US2680427A

US2680427A - V-type engine

Info

Publication number: US2680427A
Application number: US269227A
Authority: US
Inventors: Robert F Summers
Original assignee: Chrysler Corp
Current assignee: Old Carco LLC
Priority date: 1952-01-31
Filing date: 1952-01-31
Publication date: 1954-06-08
Anticipated expiration: 1971-06-08

Description

June 8, 1954 R. F. suMMERs 2,680,427

V-TYPE ENGINE Filed Jan. 3l, 1952 3 Sheets-Shee':I 1

4424x577' i Nl i f *213' E E E INVENTOR.

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Array/W506i June 8, 1954 R.' F. sUMMERs 2,680,427

V-TYPE ENGINE Filed Jan. 31, 1952 3 Sheets-Sheet 2 ffl, :55, .55,5212 Slg-152x574 INVENTOR. derf Sarrrmfs'. BY

June 8, 1954 R; F. suMMERs 2,680,427

V-TYPE ENGINE Filed Jan. 3l, 1952 3 Sheets-Sheet 3 l l l HWWQHW Patented June 8, p 1954 UNITED STATES PATENT OFFICE V-TYPE ENGINE Robert F. Summers, Highland Park, Mich., as-

signor to Chrysler Corporation, Highland Park, Mich., a corporation of Delaware Application January 31, 1952, Serial No. 269,227

26 Claims. 1

rIhis invention relates to odd angle V-eight internal combustion engines and particularly to the bank angle and crankshaft crank arrangements for such engines whereby a completely balanced engine may be achieved without the use of socalled accessory counterbalance equipment.

It is a primary object of this invention to determine what cylinder bank anglesl other than the conventional 90 and 180 degree bank angle can be used in V-eight engines to provide an even firing, equal Cylinder bore spaced engine that can be completely balanced by crankshaft counterweighting alone. l

It is another object of this invention to determine the crankshaft crank arrangement for odd angle, even firing V-eight engines that will permit complete balance of the engine by the utilization of crankshaft counterweighting alone.

Other objects and advantages of this invention will become readily apparent from a reading of the following description and a consideration of the related drawings wherein:

Fig. 1 is a diagrammatic perspective view of a crankshaft for one of the balanced, odd angle, V-eight engines embodying this invention, certain of the cranks of the crankshaft having the pistons, connecting rods and counterweights connected thereto also shown in diagrammatic form;

Fig. 2 is a diagrammatic end elevation of the crankshaft and associated engine structure shown in Fig. l, the View being taken in the direction of the arrow 2 of Fig. l;

Fig. 3 is another diagrammatic end elevation of the structure shown in Fig. 1 illustrating the 6 wherein the crankshaft cranks are arranged in a pattern opposite to that shown in Fig. 7;

Fig. 9 is a diagrammatic end elevation of another form of odd angle, balanced V-eight engine embodying this invention;

Fig. 10 is a diagrammatic end elevation showing the crankshaft crankpin and the connecting rod arrangement for the engine shown in Fig. 9;

Fig. 11 is a diagrammatic end elevation showing the crankshaft crankpin and the connecting rod arrangement for an engine like that shown in Fig. 9 wherein the crankshaft cranks are arranged in a pattern opposite to that shown in relative positions of the crankshaft crankpins and the connecting rods for the Fig. 1 arrangement;

Fig. 4 is a diagrammatic end elevation of an engine arrangement similar to that shown in Figs, 1-3 wherein the crankshaft crankpins for the two cylinder banks spiral in opposite directions to the arrangement shown in Figs. 1 3;

Fig. 5 is a diagrammatic end elevation showing the crankshaft crankpin and connecting rod positions for the crankshaft arrangement shown in Fig. 4;

Fig. 6 is a diagrammatic end elevation of another form of odd angle, balanced, V-eight engine embodying this invention;

Fig. 7 is a diagrammatic end elevation showing the crankshaft crankpin and the connecting rod arrangement for the engine shown in Fig. 6;

Fig. 8 is a diagrammatic end elevation of the crankshaft crankpin and the connecting rod arrangement for an engine like that shownin Fig.

Fig. 10

Fig. 12 is a diagrammatic end elevation of another form of odd angle, balanced V-eight engine embodying this invention;

Fig. 13 is a diagrammatic end elevation showing the crankshaft crankpin and the connecting rod arrangement for the engine shown in Fig. 12; and

Fig. 14 is a diagrammatic end elevation showing the crankshaft crankpin and the connecting rod arrangement for an engine similar to that shown in Fig. 12 wherein the crankshaft crankpin arrangementis opposite to that shown in Fig. 13.

It has often appeared that it would be quite advantageous to use V-eight engines of other than or 180 degree bank angles if such engines could be completely balanced by crankshaft counterweighting alone and if even ring intervals and equal cylinder bore spacing would also be characteristic of such engines. Set forth below is a description of a group of engines meeting the above requirements.

As a result of the application of the formulae set forth hereafter and certain other mathematical theory that is well known in the art, it has been determined, for the first time -it is thought, what V-eight engines. having bank angles other than 90 or 180 degrees, provide engine arrangements that maybe completely balanced by crankshaft counterweighting alone and wherein the ring intervals and the cylinder bore spacing are each-even. It has been further determined that the four V-eight engines having bank angles (d) of 36.9, 53.1, 126.9 and 143.1 degrees respectively are the only engine arrangements other than 90 and 180 V-eight arrangements that meet the above requirements. It will be seen that each of these odd angle V-eight engines are in reality different members of a single engine group and thus they represent merely different forms of the same invention. It hasbeen further determined that even if the cylinder bore spacing in any of the above noted engines is varied slight.- ly to permit the use of diierent size crankshaft bearings between the several cranks of any crankshaft, that still the above noted bank angles are substantially cor-rect within plus or

minus

1 or 2 degrees. Furthermore, the exact bank angle to insure complete engine balance for any given cylinder bore spacing or any variation from even firing intervals can be determined from the formulae set forth below.

The four V-eight engines herein describedhave the desirable features of short length, simplicity of design and perfect balance which characterize the conventional QO-degree type` of V-eight engine. A prime advantage of these four V-eight engines as compared to the conventional 90 degree V-eight engines lies in their width and/or height reductions over the 90 degree V-eight engines. A difculty experienced with conventional 90 degree V-eight engines, particularly the newer engines using overhead valves, is that their large width results in crowding of engine and accessory .units in the engine compartment. The accessibility of parts mounted on the engine, such as the carburetor and the oil lter, is adversely affected. Not only the engine units, but other accessory units, commonly mounted in the engine compartment of a motor vehicle, such as the steering mechanism, heater, battery and the like are also crowded because of the engine width.

The possibility of building a satisfactory narrow-angle V-8 engine has been investigated by a number of others in the past but the best types which have appeared to date have all had serious dynamic unbalances inherent in their crank and cylinder arrangements. In addition some of the narrow angle V-eights proposed have had uneven firing intervals. Two of the engines herein described, namely the 36.9 and 53.1 degree angle V-eight engines are the only known engines in that category which have complete inherent dynamic balance and even firing intervals as Well as equal cylinder bore spacing. The bank angles of 36.9 and 53.1 degrees are more exactly the arc tangent selon and arc tangent respectively. The other two V-eight engines of this disclosure are V-eight engines of wide bank angle having angles of 126.9 and 143.1 degrees. More exactly, these angles are are tangent and arc tangent respectively. These engines have the advantage of low height when compared with the conventional 90 degree V-eight and will be suitable for installations where height is restricted.

It can be proven mathematically from the formulae appearing hereafter that the four V- eight engines disclosed along with the conventional 90 degree V-eight and the conventional eight-cylinder opposed or 180 degree V-eight engine are the only two-bank eight-cylinder engines possible having (l) primary and secondary reciprocating inertia force balance, (2) primary and secondary inertia couple balance, and 3) even firing intervals. In the four disclosed odd angle V-eight engines and the conventional degree V-eight engine primary couple balance is achieved with the aid of crankshaft counterweighting alone. Each of the four odd angle V- eig'nt engines herein disclosed employs eight crankpins. The crankshafts for the 53.1 and the 125.9 degree V-8 engines are the same, and the crankshafts for the 36.9 and the 143.1 degree V-8 engines are the same. All the crankshafts are typified by opposite spiralling of.the two groups of four crankpins each for each of the two banks. As with most crankshafts, each of the described crankshafts can be built with the crankpins following each other at the same intervals in either the clockwise or counterclockwise direction. It is possible to change the bank angle cf any of the four odd angle V-eight engines slightly and still maintain its balance by using an uneven bore spacing or uneven firing intervals or both if such should be desired.

Fig. 1 shows a crankshaft 22 for a V-eight engine wherein the two similar banks R. and L of the engine are arranged with a bank angle (d) of 53.1 degrees therebetween as clearly shown in Figs. 2 and 3. Cranks 2|, 23, 25 and 2l of the crankshaft 2B are connected to the pistons in the cylinders of the left bank L while cranks 22, 24, 26 and 28 of crankshaft 28 are connected to the Distons in the cylinders of the right bank R of the engine. The cylinder bores of each bank and consequently the cranks of the crankshaft diagrammatically disclosed in Fig. 1 are equally spaced longitudinally of the engine. From Fig. 3 it will be noted that crank 23 is spaced clockwise from crank 2l by 90 degrees and crank 25 is spaced clockwise from crank 23 by 180 degrees with crank 2l spaced clockwise from crank 25 by 27o degrees. Accordingly, cranks 2| and 21 are diametrically opposed as are cranks 23 and 25. Furthermore, each of

cranks

2l, 23, 25 and 21 is spaced either 90 degrees or some multiple of 90 degrees from each of the other cranks of the associated'engine cylinder bank L. Likewise, from Fig. 3, it will be noted that crankfZii is spaced counterclockwise from crank 22 by 90 degrees, crank 28 is spaced counterclockwise from crank 24 by 180 degrees and crank 28 is spaced counterclockwise from crank 2S by 27() degrees. It will be noted that cranks 22 and 28 are diametrically opposed as are cranks 2e and 26 and that each of

cranks

22, 2i, 2B and 28 are spaced either 90 degrees or a multiple of 90 degrees from each of the other cranks of the associated engine cylinder bank R. It can thus be said that the cranks of the two banks R and L of this engine spiral in opposite directions. Connecting rods 3 i-S are connected to the cranks 2i-28 in conventional manner and each connecting rod has a piston connected thereto in accordance with standard practice. From Figs. 1 and 3 it is clear that the crankshaft for this balanced, odd-angle V-eight engine has eight cranks comprising two sets of four cranks each wherein the cranks of each set spiral about the crankshaft axis in opposite directions. This particular crank arrangement is one of the features that distinguishes this invention from both the conventional 90 degree and degree V-eights and from other odd angle V- eight engines that have been proposed in the past. In Fig. 3 the numeral 30 represents the plane containing the primary couple and it will be noted that this plane is between the planes of cranks 2l and 22. The counterweights 4I46 are placed So as to completely balance the primary couple. With the counterweighting arrangement shown the several counterweights are all offset angularly from the plane 30 that includes the primary couple of the engine but the arrangement still completely balances the engine primary couple and also develops forces that act to reduce the bearing loads at the central crankshaft bearing 40. 'I'he counterweight pattern shown may be varied to meet varying circumstances and need not be identical to that disclosed.

As previously mentioned the cylinder bore spacing a for the engines herein disclosed is even or constant and thus if.a represents the spacing between the adjacent intermediate cranks of either engine bank (see Fig. 1) then 0, which represents the spacing between the endcranks of either engine bank, is equal to 3 a. .This relationship C=3a is of importance in developing the formulae that pertains to the group of engines involving this invention for it will be found that the angle 1' in each of these engines equals the arc tangent 18 45 d egrees when C'=3a. The angle 1' is that angle that the front crank of a bank of cylinders makes with the axis of the cylinders of that bank when the rocking couple of that bank is a maximum.

Looking now at Figs. 2 and 3, it will be seen that the angle f is the angle by which the front crank 2l of left bank L leads the front crank 22 of right bank R. This angle f will turn out to be actually 36.9 degrees for the 53.1 degree bank angle V-eight when the appropriate, after described, equations are solved.

The angle B shown in Fig. 2 is the angle by which the primary rocking couple in one bank L leads the primary rocking couple in the other bank R. The phase angle of the primary rocking couple for each of the banks L and R can be determined by application of either graphical or mathematical means known to the engine design art and which means are not thought to require explanation for an understanding of this invention. It can further be established that the primary rocking couple in one bank L or R can lead or follow the front crank 2| or 22 respectively in that engine bank by the angle "r. The symbol "h in the below equations represents a firing interval and for equal firing intervals with the crankshaft arrangement disclosed it will be found that h equals 90 degrees or a multiple thereof. Accordingly, any of the three following relationships are possible for inherently balanced V-eight engines of two four cylinder banks:

(1) Bib for 90 and 180 degree V-eight engines.

(2) B=h+2r for certain odd angle, inherently balanced V-eight engines.

(3) Bzh-Zr for certain other odd angle, in-

herently balanced V-eight engines.l

It is now possible to write a set of equations for -eight engines which will completely denean engine having:

(a) a resultant primary rotating couple that can be completely balanced by crankshaft counterweighting;

(b) combinations of crankshaft crank groups that have reciprocating inertia force balance;

- 53.1 degrees toone another.

(c) even spacing of the cylinder bores in each .bank of the engine; and (d) even ring intervals.

(I) B=180d where d=the bank angle. (n) B=h, rugzak-2r.

(III) r=arc tangent 1/3=18.45 degrees. (IV) h=0, 90, 180, 27() degrees.

By solving the above equations it will be found that V-eight engines having bank angles (d) of and 180 degrees as well as the four odd angle V-eights that have 36.9, 53.1, 126.9 and 143.1 bank angles (cl) are the only V-eight engines meeting the aforementioned requirements of balance, equal bore spacing and even ring intervals.

By rearranging Equation I above it will be found that d:-B, or expressed verbally, the angle between' the banks (d) equals 180 degrees minus the angle (B) by which the primary rocking couple in one bank leads the primary rocking couple in the other ba By combining Equations II and III above and considering the

aforementioned Equations

1, 2 and 3, it will be found that B=h+36-9 degrees for certain inherently balanced odd angle V- eight engines and B:h*36.9 degrees for certain other inherently balanced odd angle V-eight engines. The conventional 90 or 180fdegree bank angle V-eight engines are omitted from this discussion for obvious reasons.

Now if hz, 90, 180 and 270 degrees then for B=hi36-9 degrees, it will be found that B=i36-9 degrees, $126.9 degrees, i531 degrees and i143.1 degrees for the various aforementioned values of h.

It can be shown mathematically that whenever :180-d, the primary reciprocating inertia couples of the angled banks of the several engines herein Ydisclosed always combine to give a resultant rotating couple that extends in a plane that bisects the angle between the front cranks of the two banks so that this couple can be completely balanced by a crankshaft counterweighting alone. When even firing intervals are required and even bore spacing is used balanced engines are obtained with bank angles d of 36.9, 53.1, 126.9 and 143.1 degrees. These are the only angles that will give inherently balanced odd angle V-eight engines. Because of the basic crankshaft crank arrangement disclosed for each engine of the group herein described, primary force balance and secondary force and couple balance are alsov achieved in each of the four odd angle V-eight engines herein described.

Figs. 4 and 5 show an odd angle V-eight engine wherein the two equally spaced four cylinder engine banks are arranged at an angle (d) of This is the case' with the Figs. 1-3 arrangement but in the Figs. 4 and 5 arrangement the cranks of the crankshaft are oppositely arranged to those shown in Figs. 1-3. In Figs. 4 and 5 the reference numerals are similar to those shown in Figs. 1-3 but are primed to be distinguishable from the corresponding numerals in Figs. 1-3. It will be noted that in Figs. 4 and 5 the cranks 2|', 23', 25 and 21 spiral or twist counterclockwise from front to rear and are connected to the right bank R whereas in Figs. 1-3 lthe opposite relationship existed. Similarly in Figs. a and the

cranks

22', 24', 26 and 28 spiral or coil clockwisc from front to rear and are connected to the left bank L' of the engine. In Figs 1-3 just the opposite relationship existed. All other relationships relative to crank angles L the plane of the resultant rotating couple and the angle r are the same for Figs. 1-3 and Figs. 4 5. Connecting rods 3|'38 connect the cranks 2I-28' respectively to the pistons in the two banks of cylinders as shown in Fig. 5.

Figs. 6 and '1 show a second narrow angle V- eight embodying this invention wherein the two banks of cylinders R2 and L2 are arranged at an angle (d) to each other of 36.9 degrees. In .I

this narrow angle V-eight the crankshaft 5|) has eight angularly spaced apart cranks 5|-58 inelusive,l arranged in two sets of four cranks each.

One set is composed of cranks 5|, 53, 55 and 51 that spiral counterclockwise from front to rear and are spaced 90 degrees apart clue to` cra-nk 53 being 90 degrees counterclockwise from crank 5|, crank bein'g 180 degrees counterclockwise from crank 53 and crank 51 being 270 degrees counterclockwise from crank 55. The other set of cranks is composed of cranks .52, 54, 55 and 58 that spiral clockwise from iront to rear and are 90 degrees apart due to crank 54 being 9 0 vdegrees clockwise from crank 52, crank 5B being 180 degrees clockwise from crank 54 and crank 58 being 270 degrees clockwise from crank 5B. Connecting rods 5|-6 connect the cranks 4'5l-5|?. to their respective pistons and cylinder bores. As is evident left bank L2 includes the cylinders connected to cranks 5|, 53, 55 and 51 whereas right bank R2 includes the cylinders and pistons that are connected to

cranks

52, 54, 56 and 58. The plane that bisects the angle between the cranks 5| and 52 contains the resultant of the primary reciprocating inertia forces of the two angularly related banks of cylinders R2 and L2.

Fig. 8 shows an end elevation similar to Fig. '7 but representing an varrangement wherein the two sets of cranksi'al, 53', 55', 51' and 52', 54', 55', 58' respectively are oppositely arranged to their corresponding elernents shown in Figs. 6 and 1. Cranks 51253', 55' and k51' spiral clockwise from iront to rear and are spaced equally at multiples of 9G degrees. Likewise cranks 52', 54', 56' and 5S' spiral counterclockwise from front to rear and are spaced equally at intervals of 90 degrees or multiples thereof. The plane 59' .includes the resultant rotating couple of the primary reciprocating inertia couples. All relationshipsthat applied to the Fig. 5 and 7 form arelikewise true of the Fig. 8 form of the invention. Connecting rods 6|'68' connect the cranks 5|5,8' respectively to the pistons in the two .banks of cylinders as shown in Fig. 8.

Figs. 9 and 10 show one form of wideangle V- eight engine that embodies this invention.v V'The two banks R3 and L3 of this engine are arrangedA at an angle (d) of 126.9 degrees to each other. In this wide angle AV-eight engine the crankshaft 1e has eight angularly spaced apart cranks 'ii-18 inclusive arranged in twosets of four cranks each with the cranks of each set spiralling in opposite directions about the crankshaft axis. 'One ySetv of .cranks is composed .of cranks 1|., '13, 15 and A17| that vspira-l oounterclockwise Afrom front torear .about the crankshaft axis and are equally spaced vat 90 degree interi/'als from one another due to Ycrank 13-being :90 degrees counterclockwise from crank 1i|,cr.ank .15 being 180 'degrees counterclockwise fromfcrank 13 and crank 11 being 270 degrees counterclockwise from crank 15. Cranks 1|, 13, 15 and 11 are connected by connecting rods 8|, 83, 85 and 81 respectively to the pistons in the left bank of cylinders L3. The other set of

cranks

12, 14, 16 and 13 spiral clockwise from front to rear about the crankshaft axis and are equally spaced at 90 degrees clockwise due to crank 14 being 90 degrees clockwise from crank 12, crank 16 being 180 degrees clockwise from crank 14 and crank 18 being 270 degrees clockwise from crank 15.

Cranks

12, 14, 16 and 18 are connected by connecting rods 82, 84, 86 and 88 respectively to the pistons in the right bank of cylinders R3. The plane that bisects the angle between the cranks 8| and 8.2 contains the resultant rotating couple of the primary reciprocating inertia forces of the two banks of cylinders. The several angular relationships that exist for the other forms of this invention are likewise true of this form of the invention.

Fig. 1l shows an end elevation of engine similar to that shown in Figs. 9 and 10 but disclosing an arrangement wherein the two sets of crankshaft cranks 1|', 15', 15', 11' and 12", 14', 16' and 1B respectively spiral in opposite directions to that shown in Figs. 9 and 10. Cranks 1 |313', 15' and 11' spiral clockwise from front to rear and are arranged at equally spaced angular intervals that are inuitiplcs of 90 degrees. Cranks 1|', 13', 15' and '11" are connected to the pistons in the right bank ci ,cylinders R3 by connecting rods 8|', 83', 85 and 81' respectively. Cranks 12', 14', 15' and 18' spiral counterclockwise from front to rear and are arranged at equally spaced angular intervals that are multiples oi 90 degrees. Cranks 12', 14', 15', 18 are connected by connecting

rods

82', 84', 8,5 and 82 to the pistons in the left bank L3. The plane til' that bisects the angle between cranks 1|' and 12' contains the resultant rotating couple of the primary reciprocating inertia force rocking couples.

Figs. 12 and 13 show another form of wide angle V-eight engine that embodies this invention. The two banks R4 and L4 of this engine are arranged at an angle (d) or" 143.1 degrees to each other. vIn this wide angle V-eight engine the crankshaft 99 has eight angularly spaced apart cranks `SI--Qii inclusive arranged in two sets of four .cranks each with thecranksof eachset spiralling in opposite .directions about the crankshaft axis. One set of cranks is composed of cranks 9|, 93, and 51 that spiral clockwise from front to rear about the crankshaft .axis and are equally spa-ced .at 90 degrees intervals from one another due to crank 93 ,being 90 degrees clockwise from crank 9|, crank 95 being 180 degrees clockwise from crank 53 and crank ,9 1 being 270 degrees clockwise `from crank 95. Cranks 9|, 93, 95 and S1 are ccnnectedfby connecting rods 19|, |93, |05 and 01 to the pistons in the left bank of cylinders L?. The other set of

cranks

92, 94, 96 and 98 spiral counterclock-wise from front to rear about the crankshaft axis and are equally spaced at 90 degree intervals clue to crank 94 being 90 degrees counterclock-wise from crank 92, crank 9S being 180 .degrees counterclockwise from crank 94 and crank VSii-being .27.0 degrees counterclockwise from crank 9S.

Cranks

92, 94, 96 and gareconnected to the pistons in the right bank of cylinders R4 by connecting rods |92, |114, U16-and |08 respectively. The plane 100 that `bisects the VangIebetween cranks 9| and 92 contains the .resultant rotating couple of the primary reciprocating inert-aorce rocking couples 4of the :two engine banks R4, L4. The several angular relationships that exist for the other forms of the invention are likewise true of this form of the invention.

Fig. 14 shows an end elevation of an engine similar to that shown in Figs. 12 and 13 but disclosing an arrangement wherein the two sets of crankshaft cranks 9|', 93', 95', 91 and 92', 94', 96' and 98' respectively spiral in opposite directions to that shown in Figs. 12 and 13. Cranks 9|', 93', 95' and 91 spiral counterclockwise from front to rear and gular intervals that are multiples of 90 degrees. Cranks 9|', 93', 95 and 91' are connected to the pistons of the right bank R4' by connecting rods l, |93', |35' and |01 respectively. Cranks 92', 94', 96' and 98' spiral clockwise from front to rear about the crankshaft axis from front to rear and are arranged at equally spaced angular intervals that are multiples of 90 degrees. Cranks 92', 94', 96' and 98' are connected by connecting rods |02', |64', |96' and |08 to the pistons of the left bank L4'. The plane |00' that bisects the angle between cranks 9| and 92' contains the resultant rotating couple of the primary reciprocating inertia force rocking couples of the two engine banks. The other angular relationships that apply to the other forms of this invention likewise apply to the form shown in Fig. 14.

I claim:

1. In an inherently balanced eight cylinder V- type engine having a bank angle of other than ninety-degrees or full multiples thereof comprising two banks of four cylinders each wherein the angle between the two banks equals 180 degrees minus the angle by which the primary rocking couple in one bank leads the primary rocking couple in the other bank and wherein the crankshaft for the engine includes eight angularly spaced cranks arranged in two sets of four equally angularly spaced apart cranks arranged such that the directions of spiral of the two sets of cranks are opposite when looking from the front crank of each set towards the rear crank thereof and the cranks in each bank are arranged such that the second crank is radially spaced from the first crank by ninetydegrees, the third crank radially spaced from the second crank by one-hundred-eighty degrees, and the fourth crank radially spaced from the third crank by two-hundred-seventy degrees.

2. In an inherently balanced eight cylinder V- type engine comprising two banks of four cylinders each wherein the angle between the two banks equals substantially 36.9 degrees and wherein the crankshaft for the engine includes arranged in two eight angularly spaced cranks sets of four equally angularly spaced apart cranks arranged such that the directions of spiral of the two sets of cranks are opposite when looking from the front crank of each set towards the rear crank thereof and the cranks in each bank are arranged such that the second crank is radially spaced from the rst crank by ninetydegrees, the third crank radially spaced from the second crank by one-hundred-eighty degrees, and the fourth crank radially spaced from the third crank by two-hundred-seventy degrees.` 3. In an inherently balanced eight cylinder AV- type engine comprising two banks of four cylinders each wherein the angle between the two banks equals substantially 53.1 vdegrees and wherein theV crankshaft forthe engine includes eight angularly spaced cranks arranged intwo sets of four equally angularly spaced apart cranks arranged such that the directions of spiral are arranged at equally spaced ant 10 of the two sets of cranks are opposite when looking from the front crank of each set towards the rear crank thereof and the cranks in each bank are arranged such that the second crank is radially spaced from the first crank by ninetydegrees, the third crank radially spaced from the second crank by one-hundred-eighty degrees, and the fourth crank radially spaced from the third crank by two-hundred-seventy degrees.

4V. In an inherently balanced eight cylinder V- ytype engine comprising two banks of four cylinders each wherein'the angle between the two banks equals substantially 126.9 degrees and wherein the crankshaft for the engine includes eight angularly spaced cranks arranged in two sets of four equally angularly spaced apart cranks arranged such that the directions of spiral of the two sets of cranks are opposite when looking from the front crank of each set towards the Arear crank thereof and the cranks in each bank are arranged such that the second crank is radially spaced from the first crank by ninetydegrees, the third crank radially spaced from the second crank by one-hundred-eighty degrees, and the fourth crank radially spaced from the third crank by two-hundred-seventy degrees.

5. In an inherently balanced eight cylinder V- type engine comprising two banks of four cylinders each wherein the angle between the two banks equals substantially 143.1 degrees and wherein the crankshaft for the engine includes eight angularly spaced cranks arranged in two V'sets of four equally angularly spaced apart .cranks arranged such that the directions of spiral of the two sets of cranks are opposite when looking from the front crank of each set towards the rear crank thereof and the cranks in each bank are arranged such that the second crank is radially spaced from the first crank by ninety-l degrees, the third crank radially spaced from the second crank by one-hundred-eighty degrees, and the fourth crank radially spaced from the third crank by two-hundred-seventy,degrees.

` 6. In an inherently balanced eight cylinder V- type engine having a bank angle of other than ninety-degrees or full multiples thereof comprising two banks of four equally spaced apart cylinders alternately arranged longitudinally of the engine wherein the angle between the two banks. equals degrees minus the angle by which the primary rocking couple of one bank leads the primary rocking couple of the other bank and wherein the crankshaft for the engine ,includes eight angularly spaced cranksA arranged in two sets of four equally angularly spaced apart cranks each with the cranks of each set arranged such that the direction of coil of each set of cranks when traveling from the front crank of each set to the rear crank thereof is opposite to that of the other set and wherein the front crank of one set is angularly spaced from the front. crank of the other set by 36.9 degrees and the cranks in each bank are arranged such that the second crank is radially spaced from the first crank byv gine includes eight angularly spaced cranks arranged in two sets of four equally angularly spaced apart cranks each with the cranks of each set arranged such that the direction of coil of each set of cranksv when traveling fromv the front crank of each set to the rear crank thereof is opposite to that of the other set and wherein the front crank oi one set is angularly spaced from the front crank of the other set by substantially 143.1 degrees and the cranks in each bank are arranged such that the. second crank is radially spacedfrom the rst crank by ninetydegrees, the third crank radially spaced from the second crank by one-hundred.-eighty degrees, and the fourth crank radially spaced from the third crank by two-hundred-seventy degrees.

8. In an eight cylinder V-typeengine comprising two banks of four equally spaced apart cylinders alternately arranged longitudinally of the engine wherein the angle between the two banks equals substantially 53.1 degrees and wherein the crankshaft. for the engine includes eight angularly spaced cranks arranged in two setsof four equally angularly spaced apartv cranks each with the cranks of each set arranged such that the direction of coil of each set of cranks when traveling from the front crank of each set to the rear crank thereof is opposite tov that of the other set and wherein the iront crank of one set is. angularly spaced from the front crank of the other set by substantialy 36.9 degrees.

9. In an eight cylinder V-type engine comprising two banks of four equally spaced, apart. cylinders alternately arranged longitudinally of the engine wherein. thev angle between the two. banks equals. substantially 1261.9 degrees and wherein the crankshaft for the enginey includes eight angularly spaced cranks arranged in two sets of four equally angularly spaced apart cranks each with the cranks of each set arranged such that the. direction of coil of each set of cranks when traveling from the iront crank of each set to the rear crank thereof is opposite to that of the other set and wherein the fronty crank. of. one set is angularly spaced from the front crank of the. other set by substantially 36.9 degrees. Y

10. In aninherently balanced eight` cylinder V- type engine comprising two banks. of four equally spaced apart cylinders alternately arranged longitudinally of the. engine wherein the angle between the two banks equals substantially 143.1 degrees. and wherein the crankshaft for the engine includes eight angularly spaced cranks arranged in two sets of four equally angularly spaced apart cranks each with the cranks of each set arranged such that the direction of coil of each set of cranks when traveling from the front crank of each set tothe rear crank thereof is opposite to that of the other setand wherein the front crank of one set is angularly spaced from the front crank of the other set by substantially 143.1 degrees and the cranks in each bank are arranged such that the second crank is radiaily spacedfrom the. first crank by ninetydegrees, the third crank radially spaced from the second crank by one-hundred-eighty degrees, and the fourth. crank radially spaced from the third crank by two-hundred-seventy degrees.

11. An inherently balanced eight cylinder V- type engine having a bank angle of other than ninety-degrees or full multiples thereof` comprising a crankshaft extending longitudinally of the engine and a pair of banks of four cylinders each, said cylinder banks being arranged at an angle to one another such that the resultant gularly of the of the primary reciprocating inertia force rocking couples of the twobanks is a rotating couple that lies in a plane extending perpendicular to and. longitudinally of the crankshaft whereby said resultant rotating couple can be counterbalanced` by crankshaft counterweighting alone, said crankshaft having eight angularly spaced apart cranks comprising two sets of four cranks each wherein the cranks of each set are equally spaced angularly oi the crankshaft at ninety degree intervals and the direction of twist of the cranks of one set going from the front crank to the rear crank thereof is opposite to the direction of twistof the other set and the cranks in each bank are arranged such that the second crank is radially spaced. from the rst crank by ninetydegrees, the third crank radially spaced from the second crank by one-hundred-eighty degrees, and the fourth crank radially spaced from the third crank by two-hundred-seyenty degrees.

12- An inherently balanced eight cylinder V- type engine comprising a crankshaft extending longitudinally of the engine and a pair of banks of four cylinders each, said cylinder banks being arranged at an angle to one another of 36.9 degrees such thatY the resultant of the primary reciprocating inertia force rocking couples of the two banks is a rotating couple that lies in a plane extending perpendicular to and longitudinally of the crank shaft whereby said resultant rotating couplecan be counterbalanced by crankshaft counterweighting alone, said crankshaft having eight angularly spaced apart cranks comprising two sets of four cranks each wherein the cranks of each setV are equally spaced angularly of the crankshaft at ninety degree intervals and the direction oi twist of the cranks of one set going from the iront crank to the rear crank thereof is opposite to the direction of twist of the other set.

13. An inherently balanced eight cylinder V- type engine comprising a crankshaft extending longitudinally of the engine and a pair of banks of four cylinders each.1 said cylinder banks being arranged at an angle toone another of 53.1 degrees such that the resultant of the primary.

reciprocating inertia force rocking couples of the two banks is a rotating couple that lies in a plane extending perpendicular to and longitudinally of the crankshaft whereby said resultant rotating couple can be counterbalanced by crankshaft counterweighting alone, said crankshaft having eight angularly spaced apart cranks comprising two sets of four cranks each wherein the cranks of each set are equally spaced ancrankshaft at ninety degree intervals andthe direction of twist of the cranks of one set going from the front crank to the rear crank thereof is opposite to the direction of twist of the other set.

14. An inherently balanced eight cylinder V- type engine comprising a crankshaft extending longitudinally of the engine and a pair of banks of four cylinders each, said cylinder banks being arranged at an angle to one another of 126.9 degrees such that the resultant of the primary reciprocating. inertia forceV rocking couples of the two banks is a rotating couple that lies in a plane extending perpendicular to and longitudinally of the crankshaft whereby said resultant rotating couple can be counterbalanced by crankshaft counterweighting alone, said crankshaft having eight angularly spaced apart cranks comprising two sets of four cranks each wherein the cranks Qi each set are equally spaced y 13L anguIarly of the crankshaft at ninety degree intervals and the direction of twist of the cranks of one set going from the front crank to the rear crank thereof is opposite to the direction of twist of the other set.

15. An inherently balanced eight cylinder V- type engine comprising a crankshaft extending longitudinally of the engine and a pair of banks of four cylinders each, said cylinder banks being arranged at an angle to one` another of 143.1 degrees such that the resultant of the primary reciprocating inertia force rocking couples of the two banks is a rotating couple that lies in a plane extending perpendicular to and longitudinally of the crankshaft whereby said resultant rotating couple can be counterbalanced by crankshaft counterweighting alone, said crankshaft having eight angularly spaced apart cranks comprising two sets of four cranks each wherein the cranks of each set are equally spaced angularly ofthe crankshaft at ninety degree intervals and the direction of twist of the cranks of one set going from the front crank to the rear crank thereof is opposite to the direction of twist of the other set.

16. An inherently balanced eight cylinder V- type engine having a bank angle of other than ninety-degrees or full multiples thereof comprising a crankshaft extending longitudinally of the engine and a pair of banks of four equally spaced cylinders each, said cylinder banks being arranged at an angle to one another such that the resultant of the primary reciprocating inertia force rocking couples of the two banks is a rotating couple that lies in a plane extending perpendicular to and longitudinally of the crankshaft whereby said resultant rotating couple can` be counterbalanced by crankshaft counterweighting4 alone, said crankshaft having eight angularly spaced apart cranks comprising two sets of four cranks each wherein the cranks of each set are equally spaced angularly of the crankshaft at ninety degree intervals and the direction of twist of the cranks of one set going from the front crank to the rear crank thereof is opposite to the direction of twist of the other set and the cranks in each bank are arranged such that the second crank is radially spaced from the first crank by ninety-degrees, the third crank radially spaced from the second crank by one-hundredeighty degrees, and the fourth crank radially spaced from the third crank by two-hundredseventy degrees.

17. An inherently balanced eight cylinder V-eight engine comprising two banks of four cylinders each arranged at an angle of substantially 36.9 degrees and including a crankshaft having eight angularly spaced cranks arranged in two sets of four oppositely twisting patterns with each crank connected to an engine cylinder in an arrangement whereby the resultant of the primary reciprocating inertia force rocking couples of the two cylinder banks is a rotating couple that can be` balanced by crankshaft ccunterweighting alone and wherein the secondary reciprocating inertia force rocking couples and the primary and secondary reciprocating inertia forces are inherently balanced within each bank.

1S. An inherently balanced eight cylinder V-eight engine comprising two banks of four cylinders each arranged at an angle of substantially 53.1 degrees and including a crankshaft having eight angularly spaced cranks arranged in two sets of four oppositely twisting patterns with each crank connected to an engine cylinder in an arrangement whereby the resultant of the primary reciprocating inertia force rocking couples of the two cylinder banks is a rotating couple that can be balanced by crankshaft counter- Weighting alone and wherein the secondary reciprocating inertia rocking couples and the primary 'and secondary reciprocating inertia forces are inherently balanced within each bank.

19. An inherently balanced eight cylinder V-eight engine comprising two banks of four cylinders each arranged at an angle of substantially 126.9 degrees and including a crankshaft having eight angularly spaced cranks arranged in two sets of four oppositely twisting patterns with eachcrank connected to an engine cylinder in an arrangement whereby the resultant of the primary reciprocating inertia force rocking couples of the two cylinder banks is a. rotating couple that can be baalnced by crankshaft counterweighting alone and wherein the secondary reciprocating inertia force rocking couples and the primary and secondary reciprocating inertia forces are inherently balanced within each bank.

20. An inherently balanced eight cylinder V-eight engine comprising two banks of four cylinders each arranged at an angle of substantially 143.1 degrees and including a crankshaft having eight angularly spaced cranks arranged in two sets of four oppositely twisting patterns with each crank connected to an engine cylinder in an arrangement whereby the resultant of the primary reciprocating inertia force rocking couples of the two cylinder banks is a rotating couple that can be balancedby crankshaft counterweighting alone and wherein the secondary reciprocating inertia force rocking couples and the primary and secondary reciprocating inertia forces are inherently balanced within each bank.

21. An eight cylinder V-type engine comprising a crankshaft extending longitudinally of the engine and a pair of banks of four cylinders each, said cylinder banks being arranged at an angle to one another of 36.9 degreesV such that the resultant of the primary reciprocating inertia force rocking couples of the two banks is a rotating couple that lies in a plane extending perpendicular to and longitudinally of the crankshaft whereby said resultant rotating couple can be counterbalanced by crankshaft counterweighting alone, said crankshaft having eight kangularly spaced apart cranks comprising twoI sets of four cranks each wherein the cranks of each set are equally spaced angularly about the crankshaft axis and the direction of twist of the cranks 0f one set going from the front crank to the rear crank thereof is opposite to the direction of twist of the other set, said cranks of each set being arranged such that going from front to rear of the crankshaft the second crank of each set is spaced angularly 9() degrees from the front crank, the third crank of each set is spaced angularly 180 degrees from the second crank and the fourth crank of each set isspaced angularly 270 degrees g: from the third crank.

- the resultant of the primary reciprocating inertia force rocking couples of the two banks is a rotating couple that lies in a plane extending perpendicular to and longitudinally of the crankshaft whereby said resultant rotating couple can be counterbalanced by crankshaft counterweighting alone, said crankshaft having eight angularly spaced apart cranks comprising two sets of four cranks each wherein the cranks of each set are equally spaced angularly about the crankshaft axis `and the direction of twist of the cranks of one setgoing from the front crank to the rear crank thereof is opposite to the direction of twist of the other set, said cranks of each set being arranged such that going from front to rear of the crankshaft the second crank of each set is spaced angularly 90 degrees from the front crank, the third crank of each set is spaced angularly 180 degrees from the second crank and the fourth crank of each set is spaced angularly 270 degrees from the third crank.

23. An eight cylinder V-type engine comprising a crankshaft extending longitudinally of the engine and a pair of banks of four cylinders each, said cylinder banks being arranged at an angle to one another of 126.9 degrees such that the resultant of the primary reciprocating inertia force rocking couples of the two banks is a rotating couple that lies in a plane extending perpendicular to and longitudinally of the crankshaft whereby said resultant rotating couple can be counterbalanced by crankshaft counterweighting alone, said crankshaft having eight angularly spaced apart cranks comprising two sets of four cranks each wherein the cranks of each set are equally spaced angularly about the crankshaft axis and the direction of twist of the cranks of one set going from the front crank to the rear crank thereof is opposite to the direction of twist of the other set, said cranks of each set being arranged such that going from front to rear of the crankshaft the second crank of each set is spaced angularly 90 degrees from the front crank, the third crank of each set is spaced angularly 180 degrees from the second crank and the fourth crank of each set is spaced angularly 270 degrees from the third crank.

24. An eight cylinder V-type engine comprising a crankshaft extending longitudinally of the engine and a pair of banks of four cylinders each, said cylinder banks being arranged at an angle to one another of 143.1 degrees such that the resultant of the primary reciprocating inertia force rocking couples of the two banks is a rotating couple that lies in a plane extending perpendicular to and longitudinally of the crankshaft whereby said resultant rotating couple can be counterbalanced by crankshaft counterweighting alone, said crankshaft having eight angularly spaced apart cranks comprising two sets of four cranks each wherein the cranks of each set are equally spaced angularly about the crankshaft axis and the direction of twist of the cranks of one set going from the front crank to the rear crank thereof is opposite to the direction of twist of the other set, said cranks of each set being arranged such that going from front to rear of the crankshaft the second crank of each set is spaced angularly 90 degrees from the front crank,

. Number Name Date 1,665,521 Wrentmore Apr. l0, 1928 1,911,874 Barkeij May 30, 1933 2,434,038 Ford Jan. 6, 1948 FOREIGN PATENTS Number Country Date 102,378 Great Britain Mar. l5, 1917 274,564 Italy May 26, 1930 l the third crank of eachssi-a` is' Sha degrees from the second crank acr' tgrarli crank of each set is spaced angularly 270 decgi; from the third crank.

25. In an inherently balanced eight cylinder V-type engine having a bank angle of other than ninety-degrees or full multiples thereof comprising two banks of four equally spaced apart cylinders alternately arranged longitudinally of the engine wherein the angle between `the two 'banks equals 180 degrees minus the angle by 'y which the primary rocking couple of one bank leads the primary rocking couple of the other bank and wherein the crankshaft for the engine includes eight angularly spaced apart cranks arranged in two sets of four equally angularly spaced apart cranks each with the cranks of each set arranged such that the direction of coil of each set of cranks when traveling from the front crank of each set to the rear crank thereof is opposite to that of the other set and wherein the front crank of one set is angularly spaced from 'the front crank of the other set by 143.1 degrees and the cranks in each bank are arranged such that the second crank is radially spaced from the first crank by ninety-degrees, the third crank radially spaced from the second crank by onehundred-eighty degrees, and the fourth crank radially spaced from the third crank by twohundred-seventy degrees.

26. In an inherently balanced eight cylinder V-type engine comprising two banks of four equally spaced apart cylinders alternately arranged longitudinally of the engine wherein the angle between the two banks equals substantially 36.9 degrees and wherein the crankshaft for the engine includes eight angularly spaced cranks arranged in two sets of four equally angularly spaced apart cranks each withV the cranks of each set arranged such that the direction of coil of each set of cranks when traveling from the front crank of each set to the rear crank thereof is opposite to that of the other set and wherein the front crank of one set is angularly spaced from the front crank of the other set by substantially 143.1 degrees and the cranks in each bank are arranged such that the second crank is radially spaced from the first crank by ninety-degrees, the third crank radially spaced from the second crank by one-hundred-eighty degrees, and the fourth crank radially spaced from the third crank by two-hundred-seventy degrees.

References Cited in the le of this patent UNITED STATES PATENTS