US2783964A - Turbines - Google Patents

Description

0. THEIMER March 5, 1957 TURBINES 8 Sheets-Sheet 1 lu ik March 5, 1957 Original Filed July 11, 1945 March 5, 1957 0. THEIMER TURBINES 8 Sheets-Sheet 3 Original Filed Jlily 11, 1945 I l v March 5, 1957 o. THEIMER 2,783,964

'ruRBINEs Original Fil ed July 11, 1945 a Sheets-Sheet 4 March 5, 1957 o. THEIMER 2,783,964

TURBINES Original Filed July 11. 1945 8 Sheets-Sheet 5 IN VEIggR. (41m ywiiyzg March 5, 1957 o. THEIMER 2,783,964

'TURBINES Original Filed July 11, 1945 8 Sheets-Sheet 6 IN VEN T R.

o. THEIMER 2,783,964

TURBINES s She ets-Sheet 7 March 5, 1957 Original Filed July 11, 1945 IN VEN T0 (Q! 6% cum March 5, 1957 o. THEIMER TURBINES Original Filed Jul 11, 1945 a Sheets-Sheet s vide a turbine with equal radial diameters and w 'g United States Patent TURBINES Oscar Theimer, New York, N. Y.

Original application July 11, 1945, Serial No. 604,383, now Patent No. 2,524,549, dated October 3, 1950. Divided and this application August 16, 1950, Serial No. 179,697 a 9 Claims. c1. zss sals This invention refers to improvements in or relating to rotary engines and more particularly to turbines. The invention contemplates a new working method for turbines which is highly economical and may be carried out with any kind of fuel or power medium, sueh as gas, steam, water and the like.

One of the objects of the present invention is the provision of means aifording utilization of apower medium repeatedly by action and reaction whereas said power medium is not discharged from the turbine until its highest possible expansion has taken place within the turbine and has been fully transformed into driving power.

Another object of the present invention is the provision of means permitting compression of the power medium to reach its highest degree immediately prior to ignition or, in case of steam, the highest tension thereof is brought about immediately before expansion.

Still another object of the present invention is to provide a turbine in which the flow of the power medium to the rotor occurs in substantially straight uninterrupted passage and the impulse resulting from the expansive or explosive force of the power medium is immediately directed from an improved nozzle to the rotor to th reby attain the least possible heatdrop of the power and the most favorable impulsive force thereof.

Yet, a further object of the present invention is the provision of a turbine equipped with :a most ftective injection nozzle giving high efi'iciency to the 1n"cted powermedium. I

.Still another object of the present invention is toprofor each rotary stage, this being very advantageoii sbecause of the avoidance of additional strainsand stresses exerted on additional rotary stages which 'a eiprsent in known turbines.

A further object of the present invention is the ,provision of an engine in which the expansion of theip ower medium is directed in a substantially radial direction through circumferentially arranged stages, thus reducing the length of the engine, although the length of .the

passage of the power medium is increased the increased working surface also making repeated use ofthe impulse forces of the power medium and also of its repulsion forces. i

Still another object of the present invention is the provision of a turbine whi ch in'the case of an internal combustion turbine is designed so that the importantworking parts exposed to high temperatures are effectively copled by means of a comparatively simple Bravery reliable and efficient cooling system without resorting toa' particul ar .coolingaggregate and impairing onlytoa niall extent theefi'ectivenessof the powerrrnediu m and the power derived from said medium.

This loss of efiiciencyfcamedbythe b ak efljectin consequence ofthe air resistance agains'tQtlierrap drevolving rotor is considerably compensated bylthe" out- .put exerted against the inner walls of peciiharcui'ved said shutter. in another position;

pro s w ch rotor air cooling canals, which are open at both ends, at the inner and outer rotor peripheries. This output results from the air flow circulating with high velocity through the rotor air cooling canals in like mann'er when gas power medium is circulating through the rotor gas canals. The aircirculation is caused by aviolent suction on account of the diiference of air pressure between the inner and outer rotorperiphery.

Above mentioned loss by means of the brake effect is further quite compensated by the forces of impulse and repulsion, first on entering of the air flow at the inner rotor periphery into the rotor air cooling canals and second when escaping from the air cooling canals at the outer rotor periphery. 'Astill furtherobject of the present invention is the provision of a turbine in which detrimental frictionis effectively reduced because the power medium while passing through 'the'power canals issimuItaneOusly revolving in an enclosed condition within the stationary turbine casing, therefore no contact and no detrimental friction of the power medium with the walls of the stationary casing during the passage through the rotor powerc na s takes p a Still another object of the present invention is to provide a'turbine in'which detrimental back pressure is effectively redueed within the rotor because the exhaust of the power mediurn'is (by means of centrifugal force during a sufficient part of time oflthe revolution of the rotor) practically fe ntirely expelled from the rotor before a new charge ofj'the power medium is applied to f the rotor.

' Another object of the invention is the provision of means for obtaining I effective sealing conditions" of the turbine" against leakage of the hot media. derived from the combustion before expulsion of said media. These'andother objects and advantages of the invention' will become more apparent as the following description of the several embodiments of the invention are illustrated on the attached fdrawings', in which Fig. l is a partial cross-sectional view of a preferred embodiment of'my invention taken along line" 1-'--1 of Fig. 2;

Fig. 2 is a vertical section taken along line 22 of Fig. 2a is a fragmentary vertical section taken along Fig. 2b is a sectionalview of a detail of the turbine to which reference is made in the specification. Fig. 2c shows diagrammatically an embodiment of the injection nozzle employed in "the'inventio'n;

Fig. 2d is the discharge unit inmodified form connected with the injection no'zzle shown .insection;

"Fig. 3 is a fragmentary elevationalyiew of the rotor;

Fig. 4 is a fragmentary vertical section throughamodified fai h of the presentinvention taken'alongline 4-4 Fig; 8 is across-sectional view of the shutter used in .ii i power canal ,of themodification shown in Pig's. 4- 6, in c lu'siv'e';

Fig. 9 is a horizontal sectional view taken along line 9- 9 of Fig. 8;

Fig. 10 is also a cross-sectional view ofthe shutter of Figsi 8' and 9 taken along line El -1,0 of 9, sh0wing Fig. 11 is a horizontal sectional view of the turbine ofr 2, 2a and 3 illustrate one preferred embodiment of the invention which can be used without substantial changes as an internal combustion turbine or steam turbine and comprises principally a substantially ring-shaped rotor 1 which is secured to a shaft 2 and turns within an outer guide body or housing 3 and an inner guide body 4, the latter being preferably in the form of a drum. The outer guide body 3 is provided with an inner rim part 3a. The inner guide body 4 is provided with an outer rim part 4a. From the outer guide body 3 extends toward said shaft 2 at opposite sides of said rotor 1 guide body plates 6 and 7.

. which may be integral with or otherwise fastened to hub and with members 8 and 9. Members 8 and 9 of the rotor ,1 are further supported by a ring shaped rotor disc 12 ,or rotor supporting member with suitable cut outs 14 or passage ways through which a cooling medium,

preferably air, may enter in accordance with arrow A (Fig. 2) from apertures 37 provided in guide body plate 6. The inner and outer guide body and the rotor as well as other parts of the turbine may be constructed in sections in order to facilitate assembling of the turbine.

The outer portions 15 and 16 of discs 12 and 13 of the T rotor 1 are circular and adapted to run in corresponding annular grooves 15a and 16a provided in the inner rim part 3110f the outer guide body 3, as may be seen in Fig.

2, to thereby obtain efiective sealing means for the turbine.

Between the inner and outer rotor rim members 8 and 9, there are disposed power canals or power medium directing means 17, which, in this instance, are arranged in fixed relation to the rotor, but may also be interchangeably mounted thereon not shown in the drawings and extend in radial direction from the inner rotor rim member 9 and a predetermined distance from shaft 2, thereby providing between the shaft 2 and rotor rim 4 member 9 a chamber 18 for supply and passage of air or another suitable cooling medium. The power canals 17 terminate adjacent the outer rotor rim member 8.

Rotor 1 may be made as a unit from a disc-shaped casting containing said power canals 17 whose walls may be provided with metallic or fireproofed coatings (not shown) or other interchangeable protective means in order to protect the interior of said power canals.

' These rotor power canals 17, particularly in the case of an internal combustion turbine, may be surrounded by cooling canals 19 which both power and cooling-canals are curved in the direction of movement of the rotor,

the curvature forming preferably a part of an absolute or an approximate logarithmic spiral.

These canals or directing means for the power medium and for the cooling medium are curved at opposed ends;

17 "and 19 of the power medium and cooling medium, respectively, within the rotor 1 contact and detrimental friction of the power and cooling medium with the walls of the stationary turbine housing during their passage through the turbine is effectively reduced.

Both canal means are open at said opposite ends, therefore allowing the expansion of the power medium and contributing to the circulation of the cooling medium.

This turbine may also be constructed to include more than one rotor as herein described (not shown in the drawing), said rotors Working on the same principle and method as the single rotor.

A plurality of rotors may be fixed on the same shaft and one or more rows of power and cooling canals may be arranged in each rotor while the outer guide body and the inner guide body of the turbine will be readily modified to correspond to the number and type of rotors employed.

The width of the curved power canals 17 is preferably gradually increased from its inner rotor rim member 9 toward the outer rotor rim member 8 and are thus tapered from the outer rotor rim member 8 toward the inner rotor rim member 9 (Fig. l). The surrounding cooling canals 19 are shaped and curved correspondingly.

The cross section of the power canals 17 and of the cooling canals or jackets 19 may be of any suitable configuration, such as elliptical, ova], oblong, rectangular,

round. In the present instance, they are substantially elongated (Fig. 3) and the cooling canals 19 surrounding the power canals 17 may be similarly shaped or may i be guided around the power canals in spiral form.

suitable means, such as plates 21 (Fig. 3), disposed at the outer and inner periphery of the rotor 1 and at predetermined locations thereof where the hot power medium discharged from the nozzle and guide pocket units into the power canals is efiectively prevented from entering into the cooling canals 19.

Suitable shaped ring members forming extensions 22 (Figs. 2b, 3) and 23 (Fig. 2) of the rotor 1 and positioned adjacent the power canals 17 engage correspondingly shaped annular grooves 22a, 23a provided (Fig. 2), respectively, in the inner rim part 3a of the outer guide body 3 and in the outer rim part 4a of the inner guide body 4 to act as effective sealing means. Extensions 22, 23 and grooves 22a, 2311 may be constructed to form inner and outer gas traps, such as exemplified by numeral 24 in Fig. 2b, against escape of the power medium.

These above mentioned ring members forming extenextend into these grooves of both said guide bodies which projections guide that part of the power medium tending to escape between the rotor and said guide bodies. Each of these projections 22, 23 are further provided with V extensions 22a, 22 (Fig. 2b) and end rims 22b, 23!;

these curvatures on both ends are situated with respect to the inner and outer rotor peripheries in an angle'directly opposite to the direction of the rotor movement (Fig. IL The rotor forms a revolving casing within the stationary outer and inner guide bodies of the turbine.

Due to the fact that the power medium and thecooling medium are simultaneously moving in an enclosed condition while passing through therevolving directing means 22a 23a (Figs. 2, 13) of the respective guide bodies.

These grooves contain circumferentially directed partitions 22c, 23c (Figs. 2b,,13) terminating short of said extensions of the rotor.

Between these partitions 22c, 23c'(Figs. 2b, 13), and

A 5 end walls of these grooves, containers 22 1, 23 d (Figs. 2, 3) are formed which may be filled with suitable heatrresistant sealing material, for instance graphite, graphite'compounds, etc. with which the projecting rims 22b, 23b (Figs. 2b, 13) engage.

Portions of said power medium escaping through the gap between said rotor and inner and outer guide bodies will not be able to take its course in downward direction between partitions 22c, 23c and end rims 2212, 23:) and are therefore blocked and held back by the sealing material within said containers above referred to.

As may be seen in Fig. 2, sealing means 25, 26, 29b of rotor 1, and 27, 28 of outer guide body rim part 3a and 29 of inner guide body rim part 4a engage in corresponding grooves 25a, 26a, 274,28 1, 29a and 29c provide sealing means.

Within the outer guide body 3 and within the inner guide body 4 are positioned adjacent said outer and inner rotor rim members 8 and 9 a plurality of inner guide pockets or guide pocket units 52, 53, 54 and outer guide pockets 62, 63. Instead of these units, guide canals could be arranged.

The guide pocket units are, respectively, provided with a plurality of stationary guide members 52a, 534:, 54a, 62a, 63a which function in some cases somewhat similar to nozzles, thereby increasing the speed of the power medium entering the rotor power canals. The guide pocket units have further guide walls 52b, 53b, 551b, 62b, 6312 (Fig. 1). Instead of guide pockets, guide ducts may be arranged.

The inner and outer guide pocket units .of which one portion is a receiving section and another portion a delivery section for the incoming circulating power medium, are designed so that the diameter of the receivingsection is measured in accordance with the volume of the circulating power medium in order to provide possible smallest back pressure against the incoming power medium expelled from the rotor power canals. The diameter of the delivery section is proportionally larger in comparison to the receiving section in order to provide possible highest pressure of the power medium returning to the power canals so as to overcome the centrifugal force executed by the revolving rotor power canals against the entering power medium.

Due to the circumferential arrangement, .the radial weights and radial distances of the rotor stages are kept substantially equal to eliminate increasing strain .to each following stage, although each turbinestage including the respective rotor sections are relatively enlarged in circumferential direction.

The walls of the guide pocket units andof its guide members are shaped and arranged .in such a l anner that they will guide the power medium from .andto the periphery of the outer and inner rotor member, as will be hereinafter explained. Exhaust openings 30 are arranged within the outer guide body 3 (Fig. 2 to allow the escape of the used power medium; further escape openings 31 (Fig. 2) allow the escape of the cooling medium emanating from the rotor cooling canals 19.

The inner guide body 4, in thisinstancein the form of a drum, has entrance openings 32 (Fig. 2) to allow the entrance of air or of another cooling medium into the cooling canals 19 of the rotor 1. Drum or inner guide body 4 is connected in fixed relation to the-housing or outer guide body 3.

A space 33 is provided between shaft 2 (Fig. 2) and sleeve 34, the latter'being screwed or otherwise fastened to collar or shoulder 34a arranged for support by outer guide body plate 6. i

Rotor disc ring 12 is adapted to revolve by means of ball bearing 36 around stationary sleeve 34. To suitablysupport the inner guide body 4, bearingsd35a may be disposed between shaft 2 and sleeve 34. Shaft bearings 35 and 351) are provided at opposed sides of the turbine.

Tbs 2915. 23 medium a e s n a al dire t on hr h apertu i7iof outer" :de body plate '6 and 1th cle gasse awa d n J I 19W A in axia d re i ,Qfs 2 through cutouts which are provided in'ro'tor' ring 1;, and is iinally urged by means of a violent autoin s st n a i l .d ss thm igh sain s .32 .w' thin'tlr i 4'i lto the'coolihg d m directing means or coeling canals 19 through openings3 1 of the housing 3 preferably into the atmosphere, thereby efiec- Itively cooling the drum 4, .the canals 17 of the power medium and the housing 3.

The air surrounding the outer rotor periphery is hurled or pushed aside from the ,outer peripherybecause of the high speedof revolving rotor and thereforeis creatin m ana wli w va m h b a i q for the "following air incoming ion the inner rotor periphery, in some modifications through the cooling canals 1 9 and other modifications direct through the power canals 17 a account of the existing difierence'of atmospheric pressure between the inner and outer peripheries were pf i t l The driving or power medium, such as gas, steam and the like 1s injected into the rotor power canals or ducts of the turbinm pre'ferably by means of one or more nozzle means 40 include a short constriction fo'rming a necl he acting according'to the Bernoulli nact. Ea h nzz means may Pr ide w ia' o n jacket 41 and has further a spring supported resistance c ornpresision :shn'tter or resistance compression valve i a The resistance co npression shutter or resistance compression vvalve 4 2may be opened and closed at 'pfedetermined intervals and maybe timed with the ignition and i ih r 9 he gi n dia l a r t means, such as eccentric or cam gears 43,431, as shown ,and ernploye'd for valves 44, '45 hereinafter described (Fig. 2d).

In the case of an internal combustion turbine, the nozzle means 4i) is integral or in another manner connected with the discharge unit 38 comprising' an explosion chamber 46 with means for scavenging it from the used power medium, a pre cornpression chamber 47, a'feeding chambe rz ifl with flange connection 50. The pi e-compression chamber 47 and-explosion chamber 46 contain said valves 44 and 45.

Explosion chamber 46 further contains the ignition device 491.

Feeding chamber 43 may be constantly filled with fresh driving medium from a gas compressor (not shown) which is connected to flangeiconnection 50.

When valve 44 opens (by means of action of cam 43), gas enters from the feeding chamber 48 intoithe precompression chamber 47 from where the'gas is introduced into the explosionchainberi46 through valve 45, actuated in predetermined intervals by'cam 43a. After closing valve 45, the ignition device 4 9ignites the compressed gas, and the gas expansion caused'by the explosion opens the nozzle compression shutter 42 and the now expanding gas passes through the nozzle 40 into the rotor power canals 17. i

The expanding gas ineach power canal 17 causes an impulse upon rotor 1 indesired direction, in the present instance in a clockwise direction. The expanding gas while passing through canals 17 will be compressedand/ or its speed will be increased, dueto the. fact that the power canals 17 are tapered towards the inner rotor periphery. The inner and outer guide bodies comprise either guide pockets, and/or guide pocket units orguide canals." The guide pocket units comprise, either .curved guide elements or guide ducts.

vIn this instance, the inner guide pocket units 5 2, 5 3, 5 4 are divided by respective curved guide elements 52a, 53a, 54a and having the respective curved guide walls :Rferring tial? t nne g de P99 5 a? 2.

it will be realized that if the power medium (gas) is supplied by nozzle 40 to power canal 170' the power medium will then expand within the inner guide pocket 'unit 52. The curved guide elements 52a and the curved guide pocket wall 52b provided within the inner guide bodyor drum 4 causes a flow of the combustion power medium in the direction of arrow 55 so that the power medium enters into the rotor power canals 17c and 17d toward the outer guide pocket units. 62, while the remainder of the power medium within canal 17b is still moving toward the guide elements 524: within the inner guide pocket unit 52.

The outer guide body or housing 3 comprises guide pocket units 62, 63, etc. Guide pocket units 62 has the curved guide elements 62a and the curved guide pocket wall 62b, which causes the power medium having subsequently expanded again to enter into the moving power canals 17g, 17 17c within which the power medium is compressed again toward the inner guide body and passes then into the next inner guide pocket unit 33.

The inner guide pocket-unit 53 is equipped with the curved guide elements 53a and has the curved inner guide pocket wall 53b which guide the now further expanding f powe'r medium into the rotor power canals 171,.17k, 17:,

17h, which are moving past guide pocket unit 53. x From these power canals 1711, UL the power medium further expands into the following outer guide pocket unit 63 having the curved guide elements 63a and the further curved outer guide pocket wall 63b. Due to the curvature of the guide elements 63a and of the guide 'pocket wall 63b, the expanding power medium is conducted back into the moving rotor 1 and through its power canals 17m to 171 in the direction or arrow 65. While passing through these power canals 17m, 17q, 17r, the impulse of the power medium is still exerted against the walls of the power canals toward the ends of which the power medium is again somewhat compressed.

The power medium from the power canals 17m to 171' further expands into the following inner guide pocket unit 54 having the curved guide elements 54:: and the respective curved guide pocket wall 54b from where the power medium still further expands into the following rotor power canals with the result that the power medium is only capable of exerting negligible pressure and is allowed to escape through exhaust opening 30 into the atmosphere or a suitable receptacle, if desired.

While the gas finally escapes through said exhaust opening 30, the rotor power canals still receive an impulse which is caused by the reaction resulting from the characteristic curvature of the rotor power canals 17 and due to the opposed ends thereof.

Each time the power medium passes from the inner and outer guide bodies to the rotor and vice versa, an

additional impulse against the rotor takes place by way of either action or reaction.

Although the rotor is being rotatably moved, due to the action, reaction and expansion of the power medium. the rotor (for the purpose of explaining the conduct of the power medium through the inner and outer guide pockets and through the rotor and for the sake of simplifying a full understanding of the invention) is assumed I to be stationary with respect to these guide pockets.

It is self-evident that the turbine may be variously modified in that'instead of power canals in the rotor, power'ducts may be used which may form a unit, and 1 instead of guide pocket units with guide members, such with guide ducts, and instead of guide pockets, guide canals may be used in the housing 3 and drum 4.

If continuous flow of combustiblegas is used as the preferred power medium, elements subjected to explosion, or if steam or water are employed instead of gas, the

explosion chamber 46 and other parts as shown in Figs.

1, 2, 24, as well as the compression shutter 42 within the nozzle means 40 maybe omitted.

The number of the power canals 17 may vary' and their shape is preferably oblong, whereas the various guide pockets with the 'guide elements or members (or guide ducts or guide canals) are made according to the size of the turbine and are chosen according to the characteristics of the power medium employed and its ability of expansion.

In order to prevent the power medium from escaping from the' combustion or explosion chamber through the nozzle 40 into the rotor power canals before the power medium has reached its highest degree of compression so that it may be ignited at the proper time and brought to explosion, the compression shutter is normally closed, either by a spring or other suitable means in order to resist the predetermined pressure of the compressed power medium and opens only when its resistance is overcome by the force of explosion or other excessive pressure from the power medium which will overcome the predetermined pressure of the spring or other suitable means attached to the explosion chamber or to the pre-compression chamber.

If the resistance compression shutter or resistance compression valve 42 is opened and closed at predetermined intervals and timed with the ignition and discharge of the driving medium, it will be actuated by any appropriate means, such as eccentric or cam gears 43, 43a, as

for instance shown and employed for valves 44, 45, previously described.

It is preferred to carry out this feature of the invention in the manner shown more clearly in the enlarged embodiments of Figs. 5 and 6 where it will be seen that a pivotal shaft '71 to which the power operated or compression shutteris secured, carries a lever 72 (Fig. 5) upon which acts a spring member 73 in such a manner that compression shutter 42 (Figs. 1, 2, 2c, 2d, 5, 6, 11) is held normally in closed position, as illustrated in Fig. 2d and in dot-dash lines in Fig. 6, and will thus close the nozzle 40.

As soon as the explosion takes place within the explosion chamber 46, or if compressed gas alone is being employed, the impact of the exploded or expanding power medium, as the case may be, will move the compression shutter 42 into position illustrated in Figs. 1, 2 and 6 and will thus open the nozzle 40 to allow the passage of the power medium.

In order to avoid detrimental counterflow of the power medium during its passage through the rotor 1 and the inner and outer guide bodies, arrangements may be made in the guide pockets and/or in sections of the guide bodies in relation to the power canals 17 to prevent the moving power canals during their discharge periods from receiving a further quantity of power medium from said guide pockets.

To this end, sections 66, 66b, etc. of the inner rim part 3a of housing 3 and sections 67, etc. of the outer rim part 411 of drum 4 within or adjacent the outer and inner guide pocket units, seal the power canals 17 during a portion of the revolution of the rotor, thereby preventing any supply of said medium to those power canals which were not; yet completely emptied.

According to the modifications of the turbine structure shown in Figs. 4 to 10, the explosion (in the case of an internal combustion turbine) takes place in the rotor power canals themselves. In this instance, the explosion chamber 46 (Fig. 2d) of the discharge unit 38 may be dispensed with and the precompression chamber 47 (Fig/2d) is directly connected (not shown) to the nozzle 40 from which the fresh charge of the highly compressed power medium enters the power canals where the power medium is initially stopped or arrested by a compression shutter 76 which is hingedly secured at 77a where, if. desired, each power canal 70 meets a branch canal (Figs. 4 and 6). This compression shutter 76 serves the same purpose as a piston in a conventional combustion engine.

greases .Each power canal 70 contains .such a compression .shutter 76 whose a ctuation may .be effectuated by the centrifugalforce during rotative movement ofthe rotor. Therefore that portion 64 of the power canals between the outer rotor periphery and the compression shutter 76 (in closed condition) constitutes during the closure period an explosion chamber as explained as follows.

While rotor 6 9 (Fig. rotates in clockwise direction, the power canal 70 (Figs. 5, 6) movestoward thespark plug -or ignition means 74 (Fig. 5 The power medium in this explosion chamber 64 moves together with the power canals 70 to the position adjacent the ignition means 74 and is there ignited. As a consequence of the force of'the resulting explosion the respective compression shutter 7 6 is then moved into such a position in which it opens the power canal 70. Branch canal 75 connected to canal 70 is then closed by the compression .-shutter-76 (Figs. .4 and (Theexpansion of theexploded power medium causes the latterto move in substantially the same manner as described with reference to Figs. 1 and 2, namely, through the rotor, theinnerand outerguide bodies and parts. thereof.

-Shutter :76 is-retainedin the aforesaid position (Fig. 10) until thepower medium is fully expanded and the latter will-thenescapethrough an exhaust opening in the housing in the same manner as the power medium escapes through the exhaust opening 30 shown in Figs. 1 and 2, or through the exhaust opening 130 shown in Fig. 12. Obviously, this modification as shown in Figs. 4 to 10, may-alsobe provided with cooling canals, as hereinabove described.

Shutter--76, in 'tbisinstance, is retained-in its position of Fig. 1-0 by means of a hook 77 which 'is-fixedly secured toaeach shutter 76 and which engages with slot 78 provided in a control organ in the form of a rod 79 (Figs. 8,9, 10). 3 Each rod '79 is radially slidably supported with respect to each power canal 76 and is adapted to be engaged ateither end by oneof the cams 80 disposed at the outer periphery ofthe drum 4 orby cam 81 arranged at the inner periphery of the housing 3 (Fig. 7).

80 pushesduring rotation of the power canal 70 rod 79 outwardly toward the housing 3 so that the respective rod 79 engages a respective hook '77, as may be depicted in Figs. 4 to 10, Whereas .cam 81 pushes the rod 79 during rotation of the powercanal 70 toward the drum .4 so thatthe rodsrelease the respective hooks 77, as

may be realiz ed from Figs. 6 and 8.

The shutters 76 t hus,released cannow close the .main

power canals 76Lby means of the centrifugal force acting upon the shutters 7 6. The portion of the power meditnn having passed all stages of the rotor but having not escaped yet .t hrough the exhaust opening .of .thernain power canal 70 escapesthrough the exhaust opening 30a of the branch canal 75 (Fig. 8) in the; manner that the ,exhaust gas leaves the rotor through the open branch canal 75, while the shutter '76 is again in closingposition within the power canal.

If preferred, thecxhaust gas may leave .by way of the power canal 70 itself and then through an exhaust opening located .withinthe adjacent outer gu de body or housing in thesame manner as the power medium escapes through the exhaust opening 30 located within the -adjacent outer guide body or housing shown in Figs. 1 and 2, or through the exhaust opening 130 shown infig.

'12, in whichcase the engagement ofthehook 77 with slot 78 of rod 79 is to be properlyatimed so as .to keep during the period of explosion and .expansionthe main powercanal .70 open. and thebranch canal .75. closed.

,In Figs. ,6 and -8 shutter 76=is illustrated intheposition .during .which. the .power. canal 70;,has been .closed and the branch canal 75 opened, .aftenhook .77 .has.been

. releasedfrom -its.engagement with..-sjlot 7.8 of. the sli dably supported control rod .79by outer .cam .81. 'lhelatter -is alternately, directed through the rotor canals.

cam 81 is indicatedinFig. 7.at. the outer guide body. .Figs. 4 andlO shutter 76'is illustrated in the positiondur- .the mainpower canal .70 is open, the branch canal 75 is closed by shutter 76 retained by means of hook 77 en gaged with slot 78 providedin the slidably supported .controlrod 79 which latter has been moved during ,ro- .tationof the. rotor towards the outer guide body by inner Siam sfl-indicatedin .Fig, lat the inner guide .body.

Fig. 8 shows that the right side of the'topof the open branch canal 75 is vacant, meaning that no portion of the control rod 79 covers the right'side of .the'top of the branch canal 75, whereas the left .side ofthe top of the branch canal'75 is in part covered by a portion of the control rod 79.

Further it is shown in Fig-,8 that the distancebetween the right end of slot 78 ofncontrol rod 79 and the center of hinge 77a is larger than in Fig. 10,,also.that the left end of control :rod 79 is even or level with the left .hand boundary line of Fig. ,8, indicating that control rod 79 on its left end has been pushedby cam 81 located on the outer guidebody (Fig. 7) toward the inner'guide body, thereby releasing compression shutter 76 (Fig. v8)

having been engaged by meansof its hook 77 with slot 78 .of control .rod 79 (Fig. 10) and herewith opens main .power canal (Fig. 8).

Fig. 10 shows in comparison with Fig. 8, that the right side of the top .of theibranchicanal is in partcovered by :a portion. of'control .rod .79, whereas the left side of the top of the open branch canal 75 ;is vacant, showing that no portion of. the control .rod 79covers the left side of the topof the open. branch canal 75; Fig. 10 also shows that the distance betweenthe center of the hinge 77a .and the right endof fslot .78 is smaller than in Fig. 8; italso shows thatv the left end of control rod 79 protrudes beyond the left handboundary line .of Fig. 10 indicating that control rod 79 on its right end has been pushed by cam located on the inner. guide body (Fig. 7) towards .the outer .guide body therebyengaging hook 77 of compression .shutter 76 with slot 78 of the control rod 79 and simultaneously opening power tube 70 (Fig. 10).

,Duringthe period of explosion and expansion, the power-medium imparts its main driving impulse upon the .ro'tor.69 in a mannersi milar to that described with .r'especttorotor 1."

,In turbines. without cooling canals (Figs. 11, 12'), any suitable means, such as openings .132 of various dimensions (Fig. 1.1) or openingsof equal dimensions may be provided for within theouter rim part 4a of the inner "guide-bodyoridrum 104 (Fig. 11) to allow and regulate theincoming supply of coolingair or other cooling mediumalonglandwithin the power canals 117 for thepurpose to .prevent excessive differences in temperatures withinthe power canals.

-In. theembodiment shown inFig. 11, the rotor includes a predetermined numberof full length and of shortened canals, respectively, towardthe outer rotor peripheryprovidingthereby receiving chambers which are enclosed "by the respective rim parts of the outer guide body. From such receiving chambersgas is directed through the rotor canals. .Receiving chambers may'in thepsarne way be providedforlat opposed sides of canals whichreceiving chambers will be enclosed bythe. respective rim parts of the inner guide. body. From the receiving chambers gas is directed, and if provided for, gas .and cooling medium The receiving chambers .counteract partially the detrimental etfect .r esultingdue tothe highispeed o-f.the rotor. The

power medium is caused to expand continuouslyfromone 11 rotor stage section to another rotor stage section and through the outer guide body stage sections 118, 119 and 120 and the inner guide body stage sections 122, 123, 124 and 125. a

The cooling medium entering through said openings 132 in drum 104 into the rotor power canals 117 escapes from the latter through openings 130 of housing 103 into the atmosphere or any suitable receptacle (not shown), thereby cooling hot power canals 117.

In accordance with the above it is well understood that deviations and changes may be made from the embodiment herein set forth without departing from the spirit of this invention, for instance, the injection nozzles may also be located at the inner rotor periphery, so that the injection of the power medium may be also applied from this direction to the rotor.

Having described the invention, what is claimed as new and desired to be secured by Letters Patent, is:

1. A turbine of the character described comprising a shaft, a rotor connected with said shaft and for rotation therewith, a sleeve surrounding said shaft, an outer guide body, an inner guide body, said rotor being positioned intermediate said outer guide body and said inner guide body, respective means provided on said rotor sealingly engaging said outer guide body and said inner guide body, first supporting means for said rotor connected with said shaft, second supporting means for said rotor journaled on said sleeve, nozzle means for supplying a power medium to said rotor, said rotor being provided with a plurality of stage sections, said stage sections permitting continuous expansion of said power medium and being arranged successively to each other, each stage section being substantially the same distance from said shaft, each rotor stage section including power canals different in number but equal in radial length, outer guide pocket units and inner guide pocket units circumferentially positioned, respectively, at opposed ends of said power canals, said outer guide pocket units and said inner guide pocket units communicating with said power canals, respectively, during rotation of the latter, and movable means in said power canals actuated by the centrifugal force of said rotor to close said power canals and urged to open said power canals, when the expanding force of said power medium overcomes said centrifugal force.

2. A turbine of the character described comprising a shaft, a rotor connected with said shaft and for rotation therewith, a sleeve surrounding said shaft, an outer guide body, an inner guide body, said rotor being positioned intermediate said outer guide body and said inner guide body, respective gas trap sealing extension means provided on said rotor, sealingly engaging gas trap grooves within said outer guide body and said inner guide body, first supporting means for said rotor connected with said shaft, second supporting means for said rotor journaled on said sleeve, nozzle means for supplying a power medium to said rotor, said rotor being provided with a plurality of stage sections, said stage sections permitting continuous expansion of said power medium and being arranged successively to each other, each stage section having substantially the same distance from said shaft, each rotor stage section including power canals different in number but equal in radial length, outer guide pocket units and inner guide pocket units circumferentially positioned, respectively, at opposed ends of said power canals, said outer guide pocket units and said inner guide pocket units communicating with said power canals, respectively, during rotation of the latter, and movable means in said power canals actuated by the centrifugal force of said rotor to close said power canals and urged to open said power canais when the expanding force of said power medium overcomes said centrifugal force, each portion of said power canals positioned between said outer, guide body and said movable means formingman explosion chamber in closed position of said movable means in said'power canals.

3. A turbine of the character described comprising a shaft, a rotor connected with said shaft and for rotation therewith a sleeve surrounding a portion of said shaft, means connected with said rotor and journaled on said sleeve for rotation thereabout, an outer guide body, an inner guide body, said rotor being positioned between said outer guide body and said inner guide body, respective gastrap sealing extension means provided on said rotor and engaging gastrap grooves within said outer guide body and said inner guide body, nozzle means supplying a power medium to said rotor, said rotor being divided into stage sections each of said rotor stage sections including a plurality of power canals affording enclosed condition of power medium while passing through the power canals during rotation thereof, said stage sections permitting continuous expansion of said power me dium and being arranged successively to each other, each stage section having substantially the same distance from said shaft and including predetermined numbers of interchangeable power canals, each of said power canals being equal in radial length, said outer guide body including a predetermined number of outer guide pocket units, said inner guide body including a predetermined number of inner guide pocket units and positioned substantially opposite said outer guide pocket units, said outer guide pocket units and said inner guide pocketunits extending along a circumferential portion of said outer guide body and of said inner guide body, respectively, and means facilitating introduction of a cooling medium into said chamber means for directing said cooling medium parallel to the axis of said shaft, the remaining circumferential portion of said inner guide body and of said outer guide body including respective passageways, the cross sections of said passage ways in sequence progressively increasing and in sequence progressively decreasing in said remaining circumferential portions of said inner guide body and of said outer guide body and permitting a flow of said cooling medium from one end to the other end and lengthwise of and through said power canals when the latter are moved for position in said remaining circumferential portion.

4. A turbine of the character described comprising a shaft, a rotor connected with said shaft and for rotation therewith, an outer guide body, an inner guide body, said guide bodies being provided with respective rim parts, said rotor being positioned between said outer guide body and said inner guide body, radially extending power canals carried by said rotor for directing a power medium, respective means for sealing said rotor relatively to said outer guide body and said inner guide body, gas sealing grooves at said rim part of said outer guide body and said rim part of said inner guide body, extension means fixed to said rotor and provided adjacent opposed ends of said power canals, engaging said gas sealing grooves to form gastraps therewith, nozzle means supplying a power medium to said rotor, a plurality of power stages circumferentially arranged about the outer and inner rotor periphery, each power stage including an outer guide body stage section, a rotor stage section and an inner guide body stage section, said power stages being arranged successively to each other, whereby said power medium is caused to expand continuously from one power stage to another power stage, means movable within said power canals and actuated by the centrifugal force of said rotor to close said power canals, said movable means being urged to open said power canals, when the expanding force of said power medium overcomes said centrifugal force, cam means disposed at said outer guide body rim part and at said inner guide body rim part, latch means attached to said movable means, and means actuatably by said cam means to operate said latch means for regulating opening and closing periods of said power canals, respectively. p

5. A turbine of the character described comprising a shaft, a rotor connected with said shaft, a sleeve sur- 13 rounding a portion of said shaft, means journaled on said sleeve and connected with said-rotor to facilitate r'otationtof .said rotor about saidlsle'eve said-sleeve additionally supporting and securedlytstabilizing said rotor,

an outer guide body, .an inner guide body, .said inner guide body being fixed to said sleeve and mounted thereon for support, means connecting said sleeve with said outer guide body, said rotor being positioned between said outer guide body and said inner guide body, respective means for sealing said rotor relatively to its outer guide body and its inner guide body, nozzle means supplying a power medium to said rotor, said outer guidebody and said inner guide body including each a predetermined number of outer guide body stage sections and of inner guide body stage sections extending in circumferential direction along at least a portion of the outer and inner rotor periphery, respectively, said rotor comprising a predetermined number of circumferentially positioned rotor stage sections, each rotor stage section including power canals different in numbers but equal in radial length, said power medium is caused to expand continuously from one rotor stage section to another rotor stage section and through the outer guide body stage sections and inner guide body stage sections.

6. A turbine of the character described comprising a shaft, a rotor connected with said shaft and for rotation therewith, a housing, an inner guide body, said shaft extending through said inner guide body and projecting there beyond, said rotor being positioned intermediate said housing and said inner guide body, respective gas trap sealing extension means provided on said rotor sealingly engaging gas trap grooves within said housing and said inner guide body, said housing including escape openings, said inner guide body including passage openings, means suporting said rotor and connected with said shaft, nozzle means for supply of power medium to said rotor, said rotor being provided with a plurality of stage sections, said stage sections permitting continuous expansion of said power medium and being arranged successively to each other, each stage section being substantially the same distance from said shaft and including power canals equal in radial length, the opposed ends of each power canal being angularly directed toward each other and being arranged opposed to the direction of rotation of the rotor, the remaining portion of said power medium rotor canal means are curved in the direction of rotation of said rotor.

7. A turbine of the character described, comprising a rotatable shaft, a rotor, a sleeve surrounding said shaft, a housing for said rotor including passage means in communication with said rotor, an inner guide body positioned between said shaft and said rotor and including passage means leading to said rotor, a chamber between said inner guide body and said shaft, respective gas trap sealing means provided on said housing and said inner guide body, first supporting means for said rotor connected with said shaft, second supporting means for said rotor journaled on said sleeve, at least one of said rotor supporting means being provided with passage ways for guiding cooling means through said chamber said inner guide body to both said passage means and to said rotor, and nozzle means for supplying a power medium to said rotor, said rotor being provided with a plurality of stage sections constructed to permit continuous expansion of said power medium and arranged successively to each other, each stage section being substantially the same distance from said shaft to insure uniform strain and pull caused by centrifugal force throughout said rotor.

8. A turbine of the character described comprising a shaft, a rotor connected with said shaft and for rotation therewith, a sleeve surrounding a portion of said shaft, said shaft being rotatable within said sleeve, a housing, an inner guide body, means supportedly connecting said sleeve with said housing, said rotor being positioned intermediate said housing and said inner guide body, respeci e .s t ap sea in ex en io me n pmv rd 0 1' lsa o or ns y. e a n a dh il in an sai in e ui y, i inner 8 d "ib9 lYlb 8:PIQ Skd w th P sage openings, said housing being provided with escape openings, .said ,rotor vbeing spacadifrom saidshaft providing therebetween a chamberfor-airsupply, first supporting means for said rotor connected with said shaft, second supporting means-for said rotor-journaled on said sleeve, said housing enclosing said first and second supporting means for said rotor, said sleeve additionally supporting and securedly stabilizing said rotor, no zzle means for the supply of "power medium to said rotor, guide pockets circumferentially positioned along said rotor, said rotor being provided with a plurality of stage sections, said stage sections being constructed for permitting continuous expansion of said power medium and being arranged successively to each other, each stage section being substantially the same distance from said shaft, each rotor stage section including power canals equal in radial length, and means provided in the guide pockets relative to the power canals for avoiding detrimental counterflow of power medium during its passage through the turbine, said chamber communicating through said passage openings with said rotor and said escape openings.

9. A turbine of the character described comprising a shaft, a rotor connected with said shaft and for rotation therewith, a sleeve surrounding a portion of said shaft, means connected with said rotor and journaled on said sleeve for rotation thereabout, an outer guide body, an inner guide body, said rotor including more than one row of power canals arranged in superposed position for rotation with said shaft, said rotor being positioned between said outer guide body and said inner guide body, said inner guide body being spaced from said sleeve to provide a chamber for supply and passage of a cooling medium, gas trap sealing extension means provided on said rotor and engaging gas trap grooves within said outer guide body and said inner guide body, nozzle means supplying a power medium to said rotor, said rotor being divided into stage sections, said stage sections permitting continuous expansion of said power medium and being arranged successively to each other, each section being substantially the same distance from said shaft and including predetermined numbers of said rows of power canals, said outer guide body including a predetermined number of outer guide pockets, said inner guide body including a predetermined number of inner guide pockets and positioned substantially opposite said outer guide pockets, said outer guide pockets and said inner guide pockets extending along a circumferential portion of said outer guide body and said inner guide body, respectively, means facilitating introduction of a cooling medium into said chamber, and means for directing said cooling medium parallel to the axis of said shaft, said chamber permitting the flow of said cooling medium from one end to the other and lengthwise of the power canals, said outer guide body and said inner guide body being provided with openings communicating with said chamber and power canals to permit automatically entrance, flow and escape of said cooling medium through said power canals as a consequence of suction produced due to the rapid revolution of said rotor, said inner guide pockets and said outer guide pockets of which one portion is a receiving section and another portion a delivery section for the incoming circulating power medium are so designed that the diameter of said receiving section is accordingly measured in proportion to the volume of the circulating power medium in order to provide smallest back pressure against the incoming power medium expelled from the rotor power canals, and the diameter of the delivery section is in comparison to the receiving section in proportion larger in order to provide possible highest pressure of the power medium returning to the power canals from the delivery section of the outer guide 15 pocket in order to overcome the centrifugal force executed by the revolving rotor power canals against the power medium entering the latter.

References Cited in the file of this patent 5 UNITED STATES PATENTS 787,907 Farwell Apr. 25, 1905 891,643 Trow June 23, 1908 976,236 Weiss Nov. 22, 1910 m 1,008,576 Ahlquist Nov. 14, 1911 1,088,761 Anderson Mar. 3, 1914 1,237,639 Hachenberg Aug. 21, 1917 15 Guerini June 14, 1921 Holzwarth Oct. 15, 1929 Sedimeir May 9, 1935 Holzwarth Sept. 27, 1938 Muller Oct. 26, 1943 Theimer Oct. 3, 1950 Telhizoif Nov. 28, 1950 Hottel et a1 Aug. 21, 1951 FOREIGN PATENTS Great Britain 1905 France 1912

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