Engine driven by acting force generated by force generator to operate

Abstract

The invention discloses an engine driven by acting force generated by a force generator to operate, and belongs to the technical field of engines. The device is composed of a force generator capable of generating acting force to the energy input end of an engine and a gear mechanism capable of synchronously and reversely rotating. The technical key points are as follows: (1) an inner gear ring is driven to rotate by utilizing acting force generated by a force generator, and the inner gear ring forms a state that forward torque and reverse torque on a planet carrier are opposite in rotation of a transmission planet wheel; (2) the counter torque on the planet carrier is amplified by utilizing the lever principle to promote the planet carrier to strongly rotate in the reverse direction; and (3) the synchronous reverse rotation technology of the planet carrier and the inner gear ring is utilized to enable the inner gear ring to be always kept at the original rotating angle during operation, so that the acting force generated by the force generator is continuously kept, and the machine is continuously driven to operate by utilizing the acting force. The method has the advantages of no energy cost, no emission and pollution, and no damage and influence on the natural environment; power is strong, manufacturing is easy, and convenience and practicability are achieved. The method can be used for power generation, power machinery, vehicles and the like.

Description

Technical Field

[0001] The present invention relates to an engine driven by the force generated by a power generator, specifically a prime mover driven by the force generated by the power generator directly on the energy input end of the engine and outputting power, belonging to the technical field of engines. Background Art

[0002] Traditional engines (steam engines, internal combustion engines, etc.) all use physical energy to drive their operation and convert it into mechanical energy to be transported out for work. Therefore, they all have problems such as consumption of physical energy, pollution, and emissions.

[0003] At present, with the rapid development of social economy and the strong demand of the international community for emission reduction and carbon reduction, there is an urgent need for an engine that does not use material energy and has no pollution and emissions, but there is no such machine on the market. Summary of the Invention

[0004] In view of the above-mentioned deficiencies, the present invention provides an engine driven by the force generated by a power generator.

[0005] The present invention comprises a force generator capable of exerting a force on the energy input end of an engine and a synchronously counter-rotating gear transmission mechanism. The force generator specifically refers to a device (such as a jack, electric hoist, winch, etc.) or a weighted object that can exert an upward pushing or downward pulling force on the end point of the engine's drive rod, causing the end point of the drive rod to be subjected to force, and can maintain the force exerted on the end point of the drive rod constant (expressed as potential energy) under the condition that the parallel angle of the drive rod remains unchanged. As is well known, when a jack exerts a certain amount of upward pushing force on the end point of the parallel drive rod, as long as the parallel angle of the drive rod remains unchanged, the force exerted by the jack to push the end point of the drive rod upward will remain constant. Similarly, when an electric hoist or winch exerts a certain amount of downward pulling force on the end point of the parallel drive rod, as long as the parallel angle of the drive rod remains unchanged, the force exerted by the electric hoist or winch to pull the end point of the drive rod downward will remain constant. The same is true for the weight. Under the condition that the weight is suspended at the end point of the parallel drive rod, as long as the parallel angle of the drive rod remains unchanged, the downward force generated by the weight on the end point of the drive rod remains unchanged. The synchronous counter-rotating gear transmission mechanism specifically refers to the engine's combined planetary carrier, which can rotate synchronously in the opposite direction to the inner ring gear under the drive of the inner ring gear and the compound four-stage planetary gear, and replace the angle of the inner ring gear rotating in the forward direction with the angle of its synchronous counter-rotation, thereby causing the rotation angle of the inner ring gear to remain unchanged. The present invention mainly includes the following technical points: ① Use a force generator to send an upward pushing or downward dragging force (through the input wheel) to the end point of the drive rod to drive the inner ring gear to rotate in the forward direction (Note: the direction of the inner ring gear is defined as the forward direction, and the direction of other gears after the inner ring gear is based on this, the same below), and then the compound four-stage planetary gear installed on the combined planetary carrier is sequentially driven by the inner ring gear to rotate in the forward or reverse direction respectively. ② While the circumferential force of the initial planetary gear rotating in the forward direction is converted into the circumferential force of the initial planetary gear shaft (pushed by the inner ring gear) revolving in the forward direction, pushing the combined planetary carrier in forward rotation, the circumferential force of the final planetary gear rotating in the reverse direction (supported by the sun gear) is converted into the circumferential force of the final planetary gear shaft revolving in the reverse direction, and the circumferential force of the final planetary gear shaft revolving in the reverse direction is used to push the combined planetary carrier in the reverse direction. ③ By utilizing the lever effect formed in the planetary gear transmission mechanism, the reverse torque on the combined planetary carrier is caused to be greater than the forward torque, thereby forcing the combined planetary carrier to rotate strongly in the reverse direction. ④ The reversely rotating combined planetary carrier is used to forcibly drive the compound four-stage planetary gears (including the initial planetary gear) to revolve in the reverse direction, thereby forcibly driving the initial planetary gear to use its gear teeth to drag the forward-rotating inner ring gear in the reverse direction.⑤ By utilizing the technology that the combined planetary carrier rotates in the reverse direction at the same angle as the inner gear ring rotates in the forward direction, the inner gear ring rotating in the forward direction is ensured to maintain its original rotation angle while the driving planetary gear pushes the combined planetary carrier in the reverse direction, thereby ensuring that the parallel angle of the drive rod remains unchanged. The above five technical points ensure that the force exerted by the power generator on the end point of the drive rod remains unchanged while the engine is running, and continuously drives the inner gear ring to rotate in the forward direction through the input wheel; the inner gear ring rotating in the forward direction continuously drives the compound four-stage planetary gear to rotate, thereby continuously pushing the combined planetary carrier to rotate strongly in the reverse direction; finally, a portion of the kinetic energy of the combined planetary carrier rotating in the reverse direction is transmitted to the output wheel to perform work.

[0006] The present invention is achieved through the following technical solution: an engine driven by the force generated by a power generator, comprising a fixed system, a power generating system, an input system, a rotation system, and an output system. The fixed system comprises a housing and two sun gears; the power generating system comprises the power generator; the input system comprises two internal gear rings, two input wheels, and two drive rods; the rotation system comprises a combined planetary carrier, four starting planetary gears, two starting coaxial planetary gears, two number one idler gears, two number two idler gears, two ending coaxial planetary gears, and four ending planetary gears; and the output system comprises an output transmission wheel and an output wheel. The characteristics are as follows: the box body is both the sealed outer shell of the machine and the shaft seat for installing and supporting the star gear shaft, input gear shaft and output gear shaft, is located on the outside of the machine, and seals the gear transmission mechanism of the machine inside; the shape is like three connected cylinders, the middle is the rotating system box body, and the radial ends are the input system box body and the output system box body respectively; a shaft seat for fastening and installing the star gear shaft is prefabricated at the center position of the box wall on both axial sides of the rotating system box body, a bearing seat for installing the input gear shaft is prefabricated at the center position of the box wall on both axial sides of the input system box body, and a bearing seat for installing the output gear shaft is prefabricated at the center position of the box wall on both axial sides of the output system box body. The two sun gears are cylindrical external gears with a diameter smaller than the inner ring gear and larger than the starting and ending planetary gears. They are located at the radial center positions on both sides of the axial direction of the combined planetary carrier in the rotating system housing, and are on the same axis as the combined planetary carrier and the inner ring gear. The hubs are fastened to the two sides of the sun gear shaft, and the gear teeth mesh with the outer ends of the ending planetary gears. The two ends of the sun gear shaft are fastened to the prefabricated shaft seats for mounting the sun gear shaft at the center positions of the box walls on both sides of the axial direction of the rotating system housing, and cannot rotate. The functions of the sun gear are: first, to use the sun gear shaft to install and support the combined planetary carrier and the inner ring gear, becoming the central axis supporting the rotation of the combined planetary carrier and the inner ring gear; second, to use its non-rotatable characteristic to support the ending planetary gear rotating in the opposite direction, causing the ending planetary gear to roll and revolve in the opposite direction along the gear teeth of the sun gear, thereby driving the combined planetary carrier to rotate in the opposite direction with the wheel shaft. The two inner gear rings are cylindrical internal gears with a diameter larger than the sun gear and the end coaxial planetary gears; they are respectively located at the radial center positions on both sides of the axial direction of the rotating system housing, on the same axis as the combined planetary carrier and the sun gear, and the gear teeth are meshed with the starting planetary gear; the axial edge of the inner gear ring on the side close to the housing wall is fastened or integrated with the inner gear ring support bracket, and a hollow shaft facing the inner side of the inner gear ring is prefabricated at the radial center position of the support bracket (that is, the radial center position of the inner gear ring), and the inner gear ring is respectively installed and supported on both sides of the sun gear shaft through this hollow shaft (installed with bearings or in a sliding state); a force-bearing gear tooth composed of several gear teeth of a cylindrical external gear is prefabricated on the radial outer ring of the inner gear ring close to the input wheel, and the force-bearing gear teeth of the inner gear ring are fastened or integrated with the outer wall of the inner gear ring or the inner gear ring support bracket, and mesh with the outside of the input wheel.The inner ring gear's functions are: first, it rotates in the forward direction under the drive of the input wheel's force-bearing teeth, thereby driving the starting planet gear in the forward direction; second, it maintains a constant rotational angle during operation, dragged by the teeth of the starting planet gear (driven by the synchronously counter-rotating combined planet carrier), thereby ensuring that the force exerted by the power generator on the energy input end of the machine remains constant. The two input wheels are cylindrical external gears, located at the radial center of the input system housing on either side. The hubs are fixedly mounted on either side of the input wheel shaft, and their teeth mesh with the force-bearing teeth of the inner ring gear. Bearings are mounted on either side of the input wheel shaft in bearing seats prefabricated at the center of the input system housing's axial walls. The extension shafts at both ends of the input wheel shaft extend outside the bearing seats and are fixedly connected to the shaft holes at the starting end of the drive rod. The function of the input wheel is to rotate through the extension shaft of the input wheel shaft when the starting end of the drive rod is twisted, thereby driving the inner ring gear to rotate by driving the force-bearing teeth of the inner ring gear. The two drive rods are parallel rods that receive the force generated by the power generator and use this force to twist the input axle. They are located on opposite axial sides of the input system housing. A pre-formed axial hole is formed at the starting end of the drive rod, which is tightly connected to the extended shaft of the input axle. A force point is provided at the end of the drive rod, which is connected to the power-generating end of the power generator. The function of the drive rod is to swing upward or downward when the power generator applies an upward pushing or downward pulling force to the end force point of the drive rod, thereby causing the starting end of the drive rod to twist the extended shaft of the input axle, which is tightly connected to the starting end axial hole. The power generator is a device that applies force to the end force point of the drive rod. It is composed of an instrument (such as a jack, electric hoist, winch, etc.) or a weight that can apply an upward pushing or downward pulling force to the end force point of the drive rod of the engine, causing the end force point of the drive rod to be forced upward or downward, and can maintain the generated force while maintaining the parallel angle of the drive rod. It is located radially outside the input system housing, and its force-generating end is connected to the end force point of the drive rod. The function of the force generator is to drive the machine to operate by exerting an upward pushing or downward pulling force on the end point of the driving rod.The combined planetary carrier is a cylindrical planetary carrier consisting of an outer ring frame and two planetary carriers, which are located at the radial center position in the axial middle of the rotating system housing and on the same axis as the inner gear ring and the star gear. The bearing seats for mounting the star gear shaft prefabricated at the radial center positions of the two planetary carriers are respectively mounted and supported on the star gear shaft with bearings, and rotate in the opposite direction under the push of the end planetary gear shaft revolving in the opposite direction; the outer ring frame is a cylindrical frame for mounting and fixing the two planetary carriers, which is located at the radial outer ring of the combined planetary carrier; the two planetary carriers are side plates for mounting the planetary gear shafts, which are located on both axial sides of the outer ring frame, and the two planetary carriers respectively prefabricate two bearing seats for mounting the starting planetary gear shaft, two for mounting the number one idler gear shaft, two for mounting the number two idler gear shaft and two for mounting the end planetary gear shaft in radially symmetrical positions, and prefabricate one bearing seat for mounting the star gear shaft at the radial center position; the radial edges of the two planetary carriers are fastened to the axial edges on both sides of the outer ring frame. The combined planetary carrier functions as follows: first, it is used to mount the planetary axles; second, it rotates in the opposite direction under the push of the counter-rotating end planetary axles; and third, during synchronous counter-rotation with the inner ring gear, it forcibly drives the start planetary gears to drag the inner ring gear, which is rotating in the forward direction, in the reverse direction, with their gear teeth, so that the inner ring gear maintains a constant rotation angle during operation. The four start planetary gears are cylindrical external gears with a smaller diameter than the sun gear and the end coaxial planetary gears. They are located in radially symmetrical positions within the inner ring gear on either side of the combined planetary carrier's outer axial direction, with their gear teeth meshing with the inner ring gear and rotating in the forward direction under the drive of the inner ring gear. The two start planetary axles are mounted on both sides of the planetary carrier using bearings in bearing seats prefabricated at symmetrical positions on the two sides of the planetary carrier for mounting the start planetary axles. The extended shafts at both ends of the two start planetary axles extend to the inner side of the inner ring gear on either side of the combined planetary carrier's outer axial direction. The hubs of the start planetary gears are fastened to the extended shafts of the two start planetary axles. The functions of the starting planetary gears are: first, they rotate in the forward direction under the drive of the inner ring gear, and drive the starting coaxial planetary gear in the combined planetary carrier to rotate in the forward direction via the starting planetary gear shaft; second, they roll and revolve in the reverse direction along the inner ring gear teeth under the forcible drive of the combined planetary carrier, which rotates synchronously with the inner ring gear in the reverse direction, thereby dragging the inner ring gear rotating in the forward direction with its teeth in the reverse direction, causing the inner ring gear to maintain a constant rotation angle during operation. The two starting coaxial planetary gears are cylindrical external gears with the same module, number of teeth, and diameter as the starting planetary gears. They are located in radially symmetrical positions in the axial center of the combined planetary carrier, and their teeth mesh with the outer portion of the first idler gear. They are coaxial with the starting planetary gears, and their hubs are fixedly mounted in the middle of the two starting planetary gear shafts. They rotate in the forward direction under the drive of the starting planetary gear shafts. The function of the starting coaxial planetary gears is to introduce the circumferential force of the inner ring gear driving the starting planetary gear into the combined planetary carrier and drive the first idler gear in the combined planetary carrier.The two number one idler gears are cylindrical external gears, located in radially symmetrical positions axially in the center of the combined planetary carrier. Their hubs are fixedly mounted in the middle of the two number one idler gear shafts. Their front gear teeth mesh with the outer teeth of the coaxial planetary gear at the start, and their rear gear teeth mesh with the outer teeth of the number two idler gear. Driven by the coaxial planetary gear at the start, they rotate in opposite directions. Bearings are mounted at each end of the two number one idler gear shafts in bearing seats prefabricated in symmetrical positions on the two planetary carriers. The number one idler gears function by: first, by adjusting their mounting position on the planetary carrier, they reduce the angle between the meshing point between the start planetary gear shaft and the inner ring gear and the meshing point between the start planetary gear shaft and the number one idler gear; second, they drive the number two idler gear. The two second idler gears are cylindrical external gears, located in radially symmetrical positions axially in the center of the combined planetary carrier. Their hubs are fixedly mounted in the middle of the two second idler shafts. Their front teeth mesh with the outer teeth of the first idler, while their rear teeth mesh with the outer teeth of the coaxial planetary gear at the end. They rotate in the forward direction driven by the first idler. Bearings are mounted at each end of the two second idler shafts in bearing seats prefabricated in symmetrical positions on the two planetary carriers. The second idler gears serve two functions: first, to adjust the rotational direction of the coaxial planetary gears at the end; second, by adjusting their mounting position on the planetary carrier, they increase the angles between the meshing points of the planetary shafts with the sun gear and the second idler. The two coaxial planetary gears at the end are cylindrical external gears with a diameter smaller than the inner ring gear and larger than the initial and final planetary gears. They are located in radially symmetrical positions axially in the center of the combined planetary carrier, coaxial with the final planetary gears, and have hubs fixedly mounted in the middle of the two final planetary gear shafts. Their teeth mesh with the outer surface of the second idler gear, and the gears rotate in opposite directions under the drive of the second idler gear. The coaxial planetary gears at the end utilize their larger diameter to increase the circumferential force of the final planetary gears' rotation, thereby increasing the circumferential force of the final planetary gears' rotation in the opposite direction and making it greater than the circumferential force of the initial planetary gears' rotation in the forward direction. The four terminal planetary gears are cylindrical external gears with a smaller diameter than the sun gear and the terminal coaxial planetary gears. They are located in pairs at radially symmetrical positions on either side of the combined planetary carrier, with their hubs fixedly mounted on either side of the two terminal planetary gear shafts. They are coaxial with the terminal coaxial planetary gears, with their teeth meshing with the sun gear's exterior. Driven by the terminal planetary gear shafts, they rotate in the opposite direction and roll and revolve along the sun gear's teeth in the opposite direction. Bearings are mounted at each end of the two terminal planetary gear shafts in bearing seats prefabricated for mounting the terminal planetary gear shafts at symmetrical locations on the two planetary carriers. The function of the terminal planetary gears is to roll and revolve along the sun gear's teeth in the opposite direction, supported by the sun gears, thereby driving the combined planetary carrier in the opposite direction. The output transmission wheel is a cylindrical external gear located axially midway along the radial outer ring of the combined planetary carrier's outer ring frame. It is fixedly connected to or integrated with the outer ring frame and rotates in the opposite direction driven by the combined planetary carrier. Its teeth mesh with the output wheel's exterior.The output transmission wheel transfers the kinetic energy generated by the rotation of the combined planetary carrier to the output wheel. The output wheel is a cylindrical external gear located in the radial center of the output system housing. Its hub is securely mounted to the center of the output wheel shaft. Its teeth mesh with the outer edge of the output transmission wheel, allowing it to rotate in the forward direction. Bearings are mounted on either side of the output wheel shaft in prefabricated bearing seats located in the center of the housing wall on either axial side of the output system housing. One or both ends of the output wheel shaft extend beyond the bearing seats. The output wheel transfers some of the rotational kinetic energy transmitted by the output transmission wheel to perform work.The above-mentioned gear transmission mechanism: ① In the direction of gear rotation, the rotation direction of the end planetary gear must be opposite to that of the starting planetary gear, so as to ensure that when the end planetary gear shaft pushes the combined planetary carrier to rotate strongly in the reverse direction, the combined planetary carrier that rotates synchronously with the inner gear ring in the reverse direction can forcibly drive the starting planetary gear rotating in the forward direction to roll and revolve in the reverse direction along the gear teeth of the inner gear ring, thereby dragging the inner gear ring rotating in the forward direction in the reverse direction with the gear teeth; ② In terms of gear transmission ratio, the inner gear ring drives the starting planetary gear, the starting coaxial planetary gear drives the No. 1 idler gear, the No. 1 idler gear drives the No. 2 idler gear, the No. 2 idler gear drives the end coaxial planetary gear, and the end planetary gear In the process of the planetary gear rolling and rotating along the teeth of the sun gear, the average transmission rate of each gear transmission must reach more than 85%, ensuring that the circumferential force of the end planetary gear rotating in the reverse direction (after being amplified by the end coaxial planetary gear) is greater than the circumferential force of the starting planetary gear rotating in the forward direction; ③ In terms of the specifications of the planetary gears, the diameter of the end coaxial planetary gear should be increased as much as possible and the diameter of the end planetary gear should be reduced as much as possible, so as to maximize the circumferential force of the end planetary gear rotating in the reverse direction by maximizing the difference between the two diameters; ④ In terms of the orbital diameter of the gear, the diameter of the end planetary gear rotating in the reverse direction should be greater than or not less than the diameter of the starting planetary gear (when the inner gear ring pulls the planetary gear). ) in the forward direction of revolution, ensuring that the force arm of the end planetary gear on the combined planetary carrier in the reverse direction of revolution is greater than or not less than the force arm of the start planetary gear (under the pull of the inner gear ring) in the forward direction of revolution; ⑤ In the installation position of the planetary gear shaft on the planetary carrier, the angle between the meshing point of the start planetary gear shaft to the inner gear ring and the meshing point of the start planetary gear shaft to the No. 1 idler gear should be minimized (below 90°), thereby reducing the lever angle with the start planetary gear shaft as the fulcrum (below 0°), so as to utilize the lever effect with the start planetary gear shaft as the fulcrum to reduce the circumferential force of the start planetary gear shaft (under the pull of the inner gear ring) in the forward direction of revolution; at the same time, the end planetary gear shaft should be increased as much as possible The included angle between the meshing point of the wheel shaft to the sun gear and the meshing point of the end planetary gear shaft to the second idler gear (above 90°) is increased, thereby increasing the included angle of the lever with the end planetary gear shaft as the fulcrum (above 0°), so as to utilize the lever effect with the end planetary gear shaft as the fulcrum to increase the circumferential force of the end planetary gear shaft in the reverse direction; ⑥ In terms of the gear ratio, the gear ratio of the sun gear to the end planetary gear must be equal to the gear ratio of the inner ring gear to the end coaxial planetary gear, or the gear ratio of the sun gear to the inner ring gear must be equal to the gear ratio of the end planetary gear to the end coaxial planetary gear, so as to ensure that the angle of the combined planetary carrier rotating in the reverse direction is the same as the angle of the inner ring gear rotating in the forward direction.

[0007] The invention has the following advantages: low manufacturing cost, strong power, convenience and practicality; no energy required, no pollution, no emissions, no noise, and no damage or impact on the ecological environment. It can be used for power generation, power machinery, and transportation. BRIEF DESCRIPTION OF THE DRAWINGS

[0008] Attachment Figure 1 :It is the appearance drawing of the invention;

[0009] Attachment Figure 2 : This is the main view of the internal structure of the box of the invention;

[0010] Attachment Figure 3 : Main view of outer ring frame and planet carrier;

[0011] Attachment Figure 4 : It is a top view of the invention along the plane of the axis of the input wheel, the sun wheel and the output wheel;

[0012] Attachment Figure 5 :It is attached Figure 4 Axial cross-section view along line AA;

[0013] Attachment Figure 6 :It is attached Figure 4 Axial cross-section view along line BB;

[0014] Attachment Figure 7 :It is attached Figure 4 Axial cross-section view along the CC line;

[0015] Attachment Figure 8 :It is attached Figure 5 、 6 , axial side cross-sectional view along line DD in 7;

[0016] Attachment Figure 9 :It is attached Figure 5 、 6 , axial side cross-sectional view along line EE in 7;

[0017] Attachment Figure 10 :It is attached Figure 5 、 6 , axial side cross-sectional view along line FF in 7;

[0018] Attachment Figure 11 :It is attached Figure 5 、 6 , axial side cross-sectional view along line GG in FIG7.

[0019] In the figure: housing 01; rotating system housing 0101; input system housing 0102; output system housing 0103; sun gear axle seat 0121; input gear bearing seat 0122; output gear bearing seat 0123; housing base 0124; sun gear 11; sun gear axle 111; inner ring gear 12; inner ring gear support bracket 121; hollow shaft 122 at the radial center of the inner ring gear support bracket; inner ring gear teeth 123; input gear 13; input wheel axle 131 ; Input wheel shaft extension shaft 132; Output transmission wheel 14; Output wheel 15; Output wheel shaft 151; Output wheel shaft extension shaft 152; Starting planetary gear 21; Starting planetary gear shaft 211; Starting planetary gear shaft extension shaft 212; Angle 213 between the starting planetary gear shaft and the inner gear ring meshing point and the starting planetary gear shaft and the first idler gear meshing point; Starting coaxial planetary gear 22; First idler gear 23; First idler gear shaft 231; Second idler gear 24; Second idler gear shaft 241; End Coaxial planetary gear 25; terminal planetary gear 26; terminal planetary gear shaft 261; angle 262 between the meshing point between the terminal planetary gear shaft and the sun gear and the meshing point between the terminal planetary gear shaft and the second idler gear; drive rod 31; shaft hole 311 at the starting end of the drive rod; force point 312 at the end of the drive rod; screw-type force generating device 32; force generating beam 321; nut 322 mounted in the nut seat of the force generating beam; prefabricated circular shafts 323 at both ends of the force generating beam; screw 324; knob 325 on the screw ; Thread 326 in the middle section of the screw; screw shaft 327; screw bearing seat 328; combined planetary carrier 33; outer ring frame 331; planetary carrier 332; bearing seat 3322 for mounting the star gear shaft at the radial center position on the planetary carrier; bearing seat 3321 for mounting the starting planetary gear shaft on the planetary carrier; bearing seat 3323 for mounting the number one idler gear shaft on the planetary carrier; bearing seat 3324 for mounting the number two idler gear shaft on the planetary carrier; bearing seat 3326 for mounting the end planetary gear shaft on the planetary carrier. DETAILED DESCRIPTION

[0020] The following is a clear and complete description of the technical solutions of the present invention in conjunction with the accompanying drawings. It is obvious that the embodiments described are only some of the embodiments of the present invention, not all of them. All other embodiments derived by persons of ordinary skill in the art based on the embodiments of the present invention without inventive effort are within the scope of protection of the present invention.

[0021] An engine driven by the force generated by a power generator includes a fixed system, a power generation system, an input system, a rotation system, and an output system. The fixed system consists of a housing 01 and two sun gears 11; the power generation system comprises a screw-type power generation device 32; the input system comprises two internal gear rings 12, two input wheels 13, and two drive rods 31; the rotation system comprises a combined planetary carrier 33, four starting planetary gears 21, two starting coaxial planetary gears 22, two number one idler gears 23, two number two idler gears 24, two ending coaxial planetary gears 25, and four ending planetary gears 26; and the output system comprises an output transmission wheel 14 and an output wheel 15. The characteristics are as follows: the box body 01 is not only the sealed outer shell of the machine, but also the shaft seat for installing and supporting the star gear shaft 111, the input gear shaft 131 and the output gear shaft 151. It is located on the outside of the machine and seals the gear transmission mechanism of the machine inside; it is shaped like three connected cylinders, with the rotating system box body 0101 in the middle and the input system box body 0102 and the output system box body 0103 at both ends respectively; a shaft seat 0121 for fastening and installing the star gear shaft 111 is prefabricated at the center position of the box wall on both axial sides of the rotating system box body 0101, a bearing seat 0122 for installing the input gear shaft 131 is prefabricated at the center position of the box wall on both axial sides of the input system box body 0102, and a bearing seat 0123 for installing the output gear shaft 151 is prefabricated at the center position of the box wall on both axial sides of the output system box body 0103. The two sun gears 11 are herringbone external gears with a module of 3, a tooth width of 80 mm, 34 teeth, and a diameter of 102 mm. They are respectively located at the radial center positions on both sides of the axial direction of the combined planetary carrier 33 in the rotating system housing 0101, and are on the same axis as the combined planetary carrier 33 and the inner ring gear 12. The hubs are respectively fastened to the two sides of the sun gear shaft 111, and the gear teeth are externally meshed with the end planetary gears 26. The two ends of the sun gear shaft 111 are respectively fastened to the shaft seat 0121 for installing the sun gear shaft prefabricated at the center position of the box wall on both sides of the axial direction of the rotating system housing 0101, and cannot rotate.The two inner gear rings 12 are helical cylindrical internal gears with a module of 3, a tooth width of 50 mm, 68 teeth, and a diameter of 204 mm. They are located at the radial center positions on both sides of the axial direction of the rotating system housing 0101, and are on the same axis as the combined planet carrier 33 and the sun gear 11. The gear teeth are meshed with the starting planet gear 21. The inner gear ring 12 is fastened to the inner gear ring support bracket 121 along the axial side of the housing wall. A prefabricated inner gear ring support bracket 121 is provided at the radial center position of the inner gear ring support bracket 121 (i.e., the radial center position of the inner gear ring 12). A hollow shaft 122 faces the inner side of the inner ring gear 12, and the inner ring gear 12 is respectively mounted and supported on both sides of the sun gear shaft 111 (in a sliding state) through this hollow shaft 122; an inner ring gear force tooth 123 consisting of 6 gear teeth of a spur gear is prefabricated at the end of the inner ring gear support bracket 121 radially close to the input wheel 13, with a module of 5, a tooth width of 20mm, and a pitch circle radius of 195mm. The inner ring gear force tooth 123 is integrated with the inner ring gear support bracket 121 and meshes with the outside of the input wheel 13. The two input wheels 13 are half spur gears with a module of 5, a tooth width of 20 mm, 9 teeth, and a pitch circle radius of 45 mm. They are respectively located at the radial center positions on both sides of the axial direction of the input system box 0102, and the wheel hubs are respectively fastened to the two sides of the input wheel shaft 131, and the gear teeth are externally meshed with the force-bearing gear teeth 123 of the inner gear ring. The two sides of the input wheel shaft 131 are respectively installed with bearings in the bearing seats 0122 for installing the input wheel shaft, which are prefabricated at the center positions of the box walls on both sides of the axial direction of the input system box 0102. The protruding shafts 132 at both ends of the input wheel shaft extend to the outside of the bearing seat 0122 and are fastened to the shaft hole 311 at the starting end of the drive rod. The two drive rods 31 are parallel rods that receive the force generated by the screw-type force generating device 32 and use this force to twist the input wheel shaft 131. They are located on both axial sides outside the input system housing 0102. A prefabricated axial hole 311 is fixedly connected to the extended shaft 132 of the input wheel shaft at the starting end of the drive rod. A prefabricated axial hole is connected to the circular shaft 323 prefabricated at both ends of the force beam 321 of the screw-type force generating device 32 at the end of the drive rod at the end fulcrum 312 (the axial hole and the circular shaft are in a sliding state). The center distance between the starting axial hole 311 and the end fulcrum 312 of the drive rod is 350 mm. The screw-type force generating device 32 consists of a force beam 321, a screw 324, and a screw bearing seat 328, and is located radially outside the input system housing 0102. The force-generating crossbeam 321 is located between the two driving rod end points 312. A circular shaft 323 is prefabricated at each end of the force-generating crossbeam 321 and installed in a prefabricated shaft hole at the two driving rod end points 312. A nut seat is prefabricated in the middle of the force-generating crossbeam 321, and a nut 322 is installed in the nut seat. The screw bearing seat 328 is a device for mounting the screw shaft 327. It is located on the box base 0124 below the nut 322 in the middle of the force-generating crossbeam and is tightly connected to the box base 0124.The screw rod 324 is a screw rod with a thread, which is perpendicular to the force beam 321; the upper end of the screw rod 324 is a knob disk 325, the middle section is a thread 326 that is screwed into the nut 322 in the middle of the force beam, and the lower end is a screw shaft 327 that is installed in the screw bearing seat 328 with a bearing. The combined planetary carrier 33 is a cylindrical planetary gear carrier composed of an outer ring frame 331 and two-sided planetary carriers 332. It is located in the radial center position of the axial middle of the rotating system housing 0101 and is on the same axis as the inner gear ring 12 and the star gear 11. The bearing seat 3322 for installing the star gear shaft prefabricated at the radial center position on the two-sided planetary carriers 332 is installed and supported on the star gear shaft 111 with a bearing; the outer ring frame 331 is a cylindrical frame for installing and fixing the two-sided planetary carriers 332. The outer diameter of the frame is 354mm and is located in the radial outer ring of the combined planetary carrier 33; the two-sided planetary carriers The frame 332 is a side plate for installing the planetary gear shaft. The outer diameter of the side plate is 354 mm. It is located on both axial sides of the outer ring frame 331. The two planetary frames 332 are prefabricated with two bearing seats 3321, 3323, 3324, and 3326 for installing the starting planetary gear shaft 211, two for installing the No. 1 idler gear shaft 231, two for installing the No. 2 idler gear shaft 241, and two for installing the end planetary gear shaft 261 at radially symmetrical positions. A bearing seat 3322 for installing the star gear shaft 111 is prefabricated at the radial center position; the radial edges of the two planetary frames 332 are fastened to the axial edges on both sides of the outer ring frame 331. The four starting planetary gears 21 are helical cylindrical external gears with a module of 3, a tooth width of 40 mm, 21 teeth, and a diameter of 63 mm. They are located in radially symmetrical positions in the inner gear ring 12 on both sides of the outer axial direction of the combined planetary carrier 33, and the gear teeth are meshed with the inner gear ring 12. The two sides of the two starting planetary gear shafts 211 are respectively mounted with bearings in the bearing seats 3321 for mounting the starting planetary gear shafts, which are prefabricated in symmetrical positions on the two-sided planetary carriers 332. The protruding shafts 212 at both ends of the two starting planetary gear shafts extend to the inner sides of the inner gear ring 12 on both sides of the outer axial direction of the combined planetary carrier 33. The hubs of the starting planetary gears 21 are respectively fastened and mounted on the protruding shafts 212 of the two starting planetary gear shafts. The two coaxial planetary gears 22 at the starting end are herringbone tooth cylindrical external gears with a module of 3, a tooth width of 80 mm, 21 teeth, and a diameter of 63 mm. They are respectively located in radially symmetrical positions in the axial middle of the combined planetary carrier 33, and the gear teeth are externally meshed with the number one idler gear 23. They are coaxial with the starting planetary gear 21, and the wheel hubs are respectively fastened to the middle parts of the two starting planetary gear shafts 211.The two No. 1 idler gears 23 are herringbone cylindrical external gears with a module of 3, a tooth width of 80 mm, 27 teeth, and a diameter of 81 mm. They are respectively located in radially symmetrical positions in the axial middle of the combined planetary carrier 33, and the wheel hubs are respectively fastened and mounted in the middle parts of the two No. 1 idler gear shafts 231. The front gear teeth are externally meshed with the coaxial planetary gear 22 at the starting end, and the rear gear teeth are externally meshed with the No. 2 idler gear 24. The two ends of the two No. 1 idler gear shafts 231 are respectively mounted with bearings in bearing seats 3323 for mounting the No. 1 idler gear shafts, which are prefabricated in symmetrical positions on the two planetary carriers 332. The two second idler gears 24 are herringbone external gears with a module of 3, a tooth width of 80 mm, 17 teeth, and a diameter of 51 mm. They are located in radially symmetrical positions in the axial center of the combined planetary carrier 33, with their hubs fixedly mounted in the middle of the two second idler gear shafts 241. The front gear teeth mesh externally with the first idler gear 23, and the rear gear teeth mesh externally with the terminal coaxial planetary gear 25. The two second idler gear shafts 241 are mounted at both ends with bearings in bearing seats 3324 prefabricated for mounting the second idler gear shafts at symmetrical positions on the two planetary carriers 332. The terminal coaxial planetary gears 25 are herringbone external gears with a module of 3, a tooth width of 80 mm, 34 teeth, and a diameter of 102 mm. They are located in radially symmetrical positions in the axial center of the combined planetary carrier 33, coaxial with the terminal planetary gear 26, with their hubs fixedly mounted in the middle of the two terminal planetary gear shafts 261, with their teeth externally meshing with the second idler gear 24. The four terminal planetary gears 26 are herringbone external gears with a module of 3, a tooth width of 80 mm, 17 teeth, and a diameter of 51 mm. They are located in pairs at radially symmetrical positions on either side of the combined planetary carrier 33, with their teeth meshing with the outer portion of the sun gear 11. They are coaxial with the terminal coaxial planetary gears 25, and their hubs are fixedly mounted on either side of the two terminal planetary gear shafts 261. The two ends of the two terminal planetary gear shafts 261 are mounted with bearings in bearing seats 3326 prefabricated for mounting terminal planetary gear shafts at symmetrical positions on the two-sided planetary carrier 332. The output transmission gear 14 is a herringbone external gear with a module of 3, a tooth width of 80 mm, 128 teeth, and a diameter of 384 mm. It is located axially in the middle of the radial outer ring of the outer ring frame 331 of the combined planetary carrier 33, is fixedly connected to the outer ring frame 331, and its teeth mesh with the outer portion of the output gear 15. The output wheel 15 is a herringbone tooth cylindrical external gear with a module of 3, a tooth width of 80 mm, 19 teeth, and a diameter of 57 mm; it is located at the radial center of the axial middle of the output system box 0103, and the hub is fastened to the middle part of the output wheel shaft 151, and the gear teeth are engaged with the outside of the output transmission wheel 14; the output wheel shaft 151 is mounted on both sides with bearings in the bearing seat 0123 for mounting the output wheel shaft prefabricated at the center position of the box wall on both sides of the axial direction of the output system box 0103, and the extended shaft 152 of the output wheel shaft at one end extends to the outside of the bearing seat 0123.The above-mentioned gear transmission mechanism: ① In the direction of gear rotation, the starting planetary gear 21 rotates in the forward direction, and the ending planetary gear 26 rotates in the reverse direction; ② In terms of gear transmission ratio, the inner ring gear 12 drives the starting planetary gear 21, the starting coaxial planetary gear 22 drives the first idler gear 23, the first idler gear 23 drives the second idler gear 24, the second idler gear 24 drives the ending coaxial planetary gear 25, and the ending planetary gear 26 rolls and rotates along the teeth of the sun gear 11. The average transmission ratio of each gear transmission level is 95%; ③ In terms of gear specifications, the number of teeth (34) and diameter (102mm) of the ending coaxial planetary gear 25 are twice the number of teeth (17) and diameter (51mm) of the ending planetary gear 26; ④ In terms of gear orbital diameter, the diameter of the starting planetary gear 21 (pushed by the inner ring gear) in the forward direction is 141mm, and the diameter of the ending planetary gear 26 in the reverse direction is 153mm; ⑤ The installation position of the planetary gear shaft on the planet carrier The angle 212 between the meshing point of the starting planetary gear shaft 211 and the inner gear ring 12 and the meshing point of the starting planetary gear shaft 211 and the first idler gear 23 is 73.5° (the lever angle with the starting planetary gear shaft 211 as the fulcrum is -16.5°, and the length of the lever resistance arm is 8.8 mm), and the angle 262 between the meshing point of the end planetary gear shaft 261 and the sun gear 11 and the meshing point of the end planetary gear shaft 261 and the second idler gear 24 is 114.5° (the meshing point of the end planetary gear shaft 211 as the fulcrum is -16.5°, and the length of the lever resistance arm is 8.8 mm). The lever angle with shaft 261 as the fulcrum is 24.5°, and the length of the lever power arm is 21.21 mm); ⑥ In terms of the gear ratio, the gear ratio of the sun gear 11 to the terminal planetary gear 26 (34 / 17) is equal to the gear ratio of the inner ring gear 12 to the terminal coaxial planetary gear 25 (68 / 34), or the gear ratio of the sun gear 11 to the inner ring gear 12 (34 / 68) is equal to the gear ratio of the terminal planetary gear 26 to the terminal coaxial planetary gear 25 (17 / 34).

[0022] How it works

[0023] When the screw knob disk 325 on the knob screw type force device 32 is rotated in the clockwise or counterclockwise direction with sufficient force, the inclined surface of the thread 326 on the screw generates friction with the inclined surface of the thread in the middle nut 322 of the force beam, thereby pushing the force beam 321 to move upward or downward along the screw 324; the upward or downward movement of the force beam 321 drives the end force point 312 of the driving rod connected to the circular shaft 323 at both ends of the force beam to be forced upward or downward; the end force point 312 of the driving rod is forced upward or downward, and the input wheel extension shaft 132 fastened to the starting end shaft hole 311 of the driving rod is twisted to rotate in the direction of the force, thereby driving the input wheel 13 to rotate; the rotation of the input wheel 13 drives the force gear teeth 123 of the inner ring gear to rotate, thereby driving the inner ring gear 12 to rotate in the positive direction. When the inner ring gear 12 rotates in the forward direction, it sequentially drives the starting planetary gear 21 and the starting coaxial planetary gear 22 mounted on the combined planetary carrier 33 to rotate in the forward direction, the number one idler gear 23 to rotate in the reverse direction, the number two idler gear 24 to rotate in the forward direction, the end coaxial planetary gear 25 and the end planetary gear 26 to rotate in the reverse direction, and stops at the (unable to rotate) sun gear 11. This gear transmission state, under the action of the combined planetary carrier 33, sequentially produces the following operating characteristics: ① As the forward-rotating inner ring gear 12 drives the starting planetary gear 21 mounted on the combined planetary carrier 33 to rotate forward, its teeth pull the starting planetary gear 21 to revolve in the forward direction, thereby generating a forward-rotating torque on the combined planetary carrier 33 driven by the starting planetary gear shaft 211. Simultaneously, as the final planetary gear 26 mounted on the combined planetary carrier 33 is supported by the (immovable) sun gear 11 during its reverse rotation, it rolls and revolves in the reverse direction along the teeth of the sun gear 11, thereby generating a reverse-rotating torque on the combined planetary carrier 33 driven by the final planetary gear shaft 261. Consequently, a state is formed on the combined planetary carrier 33 where the forward-rotating torque of the starting planetary gear axis point 3321 counteracts the reverse-rotating torque of the final planetary gear axis point 3326. (The circumferential force and torque of the number one idler gear 23 rotating in the reverse direction and the number two idler gear 24 rotating in the forward direction mounted on the planet carrier 33 do not affect the rotation direction of the combined planet carrier 33.) ② Since the average transmission ratio of each gear transmission stage is 95%, the circumferential force of the terminal coaxial planetary gear 25 rotating in the reverse direction, after passing through four stages of gear (gear teeth) transmission (the initial coaxial planetary gear 22 drives the number one idler gear 23, the number one idler gear 23 drives the number two idler gear 24, the number two idler gear 24 drives the terminal coaxial planetary gear 25, and the terminal planetary gear 26 rolls and rotates along the gear teeth of the sun gear 11), still reaches 81.45% of the circumferential force of the initial planetary gear 21 rotating in the forward direction (pushed by the inner ring gear);Since the number of teeth (34) and diameter (102 mm) of the end coaxial planetary gear 25 are twice the number of teeth (17) and diameter (51 mm) of the end planetary gear 26, the circumferential force of the end planetary gear 26 in the reverse direction is twice the circumferential force of the end coaxial planetary gear 25, and 1.629 times the circumferential force of the start planetary gear 21 in the forward direction (the ratio of the circumferential force of the end coaxial planetary gear 25 in the reverse direction to the circumferential force of the start planetary gear 21 in the forward direction is 81.45% x the circumferential force of the end coaxial planetary gear 26 in the reverse direction). =Radius 25 51mm ÷ radius 25.5mm of the end planetary gear 26); Since the angle 212 between the meshing point of the starting planetary gear shaft 211 and the inner gear ring 12 (pushed by the inner gear ring) and the meshing point of the starting planetary gear shaft 211 and the first idler gear 23 is 73.5° (the lever angle with the starting planetary gear shaft 211 as the fulcrum is -16.5°, and the lever resistance arm length is 8.8mm), the starting planetary gear shaft 211 (pushed by the inner gear ring) is rotated in the positive direction under the action of the lever principle. The circumferential force of the positive revolution is reduced by 27.936% compared with the circumferential force of the starting planetary gear 21 in the positive direction (the lever resistance arm length with the starting planetary gear shaft 211 as the fulcrum is 8.8mm ÷ the radius of the starting coaxial planetary gear 22 is 31.5mm); on the contrary, since the angle 262 between the meshing point of the end planetary gear shaft 261 to the sun gear 11 and the meshing point of the end planetary gear shaft 261 to the second idler gear 24 in the reverse revolution is 114.5° (the lever angle with the end planetary gear shaft 261 as the fulcrum is 2 4.5°, the lever power arm length is 21.21 mm), so that under the action of the lever principle, the circumferential force of the end planetary gear shaft 261 in the reverse revolution is increased by 20.794% compared with the circumferential force of the end planetary gear 26 in the reverse rotation (the lever power arm length 21.21 mm with the end planetary gear shaft 261 as the fulcrum ÷ the radius 51 mm of the end coaxial planetary gear 25 × the ratio of the circumferential force of the end coaxial planetary gear 25 in the reverse rotation to the circumferential force of the end planetary gear 26 in the reverse rotation is 1 / 2);This decrease and increase makes the circumferential force of the end planetary gear shaft 261 in the reverse revolution greater than the circumferential force of the start planetary gear shaft 211 in the forward revolution (pushed by the inner gear ring) by 1.73053 times [the ratio of the circumferential force of the end planetary gear shaft 261 in the reverse revolution to the circumferential force of the start planetary gear 21 in the forward revolution is 196.773% (the circumferential force of the end planetary gear shaft 261 in the reverse revolution is 20.794% greater than the circumferential force of the end planetary gear 26 in the reverse revolution) x the circumferential force of the end planetary gear 26 in the reverse revolution to the circumferential force of the start planetary gear 21 in the forward revolution is 20.794% greater than the circumferential force of the end planetary gear 26 in the reverse revolution Ratio of the circumferential force of the planetary gear 21 rotating in the forward direction (162.9%) + Ratio of the circumferential force of the planetary gear 26 rotating in the reverse direction to the circumferential force of the planetary gear 21 rotating in the forward direction (162.9%) / Ratio of the circumferential force of the planetary gear shaft 211 rotating in the forward direction to the circumferential force of the planetary gear 21 rotating in the forward direction (72.064%) (Circumferential force of the planetary gear 21 rotating in the forward direction minus the circumferential force of the planetary gear shaft 211 rotating in the forward direction compared to the circumferential force of the planetary gear 21 rotating in the forward direction (27.936%)).Since the diameter of the end planetary gear shaft 261 in the reverse revolution (153 mm) is larger than the diameter of the start planetary gear shaft 211 in the forward revolution (141 mm) (pushed by the inner ring gear), the force arm of the end planetary gear shaft 261 pushing the combined planetary carrier 33 in the reverse revolution is larger than the force arm of the start planetary gear shaft 211 pushing the combined planetary carrier 33 in the forward revolution, thereby making the reverse torque on the combined planetary carrier 33 1.96291 times larger than the forward torque (the ratio of the circumferential force of the end planetary gear shaft 261 in the reverse revolution to the circumferential force of the start planetary gear shaft 211 in the forward revolution is 273.053% × the diameter of the end planetary gear shaft 261 in the reverse revolution 153 mm ÷ the diameter of the start planetary gear shaft 211 in the forward revolution 141 mm). Therefore, under the condition of an average transmission ratio of 95% for each gear stage, the planetary gears and the planetary carrier exert a lever effect during the transmission process, ultimately causing the torque on the combined planetary carrier 33 to rotate in the reverse direction to be 1.96291 times greater than the torque on the combined planetary carrier 33 in the forward direction, thereby forcing the combined planetary carrier 33 to rotate strongly in the reverse direction. ③ Because all planetary gear shafts are mounted on the combined planetary carrier 33, when the combined planetary carrier 33 rotates strongly in the reverse direction, it forcibly drives all planetary gears to revolve in the reverse direction. ④ Because the teeth of the forward-rotating inner ring gear 12 pull the teeth of the starting planetary gear 21 in the forward direction while driving the starting planetary gear 21 in the forward direction, the starting planetary gear 21, when forcibly driven in the reverse direction by the strongly reverse-rotating combined planetary carrier 33, revolves in the reverse direction along the teeth of the inner ring gear 12, thereby dragging the inner ring gear 12, which is rotating in the forward direction, in the reverse direction. ⑤ Since the gear ratio (68 / 34) between the inner ring gear 12 and the terminal coaxial planetary gear 25 is equal to the gear ratio (34 / 17) between the sun gear 11 and the terminal planetary gear 26, the angle of the forced reverse rotation of the combined planetary carrier 33 is the same as the angle of the forward rotation of the inner ring gear 12. This causes the starting planetary gear 21, which is dragging the inner ring gear 12 in the reverse direction (forced by the combined planetary carrier 33), to roll along the teeth of the inner ring gear 12 in the reverse direction to an angle that exactly offsets the angle of the inner ring gear 12's forward rotation, thereby ensuring that the inner ring gear 12, which is rotating in the forward direction, always maintains its original rotation angle. ⑥ Since the rotation angle of the inner gear ring 12 remains unchanged, the rotation angle of the input wheel 13 that is in external mesh with the force-bearing gear teeth 123 of the inner gear ring also remains unchanged; since the rotation angle of the input wheel 13 remains unchanged, the parallel angle of the drive rod 31 that is tightly connected to the input wheel extension shaft 132 remains unchanged, thereby causing the force exerted by the screw-type force-generating device 32 on the end point 312 of the drive rod to remain unchanged. In this state, the end point 312 of the drive rod continues to receive the force (expressed as potential energy) exerted by the screw-type force-generating device 32. ⑦ Since the end point 312 of the drive rod continues to receive the force exerted by the screw-type force-generating device 32, the end point 312 of the drive rod continues to be stressed;When the force point 312 at the end of the driving rod is continuously subjected to force, the input wheel extension shaft 132 that is tightly connected to the shaft hole 311 at the starting end of the driving rod is continuously twisted, thereby driving the input wheel 13 to continuously rotate. ⑧ As the input wheel 13 rotates continuously, it continuously transmits the force-bearing gear teeth 123 of the inner ring gear, driving the inner ring gear 12 to rotate continuously in the forward direction; as the inner ring gear 12 rotates continuously in the forward direction, it continuously transmits the planetary gears on the combined planetary carrier 33 to rotate; as the planetary gears rotate continuously, the end planetary gear 26 continuously rolls and revolves in the reverse direction along the gear teeth of the sun gear 11 under the support of the sun gear 11, thereby using the wheel shaft 261 to push the combined planetary carrier 33 to rotate continuously and strongly in the reverse direction at the same rotation angle of the inner ring gear 12; and as the combined planetary carrier 33 continuously rotates in the reverse direction at the same rotation angle of the inner ring gear 12, it forcibly drives the starting planetary gear 21 rotating in the forward direction to continue to roll and revolve in the reverse direction along the gear teeth of the inner ring gear 12 at the same rotation angle of the inner ring gear 12, thereby continuously dragging the inner ring gear 12 in the reverse direction, causing the inner ring gear 12 rotating in the forward direction to always maintain the original rotation angle unchanged... This cycle repeats, thereby achieving continuous operation of the machine. 9. Because the output transmission wheel 14 is securely connected to the outer ring frame 331 of the combined planetary carrier 33, the continued reverse rotation of the combined planetary carrier 33 drives the output transmission wheel 14 to rotate in the same direction. 10. Because the output wheel 15 is meshed with the outside of the output transmission wheel 14, the continued reverse rotation of the output transmission wheel 14 drives the output wheel 15 to rotate in the forward direction. The continued forward rotation of the output wheel 15 continuously transmits a portion of the rotational kinetic energy via the extended shaft 152 to perform work.

[0024] When the screw knob disk 325 on the screw-type force device 32 is turned in the reverse direction, the inclined surface of the thread 326 on the screw loosens the friction with the inclined surface of the thread in the middle nut 322 of the force beam, thereby stopping the screw-type force device 32 from exerting force; when the screw-type force device 32 stops exerting force, the drive rod 31 stops being subjected to force; when the drive rod 31 stops being subjected to force, it stops twisting the input wheel extension shaft 132, and the engine stops working.

[0025] In summary, the operating principle of the present invention can be logically divided into five steps: the first step is to use the force generator to exert force on the energy input end of the machine (the end point 312 of the driving rod); the second step is to use the inner ring gear 12 rotating in the forward direction to drive the planetary gear to rotate under the driving force; the third step is to use the fixed sun gear 11 to support the end planetary gear 26 rotating in the reverse direction, so as to cause the end planetary gear 26 to roll and revolve in the reverse direction along the gear teeth of the sun gear 11, thereby using the wheel shaft 261 to push the combined planetary carrier 33 to rotate in the reverse direction; the fourth step is to use the lever principle to amplify the circumferential force of the end planetary gear shaft 261 rotating in the reverse direction and reduce the circumferential force of the starting planetary gear shaft 211 (under the pull of the inner ring gear) The circumferential force of the forward revolution, the amplification of the torque of the combined planetary carrier 33 in the reverse rotation, and the reduction of the torque of the combined planetary carrier 33 in the forward rotation make the reverse torque on the combined planetary carrier 33 much greater than the forward torque, thereby strongly rotating in the reverse direction and forcibly driving all the planetary gears to revolve in the reverse direction; the fifth step is to use the operating principle of the combined planetary carrier 33 rotating in the reverse direction and the inner gear ring 12 rotating in the forward direction to rotate synchronously in the reverse direction, so as to prompt the inner gear ring 12 rotating in the forward direction to maintain the rotation angle unchanged during the rotation of the driving planetary gear, thereby causing the force exerted by the force generator on the energy input end of the machine (the end point 312 of the driving rod) to remain unchanged, thereby continuously driving the machine to operate until it stops.

[0026] For those skilled in the art, according to the teachings of the present invention, without departing from the principles and spirit of the present invention, changes, modifications, substitutions and variations to the implementation methods are still within the scope of protection of the present invention.

[0027] Energy Operation Analysis: From the above embodiments and working principles, it can be seen that the reason why an engine driven by the force generated by the power generator can continuously operate by using the force generated by the power generator is that, under the condition that the power generator exerts sufficient force on the end point 312 of the drive rod, the force exerted by the power generator on the end point 312 of the drive rod can remain unchanged during the process of twisting the input wheel extension shaft 132 (thereby driving the engine), thereby providing a continuous force for continuously twisting the input wheel extension shaft 132. Among them:

[0028] ① The reason why the force exerted by the power generator on the end point 312 of the driving rod can remain unchanged is that the parallel angle of the driving rod 31 remains unchanged; the reason why the parallel angle of the driving rod 31 remains unchanged is that the rotation angle of the input wheel extension shaft 132 tightly connected to its starting shaft hole 311 remains unchanged; the reason why the rotation angle of the input wheel extension shaft 132 and the input wheel 13 remains unchanged is that the rotation angle of the inner gear ring 12 remains unchanged.

[0029] ② The reason the rotation angle of the inner ring gear 12 remains constant is due to the operating principle that the combined planetary carrier 33, which is forced to rotate in the reverse direction, rotates synchronously with the inner ring gear 12, which is rotating in the forward direction. Specifically, the inner ring gear 12 continuously rotates in the forward direction under the drive of the input gear 13, and during this rotation, it continuously drives the starting planetary gear 21 in the forward direction. However, because the angle of the inner ring gear 12's forward rotation is the same as the angle at which the combined planetary carrier 33 forcibly drives the starting planetary gear 21 to roll in the reverse direction along the teeth of the inner ring gear 12, the angle of the inner ring gear 12's forward rotation is replaced by the same angle at which the combined planetary carrier 33 forcibly drives the starting planetary gear 21 to roll in the reverse direction along the teeth of the inner ring gear 12, resulting in the inner ring gear 12 maintaining its original rotation angle. Because the angle at which the combined planetary carrier 33 forcibly drives the starting planetary gear 21 to roll and revolve in the reverse direction along the teeth of the inner ring gear 12 is equal to the angle at which the inner ring gear 12 rotates in the forward direction, we can calculate the angle and speed at which the inner ring gear 12 rotates in the forward direction using the angle and speed at which the combined planetary carrier 33 forcibly drives the starting planetary gear 21 to roll and revolve in the reverse direction along the teeth of the inner ring gear 12. Just like a person running on a human-powered treadmill, when they run forward, their legs push backward, causing the running belt to rotate backward. When the running belt's backward speed equals the person's forward speed, the speed and distance of the running belt's backward rotation offset the person's forward speed and distance. At this point, although the person is running forward, they appear to be running in place. Obviously, this phenomenon should not be interpreted as the person not running forward. Since the speed and distance of the person's forward running are the same as the speed and distance of the running belt's backward rotation, and the energy driving the running belt's backward rotation comes from the person's forward running, we can calculate the person's forward running speed and distance on the treadmill by measuring the running belt's backward speed and distance.

[0030] ③ The reason why the angle of the inner ring gear 12's forward rotation can be replaced by the same angle at which the combined planetary carrier 33 forcibly drives the starting planetary gear 21 to roll and orbit in the reverse direction along the teeth of the inner ring gear 12 is because the combined planetary carrier 33 forcibly drives the starting planetary gear 21 to roll and orbit in the reverse direction along the teeth of the inner ring gear 12 at the same rotation angle as the inner ring gear 12. Principle: Because the teeth of the starting planetary gear 21 are pulled forward by the inner ring gear 12, while the axle is forcibly driven in the reverse direction by the combined planetary carrier 33, the starting planetary gear 21 continues to roll and orbit in the reverse direction along the teeth of the inner ring gear 12, pulled by the teeth of the inner ring gear 12. Because the angle at which the combined planet carrier 33 forcibly drives the starting planet gear 21 to roll and orbit along the teeth of the inner ring gear 12 in the reverse direction is the same as the angle at which the inner ring gear 12 rotates in the forward direction, the starting planet gear 21, driven by the combined planet carrier 33, rolls and orbits along the teeth of the inner ring gear 12 in the reverse direction by the same amount as the inner ring gear 12 rotates in the forward direction. In terms of the number of teeth, the teeth of the inner ring gear 12 pull the starting planet gear 21 forward by the same amount; and conversely, the starting planet gear 21, driven by the combined planet carrier 33, rolls and orbits along the teeth of the inner ring gear 12 in the reverse direction by the same amount as the teeth of the inner ring gear 12 rotate in the forward direction. This ensures that the inner ring gear 12 maintains its original rotation angle while its teeth pull the starting planet gear 21 in the forward direction.

[0031] ④ The reason why the combined planetary carrier 33 can forcibly drive the starting planetary gear 21 to roll and revolve in the reverse direction along the teeth of the inner ring gear 12 is that the reverse torque on the combined planetary carrier 33 is much greater than the forward torque; and the reason why the combined planetary carrier 33 can rotate in the reverse direction at the same angle as the inner ring gear 12 is that the tooth ratio of the end coaxial planetary gear 25 to the inner ring gear 12 is equal to the tooth ratio of the end planetary gear 26 to the sun gear 11.

[0032] ⑤ The reason why the reverse torque on the combined planetary carrier 33 is much greater than the forward torque is that under the condition that the average transmission rate of each gear transmission level reaches 95%, the planetary gears and the planetary carrier utilize multiple lever technologies in the transmission process. First, the number of teeth and diameter of the coaxial planetary gear 25 at the end is twice that of the planetary gear 26 at the end, so that after removing the energy loss in the 4-stage gear transmission, the circumferential force of the planetary gear 26 in the reverse direction is still 62.9% greater than the circumferential force of the planetary gear 21 in the forward direction at the beginning; second, the lever angle with the planetary gear shaft 211 at the beginning is adjusted to -16.5°, so that the circumferential force of the planetary gear shaft 211 in the forward direction (pushed by the inner gear ring) at the beginning is 27.936% smaller than the circumferential force of the planetary gear shaft 261 in the forward direction; third, the lever angle with the planetary gear shaft 261 at the end is adjusted to 24.5°, so that the circumferential force of the planetary gear shaft 261 in the reverse direction is The circumferential force of the combined planetary carrier 33 is 20.794% greater than the circumferential force of the final planetary gear 26 in reverse rotation and 1.730 times greater than the circumferential force of the initial planetary gear shaft 211 in forward orbit (driven by the inner ring gear). Fourthly, the diameter of the final planetary gear shaft 261 in reverse orbit is larger than the diameter of the initial planetary gear shaft 211 in forward orbit (driven by the inner ring gear). This causes the lever arm of the final planetary gear shaft 261 in reverse orbit on the combined planetary carrier 33 to be larger than the lever arm of the initial planetary gear shaft 211 in forward orbit (driven by the inner ring gear). This further increases the reverse torque on the combined planetary carrier 33, making it 1.963 times greater than the forward torque. This 95% gear ratio, coupled with the four-lever technology used in the transmission process between the planetary gears and the planetary carrier, ensures that the torque of the combined planetary carrier 33 in reverse rotation is far greater than the torque in forward rotation.

[0033] ⑥ Because the reverse torque on the combined planetary carrier 33 is much greater than the forward torque, after the reverse torque on the combined planetary carrier 33 is partially offset by the forward torque, a portion of the reverse torque can still be converted into kinetic energy to strongly drive the machine operation and transmit it to work. Since the forward torque on the combined planetary carrier 33 comes from the energy of the inner ring gear 12 rotating in the forward direction, the portion of the reverse torque offset by the forward torque is the energy consumed by the combined planetary carrier 33 when the teeth of the inner ring gear 12 drag the inner ring gear 12 during the reverse rolling revolution (keeping the inner ring gear 12 at its original rotation angle during operation). Thus, the energy conservation state of the machine during operation is: the reverse torque (kinetic energy + potential energy) on the combined planetary carrier 33 = the forward torque (potential energy) on the combined planetary carrier 33 + the reverse torque (kinetic energy) on the combined planetary carrier 33. In other words, the reverse torque (kinetic energy) on the combined planetary carrier 33 = the reverse torque (kinetic energy + potential energy) on the combined planetary carrier 33 - the forward torque (potential energy) on the combined planetary carrier 33. The rotational speed is determined by the force-speed ratio of the combined planetary carrier 33 in the reverse direction. The greater the torque (kinetic energy) of the combined planetary carrier 33 in the reverse direction, the faster the rotational speed. Assuming that the force-speed ratio of the reverse rotation of the terminal planetary gear axis point 3326 on the combined planetary carrier 33 is 1N / 1mm / second, if the reverse torque (kinetic energy) of the combined planetary carrier 33 is 1000Nm, then its idling speed should be: (1000Nm ÷ the orbital radius of the terminal planetary gear 26 76.5mm × 1000) ÷ the orbital diameter of the terminal planetary gear 26 153mm ÷ 3.1416 = 27r / s.

[0034] ⑦ The force exerted by the generator on the end point 312 of the drive rod remains constant, manifesting as potential energy. This potential energy is transmitted to the input wheel 13 by the drive rod 31 twisting the input wheel extension shaft 132. The input wheel 13 then transmits this potential energy to the internal ring gear 12 through the meshing force-bearing teeth 123 of the internal ring gear. This energy is then converted into kinetic energy by the internal ring gear 12, which then drives the starting planetary gear 21 in the forward direction. Finally, the combined planetary carrier 33, which rotates in the reverse direction, forcibly drives the starting planetary gear 21 to roll in the reverse direction along the teeth of the internal ring gear 12, dragging the internal ring gear 12 with its teeth, causing the internal ring gear 12 to maintain its original rotation angle. This maintains the force exerted by the generator on the end point 312 of the drive rod. In this process of continuous conversion of potential energy into kinetic energy, and then of kinetic energy continuously driving potential energy to remain constant, the various energy transmission and operating links of the engine are in a state of tension, pushing or pulling against each other. In this tensioned state, each energy transmission and operation link operates in unison, interconnected, and coordinated, seamlessly moving forward. There's only a logical sequence between them, no gaps in time or space. Therefore, as soon as the force generator applies sufficient force to the end point 312 of the drive rod, the driven drive rod 31 instantly drives the inner ring gear 12 in the forward direction via the input gear 13 and the inner ring gear's force-bearing teeth 123. The forward-rotating inner ring gear 12 then instantly drives the starting planet gear 21 in the forward direction... Simultaneously, the strongly reverse-rotating combined planet carrier 33 also forcibly drives the starting planet gear 21 in a reverse rolling orbital motion along the teeth of the inner ring gear 12, thereby instantly replacing the inner ring gear 12's rotation angle, causing the inner ring gear 12 to maintain its original rotation angle... As long as the force applied by the generator to the end point 312 of the drive rod is not withdrawn, the continuously stressed drive rod 31 will continue to drive the inner ring gear 12 in forward rotation via the input wheel 13 and the inner ring gear's force-bearing teeth 123. The inner ring gear 12, which continues to rotate in the forward direction, in turn continues to drive the starting planetary gear 21 in forward rotation. Simultaneously, the combined planetary carrier 33, which continues to rotate strongly in the reverse direction, also forcibly drives the starting planetary gear 21 to roll and revolve in the reverse direction along the teeth of the inner ring gear 12, thereby continuously replacing the rotation angle of the inner ring gear 12 and ensuring that the inner ring gear 12 remains at its original rotation angle. It is precisely this energy-generating state of the engine that ensures that the force applied by the generator to the end point 312 of the drive rod remains constant, thereby providing a continuous force to continuously twist the input wheel extension shaft 132, thereby driving the machine to continue operating.

Claims

1. The engine driven by the force generated by the power generator of the present invention comprises a fixing system, a power generating system, an input system, a rotation system and an output system; wherein: The fixed system consists of a box and two star gears, the power generation system consists of a power generator, the input system consists of two inner rings, two input wheels and two drive rods, the rotating system consists of a combined planetary carrier, four starting planetary gears, two starting coaxial planetary gears, two No. 1 idler gears, two No. 2 idler gears, two end coaxial planetary gears and four end planetary gears, and the output system consists of an output transmission wheel and an output wheel.

2. The housing described in Item 1 is both the sealed outer shell of the machine and the shaft seat for installing and supporting the star gear shaft, input gear shaft and output gear shaft. It is located on the outside of the machine and seals the gear transmission mechanism of the machine inside; it is shaped like three connected cylinders, with the rotating system housing in the middle and the input system housing and the output system housing at the radial ends respectively; a shaft seat for fastening and installing the star gear shaft is prefabricated at the center position of the box wall on both axial sides of the rotating system housing, a bearing seat for installing the input gear shaft is prefabricated at the center position of the box wall on both axial sides of the input system housing, and a bearing seat for installing the output gear shaft is prefabricated at the center position of the box wall on both axial sides of the output system housing.

3. The two star gears described in Item 1 are cylindrical external gears with a diameter smaller than the inner gear ring and larger than the starting planetary gear and the ending planetary gear; they are respectively located at the radial center positions on both sides of the axial direction of the combined planetary carrier in the rotating system housing, on the same axis as the combined planetary carrier and the inner gear ring, and the wheel hubs are respectively fastened and installed on both sides of the star gear shaft, and the gear teeth are engaged with the outside of the end planetary gear; the two ends of the star gear shaft are respectively fastened and installed in the shaft seats for installing the star gear shaft prefabricated at the center position of the box wall on both sides of the axial direction of the rotating system housing, and cannot rotate.

4. The two inner gear rings described in item 1 are cylindrical internal gears with a diameter larger than that of the sun gear and the coaxial planetary gear at the end; they are respectively located at the radial center positions on both sides of the axial direction of the rotating system housing, on the same axis as the combined planetary carrier and the sun gear, and the gear teeth are meshed with the inner of the starting planetary gear; the axial edge of the inner gear ring close to the housing wall is fastened or integrated with the inner gear ring support bracket, and a hollow shaft facing the inner side of the inner gear ring is prefabricated at the radial center position of the inner gear ring support bracket (i.e. the radial center position of the inner gear ring), and the inner gear ring is connected to the inner side of the inner gear ring through this hollow shaft. The shafts are respectively installed and supported on both sides of the sun gear shaft (installed with bearings or in a sliding state); a force-bearing gear tooth of the inner gear ring composed of several gear teeth of a cylindrical external gear is prefabricated on the side of the radial outer ring of the inner gear ring close to the input wheel. The force-bearing gear teeth of the inner gear ring are fastened or integrated with the outer wall of the inner gear ring or the inner gear ring support bracket, meshing with the outside of the input wheel, and driving the inner gear ring to rotate in the positive direction under the transmission of the input wheel (Note: the rotation direction of the inner gear ring is defined as the positive direction, and the direction of rotation of other gears after the inner gear ring is based on this, the same below).

5. The two input wheels described in item 1 are cylindrical external gears, which are respectively located at the radial center positions on both sides of the axial direction of the input system housing. The wheel hubs are respectively fastened and installed on both sides of the input wheel shaft, and the gear teeth are externally meshed with the force-bearing gear teeth of the inner gear ring; the two sides of the input wheel shaft are respectively installed with bearings in the bearing seats for installing the input wheel shaft prefabricated at the center positions of the box walls on both sides of the axial direction of the input system housing; the protruding shafts at both ends of the input wheel shaft extend to the outside of the bearing seats respectively, and are fastened to the shaft holes prefabricated at the starting end of the drive rod, and rotate under the torsion of the starting end of the drive rod, thereby driving the input wheel to rotate.

6. The two driving rods described in item 1 are parallel rods that receive the force generated by the force generator and use the force to twist the input wheel axle. They are respectively located on both axial sides outside the input system box. An axial hole is prefabricated at the starting end of the driving rod and is tightly connected to the extended shaft of the input wheel axle. A fulcrum is set at the end of the driving rod and is connected to the force-generating end of the force generator. The driving rod swings upward or downward under the condition that the force generator exerts an upward pushing or downward dragging force on the fulcrum at the end of the driving rod, thereby driving the starting end of the driving rod to twist the extended shaft of the input wheel axle that is tightly connected to the axial hole at the starting end of the driving rod to rotate.

7. The force generator described in Item 1 is a device that exerts a force on the end point of the drive rod, and is composed of an instrument (such as a jack, electric hoist, winch, etc.) or a gravity object that can exert an upward pushing or downward pulling force on the end point of the drive rod of the engine, causing the end point of the drive rod to be forced upward or downward, and can keep the exerted force constant (expressed as potential energy) under the condition that the parallel angle of the drive rod remains unchanged; it is located radially outside the input system box, and its force-generating end is connected to the end point of the drive rod.

8. The combined planetary carrier described in Item 1 is a cylindrical planetary gear carrier consisting of an outer ring frame and two planetary gear carriers. It is located at the radial center position in the axial middle of the rotating system housing and is on the same axis as the inner gear ring and the sun gear. It is mounted and supported on the sun gear shaft by bearings through bearing seats for mounting the sun gear shaft prefabricated at the radial center position of the two planetary gear carriers. It rotates in the opposite direction under the push of the end planetary gear shaft revolving in the opposite direction; the outer ring frame is a cylindrical frame for mounting and fixing the two planetary gear carriers, located at the radial outer ring of the combined planetary carrier; the two planetary gear carriers are side plates for mounting the planetary gear shafts, located on both axial sides of the outer ring frame, and the two planetary gear carriers have two bearing seats for mounting the starting planetary gear shaft, two for mounting the number one idler gear shaft, two for mounting the number two idler gear shaft and two for mounting the end planetary gear shaft prefabricated at radially symmetrical positions, and one bearing seat for mounting the sun gear shaft is prefabricated at the radial center position; the radial edges of the two planetary gear carriers are fastened to the axial edges on both sides of the outer ring frame.

9. The four starting planetary gears described in item 1 are cylindrical external gears with a diameter smaller than the sun gear and the terminal coaxial planetary gears; two of them are located in radially symmetrical positions in the inner gear ring on both sides of the outer axial direction of the combined planetary carrier, and the gear teeth are engaged with the inner gear ring and rotate in the positive direction under the drive of the inner gear ring; the two sides of the two starting planetary gear shafts are respectively mounted with bearings in the bearing seats for mounting the starting planetary gear shafts prefabricated at symmetrical positions on the two sides of the planetary carrier, and the protruding shafts at both ends of the two starting planetary gear shafts extend to the inner sides of the inner gear ring on both sides of the outer axial direction of the combined planetary carrier; the hubs of the starting planetary gears are respectively fastened and mounted on the protruding shafts of the two starting planetary gear shafts.

10. The two coaxial starting planetary gears described in Item 1 are cylindrical external gears with the same module, number of teeth and diameter as the starting planetary gears. They are respectively located in radially symmetrical positions in the axial middle of the combined planetary carrier, and the gear teeth are engaged with the outer surface of the idler gear No.

1. They are coaxial with the starting planetary gear, and the hubs are respectively fastened and mounted in the middle part of the two starting planetary gear shafts, and rotate in the forward direction under the drive of the starting planetary gear shafts.

11. The two No. 1 idler gears described in Item 1 are cylindrical external gears, which are respectively located in radially symmetrical positions in the axial middle of the combined planetary carrier. The wheel hubs are respectively fastened and installed in the middle parts of the two No. 1 idler gear shafts. The front gear teeth are engaged with the external part of the coaxial planetary gear at the starting end, and the rear gear teeth are engaged with the external part of the No. 2 idler gear. They rotate in opposite directions under the drive of the coaxial planetary gear at the starting end; the two ends of the two No. 1 idler gear shafts are respectively mounted with bearings in bearing seats for mounting the No. 1 idler gear shafts, which are prefabricated in symmetrical positions on the two sides of the planetary carriers.

12. The two No. 2 idler gears described in Item 1 are cylindrical external gears, which are respectively located in radially symmetrical positions in the axial middle of the combined planetary carrier. The wheel hubs are respectively fastened and mounted in the middle parts of the two No. 2 idler gear shafts. The front gear teeth are meshed with the outer portion of the No. 1 idler gear, and the rear gear teeth are meshed with the outer portion of the coaxial planetary gear at the end. They rotate in the forward direction under the drive of the No. 1 idler gear. The two ends of the two No. 2 idler gear shafts are respectively mounted with bearings in bearing seats for mounting the No. 2 idler gear shafts, which are prefabricated in symmetrical positions on the two planetary carriers.

13. The two coaxial planetary gears at the end described in Item 1 are cylindrical external gears with a diameter smaller than the inner ring gear and larger than the starting planetary gear and the ending planetary gear. They are respectively located in radially symmetrical positions in the axial middle of the combined planetary carrier, are coaxial with the ending planetary gears, and have wheel hubs fastened to the middle parts of the two ending planetary gear shafts; the gear teeth are engaged with the outer surface of the No. 2 idler gear and rotate in the opposite direction under the drive of the No. 2 idler gear.

14. The four terminal planetary gears described in Item 1 are cylindrical external gears with a diameter smaller than the sun gear and the terminal coaxial planetary gear; two of them are located in radially symmetrical positions on both sides of the axial direction within the combined planetary carrier, and the hubs are fastened and mounted on both sides of the two terminal planetary gear shafts; they are coaxial with the terminal coaxial planetary gears, and the gear teeth are meshed with the outer side of the sun gear. They rotate in the opposite direction under the drive of the terminal planetary gear shaft and roll and revolve in the opposite direction along the gear teeth of the sun gear; the two ends of the two terminal planetary gear shafts are respectively mounted with bearings in bearing seats for mounting the terminal planetary gear shafts which are prefabricated in symmetrical positions on the two sides of the planetary carriers.

15. The output transmission wheel described in item 1 is a cylindrical external gear, which is located in the axial middle position of the radial outer ring of the outer ring frame of the combined planetary frame, is tightly connected to or integrated with the outer ring frame, and rotates in the opposite direction under the drive of the combined planetary frame; the gear teeth are engaged with the outside of the output wheel.

16. The output wheel described in item 1 is a cylindrical external gear, which is located in the radial center of the axial middle of the output system housing. The hub is tightly installed in the middle part of the output wheel shaft. The gear teeth are engaged with the outside of the output power transmission wheel and rotate in the positive direction under the transmission of the output power transmission wheel. The two sides of the output wheel shaft are respectively installed with bearings in the bearing seats for installing the output wheel shaft prefabricated at the center position of the box wall on both sides of the axial direction of the output system housing, and one end or both ends of the output wheel extend out of the bearing seat.

17. For the sun gear, ring gear, starting planetary gear, starting coaxial planetary gear, number one idler gear, number two idler gear, final coaxial planetary gear, and final planetary gear described in items 1, 3, 4, and 9-14, the average transmission ratio of each gear transmission stage must be 85% or higher during the process of the ring gear driving the starting planetary gear, the starting coaxial planetary gear driving the number one idler gear, the number one idler gear driving the number two idler gear, the number two idler gear driving the final coaxial planetary gear, and the final planetary gear rolling along the sun gear teeth.

18. Regarding the orbital diameters of the starting and ending planetary gears described in Items 1, 9, and 14, the diameter of the ending planetary gear in the reverse direction should be larger than or not smaller than the diameter of the starting planetary gear in the forward direction (when pulled by the internal gear ring).

19. Regarding the installation positions of the starting planetary gear shaft, the No. 1 idler gear shaft, the No. 2 idler gear shaft, and the ending planetary gear shaft on the combined planetary carrier as described in Items 9, 11, 12, and 14, the angles between the meshing points of the starting planetary gear shaft to the inner ring gear and the meshing points of the starting planetary gear shaft to the No. 1 idler gear should be minimized (below 90°), thereby reducing the lever angle with the starting planetary gear shaft as the fulcrum (below 0°); at the same time, the angles between the meshing points of the ending planetary gear shaft to the sun gear and the meshing points of the ending planetary gear shaft to the No. 2 idler gear should be maximized (above 90°), thereby increasing the lever angle with the ending planetary gear shaft as the fulcrum (above 0°).

20. The gear ratios of the sun gear, internal ring gear, terminal coaxial planet gear, and terminal planet gear described in Items 1, 3, 4, 13, and 14 must be such that the gear ratio of the sun gear to the terminal planet gear must be equal to the gear ratio of the internal ring gear to the terminal coaxial planet gear, or the gear ratio of the sun gear to the internal ring gear must be equal to the gear ratio of the terminal planet gear to the terminal coaxial planet gear.

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