FIELD OF THE INVENTION:

This invention relates to the field of mechanical engineering.

Particularly, this invention relates to the field of load-driven energy system.

BACKGROUND OF THE INVENTION:

Energy can be transformed from one form to another.

There is a need for a system which infuses kinetic energy, with some impetus from electric energy, and uses them, both, to generate an output power which is greater than the input electric power.

OBJECTS OF THE INVENTION:

An object of the invention is to harness energy efficiently.

SUMMARY OF THE INVENTION:

According to this invention, there is provided a load-driven energy system, comprising: a motor configured to input motor power; an input drive configured to transfer said input motor power to further drives, said transferred input power being input drive power; a load bearing drive, configured with loads, in order to receive said input drive power, at a driver end, to transfer to drive said loads across said load bearing drive, said load bearing drive having a downward slope from its said driver end to its driven end, said loads sliding down said load bearing drive with: o a first force assisted with rails running laterally spaced apart from said load bearing drive, said first force being gravity-fed force caused due to said downward slope; o a second force provided by a load supporting drive provided further to said load bearing drive; o output of said loads bearing drive being load bearing force caused by the summation of said first force and said second force; said load supporting drive configure to receive said input drive power in order to drive a shaft, bearing second loads located at its distal driven end, through its driver end point connected to said load bearing drive by means of a cam which converts angular displacement caused by said input drive power to linear displacement of said shaft, said cam-based load displacement causing generation of said second force to be given to said load supporting drive; and an output drive connected to said driven end of said load bearing drive in order to provide said load bearing force to an alternator configured to output load- driven power.

In at least an embodiment, said input drive comprising: o a first drive, from said motor, configured to angularly displace a first angularly displaceable shaft;

□ a first teethed wheel located on a second angularly displaceable shaft, said second angularly displaceable shaft being transverse to said first angularly displaceable shaft; o a second drive, from a second teethed wheel coupled to said first teethed wheel by means of a second drive, said second teethed wheel located on a third angularly displaceable shaft, said third angularly displaceable shaft being laterally spaced apart from said second angularly displaceable shaft;

□ a third teethed wheel being located on said third angularly displaceable shaft;

□ a fourth teethed wheel connected to said third teethed wheel by means of a third drive, in that, radius of said fourth teethed wheel always being greater than radius of said third teethed wheel so as to cause a downward slope of said second drive from said third teethed wheel to said fourth teethed wheel in order to harness gravity-fed kinetic energy of loads on the said third drive; and

□ a fifth teethed wheel located on said third angularly displaceable shaft; said load bearing drive comprising: o a plurality of loads installed on said third drive, in that, • number of said loads being correlative to teeth of said third teethed wheel and adjusted according to said fourth teethed wheel;

• number of said loads being correlative to slope achieved between said third teethed wheel and said fourth teethed wheel;

□ a sixth teethed wheel coupled to said fifth teethed wheel by means of a fourth drive; said load supporting drive comprising: o a fourth angularly displaceable shaft configured to host said sixth teethed wheel, in that.

• a distal end, of said fourth angularly displaceable shaft, is fixed while a proximal end, of said fourth angularly displaceable shaft, is connected to an L-shaped lever, said distal end of said L-shaped lever being connected to a fifth angularly displaceable shaft; a short arm of said L-shaped lever being co-axial with said fourth angularly displaceable shaft and a long arm of said L-shaped lever extending away and upwards from said short arm and being orthogonal to said fourth angularly displaceable shaft; o a slide bearing provided at a point, on said fifth angularly displaceable shaft, such that it ensconces said sixth shaft circumferentially through a hole in said slide bearing; said output drive comprising o a sixth angularly displaceable shaft with a fixed end extends from an operative bottom of said slide bearing such its threadings forms a coupling between a threaded shaft and said slide bearing; o a seventh teethed wheel is connected by a fourth drive to an eighth teethed wheel; and o an eighth teethed wheel located, axially, about a seventh angularly displaceable shaft from which output is derived.

In at least an embodiment, said first drive being a belt drive configured to drive a communicably coupled first belt wheel which is coupled to a spaced apart worm and worm wheel by means of said first angularly displaceable first shaft; said first belt wheel, said worm, and said worm wheel being synchronously angularly displaceable in relation to output of said motor. In at least an embodiment, said first teethed wheel connected, by means of a said second drive being a first chain drive, to a second teethed wheel, located on said third shaft, said third shaft being spaced apart from said second shaft, the first teethed wheel being a free wheel ensuring that it moves in a single direction only.

In at least an embodiment, said first teethed wheel is the same diameter as the second teethed wheel.

In at least an embodiment, said second teethed wheel is located, axially, on said angularly displaceable third shaft and said third teethed wheel is located on same said angularly displaceable third shaft.

In at least an embodiment, on said third angularly displaceable shaft, said fifth teethed wheel is located such that said second teethed wheel and said fifth teethed wheel are on either side of said third teethed wheel, said second teethed wheel, said fifth teethed wheel, and said third teethed wheel are all co-axially located about said third angularly displaceable shaft.

In at least an embodiment, said third angularly displaceable shaft connects said third teethed wheel to said fifth teethed wheel, said second teethed wheel, said fifth teethed wheel, said third teethed wheel, and said third shaft being synchronously angularly displaceable.

In at least an embodiment, said fourth teethed wheel is connected to the third teethed wheel by means of said second drive.

In at least an embodiment, said fourth teethed wheel having a specific correlation with said third teethed wheel in terms of number of teeth / diameters / radii / size, in that, ratio of said fourth teethed wheel to said third teethed wheel, in terms of number of teeth / diameters / radii / size, is selected from a group of ratios consisting of 1:2, 1:3, 1:4, 1:5.

In at least an embodiment, said loads being provided pre-defined spaced apart intervals according to teeth of said third teethed wheel on said third drive. In at least an embodiment, said loads deriving support from rails running laterally spaced apart from said third drive, on either side of said second drive.

In at least an embodiment, half the number of teeth on said third teethed wheel equals distance between two consecutive loads.

In at least an embodiment, ratio, in terms of number of teeth / diameters / radii / size between said fifth teethed wheel and said sixth teethed wheel is 1:1.

In at least an embodiment, said L-shaped lever forming a cam such that angular displacement of said sixth teethed wheel causes said proximal end, of said fourth angularly displaceable shaft, to be angularly displaced, in a first direction, only up to a first end point before reversing the direction to cause angular displacement, in a second direction, only up to a second end point, and so on and so forth, to form a rocking angular displacement motion, in a roll degree of freedom of a first plane, of a short arm of the L-shaped lever; said long arm of said L-shaped lever, causes rocking itself in terms of angular displacement, in a yaw degree of freedom of a second plane, orthogonal to said first plane, said rocking angular displacement causes said fifth shaft to be linearly displaceable about is length-wise axis; due to said cam action provisioned by said L-shaped lever.

In at least an embodiment, said angular displacement, of the L-shaped lever, traverses 240 degrees which is 30 degrees beyond its highest point and 30 degrees beyond its lowest point, said extra traversal of 30 degrees, in either direction, provides extra force required to ride up said loads from their nadir point (at their point of engagement with the third teethed wheel) to their zenith point (at their point of disengagement with the third teethed wheel).

In at least an embodiment, said fifth angularly displaceable shaft has a proximal end which connects to said L-shaped lever and a distal end consisting essentially of an auxiliary load. In at least an embodiment, a sixth angularly displaceable shaft with a fixed end extends from an operative bottom of said slide bearing such that threadings, of said threaded sixth angularly displaceable shaft forms a coupling between said sixth threaded shaft and said slide bearing.

In at least an embodiment, said fourth teethed wheel is located, axially, about said sixth angularly displaceable shaft.

In at least an embodiment, said output generator is coupled to said seventh shaft by means of a belt drive.

In at least an embodiment, said input drive’ s shaft is the same as said output drive’s shaft.’

BRIEF DESCRIPTION OF THE ACCOMPANYING DRAWINGS:

The invention will now be described in relation to the accompanying drawings, in which:

FIGURES 1, 2, 3, and 4 illustrate various schematic drawings of the system of this invention;

FIGURES 5a and 5billustratea schematic drawing of a load and a load bracket associated with the load;

FIGURE 5c illustrates a schematic drawing of another type of the same load;

FIGURES 5d and 5e illustrate a schematic drawing of another type of the same load;

FIGURE 6 illustrates a schematic drawing of loads on the second chain drive; FIGURE 7 illustrates another schematic drawing of loads on the second chain drive;

FIFURE 8 illustrates another schematic drawing, depicting an alternative version, of the entire system.

FIGURES 9a, 9b, 9c, and 9d show various positions of the L- shaped lever along with corresponding location of loads (50) and corresponding location of auxiliary load;

FIGURES 10, 11, 12, and 13 illustrate the system of this invention in relation to rpm of drives at various nodes in the system; and FIGURE 14 illustrates how slope increases as ratio of driver end to driven end increases.

DETAILED DESCRIPTION OF THE ACCOMPANYING DRAWINGS: According to this invention, there is provided a load-driven energy system.

FIGURES 1, 2, 3, and 4 illustrate various schematic drawings of the system of this invention.

In at least an embodiment, input power being provided by means of a motor (12). Input power, according to a first non-limiting exemplary embodiment, can range from 1/15HP to 14 HP. The motor provides the requisite additional impetus to overcome, and compensate for, any frictional losses in this system that occur from input to output.

In at least an embodiment, a belt drive (11), from this motor (12), drives a communicably coupled first belt wheel (14a) which is coupled to a spaced apart worm and worm wheel (15a, 15b) by means of an angularly displaceable first shaft (16a); the first belt wheel (14a), the worm (15a), and worm wheel (15b) being synchronously angularly displaceable in relation to output of motor (12). RPM can be changed by changing belt wheel size of first belt wheel (14a) or ratio of worm and worm wheel (15a, 15b).

In at least an embodiment, a first teethed wheel (18a), located on a second shaft (16b), is connected, by means of a first chain drive (19a), to a second teethed wheel (18b), located on a third shaft (16c). The third shaft (16c) is spaced apart from the second shaft (16b). The first teethed wheel (18a) is, typically, a free wheel and ensures that it moves in a single direction only. The first teethed wheel (18a) is, in at least an embodiment, the same diameter as the second teethed wheel (18b).

In at least an embodiment, the second teethed wheel (18b) is located, axially, on the angularly displaceable third shaft (16c) and a third teethed wheel (18c) is located on the same angularly displaceable third shaft (16c). On the same angularly displaceable third shaft (16c), a fifth teethed wheel (18e) is located such that the second teethed wheel (18b) and the fifth teethed wheel (18e) are on either side of the third teethed wheel (18c); the second teethed wheel (18b), the fifth teethed wheel (18e), and the third teethed wheel (18c) are all co-axially located about the third shaft (16c).

In at least an embodiment, the third shaft (16c) connects the third teethed wheel (18c) to a fifth teethed wheel (18e); the second teethed wheel (18b), the fifth teethed wheel (18e), the third teethed wheel (18c), and the third shaft (16c) being synchronously angularly displaceable.

In at least an embodiment, a fourth teethed wheel (18d) is connected to the third teethed wheel (18c) by means of second chain drive (19b).The fourth teethed wheel (18d) has a specific correlation with the third teethed wheel (18c) in terms of number of teeth / diameters / radii / size. In a preferred embodiment, the ratio of the fourth teethed wheel (18d) to the third teethed wheel (18c), in terms of number of teeth / diameters / radii / size, is 1:2. In some other embodiments, this ratio can be 1:3, 1:4, 1:5, and so on and so forth. Basically, this increase in size from fourth teethed wheel (18d) to the third teethed wheel (18c) ensures a downward slope of the second chain drive (19b) from the third teethed wheel (18c) to the fourth teethed wheel (18d); this is very important to the working of this entire system because this slope ensures a gravity-fed mechanism which allows the system to harness gravity-fed kinetic energy of loads on the second chain drive (19b), as explained further.

The ratio, in terms of number of teeth/diameters/size, of the fourth teethed wheel (18d) to the third teethed wheel (18c) is 1:2, 1:3, 1:4, 1:5; this is according to the slope and length of the second chain drive (19b).

FIGUREs5a and 5billustratea schematic drawing of a load (50) and a load bracket (50a) associated with the load (50).

FIGURE 5c illustrates a schematic drawing of another type of the same load (50). FIGURES 5d and 5e illustrate a schematic drawing of another type of the same load (50).

FIGURE 6 illustrates a schematic drawing of loads (50) on the second chain drive (19b). FIGURE 7 illustrates another schematic drawing of loads (50) on the second chain drive (19b).

In at least an embodiment, there are a plurality of loads (50) installed on the second chain drive (19b). The number of these loads (50) can be 1, 2, 3, 4, 5, and so on and so forth; determined according to the teeth of the third teethed wheel drive (18c) and adjusted according to the fourth teethed wheel (18c).In at least an embodiment, a plurality of loads (50) are provided at pre-defined spaced apart intervals according to the teeth of the third teethed wheel (18c) on the second chain drive (19b). The loads (50) derive support from rails (52a, 52b) which run laterally spaced apart from the second chain drive (19b), on either side of the second chain drive (19b).

The slope of the second chain drive (19b), on its operative upper side, along with the weight of the load/s (50), is more than enough to induce kinetic energy into the load when it traverses the exit point (highest point where the second chain drive (19b) exits the third teethed wheel (18c)) of the second chain drive (19b) at the third teethed wheel (18c) up until it hits the entry point (engagement) of the second chain drive (19c) at the fourth teethed wheel (18d). This ‘induced’ kinetic energy is translated to further embodiments, discussed below, in this specification.

It is to be noted that number of loads (50) on the second chain drive (19b) is correlative to the slope achieved between the third teethed wheel (18c) and the fourth teethed wheel (18d); which is why number of loads (50), on the second chain drive (19b), is correlative to ratio of the fourth teethed wheel (18d) to the third teethed wheel (18c) in terms of number of teeth / diameters / radii / size, can be 1:2, 1:3, 1:4 or more.

According to preferred embodiments, if the ratio, in terms of number of teeth / diameters / radii / size, of the fourth teethed wheel (18d) to the third teethed wheel (18c) is 1:2, number of loads can be 1, 2, 3, 4, 5, or more.

According to preferred embodiments, if the ratio, in terms of number of teeth / diameters / radii / size, of the fourth teethed wheel (18d) to the third teethed wheel (18c) is 1:3, number of loads can be 1, 2, 3, 4, 5, or more. According to preferred embodiments, if the ratio, in terms of number of teeth / diameters / radii / size, of the fourth teethed wheel (18d) to the third teethed wheel (18c) is 1:4, number of loads can be 1, 2, 3, 4, 5, or more.

In at least an embodiment, it is to be noted that ^(number of teeth on the third teethed wheel (18c) = distance between two consecutive loads (50).

In at least an embodiment, a sixth teethed wheel (18f) is coupled to the fifth teethed wheel (18e) by means of a third chain drive (19c). The correlation, in terms of number of teeth / diameters / radii / size between the fifth teethed wheel (18e) and the sixth teethed wheel (18f), in preferred embodiments, is 1:1, as can be seen in FIGURE 1.

According to preferred embodiments, if the ratio, in terms of number of teeth / diameters / radii / size, of the fifth teethed wheel (18e) to the sixth teethed wheel (18f) is 1:1, number of loads can be 1, 2, 3, 4, 5 or more, as shown in Figure 10.

According to preferred embodiments, the ratio, in terms of number of teeth / diameters / radii / size, of the fifth teethed wheel (18e) to the sixth teethed wheel (18f) is 1:2, as shown in FIGURES 3, 9A, 9B, 9C, and 9D.

According to preferred embodiments, the ratio, in terms of number of teeth / diameters / radii / size, of the fifth teethed wheel (18e) to the sixth teethed wheel (18f) is 1:3, as shown in FIGURE 4.

In at least an embodiment, a fourth shaft (16d) is provided about which the sixth teethed wheel (18f). A distal end (25), of this fourth shaft (16d), is fixed while a proximal end (27), of this fourth shaft (16d), is connected to an L-shaped lever (30), the distal end (29) of the L-shaped lever (30) is connected to a fifth shaft (16e); the short arm of the L-shaped lever (30) being co-axial with the fourth shaft (16d) and the long arm of the L-shaped lever (30) extending away and upwards from the short arm and being orthogonal to the fourth shaft (16d). Essentially, the L-shaped lever (30) forms a cam such that angular displacement of the sixth teethed wheel (18f) causes the proximal end (27), of the fourth shaft (16d), to be angularly displaced, in a first direction, only up to a first end point before reversing the direction to cause angular displacement, in a second direction, only up to a second end point, and so on and so forth, to form a rocking angular displacement motion, in a roll degree of freedom of a first plane, of a short arm of the L-shaped lever (30). This limited angular displacement in a first direction and a second direction is due to the fact that the distal end (25) of the fourth shaft (16d) is fixed and causes limitations to the range of angular displacement of the fourth shaft (16d) in any direction. Meanwhile, the long arm of the L-shaped lever (30), also causes rocking itself in terms of angular displacement, in a yaw degree of freedom of a second plane, orthogonal to the first plane. This rocking angular displacement causes the fifth shaft (16e) to be linearly displaceable about is length- wise axis; due to the cam action provisioned by the L-shaped lever (30).

This angular displacement of lever causes generation of a second force which is an extra force which allows the loads (50) to traverse a driver end (18c) of from where slope begins so that it can freeball along the slope to the driven end (18d); thereby, causing generation of a first force. The provisioning of rails (52a) ensures that the loads get a smoother ride which is gravity-fed and also that this extra force is captured. Thus, the load (31) causes the load (50) to be lifted up to a zenith of downward slope. When loads (50) are down, the shaft (16e) is forwardly displaced and upwardly displaced by the cam (30). When loads (50) are up, the shaft (16e) is backwardly displaced and downwardly displaced by the cam (30).

In preferred embodiments, the angular displacement, of the L-shaped lever (30), traverser 240 degrees i.e. 30 degrees beyond its highest point and 30 degrees beyond its lowest point. This extra traversal of 30 degrees, in either direction, provides the extra force required to ride up the loads (50) from their nadir point (at their point of engagement with the third teethed wheel (18c)) to their zenith point (at their point of disengagement with the third teethed wheel (18c)).

FIGURES 9a, 9b, 9c, and 9d show various positions of the L-shaped lever (30) along with corresponding location of loads (50) and corresponding location of auxiliary load (31). In at least an embodiment, the fifth shaft (16e) has a proximal end (29) which connects to the L-shaped lever (30) and a distal end (31). An auxiliary load (60) can be provided at this fixed distal end (31) or at any point, in between, on the fifth shaft (16e).

Thus, the L-shaped lever (30) traverses 240 degrees for every load (50) present on the second chain drive (19b). When any load (50) is at the nadir point (at its point of engagement with the third teethed wheel (18c)), the proximal end (29) of the L- shaped lever (30) is 30 degrees beyond the positive 90 degrees (in a first quadrant) with respect to the axis of the fourth shaft (16d). When any load (50) is at the zenith point (at its point of disengagement with the third teethed wheel (18c)), the proximal end (29) of the L-shaped lever (30) is 30 degrees beyond the minus 90 degrees (in a fourth quadrant) with respect to the axis of the fourth shaft (16d).

In at least an embodiment, at some point, on the fifth shaft (16e), a slide bearing (35) is provided such that it ensconces the sixth shaft (16e) circumferentially through a hole in the slide bearing (35). A threaded sixth shaft (16f) with a fixed end (39) extends from the operative bottom of the slide bearing (35) such that the threadings (37), of the threaded sixth shaft (16f) form a coupling between the sixth threaded shaft (37) and the slide bearing (35). A linear displacement (forwardbackward displacement) of the fifth threaded shaft (16e) causes the slide bearing (35) to angularly displace, alternatingly, between a first angular displacement direction and a second angular displacement direction to cause the threaded sixth shaft (16f) to also be angularly displaced about its linear length- wise axis. The ‘induced’ kinetic energy, from angular displacement of the slide bearing (35), is transferred to the loads (50) which is translated an output (60).

In at least an embodiment, the fourth teethed wheel (18d) is located, axially, about a sixth shaft (16f). About this sixth shaft, a seventh teethed wheel (18g) is also provided which, further, is connected by a fourth chain drive (19d) to an eighth teethed wheel (18h).

In at least an embodiment, the eighth teethed wheel (18h) is located, axially, about a seventh shaft (16g) from which output is, eventually, derived. In at least an embodiment, an output generator (60) is coupled to the seventh shaft (16g) by means of a belt drive (13). The output (60) is more the electrical input (12); this jump is achieved by harnessing the gravity fed kinetic energy of the loads (50, 31) and further induced / enunciated by actions of the slide bearing (35) and the L-shaped lever (30).

In at least an embodiment, input drive’s shaft is the same as output drive’s shaft.

Output power, according to the first non-limiting exemplary embodiment, can range from 2 to 5 times of input power.

Flywheels (45) are provided, in a balanced manner, at various locations, on various shafts.

FIFURE 8 illustrates another schematic drawing, depicting an alternative version, of the entire system.

FIGURES 10, 11, 12, and 13 illustrate the system of this invention in relation to rpm of drives at various nodes in the system; and

FIGURE 14 illustrates how slope increases as ratio of driver end to driven end increases.

In terms of working,

1. The loads (50) moves to downward slope, it moves the third teethed wheel (18c) which is connected to the fifth teethed wheel (18e) through a third shaft (16c) and the fifth teethed wheel (18e) is connected to the sixth teethed wheel (18f) through a third chain drive (19c). The ratio of the fifth teethed wheel drive (18e) to sixth teethed wheel (18f) is 1:1. The sixth teethed wheel (18f) is connected to a fourth shaft (16d) which is connected to L-shaped lever (30). When the L- shaped lever (30) is in bottom position, at the same time loads (50a), in second chain wheel (21), moves to the downward slope. When the loads (50) moves downslope, it moves the third teethed wheel (18c) which is connected to the fifth teethed wheel (18e) through the third shaft (16c), at the same time fifth teethed wheel (18e) moves the sixth teethed wheel (18f) which is connected through a third chain drive (19c), and at the same time the sixth teethed wheel (18f) moves the L- shaped lever (30) to upward side, which is connected through the fourth shaft (16d). So, basically, loads (50) help the L-shaped lever (30) to move upward.

2. L-shaped lever (30) moves downward due to the load (31). The L-shaped lever (30) is connected to the load (31) through the long shaft (16e) via a slide bearing (35). The load (31) can be adjusted anywhere on the fifth shaft (16e) as per requirement. Due to the load (31), the L-shaped lever (30) moves downward rapidly through the slide bearing (35) which moves the fifth teethed wheel (18f) and the sixth teethed wheel (18e), which moves the third teethed wheel (18c), which helps the last load (50) on the second chain drive (19b) to step-up or move upward to an upper position of the third teethed wheel (18c). Basically, in this, the load (31) helps the load (50) to move upward.

The TECHNICAL ADVANCEMENT of this invention lies in inducing gravity- fed kinetic energy via loads, located on a sloped drive, and via loads which cause slide-bearings to angularly displace levers beyond their stipulated degree of angular displacement; thereby causing the extra thrust of kinetic energy which can be translated into electrical energy.

While this detailed description has disclosed certain specific embodiments for illustrative purposes, various modifications will be apparent to those skilled in the art which do not constitute departures from the spirit and scope of the invention as defined in the following claims, and it is to be distinctly understood that the foregoing descriptive matter is to be interpreted merely as illustrative of the invention and not as a limitation.