Stepless power transmission planetary gear transmission device

Abstract

Conventional mechanical powertrains exhibit an inherent compromise between torque and speed. This traditional relationship shapes past and existing designs. According to the innovation, the traditional example is challenged by introducing a forefront mechanical power system. Through creative fusion of known mechanical systems, we implement an exemplary embodiment: a stepless power transfer planetary gear transmission (EPTPGDT). The breakthrough mechanical power transmission device is elaborately designed to simultaneously realize 1: 1gt; the torque transmission ratio and the speed transmission ratio are 1: 2, so that the conventional constraint of the torque-speed relation is effectively destroyed. The integrated innovation means a revolution leap of the mechanical power transmission technology, and provides a novel solution to optimize torque and speed in an unprecedented manner.

Description

Technical Field

[0001] This invention relates to a mechanical power transmission system having a gear or chain and sprocket mechanism. The type of mechanical power transmission system described herein can be used in any transmission system application. Background Technology

[0002] James Watts and the steam engine. Ancient Chinese technology.

[0003] The steam engine, invented by the Frenchman Denis Papin (1647-1712), the Englishmen James Savery (1650-1715) and Thomas Newcomen (1664-1729), and the Scotsman James Watts (1736-1819), was used to pump water out of flooded coal mines. (See also...) Figure 1A and Figure 1B The main structure is 1. A water pump 6 is pivotally connected to the main beam 4 via a connecting rod 5. The combustion side consists of a roaster 2 and a cylinder chamber 3 that houses the piston and connecting rod, which is also pivotally connected to the 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 and 1782, respectively.

[0004] In the late 18th century, the Western Industrial Revolution was accelerated by corn, malt, and cotton mills, iron rolling mills, blast furnaces, forging furnaces, and many other emerging new industries. These new industries required a new power source to supplement the old rotating water turbines. All kinds of mills used these water turbines and horses to turn the "wheels," however, while these power sources were sufficient for small operations, the available water volume was usually limited, and using large herds of horses was often impractical.

[0005] A steam engine with rotary capability was needed, not merely one that pumped water from mines through the reciprocating vertical motion of its horizontal oscillating beam. This reciprocating vertical motion of the horizontal oscillating beam could easily be converted into rotary motion using a crank mechanism first invented in ancient China during the Han Dynasty (206 BC – 220 AD). The earliest true hand-cranked crank was found in a Han Dynasty glazed pottery tomb. It is a model of an agricultural winnowing fan dating no later than 200 AD. Crank mechanisms continued to be used in grain mills, silk reeling machines and hemp spinning machines, hydraulically powered flour sieves, hydraulically powered bellows, well winches, and other equipment in the later imperial period of China [Tang Dynasty (618 AD – 907 AD) and Song Dynasty (960 AD – 1279 AD)]. Centuries later, crank mechanisms were imported to Europe. The Englishman James Pickard incorporated a crank mechanism into the Newcomen steam engine and obtained a patent in 1780 (see [link to patent]). Figure 2A and 2B The main beam 4 is pivotally mounted on the main structure 1, and 7 is a crank lever that is rigidly connected to the flywheel 9a via a crankshaft 8. The connecting rod 5 is pivotally connected to the main beam 4 and the crank lever 7 via its respective end.

[0006] Therefore, to circumvent the patent on the crank mechanism, Watt commissioned William Murdock (chief mechanic of Bolton & Watts Steam Engine Company) to design an alternative to convert the reciprocating vertical motion of the oscillating beam into rotational motion. Murdock designed five alternatives, which Watt patented on October 25, 1781, as British Patent 1306. One of the five alternatives employed a special arrangement of two gears with similar diameters and numbers of teeth in a solar planetary structure (see...). Figure 3A , 3B Along with 3C, the main beam 4 is pivotally mounted on the main structure 1. The combustion side consists of a roaster 2 and a cylinder chamber 3 housing a piston and connecting rod, which is pivotally connected to the main beam 4. The rotation side consists of a sun gear 11 rigidly connected to an output shaft 12, which is rigidly connected to a flywheel 9b. Planetary gears 10 are rigidly connected to the end of the connecting rod 5 and pivotally connected to the main beam 4 at their opposite ends. The sun gear 11 and planetary gears 10 are kept meshed by a tie rod 13a.

[0007] The concept of the solar and planetary gears (also known as planetary gears) has ancient origins, tracing back to their early applications by ancient Chinese mechanics (i.e., craftsmen). They utilized this innovative gear system in the manufacture of precision astronomical instruments and complex mechanical clocks.

[0008] In the Watts-Murdock design, planetary gear 10 is rigidly connected to the end of the shaft where the water pump was previously located. Rigidly connected to the end of this shaft, planetary gear 10 does not rotate about its own axis. Its shaft is connected to the shaft of sun gear 11 via a link 13a, which rotates about the axes of both planetary and sun gears and maintains a constant distance between the centers of the planetary and sun gears, thus keeping them meshed (see...). Figure 3A , 3B (and 3C). Therefore, the planetary gear 10 orbits the sun gear 11.

[0009] The first phenomenon of this design is that, for each orbit of the planetary gear 10 around the sun gear 11, the sun gear undergoes two rotations on its axis (see...). Figure 4A , 4B 4C, 4D, and 4E).

[0010] The explanation is as follows. Figure 4A The TDC (Top Dead Center) is shown. 16 The sun and planetary gears are located at [location missing]. Note the A slot of the planetary gear and tooth 1 of the sun gear. Figure 4B This shows the planetary gear 10 in the first quarter of its orbit around the sun gear 11. 17 At this point, the sun gear 11 has already rotated 180 degrees on its axis. Figure 4C This shows the planetary gear 10 at BDC (Bottom Dead Center). 18 At that time, the Sun Gear 11 had completed a full 360 degrees. Figure 4D The planetary gear 10 is shown to be in the third quarter of its orbital rotation. 19 At that point, the sun gear 11 had already rotated another 180 degrees. Finally, Figure 4E This shows that planetary gear 10 is in the final stage, namely TDC. 16 Sun gear 11 has completed its second 360-degree rotation on its shaft.

[0011] Flywheel 9b is connected to the sun gear via output shaft 12 to provide smooth rotational power to the factory floor. Flywheel 9b reduces jolt motion (a characteristic of the reciprocating vertical motion of beam 4). This results in a second phenomenon: flywheel 9b, which rotates two revolutions during a single operating cycle, requires only a quarter of the engagement compared to flywheel 9a of the crank mechanism (see [link to relevant documentation]). Figure 2A , 2B (3A, 3B, and 3C).

[0012] Impressive was its 1:2 speed ratio and the fact that it required only a quarter of the locking mechanism of the flywheel 9b and the crank mechanism 9a; however, the primary objective was to obtain rotational power as efficiently as possible. Therefore, it was inevitable that the solar-planetary mechanisms 10, 11, 12, and 13a were abandoned, and that the much simpler crank mechanisms 7, 8, and 5, which were simpler in operation and manufacture, were adopted when their patents expired. This adjustment was appropriate for the end of the Bolton-Watt steam engine's production lifecycle.

[0013] In addition to being more complex to operate and manufacture, Watt-Murdoch's solar planetary mechanism had several design flaws that led to its abandonment.

[0014] First, the transmitted power is a vertical reciprocating force via the swing beam 4. This vertical reciprocating force must be constantly concentrated in the orbital motion via the tie rod 13a. The planetary gear 10 tends to move in a straight line, therefore, any opportunity it has (e.g., wear of the tie rod sleeves 13b and 13c, see...) Figure 3C This will result in a tangential contact point between planetary gear 10 and sun gear 11. 20 It is not optimal, resulting in insufficient force transmission (see...). Figure 4G See also Figure 4F and Figure 4G Because at the front of the planetary gear pin 13b of the connecting rod 21 There is no fulcrum structure at that point, so a similar situation occurs.

[0015] Secondly, at the front of the output shaft 13c 22 In the absence of a fulcrum structure, see Figure 4F The force transmitted by the beam causes the sun gear 11 to rotate and deform, further leading to the tangential contact point. 20 For the defects, see Figure 4G .

[0016] Third, there are two instances of force transmission loss between planetary gear 10 and sun gear 11. These occur at TDC and BDC. Here, at both contact points, only vertical force is experienced. 23 See Figure 4H (Only TDC is shown) 16 Furthermore, the inertia of flywheel 9b is necessary to push sun gear 11 in the direction of rotation so that it can again undergo tangential contact with planet gear 10. 20 (see Figure 4G ).

[0017] From the above, it can be determined that flywheel 9b is for Figure 3A The operation of the Watt-Murdoch solar planetary mechanism is crucial. This also applies to the Picard-Newcomb crank mechanism (…). Figure 2A (9a)

[0018] In the development of the current embodiment of the invention, the deficiencies detailed above have been thoroughly considered. These deficiencies will be corrected through innovative features, and these innovations will be successfully incorporated into the current embodiment of the invention. The success of this incorporation will ultimately result in a third phenomenon, namely a torque transmission ratio of 1:1 ≥.

[0019] The following sections introduce Archimedes (287-212 BC) and the lever, Zhuge Liang (181-234 AD) and the wheelbarrow, Su Song (1020-1101 AD) and the continuously variable transmission chain drive, and Christoph Grienberger (1561-1636 AD) and the 24-gear reducer.

[0020] Any device that transmits force from the point of its action to another point of its reaction is a machine. This is achieved in a simple way that cannot be simplified further. Thus, it is an example of a simple machine.

[0021] Examples of simple machines are: 1. levers, 2. inclined planes, 3. wheels and axles, 4. screws, 5. pulleys, 6. wedges, 7. gears, and 8. chain and sprocket mechanisms. However, physicists recognize only two fundamental principles in simple machines: those of levers and inclined planes. Wheels and axles, pulleys, gears, and sprockets can be considered levers, more precisely, rotating levers. Wedges and screws utilize the principles of inclined planes.

[0022] The lever is described below. It is a rigid object that can rotate about a fixed point called the fulcrum. See [link to relevant documentation]. Figure 5A As a practical example, we can consider a plank placed on a triangle, where the plank is the lever 25 and the triangle is the fulcrum 24. If the fulcrum is at the center of gravity 26 of the lever, the lever will remain balanced, neither tilting to one side nor the other. Because the lever 25, like any other object, behaves as if all its weight were concentrated at its center of gravity. 26 Therefore, it can be supported as a whole on the narrow side of fulcrum 24. If lever 25 has uniform size and density, its center of gravity is at its geometric center. 26 And fulcrum 24 must be placed there.

[0023] exist Figure 5B In the middle, if the downward force 29 The distance from the point on lever 25 to the fulcrum 24 is the distance from the point on lever 25 to the fulcrum. 28 Synchronous forces 29 This represents torque, and the lever rotates in the direction of the torque. In this case, it is the torque in the counterclockwise direction. 30Assuming equal downward forces 29 At the same time, it acts on the lever 25 on the other side of the fulcrum by the same distance. 28 At fulcrum 24, the two torques are equal in magnitude but opposite in direction. The torque on one side of fulcrum 24 tends to produce clockwise rotation, and the torque on the other side tends to produce counterclockwise rotation. If one torque is denoted by the symbol t, the other torque must be -t, and the sum of the two torques must be zero. In this case, the lever does not move and remains balanced. 27 (see Figure 5C ).

[0024] On the other hand, see Figure 5D If force 29 A downward force acts on one side of fulcrum 25, and an upward force acts on the other side, resulting in motion in the same direction—either both clockwise or both counterclockwise. Therefore, the two torques have the same sign, and when added together for clockwise rotation, they equal 2t, or when added together for counterclockwise rotation, they equal -2t. This dual torque is a coupling. 31 And through coupling 31 The lever's kinematic ratio about the fulcrum is 24 times that of a single torque. 30 Naturally easier (see Figure 5B See also Figure 2B Crank 7 is a single torque lever.

[0025] See Figure 5E For a lever to be balanced, it must experience equal and opposite torques, and this is true even if the forces applied are not equal. The principle is explained below. Consider a lever on one side of the fulcrum at a given distance (r) from the fulcrum. 32 The downward force (f) acting at the point. 29 The torque will be fr. Next, consider the downward force (2f) acting on the other side of the fulcrum, which is twice as large. 34 However, the distance is only half that of the first one (-r / 2). 33 The distance is given a negative sign here because it is in the opposite direction to the fulcrum compared to the first. The second torque is (2f)(-r / 2) or (-fr). The two torques are equal and opposite, namely (fr) and (-fr), and the lever remains balanced. 27 .

[0026] Because torque, rather than force, must be equal in order to achieve balance, levers can be used effectively; see [reference needed]. Figure 5F .

[0027] See Figure 5F Assume a force of 2450 N is applied to the left end of the lever. 38 A relatively large force is required, and it needs to be 245N from the right end of the lever. 37A smaller force is needed to balance it. What one must do is place the fulcrum 24 at a distance of 2450N. 38 1 meter of force 36 The position is far away, and the fulcrum 24 will be placed at a distance of 245N. 37 10 meters of force 35 At a distant position, the primary force of 2450 N (2450 × 1 = 2450 N) is supported by a secondary force of 245 N (245 × 10 = 2450 N). By utilizing this phenomenon, a lever can accomplish a task with one-tenth of the force required for direct motion. By appropriately adjusting the difference, one can achieve the same result with 1 / 100, 1 / 1000, or any fraction of the force required for direct motion.

[0028] Undoubtedly, even primitive humans stumbled upon this "lever principle," using tree branches as levers and fishing rods. However, it wasn't until the time of the Greek scholar Archimedes (287-212 BC) that the situation was scientifically analyzed. Archimedes greatly admired the lever principle and its application in the infinite multiplication of force, so he exaggeratedly said, "Give me a lever long enough and a fulcrum on which to place it, and I shall move the world."

[0029] There are three types of levers. Their main differences lie in the relative positions of the applied forces, the location where the force is generated, and the location of the fulcrum:

[0030] Type 1 leverage, see [link / reference] Figure 6A (b) has a force acting on the opposite side of fulcrum 24. 39 and reaction force 40 Force 39 and reaction force 40 In the opposite direction 41 Movement. A typical example of this is as shown in (a) where it is used as a pry bar. 42 (force) 39 To move the boulder (reaction force) 40 (The branches of the tree.) Two forces in opposite directions. 41 Move, see Figure 6A (a). The first type of lever causes the force to act 39 The amount increases and the reaction force decreases. 40 The speed. The force. 39 The multiple of the enhancement and the fulcrum 24 and action force 39 Distance and fulcrum between 24 Reaction force 40 The ratio is directly related. The higher the ratio, the stronger the multiplication. This phenomenon is described in more detail below.

[0031] Type 3 leverage, see Figure 6B (b) has a force acting on the same side of the fulcrum. 39As a reaction force 40 However, the force 39 In reaction force 40 and pivot 24 Between, and the force 39 and reaction force 40 They all move in the same direction (43). A typical example of this is when used as a fishing rod. 44 Branches, see Figure 6B (a) The third type of lever increases the distance and speed of motion, but does not increase the force applied. 39 .

[0032] Type 2 levers, see Figure 6C (b) has a force acting on the same side opposite to the fulcrum 24. 39 and reaction force 40 However, the force 39 Specific reaction force 40 Further away from the fulcrum 24 Force 39 and reaction force 40 All in the same direction 43 Movement. A typical example of this is a wheelbarrow. 46 See Figure 6C (a) One name is associated with the person who "accidentally discovered the lever," or more accurately, the "inventor"—Zhuge Liang (181-234 AD), a minister of the Han Dynasty. This invention was remarkably successful in supplying... 45 They transported soldiers to the front lines and sent wounded soldiers back to the rear, to the point that military officials tried to keep it a secret.

[0033] From here, we will apply force. 39 This is called the applied torque. 59 , will reaction force 40 This is called reaction torque. 60 This is because, whether it's a piston engine... 48 (see Figure 7A Turbines from coal-fired power plants, nuclear power plants, or hydroelectric power plants. 49 (see Figure 7B Wind turbine 50 (see Figure 7C ), or electric motor / generator (see Figure 7D At the source of all power sources, the force of all modes 47a All of these act on the lever. 47b This generates torque. 47c , (f×d=t).

[0034] Gears and chains, along with sprockets, act as levers. Circular levers allow torque to be applied continuously, and because it's convenient to apply new torque without stopping, this is a key feature. Figure 8A Medium rotating lever 52 The concept is easy to visualize, so it will be explained below. Figure 5A The basic lever is shown, which is Figure 8A (a) is transformed into (b) and (c), and then into the basic structure of a gear in (d).

[0035] The following section introduces gears. Figure 8B and Figure 8C In this configuration, the two meshing gears 53 are geometrically similar in size and tooth structure. Two or more gears are considered a gear system. 56 If the gear 53(b) on the right is the driving gear, then the other gear 53(a) on the left is the driven gear. Figure 8C In the middle, the drive gear 53(b) rotates clockwise. 57 Rotation, therefore the driven gear 53(a) rotates counterclockwise. 58 Rotation. Input torque. 59 The gear train enters via the input shaft 54, which is rigidly attached to the center of the drive gear 53(b), and exits via the output shaft 55, which is rigidly attached to the driven gear 53(a). 56 At the ends of the teeth of each gear in the drive gear 53(b), the torque acting from the input shaft 54... 59 This becomes the reaction torque (tr1). 60 r1 is the distance from the center of the input shaft 54 ​​to the end of the tooth of the drive gear 53(b) in the imaginary lever 25(b). It is the point of tangential contact with the teeth of the drive gear 53(b) and the driven gear 53(a). 61 At the point, reaction torque 62 The output shaft 55 is rigidly attached to the center of the driven gear 53(a). It now outputs a torque (tr2) 63. This distance is r2 of the imaginary lever 25(a). These gears are geometrically equal, r1 = r2, therefore, the output torque of the driven gear 53(a) output shaft 55 is... 63 The speed is equal to the input torque of the driving gear 53(b) 59 And speed. The only difference is that if the drive gear 53(b) is in a clockwise direction 57 If rotated, the driven gear will rotate counterclockwise. 58 Rotation, and vice versa. If it is necessary for the driving gear 53(b) and the driven gear 53(a) to rotate in the same direction, then a freewheeling gear 64 with the same geometry is placed in the gear set. 65Between, see Figure 8D The additional gear 64 does not affect the equality of torque and speed mentioned above, but it adds complexity and weight. The gear shafts (input, output, and idling) are used as... Figure 8A , 8B And the fulcrum 24 of the mechanism shown in 8C. These shafts are supported by bearings arranged in the transmission structure for rotation and serving as fulcrums. The bearings and the structure (not shown) are strategically positioned behind and in front of the gear to maximize the efficiency of fulcrum 24.

[0036] Extremely high torque or speed can be achieved by changing the geometry of the driven gear relative to the driving gear. This is a purely geometric inverse relationship.

[0037] Astronomical speeds are limited by centrifugal force and materials science. Astronomical torques are limited by the fact that the speed of the last gear with all the desired torques could take hundreds, thousands, millions, billions, or trillions of years to achieve a single rotation. These astronomical torques are what Archimedes was referring to when he also stated, "I have figured it out, and there is no single object on this earth that I cannot move."

[0038] The following section describes chains and sprockets. See also... Figure 9 (a) The chain and sprocket mechanism is also known as the Endless Power-Transmitting Chain Drive (EPTCD) 68-1. It was invented by Su Song (1020-1101 AD), a Chinese court official, naturalist, astronomer, clockmaker, and mechanic. Su Song's greatest legacy is the clock tower he built in Kaifeng in 1094. It is a masterpiece of cutting-edge mechanical systems, the most important of which is the innovative clock drive system. At the center of the clock tower is the "celestial ladder." This is the earliest known continuously power-transmitting chain drive (EPTCD) 68-1.

[0039] The basic components of the chain drive system 68-1 include a chain 66 (typically made of metal links) and sprockets 67a and 67b (gears with teeth that mesh with the chain). One sprocket is the driving sprocket (input), and the other is the driven sprocket (output). For the current embodiment of the invention, the driving sprocket is 67a, and the driven sprocket is 67b. A continuously variable power transmission (CVT) chain drive will be incorporated into the first and second embodiments of the invention; furthermore, an improved form integrating the planetary gear carrier 96 into the driven sprocket 67b will also be incorporated. These improved forms will be referred to as a continuously variable power transmission planetary gear drive (EPTPGD) 68-2, see [link to ETPGD]. Figure 9 (b), (c) and (d).

[0040] In the clock tower, sprockets 67a and 67b are mounted on separate shafts (not shown). The shaft serves as a fulcrum 24 and is supported by bushings within a support structure for rotation. Both the bushings and the support structure are strategically positioned in front of and behind the sprockets to maximize the efficiency of the fulcrum 24. When the drive sprockets are rotated by a waterwheel in this case, the motion causes a linked chain to rotate another sprocket (the driven sprocket), thereby transmitting power to rotate the armillary sphere and power the clock.

[0041] Prior to Su Song's chain drive, transmission belts had existed in China for approximately 1000 years. However, these belts were primitive and haphazard, lacking the precision required to drive clocks and armillary spheres. The advantages of this continuously variable power transmission chain drive device 68-1 are: 1. The chain links equipped with sprockets will not slip; 2. The driving sprocket 67a and driven sprocket 67b, rotating on their respective shafts, rotate in the same direction, thus eliminating the need for an idler unit, and making the following advantages possible: 3. The driving sprocket 67a and driven sprocket 67b can be any distance apart from each other; 4. Tangential contact points... 61 (see Figure 8C All of these are distributed along the driving / driven sprockets in chain contact, resulting in coupling. 31 Effects (see) Figure 5D As mentioned above, this is a more efficient way to transmit torque. Summary of the Invention

[0042] 1. Rotating lever ( Figure 8A ), 2. The Sun and Planetary Gears ( Figure 4A ), 3. Type 2 levers ( Figure 6C ), 4. Continuously Variable Transmission Chain Drive Device (EPTCD) ( Figure 9 A) and 5. Continuously Variable Power Transmission Planetary Gear Drive (EPTPGD) Figure 9 The groundbreaking convergence of (b), (c), and (d) will be innovatively integrated to produce an ideal embodiment of an efficient mechanical power transmission system, meticulously designed to simultaneously achieve a speed transmission ratio of 1:2 and a torque transmission ratio of 1:1 or greater. This integrated innovation will be termed a continuously variable power transmission planetary gear drive (CVT). 68-2T [A]), (i.e., ARC-EPTPGDT 1), see [link / reference] Figure 10A , Figure 10B , Figure 10C and Figure 10D .

[0043] The combination of a rotating lever, a sun-planetary gear, a type 2 lever, a continuously variable transmission (CVT) chain drive, and a CVT planetary gear drive culminates in an innovative architecture, resulting in an embodiment of a cutting-edge mechanical power transmission device known as the CVT planetary gear transmission (ARC-EPTPGDT 1). This embodiment is illustrated by 64 figures (Figures 10 to 48), each systematically detailing the assembly of each component of the invention, as well as the pivoting joints during assembly. We clearly reveal how this innovative structure achieves a 1:2 synchronous speed transmission ratio and a torque transmission ratio of 1:1 ≥. The 1:2 speed transmission ratio depends on the tooth configuration of the sun and planetary gears having equal diameters, regardless of their specific dimensions. The torque transmission ratio may be equal to or greater than 1:1, expressed as 1:1 ≥. The magnitude of this increase will depend on how much larger the center-to-center distance (ctc#1) between the outer periphery of the planetary gear carrier and the sun gear is compared to the center-to-center distance (ctc#2) between the planetary gears and the sun gear. The larger this ratio, the more significant the increase in torque transmission. While the value can be as large as desired, practical limitations do apply. The first embodiment is based on the additional embodiments ARC-EPTPGDT 2, [3-1], [3-2]. These additional embodiments, with 15 figures ( Figure 8D and 49 Up to 62), although sharing core features with the first embodiment, different enhancements are provided to extend the utility and applicability of the invention to various situations. A series connection of several ARC-EPTPGDTs coupled to a compound gear reducer power source will be referred to as ARC-Kinetic Energy Multi Endless Drives En Serie I (ARC-KEMEDES I for short). Additionally, if a compound gear multiplier is coupled to this ARC-KEMEDES I system, the resulting system will be referred to as ARC-KEMEDES II.

[0044] The first aspect of this application discloses a transmission device, namely a continuously variable power transmission planetary gear transmission device (ARC-EPTPGDT 1), comprising: at least one input shaft, which is a secondary input shaft in a first embodiment and a primary input shaft in a second embodiment; at least one output shaft, which is a secondary output shaft in a first embodiment and a primary output shaft in a second embodiment; and at least one power transmission component, which can be a continuously variable power transmission chain drive device (EPTCD) or a gear set including a freewheeling gear. 65Each power transmission component includes: a power transmission drive gear rigidly attached to the input shaft; a power transmission driven gear having the same diameter and number of teeth as the power transmission drive gear; and a power transmission connection mechanism for connecting the power transmission drive gear and the power transmission driven gear; and at least one power output transmission component, namely a continuously variable power transmission planetary gear drive (EPTPGD), each power output transmission component 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, wherein the planetary gear does not rotate around its own center, but orbits around the sun gear; and a planetary gear carrier housing the sun gear and planetary gears, wherein the driven gear of the power transmission component is securely bolted to the planetary gear carrier and drives the planetary gear to orbit around the sun gear via the planetary gear carrier.

[0045] In embodiments of this application, the transmission device further includes: multiple internal support structures, through which the input shaft and output shaft pass and are supported by the internal support structures for rotation via corresponding support bearings; each power output transmission component further includes: a planetary gear carrier hub, securely bolted to the corresponding internal support structure; wherein the planetary gear carrier is mounted in the internal support structure via a front first bearing mounted on the surface of the planetary gear carrier, and is also mounted on the planetary gear carrier hub via 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.

[0046] In the first embodiment of this application, there are two input shafts; there are four output shafts, four power transmission components, and four power output transmission components; the two input shafts, four power transmission components, four power output transmission components, and four output shafts form two sets of coaxial structures.

[0047] In a first embodiment of this application, the device further includes: a connecting rod and two connecting rod pins, wherein the two connecting rod pins are rigidly connected to the two ends of the connecting rod and intersect the two ends of the connecting rod at right angles; each connecting rod pin is pivotally connected to the planetary gear carriers of two coaxial power output transmission assemblies; the planetary gears of the two coaxial power output transmission assemblies are rigidly connected to the two ends of the corresponding connecting rod pins; the length of the connecting rod is such that the planetary gear carriers of the two sets of coaxial power output transmission assemblies rotate uniformly and are aligned with each other; a plurality of bearings for supporting the pivoting movement of the connecting rod are respectively mounted in front of and behind the planetary gears of each power output transmission assembly and housed in the planetary gear carriers of the power output transmission assemblies.

[0048] In the first embodiment of this application, it further includes: a main input shaft; a main output shaft, wherein the main input shaft and the main output shaft pass through an internal support structure and are supported by the internal support structure through corresponding support bearings for rotation; and two power input components, which can be a continuously variable transmission chain drive (EPTCD) device or a gear set including a freewheeling gear. 65 The two power input components correspond one-to-one with the two input shafts. Each power input component includes: a power input drive 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 drive gear and rigidly attached to the corresponding input shaft; a power input connection mechanism for connecting the power input drive gear and the power input driven gear; and four power output components, which can be continuously variable transmission chain drive (EPTCD) devices or gear sets including idler gears. 65 The four power output components correspond one-to-one with the four output shafts. Each power output component includes: a power output drive gear, rigidly attached to the corresponding output shaft; a power output driven gear, having the same diameter and number of teeth as the power output drive gear, and rigidly attached to the main output shaft; and a power output connection mechanism for connecting the power output drive gear and the power output driven gear.

[0049] In the first embodiment of this application, 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. The main input shaft is disposed between the first and second support structures; the main output shaft is disposed between the second and seventh support structures; the planetary gear carrier hubs of the four power output transmission components are securely bolted to the third and sixth support structures, respectively; the planetary gear carriers of the four power output transmission components are respectively disposed in the fourth and fifth support structures via their respective front first bearings; two input shafts are disposed between the first and sixth support structures; and four output shafts are respectively disposed between the second and fourth support structures and between the fifth and seventh support structures.

[0050] In the second embodiment of this application, the plurality of internal support structures include a first support structure, a second support structure and a third support structure; one each of an input shaft, an output shaft, a power transmission assembly and a power output transmission assembly; the planetary gear carrier hub is securely bolted to the third support structure, the input shaft is disposed between the first support structure and the second support structure, and the output shaft is disposed between the second support structure and the third support structure.

[0051] In the second embodiment of this application, it further includes: a driven shaft disposed between the first support structure and the third support structure; three planetary gear carrier followers; and two power input components, which can be a continuously variable transmission chain drive (EPTCD) device or a gear set including a freewheeling gear. 65 Each power input assembly includes: a power input drive gear rigidly attached to an input shaft; a power input driven gear having the same diameter and number of teeth as the power input drive gear and rigidly attached to a driven shaft; and a power input connection mechanism for connecting the power input drive gear and the power input driven gear; and three power follower assemblies, which can be continuously variable transmission chain drive (EPTCD) devices or gear sets including idler gears. 65 The three power follower assemblies correspond one-to-one with the three planetary gear carrier followers. Each power follower assembly includes: a power follower drive gear; a power follower driven gear having the same diameter and number of teeth as the power conversion drive gear and rigidly attached to the corresponding planetary gear carrier follower; and a power follower connecting mechanism for connecting the power follower drive gear and the power follower driven gear; wherein, the power follower drive gears of two power follower assemblies are rigidly attached to the driven shaft, and the power follower drive gear of the other power follower assembly is rigidly attached to the input shaft; a connecting rod and two connecting rod pins, wherein the two connecting rod pins are rigidly connected to the two ends of the connecting rod and intersect the two ends of the connecting rod at right angles; one of the two connecting rod pins is pivotally connected to the planetary gear carrier and one of the three planetary gear carrier followers; and two connecting rod pins are also included. Another link pin is pivotally connected to two of the other two planetary gear carrier followers; multiple bearings for supporting the pivoting movement of the connecting rod are mounted on the two connecting link pins; and three planetary gear carrier follower hubs correspond one-to-one with the planetary gear carrier follower hubs, wherein each planetary gear carrier follower hub is securely bolted to a first support structure and a third support structure; wherein the planetary gear is rigidly connected to one end of one of the two connecting link pins, and the three planetary gear carrier followers are respectively attached to the other ends of the two connecting link pins; each planetary gear carrier follower is mounted on the corresponding planetary gear carrier follower hub by a rear second bearing mounted on the surface of the corresponding planetary gear carrier follower hub and is supported by the rear second bearing for rotation; the length of the connecting rod is such that the three planetary gear carrier followers rotate in unison with the planetary gear carrier and are aligned with each other.

[0052] In the embodiments of this application, the power transmission connection mechanism, and / or power input connection mechanism, and / or power output connection mechanism, and / or power follower connection mechanism is a chain or a freewheeling gear; when the power transmission connection mechanism, and / or power input connection mechanism, and / or power output connection mechanism, and / or power follower connection mechanism is a chain, the drive gear and the driven gear are linked to the chain; when the power transmission connection mechanism, and / or power input connection mechanism, and / or power output connection mechanism, and / or power follower connection mechanism is a freewheeling gear, the freewheeling gear is located between the drive gear and the driven gear, and meshes with the drive gear and the driven gear.

[0053] The speed transmission ratio of the transmission device in this embodiment is 1:2; the torque transmission ratio of the transmission device is a function of the center-to-center distance between the outer circumference of the planetary gear carrier and the sun gear and the center-to-center distance between the planetary gear and the sun gear.

[0054] The torque transmission ratio of the transmission device in the embodiments of this application is equal to or greater than 1:1.

[0055] The second aspect of this application discloses a speed reduction transmission system, namely ARC-KEMEDESI in the embodiments of this application, which includes at least one transmission device as described above, wherein each transmission device is equipped with a clutch box on its input side.

[0056] The third aspect of this application discloses a multiplier transmission system, namely ARC-KEMEDESII in the embodiments of this application, which includes the reduction transmission system as described above, and further includes a compound gear multiplier transmission device connected to the output of the reduction transmission system. Attached Figure Description

[0057] Figure 1A This is a typical side view of a steam engine, with the combustion 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.

[0058] Figure 1B yes Figure 1A Axonometric drawing.

[0059] Figure 2A This is a side view of a steam engine with a crank mechanism that converts the oscillating motion of the top beam into rotational power. This crank mechanism was incorporated into the Newcomb steam engine and was patented by James Picard.

[0060] Figure 2B yes Figure 2A Axonometric drawing.

[0061] Figure 3AIt was a steam engine designed by James Watt, which converted a oscillating beam into rotary motion, with a sun and planetary gear mechanism on the right side. This sun and planetary mechanism was a kind of avoidance... Figure 2A and Figure 2B The mechanism of James Picard's patented crank mechanism.

[0062] Figure 3B yes Figure 3A Axonometric drawing.

[0063] Figure 3C yes Figure 3A The front view shows the sun and planetary gear mechanism connected to the flywheel.

[0064] Figure 4A yes Figure 3A A close-up view of the solar and planetary structures at TDC (top dead center). The rotation is clockwise. 14 and 15 ).

[0065] Figure 4B This is a close-up view of the solar and planetary mechanism. The planetary gears are in the first stage of their orbital motion around the sun gear. The sun gear has rotated 180 degrees. The tangential contact point is... 20 .

[0066] Figure 4C This is a close-up view of the solar and planetary mechanism. The planetary gears are in the second stage of their orbital motion around the sun gear, at BDC (bottom dead center). The sun gear has rotated 360 degrees (1 revolution).

[0067] Figure 4D This is a close-up view of the solar and planetary mechanism. The planetary gears are in the third stage of their orbital motion around the sun gear. The sun gear has then rotated another 180 degrees.

[0068] Figure 4E This is a close-up view of the solar and planetary mechanism. The planetary gears are in the fourth stage of their orbital motion around the sun gear. They have returned to TDC (top dead center). For each revolution of the planetary gears along their orbit, the sun gear has rotated an additional 360 degrees, for a total of 2 revolutions.

[0069] Figure 4F Showing a front view of the solar and planetary structures. 21 and 22 This shows that the sun and planetary gears have no frontal support as a fulcrum.

[0070] Figure 4G It is a solar and planetary organization 17 First stage tangential contact point 20 The isometric view. This is also similar to the contact point in the third stage.

[0071] Figure 4H It is the Sun and Planets TDC 16 Contact point 23 Axonometric drawing.

[0072] Figure 5A It is the lever and fulcrum mechanism (of a children's seesaw) that balances 27 Side view at the time.

[0073] Figure 5B It is subjected to the force (f) on the left. 29 Causes counterclockwise torque rotation 30 of Figure 5A Side view of the lever mechanism in the image.

[0074] Figure 5C It is through endurance that balance is achieved. 27 The equal forces (f) on the left side. 29 And the force (f) on the right. 29 of Figure 5A Side view of the lever mechanism in the image.

[0075] Figure 5D It experiences a downward force (f) during counterclockwise rotation. 29 And an equal upward force (f) 29 A side view of the lever and fulcrum. This is the coupling effect (-2t). Negative numbers indicate counterclockwise rotation.

[0076] Figure 5E It experiences a downward force (f) from the left. 29 And twice the force on the right (2f) 34 A side view of the lever and fulcrum. The center of gravity shifts to the right. 26 However, the leverage remains balanced. 27 .

[0077] Figure 5F It shows a small force of 245N. 37 Balance a much larger force of 2450N 38 A side view of the lever and fulcrum with a 10x probability. This is achieved through a much larger mass. 38 Between the fulcrum and the smaller force from the fulcrum. 37 This is achieved by having a length ratio of 1:10 between them.

[0078] Figure 6A This is a side view showing a tree branch as a crowbar / Type 1 lever. Force. 39 and reaction force 40 In the opposite direction 41 move.

[0079] Figure 6B This is a side view showing a tree branch as a fishing rod / type 3 lever. Force. 39and reaction force 40 Along the same direction 43 move.

[0080] Figure 6C This is a side view showing a wheelbarrow as a type 2 lever. Force 39 and reaction force 40 Along the same direction 43 Movement. Force. 39 The length between the fulcrum and the reaction force is much greater than the reaction force. 40 The length between the fulcrum and the load. A large box of lifting arrows indicates the load acting on it. 45 The reaction force on 40 .

[0081] Figure 7A This shows the action on the lever (connecting rod journal). 47b The force (of combustion) 47a This results in torque at the crankshaft 47c piston engine 48 Side view.

[0082] Figure 7B This illustrates the action on the lever (turbine blade). 47b The force (steam) 47a This results in torque at the turbine shaft. 47c steam turbine 49 Side view.

[0083] Figure 7C This illustrates the action on the lever (blade). 47b The force (wind) 49a This results in torque at the blade shaft. 47c wind turbine 50 Side view.

[0084] Figure 7D This illustrates the action on the lever (stator). 47b The force (electromotive force) 47a This leads to problems on the stator shaft. 47c Electric motor with torque at the point 51 The front view and side view.

[0085] Figure 8A The gear shown is essentially a lever (rotating lever) 52 The fact that... Figure 5A The basic levers (a), (b) to (c), and finally to (d) (gear).

[0086] Figure 8B This is a side view showing two ((a) and (b)) or more gears 53, referred to as a gear train. 56 .

[0087] Figure 8C This shows the gear system. 56 Dynamics of the movement.

[0088] Figure 8D This shows the gear system. 65 The rotational dynamics. A freewheeling gear 64 is required so that the driving gear 53(b) moves in the same direction as the driven gear 53(a). 57 Rotation. This mechanism is described in the third embodiment of the invention, ARC-EPTPGDT 3. 68-2T [C]) is the foundation.

[0089] Figure 9 These are front views (a) of the continuously variable transmission chain drive device 68-1, and isometric views (b), (c) and (d) of the continuously variable transmission planetary gear drive device 68-2.

[0090] Figure 10A It is a continuously variable power transmission planetary gear transmission device. 68-2T [A] Rear axonometric view, in which the external structures of the sides, top, and bottom are hidden for clarity.

[0091] Figure 10B It is a continuously variable power transmission planetary gear transmission device. 68-2T [A] Rear axonometric view, in which the external and internal support structures are hidden for clarity.

[0092] Figure 10C It is a continuously variable power transmission planetary gear transmission device. 68-2T [A] is a right view in which the external support structure is hidden.

[0093] Figure 10D It is a continuously variable power transmission planetary gear transmission device. 68-2T [A] is a top view in which the external support structure is hidden.

[0094] Figure 11A This is a rear axonometric view of the internal support structure 69-75. For clarity, all other components are hidden.

[0095] Figure 11B This is a left view of the internal support structure 69-75. For clarity, all other components are hidden.

[0096] Figure 11C This is a right view of the internal support structure 69-75. For clarity, all other components are hidden.

[0097] Figure 11DThis is a top view of the internal support structure 69-75. For clarity, all other components are hidden.

[0098] Figure 11E This is a bottom view of the internal support structure (69-75). For clarity, all other components are hidden.

[0099] Figure 11F This is a rear view of the internal support structure 69.

[0100] Figure 11G This is the front view of the internal support structure 75.

[0101] Figure 12A This is a rear axonometric view of the internal support structure 69-75, which is used for rotation and serves as a support for a fulcrum bearing located in a machined opening. For clarity, all other components are hidden.

[0102] Figure 12B This is a rear axonometric drawing of all the locations used for rotation and as supports for the pivot bearings. For clarity, the external support structure, internal support structure, and other components are hidden.

[0103] Figure 12C This is a rear axle view showing the positions of all planetary gear carriers that rotate and serve as pivot bearings. For clarity, all other components are hidden.

[0104] Figure 13A This is a rear axonometric drawing showing the positions of the main input shaft and the two auxiliary input shafts, as well as their respective uses for rotation and support as pivot bearings. For clarity, all other components are hidden.

[0105] Figure 13B This is a right view of the main input axis and two sub-input axes located within the internal structure. All other components are hidden.

[0106] Figure 13C This is a top view of the main input shaft 83 and two secondary input shafts 84 located within the internal structure 69-75. All other components are hidden from view.

[0107] Figure 13D This is a rear axle view of the main input shaft 83, the two auxiliary input shafts 84, and their respective continuously variable transmission chain drive units 68-1. For clarity, all other components are hidden.

[0108] Figure 13E This is a right view of the main input shaft 83 and two auxiliary input shafts 84, along with their respective continuously variable transmission chain drive units 68-1, housed within the internal support structure 69-75. All other components are concealed.

[0109] Figure 13F This is a bottom view of the main input shaft 83 and two auxiliary input shafts 84, each with its own continuously variable transmission chain drive 68-1, housed within the internal support structure. All other components are hidden from view.

[0110] Figure 14A This is a rear axonometric view of the main output shaft 85 and four auxiliary output shafts 86, as well as their respective supports for rotation and fulcrum bearings. Only the internal structure 75 is shown. All other components are hidden.

[0111] Figure 14B This is a right view of the main output shaft 85 and four auxiliary output shafts 86 housed within the internal support structure 69-75. For clarity, all other components are concealed.

[0112] Figure 14C This is a top view of the main output shaft 85 and four auxiliary output shafts 86 housed within the internal support structure 69-75. For clarity, all other components are concealed.

[0113] Figure 14D The rear axle view shows the main output shaft 85 connected to four auxiliary output shafts 86 via a corresponding continuously variable transmission chain drive device 68-1. For clarity, all other components are hidden.

[0114] Figure 14E The right view shows the main output shaft 85, located within the internal support structure 69-75, connected to each of the four auxiliary output shafts 86 via a corresponding continuously variable transmission chain drive device 68-1. For clarity, all other components are concealed.

[0115] Figure 14F This is a top view of the main output shaft 85, located within the internal support structure 69-75, connected to each of the four auxiliary output shafts 86 via a corresponding continuously variable transmission chain drive device 68-1. For clarity, all other components are concealed.

[0116] Figure 15 yes Figure 13B and Figure 14B The right view of the combination shows a continuously variable power transmission planetary gear transmission device. 68- 2T The dynamics of power transmission in [A]. For clarity, all other components are hidden.

[0117] Figure 16A It is the input power transmission and transfer chamber 88 The rear axle view. For clarity, all other components are hidden.

[0118] Figure 16B It is the input power transmission and transfer chamber 88 The right view. For clarity, all other parts are hidden.

[0119] Figure 16C It is the input power transmission and transfer chamber 88 A top view. For clarity, all other components are hidden.

[0120] Figure 17A It is the output power transmission conversion chamber 89 The rear axle view. All other components are hidden.

[0121] Figure 17B It is the output power transmission conversion chamber 89 The right view. For clarity, all other parts are hidden.

[0122] Figure 17C It is the output power transmission conversion chamber located within the internal structure 69-75. 89 A bottom view (right rear, left rear, right front, and left front). All other parts are hidden.

[0123] Figure 18 This shows the output power transmission conversion chambers of the right front continuously variable transmission (CVT) chain drive and the left front CVT chain drive, positioned relative to the four auxiliary output shafts 86 and two auxiliary input shafts 84. 89 The rear axle view is shown. The bearings 78-1, 78-2, 78-3, and 78-4 of the four auxiliary output shafts 86 planetary gear carriers are also shown. For clarity, the right and left rear continuously variable transmission (CVT) chain drives are concealed.

[0124] Figure 19 This shows the right front planetary gear carrier hub 92-3 and the left front planetary gear carrier hub 92-4, as well as the output power transmission conversion chamber of each component. 89 The rear axle view. For clarity, the right rear planetary gear carrier hub 92-1, the left rear planetary gear carrier hub 92-2, and other components are concealed.

[0125] Figure 20 This shows the right rear planetary gear carrier hub 92-1 and the right front planetary gear carrier hub 92-3, as well as the output power transmission conversion chamber of various components. 89 The right view. For clarity, all other parts are hidden.

[0126] Figure 21This shows the planetary gear carrier hubs 92-1, 92-2, 92-3, and 92-4, as well as the output power transmission conversion chamber of various components. 89 A bottom view. For clarity, all other components are hidden.

[0127] Figure 22 This shows the output power transmission conversion chamber of the sun gears 93-1, 93-2, 93-3, and 93-4, as well as various components. 89 The rear axle view. For clarity, all other components are hidden.

[0128] Figure 23 This shows the output power transmission conversion chamber of the sun gears 93-1, 93-2, 93-3, and 93-4, as well as various components. 89 A bottom view. For clarity, all other components are hidden.

[0129] Figure 24 This shows the output power transmission conversion chamber of planetary gears 94-1, 94-2, 94-3, and 94-4, as well as various components. 89 The rear axle view. For clarity, all other components are hidden.

[0130] Figure 25 This shows the output power transmission conversion chamber of planetary gears 94-1, 94-2, 94-3, and 94-4, as well as various components. 89 A bottom view. For clarity, all other components are hidden.

[0131] Figure 26 This shows the output power transmission conversion chamber of connecting rod 97, pin 95-1 and pin 95-2, and various components. 89 The rear axle view. For clarity, all other components are hidden.

[0132] Figure 27 This shows the output power transmission conversion chamber of connecting rod 97, pin 95-1 and pin 95-2, and various components. 89 A bottom view. For clarity, all other components are hidden.

[0133] Figure 28 This shows the output power transmission conversion chamber of the connecting rod 97 and various components. 89 The rear axle view. For clarity, all other components are hidden.

[0134] Figure 29 This shows the output power transmission conversion chamber of the connecting rod 97 and various components. 89 A bottom view. For clarity, all other components are hidden.

[0135] Figure 30 This shows the output power transmission conversion chamber of connecting rod 97, pin 95, bearing 79 and bearing 80, and various other components. 89 The rear axle view. For clarity, all other components (including connecting rod 97) are hidden.

[0136] Figure 31 This shows the output power transmission conversion chamber of connecting rod 97, pin 95, bearing 79 and bearing 80, and various other components. 89 A bottom view. For clarity, all other components are hidden.

[0137] Figure 32 This shows the output power transmission conversion chamber of planetary gear carrier 96-4 and planetary gear carrier 96-1. 89 The rear axle view. For clarity, planetary gear carriers 96-2 and 96-3 are concealed, like the other components.

[0138] Figure 33 This shows the output power transmission conversion chamber of planetary gear carriers 96-2 and 96-3. 89 A top view. For clarity, planetary gear carriers 96-1 and 96-4, along with other components, are hidden.

[0139] Figure 34 This shows the second bearings 82-1, 82-2, and 82-3 of the planetary gear carrier, the first bearing 81-4 of the planetary gear carrier, and the output power transmission conversion chamber of various components. 89 The rear axle view. For clarity, all other components are hidden.

[0140] Figure 35 This shows the left rear planetary gear carrier 96-2, the right front planetary gear carrier 96-3, the second bearings of the planetary gear carrier 82-4 and 82-1, and the output power transmission conversion chamber of various components. 89 A bottom view. For clarity, all other components are hidden.

[0141] Figure 36 This is a rear axle view of the left front planetary gear carrier 96-4, the left front first bearing 81-4, and other components housed within the internal structure 73. For clarity, all other components are concealed.

[0142] Figure 37 Detail A shows the output power transmission conversion chamber of the driven sprocket 67b, which is securely bolted to the right rear planetary gear carrier 96-1. 89 The rear axle view. For clarity, all other components are hidden.

[0143] Figure 38 This shows the additional left rear continuously variable power transmission planetary gear drive unit 68-2 / 2 and left rear planetary gear carrier hub 92-2, right rear planetary gear carrier hub 92-1 and right front planetary gear carrier first bearing 81-3, as well as the output power transmission conversion chamber of various components. 89 The rear axle view. For clarity, all other components are hidden.

[0144] Figure 39 This shows the additional left rear planetary gear carrier first bearing 81-2, right front planetary gear carrier 96-3, and right front continuously variable power transmission planetary gear drive unit 68-2 / 3, as well as the output power transmission conversion chamber of various components. 89 The rear axle view. For clarity, all other components are hidden.

[0145] Figure 40 This shows the output power transmission conversion chamber of the additional right rear continuously variable power transmission planetary gear drive unit 68-2 / 1 and the first bearing 82-1 of the right rear planetary gear carrier. 89 The rear axle view. For clarity, all other components are hidden.

[0146] Figure 41 This shows the input power transmission chamber. 87 Input power transmission and transfer chamber 88 Output power transmission conversion chamber 89 And a rear axonometric view of the main output shaft 85. For clarity, all other components are hidden.

[0147] Figure 42 This shows the output power transmission chamber #1 ( 91 ) and #2 ( 90 The rear axle view. For clarity, all other components are hidden.

[0148] Figure 43 This is the first disclosure of how the innovative structure of this invention achieves a 1:2 speed ratio. It shows the right front upper input power transmission transfer chamber. 88 and left front upper input power transmission transfer chamber 88 and the lower output power transmission conversion chamber 89 The main view shows the components integrated in a carefully designed scheme, as shown in detail A, to achieve a specific speed ratio. For clarity, all other components are hidden.

[0149] Figure 44 This is the second disclosure of how the innovative structure of this invention achieves a torque ratio of 1 ≥ (equal to or greater than 1). It shows the right front upper input power transmission transfer chamber.88 and left front upper input power transmission transfer chamber 88 and the lower output power transmission conversion chamber 89 The front view shows the components integrated in a carefully designed scheme, as shown in details A and B, to achieve a specific torque ratio of 1 ≥ 1. The key type 2 lever effect is clearly illustrated in the figure. Figure 6C ), and coupling effect ( Figure 5D For clarity, all other components are hidden.

[0150] Figure 45 This is the original view of the 24-gear reduction gear designed by Christoph Gryenberg.

[0151] Figure 46 An 80-square chessboard is shown. This illustrates the concept of exponential growth. In this case, the amount of rice doubles each time a square is moved to the next. This demonstrates how quickly exponential growth can lead to enormous quantities. 2 80 It's an amazing 483,570,327,845,851,670 bags of rice.

[0152] Figure 47 An 80-square chessboard is shown on the number lines to illustrate the three phases of exponential increase and exponential decrease.

[0153] Figure 48A Showing connection to 80ARC-EPTPGDT 1 ( 68-2T [A]) Grünberg compound gear reducer, which can be used to traction the Earth in a timely manner.

[0154] Figure 48B The diagram shows the connection to the 2nd ARC-EPTPGDT 1, an integrated gear multi-stage transmission device connected to the 3rd ARC-EPTPGDT 1. 68-2T [A]) Any configuration of a geared transmission connected by 1 can meet a wide range of specific power applications. The combination of numbers 1 and 2 is called ARC-KEMEDES I, and numbers 1, 2, and 3 are called ARC-KEMEDES II.

[0155] Figure 49 This is the second embodiment of the present invention, ARC-EPTPGDT 2. 68-2T [B]. The second embodiment of the invention comprises only a single main input shaft 83, a single main output shaft 85 (without a secondary shaft), a driven shaft 123, and only three internal structures 118, 119, and 120. For clarity, the side, top, and bottom structures, as well as all other components, are concealed.

[0156] Figure 50 It is a continuously variable power transmission planetary gear drive (ARC-EPTGDT 2).68-2T [B] Rear axle view. For clarity, the front structure 118 and other components are hidden.

[0157] Figure 51 It is ARC-EPTGDT 2 ( 68-2T [B]) Rear axonometric view. For clarity, all internal structures and other parts are hidden. Output shaft 85 is now visible.

[0158] Figure 52 It is ARC-EPTGDT 2 ( 68-2T [B]) Right view. For clarity, some parts are not mentioned.

[0159] Figure 53 It is ARC-EPTGDT 2 ( 68-2T [B]) Top view. For clarity, all other parts are hidden.

[0160] Figure 54 It is ARC-EPTPGDT 2 ( 68-2T [B]) Rear axle view. Showing 1, the input power transmission transfer chamber with its single main input shaft 83 and continuously variable power transmission planetary gear drive 68-2. 88 , and 2, an output power transmission conversion chamber having its single main output shaft 85 and its respective sun gear 93 and bearing 78 housed in the planetary gear carrier hub 92. 89 For clarity, all other components are hidden from the view.

[0161] Figure 55 This is a rear axle view showing additional components (e.g., connecting rod pin 95-1 and its rigidly attached planetary gear 94 meshing with the sun gear 93). All corresponding supports for pivot bearings 79 and 80 are also shown. Internal support structure 120 is also shown. However, for clarity, all other components are concealed.

[0162] Figure 56 This is a rear axle view showing the planetary gear carrier 96 and the driven sprockets of 68-2 securely bolted to the gear carrier 96-3. For clarity, some parts are not mentioned, and all other parts are hidden.

[0163] Figure 57 This is a rear axonometric view of the connecting rod 97, which has its left-side pin 95-2 and corresponding supports for the pins of pivot bearings 79-2 and 79-4. For clarity, some parts are not mentioned, and all other parts are hidden.

[0164] Figure 58This is a rear axle view showing the planetary gear carrier followers 121-1, 121-2, and 121-3 located at the ends of pins 95-1 and 95-2 on their respective connecting rods 97. These components are located in the output power transmission conversion chamber. 89 In the middle. To make it clear, all other parts are hidden.

[0165] Figure 59 This is a rear axle view showing: 1. the right rear planetary gear carrier follower hub 122-1 and the support for the right rear planetary gear carrier follower 121-1, which rotates and acts as a pivot bearing 82-1 (detail B); 2. the left front planetary gear carrier follower hub 122-3 and its corresponding planetary gear carrier follower 121-3; and 3. the left rear planetary gear carrier follower 121-2 and its corresponding planetary gear carrier follower hub 122-2. Detail A shows the support for rotation, which acts as a pivot bearing 82-4 and a pivot bearing 78, and the connecting rod pin 95-2. For clarity, some components are not mentioned, and all other components are hidden.

[0166] Figure 60 This is a top view showing the first internal support structure 118 and the third internal support structure 120, the input shaft 83, and the output shaft 85. In this figure, a single right front planetary gear carrier hub 82-3, having its corresponding planetary gear carrier 96-3 (part of the continuously variable power transmission planetary gear drive 68-2 / 3), is securely bolted to the third support structure 120, as is the left front planetary gear carrier follower hub 122-3 with its corresponding planetary gear carrier follower 121-3. The right rear planetary gear carrier follower hub 122-1 and the left rear planetary gear carrier follower hub 122-2, having their corresponding planetary gear carrier followers 121-1 and 121-2, are securely bolted to the first support structure 118. For clarity, some components are not mentioned, and all other components are hidden.

[0167] Figure 61 This is a complete supplementary rear axle view showing the continuously variable transmission (CVT) chain drive units 68-1 / 1, 68-1 / 2, 68-1 / 3, 68-1 / 4, and 68-1 / 5, and also includes a single right front CVT gear drive unit 68-2 / 3 and its support for rotation and as the first fulcrum bearing 81-3. For clarity, some components are not mentioned, and all other components are hidden.

[0168] Figure 62This is a top view showing all the additions to the continuously variable transmission (CVT) chain drive units 68-1 / 1, 68-1 / 2, 68-1 / 3, 68-1 / 4, and 68-1 / 5, and also includes a single CVT planetary gear drive unit 68-2 / 3 and its support for rotation and as the first fulcrum bearing 81-3. For clarity, some components are not mentioned, and all other components are hidden.

[0169] Figure label:

[0170] XX =The underlined reference numerals indicate:

[0171] (a) Process, for example, force 39 The direction;

[0172] (b) Names of locations in the diagram, for example, conversion chambers. 89 ;

[0173] (c) Other entities besides this invention, such as piston engines. 48 .

[0174] XX = Ununderlined reference numerals indicate component reference numerals.

[0175] 1-The main structure of a steam engine used to pump water out of a flooded coal mine.

[0176] 2- Steam oven.

[0177] 3- Piston and connecting rod of a steam engine.

[0178] 4-The main swing arm of the steam engine.

[0179] 5. Connect the connecting rod to the water pump piston of the steam engine.

[0180] 6- A water pump with a steam engine having a pipe leading downwards to a flooded mine shaft.

[0181] 7- The crankshaft of the Newcomen steam engine.

[0182] 8- The flywheel shaft of the Newcomen steam engine.

[0183] 9a - Flywheel of the Newcomb steam engine.

[0184] 9b - The flywheel of Watt's steam engine.

[0185] Planetary gears of a 10-watt steam engine.

[0186] 11-The sun gear of Watt's steam engine.

[0187] 12 - Sun gear shaft to the flywheel of Watt's steam engine.

[0188] 13a - The tie rod of Watt's steam engine.

[0189] 13b - The connecting rod and planetary gear pin sleeve of the Watt steam engine.

[0190] Sun gear and flywheel shaft bushing of the 13c Watt steam engine.

[0191] 14 - The planetary gears of Watt's steam engine rotate clockwise.

[0192] 15 - The sun gear of Watt's steam engine rotates clockwise.

[0193] 16 - Watt's steam engine's sun and planetary gears' TDC (Top Dead Center).

[0194] 17 - The first quarter of the planetary gear's orbit around the sun gear.

[0195] 18 - Watt's steam engine's sun and planetary gears' BDC (Bottom Dead Center).

[0196] 19 - The third quarter of the orbit of the planetary gears of Watt's steam engine around the sun gear.

[0197] 20 - The tangential contact point between the sun and the planetary gears.

[0198] 21 - There is no front support for the connecting rod and planetary gear pins.

[0199] 22 - There is no front support for the sun gear shaft.

[0200] 23 - Vertical force at TDC (top dead center).

[0201] 24 - The fulcrum of the lever.

[0202] 25-Leverage.

[0203] 26 - The center of gravity of the lever.

[0204] 27 - The balance state of the lever.

[0205] 28 - Center of gravity on the lever 26 to the force 29 The distance.

[0206] 29 - Force (f).

[0207] 30 - A counterclockwise torque is applied to the lever mechanism.

[0208] 31 - Coupling effect on lever mechanism.

[0209] 32 - The force acting on the lever 29 to center of gravity 26 The largest radius (r).

[0210] 33 - The force acting on the lever 29 to center of gravity 26 The smaller radius (r / 2).

[0211] 34 - Twice the force (f) (2f).

[0212] 35 -exist 26 From the position of the fulcrum to the force 37 The distance.

[0213] 36 -exist 26 From the position of the fulcrum to the force 38 The distance.

[0214] 37 - Force applied: 245 N.

[0215] 38 - Force applied: 2450 N.

[0216] 39 - The force applied at one end of a type 1 lever.

[0217] 40 - The reaction force at the other end of the first type of lever.

[0218] 41 -Force 39 and reaction force 40 Move in the opposite direction.

[0219] 42 -Tree branches as levers / Class 1 levers.

[0220] 43 -Force 39 and reaction force 40 Move in the same direction.

[0221] 44-Tree branches as fishing rods / Class 3 levers.

[0222] 45 - A box of arrows as a reaction force 40 .

[0223] 46 - The wheelbarrow is a type of lever.

[0224] 47a - Force.

[0225] 47b - The force acts on the lever.

[0226] 47c - The force acts on the lever, generating torque.

[0227] 48 - This shows a piston engine acting as a lever.

[0228] 49 - This shows a steam turbine acting as a lever.

[0229] 50 - This shows a wind turbine acting as a lever.

[0230] 51 - This shows an electric motor acting as a lever.

[0231] 52 - Shows a single lever that has been transformed into a rotating lever.

[0232] Figure 53 shows two gears, (a) the driven gear and (b) the driving gear.

[0233] 54 - Input axis.

[0234] 55 - Output shaft.

[0235] 56 Two or more meshing gears are called a gear system.

[0236] 57 - Drive gear 53(b) to rotate clockwise.

[0237] 58 - The driven gear 53(a) rotates counterclockwise.

[0238] 59 - The torque (at) applied at the input shaft of the drive gear (b).

[0239] 60 - The reaction torque (rt) at the tangential contact point of the drive gear (b).

[0240] 61- Tangential contact point.

[0241] 62 - The torque (at) applied at the tangential contact point on the driven gear (a).

[0242] 63 - The reaction torque (rt) on the output shaft of the driven gear (a).

[0243] 64 - Idle gear.

[0244] 65 - A gear train with a freewheeling gear. This mechanism is based on the third embodiment of the present invention, ARC-EPTPGDT 3 (68-2T[C]).

[0245] 66-Chain.

[0246] 67a - Drive sprocket.

[0247] 67b - Driven sprocket.

[0248] 68-1-Continuously Variable Power Transmission Chain Drive (EPTCD). Part Numbers: 68-1 / 1, 68-1 / 2, 68-1 / 3, 68-1 / 4, 68-1 / 5 and 68-1 / 6.

[0249] 68-2 - Continuously Variable Power Transmission Planetary Gear Drive (EPTPGD). Part Numbers: 68-2 / 1, 68-2 / 2, 68-2 / 3, and 68-2 / 4.

[0250] 68-2 / T[A] -ARC-EPTPGDT 1. The first embodiment of the present invention is a continuously variable power transmission planetary gear transmission device called ARC-EPTPGDT 1.

[0251] 68-2 / T[B] -ARC-EPTPGDT 2. A second embodiment of the present invention is a continuously variable power transmission planetary gear transmission device called ARC-EPTPGDT 2.

[0252] 68-2T[C] -ARC-EPTPGDT 3. The third embodiment of the present invention is called ARC-EPTPGDT 3.

[0253] 68-3 -ARC-KEMEDES I. A multi-stage drive system consisting of two or more different combinations of ARC-EPTPGDT 1, ARC-EPTPGDT 2, or ARC-EPTPGDT 3 is called ARC-KEMEDES I.

[0254] 68-4-ARC-KEMEDES II. The ARC-KEMEDES II system integrates a compound gear multiplier drive into the ARC-KEMEDES I system.

[0255] 69-75 - Internal support structures from the 1st to the 7th. 69-1, 70-2, 71-3, 72-4, 73-5, 74-6, 75-7.

[0256] 76-1- Main input shaft support for rotation and as a fulcrum bearing (2 in total).

[0257] 76-2 - Main output shaft support for rotation and as a fulcrum bearing (7 in total).

[0258] 77-1-Right auxiliary input shaft support for rotation and as a fulcrum bearing (12 in total).

[0259] 77-2- Left auxiliary input shaft support for rotation and as a fulcrum bearing (12 in total).

[0260] 77-3- Right / Right Rear Auxiliary Output Shaft Supports (4 in total) for rotation and as fulcrum bearings.

[0261] 77-4 - Left / left rear auxiliary output shaft supports for rotation and as fulcrum bearings (4 in total).

[0262] 77-5 - Right-side / right front auxiliary output shaft support for rotation and as a fulcrum bearing (4 in total).

[0263] 77-6 - Left / left front auxiliary output shaft supports for rotation and as fulcrum bearings (4 in total).

[0264] 78-1- Right / Right Rear Planetary Gear Carrier Output Shaft Support for Rotation and as a Pivot Bearing (1 in total).

[0265] 78-2- Left / left rear planetary gear carrier output shaft support for rotation and as a fulcrum bearing (1 in total).

[0266] 78-3- Right / Right Front Planetary Gear Carrier Output Shaft Support for Rotation and as a Pivot Bearing (1 in total).

[0267] 78-4 - Left / left front planetary gear carrier auxiliary output shaft (1 in total) for rotation and as a fulcrum bearing.

[0268] 79-1- Right rear first connecting rod support for pivot bearing.

[0269] 79-2- Support for the left rear second connecting rod of the pivot bearing.

[0270] 79-3- Right front first connecting rod support for pivot bearing.

[0271] 79-4- Support for the left front first connecting rod of the pivot bearing.

[0272] 80-1- Right rear second connecting rod support for pivot bearing.

[0273] 80-2- Support for the second rear connecting rod of the pivot bearing.

[0274] 80-3- Right front second connecting rod support for pivot bearing.

[0275] 80-4 - Support for the left front second connecting rod of the pivot bearing.

[0276] 81-1-Right rear first planetary gear carrier support for rotary / pivot bearings.

[0277] 81-2- Support for the left rear first planetary gear carrier for rotation and as a fulcrum bearing.

[0278] 81-3-Right front first planetary gear carrier support for rotary / pivot bearings.

[0279] 81-4- Left front first planetary gear carrier support for rotary / pivot bearings.

[0280] 82-1-Right rear second planetary gear carrier support for rotary / pivot bearings.

[0281] 82-2- Left rear second planetary gear carrier support for rotary / pivot bearings.

[0282] 82-3-Right front second planetary gear carrier support for rotary / pivot bearings.

[0283] 82-4- Left front second planetary gear carrier support for rotary / pivot bearings.

[0284] 83 - Main input axis 83.

[0285] 84-1-Right side of the secondary input shaft.

[0286] 84-2-Left side of the secondary input shaft.

[0287] 85 - Main output shaft.

[0288] 86-1-Right rear auxiliary output shaft.

[0289] 86-2-Left rear auxiliary output shaft.

[0290] 86-3-Right front auxiliary output shaft.

[0291] 86-4-Left front auxiliary output shaft.

[0292] 87 - Input power transmission chamber.

[0293] 88 - Input power transmission transfer chamber.

[0294] 89 - Output power transmission conversion chamber.

[0295] 90 - Output power transmission chamber #2.

[0296] 91 - Output power transmission chamber #1.

[0297] 92-1-Right rear planetary gear carrier hub.

[0298] 92-2-Left rear planetary gear carrier hub.

[0299] 92-3-Right front planetary gear carrier hub.

[0300] 92-4-Left front planetary gear carrier hub.

[0301] 93-1-Right rear sun gear.

[0302] 93-2-Left rear sun gear.

[0303] 93-3-Right front sun gear.

[0304] 93-4-Left front sun gear.

[0305] 94-1--Right rear planetary gear.

[0306] 94-2-Left rear planetary gear.

[0307] 94-3-Right front planetary gear.

[0308] 94-4-Left front planetary gear.

[0309] 95-1-Right side connecting rod pin.

[0310] 95-2-Left connecting rod pin.

[0311] 96-1-Right rear planetary gear carrier.

[0312] 96-2-Left rear planetary gear carrier.

[0313] 96-3-Right front planetary gear carrier.

[0314] 96-4-Left front planetary gear carrier.

[0315] 97-Connecting rod.

[0316] 98 - Gradually increasing.

[0317] 99 - Explosive growth.

[0318] 100 -Astronomical growth.

[0319] 101 - Gradually decrease.

[0320] 102 - Explosive reduction.

[0321] 103 - An astronomical reduction.

[0322] 104 - A schematic illustration of a Grienberger Compound-Gear Reduction Transmission (GGRT) powered by a treadmill.

[0323] 105 - The starting point of the curve for the synthetic speed (rs) of the GGRT treadmill at 667 revolutions per minute, calculated by Gryenberger.

[0324] 106 - The starting point of the curve for the combined speed (rs) of the GGRT treadmill. Grignberg does not provide the calculation.

[0325] 107 -After calculating the astronomical reduction of the treadmill by 1 revolution every 100 trillion years, the curve for the synthetic velocity rs ends.

[0326] 108 -Calculated by Mr. Grignberg, the astronomical growth (rt) × 2 80 The endpoint of the curve is the reaction torque (rt) that is sufficient to pull the Earth.

[0327] 109 -Schematic illustration of their respective clutch mechanisms 109a A series connection of 80 continuously variable power transmission planetary gears (ARC-EPTPGDT 1) 68-2T[A]. This multi-stage ARC-EPTPGDT 1 (68-2T[A]) system will be referred to as the kinetic energy multi-stage drive En series (ARC-KEMEDES I). 68-3 .

[0328] 109a - Clutch mechanism.

[0329] 110 -in the curve 107The final velocity is transmitted to the first clutch of the ARC-KEMEDES I system, ARC-EPTPGDT I, as the operating velocity (as) and is increased by 2. 80 Times (1 revolution per 100 trillion years × 2) 80 See below. 112 .

[0330] 111 -in the curve 108 The reaction torque at the endpoint is transmitted to the first clutch of the ARC-KEMEDES I system, ARC-EPTPGDT 1, as the operating torque (at) and multiplied by a factor of 1≥. See below. 113 .

[0331] 112 The final output speed at the 80th ARC-EPTPGDT 1 of the -ARC-KEMEDES I multistage system (1 revolution × 2 per 100 trillion years) 80 =677 revolutions per minute). This is the original output speed of the pedal wheel: 677 revolutions per minute. 105 A timely approach has already been implemented.

[0332] 113 The final output torque at the 80th ARC-EPTPGDT 1 of the -ARC-KEMEDES I multi-stage system, (((at)×2) 80 ()×1≥)=Calculate to pull the Earth).

[0333] 114 The ARC-KEMEDES I multistage system adds four more ARC-EPTPGDT 1 modules (totaling 84), increasing the speed from 667 RPM to 10672 RPM (667 RPM x 2). 4 =10,672 RPM).

[0334] 115 With the integration of one or more compound gear multiplier drives (CGMT), ARC-KEMEDES I is now referred to as ARC-KEMEDES II.

[0335] 115a - Integrated 4-gear 1:2 multiplier mechanism (CGMT). Each gear multiplier has its own clutch 9a on the input side. Torque is reduced by 24 times, and speed is increased by 2. 4 Multiples. The opposite relationship.

[0336] 116 - At that time, due to 115a, the torque is at a coefficient of 2 4 The torque is reduced by a factor of 2. 80))×1≥) / 24= is still a staggering torque.

[0337] 117 -as 115a As a result, the speed is 2 4 The speed increases by a factor of 2, ((as)×2) 84 )×2 4 =170752 RPM).

[0338] The first internal structure of 118-ARC-EPTPGDT 2.

[0339] The second internal structure of 119-ARC-EPTPGDT 2.

[0340] The third internal structure of 120-ARC-EPTPGDT 2.

[0341] 121-1-Right rear planetary gear carrier follower.

[0342] 121-2-Left rear planetary gear carrier follower.

[0343] 121-3-Left front planetary gear carrier follower.

[0344] 122-1-Right rear planetary gear carrier follower hub.

[0345] 122-2-Left rear planetary gear carrier follower hub.

[0346] 122-3-Left front planetary gear carrier follower hub.

[0347] 123-Driven Shaft Detailed Implementation

[0348] The foregoing background art of the present invention provides 33 figures ( Figures 1A-9 Extensive visual guidance provided a clear and detailed insight into the machinery, which helped establish our innovative continuously variable power transmission planetary gear drive. 68-2T The science of the assembly and operation mode of [A]. In the detailed description of the embodiments of the present invention, by referring to the 79 figures in the accompanying drawings (Figures 10- ) Figure 62 This will make it easy to understand the complex component-by-component assembly in the embodiments of the present invention, the pivoting joints during the assembly process, and the ingenious structure by which the embodiments of the present invention achieve a synchronous speed transmission ratio of 1:2 and a torque transmission ratio of 1:1 or higher. Furthermore, two other embodiments are shown to demonstrate the design flexibility of the present invention, providing different assembly methods suitable for different applications.

[0349] Based on the deficiencies identified in the prior art, see [link to relevant documentation]. Figure 11A , Figure 11B, Figure 11C , Figure 11D , Figure 11E , Figure 11F and Figure 11G The present embodiments of the invention address these deficiencies by incorporating a sufficient number of support structures for the various mechanisms used in the embodiments of the invention. Figure 11A This is an isometric view of the rear of this embodiment, showing the first (rear) support structure 69, the second support structure 70, the third support structure 71, the fourth support structure 72, the fifth support structure 73, the sixth support structure 74, and the seventh (front) support structure 75. Figure 11B It is the left view. Figure 11C It is the right view. Figure 11D It is a top view. Figure 11E It is a bottom view. Figure 11F It is a diagram of the rear structure, and Figure 11G This is a front structure diagram. Not shown are: 1. Right and left side panels, 2. Bottom panel, and 3. Top panel. Each support structure has various machined openings to accommodate rotation and serve as a fulcrum; different bearings are used to hold the continuously variable power transmission planetary gear drive. 68-2T For all institutions in [A], see [A] Figure 12A , 12B And 12C.

[0350] From this point onward, speed and torque will be referred to as power. (Power = Speed ​​and Torque)

[0351] Figure 13A This is a rear axonometric view showing the main input shaft 83 and its two secondary input shafts (right secondary input shaft 84-1 and left secondary input shaft 84-2). The main input shaft 83 is positioned between the first support structure 69 and the second support structure 70. See also... Figure 13B The right-side secondary input shaft 84-1 and the left-side secondary input shaft 84-2 are positioned between the first support structure 69 and the sixth support structure 74. For illustrative purposes, all other parts are concealed.

[0352] Figure 13B This is the right view. The right sub-axis 84-1 and the left sub-axis 84-2 are both on the same plane; therefore, only the right sub-input axis 84-1 is visible. For illustrative purposes, all other components are hidden.

[0353] Figure 13C It is a top view that clearly shows the right sub-input shaft 84-1, the left sub-input shaft 84-2, and the main input shaft 83.

[0354] Figure 13DThis is an isometric drawing, clearly showing the function of the continuously variable transmission (CVT) chain drive mechanism on the right side (68-1 / 1) and left side (68-1 / 2) in distributing power from the autonomous input shaft 83 to the two auxiliary input shafts (right side 84-1 and left side 84-2). The driving sprocket 67a is rigidly attached to the main input shaft 83, and the driven sprocket 67b is rigidly attached to the auxiliary input shafts. The driving and driven sprockets 67a and 67b are identical in diameter and tooth structure, ensuring a synchronized 1:1 speed ratio and a 1:1 torque ratio.

[0355] Figure 13E This is a right view showing the right continuously variable power transmission chain drive device 68-1 / 1 and the left continuously variable power transmission chain drive device 68-1 / 2 disposed between the first support structure 69 and the second support structure 70.

[0356] Figure 13F This is a bottom view showing the right continuously variable power transmission chain drive device 68-1 / 1 and the left continuously variable power transmission chain drive device 68-1 / 2 disposed between the first support structure 69 and the second support structure 70.

[0357] Figure 14A It is an axonometric drawing. Figure 14B It is the right view. Figure 14C These are top views. They are three perspective views revealing the innovative arrangement of the four secondary output shafts 86-1, 86-2, 86-3, and 86-4 of this invention. These four secondary output shafts 86-1, 86-2, 86-3, and 86-4 are arranged in pairs: left rear secondary output shaft 86-2, left front secondary output shaft 86-4, right rear secondary output shaft 86-1, and right front secondary output shaft 86-3. The pair of left rear secondary output shafts 86-2 and left front secondary output shafts 86-4 are coaxial, and their parallel counterparts on their right sides, the pair of right rear secondary output shafts 86-1 and right front secondary output shafts 86-3, are also coaxial. See also... Figure 14B and Figure 14C These secondary output shafts 86-1, 86-2, 86-3 and 86-4 are arranged between the second support structure 70 and the fourth support structure 72 and the fifth support structure 73 and the seventh support structure 75.

[0358] These four secondary shafts 86-1, 86-2, 86-3, and 86-4 seamlessly guide power to the main output shaft 85, which is located between the second support structure 70 and the seventh support structure 75, via continuously variable power transmission chain drive devices 68-1 / 3, 68-1 / 4, 68-1 / 5, and 68-1 / 6, respectively. (See also...) Figure 14D , 14E 14F.

[0359] like Figure 12A and Figure 12B As shown, these shafts are supported by bearings 76-1, 76-2, 77-1, 77-2, 77-3, 77-4, 77-5 and 77-6 for rotation and as fulcrums, which are located at the points where each shaft intersects with the first support structure 69 to the seventh support structure 75.

[0360] Figure 15 yes Figure 13B and Figure 14B The combined right view. Power is applied to the main input shaft 83, and then distributed to the secondary input shafts 84-1 and 84-2. 87 At the ends of each secondary input shaft 84-1 and 84-2, between the third support structure 71 and the sixth support structure 74, is the input power transmission transfer chamber. 88 At this location 88 Each chamber transmits power to its corresponding output power transmission conversion chamber. 89 After conversion, the converted power (speed × 2 / torque × 1 ≥) is distributed to all four auxiliary output shafts 86-1, 86-2, 86-3, and 86-4, and then concentrated to the main output shaft 85. Input power transmission chamber. 87 and output power transmission chamber #1 91 and #2 90 The details are explained below.

[0361] The input power transmission and transfer chamber will now be explained. 88 and output power transmission conversion chamber 89 It is precisely here that the complexity of the original structure of this invention seamlessly facilitates the key technological realization of a synchronous speed transmission ratio of 1:2 and a torque transmission ratio of 1:1≥.

[0362] Input power transmission transfer chamber 88 At the ends of each secondary input shaft 84-1 and 84-2, between the third support structure 71 and the fourth support structure 72 and the fifth support structure 73 and the sixth support structure 74, a dual coaxial continuously variable power transmission planetary gear drive device 68-2 / 1 and 68-2 / 3, 68-2 / 2 and 68-2 / 4 (see...) Figure 16A , Figure 16B and Figure 16C This facilitates the transmission of power to the output power transmission conversion chamber. 89 Located in the upper transfer chamber 88 The sprocket in the middle is the drive sprocket, while the one located in the lower conversion chamber is the drive sprocket. 89 The sprockets in the middle are driven sprockets. The driving sprocket and driven sprocket are identical in diameter and tooth structure, and are connected by a chain to ensure a synchronized 1:1 speed transmission ratio and a 1:1 torque transmission ratio. Specifically, located in the upper transfer chamber... 88The drive sprocket is rigidly attached to the secondary input shaft, and the chain is linked to the drive sprocket and the driven sprocket, thereby enabling power to be transferred from the upper chamber. 88 Passed to the lower conversion room 89 .

[0363] Output power transmission conversion chamber 89 : Figure 17A , Figure 17B and Figure 17C The output power transmission conversion chamber is shown in the lower portion between the third support structure 71 and the sixth support structure 74. 89 Also shown are all the supplements to the continuously variable transmission (CVT) chain drive units 68-1 / 1, 68-1 / 2, 68-1 / 3, 68-1 / 4, 68-1 / 5, 68-1 / 6 and the continuously variable transmission planetary gear drive units 68-2 / 1, 68-2 / 2, 68-2 / 3, and 68-2 / 4. The transmission conversion chamber will be constructed below. 89 The architecture.

[0364] See Figure 12C and Figure 18 In the output power transmission conversion chamber 89 At each end of all four secondary output shafts 86-1, 86-2, 86-3, and 86-4, output shaft planetary gear carrier bearings 78-1, 78-2, 78-3, and 78-4 are provided. See also Figure 19 , Figure 20 and Figure 21 Between the bearings 78-1 and 78-2 and the third support structure 71, and between the bearings 78-3 and 78-4 and the sixth support structure 74, each output shaft 86-1, 86-2, 86-3, and 86-4 is housed in a planetary gear carrier hub 92-1, 92-2, 92-3, and 92-4, which are securely bolted to their respective third support structures 71 and sixth support structures 74. For clarity, all other components are concealed.

[0365] The unique feature of our design is that the sun gears 93 (i.e., 93-1, 93-2, 93-3, and 93-4) are integrated onto all four secondary output shafts and rigidly attached between the corresponding front bearings 78-1, 78-2, 78-3, and 78-4 on each shaft and the planetary gear carrier hubs 92-1, 92-2, 92-3, and 92-4 (see [reference]). Figure 22 and Figure 23 See also Figure 24 and Figure 25 Sun gears 93-1, 93-2, 93-3, and 93-4 mesh with planetary gear 94, which has matching dimensions and tooth structure. See also Figure 26 and Figure 27 Each set of coaxial planetary gears 94-1 and 94-3 and their parallel counterparts 94-2 and 94-4 are rigidly connected to the ends of common connecting pins 95-1 and 95-2. See also... Figure 28 and Figure 29 These connecting pins 95-1 and 95-2 are rigidly connected to the end of connecting rod 97 and intersect the end of connecting rod 97 at a right angle. See also Figure 12C , Figure 30 and Figure 31 Bearings 79-1, 79-2, 79-3, 79-4 and 80-1, 80-2, 80-3, 80-4 are mounted at the ends of each connecting rod pin 95-1 and 95-2, on the front and rear of the planetary gear. These bearings support the pivoting movement of the connecting rod 97. For clarity, all other components are concealed.

[0366] See Figure 9 (c) Figure 9 (d) Figure 22 , Figure 23 , Figure 32 and Figure 33 These sun gears 93-1, 93-2, 93-3, 93-4 and planetary gears 94-1, 94-2, 94-3, 94-4, along with their respective bearings 79-1, 79-2, 79-3, 79-4 / 80-1, 80-2, 80-3, 80-4, and output shaft bearings 78-1, 78-2, 78-3, and 78-4, are all housed in planetary gear carriers 96-1, 96-2, 96-3, and 96-4. These planetary gear carriers are mounted on their respective planetary gear carrier hubs 92-1, 92-2, 92-3, and 92-4, while the rear second bearings 82-1, 82-2, 82-3, and 82-4, mounted on the surfaces of the planetary gear carrier hubs, and the front first bearings 81-1, 81-2, 81-3, and 81-4, mounted on the surfaces of their respective planetary gear carriers 96, are supported for rotation and serve as fulcrums (see [link]). Figure 12B , Figures 34 to 36 In this configuration, the first bearings 81-1, 81-2, 81-3, and 81-4 are supported by the fourth support structure 72 and the fifth support structure 73, while the second bearings 82-1, 82-2, 82-3, and 82-4 are supported by the planetary gear carrier hub. It should be understood that the first bearings 81-1, 81-2, 81-3, and 81-4, along with the second bearings 82-1, 82-2, 82-3, and 82-4, act as fulcrums and support the rotation of the planetary gear carriers 96-1, 96-2, 96-3, and 96-4. For clarity, the fourth support structure 72 is concealed.

[0367] See Figure 15 , Figure 16A , Figure 16B and Figure 16C Power is transmitted via continuously variable transmission (CVT) planetary gear drives 68-2 / 1, 68-2 / 2, 68-2 / 3, and 68-2 / 4 to their respective driven sprockets 67b, which are securely bolted to their respective planetary gear carriers 96 (see [link to CVT]). Figure 37 Details A), and these driven sprockets 67b have a connection with the input power transmission transfer chamber. 88 The drive sprockets on the secondary input shafts 84-1 and 84-2 have similar diameters and number of teeth.

[0368] Connecting pins 95-1 and 95-2, pivotally connected to their respective planetary gear carriers 96, are used to pivotally connect their respective planetary gear carriers 96 to their directly opposite counterparts 96-1 and 96-3, and 96-2 and 96-4. The length of the connecting rod 97 allows the two sets of planetary gear carriers to rotate uniformly and align with each other.

[0369] These planetary gear carriers 96-1, 96-2, 96-3, and 96-4, the first bearing 81 disposed in the fourth support structure 72 and the fifth support structure 73, the second bearing 82 of the planetary gear carrier disposed on their respective planetary gear carrier hubs 92, the planetary gear carrier hubs 92 which are themselves firmly bolted to the third support structure 71 and the sixth support structure 74, the bearings 79 and 80 on the connecting rod pins, and the output shaft 86 having the planetary gear carrier bearing 78, all serve as key fulcrums in the power conversion.

[0370] See Figure 38 , Figure 39 , Figure 40 , Figure 41 and Figure 42 Now, the output power transmission conversion chamber will be constructed. 89 Output Room #1 91 and #2 90 The remaining components.

[0371] Speed ​​conversion: See Figure 43Detail A. As the planetary gear carriers 96-1, 96-2, 96-3, and 96-4 rotate uniformly and align with each other, their respective planetary gears 94-1, 94-2, 94-3, and 94-4 are rigidly connected to the connecting rod pins 95-1 and 95-2, and thus to the connecting rod 97. Therefore, their respective planetary gears 94-1, 94-2, 94-3, and 94-4 are restricted and cannot rotate on their respective connecting rod pins 95-1 and 95-2. However, with the pivoting motion of connecting pins 95-1 and 95-2, planetary gears 94-1, 94-2, 94-3, and 94-4 are allowed to freely follow the planetary gear carriers 96-1, 96-2, 96-3, and 96-4 in orbital motion around their respective sun gears 93-1, 93-2, 93-3, and 93-4. This results in a situation where for every revolution of the planetary gears around the sun gear orbit, the sun gears 93-1, 93-2, 93-3, and 93-4 rotate twice. Therefore, the speed ratio is 1:2.

[0372] This process replicates the results achieved in the Watt-Murdoch solar and planetary mechanism in British Patent No. 1306 of 1786, see [link to patent]. Figure 14A , Figure 14B , Figure 14C , Figure 14D , Figure 14E , Figure 14F Figures 14G and 14H.

[0373] Torque conversion: Due to the presence of more than one planetary gear, the load is distributed among multiple planetary gears. This results in increased torque capacity and density, as well as increased load capacity. As mentioned above, Figure 8A , Figure 8B and Figure 8C Gears and sprockets are essentially rotating levers. Figure 44 In detail A, a hypothetical rod 25 of length x is shown, which extends from fulcrum 24 (located at the center of the sun gear 93 / output shaft 86) through planetary gear 94 to the periphery of the sprocket of the planetary gear carrier 96. Fulcrum 24 is the combination of all the components described in the preceding paragraph as "serving as a key fulcrum in power conversion." The torque acting at planetary gear 94... 39 -1 and reaction torque 40 Move in the same clockwise direction. Actual torque. 39 -1 The distance between the fulcrum 24 and the reaction torque is greater than the reaction torque. 40 The distance between the fulcrum and point 24. This operation is a common type 2 lever, as described previously with a wheelbarrow (…). Figure 6CIf the hypothetical lever 25 (length x) extends to the other side of the sprocket (length x+y), see [reference needed]. Figure 44 Detail A, Second Acting Torque 39 -2 To be realized and along with 39 -1 The sprocket moves in the same clockwise direction. When a sprocket is subjected to multiple torques simultaneously, its reaction torque is the algebraic sum of these acting torques. This operation is a familiar coupling effect. Figure 5D ).

[0374] Since planetary gear 94 and sun gear 93 have the same dimensions and tooth structure, the reaction torque at planetary gear 94 is... 40 The torque is transmitted to the sun gear 93 at a 1:1 ratio. For clarity, the applied torque... 39 (Periphery of driven sprocket 96) and reaction torque 40 A ratio of 1:1 or higher is achieved between (planetary gears 94). This is a type 2 lever and coupling effect, and regardless of the reaction torque at planetary gear 94... 40 What is it, 100% of it is transmitted to the sun gear 93 at a 1:1 ratio, and then to their respective output shafts 86.

[0375] Therefore, a speed ratio of 1:2 and a torque conversion ratio of 1:1 or higher were achieved simultaneously.

[0376] To date, three different ratios have been incorporated into embodiments of the present invention. These are: 1) a speed ratio of 1:2; 2) a final torque conversion ratio of 1:1 or higher; and 3) a torque transmission ratio of 1:1 between planetary gear 94 and sun gear 93. Additionally, a fourth point concerns the operating torque. 39 Distance to pivot 24 (sun gear 93) and reaction torque 40 The relationship between the distances from planetary gear 94 to fulcrum 24 (sun gear 93). The final torque conversion ratio of 1:1 ≥ in point 2 depends on this relationship. The larger the ratio in point 4, the more effective the 1 ≥ number in point 2 will be. In embodiments of the invention, this ratio in point 4 is a key factor in obtaining balanced transmission (1:1) or multiplied (1:1 ≥) torque potential. To achieve a minimum balanced transmission of 1:1, a benchmark formula will be established. This benchmark formula is the applied torque (at). 39 The center-to-center (ctc#1) distance between pivot 24 and fulcrum 94 is divided by the planetary gear 94 (reaction torque). 40 The distance from the center to the center (ctc#2) between the pivot point 24 and the pivot point 24 is equal to n, where n must be 1 or greater, i.e., (ctc#1) / (ctc#2) = n, where n = 1 ≥ (i.e., n equals or is greater than 1). Figure 44In detail B of this embodiment of the invention, the applied torque 39 The center-to-center distance (ctc#1) between pivot 24 and fulcrum 24 is 150mm, planetary gear 94 (reaction torque) 40 The center-to-center distance (ctc#2) between point 24 and fulcrum 24 is 50mm. Therefore, n = 3 (150mm / 50mm = 3), and the ratio is 1:3. To reiterate, in this embodiment of the invention, the ratio in point 4 is 1:3. This ratio can be as large as desired, but there are practical limitations.

[0377] It will be readily apparent to those skilled in the art that the descriptions in the above embodiments of the present invention are merely exemplary. The present invention does not limit the number of input shafts and output shafts. Increasing or decreasing the number of input shafts and / or output shafts will correspondingly increase or decrease the number of internal support structures, driven sprockets, drive sprockets, chains, planetary gears, sun gears, planetary gear carriers, planetary gear carrier hubs, connecting rods, connecting rod pins, and various bearings. The embodiments of the present invention are intended to exemplarily describe the invention so that those skilled in the art can readily understand it. The scope of the invention is not limited to the descriptions of the embodiments, but is defined only by the appended claims. The present invention achieves a speed transmission ratio of 1:2 and a torque transmission ratio of 1:≥1 through the technical solutions protected in the appended claims, representing a significant advancement compared to the prior art. Furthermore, since the sun gear, planetary gears, planetary gear carriers, input shafts, and output shafts are all supported by support structures and various bearings, wear and deformation of these components are avoided, ensuring sufficient power transmission.

[0378] Even in other types of levers, as previously mentioned, relative to the reaction torque 40 The distance between the fulcrum 24 and the applied torque 39 The relationship between the point of application of torque and the fulcrum 24 is crucial for achieving torque multiplication. To reiterate, this means that the greater the distance between the point of application of torque and the fulcrum, the more effective the torque multiplication will be, compared to the distance between the reaction torque and the fulcrum. Theoretically, this distance can be extended indefinitely, but again, practical limitations must be considered.

[0379] Archimedes famously said he could move the Earth using only one lever, one fulcrum, and one foothold. While this statement may seem extravagant, it reveals a profound understanding of physics on an astronomical scale. To move the Earth, Archimedes calculated that 88 × 10⁻⁶ kilometres per second would be needed. 21 (880000000000000000000000) miles long (2 53 Even with a fulcrum, he would still encounter another daunting task: 88 × 10⁻⁶. 21 A lever and its footing, miles long. This is the nature of a Class 1 lever. Figure 6A In (a), Archimedes has his fulcrum, the required lever, and the foothold. However, there is a practical problem here. We know that Archimedes applies a lever to 88 × 10⁸ ohms. 21 A component of the force exerted by a lever mile long is enough to move the Earth, but this component must be applied over a correspondingly larger distance (m) to achieve the desired effect at 88 × 10⁸ meters. 21 Any movement would occur at the other end (n) of the mile-long lever. Therefore, Archimedes would have to travel trillions of miles at his end (m) just to move the Earth (n) at the other end of his enormous device.

[0380] Unfortunately, there's a small problem for any potential Earth-powered being like us. In the known universe, there's no mass that could allow him to traverse such a vast distance while attempting this immortal feat.

[0381] Fortunately, Christoph Grünberg (1561-1636, chief mathematician of the Austrian Catholic Jesuits, responsible for the technical review of all mathematical works by Jesuit authors), an admirer of Archimedes, offered a better solution. Typically, Grünberg would send the authors detailed calculations and suggested revisions, requesting that they incorporate these before publication.

[0382] Grünberg's solution utilized another of Archimedes' inventions—the compound pulley. Archimedes himself demonstrated the effectiveness of this system by towing one of King Hiero's largest warships ashore. However, instead of using ropes and pulleys, Grünberg incorporated a new technology of gears, imported from China to Europe in the Middle Ages. This resulted in a system of 24 gears with a gear ratio of 10:1. In modern terms, this is a compound gear reducer; see [link to relevant documentation]. Figure 45 In this system, ropes are still needed to replace 88×10 21The lever is miles long, but the foothold will be closer, smaller, and the foothold is also the fulcrum. The power of the 24-ply gear reducer will be provided by a treadmill (a human-sized hamster wheel, another import from China), with several people providing kinetic energy inside the wheel. Grignberg calculated that the torque (rt) generated by the treadmill rotating at 667 revolutions per minute and applied to its compound gear reducer will be converted to the power of 10 to the 24th power (24 gears in a 10:1 ratio), which, while very slow, will be enough to move the Earth, since the final gear connecting the rope to the Earth will take 100 trillion years to complete one rotation (one revolution every 100 trillion years). Remember, there is an inverse relationship here, i.e., torque increases while speed decreases. The main problem here is that our sun's lifespan is estimated to end in about 5 billion years. Our sun will run out of nuclear fuel and enter the red giant phase, expanding in volume and engulfing the inner planets (including Earth and the base where this treadmill will be located). Therefore, a method is needed to accelerate this large-scale experiment, making it at least less than 5 billion years. Ideally, the speed needs to be fast enough so that the workers present can experience the fruits of their labor.

[0383] The Grains of Rice on the Chessboard: The following is a story of an emperor and a mechanic. During an audience with the emperor, a mechanic, having done a good deed for the country, was asked by the emperor what reward he desired. The mechanic pointed to a chessboard beside the throne and said that if the emperor placed one grain of rice on the first square, two on the second, four on the third, and so on, doubling the amount each time, until all the squares were covered, that would be the amount of rice he wished to receive as a reward. The emperor looked at the chessboard, quickly calculated with his ministers using an abacus, and agreed to the mechanic's request. Here, the emperor had a major problem. See also... Figure 46 In its rapid calculations, the emperor's rice grains were likely equivalent to approximately hundreds of millions of grains of rice, or 2 billion sacks of rice. 30 He stopped calculating at that point. Therefore, he deduced that he was not far from the final number. If he continued to the last square, 2... 80 He would realize that this amount would equal the rice production of the entire kingdom for centuries to come.

[0384] This is the mathematical phenomenon of exponential growth and exponential decline. If we place the emperor's chessboard on a horizontal line and represent it as a curve, see... Figure 47 The upper part has three distinct phases: gradual growth / increase 98 Explosive growth / increase 99 And astronomical growth / increase 100 It is precisely in this gradual growth / increase 98 During that period, the emperor made his fatal mistake. Figure 47The lower half shows exponential decay / deceleration: gradual decay / deceleration 101 Explosive decay / deceleration 102 And astronomical decay / deceleration 103 The correlation of the curve below will be presented in the next paragraph.

[0385] Now we will explain in detail how Grünberg's compound gear reduction system can pull the Earth in time. But first, let's put 10 24 Convert to binary. 10 24 Approximately 2 80 We will replace growth with increase, and decay with slowdown, such as Figure 47 As shown.

[0386] exist Figure 48A The image shows a device with its power supply. 104 The Grünberg compound gear reducer. The output of this power supply is a reaction torque (rt). 106 And reaction speed (rs) 667 revolutions per minute (RPM) 105 Grünberg does not provide reaction torque (rt). 106 The precise value of is given, therefore for our purposes, the reaction torque factor is (rt). 106 The upper left quadrant of the figure shows the sequence from 1... 106 to 2 80 108 The curve represents the multiplication of the reaction torque {Earth's pull}. Conversely, the lower left quadrant shows the speed from 667 revolutions per minute. 105 To (667 revolutions per minute / 2) 80 ) 107 The deceleration is approximately 1 revolution every 100 trillion years.

[0387] See Figure 48A A series of 80 ARC-EPTPGDT 1 68-3 The transmission is connected to the Grünberg compound gear reducer. As shown in the lower right quadrant, it will rotate once every 100 trillion years. 107 Reaction velocity (rs) Input #1 ARC-EPTPGDT 1 68-3 As the rate of action (as) 110 and accelerate 2 80 times, that is, ((as)×2 80 ). In #80 ARC-EPTPGDT1 68-3 At the point of application, the velocity (as) 112 Returning to its 667 revolutions per minute 110 The original starting point. This enabled a timely approach.

[0388] See Figure 48A The applied torque is plotted in the upper right quadrant. (Due to ARC-EPTPGDT 1) 68-3 The torque transmission property of 1:1 ≥, the applied torque 113 With applied torque 111 (equals (rt)) 108 Keep them the same.

[0389] See Figure 48A ARC-EPTPGDT 1 connected in series 68-3 Each of these drives is equipped with a clutch housing 109a on its input side. The purpose of these clutch housings 109a is to prevent the next drive from receiving input power until the previous drive has reached its operating speed. The system comprises one or more ARC-EPTPGDT 1 drives and their respective clutch housings 109a, and will be referred to herein as the Kinetic Multi-Stage Drive En Series (ARC-KEMEDES I). 68-3 .

[0390] See Figure 48B Connecting the power source to a compound gear reduction transmission similar to the Grünberg one 104 The gear reduction transmission is combined and the system is connected to ARC-KEMEDES I 68-3 109 system Figure 48A The aforementioned system can meet a wide range of array power output specifications. For example, by using an additional 4 ARC-EPTPGDT 1 68-3 Extended ARC-KEMEDES I 109 (A total of 84), the speed can be increased to 10672 RPM (667 revolutions per minute x 2). 4 ) 114 This is because Figure 28 The reciprocating connecting rod 97 generates ARC-EPTPGDT 1 68-3 The speed limit is set at this point. From here, speed can be increased, but at the cost of torque. For example, to provide 170,752 RMP (10,672 × 2) to the turbocharger 47... 4 ) 115 The power requires a compound gear multiplier 115a, which has four independent 1:2 (2 4 ( ) stages. Of course, a clutch housing 109a is also integrated before each stage, which has been explained above (see Figure 48A This will result in a partial reduction in torque ((operating torque) / 2). 4 ) 116 But this is still an astonishing amount of torque. This is the ARC-KEMEDES I, which features a compound gear multiplier transmission.68-3 109 It will be called ARC-KEMEDES II 68-4 115 .

[0391] The second embodiment of the present invention, ARC-EPTPGDT 2, is described below. 68-2 / T [B]. See also Figure 49 In the second embodiment of the present invention, there are only three internal structures: a first support structure 118, a second support structure 119, and a third support structure 120. See also Figures 49 to 62 It has no secondary shaft, only a main input shaft 83 and a main output shaft 85, as well as a single continuously variable power transmission planetary gear drive 68-2 and six continuously variable power transmission chain drives 68-1. This second embodiment is designed for applications where lightweight and small footprint are critical, such as electric vehicles.

[0392] Figure 54 The transfer chamber shown is equipped with a single continuously variable power transmission planetary gear drive 68-2. 88 and conversion room 89 Its single sun gear 93 is rigidly attached to the end of the output shaft 85 via a bearing 78, and the output shaft 85 is housed in the planetary gear carrier hub 92-3. See also Figures 52 to 54 The planetary gear carrier hub 92-3 is securely bolted to the third support structure 120. Figure 55 The diagram shows a planetary gear 94 with its connecting rod pin 95-1, bearings 79-1 and 79-3, and bearing 80-3. See also Figures 60-62 The rear second bearing 82-3 on the surface of the planetary gear carrier hub 92-3, and the front first bearing 81-3 mounted on the surface of the planetary gear carrier 96, are both supported for rotation and serve as fulcrums. Bearings 82-3 and 81-3 serve as fulcrums and support the rotation of the planetary gear carrier 96. The sun gear 93 and planet gears 94 are housed in the planetary gear carrier 96, and the driven sprocket 68-2 is bolted to the planetary gear carrier 96. See [reference needed]. Figure 56 . Figure 57 A connecting rod 97 is shown, along with pins 95-1 and 95-2 rigidly connected to two opposite ends of the connecting rod 97 and intersecting at right angles. Bearings 79-2 and 79-4 for pivoting motion are attached to pin 95-2. A planetary gear 94-3 is rigidly connected to the end of its corresponding connecting rod pin 95-1, and bearings 79-1, 79-3, and 80-3 are configured for pivoting assistance. It should be noted that in all embodiments of the invention, connecting rod pins 95-1 and 95-2 are rigidly connected to the ends of the connecting rod 97 and intersect the ends of the connecting rod 97 at right angles.

[0393] To support the connecting rod 97 at the right front connecting rod pin 95, allowing the connecting rod 97 to orbit the sun gear, the planetary gear carrier follower 121 is attached to each of the other right rear, left rear, and left front pins, see [reference]. Figure 58 Each planetary gear carrier follower 121 is supported by its respective planetary gear carrier follower hub 122, and each hub has a bearing 82 and a bearing 78 mounted at its center for supporting the rotation of the planetary gear carrier follower 121, see [link to relevant documentation]. Figure 59 Detail A and detail B, and Figure 60 See also Figure 60 Each planetary gear carrier follower hub 122 is bolted to its respective first support structure 118 or third support structure 120.

[0394] See Figure 61 and Figure 62 To facilitate the reciprocating motion of the connecting rod 97 around the sun gear 93, power is supplied from the input shaft 83 via five continuously variable transmission (CVT) chain drives 68-1 / 1, 68-1 / 2, 68-1 / 3, 68-1 / 4, and 68-1 / 5, which are connected to their respective planetary gear carrier followers. Specifically, to ensure that the planetary gear carrier followers rotate in unison with and are aligned with the planetary gear carrier, the input shaft is connected to four of the CVT chains via a driven shaft 123. See [reference needed]. Figure 53 Furthermore, the planetary gear carrier bearing 81-3 in the second support structure is also shown. For final assembly, see [link to documentation]. Figure 49 and Figure 50 .

[0395] The third embodiment of the present invention, ARC-EPTPGDT 3, is described below. This third embodiment is essentially gear-driven rather than chain-driven. See also... Figure 8D Because the drive gear and driven gear are required to rotate in the same direction, a central idler gear is needed. The gear-driven ARC-EPTPGDT 1 will be referred to as ARC-EPTPGDT 3-1, and the gear-driven ARC-EPTPGDT 2 will be referred to as ARC-EPTPGDT 3-2. This third embodiment is suitable for applications where weight and space are not paramount, but speed is, such as turbines used for propulsion.

[0396] It should be noted that the descriptions in the above embodiments of this disclosure are for illustrative purposes only, and the number of input shafts, output shafts, and driven shafts can be changed without departing from the scope of this disclosure. If the number of input shafts and / or output shafts and / or driven shafts increases or decreases, the number of internal structures, driven sprockets, driving sprockets, chains, planetary gears, sun gears, planetary gear carriers, planetary gear carrier hubs, connecting rods, connecting rod pins, and various bearings can be increased or decreased accordingly. The embodiments of this disclosure are intended to describe this disclosure by way of example so that those skilled in the art can readily understand it. The scope of this disclosure is not limited by the description of the embodiments, but only by the claims. According to the technical solutions protected by the claims, a speed transmission ratio of 1:2 and a torque transmission ratio of 1:≥1 are achieved, which is a significant improvement compared to the prior art. Furthermore, since the sun gear, planetary gears, planetary gear carriers, input shafts, output shafts, and driven shafts are all supported by support structures and various bearings, wear and deformation of these components can be avoided, and better power transmission than conventional devices can be achieved.

Claims

1. A transmission device, comprising: At least one input axis; At least one output shaft; At least one power transmission component, each of the power transmission components comprising: The power transmission drive gear is rigidly attached to the input shaft; The driven gear for power transmission has the same diameter and number of teeth as the driving gear for power transmission, and A power transmission connection mechanism is used to connect the power transmission drive gear and the power transmission driven gear; and At least one power output transmission component, each of the power output transmission components comprising: Planetary gears; A sun gear, rigidly attached to the output shaft, has the same diameter and number of teeth as the planetary gears and meshes with them, wherein the planetary gears do not rotate around their own center but orbit the sun gear; and A planetary gear carrier houses the sun gear and the planetary gears, wherein the driven gear of the power transmission assembly is securely bolted to the planetary gear carrier and drives the planetary gears to orbit around the sun gear via the planetary gear carrier.

2. The transmission device as described in claim 1, further comprising: Multiple internal support structures are provided, through which the input shaft and the output shaft pass and are supported by the internal support structures via corresponding support bearings for rotation; Each of the aforementioned power output transmission components also includes: The planetary gear carrier hub is securely bolted to the corresponding internal support structure; The planetary gear carrier is mounted in the internal support structure via a front first bearing mounted on the surface of the planetary gear carrier, and is also mounted on the planetary gear carrier hub via 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.

3. The transmission device as described in claim 2, wherein: There are two input shafts; there are four output shafts, four power transmission components, and four power output transmission components; the two input shafts, the four power transmission components, the four power output transmission components, and the four output shafts form two sets of coaxial structures.

4. The transmission device as described in claim 3, further comprising: A connecting rod and two connecting rod pins, wherein the two connecting rod pins are rigidly connected to the two ends of the connecting rod and intersect the two ends of the connecting rod at right angles; each connecting rod pin is pivotally connected to the planetary gear carriers of the two coaxial power output transmission assemblies; the planetary gears of the two coaxial power output transmission assemblies are rigidly connected to the two ends of the corresponding connecting rod pin; the length of the connecting rod is such that the planetary gear carriers of the two sets of coaxial power output transmission assemblies rotate uniformly and align with each other; Multiple bearings for supporting the pivoting motion of the connecting rod are respectively mounted in front of and behind the planetary gear of each of the power output transmission assemblies and housed in the planetary gear carrier of the power output transmission assembly.

5. The transmission device as described in claim 3, further comprising: Main input axis; The main output shaft, wherein the main input shaft and the main output shaft pass through the internal support structure and are supported by the internal support structure through corresponding support bearings for rotation; Two power input components, corresponding one-to-one with the two input shafts, each power input component including: The power input drive gear is rigidly attached to the main input shaft; A power input driven gear has the same diameter and number of teeth as the power input drive gear and is rigidly attached to the corresponding input shaft; and A power input connection mechanism is used to connect the power input drive gear and the power input driven gear; and Four power output components, each corresponding to one of the four output shafts, each power output component including: The power output drive gear is rigidly attached to the corresponding output shaft; A power output driven gear has the same diameter and number of teeth as the power output drive gear and is rigidly attached to the main output shaft; and A power output connection mechanism is used to connect the power output drive gear and the power output driven gear.

6. The transmission device as described in claim 5, wherein, 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, wherein, The main input shaft is disposed between the first support structure and the second support structure; The main output shaft is disposed between the second support structure and the seventh support structure; The planetary gear carrier hubs of the four power output transmission components are securely bolted to the third support structure and the sixth support structure, respectively. The planetary gear carriers of the four power output transmission components are respectively mounted in the fourth support structure and the fifth support structure via their respective front first bearings. The two input shafts are arranged between the first support structure and the sixth support structure; The four output shafts are respectively disposed between the second support structure, the fourth support structure, the fifth support structure, and the seventh support structure.

7. The transmission device as claimed in claim 2, wherein, The plurality of internal support structures include a first support structure, a second support structure, and a third support structure; one each of the input shaft, the output shaft, the power transmission assembly, and the power output transmission assembly; the planetary gear carrier hub is securely bolted to the third support structure; the input shaft is disposed between the first support structure and the second support structure; and the output shaft is disposed between the second support structure and the third support structure.

8. The transmission device as claimed in claim 7, further comprising: The driven shaft is disposed between the first support structure and the third support structure; Three planetary gear carrier followers; Two power input components, each of the power input components comprising: The power input drive gear is rigidly attached to the input shaft; A power input driven gear has the same diameter and number of teeth as the power input drive gear and is rigidly attached to the driven shaft; and A power input connection mechanism is used to connect the power input drive gear and the power input driven gear; Three power follower components, each corresponding to one of the three planetary gear carrier follower components, each power follower component comprising: Power-driven gears; A power-driven driven gear has the same diameter and number of teeth as the power-driven drive gear and is rigidly attached to the corresponding planetary gear carrier follower; and A power follower connection mechanism is used to connect the power follower drive gear and the power follower driven gear; Among them, the power follower drive gears of two of the power follower components are rigidly attached to the driven shaft, and the power follower drive gear of the other power follower component is rigidly attached to the input shaft; A connecting rod and two connecting rod pins, wherein the two connecting rod pins are rigidly connected to the two ends of the connecting rod and intersect the two ends of the connecting rod at right angles; one of the two connecting rod pins is pivotally connected to the planetary gear carrier and one of the three planetary gear carrier followers; the other of the two connecting rod pins is pivotally connected to the other two of the three planetary gear carrier followers; a plurality of bearings for supporting the pivoting movement of the connecting rod are mounted on the two connecting rod pins; and Three planetary gear carrier follower hubs correspond one-to-one with the planetary gear carrier follower hubs, wherein each planetary gear carrier follower hub is securely bolted to the first support structure and the third support structure; The planetary gear is rigidly connected to one end of one of the two connecting rod pins, and the three planetary gear carrier followers are respectively attached to the other ends of the two connecting rod pins; each planetary gear carrier follower is mounted on the corresponding planetary gear carrier follower hub by a rear second bearing mounted on the surface of the corresponding planetary gear carrier follower hub, and is supported by the rear second bearing for rotation; the length of the connecting rod is such that the three planetary gear carrier followers rotate in unison with the planetary gear carrier and are aligned with each other.

9. The transmission device according to any one 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 is a chain or a freewheeling gear; when 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 the chain, the driving gear and the driven gear are connected to the chain; when 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 the freewheeling gear, the freewheeling gear is located between the driving gear and the driven gear, and meshes with the driving gear and the driven gear.

10. The transmission device as claimed in claim 9, wherein, The speed transmission ratio of the transmission device is 1:2; the torque transmission ratio of the transmission device is a function of the center-to-center distance between the outer circumference of the planetary gear carrier and the sun gear and the center-to-center distance between the planetary gears and the sun gear.

11. The transmission device as claimed in claim 10, wherein, The torque transmission ratio is equal to or greater than 1:

1.

12. A speed reduction transmission system comprising at least one transmission device as claimed in any one of claims 1 to 11, wherein each of the transmission devices is provided with a clutch housing on its input side.

13. A multiplier transmission system, comprising the reduction transmission system as described in claim 12, and further comprising a compound gear multiplier transmission device connected to the output of the reduction transmission system.

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