Jan. 19,­ 1965 w. c. coNovER 3,166,054 ENGINE 2 Sheets-Sheet 1 Filed Sept. 18,_ 1962 Jan.'l9, 1965 W. C. CONOVER 3,166,054 ENGINE Filed Sept. 18, 1962 2 Sheets-Sheet 2

INVENTOR IHN /íáœef/v C (aA/arf? BY Y@ Mw@ , AJM y A@ ,/rrmwfyf. „ 3,166,054 United States Patent iCC Patented Jan. 19, 1965

1 2 ' ing one embodiment of a crankshaft providing various of 3,166,054 ­ the features of the invention; » Y ENGINE FIGURE 5 is a partially diagrammatic view illustrat Warren C. Conover, Waukegan, Ill., assignor to Outboard ing the arrangement of the crank pins associated with the Marine Corporation, Waukegan, Ill., a corporation of crankshaft shown in FIGURE 4; Delaware Filed Sept. 18, 1962, Ser. No. 224,350 FIGURE 6 is a view similar to FIGURE 4 showing a 14 Claims. (Cl. 123-55) i second embodiment of a crankshaft providing various of the features ofthe invention; and The invention relates generally to multi-cylinder, inter FIGURE 7 is a partially diagrammatic view illustrating nal combustion engines. More particularly, the inven 10 the arrangement of the Vcrank pins associated with> the tion relates to six cylinder, V engines having a 90 degree crankshaft shown in'FIGURE 6. i included angle between the cylinder banks which pro The engine 111 shown in FIGURES 1, 2, and 3 conven vide the V form. . tionally includes a V type engine block 113 including two The invention provides a 90 degree V, internal com cylinder banks 115 and 117 disposed at an included angle bustion engine including two banks of three cylinders 15 of 90 degrees to each other. Each of the cylinder banks each wherein adjacent pairs of cylinders are oppositely 115 and 117 includes three cylinders in aligned series acting, i.e., »are alternately ñred at intervals corresponding with engine bank 115 including cylinders 1, 3, and 5, and to 180 degrees of crankshaft rotation. Such an arrange with engine bank 117 including cylinders 2, 4, and 6 in ment is speciñcally advantageous with a two stroke en respective generally adjacent opposing relation to cylinf gine wherein each cylinder has an associated separate ders 1, 3, and 5. Each of the cylinders 1, 2, 3, 4', 5, and crank case Ythrough which a combustion air-fuel mixture 6 has movable therein respective pistons (only pistons is pumped by reason of piston reciprocation. More spe 11 and 21 being shown in the drawings in FIGURE 2), cifically, the arrangement permits use of a three throat each of which pistons is pivotally connected to respective carburetor or other combustion air intake `wherein each separate piston rods (only piston rods 12 and 22 being throat serves one pair of adjacent oppositely acting cylin 25 shown in the drawings in FIGURE 2). In turn, the ders. 'As a result, each throat operates to pass the main piston rods are each connected to a common crank-r portion of a charge of combustion air at intervals cor shaft 119. ~ responding to 180 degrees of crankshaft rotation. As various of the advantages obtained by the disclosed , The invention also provides, in association with the invention are generally'related to two-stroke, spark igni above features, an engine wherein the cylinders of each' 30 tion engines, each of the cylinders 1, 2, 3, 4, 5, and 6 bank are fired at intervals corresponding to 120 degrees includes- an exhaust port (only. exhaust ports 13 and 23 of crankshaft rotation, thereby obtaining balanced opera being shown in the drawings ÍnFIGURE 2), and a gen tion in each‘bank,rand consequent overall balance. erally diametrically oppositely located transfer port (only The> invention further provides tir-ingorderswherein transfer ports 13a and 23a being shown in the drawings the cylinder banks alternately íire at even intervals cor 35 in FIGURE 2) , communicating with respective crankcases responding to 60 degrees of crankshaft rotation, thereby 14, 24, 34, 44, 54, amd64 (see FIGURE 4) which extend distributing ,asl uniformly as possible the flow of power to from the respective‘cylinders 1, 2, 3, 4, 5, and 6 and the' crankshaft and flywheel. In addition, as ­one of the which are generally closed except for respective valved cylinders isñred for each 60 degrees of crankshaft rota ports (only ports 15 and 25 being shown in the drawings tion and as the ñring Vin each bank occurs at intervals 40 in FIGURE 3) through which a combustion air or com corresponding to 120 degrees ofl crankshaft rotation, the bustion air-fuel mixture is introduced. As will be seen, exhaust flow is distributed as uniformly as possible both one specific advantage ofthe disclosed engineconñgura when utilizing a single exhaust manifold and when the tion is its applicability for use with either a single three exhaust is dischargedfrom each bank to a separate throat carburetor, or other combustion air intake, or with 45 manifold. ' ­ ` " ­ ­ - three separate carburetors, or other combustion air in To carry out these objectives,l the crankshaft isV de takes, rather than with separate throats or carburetors for signed, toeifect the desired action in the cylinders. In each crankcase.V Accordingly, there is shown in FIGURE the preferred embodimenn'each pair of crank pins as-V l three separate combustion-air intakes 201, 202, and sociated with adjacent cylinders in each bank> are an 203, each including respective throats 204,» 205, and 206. gularly displaced 9()v degrees from each other, while each 50 If desired, throats 204, 205, and 206 could connect with pair o_f such crankV pins is displaced 120 degrees from a single combustion `air supply manifold preferably pro each of the other two pairs of crank pins. As will be de vided with an air cleaner as shown at 207 in FIGURE 2. scribed hereinafter, the advantages of the invention can It is broadly immaterial to the present invention whether be obtained utilizing at least two diüere‘nt crankshaft con the air is carbureted at the manifold or in the respective ñgurations and two respectively associated firing orders. 55 air intakes or by direct vfuel injection into the respective ­ Other objects and advantages of the invention will be­_` cylindersl A ­ v Y come known by reference to the following description and Unless the operation is by compression-induced or hot the accompanying drawings of the invention wherein: , spot ignition, according to the Diesel principle, suitable FIGURE l is a side view of an engine incorporating 60 ignition means is provided including a .distributor 121 various of the features of theinvention; (see FIGURE l) which is connected with respective spark FIGURE 2 is an enlarged sectional >View taken gen plugs (only plugs 16 and 26 being shown inV FIGURE 2 erally along Iline‘Z-Z of FIGURE 1; and plugs 26, 46, and 66 being shown in FIGURE 1) lo FIGURE 3 is a fragmentary sectional view­ taken gen­` cated in cylinders l, 2, 3, 4, 5, îand 6, whereby the firing . erally along line-3_3 of FIGURE 1; orders, still to be described, can be obtained.- , . ‘.FIGURE 4 is a partially diagrammatic sectionaliview ­ Although various arrangements can be employed, in the taken generally along line 4_4 of FIGURE l and 4show- A Y speci?cally disclosed construction, shown in FIGURE 4, 3,166,054 3 , 4 , the crankshaft 119 is journaied in the engine block at adjacent pairs of cylinders including one cylinder in each locations 123, 125,` 12,7, andV 129 and includes disc-like bank are alternately acting, permitting supply of coni throws 130 through 138, inclusive, which'co-operate with bustion air to the associated crankcases througha single cylindrical wall portions V230 through 238,'inclusive», in a Y carburetor throat. In addition, use of the disclosed crank crankcase par-t 239 ofthe engine block 113 to deñne the shaft conñgurations permits iiring every 6() degrees of separate crankcases 14, 24, 34, 44, 54, and 64. Thev crankshaft rotation and'ñring, in each bank, at 120 de crankshaft 119 shown in FIGURE 4 also includes crank grees of crankshaft rotation. Thus, there is provided a pins 17, 27, 37, 47, S7, and'6’7 which fare supported by crankshaft configuration for a 90 degree V six engine the disc-like throws and toV which are respectively. con affording balanced ’operationV and permitting use of three i n_ected, injany suitable manner, the associated piston rods. 10 separate carburetor throats, each supplying a charge of ' The crank pins are >arrangedon the crankshaft 119, combustion air or a charge of combustion air-fuel for shown in FIGURES 4 through 7, so that each pair of gen- ~ ' every 180 degrees of crankshaft rotation. Y erally adjacent opposing cylinders,1i.e., cylinders 1 and 2, l Various of the features of the invention are set. forth 3 and 4, and 5 and 6, are oppositely acting, Le., ñre at in the following claims.` Y intervals Ícorresponding Vto 180 degrees of crankshaft rota What is claimed is: , tion,_ and so», that one cylinder'is iired for every 6l) degrees 1. A V type internal combustion engine includinga of cnankshaft rotation alternately from each bank, with . first cylinder bank including, in series, first, third and ñfth the cylinders in each‘bank tiring at even intervals, i.„e., for . cylinders, a second cylinder bank including, »in series, each`120 degrees of> crankshaft rotation. The-arrange second, fourth, and sixth cylinders, saidbanks being dis ment >of the crank pins toprovide for oppositely acting 20 posed at an angle of 90 degrees relative to each other, a pairs. of cylinders, permits the association with each pail­ separate piston reciprocably movable in each of said cyl of cylindersfof a single throat from a multi-throat car inders, a pistonrod extending from each of said pistons, buretor, or other combustion air intake. Thus each car a crankshaft including means connectingfsaid piston rods buretor or throat serves to pass a major portion of a com to said crankshaft for effecting, with respect to crankshaft bustion air or combustion-air-to-fuel mixture charge at 25 rotation, oppositely directed piston movement throughout intervals corresponding, to 180 degrees of crankshaftV the piston stroke in said first and second cylinders, in said rotation. thirdY and fourth cylinders, and in said lifth and ­sixth At least two- crankpin arrangements, and associated `cylinders, and for effectingY balanced operation of the ñring'orders, can be employed. In the embodiment'v cylinders in eachof said banks.y l l r I shown in FIGURES 4 and 5, the crank pin 17 can be 30 2. A V type internal combustion engine _including a consideredV as establishing a3 reference mark relative to íìrst cylinder'bank including, series, first, third, and iifth vwhich the other crank pins are offset-about the axis of cylinder, a second cylinder bank including', in series, Sec-f» the crankshaft 119.V As usual Yall crank pins are at like ond, fourth and sixth cylinders, said banks being disposed radius. Speciñcally, crank -pin- 27 is angularly displaced at an angle of 90 degrees relative to each other, aseparaté from crank pin~ 17 by approximatelyV 270 degrees when 35 piston reciprocably movable .in said cylinders, a crank= viewed in the clockwise direction as seen inFlGURE 5; shaft comprising means including a piston rod connecting' crank. pin 4.17 isangularly displaced from crank pin 17 by ` each of saidpistons with said crankshaft for sequentially , about 240 degrees in the clockwise direction; crank-pin disposing said pistons adjacent top dead center alternately 47 is angularly displaced from crank pin 17 by approx from each bank at intervals ofY 60 degrees öflërânkshaft i imately IÃO’degreesinv the> clockwise direction; crank pin g 40 rotation, for disposing one of said fourth and sixth pistons 5'7 is angularly displacedfromfcrank pin 17'by about Y120 adjacent top dead center next after arrival of saidv first degrees ­in the clockwise direction; and crank pin >67V is cylinderv at top dead center,V for disposing one­ of saidl angularly displaced from cnank-pin 171 by about 30 degrees third andñfth pistons adjacent top dead centerznext after in the clockwise direction.. Thus, as can be readily ob- . I arrival of said second cylinder at top dead center, for served, the respective crank >pins 17 and 27, 37 and 47, Vdisposingone'of saidrsecond and'sixth pistons adjacent;V and.57 and’ 67 for each pair` of oppositely acting cylinders top dead center next after arrival of said third cylinder at 1. and'2,*3> and 4, and 5 and‘6, are located at 90 Vdegrees top dead center, for'disposing one of said ñrst andV fifth from each other. When using the crankshaft 119 .withA pistons adjacent top dead center next after arrival of said the crank. pin arrangement just described, the ldistributor fourth cylinder at top dead center, for disposing one of is adjusted to ñre the ycylinders in the following order: 50 said second and fourth pistons adjacent top dead center 1-6­3-2-5'-4.` ` r l * . ~' Í' ~ ' i next afterV arrival of said lifth cylinderrat top dead center, ’ In theembodirnentvshown in FIGURES 6 and 7, the and for disposing one of said-third and íirst pistons adja crank pin 17' can be considered as establishing a refer cent top dead center next after arrival of said sixthcylin ence mark relative to'which the other crank pins are olf der at top dead center. ' set angularly about the axis of the crankshaft 119': Spe ` 3. A V type internal combustion engine including »á ciiically, crank pin 27' >is angularly; displaced from crank first cylinder bank including, in series, ñrst, third, and. , pin 17"by approximately l270 degrees when viewed inn fifth cylinders, a second cylinder bank including, in series, ' the clockwiseidirection asl seen ínFIGURE 7; crank pin second, fourth,` and sixth cylinders, said banks being dis~ 37’ yis angularly displacedffrom crank pin 17’ »byrapprox posed at an angle of 90 degrees relative to each other, a imately »120 degrees in the clockwise direction; crank pin 60 47' is angularly displaced from crank pin 17l by approx separate piston reciprocably movable in each of said cyl-l imately 30 degrees in the clockwise direction; crank»y pin inders, a crankshaft, a separate piston rod extendingfrom 5‘7’V is angularlyk displaced from crank pin 17’v by ap each of said pistons to said crankshaft, and means for' proximately 240»degrees `in the clockwise directiomand sequentially disposing the pistons respectively associated crank pin 67’ is angularly displaced from crank pin 17’ with said iirst, sixth, third, second, lifth, and fourth cyl ` by'approximately 150 degrees in the clockwise direction. inders adjacent top dead center at intervals corresponding. Thus, as in the embodiment shown in FlGURES 4 and 5, to 60 degrees of crankshaft rotation and for sequentially the respective crank pins 17’ andV 27', 37’ and 47', and firing said first, sixth, third, second, lifth, and fourth cyl 57’ and 67' for each pair of oppositely acting cylinders l Vinders when their respectively associated pistons are adja 1' and 2', 3' and 4', and‘S' and 6', are located lat 90 70 cent top dead center. Y degrees from each other. In operation, theembodiment 4. A V: type internal combustion engine including a shown in FIGURES 6 and 7 is employed with an engineV first cylinder bank including, in series, first, third, and having aliring order of l­4-5-2-3-6. - . lifth'cylinders, a second cylinder bank including, in series, `Both of the disclosed crankshaft configurations permi second, fourth, and sixth cylinders, said banks beingdis operation of a 90 degree V six cylinder engine to that posed at-an angleof 90 degrees relative to each other, a 5. 6.. separate piston reciprocably movable in each of said cyl first bank,`a separate crankcase >extending fromeach ¿of inders, a crankshaft, a separate piston rod extending from said cylinders and being closed except for a transfer pas each of said pistons to said crankshaft, and means for sage adapted for communication with the associated sequentially disposing the pistons respectively associated cylinder, and pressure responsive valve means for admit with said ñrst, fourth, fifth, second, third and sixth cyl ting combustion air, a separate piston reciprocably mov inders adjacent top dead center at intervals corresponding able in each of said cylinders, a separate pistonfrod ,ex- to 60 degrees of crankshaft ­rotation and for sequentially tending from each of said pistons, a crankshaft extend firing said first, fourth, fifth, second, third and sixth cyl ing »through said crankcases and including means vc011 inders when their respectively associated pistons are adja necting said piston rods to said crankshaft for effecting, cent Iltop dead center. ' 10 with respect to crankshaft rotation, opposite action of said 5. A six cylinder, V-type, two cycle, internal combus first and second cylinders, of said third and fourth cyl tion engine comprising an engine block including a first inders, and of said fifth and sixth cylinders, and for effect cylinder bank including, in aligned series, first, third, and ing balanced operation of the cylinders in each of said fifth cylinders, a second cylinder bank including, in aligned banks, and a separate combustion air intake communi series, second, fourth, and sixth cylinders in respectively 15 cating with said pressure responsive valve means asso generally adjacently opposing position to said first, third, ciated with said crankcases extending from each of 'a and fifth cylinders, said second bank being disposed at first pair of said cylinders including said ñrst and second an included angel of 90 degrees relative to said first bank, cylinders, a second pair of said cylinders including said and a crankshaft having, in series, first, second, third, third and fourth cylinders, and a third pair of said cyl fourth, fifth and sixth crank pins, said pins being con 20 inders including said fifth and sixth cylinders. nected to said pistons operable respectively in said first, 10. A V type internal combustion engine including a second, third, fourth, fifth, and sixth cylinders, said sec first cylinder bank including, in series, first, third and ond crank pin being angularly offset from said first crank fifth cylinders, a second cylinder bank including, in pin by 270 degrees in one rotative direction, said third series, second, fourth, and sixth cylinders, said banks crank pin being angularly offset from said ñrst pin by 25 being disposed at an angle of 90 degrees relative to each 240 degrees in said one rotative direction, said fourth other, a separate piston reciprocably movable in each of crank pin being angularly offset from said first pin by 150 said cylinders, a piston rod extending from each of said degrees in said one rotative direction, said fifth crank pin pistons, a crankshaft including means connecting said being angularly offset from said first pin by 120 degrees piston rods to said crankshaft for effecting, with respect in said one rotative direction, and said sixth crank pin 30 to crankshaft rotation, oppositely directed piston move being angularly offset from said first pin by 30 degrees in ment throughout the piston stroke in said first and sec said one rotative direction. ondrcylinders, in said third and fourth cylinders, and in 6. An engine in accordance with claim 5 wherein said said fifth and sixth cylinders, and for effecting balanced engine block includes a crankcase part having generally operation of the cylinders in each of said banks, and cylindrical wall portions located between adjacent cylin 35 means for supplying combustion air to said cylinders in ders and said crankshaft includes disc-shaped throws at equence corresponding to, and prior to, arrival of the least partially supporting each of said crank pins and c0 respective pistons at top dead center. operating with said wall portions to define a separate 1l. A crankshaft having, in series, a first, second, third, crankcase for each of said cylinders and to prevent gaseous fourth, fifth, and sixth crank pin, each pin being dis ñow between adjacent crankcases. 40 posed in parallel relation to the rotational axis of said 7. A six cylinder, V-type, two cycle, internal combusion crankshaft, said first and second pins being spaced sub engine comprising an engine block including a first cyl stantially at 90 degrees from each other, said third and inder bank including, in aligned series, first, third, and V fourth pins being spaced substantially at 90 degrees from fifth cylinders, a second cylinder bank including, in aligned each other, said fifth and sixth pins being spaced sub series, second, fourth, and sixth cylinders in respectively 45 stantially at 9() degrees from eachother, said first, third, generally adjacently opposing position to said first, third, and fifth pins being ,spaced substantially at 120 degrees and fifth cylinders, said second bank being disposed at an from each other, and said second, fourth, and sixth pins' included angle of 90 degrees relative to said first bank, and being spaced substantially at 120 degrees from each other. a crankshaft having, in series, ñrst, second, third, fourth, l2. A crankshaft in accordance with claim 1l in 50 cluding disk-shaped throws connecting the adjacent ends fifth, and sixth crank pins, said pins being connected to of said first and second crank pins, of said third and pistons operable respectively in said first, second, third, fourth crank pins, and of said fifth and sixth crank pins. fourth, fifth, and sixth cylinders, said second crank pin 13. A crankshaft having, in series, a first, second, being angularly offset from said first crank pin by 270 third, fourth, fifth, and sixth crank pin, each pin being degrees in one rotative direction, said third crank pin being disposed in parallel relation to the rotational axis of angularly offset from said first pin by 120 degrees in said said crankshaft, said second crank pin being located one rotative direction, said fourth crank pin being angu relative to said first crank pin at an angle of 270 de larly offset from said first pin by 30 degrees in said one rotative direction, said fifth crank pin being angularly grecs measured in one rotative direction about the crank offset from said first pin by 240 degrees in said one rota shaft axis, said third crank pin being located relative to 60 said first crank pin at an angle of 240 degrees measured tivedirection, and said sixth crank pin being angularly in said one rotative direction, said fourth crank pin be offset from said first crank pin by 150 degrees in said ing located relative to said first crank pin at an angle of one rotative direction. 150 degrees measured in said one rotative direction, said 8. An engine in accordance with claim 7 wherein fifth crank pin being located relative to said first crank said engine block includes a crankcase part having gen erally cylindrical wall portions located between adjacent pin at an angle of 120 degrees measured in said one ro cylinders and said crankshaft includes disc-shaped throws tative direction, and said sixth crank pin being located at least partially supporting each of said crank pins and relative to said first crank pin at an angle of 30 degrees co-operating with said wall portions to define a separate measured in said one rotative direction. crankcase for each of said cylinders and to prevent gase 14. A crankshaft having, in series, a first, second, third, out fiow between adjacent crankcases. 70 fourth, fifth, and sixth crank pin,-each pin being disposed 9. A V type internal combustion engine including a in parallel relation to the rotational axis of said crank first cylinder bank including, in series, first, third, and shaft, said second crank pin being located relative to said fifth cylinders, a second cylinder bank including, in series, first crank pin at an angle of 270 degrees measured in second, fourth, and sixth cylinders, said second bank one rotative direction about the crankshaft axis, said being disposed at an angle of 90 degrees relative to said 75 third crank pin being located relative to said first crank pin at an angl-e’rof 1,20 degrees measured in said'one roèj ~ ~ ï ' References Citedv in the inile of this patent tativedirection, said fourth crank pin being located rela-` tive toV said1íìrst’crank pinfat an angley of 30 degrees f `_' ` UNITED STATES PATENTS ~ measuredïiny said one rotative direction, ¿said fifthV crank 2,973,752"Y „ Tórre". ______`____ Mar. 7, 1961 pin being located relative -to said Ijrst crankpinV at `an '5 V3,105,474 Y VfKiekßaeferYV ...... _` ______Oct. 1, 1963 anglerof KA240 degrees measured in said one rotativedi rectionQand said >sixth crank pin beingl located relative FOREIGN PATENTS to said first crank pin at anV angle of 150 degrees meas~ >ured in said one rotative direction.l Y