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 is amplified by utilizing the lever principle to promote the planet carrier to rotate reversely; and (3) the technology that the planet carrier and the inner gear ring are opposite in rotating direction and the same in rotating angle is utilized, so that the inner gear ring is always kept at the original rotating angle during operation, the acting force generated by the force generator is continuously kept, and the machine is continuously driven to operate and work 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 exerted by a force generator, specifically a prime mover that is directly driven by the force exerted by the force generator on the energy input end of the engine and outputs power, belonging to the technical field of engines. Background Art

[0002] Traditional engines (such as steam engines, internal combustion engines, etc.) are all driven by physical and chemical energy and converted into mechanical energy for delivery and work. Therefore, they all have problems such as consumption of physical and chemical energy, pollution, and emissions.

[0003] Currently, with the rapid development of social economy and the strong demand of the international community for carbon emission reduction, there is an urgent need for an engine that neither uses physical and chemical energy nor causes pollution and emissions. However, such machines are not yet available on the market. Summary of the Invention

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

[0005] The present invention is composed of a force generator capable of exerting a force on the energy input end of the engine and a synchronously counter-rotating gear mechanism. The force generator specifically refers to a device (such as a jack, an electric hoist, a winch, etc.) or a weight that can exert a pushing or dragging force on the end force point of the driving rod of the engine (the beginning of the driving rod is tightly connected to the input wheel shaft of the engine), so as to cause the end force point of the driving rod to be stressed, and can make the force exerted on the end force point of the driving rod remain unchanged (expressed as potential energy) under the condition that the angle of the driving rod remains unchanged. It is well known that under the condition that the jack exerts a certain amount of upward pushing force on the lower side of the end force point of the driving rod, as long as the angle of the driving rod remains unchanged, the force exerted by the jack to push the end force point of the driving rod upward remains unchanged. Similarly, under the condition that the electric hoist or winch exerts a certain amount of downward dragging force on the end force point of the driving rod, as long as the angle of the driving rod remains unchanged, the force exerted by the electric hoist or winch to drag the end force point of the driving rod downward remains unchanged. The same is true for the weight. When the weight is suspended at the end of the parallel driving rod, as long as the parallel angle of the driving rod remains unchanged, the downward force exerted by the weight on the end of the driving rod will remain unchanged. The synchronous reverse rotating gear mechanism refers specifically to a gear mechanism in which the combined planetary carrier of the engine can rotate synchronously in the opposite direction to the inner gear ring under the transmission of the inner gear ring, and replaces the angle of the inner gear ring's synchronous rotation in the forward direction with its angle of synchronous rotation in the reverse direction, thereby causing the rotation angle of the inner gear ring to remain unchanged. The gear mechanism is composed of mechanical structures such as driving rod + input wheel + inner gear ring + compound four-stage planetary gear + sun wheel + output wheel. The main technical points include the following: ① Use a force generator to push or pull the end point of the driving rod. The driving rod is subjected to force, that is, the input wheel shaft is twisted to drive the input wheel to rotate, and the input wheel drives the inner gear ring to rotate in the positive direction (hereinafter, the inner gear ring is defined as the positive direction, and the direction of other gears is based on this); the inner gear ring rotates in the positive direction, and the compound four-stage planetary gear rotates in the positive or reverse direction in turn. Under the blocking and support of the fixed star gear, the positive torque of the starting planetary gear shaft pulling the combined planetary carrier and the reverse torque of the end planetary gear shaft pushing the combined planetary carrier are formed. ② The gear mechanism uses the lever principle in operation to form a state where the reverse torque on the combined planetary carrier is greater than the positive torque, which prompts the combined planetary carrier to rotate in the reverse direction and drives the four-stage planetary gear to revolve in the reverse direction, so that the starting planetary gear revolving in the reverse direction is used to drag the inner gear ring rotating in the forward direction in the reverse direction. ③ By using 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 always maintain the original rotation angle while the transmission planetary gear pushes the combined planetary carrier to rotate in the reverse direction, thereby ensuring that the angle of the drive rod remains unchanged.The above three technologies enable the force exerted by the generator on the end point of the driving rod to remain unchanged during the operation of the driving engine, and continuously drive the inner gear ring to rotate in the positive direction through the input wheel; the inner gear ring rotating in the positive direction continuously drives the compound four-stage planetary gear to rotate, so that the end planetary gear shaft continuously drives the combined planetary carrier to rotate in the opposite direction; and the output wheel transmits part of the kinetic energy of the combined planetary carrier rotating in the opposite direction to do work.

[0006] The present invention is achieved through the following technical solutions: An engine driven by the acting force emitted by an acting force generator, which includes a fixing system, an acting force system, an input system, a rotating system, and an output system. Among them, the fixing system consists of a box body and a sun gear; the acting force system consists of an acting force generator; the input system consists of an internal gear ring, an input wheel, and two driving rods; the rotating system consists of a combined planet carrier, two initial planet wheels, two initial coaxial planet wheels, two first idler wheels, two second idler wheels, two terminal coaxial planet wheels, and two terminal planet wheels; the output system consists of an output force transmission wheel and an output wheel. It is characterized in that: The box body is both the sealed outer shell of the machine and the axle seat for installing and supporting the sun gear shaft, the input wheel shaft, and the output wheel shaft, located on the outer surface of the machine; it is shaped like three connected cylindrical shapes, with the middle being the rotating system box body, and the two ends being the input system box body and the output system box body respectively; at the center positions of the two side walls of the rotating system box body, a shaft seat for firmly installing the sun gear shaft is prefabricated respectively, at the center positions of the two side walls of the input system box body, a bearing seat for installing the input wheel shaft is prefabricated respectively, and at the center positions of the two side walls of the output system box body, a bearing seat for installing the output wheel shaft is prefabricated respectively, sealing the gear mechanism of the machine inside. The sun gear is an external cylindrical gear, with a diameter smaller than the internal gear ring and larger than the terminal planet wheel; it is located at the radial center position on one axial side inside the combined planet carrier within the rotating system box body, on the same axis as the combined planet carrier and the internal gear ring; its teeth are externally meshed with the terminal planet wheel, and the two side shafts are respectively firmly installed in the shaft seats prefabricated at the center positions of the two side walls of the rotating system box body and cannot rotate. Its first function is to use the sun gear shaft to install and support the combined planet carrier and the internal gear ring, becoming the central axis for supporting the rotation of the combined planet carrier and the internal gear ring; the second function is to use its non-rotating characteristic to block and support the terminal planet wheel rotating in the reverse direction, prompting the terminal planet wheel to roll and revolve in the reverse direction along its teeth, thereby driving the combined planet carrier to rotate in the reverse direction with the shaft. The internal gear ring is an internal cylindrical gear, with a diameter larger than the sun gear and the terminal coaxial planet wheel; it is located on the other axial side of the combined planet carrier within the rotating system box body, on the same axis as the combined planet carrier and the sun gear, and its teeth are internally meshed with the initial planet wheel; the edge of the internal gear ring on the side close to the box wall in the axial direction is firmly connected or integrated with the internal gear ring support bracket. At the radial center position of the support bracket (the radial center position of the internal gear ring), a hollow shaft facing the inside of the internal gear ring is prefabricated. The internal gear ring is installed and supported on the sun gear shaft through this hollow shaft (installed with bearings or in a sliding state); on the outer ring of the internal gear ring in the radial direction, on the side close to the input wheel, a force-receiving tooth composed of several external cylindrical gear teeth is prefabricated, which is firmly connected or integrated with the internal gear ring or the internal gear ring support bracket, and the force-receiving tooth is externally meshed with the input wheel. Its function is to rotate in the positive direction under the transmission of the input wheel, thereby driving the rotation of the initial planet wheel installed on the combined planet carrier.The input wheel is a cylindrical external gear located inside the input system housing. Its teeth are in external meshing with the teeth of the force-receiving internal gear ring. The two side wheel shafts are respectively installed in the bearing seats prefabricated at the center positions of the two side walls of the input system housing by bearings. The two ends of the wheel shafts extend out of the shafts to the outside of the bearing seats and are firmly connected to the shaft holes at the starting ends of the driving rods. Its function is to receive the acting force of the twisting of the driving rod through the wheel shaft, and thus drive the rotation of the internal gear ring through the meshing of the force-receiving teeth of the internal gear ring. The driving rod is a rigid rod that receives the acting force from the force-applying device and twists the input wheel shaft. It is located on both sides outside the input system housing. A shaft hole is prefabricated at the starting end of the rigid rod and is firmly connected to the extending shaft of the input wheel. A force-applying point is provided at the ending end of the rigid rod and is connected to the force-applying end of the force-applying device. Its function is to receive the pushing or pulling acting force from the force-applying device on its ending force-applying point, and use the received acting force to twist the input wheel shaft firmly connected to its starting-end shaft hole, so as to drive the rotation of the input wheel. The force-applying device is a device that applies an acting force to the ending force-applying point of the driving rod, and is composed of an instrument (such as a jack, an electric hoist, a winch, etc.) or a gravity object that can apply a pushing or pulling acting force to the ending force-applying point of the driving rod of this engine, so that the ending force-applying point of the driving rod is subjected to the force, and under the condition that the angle of the driving rod remains unchanged, the acting force applied can be continuously kept unchanged; it is located outside the housing, and its force-applying end is connected to the ending force-applying point of the driving rod. The combined planet carrier is a cylindrical planet gear carrier composed of an outer ring frame and two planet carriers. It is located on the axial other side of the internal gear ring inside the rotating system housing, on the same axis as the internal gear ring and the sun gear, and is respectively installed and supported on the sun gear shaft by bearings through the bearing seats prefabricated at the radial center positions of the two planet carriers; the outer ring frame is a cylindrical frame for installing and fixing the two planet carriers, located on the outer circle in the radial direction of the combined planet carrier; the two planet carriers are side plates for installing planet gear shafts, located on both sides in the axial direction of the outer ring frame. Two bearing seats for installing the starting-end planet gear shafts, two bearing seats for installing the first idler gear shafts, two bearing seats for installing the second idler gear shafts, and two bearing seats for installing the ending-end planet gear shafts are prefabricated at the corresponding positions in the radial direction of the two planet carriers. A bearing seat for installing the sun gear shaft is prefabricated at the radial center position of each; the radial edges of the two planet carriers are firmly connected to the axial edges on both sides of the outer ring frame. Its functions are: one is to install planet gear shafts; the other is to form a state where the forward torque and the reverse torque are counteracted under the push of the starting-end planet gear shaft rotating in the forward direction and the ending-end planet gear shaft rotating in the reverse direction, and rotate in the direction with the larger torque. The starting-end planet gear is a cylindrical external gear, and the number of teeth and the diameter are minimized as much as possible in terms of specifications; it is located inside the internal gear ring, and its teeth are in internal meshing with the internal gear ring; it is coaxial with the starting-end coaxial planet gear inside the combined planet carrier, and the wheel shafts are respectively installed in the bearing seats prefabricated at the corresponding positions of the two planet carriers by bearings. The extending shaft on the side close to the internal gear ring extends to the inside of the internal gear ring and is firmly connected to the hub of the starting-end planet gear.One of its functions is to rotate in the positive direction under the drive of the internal gear ring, and drive the starting coaxial planet gear in the planetary carrier to rotate in the positive direction through its axle; the other is to roll and revolve in the reverse direction along the teeth of the internal gear ring under the drive of the combined planetary carrier, so as to hold back the internally toothed ring rotating in the positive direction in the reverse direction. The starting coaxial planet gear is an external cylindrical gear, with the same module, number of teeth and diameter as the starting planet gear; it is located on the other axial side of the sun gear in the combined planetary carrier, coaxial with the starting planet gear, and the hub is fixedly installed on the starting planet gear axle; its teeth are externally meshed with the first idler gear. Its function is to serve as an extension of the starting planet gear, introduce the circumferential force of the internally toothed ring driving the starting planet gear into the combined planetary carrier, and drive the first idler gear in the combined planetary carrier. The first idler gear is an external cylindrical gear, located on the other axial side of the sun gear in the combined planetary carrier, with its front teeth externally meshed with the starting coaxial planet gear and its rear teeth externally meshed with the second idler gear, and the two side axles are respectively installed in the bearing seats prefabricated at the corresponding positions on the two-sided planetary carrier with bearings. One of its functions is to reduce the angle between the meshing point of the starting planet gear axle and the internally toothed ring and the meshing point of the starting planet gear axle and the first idler gear by adjusting its own position; the other is to drive the second idler gear. The second idler gear is an external cylindrical gear, located on the other axial side of the sun gear in the combined planetary carrier, with its front teeth externally meshed with the first idler gear and its rear teeth externally meshed with the ending coaxial planet gear, and the two side axles are respectively installed in the bearing seats prefabricated at the corresponding positions on the two-sided planetary carrier with bearings. One of its functions is to adjust the rotation direction of the ending coaxial planet gear; the other is to increase or decrease the angle between the meshing point of the ending planet gear axle and the sun gear and the meshing point of the ending planet gear axle and the second idler gear by adjusting its own position. The ending coaxial planet gear is an external cylindrical gear, with a diameter smaller than that of the internal gear ring and larger than that of the starting planet gear and the ending planet gear; it is located on the other axial side of the sun gear in the combined planetary carrier, with its teeth externally meshed with the second idler gear; it is coaxial with the ending planet gear, and the hub is fixedly installed on the ending planet gear axle. Its function is to amplify the torque and circumferential force of the ending planet gear by virtue of its diameter being larger than that of the starting planet gear and the ending planet gear, so that the torque and circumferential force of the ending planet gear are greater than those of the starting planet gear. The ending planet gear is an external cylindrical gear, with a diameter smaller than that of the ending coaxial planet gear; it is located on one side of the sun gear in the combined planetary carrier, with its teeth externally meshed with the sun gear; the two side axles are respectively installed in the bearing seats prefabricated at the corresponding positions on the two-sided planetary carrier with bearings. Its function is to roll, rotate and revolve in the reverse direction along the teeth of the sun gear under the blocking and support of the sun gear by using the torque and circumferential force greater than that of the starting planet gear rotating in the positive direction, so as to drive the combined planetary carrier to rotate in the reverse direction with the axle. The output force transmission gear is an external cylindrical gear, located on the outer radial circle of the outer ring frame of the combined planetary carrier or on the outer side of the axial direction of the planetary carrier close to the box wall, fixedly connected or integrated with the outer ring frame or the planetary carrier close to the box wall, and its teeth are externally meshed with the output gear. Its function is to transmit the rotational kinetic energy on the combined planetary carrier to the output gear.The output wheel is an external cylindrical gear located inside the output system housing. The two side wheel shafts are respectively installed in the bearing seats prefabricated at the center positions of the two side walls of the output system housing by bearings, and one end or both ends of the shafts extend outside the bearing seats; the gear teeth are externally meshed with the output transmission wheel. Its function is to convey part of the rotational kinetic energy transmitted by the output transmission wheel to do work. For the above-mentioned gear mechanism, ① in the rotational direction of the gears, the rotational direction of the end planet gear must be opposite to that of the starting planet gear to ensure a state where the positive torque and the reverse torque on the combined planet carrier cancel each other out; ② in terms of the specifications of the gears, the number of teeth and the diameter of the starting planet gear must be minimized as much as possible to minimize the torque of the starting planet gear (dragged by the internal gear ring) revolving in the positive direction; the diameter of the end coaxial planet gear must be larger than that of the starting planet gear and the end planet gear, so as to increase the torque and circumferential force of the end planet gear revolving in the reverse direction by increasing the diameter of the end coaxial planet gear, ensuring that the torque and circumferential force of the end planet gear revolving in the reverse direction are greater than those of the starting planet gear revolving in the positive direction; ③ in terms of the transmission efficiency of the gear transmission, during the process of the internal gear ring driving the starting planet gear, the starting coaxial planet gear driving the first idler gear, the first idler gear driving the second idler gear, the second idler gear driving the end coaxial planet gear, and the end planet gear driving the sun gear, the average transmission efficiency of each stage of gear transmission must reach more than 90%, ensuring that the torque and circumferential force of the end planet gear shaft revolving in the reverse direction are still much greater than those of the starting planet gear shaft revolving in the positive direction after being amplified by the end coaxial planet gear, so as to be sufficient to drive the combined planet carrier to rotate in the reverse direction and output part of the power; ④ in terms of the revolving diameter of the gears, the revolving diameter of the end planet gear in the reverse direction should be greater than or not less than the revolving diameter of the starting planet gear in the positive direction, ensuring that the lever arm of the end planet gear shaft revolving in the reverse direction on the combined planet carrier is greater than or not less than the lever arm of the starting planet gear shaft revolving in the positive direction; ⑤ in terms of the layout of the gears, the angle between the starting planet gear shaft to the meshing point with the internal gear ring and the starting planet gear shaft to the meshing point with the first idler gear must be adjusted to 90° or less (the lever angle with the starting planet gear shaft as the fulcrum is zero), so as to cause the starting planet gear shaft to lose the effect of the lever fulcrum when pulling the combined planet carrier to rotate in the positive direction; while the angle between the end planet gear shaft to the meshing point with the sun gear and the end planet gear shaft to the meshing point with the second idler gear should be adjusted to be greater than 90° (the lever angle with the end planet gear shaft as the fulcrum is greater than 0°) to increase the torque of the end planet gear shaft pushing the combined planet carrier to rotate in the reverse direction by using the lever effect, or it can also be adjusted to 90° or less (the lever angle with the starting planet gear shaft as the fulcrum is zero) according to specific needs to reduce the diameter of the combined planet carrier; ⑥ in terms of the tooth ratio of the gear transmission, the tooth ratio of the sun gear to the end planet gear must be equal to the tooth ratio of the internal gear ring to the end coaxial planet gear, or the tooth ratio of the sun gear to the internal gear ring must be equal to the tooth ratio of the end planet gear to the end coaxial planet gear, to ensure that the angle of the combined planet carrier rotating in the reverse direction is the same as the angle of the internal gear ring rotating in the positive direction.

[0007] The advantages of the invention are as follows: low manufacturing cost, strong power, convenient and practical; no need for energy, no pollution, no emissions, no noise, and no damage to or impact on the ecological environment. It can be used for power generation, power machinery, transportation tools, etc. BRIEF DESCRIPTION OF THE DRAWINGS

[0008] Attached Figure 1 : is the external view of the invention;

[0009] Attached Figure 2 : is the front view of the internal structure of the box of the invention;

[0010] Attached Figure 3 : is the front view of the outer ring frame and the planet carrier;

[0011] Attached Figure 4 : is the top view of the sectional plane of the invention along the plane of the axes of the input wheel, the fixed star wheel and the output wheel;

[0012] Attached Figure 5 : is the sectional view of the axial section along the A-A line in Attached Figure 4 ;

[0013] Attached Figure 6 : is the sectional view of the axial section along the B-B line in Attached Figure 4 ;

[0014] Attached Figure 7 : is the sectional view of the axial section along the C-C line in Attached Figure 4 ;

[0015] Attached Figure 8 : is the sectional view of the axial side along the D-D line in Attached Figure 5 、 6 、7;

[0016] Attached Figure 9 : is the sectional view of the axial side along the E-E line in Attached Figure 5 、 6 、7;

[0017] Attached Figure 10 : is the sectional view of the axial side along the F-F line in Attached Figure 5 、 6 、7.

[0018] In the figure: housing 01; rotating system housing 0101; input system housing 0102; output system housing 0103; sun gear shaft seat 0121; input wheel bearing seat 0122; output wheel bearing seat 0123; housing base 0126; sun gear 11; sun gear shaft 111; internal gear ring 12; internal gear ring support bracket 121; hollow shaft 122 at the radial center position of the internal gear ring support bracket; internal gear ring loaded tooth 123; input wheel 13; input wheel shaft 131; input wheel extension shaft 132; output force transmission wheel 14; output wheel 15; output wheel shaft 151; output wheel extension shaft 152; starting planetary gear 21; starting planetary gear shaft 211; extension shaft of the starting planetary gear shaft 212; included angle between the starting planetary gear shaft to the internal gear ring engagement point and the starting planetary gear shaft to the first idler gear engagement point 213; starting coaxial planetary gear 22; first idler gear 23; second idler gear 24; second idler gear shaft 241; end coaxial planetary gear 25; end planetary gear 26; end planetary gear shaft 261; included angle between the end planetary gear shaft to the sun gear engagement point and the end planetary gear shaft to the second idler gear engagement point 262; drive rod 31; shaft hole 311 at the starting end of the drive rod; force application point 312 at the ending end of the drive rod; screw type force application device 32; force application cross beam 321; nut 322 installed in the nut seat of the force application cross beam; round shafts 323 prefabricated at both ends of the force application cross beam; lead screw 324; knob disc 325 on the lead screw; thread 326 in the middle section of the lead screw; lead screw shaft 327; lead screw bearing seat 328; combined planetary carrier 33; outer ring frame 331; planetary carrier 332; bearing seat 3322 for installing the sun gear shaft at the radial center position on the planetary carrier; bearing seat 3321 for installing the starting planetary gear shaft on the planetary carrier; bearing seat 3323 for installing the first idler gear shaft on the planetary carrier; bearing seat 3324 for installing the second idler gear shaft on the planetary carrier; bearing seat 3326 for installing the end planetary gear shaft on the planetary carrier. Detailed implementation manners

[0019] The technical solutions in the present invention will be clearly and completely described below with reference to the accompanying drawings in the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, rather than all embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments in the present invention without creative efforts shall fall within the protection scope of the present invention.

[0020] An engine driven by the acting force generated by a force generator, comprising a fixing system, a force generating system, an input system, a rotating system and an output system. Among them, the fixing system consists of a box body 01 and a sun gear 11; the force generating system consists of a screw-type force generating device 32; the input system consists of an internal gear ring 12, an input wheel 13 and two driving rods 31; the rotating system consists of a combined planet carrier 33, two initial planet wheels 21, two initial coaxial planet wheels 22, two first idler wheels 23, two second idler wheels 24, two end coaxial planet wheels 25 and two end planet wheels 26; the output system consists of an output force transmission wheel 14 and an output wheel 15. It is characterized in that: the box body 01 is both the sealed outer shell of the machine and the axle seat for installing and supporting the sun gear shaft 111, the input wheel shaft 131 and the output wheel shaft 151, and is located on the outer surface of the machine; it is shaped like three connected cylinders, with the middle being the rotating system box body 0101, and the two ends being the input system box body 0102 and the output system box body 0103 respectively; at the center position of the two side walls of the rotating system box body 0101, a seat 0121 for firmly installing the sun gear shaft 111 is prefabricated on each side; at the center position of the two side walls of the input system box body 0102, a bearing seat 0122 for installing the input wheel shaft 131 is prefabricated on each side; at the center position of the two side walls of the output system box body 0103, a bearing seat 0123 for installing the output wheel shaft 151 is prefabricated on each side, sealing the gear mechanism of the machine inside. The sun gear 11 is a herringbone tooth cylindrical external gear, with a module of 3, a tooth width of 60 mm, 32 teeth, and a diameter of 96 mm; it is located at the radial center position on the side of the combined planet carrier 33 in the rotating system box body 0101 close to the internal gear ring 12, and is on the same axis as the combined planet carrier 33 and the internal gear ring 12; the teeth are externally meshed with the end planet wheels 26, and the two side shafts 111 are respectively firmly installed in the seats 0121 prefabricated at the center positions of the two side walls of the rotating system box body 0101 and cannot rotate. The internal gear ring 12 is a herringbone tooth cylindrical internal gear, with a module of 3, a tooth width of 65 mm, 64 teeth, and a diameter of 192 mm; it is on the other axial side of the combined planet carrier 33 in the rotating system box body 0101, and is on the same axis as the combined planet carrier 33 and the sun gear 11, and the teeth are internally meshed with the initial planet wheels 21; the edge of the internal gear ring 12 on the side close to the box wall axially is firmly connected to the internal gear ring support bracket 121, and a hollow shaft 122 facing the inside of the internal gear ring 12 is prefabricated at the radial center position of the support bracket 121 (the radial center position of the internal gear ring 12), and the internal gear ring 12 is installed and supported on the sun gear shaft 111 through this hollow shaft 122 (in a sliding state); at the radial position of the internal gear ring support bracket 121 close to the input wheel, a force-bearing tooth 123 composed of the teeth of 6 straight-tooth cylindrical external gears is prefabricated, with a module of 5, a tooth width of 20 mm, and a pitch circle radius of 175 mm, and is integrated with the internal gear ring support bracket 121, and the teeth are externally meshed with the input wheel 13.The input wheel 13 is a half external spur gear with a module of 5, a tooth width of 20 mm, 9 teeth, and a pitch circle radius of 42.5 mm. It is located inside the input system housing 0102, and its teeth are in external mesh with the teeth of the internal gear ring 123. The two wheel shafts 131 are respectively installed in the bearing seats 0122 prefabricated at the center positions of the two side walls of the input system housing 0102 by bearings. The two ends of the wheel shafts extend out of the shafts 132 to the outside of the bearing seats 0122 and are fixedly connected to the shaft holes 311 at the starting ends of the driving rods. The driving rod 31 is a rigid rod that receives the force exerted by the screw-type force application device 32 and twists the input wheel shaft 131. It is located on both sides outside the input system housing 0102. An axis hole 311 is prefabricated at the starting end of the rigid rod and is fixedly connected to the extending shaft 132 of the input wheel. An axis hole is prefabricated at the force application point 312 at the end of the rigid rod and is connected to the round shafts 323 prefabricated at both ends of the force application cross beam 321 of the screw-type force application device 32. The length from the axis hole 311 at the starting end of the rigid rod to the force application point 312 at the end is 350 mm. The screw-type force application device 32 consists of a force application cross beam 321, a screw rod 324, and a screw rod bearing seat 328. The force application cross beam 321 is located between the force application points 312 at the ends of the two driving rods. A round shaft 323 is prefabricated at each end of the force application cross beam 321 and is respectively installed in the axis holes prefabricated at the positions of the force application points 312 at the ends of the two driving rods (the round shaft and the axis hole are in a sliding state). A nut seat is prefabricated at the middle position of the force application cross beam 321, and a nut 322 is installed in the nut seat. The screw rod bearing seat 328 is a device for installing the screw rod shaft 327. It is located on the housing base 0126 below the nut 322 in the middle of the force application cross beam and is fixedly connected to the housing base 0126. The screw rod 324 is a threaded screw perpendicular to the force application cross beam 321. The upper end of the screw rod 324 is a knob disc 325, the middle section is a thread 326 that is screwed into the nut 322 in the middle of the force application cross beam, and the lower end is a screw rod shaft 327 that is installed in the screw rod bearing seat 328 by a bearing.The combined planet carrier 33 is a cylindrical planet gear carrier composed of an outer ring frame 331 and two-sided planet carriers 332. It is located on the axial other side of the internal gear ring 12 within the rotating system housing 0101, on the same axis as the internal gear ring 12 and the sun gear 11, and is installed and supported on the sun gear shaft 111 by bearings through the bearing seats 3322 prefabricated at the radial center positions of the two-sided planet carriers 332. The outer ring frame 331 is a cylindrical frame for installing and fixing the two-sided planet carriers 332, located on the radial outer circle of the combined planet carrier 33. The two-sided planet carriers 332 are side plates for installing planet gear shafts, located on both axial sides of the outer ring frame 331. At the radially corresponding positions on the two-sided planet carriers 332, two bearing seats 3321, 3323, 3324, and 3326 for installing the starting planet gear shafts 211, the first idler gear shafts 231, the second idler gear shafts 241, and the ending planet gear shafts 261 are prefabricated respectively, and a bearing seat 3322 for installing the sun gear shaft 111 is prefabricated at the radial center position. The radial edges of the two-sided planet carriers 332 are firmly connected to the axial side edges of the outer ring frame 331. The starting planet gear 21 is a herringbone cylindrical external gear, with a module of 3, a tooth width of 60 mm, 17 teeth, and a diameter of 51 mm. It is located within the internal gear ring 12, and its teeth are in internal meshing with the internal gear ring 12. It is coaxial with the starting coaxial planet gear 22 within the combined planet carrier 33. The gear shafts 211 are respectively installed in the bearing seats 3321 prefabricated at the corresponding positions on the two-sided planet carriers 332 by bearings. The protruding shaft 212 on the side close to the internal gear ring extends to the inner side of the internal gear ring 12 and is firmly connected to the hub of the starting planet gear 21. The starting coaxial planet gear 22 is a herringbone cylindrical external gear, with a module of 3, a tooth width of 60 mm, 17 teeth, and a diameter of 51 mm. It is located on the side close to the housing wall within the combined planet carrier 33, is coaxial with the starting planet gear 21, and its hub is firmly installed on the starting planet gear shaft 211, and its teeth are in external meshing with the first idler gear 23. The first idler gear 23 is a herringbone cylindrical external gear, with a module of 3, a tooth width of 60 mm, 28 teeth, and a diameter of 84 mm. It is located on the side close to the housing wall within the combined planet carrier 33. The front teeth are in external meshing with the starting coaxial planet gear 22, and the rear teeth are in external meshing with the second idler gear 24. The two side gear shafts are respectively installed in the bearing seats 3323 prefabricated at the corresponding positions on the two-sided planet carriers 332 by bearings. The second idler gear 24 is a herringbone cylindrical external gear, with a module of 3, a tooth width of 60 mm, 17 teeth, and a diameter of 51 mm. It is located on the side close to the housing wall within the combined planet carrier 33. The front teeth are in external meshing with the first idler gear 23, and the rear teeth are in external meshing with the ending coaxial planet gear 25. The two side gear shafts 241 are respectively installed in the bearing seats 3324 prefabricated at the corresponding positions on the two-sided planet carriers 332 by bearings. The ending coaxial planet gear 25 is a herringbone cylindrical external gear, with a module of 3, a tooth width of 60 mm, 34 teeth, and a diameter of 102 mm. It is located on the side close to the housing wall within the combined planet carrier 33, is coaxial with the ending planet gear 26, and its hub is firmly installed on the ending planet gear shaft 261, and its teeth are in external meshing with the second idler gear.The end planet gear 26 is a herringbone cylindrical external gear with a module of 3, a tooth width of 60 mm, 17 teeth, and a diameter of 51 mm; it is located inside the combined planet carrier 33 on the side close to the internal gear ring 12, and its teeth are externally meshed with the external teeth of the star gear 11; the two side wheel shafts 261 are respectively installed in the bearing seats 3326 prefabricated at corresponding positions on the two-sided planet carrier 332 by bearings. The output force-transmitting gear 14 is a herringbone cylindrical external gear with a module of 3, a tooth width of 60 mm, 123 teeth, and a diameter of 369 mm; it is located on the outer radial circle of the outer ring frame 331 of the combined planet carrier 33 and is fixedly connected to the outer ring frame 331; its teeth are externally meshed with the external teeth of the output gear 15. The output gear 15 is a herringbone cylindrical external gear with a module of 3, a tooth width of 60 mm, 19 teeth, and a diameter of 57 mm; it is located inside the output system box body 0103, and the two side wheel shafts 151 are respectively installed in the bearing seats 0123 prefabricated at the central positions of the two side walls of the output system box body 0103 by bearings, and one end of the shaft 152 extends outside the bearing seat 0123; its teeth are externally meshed with the external teeth of the output force-transmitting gear 14. For the above gear mechanism, ① in terms of the transmission efficiency of the gears, during the process of the internal gear ring 12 driving the starting planet gear 21, the starting coaxial planet gear 22 driving the first idler gear 23, the first idler gear 23 driving the second idler gear 24, the second idler gear 24 driving the end coaxial planet gear 25, and the end planet gear 26 driving the star gear 11, the average transmission efficiency of each stage of gear transmission is 95%; ② in terms of the rotation direction of the gears, the starting planet gear 21 rotates in the positive direction, and the end planet gear 26 rotates in the reverse direction; ③ in terms of the specifications of the gears, the number of teeth of the starting planet gear 21 has been reduced to the minimum (17 teeth), and the diameter has been reduced to the minimum (51 mm), and the diameter of the end coaxial planet gear 25 (102 mm) is twice the diameter of the starting planet gear 21 and the end planet gear 26 (51 mm); ④ in terms of the diameter of the gear revolution, the diameter of the starting planet gear 21 revolving in the positive direction is 141 mm, and the diameter of the end planet gear 26 revolving in the reverse direction is 147 mm; ⑤ in terms of the layout of the gears, the angle 212 between the meshing point of the starting planet gear shaft 211 and the internal gear ring 12 and the meshing point of the starting planet gear shaft 211 and the first idler gear 23 is 76° (the lever angle with the starting planet gear shaft 211 as the fulcrum is zero), and the angle 262 between the meshing point of the end planet gear shaft 261 and the star gear 11 and the meshing point of the end planet gear shaft 261 and the second idler gear 24 is 113° (the lever angle with the end planet gear shaft 261 as the fulcrum is 23°, and the length of the lever power arm is 19.9 mm); ⑥ in terms of the tooth ratio of the gear transmission, the tooth ratio of the star gear 11 to the end planet gear 26 (32 / 17) is equal to the tooth ratio of the internal gear ring 12 to the end coaxial planet gear 25 (64 / 34), or the tooth ratio of the star gear 11 to the internal gear ring 12 (32 / 64) is equal to the tooth ratio of the end planet gear 26 to the end coaxial planet gear 25 (17 / 34).

[0021] Working principle

[0022] When the screw knob disk 325 on the knob screw type force device 32 is rotated clockwise or counterclockwise 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 shaft 131, which is tightly connected to the shaft hole 311 at the starting end of the driving rod, is twisted to rotate in the direction of the force, and the input wheel shaft 131 drives 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) star gear 11. Under the action of the combined planet carrier 33, the gear transmission state forms the following operating characteristics in sequence: ① When the inner gear ring 12 rotating in the forward direction drives the starting planetary gear 21 installed on the combined planet carrier 33 to rotate in the forward direction, the gear teeth drag the starting planetary gear 21 to revolve in the forward direction, thereby forming a torque for the combined planet carrier 33 to rotate in the forward direction under the pull of the starting planetary gear shaft 211; since the terminal planetary gear 26 installed on the combined planet carrier 33 is blocked by the (unrotatable) sun gear 11 during the reverse rotation, it rolls and revolves in the reverse direction along the gear teeth of the sun gear 11, thereby forming a torque for the combined planet carrier 33 to rotate in the reverse direction under the push of the terminal planetary gear shaft 261. Therefore, a state is formed on the combined planet carrier 33 where the forward rotation torque of the starting planetary gear shaft point 3321 and the reverse rotation torque of the terminal planetary gear shaft point 3326 counteract each other. (The rotational force of the No. 1 idler gear 23 and the No. 2 idler gear 24 installed on the planet carrier 33 does not affect the rotation direction of the planet carrier 33) ② Since the average transmission rate of each gear transmission is 95%, the circumferential force of the terminal coaxial planetary gear 25 rotating in the reverse direction still reaches 85.7% of the circumferential force of the starting planetary gear 21 rotating in the forward direction after passing through three gear (gear teeth) transmissions (the starting coaxial planetary gear 22 drives the No. 1 idler gear 23, the No. 1 idler gear 23 drives the No. 2 idler gear 24, and the No. 2 idler gear 24 drives the terminal coaxial planetary gear 25);Since the number of teeth (34) and diameter (102 mm) of the end coaxial planet gear 25 are twice those of the start planet gear 21 (number of teeth 17, diameter 51 mm) and the end planet gear 26 (number of teeth 17, diameter 51 mm), the torque causing the end coaxial planet gear 25 to rotate in the reverse direction reaches 171.4% of the torque causing the start planet gear 21 to rotate in the forward direction (ratio of the circumferential force of the end coaxial planet gear 25 to the start planet gear 21 85.7% × radius of the end coaxial planet gear 25 51 mm ÷ radius of the start planet gear 21 25.5 mm). The torque and circumferential force causing the end planet gear 26 to rotate in the reverse direction also reach 171.4% of the torque and circumferential force causing the start planet gear 21 to rotate in the forward direction (ratio of the circumferential force of the end coaxial planet gear 25 to the start planet gear 21 85.7% × radius of the end coaxial planet gear 25 51 mm ÷ radius of the end planet gear 26 25.5 mm); Since the angle 212 between the engagement point of the start planet gear shaft 211 with the internal gear ring 12 and the engagement point of the start planet gear shaft 211 with the first idler gear 23 during forward revolution is 76° (the lever angle with the start planet gear shaft 211 as the fulcrum is zero), the start planet gear 21 loses the lever effect with the gear shaft 211 as the fulcrum during forward rotation; Since the angle 262 between the engagement point of the end planet gear shaft 261 with the sun gear 11 and the engagement point of the end planet gear shaft 261 with the second idler gear 24 during reverse revolution is 113° (the lever angle with the end planet gear shaft 261 as the fulcrum is 23°), the end coaxial planet gear 25 and the end planet gear 26 gain a lever effect with the gear shaft 261 as the fulcrum during reverse rotation (lever power arm length is 19.9 mm), thereby further increasing the torque of the end planet gear shaft 261 during reverse revolution, and causing the torque of the combined planet carrier 33 (pushed by the end planet gear shaft 261) to rotate in the reverse direction to reach 238.3% of the torque to rotate in the forward direction (ratio of the circumferential force of the end coaxial planet gear 25 to the start planet gear 21 85.7% × lever power arm length with the end planet gear shaft as the fulcrum 19.9 mm ÷ radius of the start planet gear 21 25.5 mm + ratio of the torque of the end planet gear 26 to the start planet gear 21 171.4%);Since the diameter (147 mm) of the end planet gear shaft 261 revolving in the reverse direction is greater than the diameter (141 mm) of the starting planet gear shaft 211 revolving in the forward direction, the lever arm of the end planet gear shaft 261 pushing the combined planet carrier 33 to rotate in the reverse direction is greater than the lever arm of the starting planet gear shaft 211 pushing the combined planet carrier 33 to rotate in the forward direction. As a result, the reverse torque on the combined planet carrier 33 is further increased, and the reverse torque on the combined planet carrier 33 reaches 248.4% of the forward torque (the ratio of the torque of the combined planet carrier 33 rotating in the reverse direction to the torque rotating in the forward direction 238.3% × the diameter of the end planet gear shaft 261 revolving in the reverse direction 147 mm ÷ the diameter of the starting planet gear shaft 211 revolving in the forward direction 141 mm). Therefore, under the condition that the average transmission efficiency of each stage of gear transmission reaches 95%, through the action of the lever principle during the transmission process of the planet gears and the planet carrier, finally, the torque of the combined planet carrier 33 rotating in the reverse direction is 1.48 times greater than the torque rotating in the forward direction, thus prompting the combined planet carrier 33 to rotate in the reverse direction. ③ Since all the planet gear shafts are installed on the combined planet carrier 33, when the combined planet carrier 33 rotates in the reverse direction, it drives all the planet gears to revolve in the reverse direction. ④ Since the internal gear ring 12 rotating in the forward direction drags the teeth of the starting planet gear 21 in the forward direction with its teeth during the process of the starting planet gear 21 rotating in the forward direction at the transmission starting end, the starting planet gear 21 rolls and revolves in the reverse direction along the teeth of the internal gear ring 12 under the drive of the combined planet carrier 33 rotating in the reverse direction, and thus drags the internally gear ring 12 rotating in the forward direction with its teeth in the reverse direction. ⑤ Since the tooth number ratio of the internal gear ring 12 and the end coaxial planet gear 25 is equal to the tooth number ratio of the fixed star gear 11 and the end planet gear 26, the angle of the combined planet carrier 33 rotating in the reverse direction is the same as the angle of the internal gear ring 12 rotating in the forward direction. This prompts the starting planet gear 21 dragging the internal gear ring 12 in the reverse direction, under the drive of the combined planet carrier 33, to roll and revolve in the reverse direction along the teeth of the internal gear ring 12 by an angle that exactly offsets the angle of the internal gear ring 12 rotating in the forward direction, thus prompting the internally gear ring 12 rotating in the forward direction to always remain at the original rotation angle. ⑥ Since the rotation angle of the internal gear ring 12 remains unchanged, the rotation angle of the input gear 13 externally meshing with the force-bearing teeth 123 of the internal gear ring also remains unchanged; the rotation angle of the input gear 13 remains unchanged, and the angle of the drive rod 31 tightly connected to the extending shaft 132 of the input gear remains unchanged, thus prompting the force exerted by the screw rod type force generating device 32 on the force application point 312 at the end of the drive rod to continuously remain unchanged. In this state, the force application point 312 at the end of the drive rod continuously receives the force (manifested as potential energy) emitted by the screw rod type force generating device 32. ⑦ Since the force application point 312 at the end of the drive rod continuously receives the force emitted by the screw rod type force generating device 32, the force application point 312 at the end of the drive rod is continuously under force;When the force application point 312 at the end of the driving rod is continuously stressed, it drives the shaft hole 311 at the beginning of the driving rod to continuously twist, and then drives the input wheel shaft 131 fixedly connected thereto. The input wheel shaft 131 drives the input wheel 13 to continuously rotate. ⑧ When the input wheel 13 continuously rotates, it continuously drives the driven teeth 123 of the internal gear ring to drive the internal gear ring 12 to continuously rotate in the positive direction; when the internal gear ring 12 continuously rotates in the positive direction, it continuously drives the planet gears on the combined planet carrier 33 to rotate; when the planet gears continuously rotate, the end planet gear 26 uses the shaft 261 to push the combined planet carrier 33 to continuously rotate in the reverse direction at the same angle as the internal gear ring 12 under the block and support of the fixed star gear 11; and when the combined planet carrier 33 continuously rotates in the reverse direction at the same angle as the internal gear ring 12, it drives the starting planet gear 21 rotating in the positive direction to continuously roll and revolve in the reverse direction along the teeth of the internal gear ring 12 at the same angle as the internal gear ring 12, thereby continuously dragging the internal gear ring 12 in the reverse direction and causing the internal gear ring 12 rotating in the positive direction to always remain at the original rotation angle unchanged... and so on in a cycle to achieve the continuous operation of the machine. ⑨ Since the output force transmission wheel 14 is fixedly connected to the outer ring frame 331 of the combined planet carrier 33, when the combined planet carrier 33 continuously rotates in the reverse direction, it drives the output force transmission wheel 14 to also continuously rotate in the reverse direction. ⑩ Since the output wheel 15 is externally meshed with the output force transmission wheel 14, when the output force transmission wheel 14 continuously rotates in the reverse direction, it drives the output wheel 15 to continuously rotate in the positive direction, and when the output wheel 15 continuously rotates in the positive direction, it continuously transmits a part of the rotational kinetic energy through the extension shaft 152 to do work.

[0023] When turning the screw knob disc 325 on the reverse-acting screw rod type force application device 32, the inclined plane of the thread 326 on the screw rod releases the friction with the inclined plane of the thread in the force application cross beam, so that the screw rod type force application device 32 stops applying force; when the screw rod type force application device 32 stops applying force, the driving rod 31 stops being stressed; when the driving rod 31 stops being stressed, it stops driving the machine to run and the engine stops working.

[0024] For those of ordinary skill 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 made to the embodiments still fall within the protection scope of the present invention.

[0025] Energy operation analysis As can be seen from the above embodiments and working principles, the reason why the engine driven by the force exerted by the force applicator can use the force exerted by the force applicator to drive the engine to continuously run is that under the condition that the force applicator exerts sufficient force on the force application point 312 at the end of the driving rod, it can make the force exerted by the force applicator on the force application point 312 at the end of the driving rod continuously remain unchanged during the process of the driving rod 31 twisting the input wheel shaft 131 (thereby driving the engine to run), so as to provide a continuous stream of force for continuously twisting the input wheel shaft 131. Among them:

[0026] 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 angle of the driving rod 31 remains unchanged; the angle of the driving rod 31 remains unchanged because the rotation angle of the input wheel shaft 131, which is tightly connected to the starting shaft hole 311, remains unchanged; the rotation angle of the input wheel shaft 131 and the input wheel 13 remains unchanged, which is because the rotation angle of the inner gear ring 12 remains unchanged.

[0027] ②The rotation angle of the inner gear ring 12 remains unchanged, and the reason is not that the inner gear ring 12 does not rotate. In fact, the inner gear ring 12 is continuously rotating in the positive direction under the drive of the input wheel 13, and continuously drives the starting planetary gear 21 to rotate in the positive direction, but the angle of the inner gear ring 12 rotating in the positive direction is the same as the angle of the combined planet carrier 33 driving the starting planetary gear 21 to roll and revolve in the reverse direction along the gear teeth of the inner gear ring 12, so that the angle of the inner gear ring 12 rotating in the positive direction is replaced by the same angle of the combined planet carrier 33 rotating in the reverse direction and the starting planetary gear 21 rolling and revolving in the reverse direction along the gear teeth of the inner gear ring 12. Therefore, the angle of the combined planet carrier 33 rotating in the reverse direction and the starting planetary gear 21 rolling and revolving in the reverse direction along the gear teeth of the inner gear ring 12 reflects the angle of the inner gear ring 12 rotating in the positive direction. We can calculate the angle and speed of the inner gear ring 12 rotating in the positive direction through the angle and speed of the combined planet carrier 33 rotating in the reverse direction and the starting planetary gear 21 rolling and revolving in the reverse direction along the gear teeth of the inner gear ring 12. Just like a person running on a human-powered treadmill, when a person runs forward, the legs push backward, and the legs push backward to push the belt backward. When the speed of the belt turning backward is the same as the speed of the person running forward, the speed and distance of the person running forward are offset by the speed and distance of the belt turning backward. At this time, although the person is running forward, he appears to be running continuously in place. Obviously, we cannot understand this phenomenon as the person is not running forward. In fact, the speed and distance of the person running forward are the same as the speed and distance of the belt turning backward, and the energy that drives the belt to turn backward comes from the energy generated by the person running forward. Therefore, we can calculate the speed and distance of the person running on the treadmill by measuring the speed and distance of the belt turning backward.

[0028] ③The reason why the angle of the internal gear ring 12 rotating in the positive direction can be replaced by the same angle of the combined planet carrier 33 rotating in the reverse direction and the initial planet gear 21 rolling in the reverse direction along the teeth of the internal gear ring 12 is that the combined planet carrier 33 drives the initial planet gear 21 to roll in the reverse direction along the teeth of the internal gear ring 12 with the same rotation angle as the internal gear ring 12. Principle: Since the teeth of the initial planet gear 21 are pulled in the positive direction by the internal gear ring 12 while the axle is driven in the reverse direction by the combined planet carrier 33, when the initial planet gear 21 is driven by the combined planet carrier 33 to revolve in the reverse direction, it continuously rolls in the reverse direction along the teeth of the internal gear ring 12 under the pulling of the teeth of the internal gear ring 12. Since the angle of the combined planet carrier 33 driving the initial planet gear 21 to roll in the reverse direction along the teeth of the internal gear ring 12 is the same as the angle of the internal gear ring 12 rotating in the positive direction, no matter how many degrees the internal gear ring 12 rotates in the positive direction, the initial planet gear 21 will roll in the reverse direction along the teeth of the internal gear ring 12 by the same number of degrees under the drive of the combined planet carrier 33. In terms of the number of teeth, no matter how many teeth the internal gear ring 12 rotates in the positive direction, it will pull the initial planet gear 21 to rotate in the positive direction by the same number of teeth; and no matter how many teeth the initial planet gear 21 rotates in the positive direction, it will roll in the reverse direction along the teeth of the internal gear ring 12 by the same number of teeth under the drive of the combined planet carrier 33. Thus, the internal gear ring 12 remains at its original rotation angle all the time when pulling the initial planet gear 21 to rotate in the positive direction with its teeth (just like a person running on a manual treadmill. No matter how far the person runs forward, the legs will kick the running belt to rotate backward by the same distance, so that the person remains in a state of running in place).

[0029] ④The reason why the combined planet carrier 33 can drive the initial planet gear 21 to roll in the reverse direction along the teeth of the internal gear ring 12 is that the reverse torque on the combined planet carrier 33 is much greater than the forward torque; and the reason why the combined planet carrier 33 can rotate in the reverse direction with the same rotation angle as the internal gear ring 12 is that the tooth number ratio of the end coaxial planet gear 25 to the internal gear ring 12 is equal to the tooth number ratio of the end planet gear 26 to the fixed star gear 11.

[0030] ⑤ The reason why the reverse torque on the combined planet carrier 33 can be much greater than the forward torque is that under the condition that the average transmission efficiency of each stage of gear transmission reaches 95%, the planet gears and the planet carrier utilize multiple lever technologies during the transmission process. First, the number of teeth and diameter of the starting planet gear 21 are reduced to the minimum. By shortening the radius (lever arm) of the starting planet gear 21, the torque that pulls the combined planet carrier 33 to rotate forward by the starting planet gear shaft 211 is reduced to the minimum. Second, the number of teeth and diameter of the end coaxial planet gear 25 are twice those of the starting planet gear 21 and the end planet gear 26. After removing the energy loss in the three-stage gear transmission, the torque and circumferential force that push the combined planet carrier 33 to rotate backward by the end planet gear shaft 261 are still 71.5% greater than the torque and circumferential force that pull the combined planet carrier 33 to rotate forward by the starting planet gear shaft 211. Third, the lever angle with the starting planet gear shaft 211 as the fulcrum is adjusted to zero, so that the starting planet gear 21 completely loses the lever effect when pulling the combined planet carrier 33 to rotate forward by the gear shaft 211, thereby reducing the torque that pulls the combined planet carrier 33 to rotate forward by the starting planet gear shaft 211. Fourth, the lever angle with the end planet gear shaft 261 as the fulcrum is adjusted to 23°, so that the end planet gear 26 increases the lever effect when pushing the combined planet carrier 33 to rotate backward by the gear shaft 261, thereby further increasing the torque of the combined planet carrier 33 (pushed by the end planet gear shaft 261) to rotate backward (1.38 times greater than the torque to rotate forward). Fifth, the diameter of the revolution of the end planet gear shaft 261 is greater than that of the starting planet gear shaft 211, so that the lever arm of the end planet gear shaft 261 on the combined planet carrier 33 to revolve backward is greater than that of the starting planet gear shaft 211 to revolve forward, thereby further increasing the reverse torque on the combined planet carrier 33 (1.48 times greater than the forward torque). The above 95% gear transmission efficiency, plus the five lever technologies, prompt the torque of the combined planet carrier 33 to rotate backward to be much greater than the torque to rotate forward.

[0031] ⑥ Since the reverse torque on the combined planet carrier 33 is much greater than the forward torque, after a part of the reverse torque on the combined planet carrier 33 is offset by the forward torque, there is still a part of the reverse torque left to be converted into kinetic energy to drive the machine to operate and be transmitted for work. Since the forward torque on the combined planet carrier 33 comes from the energy of the internal gear ring 12 rotating in the forward direction dragging the starting planet gear 21 with its teeth, therefore, in the reverse torque of the combined planet carrier 33, the part of the reverse torque offset by the forward torque is the energy consumed when the combined planet carrier 33 drives the starting planet gear 21 to roll along the teeth of the internal gear ring 12 in the reverse direction (keeping the internal gear ring 12 at the original rotation angle during its forward rotation). Thus, it can be seen that the energy conservation state during the operation of this machine is: the reverse torque (kinetic energy + potential energy) on the combined planet carrier 33 = the forward torque (potential energy) on the combined planet carrier 33 + the reverse torque (kinetic energy) on the combined planet carrier 33, that is: the reverse torque (kinetic energy) on the combined planet carrier 33 = the reverse torque (kinetic energy + potential energy) on the combined planet carrier 33 - the forward torque (potential energy) on the combined planet carrier 33. And in terms of the rotational speed, it depends on the force-speed ratio of the combined planet carrier 33 rotating in the reverse direction. The greater the torque (kinetic energy) of the combined planet carrier 33 rotating in the reverse direction, the faster the rotational speed. Assuming the force-speed ratio of the combined planet carrier 33 rotating in the reverse direction is 1N / 1mm / second, if the reverse torque (kinetic energy) of the combined planet carrier 33 is 1000 Nm, then its idling rotational speed should be: (1000 Nm ÷ the orbital radius 73.5 mm of the end planet gear 26 x 1000) ÷ the orbital diameter 147 mm of the end planet gear 26 ÷ 3.1416 = 29 r / s.

[0032] ⑦ The force exerted by the power generator on the end force point 312 of the driving rod remains unchanged, which is expressed as potential energy. This potential energy is transmitted to the input wheel 13 through the driving rod 31 twisting the input wheel shaft 131, and the input wheel 13 is transmitted to the inner ring gear 12 through the meshing inner ring gear force gear 123, and then the inner ring gear 12 drives the starting planetary wheel 21 to rotate in the positive direction and converts it into kinetic energy; finally, the combined planetary carrier 33 drives the starting planetary wheel 21 to roll and revolve along the inner ring gear 12 gear teeth in the reverse direction and drags the inner ring gear 12, so that the inner ring gear 12 is kept at the original rotation angle, so that the force exerted by the power generator on the end force point 312 of the driving rod remains unchanged. In this operation process where potential energy is continuously converted into kinetic energy and kinetic energy continuously causes potential energy to remain unchanged, all energy transmission and operation links of the engine are in a tense state of pushing or pulling each other. In this tense state, all energy transmission and operation links are shown to be in line with the force, interlocking, coordinated and advanced, and completed in one go. There is only a logical sequence between them, but no time and space gap. Therefore, as long as the force generator exerts enough force on the end point 312 of the driving rod, the driven rod 31 will immediately drive the inner gear ring 12 to rotate in the positive direction through the input wheel 13 and the inner gear ring force gear 123, and the inner gear ring 12 rotating in the positive direction will immediately drive the starting planetary gear 21 to rotate in the positive direction...; At the same time, the combined planet carrier 33 rotating in the reverse direction will also immediately drive the starting planetary gear 21 to roll and revolve in the reverse direction along the gear teeth of the inner gear ring 12, thereby immediately replacing the rotation angle of the inner gear ring 12, causing the inner gear ring 12 to remain at the original rotation angle unchanged... As long as the force exerted by the generator on the end force point 312 of the driving rod is not withdrawn, the continuously stressed driving rod 31 will continue to drive the inner gear ring 12 to rotate in the positive direction through the input wheel 13 and the force-bearing gear teeth 123 of the inner gear ring, and the inner gear ring 12 that continues to rotate in the positive direction will continue to drive the starting planetary gear 21 to rotate in the positive direction; at the same time, the combined planetary carrier 33 that continues to rotate in the reverse direction will also continue to drive the starting planetary gear 21 to roll and revolve in the reverse direction along the gear teeth of the inner gear ring 12, thereby continuously replacing the rotation angle of the inner gear ring 12, and causing the inner gear ring 12 to always maintain the original rotation angle unchanged... It is this energy operation state of the engine that causes the force exerted by the generator on the end force point 312 of the driving rod to remain unchanged, thereby providing a continuous force for continuously twisting the input wheel shaft 131, thereby driving the machine to continue to operate.

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 a star gear, the power generation system consists of a power generator, the input system consists of an inner ring gear, an input wheel and two drive rods, the rotating system consists of a combined planetary carrier, two starting planetary gears, two starting coaxial planetary gears, two No. 1 idler gears, two No. 2 idler gears, two terminal coaxial planetary gears and two terminal 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 axle, input axle and output axle, and is located on the outside of the machine; 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 both ends; a shaft seat for fastening and installing the star axle is prefabricated at the center of the box wall on both sides of the rotating system housing, a bearing seat for installing the input axle is prefabricated at the center of the box wall on both sides of the input system housing, and a bearing seat for installing the output axle is prefabricated at the center of the box wall on both sides of the output system housing, so that the gear mechanism of the machine is sealed inside.

3. The star gear described in Item 1 is a cylindrical external gear, the diameter of which must be smaller than the inner gear ring and larger than the terminal planetary gear; it is located at the radial center position on one side of the axial direction of the combined planetary carrier in the rotating system housing, and is on the same axis as the combined planetary carrier and the inner gear ring; the gear teeth are meshed with the outside of the terminal planetary gear, and the wheel axles on both sides are respectively fastened and installed in the prefabricated shaft seats at the center position of the box walls on both sides of the rotating system housing, and cannot rotate.

4. The inner gear ring described in Item 1 is a cylindrical internal gear, and its diameter must be larger than that of the star wheel and the coaxial planetary wheel at the end; it is located on the other axial side of the combined planetary carrier in the rotating system housing, on the same axis as the combined planetary carrier and the star wheel, and its gear teeth are meshed with the inner side of the starting planetary wheel; the axial edge of the inner gear ring on the side close to the housing wall is tightly connected 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 (radial center position of the inner gear ring), and the inner gear ring is installed and supported on the star wheel shaft through this hollow shaft (installed with bearings or in a sliding state); a load-bearing gear tooth composed of several cylindrical external gear teeth is prefabricated on the radial outer ring of the inner gear ring on the side close to the input wheel, which is tightly connected or integrated with the inner gear ring or the inner gear ring support bracket, and the load-bearing gear tooth is meshed with the outside of the input wheel.

5. The input wheel described in item 1 is a cylindrical external gear, which is located in the input system housing, and the gear teeth are externally meshed with the force-bearing gear teeth of the inner gear ring; the wheel axles on both sides are respectively installed with bearings in the bearing seats prefabricated in the center of the box walls on both sides of the input system housing, and the shafts at both ends of the wheel axles extend to the outside of the bearing seats and are tightly connected to the prefabricated shaft holes at the starting end of the drive rod.

6. The driving rod described in Item 1 is a hard rod that receives the force generated by the force generator and twists the input wheel axle. It is located on both sides of the outside of the input system box. An axial hole is prefabricated at the starting end of the hard rod and is tightly connected to the extended shaft of the input wheel. A fulcrum is set at the end of the hard rod to connect to the force generating end of the force generator.

7. The force generator described in Item 1 is a device that generates a force on the end point of the driving rod, and is composed of a device (such as a jack, electric hoist, winch, etc.) or a gravity object that can generate a pushing or pulling force on the end point of the driving rod of the engine, causing the end point of the driving rod to be subjected to force, and can keep the generated force constant (expressed as potential energy) under the condition that the angle of the driving rod remains unchanged; it is located outside the box, and its force generating end is connected to the end point of the driving rod.

8. The combined planetary carrier described in Item 1 is a cylindrical planetary wheel carrier composed of an outer ring frame and two-sided planetary carriers, which is located on the other axial side of the inner gear ring in the rotating system housing and on the same axis as the inner gear ring and the star wheel. It is installed and supported on the star wheel shaft by bearings through bearing seats prefabricated at the radial center position of the two-sided planetary carriers; the outer ring frame is a cylindrical frame for installing and fixing the two-sided planetary carriers, which is located at the radial outer ring of the combined planetary carrier; the two-sided planetary carriers are side plates for installing planetary wheel shafts, which are located on both axial sides of the outer ring frame, and the two-sided planetary carriers each have two bearing seats prefabricated at radially corresponding positions for installing the starting planetary wheel shaft, two for installing the No. 1 idler shaft, two for installing the No. 2 idler shaft, and two for installing the terminal planetary wheel shaft, and each has a bearing seat prefabricated at the radial center position for installing the star wheel shaft; the radial edges of the two-sided planetary carriers are fastened to the axial edges on both sides of the outer ring frame.

9. The starting planetary gear described in Item 1 is a cylindrical external gear, and the number of teeth and the diameter must be minimized in terms of specifications; it is located inside the inner gear ring, and the gear teeth are meshed with the inner gear ring; it is coaxial with the starting coaxial planetary gear in the combined planetary carrier, and the wheel axles are installed in the bearing seats prefabricated at the corresponding positions on the two planetary carriers with bearings, and the protruding shaft on the side of the inner gear ring extends to the inner side of the inner gear ring and is tightly connected to the hub of the starting planetary gear.

10. The starting coaxial planetary gear described in Item 1 is a cylindrical external gear, and its module, number of teeth and diameter must be consistent with those of the starting planetary gear; it is located on the other axial side of the star gear in the combined planetary carrier; it is coaxial with the starting planetary gear, and its hub is firmly mounted on the starting planetary gear shaft; its teeth are externally meshed with the No. 1 idler gear.

11. The idler gear No. 1 described in Item 1 is a cylindrical external gear, which is located on the other axial side of the star gear in the combined planetary carrier. The front gear teeth are meshed with the external surface of the coaxial planetary gear at the starting end, and the rear gear teeth are meshed with the external surface of the idler gear No.

2. The wheel axles on both sides are installed in the bearing seats prefabricated at the corresponding positions on the two planetary carriers with bearings.

12. The No. 2 idler gear described in Item 1 is a cylindrical external gear, which is located on the other axial side of the star gear in the combined planetary carrier. The front gear teeth are meshed with the external surface of the No. 1 idler gear, and the rear gear teeth are meshed with the external surface of the coaxial planetary gear at the end. The wheel axles on both sides are installed in the bearing seats prefabricated at the corresponding positions on the two planetary carriers with bearings.

13. The terminal coaxial planetary gear described in Item 1 is a cylindrical external gear, the diameter of which must be smaller than the inner gear ring and larger than the initial planetary gear and the terminal planetary gear; it is located on the other axial side of the star gear in the combined planetary carrier, and its gear teeth are meshed with the outer side of the No. 2 idler gear; it is coaxial with the terminal planetary gear, and its hub is securely mounted on the terminal planetary gear shaft.

14. The terminal planetary gear described in Item 1 is a cylindrical external gear, the diameter of which must be smaller than that of the terminal coaxial planetary gear; it is located on one side of the star gear in the combined planetary carrier, and its gear teeth are meshed with the outside of the star gear; it is coaxial with the terminal coaxial planetary gear, and the wheel axles on both sides are installed in bearing seats prefabricated at corresponding positions on the two sides of the planetary carriers with bearings.

15. The output transmission wheel described in item 1 is a cylindrical external gear, which is located on the radial outer ring of the outer ring frame of the combined planetary frame or the axial outer side of the planetary frame on the side close to the box wall, and is tightly connected or integrated with the outer ring frame or the planetary frame on the side close to the box wall, and the gear teeth are meshed 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 output system housing, and the gear teeth are meshed with the outside of the output transmission wheel; the wheel axles on both sides are installed with bearings in the prefabricated bearing seats at the center of the box walls on both sides of the output system housing, and one end or both ends of the shaft extend to the outside of the bearing seat.

17. Regarding the starting planetary gear and the ending planetary gear described in Items 1, 9, and 14, the rotation direction of the ending planetary gear must be opposite to that of the starting planetary gear.

18. In the gear transmission ratio of the sun gear, inner ring gear, starting planetary gear, starting coaxial planetary gear, No. 1 idler gear, No. 2 idler gear, terminal coaxial planetary gear and terminal planetary gear described in Items 1, 3, 4, 9-14, in the process where the inner ring gear 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 terminal coaxial planetary gear, and the terminal planetary gear drives the sun gear, the average transmission ratio of each gear transmission must reach more than 90%.

19. Regarding the orbital diameters of the starting planetary gear and the ending planetary gear 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.

20. In the radial layout of the sun gear, inner gear ring, starting planet gear, No. 1 idler gear, No. 2 idler gear and ending planet gear described in Items 1, 3, 4, 9, 11, 12 and 14 on the combined planet carrier, the angle between the starting planet gear shaft and the meshing point of the inner gear ring and the meshing point of the starting planet gear shaft and the No. 1 idler gear must be adjusted to 90° or less (the lever angle with the starting planet gear shaft as the fulcrum is zero); and the angle between the meshing point of the ending planet gear shaft and the sun gear and the meshing point of the ending planet gear shaft and the No. 2 idler gear should be adjusted to be greater than 90° (the lever angle with the ending planet gear shaft as the fulcrum is greater than 0°) so as to utilize the lever effect to increase the torque of the ending planet gear shaft pushing the combined planet carrier to rotate in the opposite direction, and can also be adjusted to 90° or less (the lever angle with the starting planet gear shaft as the fulcrum is zero) according to specific needs so as to reduce the diameter of the combined planet carrier.

21. For the sun gear, internal gear ring, terminal coaxial planetary gear and terminal planetary gear described in Items 1, 3, 4, 13 and 14, the gear ratio of the sun gear to the terminal planetary gear must be equal to the gear ratio of the internal gear ring to the terminal coaxial planetary gear, or the gear ratio of the sun gear to the internal gear ring must be equal to the gear ratio of the terminal planetary gear to the terminal coaxial planetary gear.

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