Transmission device, transmission system and multiplier transmission system

Abstract

Conventional planetary transmission systems exhibit an inherent trade-off between speed and torque. The present transmission embodiments overcome this limitation by achieving a 1 : 2 speed increase while preserving torque transfer efficiency of 1 : 1. Key Features : Kinematic Symmetry. Identical sun and planet gear diameters produce a predictable 1 : 2 speed ratio, based on the classical sun-planet mechanism patented by James Watt in 1781. This principle is re-engineered in the present embodiments for enhanced compactness, mechanical robustness and torque retention. Torque Retention. The planetary gear is constrained from rotating about its own axis but remains free to orbit the sun gear. This orbital motion converts tangential force from the driven planetary gear carrier into output torque. This conversion exploits the entire center-to-center distance between the sun gear and the rotationally constrained planetary gear as an effective lever arm, enabling torque retention at 1 : 1 ratio relative to input torque.

Description

[0001]TITLE of the INVENTION TRANSMISSION DEVICE, TRANSMISSION SYSTEM AND MULTIPLIER TRANSMISSION SYSTEM TECHNICAL FIELD of the INVENTION The present invention relates to mechanical power transmission systems having gears or chain & sprockets mechanisms. The type of mechanical power transmission system presented here can be utilized in any power train application. BACKGROUND of the INVENTION James Watt & The Steam Engine. The Steam Engine, as developed by Frenchman Denis Papin (1647- 1712), Englishmen James Savery (1650-1715), Thomas Newcomen (1664-1729) and Scotsman James Watt (1736-1819), was to pump water out of flooded coal mines, (SEE FIG. 1(A) & 1(B). Main structure is 1. water pump 6 is pivotally connected to main beam 4 via connecting rod bar 5. The fire side consist of broiler 2 and cylinder chamber 3 which houses the piston and connecting rod which is also pivotally connected to main beam 4). The pinnacle of steam engine design was the addition of a separate condenser and a double acting cylinder, patented by Instrument Mechanic James Watt in 1869 & 1782 respectively. In the late 18th century, the Industrial Revolution was in full acceleration with corn, malt and cotton mills, iron-rolling mills, blast furnaces, forges and a dozen other burgeoning new industries. These new industries needed a new kind of power to supplement the old rotating waterwheel. Mills of all kind used these water wheels and also horses to turn “wheel work”, but while these sources of power were adequate for small operations, the quantity of water available were often limited, and the use of enormous herds of horses was frequently impractical. A steam engine with a rotative capacity was needed, not merely one which would pump mines dry with the reciprocal - vertical motion of its horizonal rocking beam. This reciprocal / vertical motion of the horizontal rocking beam was easily converted to rotary motion by means of a crank mechanism which was incorporated into a Newcomen Steam engine and patented by Englishman James Pickard in 1780, (SEE FIGS. 2A & 2B. Main beam 4 is pivotally mounted on main structure 1, 7 is the crank lever, rigidly connected to the flywheel 9a via a crank shaft 8. Connecting rod 5 is pivotally connected to main beam 4 and crank lever 7 via its respective end portions. So, to circumvent the crank mechanism patent, Watt assigned William Murdock, Chief Mechanic at Bolton & Watt Steam Engine Ltd., to devised alternatives for the conversion of the reciprocal vertical motion of the rocking beam to rotary motion. William Murdock devised 5 alternatives and these 5 alternatives were patented by James Watt. British Patent No.1306, October 25, 1781. Of the five alternatives, the one that was adopted was a peculiar arrangement of two gears that are similar in diameter and number of teeth in a sun - planet configuration, (SEE FIGS.3A, 3B, & 3C. Main beam 4 is pivotally mounted on main structure 1, fire side consist of broiler 2 and cylinder chamber 3 which houses the piston and connecting rod 5 which is pivotally connected to the main beam 4. Rotative side consist of sun gear 11 rigidly attached to output shaft 12 which is rigidly attached to flywheel 9b. Planet gear 10 is rigidly attached to end portion of connecting rod 5, and is pivotally attached to main beam 4 at opposite end portion which was where the water pump was previously positioned. Sun gear 11 and planet gear 10 are kept in mesh by tie bar 13a. In the Watt patented design, the planet gear 10 being rigidly attached to the end portion of connecting rod 5 does not rotate on its own axis (rigidly attached). Its axle is tied to the axle of the sun gear 11 by a tie bar 13a that rotate around the axles of both the planet and sun gears preserving a constant distance between their centers keeping them meshed, SEE FIGS.3A, 3B & 3C. Hence, the rigidly attached planet gear 10 orbits around the sun gear 11. The first phenomenon of this design is that for every one orbit of the rigidly attached planet gear 10 around the sun gear 11, there are two rotations of the sun gear on its axis. The following sequential views FIGS.4A-4H illustrate this operational principle. Initial Position FIG. 4A: • Planet gear 10 is meshed with sun gear at position ^^^^=0oTDC 16 (top dead center). • Reference mark (A) on planet gear. • Reference mark (1) on sun gear. 1stQuarter Orbit FIG. 4B: • Rigidly attached planet gear 10 orbits 900in a clockwise (CW)direction and rotates the sun gear 11 in a CW direction. • Sun gear reference mark (1) now at ^^^^=18002ndQuarter (Half) Orbit FIG. 4C: • Rigidly attached planet gear 10 reaches 1800of CW orbital travel, BTC 18(bottom dead center). • Sun gear 11 has been rotated another 1800for a total of 3600 and its reference mark (1) is now back at ^^^^ = 00, TDC3rdQuarter Orbit FIG.4D: • Rigidly attached planet gear 10 reaches 2700of CW orbital travel. •Sun gear 11 has been rotated another 1800 for a total of ^^^^ =5400and its reference mark (1) is now back at BDC 18. 4thQuarter (Full) Orbit FIG.4E: • Rigidly attached planet gear 10 reaches 3600of CW orbital travel. •Sun gear 11 has been rotated another 1800 for a total of ^^^^ =7200and reference mark (1) is now back at TDC 16. • A speed transfer ratio of 1:2. Connected to the sun gear via an output shaft 12 is a flywheel 9b to provide smooth rotative power to the factory floor. The flywheel 9b reduces the jerky motion which is the nature of the reciprocal vertical motion of the beam 4. This leads to the second phenomenon in that a flywheel 9b turning through two revolutions during a single cycle of operation needs to be only one-fourth the seize compared to a flywheel 9a of the crank mechanism, SEE FIGS.2A, 2B, 3A ,3B & 3C. As impressive as it was, with its 1:2 speed ratio and only requiring a flywheel 9b one fourth the seize that what is required for a crank mechanism 9a, the overarching objective was to obtain rotative power as efficiently as possible. So, inevitable the sun-planet mechanism 10, 11, 12 & 13a was abandoned and the crank mechanism 7, 8 & 5 being much simpler in terms of operation and manufacturing was adopted when its patent expired in 1794. This adaption was for the remainder of the Boulton-Watt steam engine production life cycle. In addition to be more complicated in terms of operation and manufacturing, there are several design deficiencies of the Watt patented sun-planet mechanism that contributed to its abandonment. Firstly, the power being delivered was a vertical reciprocal force via the rocking beam 4. This vertical reciprocal force must be constantly cohered in an orbital motion via the tie bar 13a. The planet gear 10 tendency is to travel in a straight line, so therefore, any opportunity it has, such as the wearing down of the tie bar bushings, 13b & 13c, SEE FIGS. 3C, will result in the tangential contact 20 point between the planet gear 10 and sun gear 11 to be less optimal causing a deficiency of force transfer, SEE FIG. 4G. A similar situation occurs because of the absent of a fulcrum structure 21 at the front of the tie bar planet gear pin 13b, SEE FIG. 4F & FIG. 4G. Secondly, with the absence of a fulcrum structure at position 22 at the front of the output shaft 12, SEE FIG. 4F, force delivered by beam causes distortion in the rotation of the sun gear 11, further contributing to the tangential contact point 20 deficiencies, SEE FIG. 4G. Thirdly, there are two instances where there is loss of force transfer between the planet gear 10 and sun gear 11. They occur at TDC and BDC. Here, in both contact points, only a vertical force 23 is experienced, SEE FIG. 4H (only TDC 16 is shown), and the inertia of the flywheel 9b is necessary to nudge the sun gear 11 in the direction of rotation in order for it to be again experiencing tangential contact 20 with the planet gear 10, SEE FIG. 4G. As can be ascertained, a flywheel 9b is critical for the operation of the Watt patented sun-planet mechanism, FIG. 3A. This also applies the James Pickard’s Newcomen steam engine crank mechanism, FIG. 2A, 9a. The deficiencies detailed above have been thoroughly considered in the development of the present embodiments of the invention. These deficiencies will be rectified by innovative features and these innovations will be successfully integrated into the embodiments of the invention. The embodiments of the invention will be based on: • The rotationally constrained planetary gear of the Watt patented sun-planet kinematic arrangement, FIG. 4A. • Chain-sprocket mechanism, aka Endless Power-Transmitting Chain Drive (EPTCD)68-1, SEE FIG. 9 (a). • A modified versions of the EPTCD 68-1 that integrate a planetary gear carrier 96 into the driven sprocket 67b will also be incorporated. These modified versions will be referred to as Endless Power-Transmitting Planetary Gear Drives (EPTPGD) 68-2, SEE FIGS. 9 (b), (c) & (d). SUMMARY of the INVENTION The convergence of: • The rotationally constrained planetary gear of the Watt patented sun-planet kinematic arrangement, FIG. 4A, • Endless Power-Transmitting Chains Drives (EPTCD), FIG.9 (a), and • Endless Power-Transmitting Planetary Gear Drive (EPTPGD), FIG. 9 (b), (c) & (d), will fuse in a manner to create the embodiment of a mechanical power transmission design that is engineered to simultaneously attain a speed transfer ratio of 1:2 and an efficient torque transfer ratio of 1:1. This integrated innovation will be referred to as an Endless Power-Transmitting Planetary Gear Drive Transmission (ARC- EPTPGDT I (68-2T[A]), SEE FIGS. 10A, 10B, 10C, & 10D. This first embodiment ARC-EPTPGDT I(68-2T[A]), will serve as the foundation for additional embodiments: ARC-EPTPGDT II (68-2T[B]) & ARC-EPTPGDT III (68-2T[C]). These additional embodiments while sharing core features with the first embodiment, offer distinct enhancements, tailored to broaden the utility and applicability of the invention to various scenarios. Systems incorporating multiple transmission devices have been developed to enhance mechanical efficiency and kinetic energy transfer. In one such configuration, two or more EPTPGDT units connected in series, where each transmission device is equipped with a clutch box at its input shaft, will be referred to as ARC-Kinetic Energy Multi Endless Drives En Serie I, (ARC-KEMEDES I (68-3)). The clutch box is configured to engage only after a preceding device achieves a predetermined rotational speed (RPM), thereby enabling sequential activation and optimized speed transfer. Additionally, if a compound gear multiplier is coupled to the output of an ARC-KEMEDES I (68-3) system, the resulting system will be referred to as ARC-KEMEDES II (68-4). The compound gear multiplier is configured to deliver a predetermined rotational speed (RPM) output to a driven device that operate at a fixed speed. In accordance with a first aspect of the embodiments of the present disclosure, a transmission device (which is the Endless Power-Transmitting Planetary Gear Drive Transmission (ARC- EPTPGDT I)) is provided, which includes: at least one input shaft (in the first embodiment, which is the secondary input shaft, and in the second embodiment, which is the primary input shaft); at least one output shaft (in the first embodiment, which is the secondary output shaft, and in the second embodiment, which is the primary output shaft.); at least one Power Transmission Assembly (which may be the Endless Power- Transmitting Chains Drives (EPTCD) or a gear train with an idler gear), each Power Transmission Assembly including: a power transmission driver gear rigidly attached to the input shaft; a power transmission driven gear having the same diameter and number of teeth as the power transmission driver gear, and a power transmission connection mechanism for connecting the power transmission driver gear and the power transmission driven gear; and at least one Power output Transmission Assembly (which is the Endless Power-Transmitting Planetary Gear Drive (EPTPGD)), each Power Output Transmission Assembly including: a planetary gear; a sun gear rigidly attached to the output shaft, the sun gear having the same diameter and number of teeth as the planetary gear and meshing with the planetary gear, where the planetary gear does not rotate around its own center, but orbits around the sun gear; and a planetary gear carrier for accommodating the sun gear and the planetary gear, where the driven gear of the Power Output Transmission Assembly is securely bolted to the planetary gear carrier and drives the planetary gear to move around the sun gear for orbital motion through the planetary gear carrier. In the embodiments, the transmission device further includes: a plurality of internal support structures, where the input shaft and the output shaft penetrate corresponding internal support structures and are supported by the corresponding internal support structures through corresponding support bearings for rotation; each Power Output Transmission Assembly further including: a planetary gear carrier hub securely bolted to corresponding internal support structures; where, the planetary gear carrier is installed in a corresponding internal support structure through a front first bearing mounted on a surface of the planetary gear carrier, and also installed on the planetary gear carrier hub through a rear second bearing mounted on the surface of the planetary gear carrier hub, and is supported by the front first bearing and the rear second bearing for rotation. In the first embodiment, there are two secondary input shafts, four secondary output shafts, four Power Transmission Assemblies and four Power Output Transmission Assemblies; and the two secondary input shafts, the four Power Transmission Assemblies, the four Power Output Transmission Assemblies and the four secondary output shafts form two groups of coaxial structures. In the first embodiment, the transmission device further includes a connecting bar and two connecting bar pins, where the two connecting bar pins are rigidly attached to two end portions of the connecting bar and intersect with the two end portions of the connecting bar at right angles respectively; each connecting bar pin is pivotally connected to planetary gear carriers of two coaxial Power Output Transmission Assemblies; planetary gears of two coaxial Power Output Transmission Assemblies are rigidly attached to two end portions of a corresponding connecting bar pin; a length of the connecting bar is such that two groups of coaxial planetary gear carriers of the Power Output Transmission Assemblies rotate synchronously and in alignment with each other; a plurality of bearings for supporting pivotal movement of the connecting bar are respectively installed in front of and behind the planetary gear of each Power Output Transmission Assembly, and accommodated in the planetary gear carrier of each Power Output Transmission Assembly. In the first embodiment, the transmission device further includes: a main input shaft; a main output shaft, where the main input shaft and the main output shaft penetrate corresponding internal support structures and are supported by the corresponding internal support structures through corresponding support bearings for rotation; two Power Input Assemblies which may be the Endless Power-Transmitting Chains Drives (EPTCD) or a gear train with an idler gear, corresponding to the two secondary input shafts one by one, each Power Input Assembly including: a power input driver gear rigidly attached to the main input shaft; a power input driven gear having the same diameter and number of teeth as the power input driver gear and rigidly attached to a corresponding secondary input shaft; and a power input connection mechanism for connecting the power input driver gear and the power input driven gear; and four Power Output Assemblies which may be the Endless Power- Transmitting Chains Drives (EPTCD) or a gear train with an idler gear, corresponding to the four secondary output shafts one by one, each Power Output Assembly including: a power output driver gear rigidly attached to a corresponding secondary output shaft; a power output driven gear having the same diameter and number of teeth as the power output driver gear and rigidly attached to the main output shaft; and a power output connection mechanism for connecting the power output driver gear and the power output driven gear. In the first embodiment, the plurality of internal support structures include a first support structure, a second support structure, a third support structure, a fourth support structure, a fifth support structure, a sixth support structure and a seventh support structure, where, the main input shaft is arranged between the first support structure and the second support structure; the main output shaft is arranged between the second support structure and the seventh support structure; the planetary gear carrier hubs of the four Power Output Transmission Assemblies are respectively and securely bolted to the third support structure and the sixth support structure; the planetary gear carriers of the four Power Output Transmission Assemblies are respectively arranged in the fourth support structure and the fifth support structure through a respective front first bearing; the two secondary input shafts are arranged between the first support structure and the sixth support structure; the four secondary output shafts are respectively arranged between the second support structure and the fourth support structure, and the fifth support structure and the seventh support structure. In the second embodiment, the plurality of internal support structures include a first support structure, a second support structure and a third support structure; there are one input shaft, one output shaft, one Power Transmission Assembly and one Power Output Transmission Assembly; the planetary gear carrier hub is securely bolted to the third support structure, the input shaft is arranged between the first support structure and the second support structure, and the output shaft is arranged between the second support structure and the third support structure. In the second embodiment, the transmission device further includes: a follower shaft arranged between the first support structure and the third support structure; three planetary gear carrier followers; two Power Input Assemblies (which may be the Endless Power-Transmitting Chains Drives (EPTCD) or a gear train with an idler gear, each Power Input Assembly including: a power input driver gear rigidly attached to the input shaft; a power input driven gear having the same diameter and number of teeth as the power input driver gear and rigidly attached to the follower shaft; and a power input connection mechanism for connecting the power input driver gear and the power input driven gear; three Power Follower Assemblies (which may be the Endless Power Transmitting Chains Drives (EPTCD) or a gear train with an idler gear, corresponding to the three planetary gear carrier followers one by one, and each Power Follower Assembly including: a power follower driver gear; a power follower driven gear having the same diameter and number of teeth as the power follower driver gear and rigidly attached to a corresponding planetary gear carrier follower; and a power follower connection mechanism for connecting the power follower driver gear and the power follower driven gear; where the power follower driver gears of two of the Power Follower Assemblies are rigidly attached to the follower shaft, and the power follower driver gear of another power follower assembly is rigidly attached to the input shaft; a connecting bar and two connecting bar pins, where the two connecting bar pins are rigidly attached to two end portions of the connecting bar and respectively intersect with the two end portions of the connecting bar at right angles; one of the two connecting bar pins is pivotally connected to the planetary gear carrier and one of the three planetary gear carrier followers; another one of the two connecting bar pins is pivotally connected to the other two of the three planetary gear carrier followers; a plurality of bearings for supporting pivotal movement of the connecting bar are mounted on the two connecting bar pins; and three planetary gear carrier follower hubs corresponding to the three planetary gear carrier followers one by one, where each planetary gear carrier follower hub is securely bolted to the first support structure and the third support structure; where the planetary gear is rigidly attached to one end portion of one of the two connecting bar pins, and the three planetary gear carrier followers are respectively attached to the other end portions of the two connecting bar pins, and the three planetary gear carrier followers are respectively attached to the other end portions of the two connecting bar pins; each planetary gear carrier follower is installed on a corresponding planetary gear carrier follower hub through a respective rear second bearing mounted on a surface of the corresponding planetary gear carrier follower hub, and is supported by the respective rear second bearing for rotation; and a length of the connecting bar is such that the three planetary gear carrier followers rotate synchronously and in alignment with the planetary gear carrier. In the embodiments of the present disclosure, the power transmission connection mechanism, and / or the power input connection mechanism, and / or the power output connection mechanism, and / or the power follower connection mechanism are chains or idle gears; when any one of the power transmission connection mechanism, and / or the power input connection mechanism, and / or the power output connection mechanism, and / or the power follower connection mechanism is a chain, the driver gear and the driven gear are linked with the chain; and when any one of the power transmission connection mechanism, and / or the power input connection mechanism, and / or the power output connection mechanism, and / or the power follower connection mechanism is an idle gear, the idle gear is located between the driver gear and the driven gear and meshes with the driver gear and the driven gear. In the embodiments of the present disclosure, the transmission device exhibits a speed transfer ratio of 1:2. This ratio results from the meshed engagement between the sun gear and the rotationally constrained planetary gear which is rigidly attached to a connecting bar and pivotally connected to its respective rotating planetary gear carrier. The connecting bar is configured to guide the planetary gear along an orbital path while preventing rotation about its own axis. This kinematic arrangement causes the sun gear and output shaft assembly to complete two full revolutions for every single orbital revolution of the rotationally constrained planetary gear. In the embodiments of the present disclosure, the transmission device exhibits a torque transfer ratio of 1:1. This ratio results from: • A mechanical advantage (MA) not found in conventional planetary gear systems. This MA is defined as the center- to-center (c-t-c) distance from the sun gear to the periphery of the planetary gear carrier, divided by the c- t-c distance between the sun gear and the rotationally constrained planetary gear. • The force applied to the rotationally constrained planetary gear is multiplied by this MA and is transmitted to the sun gear and output shaft assembly along the entire c-t-c distance of the meshed engagement between the rotationally constrained planetary gear and the sun gear and output shaft assembly. This distance acts as an effective lever arm that results in a torque transfer ratio of 1:1. In accordance with a second aspect of the embodiments of the present disclosure, a transmission system (herein referred to as ARC-KEMEDES I, 68-3) is provided, which includes at least two or more transmission device, where each transmission device is equipped with a clutch box coupled to its input shaft. The clutch box is configured to engage only after a preceding device achieves a predetermined rotational speed (RPM), thereby enabling sequential activation and optimized speed transfer. In accordance with a third aspect of the embodiments of the present disclosure, a multiplier transmission system (herein referred to as ARC-KEMEDES II, 68-4) is provided, which includes (a) the transmission system of ARC-KEMEDES I, and (b) a compound gear multiplier connected to the output of the ARC-KEMEDES I transmission system. The compound gear multiplier is configured to deliver a predetermined rotational speed (RPM) output to a driven device designed for fixed-speed operation. BRIEF DESCRIPTION OF DRAWINGS - FIGURES FIG. 1A. A side view of a typical steam engine with the fire side on the left and the pump side on the right. These typical steam engines were primarily used to pump water out of flooded coal mines. FIG. 1B. An isometric view of FIG. 1A. FIG. 2A. A side view of a steam engine with a crank mechanism that convert the rocking mechanism of the overhead beam to rotative power. This crank mechanism was incorporated in a typical Newcomen steam engine and patented by James Pickard. FIG. 2B. An isometric view of FIG. 2A. FIG. 3A. A James Watt design steam engine with his version of converting the rocking beam into rotary motion, the sun-planet gear mechanism on the right. This sun-planet mechanism was in order to circumvent James Pickard patented crank mechanism of FIG. 2A & 2B. FIG. 3B. An isometric view of FIG. 3A. FIG. 3C. A front view of FIG. 3A depicting the sun-planet gear mechanism connected to a flywheel. FIG.4A. A close-up view of the sun-planet mechanism of FIG. 3A at TDC (top dead center). Rotation is clockwise, 14 & 15. FIG. 4B. A close-up view of the sun-planet mechanism. The planet gear is in its 1st quarter orbit of orbital travel around the sun gear. The sun gear has rotated 180 degrees. Tangential contact point is 20. FIG. 4C. A close-up view of the sun-planet mechanism. The planet gear is in its 2nd quarter orbit of orbital travel around the sun gear, BDC 18 (bottom dead center). The sun gear has rotated 360 degrees, (1 revolution). FIG. 4D. A close-up view of the sun & planet mechanism. The planet gear is in its 3rd quarter orbit of orbital travel around the sun gear. The sun gear has rotated another 180 degrees. FIG. 4E. A close-up view of the sun-planet mechanism. The planet gear is in its 4th quarter orbit of orbital travel around the sun gear. Its back at TDC 16 (top dead center). The sun gear has rotated another 360 degrees, for a total of 2 revolutions, for every 1 orbital revolution of the planet gear. FIG. 4F. A front view depicting the sun-planet mechanism. 21 & 22 depicts the sun gear and planet gears has no frontal support to act as a fulcrum. FIG. 4G. An isometric view of the sun-planet mechanism 171st quarter orbit tangential contact point 20. This is also similar to 3rd quarter orbit contact point. FIG. 4H. An isometric view of the sun-planet 16 TDC contact point 23. " FIGS. 5-8 and pages 9-16, which contain the figures, are intentionally omitted from this international filing." FIG. 9. A front view (a) of an Endless Power-transmitting Chain Drive 68-1, and isometric views (b), (c) & (d) of an Endless Power-Transmitting Planetary Gear Drive 68-2. FIG. 10A. A rear isometric view of an Endless Power-Transmitting Planetary Gear Drive Transmission 68-2T [A] with sides, top & bottom external structures hidden from view for illustrative clarity. FIG. 10B. A rear isometric view of an Endless Power-Transmitting Planetary Gear Drive Transmission 68-2T [A] with the external & internal support structures hidden from view for illustrative clarity. FIG. 10C. A right-side view of an Endless Power-Transmitting Planetary Gear Drive Transmission 68-2T [A] with the external support structures hidden. FIG. 10D. A top view of an Endless Power-Transmitting Planetary Gear Drive 68-2T [A] with the external support structures hidden from view. FIG. 11A. A rear isometric view of the internal support structures 69-75. All other parts are hidden from view for illustrative clarity. FIG. 11B. A left-side view of the internal support structures 69-75. All other parts are hidden from view for illustrative clarity. FIG. 11C. A right-side view of the internal support structures 69-75. All other parts are hidden from view for illustrative clarity. FIG. 11D. A top view of the internal support structures 69-75. All other parts are hidden from view for illustrative clarity. FIG. 11E. A bottom view of the internal support structures 69- 75. All other parts are hidden from view for illustrative clarity. FIG. 11F. A rear view of internal support structure 69. FIG. 11G. A front view of internal support structure 75. FIG. 12A. A rear isometric view of internal support structures 69-75 with bearings that provide rotational support and function as fulcrum points disposed in machined openings. All other parts are hidden from view for illustrative clarity. FIG. 12B. A rear isometric view of the position of all the bearings that provide rotational support and function as fulcrum points. External & internal support structures and other parts are hidden from view for illustrative clarity. FIG. 12C. A rear isometric view of the position of all the planetary gear carrier bearings that provide rotational support and function as fulcrum points. All other parts are hidden from view for illustrative clarity. FIG. 13A. A rear isometric view of the position of the primary 83 and 2 secondary 84 input shafts with their respective bearings that provide rotational support and function as fulcrum points. All other parts are hidden from view for illustrative clarity. FIG. 13B. A right-side view of the primary 83 and 2 secondary 84 input shafts deposed within the internal structures. All other parts are hidden from view. FIG. 13C. A top view of the primary 83 and 2 secondary input shafts 84 deposed within the internal structures 69-75. All other parts are hidden from view. FIG. 13D. A rear isometric view of the primary 83 and 2 secondary 84input shafts with their respective Endless Power- Transmitting Chain Drives 68-1. All other parts are hidden from view for illustrative clarity. FIG. 13E. A Right-side view of the primary 83 & 2 secondary 84 input shafts with their respective Endless Power-Transmitting Chain Drives 68-1 deposed within the internal support structures 69-75. All other parts are hidden from view. FIG. 13F. A bottom view of the primary input shaft 83 and 2 secondary 84 input shafts with their respective Endless Power- Transmitting Chain Drives 68-1 deposed within the internal support structures. All other parts are hidden from view. FIG. 14A. A rear isometric view of the position of the primary 85 and 4 secondary 86 output shafts with their respective bearings that provide rotational support and function as fulcrum points. Only internal structure 75 is depicted. All other parts are hidden from view. FIG. 14B. A right-side view of the primary 85 and 4 secondary 86 output shafts deposed within the internal support structures 69- 75. All other parts are hidden from view for illustrative clarity. FIG, 14C. A top view of the primary 85 and 4 secondary output shafts 86 deposed within the internal support structures 69-75. All other parts are hidden from view for illustrative clarity. FIG. 14D. A rear isometric view of the primary output shaft 85 connected to the 4 secondary output shafts 86 via their respective Endless Power-Transmitting Chain Drives 68-1. All other parts are hidden from view for illustrative clarity. FIG. 14E. A right-side view of the primary output shaft 85 connected to each of the 4 secondary output shafts 86 via their respective Endless Power-Transmitting Chain Drives 68-1 deposed within the internal support structures 69-75. All other parts are hidden from view for illustrative clarity. FIG. 14F. A top view of the primary output shaft 85 connected to each of the 4 secondary output shafts 86 via their respective Endless Power-Transmitting Chain Drives 68-1 deposed within the internal support structures 69-75. All other parts are hidden from view for illustrative clarity. FIG. 15. A right-side view. A combination of FIG. 13B & FIG. 14B. This is a depiction of the power-transmitting flow dynamics of The Endless Power-Transmitting Planetary Gear Drive Transmission 68-2T [A]. All other parts are hidden from view for illustrative clarity. FIG. 16A. A rear isometric view of the Input Power-Transmitting Transfer Chambers 88. All other parts are hidden from view for illustrative clarity. FIG. 16B. A right-side view of the Input Power-Transmitting Transfer Chambers 88. All other parts are hidden from view for illustrative clarity. FIG. 16C. A top view of the Input Power-Transmitting Transfer Chambers 88. All other parts are hidden from view for illustrative clarity. FIG. 17A. A rear isometric view of the Output Power-Transmitting Conversion Chambers 89. All other parts are hidden from view. FIG. 17B. A right-side view of the Output Power-Transmitting Conversion Chambers 89. All other parts are hidden from view for illustrative clarity. FIG. 17C. A bottom view of the output Power-Transmitting Conversion Chambers 89 (RIGHT-REAR, LEFT-REAR, RIGHT-FRONT and LEFT-FRONT) deposed within the internal structures 69-75. All other parts are hidden from view. FIG. 18. A rear isometric view of the Output Power-Transmitting Conversion Chambers 89 depicting the RIGHT-FRONT and LEFT-FRONT Endless Power-Transmitting Chain Drives positioned in relation to the 4 secondary output shafts 86 and the 2 secondary input shafts 84. Also depicted are the 4 secondary output shafts 86 planetary gear carrier bearings 78-1, 78-2, 78-3 & 78-4. The RIGHT-REAR and LEFT-REAR Endless Power-Transmitting Chain Drives are hidden from view for illustrative clarity. FIG. 19. A rear isometric view of the Output Power-transmitting Conversion Chambers 89 depicting the RIGHT-FRONT 92-3 and LEFT- FRONT 92-4 planetary gear carrier hubs and various parts. The RIGHT-REAR 92-1 and LEFT-REAR 92-2 planetary gear carrier hubs are hidden from view for illustrative clarity as are the other parts. FIG.20. A right-side view of the Output Power-Transmitting Conversion Chambers 89 depicting the RIGHT-REAR 92-1 and RIGHT- FRONT 92-3 planetary gear carrier hubs and various parts. All other parts are hidden from view for illustrative clarity. FIG. 21. A bottom view of the Output Power-Transmitting Conversion Chambers 89 depicting the planetary gear carrier hubs 92-1, 92-2, 92-3 & 92-4 and various parts. All other parts are hidden from view for illustrative clarity. FIG. 22. A rear isometric view of the output Power-transmitting Conversion Chambers 89 depicting the sun gears 93-1, 93-2, 93-3 & 93-4 and various parts. All other parts are hidden from view for illustrative clarity. FIG. 23. A bottom view of the Output Power-Transmitting Conversion Chambers 89 depicting the sun gears 93-1, 93-2, 93-3 & 93-4 and various parts. All other parts are hidden from view for illustrative clarity. FIG. 24. A rear isometric view of the Output Power-Transmitting Conversion Chambers 89 depicting the planetary gears 94-1, 94-2, 94-3 & 94-4 and various parts. All other parts are hidden from view for illustrative clarity. FIG. 25. A bottom view of the Output Power-Transmitting Conversion Chambers 89 depicting the planetary gears 94-1, 94-2, 94-3 & 94-4 and various parts. All other parts are hidden from view for illustrative clarity. FIG. 26. A rear isometric View of the Output Power-Transmitting Conversion Chambers 89 depicting the pins 95-1 & 95-2 of connecting bar 97 and various parts. All other parts are hidden from view for illustrative clarity. FIG. 27. A bottom view of the Output Power-Transmitting Conversion Chambers 89 depicting the connecting bar 97 and various parts. All other parts are hidden from view for illustrative clarity. FIG. 28. A rear isometric view of the Output Power-Transmitting Conversion Chambers 89. Depicting the connecting bar 97 and various parts. All other parts are hidden from view for illustrative clarity. FIG. 29. A Bottom view of the Output Power-Transmitting Conversion Chambers 89, depicting the connecting bar 97 and various parts. All other parts are hidden from view for illustrative clarity. FIG. 30. A rear isometric view of the Output Power-Transmitting Conversion Chambers 89 depicting the bearings 79 & 80 for the pins 95 of connecting bar 97 and various parts. All other parts, including the connecting bar 97, are hidden from view for illustrative clarity. FIG. 31. A bottom view of the Output Power-Transmitting Conversion Chambers 89 depicting the bearings 79 & 80 for the pins 95 of connecting bar 97 and various parts. All other parts are hidden from view for illustrative clarity. FIG. 32. A rear isometric view of the Output Power-Transmitting Conversion Chambers 89 depicting the planetary gear carriers 96- 4 & 96-1. Planetary gear carriers 96-2 & 96-3 are hidden from view for illustrative clarity as are other parts. FIG. 33. A top view of the Output Power-Transmitting Conversion Chambers 89 depicting the planetary gear carriers 96-2 & 96-3. Planetary gear carrier 96-1 & 96-4 are hidden from view for illustrative clarity as are other parts. FIG. 34. A rear isometric view of the Output Power-Transmitting Conversion Chambers 89 depicting planetary gear carrier 2ndbearings 82-1, 82-2 & 82-3 and planetary gear carrier 1stbearing 81-4 plus various parts. All other parts are hidden from view for illustrative clarity. FIG. 35. A bottom view of the Output Power-Transmitting Conversion Chambers 89 depicting planetary gear carriers LEFT- REAR 96-2 and RIGHT-FRONT 96-3 plus planetary gear carrier 2ndbearings 82-4 & 82-1 and various parts. All other parts are hidden from view for illustrative clarity. FIG. 36. A rear isometric view of LEFT-FRONT planetary gear carrier 96-4, LEFT FRONT 1stbearing 81-4 deposed in internal structure 73 plus various parts. All other parts are hidden from view for illustrative clarity. FIG. 37. Detail A. A rear isometric view of the Output Power- Transmitting Conversion Chambers 89 depicting a driven sprocket 67b securely bolted to the RIGHT-REAR planetary gear carrier 96- 1. All other parts are hidden from view for illustrative clarity. FIG. 38. A rear isometric view of the Output Power-Transmitting Conversion Chambers 89 depicting additional LEFT-REAR Endless Power-Transmitting Planetary Gear Drive 682 / 2 and LEFT-REAR planetary gear carrier hub 92-2, RIGHT-REAR planetary gear carrier hub 92-1 and RIGHT-FRONT planetary gear carrier 1stbearing 81-3 plus various parts. All other parts are hidden from view for illustrative clarity. FIG.39. A rear isometric view of the Output Power-Transmitting Conversion Chambers 89 depicting additional LEFT-REAR planetary gear carrier 1stbearing 81-2, RIGHT-FRONT planetary gear carrier 96-3 and RIGHT-FRONT Endless Power-Transmitting Planetary Gear Drive 68-2 / 3 plus various parts. All other parts are hidden from view for illustrative clarity. FIG. 40. A rear isometric view of the Output Power-Transmitting Conversion Chambers 89 depicting additional RIGHT-REAR Endless Power-Transmitting Planetary Gear Drive 682 / 1 and RIGHT-REAR planetary gear carrier 1st bearing 82-1. All other parts are hidden from view for illustrative clarity. FIG. 41. A rear isometric view depicting the Input Power- Transmitting Chambers 87, Input Power-Transmitting Transfer Chambers 88 and the Output Power-transmitting Conversion Chambers 89. Also, primary output shaft 85. All other parts are hidden from view for illustrative clarity. FIG. 42. A rear isometric view depicting the Output Power- Transmitting Chambers #1 (91) and #2 (90). All other parts are hidden from view for illustrative clarity. FIG. 43. This is how the embodiment of the invention achieves a speed ratio of 1:2. It presents a front view of the RIGHT-FRONT and LEFT-FRONT upper Input Power-Transmitting Transfer Chambers Conversion Chambers 88 and lower Output Power-Transmitting 89. The components depicted are integral in the engineered design, as illustrated in Detail A, to achieve the specified speed ratio. All other parts are hidden from view for illustrative clarity. FIG. 44. In this depiction, a front view, the power-transmitting flow dynamic at Transfer Chambers 88 (top) and Output Power- Transmitting Conversion Chambers 89 (bottom). A 100 Nm input – F 100Nm output. All other parts are hidden from view for illustrative clarity. " FIGS. 45-48 and pages 48-51, which contain the figures, are intentionally omitted from this international filing." Fig. 49. Second embodiment of the invention, ARC-EPTPGDT II, (68-2T [B]). This second embodiment of the invention contains only a single main input shaft 83, a single main output shaft 85 (there are no secondary shafts), a follower shaft 123 and only three internal structures 118, 119 & 120. The sides, top & bottom structures as are all other parts are hidden from view for illustrative clarity. FIG. 50. A rear isometric view of an Endless Power-Transmitting Planetary gear Drive Transmission (ARC-EPTGDT II) (68-2T [B]). Front structure 118 and other parts are hidden from view for illustrative clarity. FIG. 51. A rear isometric view of an ARC-EPTGDT II (68-2T [B]). All internal structures and other parts have been hidden for illustrative clarity. Output shaft 85 is now visible. FIG. 52. A right-side view of an ARC-EPTGDT II (68-2T [B]). Some parts are not referred to, for illustrative clarity. FIG. 53. A top view of an ARC-EPTGDT II (68-2T [B]). All other parts are hidden from view for illustrative clarity. FIG. 54. A rear isometric view of an ARC-EPTPGDT II (68-2T [B]). Depicted are 1] the Input Power-Transmitting Transfer Chambers 88 with its single main input shaft 83 and 2] the Output Power- transmitting Conversion Chamber 89 with its single main output shaft 85 housed in a planetary gear carrier hub 92 and its respective sun gear 93 and shaft bearing 78. All other parts are hidden from view for illustrative clarity. FIG.55. A rear isometric view depicting additional parts such as connecting bar pin 95-1 with its rigidly attached planet gear 94 that is meshed with sun gear 93. Also depicted are all the respective support for pivoting bearings 79 & 80. Internal support structure 120 is all also depicted, but all other parts are hidden from view for illustrative clarity. FIG. 56. A rear isometric view depicting the planetary gear carrier 96 with the driven sprocket of 68-2 / 3 securely bolted to carrier 96-3. Some parts are not referred to and all other parts are hidden from view for illustrative clarity. FIG. 57. A rear isometric view depicting the connecting bar 97 with its left-side pin 95-2 and the pin’s respective support for pivoting bearings 79-2 & 79-4. Some parts are not referred to and all other parts are hidden from view for illustrative clarity. FIG. 58. A rear isometric view depicting the planetary gear carrier followers 121-1, 121-2 & 121-3 deposed on the end portions of their respective connecting bar pins 95-1 & 95-2. These parts are located in the Output Power-Transmitting Conversion Chambers 89. All other parts are hidden from view for illustrative clarity. FIG. 59. A rear isometric view: 1] Detail A depicts LEFT-FRONT planetary gear carrier follower hub 122-3 with bearing 82-4 & 78-4 that provide rotational support and function as fulcrum points and connecting bar pin 95-2. 2] Detail B depicts the RIGHT-REAR planetary gear carrier follower 121-1, bearing 82-1 that provide rotational support and function as a fulcrum point. Some parts are not referred to and all other parts are hidden from view for illustrative clarity. FIG. 60. A top view depicting 1st(118) & 3rd(120) internal support structures, input shaft 83 & output shaft 85. In this depiction, the single RIGHT-FRONT planetary gear carrier hub 82- 3 with its planetary gear carrier 96-3 (which is a part of an Endless Power Transmitting Planetary Gear Drive 68-2 / 3) and is securely bolted to 3rd(120) structure as is LEFT-FRONT planetary gear carrier follower hub 122-3 with its respective planetary gear carrier follower 121-3. Securely bolted to 1st(118) structure are RIGHT-REAR and LEFT REAR planetary gear carrier follower hubs 122-1 & 122-2 with their respective planetary gear carrier followers 121-1 & 121-2. Some parts are not referred to and all other parts are hidden for illustrative clarity. FIG. 61. A rear isometric view depicting the complete complement of Endless Power Transmitting Chain Drives 68-1 / 1, 68-1 / 2, 68- 1 / 3, 68-1 / 4 & 68-1 / 5. Also included is the single RIGHT-FRONT Endless Power-Transmitting Gear Drive 68-2 / 3 and 1stbearing 81-3 that provide rotational support and function as a fulcrum point. Some parts are not referred to and all other parts are hidden from view for illustrative clarity. FIG. 62. A top view depicting the complete complement of Endless Power-Transmitting Chain Drives 68-1 / 1, 68-1 / 2, 68-1 / 3, 68-1 / 4 & 68-1 / 5. Also included is the single Endless Power-Transmitting Planetary Gear Drive 68-2 / 3 and 1stbearing 81-3 that provide rotational support and function as fulcrum points. Main Input Shaft 83 and Main Output Shaft 85 are on different plains. Some parts are not referred to and all other parts are hidden from view for illustrative clarity. BRIEF DESCRIPTION OF DRAWINGS – REFERENCE NUMERALS XX = Reference Number underlined indicate: (a) a process, e.g., clockwise rotation 14, (b) the name of a location within the FIGS., e.g., conversion chamber 89, XX = Reference Number not underlined indicate a part reference number. 1 - Main structure of a steam engine utilized to pump water out of flooded coal mines. 2 - Broiler of a steam engine. 3 - Piston & connecting rod of a steam engine. 4 - Main rocking beam of a steam engine. 5 - Connecting rod to water pump piston of a steam engine. 6 - Water pump of a steam engine with piping down to the flooded mines. 7 - Crankshaft of a Newcomen steam engine. 8 - Flywheel shaft of a Newcomen steam engine. 9a - Flywheel of a Newcomen steam engine. 9b - Flywheel of a Watt steam engine. 10 - Planet gear of a Watt steam engine. 11 - Sun gear of a Watt steam engine. 12 - Sun gear shaft to flywheel of a Watt steam engine. 13a - Tie bar of a Watt steam engine. 13b - Tie bar & planet gear shaft pin bushing of a Watt steam engine. 13c - Sun gear & flywheel shaft bushing of a Watt steam engine. 14 - Clockwise rotation of the planet gear of a Watt steam engine. 15 - Clockwise rotation of the sun gear of a Watt steam engine. 16 - TDC (Top Dead Center) of the sun & planet gearing of a Watt steam engine. 17 - 1st quarter of the orbital rotation of the planet gear around the sun gear. 18 - BDC (Bottom Dead Center) of the sun & planet gearing of a Watt steam engine. 19 - 3rd quarter of the orbital rotation of the planet gear around the sun gear of a Watt steam engine. 20 - Tangential contact point of a sun & planet gearing. pin. 22 - No frontal fulcrum point for sun gear shaft. 23 - Vertical force at TDC (Top Dead Center). " Reference Numerals 24-65 are intentionally omitted from this international filing." 66 - Chain. 67a - Driver sprocket. 67b - Driven sprocket. 68-1 - Endless Power-Transmitting Chain Drive (EPTCD). Nos. 68- 1 / 1, 68-1 / 2, 68-1 / 3, 681 / 4, 68-1 / 5 & 68-1 / 6. 68-2 - Endless Power-Transmitting Planetary Gear Drive (EPTPGD), Nos.68-2 / 1, 68-2 / 2, 682 / 3 & 68-2 / 4. 68-2T[A] - ARC-EPTPGDT First embodiment of the invention, Endless Power-Transmitting Planetary Gear Drive Transmission referred to as ARC-EPTPGDT I. 68-2T[B] - ARC-EPTPGDT Second embodiment of the invention, Endless Power Transmitting Planetary Gear Drive Transmission referred to as ARC-EPTPGDT II. 68-2T[C] - ARC-EPTPGDT Third embodiment of the invention, referred to as ARC EPTPGDT III. 68-3 - ARC-KEMEDES I. A multi-stage transmission system consisting of two or more various combinations of ARC-EPTPGDT 1, 2 or 3, referred to as ARC-KEMEDES I. 68-4 - ARC-KEMEDES II. The integration of a compound gear multiplier device to an ARC-KEMEDES I system is referred to as ARC-KEMEDES II. 69-75 – 1stto 7thinternal structures. 69-1st, 70-2nd, 71-3rd, 72- 4th, 73-5th, 74-6th, 75-7th. 76-1 - Primary input shaft bearings that provide rotational support and function as fulcrum points (2 total). 76-2 - Primary output shaft bearings that provide rotational support and function as fulcrum points (7 total). 77-1 - Right-side secondary input shaft bearings that provide rotational support and function as fulcrum points (12 total). 77-2 - Left-side secondary input shaft bearings that provide rotational support and function as fulcrum points (12 total). 77-3 - Right-side / RIGHT-REAR secondary output shaft bearings that provide rotational support and function as fulcrum points (4 total). 77-4 - Left-side / LEFT-REAR secondary output shaft bearings that provide rotational support and function as fulcrum points (4 total). 77-5 - Right-side / RIGHT-FRONT secondary output shaft bearings that provide rotational support and function as fulcrum points (4 total). 77-6 - Left-side / LEFT-FRONT secondary output shaft bearings that provide rotational support and function as fulcrum points (4 total). 78-1 - Right-side / RIGHT-REAR bearing that provide rotational support and function as fulcrum point for the secondary output shaft disposed in in its respective planetary gear carrier (1 total). 78-2 - Left-side / LEFT-REAR bearing that provide rotational support and function as a fulcrum point for the secondary output shaft disposed in its respective planetary gear carrier (1 total). 78-3 - Right-side / RIGHT-FRONT bearing that provide rotational support and function as a fulcrum point for the secondary output shaft disposed in its respective planetary gear carrier (1 total). 78-4 - Left-side / LEFT-FRONT bearing that provide rotational support and function as a fulcrum point for the secondary output shaft disposed in its respective planetary gear carrier (1 total). 79-1 - RIGHT-REAR connecting bar pin inner bearing that provide pivoting support and function as a fulcrum point. 79-2 - LEFT-REAR connecting bar pin inner bearing that provide pivoting support and function as a fulcrum point. 79-3 - RIGHT-FRONT connecting bar pin inner bearing that provide pivoting support and function as a fulcrum point. 79-4 - LEFT-FRONT connecting bar pin inner bearing that provide pivoting support and function as a fulcrum point. 80-1 - RIGHT-REAR connecting bar pin outer bearing that provide pivoting support and function as a fulcrum point. 80-2 - LEFT-REAR connecting bar pin outer bearing that provide pivoting support and function as a fulcrum point. 80-3 - RIGHT-FRONT connecting bar pin outer bearing that provide pivoting support and function as a fulcrum point. 80-4 - LEFT-FRONT connecting bar pin outer bearing that provide pivoting support and function as a fulcrum point. 81-1 - RIGHT-REAR 1stplanetary gear carrier bearing that provide rotational support and function as a fulcrum point. 81-2 - LEFT-REAR 1stplanetary gear carrier bearing that provide rotational support and function as a fulcrum point. 81-3 - RIGHT-FRONT 1stplanetary gear carrier bearing that provide rotational support and function as a fulcrum point. 81-4 - LEFT-FRONT 1stplanetary gear carrier bearing that provide rotational support and function as a fulcrum point. 82-1 - RIGHT-REAR 2ndplanetary gear carrier bearing that provide rotational support and function as a fulcrum point. 82-2 - LEFT-REAR 2ndplanetary gear carrier bearing that provide rotational support and function as a fulcrum point. 82-3 - RIGHT-FRONT 2ndplanetary gear carrier bearing that provide rotational support and function as a fulcrum point. 82-4 - LEFT-FRONT 2ndplanetary gear carrier bearing that provide rotational support and function as a fulcrum point. 83 - Primary input shaft. 84-1 - Secondary input shaft right-side. 84-2 - Secondary input shaft left-side. 85 - Primary output shaft. 86-1 - RIGHT-REAR secondary output shaft. 86-2 - LEFT-REAR secondary output shaft. 86-3 - RIGHT-FRONT secondary output shaft. 86-4 - LEFT-FRONT secondary output shaft. 87 - Input Power-Transmitting Chambers. 88 - Input Power-Transmitting Transfer Chambers. 89 - Output Power-Transmitting Conversion Chambers. 90 - Output Power-Transmitting Chamber #2. 91 - Output Power-Transmitting Chamber #1. 92-1 - RIGHT-REAR planetary gear carrier hub. 92-2 - LEFT-REAR planetary gear carrier hub. 92-3 - RIGHT-FRONT planetary gear carrier hub. 92-4 - LEFT-FRONT planetary gear carrier hub. 93-1 - RIGHT-REAR sun gear. 93-2 - LEFT-REAR sun gear. 93-3 - RIGHT-FRONT sun gear. 93-4 - LEFT-FRONT sun gear. 94-1 - RIGHT-REAR planetary gear. 94-2 - LEFT-REAR planetary gear. 94-3 - RIGHT-FRONT planetary gear. 94-4 - LEFT-FRONT planetary gear. 95-1 - Right-side connecting bar pin. 95-2 - Left-side connecting bar pin. 96-1 - RIGHT-REAR planetary gear carrier. 96-2 - LEFT-REAR planetary gear carrier. 96-3 - RIGHT-FRONT planetary gear carrier. 96-4 - LEFT-FRONT planetary gear carrier. 97 - Connecting bar. " Reference Numerals 98-117 are intentionally omitted from this international filing." 118 – 1stinternal structure of an ARC-EPTPGDT II. 119 – 2ndinternal structure of an ARC-EPTPGD II. 120 – 3rdinternal structure of an ARC-EPTPGD II. 121-1 - RIGHT-REAR planetary gear carrier follower. 121-2 - LEFT-REAR planetary gear carrier follower. 121-3 - LEFT-FRONT planetary gear carrier follower. 122-1 - RIGHT-REAR planetary gear carrier follower hub. 122-2 - LEFT-REAR planetary gear carrier follower hub. 122-3 - LEFT-FRONT planetary gear carrier follower hub. 123 - Follower shaft DETAILED DESCRIPTION OF THE INVENTION The preceding Background of the Invention, FIGS.1-4 & 9 (FIGS.5- 8 are intentionally omitted from this international filing), offers a clear and detail insight into the mechanics, kinematics, and established science that inform the assembly and modes of operation of the Endless Power-Transmitting Planetary Gear Drive Transmissions (EPTPGDT). This Detailed Description of the Invention, FIGS. 10–44 (FIGS.45-48 are intentionally omitted from this international filing), will meticulously guide the reader through the intricate part-by-part assembly process, and at pivotal junctures in the assembly process we will pinpoint the architecture that enable the critical technical achievement of a simultaneous speed transfer of 1:2 and a torque transfer ratio of 1:1. Additionally, the depiction of a second embodiment, FIGS.49-62, demonstrates the invention’s design flexibility, offering different assembly methodologies tailored to suit varied applications. An ample amount of support structures that function as fulcrum points for the various mechanisms in the first embodiment of the invention, SEE FIGS. 11A, 11B,11C, 11D, 11E, 11F, & 11G. FIG. 11A is an isometric view of the rear of the embodiment. 1st (rear) structure 69, 2nd structure 70, 3rd structure 71, 4th structure 72, 5th structure 73, 6th structure 74 and 7th (front) structure 75. FIG. 11B is a left-side view, FIG. 11C, a right- side view, FIG. 11D, a top view, FIG. 11E, a bottom view, FIG. 11F, a rear structure view & FIG. 11G, a front structure view. Not shown are 1) The right and left side panels, 2) The bottom panel, and 3) The top panel. Each support structure has its various sizes of machined openings in order to accommodate bearings that support rotation and function as fulcrum points for all the mechanism that constitute the Endless Power-Transmitting Planetary Gear Drive Transmission 68-2T [A], SEE FIGS. 12A,12B & 12C. FIG. 13A is an isometric view rear depicting the primary input shaft 83, and its two secondary right-side 84-1 & left-side 84-2 input shafts. The primary input shaft 83 is disposed between 1st 69 and 2nd 70 structures. The right-side 84-1 & left-side 84-2 secondary input shafts are disposed between 1st (69) thru 6th (74) structures, SEE FIG. 13B. All other parts have been hidden from view for illustrative purposes. FIG. 13B depicts a right-side view. Both right-side 84-1 & left- side 84-2 secondary shafts are on the same plane, so therefore, only the right 84-1 secondary input shaft is in view. All other parts have been hidden from view for illustrative purposes. FIG. 13C depicts a top view showing clearly the right-side 84-1 & left-side 84-2 secondary input shafts and the primary input shaft 83. FIG. 13D is an isometric view, clearly depicting the functionality of the Endless Power Transmitting Chain Drive mechanism, right-side 68-1 / 1 & left-side 68-1 / 2, in distributing power from the primary input shaft 83 to both right-side 84-1 & left-side 84-2 secondary input shafts. The driver 67a and driven 67b sprockets of the mechanism, equal in diameter and tooth configuration, ensure a simultaneous speed transfer ratio of 1:1 and a torque transfer ratio of 1:1. FIG. 13E is a right-side view depicting the right-side 68-1 / 1 & left-side 68-1 / 2 Endless Power-Transmitting Chain Drive disposed between 1st 69 & 2nd 70 structures. FIG. 13F is a bottom view depicting the right-side 68-1 / 1 & left-side 68-1 / 2 Endless Power-Transmitting Chain Drive disposed between 1st 69 & 2nd 70 structures. FIG. 14A an isometric view, FIG. 14B a right-side view & FIG. 14C a top view, are 3 perspectives unveiling the arrangement of four secondary output shafts, 86-1, 86-2, 86-3 & 86-4. These 4 secondary output shafts 86-1, 86-2, 86-3 & 86-4 are arranged in pairs: the LEFT-REAR 86-2 and the LEFT-FRONT 86-4. This pair 86- 2 & 86-4 are co-axial, as are their right-side parallel counterparts RIGHT-REAR 86-1 & RIGHT FRONT 86-3. These secondary output shafts, 86-1,86-2,86-3 & 86-4 are disposed between 2nd (70) & 4th (72) structures and 5th (73) & 7th (75) structures, SEE FIGS. 14B & 14C. These 4 secondary shafts, 86-1,86-2,86-3 & 86-4, seamlessly channel power to the primary output shaft 85, deposed between 2nd 70 thru 7th 75 structures, via each respective secondary output shaft Endless Power-Transmitting Chain Drives 68-1 / 3, 68-1 / 4, 68-1 / 5 & 68-1 / 6, SEE FIGS. 14(D),14(E), 14(F). As depicted in previous illustrations, FIGS.12(A) & 12(B), these shafts are supported for rotation and as fulcrum points by bearings 76-1,76-2,77-1,77-2,77-3, 77-4, 77-5 & 77-6, that are deposed at points where each shaft intersects with supporting structures 1st (69) thru 7th (75). FIG. 15(A) is a combined right-side view of FIG.13(B) & FIG.14(B). Power is applied to the primary input shaft 83 and then distributed the secondary input shafts 84-1 & 84-2 (87). At the end portions of each secondary input shafts 84-1 & 84-2, between 3rd (71) & 6th (74) structures are the Input Power- Transmitting Transfer Chambers 88. At this location 88, each chamber transmit power to its respective Output Power- Transmitting Conversion Chambers 89. After the conversion, the converted power (speed × 2 / torque × 1) is distributed to all 4 secondary output shafts 86-1, 86-2, 86-3 & 86-4 which is then concentrated into the primary output shaft 85. Input Power- Transmitting Chambers (87) and Output Power-Transmitting Chambers #1 (91) & #2 (90) were detailed in the aforementioned paragraphs. Attention will now turn to the Input Power-Transmitting Transfer Chambers 88, and the Output Power-Transmitting Conversion Chambers, 89. It is here that the embodiments seamlessly facilitate the technical achievement of a simultaneous speed transfer ratio of 1:2, and a 1:1 torque transfer ratio. Input Power-Transmitting Transfer Chambers 88: At the end portions of each secondary input shafts 84-1 & 84-2, between 3rd (71) & 4th (72) structures and 5th (73) & 6th (74) structures are disposed a dual co-axial Endless Power-Transmitting Planetary Gear Drives 68-2 / 1 & 68-2 / 3, 68-2 / 2 & 68-2 / 4, SEE FIGS. 16(A), 16(B) & 16(C), that facilitates the transfer of power to the Output Power-transmitting Conversion Chambers 89. The sprockets located in the upper Transfer Chambers 88 are the driver sprockets, and the sprockets located in the lower Conversion Chambers 89 are the driven sprockets. Output Power-Transmitting Conversion Chambers 89: FIGS.17(A),17(B) & 17(C) depicts the lower sections between 3rd (71) structure and 6th (74) structure of the Output Power- Transmitting Conversion Chambers 89. Also depicted, are the full complement of Endless Power-Transmitting Drive Chains, 68-1 / 1, 68-1 / 2, 68-1 / 3, 68-1 / 4, 68-1 / 5, 68-1 / 6, and Endless Power- Transmitting Planetary Gear Drives 68-2 / 1, 68-2 / 2, 68-2 / 3 & 68- 2 / 4. The transmission Output Power-Transmitting Conversion Chambers 89 will now be assembled. At each end portion of all the 4 secondary output shafts, 86- 1,86-2,86-3 & 86-4 located in the Output Power-Transmitting Conversion Chambers 89, are disposed the output shaft planetary carrier bearings 78-1, 78-2, 78-3 & 78-4, SEE FIG.12(C) & FIG.18. Between said bearings 78-1, 78-2, and 3rd structure (71) and bearings 78-3 & 78-4 and 6th structure (74), each output shaft 86-1, 86-2, 86-3 & 86-4 are housed in a planetary gear carrier hub, 92-1, 922, 92-3 & 92-4, that are securely bolted to their respective supporting structure 3rd (71) & 6th (74), SEE FIGS.19,20 & 21. All other parts are hidden for illustrative clarity. Unique to our design is the integration of sun gears 93, on all 4 secondary output shaft 93-1, 93-2, 93-3 & 93-4. Said sun gears are rigidly attached on their respective output shaft between each shaft’s front bearing 78-1, 78-2, 78-3, 78-4 and planet gear carrier hub 92-1,92-2,92-3 & 92-4, SEE FIG. 22 & FIG. 23. The sun gears 93-1, 93-2, 93-3 & 93-4 are meshed with planetary gears 94 of matching size and tooth configuration, SEE FIG. 24 & FIG. 25. Each set of coaxial planetary gears 94-1 & 94-3 and its parallel counterpart 92-2 & 92-4, are rigidly attached to the end portions of a shared connecting bar pin 95-1 & 95-2, SEE FIGS. 26 & 27. In addition, these pins 95-1 & 95-2 are rigidly attached at right-angle, intersecting the end portions of the connecting bar 97, SEE FIGS. 27, 28 & 29. Mounted at the end portions of each connecting bar pin 95-1 & 95-2, in front of and behind the planetary gear, are bearings 79-1, 79-2, 79-3, 79-4 & 80-1, 80- 2, 80-3, 80-4 that support the connecting bar 97 pivoting motion and function as fulcrum points, SEE FIGS. 12(C), FIGS. 30 & 31. All other parts are hidden for illustrative clarity. These sun gears 93-1, 93-293-3, 93-4 and planetary gears 94-1, 94-2, 94-3, 94-4 with their respective bearings 79-1, 79-2, 79- 3, 79-4 / 80-1,80-2, 80-3, 80-4, output shaft bearings 78-1, 78- 2, 78-3 & 78-4 are housed in planetary gear carriers 96-1, 96-2, 96-3 & 96-4, SEE FIG. 9 (c) & (d), FIGS. 32 & 33. These planetary gear carriers are mounted on their respective planet gear carrier hubs, 92-1, 92-2, 92-3, 92-4, and said planetary gear carriers are supported for rotation and as fulcrum points by rear 2nd bearings 82-1, 82-2, 82-3 & 82-4, which are mounted on face of the planet gear carrier hubs, and also front 1st bearings 81-1, 81-2, 81-3 & 81-4 mounted on the face of its respective planetary gear carrier 96, SEE FIG. 12(B), FIGS. 34 & 35, and are disposed in their respective support 4th (72) structure & 5th (73) structure, SEE FIG. 36. The 4th (72) structure is hidden for illustrative clarity. Force is transferred to each planetary gear carrier 96-1, 96-2, 96-3 & 96-4 via their respective driven sprockets 67b of the Endless Power-Transmitting Planetary Gear Drive 682 / 1, 68-2 / 2, 68-2 / 3 & 68-2 / 4 that are securely bolted to their respective planetary gear carriers 96, SEE FIG. 37, Detail A, and these driven sprockets are of similar diameter and tooth count of the driver sprockets on the secondary input shafts 84-1 & 84-2, located in the Input Power Transmitting Transfer Chambers 88, SEE FIGS. 15(A), 16(A), 16(B) & 16(C). The connecting bar pins 95-1 & 95-2, being pivotally attached to each of its respective planetary gear carrier 96, serve to pivotally join each planetary gear carrier 96 to its directly opposite counterpart, 96-1 with 96-3, and 96-2 with 96-4. And with connecting bar 97 being such a length, it enables the two sets of planetary gear carriers to rotate synchronously and in alignment with each other. The planetary gear carriers 96-1, 96-2, 96-3, and 96-4, together with the first bearings 81 disposed within their respective fourth (72) and fifth (73) support structures, and the second planetary gear carrier bearings 82 mounted on their respective planetary gear carrier hubs 92—which are themselves securely bolted onto the third (71) and sixth (74) support structures— along with the bearings 79 and 80 on the connecting bar pins, and the secondary output shaft planetary gear carrier bearings 78, collectively serve as critical fulcrum points in the conversion of power. The remaining transmission components are now assembled to complete the first embodiment of the invention as illustrated in FIGS. 38–42. SPEED CONVERSION: See FIG.43, Detail A. Referring also to the aforementioned second-to-last paragraph, as the planetary gear carriers 96-1 through 96-4 rotate synchronously and in alignment, their respective planetary gears 94-1 through 94-4, each rigidly attached to connecting bar pins 95-1 and 95-2, which are in turn rigidly attached to connecting bar 97, are constrained from rotating about their own axes. This constraint is imposed by the connecting bar 97 configuration, which guides the planetary gear along an orbital path while preventing axial rotation. Despite their rotational constraint, the pivoting motion of the connecting bar pins enables the rotationally constrained planetary gears to orbit their respective sun gears 93-1 through 93-4, with which they remain in continuous meshed engagement. As the planetary gears follow the circular paths defined by their rotating carriers, every single orbital revolution translate to two axial revolutions of the sun gear and output shaft assembly. This kinematic principle parallels the James Watt sun-planet mechanism disclosed in British Patent No.1306, October 25, 1781. Sequential views in FIGS. 14(A)–(H) illustrate the operation of this classical established system, wherein one full orbit of a rotationally constrained planetary gear produces two complete revolutions of the sun gear. While employing this classical established principle, the present embodiments achieve enhanced compactness and force transfer efficiency through the incorporation of Endless Power- Transmitting Chain Drives, Endless Power-Transmitting Planetary Gear Drives, and strategically positioned fulcrum points. TORQUE CONVERSION: SEE FIG.44. As the planetary gear carriers 96-1 through 96-4 rotate synchronously and in alignment, their respective planetary gears 94-1 through 94-4, each rigidly attached to connecting bar pins 95-1 and 95-2, which are in turn rigidly attached to the connecting bar 97, are constrained from rotating about their own axes. This constraint is imposed by the connecting bar 97 configuration, which guides the planetary gear along an orbital path while preventing axial rotation. Despite their rotational constraint, the pivoting motion of the connecting bar pins enables the planetary gears to orbit their respective sun gears 93-1 through 93-4, with which they remain in continuous meshed engagement. As the rotationally-constrained planetary gears follow the circular paths defined by their rotating carriers, the rigid attachment of the sun gears to the output shaft translates this orbital motion into axial motion. This meshed engagement allows the entire center-to-center (c-t- c) distance between each sun gear and its respective rotationally constrained planetary gear to act as an effective lever arm for force conversion back to torque, SEE FIG.48. A. An external power source delivers 100 Nm of torque to the input shaft / driver sprocket which rotates clockwise. B. This 100 Nm of torque is converted to 666 N of tangential force (100 Nm / .15m) at the periphery of the 300mm driver sprocket (radius= 150mm). C. Given a planetary gear carrier radius of 150mm and a sun gear - planetary gear c-t-c distance of 50mm, the resulting Mechanical Advantage = 3 (150mm / 50mm). D. During clockwise rotation, chain tension and thus force transfer occurs on the left side of the driver / driven mechanism, applying the calculated 666 N of force. E. With a MA of 3, the force experience by the rotationally constrained planetary gear is 2000 N (666 N x 3). F. With the entire c-t-c 50mm distance (.05m) between the sun gear / secondary output shaft assembly and rotationally constrained planetary gear, acting as an effective lever arm, torque output at the sun gear / output shaft assembly is 100 Nm (2000 N x .05m). Due to the rotationally-constraint and orbital motion of the planetary gears, this force is continuously exerted on the sun gear / output shaft assembly across a full 360orotation, delivering a consistent 100 Nm of output torque, regardless of chain engagement phase. In the first embodiment, having more than one planetary gear results in the load being shared among the multiple planetary gears. This design results in increased load handling capacity, improved torque density, and enhanced mechanical robustness. As a result, the system achieves a 1:2 speed transfer ratio and a 1:1 torque transfer ratio simultaneously - a key functional outcome of the described geometry and kinematic constraint. Second embodiment of the invention, ARC-EPTPGDT II, 68-2 / T [B]. SEE FIG. 49. In this second embodiment of the invention, there are only three internal structures, 1st (118), 2nd (119) & 3rd (120). No secondary shafts, only the primary input shaft 83, and primary output shaft 85, the follower shaft 123 and a single Endless Power-Transmitting Planetary Gear Drive 68-2 and 6 Endless Power-Transmitting Chain Drives 68-1, SEE FIG. 49, FIG. 50, FIG. 51, FIG. 52 & FIG. 53. This second embodiment design is for applications where less weight and space are of paramount importance, e.g., electric vehicles. FIG. 54 depicts the Transfer Chambers 88 and Conversion Chambers 89 with the single Endless Power-Transmitting Planetary Gear Drive 68-2, its sole sun gear 93-3 rigidly attached at the end portion of the output shaft 85 with bearing 78, and output shaft 85 is housed in planetary gear carrier hub 92-3. Planetary gear carrier hub 92-3 is securely bolted to 3rd structure 120, SEE FIG. 55. Also, planetary gear 94-3, is rigidly attached to the end portion of its respective connecting bar pin 95-1, and for orbital assistance, bearings 79-1,79- 3 & 80-3. Bearing 82-3 is support for rotation and function as a fulcrum point for the planetary gear carrier 96-3. The sun gear 93-3 and planetary gear 94-3 are housed in planetary gear carrier 96-3 and securely bolted to it is the driven sprocket of 68-2, SEE FIG. 56. FIG. 57 depicts the connecting bar 97 with both its rigidly attached at right-angle intersecting pins 95-1 & 95-2 at its opposite end portions. Orbital motion bearings 79-2 & 79-4 are attached to pin 95-2. It should be noted that all the connecting bar pins 95-1 & 95-2 in all embodiments are rigidly attached at right- angle intersecting the end portions of the connecting bar 97. To support the connecting bar 97 at its RIGHT-FRONT connecting bar pin (95) in its orbital travel around the sun gear, there are planetary gear carrier followers 121-1,121-2 & 121-3 attached to each of the other RIGHT-REAR, LEFT-REAR & LEFT-FRONT pins, SEE FIG. 58. Each planetary gear carrier follower 121- 1,121-2 & 121-3 is supported by their respective planetary gear carrier follower hub 122-1, 122-2 & 122-3 and each hub has their respective bearings 82 & 78 mounted at its center for support for rotation and function as a fulcrum point for the planetary gear carrier followers 121-1, 122-2 & 122-3, SEE FIG. 59 Detail A & B plus FIG. 60. Each planetary gear carrier follower hub 122-1, 122-2 & 122-3 is securely bolted to its respective 1st (118) or 3rd (120) structures, SEE FIG. 60. To assist the connecting bar 97 in its reciprocal orbital travel around the sun gear 93-3, power is provided from the input shaft 83 via 5 Endless Power-Transmitting Chain Drives, 68-1 / 1, 68- 1 / 2,68-1 / 3,68-1 / 4 & 68-1 / 5 that are connected to their respective planetary gear carrier followers, SEE FIG. 61 & FIG. 62. Also depicted is planetary gear carrier, 2nd structure, and bearing 81. For final assembly SEE FIGS. 50 & FIG. 49. Third embodiment of the invention, ARC-EPTPGDT III, 68-2 / T [C]. The third embodiment of the invention is basically gear driven instead of chain driven. And since it is required that the rotation of the drive and driven gear are in the same direction, a center idler gear is required. This third embodiment is suitable for application where weigh and space are not of paramount importance, but speed is, e.g., turbines for propulsion. It should be noted that, the description in the above embodiments of the present disclosure is only for illustration, and the number of input shafts, output shafts and follower shaft may be changed without departing from the scope of the present disclosure. If the number of input shafts and / or output shafts and / or follower shaft is increased or decreased, the number of internal structures, driven sprockets, driver sprockets, chains, planetary gears, sun gears, planetary gear carriers, planetary gear carrier hubs, connecting bar, connecting bar pins and various bearings may be correspondingly increased or decreased. The embodiments of the present disclosure are intended to describe the present disclosure by way of example so that those skilled in the art can easily understand. The scope of the present disclosure is not limited by the description of the embodiments, but only by the claims. According to the technical scheme protected in the claims, the speed transfer ratio of 1:2 and the torque transfer ratio of 1:1 is achieved, which is a great progress compared with the existing technology. In addition, since the sun gear, planetary gear, planetary gear carrier, input shafts, output shafts and follower shaft are all supported by supporting structures and various bearings, the tends of wear and deformation of these parts can be avoided, and better torque transmission than the traditional device is achieved.

Claims

CLAIMS 1. A transmission device comprising: at least one input shaft; at least one output shaft; at least one Power Transmission Assembly, each Power Transmission Assembly comprising: a power transmission driver gear rigidly attached to the input shaft; a power transmission driven gear having the same diameter and number of teeth as the power transmission driver gear, and a power transmission connection mechanism for connecting the power transmission driver gear and the power transmission driven gear; and at least one Power Output Transmission Assembly, each Power Output Transmission Assembly comprising: a planetary gear; a sun gear rigidly attached to the output shaft, the sun gear having the same diameter and number of teeth as the planetary gear and meshing with the planetary gear, wherein the planetary gear does not rotate around its own center, but orbits around the sun gear; and a planetary gear carrier for accommodating the sun gear and the planetary gear, wherein the driven gear of the Power Transmission Assembly is securely bolted to the planetary gear carrier and drives the planetary gear to move around the sun gear for orbital motion through the planetary gear carrier.

2. The transmission device of claim 1, further comprising: a plurality of internal support structures, wherein the input shaft and the output shaft penetrate corresponding internal support structures and are supported by the corresponding internal support structures through corresponding support bearings for rotation; each Power output Transmission Assembly further comprising: a planetary gear carrier hub securely bolted to corresponding internal support structures; wherein, the planetary gear carrier is installed in a corresponding internal support structure through a front first bearing mounted on a surface of the planetary gear carrier, and also installed on the planetary gear carrier hub through a rear second bearing mounted on the surface of the 1planetary gear carrier hub, and is supported by the front first bearing and the rear second bearing for rotation.

3. The transmission device of claim 2, wherein, there are two secondary input shafts, four secondary output shafts, four Power Transmission Assemblies and four Power Output Transmission Assemblies; the two secondary input shafts, the four Power Transmission Assemblies, the four Power Output Transmission Assemblies and the four secondary output shafts form two groups of coaxial structures.

4. The transmission device of claim 3, further comprising: a connecting bar and two connecting bar pins, wherein the two connecting bar pins are rigidly attached to two end portions of the connecting bar and intersect with the two end portions of the connecting bar at right angles respectively; each connecting bar pin is pivotally connected to planetary gear carriers of two coaxial Power Output Transmission Assemblies; planetary gears of two coaxial Power Output Transmission Assemblies are rigidly attached to two end portions of a corresponding connecting bar pin; a length of the connecting bar is such that two groups of coaxial planetary gear carriers of the Power Output Transmission Assemblies rotate synchronously and in alignment with each other; a plurality of bearings for supporting pivotal movement of the connecting bar are respectively installed in front of and behind the planetary gear of each Power Output Transmission Assembly, and accommodated in the planetary gear carrier of each Power Output Transmission Assembly.

5. The transmission device of claim 3, further comprising: a main input shaft; a main output shaft, wherein the main input shaft and the main output shaft penetrate corresponding internal support structures and are supported by the corresponding internal support structures through corresponding support bearings for rotation; two Power Input Assemblies corresponding to the two secondary input shafts one by one, each Power Input Assembly comprising: a power input driver gear rigidly attached to the main input shaft; a power input driven gear having the same diameter and number of teeth as the power input driver gear and rigidly attached to a corresponding secondary input shaft; and 2a power input connection mechanism for connecting the power input driver gear and the power input driven gear; and four Power Output Assemblies corresponding to the four secondary output shafts one by one, each Power Output Assembly comprising: a power output driver gear rigidly attached to a corresponding secondary output shaft; a power output driven gear having the same diameter and number of teeth as the power output driver gear and rigidly attached to the main output shaft; and a power output connection mechanism for connecting the power output driver gear and the power output driven gear.

6. The transmission device of claim 5, wherein the plurality of internal support structures comprises a first support structure, a second support structure, a third support structure, a fourth support structure, a fifth support structure, a sixth support structure and a seventh support structure, wherein, the main input shaft is arranged between the first support structure and the second support structure; the main output shaft is arranged between the second support structure and the seventh support structure; the planetary gear carrier hubs of the four Power Output Transmission Assemblies are respectively and securely bolted to the third support structure and the sixth support structure; the planetary gear carriers of the four Power Output Transmission Assemblies are respectively arranged in the fourth support structure and the fifth support structure through a respective front first bearing; the two input shafts are arranged between the first support structure and the sixth support structure; the four output shafts are respectively arranged between the second support structure and the fourth support structure, and, the fifth support structure and the seventh support structure.

7. The transmission device of claim 2, wherein the plurality of internal support structures comprise a first support structure, a second support structure and a third support structure; there are one input shaft, one output shaft, one Power Transmission Assembly and one Power Output Transmission Assembly; the planetary gear carrier hub is securely bolted to the third support structure, the input shaft is arranged between the first support structure and the second support structure, and the 3output shaft is arranged between the second support structure and the third support structure.

8. The transmission device of claim 7, further comprising: a follower shaft arranged between the first support structure and the third support structure; three planetary gear carrier followers; two Power Input Assemblies, each Power Input Assembly comprising: a power input driver gear rigidly attached to the input shaft; a power input driven gear having the same diameter and number of teeth as the power input driver gear and rigidly attached to the follower shaft; and a power input connection mechanism for connecting the power input driver gear and the power input driven gear; three Power Follower Assemblies corresponding to the three planetary gear carrier followers one by one, and each Power Follower Assembly comprising: a power follower driver gear; a power follower driven gear having the same diameter and number of teeth as the power follower driver gear and rigidly attached to a corresponding planetary gear carrier follower; and a power follower connection mechanism for connecting the power follower driver gear and the power follower driven gear; wherein the power follower driver gears of two of the Power Follower Assemblies are rigidly attached to the follower shaft, and the power follower driver gear of another Power Follower Assembly is rigidly attached to the input shaft; a connecting bar and two connecting bar pins, wherein the two connecting bar pins are rigidly attached to two end portions of the connecting bar and respectively intersect with the two end portions of the connecting bar at right angles; one of the two connecting bar pins is pivotally connected to the planetary gear carrier and one of the three planetary gear carrier followers; another one of the two connecting bar pins is pivotally connected to the other two of the three planetary gear carrier followers; a plurality of bearings for supporting pivotal movement of the connecting bar are mounted on the two connecting bar pins; and three planetary gear carrier follower hubs corresponding to the three planetary gear carrier followers one by one, wherein 4each planetary gear carrier follower hub is securely bolted to the first support structure and the third support structure; wherein the planetary gear is rigidly connected to one end portion of one of the two connecting bar pins, and the three planetary gear carrier followers are respectively attached to the other end portions of the two connecting bar pins; each planetary gear carrier follower is installed on a corresponding planetary gear carrier follower hub through a respective rear second bearing mounted on a surface of the corresponding planetary gear carrier follower hub, and is supported by the respective rear second bearing for rotation; and a length of the connecting bar is such that the three planetary gear carrier followers rotate synchronously and in alignment with the planetary gear carrier.

9. The transmission device of any of claims 1 to 8, wherein the power transmission connection mechanism, and / or the power input connection mechanism, and / or the power output connection mechanism, and / or the power follower connection mechanism are chains or idle gears; when any one of the power transmission connection mechanism, and / or the power input connection mechanism, and / or the power output connection mechanism, and / or the power follower connection mechanism is a chain, the driver gear and the driven gear are linked with the chain; and when any one of the power transmission connection mechanism, and / or the power input connection mechanism, and / or the power output connection mechanism, and / or the power follower connection mechanism is an idle gear, the idle gear is located between the driver gear and the driven gear and meshes with the driver gear and the driven gear.

10. The transmission device of claim 9, wherein the transmission exhibits a speed transfer ratio of 1:2, derived from sustained force engagement across the full center-to-center (c-t-c) distance of the meshed gear assembly, specifically between each rotationally constrained planetary gear and the rigidly attached sun gear / output shaft assembly, said distance functioning as an effective lever arm that converts orbital motion into rotational output.

11. The transmission device of claim 10, wherein the torque transfer ratio is 1:1, governed by a mechanical advantage (MA) defined as: (a) a center-to-center distance between the periphery of the planetary gear carrier and the sun gear; and divided by (b) a center-to-center distance between each rotationally constrained planetary gear and its corresponding sun gear; wherein said mechanical advantage produces sustained tangential force across the full center-to-center distance of 5the meshed engagement, acting continuously as an effective lever arm to regenerate torque at the sun gear / output shaft assembly.

12. A transmission system comprising at least two or more transmission device of claim 1, wherein each transmission device is equipped with a clutch box coupled to its input shaft, said clutch box configured to engage only after the preceding device reaches a predetermine rotational speed (RPM).

13. A multiplier transmission system, comprising:(a) the transmission system of claim 12, and (b) a compound gear multiplier coupled to an output shaft of said transmission system, wherein the compound gear multiplier is configured to deliver a predetermined rotational speed (RPM) output to a driven device designed for fixed-speed operation. 6

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