EARLIEST PRIORITY DATE

This Application claims priority from a Complete patent application filed in India having Patent Application No. 202141060642, filed on December 24, 2021, and titled “SYSTEM AND METHOD FOR SPIRAL HELICAL GEAR SETUP FOR SIMULTANEOUS AMPLIFICATION OF SPEED AND TORQUE”.

FIELD OF INVENTION

Embodiments of the present disclosure relate to the field of transmissions and more particularly to a system and a method for spiral helical gear setup for simultaneous amplification of speed and torque.

BACKGROUND

A gearbox is a mechanical power transmission equipment which enables a mechanical power transmission from a prime mover to a driven equipment. The gearbox may provide variations in speed and torque during the mechanical power transmission. In most of the gearbox, there may be an input shaft and an output shaft. The input shaft may be connected to the prime mover and the output shaft may be connected to the driven equipment.

Even though, the gearbox is capable of providing controlled application of mechanical power, the speed and the torque are always inversely proportional during the mechanical power transmission. The inverse relation between the speed and the torque during the mechanical power transmission may be due to geometrical constraints of gears being used in the gearbox. The geometrical constraints may include limitation in number of teeth per inch for a predefined diameter of the gears. The inverse relation between the speed and the torque in the gearbox is making the mechanical power transmission inefficient.

Hence, there is a need for an improved system and a method for spiral helical gear setup for simultaneous amplification of speed and torque to address the aforementioned issue(s). BRIEF DESCRIPTION

In accordance with an embodiment of the present disclosure, a system for spiral helical gear setup for simultaneous amplification of speed and torque is provided. The system includes a spiral helical gear shaft mechanically coupled with an input shaft gear. The spiral helical gear shaft is adapted to rotate corresponding to a rotation of the input shaft gear. The spiral helical gear shaft includes one or more first spiral helical gear profiles corresponding to a left hand helical gear and a right hand helical gear grooved in oppositely. The system also includes a herringbone gear meshed with the spiral helical gear shaft. The herringbone gear is adapted to rotate a herringbone gear shaft corresponding to the rotation and gear ratio of the spiral helical gear shaft. The system further includes a cam mechanically coupled with the herringbone gear. The cam is adapted to provide a linear displacement to the herringbone gear over the herringbone gear shaft by converting rotary motion of the input shaft gear to a linear motion, thereby resulting in simultaneous amplification of speed and torque.

In accordance with another embodiment of the present disclosure, a method for spiral helical gear setup for simultaneous amplification of speed and torque is provided. The method includes rotating, by an input shaft gear, a spiral helical gear shaft. The method also includes rotating, by a herringbone gear, a herringbone gear shaft corresponding to the rotation and gear ratio of the spiral helical gear shaft. The method further includes providing, by a cam, a linear displacement to the herringbone gear over the herringbone gear shaft by converting rotary motion of the input shaft gear to a linear motion.

To further clarify the advantages and features of the present disclosure, a more particular description of the disclosure will follow by reference to specific embodiments thereof, which are illustrated in the appended figures. It is to be appreciated that these figures depict only typical embodiments of the disclosure and are therefore not to be considered limiting in scope. The disclosure will be described and explained with additional specificity and detail with the appended figures.

BRIEF DESCRIPTION OF THE DRAWINGS

The disclosure will be described and explained with additional specificity and detail with the accompanying figures in which: FIG. 1 is a schematic representation of a spiral helical gear shaft and an input shaft gear in accordance with an embodiment of the present disclosure;

FIG. 2 is a schematic representation of the spiral helical gear shaft in a magnified form in accordance with an embodiment of the present disclosure;

FIG. 3 is a schematic representation of the herringbone gear and a herringbone gear shaft in accordance with an embodiment of the present disclosure;

FIG. 4 is a schematic representation depicting various views the spiral helical gear shaft in accordance with an embodiment of the present disclosure;

FIG. 5 is a schematic representation of a cam in accordance with an embodiment of the present disclosure;

FIG. 6 is a schematic representation of a system for spiral helical gear setup for simultaneous amplification of speed and torque in accordance with an embodiment of the present disclosure;

FIG. 7 is a schematic representation of one embodiment of the system of FIG. 6, depicting a position of the herringbone gear and the cam after a complete rotation of the spiral helical gear shaft in accordance with an embodiment of the present disclosure;

FIG. 8 is a schematic representation of one embodiment of the system of FIG. 6, depicting a side view of the herringbone gear, the spiral helical gear shaft, and the cam in accordance with an embodiment of the present disclosure;

FIG. 9 is a schematic representation of one embodiment of the system of FIG. 6, depicting a top view of the herringbone gear, the spiral helical gear shaft, and the cam in accordance with an embodiment of the present disclosure; and

FIG. 10 is a flow chart representing the steps involved in a method for spiral helical gear setup for simultaneous amplification of speed and torque in accordance with an embodiment of the present disclosure.

Further, those skilled in the art will appreciate that elements in the figures are illustrated for simplicity and may not have necessarily been drawn to scale. Furthermore, in terms of the construction of the device, one or more components of the device may have been represented in the figures by conventional symbols, and the figures may show only those specific details that are pertinent to understanding the embodiments of the present disclosure so as not to obscure the figures with details that will be readily apparent to those skilled in the art having the benefit of the description herein.

DETAILED DESCRIPTION

For the purpose of promoting an understanding of the principles of the disclosure, reference will now be made to the embodiment illustrated in the figures and specific language will be used to describe them. It will nevertheless be understood that no limitation of the scope of the disclosure is thereby intended. Such alterations and further modifications in the illustrated system, and such further applications of the principles of the disclosure as would normally occur to those skilled in the art are to be construed as being within the scope of the present disclosure.

The terms "comprises", "comprising", or any other variations thereof, are intended to cover a non-exclusive inclusion, such that a process or method that comprises a list of steps does not include only those steps but may include other steps not expressly listed or inherent to such a process or method. Similarly, one or more devices or sub-systems or elements or structures or components preceded by "comprises... a" does not, without more constraints, preclude the existence of other devices, sub-systems, elements, structures, components, additional devices, additional sub-systems, additional elements, additional structures, or additional components. Appearances of the phrase "in an embodiment", "in another embodiment" and similar language throughout this specification may, but not necessarily do, all refer to the same embodiment.

Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by those skilled in the art to which this disclosure belongs. The system, methods, and examples provided herein are only illustrative and not intended to be limiting.

In the following specification and the claims, reference will be made to a number of terms, which shall be defined to have the following meanings. The singular forms “a”, “an”, and “the” include plural references unless the context clearly dictates otherwise.

Embodiments of the present disclosure relate to a system and a method for spiral helical gear setup for simultaneous amplification of speed and torque. In accordance with an embodiment of the present disclosure, a system and a method for spiral helical gear setup for simultaneous amplification of speed and torque is provided. The system includes a spiral helical gear shaft mechanically coupled with an input shaft gear. The spiral helical gear shaft is adapted to rotate corresponding to a rotation of the input shaft gear. The spiral helical gear shaft includes one or more first spiral helical gear profiles corresponding to a left hand helical gear and a right hand helical gear grooved in oppositely. The system also includes a herringbone gear meshed with the spiral helical gear shaft. The herringbone gear is adapted to rotate a herringbone gear shaft corresponding to the rotation and gear ratio of the spiral helical gear shaft. The system further includes a cam mechanically coupled with the herringbone gear. The cam is adapted to provide a linear displacement to the herringbone gear over the herringbone gear shaft by converting rotary motion of the input shaft gear to a linear motion, thereby resulting in simultaneous amplification of speed and torque.

FIG. 1 is a schematic representation of a spiral helical gear shaft (20) and an input shaft gear (60) in accordance with an embodiment of the present disclosure. The system (10) includes a spiral helical gear shaft (20) mechanically coupled with an input shaft gear (60). The spiral helical gear shaft (20) is adapted to rotate corresponding to a rotation of the input shaft gear (60). The spiral helical gear shaft (20) includes one or more first spiral helical gear profiles (30) corresponding to a left hand helical gear and a right hand helical gear grooved in oppositely. In one embodiment, the spiral helical gear shaft (20) is coupled to the input shaft gear (60) via a spiral shaft gear (140). In some embodiments, a helix angle of the one or more first spiral helical gear profiles (30) may be selected in such a way that the helix angle may include maximum teeth per inch. The spiral helical gear shaft (20) may be described in detail in FIG. 2.

FIG. 2 is a schematic representation of the spiral helical gear shaft (20) in a magnified form in accordance with an embodiment of the present disclosure. In one embodiment, the one or more first spiral helical gear profiles (30) may be provided on the spiral helical gear shaft (20) by milling a plurality of flutes on a periphery of the spiral helical gear shaft (20). In one embodiment, the plurality of flutes may be provided in an opposing spiral pattern intersecting at a common point. In an exemplary embodiment, number of flutes may be two. In some embodiments, the plurality of flutes may be milled corresponding to gear profile of a left-hand helical gear and a right-hand helical gear in a mutually opposite manner. In such an embodiment, the common point may facilitate a herringbone gear (FIG. 3, 40) meshed with the spiral helical gear shaft (20) to travel past the plurality of flutes. In one embodiment, the plurality of flutes may be placed equidistantly at a first point (150) and a second point (160) of the spiral helical gear shaft (20). In some embodiments, length of the plurality of flutes may depend upon number of teeth to be cut for a single rotation of the herringbone gear (FIG. 3, 40). The herringbone gear (FIG. 3, 40) may be described in detail in FIG. 3.

FIG. 3 is a schematic representation of the herringbone gear (40) and a herringbone gear shaft (50) in accordance with an embodiment of the present disclosure. The system (10) includes a herringbone gear (40) meshed with the spiral helical gear shaft (20). The herringbone gear (40) is adapted to rotate a herringbone gear shaft (50) corresponding the rotation of the spiral helical gear shaft (20). In one embodiment, land height of the plurality of flutes may exceed depth of the herringbone gear (40) to provide a linear displacement of the herringbone gear (40) meshed with the spiral helical gear shaft (20). In one embodiment, the herringbone gear (40) may be fabricated by sandwiching two identical opposing helical gears of similar width, number of teeth and helix angle. In one embodiment, the spiral helical gear shaft (20) and the herringbone gear (40) may include equal number of teeth. In some embodiments, the spiral helical gear shaft (20) and the herringbone gear (40) may include unequal number of teeth. In one embodiment, diameter of the spiral helical gear shaft (20) may be smaller than the herringbone gear (40) for achieving mechanical advantage.

Further, in some embodiments, the herringbone gear (40) may include one or more second spiral helical gear profiles (80) corresponding to a left hand helical gear and a right hand helical gear grooved in oppositely. In such an embodiment, the one or more second spiral helical gear profiles (80) may be milled with or without space in between the one or more second spiral helical gear profiles (80) corresponding a space in between the plurality of flutes of the spiral helical gear shaft (20). In one embodiment, the one or more second spiral helical gear profiles (80) of the herringbone gear (40) may be meshed with the one or more first spiral helical gear profiles (30) of the spiral helical gear shaft (20) one at a time. In a specific embodiment, the one or more first spiral helical gear profiles (30) and the one or more second spiral helical gear profiles (80) may maintain center to center distance equal throughout.

Furthermore, in one embodiment, the herringbone gear shaft (50) may include a key way (100) adapted to enable the linear displacement of the herringbone gear (40) over the herringbone gear shaft (50). In a specific embodiment, the keyway (100) may be adapted to transmit the rotation of the herringbone gear (40) to the herringbone gear shaft (50) by restricting free rotation of the herringbone gear (40) over the herringbone gear shaft (50). In some embodiments, the herringbone gear (40) may be interfaced with the herringbone gear shaft (50) through a cage bearing (110) to reduce friction between the herringbone gear (40) and the herringbone gear shaft (50) during the linear displacement of the herringbone gear (40) over the herringbone gear shaft (50). In an exemplary embodiment, the cage bearing (110) may be a brass cage linear bearing. In one embodiment, the herringbone gear shaft (50) may be a linear ball spline shaft, spline shaft and the like. In a specific embodiment, a sliding bush (170) with key way slot (180) may act as a seal between the herringbone gear shaft (50) and the herringbone gear (40).

Also, in one embodiment, the sliding bush (170) may have an inner diameter to accommodate the cage bearing (110) and a key way slot (180) matching the key way (100) of the herringbone gear shaft (50). In such an embodiment, the sliding bush (170) may positively locks into the herringbone gear (40). In some embodiments, an inner diameter of the cage bearing (110) may match with an outer diameter of the herringbone gear shaft (50) and an outer diameter of the cage bearing (110) may match with the inner diameter of the sliding bush (170). In a specific embodiment, the cage bearing (110) may be cut axially corresponding a width of the key way (100) so as to enable the cage bearing (110) to slide over the herringbone gear shaft (50). In one embodiment, linear movement of the herringbone gear (40) over the herringbone gear shaft (50) may be provided by a cam (70). In some embodiments, the linear movement of the herringbone gear (40) over the herringbone gear shaft (50) may be provided by at least one of a screw road, spring assisted plate cam and the like. In such an embodiment, coupling of the screw road and the spring assisted plate cam may be pneumatic, hydraulic, or mechanical. Various views of the spiral helical gear shaft (20) is shown in FIG. 4. Operational arrangement of the cam (FIG. 5, 70) may be described in FIG. 5.

FIG. 5 is a schematic representation of a cam (70) in accordance with an embodiment of the present disclosure. The system (10) further includes the cam (70) which is mechanically coupled with the herringbone gear (40). The cam (70) is adapted to provide a linear displacement to the herringbone gear (40) over the herringbone gear shaft (50) by converting rotary motion of the input shaft gear (60) to a linear motion, thereby resulting in simultaneous amplification of speed and torque. In a specific embodiment, the linear displacement of the herringbone gear (40) may be a bidirectional movement over the herringbone gear shaft (50) corresponding to the rotation and gear ratio of the spiral helical gear shaft (20) and the cam (70). In one embodiment, the linear displacement of the herringbone gear (40) may provide center to center meshing between herringbone gear teeth and spiral helical shaft teeth throughout the operation.

Additionally, in a specific embodiment, the spiral helical gear shaft (20) may rotate completely, and the cam shaft gear (90) may rotate half corresponding to a complete rotation of the input shaft gear (60). In one embodiment, the cam (70) may be coupled to the input shaft gear (60) through a cam shaft gear (90). In such an embodiment, the cam shaft gear (90) may include a gear ratio of 2: 1 with the one or more first spiral helical gear profiles (30) and the one or more second spiral helical gear profiles (80). In an exemplary embodiment, the cam (70) may include two opposite slots. In such an embodiment, corresponding a single rotation of the cam (70), a cam follower (190) may undergo a liner movement from a left extreme point to a right extreme point and back to the left extreme point. In one embodiment, length of the linear movement may be calculated from the linear movement of the spiral helical gear shaft (20). In one embodiment, the cam follower (190) may be composed of a cam follower roller (200), cam follower roller bearing (210), and a cam follower shaft (220).

Moreover, in some embodiments, the linear movement of the cam follower shaft (220) may be transmitted to the herringbone gear (40) via thrust bearings (230), bracket (240), and a mounting plate (250). In one embodiment, the mounting plate (250) may be mechanically coupled to one or more linear movement round bearing blocks (120) sliding on corresponding one or more linear guide roads (130). In such an embodiment, the mounting plate (250) may be secured to the one or more linear movement round bearing blocks (120) to synchronize a movement of the one or more linear movement round bearing blocks (120). In one embodiment, the mounting plate (250) may include a hole through which the cam follower shaft (220) may be secured to the bracket (240).

Also, in one embodiment, the bracket (240) may be welded or bolted to the mounting plate (250). In some embodiments, the bracket (240) may house the herringbone gear (40) through one or more thrust bearings (230). In such an embodiment, the one or more thrust bearings (230) may be provided on either side of the herringbone gear (40) to facilitate the rotation and the linear displacement of the herringbone gear (40) by minimizing friction on the herringbone gear (40) irrespective of tensile forces or compressive forces acting on the bracket (240). Operational arrangement of the system (10) may be described in FIG. 6. FIG. 6 is a schematic representation of a system (10) for spiral helical gear setup for simultaneous amplification of speed and torque in accordance with an embodiment of the present disclosure. In operation, the input shaft gear (60) may be connected to an input shaft and the input shaft may be connected to at least one of a motor or a gearbox through a direct drive, a belt drive, a gear drive, or through any suitable mechanism. The input shaft gear (60) may provide power to the spiral shaft gear (140) and the cam shaft gear (90) simultaneously, thereby driving the spiral helical gear shaft (20) and the cam (70). A right hand gear profile of the one or more second spiral helical gear profiles (80) of the herringbone gear (40) meshed with a right hand flute of the spiral helical gear shaft (20) may start to rotate.

Further, a left hand gear profile of the one or more second spiral helical gear profiles (80) may not mesh with a left hand flute of the spiral helical gear shaft (20). Rotation of the cam (70) may cause a rotation of the cam follower roller (200) and the cam follower shaft (220) may start to slide on the cam (70). Sliding of the cam follower shaft (220) on the cam (70) may provide the linear displacement to the bracket (240) thereby pushing the herringbone gear (40) axially over the herringbone gear shaft (50). The linear displacement of the herringbone gear (40) may be equal to one teeth pitch of the spiral helical gear shaft (20). Repetition of events described above may cause the herringbone gear (40) to travel along an axis of the spiral helical gear shaft (20) at a pitch distance for every teeth rotation.

Furthermore, when the herringbone gear (40) reaches the common point of the plurality of flutes of the right hand gear profile and the left hand gear profile may pass over the plurality of flutes due to cutting of the plurality of flutes at the common point. When the spiral helical gear shaft (20) completes one rotation, the herringbone gear (40) may also undergo a complete rotation and the herringbone gear (40) may reach a first end (260) of the herringbone gear shaft (50). In such a scenario, the left hand gear profile the herringbone gear (40) may mesh with the left hand flute of the spiral helical gear shaft (20).

Moreover, the cam (70) may be completed half rotation and the cam follower roller (200) may be reached at an end of a slot provided on the cam (70). In such a scenario, the cam follower roller (200) and the cam follower shaft (220) may move in an opposite direction thereby displacing the bracket (240) in the opposite direction. Position of the herringbone gear (40) and the cam follower shaft (220) after the complete rotation of the spiral helical gear shaft (20) is shown in FIG. 7. Referring to FIG. 6, the linear displacement of the herringbone gear (40) to a second end (270) of the herringbone gear shaft (50) may be described as follows. The spiral helical gear shaft (20) may continue to rotate, and the herringbone gear (40) may also rotate in a same direction of rotation of the spiral helical gear shaft (20). Even though, direction of rotation of the herringbone gear (40) and the spiral helical gear shaft (20) are same, the linear displacement of the herringbone gear (40) may be reversed. The left hand gear profile of the one or more second spiral helical gear profiles (80) may mesh with the left hand flute of the spiral helical gear shaft (20). In such a scenario, meshing of the right hand gear profile of the one or more second spiral helical gear profiles (80) with the right hand flute of the spiral helical gear shaft (20) may not happen.

Additionally, the events described above may repeat and the spiral helical gear shaft (20) and the herringbone gear (40) may complete another complete rotation. The herringbone gear (40) may reach the second end (270) of the herringbone gear shaft (50) and the right hand gear profile of the one or more second spiral helical gear profiles (80) may mesh with the right hand flute of the spiral helical gear shaft (20). The cam (70) may complete another half of the rotation and hence the cam follower roller (200) may reach an initial position along with the cam follower shaft (220), the bracket (240) and the herringbone gear (40). The side view and the top view of the system (10) is shown in FIG. 8 and FIG. 9 respectively.

FIG. 10 is a flow chart representing the steps involved in a method (500) for spiral helical gear setup for simultaneous amplification of speed and torque in accordance with an embodiment of the present disclosure. The method (500) includes rotating a spiral helical gear shaft. In one embodiment, rotating a spiral helical gear shaft includes rotating a spiral helical gear shaft by an input shaft gear in step 510. In one embodiment, the spiral helical gear shaft is coupled to the input shaft gear via a spiral shaft gear. In some embodiments, a helix angle of the one or more first spiral helical gear profiles may be selected in such a way that the helix angle may include maximum teeth per inch. In one embodiment, the one or more first spiral helical gear profiles may be provided on the spiral helical gear shaft by milling a plurality of flutes on a periphery of the spiral helical gear shaft.

Further, in one embodiment, the plurality of flutes may be provided in an opposing spiral pattern intersecting at a common point. In an exemplary embodiment, number of flutes may be two. In some embodiments, the plurality of flutes may be milled corresponding to gear profile of a left-hand helical gear and a right-hand helical gear in a mutually opposite manner. In such an embodiment, the common point may facilitate a herringbone gear meshed with the spiral helical gear shaft to travel past the plurality of flutes. In one embodiment, the plurality of flutes may be placed equidistantly at a first point and a second point of the spiral helical gear shaft. In some embodiments, length of the plurality of flutes may depend upon number of teeth to be cut for a single rotation of the herringbone gear.

The method (500) also includes rotating a herringbone gear shaft corresponding to the rotation and gear ratio of the spiral helical gear shaft in step 520. In one embodiment, rotating a herringbone gear shaft corresponding to the rotation and gear ratio of the spiral helical gear shaft includes rotating a herringbone gear shaft corresponding to the rotation and gear ratio of the spiral helical gear shaft by a herringbone gear. In one embodiment, land height of the plurality of flutes may exceed depth of the herringbone gear to provide a linear displacement of the herringbone gear meshed with the spiral helical gear shaft. In one embodiment, the herringbone gear may be fabricated by sandwiching two identical opposing helical gears of similar width, number of teeth and helix angle. In one embodiment, the spiral helical gear shaft and the herringbone gear may include equal number of teeth. In some embodiments, the spiral helical gear shaft (20) and the herringbone gear (40) may include unequal number of teeth.

Also, in some embodiments, the herringbone gear may include one or more second spiral helical gear profiles corresponding to a left hand helical gear and a right hand helical gear grooved in oppositely. In such an embodiment, the one or more second spiral helical gear profiles may be milled with or without space in between the one or more second spiral helical gear profiles corresponding a space in between the plurality of flutes of the spiral helical gear shaft. In one embodiment, the one or more second spiral helical gear profiles of the herringbone gear may be meshed with the first spiral helical gear profiles of the spiral helical gear shaft one at a time. In a specific embodiment, the first spiral helical gear profile and the second spiral helical gear profile may maintain center to center distance equal throughout.

Additionally, in one embodiment, the herringbone gear shaft may include a keyway adapted to enable the linear displacement of the herringbone gear over the herringbone gear shaft. In a specific embodiment, the key way may be adapted to transmit the rotation of the herringbone gear to the herringbone gear shaft by restricting free rotation of the herringbone gear over the herringbone gear shaft. In some embodiments, the herringbone gear may be interfaced with the herringbone gear shaft through a cage bearing to reduce friction between the herringbone gear and the herringbone gear shaft during the linear displacement of the herringbone gear over the herringbone gear shaft. In an exemplary embodiment, the cage bearing may be a brass cage linear bearing. In one embodiment, the herringbone gear shaft may be a linear ball spline shaft. In a specific embodiment, a sliding bush with keyway may act as a seal between the herringbone gear shaft and the herringbone gear.

Moreover, in one embodiment, the sliding bush may have an inner diameter to accommodate the cage bearing and a key way slot matching the key way of the herringbone gear shaft. In such an embodiment, the sliding bush may positively locks into the herringbone gear. In some embodiments, an inner diameter of the cage bearing may match with an outer diameter of the herringbone gear shaft and an outer diameter of the cage bearing may match with the inner diameter of the sliding bush. In a specific embodiment, the cage bearing may be cut axially corresponding a width of the keyway so as to enable the cage bearing to slide over the herringbone gear shaft. In one embodiment, linear movement of the herringbone gear over the herringbone gear shaft may be provided by a cam.

The method (500) further includes providing a linear displacement to the herringbone gear over the herringbone gear shaft by converting rotary motion of the input shaft gear to a linear motion in step 530. In one embodiment, providing a linear displacement to the herringbone gear over the herringbone gear shaft by converting rotary motion of the input shaft gear to a linear motion includes providing a linear displacement to the herringbone gear over the herringbone gear shaft by converting rotary motion of the input shaft gear to a linear motion by a cam. In a specific embodiment, the linear displacement of the herringbone gear may be a bidirectional movement over the herringbone gear shaft corresponding to the rotation and gear ratio of the spiral helical gear shaft and the cam.

Further, in a specific embodiment, the spiral helical gear shaft may rotate completely, and the cam shaft gear may rotate half corresponding to a complete rotation of the input shaft gear. In one embodiment, the cam may be coupled to the input shaft gear through a cam shaft gear. In such an embodiment, the cam shaft gear may include a gear ratio of 2:1 with the one or more first spiral helical gear profiles and the one or more second spiral helical gear profiles. In one embodiment, the cam may include two opposite slots. In such an embodiment, corresponding a single rotation of the cam, a cam follower may undergo a liner movement from a left extreme point to a right extreme point and back to the left extreme point. In one embodiment, length of the linear movement may be calculated from the linear movement of the spiral helical gear shaft. In one embodiment, the cam follower may be composed of a cam follower roller, cam follower roller bearing, and a follower shaft.

Also, in some embodiments, the linear movement of the cam follower may be transmitted to the herringbone gear via thrust bearings, brackets, and a mounting plate. In one embodiment, the mounting plate may be mechanically coupled to one or more linear movement round bearing blocks sliding on corresponding linear guide roads. In such an embodiment, the mounting plate may be secured to the one or more linear movement round bearing blocks to synchronize a movement of the one or more linear movement round bearing blocks. In one embodiment, the mounting plate may include a hole through which the cam follower may be secured to the bracket.

Furthermore, in one embodiment, the bracket may be welded or bolted to the mounting plate. In some embodiments, the bracket may house the herringbone gear through one or more thrust bearings. In such an embodiment, the one or more thrust bearings may be provided on either side of the herringbone gear to facilitate the rotation and the linear displacement of the herringbone hear by minimizing friction on the herringbone gear irrespective of tensile forces or compressive forces acting on the bracket.

Various embodiments of the system and a method for spiral helical gear setup for simultaneous amplification of speed and torque described above enable various advantages. Provision of the spiral helical gear shaft meshed with the herringbone gear overcomes the geometrical constraints of the gears. Driving of the herringbone gear of larger diameter by the spiral helical gear shaft of smaller diameter provides increase in the torque corresponding to an increase in the speed. Provision of additional teeth on the periphery of the spiral helical gear shaft provides increase in the speed. Provision of the linear guide roads, and a plurality of bearings may reduce friction, thereby increasing mechanical efficiency. The system is composed of cheap and readily available components enabling cost effectiveness of the system. Further, the system may be assembled and operated easily. Selection of an optimum helix angle may further reduce a length of the spiral helical gear shaft, thereby eliminating chances of distortion or bending of the spiral helical gear shaft.

It will be understood by those skilled in the art that the foregoing general description and the following detailed description are exemplary and explanatory of the disclosure and are not intended to be restrictive thereof. While specific language has been used to describe the disclosure, any limitations arising on account of the same are not intended.

The figures and the foregoing description give examples of embodiments. Those skilled in the art will appreciate that one or more of the described elements may well be combined into a single functional element. Alternatively, certain elements may be split into multiple functional elements. Elements from one embodiment may be added to another embodiment. For example, the order of processes described herein may be changed and are not limited to the manner described herein. Moreover, the actions of any flow diagram need not be implemented in the order shown; nor do all the acts need to be necessarily performed. Also, those acts that are not dependent on other acts may be performed in parallel with the other acts. The scope of embodiments is by no means limited by these specific examples.