WO2013104968A1 - System and methods for converting rotational to linear motion with non - zero force - Google Patents

Abstract

Disclosed are a system and methods enabling conversion of rotational motion to linear reciprocating motion with non-zero force, wherein the system comprises: a yoke (10a,10b); a first gear (4a) and a second gear (4b); and a first crankshaft (5) and a second crankshaft (6).

Description

SYSTEM AND METHODS FOR CONVERTING ROTATIONAL TO LINEAR MOTION

WITH NON - ZERO FORCE

FIELD OF THE INVENTION

The present invention relates to a system for converting rotary motion to linear motion or vice versa, and more particularly, for use in connection with piston-driven machines.

BACKGROUND OF THE INVENTION

The present invention relates to a yoke mechanism which generates constant high force and provides a suitable replacement for crankshaft mechanism. By using gearing system and low torque high speed motor, large torque and force is developed but it cannot be used for operating positive displacement pump for generating high pressure, as present torque to force conversion mechanisms like crankshafts are inefficient to produce constant large or non zero force as the force generated varies with angles i.e. at zero degree, the force developed is zero, though it is very high at crank angle 90 degree. Thus, there is a need for a mechanism that converts rotational motion into linear reciprocating motion or vice versa with high non zero force, in order to use low power electric motor or engines for pumping with high or very high pressure.

There is also requirement of a system that works on the principle of reversible compression for compressing fluids providing gradually increasing force when compressing fluids, thereby increasing the efficiency of the system when employed for operation of pumps, compressors and engines.

US2006107918 by Mark M. Goltsman teaches linear to rotational motion conversion using an arrangement of Crankshaft, a yoke and gears. However, the invention does not provide means for generating constant high non-zero force to provide constant rotational to linear motion at any given instance of time. The arrangement of the crankpin journals in the above mentioned patent application do not provide a phase difference to establish said constant non-zero force. The yokes used in the above mentioned patent application's invention do not enable a V shaped yoke which has grooves or voids with a combination of straight and curved paths in them that allow the motion of extended bearings connected to crankpin journals. As a result there arises a need for a system and methods thereof to provide a simple and effective arrangement to enable constant conversion of rotational to linear motion at any given point of time.

The present invention through its various embodiments aims to address the various disadvantages and drawbacks of prior art and also provide alternate systems and methods for conversion of rotational energy into linear energy effectively. The force generated by the yoke mechanism of the present invention is constant and high due to the action of two components of resultant forces namely the horizontal and the vertical components of force acting on the yoke causing the horizontal linear motion of the yoke.

The object of the invention is also to provide an improved yoke crankshaft mechanism to convert rotational motion to linear reciprocating motion or vice versa which is substantially more efficient, compact and less expensive than other systems used for similar applications. SUMMARY OF THE INVENTION

The present invention in a preferred embodiment provides system and methods enabling conversion of rotational motion to linear reciprocating motion with non-zero force, wherein the system comprises:

a) a yoke;

b) a first gear and a second gear; and

c) a first crankshaft and a second crankshaft;

wherein the said first crankshaft and the said second crankshaft have at least two crankpin journals arranged in opposing motion to each other causing crank pin bearings to approach and move away from each other simultaneously and alternately within first and second slot in the said yoke body;

and wherein the said slot in each arm of the said yoke creates at least two curved and at least two straight paths in each arm of the said yoke;

and wherein the said first crankshaft and the said second crankshaft are linked to the said first gear and the said second gear respectively;

and wherein the said first crankshaft and the said second crankshaft move in opposing motion consequent to synchronous opposing rotatory motion of the said first gear and the said second gear;

and wherein the opposing motion of the said crankpin bearings exerts a non-zero force on the said yoke;

and wherein two components of the resultant forces, namely the horizontal and the vertical component of forces act on the said yoke;

and wherein the said non-zero force acts on the said yoke causing the yoke to move in linear motion.

BRIEF DESCRIPTION OF THE ACCOMPANYING DIAGRAMS

FIG. la is a diagrammatic representation of an example of the various force components acting on the straight path of the slot of the yoke in one of the embodiments of the invention, wherein components of force influence the forward motion of the yoke.

FIG. lb is a diagrammatic representation of an example of the various force components acting on the straight path of the slot of the yoke in one of the embodiments of the invention, wherein components of force influence the backward motion of the yoke.

FIG.2a is a diagrammatic representation of an example of construction of yoke of one of the embodiments of the invention, wherein the yoke angle is around 45 degrees.

FIG.2b is a diagrammatic representation of an example of construction of yoke of one of the embodiments of the invention, wherein the yoke angle is greater than 45 degrees.

FIG.2c is a diagrammatic representation of an example of constructionof yoke of one of the embodiments of the invention, wherein the yoke shows projections.

FIG.03 is a diagrammatic representation of an example of arrangement of one of the embodiments of the invention, wherein the crankshaft gear arrangement is depicted.

FIG.4a is a diagrammatic representation of an example of four slot yoke of one of the embodiments of the invention, wherein the shape of all the four slots of the yoke are shown. FIG.4b is a diagrammatic representation of an example of four slot yoke of one of the embodiments of the invention, wherein the shape of the two slots of the yoke showing projections and two slots without projections are shown.

FIG.05 is a diagrammatic representation of an example of top view of one of the embodiments of the invention, wherein arrangement of the different components of the system are shown.

FIG.06 is a diagrammatic representation of an example of internal view of one of the embodiments of the invention, wherein the internal view of the system is shown.

FIG.07 is a diagrammatic representation of an example of top view of one of the embodiments of the invention, wherein arrangement of the different components of the system are shown.

FIG.08 is a diagrammatic representation of an example of internal view of one of the embodiments of the invention, wherein the internal view of the system is shown.

FIG. 09 is a diagrammatic representation of an example of top view of one of the embodiments of the invention, wherein arrangement of the different components of the system are shown.

FIG.10 is a diagrammatic representation of an example of internal view of one of the embodiments of the invention, wherein the internal view of the system is shown.

FIG.11 is a graphical representation of an example of force on first yoke with respect to crank angle 0 to 90 degree at Φ=45°.

FIG.12 is a graphical representation of an example of force on first yoke with respect to crank angle 0 to 90 degree at Φ=55°.

FIG.13 is a graphical representation of an example of force on first yoke with respect to crank angle 0 to 90 degree at Φ=65°.

FIG.14 is a graphical representation of an example of force on first yoke with respect to crank angle 0 to 90 degree at Φ=75°.

FIG.15 is a graphical representation of an example of force on first yoke with respect to crank angle 0 to 90 degree at Φ=85°.

FIG.16 is a graphical representation of an example of force on first yoke with respect to crank angle 0 to 90 degree at Φ=89°.

FIG.17 is a graphical representation of an example of force on first yoke ' due to first crankshaft with respect to crank angle 0 to 360 degree at Φ=45°.

FIG.18 is a graphical representation of an example of force on first yoke due to second crankshaft with respect to crank angle 0 to 360 degree at Φ=45°.

DETAILED DESCRIPTION OF THE INVENTION

The present invention in a preferred embodiment provides system and methods enabling conversion of rotational motion to linear reciprocating motion with non-zero force, wherein the system comprises:

a) a yoke;

b) a first gear and a second gear; and

c) a first crankshaft and a second crankshaft;

wherein the said first crankshaft and the said second crankshaft have at least two crankpin journals arranged in opposing motion to each other causing crank pin bearings to approach and move away from each other simultaneously and alternately within first and second slot in the said yoke body; and wherein the said slot in each arm of the said yoke creates at least two curved and at least two straight paths in each arm of the said yoke;

and wherein the said first crankshaft and the said second crankshaft are linked to the said first gear and the said second gear respectively;

and wherein the said first crankshaft and the said second crankshaft move in opposing motion consequent to synchronous opposing rotatory motion of the said first gear and the said second gear;

and wherein the opposing motion of the said crankpin bearings exerts a non-zero force on the said yoke;

and wherein two components of the resultant forces, the horizontal and the vertical component of forces act on the said yoke;

and wherein the said non-zero force acts on the said yoke causing the yoke to move in linear motion.

The present invention in yet another preferred embodiment provides system and methods enabling conversion of rotational motion to linear reciprocating motion with non zero force, wherein the system comprises:

a) a first yoke and a second yoke;

b) a first crankshaft and a second crankshaft, each having at least two crank pin journals with at least two crankpin bearings;

c) a driving gear;

d) at least two driven gears;

e) at least two linking rods; and

f) at least two positioning rods;

wherein the said first yoke and the said second yoke, the said first crankshaft and the said second crankshaft, the said driving gear, the said at least two driven gears, the said at least two linking rods, the said at least two positioning rods, at least four piston - cylinder complex, and at least a bearing or bush are assembled in a housing;

and wherein the said first yoke and the said second yoke are 'V shaped;

and wherein the said first yoke and the said second yoke are arranged parallel to each other such that the upper arm and lower arm of the said first yoke is parallel to the upper arm and lower arm of the said second yoke;

and wherein the said first yoke and the said second yoke are arranged in the said housing by means of the said at least two positioning rods and bearings so as to facilitate only the linear movement of yoke;

and wherein the said first yoke and the said second yoke comprises at least two circular notches arranged in series and in opposing manner forming slots in each arm of the said first yoke and the said second yoke;

and wherein the said each slot in each arm of the said first yoke and the said second yoke creates at least two curved and at least two straight paths in each arm of the said first yoke and the said second yoke;

and wherein the upper arm of the said first yoke and the upper arm of the said second yoke are linked through the said first crankshaft such that the said first crankshaft passes through the slot of the upper arm of the said first yoke and the slot of the upper arm of the said second yoke; and wherein the lower arm of the said first yoke and the lower arm of the said second yoke are linked through the said second crankshaft such that the said second crankshaft passes through the slot of the lower arm of the said first yoke and the slot of the lower arm of the said second yoke; and wherein each of the said first crankshaft and the said second crankshaft consists of the said at least two crankpin journals arranged perpendicular to each other in order to maintain 90 degree phase difference;

and wherein the said at least two crankpin bearings fixed on the said at least two crankpin journals arranged perpendicular to each other on the said first crankshaft, rotates or slides within the curved and straight path alternately respective to the said slot of the upper arm of the said first yoke and the said slot of the upper arm of the said second yoke in contact, during each rotation of the said first crankshaft;

and wherein the said at least two crankpin bearings fixed on the said at least two crankpin journals arranged perpendicular to each other on the said second crankshaft, rotates or slides within the curved and straight path alternately respective to the said slot of the lower arm of the said first yoke and the said slot of the lower arm of the said second yoke in contact, during each rotation of the said second crankshaft;

and wherein the said at least two driven gears are linked to the said first crankshaft and the second crankshaft such that the motion of each of the said driven gear is dependent on each other and are in mutual engagement for synchronous opposing rotation of crankshafts;

and wherein the said driving gear meshes with the said driven gear;

and wherein the rotation of the said driving gear is initiated by an external source for operation of the system;

and wherein the torque can be applied to any one of the said first crankshaft and the said second crankshaft or both of the said first crankshaft and the second crankshaft for synchronous opposing rotation of crankshafts;

and wherein when the said crankpin bearings fixed on the said counter rotating crankshaft sliding on the straight path of yoke approach towards or away from each other, develop a reaction force wherein the reaction force drives the said first yoke and the said second yoke linearly, thus converting the rotational motion to linear reciprocating motion;

and wherein during 0 to 90 degree rotation from starting position of the said at least two driven gears in the opposite direction with respect to each other, the said first crankshaft and the said second crankshaft also rotate in opposite direction with respect to each other so that the said first yoke moves forward by displacement due to the reaction force of the said crankpin bearings fixed on the said counter rotating crankshaft, sliding on the straight path of yoke approach each other in the said slots of the arms of the said first yoke,and whereas the said second yoke stays at its first extreme position;

and wherein during 91 to 180 degree rotation of the said at least two driven gears in the opposite direction with respect to each other, the said second yoke moves forward by displacement due to the reaction force of the said crankpin bearings fixed on the said counter rotating crankshafts, sliding on the straight path of yoke approach each other in the said slots of the arms of the said second yoke, and whereas the said first yoke remains at second extreme position;

and wherein during 181 to 270 degree rotation of the said at least two driven gears in the opposite direction with respect to each other, the said first yoke moves backward by displacement due to the reaction force of the said crankpin bearings fixed on the said counter rotating crankshaft, sliding on the straight path of yoke moving away from each other in the said slots of the arms of the said first yoke, and whereas the said second yoke stays at second extreme position;

and wherein during 271 to 360 degree rotation of the said at least two driven gears in the opposite direction with respect to each other, the said second yoke moves backward by displacement due to the reaction force of the said crankpin bearings fixed on the said counter rotating crankshaft, sliding on the straight path of yoke moving away from each other in the said slots of the arms of the said second yoke, and whereas the said first yoke stays at first extreme position;

and wherein this cycle repeats with every rotation wherein each yoke completes one linear reciprocating motion;

and wherein the said each yoke is connected to a piston - cylinder complex by means of the said at least two linking rods connected to a piston head of the said piston- cylinder complex, so that the reciprocating motion of the yoke corresponds to the reciprocating motion of the piston head; and wherein the said system is further coupled to piston - cylinder or diaphragm to enable the operation of pumps or compressors; and

wherein the said system is further coupled to cylinder, piston and valves head of engines to enable the operation of engines.

In an embodiment of the invention, a method of working of the system enabling conversion of rotational motion to linear reciprocating motion with non zero force, comprising the steps of a) initiating the motion of the driving gear by an external source;

b) driving of driven gears by the driving gear in synchronous opposing motion;

c) rotating motion of the two crank shaft with respect to the opposing motion of the driven gears;

d) rotating motion of the two crankpin bearings of the crankpins, arranged at 90 degree phase difference to each other in the alternating straight and curved paths of the slots in the two arms of the two yokes;

e) displacing of the first yoke forwards during 0 to 90 degree rotation of the crankshaft due to the reaction force of first set of crankpin bearings of the two crankshaft in opposing rotation, sliding on the straight path of yoke approaching towards each other while the said second yoke stays at its first extreme position;

f) displacing of the second yoke forwards during 91 to 180 degree rotation of the crankshaft due to the reaction force of the second set of crankpin bearings of the two crankshaft in opposing rotation, sliding on the straight path of yoke approaching towards each other while the said first yoke remains at second extreme position; g) displacing of the first yoke backwards during 181 to 270 degree rotation of the crankshaft due to the reaction force of first set of crankpin bearings of the two crankshaft in opposing rotation, sliding on the straight path of yoke moving away from each other while the said second yoke stays at second extreme position; h) displacing of the second yoke backwards during 271 to 360 degree rotation of the crankshaft due to the reaction force of second set of bearings of the two crankshaft in opposing rotation, sliding on the straight path of yoke moving away from each other while the said first yoke stays at first extreme position; i) guiding of the reciprocating motion of the yoke through a piston reciprocating in a corresponding cylinder or diaphragm; and

j) enabling the pumping or compressing of fluid.

In an embodiment of the invention, a method of working of the system enabling conversion of linear reciprocating motion to rotational motion with non zero force, comprising the steps of a) reciprocating motion of the piston within the cylinder due to combustion and or pressurized fluid;

b) reciprocating motion of the linking rods of the yoke with respect to the piston motion; c) reciprocating motion of the yoke;

d) enabling opposing rotating motion of the two crankpin bearings on the crankpins, by forcing them in the alternating straight and curved paths of the slots in the two arms of the yoke or yokes with respect to the motion of the yoke or yokes;

e) transferring opposing rotating motion of the two crank shaft to the two gears linked to the crankshafts with respect to the opposing motion of the crankpin bearings; and f) rotating of the flywheel or gear/gears linked to the crankshaft and obtain power from system.

In an embodiment of the invention, the said yokes are further linked to guiding means for guiding the said yokes during its reciprocating linear movement, wherein the said guiding means includes a plurality of pistons and a plurality of cylinders wherein each piston is being mounted for reciprocating linear movement in a corresponding cylinder.

In an embodiment of the invention, the reciprocating motions of the plurality of pistons are converted to rotational motion by connecting a flywheel to the crankshafts.

In an embodiment of the invention, the two resultant components of force namely the horizontal component and the vertical components act on the yoke and both these components results in greater force which drives the yoke in horizontal linear motion.

In an embodiment of the invention, the total force acting on the yoke is given by the equation FT= T/r (cos0 + sin0tan< ), wherein T/r = F is tangential force at crank pin.

FT denotes total force generated by the system

T is the applied torque

r is the length of the lever arm vector (the lever arm is the perpendicular distance from the axis of rotation to the line of action of the force)

cos0 is the vertical component of force

sin0 is the horizontal component of force

Φ is the angle made by the yokes straight arm with the horizontal median passing through the centre of the yoke

"Θ" is the angle made by the rotating body or crank shaft with its initial position.

In an embodiment of the invention, the displacement of the yoke is given by the equation X = r (sin0 - cos0/ tan ), wherein

X is the linear displacement of yoke with respect to axis of rotation of crank shaft

r is the length of the lever arm vector (the lever arm is the perpendicular distance from the axis of rotation to the line of action of the force)

cos0 is the vertical component of force

sin0 is the horizontal component of force

"Θ" is the angle made by the rotating body or crank shaft with its initial position

Φ is the angle made by the yokes straight arm with the horizontal median passing through the centre of the yoke.

In an embodiment of the invention, the velocity is given by the equation

V = r ω (coscot + sincot/tan< )

V is the velocity of yoke

t is the time

ω is the angular velocity

cosco is the radial component of velocity

sinco is the perpendicular component of velocity

"Θ" is the angle made by the rotating body or crank shaft with its initial position

Φ is the angle made by the yokes straight arm with the horizontal median passing through the centre of the yoke.

In an embodiment of the invention, the displacement is maximum at Φ =45 degrees.

In an embodiment of the invention, angle between straight paths of slots of arms of V shaped yoke is 90 degrees.

In an embodiment of the invention, when the bearing fixed on the crankpins of counter rotating crankshafts approaches towards or away from each other, the reaction force drives V shaped yoke in a linear motion with force FT = FT ^" ( 1+ sin20).

In an embodiment of the invention, for Φ is greater than 45° (Φ is the angle formed between the straight portion of yoke slot and the horizontal median passing through the centre of the yoke) the force developed on the yoke is in the increasing order causing reversible compression of gases, using considerable minimum energy for compressing gases.

In an embodiment of the invention, when the system is employed for incompressible fluids, the angle Φ should be around 45 degrees.

In an embodiment of the invention, the system employs the principle of reversible compression of gases and requires considerable minimum energy for compressing gases.

In an embodiment of the invention, the said system when used in a combustion engine includes projections in the slots of the yokes wherein the said solid projection is aligned in the same angle as that of the straight portion of the slot of the yoke with respect to the horizontal median of the yoke.

In an embodiment of the invention, the solid projection is held in place by providing a means for support in the form of a closed side wall on one side of the yoke.

In an embodiment of the invention, the system when used in a combustion engine includes projections in the slots of both the arms of the two yokes, wherein the said projections help to eliminate any lag of a piston due to insufficient force during combustion.

In an embodiment of the invention, the said system when used in a combustion engine prevents lagging of any piston due to the presence of projections in the slots whereby crankpin bearings slides or rotates on the projection, keeping the motion constant and continuous so that the lag by one piston does not affect the cyclic motion of all the pistons in phase with the reciprocating motion of the yoke.

In an embodiment of the invention, the system provides a waiting period for a certain time at the end of each reciprocating cycle of the yoke, to provide additional time for opening or closing of valves to avoid slip of valves when used in pumps.

In an embodiment of the invention, the system provides a waiting period for a certain time at the end of each reciprocating cycle of the yoke, to provide additional time for combustion as well as to open and close valves thereby causing availability of fully opened valves during suction and exhaust stroke in combustion engines.

In an embodiment of the invention, in case of a single yoke, the straight portion of the slot is longer than the curved portion, which may help in reducing the waiting time at the end of each reciprocating cycle of the yoke.

In an embodiment of the invention, the combined effect of the said four slots in the two yokes generates a very high force.

In an embodiment of the invention, the system converts rotational motion into linear reciprocating motion with a high non zero force and permits use of low power electric motor or engines for pumping fluids with high or very high pressure.

In an embodiment of the invention, the said system can be configured with a valve system to power engines such as but not limited to internal combustion engine, diesel engine, hot bulb engine, gasoline engine, hesselman engine, HCCI engine, IRIS engine, engine cooling; external combustion engine, steam engine, steam turbine, sterling engine, reciprocating engine, compressed air engine, hot gasses engine, hydraulic engine, pneumatic engine or any combinations thereof. In an embodiment of the invention, the said system can be configured with a valve system to power pumps such as but not limited to positive displacement pump, rotator positive displacement pump, reciprocating positive displacement pump, gear pump, screw pump, progressing cavity pump, roots - type pump, peristaltic pump, plunger pump, triplex - style plunger pump, compressed air powered double diaphragm pump, rope pump, flexible impeller pump, impulse pump, hydraulic ram pump, velocity pump, centrifugal pump, radial flow pump, axial flow pump, mixed flow pump, educator - jet pump, gravity pump, steam pump, valveless pump or any combinations thereof.

In an embodiment of the invention, wherein the positioning rods prevent any other movement of the yoke other than the said linear reciprocating motion, facilitating the greatest conversion of rotational motion to linear motion by preventing other power robbing conditions and vibrations.

In an embodiment of the invention, the crankpin bearings may be supported by another arm fixed to the housing for additional support of the crankpin bearings.

In an embodiment of the invention, the system comprises a pair of separable yoke members, crankshaft members, gear members, and releasable attachment means between said members providing for separation of the said members.

In an embodiment of the invention, the driving gear may be driven by means such as but not limited to a power source, peddle driven, manual, automated or any combinations thereof.

In an embodiment of the invention, a series of driven gear meshing each other is incorporated in the system in order to decrease speed and increase torque thereby increase in the force.

In an embodiment of the invention, the system enabling conversion of rotational motion to linear reciprocating motion with non - zero force can work efficiently with a single yoke or many yokes although two yokes is preferred.

In an embodiment of the invention, the system enabling conversion of rotational motion to linear reciprocating motion with non - zero force may be constructed using four crankshafts and four arm yokes having four arms arranged along the diagonal of a square and each arm having yoke slot. Arrangement is such that axes of four crankshafts remains parallel to each other and passes through vertices of square and being rotated by four identical gears meshing each other being in mutual engagement for synchronous opposing rotation and driven by drive gear in order to increase stability and force during conversion of rotational to linear reciprocating motion.

In an embodiment of the invention, the system when constructed with four yokes functions such that two of the yokes work simultaneously while the other two yokes waits till the former yokes have moved, followed by the movement of the later yokes while the former yokes which have moved waits, and the cycle repeats. In an embodiment of the invention, the system constructed with four yokes is used exclusively for multistage compressors.

In an embodiment of the invention, the word "gear" deems to include all those bodies moving in a rotatory motion and can transmit torque such as but not limited to belt system, pulley system, chain drive system, belt sheave system, chain sprocket system or any combinations thereof.

In an embodiment of the invention, the gear may be any suitable gear such as but not limited to spur gears, helical gears, skew gears, double helical gears, bevel gears, spiral gears, hypoid gears, crown gears, worm gears, non circular gears, rack and pinion gears, epicyclic gears, sun and planet gears, harmonic drive gears, cage gears, herringbone gears, internal gears, racks gears, face gears, involute spline gears, straight sided spline gears, sprocket gears, magnetic gears or any combinations thereof.

In an embodiment of the invention, the system may be configured with a valve system while used in engines or pumps and the valve may be any suitable valve such as but not limited to ball valve, poppet valve, butterfly valve, control valve, globe valve, needle valve, check valve, clack valve, non-return valve, one-way valve, tap valve, control valves, directional control valve, oneway valve, two-way valve, three-way valve, four-way valve, zone valve, reed valve or any combinations thereof.

In an embodiment of the invention, the system employs reversible compression of fluids wherein the fluid may be any fluid such as but not limited to liquids, gases, plasma, plastic solids, vapors, ideal fluid, real fluid, newtonian fluid, non-newtonian fluid, shear thinning fluid, bingham plastic, rheopectic ideal plastic fluid, isotropic fluids, anisotropic fluids, polymer fluids, atmospheric gases, green house gases, real gases, noble gas, isotopes of the said gases, or any combinations thereof.

In an embodiment of the invention, suitable lubrication system may be employed to reduce frictional losses to moving parts employing regimes of lubrications such as but not limited to fluid film lubrication, hydrostatic lubrication, hydro dynamic lubrication, elasto hydro dynamic lubrication, boundary lubrication or any combinations thereof.

In an embodiment of the invention, the shape of the yoke can be any shape resembling "V".

In an embodiment of the invention, a transverse cross-section of the yoke may be of any suitable shape such as but not limited to circular, oval, elliptical, square, triangular, rectangular, pentagonal, polygonal, any of the n-sided polygon, where n = 3 to infinity (infinity corresponds to a circle), closed wavy, irregular or any combinations thereof, wherein slots containing curved and straight paths can be carved.

In an embodiment of the invention, the word "bearings" deems to include all connectors or joints that provide relative motion between two or more parts such as but not limited to linear motion, spherical motion, axial motion, hinge motion or any combinations thereof. In an embodiment of the invention, piston - cylinder complex is a portion or component of piston assembly to which a yoke is connected via linking rods.

In an embodiment of the invention, a bearing is any suitable bearing such as but not limited to ball bearings, roller bearings, ball - thrust bearings, self aligning ball bearings, deep groove ball bearings, needle bearings, cylindrical bearings, spherical bearings, sleeve bearings or any combinations thereof.

In an embodiment of the invention, the yoke may be of any suitable transverse cross-sectional size and having suitable lengths of straight and curved paths according to waiting period of said yoke at extreme position wherein waiting period depends on length of curved paths and changeable as per application.

In an embodiment of the invention, the component or the parts of the system may be coated, painted or colored with a suitable chemical to retain or improve its properties, or to improve the aesthetics or appearance.

In an embodiment of the invention, the components of the present invention may be connected or arranged by using any suitable method and may include without limitation use of one or more of welding, adhesives, riveting, fastening devices such as but not limited to screw, nut, bolt, hook, clamp, clip, buckle, nail, pin, ring.

In an embodiment of the invention, the terms "reciprocating" and "oscillating" may be alternately used to mean the horizontal linear motion of the yoke.

In an embodiment of the invention, the terms "slots" and "transverse slots" may be alternately used.

DETAILED DESCRIPTION OF THE ACCOMPANYING DIAGRAMS

TABLE-1 : Gives the list of different labels along with their definition provided in the figures from FIG No. la to FIG No.14.

LABELLING NOS LABEL

1 Housing

2 Driving gear

3 Crankpin j ournals

4a,b Driven gear

4c,d,e series of driving gears meshing each other

19a,b,c,d Gears of the four crankshaft model

5 Crankshaft

5a Crankshaft bearings 6 Crankshaft

6a Crankshaft bearings

7a Crankpin bearings

7b Crankpin bearings

8a Crankpin bearings

8b Crankpin bearings

10a Yoke

10b Yoke

10c Yokewith projections

lOd Four slot yoke

lOe Four slot yoke with projections

12 a, b, c, d, e, f, g, h Curved paths

13 a, b, c, d, e, f, g, h Straight paths

14 Positioning rod bearings

15a, 15b Projections

16 Positioning rod

17 Piston included in the cylinder

18 Electric motor

100a, b Grooves for linking rod

101a, b Grooves for positioning rod

102a, b Grooves for positioning rods on the housing surface

FIG la is a diagrammatic representation of an example of the various force components acting on the straight path of the slot of the yoke in one of the embodiments of the invention, wherein components of force influence the forward motion of the yoke. There are two components of force acting on the yoke favoring the forward movement of the yoke. The horizontal component and the vertical component of force push the yoke in a forward linear motion. The total force acting on the yoke is given by the equation,

F_T= T/r (cosO + sin0tan< ), wherein T/r = F is tangential force at crank pin with bearing (7a) / (7b)

F_T denotes total force generated by the system

T is the applied torque

r is the length of the lever arm vector (the lever arm is the perpendicular distance from the axis of rotation to the line of action of the force)

cosO is the vertical component of force

sinO is the horizontal component of force

tan< is the angle made by the yokes straight arm (13 a) / (13 d) with the horizontal median passing through the centre of the yoke

"Θ" is the angle made by the rotating body or crank shaft with its initial position.

FIG lb is a diagrammatic representation of an example of the various force components acting on the straight path of the slot of the yoke in one of the embodiments of the invention, wherein components of force influence the backward motion of the yoke. There are two components of force acting on the yoke favoring the forward movement of the yoke. The horizontal component and the vertical component of force push the yoke in backward linear direction. The total force acting on the yoke is given by the equation,

F_T= T/r (cos0 + sin0tan< ), wherein, T/r = F is tangential force at crank pin with bearing (7a) / (7b)

F_T denotes total force generated by the system

T is the applied torque

r is the length of the lever arm vector (the lever arm is the perpendicular distance from the axis of rotation to the line of action of the force)

cos0 is the vertical component of force

sin0 is the horizontal component of force

tan< is the angle made by the yokes straight arm (13c) / (13b) with the horizontal median passing through the centre of the yoke

"Θ" is the angle made by the rotating body or crank shaft with its initial position.

FIG 2a is a diagrammatic representation of an example of yoke of one of the embodiments of the invention, wherein the yoke angle is around 45 degrees. The yoke (10a) has two arms having a slot in each arm of the yoke. Each slot has curved paths (12a, 12b, 12c, 12d) and straight paths (13a, 13b, 13c, 13d) alternating each other. The grooves (100a, 100b) are grooves for linking rods and the grooves (101a, 101b) are grooves for positioning rods.

FIG. 2b is a diagrammatic representation of an example of yoke of one of the embodiments of the invention, wherein the yoke angle is greater than 45 degrees. The yoke (10b) has two arms having a slot in each arm of the yoke. Each slot has curved paths (12a, 12b, 12c, 12d) and straight paths (13a, 13b, 13c, 13d) alternating each other. The grooves (100a, 100b) are grooves for linking rods and the grooves (101a, 101b) are grooves for positioning rods.

FIG. 2c is a diagrammatic representation of an example of yoke of one of the embodiments of the invention, wherein the yoke shows projections (15a, 15b). The yoke (10c) is meant for use in combustion engines wherein each slot has projections included. The yoke has two arms having a slot in each arm of the yoke. Each slot has curved paths (12a, 12b, 12c, 12d) and straight paths (13a, 13b, 13c, 13d) alternating each other. The grooves (100a, 100b) are grooves for linking rods and the grooves (101a, 101b) are grooves for positioning rods.

FIG. 03 is a diagrammatic representation of an example of arrangement of one of the embodiments of the invention, wherein the crankshaft gear arrangement is depicted. The crankshaft (5) is connected to gear (4a) and crankshaft (6) is connected to gear (4b). The gears (4a) and (4b) mesh each other such that the motion of each of the said driven gear is dependent on each other and are in mutual engagement for synchronous opposing rotation of crankshafts (5) and (6). Each crankshaft has two crankpin journals (3) arranged at a phase difference of 90 degree. Each crankpin journals (3) have on them crankpin bearings (7a), (7b), (8a), (8b). The crankshaft (5) has bearings (7a) and (8a) and crankshaft (6) has bearings (7b) and (8b). FIG. 4a is a diagrammatic representation of an example of four slot yoke of one of the embodiments of the invention, wherein the shape of all the four slots of the yoke are shown. Each slot has curved paths (12a, 12b, 12c, 12d, 12e, 12f, 12g, 12h) and straight paths (13a, 13b, 13c, 13d, 13e, 13f, 13g, 13h) alternating each other. The grooves (100a, 100b) are grooves for linking rods.

FIG. 4b is a diagrammatic representation of an example of four slot yoke of one of the embodiments of the invention, wherein the shape of the two slots of the yoke showing projections (15a, 15b) and two slots without projections are shown.The slots have curved paths (12a, 12b, 12c, 12d, 12e, 12f, 12g, 12h) and straight paths (13a, 13b, 13c, 13d, 13e, 13f, 13g, 13h) alternating each other. The grooves (100a, 100b) are grooves for linking rods.

FIG. 05 is a diagrammatic representation of an example of top view of one of the embodiments of the invention, wherein arrangement of the different components of the system are shown. The system is enclosed in housing (1). The top arrangement of the two yokes (10a) and (10a) linked to gear (4a) through crankshaft (5) having a crankshaft bearing (5a). The yoke is linked to the piston head through a linking rod connected to the yoke. The piston is included in the cylinder (17). An electric motor (18) is connected to the system. The housing has two grooves (102a, 102b) on its surface for positioning rods (16).

FIG. 06 is a diagrammatic representation of an example of internal view of one of the embodiments of the invention, wherein the internal view of the arrangement of the components in the system is shown. The two yokes (10a) and (10a) are linked through crankshaft (5) having bearing (5a) and crankshaft (6) having bearing (6a). Gear (4a) is linked to the crankshaft (5) and gear (4b) is linked to the crankshaft (6). The two positioning rods (16), having bearings (14) help to hold the two yokes (10a) and (10a) parallel to each other in a housing. A series of driven gears (4c, 4d, 4e) meshing each other is incorporated in the system in order to decrease speed and increase torque thereby increase in the force. The driving gear (2) drives the series of driven gears (4c, 4d, 4e).The four crankpin bearings (7a), (7b), (8a) and (8b) are stationed in their respective slots to enable their sliding or rotating movement within the slots.

FIG. 07 is a diagrammatic representation of an example of top view of one of the embodiments of the invention, wherein arrangement of the different components of the system are shown. The yokes (10c) and (10c) are held parallel to each other by means of bearings of positioning rods (14) in a housing (1). The upper arm of the two yokes (10c) and (10c) are linked through a crankshaft (5) having a crankshaft bearing (5 a). Gear (4a) is linked to the crankshaft (5). The four piston - cylinder complex (17) are connected to the two yokes (10c) and (10c). The housing has two grooves (102a, 102b) on its surface for positioning rods (16). The crankpin bearing (8a) slides and or rotates within the curved and straight paths of the slot of the yoke (10c).

FIG. 08 is a diagrammatic representation of an example of internal viewof one of the embodiments of the invention, wherein the internal view of the system is shown.The two yokes (10c) and (10c) are linked through crankshaft (5) having bearing (5 a) and crankshaft (6) having bearing (6a). Gear (4a) is linked to the crankshaft (5) and gear (4b) is linked to the crankshaft (6). The two positioning rods (16), having bearings (14) help to hold the two yokes (10c) and (10c) parallel to each other in a housing.

FIG. 09 is a diagrammatic representation of an example of top view of one of the embodiments of the invention, wherein arrangement of the different components of the system are shown.The yoke (lOd) has four arms arranged along the diagonal of a square. Two of the four gears

(19a,19c) are shown in the figure. The arrangement is housed in housing (1).

FIG. 10 is a diagrammatic representation of an example of internal view of one of the embodiments of the invention, wherein the internal view of the system is shown. The yoke (lOd) has four arms arranged along the diagonal of a square and each arm has a yoke slot. The four crankshafts are rotated by four identical gears (19a,19b,19c,19d) meshing each other being in mutual engagement for synchronous opposing rotation.

TABLE -2 gives the total force generated by the system for "Θ" values enumerated in the table.

The Inference drawn from the above table suggests that the system generates constant large force at all angles.

FIG.11 is a graphical representation of an example of force on first yoke with respect to crank angle 0 to 90 degree, when Φ = 45°. The x axis represents the measure of crank angle and y axis represents the measure of force in multiple of T/r = F. The graph shows that the force generated is between IF to 1.414F. Where F = T/r is tangential force at crank pin.

FIG.12 is a graphical representation of an example of force on first yoke with respect to crank angle 0 to 90 degree, when Φ = 55°. The x axis represents the measure of crank angle and y axis represents the measure of force. The graph shows that the force generated is between IF to 1.74F. Where F = T/r is tangential force at crank pin.

FIG.13 is a graphical representation of an example of force on first yoke with respect to crank angle 0 to 90 degree, when Φ = 65°. The x axis represents the measure of crank angle and y axis represents the measure of force. The graph shows that the force generated is between IF to 2.36 F. Where F = T/r is tangential force at crank pin.

FIG.14 is a graphical representation of an example of force on first yoke with respect to crank angle 0 to 90 degree, when Φ = 75°. The x axis represents the measure of crank angle and y axis represents the measure of force. The graph shows that the force generated is between IF to 3.85F. Where F = T/r is tangential force at crank pin.

FIG.15 is a graphical representation of an example of force on first yoke with respect to crank angle 0 to 90 degree, when Φ = 85°. The x axis represents the measure of crank angle and y axis represents the measure of force. The graph shows that the force generated is between IF to 11.47 F. Where F = T/r is tangential force at crank pin.

FIG.16 is a graphical representation of an example of force on first yoke with respect to crank angle 0 to 90 degree, when Φ = 89°. The x axis represents the measure of crank angle and y axis represents the measure of force. The graph shows that the force generated is between IF to 57.29 F. Where F = T/r is tangential force at crank pin.

FIG.17 is a graphical representation of an example of force on first yoke due to first crankshaft with respect to crank angle 0 to 360 degree. The x axis represents the measure of crank angle and y axis represents the measure of force in multiple of T/r = F.

FIG.18 is a graphical representation of an example of force on first yoke due to second crankshaft with respect to crank angle 0 to 360 degree. The x axis represents the measure of crank angle and y axis represents the measure of force in multiple of T/r = F.

While the present invention is susceptible of embodiment in various forms, there is shown in the drawings and will hereinafter be described a presently preferred embodiment with the understanding that the present disclosure is to be considered an exemplification of the invention and is not intended to limit the invention to the specific embodiments illustrated. The use of "including", "comprising" or "having" and variations thereof herein is meant to encompass the items listed thereafter and equivalents thereof as well as additional items.

For the purpose of this invention the term "indented" means any indented surface which may be a section of closed structures whose transverse cross-section may be of any suitable shape such as but not limited to circular, oval, elliptical, square, triangular, rectangular, pentagonal, polygonal, any of the n-sided polygon, where n = 3 to infinity (infinity corresponds to a circle), closed wavy, irregular, or any combinations thereof.

The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that the terms "comprises" or "comprising," when used in this specification, specify the presence of stated features, integers, steps, operations, elements, or components, but do not preclude or rule out the presence or addition of one or more other features, integers, steps, operations, elements, components, or groups thereof. Furthermore, this invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments or examples set forth herein. Rather, these embodiments or examples are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the invention to those skilled in the art. Like reference numerals refer to like elements throughout the description of the figures or diagrams. It will be understood that when an element is referred to as being "connected" or "coupled" to another element, it can be directly connected or coupled to the other element or intervening elements may be present. In contrast, when an element is referred to as being "directly connected or coupled" to another element, there are no intervening elements present. Furthermore, "connected" or "coupled" as used herein may include wirelessly connected or coupled. As used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items.

The aim of this specification is to describe the invention without limiting the invention to any one embodiment or specific collection of features. Person skilled in the relevant art may realize the variations from the specific embodiments that will nonetheless fall within the scope of the invention.

It may be appreciated that various other modifications and changes may be made to the embodiment described without departing from the spirit and scope of the invention.

Claims

I CLAIM,

1. A system and method enabling conversion of rotational motion to linear reciprocating motion or vice versa with non zero force, wherein the system comprises:

a) a yoke;

b) a first gear and a second gear; and

c) a first crankshaft and a second crankshaft;

wherein the said first crankshaft and the said second crankshaft have at least two crankpin journals arranged in the opposing motion to each other causing crank pin bearings to approach and move away from each other simultaneously and alternately within first and second slot in the said yoke body;

and wherein the said slot in each arm of the said yoke creates at least two curved and at least two straight paths in each arm of the said yoke;

and wherein the said first crankshaft and the said second crankshaft are linked to the said first gear and the said second gear respectively;

and wherein the said first crankshaft and the said second crankshaft move in opposing motion consequent to synchronous opposing rotatory motion of the said first gear and the said second gear;

and wherein the opposing motion of the said crankpin bearings exerts a non-zero force on the said yoke;

and wherein two components of the resultant forces, namely the horizontal and the vertical component of forces act on the said yoke;

and wherein the said non-zero force acts on the said yoke causing the yoke to move in linear motion.

2. A system and method enabling conversion of rotational motion to linear reciprocating motion or vice versa with non zero force, wherein the system comprises:

a) a first yoke and a second yoke;

b) a first crankshaft and a second crankshaft, each having at least two crank pin journals with at least two crankpin bearings;

c) a driving gear;

d) at least two driven gears;

e) at least two linking rods; and

f) at least two positioning rods;

wherein the said first yoke and the said second yoke, the said first crankshaft and the said second crankshaft, the said driving gear, the said at least two driven gears, the said at least two linking rods, the said at least two positioning rods, at least four piston - cylinder complex and at least a bearing or bush are assembled in a housing;

and wherein the said first yoke and the said second yoke are 'V shaped;

and wherein the said first yoke and the said second yoke are arranged parallel to each other such that the upper arm and lower arm of the said first yoke is parallel to the upper arm and lower arm of the said second yoke; and wherein the said first yoke and the said second yoke are arranged in the said housing by means of the said at least two positioning rods and bearings so as to facilitate only the linear movement of yoke;

and wherein the said first yoke and the said second yoke comprises at least two circular notches arranged in series and in opposing manner forming slots in each arm of the said first yoke and the said second yoke;

and wherein the said each slot in each arm of the said first yoke and the said second yoke creates at least two curved and at least two straight paths in each arm of the said first yoke and the said second yoke;

and wherein the upper arm of the said first yoke and the upper arm of the said second yoke are linked through the said first crankshaft such that the said first crankshaft passes through the slot of the upper arm of the said first yoke and the slot of the upper arm of the said second yoke;

and wherein the lower arm of the said first yoke and the lower arm of the said second yoke are linked through the said second crankshaft such that the said second crankshaft passes through the slot of the lower arm of the said first yoke and the slot of the lower arm of the said second yoke;

and wherein each of the said first crankshaft and the said second crankshaft consists of the said at least two crankpin journals arranged perpendicular to each otherin order to maintain 90 degree phase difference;

and wherein the said at least two crankpin bearings fixed on the said at least two crankpin journals arranged perpendicular to each other on the said first crankshaft, rotates or slides within the curved and straight path alternately respective to the said slot of the upper arm of the said first yoke and the said slot of the upper arm of the said second yoke in contact, during each rotation of the said first crankshaft;

and wherein the said at least two crankpin bearings fixed on the said at least two crankpin journals arranged perpendicular to each other on the said second crankshaft, rotates orslides within the curved and straight path alternately respective to the said slot of the lower arm of the said first yoke and the said slot of the lower arm of the said second yoke in contact, during each rotation of the said second crankshaft;

and wherein the said at least two driven gears are linked to the said first crankshaft and the second crankshaft such that the motion of each of the said driven gear is dependent on each other and are in mutual engagement for synchronous opposing rotation of crankshafts; and wherein the said driving gear meshes with the said driven gear;

and wherein the rotation of the said driving gear is initiated by an external source for operation of the system;

and wherein the torque can be applied to any one of the said first crankshaft and the said second crankshaft or both of the said first crankshaft and the second crankshaft for synchronous opposing rotation of crankshafts;

and wherein when the said crankpin bearings fixed on the said counter rotating crankshaft sliding on the straight path of yoke approach towards or away from each other, develop a reaction force wherein the reaction force drives the said first yoke and the said second yoke linearly, thus converting the rotational motion to linear reciprocating motion; and wherein during 0 to 90 degree rotation from starting position of the said at least two driven gears in the opposite direction with respect to each other, the said first crankshaft and the said second crankshaft also rotate in opposite direction with respect to each other so that the said first yoke moves forward by displacement due to the reaction force of the said crankpin bearings fixed on the said counter rotating crankshaft, sliding on the straight path of yoke approach each other in the said slots of the arms of the said first yoke, and whereas the said second yoke stays at its first extreme position;

and wherein during 91 to 180 degree rotation of the said at least two driven gears in the opposite direction with respect to each other, the said second yoke moves forward by displacement due to the reaction force of the said crankpin bearings fixed on the said counter rotating crankshafts, sliding on the straight path of yoke approach each other in the said slots of the arms of the said second yoke, and whereas the said first yoke remains at second extreme position;

and wherein during 181 to 270 degree rotation of the said at least two driven gears in the opposite direction with respect to each other, the said first yoke moves backward by displacement due to the reaction force of the said crankpin bearings fixed on the said counter rotating crankshaft, sliding on the straight path of yoke moving away from each other in the said slots of the arms of the said first yoke, and whereas the said second yoke stays at second extreme position;

and wherein during 271 to 360 degree rotation of the said at least two driven gears in the opposite direction with respect to each other, the said second yoke moves backward by displacement due to the reaction force of the said crankpin bearings fixed on the said counter rotating crankshaft, sliding on the straight path of yoke moving away from each other in the said slots of the arms of the said second yoke, and whereas the said first yoke stays at first extreme position;

and wherein this cycle repeats with every rotation wherein each yoke completes one linear reciprocating motion;

and wherein the said yoke is connected to a piston - cylinder complex by means of the said at least two linking rods connected to a piston head of the said piston- cylinder complex, so that the reciprocating motion of the yoke corresponds to the reciprocating motion of the piston within the said corresponding cylinder;

and wherein the said system is further coupled to piston-cylinder, diaphragm to enable the operation of pumps or compressor;

and wherein the said system is further coupled to piston-cylinder, valve head to enable the operation of engines.

3. The system enabling conversion of rotational motion to linear reciprocating motion or vice versa with non zero force of claim 1 , wherein the said yokes are further linked to guiding means for guiding the said yokes during its reciprocating linear movement, wherein the said guiding means includes a plurality of pistons and a plurality of cylinders wherein each piston is being mounted for reciprocating linear movement in a corresponding cylinder.

4. The system enabling conversion of rotational motion to linear reciprocating motion or vice versa with non zero force of claim 2, wherein the combined effect of the said four slots in the two yokes generates a very high force.

5. The system enabling conversion of linear reciprocating motion to rotational motion with non zero force of claim 2, wherein the reciprocating motion of the plurality of pistons are converted to rotational motion by linking a flywheel to the crankshafts.

6. The system enabling conversion of rotational motion to linear reciprocating motion or vice versa with non zero force of claim 2, wherein the system when used in a combustion engine, includes projections in the slots of both the arms of the two yokes, wherein the said projections help to eliminate any lag of piston due to insufficient force during combustion, wherein the lag is resolved by the action of bearings sliding or rotating on the projection keeping the motion constant and continuous so that the lag by one piston does not affect the cyclic motion of all the pistons in phase with each other and in turn in phase with the reciprocating motion of the yoke.

7. The system enabling conversion of rotational motion to linear reciprocating motion or vice versa with non zero force of claim 2, wherein the positioning rods prevent any other movement of the yoke other than the said reciprocating motion, facilitating the greatest conversion of rotational motion to linear motion by preventing other power robbing conditions and vibrations.

8. The system enabling conversion of rotational motion to linear reciprocating motion or vice versa with non zero force of claim 2, can be used in systems employing compressible and incompressible fluids wherein the value of "< "(the angle made by the yokes straight arm with the horizontal median passing through the centre of the yoke) can be varied to accommodate the reversible compression of compressible fluids.

9. The system enabling conversion of rotational motion to linear reciprocating motion or vice versa with non zero force of claim 1 and 2, wherein the system provides a waiting period for a certain time at the end of each reciprocating cycle, to provide additional time for opening or closing of valves to avoid slip of valves when used in pumps and a little more time for combustion, as well as availability of fully opened valves during suction and exhaust stroke and additional time for combustion when being used in combustion engines and wherein waiting period depends on lengths of curved and straight paths of said yoke slots.

10. The system enabling conversion of rotational motion to linear reciprocating motion or vice versa with non zero force of claim 2, wherein the system has a series of driven gears meshing each other in order to decrease speed and increase torque thereby increasing the force.

11. The system enabling conversion of rotational motion to linear reciprocating motion or vice versa with non zero force of claim 2, wherein the said system can be configured with valves head and piston - cylinder system to obtain mechanical power from combustion gases or pressurized fluids in engines.

12. The system enabling conversion of rotational motion to linear reciprocating motion or vice versa with non zero force of claim 2, wherein the said system can be configured with valves and piston-cylinder or diaphragm system to suck, pump or compress fluids.

13. The system enabling conversion of rotational motion to linear reciprocating motion or vice versa with non zero force of claim 2, wherein the said system can be configured with a valve system while used in engines or pumps selected from a set of ball valve, poppet valve, butterfly valve, control valve, globe valve, needle valve, check valve, clack valve, non-return valve, one-way valve, tap valve, control valves, directional control valve, oneway valve, two-way valve, three-way valve, four-way valve, zone valve, reed valve and any combinations thereof.

14. The system enabling conversion of rotational motion to linear reciprocating motion or vice versa with non zero force of claim 2, wherein the system comprises a pair of separable yoke members, crankshaft members, gear members, and releasable attachment means between said members providing for separation of the said members.

15. The system enabling conversion of rotational motion to linear reciprocating motion or vice versa with non zero force of claim2, wherein the said gear is a gear selected from a set of spur gears, helical gears, skew gears, double helical gears, bevel gears, spiral gears, hypoid gears, crown gears, worm gears, non circular gears, rack and pinion gears, epicyclic gears, sun and planet gears, harmonic drive gears, cage gears, and magnetic gears and any combinations thereof.

16. A method of working of the system enabling conversion of rotational motion to linear reciprocating motion with non zero force, comprising the steps of

a) initiating the motion of the driving gear by an external source;

b) driving of driven gears by the driving gear in synchronous opposing motion; c) rotating motion of the two crank shaft with respect to the opposing motion of the driven gears;

d) rotating motion of the two crankpin bearings of the crankpins, arranged at 90 degree phase difference to each other in the alternating straight and curved paths of the slots in the two arms of the two yokes;

e) displacing of the first yoke forwards during 0 to 90 degree rotation of the crankshaft due to the reaction force of first set of crankpin bearings of the two crankshaft in opposing rotation, sliding on the straight path of yoke approaching towards each other while the said second yoke stays at its first extreme position; f) displacing of the second yoke forwards during 91 to 180 degree rotation of the crankshaft due to the reaction force of the second set of crankpin bearings of the two crankshaft in opposing rotation, sliding on the straight path of yoke approaching towards each other while the said first yoke remains at second extreme position;

g) displacing of the first yoke backwards during 181 to 270 degree rotation of the crankshaft due to the reaction force of first set of crankpin bearings of the two crankshaft in opposing rotation, sliding on the straight path of yoke moving away from each other while the said second yoke stays at second extreme position; h) displacing of the second yoke backwards during 271 to 360 degree rotation of the crankshaft due to the reaction force of second set of bearings of the two crankshaft in opposing rotation, sliding on the straight path of yoke moving away from each other while the said first yoke stays at first extreme position; i) guiding of the reciprocating motion of the yoke through a piston reciprocating in a corresponding cylinder; and

j) enabling the pumping or compressing of fluid.

17. A method of working of the system enabling conversion of linear reciprocating motion to rotational motion with non zero force, comprising the steps of

a) reciprocating motion of the piston within the cylinder due to combustion and or pressurized fluid;

b) reciprocating motion of the linking rods of the yoke with respect to the piston motion;

c) reciprocating motion of the yoke;

d) enabling opposing rotating motion of the two crankpin bearings on the crankpins, by forcing them in the alternating straight and curved paths of the slots in the two arms of the yoke or yokes with respect to the motion of the yoke or yokes;

e) transferring opposing rotating motion of the two crank shaft to the two gears linked to the crankshafts with respect to the opposing motion of the crankpin bearings; and f) rotating of the flywheel or gear/gears linked to the crankshaft and obtain power from system.