US930766A - Steam-turbine. - Google Patents

Description

E. KARRER.

STEAM TURBINB. l APPLICATION FILED MAH.. 1, 1909.

' Patented Aug. 10, 1909.

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I IIIIIIA I 'lll/[III 'Illlll/ l l l J. KARRERu STEAM TURBIITE. APPLIOATION FILED MAR. 1, 1909.

Patented Aug. 10, 1909.

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@wammw J. KARRER..

l STEAM TURBINE. APPLICATION FILED MAR. 1, 1909,

Patented Aug. 10,1909.

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JOSEF KARRER, OF ZURICH, SWITZERLAND, ,ASSIGNOR TO THE FIRM OF MASCHINENFAB- RIK OERLIKON. OF OERLIKON,

NEAR ZURICH, SWITZERLAND.

STEAMLTURBINE.

No. escasa Specification of Letters Patent.

Patented Aug.v 1o, 1909.

Application filed March 1, 1909. seriaiNo, 480,776.

clear, and exact description of the invention, such as will' enable others skilled in the art to which it appertains to make and use the same, reference being had to the accompanying drawings, and to letters or figures of reference marked thereon, `which form a part of this specification. Y

The exhaust steam from 'intermittently working sources such as winding engines,

lhas beenused in supplying heat-accumulav tors and thence to exhaust steam turbines'.

' to ldischarge into the exhaust Vsteam turblues, so that the live-steam turbines may be l The disadvantages of such plants `are that when thesupplyof exhaust-steam stops' for a considerable time, especially when' the condensation 'of the exhaust steam turbines .fails to act, the plants become incapable of working. -For this reason `live steam turbines, which obviate the above disadvantage, have recently been placed 'ahead of and arranged placed in operation when the exhaust-steamv supply'fails. Such an arrangement of coinbined liveand exhaust'steam turbines possess,

however, the disadvantage that they have a low eiiiciency when operated'as live steam turbines, only` because the sectional areas for the flow of the steam through the low pressure (exhaust steam) turbine is much too large for the case when the plant is operated with live steam only. Supposing `for example, that a combined live and exhaust steam turbine plant has a maximum output of 1000 kw. .If such a plant is supplied-by exhaust steam' only, it works economically. If we assume for examplethat the available quantity of' heat of the live. steam is'twic'e' that of the exhaust steam, the cross sections of the'steam passages or nozzles for the high pressure turbines would have to be dmensioned for 500 kw., as the low pressure turbine also furnishes 500 kw.

If now the supply of exhaust steam fails completely, so that Vlive steam. only has to be used for ashorter or longer time, this high `pressure steam works very badly7 in the low pressure part, and does not y1e d its maximum of available work-as the leross sections oi the steam passages in the low pressure turbine are calculatedfor 1000 kw., that is to say they are twice as large as theyv ought l to be. New itis true that the cross sections of the steam passages in the high pressure parts might also be calculated for 1000 kw.,

the low pressure part, but in such case the whole plant would be twice as large at 1000 kw. out-put as it ought to be, that is to say, it would again work very badly. The object 'of the present invention is to obviatev the above disadvantages.

The invention consists in supplying exhaust steam from an intermittently operating engine or the like and dividing it up lso that they would correspond to those in into two or .more parts, to supply one or more exhaust steamturbines or two or more f parts of an exhaust turbine andaddinga high pressure turbine, the sectional areas of! 'of the high pressure and the exhaust-steam turbines. .Fig 3 is an elevation'similar to Fig. 1 of 4a modification. Fig. 3a is a vertical cross section of Fig. 2 through lines d, d. Fig. 4 is an elevation of a further modification. Fig. 5 is a vertical llongitudinal section of YFlg. 4 similar to Fig. 2. Fig. 6 is a vertical cross section of Fig. 5 through lines e, e. Fig. 7 is a vertical cross section similar to Fi 6 of a modification.

Re erringto Fig. 1, in which ,I have shown a 1000jkw. combined live and exhaust steam turbine plant., The exhaust steam from any suitable' source is supplied to two separate exh'auststeam turbines N1 and drivean electrical generator or the like; the

exhaust steam flows from a main pipe a through the'pipes b1 and b2 to the exhaust steam turbine.- Ahead of the exhaust steam turbine N,'is placed a high pressure turbine exhaust steam should fail, the tpl-bine H N1 N2 which are shown in .the cylinder H, the sectional areas of the nozzles o r steam passages of which are calculated for the same volume of steam, as the sectional areas of the steam passages of the turbine N1 and adjoin the latter. The high pressure turbine H receives live steam from the pipe c which is provided with an inlet or cut olf valve. As the available quantity of heat of the live steam is about twice as great as that of the exhaust steam, -the live steam yields 500 kw. in the turbine H and 5.00 kw. in the exhaust steamturbine N1. Consequently, if for any reason the supply of may be fed with live steam and can give the full power with the.l best eliiciency, as the cross sections are calculated accordingly. This plant works economically therefore with both live and exhaust steam. A further advantage maybe obtained by conducting the exhaust steamirst through the turbine N2 and only at a load of over 50() kw. through N1. The turbine then works economically even under half load.

.Referring now-to Fig. 2, which shows a simplification of structure from thatshown in Fig. 1, the exhaust steam turbines N 1 and Fig. 1, as separate are combined into a single turbine N in Fig. 3, the exhaust steam is nevertheless supplied separately, through the pipes b1 and b2; the fixed blade rings of the turbine N are so constructed that the passages for the steam from two concentric zones,A are separated from one another; (see Fig. Q) the outer passages correspond to those of the turbine and the inner ones with those of the N 2 turbine N1. f The exhaust steam flowing through N 1 and N2 acts upon the blades of the same rotor. The cross section of the passages of N 1correspond in their turn to the c ross section of the passages of the high pressure turbine H, see Fig. 3. If, therefore, for any reason live steam has to be used, this may be done here in an economical manner. The live steam flows through the high pressure turbine H. and afterward through the passages N1 of the low rcssure turbine N. The turbine H N therefldre posi sesses all the advantages of, the turbine H N1 and N2' of Fig. 1, but is considerably cheaper and occupies considerably less room. The

loss by leakage in the low pressure steam exhaust steam turbine N, from the passages N1 to the passages N2 is very small, because the width s of the gap is very small compared with the height or radial length 72, of the blades or' the rotor and this Vloss of eiiciency is at all events considerably smaller i than the gain secured by doing away with the idle running of the rotor of turbine N2 of Fig. 1.

Figs. 4 to 6 show another arrangement. The rotors of the turbines N1 and Nzhof Fig. 1 are again combined Linto a single lower half into `iows through all four segments of the low bine being calculated turbine,

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cylinder N. 4The guide passages are how-4 ever. not arranged in two concentric zones: the steam traverses them on their entire height la., Fig. 5. Nevertheless, the steam in the part N1 works separately from the steam in 4the part N. this is obtained by transforming for instance the upper half of the turbine N into the part N2 and the N1. The guide passages in the upper half are suitably separated from those in the lower half. b2 leads the steam to the upper half and 1 to the lower half of the exhaust steam turbine N When the turbine is worked by exhaust steam, the whole rotor of turbine N is in o eration; if there is no exhaust steam availa ile, then live steam Hows through the high pressure turbine H and thence through the lowpressure part N1 of the exhaust steam turbine N. The guide passages in the low pressure exhaust steam turbine N may, of course, be divided up into more parts, or segments say four, for example (see Fig. 7). The exhaust steam enters through the pipe b and pressure exhaust steam turbine; and live steam flows through the high pressure turbine and afterward through only two segments of the low pressure turbine. Other combinations may also be made, in all of which the essential feature will be, that a high pressure turbine is placed ahead of the low pressure or exhaust steam turbine, the sectional areas of such high pressure turfor the same volume parts of the low pressure 1 through which live steam also.

of steam as those passes.

I claim 1. The combination with a turbine operating by live steam of a plurality of turbines operatine by exhaust steam, said live steam turbine ischarging into less than the whole number of said exhaust steam turbines.

2. The combination with a turbine operating by live steam of a turbine operating by exhaust steam and divided into a plurality of parts, said live steam turbine discharging intoless than the whole number of parts of said exhaust steam turbine.

3. In combination a high pressure live' steam turbine and a plurality of exhaust steam turbines, said high pressure turbine discharging into less than the Whole number of saidI exhaust steam turbines, and that exhauststeam turbine or those exhaust steam turbines into which the high pressure turbine exhausts being designed to accommodate the steam entering from the high pressure turbine.

4. In combination a high pressure live steam turbine and an exhaust steam turbine divided into a plurality of parts, said high pressure turbineldiseharging into less than the whole number of parts of the exhaust steam turbine and an' exhaust steam turbine divided into a plurality of parts, said high pressure'turbinel discharging into less than the Wholenuinber of parts lof the exhaust steam turbine,l and that4 part or parts into which the high pressure turbine exhaustsI being designed to accommodate the steam entering from the high pressure turbine, the

steaml passages or nozzles of'the exhaust steam turbine -beihg divided into concentric zones by suitable partitions, so that the parts -form a plurality of co-axial cylinders.

- 6. In combination a high pressure live steam turbine andan exhaust steam turbine divided into a plurality of segmental parts, said high pressure turbine discharging into less than 'the Whole number4 of said segmental parts of the exhaust steam turbine,

andthat vor those segmental parts into vvhichV the high pressure turbine exhausts being designed to accommodate the steam entering from the high pressure turbine.

7. In combination a high pressure live steam turbine, and exhaust steam turbine parts operating and separately supplied with exhaust steam, said live steam turbine discharging into less than the Whole number of parts of said exhaust steamV turbine, and

f that part or parts into Which the live steam turbine exhausts being ydesigned to accomlnodate the steam from the live steam turbine.

8. In combination a high pressure live steam turbine, and an exhaust steam turbine divided into a plurality of parts, a single casing for both of said turbines, means to separately supply the several parts of the exhaust steam turbine with exhaust steam, said live steam turbine discharging into less than the Whole number of parts of the exhaust steam turbine and that part or those parts of the exhaust steam turbine into which the vlive steam turbine discharges being designed to accommodate the steam entering from said live' steamturbine.

In testimony that I claim the foregoing as my invention, I have signed my name in 4`presence of tivo subscribing Witnesses.

JOSEF KARRER.

Witnesses:

E. C. REDINGER, JOSEPH SIMON.

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