US2190109A

US2190109A - Low pressure steam injector

Info

Publication number: US2190109A
Application number: US152729A
Authority: US
Inventors: Tinker Walter Howard
Original assignee: GEORGE A BALL
Current assignee: GEORGE A BALL
Priority date: 1937-07-09
Filing date: 1937-07-09
Publication date: 1940-02-13
Anticipated expiration: 1957-02-13

Description

Feb. 13, 1940. w. H. TINKER LOW-PRESSURE STEAM INJECTOR Filed July 9, 1957 s sheets-sheet 1 INVENTOR I Rm nu s nu @n um m a u n m Nw LM. Rm .nu nu .n www wm E MM Y h. SNR om Feb. 13, 1940. w. H. TINKER 2,190,109

` I LOW PRESSURE STEAM INJECTOR Filed July 9, 1937 3 Sheets-Sheet 2 Filed July 9,` 1937 3 Sheets-Sheet 3 INVENTOR atented Feb. 13, 1946 i UNITED STATES PATENT OFFICE LOW PRESSURE STEAM INJECTOR y Walter Howard Tinker, Muncie, Ind., assignox' to George A. Ball, Muncie, Ind.

Application July 9, 19.127',v serial No. 152,729 is claims. (c1. 10e-265) This invention relates to injectors and particularly to injectors employing low pressure steam as motive fluid. Low pressure steam injectors',"a`s

now employed, utilize both high pressure and low pressure steam as motive fluid, i. e., as the medium for entraining and heating water and for delivering that water from a region of low to a region of high pressure.`

In the present embodiment of my invention I also employ both high pressure and low pressure steam as the motive fluid, but an object of myv invention is to so deliver these high andlow pressure components of the motive fluid as to ef iectively employ each and thus produce an' efficient and eiective apparatus.

A further objectis to produce an injector "of the type above defined which, when associated with the boiler of a locomotive engine, for exl ample, so utilizes the exhauststeam from the loiii" comotive cylinders as to occasion an appreciable increase in overall emciency ofthe combined unit, i. e., of the injectorfand the boiler.

A further object is'to producean injector in which the parts thereof arel so associated and combined as to not only produce an effective and eicient injector, but one vwhich facilitatesas.u sembly yand disassembly of the parts going into the make`up thereof and which,1 therefore', sirnpliiies the operation of disassembling the parts t for inspection, repair or replacement purposes.

These and other objects which will be made more apparent throughout the further description of my invention are attained `by means of apparatus embodying the features herein de-` scribed and illustrated.

In the drawings accompanying and forming a part hereof Figure l is a fragmental, longitudinal, sectionalview of the water and steam re l ceiving end of an injector embodying my invention; Fig. 2 is a corresponding view of the water delivery end of the 'injector illustrated in Fig. l i

ofthevcone shownin Fig.5 i i Fig. 7 is a iragmental sectional view on an enlarged scale of the `steam nozzle I9 of Fig. l, showing the external surface of the delivery end thereof slotted;

,Fig. 8 is an end View of the nozzle shown in- Figs. 9 and 10 are views corresponding to Figs.

` `5 and` 6 but illustrating,` on` a reduced scale,` a

somewhat different form of water delivery cone and an arrangement in which the outlet' end of iace and Figs. 11 and 12 are views, corresponding to t views 7 and 8 but disclosing the end of the cone f as notched in such a way as to provide longitudinally extending prongs on the end thereof A so arranged. that` the spaces between the prongs produce longitudinally extending ridges or ribs on the surface ofthe water stream issuing from the nozzle `and thus extend that surface andl in` crease thev electiveness of the stream in receiving heat and kinetic energy from the motive fluid, i. e., for example, the steam.4

The injector illustrated in Figures l and 2` in? `cludesthe usual water and steam passages.r `These passages are, however, so associated that during the operation of the' injector a water annulus is maintained between the high pressure motive fluid and the low pressure motive fluid and under such` conditions that both components ofthe motive fluid simultaneously act on the water in such a way as to impart heatfand longitudinalmovement thereto. Another characterizing feature of my invention is that the stream' of water entering the working passage of the injector is ribbedor otherwise formed so asto extend its surface and thus increase thesurface of contact between the water and the` motive fluid, whichis hereinaftertermed steam.

A further characterizing feature of the invention is the arrangement of overflow outlets provided both in the combiningtubes and in the casing or shell of the injector. In the illustrated embodiment, the injector is provided with two overflow chambers,V one communicating with a low pressure portion or stage of the composite combining cone and the other with a portionor stage of higher pressure. however, connected together bya port, which is 4controlled by a non-return valve so arranged as to prevent a back flow from the high'to the low pressure chamber. Communication between the second or nal overflowchamber and the atmosphere is also controlled by a non-return valve which opens in response to the pressure Both chambers are,

the cone is serrated or grooved only on its inner f in the nal .overflow chamber, but which is provided with means for closing it and holding it in the closed position in response to the pressure developed within the delivery passage of the injector.

Thus injectors embodying my invention are characterized by the arrangement and relationship of the steam and water passages herein broadly deiinedand such injectors preferably include an arrangement of overflow passages and chambers such as above defined.

As illustrated, the injector is provided with a shell It? made up in two parts ma and IDD. This shell is provided with a water inlet port II, a high pressure steam inlet port I2, a low pressure steam inlet port i3, an overilow port I4, and a water delivery vport I5. The two parts of the shell Illa and It?) are so formed and so connected together that they provide supports for a series of water and steam delivery tubes and nozzles which constitute, in their effect and function, the water entraining passages, the combining tubes or passages and the delivery tubes or passages of the injector.

As shown, the shell encloses a water chamber I6 with which the water inlet port l communicates and which extends upwardly of the shell and communicates .with a water delivery cone Il, which is in eieet located within a low pressure steam chamber i8 and is so arranged that it is surrounded by low pressure steam admitted to the chamber IG through the port i3. The cone I'I surrounds a high pressure delivery nozzle i9, which is axially aligned therewith and which is so located within the cone Il that itsoutlet 23 is in open communication with the chamber' I6. A low pressure steam-directing cone 2i is so formed and located within the shell that it, in eect, forms two expansion nozzles 22 and 23, each of which communicates with, and receives steam from the low pressure steam chamber I8. In they illustrated embodiment, 'this is accomplished by providing the larger end of the cone 2| 'with an annular flange Zia, which extends forwardly of the cone and with its two circular series of ports 2lb constitutes a supporting cage for the cone 2I.

As a matter oi structural detail this flange 2 Ia is screwed onto and supported by a primary combining cone 2d into whichthe steam cone 2| projects and which is concentrically arranged with relation thereto so as to provide the expansion nozzle 23. rlhis nozzle 23 is annular in form, surrounds the cone 2l and communicates at its throat end with the low pressure steam chamber I8 through the aforementioned cage. The annular steam nozzle 22 is formed by the cones Il and 2|.

A secondary combining cone 25 is spaced from but axially alignedwith the cone 24 and, liker that cone,is a converging cone. This cone 25 constitutes one of three axially aligned converging cones 25, 23 and 2l, each of which is spaced from the other to provide an overflow passage, but each cooperates with the others to form the main combining tube of the injector.

As shown, the cone26 is supported in an aperture, formed in a partition 23 of the shell, and the'cone 25 is supported at 'the inlet end thereof by means of a forwardly projecting, annular ange 25a formed on the cone 25. The flange 25a is provided with an annular series of ports 25h so located that they establish communication between an overflow chamber 3l and the space'intervening between the cones 25 and 26. The cone 2l is provided with a similar, but rearwardly extending annular ilange 2l@ and the annular series of ports 2lb formed therein communicate with the space intervening between the cones .26 and 21 and with an overilowvchamber 34. The delivery end of the cone 2l (Fig. 2) is axially aligned with, but spaced from a Venturi tube 29 which extends through an aperture formed in a partition 3U or" the shell and is secured to that partition. This venturi is similar to the ordinary Venturi tube usually employed in injectors, except that the converging portion thereof is relatively short and the throat is not interrupted by the provision of an overow aperture. The cone 2l` in elTect, constitutes an effective part of the venturi and by being spaced from the tube 29 provides an overflow outlet space on the inlet side of the throat of the venturi.

The partition 28 is so formed that it, together with the shell lIlb and the cone 2li, forms the overflow chamber 3| within the shell. As shown in Figure 2, this chamber 3l is provided with an outlet port 32, which is controlled by a nonreturn valve 33 so arranged as to rmit flow from the chamber 3I into the overflow chamber 34 but to prevent flow in the reverse direction.

The chamber 34 is formed between the

partitions

28 and 30 and is provided with an overilow port 35, which is also controlled by a nonreturn valve 3G. As shown, the valve 355 is located within a chamber or closure 3l, formed by v-the partition 30, a partition 38, the peripheral wall of the shell Ilib and the end wall 39 of the shell. This closure or chamber 3l is provided with th-e overflow port I4 which is in open communication with the atmosphere.

The shell portion Illb, the partition3 and the partition 38 cooperate to enclose the water delivery chamber l vof the injector. The water delivery port I5 communicates with the chamber 4l) and the outlet end of the venturi 23 projects into this chamber. A specially formed head 4l forms a removable closure for the chamber 40 and is located opposite the partition 3i), thus giving access tothe interior of the chamber 4i).

In the illustrated embodiment, the high pressure steam nozzle I9 receives steam from the high pressure steam inlet port I2 through a pipe 42, which is supported by the shell lila and which in turn forms a support for the nozzle I9. In Figures l and 3 of the drawings I have shown the pipe 42 provided with radially projecting, longitudinally extending lugs 42a which extend beyond the delivery end of the pipe and are adapted to engage the internal surface of the water delivery tube Il and thus support the end of the pipe 42 on the tube I'I and positively hold it in predetermined spaced relation to that tube. 'I'hese lugs extend in the direction of water ilow through the passage 2U and are stream-lined in that direction as shown in Figure 4.

As shown in Figure l, the high pressure steam nozzle I9 terminates at a point somewhat in advance of the delivery edge of the cone I'I. This is for the purpose of increasing the entraining eifect of the steam issuing from the nozzle I9 and, as a result of this location, the nozzle I9 and the injector parts associated therewith function to some extent as an injector in discharging noncond'ensible gases,"sucli as'air,

`and condensible vapors from the water chamber The nozzle 44 is shown screwed `intofa hollow boss 4B forming apart of the shell Ib, and this hollow boss is provided wtih a steam inlet port 46a, throughv which high' pressure steam is delivered. As shown, the combining-diffusion cone 45 is so formed that it may be conveniently screwed into an apertured partition of the shell portion Illb, which -intervenes between the water inlet II and the water chamber |46. The cone 45 is axially aligned with the steam nozzle 44 and is adapted to receive the stream of expanded steam issuingtherefrom. For lack of a better term the combination 44 -45' may be termed a lifting injector. It, however, functions as the rst stage of a two stage ejector during the preliminary operation of starting the injector and while water is being drawn through the port Il so that it may be delivered to the water chamber I6.

In connection with the preliminary 'operation of starting the injector it should be noted that the main injector is capable of liftingwater through the port II and into the water chamber I6, consequently the combination 44-45 supplements this action and after water has been lifted to such a height that it partially and then wholly submerges the inlet of the cone 45,` the combination 44-45 operates as an injector and delivers water to the chamber I5.` Thus it is apparent that during the starting operation the steam nozzle I9 and the injector'parts associated therewith function as the second stage of an ejector in that it discharges the partiallyvcompressed noncondensible gases and steam from the water chamber I6.

In Figure 1 I have also illustrated annular steam nozzle 41, which surrounds the steam pipe 42 and is located within the annular water passage communicating With the annular water nozzle 20. As there shown,ithe steam nozzle 41Ais adapted to receive high pressure steam from a steam chamber 48 through a pipe 49, whichsurrounds the high pressure steam pipe 42. It will be'understood that while this steam nozzle 41` may i be employed simultaneously with thecombinationy 44-45 in the operation of vstarting the injector, such a procedure is unnecessary except possibly in installations where water is to be lifted to unusual heights'. Forthis reason the steam nozzle 41 may be omitted from the particular embodiment of my invention here illustrated or it may be employed asan alternative form and be utilized in place of the combination 44-45. Throughout the further description of the operation of the injector I will assume that the nozzle 41 and its connecting steam pipe 49 are omitted from the disclosure.

In starting the injector, high pressure steam is delivered to the nozzle I9 'through the pipe 42 and low pressure steam -is delivered to the chamber I8 through the port I3.` As previously stated, vthe nozzle I9 vand the operating parts of the injector associated therewith function, durlng this portion of the operation, to evacuate thel chamber I6 and thus lift water into that chamber As the water rises in the passage communicat` ingvv .with'thewater inlet portl H it nally lls theco'ner45and the combination 44--45 is therefore' gradually transformed into an elementary water injector and functionsto pump waterfrom the passage II to the water chamber IB.` During this periodin the starting of the injector the nozzle.` I9 andassociated parts continue to funci tion as an air and vapor ejector, with the result that the chamber I6 is rapidly lled with water due to the combined pumping action of the combination 44,-45 andthe ejector action` of the nozzle I9 and parts associated therewith.

After water is delivered to the nozzle 20 and the maininject'or starts to operate as a water en training agent thecombination 44-45 may beV said to function as an isolated initial` stage `of the main injector becauseit imparts some abso` self-regulating. It is well recognized that as the j back pressure increases on a `locomotive engine the rate of evaporation within `the associated boiler` alsoincreases and `lthat, therefore, the boiler requires more water.4 With anvinjector embodying my invention applied to a `locomotive engine variations in back pressure, on the engine occasion variations in the amount of low pressure steam delivered to the workingy passages of the injector, consequently as the back pressure increases the increase in the amount of I exhauststeam delivered to the low pressure steam nozzles 22 and 23 induces alarger now of water through the water nozzle 20. Conversely, as the back pressure decreases on the locomotive` enginev and the demand by the boiler forwater decreases, the combined effect of the steam nozzles forming a part of my injector occasions a decrease in the flow of water.

In connectionwith this regulating function of the combination 44-45 it should be noted that the rate of water flow through the throat of the combined combining tube and diffusion nozzle 45 depends upon several varying conditions, oneof which isthe absolute pressure of the water with-v in the chamber -I6 and that, therefore, if thepres` sure of the exhaust steam within the chamber I8 is such as to induce an increase in the ilow of water through the nozzle y 20 the combination 44-45 will respond to this` more favorable condition ancl increase the flow of water to the chamber I6. Conversely, a reduction in the iiow` of water through the nozzle 20, occasioned by a reduction in the exhaust 'steamvpressure within the chamber I8, will contribute toa reduced ilow i of water through the tube 45. `Thus it is apparent thatthe `injector is to a large extent self--regulat-4 ing and that the combination 44-45 functions largely as a regulating stage of the main injectorbecause it controls delivery of water to thecham-l ber `It in `response to the varying conditions within the main injector.

Itwill ybe understood that the steam nozzle I9` is so designed as to expand the ysteam -receivedjby (external surface of cone I1 and internal surfacej ng of cone' 24)', that the'low pressure steam nozzles 2l and 23 likewise expand .the low pressure steam delivered to them to about the desired fluidV pressures maintained within the inlet end of the combiningtube.

The degree of expansion of both the high pressure and the low pressure steam will be determined by the initial pressure of the steam as it is delivered to the expansion nozzle and by the pressures in the working passages of the injector during normal operating conditions. Each expansion nozzle should, therefore, be proportioned so that the steam issuing from it is neither materially over non under expanded. Where the steam is under expanded bythe expansion nozzle it issues therefrom with an explosive effect and thusto some extent destroys the directional effect of the'steam and renders the steam less effective as van entraining medium. Over eX- r' panding the steam within the expansion nozzle has a similar effect, in that it also tends to set up eddy currents 4, or.` turbulence within the stream of steam and thus the kinetic energy in the form of velocity which is developed by the expansion of the steam, cannot be as effectively employed in imparting directional velocity to the Water. f

Inl designingboth the high pressure and low pressure steam delivery' nozzles it must be borne in mind that the kinetic' energy in the form of dered available by theexpansion of the steam,

cari be most eiTectit/ely employed where the water is so introduced that it is maintained in a solid or well defined stream, as distinguished from a moving lmass of separate drops or spray. On the other hand, I have discovered that the energy of the steam-including energy in the form of heat-can be most effectively transferred to the Water where conditions are such that the surfaceof the water stream is somewhat ex tended by vforming ribs or ridges thereon which extend in the direction of the water dow. For this reason, I so form the water delivery nozzle that it produces longitudinally extending surface ribs or ridges on the Water stream, but at the same time avoids breaking the stream, or any part oi it, into a mass of separate drops or sprays.

I have also discovered that the best results are accomplished in an injector such as here conn templated, i. e., one employing' both high pressure and lou7 pressure steam as motive fluid,

Where the high pressure steam is segregated from f the loW pressure steamv and delivered to the working passages of the injector Without having Way I not'fonly segregate the high pressure steam from the low pressure steam prior to delivery to the working passages of the injector, but I also segregate the steam from the two sources after delivery to the working passages and the annular wall of the Water stream constitutes the segregating medium.

In the present embodiment of my invention steam from the high pressure source is delivered to the interior of the lhollow stream of water issuing from the nozzle 2l), and consequently steam from the W pressure source is delivered to and around the external surface of this annular Water stream. l' also so form the Water delivery nozzle 2t that the surface of the annular stream is corrugated or ribbed by the delivery edges of the Water nozzle, and in such a way as to materially extend that surface but at the same time Aavoid the formation of sprays in appreciable amounts.

The foregoing discussion discloses that the steam and water nozzles must be so positioned as to minimize shock at the time of impact between steam and water. This primarily involves the angles at whiclrthe steam is delivered from the steam nozzles and it will be apparent that the ideal situation is to so deliver the steam from each such nozzle that while each particle of steam moves toward the Water stream, nevertheless steam and water move in substantially parallel lines. This ideal situation, however, cannot be attained under practical operating conditions but I have discovered that the angle of incidence (at the time of steam and water Contact) should not be greater than eight degrees in order to obtain the best results.

Where a low pressure steam injector is employed in delivering feed water to a boiler, such as the boiler of a locomotive engine, the eiciency oi the combined unit is increased somewhat by the amount of low pressure steam utilized as motive iiuid for the. injector, since such steam is ordinarily wasted. It is, therefore, desirable to designthe working passages and the steam delivery nozzles of the injector so as to utilize in the injector a substantial portion of the 10W pressure steam rendered available during average operating conditions of the locomotive. As heretofore made apparent, my invention also involves the use of high pressure steam as motive iluid for the injector and the high pressure steam contributes tothe effectiveness of the injector operation. It is, therefore, apparent that in designing the injector the nozzle areas must be so proportioned, as between high pressure and low pressure steam, as to render steam from both sources highly effective,` The injector illustrated is primarily for use in connection with locomotive engines and where the boiler pressure of the associated boiler ranges from about 150 pounds to 200 pounds the effective throat of the high pressure steam nozzle is about one-twentieth of the effective throat of the combined low pressure steam nozzles 22 and 23. Where, however, the gage pressure of the associated boiler is higherfor example, :from 35u to 400 poundsa slight decrease in this ratio will produce more effective results. For example, where the boiler gage pressure is 400 pounds theeiective throat of the high pressure steam nozzle should be about one-fifteenth of the effective throat of the combined lov.r pressure steam nozzles. By thus pl'oportioning the effective throats of the nozzles I proportion the amount oi high and low pressure steam delivered to the injector.

After the water chamber `I 6 is `filled with water, vto the extent that the inletto the water passage y or nozzle 2t is completely filled, the water issuing from thelwater nozzle 20, in the form of an annular stream, is subjected on its inner surfaceto the action ofthe steam issuing from thenozzle I9 andfonlits outersurface to theaction of the various cone shaped members `whichconstitutethe combining tube of the injector. i,

I t is apparent from the drawings that thefcone 2| not only actsin conjunction with the cones I 'I and 24 to form the steam expansion nozzles 22 and 1 23,lbut that the internal surface of-the delivery or tained in the form of an annular stream, and the municates with the chamber 34.

Way is provided between the conical members 26 rear end ofy this cone also functions as a combining cone. The water issuing from the nozzle 20 is thus impelled through the cone 2IWhile retrailing internal' surface of the cone tends to gradually direct the flow of steainirom nozzle 22 against the external surface of ther annular stream of water and also tends to compact the ,combined or combining streams. i Upon issuing from the cone 2| theexternal surfaceof the annular water stream is subjected to theaction of the annular jet of steam issuing from the expansion nozzle `23. The rear or delivery end of thecone 24 projects beyond the cone 2| and thus beyond the portionthereof which constitutes a part of the expansion nozzle 23, andit therefore may be said that this portion of the cone 24 constitutes a part of' the combining tube of the injector. The tube 24 is of slightly less diameter at its outlet end` than the inlet ofthe `tube 25 and `is jspaced from that tube so as `to provide `-a free overflow of spillway for the water, and this spillway communicates directly with the chamber 3 I i i i ThusV it is apparent that upon starting the injector, thewwaterI issuing from the nozzle 2d is simultaneously acted upon by-thehigh velocity steam issuing fromthe steam nozzles I 9, 22 and23 and that a spillway is provided atthe end of the conical member 24 in order that the watermay freely flow toward thev overflow I4 of the injector during the interval necessaryto developsufcient `velocity energy in itto carry-al1 of itv through f'theycombining cone" 25. A secondspillway is water during thel initial period of` startingthe inl jector.v The outlet end of thetubezis of slightly less diameter than the inlet of 'tube 26. The ,over- `iiovv or spillway between the vconical members 25 `and 26 also communicates `with the chamber 3| and such ,water asspills through it during the starting period, collects in the lower portion of the chamber, 3| and moves fromthat chamber i through the one-way `or check valve 33 vand `into the chamber 34.

The combining tube is also so formed as toprovide two additional spillways, each of which comand 21 and the final spillway is located adjacent to thefthroat of the diiusionor Venturi tube 29 and, as illustrated, between thedeliveryiendof the conical member 21 and the inlet end of the Venturi tube 29. In each case they outlet end of the cone ahead 'of the spillway is `of 'slightly 4,less i diameter than the inlet end ofthe followingcone. Water delivered to the chamber 34` fromthe combining tube.

One such spill-i` spillways directly communicating with that cham.- ber and from the chamberl is delivered totheinjector overiiow I4 through the valve St, which is free to open inresponse to pressure within the chamber 34, except as controlled `bythe plunger I,5 5I, as will hereinafter bedescribed. "From the foregoing it will be apparent that spillwaysare formed at short intervals along the combining; ltube and that the `'arrangement.of these spillwaysl is such as to facilitate the `rapid building up of 1o velocity energy inthe water .to `such. point ,where `it can be delivered tothe boiler after traversing l the diffusion tube 29. 'In addition, thevalves 33 l and 36 are so arrangedthat they will successively close off communication between'the chambers. 3| 15 and 34 and the overow ItasA normal operating: pressures are=reached and establishedwithin the f rChat is to say, after-the water issuing from the nozzle kEuhas acquired suicient velocity to carry all of it past the spillwayscom- 2O mun'icating with the chamber 3 i, thevalve 33 `will close the port 32 and thus close oii communication between the chamber 3i and the chamber 34,2tnd consequently between `thecharnber 3| and the atmosphere. This tends `to maintain .the desired, 25

or normal operating pressure within the4 chamber 3| and also prevents pressures within the chamber 34 influencing or `upsetting conditions established Within chamber 3| and the-communicating portions of the combiningY tube.}` .Y l

The spillways communicating directly with the chamber 34 will, in eiiect,-be in open communica` tion with the atmosphere-through lthe overflow i port I4 until -normal operating conditions k are reached within the chamberllii. Thisof course, 35 means thatthese spillways and the chamber `.'54 will be in yopen communication with theoverflow port |41untlthe velocity of the water traversing i the combining tube is suflicient to cause all of it toenter and passv through thediiiusion tube 29.1.40 c

` boiler throughthe port I5, which, as illustrated,

is controlledy byk an outwardly opening'` check` 45 valve52. i During `the period of starting the injector and during normal operating conditionsthe steam vis 4so delivered to the working passages of `thefinjector `as to tend to holdthe `water in annular 50 form, with the' result `that Ithe water stream is* subjected to the impelling as well as theheating effect ofsteam `delivered from both sourcesduring some portion of its travelthrough the `comi binding tube. l The areas of the various tubes 2|., 1 25,28 and 21 are so proportioned that thewater entering through the nozzle. 29 is4 maintained.in` thel form .of an annular stream, havingaco're-of steam,.from the water delivery nozzle 2i) throughout themajor portion of thecombining tubeand in this way the wateris subjected tothe impelling4 effector" `a confined stream of steam `during a larger part of its movement through the converging portion of the working passages of the `in-r -jector. For this reasonn steam from the `high `65 pressure source is delivered to -the interiorof the annular stream of water. Under normal working conditions of the locomotive engine and the irl--y jector, the steam deliveredby the nozzle i9 will` contain more energy, per pound, than the steam 70 delivered through the combined nozzles22 and` 23, and thus the impelling eifect may beconl tinued for a longer period and throughout a greater range of travel vof the water than is possiv'ble in I`connectionvvith 4the Vsteam from :the 'low4 76 i pressure source. Then too, the angle of diverf gence between the path of travel of the steam issuing from the nozzle I3 and the path of travel of the internal surface water is less than is the case in connection with the steam delivered to the external surface of a water stream, and the rresult of all this is that `the interval (measured in period of water travel) during which water is being impelled and during which it ls taking up 'heat from condensing steam is greatly increased by employing the annular jet of Water and by delivering steam to the interior of the annular water stream.

In addition, the annular Water stream increases the effectiveness of the injector by reason of the fact thatthe water is retained in a conf solidated stream, but at the same time exposes a large surface to the motive steam. This not only maintaining the water in theform of a gradually converging annular stream, vthe steam issuing from the expansion nozzle I9 may be directed axially of the combining tube and at the same time be effectively employed as an impelling medium for the water. This is also to some extent true of the steam issuing from the expansion nozzles 22 and 23. In connection with these nozzles it will, however, be apparent thatfthe external surface of the annular water stream is gradually decreasing in diameter along the combining tube and that, therefore, the steam issuing from the nozzles 22 and 23 is directed inwardly with relation-t the axis of the combining tube. This angle of steam delivery is, however', slight when measured from the external surface of the annular rStream, with the result that each steam Y particle issuing from either the nozzle 22 or the l between steam and water.

nozzle 23 is traveling in substantially the same direction as the water at the instant of impact that there is little .or no tendency to set up turbo: lence in the streams of steam issuing from either ofv the nozzles 22 or 23. This is also true of the steam issuing from the nozzle I9.

In the drawings I have shown the tube 26 provided with an annular series of forwardly inclined vapor entraining apertures 53. These apertures `extend. through the nozzle 25 and thus com municate at their outer ends with the chamber 3l and at their inner ends with the interior of the combining cone. The inclination of these apertures is such that there is little or no tendency to spill Water through them, even during the period of starting the injector. The movement of the water or the combining streamjof steam and water past their inner ends, occasions an ejector action and thus tends to supplement the effect of the spillways between the nozzles 24 and 25 and the nozzles 25 and 26 inwithdrawing ambient air and vapor from the chamber 3l. It will, of course, be apparent that the ejector effect of each spillway is accentuated by reason of the factthat the outlet end of the leading cone associated with'the spillway is of slightly less diamn eter than the inlet end of the associated or cooperating trailing cone.

The cone 21 is also provided with an annular series of vapor entraining apertures t which Thusit is apparent for manually closing4 the valve 36.

communicate with the chamber 34 and which supplement the vapor entra-ining effect of the spillway provided between `the cones 2G and 2l and between the `cone 2l and tube 29.

The valve 35 is adapted to be closed and held closed by the pressure in the outlet chamber 4W when that pressure has reached the predetermined pressure to which the water is to be raised by the injector action. For this reason the valve 36 is provided with a closing cam 36a, which is adapted to be engaged by the plunger '5l as the plunger moves to closelthe valve. The plunger 5l is operatively connected to a piston Sla located in a cylinderflb. The plunger 5l projects through and isguided by an aperture formed in the end of the cylinder bib-adjacent to the valve 35 and is surrounded by a coil spring dic which operates'between that end of the cylinder and the piston 5ta and, therefore, normally tends to retract the plunger 5i. The end of the cylinder 5E?? remote from the valve 35 is in open communication with the chamber Ml through suitable ports and piping 55d, with the result-that pressure developed within the chamber 48 tends to move the piston Eid to advance the plunger 5l and thus close the valve. The strength of the spring 51o is so proportioned that this movement will not be completed until the pressure within the chamber Ml has arrived at a pressure slightly above boiler pressure.

The cam 36a is so formed and positioned that its active face lies adjacent to the retracted plunger 5l when the valve is fully open. In addition,the contour of the active face of the cam y is such that as the plunger advances to close' the valve, the face of the cam-readily slides under the plunger and nally provides a seat for the plunger, which extends substantially at right angles to the axis of the plunger when the valve is closed.

Withi this arrangement the valve 36 is automatically closed when the desired pressure is established within the'chamber 40. As has been said, this shuts oi communication between the chamber 3d and the atmosphere. Under such conditions the ejector action, above referred to, reduces the pressure within the chamber 34 sub.-

stantially below atmospheric pressure and to a pressure corresponding somewhat to the pressure existing within the combiningtube at the spillway,

break, after it is in normal operation, is great" ly minimized.

In the drawings, I have also illustrated means As there illustrated, the head 5l@ of the cylinder 51h is provided with an internally threaded aperture which 'receives the threaded end of a rod 54. The rod passes through a suitably packed gland lili and is provided at its outer end with a hand wheel 5ft. A pad 54a, isswiveled or otherwise suitably connected to the inner end of the rod 5d and is adapted to engage the piston 5in when the hand wheel 54 is urned to move the rod inwardly. Thispad also forms a stop for the piston 5ta and the throw of the rod is such that the t valve 3S may be closed and held to its seat by turning the hand wheel.

During the operationof the injector the supplyof low pressure steam, aswell as high pressure steam, 'must be maintained substantially` con= stant. For this reason some means, such as an ordinary reducing valve, is providedfor delivering steam from a high pressure source to the low` pressure steam chamber I8 when the pressure within that chamber falls below a predetermined point. That is to say, means are provided for i augmenting the supply of low pressure steam and thereby maintaining a substantially constant `steam pressure within the `chamber I8 independently of variations in the amount of steam exhausted from the locomotive, and where no `exhaust steam is` available then the entire supply of low pressure steam' is received ironia high pressure source through the reducing valve. It

should, however, be noted that the reducing valve here mentioned should be so adjusted that variations in back pressure on the locomotive, during average operating conditions, will occasion variations in pressurewithin the chamber I8 so asto obtain the self-regulation heretofore commented upon.

In Figs. 5 to 10, inclusive,`of the drawings, I

"have shown several ways of extending the surface The grooves 56 located internally of the mernber ll extend axially of the member and conse- `duently axially of the assembly of conical members which constitutes the combining tube of the injector. It is apparent from rthe drawings that the internal surface of the member ll and the external surface of the steamnozzle 9 give form to the water stream issuing from the nozzle 2!! and that, therefore, the longitudinal extending grooves or corrugations provide surface extending ribs or ridges on the external surface of this annular water stream. These ribs or ridges necessarily extend in the direction of water flow and consequently longitudinally of the stream. They are spaced apart a distance corresponding to the spacing of the grooves 56 and consequently valleys or depressions intervene between them, `thus producing an external surface on the stream which is in effect corrugated longitudinally of the stream.

My invention also contemplates forming such corrugations on 'the internal surfaceof the Water streamand in Figs. 'l' and 8 I have shown an eni larged view of the high pressure steam nozzle I9 provided with grooves 5t' formed on the outer peripheral *surface and at the delivery `end thereof. These grooves correspond in function to the slots 56 of the tube `Il and form surface extending 'ribs or ridges on the vinner faceof the annular water stream. These ribs or ridges also extend in the directionof the water flow and consequently longitudinally of the stream.

Similar surface extending grooves may also be formed on intermediate conical members included inthe makeup of the combining tube. That is to say, the outlet end of both the tubular members 25 and 26 may be provided with grooves correspending to the grooves 5t of the tubular member l l and these grooves will re-establish the surface extending ribs on the outer surface of the water stream,

The grooves 55 formed on the outer surface of the tubular member il are located within the connes of the steam nozzle 22. They, therefore, have the eilcctof extending the inner sur1 face of the annular 'steam jetissuin'g `fori'ithat nozzle and they insure 'the deliveryrof steamto the valleys or depressions 'located between "the ribs or corrugations formed on the externalv surface of the water stream. It is, ofl course,` apparent that the conical member 2l may be provided with slots corresponding to the slots ISand having a corresponding function. i

In Figs. 9 and 10 I have shown, on a somewhat reduced scale, a modified form of Water delivery nozzle 5l' in which the internal surface of the delivery end of the nozzle is grooved to formthe slots 5S. Figs.- l1 and 12 disclose a water nozzle corresponding to that illustrated in Figs. 9 and l0, `but here the delivery end of the nozzle `is slotted to provide a series of notches 58 which correspond in Heffect and in function to. the grooves 5S of Figs. 5 andG. `Itwill be apparent that the outlet edges of the c'ones25 and 2610i the injector illustrated may be `similarly formed to provide thelongitudinally `extending serrations in the surfaceof the Water stream. f

The removable head l#il ofthe shell portion 10b not only provides access ntofthe chamber 40, but

also facilitates the operation of securing the tube 23 in place within the shell portion |011." That is to say, the removable head 4l facilitates the operation of assembling :and 'disassembling'wthe working parts of the injector insofar as the tube 29l is concerned. Bydividing the shell portion into the two parts, illur and lub, the operation of i assembling or disassembling the other working parts of the injector is materiallysimplied. The

drawings make itapparent that the'tubular member Il, the steam nozzle 'i9 and the `steam and internally threaded at the other. This cylinf der member 57d may be formed as a unitary part of the tubular member il and when so formed the tubular member is then secured directly to the shell section Illa.

The drawings disclose the vconical memberz screwed into a tapped aperture formed in apartition wall @il of the shell'section lllb andthat the tubular member 2i is secured by means oi `screw threads to this memberZd. The drawings also disclose that the aperture of the partition wall 5G, into which themember 24 is tted,is of such diameter as lto permit the introduction therethrough of the assembly comprising the` tubular members 25, 2B and 2l;l Thus `it is ap-` parentl that thcse'niembers are not only intron duced through the aperture of the partition iil,

but are also secured in place on the partitionr 28, by reason of access made available by the aperture in partition Eil. The assembly of elements including the tubular members 2l and 24 are secured in place` on the shell section 10b after tubes 25, 2e and 21 are in place and all parts arethus in working position when the shell section ida, is tted on and secured to the shell section i531). It will also be apparent', that the parts lreferred to as woilsing'parts of the injector may all be adjusted longitudinally with relation to each other by reason ofthe fact that they are fitted in place by means of screw threads. Thisis partie ularly apparent 'inconnection with the' `steam enla ifi

nozzle i9, the position of which can be readily adjusted, with relation to the outlet end of the tubular member il, by merely changing its longitudinal position with relation to the steam delivery pipe 42.

From the foregoing description it will be apparent that the lpresent invention involves an association of certain special structural parte and the iollowing individual features, viz., delivering the Water to the Working passages of the injector` lin the form of an annular stream; maintaining the Water stream in annular form during the greater' portion of its travel through the conibining tube; delivering impelling steam from two sources of supply and so that the internal and the external surfaces of the annular water stream are both subjected to the impelling and heating electoi steam; employing the water stream as segregatinginedium between the steam jets supplied from the two sources; extending the sur face of the water stream by providing thereon. longitudinally extending ribs or ridges; so delivering the steam from both sources as to avoid shock at the instant of contact between steam and .Water and so as to avoid turbulence in both the steam and water; maintaining a core of steam -within the Water stream throughout the major portion of its travel through the combining tube; employing a plurality of spillways along the length of the combining tube; employing a plurality of overflow chambers, each communicating with one or more such spillvvays; providing separate means for closing oif communication be tween each such chamber and the atmosphere; v

providing vapor entraining apertures at spaced points alongthe combining tube for augmenting the ejector effect at the'spillways; and so forming the injector casing or shell that the working parts can be readily assembled and adjusted and can be readily disassembled or replaced. Y

Other advantageous structural and functional features will be apparent to those skilled in` the art and it will also be apparent that various changes, additions, omissions and substitutions may be made in the apparatus without departing from the spirit or scope of the inventionas defined by the appended claims.

What I claim is:

1. A method of delivering Water into a boiler, which consists in creating a flow of Water in the form of an annular stream, subjecting such stream to the impelling action of condensible motive fluid moving at a high velocity and surrounding such stream, simultaneously subjecting such stream to the impelling action of a condensible motive huid delivered to the interior thereof and moving at a velocity substantially greater than that of the motive uid surrounding said stream, gradually contracting said stream while combining lit with such motive uid by condensation thereof and while maintaining its annular form and the flow of high velocity motive fluid throughout the hollow interior thereof, consolidating` said annular stream into a solid stream moving at a high velocity, converting the kinetic energy thereof into potential energy in the form of pressure and delivering such Water to a boiler under such pressure.

2. A method of delivering water from substantially atmospheric pressure into a region existing at a pressure substantially above atmos- 'pheric pressure, which consists in creating a` flow of water in the form of a confined, directed stream at a pressure approximating atmospheric pressure, projecting such stream beyond its com ning and directingfwalls .in the form of an annular streamand substantially simultaneously .subjecting it to the impelling action of an internel and external stream, of a condensible motive fluid moving at a high velocity in substantially the direction of such. flow, gradually contracting said stream while maintaining an internal core of such high velocity motive fluid and while combining it with such motive fluid by the condensation thereof, consolidating said hollow stream of water into a solid stream moving at a high velocity, converting the kinetic energy of said consolidated Water stream into potential energy in the form of pressure, and delivering the Water thereof to such region of high pressure by reason of such potential energy.

3. A method of delivering Water from substantially atmospheric pressure into a boiler existing at a pressure substantially above atmospheric pressure, which consists in creating a ow of water in the form of a confined, directed, annular stream at a pressure approximating atmospheric pressure, projecting such stream beyond its conning and directing walls, in the form f an unsupported annular stream, subjecting the interior and exterior of said annular stream to jets of motive uid moving at a high velocity in the direction of such stream and applied to said `stream at points substantially equally spaced n from such coniining and directing Walls, gradually contracting said annular stream while combining it with such motive fluid by condensation of the fluid and While maintaining the annular form thereof and the flow of such high velocity motive fluid throughout its hollow interior, consolidating said annular stream into a solid stream of water moving at a high velocity and substantially simultaneously with such consolidation occasioning a gradual transformation of such Velocity energy into potential energy in the form of pressure, and delivering such Water to the boiler under such pressure.

4. A method of delivering Water into a steam boiler While the same is under pressure, which consists in creating a ilow of water at substantially atmospheric pressure and in the form of a confined and directed stream, projecting such flow beyond its confining and directing walls in the form of an annular stream, simultaneously subjecting the interior and exterior of such stream to the impelling action of separate jets of steam moving at different velocities in' substantially the direction of said stream flow, gradually contracting said stream While combining itwith steam from both suchjets, converting the velocity energy of said stream into potential energy in the form of pressure and delivering said stream to a boiler by reason of such pressure.

5. A method of delivering Water into a steam boiler while the same is under pressure, which consists in creating a flow of water at substantially atmospheric pressure in the form of a confined and directed stream, projecting said stream in the form of an unsupported annular stream, subjecting the exterior and the interior of said annular stream to the impelling action of jets of steam moving at different velocities in substantially the direction of said stream and simultaneously applied to said stream at substantially coincident points along its length, gradually contracting said stream while maintaining its annular form and such steam iioW along the interior thereof and While combining such stream and steam by condensation of the steam, then consolidating such annular stream into a solidV stream of Water moving at a high velocity, converting the kinetic energy of said consolidated stream into potential energy in the form of pressure,fand delivering the Water thereof into such boiler under such pressure.

6. A method of delivering Water into a steam` boiler while the same is under pressure, which ,consists in creating a confined, directed now of Water existing at substantially atmospheric prese sure, projecting suoli; ilow in the form of an un# supported `annular stream, simultaneously v subjecting `the exterior of said stream to. the imt peiling action of an annular jet of steam moving at a high velocity in substantially the direction of said stream and the interior of said stream to `the impelling action of a jet of motive fluid moving at a velocity in excess of that of said annular jet, gradually contracting said annular stream of Water while maintaining therein a core 'of such high Velocity steam, consolidating said annularA stream into a solid stream moving at a high velocity, converting the velocity energy of said stream into-potential energy in the 'form of pres sure, delivering the Water of said stream to said boiler by reason of `said pressure, and varying the 'rate of such delivery in responses to variations in the rate of delivery of steam in such annular jet. 7. A method of deliveringwater into a steam boiler While the same is under pressure, Which'r i' consists in expanding steam from a low pressure source to a substantially lower pressure and delivering such steamso expanded in the form of a unidirectional jet, expanding f steam from a high pressure source to al pressure substantially equal to the expansion pressure 'of the vsteam from the low pressure source and delivering such steam so expanded in the form of a unidirectional jet and in a direction substantially parallel to the direction of said first mentioned jet, projecting a stream of water between such jets so that both such jets are effective in exertinga propelling` force on said stream at pointssubstantially coin` cident therealong, then converting the velocity sure and delivering the steamso expanded in the form of a unidirectional` jet, expanding steam from a low pressure source to a sub-atmospheric pressure substantially equal to lsaid first-men tioned sub-atmospheric pressure, and delivering the steam so expanded in the form of `a unidirectional annular jet surrounding said first mentioned jet and moving in substantially the direction thereof, projecting a 'flow of Water in the form of an annular stream between said jets so that such stream is simultaneously acted upon by said jets and at points substantially zo-incident along its length, gradually combining said stream with steam of said rjets while maintaining it in annular form, consolidating the annular stream into a substantially solid water stream, converting the velocity energy thereof into potential energy in `the form of pressure and delivering such Water to a `boiler by reason `oi such pressure.

9. A method of'delivering Water, into a steam boiler While the same is under pressure, Which consists in creating a flow of Water at. substantially atmospheric pressure in the form of a directed stream, projecting said stream as an unsupported' e ow in the form of an annular stream, `simultaneously subjecting the exterior of such annular stream to theimpelling.k action of steam from a low pressure source moving at a high velocity, subjecting the interior of said streamfto the impelling action of steam, from a high-pressure source moving at a Velocity in excess ofthe velocityoi the steam from the 10W pressure source,

gradually contracting said` annular stream' of water While 'combining itr with steam from' both such sources and While maintaining its annular term. consolidating said stream into` asubStanti dy solid stream, then converting the velocity el'` pressure, delivering the Water of `said stream y to a boiler by reason of such pressure and varying..

the rate of such delivery in response to variations thereof into potentialenergy` inthe ieorm` inthe impelling effect ci steam from saldlovv i pressure source. K i .c lll. In combination in an injector,V means for creating a flow of Water in the formel an unsupy ported annular stream, means for substantially exterior of stream tojets of motive iiuid moving at high butdifierentvelocities in the di-.

rection or" such flow and at substantially identical points along said stream, means for gradually contracting said stream while maintaining alsubstantial core of high velocity motive iluid on the interior thereof, means for consolidating `the an` nular stream into a solid stream and a diffusion tube for receiving theoonsolidated stream.v ll. In combination in an injector, an annular Water passage, an expansion nozzle surrounded,V

bysaid passages and terminating at a point adja-` `simultaneously subjecting the interior andthe f cent the outlet end thereof, means for connecting `said nozzle to a. source of high pressure steam,4

an vannular expansion nozzle surrounding said passage and terminating ata point `adjacent the `outlet end thereof, means for connecting said annular nozzle to a source of lovv pressure steam,

-means for creating a Water flow through said passage in the form of an annular stream, aligned combining tubes for receiving and consolidating said annular stream and adiiusion tube `for `re;-

ceiving the consolidated stream.

12. In combination with the sectional comloin` ing tube and the diffuser tube of a `steam actu-` ated injector, an expansion-knozzle,` an annular water passage' and an. annular expansion nozzle all arranged in concentric" relationship, all 'terminating in rsubstantially the same plane transverse to 'the line of ilovv therethrough and all-ain` ially aligned with said combining tube, means for V 'delivering steam lfrom one source and at onepressure to one oi said expansion' nozzles, means for delivering steam from another source at a differ'n ent pressure to the other of said expansion ,nozzles and means for delivering water to said passage.

13. In aninjector, two expansion nozzles andfo an annular water passage'arranged in concentric relationship with the delivery edges thereofterminating in substantially a single plane transverse to the line of flow therethrough and with one such expansion nozzle surrounded by and the `other such nozzle surrounding said annular passage, `means for delivering steam :from` a high H pressuresource to the inner. of such nozzles, means for delivering steam from a low pressure sourcel to the outer of such nozzles, means for delivering waterito said passage, a combining tube` yreceiving Water and steam delivered `from saidconcentric assembly and a diffusercommunicating with saidtube. l y. e

. WALTER HoWARDjTINKEa.