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3,138,923 a( 41 ratio more than three times greater than the gear ratio possible to attain in previous known gas turbines contain ingaseparatedrivingturbine. Itmightbementioned, furthermore, that the utilization factor (de?ned as the ratio between the higher and the lower speeds at which thee?iciencycurveamountsto70% atfullgas)inacom bination according to the present invention amounts to about 3.5, whereas the same ratio amounts to about 2.5 in gas turbines containing a free turbine. adapted relatively to each other that the speed of the compressor and thus of the compressor turbine and of the pump of the hydrodynamic torque converter becomes constant or nearly so, independently of the load, corre sponding to the curve I in FIG. 4. By altering the leverage between the throttle valve control and the blade control another operating line, cor responding to a compressor speed increasing with an in creasingload,orviceversa,maybeobtained. Thisis illustratedbythecurveH inFIG.4. FIG. 5 illustrates the ef?ciency and the gear ratio for the hydrodynamic torque converter with adjustable pump and/or guide blades as used in the plant according to the invention (and is related to the progress of the absorbed The invention will be further explained in the following with reference to forms of embodiment with appertaining diagramsshownintheaccompanyingdrawings. FIG.1 represents a section through the turbine member and the pump member of a hydrodynamic torque converter with adjustable pump blades, and PEG. 2 shows a similar sec 15 pump torque shown in FIG. 3). With respect to the tion through the reaction member of a torque converter withadjustablereactionblades. FIG.3isadiagram referring to the torque converter according to FIGS. 1 and2. FIG.4isadiagramreferringtoauni-shaftgas turbine with ?xed and pivoted guide blades, respectively. FIG. 5 is a diagram of the e?iciency and the gear ratio of a hydrodynamic torque converter according to the presentinvention. FIG.6isadiagrammaticrepresenta tion of a substantially complete gas turbine power plant accordingtotheinvention,andFIGS.7to9showvarious 25 following. embodiments of a torque converter pertaining to the plant. FIGS.10and11showapairofembodimentsof the gas turbine member in a plant according to the in vention. FIG. 1 shows the pump and turbine members of a hydrodynamic device combined with a gas turbine, where in the pump member is provided with adjustable blades. FIG. 2 shows the reaction member of the hydrodynamic torque converter considering the case of the same being providedwithadjustableblades. FIG. 3 shows how the torque (MP’I‘) absorbed by the pump of the hydrodynamic torque converter varies as a function of the speed ratio between the turbine and the pump thereof (nT/11p) and as a function of the angle of adjustment for the pump and guide blades (gap and gas), respectively. Thetorqueabsorbedbythepumpincreases withanincreasingoutletangleforthepump andtheguide blade, respectively, in accordance with the showing of FIG. 3. FIG.6showsanarrangementwithacompressorK and acompressorturbineKTononeandthesamepowerout put shaft 16, which also drives the pump (P) of a hydro dynamic torque converter over a planet gear R. The torqueconverterconsistsofastationaryhousingH and thepumpP,areactionmemberM andaturbinemember S2 connected to the output shaft 11 which includes a re verse gear BV and reduction gear RV. The reaction member is provided with pivoted blades in at least one of the rims. The guide blade rims of the compressor and the gas turbine may be made either with ?xed or with pivoted blade elements. The reverse gear BV is arranged behind the hydro~ dynamic torque converter, possibly in combination with the reduction gear RV. Furthermore, a free wheel F is incorporated between the pump and the turbine to provide an engine brake, said free wheel being so arranged that the pump may ro tatefasterthantheturbine,butnotviceversa. Witha Bymakingtheadjustmentofthebladesautomaticand 45 drivingturbine,thefreewheellockstheturbinetothe continuously variable as a function of the throttle valve position, i.e. of the injected fuel quantity, different pro gresses of said pump torque (Mpi‘) may be obtained. The groups of curves a, b and c and a1, [21 and c1, re pump, so that both of said elements rotate with the same speed, a very valuable additional brake (hydrodynamic brake) being thus obtained. By turning the reaction blades so as to reverse the spectively, as shown in FIG. 3 represent said torque ab 50 torque acting on the turbine member said brake effect sorbed by the pump for different throttle valve adjust ments and as a function of the speed ratio (nT/np), the curves a, b and 0 representing one construction and the curves (:1, b1 and 01 another construction, which is de maybecontrolledcontinuouslyasdesired. Thearrange ment for turning the blades may possibly be connected to the braking mechanism of the vehicle as denoted by the legend on FIG. 6, the braking effect then permitting pendent on the leverage selected for the movement of 55 of taking place in a stepwise or continuously varying the throttle valve control and the control for the angle ofadjustmentoftheblades. FIG. 4 shows the output torque for a uni-shaft gas turbine. ThecurvesTf“,T51‘andTy!‘indicateavarying fashion. KF denotes cooling ?anges, which in the illustrated case have been cast integrally with the stationary con verter housing, which is preferably made from light metal turbinetemperature(T*)and?xedguideblades. Acor 60 (electron). Throughthearrangementshown,coolingof responding progress of the torque with pivoted guide blades is indicated by T1*(VR), T2==‘(VR) and T3*(VR). With a constant fuel quantity the progress of the torque varies according to the corresponding curves 131*, 132* the flowing medium in the hydrodynamic converter, val uableparticularlyinbraking,willbeobtained. Ifde sired, said cooling ?anges may be made hollow to be traversed by the ?owing medium of the hydrodynamic and33*andB1*(VR),B2*(VR)andB3*(VR),respec 65 torqueconverter,thenaturaldifferenceinpressureinthe tively. FIG.‘4alsocontainsthegroupsofcurves0,band c and a1, b1 and c1, respectively, for the absorbed pump torque (MP‘F), which correspond to the throttle valve positions for a constant turbine temperature Tf", T55‘ torqueconverterthenpermittingofbeingutilizedtobring about said circulation through the cooling ?anges. In connection with FIG. 6 itshould be noted, further more, that the hydrodynamic torque converter is made of andTail‘oraconstantfuelquantityBf“,Bf‘andB3‘ 70atorus-shapeofthelyingtype,thepumpbladesbeing The points of intersection between the curves a and T1*, b and T55‘ and c and T3* are located on a curve which in FIG. 4 is parallel to the ordinate axis, that is to say, the fuel control and the blade control of the hydrodynamic torque converter and/or the compressor turbine are so 75 ment shown, the reduction gear R may be made with a e?ciency and the torque multiplication itholds true within certain limits that the maximum e?iciency is displaced toward lower turbine speeds corresponding to a lower speed ratio (nT/np) at decreasing angles of adjustment for pump and guide blades, respectively, with a simul taneous increase of the torque multiplication at start, and vice versa. A fewembodimentsofthegasturbinepowerplantand elements associated therewith will be described in the arranged on a small hub at the inner portion, whereas the turbinebladesaredisposedattheouterportion. Hereby a particularly high gear is obtained over the hydrodynamic torque converter, and consequently, with the arrangePDF Image | KRONOGARD AUTOMOTIVE GAS TURBINE POWER PLANT
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