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4,336,039 34 of the passage 20 will be diverted into the water rotor. The steam being lighter is diverted inwardly into the steam rotor inlet. _ _ Abovetheconicalportionoftheshaft,"thatserves with the vanes 26 and the cooperating wall surface as a centrifuge to separate the water and solids from the steam in the power ?uid and divert the water and solids into the water rotor, the shaft has an axially curved wall 30 forming the concave inner surface of the inlet pas sage 32 to the steam turbine wheel or rotor. The outer wall 34 of this passage is convex and is an inward and upward continuation of the wall 28 of the Water rotor. This passage 32 curves slightly toward the axis of the shaft then turns outwardly to a generally radial direc tion forming a radial passage 36 terminating in nozzles 38. These nozzles are positioned between the outer ends of the wall 34 and an opposing wall 40 formed by a generally radially extending disk on the shaft. Although in many instances the discharge from the rotorswouldbeinaplaneperpendiculartotheaxisof20 the shaft,,in this concept the turbine rotor passages are contoured to position the nozzle so that the discharge is at a slight angle to the perpendicular, beingin fact al most parallel to the domed casing at this point. This directionofdischargemakespossibleawashingaction25 of the discharging ?uid over the surface of the casing to remove any sludge collecting thereon. The same istrue of the nozzles for the water rotor although the “out-of perpendicular” effect is less as shown since the periph ery of the water rotor is not closely adjacent to the casing. . For the same pressure ratio between inlet and exhaust a water turbine needs a smaller diameter than a steam turbinebecauseofthesigni?cantdifferenceindischarge velocities. Thus, the water rotor is shown as a smaller 35 diameter than the steam rotor. Since itisinef?cient to discharge water and steam together in a single wheel, it is most effective to have the two-wheel rotor construc tiondescribedwiththeintegralcentrifugalseparatorto divide the ?uid stream between the rotors. An exampleofanozzleconstructiontoproducehigh efficiency in both rotors is shown in the steam rotor of FIG. 2 and the sectional view of FIG. 3. The particular advantages of this form of nozzle are clearly described in US. Pat. No. 3,968,935 above referred to and asimi lar construction nearly as effective in this arrangement is described in US. Pat. No. 3,804,335. As shown in these?gures,thenozzle38hasopposedwallsurfaces42 and 44 which converge toward each other from a blendingwiththesurfacesofwalls34and40toanozzle50 throat 46. Downstream from the throat the walls 48 and 50divergetoformthesupersonicexpansionvolumefor the power ?uid. These walls are shown to diverge more rapidly close to the throat and less rapidly later to ac commodatetheshockwavesandtheexpansionofthe55 fluid or ?uids. The circumferential pattern of these converging and diverging surfaces is broken up by axially extending streamlined or airfoil shaped vanes 52, FIG. 3, extend ingbetweenthewalls34and40asshowntodirectthe60 ?ow intoadirectiontangentialtotheperipheryofthe wheel thereby obtaining the most thrust on the rotor fromthedischargeofthefluidthroughthenozzles.The shape of these“ vanes is dependent on the pressure drop throughthenozzles,essentially,thebestairfoilshapeis65 selected to produce a minimum of impedance to the ?ow while guiding the ?ow into the desired tangential direction. I These vanes 52 preferably extend radially from the upstream ends of the convergent surfaces 42 and 44, representedbytheline53,FIG.3,pastthethroat46and substantiallytotheouterperipheryoftherotor,repre sented by the line 54, FIG. 3. Although the vanes are shown as airfoil in shape, the term is used for either a subsonic or supersonic airfoil dependent upon the ve locityofthe?uidapproachingandthroughthenozzles. The particular contours and lengths of the convergent surfaces 42 and 44'and of the divergent wall surfaces 48 and 50 will be determined in any speci?c rotor con struction by the pressure drops across the nozzles as well as the mass of the particular ?uid. Obviously for water, ?ashing in part into steam as it flows into and through the nozzle, the contours would be different from the contours for the steam nozzles on the steam wheel. Both rotor elements are shown as having no structure extending across the ?ow passages as the power ?uid movesoutwardlyintherotorsuntilthe?uidreachesthe nozzles. It is desirable to allow the ?uid to move radi ally outward in these passages without any tangential accelerationofthefluid.The priorarthastangentially accelerated the driving ?uid from standstill (pure radial ?ow)tothecircumferentialvelocityoftherotorwhile the ?uid is ?owing through radial guide passages in the rotor to the nozzles. Such acceleration consumes con siderableenergyparticularlyinhighspeedrotorssince the work to accelerate the ?uid increases as the square of the circumferential velocity. Further, in a pure reac tionturbine,ofthetypeofthisinvention,highcircum ferential rotor speeds are required in‘order to obtain suitable operating characteristics and ef?ciencies that would be superior to conventional turbines. Itmay bedesirable,toassure‘aminimum oftangential accelerationofthe?uidsintherotorstoprovidecurved guide vanes 55, FIG. 4, extending upstream of and in alignment with the nozzle vanes, with the passages 56 establishedbetweenthesevanescontouredinrelationto wheel velocity and ?uid velocity in the wheel so that the?ow inthesepassageswillbeessentiallyradiallyof the wheel. Such passages reduce any tangential acceler ation resulting from boundary layer effects and assure entry of the ?uid into the nozzle free of any tangential velocity. Such vanes may extend inwardly for most of the radial ?ow or may be positioned in only the outer halfoftheradial?ow. The geometryofthesespirallike vanes isdetermined by the area pro?le in the axial plane andtheproportionsofthevaneswouldbedetermined from the radial velocity pro?le. Although these guide vanes are shown as aligning directly with the nozzle vanes 52' and equal in number, itmay be desirable to use less guide vanes, for example one for each second noz zlevane‘.Itshouldbeunderstoodthatinmanyinstalla tiqns such guide vanes would be entirely unnecessary. The prime purpose isto keep to a minimum any tangen tialaccelerationofthepower fluid.Where highestper formance is not of prime importance, the omission of theseguidevaneswouldreducethedevelopmentand production costs of the overall turbine. One particular advantage of the present arrangement is that the capacity of either rotor is readily varied by adjustingthespacingoftheoppositewallsoftherotor. Thismaybeaccomplishedbylengtheningorshortening the axially extending vanes and the turbine rotor isthus adaptable vto the' quantity of geothermal power ?uid and/or tothepercentage ofwater inthe fluid. 40PDF Image | Geothermal Turbine 1982
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