US1313058A

US1313058A - Reversible turbine

Info

Publication number: US1313058A
Authority: US
Publication date: 1919-08-12
Anticipated expiration: 1936-08-12

Description

A. BONOIVI.

REVERSIBLE TURBINE.

APPLICATION FILED DEQZG 191B.

Patented Aug. 12, 1919.

4 SHEETS+SHEET l.

(A, BONOII/I.

REVERSIBLE TURBINE.

APPLICATION FILED 050.26. I9I8.

1,313,058,` PatentedAug. 12,1519..

. 4 SHEETS-SHEET 3;

LLC//f A TTH/VEYS AK BONIVI.

REVERSIBLE TURBINE.

APPLICATION FILED DEc.26. IQIII.

1,313,058, Patented Aug. 12,1912).

4 SHEETS-SHEET 4.

A Tram/E rs ALFRED IBONI'OM, OF PATERSON, NEW JERSEY.

. REVERSIBLE TURBINE.

Specication of Letters Patent. Y Patented Allg. 1,2, 1919.

Application filed lDecember. 2 6, 1918. Serial No. 28,3.62.

To all whom t may concern.'

Be it known that I, ALFRED BoNoM, a citizen of France, and a resident of Paterson, in the county 0f Passaic and State o-f New Jersey, have invented a new and Improved ReversibleTurbine, of which the following is a full, clear, and exact description. i

This invention relates to high speed fluid turbines and has particular reference to re.- versiblesteam turbines.

Among the objects of the invention is to provide a direct action and reaction turbine comprising a plurality of oppositely moving or movable members or rotors so designed and constructed as to possess maximum efficiency with af minimum amount of, weight of material and expenditure of steam or fuel.-

Another object of the invention is to provide improyed labyrinth paekings between all-relatively movable parts subjected to the steam ressure.

Anot er object of the invention is to -proyvide for delicacy of adjustment of the labyrinth packings.

Another object of the invention is to provide for a. perfect counterbalance of the ex pansive force vof the driving fluid in every direction whereby the rotors are relieved from end thrust.`

A 'still further object is to provide compound rotor members which may be described as inner and outer rotors, said rotors involving two stages, one for high pressure and the other for low pressure, and the inner rotor comprising a disk.' member pertaining tothe high pressure stage and another disk member pertaining t-o the low pressure stage,

each disk member being opposed by a. simi-V lar disk member of the outer rotor.

Another object of the invention is to'improvel the specific constru'ctionf of the rotors'- with respect to the manner of mak-ing' the blade structures, and the means for supportv ing them upon the disk elements. V

A still further object is to provide4 oppositely movable sets of blades each set constituting a circular series of blade elements with flexible supporting means therefor ca rw lried by one of the disks, adjacentA sets of blades of one rotor being interspersed with corresponding sets of blades carried by the .opposite rotor and with peculiar labyrinth packings between each set of blades and the next inner or outer s'et carried by the 0912 site disk.

' tion.

Anotherl object of the invention is to provide a compound turbine engine having high pressure and low pressure stages, and with means causing pressure fluid to passV outward radially through respective stages.

With the foregoing and other objects in view the invention consists in the arrangev mentand combination of parts hereinafter described and claimed, and while the invention is not restricted to the ex'act detailsv of construction disclosed or suggested herein,

still for the purpose ofillustrating a practical embodiment thereof reference is had to the accompanying drawings, in which like reference characters designate the same parts in the several views, and in which- 'Figure 1 is a vertical central longitudinal section of the upper half of a steam turbine made in accordance -with my invention.

Fig. 2 is an enlarged vertical longitudinal section of a portion of the high pressure stage structure. v

' Fig. 3 is a similar view of the low pressure stage structure. l

. -F ig. 4 is an enlarged longitudinal section pressure labyrinth bearing packi'g. v5 is a similarview of the preferred form of the 'low pressure labyrinth bearing packing and Fig. 6 1s a modifiedform of transmissionv gearing between the main shaft .and the sleeve on .which 4the rotors are respectively connected.

Referring nowmorejspecifically'to Fig. 1

Athe main shaft isindicated at 10 and fixed "is a 'beveled gear 14, and also fixed to the shaft at the end opposite from the gear 14 -is a clutch member 15 of any suitable type.

The outer rotor 16 comprises three

disk members

17, 18, and 19, the member 17 being opposed to the disk 12 of the high pressure stage construction, and the disk 19 being opposed to the low pressure disk 13. The disk 18 is located between the two stages and provides a means for the return of the pressure Huid to a position adjacent to the shaft whence it will act through the low pressure stage in a radially outward direc- The outer rotor comprises also4 two

sleeve extensions

20 and 21 journaled either directly upon the main shaft 1Q, or upon rality of outwardly this shaft through suitable bearing bushings 22 and 23 respectively. Fixed in any suitable manner to the end of the sleeve 20 remote from the rotor disk is a gear 24 opposed to the gear 14 and between which are interposed a plurality of beveled idlers 25 each journaled upon a fixed support 26 by means of a multiple bushing bea-ring 27. f

Surrounding and inolosing the rotois is a stationary casing Y28 having a steam inlet 29 and an exhaust dome or drum 30. The inlet 29 has a restricted passageway' 31 lead` ing into the-hollow hub 32 of the high pressure stage structure whence the steam is delivered radially outward through an annular outlet 33 into driving coperatien with alternately arranged blades v341 and 35 carried respectively by the inner and outer rotors. The flow of the steam thus is radial and outward from the hub 32 while the expansive force thereof is exerted against the two sets of

blades

34 and 35 circumferentially causing the rotors to which these blades are connected to rotate in opposite directions, either actually or relatively. From the periphery of this high pressure stage structure .the steam passes throughthe passageway 36 between the disks 12 and 18 to the hollow hub 37 of the low pressure stage structure, whence the steam again flows radially outward so as to act against the reversely arranged sets of

blades

38 and 39 carried respectively by the

disks

13 and 19 of said low pressure stage structure, the steam acting as before described to expand circumferentially while-it flows radially-outward .and is delivered finally into the exhaust dome 30.

One of the serious problems to be met in perfecting a steam turbine is to insure sub-r4 stantially free rotation-of the rotors with a substantially steam tight packing Isystem to prevent leakage of steam and consequent loss of efficiency. 'llhis problem I have solved by the provision o-f a new and elficient system'of labyrinth packings which constitutes one of the important features of this invention. Referring now therefore more specifically to-F ig. 1t I show the high pressure packing devices as comprising mating pairs of inner and

outer rings

40 and 41 having screw threaded engagement respectively with a sleeve 42 mounted adjustably upon the hub extension 32 from the disk 17 and the hub extension 28 constivtuting a portion of: the 'stationary casing 23.

are preferably, exactly alike except for av slight' dierence in` diameter.

- The flange 40d is the largest and is provided with a pluprojec-ting iins 09. Each of the flanges just described has a lat- 'erally projecting fin 0f the free edgesvof which all lie in the saine plane perpendicular to the axis of the rotorto which they I pertain. Again', each ange has an inwardly ofthe corresponding flanges 40e and 40d of the mating ring. The-flange 41d is shown provided with a pair of inwardly projecting fins 41e, the points or edges of which have close relation to the outer surface of the hub 40a. Againyeach flange 41C and 41d has a laterally projecting fin -tlf all of the edges of which liein the same plane and in close proximity to the inner radial wall of the web 40b'of the mating ring, while the edges of the fins 40f of said vlatter ring have 'similar proximity to the inner radial wall of the webv'tlb. While each of the flanges 40C or 41' has a smooth cylindrical ontersurface the inwardly projecting fin of the next outer flange has close contact with said smooth Surface, that is to say, the fins 40g of the ring 40 bear respectively upon or close to the smooth exterior surfaces of the flanges tlc and 41d of. the ring all, while the fins 41g of the flanges illc bear respectively upon the outer surfaces of the flanges t0, and the'fins 41e have similar bearing upon the outer cylindrical surface of the hub 40a. Obviously each of the-se ring members is made so as to be perfectly circular and symmetrical with respect to the axis of the rotor to which it pertains, and hence all of the respective flange and linfeatures are precisely alike and interchangeable so that when each mating pair of rings -lO and `adjustment of the rings 40 with respect to the several mating rings 41 may be effected bythe rotation of the sleeve -l2 around the extension support 32r` and the position of the sleeve -12 may be locked after adjustment by means of a set screw l2. There are provided i'n t-he form shown in Fig. 4 at leastv fifteen lines of contact between each two relatively movable parts making ilp the system. It is furthermore to be noted that the line or course through which the steam would be obliged to pass to escape through this labyrinth is exceedingly circuitous,1naking it a practical impossibility for any leakage to resul-t even'though the actual contact between adjacent and relatively movable parts is slight or entirely wanting. Furthermore this exemption from leakage "is multiplied as many times as .there arey pairs ofmating rings throughout the packing. lVhile each ring l0k may abut at its hubsquarely against the next simil-ar ring so that no steam can escape between any of these rings and the sleeve -l2 on which they are litted,-so also the rings 41 have steam tight fit in the hub extension 28 and abut squarely against one another'. It, of

course, is understood that between each pair mulate in the labyrinths will add to thediiiiculty for the steam to escape, but will add no 'appreciable resistance to the rota.- tion of the rotors; These packing rings 40 'and 41 when put in place are locked by means of adjustable abutment rings 43and 44yrespecti'vely which hold the packing rings in place with any suitable degree of frictional contact with the lother adjacent n Fig. 5 I show in detail the construction of labyrinth packings that may beI used in connection with the low pressure stage construction, such packings being indicated at 145 at three different parts in Fig. 1. This type of bushing comprises mating series of -mner and outer packing rings 4'6 and 47 1espectively coperating with a sleeve or bearing bushing 48 through a sleeve 49, with respect to the rings 46, and with an outer member 50 Which at the central portion of Fig. l is indicated as constituting a flanged extension from the intermediate disk 18 of the outer rotor, which .the member 48 is indicated as constituting a flanged extension of the disk 13 of the inner rotor.

support 48 serves to cause the longitudinal adjustment of the mating rings 46 and 47 in a manner similar to the adjustment o-f the rings 40 above described, and this sleeve 49- ential flanges 46c projecting laterally from' opposite sides of the web 46", and an outside double flange 46d. Each flange 46d has a plurality vof outwardly projecting fins 46e and a laterally projecting fin 46E, and also inwardly projecting finsK 46g. .The vflanges 46C. have laterally projecting contact edges 'or fins 46t and inwardly projecting edges or fins 46g similar to those features of the ianges 46d. A

Each packing ring -47 comprises a hub portion 47a, a central web- 47h, and laterally projecting flanges 47 c and 47d. The flanges 47 d have a plurality of inwardly projecting fins 47e, and eachof the lateral anges has a lat- The adjustment of the sleeve 49 around and along the erally projecting fin 47f;. also the Hanges 47C. have inwardly projecting fins 47g.

l/Vhile the hub portions 46L and v47a of. these members have threaded connection respectivel-y with the sleeve 49 and hub exten- 70 sion 50 the directly opposite surfaces of these parts have smooth cylindrical surfaces with which the li'ns 4"e and 46e of the adj acent parts coperate respectively. Likewise the fins 46g and 47g coperate respectively 75 with the smooth outer surfaces of the flanges 47c and 46c respectively. Also the laterally projecting fins or edges 46t and 47 f. coperate respectively with the radial webs-47b and 46". As in the packirrgs for the. high pres- 80 sure stage structure of Fig. 4, it -is obvious that the path of escape-of steam of this packing of F 5 is so circuitous that it is practically impossible for any 1oss of efficiency from this cause even though ,the acnoted that the

disks

12 and 17 of the high pressure stage lstructure are so disposed with respect to each other that there is a tendencyY for the 'expansive force of the steam to "act to cause the separation of the disks in a di- 100 rection parallel to the axis of the shaft 10, and obviously this force is exerted equally in two opposite directions. Likewise the expansive force of the steam in the low p'res- Y sure stage structure tends to force the disks/(1765 13 and 19 in opposite directions parallel to theshaft and with equal degrees of force. In this connection it is to be noted particui llarly that the diameter of the disks of the respective stages is calculated according to the expansive force of ,the steam while passing through said stages. That is to say the diameter of either

disk

12 or 17 is universally proportional to the steam pressure acting thereon. Since, therefore, the

disks

12 and 13, constituting the linner rotor, are

i coupled together they constitute a rigid unit,

and likewise the

disks

17 and 19 are coupled together and constitute the outer rotor.- By making the disks 18 and 19 materially larger in diameter than

lthe disks

12 and 17 the .lower pressure of the steam acting longitudinally therebetween will 'have the effect of counterbalancing the tendency of the high pressure steam in the high pressure stage to cause longitudinal movement of either of the disks-17 or 12.

Any suitable lateral bearings may be provided for the main shaft `10A and sleeve extensions'orhubs cooperating therewith or 13o therearound. By reference, however, to Fig. 1 it will be noted that I provide an adjustable tapered bearing bushing 51 having a similarly shaped brass 52 cooperating with a tapered portion 10a of the main shaft. The bushing 51 has an end extension and a vterminal fiange 53 through which adjustment screws 5i project into the end portion 550i the hub extension 21 to the outerl rotor.- Hence by the turningof these screws the bearing bushings 51 and 52 maybe adjusted to compensate for wear. Other compound bearing. members 56 are arranged between the outer surface of the extension 9.1 and The sleeve extension 55 includes also clutch teeth between which and the teeth of the clutch member 15 a shiftable clutch collar 59 coperates so as to couple the shaft extension 10, directly to the shaft 10 through

clutch members

15 and 59 or to connect th'e shaftl extension 10 with the outer rotor through the clutch members59 and 55.

Referring now more specifically to Figs. 2

and .3 for a further description of. the propelling" blades, 6 0 indicates the. type of flexible ring connection I prefer to use between the blades 35 and the high pressure' disk 17.

Each of these rings has an anchorage por-` tionnbase 61 and a relatively slender neck portion 62 between the same and the ring 60. The otherside of the steam space and parallell to thering ,60 is a companion floating ring" 63 of the same diameter as the ring 60. The v,blades 35 are connected up in circumferential series and are fitted in the rings and '63 by any suitable interlocking means such as dove-tailed tenons and grooves, and are finally secured therein by means of fingers 6s and 65 fixed to the

rings

60 and 63 respectively. With respect to the disk 12 I provide rings. '66 each having van anchorage base 67 and afiexible neck connection 68. Opposite each of these rings 66 is a companion floating ring 69 and between the rings 66 and'69 are locked a series 'of blades 34 by means of fingers 70 and 71 fixed to the

rings

66 and 69 respectively. Each ring base 61 or 67 1s provided with a plurality of laterally projecting concentric contact fins 72 which coperate with the

mating floating ring

69 or 63 of the Vopposite set of blades respectively. Between each pair of concentric fins 72 is a fin 73 projecting laterally outward from the

mating iioating ring

69 or 63 respectively. Thus it-will be seen that each pair of mating base and oating rings constitute a packing labyrinth serving' to prevent the escape of steam in such a direction as would interfere with the efficiency of the machine. y

In Fig. 3 I/show a detail of the blades for the low pressure stage construction. In this connection for the 'blades 38 I provide rings 7& having bases 75 with fiexibleeneck con- :sections 76. Opposite each ring vis a companion floating'ring 77 which coperates directly with the base 78 of the ring `v`7 9. located next thereto inward. The

parte

78 and 79 are connected by a flexible neck 80. Opposite 'each ring 79 is a oating ring 81 which coperates in turn with the base 75 of the next inward series of blades. blades 38 are held tothe rings 74 and 77V by means of dovetailed interlocking connections and detachable fingers 82 and 83 respectively. f Likewise the series of blades 39 are anchored to the

rings

79 and 81 by .interlocking connections and detachable fingers S4 and .85 respectively. The rings in this form of the invention are of a simpler nature than those in Fig. :2, having 'a lower number of labyrinth ns 86. The iexibility The of the

necks

62, 68, 76, and 80 provides for the accommodation of the several series of blades to variations of expansionl due to changes in temperature, and also insuring the accurate' centering of the several annular series of blades automatically due to the high speed of rotation.

Fig. 6 .shows a slight modification in de` sign of bevel gearing between theAtwo rotors. In -this form the shaft 10 has a bearing in the hub portion of the gear`24 and te the Aend of the shaft is secured a similar gear 14. Between these two gears are arranged a circular series of idlers 25 each mounted upon a stationary stud 27 constituting a part of or anexten'sion from the stationary bearing box 37. Each bearing or Aset of bearings has an oil inlet pipe 88 whereby complete circulation of oil may be observed, thedischarge of the .oil from the bearing being through a large duct 89 at the bottom "of the bearing box. Another delivery pipe for oil is shown at 90 along the inner end of the bearing box adjacent to the sleeve extension 20 to which the gear 24; is attached. One or more rings 91 are fixed to the shaft and serve to deflect the oil whereby the creeping thereof along the shaft beyond the bearing box is permitted.

I claim:

1. The herein described compound steam turbine comprising an inner rotor and an outer rotor, the inner rotor comprising a high pressure disk and a low pressure disk,

the outer rotor comprising a high pressure disk coacting with the first mentioned Ahigh pressure disk, a. low pressure disk coperatng with the aforesaid low pressure disk,

rigid connections between the aforesaid disks oA the outer rotor, and athird disk extending between the two disks of the inner rotor,

means supporting the two rotors'v for inde-v pendent rotation in relatively opposite directions, and means to cause the flow of motive fluid outward radially between the vtwo sets of cooperating disks.

2. In a compound steam turbine, the combination of an inner rotorcomprising high pressure and low pressure disks, an outer to flow radially outward between one pair of disks and thence subsequently radially outward through the other pair of disks.

3. The herein described compound steam' turbine comprising a shaft, an 'inner rotor 'fixed thereto and comprising a plurality of blade carrying disks, an outer rotor supported for rotation .around ,said shaft in a direction opposite from the rotation of the inner rotor, the outer rotor comprising a plurality of blade carrying disks coperating each to each with the aforesaid blade carrying disks, and means to cause the steam to pass radially outward between each pair of coperating disks in succession.

4. The herein described compound steam turbine comprising av high pressurestage and a low pressure stage,each stage com'` prising a pair of coperating blade carrying disks, and means to cause the steam to pass radially outward through the 'blades of the high .pressure stage and thence raf dially outward through the blades of the low pressure stage, the two stages being coaxial but one being arranged at the side of the other. i

5. In a high 'speed fluid turbine, the combi-v nation 0f two coaxial spaced disks representin independent rotors, a succession of radia y spaced blades and means connecting them to each disk, the blades of one disk being arranged in alternation with those of the opposite disk, the supporting means for each series of blades comprising a pair of coaxial rings of the same diameter, one oftherings` being floating, and an 'attachment base for the other ring of a different diameter, the

next adjacent series of blades of the other disk being approximately of the same diameter as I`said attachment base and lying adjacent thereto.

6. In a high speed steam turbine, the combination of a pair of coaxial spaced disks Arepresenting independent rotors, a radially disposed successionof spaced series of blades for each rotor, the series of blades for one vdiameter as the alternate blades of the other disk.

7. In a high speedsteam turbine, the combination of al main shaft, a sleeve journaled for rotation therearound, a pair of rotors connected respectively to the shaft and the sleeve, an ad]us`table tapered bearing surrounding the 'shaft and connected to the sleeve to take up for wear, and means cooperatin control t e actualrotation of the'shaft and sleeve. l

8. In a compound' steam turbine, a pair of rotors adapted to operate in relatively opposite directions, each rotor comprising a high pressure disk and a Alow pressure disk coperating respectively with similar disks of the other rotor, and means to support said disks so that the pressure between the high pressure disks will be exerted equally in opposite directions, while the pressure between the lower pressure disks will likewise beexerted in opposite directions.

9. In a compound steam turbine, the com,

'the steam at Whatever pressure acting with the shaft and the sleeve to y against any disk to be reacted by the steam pressure in the opposite direction against theother disk of the same rotor whereby a perfect counterbalancing eiect is produced irrespective of the variations in steam pressure while passing through the turbine.

" ALFRED BONGM`