US1678484A - rushmore - Google Patents

Description

July 24, 1928.

S. W. RUSHMORE COOLINfi SYSTEM Filed Aug. 10, 19 26 3. Sheets-Sheet INVENTOR lkmml IV fizz /321201? BY L M ATTORN EY July 24, 1 928. 1,678,484

s. w. RUSHMORE COOLING SYSTEM Filed Aug. 10, 1926 3 Sheets-Sheet 2 [1mm aw l l I1 I l H l INVENTOR Jamaal Wfiam/zmure M ATTORNEY July 24,1928. 1,678,484

5. w. RUSHMORE- COOLING SYSTEM INVENTOR Jkmzm Wily/0120i? ATTORNEY Patented ,inly 24, 1928.

SAMUEL V]. RUSK- MORE OF PLAIN hitch Parent" orric an, NEW JERSEY.

COOLING SYSTEM,

Application filed August 10, 1926.

My present invent-ion is related to that set forth in my companion applications, Ser. Nos. 1,28,3 ,23 and 128,345, in that it concerns cooling; systems of the type commonly employed on automobiles or the like, but in which the heat transfer is mainly by boiling or superheating water to absorb surplus heat of the engine and condensing the resultant steam to dissipate said heat in the radiator. Preferably, the boiling is brought about as in my prior Patent No. 1,378,721, granted May 17, 1921, by having a force feed, water circulating system of small heat radiating capacity that serially includes the engine jacket, a conduit therefrom discharging into the base of the radiator and a pump drawing water from said base and force feeding it into the jacket, so that the cooling tubes of the large capacity radiating means are in shunt rather than series relation to the direct path of flow from the water jacket outlet to the pump intake. It is also possible to have some or all of the cooling;- tubes in series with the pump circuit, some or all of the jacket supply being drawn from the upper chamber and the boiling being: brought about by merely limiting the amount of the water supply.

As in said companion applications, the upfiow of steam into the honeycomb is con trolled by having the radiator full of water, so that liquid flow and liquid resistances will. dominate the distribution and upilow of the steam into the radiator tubes.

in said application, Ser. No. 128,345, this liquid circulation is mainly thermal, being primarily induced by the down pressure of cold water in some of the tubes forcingup warmer water in other tubes and then accelerated by ballooning effects of steam in the up'llow tubes but, in the present case, I more or less modify or control the thermal circulation tendencies by a forced circulation. hen the engine starts, there is rela tively feeble, sinall-volun'ie discharge of water, which. is preferably short-circuited to the intake of the pump, so that the water in the jacket soon boils. Preferably, the discharge outlet is throttled or constricted so as to establish back pressure in the ennine jacket, sometimes as much as three pounds or more, and so that the steam is discharged into the water in the lower chan'iher at correspondingly high velocity. Preferably, this discharge is through a surround- Serial No. 128,344.

ing tube like an injector tube. The steam and hot water discharged through the tube draw in, mix with and propel relatively large volumes of outside water. The dis charge of this composite stream, being lengthwise of the lower chamber, forces water with steam forward and upward in tubes that are in front of the injector and draws cool water downward in tubes in the rear thereof.

The mixing in the injector tube causes condensation of substantial amounts of steam, but as the volume increases, more and more uncondenscd steam mine'lcs with and is carried by the water in bubbles which partake of the forced circulation of the water, although the bubbles have an upward ballooning tendency of their own, due to the depth pressure;

The mixing); and condensing action of the injector tube also decreases and practically prevents noise and water han'nner effects in the lowerchamber, but may or may not be sutiicient to prevent such effects in the upfiow tubes.

In certain cases, the circulation is permitted to distribute itself freely through more or less of the cooling; passages of the honeycon'ib, more of them becoming upflow the volume and velocity of the steam discharge increases, butin other cases the lower chamber m.. be partitioned in such a way that certain selected tubes will be exposed only to the suction of the discharge, so that said tubes will always be down-flow. In such case, all of the remaining; tubes may be free to become all upflow, or part of them may be neutral, or downflow, according to varying conditions of steam evolution and radiator cooling rates.

The above and other features of my invention will be more evident from the following description in connection with the accompanying drawings, in which:

Fig. 1 is a side elevation conventionally indicating my present system as applied to an automobile engine and radiator, the radiator being shown in transverse section on the line 11, Fig. 2;

2 is a vertical sectional view of the radiator, approximately on the line 2-2, Fig. 1; and

Figs. 3 to 7 are vertical sectional views of radiators, illustrating modifications of my invention.

In Fig. 1, the motor is conventionally in dicated as including the usual crank case 1 and cylinder block 2, the upper parts of which are enclosed by water jacket The water cooling system is conventionally indic including the radiator 4, located as usual, on the same level with the motor and directly in front of it so that the lower part the radiator below the level of the water jacket of the motor. The circulation of the water from the'bottom of the radiator is through a pipe 5 topump '6, the latter be' n-etcrably driven from the engine at proportional speeds. The pump is indicated as being a gear pump, but this is merely to illustrate that the pump is one adapted to receive boiling water and force it into the water jacket againstfriction and any back pressure that may be caused by steaming. The pump discharges through a pipe '7' into water jacket 3, whence thepath of tiow is through riser outlet 8, and downwardly extending return pipe 9. The pipe 7 may contain a check valve 10 to insure against back flow of water or steam such as might otherwise occur under operating con ditions when the engine and pump are stopped. The return pipe 9 connects with a pipe 11, passing through the rear wall of the lower chan'iber of the radiator and discharging horizontally through two oppositely directed nozzles 13, 13.

The radiator is indicated as having the usual lower chamber 12 and upper chamber 15, serving as headers for the intermediate core, indicated in this case as comprising a great multiplicity of small tubes, there being in practice many more than indicated in the drawin The upper chamber is preferably provioed with an overflow pipe 17, which pre'ierably extends into the neck 18, which is CLOtiQil by filler cap 19. This overflow pipe is preferably freely opened to atmosphere, altho h it may be supplied with pressure sust. ining: breather valves as described in v ous of my prior patents and applications.

These radiators are thin from 'front to rear, usually 2 A inches to 3 inches, and the core may consist of tubes which may he, say, f; inch to inch diameter. The core may be. say, 21 inches by 24 inches, the usual fan, 20. beii g of somewhat smaller diameter and, being circular, naturally cools the middle tubes much more than the side tubes.

In such a radiator, even with'the bottom compartment entirely unpartitioned, the jets 13. 1S, naturally tend to apply suction on the central tubes and pressure on the side tubes but. the central tubes being the best cooled tubes. it is desirable to use as many of them as possible as upflow tubes. Therefore. prefer to limit the region of active e *"ion to a few of the r entral tubes by par- .11.; 1, 21 defining a central compartment, 22, in the suction region of the jets with two end compartments, 23, 23 in which the pressure from the jets takes effect. The partitions are formed with passages through -which the jets discharge and also with drain holes 24:, 24-" affording limited communication between the end compartments and the :enter compartn'ient. The jets 13, 13 may be, say 3'} of an inch in diameter so as to give a very small flow section. The result is to impose a substantial pressure of several pounds on the water jacket, thereby raising the water jacket boiling point up to, say, 218 to 225, and with the further result that when large volumes of steam are evolved, the jets discharge at high velocity. As shown, the discharge is through Venturi tubes 25, 25 whereby water in compartment 22 will be driven by injector action into the end compartment 23, 23, thus simultaneously applying suction on the central group of tubes 26 and pressure on the side groups of tubes 27, 27, tins definitely determining downflow in the former and upflow in the latter, as indicated by the arrows. There will be some dillerence in the two cases, however, since the suction in the central COll'lPtl-Itll'lfillt takes ei'h t l1E1li ()lll.il "O1] all the central tubes relless of its amount, whereas in case of high velocity discharge, the momentum effects of the jet discharge may apply greater pressure to the outermost tubes. The down flow suction being applied on a few tubes permits a maximum number of the tubes to be utilized for steam-carrying uptlow.

This injector arrangement of the jets brings the steam into contact with the indrann cool water, under conditions favorable lor mixing and scattering the steam so that much condensation will occur without producing objectionable noise or water ham iner effects in the lower chamber. The surplus steam as also superheated water evolving steam in finely subdivided bubbles, tends to follow the flow of the water and the distribution of its flow to the bottoms of the tubes is not materially diiterent from that of the water.

.12 will be evident that initially the discharge will. be oi small volume and at low velocity, causing but slight circulation in the ti'ibesibut, when the radiator is taxed to its maximum capacity, the steam with more or less entrained water, will flow very nearly to the tops of the upfiow tubes before being condensed. Under such conditions, the side tubes operate as uptiow condensers for a greater or less portion of: their length, while the central tubes connecting the top tank with the central compartment will act merely as water cooling return drains.

Where a balanced circulation is desired, the intake pipe 5 is branched so as to draw water equally from noints 28. 28" in the respectivechambers23, 23, preferably from just below the injector discharge.

The modified radiator arrangements shown in Figs. 3 and l function in somewhat the same general way as above described in connection with Figs. 1 and .2, so corresponding parts in Figs. 3 and a are indicated by the same reference numerals, but with different exponents for the modified forms. In Figs. 8 and t the main difi'erence is that instead of two nozzles discharging oppositely at the center, there only one nozzle, 15 in Fig. 3 and 13 in Fig. 4:. and this nozzle is located at one end of the lower chamber instead of at the center. In this way, the circulation in the entire radiator is somewhat like that described above for one of the halves of the radiator of Fig. 11,. The single nozzle arrangement has the advantage that the passages most definitely deteri'nined as downflow are near the side of the radiator where: the tubes are usually less effectively cooled, thus leaving the more central tubes which are better cooled by the direct dratt of the fan. freer for invasion by uptlow circulation. said uptlow being much less definitely predetermined and more likely to shift than in Fig. 1.

However, the downflow tubes can be more definitely predetermined by using one parti tion 21 as in Fig. 3, but this is not necessary and may be omitted as in Fig. 41. As shown. the nozzle discharges through a vcnturi 25", Fig. 3 and: 25, Fig. 4, but this may be omitted.

The specific arrangement shown in Fig. 4 has practical advantages for changing small radiators such as those on the well known Ford cars, from downflow water cooling, to uptlow steam cooling, the nozzle 13 being in this case rigidly positioned with respect to the venturi 25 by casting the parts integrally connected through webs 30. The venturi itselt has an integral support 31, which serves to anchor one end of the casting to the bottom ot the radiator while the other end is held by the collar 32 which has the bottom of the radiator clamped between it and the fitting collar of discharge pipe 9.

In Fist. 3, the cooling tubes may be the same as in Figs. 1 and 2, in which case the side tubes 26 will be most exposed to the suction in the rear of the venturi, although there may be a. secondary injector efi'ectoperating on tubes further forward by reason of the composite discharge from the front end of the venturi.

Fig. 4 ditl'ers from Fig. 3 in that there are cross-flow passages c, c, in the honeycomb whereby there is more opportunity for the forced circulation to short-circnit without going through the upper chamber. during times when there litt e or no steam evolution. As the nozzle is preferabl small, however, say, ,4; inch or less in diameter, the back pressure in the watc r j ket will be considerable and when the discharge carries considerable steam, it will be throttled and of relatively high velocity, thereby establishing water circulation in the cooling tubes and as soon as there is enough uncondensed steam so that considerable amounts of it penetrate the uptlow tubes, the rip-circulation. of the water will acquire a velocity that will carry it into the upper chamber with less tendency to short-circuit through the crosstubes.

ll hi lo the conditions and operations of the device are thus widely variable with changing conditions of the same device and are further variable with clitlercnt proportions of parts, back pressures, temperatures, etc, the circulation results from suction an d pres sure applied in the lower chamber. Primarily. the heavy water in the down-flow tubes applies static pressure in the lower chamber which pushes up the warmer lighter water into and through the upflow tubes and such push will be increased and, in most cases, practically dominated by the jet suction under some at the tubes and jet pressure under others. The water circulation resulting from these causes will be promoted by the steam because the steam bubbles have a balloon tendency of their own which tends to carry the bubbles upward into the tubes at a rapid rate and when the bubbles are once in the tubes, they decrease the hydrostatic load that the pressure from the down tubes and the jet is overbalancing.

lVhile I have illustrated the honeycomb tubes as being all of the same size, it obvious that variations are possible, particuhirly that the downtiow tubes may be much tower in number provided they have the required down-flow capacity. The space thus saved may be devoted to upflow tubes, Also the entire core may he upflow, the down-flow being: through one or more large tubes, outside the radiator.

Even standard equipment radiators ot the automobile type vary so widely in construction and proportion and, when operated by my system, the water-carrying steam and steam-carrying water are so widely variable, that detailed consideration ot the "functioning under any one condition is likely to be misleading, but for general application o1 my invention, it may be well to note the following ditliculties that I have discovered and solved:

For instance, the tubes are characteristically long and thin. A straight cylindrical tube, say, 20 inches high. by one-quarter inch diameter will have a How section of only about one-twentieth of a square inch, so that its total cubic content is about 1 cubic inch. Consequently, if as much as one-quarter of" a cubic inch of steam is given opportunity to enter the tube as a single body, withoutbeing subdivided into further bubbles by surface tension. plus depth pressure, it'will fill about 5 inches of the tube; one-halt cubic the tube, such body or bubble of steam, whatever its length, will be squeezed between theabove described dominant pressure from below and the opposing' static pressure of the water above. so that primarily it will tend to assume the term of a cylindrical piston with its cylindrical surfaces yieldingly pressed toward the cold walls of the tube. The details if what will happen thereafter either to the condensate or to the bubble it rises in-the tube,need not be followed "fur-- ther than to explain that in its final stage of cooling and condensing .he body of steam collapses and the water i hes into the vacuum at high velocity, being impeller by both atmospheric and depth pressures. The Sull'lllfl uncushioned head-on collision in the tube between columns ol' incompi sible water, produces a violent shock or water hammer eli'ect which the thin radiator walls eli'ectively apply to the air as cracking and banging noises. This is a so aecaanpaaied by violent surgings of the. er in the upper chamber resultii'ig in excessive losses tlnrouggh the overflow pipe.

Underlcertainconditions the above opera.- tions occur, in repeating cycles. the .intlow of steam being by high velo ape-a h interu'iittently cut oil by up-rush l water, and the resulting noises and surgings are t practically and comn'lcrcially prohibitive violence.

In the present case, it will be found that the mixing, condensing and subdividing o't the steam in the injector whereby noise is prevented in the lower chamber, will greatly decrease the violence of the above described effects of steam that enters the tubes. The smaller bubbles are less piston like and the surrounding condensate aflores them better protection 'rom the walls ot the cooling tubes. Furthermore, it the bubbles are small enough, the noise of their collapse will be unnoticeable and a large number of them occurring continuously in. the same tube, there will be little or no surging.

However, if the injector action is e'lfcctive for forcing the desired circulation or" water in the tubes and preventing an oojcctioneble amount of noise in the lower chamber, proper distribution and practically noiseless condensation in the tubes may in ensured l y suitable flow resistances.

Flow resistances suitable for my present systen'i o't water circulation. are shown n my eon'ipanion application Scr. No. 128.31% tiled August 10. 1926, wherein the tul es have tlc-w-bafilinzr devices of such a character that they allord small opposition to normal. relatively low speed circulation, but atliord practically prohibitive resistance as against his-"h speed flow of water such as can produce ob jectionable noise e'tl'ects in the tn res when considerable bodies of steam collapse there inch ill till inches of the tube, etc. I. in. Such flOW-llzltillng devices have also an important function in decreasing the llow section and thereby promoting cut-on and bubble effects reducing sizes or the collapsible bubbles, limiting exposure of the bubble to cooling tube surface, etc, so that the action of the high velocity jet discharge need only ell'ective enough to keep up active circulation and prevent objectionable noise in the lower chamber.

Similar flow resistance ettcct-s are obtainal le without. special forms of flow resistance devices, by employing a honeycomb ot the so-called cellular type, wherein. the pas have v I or octagonal, or rectanguunarrangement, so that high velocity llow at short i is balilcd by abrupt tur's intervals.

Such a cellular honeycomb is schematically indicated in Fig. 5, wherein parts corresnonding to similar parts in the other ti 1 s are indicated by the same numerals but with a different evponent. In Fig. 5 the core or honeycomb consists of tubes 26. 527. in flattened or ribbon form, the width of each tube reprgsenting the entire thicl-mcss of the honeycomb which may he. say, 2 inches to 3 inches, so that it is possible to flex them to the rectangular arrai'igement shown.

In actual practice, each uptlow passage has to or more of these right angle deflections and they are only a quarter of: an inch so apart. Consequently. while ottering hardly more than simple friction resistance to ordinary slow flow of water, hi; ijh velocity flow of considerable columns of water such as will produce noise and water hammer effects is prevented by the rightangle impacts every quarter inch of: the way. each impact causing obstructing turbulence and whirls in the water. Consequently, the water hammer tendency, in so far as it has any e'tlect, is more likely to cause further mixing and subdividing of the steam bulb bles than to produce objectionable noise in the tubes or surging in the upper chan'iber. This is notwithstanding but rather because of the fact that such ribbon tubes may hare thin passages, only 1 to inch, l'll'lCli'. 'iu wl ich a bubble of any size may contact with both walls.

Fig. 7 is merely to illustrate that the pump may draw part or all of the jacket supply through an intake- 27* in the upper chamber, preferably adjacent the upper end ot the side uptlow tubes that are in best position to have their circulation. forced by the mo mentum of the stream discharged from the injector. Otherwise the construction is the same as in Fig. 5.

As to all forms of my invention, it will be unders ood that if the cooling capacity he CHOW... d, as may be the case when a tan belt breaks, thesystem will continue operative.

with more or less loss of steam and water until the water is substantially exhausted, the final stages of the operation being in accordance with the method specifically described in my said Patent No. l,378,72 l.

I claim 1. An internal combustion engine having a water and steam cooling circuit of inadequate radiating capacity, serially including a force feed pump supplying water to the jacket of the engine, an outlet discharging hot water and steam from the jacket into the lower chamber of an air. cooled radiator of the upright type having a multiplicity of small diameter cooling passages of great radiating capacity connecting a lower chamber of small radiating capacity with an upper chamber which has a high level overflow outlet, and in combination with said parts, means for maintaining a circulating body of water submerging and upllowing through some of said cooling passages and downward through others, said means including a discharge means arranged to discharge warm water and then hot water and the steam from the engine lengthwise along a region of said body of water that is below and in proximity to the lower ends of most of said passages and to draw water from a region below other passages.

2. An internal combustion engine having a water and steam cooling circuit of inadequate radiating capacity, serially including a force feed pump supplying water to the jacket of the engine, an outlet discharging hot water and steam from the jacket into the lower chamber of an air cooled. radiator of the upright type having a multiplicity of small diameter cooling passages of great radiating capacity connecting a lower cham ber of small radiating capacity with an upper chamber which has a high level overflow outlet, and in combination with said parts, means for maintaining a circulating body of water submerging and upflowing through some of said cooling passages and downward through others, said means including a discharge means arranged to discharge warm water and then hot water and the steam from the engine lengthwise along a region of said body of water, that is below and in proximity to the lower ends of most of said passages and to draw water from a region below other passages; said regions being sepa' rated by partition means.

8. An internal combustion engine having a water and steam cooling circuit of inadequate radiating capacity, serially including a force feed pump supplying water to the jacket of the engine, an outlet discharging hot water and steam from the jacket into the lower chamber of an air cooled radiator of the upright type having a multiplicity of small diameter cooling passages of great radiating capacity connecting a lower chamber of small radiating capacity with an upper chamber which has a high level overflow outlet, and in combination wvith said parts, means for maintaining a circulating body of water submerging and upiiowing through some of said cooling passages and downward through others, said means including an injector discharge device in the lower chamber arranged to discharge hot fluid from the engine lengthwise along a region of said body of water that is below and in proximity to the lower ends or a large number of said cooling passages.

4. An internal combustion engine having a water and steam cooling circuit of inadequate radiating capacity, serially including a force feed pump supplying water to the jacket of the engine, an outlet discharging hot water and steam from the jacket into the lower chamber of an air cooled radiator of the upright type having a multiplicity of small diameter cooling passages of great radiating capacity connecting a lower chamber of small radiating capacity with an upperchamber which has a high level overflow outlet, and in combination with said parts, means for maintaining a circulating body of water submerging and upllowing through some of said cooling passages and downward through others, said means including an injector discharge device in the lower chamber arranged to discharge hot fluid from the engine lengthwise along a region of said body of water that is below and in proximity to the lower ends of a large number of said cooling passages, the suction intake of said injector being in proximity to the lower ends of relatively few cooling passages.

5. An internal combustion engine having aiwater and steam cooling circuit of inadequate radiating capacity, serially including a force feed pump supplying water to the jacket of the engine, an outlet discharging hot water and steam vfrom the jacket into the lower chamber of an air cooled radiator of the upright type having a multiplicity of small diameter cooling passages of great radiating capacity connecting a lower chairiber of small radiating capacity with an upper chamber which has a high level overflow outlet, and in combination with said parts, means for maintaining a circulating body of water submerging and upllowing through some of said cooling passages and downward through others, said means including an injector discharge device in the lower chamber arranged to discharge hot fluid from the engine lengthwise along a region of said body of water that is below and in proximity to the lower ends of a large number oi said cooling passages, the suction intake of said injector being in proximity to the lower ends of relatively few cooling passages, and partition means separating the intake region trom the discharge region.

6. An internal combustion engine having a water and steam cooling circuit 0"" inadequate radiating capacity, serially including a force teed pump siiipplying water to the jacket of the engine, an outlet discharging hot water and steam from the jacket into the lower chamber of an air cooled radiator oi? the upright type having a nmltiplicity of small diameter cooling passages oi great radiating capacity connecting a lower chamber of small radiating capacity with an upper chamber which has a high level overtlow outlet, and in combination with said parts, means for maintaining a circulating body oi? water subi'nerging said cooling passages, uptlowing through some o't them and downward through others, said means including a discharge device having a multiplicity of out-lets arranged to cause high velocity discharge of hot water and steam "from the engine lengthwise along a region of said body of water that is below and in proximity to the lower ends of a large number of said cooling passages, the intake of the pump being arranged to maintain an active. cycle of boiling and condensing varying with the operations of the automotive parts, by withdrawing highly heated water from the region oii said hot water discharge in said lower chamber.

7. An internal combustion engine having a water and steam cooling circuit of inadequate radiating capacity, serially including a force teed pump supplying water to the jacket of the engine, an outlet discharging hot water and steam from the jacket into the lower chamber of an air cooled radiator of the upright type having a multiplicity 01 small diameter cooling passages of great radiating capacity connecting a lower chamber of small radiating capacity with an upper chamber which has a high level overtlow outlet, and in combination with said parts, means for maintaining a circulating body of water submerging and upilowing through some of said cooling passages and downward through others, said means including a discharge device for hot water and steam from the engine, discharging from one side of the lower chamber lengthwise along a region of said body of water that is below and in proximity to the lower ends of the central passages as well as those beyond the same.

8. i-in internal combustion engine having a water and steam cooling circuit of inade- (plate radiating capacity, serially including a force feed pump supplying water to the jacket of the engine, an outlet discharging hot water and steam from the jacket into the lower chamber of an air cooled radiator oi the upright type having a multiplicity of small diameter cooling passages of great radiating capacity connecting a lower cham ber of small radiating capacity with an upper chamber which has a high level overtlow outlet, and in combination with said parts, means for maintaining a circulat ng body of water submerging and upflowmg through some of said cooling passages and downward through others, said means including a discharge device for hot water and steam from the engine, discharging from one side of the lower chamber lengthwise along a region of said body of water that is below andin proximity to the lower ends of the central passages as well as those beyond the same, said discharge device being in the form of an injector nozzle with a tube surrounding the jet therefrom.

9. An internal combustion engine having a water and steam cooling circuit of inadequate radiating capacity, serially including a force ttecd pump supplying water to the jacket of the engme, an outlet discharging hot water and steam from-the acket into the lower chamber of an air cooled radiator of the upright type having a multiplicity of small diameter cooling passages of great radiating capacity connecting a lower chamber of small radiating capacity with an upper chamber which has ahigh level overflow outlet, and in combination with said parts, means for maintaining a circulating body of water submerging and upfiowing through some-of said cooling passages and downward through others, said means including a discharge device for hot water and steam from the engine, discharging from one side of the lower chamber lengthwise along a region of said body of water that is below and in proximity to the lower ends of the central passages as well as those beyond the same, saiddischarge device being in the form of an injector nozzle with a tube surrounding the jet therefrom, the tube and the jet being a single casting.

10. An internal combustion engine having a water and steam cooling circuit of inadequate radiating capacity, serially including a force teed pump supplyin water to the jacket of the engine, an outfet discharging hot water and steam from the acket into the lower chamber of an air cooled radiator of the upright type having a multiplicity of small diameter cooling passages of great radiating capacity connecting a lower chamber of small radiating capacity with an upper chamber which has a high level overiiow outlet, and in combination with said parts, means for maintaining a circulating body of water submerging and upflowing through some of said cooling passages and downward through others, said means including a discharge device for hot water and steam from the engine, discharging from one side of the lower chamber lengthwise along a region of said body of water that is below and in proximity to the lower ends of the central passages as well as those beyond the same, said discharge device being in the :torm of an injector nozzle with a tube surrounding the jet therefrom, the tube and the jet being a single casting and having support means whereby the tube and also the inlet end of the nozzle are anchored in and to the lower chamber.

Signed at Plainfield, in the county of 10 Union. and State of New Jersey, this ninth day of August, A. D. 1926.

SAMUEL W. RUSHMORE.

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