US2862483A - Engine cooling system - Google Patents

Description

Dec. 2, 1958 E. w. RoHRBAcHER ET AL 2,862,483

ENGINE COOLING SYSTEM 2 Sheets-Sheet 1 Filed 00's. 4. 1954 E. w. ROHRBACHER ET AL 2,862,483

ENGIN COOLING SYSTEM Y De'c. 2, 1958 United States Patent C)l ENGINE cooLlNG SYSTEM Application october 4, 1954, serial No. 460,205 13 claims. (AC1. 12s-41.73)

This invention relates to cooling systems for internal combustion engines and has particular relation to an improved cooling system especially applicable for V-type, 8cylinder internal combustion engines for automotive and other uses. Y

It has been the practice heretofore to construct cooling systems for internal combustionengines by providing cooling cavities in the heads and blocks of engines and then supplying cooling liquid to and exhausting cooling liquid from these cavities. To provide a good cooling system it has been the practice to make these cavities as large as possible within the space and cost limitations applicable, it having been assumed that the availability of large quantities of'cooling liquid adjacent the parts to be cooled would provide the best cooling system possible. However, it now appears that in these systems thecooling liquid supplied generally circulated between the cavity inlets and outlets by the shortest possible path or by the path oifering the least restriction to the flow of cooling liquid. Since the cavities were large the cooling liquid had a tendency to stratify in other parts of the cavities and to circulate only by thermosyphon circulation caused by the adjacent heated parts of the engine or by entrainment in the stream of cooling liquid owing between the inlet and the outlet for the cavities. Since the most highly heated parts of the engine were usually not in the shortest path between the inlet and the outlet or the path where there was less restriction to the flow of cooling liquid-between the inlet and the outlet, the parts requiring the greatest cooling often were provided with the least effective means for cooling. Also, the provision of largecooling cavities tended to enclose parts that did not require cooling. .This caused the heat rejection to the cooling liquid to -be excessive and required excessive and unnecessarily expensive heat radiating means for the engine.

It is proposed to limit the size of the cooling liquid cavities in an internal combustion engine and to provide means for directing the circulation of cooling liquid within the cavities so that substantially all of the cooling liquid in the cavities will be compelled to follow definite circulation paths within the cavities and over the parts of the engine that especially require cooling by the cooling liquidA supplied to the engine. The reduction in the size of the cooling cavities particularly in the heads of the engine tends to exclude from the cavities various heated parts of the engine that do not require cooling. Since this decreases the amount of heat that must be absorbed by the cooling liquid circulated throughout the engine, it is possible to employ a smaller and much less expensive radiator for the engine. In these cooling cavities of reduced size it is proposed to provide vmeans for creating a definite and continuous circulation throughout the cooling cavities of the engine so that the cooling liquid will be positively circulated over all the heated parts ofl the engine that require cooling. Hence the stratification of liquid in various parts of the cooling cavities where .cooling is required will be greatly reduced if not entirely 2,862,483 Patented Dec. 2, 1958 eliminated. In parts of the engine where space limitations might require the construction of narrow passages and in parts through which the circulation of cooling liquid would be diicult it is proposed to employ cooling by conductivity through the metallic parts of the engine to places where better circulation of cooling liquid can be obtained. This also reduces the rejection of heat to the cooling liquid of the engine and therefore decreases the size of the radiator due to the factv that these heat conducting parts also radiate heat to various objects adjacent the engine and are cooled by the air surrounding ice the engine so that the amount of heat that must be con` will insure against stratification of the cooling liquid in places where circulation is required.

In the drawing:

Figure 1 is a fragmentary end elevational view of an engine having various parts thereof broken away and shown in cross-section to better illustrate the features of the cooling system employed in the'engine.

Figure 2 is a plan view of the engine disclosed by Figure l.

Figure 3 is a cross-sectional view taken substantially in the plane of line 3-3 on Figure 1 and having various parts of the structure broken away and illustrated in cross-section to better illustrate the features of the cooling system embraced in the heads of the engine.

lFigure 4 is a diagrammatical illustration of the operation of the cooling liquid distribution nozzle disclosed by Figure 5 and showing how the nozzle distributes the cooling liquidthroughout the lower part of the inside cavities in each bank of cylinders of the block.

Figure 5 is a cross-sectional view taken through the front wall of the engine and illustrating a cooling liquid distribution nozzle employed in the cooling system embracing the invention.

Figure 6 is anend View of one ofthe distribution nozzles as illustrated by Figures 4 and 5.

The engine 10 embodying the invention comprising an engine block 11 in which parallel rows vof obliquely disposed'cylinders 12 are formed. Pistons 13 are adapted to reciprocate in the cylinders 12 in response to the operation of connecting rods 14 which are rotated and reciprocated by the crankshaft 16 of the engine. The cylinders 12 are formed by cylinder walls 17 and are surrounded by cooling cavities 18 which are formed within the outer or cooling liquid jacket walls 19 of the block 11. The cavities 18 extend between and at the ends of the rows of cylinders 12 and throughout the length of the rows of cylinders 12 and on opposite sides thereof. The cylinders 12 are closed by heads 21 secured tothe block 11 by bolts 22. The heads 21 provide ring chambers 23 for each of the cylinders 12 and in which spark plugs 24 and inlet and exhaust valves 26 and 27 respectively are provided. The ringrchambers 23 and the ports for the inlet and exhaust valvesv26 and 27 are formed in inner walls 28 of the heads 21 which close the ends of the cylinders 12 and directly engage the outer end surfaces of each cylinder bank of the block 11. The heads 21 contain cooling liquid cavities 29` which are provided by cooling liquid cavity or jacket walls 31 which enclose a limited amount of space upwardly of the inner walls 28 and adjacent the ring chambers 23. Inlet passages 31 and the exhaust passages 32 lead inwardly and outwardly respectively through the cavities 29 and from the inlet valves 26 and the exhaust valves 27. The exhaust passages extend outwardly to branch passages 25 leading to exhaust manifolds 33 and the inlet passages 31 extend inwardly to branch passages 34 leading to one or the other of the maindistribution passages 3 6 of the 4inlet manifold 37 of'the engine 10.' Itispioposed to construct the walls 38u forming the exhaus'tpassages 32 in such manner as to extend the exhaustspa'ssages 32 upwardly andoutwardly 'fromv the cylinders'` 12 of thev engine vwith as little curvature as is possible in the exhaust passages`32. Then itlis proposed to construct the outerlside walls 39 of the heads 21 to intersect the outer ends of the passages 32 substantially normally and to extend upwardly from the outer sides of theheads 21 substantially in-parallel 'relation to the vertical yplane of the engine. This will provide' exhaust passages of minimum length which will be adequately cooled adjacent the exhaust valve stem guidesv 41 and the ports in'which the exhaust valves 27 are seated. -It is only for the purpose of lcooling the exhaust valvestetn guides and' the exhaust ports that it is necessary `te cool any `of the wallsin which the exhaust passages'32 are formed. It is considered preferable to provide a separate exhaust ypassage 32 for each of the exhaust valves 27 of the engine so that the walls 33 may extend vdirectly to the side walls 39' and therefore be of minimum length.

It is also proposed to form the ,inner walls 42 of the heads 21 to extend substantially in' parallel relation to the axes of the cylinders 12 and to intersect the walls forming the inlet passages 31 substantially normally. It has been the practice heretofore to dispose the walls 42 outwardly toward the inlet manifold' and to secure the inlet manifold to the inner walls of the heads. This has been done to increase the size of the cooling cavities in the heads as may be seen from the fact that the walls of the inlet passages are cooled by the incomingcharge and do not require cooling by the cooling liquid of the engine. In the present instance it is proposed to move the inner walls 42 inwardly to enclose within the heads only the space immediately above the cooling cavities 18 on the inside of the cylinders 12 and to reduce to a minimum the cooling liquid cavity 29 within the heads 21. The outer walls 44 of the heads 21 may be disposed substantially in parallel relation to the inner walls 28 and in ,spaced relation to the walls forming the outlet passages 31 except at the outer edges thereof where they maybe turned *outwardly slightly in normal relation to the stems for the valves 26 and 27. It will be noted that the walls 39, 42 and 44 of the heads are positioned to include as little as possible of the walls forming the inlet and exhaust passages extending through the head to reduce the cavities 29 to a minimum size.

Y A pump 46 may be bolted or otherwise secured at 47 i to thefront ofthe block 11 for the purpose of supplying cooling liquid, preferably water, to the cooling cavities 18 and 29 in the block and heads of the engine. Any suitable pump may be employed although in the present instance it is considered preferable to employ a pump with an impeller 48 having vanes 49 which are substantially radially disposed at the outer extremities thereof and curved inwardly at the inner extremities thereof to lead the vanes 49 as in Figure 1 the impeller 4S rotates in a clockwise direction. It is customary to drive the impeller 48 by employing a shaft 51 on which the fan of the engine is mounted. This necessitates securing the casing 52 of the pump to the front wall of the engine near the upper part of the block 11. Outwardly of the impeller 48 it is considered preferable to provide an enlarged distribution chamber 53 which completely surrounds the impeller 48 and tapers in opposite directionsV toward outlet passages 54 leading from the pump casing. The outlet passages S4 at each end of the distribution chamber 53 are adapted tofcommunicate with inlet openings formed in the front wall 56 of the block 11 near the upper extremities of the c avities v43 thatextend the-length of Atheblock 11 and inside-the cylinders 12. Nozzles 57 are adapted to be pressed in the openings in the wall 56 to extend inwardly of the cavities 43 at one side of the walls 17 of the cylinders 12. Orifces 58 are provided in the rounded outer ends 59 of the nozzlesV 57. The orices 58 are not as Wide as the nozzles 57 and are elongated in planes between and parallel to the yinner surfaces of the inner side walls of the block 11 and the adjacent surfaces of the walls 17 of the cylinders 12. The orifices 58 are also formed in the roundedends 59 of the nozzles 57 so that the upper extremities of the orifices intersect theside walls of the nozzles toward the extreme ends of the Vnozzles -and beyond the place where the rounding of the ends cornmences. This results in the ends of the nozzles adjacent the upper ends of the orifices 58 forming curved and downwardly directed deflection means 59 adjacent the extremities of the nozzles 57. The lower ends of the oriiices 58 are adapted to extend beyond the rounded ends 59 and to terminate toward the opposite ends of the nozzles 57. Since theoriiice's 58 are not as large as the outlet passages 54 nor the parts of the nozzles 57 leading to the oriiices 58 it will be apparent that the velocity of the cooling liquid owing through the orifices 58 will be increased by the orices 58 to discharge the cooling liquid into the upper parts of the inner cooling cavities 43 in high velocity streams as is indicated by the Vflow lines in Figure 4. The upper parts 59 of the rounded ends of the nozzles will cause these streams to be discharged downwardly in the inner cavities 43 and the narrow and elongated form of the orifices 58 will cause these streams to be directed toward the bottom of the cavities 43 and substantially throughout the greater part `of the length thereof. At'the lower extremities of the cavities 43 it will be apparent that the cooling liquid in fthe streams discharged by the nozzles 58 will be dellected between the lcylinders 12 and to the lower extremities of the elongated cavities 61 on the outer sides of the cylinders 12. Therefore, the pump 46 will supply cooling liquid to the lower extremities of the cooling cavities 18 in the block 11 and substantially through@ out the length of the block 11. l

As the ycooling liquid in the cavities 18 is displaced upwardly by the continuous supply of cooling Vliquid through the nozzles 57 the cooling liquid will absorb heat from the cylinder `walls 17 for cooling the cylinders and the pist-ons v1? reciprocating therein. It will also'be apparent that the temperature of the cooling liquid will increase as it approaches the-upper extremities of the cylinders and that there wil-l be no by-pass through the cooling cavities 18 vwhere'theliquid supplied'by the pump 46 may-take the shortest path of movement between the pump outlets .54 and the upper extremities of the cyl-l inders 12. v

It is proposed to transfer the coolingliquid from Vthe block cavities 18 to the head cavities `29 principally through the pairs of mainsupply passages indicated at 62 and 63. The supply passages 62 and 63 maybe formed through the lower walls of the heads and the upper walls of the block in parallel relation to the axes of the cylinders 12.v vIt is proposed to locate the passages 62 on the outer sides of the heads 29 and immediately within the outer side walls 39 which are not disposed in parallel relationto'the axes of the cylinders 12 lbut in substantially parallel .relation to the central vertical plane of the engine l10. Itis proposed to locate one of the main supply passages 62 between each lpair of the cylinders 12. In each pair of the cylinders 12 it is proposed to arrange the inlet valves 26 on the adjacent sides of the cylinders and the exhaust valves 27 on the opposite sides of the cylinders with the valves extending substantially across diameters of the cylinders and substantially aligned throughout the length of each head.- It is therefore proposedv to arrange the main supply passages 62 adjacent the outer side walls 39 and between pairs vof the cylinders 12in which the inlet valves 26 are disposedonadjacent sides ofthe cylinders. The supply passages 62 therefore will be located a consider- .passages 63 are the inlet passages 31 able distancefrom the exhaust passages 32 which extend directly outwardly from the exhaust valves 27. The main supply passages 63 are to be located directly across the heads 21 from the passages 62 'and in close proximity to inwardly directed parts 64 of the inner side walls 42 of the heads 21. The passages 63 are therefore located between pairs of the cylinders 12 and on the inlet valve sides of the cylinders 12. Immediately above the supply by which combustible mixtures are supplied to the( cylinders 12. Since the inlet valves 26 are on adjacent sides of pairs of the cylinders 12 it will be apparent that the inlet passages 31 for each pair of the cylinders 12 may be brought together closely enough so that a common dividing wall may be provided between adjacent passages 31 for the pairs of the cylinders 12. It is proposed to form the inlet passages 31 of. substantially rectangular crosssectional configuration between the inlet valves 26 and the inner extremities .of the heads 21. Under such circumstances the lower walls ofl each pair of inlet passages 31 will be substantially flat. Since the inlet passages 31 are directed inwardly of the heads 21.and toward the branch passages in the inlet manifold 37 it is possible to position the common lower wall for each pair of the inlet passages 31 in spaced relation to the inner walls 28 ot' the heads 21 with the inner extremities of the lower walls merging with the inner walls 28 around the seats for the inlet valves 26 and the outer extremities thereof closely approaching the inner walls 28 adjacent the inner side walls 42. Under such 'circumstances it will be apparent that the common lower walls of the pairs of inlet passages for the pairs of cylinders in each head will provide circulation deectionbaies 66 immediately above each of the main supplypassages 63. It will be apparent that when streams of water discharged'into the heads 21`through the mainsupply passages 62 and 63, the streams from the supply passages 62 will move upwardly in the cavities 29 and along the outer side v walls 39 of the heads which are disposed obliquely and are directed inwardly with respect to the streams. However, the streams of liquid supplied by the passages 63 will flow inwardly of the cavities 29 and directly against the circulation batlies 66 provided by the lower walls of adjacent pairs of the inlet passages 31. These streams of liquid discharged by the supply passages 62 and 63 willcause a circulation of liquid in the lower parts of the cavities 29 in planes extending transversely of the engine heads and substantially throughout the entire length of the engine heads. This will be apparent when it is considered that the streams -of liquid discharged by the main supply passages 63 are prevented from owing upwardly in the cavities 29 `by the batlles 66, are prevented from flowing outwardly by the inwardly extending parts 64 of the outer side walls 42, are prevented from'flowing directly across the cavities 29 by the inlet valves 26 and therefore must divide to form two streams which flow outwardly of the baffles 66 and toward the exhaust valves 27 on opposite sides of each pair of the cylinders 12. It will be noted that each cylinder of the engine has five of the bolts 22 for securing the heads 21 tothe block 11. The bolts 22 are arranged inv three rows throughout the length of the engine with the middle row of bolts extending through bolt columns 67 and the inner row extending through bolt columns 68. It will be noted that one of the bolt columns 67 is positioned between each pair of the cylinders 12 and immediately adjacent the supply passages 63. These bolt columnswill cause the streams of liquid supplied by the passages 63to divide immediately adjacent the passages 63 to ow around the columns 67 and the places where the lower walls of the pairs of inlet passages 31 merge with the inner walls 28. Also, it will be noted that a pair of the` bolt columns 68 are located on each side of the supply passages 63 and Ain a position to deect the divided streams toward the exhaust valves 27. It will therefore be apparent that the divided streams 6 of liquid supplied by the supply passages 63. will flow outwardly from beneath the baiiie 67 and toward the ends of the exhaust passages 32 which communicate with the exhaust valves 27 and which extend v across the heads 21 in a direction opposite that in which the inlet passages 31 extend. It will be further apparent that the streams of liquid directed upwardly by the supply passages 62 and deilected inwardly by the side walls 39 will entrain liquid in the parts of the cavities 29 between the exhaust passages 32. The liquid so entrained will result in low fluid pressure areas beyond the inner ends of the inlet passages 31 and adjacent the outerends of the exhaust passages 32. Since iow pressure areas will cause the divided streams of liquid supplied by the passages 63 to flow around the ends of the walls 38 in which the exhaust passages 32 are formed and to cool the walls 38 and particularly 'the parts of the walls 38 adjacent the exhaust ports formed inthe lower walls 28. .It will be noted that the baiile 66 will direct the divided streams outwardly and immediately-adjacent the lower walls 28 and directly toward the exhaust valve seats. After the divided streams of liquid flow around the ends of the exhaust passage walls 38 the liquid will move upwardly along the walls 39 as the liquid is entrained in the streams .of .liquid discharged by the main supply passages 62.

This movement of liquid around the inlet valves and V'across the heads adjacent the lower walls 28 and upwardly adjacent the vside walls 39 will result in a circulation of liquid transversely of the heads and about an axis extending throughout the length of the heads and nor.-

mally intersecting theparallel transverse planes through the axes of the cylinders 12. This will be apparent when itis considered that at the upper extremities of the walls 3,9 the liquid will engage the upper walls 44 and particularly the outer extreme parts rof the upper walls 44 which are v constructed in such a way as to be normal to the axes of the stems of the valves 26 and 27. These parts of the upper walls44 will deflect the liquid downwardly and inwardly and toward the upper walls of the pairs of inlet passages 31' and toward the space between and on opposite sides of the pairs of inlet passages 31. The liquid that is directed between and on opposite sides of the pairs of inlet passages 31.will be entrained in the divided streams of liquid flowing outwardlyfrom beneath the innerextremities of the baie 66. The' liquid engaging the upper walls of the pairs of inlet passages 31 will be deflected in opposite directions to be entrained in the liquid moving downwardly between the pairs of inlet passages. It will, therefore, be apparent that instead of the liquid introduced into the heads merely ilowing upwardly in the heads and outwardly through the path vof least resistance the liquid will be compelled to circulate inv the heads and over the walls of the tiring chambers 23 and across the parts of the wallsin which the exhaust 'ports are formed, these being thefparts of the heads that need' the greatest cooling.

It will be noted that the outer side walls 39 merge with the inner walls 28' of the heads at the large ends of the ring chambers 23 which are formed in the inner walls 28 of the'heads. The walls 39 also merge with bosses 71 through which pairs of the bolts 22 located on opposite sides of the spark plugs for each cylinder extend. The bosses 71 and the merging walls 39 and 28 at the larger 'ends of the firing chambers 23 form relatively thick wall sections 72 which vprovide relatively low resistance paths for conductivity of heat from the larger ends of the firing chambers 23 and from around the spark plugs 24. The wall sections 72 are surrounded bythe cavities 29 in the heads 21V and the cavities 18 in the block 11. These thick wall sections indicated at 72 and the bosses 71 therefore will rapidly conduct heat to the cavities 29 and 18 and to parts of they cavities 29 and 18 where relatively wide surface areas at they edges of thepsections 72 are exposed to the cooling liquid in the cavities 29 and 18. In order to increase the conductivity between the sections 72 and the walls of the block 19 so that the heat from the sections 72 may. be more rapidly absorbed by the liquid in the cavities 18 in the block it is proposed to employ metallic head gaskets 73 which will conduct heat better than asbestos or other gaskets which may be employed.

It willv be noted that the upper parts of the cavities 29 in the heads 21 are the inner parts of the cavi-ties and that these .inner parts are relatively remote from the parts in which liquid is circulated across the exhaust valve ports and the tiring chambers of the engines. Cooling liquid therefore may tend to stratify in the upper parts of the cavities 29, particularly above the walls forming the inlet passages 31and between the upper parts of the side walls forming the passages 31. The stratified `cooling liquid in such parts of the cavities 29 therefore is free to move lengthwise of the heads where at the front ends of the heads outlet passages 74 are formed. The outlet passages 74 are adapted to communicate with a passage 76- formed in manifold 77 eX- tending across the heads 21 at the front of the engine. The outlet 78 from the manifold 77 may be connected to the radiator of the engine which by reason of the improved cooling system previously described may be greatly reduced in heat radiating surface and cost. The heads 21 may be made reversible if this is desired and Vin such instance the outlet passages 74 will be provided at each end of the heads 21. With such passages 74 provided at each end of the heads the passages at the rear of the heads may be closed by walls 76 extending from the connecting wall 77 in which the inlet and cooling liquid manifolds 37 and 77 respectively may be formed.

At places in the cavities 29 which are somewhat remote from the main supply passages 62 and 63 it may befound desirable to provide secondary supply passages indicated at 75. These may be employed to supply additional cooling liquid -from the cavities in -the block to the cavities in the head and to prevent stratiiication of liquid in the remote parts vof the cavities of the heads. Also, one of these auxiliary passages which is indicated at 78 may be positioned aboutthe middle of the cavities 29 and adjacent the exhaust cross-over passage 79; The .passage 79 -leads -fromone of the exhaust passages 32 toward the middle of the engine and communicates with the exhaust heating passage 81 which is formed in the connecting wall 77 and which is employed for heating the inlet mani- Afold37.

We claim:

15. A cooling system for an 4internal combustion engine comprising an engine block having a row of cylinders formed therein and cooling liquid cavities surrounding said cylinders throughout the length of said block, a head forsaid cylinders secured to said block and having cooling liquid cavities formed therein, a pair of inlet passages formed in said head and extending through said cavities in said head from inlet portsleading to an adjacent pair of said cylinders and terminating in a sidewall of said head, said inlet ports being disposed on adjacent sides of. said pair of cylindersl and said pair of inlet passages being formed fromsaid ports to said side walls to include a commonl lower wall extending laterally in said head in spaced relation to the lower wall of said head, a pair of spaced exhaust ypassages formed in said head and extending'from exhaust ports formed on opposite sides of said inlet ports and terminating in an opposite side walll of said` head, a cooling liquid supply passage extending between said cavities in said head and block andformed in the lower wall of said head and adjacent said one side wall of said head and between the opposite edges of said common lower wall of said inlet passages and being positioned to discharge a stream of cooling liquid into said head and against said common lower wall of said inlet passages, saidvstream of cooling liquid being directed to engage said common lower wall ofsaid inlet passages and to be deflected by said lower wall and said one side wall to form two streams of cooling liquid flowing toward said opposite'wall and outwardly from beneath saidl common lower wall and against the `-inner ends of said exhaust ,passages adjacent saidvexhaust. ports, and means for exhausting said cooling. liquid from said head.

2. A cooling system for an internal combustion engine having an engine block and a pair of cylinders formed therein and comprising a head secured to said block and upon said cylinders and having cooling cavity means formed therein, a pair of inlet and exhaust valves disposed in said head and in opposed relation to the ends of each of said cylinders, said inlet valves being disposed on adjacent sides of adjacent cylinders and said exhaust valves being disposed on the opposite sides of said adjacent cylinders, a pair ofexhaust passages formed in said head and extending across said cooling cavity means from said exhaust valves in saidl adjacent cylinders to one side wall of said adjacent head, means disposed between said cylinders and onthe side of said adjacent cylinders opposite said exhaust passages for directing a column of cooling liquidvupwardly within said cooling cavity means, a battle formed in said head in opposed relation to said column and extending from the opposite side wall of said head toward said inlet valves and in spaced relation to the inner wall'of said head, said bailie being formed to terminate in said-inner wall and adjacent said inlet valves and between said exhaust valves and said exhaust passages to provide oppositely disposed outlets from between said bai-lle and said inner wall, said baiie being positioned to direct said uid suppliedby said column of fluid from beneath said baille around said inlet valves and upon Vthe inner extremities of said exhaust passages.

3. A cooling system for an-internal combustion engine as defined by claim 2 and.in which another means is provided in said inner wall of said head for discharging a column of cooling liquid upwardly into said cooling ,cavity means, said other means being located adjacent said opposite wall of said head and between said cylinders and between said pair of exhaust passages.

4. A method of cooling a cylinder of an internal cornbustion engine having a cavity in the head of the cylinder for cooling liquid for cooling the cylinder and in which said head isformed to provide inlet and exhaust passages communicating with said cylinder and extending across said cavity and comprising, moving cooling liquid in said cavity from the outlet toward the inlet end of said inletv passage, thenmoving said liquid along the lower wall of said head and toward and into contact with the inlet end of said exhaust passage and along said exhaust passage toward theV outlet'- end of said exhaust passage, and thereafter moving said liquid away from said exhaust passage and toa part of said cavity adjacent the inlet end of said inlet passage. 4 5. A method of cooling a cylinder of an internal cornbustion engine havinga cavity in the Ihead of the cylinder for `cooling liquid for cooling the cylinder and in which said head is formed toy provide an exhaust passage cornrmunicating with Said cylinder and extending across said cavity, and comprising, moving cooling liquid in said cavity towardsand'into contact with the inletrend of said exhaust passage and along said exhaust passage toward the outlet end of saidexhaust passage, and thereafter moving said liquid away from said outlet end of said exhaust passage and toward said inlet end of said exhaust passage.

6. A method of cooling a cylinder of an internal combustion engine having a cavity in the head yof the cylinder for cooling liquid for cooling the cylinder and in which said head is formed to provide an yexhaust passage extending across said cavity, and comprising, supplying cooling liquid to said cavity in a continuous stream during the operation of said engine, directing said stream at the inlet end of said exhaust passage, continuing the movement of said stream towardl the outlet end of said exhaust passage, reversing the movement of said stream by .moving said liquid away from said outlet end of said exhaust passage and toward said inlet end of said exhaust passage, dividing said stream adjacent the inlet end of said exhaust passage and exhausting some of said liquid from said cavity, and thereafter directing the remaining part of said stream toward the inlet end of said exhaust passage.

7. A method of cooling a cylinder of an internal combustion engine having a cavity in the head of the cylinder for cooling liquid for cooling the cylinder and in which said head is formed to provide an exhaust passage communicating with said cylinder and extending across said cavity, and comprising, supplying cooling liquid to said cavity in a pair of continuous streams during the operation of said engine, directing one of said streams toward the inlet end of said exhaust passage and transversely of said cylinder and toward the outlet end of said exhaust passage, and directing the other of said streams transversely of said exhaust passage and adjacent the outlet end of said exhaust passage.

8. A method of cooling the cylinders of an internal combustion engine in which the cylinders are arranged in a row and having cavity means in the head means for said row of cylinders for cooling liquid for cooling said cylinders and in which said head means is formed to provide oppositely directed inlet and exhaust passages communicating with said cylinders and with the inlet and outlet ends thereof terminating in opposite side walls of said head means and comprising, supplying and exhausting cooling liquid to and from said cavity means in said head means, and rotating said liquid in said cavity means about an axis extending longitudinally of said head means and transversely to the axes of said cylinders and in a direction to move along the inner wall of said head means from the inlet side to the exhaust side of said head means. y

9. A method of cooling the cylinders of an internal combustion engine in which the cylinders are arranged in a row and having a cavity in the head for said row of cylinders for cooling liquid for cooling said cylinders and in which said head is formed to provide oppositely directed inlet and exhaust passages communicating with said cylinders and with the inlet and outlet ends thereof terminating in opposite side walls of said head, and cornprising, continuously supplying and exhausting cooling liquid to and from said cavity in said head, directing said cooling liquid supplied to said head against said inlet passages on one side of said head, and directing said cooling liquid supplied to said head between said exhaust passages on the opposite side of said head.

10. A method of cooling the cylinders of an internal combustion engine in which the cylinders are arranged in a row and having a cavity in the head for said row of cylinders for cooling liquid for cooling said cylinders and in which said head is formed to provide oppositely directed inlet and exhaust passages extending across said cavity and communicating with said cylinders and with the inlet and outlet ends thereof terminating in opposite side walls of said head and with the lower walls of said passages spaced from the lower wall of said head, and comprising, supplying and exhausting cooling liquid to and from said v10 cavity in said head, directing said cooling liquid supplied to said head against said lower walls o said inlet passages on one side of said head and directing said cooling liquid supplied to said head between said exhaust passages on the opposite side of said head.

ll. A cooling system for an internal combustion engine having cylinders arranged in a r-ow and having a cavity in the head for said row of cylinders for cooling liquid for ycooling said cylinders and in which said head is formed to provide oppositely directed inlet and exhaust passages extending through said cavity and communicating with said cylinders and with the inlet and outlet ends thereof terminating in opposite side walls of said head and with the lower walls of said passages spaced from the lower wall of said head, and comprising means for directing cooling liquid against the lower Walls of said inlet passages and toward the inlet ends of said exhaust passages, and means for supplying cooling liquid to and for exhausting cooling liquid from said cavity.

12. A cooling system for an internal combustion engine having cylinders arranged in a row and having a cavity in the head for said row of cylinders for cooling liquid for cooling said cylinders and in which said head is formed to provide oppositely directed inlet and exhaust passages extending through said cavity and communicating with said cylinders and with the inlet and outlet ends thereof terminating in opposite side walls of said head and with the lower walls of said passages spaced from the lower wall of said head, and comprising, means for directing a stream of cooling liquid against the walls of said inlet passages and toward the inlet ends of said exhaust passages and along the walls of said exhaust passages toward the outlet ends of said exhaust passages, and means for supplying cooling liquid to and for exhausting cooling liquid from said cavity.

13. An internal combustion engine having a row of cylinders and a head for said row of cylinders, said head being formed to provide a cooling liquid cavity therein for cooling said cylinders, a pair of inlet passages having a common lower wall spaced from the lower wall of said head and entering said head through a side wall of said head and communicating with adjacent sides of a pair of said cylinders, a pair of outlet passages formed in said head and communicating with opposite sides of said pair of cylinders and having the outlet ends thereof terminating in an opposite side wall of said head, means for discharging cooling liquid into said head and against said common lower wall of said inlet passages, and means for discharging cooling liquid into said head and into the space between said exhaust passages.

References Cited in the file of this patent UNITED STATES PATENTS 2,175,448 Schlagintweit Oct. 10, 1939 2,182,990 Kishline Dec. 12, 1939 2,186,080 Sheldrick Jan. 9, 1940 2,339,972 Anderson et al Ian. 25, 1944 2,533,442 Falcon Dec. 12, 1950

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