1 2 7 mm. diameter holes. (gauze 437) (central input column 440) Baffle for No.1 turbine is 3 5m. by 4 5m. and .12m. thick with 250 holes followed by 500x holes followed by 500x holes followed by 1,000 holes in the 3x consecutive plates on either side of central column 440 in baffle. No.2 size turbine: .5m. x .65m.. x 1 5m. thick with 3x plates having 500x then 1000x then 2 0 00x holes consecutively. No.3. size turbine: 7 m.x.9m.x.2m. thick with 3x plates having 9 4 0x then 1 8 88x then 3 7 50x holes consecutively. No.4 size turbine: 8 thick with 3x plates having 1500x then 3 0 00x then 6 000x holes consecutively. In Figure 16b the plates 436 are attached to top of baffle by bolts 4 38a by channel that spaces plates and bolts 438b attach plates 436 to sides of channel and hold gauze 437 on front. The channel 439 is on either side of central input passage 440. The baffle 435 is supported by flange to rectangular passage 433 (flange 434). The channel spaces plates 436 for No.l turbine spacing is 15mm. for No.2 turbine 2 0mm.,No.3 turbine 2 5mm.,No.4 turbine 35mm.. Figure 17 describes the blades of the turbine with Figure 17a being of the rear blades which are discs with slits for blades. The magnetic field is crucial to turbines operation with electrons from spark gap ejected down turbine and peripheral magnetic fields of 4 tesla or greater being produced and combusted gas being forced through slits at pressures in excess of 10 Pa. in rear of turbine with clock-wise current flow in windings, seen from front of turbine, field is towards back which means that inwards motion of electrons causes electrons to go 50 in anti-clockwise direction and torque is assisted anti-clockwise and with a radially in field component anti-clockwise electron motion or clockwise current means magnetic -field exerts a massive pressure on peripheral gases through circumferentially perpheral slits in rear of turbine. For anti-clockwise current flow in windings seen from front of turbine the reverse is true, electrons circulate in clockwise direction assisting clockwise rotation and a radi.al.l.y out field on clockwise electrons or aniti.-c.lockwi.se current forces circumferentially peripheral gas down turbine with high pressure. For anti-clockwise rotation blades or slits at top of blade plate or disc, the blades or slits angle to right and for clock-wise rotation top of blade plate or disc the blades or slits angle to left, looking from front of turbine. For No..1 size turbine rear blade discs are 8mm. thich with 24x slits to a diameter on disc of 25mm. with slits .3mm. wide. No.2 turbine rear discs are thick with 32x slits to a circumference of of 30mm. with slits being .5mm. wide. For No.3 size turbine rear blade discs are 12mm. thick with 40x slits to a circumference of 37mm. with slits being .6mm. wide. For No.4 size turbine rear blade discs are 16mm.

thick with 48x slits to a circumference of 45mm. with slits being .8mm. wide. For anti-clockwise rotation of slits looking at top of disc and front of turbine slits angle to right and are cut about radially at about 450 to turbine shaft with base face of slit being about 450 and right face looking at of disc from front angles about about 460 to turbine shaft with slit angular divergence being less than 1 For tungsten alloy rear discs and up to 2,500 K near stoiciometric combustion tungsten alloy powder is pressed on High o temperature alloy bush and for No.1 turbine 0.D. of bush is 16mm.

and I.D. is 13mm. being for a 13mm. O.D.,10mm. I.D. shaft with 4x 51 protrusions from bush to hold sinter powder alloy. No.2 turbine O.D. of bush is 20mm. and I.D. is 16mm. for a 16mm. O.D. and I.D. shaft with 4x protrusions to grab sinter alloy. No.3 turbine O.D. of bush is 2 4 mm. and I.D. is 2 0mm. O.D. and 10mm. I.D. shaft with 4x protrusions to grab sinter alloy. No.4 turbine O.D. of bush is 30mm. and I.D. is 25mm. for a 25mm. O.D. and 10mm. I.D.

shaft with 4 x protrusions to grab sinter alloy at 454. For less than 1,1000C combustion exiting gas is about 1.5x faster and rear discs are just made of high temperature alloy being the same size as tungsten high temperature discs with slits and slit widths being the same. Combustion speeds are higher and this requires more propellant gas (ethylene) and a greater proportion of surfactant in surfactant/fuel mix which is sucked in to fuel loading pump 59 from surfactant/fuel tank. More grooves can be introduced on the misting surface blades in terms of more grooves per millimeter thus with this and more surfactant and propellant gas combustion speed can go to 300m/s.. Figure 17a is of rear disc with slits with bush of high temperature alloy being 441 and contact surface of slit 442 for anti-clockwise rotation seen from front of turbine (anti-clockwise rotation 445) with this electron membrane affect of in excess of 20 0 ,000m/s on total electrons from spark gap whether as a ion pair with a matching positive ion close in hot gas or as charge excess electrons. The top slit surface 443 is less than 10 divergent from bottom contact surface 442. The disc with slits from bush outwards is of tungsten high temperature sintered alloy 444. Figure 17a2 is of high temperature alloy Bush 441 with at least 4x protrusions 454 prior to pressing and sintering of Tungsten alloy powder. In Figure 17b the blade plates of the front and misting surface blade plates 446 are welded between bushes 460 52 and welded or weld tacked at 447b on blade plate and 44 7a on shaft with rear blade discs with slits only welded at 44 7 a at high temperature bush 441. In Figure 17c the front blade that turns anti-clockwise looking from front, top of blade plate has blades angling to right 449 with crease on bottom right underside 450 to build a pressure zone under blade and limit speed of turbine. Anticlockwise rotation is 448 and for clockwise rotation seen from front at top blades angle to left with crease on l.eft underside.

The stainless steel bush that holds blade plate 446 by welding at 447b by weld tack or continuous weld to bush 460 is shown. Eight or more blades are on each blade plate of front blade plates and misting blade plates. Figure 17d is of misting blade plate 446 with blade angling to right 449 for anti-clockwise rotation seen from front looking at top of blade plate. The grooves are more than 16x per millimeter (grooves 452) for less than 50 micron droplet size.

The serations 453 are at the top and bottom surface edge of the blades and help droplet formation. The hole in the centre of the blade plate 451. Misting blade plate grooves are machined on a flat disc in lathe then blades are cut in plate and the profile pressed .20 in plate. Overall slit number and width is final but fewer slits and wider slit combinations can be used. This is however at the Sexpense of torque which is the main advantage of this invention.

o e..

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Claims (32)

1. The fuel combustion turbine system having primarily a Hyperbol- ic tapering Sheath which tapers from a large curved end to a narrow about parallel end by five or more cones welded together with a Stainless Steel plate (about 3mm. thick) welded t- the to the front of the turbine with numerous small holes near large front blades of Turbine that speeds-up air intake flow into turbine so that plate with holes limits the air intake so that combustion is almost stoiciometric and reaching up to 2,5000K or with more holes combust- ion is limited to less than 1,100oC, with rear discs with slightly divergent slits that angle back at about 450 to lonatitudinal direc- tion of flow with top non-contact surface angling less to longtit- udinal direction of flow by about 10 and for 2,5000K stoiciometric combustion combusting gases flow through sintered Tungsten alloy J5 discs with slits and for less than 1,100oC combusting gases flow through Inconel 600 (or high temperature alloy) discs with slits which are welded to hollow shaft with Disc's outer tip speeds at up to 150m./s. with liquid fuels injected through less than .3mm. holes with fuel mixed with surfactant and loaded with dissolved propellant gases as Ethylene or Acetylene which gives droplet dis- persion of less than 50 m. (microns) in diameter projected at up to 100m./s. for combustion speeds over 150m./s. and injection pressure over 2x MPa. with the assistance of misting surface blades with spiral grooves of greater than 4x grooves per millimeter as fuel strikes misting grooves and is flung off as droplets at less than 50pm. in diameter so that the front blades speed-up the low density air stream that carry droplets to spark gap of a point iode pointing electrons through a anode ring by a (up to) 7,000 0 J 54 volt primary voltage with a high power secondary at up to 48 volts and high current with electrons in hot combusted gas in high stren- gth magnetic field circulating around shaft at up to 200,000m./s. as gas is contracting inwards as gas and electrons move down taper- ing hyperbolic sheath with electrons at up to 200,000m./s. contrib- uting to torque of rotating turbine shaft with hot combusted gases acting as a electron membrane for torque assistance so that high energy idle has energy extracted through sheath by cooling air flowing down corridor over magnetic coil over turbine sheath and about half of the thermal energy extracted through hollow shaft by flowing water with turbine shaft transmitting energy to a second S water cooled parallel shaft by flat plastic or rubber belting bet- ween concave pulleys that drive a high speed generator for spark gap and magnetic coil, water centripetal pump for water cooling main turbine shaft and oil centripetal pump that supplies oil to the first in line gear reduction unit from Turbine and a reducing conical fan that gives a air pressure differential that supplies lubricating oil from oil reservoir to second in line gear reduction unit which connects by gears to main drive shaft of turbine which 0 is about one-tenth of the rotation speed of turbine as well as lub- ricating bearing housing in turbine system and lubricating reduct- ion gear box on fuel pump with air pressure differential also supp- lying cooling water from water reservoir for cooling parallel shaft generator, centripetal pumps and conical fan are on as well as cooling water for bearing housings in turbine system with a second parallel shaft being transmission driven by main turbine shaft by flat plastic or rubber belting between concave pulleys that drive starter D.C. electric motor (principally 24V. or 48V.) that spins Sr e to over 7,000R.P.M. and starts turbine with Turbinetwo InturZI4ur e to over 7, OOOR. P.M. and starts turbine with Turbine, two .55 in-line gear reduction units, two parallel shafts and main drive shaft all housed in cylindrical container with top cover able to open about mid-line along length of cylindrical housing.

2. The fuel combustion turbine system as claimed in claim 1 with the turbine system having a corridor for cooling air to move Over external magnetic coil of copper strip that has been exchange coated with Silver and heated and spaced by up to .5mm. grit or greater with cooling air extracting heat from high energy Turbine idle and operation by Turbulent forced flow convection at air speeds over 300 meters/second with the corridor being formed by a cone and cylinder with serations on the internal surface of cylinder aiding in turbulent forced flow convection and air introduced by stainless steel fan in 5mm. thick casing with holes S at front with down to 400# stainless steel mesh (spacings per inch) gauze over fan casing with second corridor of cone and cylinder with up to 200m./s. air flow with up to and over 40 meters of flattened copper tube for cooling hollow shaft of turbine with various size holes in 3mm. front of turbine governing flow speed Sgo: down corridor with extra surface area for turbulent forced flow convection by a Tungsten sleeve on the end of a turbine adding 33% to 42% to length of Turbine sheath so over 50% of thermal energy from combustion limit in Turbine can be extracted through turbine sheath and coil and Tungsten sleeve.

3. The fuel combustion turbine system as claimed in claim 1 and claim 2 having a large fan at front of cylindrical housing of turbine for supply of large volume of air to cool air from inner corridor mixing with exhaust gas by flared ends of turbine and c M34ing with air for cooling water from shaft in spiral in outer corri or that mixes with air from fan at front of cylindrical 56 housing with flared ends and copper filled cone over shaft that deflects exhaust gas from turbine with flared ends on end of sheath with tungsten sleeve and cone and cylinders that form corridors with final cooled air and exhaust being slowed through a baffle on either side of cylindrical housing of turbine withthe actual turbine and (up to) 3mm. thick front plate and turbine fan and (up to) 5mm. thick stainless casing for Turbulent forced flow convec- tion and corridors being between flanges so that turbine assembly can be removed from cylindrical housing for turbine.

4. The fuel combustion turbine system as claimed in claim 1 and claim 3 with the cylindrical housing that houses and alligns turbine with covers such as corridors of cone and cylinder which convey high speed cooling air for sheath and water from hollow shaft with (up to) 5mm. thick stainless steel casing for stainless steel fan in front of turbine being supported by a set of up to five or more circular ribs spaced by bars or rods which give turb- ine face orthogonality to length of cylinder and alligns turbinE in length of cylindrical housing with parallel ribs strengthening and alligning turbine to gear reduction units in line with turbine as .20 well as supporting rigidly parallel shafts for generator, centrip- etal pumps, conical fan and non-water cooled shaft for starter motors (24V. or 48V.) with main drive shaft support by up to five or more ribs which are rigidly attached by spacing rods or bars which give accurate orthogonal and parallel surfaces.

5. The fuel combustion turbine system as claimed in claim 1 with the first gear reduction unit being in-line with turbine and accurately alligned by cylindrical housing's rib sections with each with 57 three or more intermediate peripheral gears outside of which a internal spur gear ring rotates and this conveys torque by accur- ate allignment through a bearing on end of shaft for central spur gear with sliding seal surface being P.T.F.E. (Poly-Tetra-Fluoro- Ethylene) bushes and ring with a water cooled plate next to bearing and oil sprayed onto gear mesh sites from centripetal oil pump and oil retrieved to reservoir by air pressure differential from conical fan on parallel shaft driven by turbine with each separate bearing housing for central gear and intermediate bearing housings being supplied oil and cooling water from oil and water reservoirs by a air pressure differential from conical fan which also gives retrieval.

6. The fuel combustion turbine system as claimed in claim 1 with the second gear reduction unit is also in-line with first gear reduction unit and turbine and accurately alligned by cylindrical *.housing rib section and unit drops rotation rate by a further factor of about three times with central spur gear with bearing housing of two bearings at one end and a single bearing in the rotating plate of the outer gear ring which is around intermediate 0 peripheral spur gears to the central gears with exit torque from rotating plate with internal spur gear ring driving a gear which drives air supply fan at front of cylindrical housing of turbine as well as a gear which drives gear on main drive shaft on side but inside part of cylindrical housing with sliding seal surfaces being P.T.F.E. bushes and rings with a water cooled plate next to bearing of central gear and oil sprayed onto gear mesh sites from oil res- ervoir and oil and water to bearing housings of central gear and i7termediate gears supplied by oil and water reservoir pushed by ail ressure differential from conical fan and retrieved back to 58 oil and water reservoirs by air pressure differential from conical fan.

7. The fuel combustion turbine system as claimed in claim 1 with a centripetal water pump for the high pressure, high speed water flow through central turbine and shaft and 40 meter flattened copper tube spiral for cooling in outer air cooled corridor which is principally a metal disc (stainless steel) with near radial slits near circumference such that fins are inserted into near radial slits and weld tacked with a slight angle outwards and a cylindrical ring over this is welded with holes in disc so fluid can flow either side of disc with this being the principle rotating component of pump which is housed in a cover and cover plate with oO.. P.T.F.E. bushes or dual half bushes forming seal that hollow para- llel shaft to turbine rotates in at high speed giving a high press- ure, high speed water flow.

S8. The fuel combustion turbine system as claimed in claim 1 with a centripetal oil pump for high speed oil flow to high speed spur o4 •o gear sites of first gear reduction unit which is a metal disc oeoo (stainless steel) with near radial slits near circumference such that fins are inserted into near radial slits and weld tacked with a slight angle outwards and a cylindrical ring over this is welded with holes in disc so fluid can flow either side of disc with this being the principle rotating component of pump which is housed in a cover and cover plate with P.T.F.E. bushes or dual half bushes forming seal that hollow parallel shaft to turbine rotates in at high speed giving high speed large volume rate flow of oil.

9. The fuel combustion turbine system as claimed in claim 1 with -a conical air fan running off turbine shaft on parallel water j/ c(oed shaft with conical sheath and cover plate with holes for 59 limited air intake supported by parallel support rods parallel to shaft and plate of blades have blades pressed in and each blade plate welded between two bushes to a stainless steel tube and this tube with t'-e welded five blade plates welded to water cooled para- ilel shaft with rotors or blades spinning at high speed for a pressure differential to develop between two points down sheath with the higher pressure at the larger diameter so that return air is at lower diameter section of sheath being at lower pressure as this is the lower pressure for supplying the air pressure differ- ential that forces oil and water to cooling and lubricating sect- ions as bearing housings and gear mesh sites and the parallel shaft conical fan is on. 0%

10. The fuel combustion turbine system as claimed in claim 1 with a high speed generator on water cooled parallel shaft with rows of rectanguloid magnets with magnetic pole on large face and facing **inwards so that magnets are mounted in slots with a step such that magnets are glued in with about 10mm. thick steel rings with o*o.°o numerous holes along length for air cooling in Aluminium outer casing so that rotor or dynamo with about eight-teen longtitudinal loops generate high currents at voltages from 24V. to 48 volts with loop over (about) 10mm. thick rings over Aluminium sleeve for shielding from opposite direction return length of loop with stainless steel ends welded to stainless steel tube and electric wire wound in thread (cotton or through ends to commutator rings with bronze rollers on small diameter stainless steel shaft for commutator contact and square section mounted to outer Aluminium casing by Aluminium cover with a spring in i{"Tutator square section alligned by holes and wires in corners of i squar. section with a fan or pressed plates of blades on commutator 60 ring assembly for moving air through holes in (about) 10mm. thick steel rings for cooling with angular groove ball bearing opposite- ly faced at each end with oil and water supply from reservoirs with air pressure differential for retrieval in end plates or each end of outer Aluminium casing and flanges with allignment covers at each end of generator so generator assembly can be taken out from water cooled parallel shaft.

11. The fuel combustion turbine system as claimed in claim 1 for each bearing housing typically for high rotation rate shaft support which comprises two opposed angular grooved ball bearings in a hollow copper cover with brazed or silver soldered support ring with holes for the passage of cooling water with a hollow shaft that cools bearing with water and oil introduced into bearing housing and copper cooling cover through a ring with orthogonal holes for oil retrieval through side or grooves in side of bearing "housing and holes along length of ring for water input to copper cooling cover with water retrieval through grooves in side of bear- ing housing from cooling copper cover with P.T.F.E. rings sealing bearing housing and air pressure differential used for particularly oil retrieval.

12. The fuel combustion turbine system as claimed in claim 1 with a air tight container for water storage that sustains a applied air pressure differential from conical fan so that pressure applied by air circulation through container forces out water to parallel shaft for generator, conical fan and centripetal pumps and cooling water for bearing housings with retrieval being by applied pressure.

'13. \The fuel combustion turbine system as claimed in claim 1 with a air\tight container for oil storage that sustains a applied air 61 pressure differential from conical fan so that pressure applied by air circulation through container forces out oil to second in-line gear reduction unit at gear mesh sites and separate bearing hous- ings and gear box for fuel pump and bearings on generator and D.C. starter motor and high voltage motor with retrieval by air pressure differential in cavity where oil is released by second in-line gear reduction unit, fuel pump gear box, bearing housings and bearings of generator, D.C. starter motor and high voltage motor.

14. The fuel combustion turbine system as claimed in claim 1 with a high speed D.C. starter motor essentially 24V. or 48V.) running off main turbine shaft by transmission belting being rubber or flat S plastic between concave pulleys to second parallel shaft on other side of cylindrical housing to water cooled shaft with rows of rec- tanguloid permanent magnets with magnetic pole on large face and facing inwards so that magnets are mounted in slots with a step SSSS** S such that magnets are glued in with dynamo comprising a four-fin support mounted on a brass sleeve and brass screws soldered with S S each perpendicular fin supporting a one-quarter sleeve with up to nine or more grooves for windings with each segment or quarter sleeve screwed onto four fin support with brass strip (soldered) in slots that form from quarter sleeves forming circle so that the thirty-six parallel windings (or numbered windings) connect to electrically isolated brass ring at each end of four fin support and this going to commutator ring at each end for power connection to round section that holds a bronze roller that spins on a small diameter stainless steel shaft that supports roller for power supply through round section, spring supported by four holes with ?,Are and round section held in a compression fitting for power sup- 4p. ply hat attains over 7,000 R.P.M. on motor dynamo with fan for air LU 0 62 cooling and oil and water supply to bearings with air pressure differential for oil retrieval.

The fuel combustion turbine system as claimed in claim 1 with a high voltage supply of about 7,000 volts to stabilize the high power arc in the turbine at about three spark points generated by a 24 volt or 48 volt A.C. supply through a transformer to 7,000 volts which is full wave rectified high voltage diodes in parallel that form a rectifying bridge and then pass to three spark points in turbine with almost all this energy consumed in a high voltage motor that consumes energy by blowing air through motor with any run-off stored in a 7,000 volt capacitor thus making the 7,000 volt isolated and safe.

16. The fuel combustion turbine system as claimed in claim 1 and claim 15 having a capacitor consisting of Aluminium plate pairs spaced by nylon line to about .6mm. with Barium Titanate paste and epoxy resin with two Aluminium connectors as terminals with each connector to each alternate plate by steps on Aluminium connector oo with a gap filled with epoxy resin around each alternate plate so that the assembly of plate pairs is spaced by polyester spacer and this assembly is housed in a polyester fibre glass container with lid and connectors through lid.

17. The fuel combustion turbine system as claimed in claim 1 and claim 15 having a high voltage motor that can spin up to 60,000 R.P.M. and blow air as means of consuming high voltage energy and is essentially the same as D.C. starter motor with rectanguloid permanent magnets in grooves with steps and glued with large pole face facing inwards to Aluminium four fin support for Aluminium k rter sleeves that hold around 2,500 windings each encased in at lea .5mm. of epoxy resin with connections to isolated brass ring of epoxy resin with connections to isolated brass ring 63 at each end which connects to commutator rings at each end with a plate of blades blowing air through motor to consume energy and a end plate for bearings at each end of casing with differential air pressure supplying water and oil to bearings at each end with oil retrieval by air pressure differential to each end plate.

18. The fuel combustion turbine system as claimed in claim 1 with the fuel supply system comprising a four level fin disc pump fuel intake, surfactant, propellant loading and fuel and surfactant high pressure loading with surfactant stored in separate tank with fuel at high concentration and propellant ethylene or acetylene in a high pressure bottle released through a solenoid to the four level fin-disc pump which is driven by a about a .18 Kw. 12 volt D.C. S motor at about 3,000 R.P.M. geared down about six times through a gear box that drives four level fin disc pump that fills a cylin- drical cavity with a motion/position switch that switches fuel pump o0o0o* off when a certain level is reached in cylindrical storage cavity ooo so that fuel loaded to over 2 Mpa. is reached through a variable o S: position solenoid to jets in turbine which are a multiplicity of oooo S. holes of less than .3mm. diameter at speeds of up to 100m./s. with droplets being less than 50pm. in diameter to be easily blown down turbine.

19. The fuel combustion turbine system as claimed in claim 1 and claim 18 with the four level fin disc pump driven through about a six times reduction gear box from about .18Kw., about 3,000 R.P.M., about 12 volt D.C. motor with the gear box being a input drive through double opposed bearings through step down spur gear through a second set of step down spur gears on the same shaft with bearings at either end and drive out from a double opposed pair of bea pgs on other side of gear box through to synchronizing gears 64 of four level fin pump through four levels of disc-fins threaded on a pair of reducing shafts so that discs tighten on rotation of shaft with level one of fins on disc being large fins for fuel intake and level four of small fins being surfactant-fuel intake being pressure loaded at level three of small fins and propellant gas loaded as fuel and fuel-surfactant is loaded for injection into storage cylinder as loaded fuel from level two of large fins on disc.

The fuel combustion turbine system as claimed in claim 1 and claim 18 with the surfactant-fuel mix stored in a container near cylindrical housing and this mixture of concentrated surfactant mix :00 drawn in at level four being small fins in the four level fin-disc pump by rotation of level four fin-disc from surfactant-fuel tank.

21. The fuel combustion turbine system as. claimed in claim 1 and claim 18 with the compressed propellant gas bottle releasing pro- 555555 ooo o pellant gas through a solenoid valve at various dosage amounts of propellant for different fuels when motor is on and activating the solenoid valve to release propellant gas to four level fin-disc oooS s pump and supply is off when motor for four level fin disc pump is off by solenoid valve switching off and is only on when pump motor is on.

22. The fuel combustion turbine system as claimed in claim 1 and claim 18 with the cylindrical storage cavity for loaded fuel press- urized by a tapered spring that gives almost constant force in small travels of about 50mm. in cylindrical storage cavity with spring loaded position switch which switches motor to four level fin-disc pump off when cylindrical storage cavity is full and rel- 2 RAtj Sea; through variable position solenoid valve.

S23. e fuel combustion turbine system as claimed in claim 1 and ~nVT 65 claim 18 with variable position needle-Solenoid valve comprising a needle valve for fine control over fuel release by position of nee- dle through narrow exit with opening opened by variable power to solenoid through electric resistor which gives variable strength to magnetic coil which acts on hollow shaft that acts on permanent magnets in the hollow shaft of the needle valve against a spring to open valve or allow it to close when coil is off.

24. The fuel combustion turbine system as claimed in claim 1 with two rectanguloid exhaust baffles to slow exhaust and cooling gas down through a series of three plates with increasing number of 0:0. holes with three plate series being on either side of a central 600: 0 passage and all plates and gauze covers attached to channel for i

25. The fuel combustion turbine system as claimed in claim 1 and claim 15 with special high voltage connectors required for the spacing and000 volt sysupportem with gauze one outside and relectrically dead metal tersupplyinlsg coolingsed ar nd female connectorust gas asto central passage of eachlive metal terminals withdrawn in connector with all connectors being plastic and male connectors have lead with insulation tightened by ferrell in comp- ression socket and conical brass ring being metal terminal connec- 15ted by wire through ringside of cylindrical housing of turbine.al having lead fixed by ferrell in compression socket with conical brass ring on spring inside connector cavity with wire through ring for connec- tion to lead with male and female connector being dual connectors or even more than two unions with the central cavities filled with Sresin to insulate and separate individual connections. 25. The fuel combustion turbine system as claimed in claim 1 and *oo. •go* claim 15 with special high voltage connectors required for the 7,000 volt system with male connectors with electrically dead metal terminals exposed and female connectors as live metal terminals o withdrawn in connector with all connectors being plastic and male connectors have lead with insulation tightened by ferrell in comp- ression socket and conical brass ring being metal terminal connec- ted by wire through ring to lead and female terminal having lead fixed by ferrell in compression socket with conical brass ring on spring inside connector cavity with wire through ring for connec- tion to lead with male and female connector being dual connectors or even more than two unions with the central cavities filled with j ppoxy resin to insulate and separate individual connections. d 26.\The fuel combustion turbine system as claimed in claim 1 and 66 claim 15 and claim 25 for the principle connection of high voltage power and high current power to spark gap in turbine so that holes in outer corridor covers of turbine with covering tubes allow a Alumina slug or cylinder containing the tungsten cathode point and anode ring such that electrons are targeted down spark gap which is down turbine sheath and this slug is held by a copper ferrell in stainless steel compression socket which is held by screw fitting on turbine's sheath, with the Alumina slug giving adequate insul- ation for the 7,000 volt supply with a separate junction screw fitting of two high voltage male connectors on side of main power input through compression socket to rings spaced and alligned P.T.F.E. bushes and wire and holes to each wire on top of Alumina slug.

S;

27. The fuel combustion turbine system as claimed in claim 1 with rear disc of turbine having slits cut about radially and angling about 450 to longtitudinal direction of flow down turbine being slightly divergent so that gas contact surface is 450 to direction S of flow and upper surface angling about lo less to direction of flow S so that whether discs are high temperature alloy for less than 1,100oC combustion or sintered Tungsten alloy for stoiciometric combustion with air of up to 2,5000K the ions injected down turbine by the magnetic field applied through external coil develop pressures of over 107 Pa. down turbine forcing gas through narrow slits by electron membrane affects in gas of electron circulation speeds of up to 200,000 so that if field is towards back of turbine inwards motion of electrons causes electrons to go anti- clockwise looking from front of turbine so torque is assisted anti- ~tcyockwise lookinq from front and for current flow in different dir- 67 ection, being anti-clockwise, field is to front, rotation is clock- wise, so for anti-clockwise rotation looking from front at top of blades slits angle right and for clockwise rotation looking from front at top of blades slits angle to left with Tungsten alloy pow- der pressed on high temperature alloy bush, slits ground in and bush section welded to shaft with alloy discs welded between bushes and bushes welded to shaft.

28. The fuel combustion turbine system as claimed in claim 1 with the intermediate misting surface blades being made from discs with spiral grooves machined on flat surface with pointed tool with less than a 600 angle with blades then pressed in plate to make blades ~so that edge serations help fling off droplets of less than 50 Pm. S: diameter which are easily carried down turbine in low density air stream with up to 16x or more grooves per millimeter with blade plate welded to bushes and bush assembly of blade plate and bushes oooo• welded to shaft.

29. The fuel combustion turbine system as claimed in claim 1 with oo the front section blades having creases pressed in such a way that for rotation anti-clockwise from front, top of blades angling to S: 20 right with crease on bottom right underside and for clockwise rotation seen from front top, blades angle to left with crease on left under-side such that pressure zone around crease limits speed of rotation in low density air intake stream of turbine with blade plates welded between bushes and bushes with plate, bush assembly welded to turbine shaft.

The fuel combustion turbine system as claimed in claim 1 with the sintered tungsten alloy disc composition being made of 50% to S(weight percent) of less than 5 micron tungsten powder plus Sto 25% Tantalum Oxide powder (wt. percent) and 10% to 15% Hafnium !-oJ KC J 68 Oxide (wt. and 3% to 8% of Thorium Oxide with up to carbon with the powder pressed and infiltrated with Ruthenium Nit- rosylnitrate to make the Ruthenium binder up to 1.5% when heated back to metal with all oxide powder ball milled and being signific- antly less than 5x microns and pressed on bush with protrusions so sintered alloy contracts around protrusions on bush when sintered in hydrogen above 1,000oC at less than 10-3 atmospheres.

31. The fuel combustion turbine system as claimed in claim 1 fewer and wider slits give higher flow speeds through rear disc section with higher combustion speeds being attained by using higher doses of propellant gas but this is done at the expense of torque which is lower.

32. The fuel combustion turbine system as claimed in claim 1 the Turbine system in cylindrical housing and associated components substaintially as herein described with reference to accompanying 600600 Sdrawings. GEORGE ANTHONY CONTOLEON 20TH.,AUGUST,2001. APPLICANT DATE se S