CN110953311B - Gear ring eccentric rotation stepless speed change system - Google Patents

Gear ring eccentric rotation stepless speed change system Download PDF

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Publication number
CN110953311B
CN110953311B CN201911388861.0A CN201911388861A CN110953311B CN 110953311 B CN110953311 B CN 110953311B CN 201911388861 A CN201911388861 A CN 201911388861A CN 110953311 B CN110953311 B CN 110953311B
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gear
shaft
hole
main
planet
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CN201911388861.0A
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CN110953311A (en
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赵晓东
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Dalian Bilan Energy Saving and Environmental Protection Technology Co Ltd
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Dalian Bilan Energy Saving and Environmental Protection Technology Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/76—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with an orbital gear having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/088—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft
    • F16H2037/0886—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft with switching means, e.g. to change ranges

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)

Abstract

The invention discloses a gear ring eccentric rotation stepless speed change system, and relates to a stepless speed change system. The revolution speed of the swing gear ring of the first continuously variable transmission and the second continuously variable transmission is related to the eccentric distance of the swing gear ring during eccentric movement, the purpose of continuously variable transmission is achieved by changing the eccentric distance of the swing gear ring, and the rotation speed and the rotation direction of the output shaft of the main reducer are controlled by changing the difference between the rotation speeds of the output shafts of the first continuously variable transmission and the second continuously variable transmission. The transmission part of the stepless speed change system adopts full gear transmission, the transmitted torque is large, and the stepless speed change system can be applied to a high-power fuel automobile power system and a stepless speed change device of large machinery.

Description

Gear ring eccentric rotation stepless speed change system
Technical Field
The invention discloses a gear ring eccentric rotation stepless speed change system, relates to a stepless speed change system, and particularly relates to a gear ring eccentric rotation stepless speed change system adopting all-gear transmission.
Background
The CVT continuously variable transmission applied to the automobile field adopts a friction force generated between a pressure steel belt or a chain and V-shaped groove walls of two cone pulleys to transmit torque, and a planetary friction type mechanical continuously variable transmission applied to the mechanical field also adopts the friction force to transmit the torque.
Due to the release and implementation of new emission standards in the automobile industry, the current situation of the automobile industry is that the fuel automobile field faces crisis when the electric automobile technology is not mature. The core of reducing the pollutant discharge amount of the fuel engine is to develop a brand-new transmission system, realize zero-rotation-speed output when the internal combustion engine is not stopped on the premise of ensuring that the fuel engine always operates in an economic rotation speed region, and can gradually increase the output rotation speed from the zero rotation speed to the cruising speed to reduce the pollutant discharge amount of the internal combustion engine.
The CN109854681A double bevel gear differential speed reducing mechanism in the published document of Chinese invention patent application is a speed reducer with two input shafts, which has the advantages of low cost, high performance, large transmission ratio and large output torque, and the rotating speed and the rotating direction of the output shaft are related to the rotating speed difference of the two input shafts. The double-bevel-tooth differential speed reducing mechanism is applied to the fields of electric automobiles, washing machines and the like which are driven by motors, and if the double-bevel-tooth differential speed reducing mechanism is applied to fuel automobiles, a transmission is required to be arranged to adjust the rotating speed difference of two input shafts of the double-bevel-tooth differential speed reducing mechanism.
Both a CVT (continuously variable transmission) applied to the field of automobiles and a planetary friction type mechanical stepless transmission applied to the field of machinery cannot realize zero rotating speed output when a prime motor is not stopped and cannot realize change of the rotating direction of an output shaft when an input shaft is not changed in the rotating direction, and torque transmitted by friction is small, so that the CVT cannot be applied to a high-power fuel automobile power system and a large-scale mechanical stepless transmission. The automotive field and the mechanical field need a stepless speed change technical scheme adopting all-gear transmission, and can realize zero rotating speed output when a prime motor is not stopped, and can realize a speed reduction system for changing the rotating direction of an output shaft when an input shaft does not change the rotating direction.
Disclosure of Invention
The invention aims to overcome the defects that the torque transmitted by friction force is small in the prior continuously variable transmission technology and the zero-rotation speed output of an internal combustion engine cannot be realized when the internal combustion engine is not stopped by a common CVT (continuously variable transmission), and provides a gear ring eccentric rotating continuously variable transmission system adopting all-gear transmission, which has large transmitted torque and can be applied to a high-power fuel automobile power system and a continuously variable transmission device of large machinery. The embodiments of the present invention are as follows:
the stepless speed change system comprises an internal combustion engine, a first clutch, a second connecting gear component, a first adjusting mechanism power device, a first stepless speed changer, a second adjusting mechanism power device, a second stepless speed changer, a speed measuring device, a main speed reducer and a second clutch. The input shaft of the first clutch is connected with the output shaft of the internal combustion engine, the first connecting gear component and the second connecting gear component respectively adopt two conical gears or two cylindrical gears, the first connecting gear component connects the output shaft of the first clutch with the input shaft of the first stepless speed changer, the second connecting gear component connects the output shaft of the first clutch with the input shaft of the second stepless speed changer, the first adjusting mechanism power device and the second adjusting mechanism power device respectively adopt an electric motor or a hydraulic actuator or a manual operating lever mechanism, the first adjusting mechanism power device is connected with the adjusting end of the first stepless speed changer, the second adjusting mechanism power device is connected with the adjusting end of the second stepless speed changer, the main speed reducer adopts a double-cone-tooth differential speed reducing mechanism, the two input shafts of the main speed reducer are respectively a first speed reducer input shaft, a second speed reducer, a third speed reducer and a fourth speed, And the output shaft of the main speed reducer is a main planetary support transmission shaft, the input shaft of the speed reducer is connected with the output end of the first stepless speed changer, the input shaft of the speed reducer is connected with the output end of the second stepless speed changer, one end of the main planetary support transmission shaft is connected with the input shaft of the second clutch, the other end of the main planetary support transmission shaft is connected with the speed measuring device, and the output shaft of the second clutch is connected with the load device.
The continuously variable transmission system is connected with a first gear component and a first continuously variable transmission to transmit a part of output torque of the internal combustion engine to drive a first speed reducer input shaft of a main speed reducer to form a first torque transmission channel, the continuously variable transmission system is connected with a second gear component and a second continuously variable transmission to transmit a part of output torque of the internal combustion engine to drive a second speed reducer input shaft of the main speed reducer to form a second torque transmission channel, and the first torque transmission channel and the second torque transmission channel can realize stepless speed change. The rotation speed and the rotation direction of an output shaft of a main speed reducer are related to the rotation speed difference of two input shafts of the main speed reducer, the rotation speed of an output end of a first stepless speed reducer is changed by driving an adjusting end of the first stepless speed reducer through an adjusting mechanism power device, namely, the rotation speed of a speed reducer input shaft of the main speed reducer is changed, the rotation speed of an output end of a second stepless speed reducer is changed by driving an adjusting end of the second stepless speed reducer through a second adjusting mechanism power device, namely, the rotation speed of a speed reducer input shaft of the main speed reducer is changed, the rotation speed and the rotation direction of the output shaft of the main speed reducer can be controlled, the rotation speed of the output shaft of the main speed reducer is monitored through a speed measuring device, and the torque output state of the main speed reducer is controlled through the separation.
The first stepless speed changer and the second stepless speed changer have the same structure, the first stepless speed changer comprises a fixed plate component, a coupler component, a swinging planetary gear component, a swinging planetary support component, a sliding rail support component and a balance wheel component, the fixed plate component comprises a fixed plate I, a fixed plate II, an adjusting plate, a guide fixing column, an adjusting gear, an adjusting rack and a parallel output gear, the coupler component comprises a concentric slide block, a cross slide block, a swinging slide block and a transmission pin, the swinging planetary gear component comprises a swinging gear ring, a gear fixing shaft, a sun gear, a transition gear, a planetary gear and a hinge component, the hinge component comprises a gear connecting plate I, a gear connecting plate II, a gear connecting plate III, a gear connecting plate IV, a positioning shaft and a planetary gear pin shaft, the swinging planetary support component comprises a, the sliding rail support component comprises a sliding rail support, a sliding rail II, a linkage gear shaft and a spring stop lever, the balance wheel component comprises a balance wheel, an adjusting roller pin shaft, a profiling adjusting roller and a reset spring, and the coupler component, the swinging planetary gear component, the swinging planetary support component, the sliding rail support component and the balance wheel component are sequentially arranged on the inner side of the fixed plate component in the axial direction. The input end of the continuously variable transmission is a first external spline of the sliding rail support, the output end of the continuously variable transmission is a second external spline parallel to the output gear, and the adjusting end of the continuously variable transmission is an adjusting gear shaft of the adjusting gear. The fixed part is a sun gear, the driving part is a swing planet support, the driven part is a swing gear ring, and the gear ring eccentric rotation planetary gear reducer performs speed reduction transmission.
The gear ring eccentric rotation planetary gear reducer has two working states of a concentric operation state and an eccentric operation state. When the gear ring eccentric rotation planetary gear reducer is in an eccentric operation state, the swinging gear ring and the sun gear are not concentric, the swinging planet support drives the swinging gear ring to rotate around the axis of the swinging gear ring, the swinging gear ring also can revolve around the axis of the sun gear, if the swinging planet support rotates a quarter turn along the forward rotation direction of the swinging planet support at a certain moment, the number of teeth of the swinging planet support driving the swinging gear ring to revolve around the axis of the sun gear along the forward rotation direction of the swinging gear ring is equal to the sum of the number of teeth b of the swinging gear ring and the eccentric distance of the swinging gear ring during eccentric movement divided by the tooth pitch, meanwhile, the transition gear is meshed with the sun gear and drives the planetary gear to rotate, the number of teeth of the planetary gear driving the swinging gear ring to rotate around the axis of the swinging gear ring along the opposite direction of the forward rotation direction of the swinging gear ring, because swing ring gear rotation direction is opposite with the revolution direction, and swing ring gear quarter number of teeth b is greater than sun gear quarter number of teeth a, then the actual direction of rotation of swing ring gear is the same with the revolution direction, if when the swing planet support rotated the quarter round at a certain moment, then the number of teeth that swing ring gear actually rotated along swing ring gear positive direction of rotation equals swing ring gear quarter number of teeth b plus swing ring gear eccentric number of teeth c subtracts sun gear quarter number of teeth a, the eccentric distance when increasing or reducing swing ring gear eccentric motion can increase or reduce swing ring gear eccentric number of teeth c, increase or reduce swing ring gear rotation speed promptly, realize buncher's infinitely variable speed purpose.
The second fixing plate is rectangular or disc-shaped, a first cylindrical boss is arranged at the radial center of one axial end of the second fixing plate, a first axial boss shaft hole is formed in the radial center of the first boss, a fourth radial fixing hole is formed in the radial outer surface of the first boss, a second cylindrical boss is arranged on the axial end face of the second fixing plate on the radial outer side of the first boss, a second axial boss shaft hole is formed in the radial center of the second boss, a fourth bearing mounting hole is formed in each axial two end of the second boss, the fourth bearing mounting hole is concentric with the second boss shaft hole, a plurality of second guide fixing holes are distributed in the axial end face of the radial outer side of the second fixing plate, each second guide fixing hole is provided with a second fixing hole which is vertically intersected with the second guide fixing hole.
The first fixing plate is rectangular or disc-shaped, an axial first fixing plate center hole is formed in the radial center of the first fixing plate, a first bearing mounting hole is formed in one axial end of the first fixing plate and is concentric with the first fixing plate center hole, a first fixing plate guide hole is formed in the axial end face of a first fixing plate on the radial outer side of the first bearing mounting hole, a plurality of first guide fixing holes are distributed in the axial end face of the first fixing plate on the radial outer side, each first guide fixing hole is provided with a first fixing hole which is perpendicular to the first guide fixing holes, and one end of each first fixing hole is located on the radial outer surface of the first.
The adjusting plate is rectangular or disc-shaped, a conical adjusting cone is arranged at the radial center of the adjusting plate, an axial adjusting plate center hole is formed in the radial center of the adjusting cone, a third guide fixing hole is formed in the axial end face of the adjusting plate on the radial outer side of the adjusting cone, a third fixing hole which is perpendicular to the third guide fixing hole is formed in the third guide fixing hole, one end of the third fixing hole is located on the radial outer surface of the adjusting plate, and a plurality of adjusting plate guide holes are distributed in the axial end face of the adjusting plate on the radial outer.
The guide fixing column is cylindrical, and two ends of the guide fixing column are respectively provided with a radial fixing column pin hole. One end of the adjusting gear in the axial direction is provided with a first cylindrical gear tooth, and the other end of the adjusting gear is provided with an adjusting gear shaft. The axial middle of the adjusting rack is provided with a rack, the two axial ends of the adjusting rack are cylindrical, and one axial end of the adjusting rack is provided with a radial positioning pin hole I. The axial end of the parallel output gear is sequentially provided with a second external spline, a fourth shaft neck, a fourth positioning shaft shoulder and a second cylindrical gear tooth from one end to the other end, and a third radial positioning pin hole is formed between the second external spline and the fourth shaft neck.
The concentric sliding block is disc-shaped, an axial sliding block center hole III is formed in the radial center of the concentric sliding block, a track groove II is arranged at one axial end of the concentric sliding block, the track groove II penetrates through the sliding block center hole III to be distributed in the radial direction, a bearing mounting hole III is formed in the other axial end of the concentric sliding block, the bearing mounting hole III is concentric with the sliding block center hole III, a coupler gear is arranged on the radial outer side of the other axial end of the concentric sliding block, and the coupler gear is.
The swing sliding block is disc-shaped, an axial sliding block center hole I is formed in the radial center of the swing sliding block, a track groove I is arranged at one axial end of the swing sliding block, the track groove I penetrates through the sliding block center hole I to be distributed in the radial direction, and a plurality of transmission pin holes II are uniformly distributed in the radial outer surface of the swing sliding block.
The cross sliding block is disc-shaped, an axial sliding block center hole II is formed in the radial center of the cross sliding block, a track boss II is arranged at one axial end of the cross sliding block, the track boss II penetrates through the sliding block center hole II and is distributed radially, the radial cross section outline of the track boss II is meshed with the radial cross section outline of the track groove II of the concentric sliding block, the other axial end of the cross sliding block is provided with a track boss I, the track boss I penetrates through the sliding block center hole II and is distributed radially, the radial cross section outline of the track boss I is meshed with the radial cross section outline of the track groove I of the swing sliding block, and.
The driving pin, the first fixing pin, the second fixing pin, the third fixing pin, the fourth fixing pin and the fifth fixing pin are cylindrical. The positioning retainer ring is cylindrical, a positioning retainer ring shaft hole is arranged at the radial center of the positioning retainer ring, and a radial positioning retainer ring pin hole is formed in the radial outer surface of the positioning retainer ring.
The swing gear ring is cylindrical, a cylindrical inner gear is arranged on the radial inner surface of one axial end of the swing gear ring, and a plurality of radial transmission pin holes I are uniformly distributed from the radial inner surface to the outer surface of the other axial end of the swing gear ring. The sun gear, the transition gear and the planet gear are cylindrical external gears, the radial center of the sun gear is a sun gear shaft hole, the inner surface of the sun gear shaft hole is provided with an inner key groove, the radial center of the transition gear is a transition gear shaft hole, and the radial center of the planet gear is a planet gear shaft hole.
The gear fixing shaft is cylindrical, a shaft section III, a positioning shaft shoulder III, a shaft neck III, a shaft section II and a shaft neck II are sequentially arranged from one end to the other end of the gear fixing shaft in the axial direction, a positioning pin hole II is formed in the radial outer surface of one end, far away from the positioning shaft shoulder III, of the shaft section III, an outer key groove is formed in the radial outer surface of the shaft section II, the diameter of the shaft neck II is smaller than that of the shaft section II, and the positioning shaft shoulder II is formed between the shaft neck II. The positioning shaft is cylindrical, the diameters of the two ends of the positioning shaft are smaller than the diameter of the middle position of the positioning shaft, and a positioning shaft shoulder V is formed between each of the two ends and the middle position of the positioning shaft. The planet gear pin shaft is cylindrical, and a shaft shoulder of the planet gear pin shaft is arranged at one axial end of the planet gear pin shaft.
The first gear connecting plate and the second gear connecting plate are in the same structure, the first gear connecting plate and the second gear connecting plate are in an oblong shape, a first hinge hole is formed in one radial end of the first gear connecting plate, and a second hinge hole and a third hinge hole are distributed in parallel at the other radial end of the first gear connecting plate. The gear connecting plate III is in an oblong shape, one end of the gear connecting plate III in the radial direction is provided with a hinge hole IV, the other end of the gear connecting plate III in the radial direction is provided with a hinge shaft, and the hinge shaft is perpendicular to the plate surface of the gear connecting plate III. The fourth gear connecting plate is in an oblong shape, one end of the fourth gear connecting plate in the radial direction is provided with a hinge hole six, the other end of the fourth gear connecting plate in the radial direction is provided with a hinge hole five, the position of the hinge hole five of the fourth gear connecting plate corresponds to the position of a hinge shaft of the third gear connecting plate, and the position of the hinge hole six of the fourth gear connecting plate corresponds to the position of the hinge hole four of the third gear connecting plate.
The oscillating planet support is disc-shaped, an axial planet support center hole is formed in the radial center of the oscillating planet support, two planet support dovetail grooves which are parallel to each other are formed in one axial end of the oscillating planet support, the two planet support dovetail grooves are respectively located on two radial sides of the planet support center hole, a linkage rack II is arranged between the two planet support dovetail grooves, a planet gear pin shaft fixing hole is formed in the axial end face of the oscillating planet support, close to the planet support center hole, between the two planet support dovetail grooves, and a plurality of limiting roller wheel pin shaft fixing holes are distributed in the axial end face of the radial outer side of. The swing limiting roller is cylindrical, and an axial limiting roller shaft hole is formed in the radial center of the swing limiting roller. The limiting roller pin shaft is cylindrical, and a shaft shoulder of the limiting roller pin shaft is arranged at one axial end of the limiting roller pin shaft.
The balance wheel is in a disc shape, an axial balance wheel center hole is formed in the radial center of the balance wheel, two balance wheel dovetail grooves which are parallel to each other are arranged at one end in the axial direction of the balance wheel, the two balance wheel dovetail grooves are respectively positioned at two sides in the radial direction of the balance wheel center hole, a linkage rack I is arranged between the two balance wheel dovetail grooves, a triangular roller support is arranged at the other end in the axial direction of the balance wheel, a roller mounting groove is formed in the triangular oblique side of the roller support, an adjusting roller pin shaft fixing hole is formed in the triangular oblique side direction of the roller support and penetrates through the roller mounting groove, the roller support and the linkage rack I are respectively positioned at two sides in the radial direction of the balance wheel center hole, a spring mounting groove is formed in the outer surface, the radial outer surface direction of the balance wheel is an opening end I, and the axial end surface direction of the balance wheel far away from the roller bracket of the spring mounting groove is an opening end II. The profiling adjusting roller is cylindrical, and an axial adjusting roller shaft hole is formed in the radial center of the profiling adjusting roller. The adjusting roller pin shaft is cylindrical, and one axial end of the adjusting roller pin shaft is provided with an adjusting roller pin shaft shoulder.
The axial end faces of the sliding rail bracket discs on the two radial sides of the bearing mounting hole are respectively provided with a sliding rail I, the radial section of the sliding rail I is in a dovetail shape, the section outline of the sliding rail I is meshed with the section outline of the dovetail groove of the planet bracket of the swinging planet bracket, the two sliding rails I are parallel to each other, the axial end faces of the sliding rail bracket discs on the two radial sides of the shaft section I are respectively provided with a sliding rail dovetail groove, the radial section of the sliding rail bracket is in the dovetail shape, and the two sliding rail bracket dovetail grooves are parallel to each other, the slide rail bracket dovetail grooves are parallel to the slide rail I, a rectangular gear groove hole is formed in the axial end face of the slide rail bracket disc between the two slide rail I, the gear groove hole is provided with a linkage gear shaft fixing hole which is vertically intersected with the gear groove hole, the linkage gear shaft fixing hole is vertically intersected with the two slide rail bracket dovetail grooves, two ends of the outer side of the linkage gear shaft fixing hole are located on the radial outer surface of the slide rail bracket disc, two ends of the inner side of the linkage gear shaft fixing hole are located in the gear groove hole, a spring stop rod fixing hole is formed in the axial end face of the slide rail bracket disc between the two slide rail bracket dovetail grooves, and the spring stop rod fixing hole and the gear.
The sliding rail bracket part is provided with two sliding rails II, the cross sections of the sliding rails II are in a double-dovetail shape, one dovetail-shaped profile of the cross section of each sliding rail II is meshed with the cross section profile of a dovetail groove of the sliding rail bracket, and the other dovetail-shaped profile of the cross section of each sliding rail II is meshed with the cross section profile of a dovetail groove of the balance wheel. The linkage gear is a cylindrical external gear, and the radial center of the linkage gear is a linkage gear shaft hole. The linkage gear shaft is cylindrical. The spring stop lever is L-shaped, and the section of the spring stop lever is circular.
The axial middle positions of a plurality of guide fixing columns of the fixed plate component are arranged in a guide hole of an adjusting plate, the axial two ends of each guide fixing column are respectively arranged in a guide fixing hole I of the fixed plate I and a guide fixing hole II of the fixed plate II, the first fixing pins are arranged in a fixing hole I of the fixed plate I and a fixing pin hole at one axial end of each guide fixing column, and the second fixing pins are arranged in a fixing hole II of the fixed plate II and a fixing pin hole at the other axial end of each guide fixing column. The first bearing is installed in the first bearing installation hole of the first fixing plate. One axial end of the adjusting rack is arranged in a third guide fixing hole of the adjusting plate, a third fixing pin is arranged in the third fixing hole of the adjusting plate and a first positioning pin hole at one axial end of the adjusting rack, and the other axial end of the adjusting rack is arranged in a guide hole of the fixing plate of the first fixing plate. And a first cylindrical gear tooth of the adjusting gear is meshed with a rack in the axial middle of the adjusting rack. The two bearings IV are respectively installed in bearing installation holes IV of the fixed plate II, an external spline II of the parallel output gear penetrates through a boss shaft hole II of the fixed plate II and is located on the axial outer side of the fixed plate II, a shaft neck IV of the parallel output gear penetrates through a boss shaft hole II of the fixed plate II and is installed in the shaft hole of the bearing IV, a cylindrical gear tooth II of the parallel output gear is located between the fixed plate II and an adjusting plate in the axial direction, a positioning retainer ring shaft hole of the positioning retainer ring is installed on the radial outer surface of the shaft neck IV of the parallel output gear, a fixing pin V is installed in a positioning retainer ring pin hole III of the parallel output gear and a positioning retainer ring pin hole of the positioning retainer ring, a shaft section III of the gear fixing shaft is installed in a boss shaft hole I of the.
The first track boss of the crosshead shoe of the coupling part is installed in the first track groove of the swing slider, the second track boss of the crosshead shoe is installed in the second track groove of the concentric slider, the third bearing is installed in the third bearing installation hole of the concentric slider, the shaft hole of the third bearing is installed on the radial outer surface of the journal of the gear fixing shaft, the gear fixing shaft sequentially penetrates through the third slider center hole of the concentric slider, the second slider center hole of the crosshead shoe and the first slider center hole of the swing slider, and the coupling gear of the concentric slider is meshed with the second cylindrical gear teeth of the parallel output gear.
The sun gear of the swing planet gear part is arranged on the radial outer surface of a shaft section II of the gear fixing shaft through a spline, namely the spline is arranged in an outer keyway of the gear fixing shaft and an inner keyway of the sun gear, a gear connecting plate I and a gear connecting plate II are respectively arranged at two axial ends of the sun gear, hinge holes I of the gear connecting plate I and the gear connecting plate II are respectively arranged on the radial outer surface of the shaft section II of the gear fixing shaft, two axial ends of a positioning shaft are respectively arranged in hinge holes III of the gear connecting plate I and the gear connecting plate II, hinge shafts of the gear connecting plate III are respectively arranged in hinge holes II of the gear connecting plate I and the gear connecting plate II, a transition gear is arranged between the gear connecting plate I and the gear connecting plate II in the axial direction, a transition gear shaft hole of the transition gear is arranged on the radial outer surface of the hinge shaft of the gear connecting, and the four gear connecting plates are positioned at one end of the two outer sides of the gear connecting plates, the planet gear pin shafts are respectively arranged in the six hinge holes of the four gear connecting plates and the four hinge holes of the three gear connecting plates, the shaft shoulders of the planet gear pin shafts are contacted and arranged with the four gear connecting plates together, the planet gears are arranged between the three gear connecting plates and the four axial directions of the gear connecting plates, the planet gear shaft holes of the planet gears are arranged on the radial outer surfaces of the planet gear pin shafts, the swinging gear rings are arranged on the radial outer sides of the planet gears, the transition gears and the sun gears, the swinging gear rings, the planet gears, the transition gears and the sun gears are sequentially meshed, and the two axial ends of the transmission pins are respectively arranged in the first transmission pin holes of the.
The axial middle position of a limiting roller pin shaft of the swing planet support component is arranged in a limiting roller pin shaft hole of the swing limiting roller, a limiting roller pin shaft shoulder of the limiting roller pin shaft is in contact installation with one axial end of the swing limiting roller, one axial outer end of the limiting roller pin shaft is arranged in a limiting roller pin shaft fixing hole of the swing planet support, the plurality of swing limiting rollers are located at one axial end of the swing planet support without the linkage rack II, a gear fixing shaft penetrates through a planet support center hole of the swing planet support, the radial outer surfaces of the plurality of swing limiting rollers are in contact installation with the radial outer surface of a swing gear ring, and one axial outer end of the planet gear pin shaft is arranged in a planet gear pin shaft fixing hole of the.
One axial end of a spring stop rod of a slide rail bracket component is arranged in a spring stop rod fixing hole of a slide rail bracket, a linkage gear is arranged in a gear groove hole of the slide rail bracket, a linkage gear shaft is arranged in a linkage gear shaft fixing hole of the slide rail bracket and a linkage gear shaft hole of the linkage gear, the profile of the radial section of each second half of each slide rail is arranged in a slide rail bracket dovetail groove of the slide rail bracket, so that the linkage gear shaft cannot fall off from the linkage gear shaft fixing hole of the slide rail bracket, a second bearing is arranged in a bearing mounting hole of the slide rail bracket, a first external spline of the slide rail bracket sequentially penetrates through a regulating plate center hole of a regulating plate and a fixing plate center hole of a fixing plate I and is positioned at the axial outer side of the fixing plate I, a first journal of the slide rail bracket is arranged in a shaft hole of the first bearing, a second journal of the gear fixing shaft, the linkage gear is meshed with a linkage rack II of the swing planet support.
The profiling adjusting roller of the balance wheel component is arranged in a roller mounting groove of the balance wheel, an adjusting roller pin shaft is arranged in an adjusting roller pin shaft fixing hole of the balance wheel and an adjusting roller shaft hole of the profiling adjusting roller, the radial outer surface of the profiling adjusting roller is in contact with the radial outer surface of an adjusting cone of an adjusting plate, a reset spring is arranged in a spring mounting groove of the balance wheel, a first shaft section of a slide rail support penetrates through a balance wheel center hole of the balance wheel, the other half radial cross section profile of each second slide rail is arranged in a balance wheel dovetail groove of the balance wheel, the other axial end of a spring stop lever is arranged in a spring mounting groove of the balance wheel, the other axial end of the spring stop lever is in contact with the axial end face of the reset spring, and a linkage.
The main reducer comprises a main planet support component, a second input bevel gear, a second reducer input shaft, a first input bevel gear, a first reducer input shaft, a first double bevel gear, a first shaft sleeve, a first retainer ring, a first pin, a second double bevel gear, a second shaft sleeve, a second retainer ring and a second pin, and the main planet support component comprises a main planet support transmission shaft, a main planet bevel gear, a main planet shaft, a main planet support and a third shaft sleeve. And the second input bevel gear, the second reducer input shaft, the first input bevel gear and the first reducer input shaft are respectively arranged on the radial outer side of the main planetary support component, and the two axial ends of a transmission shaft of the main planetary support are not only output shafts of the main reducer, but also output shafts of the stepless speed change system.
The main planet support is annular, a plurality of support mounting planes are uniformly distributed on the radial inner surface of the main planet support, and a support fixing shaft hole is formed in the center of each support mounting plane. A plurality of radial fixed shaft holes are uniformly distributed on the radial outer surface of a fixed shaft shoulder in the axial middle of a transmission shaft of a main planetary support, one end of the main planetary shaft is arranged in the fixed shaft hole of the transmission shaft of the main planetary support, the other end of the main planetary shaft is arranged in a support fixed shaft hole of the main planetary support, a third shaft sleeve is arranged in the axial middle of the main planetary shaft, and a main planetary bevel gear is arranged on the radial outer surface of the third shaft sleeve.
A first double-bevel gear shaft hole is formed in the radial middle of a first double-bevel gear, and a first inner gear tooth and a first outer gear tooth are respectively formed at the axial two ends of the radial outer side of the first double-bevel gear. The second radial middle of the double bevel gear is a second double bevel gear shaft hole, and the axial two ends of the second radial outer side of the double bevel gear are respectively an inner gear tooth II and an outer gear tooth II. The first double bevel gear and the second double bevel gear are respectively arranged at two axial ends of the main planetary support component, the first inner gear teeth of the first double bevel gear are meshed with the main planetary bevel gear of the main planetary support component, and the second inner gear teeth of the second double bevel gear are meshed with the main planetary bevel gear of the main planetary support component. The first shaft sleeve is arranged at the right side position of a shoulder shaft of a fixed shaft of the transmission shaft of the main planetary carrier, the first double bevel gear is arranged on the radial outer surface of the first shaft sleeve, and the first check ring and the first pin are arranged and fixed on the radial outer surface of the transmission shaft of the main planetary carrier on the right side of the first shaft sleeve. The second shaft sleeve is arranged at the left side of the shoulder shaft of the fixed shaft of the transmission shaft of the main planetary support, the second double bevel gear is arranged on the radial outer surface of the second shaft sleeve, and the second check ring and the second pin are arranged and fixed on the radial outer surface of the transmission shaft of the main planetary support on the left side of the second shaft sleeve. One axial end of an input shaft of the speed reducer is provided with a first input bevel gear, the first input bevel gear is meshed with first outer side gear teeth of a first double bevel gear, one axial end of a second input shaft of the speed reducer is provided with a second input bevel gear, and the second input bevel gear is meshed with second outer side gear teeth of the second double bevel gear.
The operation process of the first continuously variable transmission and the second continuously variable transmission is as follows: when the continuously variable transmission is in a concentric operation state, the swinging gear ring is concentric with the sun gear, and the axis of the swinging gear ring is superposed with the axis of the sun gear. The internal combustion engine drives the sliding rail bracket to rotate through the first connecting gear part or the second connecting gear part, the sliding rail bracket drives the balance wheel to rotate through the second sliding rail, the profiling adjusting roller wheel rotates along the outer surface of the adjusting cone of the adjusting plate in the radial direction, meanwhile, the sliding rail bracket drives the swinging planet bracket to rotate through the first sliding rail, in the planetary gear reducer with the eccentric rotating of the gear ring, the sun gear is a fixed part, the swinging planet bracket is a driving part, the swinging gear ring is a driven part, the swinging gear ring, the planet gear, the transition gear and the sun gear are meshed in sequence, if the swinging planet bracket rotates a quarter turn along the forward rotating direction of the swinging planet bracket at a certain moment, the swinging planet bracket drives the swinging gear ring to rotate along the forward rotating direction of the swinging gear ring around the axis through the planet gear pin shaft and the planet gear, the number of teeth of the swinging gear ring from, meanwhile, the swing planet support drives the transition gear to rotate around the sun gear through the planet gear pin shaft and the planet gear, so that the transition gear rotates along the positive rotation direction of the transition gear, the transition gear drives the planet gear to rotate along the positive rotation direction of the planet gear, the planet gear drives the swing gear ring to rotate around the axis of the swing gear ring along the opposite direction of the positive rotation direction of the swing gear ring, the number of teeth of the rotation is equal to the quarter tooth number a of the sun gear, the actual rotation direction of the swing gear ring is the same as the revolution direction due to the fact that the rotation direction of the swing gear ring is opposite to the revolution direction and the quarter tooth number b of the swing gear ring is larger than the quarter tooth number a of the sun gear, and the gear ring eccentrically. When the continuously variable transmission is in a concentric operation state, if the swinging planet support rotates for a quarter turn along the forward rotation direction of the swinging planet support at a certain moment, the actual rotation tooth number of the swinging ring gear along the forward rotation direction of the swinging ring gear is equal to the quarter tooth number b of the swinging ring gear minus the quarter tooth number a of the sun gear. The swing gear ring sequentially passes through the transmission pin, the swing sliding block, the crosshead shoe and the concentric sliding block to drive the coupler gear to rotate, and the coupler gear drives the parallel output gear to rotate.
When the continuously variable transmission is in an eccentric operation state, an adjusting gear shaft of an adjusting gear is driven to rotate by a first adjusting mechanism power device or a second adjusting mechanism power device, the adjusting gear sequentially drives an adjusting plate to move along a forward adjusting direction through an adjusting rack and a fixed pin, an adjusting cone of the adjusting plate sequentially drives an adjusting plate through a profiling adjusting roller, an adjusting roller pin shaft and a balance wheel compression reset spring and drives the balance wheel to move towards the radial outer side of a roller support, a first linkage rack of the balance wheel sequentially drives a second linkage rack of a linkage gear and a second linkage rack of a swing planetary support to move towards the opposite direction of the movement of the balance wheel, at the moment, a swing gear ring is not concentric with a sun gear, an eccentric distance exists between the axis of the swing gear ring and the axis of the sun gear, and the eccentric distance is divided by a. The internal combustion engine drives a sliding rail bracket to rotate through a first connecting gear part or a second connecting gear part, the sliding rail bracket drives a balance wheel to rotate through a second sliding rail, a profile control adjusting roller wheel rotates along the outer surface of a radial direction of a control cone of a control plate, meanwhile, the sliding rail bracket drives a swing planet bracket to rotate through the first sliding rail, in a planet gear reducer with eccentric rotation of a gear ring, a sun gear is a fixed part, a swing planet bracket is a driving part, a swing gear ring is a driven part, the swing gear ring, a planet gear, a transition gear and the sun gear are meshed in sequence, if the swing planet bracket rotates for a quarter turn along the forward rotation direction of the swing planet bracket at a certain moment, the swing planet bracket drives the swing gear ring to rotate along the forward rotation direction of the swing gear ring around the axis of the sun gear through a planet gear pin shaft and the planet gear, the number of teeth of the swing ring from a D point, meanwhile, the swing planet support drives the transition gear to rotate around the sun gear through the planet gear pin shaft and the planet gear, so that the transition gear rotates along the positive rotation direction of the transition gear, the transition gear drives the planet gear to rotate along the positive rotation direction of the planet gear, the planet gear drives the swing gear ring to rotate around the axis of the swing gear ring along the opposite direction of the positive rotation direction of the swing gear ring, the number of teeth of the rotation is equal to the quarter tooth number a of the sun gear, the actual rotation direction of the swing gear ring is the same as the revolution direction due to the fact that the rotation direction of the swing gear ring is opposite to the revolution direction and the quarter tooth number b of the swing gear ring is larger than the quarter tooth number a of the sun gear, and the gear ring eccentrically. When the continuously variable transmission is in an eccentric operation state, if the swinging planet support rotates for a quarter turn along the forward rotation direction of the swinging planet support at a certain moment, the actual rotation tooth number of the swinging ring gear along the forward rotation direction of the swinging ring gear is equal to the quarter tooth number b of the swinging ring gear, the eccentric tooth number c of the swinging ring gear and the quarter tooth number a of the sun gear. The eccentric distance of the oscillating gear ring during eccentric movement is increased or reduced, so that the eccentric tooth number c of the oscillating gear ring can be increased or reduced, namely the rotating speed of the oscillating gear ring is increased or reduced, the rotating speed of the oscillating gear ring can be subjected to stepless speed change, the oscillating gear ring sequentially passes through the transmission pin, the oscillating slider, the cross slider and the concentric slider to drive the coupler gear to rotate, the coupler gear drives the parallel output gear to rotate, and the purpose of stepless speed change of the stepless speed changer is achieved.
When the swing planet support component of the continuously variable transmission drives the swing planet gear component to rotate, the swing limiting idler wheel rolls on the radial outer surface of the swing gear ring, and the swing gear ring is ensured to rotate according to the eccentric distance set by the adjusting gear. When the swinging gear ring rotates eccentrically, the eccentric distance between the axis of the swinging gear ring and the axis of the sun gear is offset by the sliding between the first track boss of the crosshead shoe and the first track groove of the swinging slider and the sliding between the second track boss of the crosshead shoe and the second track groove of the concentric slider, so that the concentric slider and the sun gear are ensured to be concentric.
The operation process of the main reducer is as follows: the output end of the first continuously variable transmission drives a first speed reducer input shaft of a main speed reducer to rotate along the first rotation direction of the input shaft, the first speed reducer input shaft drives a first double-bevel gear to rotate around the axis of an output shaft along the first rotation direction of the double-bevel gear through a first input bevel gear, the output end of the second continuously variable transmission drives a second speed reducer input shaft of the main speed reducer to rotate along the second rotation direction of the input shaft, the second speed reducer input shaft drives a second double-bevel gear to rotate around the axis of the output shaft along the second rotation direction of the double-bevel gear through a second input bevel gear, and the first double-bevel gear rotation direction is opposite to the second. If the rotating speed of the first input shaft of the speed reducer is equal to the rotating speed of the second input shaft of the speed reducer, the main planetary bevel gear rotates around the axis of the main planetary shaft, the main planetary support is in a static state, and the rotating speed of a transmission shaft of the main planetary support is zero.
If the first speed reducer input shaft rotating speed is higher than the second speed reducer input shaft rotating speed, the first double bevel gear drives the main planetary bevel gear to rotate around the axis of the main planetary shaft along the rotating direction of the main planetary bevel gear more than the second double bevel gear drives the main planetary bevel gear to rotate around the axis of the main planetary shaft along the rotating direction of the main planetary bevel gear, in order to offset the speed difference of the first double bevel gear and the second double bevel gear which drive the main planetary bevel gear respectively, the main planetary bevel gear also revolves around the axis of the output shaft, the main planetary bevel gear drives the main planetary support to rotate at a low rotating speed, the linear speed of the main planetary support is equal to half of the difference between the linear speed of the first double bevel gear and the linear speed of the second double bevel gear, the rotating direction of the main planetary support is the same as that of the first double bevel gear, and the main planetary support drives a transmission shaft of the main planetary support to rotate at a low rotating speed in the same direction through the main planetary.
If the first speed reducer input shaft rotating speed is less than the second speed reducer input shaft rotating speed, the first double bevel gear drives the main planetary bevel gear to rotate around the main planetary shaft axis along the main planetary bevel gear rotating direction at a lower speed than the second double bevel gear drives the main planetary bevel gear to rotate around the main planetary shaft axis along the main planetary bevel gear rotating direction, in order to offset the speed difference of the first double bevel gear and the second double bevel gear which drive the main planetary bevel gear respectively, the main planetary bevel gear also revolves around the axis of the output shaft, the main planetary bevel gear drives the main planetary support to rotate at a low rotating speed, the linear speed of the main planetary support is equal to half of the difference between the linear speed of the second double bevel gear and the linear speed of the first double bevel gear, the rotating direction of the main planetary support is the same as that of the second double bevel gear, and the main planetary support drives the transmission shaft of the main planetary support to rotate at the low rotating speed in the same direction through the main planetary.
The operation process of the stepless speed change system is as follows: and if the transmission ratio of the first connecting gear part is set to be equal to that of the second connecting gear part, the transmission ratio between the first input bevel gear of the main speed reducer and the first outer side gear teeth of the first double bevel gear is set to be equal to that between the second input bevel gear of the main speed reducer and the second outer side gear teeth of the second double bevel gear. If the rotation direction of the main planetary support of the main speed reducer is set to be the same as the rotation direction of the first double bevel gear, the automobile is in a forward driving state, and if the rotation direction of the main planetary support of the main speed reducer is set to be the same as the rotation direction of the second double bevel gear, the automobile is in a backward driving state.
Before the continuously variable transmission system operates, the first clutch and the second clutch are in a separated state. When the continuously variable transmission system is started, the first continuously variable transmission is in a concentric operation state by operating the first adjusting mechanism power device, the second continuously variable transmission is in a concentric operation state by operating the second adjusting mechanism power device, the transmission ratio of the first continuously variable transmission is equal to that of the second continuously variable transmission, the internal combustion engine is started and operates in an economic rotation speed region, the automobile control module sends out a command to enable the first clutch to be in an engagement state, the output torque of the internal combustion engine is transmitted to the output shaft of the first clutch, a part of the output torque of the internal combustion engine is transmitted to the first torque transmission channel through the first connecting gear component, the part of the output torque is transmitted to the first speed reducer input shaft of the main speed reducer through the first continuously variable transmission, and meanwhile, a part of the output torque of the internal combustion engine is transmitted to the second torque transmission channel through the second connecting gear component, the partial output torque is transmitted to a second speed reducer input shaft of a main speed reducer through a second stepless speed changer, the rotating speed of the first speed reducer input shaft is equal to that of the second speed reducer input shaft, the rotating speed of a transmission shaft of a main planet carrier is zero, the main speed reducer is in a running stop state, namely an automobile is in a running stop state, and zero rotating speed output when an internal combustion engine is not stopped is achieved.
If the main reducer is in a stop running state and the automobile is operated to run, the speed measuring device detects that the rotating speed of a transmission shaft of the main planetary support is zero, the automobile control module sends an instruction to enable the clutch II to be in an engaging state, the continuously variable transmission I is in an eccentric running state by operating the adjusting mechanism power device I, the rotating speed of the continuously variable transmission I driving the speed reducer input shaft I is larger than the rotating speed of the continuously variable transmission II driving the speed reducer input shaft II, the rotating direction of the main planetary support of the main reducer is the same as that of the double bevel gear I, the main reducer is in a forward running state, and along with the increase of the eccentric distance between the axis of the swing gear ring of the continuously variable transmission I and the axis of the sun gear, the difference between the rotating speed of the speed reducer input shaft I and the rotating speed of the speed reducer input shaft II, because the rotating linear speed of the main planetary support is equal to half of the difference between the first rotating linear speed of the double bevel gear and the second rotating linear speed of the double bevel gear, the output rotating speed of a transmission shaft of the main planetary support of the main speed reducer is increased, zero rotating speed output when the internal combustion engine is not stopped is realized, the output rotating speed can be gradually increased from zero rotating speed to cruise speed, and the automobile is in a forward running state.
If the main reducer is in a stop running state and the automobile is operated to run, the speed measuring device detects that the rotating speed of a transmission shaft of the main planetary support is zero, the automobile control module sends an instruction to enable the clutch II to be in an engaging state, the stepless speed changer II is in an eccentric running state by operating the adjusting mechanism power device II, the rotating speed of the input shaft of the stepless speed changer I driving speed reducer I is smaller than the rotating speed of the input shaft of the stepless speed changer II driving speed reducer II, the rotating direction of the main planetary support of the main reducer is the same as the rotating direction of the double bevel gears II, the main reducer is in a backward running state, and along with the increase of the eccentric distance between the axis of the swing gear ring of the stepless speed changer II and the axis of the sun gear, the difference between the rotating speed of the input shaft of the speed reducer II and the rotating speed of, because the rotating linear speed of the main planetary support is equal to half of the difference between the two rotating linear speeds of the double bevel gear and the one rotating linear speed of the double bevel gear, the output rotating speed of a transmission shaft of the main planetary support of the main speed reducer is increased, zero rotating speed output when the internal combustion engine is not stopped is realized, the output rotating speed can be gradually increased from zero rotating speed to cruise speed, the automobile is in a backward driving state, and the rotating direction of an output shaft of the main speed reducer can be changed when the input shaft of the main speed reducer does not change the rotating direction.
When the first stepless speed changer and the second stepless speed changer of the stepless speed change system are in an eccentric running state, the swinging gear ring and the sun gear are not concentric, the swinging planet support drives the swinging gear ring to rotate around the axis of the swinging gear ring, the swinging gear ring also revolves around the axis of the sun gear, the revolution speed of the swinging gear ring is related to the eccentric distance of the swinging gear ring during eccentric movement, and the purpose of stepless speed change of the first stepless speed changer and the second stepless speed changer is achieved by changing the eccentric distance of the swinging gear ring. The rotation speed and the rotation direction of an output shaft of a main reducer of the stepless speed change system are related to the rotation speed difference of two input shafts of the main reducer, and the rotation speed and the rotation direction of the output shaft of the main reducer can be controlled by changing the rotation speed difference of a first output shaft of the stepless speed changer and a second output shaft of the stepless speed changer. The transmission part of the stepless speed change system adopts full gear transmission, the transmitted torque is large, and the stepless speed change system can be applied to a high-power fuel automobile power system and a stepless speed change device of large machinery. When the stepless speed change system is in an eccentric operation state, the eccentric moving direction of the balance wheel is opposite to the eccentric moving direction of the swinging planet carrier and the swinging gear ring, and dynamic balance in eccentric operation can be repaired.
Drawings
Fig. 1 is an isometric view of a first continuously variable transmission or a second continuously variable transmission.
Fig. 2 is an axial sectional view of the first continuously variable transmission or the second continuously variable transmission in a concentric operating state.
Fig. 3 is an axial sectional view of the first continuously variable transmission or the second continuously variable transmission in an eccentric operating state.
Fig. 4 is an axial cross-sectional view of the stationary plate member.
Fig. 5 is an axial sectional view of the second fixing plate.
Fig. 6 is an axial sectional view of the adjustment plate.
Fig. 7 is an axial cross-sectional view of the first fixing plate.
Fig. 8 is an axial cross-sectional view of the coupling component.
FIG. 9 is an isometric cross-sectional view of a concentric slide.
Figure 10 is an isometric view of an oldham slide.
Fig. 11 is an isometric view of the oscillating slide.
FIG. 12 is an axial cross-sectional view of an oscillating planetary gear member, in an eccentric operating condition.
Fig. 13 is an isometric view of the gear fixing shaft.
Figure 14 is an isometric view of a hinge member.
FIG. 15 is an isometric view of gear coupling plate one or gear coupling plate two.
Fig. 16 is an isometric view of the gear connecting plate three.
Fig. 17 is an isometric view of gear web four.
FIG. 18 is an isometric view of the positioning shaft.
FIG. 19 is an axial cross-sectional view of an oscillating planet carrier assembly member.
Fig. 20 is an isometric view of an oscillating planet carrier.
Fig. 21 is an axial cross-sectional view of a slide rail bracket assembly.
Fig. 22 is an axial cross-sectional view of the slide rail bracket.
Fig. 23 is an axial cross-sectional view of the balance wheel assembly.
Fig. 24 is an axial cross-sectional view of the balance wheel.
Fig. 25 is an isometric view of the adjustment gear and adjustment rack mounted together.
Fig. 26 is an isometric view of a parallel output gear.
Fig. 27 is a schematic diagram of gear engagement in the concentric operating state of the first continuously variable transmission or the second continuously variable transmission.
Fig. 28 is a schematic view of gear engagement in the eccentric operating state of the first continuously variable transmission or the second continuously variable transmission.
Fig. 29 is a schematic view of a first continuously variable transmission or a second continuously variable transmission cut along an axis line in a concentric operating state.
Fig. 30 is a schematic view of a first continuously variable transmission or a second continuously variable transmission cut along an axis line in an eccentric operating state.
Fig. 31 is a schematic path diagram of two torque transmission passages of the continuously variable transmission system.
FIG. 32 is a schematic illustration of a final drive retard operation. In the figure, if UI is larger than UII, then UIII and UI rotate in the same direction.
Fig. 33 is a shaft side sectional view of the final drive.
FIG. 34 is an isometric cross-sectional view of the first double bevel gear.
FIG. 35 is an isometric cross-sectional view of the second double bevel gear.
In the figure, the small letters are respectively the eccentric tooth number c of the swinging gear ring obtained by dividing the eccentric distance of the swinging gear ring during eccentric movement by the tooth pitch, wherein the tooth number a of the sun gear is one fourth, the tooth number b of the swinging gear ring is one fourth. The capital letters in the figures are the rotational start point D, rotational end point E, where the oscillating planet carrier member drives the oscillating planet gear member to rotate ninety degrees.
In the figure, UI is the linear speed of the rotation of the first reference circle position of the inner side gear teeth of the first double bevel gear, UII is the linear speed of the rotation of the second reference circle position of the inner side gear teeth of the second double bevel gear, and UIII is the linear speed of the rotation of the main planet support at the position which is equal to the first reference circle radius of the inner side gear teeth of the first double bevel gear or the second reference circle radius of the inner side gear teeth of the second double bevel gear.
The drawing is marked with a concentric slide block 1, a crosshead slide block 2, a swinging slide block 3, a gear fixing shaft 4, a fixing pin four 5, a bearing three 6, a fixing pin five 7, a positioning retainer ring 8, a bearing four 9, a parallel output gear 10, a key strip 11, a sun gear 12, a swinging limiting roller 13, a swinging planet support 14, a spring stop lever 15, a return spring 16, a fixing pin three 17, an adjusting gear 18, an adjusting rack 19, a fixing plate one 20, an adjusting roller pin shaft 21, a profiling adjusting roller 22, a bearing one 23, a slide rail support 24, a bearing two 25, a guiding fixing column 26, an adjusting plate 27, a balance wheel 28, a linkage gear 29, a planet gear pin shaft 30, a planet gear 31, a swinging gear ring 32, a transmission pin 33, a fixing plate two 34, a fixing pin two 35, a fixing pin one 36, a slide rail two 37, a gear connecting plate two 38, a limiting roller pin shaft 39, the first boss 42, the first boss shaft hole 43, the fourth fixing hole 44, the second boss shaft hole 45, the second boss 46, the second fixing hole 47, the adjusting plate guide hole 48, the adjusting plate center hole 49, the third guide fixing hole 50, the third fixing hole 51, the first guide fixing hole 52, the first fixing plate center hole 53, the fixed plate guide hole 54, the first fixing hole 55, the second track groove 56, the coupling gear 57, the third slider center hole 58, the second slider center hole 59, the first track boss 60, the second track boss 61, the first track groove 62, the first slider center hole 63, the second transmission pin hole 64, the third gear connecting plate 65, the fourth gear connecting plate 66, the transition gear 67, the positioning shaft 68, the first gear connecting plate 69, the first transmission pin hole 70, the second positioning pin hole 71, the third shaft section 72, the third positioning shaft shoulder 73, the third shaft neck 74, the second shaft section 75, the outer key groove 76, the second shaft neck 77, the second hinge hole 78, the third hinge hole, A fourth hinge hole 81, a hinge shaft 82, a limiting roller pin fixing hole 83, a planet support dovetail groove 84, a planet support center hole 85, a planet gear pin fixing hole 86, a linkage rack II 87, a linkage gear shaft 88, a gear slot 89, a linkage gear shaft fixing hole 90, a bearing mounting hole II 91, a slide rail I92, a slide rail support dovetail groove 93, a spring stop lever fixing hole 94, a first external spline 95, a first journal 96, a first shaft section 97, a linkage rack I98, a balance wheel dovetail groove 99, a balance wheel center hole 100, a spring mounting groove 101, a roller support 102, an adjusting roller pin fixing hole 103, a roller mounting groove 104, a first positioning pin hole 105, a second external spline 106, a third positioning pin hole 107, a fourth journal 108, a fourth positioning shaft shoulder 109, a sun gear axis 110, a swing gear axis 111, a transition gear forward rotation direction 112, a planet gear forward rotation direction 113, a swing planet support forward rotation direction 114, a, The swing gear ring comprises a swing gear ring in a forward rotation direction 115, a bearing mounting hole four 116, a bearing mounting hole one 117, a bearing mounting hole three 118, a hinge hole five 119, a hinge hole six 120 and a forward adjusting direction 121.
The device comprises an internal combustion engine 201, a first clutch 202, a second connecting gear component 203, a torque transmission direction 204, a torque transmission path 205, a first connecting gear component 206, a first adjusting mechanism power device 207, a first continuously variable transmission 208, a second adjusting mechanism power device 209, a second continuously variable transmission 210, a speed measuring device 211, a speed measuring signal line 212, a main speed reducer 213 and a second clutch 214.
A second input bevel gear 301, a second reducer input shaft 302, a first input bevel gear 303, a first reducer input shaft 304, a first double bevel gear 305, a first main planet carrier drive shaft 306, a first sleeve 307, a first retainer ring 308, a first pin 309, a first main planet bevel gear 310, a first main planet shaft 311, a first main planet carrier 312, a third sleeve 313, a second double bevel gear 314, a second sleeve 315, a second retainer ring 316, a second pin 317, a first input shaft rotation direction 318, a second input shaft rotation direction 319, a main planet carrier rotation direction 320, a main planet carrier rotation trajectory 321, a second double bevel gear rotation trajectory 322, a second double bevel gear rotation direction 323, an output shaft axis 324, a main planet bevel gear rotation direction 325, a main planet shaft axis 326, a main planet bevel gear rotation trajectory 327, a double bevel gear rotation trajectory 328, a double bevel gear rotation direction 329, a double bevel gear shaft bore one 330, a first inner gear tooth 331, a first outer gear tooth 332, a second double bevel gear tooth, a second double bevel gear shaft hole 333, a second inner gear 334 and a second outer gear 335.
Detailed Description
The invention is further described below with reference to the accompanying drawings. Referring to fig. 31 to 33, 1 to 4, and 27 to 30, the continuously variable transmission system includes an internal combustion engine 201, a first clutch 202, a second coupling gear member 203, a first coupling gear member 206, a first adjustment mechanism power device 207, a first continuously variable transmission 208, a second adjustment mechanism power device 209, a second continuously variable transmission 210, a speed measuring device 211, a final drive 213, and a second clutch 214. An input shaft of the first clutch 202 is connected with an output shaft of the internal combustion engine 201, the first connecting gear component 206 and the second connecting gear component 203 respectively adopt two conical gears or two cylindrical gears, the first connecting gear component 206 connects an output shaft of the first clutch 202 with an input shaft of the first continuously variable transmission 208, the second connecting gear component 203 connects an output shaft of the first clutch 202 with an input shaft of the second continuously variable transmission 210, the first adjusting mechanism power device 207 and the second adjusting mechanism power device 209 respectively adopt an electric motor or a hydraulic actuator or a manual operating lever mechanism, the first adjusting mechanism power device 207 is connected with an adjusting end of the first continuously variable transmission 208, the second adjusting mechanism power device 209 is connected with an adjusting end of the second continuously variable transmission 210, and the main speed reducer 213 adopts a double-cone differential speed reduction mechanism, the two input shafts of the main speed reducer 213 are a first speed reducer input shaft 304 and a second speed reducer input shaft 302 respectively, the output shaft of the main speed reducer 213 is a main planet carrier transmission shaft 306, the first speed reducer input shaft 304 is connected with the output end of the first stepless speed changer 208, the second speed reducer input shaft 302 is connected with the output end of the second stepless speed changer 210, one end of the main planet carrier transmission shaft 306 is connected with the input shaft of the second clutch 214, the other end of the main planet carrier transmission shaft 306 is connected with the speed measuring device 211, and the output shaft of the second clutch 214 is connected with the load device.
The continuously variable transmission system transmits a part of output torque of the internal combustion engine 201 through the first connecting gear component 206 and the first continuously variable transmission 208 to drive the first reducer input shaft 304 of the final reducer 213 to form a first torque transmission channel, the continuously variable transmission system transmits a part of output torque of the internal combustion engine 201 through the second connecting gear component 203 and the second continuously variable transmission 210 to drive the second reducer input shaft 302 of the final reducer 213 to form a second torque transmission channel, and both the first torque transmission channel and the second torque transmission channel can be continuously variable. The rotational speed and direction of the output shaft of the final drive 213 are related to the difference in the rotational speeds of the two input shafts of the final drive 213, the rotation speed of the output end of the continuously variable transmission one 208 is changed by driving the adjusting end of the continuously variable transmission one 208 through the adjusting mechanism power device one 207, namely, the rotating speed of the first reducer input shaft 304 of the main reducer 213 is changed, the second stepless speed changer 210 is driven by the second adjusting mechanism power device 209 to change the rotating speed of the second output end of the second stepless speed changer 210, namely, the rotational speed of the second reducer input shaft 302 of the main reducer 213 is changed, the rotational speed and the rotational direction of the output shaft of the main reducer 213 can be controlled, the rotational speed of the output shaft of the main reducer 213 is monitored by the speed measuring device 211, and the torque output state of the final drive 213 is controlled by the disengaged state or the engaged state of the second clutch 214, so that a ring gear eccentric rotation stepless speed change system adopting full gear transmission is formed.
Referring to fig. 1 to 26, 29 and 30, a first continuously variable transmission 208 has the same structure as a second continuously variable transmission 210, and comprises a fixed plate part, a coupling part, a swinging planetary gear part, a swinging planetary carrier part, a sliding rail carrier part and a balance wheel part, wherein the fixed plate part comprises a fixed plate one 20, a fixed plate two 34, an adjusting plate 27, a guide fixing column 26, an adjusting gear 18, an adjusting rack 19 and a parallel output gear 10, the coupling part comprises a concentric slider 1, a cross slider 2, a swinging slider 3 and a transmission pin 33, the swinging planetary gear part comprises a swinging gear ring 32, a gear fixing shaft 4, a sun gear 12, a transition gear 67, a planetary gear 31 and a hinge part, the hinge part comprises a gear connecting plate one 69, a gear connecting plate two 38, a gear connecting plate three 65, a gear connecting plate four 66, a positioning shaft 68 and a planetary gear, the swing planet support component comprises a swing planet support 14, a swing limiting roller 13 and a limiting roller pin 39, the slide rail support component comprises a slide rail support 24, a second slide rail 37, a linkage gear 29, a linkage gear shaft 88 and a spring stop lever 15, the balance wheel component comprises a balance wheel 28, an adjusting roller pin 21, a profiling adjusting roller 22 and a return spring 16, and the coupler component, the swing planet gear component, the swing planet support component, the slide rail support component and the balance wheel component are sequentially arranged on the inner side of the fixed plate component in the axial direction. The input end of the continuously variable transmission is a first external spline 95 of the sliding rail bracket 24, the output end of the continuously variable transmission is a second external spline 106 of the parallel output gear 10, and the adjusting end of the continuously variable transmission is an adjusting gear shaft of the adjusting gear 18. The swing planet carrier component and the swing planet gear component form a gear ring eccentric rotation planet gear reducer, the fixed part is a sun gear 12, the driving part is a swing planet carrier 14, the driven part is a swing gear ring 32, and the gear ring eccentric rotation planet gear reducer performs speed reduction transmission.
The gear ring eccentric rotation planetary gear reducer has two working states of a concentric operation state and an eccentric operation state. When the ring gear eccentric rotation planetary gear reducer is in an eccentric operation state, the swing ring gear 32 and the sun gear 12 are not concentric, the swing planet carrier 14 drives the swing ring gear 32 to rotate around the swing ring gear axis 111, the swing ring gear 32 also revolves around the sun gear axis 110, if the swing planet carrier 14 rotates a quarter turn along the swing planet carrier forward rotation direction 114 at a certain moment, the number of teeth of the swing ring gear 32 driven by the swing planet carrier 14 to revolve around the sun gear axis 110 along the swing ring gear forward rotation direction 115 is equal to the sum of the swing ring gear eccentric teeth c obtained by dividing the eccentric distance between the swing ring gear quarter teeth b and the swing ring gear 32 in the eccentric movement by the tooth pitch, meanwhile, the transition gear 67 is meshed with the sun gear 12 and drives the planetary gear 31 to rotate, and the number of teeth of the planetary gear 31 driven by the swing ring gear 32 to rotate around the swing ring gear axis 111 along the direction opposite to the swing ring gear forward rotation direction Quarter tooth number a, because swing ring gear 32 rotation direction is opposite with the revolution direction, and swing ring gear quarter tooth number b is greater than sun gear quarter tooth number a, then swing ring gear 32 actual direction of rotation is the same with the revolution direction, if when swinging planet support 14 at a certain moment and rotating the quarter round, then swing ring gear 32 equals swing ring gear quarter tooth number b along swing ring gear forward direction of rotation 115 actual rotatory tooth number and adds swing ring gear eccentric tooth number c and subtracts sun gear quarter tooth number a, the eccentric distance when increasing or reducing swing ring gear 32 eccentric motion can increase or reduce swing ring gear eccentric tooth number c, increase or reduce swing ring gear 32 rotation rate promptly, realize continuously variable transmission's infinitely variable speed purpose.
The second fixing plate 34 is rectangular, or the second fixing plate 34 is disc-shaped, a first cylindrical boss 42 is arranged at the radial center of one axial end of the second fixing plate, a first axial boss shaft hole 43 is arranged at the radial center of the first boss 42, a fourth radial fixing hole 44 is arranged on the radial outer surface of the first boss 42, a second cylindrical boss 46 is arranged on the axial end surface of the second fixing plate 34 on the radial outer side of the first boss 42, a second axial boss shaft hole 45 is arranged at the radial center of the second boss 46, a fourth bearing mounting hole 116 is respectively arranged at each axial end of the second boss 46, the fourth bearing mounting hole 116 is concentric with the second boss shaft hole 45, a plurality of second guide fixing holes 41 are distributed on the radial outer axial end surface of the second fixing plate 34, each second guide fixing hole 41 is provided with a second fixing hole 47 which is vertically intersected with the second guide fixing hole.
The first fixing plate 20 is rectangular or the first fixing plate 20 is disc-shaped, an axial first fixing plate center hole 53 is formed in the radial center of the first fixing plate 20, a bearing mounting hole 117 is formed in one axial end of the first fixing plate 20, the bearing mounting hole 117 is concentric with the first fixing plate center hole 53, a first fixing plate guide hole 54 is formed in the axial end face of the first fixing plate 20 on the radial outer side of the bearing mounting hole 117, a plurality of first guide fixing holes 52 are distributed in the axial end face of the first fixing plate 20 on the radial outer side, each first guide fixing hole 52 is provided with a first fixing hole 55 perpendicularly intersected with the first guide fixing hole 52, and one end of the first fixing hole 55 is located.
The adjusting plate 27 is rectangular or the adjusting plate 27 is disc-shaped, the radial center of the adjusting plate 27 is provided with a conical adjusting cone 40, the radial center of the adjusting cone 40 is provided with an axial adjusting plate center hole 49, the axial end surface of the adjusting plate 27 at the radial outer side of the adjusting cone 40 is provided with a third guide fixing hole 50, the third guide fixing hole 50 is provided with a third fixing hole 51 which is vertically intersected with the third guide fixing hole, one end of the third fixing hole 51 is positioned at the radial outer surface of the adjusting plate 27, and a plurality of adjusting plate guide holes 48 are distributed at the radial outer side axial end surface.
The guide fixing post 26 is cylindrical and has a radial fixing post hole at each end. One axial end of the adjusting gear 18 is provided with a first cylindrical gear tooth, and the other end of the adjusting gear 18 is provided with an adjusting gear shaft. The axial middle of the adjusting rack 19 is a rack, the two axial ends of the adjusting rack 19 are cylindrical, and one axial end of the adjusting rack 19 is provided with a first radial positioning pin hole 105. The parallel output gear 10 is sequentially provided with a second external spline 106, a fourth journal 108, a fourth positioning shaft shoulder 109 and a second cylindrical gear tooth from one axial end to the other axial end, and a third radial positioning pin hole 107 is formed between the second external spline 106 and the fourth journal 108.
The concentric sliding block 1 is in a disc shape, an axial sliding block central hole III 58 is formed in the radial center of the concentric sliding block 1, a second track groove 56 is formed in one axial end of the concentric sliding block 1, the second track groove 56 penetrates through the third sliding block central hole 58 to be distributed in the radial direction, a third bearing mounting hole 118 is formed in the other axial end of the concentric sliding block 1, the third bearing mounting hole 118 is concentric with the third sliding block central hole 58, a coupler gear 57 is arranged on the radial outer side of the other axial end of the concentric sliding block 1, and the coupler.
The swing sliding block 3 is disc-shaped, an axial sliding block center hole I63 is formed in the radial center of the swing sliding block, a track groove I62 is arranged at one axial end of the swing sliding block 3, the track groove I62 penetrates through the sliding block center hole I63 to be distributed radially, and a plurality of transmission pin holes II 64 are uniformly distributed on the radial outer surface of the swing sliding block 3.
The crosshead shoe 2 is in a disc shape, an axial slider center hole II 59 is formed in the radial center of the crosshead shoe 2, a track boss II 61 is arranged at one axial end of the crosshead shoe 2, the track boss II 61 penetrates through the slider center hole II 59 to be distributed radially, the radial section profile of the track boss II 61 is meshed with the radial section profile of a track groove II 56 of the concentric slider 1, a track boss I60 is arranged at the other axial end of the crosshead shoe 2, the track boss I60 penetrates through the slider center hole II 59 to be distributed radially, the radial section profile of the track boss I60 is meshed with the radial section profile of a track groove I62 of the swing slider 3, and the track boss II 61 is perpendicular to the track boss I60.
The driving pin 33, the first fixing pin 36, the second fixing pin 35, the third fixing pin 17, the fourth fixing pin 5 and the fifth fixing pin 7 are cylindrical. The positioning retainer ring 8 is cylindrical, a positioning retainer ring shaft hole is arranged at the radial center of the positioning retainer ring, and a radial positioning retainer ring pin hole is formed in the radial outer surface of the positioning retainer ring 8.
The swing gear ring 32 is cylindrical, a cylindrical inner gear is arranged on the radial inner surface of one axial end of the swing gear ring, and a plurality of radial transmission pin holes 70 are uniformly distributed from the radial inner surface to the outer surface of the other axial end of the swing gear ring 32. The sun gear 12, the transition gear 67 and the planetary gear 31 are cylindrical external gears, the radial center of the sun gear 12 is a sun gear shaft hole, the inner surface of the sun gear shaft hole is provided with an inner key groove, the radial center of the transition gear 67 is a transition gear shaft hole, and the radial center of the planetary gear 31 is a planetary gear shaft hole.
The gear fixing shaft 4 is cylindrical, a shaft section III 72, a positioning shaft shoulder III 73, a shaft neck III 74, a shaft section II 75 and a shaft neck II 77 are sequentially arranged from one end to the other end of the gear fixing shaft in the axial direction, a positioning pin hole II 71 is formed in the radial outer surface of one end, far away from the positioning shaft shoulder III 73, of the shaft section III 72, an outer key groove 76 is formed in the radial outer surface of the shaft section II 75, the diameter of the shaft neck II 77 is smaller than that of the shaft section II 75, and a positioning shaft shoulder II is formed between the shaft neck II 77 and the. The positioning shaft 68 is cylindrical, the diameters of the two ends of the positioning shaft 68 are smaller than the diameter of the middle position of the positioning shaft 68, and a positioning shaft shoulder V is formed between each of the two ends of the positioning shaft 68 and the middle position. The planet pin 30 is cylindrical, and a shoulder of the planet pin is formed at one axial end thereof.
The first gear connecting plate 69 and the second gear connecting plate 38 are identical in structure, the first gear connecting plate 69 and the second gear connecting plate 38 are in an oblong shape, a first hinge hole 80 is formed in one radial end of the first gear connecting plate, and a second hinge hole 78 and a third hinge hole 79 are distributed in parallel in the other radial end of the first gear connecting plate. The gear connecting plate III 65 is in an oval shape, one end in the radial direction of the gear connecting plate III is provided with a hinge hole IV 81, the other end in the radial direction of the gear connecting plate III is provided with a hinge shaft 82, and the hinge shaft 82 is perpendicular to the plate surface of the gear connecting plate III 65. The gear connecting plate four 66 is in an oval shape, one end in the radial direction of the gear connecting plate four 66 is provided with a hinge hole six 120, the other end in the radial direction of the gear connecting plate four 66 is provided with a hinge hole five 119, the position of the hinge hole five 119 of the gear connecting plate four 66 corresponds to the position of the hinge shaft 82 of the gear connecting plate three 65, and the position of the hinge hole six 120 of the gear connecting plate four 66 corresponds to the position of the hinge hole four 81 of the gear connecting plate three 65.
The oscillating planet carrier 14 is in a disc shape, an axial planet carrier central hole 85 is formed in the radial center of the oscillating planet carrier 14, two planet carrier dovetail grooves 84 which are parallel to each other are formed in one axial end of the oscillating planet carrier 14, the two planet carrier dovetail grooves 84 are respectively located on two radial sides of the planet carrier central hole 85, a linkage rack II 87 is arranged between the two planet carrier dovetail grooves 84, a planet gear pin shaft fixing hole 86 is formed in the axial end face, close to the planet carrier central hole 85, of the oscillating planet carrier 14 between the two planet carrier dovetail grooves 84, and a plurality of limiting roller pin shaft fixing holes 83 are distributed in the axial end face of the radial outer side of the. The swing limiting roller 13 is cylindrical, and an axial limiting roller shaft hole is formed in the radial center of the swing limiting roller 13. The limiting roller pin 39 is cylindrical, and a limiting roller pin shoulder is arranged at one axial end of the limiting roller pin 39.
The balance wheel 28 is in a disc shape, an axial balance wheel center hole 100 is arranged at the radial center of the balance wheel 28, two balance wheel dovetail grooves 99 which are parallel to each other are arranged at one axial end of the balance wheel 28, the two balance wheel dovetail grooves 99 are respectively positioned at two radial sides of the balance wheel center hole 100, a linkage rack I98 is arranged between the two balance wheel dovetail grooves 99, a triangular roller bracket 102 is arranged at the other axial end of the balance wheel 28, a roller mounting groove 104 is arranged on a triangular oblique side of the roller bracket 102, an adjusting roller pin shaft fixing hole 103 is arranged along the direction of the triangular oblique side of the roller bracket 102, the adjusting roller pin shaft fixing hole 103 penetrates through the roller mounting groove 104, the roller bracket 102 and the linkage rack I98 are respectively positioned at two radial sides of the balance wheel center hole 100, a spring mounting groove 101 is arranged on the radial outer surface of the balance wheel 28, the radial outer surface direction of the balance wheel 28 is an opening end I, and the axial end surface direction of the balance wheel 28 away from the roller bracket 102 of the spring installation groove 101 is an opening end II. The profile adjusting roller 22 is cylindrical and has an axial adjusting roller axle hole at its radial center. The adjusting roller pin 21 is cylindrical, and one axial end of the adjusting roller pin is provided with an adjusting roller pin shaft shoulder.
The axial end of the slide rail bracket 24 is sequentially provided with a first external spline 95, a first journal 96, a first shaft section 97 and a slide rail bracket disc from one axial end to the other axial end, the diameter of the first journal 96 is smaller than that of the first shaft section 97, a first positioning shaft shoulder is formed between the first journal 96 and the first shaft section 97, the slide rail bracket disc is disc-shaped, the radial center of the slide rail bracket disc is provided with a second axial bearing mounting hole 91, the second bearing mounting hole 91 is concentric with the first journal 96, the second bearing mounting hole 91 and the first shaft section 97 are respectively positioned at the axial two ends of the slide rail bracket disc, the axial end faces of the slide rail bracket discs at the radial two sides of the second bearing mounting hole 91 are respectively provided with a first slide rail 92, the radial cross section of the first slide rail 92 is dovetail-shaped, the cross section contour of the first slide rail 92 is meshed with the cross section contour of a dovetail groove 84 of a planet bracket 14, the two slide rails, the radial section of each slide rail bracket dovetail groove 93 is dovetail-shaped, the two slide rail bracket dovetail grooves 93 are parallel to each other, the slide rail bracket dovetail grooves 93 are parallel to the first slide rails 92, a rectangular gear groove hole 89 is formed in the axial end face of a slide rail bracket disc between the two first slide rails 92, the gear groove hole 89 is provided with a linkage gear shaft fixing hole 90 which is vertically intersected with the gear groove hole, the linkage gear shaft fixing hole 90 is vertically intersected with the two slide rail bracket dovetail grooves 93, the two outer ends of the linkage gear shaft fixing hole 90 are located on the radial outer surface of the slide rail bracket disc, the two inner ends of the linkage gear shaft fixing hole 90 are located in the gear groove hole 89, a spring stop rod fixing hole 94 is formed in the axial end face of the slide rail bracket disc between the two slide rail bracket dovetail grooves 93, and the spring stop.
The slide rail bracket part comprises two slide rails II 37, the section of each slide rail II 37 is in a double-dovetail shape, one dovetail-shaped profile of the section of each slide rail II 37 is meshed with the section profile of a dovetail groove 93 of the slide rail bracket 24, and the other dovetail-shaped profile of the section of each slide rail II 37 is meshed with the section profile of a dovetail groove 99 of a balance wheel 28. The interlocking gear 29 is a cylindrical external gear whose radial center is an interlocking gear shaft hole. The link gear shaft 88 is cylindrical. The spring catch lever 15 is L-shaped and has a circular cross-section.
The axial middle positions of a plurality of guide fixing columns 26 of the fixing plate component are arranged in a guide plate guide hole 48 of the adjusting plate 27, the axial two ends of each guide fixing column 26 are respectively arranged in a guide fixing hole I52 of the first fixing plate 20 and a guide fixing hole II 41 of the second fixing plate 34, a fixing pin I36 is arranged in a fixing hole I55 of the first fixing plate 20 and a fixing column pin hole at one axial end of the guide fixing column 26, and a fixing pin II 35 is arranged in a fixing hole II 47 of the second fixing plate 34 and a fixing column pin hole at the other axial end of the guide fixing column 26. The first bearing 23 is mounted in the first bearing mounting hole 117 of the first fixing plate 20. One axial end of the adjusting rack 19 is installed in the guide fixing hole three 50 of the adjusting plate 27, the fixing pin three 17 is installed in the fixing hole three 51 of the adjusting plate 27 and the positioning pin hole one 105 of one axial end of the adjusting rack 19, and the other axial end of the adjusting rack 19 is installed in the fixing plate guide hole 54 of the fixing plate one 20. The cylindrical teeth of the adjusting gear 18 are in engagement with the axially intermediate toothed rack of the adjusting toothed rack 19. The two bearings IV 9 are respectively installed in the bearing installation holes IV 116 of the fixed plate II 34, the external spline II 106 of the parallel output gear 10 penetrates through the boss shaft hole II 45 of the fixed plate II 34 and is positioned at the axial outer side of the fixed plate II 34, the journal IV 108 of the parallel output gear 10 penetrates through the boss shaft hole II 45 of the fixed plate II 34 and is installed in the shaft hole of the bearing IV 9, the cylindrical gear tooth II of the parallel output gear 10 is positioned between the fixed plate II 34 and the adjusting plate 27 in the axial direction, the positioning retainer shaft hole of the positioning retainer 8 is installed on the radial outer surface of the journal IV 108 of the parallel output gear 10, the fixing pin V7 is installed in the positioning pin hole III 107 of the parallel output gear 10 and in the positioning retainer of the positioning retainer 8, the shaft section III 72 of the gear fixing shaft 4 is installed in the boss shaft hole I43 of the fixed plate II 34, and the fixing pin IV 5 is installed in.
The first track boss 60 of the crosshead shoe 2 of the coupling component is installed in the first track groove 62 of the swing slider 3, the second track boss 61 of the crosshead shoe 2 is installed in the second track groove 56 of the concentric slider 1, the third bearing 6 is installed in the third bearing installation hole 118 of the concentric slider 1, the shaft hole of the third bearing 6 is installed on the radial outer surface of the third journal 74 of the gear fixing shaft 4, the gear fixing shaft 4 sequentially passes through the third slider center hole 58 of the concentric slider 1, the second slider center hole 59 of the crosshead shoe 2 and the first slider center hole 63 of the swing slider 3, and the coupling gear 57 of the concentric slider 1 is meshed with the second cylindrical gear tooth of the parallel output gear 10.
The sun gear 12 of the oscillating planetary gear part is installed on the radial outer surface of the second shaft section 75 of the gear fixing shaft 4 through the key bar 11, namely the key bar 11 is installed in the outer key groove 76 of the gear fixing shaft 4 and the inner key groove of the sun gear 12, the first gear connecting plate 69 and the second gear connecting plate 38 are respectively installed on the two axial ends of the sun gear 12, the hinge holes 80 of the first gear connecting plate 69 and the second gear connecting plate 38 are respectively installed on the radial outer surface of the second shaft section 75 of the gear fixing shaft 4, the two axial ends of the positioning shaft 68 are respectively installed in the hinge holes 79 of the first gear connecting plate 69 and the second gear connecting plate 38, the hinge shaft 82 of the third gear connecting plate 65 is respectively installed in the hinge holes 78 of the first gear connecting plate 69 and the second gear connecting plate 38, the transition gear 67 is installed at a position between the first gear connecting plate 69 and the second gear connecting plate 38 in the axial direction, a hinge hole five 119 of a gear connecting plate four 66 is arranged at one end of the axial outer side of a hinge shaft 82 of a gear connecting plate three 65, the gear connecting plate four 66 is positioned at one end of the axial outer side of a gear connecting plate two 38, the planet gear pin shafts 30 are respectively arranged in a hinge hole six 120 of the gear connecting plate four 66 and a hinge hole four 81 of the gear connecting plate three 65, the planet gear pin shaft shoulders of the planet gear pin shafts 30 are contacted and arranged with the gear connecting plate four 66, the planet gear 31 is arranged at a position between the gear connecting plate three 65 and the gear connecting plate four 66 in the axial direction, the planet gear shaft holes of the planet gear 31 are arranged on the radial outer surface of the planet gear pin shaft 30, the swinging gear ring 32 is arranged at the radial outer side of the planet gear 31, the transition gear 67 and the sun gear 12, the swinging gear ring 32, the planet gear 31, the transition gear 67 and the sun gear 12 are sequentially meshed, the And a second moving pin hole 64.
The axial middle position of a limiting roller pin shaft 39 of the swing planet carrier component is arranged in a limiting roller shaft hole of a swing limiting roller 13, a limiting roller pin shaft shoulder of the limiting roller pin shaft 39 is in contact installation with one axial end of the swing limiting roller 13, one axial outer end of the limiting roller pin shaft 39 is arranged in a limiting roller pin shaft fixing hole 83 of the swing planet carrier 14, a plurality of swing limiting rollers 13 are located at one axial end of the swing planet carrier 14 without a linkage rack II 87, a gear fixing shaft 4 penetrates through a planet carrier center hole 85 of the swing planet carrier 14, the radial outer surfaces of a plurality of swing limiting rollers 13 are in contact installation with the radial outer surface of a swing gear ring 32, and one axial outer end of a planet gear pin shaft 30 is arranged in a planet gear pin shaft fixing hole 86 of the swing planet.
One axial end of a spring stop rod 15 of the slide rail bracket component is arranged in a spring stop rod fixing hole 94 of the slide rail bracket 24, a linkage gear 29 is arranged in a gear groove hole 89 of the slide rail bracket 24, a linkage gear shaft 88 is arranged in a linkage gear shaft fixing hole 90 of the slide rail bracket 24 and a linkage gear shaft hole of the linkage gear 29, a half radial section profile of each slide rail two 37 is arranged in a slide rail bracket dovetail groove 93 of the slide rail bracket 24, so that the linkage gear shaft 88 cannot fall off from the linkage gear shaft fixing hole 90 of the slide rail bracket 24, a bearing two 25 is arranged in a bearing mounting hole two 91 of the slide rail bracket 24, an external spline one 95 of the slide rail bracket 24 sequentially passes through an adjusting plate center hole 49 of an adjusting plate 27 and a fixing plate center hole one 53 of a fixing plate one 20 and is positioned at the axial outer side of the fixing plate one 20, a journal one, the second shaft neck 77 of the gear fixing shaft 4 is arranged in the shaft hole of the second bearing 25, the two slide rails 92 of the slide rail bracket 24 are respectively arranged in the planet bracket dovetail grooves 84 of the swinging planet bracket 14, and the linkage gear 29 is meshed with the linkage rack gear two 87 of the swinging planet bracket 14.
The copying adjusting roller 22 of the balance wheel assembly is mounted in the roller mounting groove 104 of the balance wheel 28, the adjusting roller pin shaft 21 is arranged in the adjusting roller pin shaft fixing hole 103 of the balance wheel 28 and the adjusting roller shaft hole of the profiling adjusting roller 22, the radial outer surface of the profiling adjusting roller 22 is contacted and installed with the radial outer surface of the adjusting cone 40 of the adjusting plate 27, the return spring 16 is installed in the spring installation groove 101 of the balance wheel 28, the first shaft section 97 of the slide rail bracket 24 passes through the balance wheel center hole 100 of the balance wheel 28, the other half of the radial section profile of each second slide rail 37 is arranged in the balance wheel dovetail groove 99 of the balance wheel 28, the other axial end of the spring bar 15 is fitted into the spring fitting groove 101 of the balance wheel 28, and the other axial end of the spring stop rod 15 is contacted and installed with the axial end face of the return spring 16, and the linkage gear 29 is meshed with the linkage rack I98 of the balance wheel 28.
Referring to fig. 32 to 35, the final drive 213 includes a main planet carrier assembly including a main planet carrier shaft 306, a main planet bevel gear 310, a main planet shaft 311, a main planet carrier 312, and a sleeve three 313, a second input bevel gear 301, a second reducer input shaft 302, a first input bevel gear 303, a first reducer input shaft 304, a first double bevel gear 305, a first sleeve 307, a first retainer 308, a first pin 309, a second double bevel gear 314, a second sleeve 315, a second retainer 316, and a second pin 317. The second input bevel gear 301, the second reducer input shaft 302, the first input bevel gear 303 and the first reducer input shaft 304 are respectively arranged on the radial outer side of the main planetary carrier component, and the two axial ends of the transmission shaft 306 of the main planetary carrier are not only output shafts of the main reducer 213, but also output shafts of the stepless speed change system.
The main planet carrier 312 is annular, a plurality of carrier mounting planes are uniformly distributed on the radial inner surface of the main planet carrier 312, and a carrier fixing shaft hole is formed in the center of each carrier mounting plane. A plurality of radial fixed shaft holes are uniformly distributed on the radial outer surface of a fixed shaft shoulder in the axial middle of the main planet carrier transmission shaft 306, one end of a main planet shaft 311 is installed in the fixed shaft hole of the main planet carrier transmission shaft 306, the other end of the main planet shaft 311 is installed in a carrier fixed shaft hole of a main planet carrier 312, a shaft sleeve III 313 is installed in the axial middle position of the main planet shaft 311, and a main planet bevel gear 310 is installed on the radial outer surface of the shaft sleeve III 313.
The radial middle of the first double bevel gear 305 is a first double bevel gear shaft hole 330, and the axial two ends of the radial outer side of the first double bevel gear 305 are respectively an inner gear tooth 331 and an outer gear tooth 332. The radial middle of the second double bevel gear 314 is a second double bevel gear shaft hole 333, and the axial two ends of the radial outer side of the second double bevel gear 314 are respectively an inner gear tooth 334 and an outer gear tooth 335. The first double bevel gear 305 and the second double bevel gear 314 are respectively arranged at two axial ends of the main planet carrier component, the first internal gear teeth 331 of the first double bevel gear 305 are meshed with the main planet bevel gear 310 of the main planet carrier component, and the second internal gear teeth 334 of the second double bevel gear 314 are meshed with the main planet bevel gear 310 of the main planet carrier component. A first shaft sleeve 307 is arranged at the right position of a fixed shaft shoulder shaft of the main planet carrier transmission shaft 306, a first double bevel gear 305 is arranged on the radial outer surface of the first shaft sleeve 307, and a first retainer ring 308 and a first pin 309 are arranged and fixed on the radial outer surface of the main planet carrier transmission shaft 306 on the axial right side of the first shaft sleeve 307. The second shaft sleeve 315 is installed at the left side position of the fixed shaft shoulder shaft of the main planet carrier transmission shaft 306, the second double bevel gear 314 is installed on the radial outer surface of the second shaft sleeve 315, and the second retainer ring 316 and the second pin 317 are installed and fixed on the radial outer surface of the main planet carrier transmission shaft 306 on the axial left side of the second shaft sleeve 315. One axial end of the first reducer input shaft 304 is provided with a first input bevel gear 303, the first input bevel gear 303 is meshed with first outer gear teeth 332 of a first double bevel gear 305, one axial end of the second reducer input shaft 302 is provided with a second input bevel gear 301, and the second input bevel gear 301 is meshed with second outer gear teeth 335 of a second double bevel gear 314.
Referring to fig. 31 to 33, fig. 1 to 4, and fig. 27 to 30, the continuously variable transmission system operation process is: if the gear ratio of the first connecting gear member 206 is set equal to the gear ratio of the second connecting gear member 203, the gear ratio between the first input bevel gear 303 of the final drive 213 and the first outer gear teeth 332 of the first double bevel gear 305 is set equal to the gear ratio between the second input bevel gear 301 of the final drive 213 and the second outer gear teeth 335 of the second double bevel gear 314. If the main planetary carrier rotation direction 320 of the final drive 213 is set to be the same as the primary double bevel gear rotation direction 329, the vehicle is in the forward running state, and if the main planetary carrier rotation direction 320 of the final drive 213 is set to be the same as the secondary double bevel gear rotation direction 323, the vehicle is in the backward running state.
Before the continuously variable transmission system operates, the first clutch 202 and the second clutch 214 are in a separated state. When the continuously variable transmission system is started, the first continuously variable transmission 208 is in a concentric operation state by operating the first adjusting mechanism power device 207, the second continuously variable transmission 210 is in a concentric operation state by operating the second adjusting mechanism power device 209, the transmission ratio of the first continuously variable transmission 208 is equal to that of the second continuously variable transmission 210, the internal combustion engine 201 is started and operates in an economic speed region, the automobile control module sends a command to enable the first clutch 202 to be in an engagement state, the output torque of the internal combustion engine 201 is transmitted to the output shaft of the first clutch 202, a part of the output torque of the internal combustion engine 201 is transmitted to the first torque transmission channel through the first connecting gear part 206, the part of the output torque is transmitted to the first reducer input shaft 304 of the main reducer 213 through the first continuously variable transmission 208, and meanwhile, a part of the output torque of the internal combustion engine 201 is transmitted to the second torque transmission channel through the second connecting gear part 203, the partial output torque is transmitted to a second reducer input shaft 302 of the main reducer 213 through a second continuously variable transmission 210, the rotating speed of the first reducer input shaft 304 is equal to that of the second reducer input shaft 302, the rotating speed of a transmission shaft 306 of the main planet carrier is zero, the main reducer 213 is in a running stop state, namely the automobile is in a running stop state, and zero rotating speed output when the internal combustion engine 201 does not stop is achieved.
If the main reducer 213 is in a stop running state and the automobile is operated to run, the speed measuring device 211 detects that the rotating speed of the main planet carrier transmission shaft 306 is zero, the automobile control module sends a command to enable the clutch II 214 to be in an engaged state, the continuously variable transmission I208 is in an eccentric running state through the operation of the adjusting mechanism power device I207, the continuously variable transmission I208 drives the reducer input shaft I304 to rotate at a speed which is larger than the rotating speed of the continuously variable transmission II 210 to drive the reducer input shaft II 302, the rotating direction 320 of the main planet carrier of the main reducer 213 is the same as the rotating direction 329 of the double bevel gear I, the main reducer 213 is in a forward running state, and as the eccentric distance between the swinging gear ring axis 111 of the continuously variable transmission I208 and the sun gear axis 110 increases, the difference between the rotating speed of the reducer input shaft I304 and the rotating speed of the reducer input shaft II 302 increases, namely the difference between the rotating linear, because the rotating linear speed of the main planet carrier 312 is equal to half of the difference between the rotating linear speed of the first double bevel gear 305 and the rotating linear speed of the second double bevel gear 314, the output rotating speed of the main planet carrier transmission shaft 306 of the main speed reducer 213 is increased, zero rotating speed output when the internal combustion engine 201 is not stopped is realized, the output rotating speed can be gradually increased from the zero rotating speed to the cruising speed, and the automobile is in a forward driving state.
If the main reducer 213 is in a stop running state and the automobile is operated to run, the speed measuring device 211 detects that the rotating speed of the main planet carrier transmission shaft 306 is zero, the automobile control module sends a command to enable the clutch II 214 to be in an engaged state, the continuously variable transmission II 210 is in an eccentric running state by operating the adjusting mechanism power device II 209, the continuously variable transmission I208 drives the reducer input shaft I304 to rotate at a speed lower than that of the continuously variable transmission II 210 to drive the reducer input shaft II 302, the main planet carrier rotating direction 320 of the main reducer 213 is the same as the double-bevel gear II rotating direction 323, the main reducer 213 is in a backward running state, and as the eccentric distance between the swinging gear ring axis 111 of the continuously variable transmission II 210 and the sun gear axis 110 increases, the difference between the rotating speed of the reducer input shaft II 302 and the rotating speed of the reducer input shaft I304 increases, namely the difference between the rotating linear speed of the double-bevel gear II 314 and, because the rotating linear speed of the main planet carrier 312 is equal to half of the difference between the rotating linear speed of the second double bevel gear 314 and the rotating linear speed of the first double bevel gear 305, the output rotating speed of the main planet carrier transmission shaft 306 of the main speed reducer 213 is increased, zero rotating speed output when the internal combustion engine 201 is not stopped is realized, the output rotating speed can be gradually increased from the zero rotating speed to the cruising speed, the automobile is in a backward driving state, and the rotating direction of the output shaft of the main speed reducer 213 can be changed when the input shaft of the main speed reducer 213 does not change the rotating direction.

Claims (2)

1. A gear ring eccentric rotation stepless speed change system is characterized in that: the stepless speed change system comprises an internal combustion engine (201), a first clutch (202), a second connecting gear component (203), a first connecting gear component (206), a first adjusting mechanism power device (207), a first stepless speed changer (208), a second adjusting mechanism power device (209), a second stepless speed changer (210), a speed measuring device (211), a main speed reducer (213) and a second clutch (214); an input shaft of a first clutch (202) is connected with an output shaft of an internal combustion engine (201), a first connecting gear component (206) and a second connecting gear component (203) respectively adopt two conical gears or two cylindrical gears, the first connecting gear component (206) connects an output shaft of the first clutch (202) with an input shaft of a first continuously variable transmission (208), the second connecting gear component (203) connects an output shaft of the first clutch (202) with an input shaft of a second continuously variable transmission (210), a first adjusting mechanism power device (207) and a second adjusting mechanism power device (209) respectively adopt an electric motor or a hydraulic execution device or a manual operating lever mechanism, the first adjusting mechanism power device (207) is connected with an adjusting end of the first continuously variable transmission (208), and the second adjusting mechanism power device (209) is connected with an adjusting end of the second continuously variable transmission (210), the main speed reducer (213) adopts a double-cone-tooth differential speed reduction mechanism, two input shafts of the main speed reducer (213) are a first speed reducer input shaft (304) and a second speed reducer input shaft (302), an output shaft of the main speed reducer (213) is a main planet carrier transmission shaft (306), the first speed reducer input shaft (304) is connected with the output end of the first stepless speed changer (208), the second speed reducer input shaft (302) is connected with the output end of the second stepless speed changer (210), one end of the main planet carrier transmission shaft (306) is connected with the input shaft of the second clutch (214), the other end of the main planet carrier transmission shaft (306) is connected with the speed measuring device (211), and the output shaft of the second clutch (214) is connected with the load device;
the continuously variable transmission system transmits a part of output torque of an internal combustion engine (201) through a first connecting gear component (206) and a first continuously variable transmission (208) to drive a first reducer input shaft (304) of a main reducer (213) to form a first torque transmission channel, transmits a part of output torque of the internal combustion engine (201) through a second connecting gear component (203) and a second continuously variable transmission (210) to drive a second reducer input shaft (302) of the main reducer (213) to form a second torque transmission channel, and the first torque transmission channel and the second torque transmission channel can be continuously variable; the rotation speed and the rotation direction of an output shaft of a main speed reducer (213) are related to the rotation speed difference of two input shafts of the main speed reducer (213), the rotation speed and the rotation direction of the output shaft of the main speed reducer (213) are changed by driving an adjusting end of a first continuously variable transmission (208) by an adjusting mechanism power device (207), namely, the rotation speed of a first speed reducer input shaft (304) of the main speed reducer (213) is changed, the rotation speed of the output shaft of a second continuously variable transmission (210) is changed by driving an adjusting end of a second continuously variable transmission (210) by an adjusting mechanism power device (209), namely, the rotation speed of a second speed reducer input shaft (302) of the main speed reducer (213) is changed, the rotation speed and the rotation direction of the output shaft of the main speed reducer (213) can be controlled, the rotation speed of the output shaft of the main speed reducer (213) is monitored by a speed measuring device (211), and the torque, forming a gear ring eccentric rotation stepless speed change system adopting all-gear transmission;
the first stepless transmission (208) and the second stepless transmission (210) are identical in structure, the first stepless transmission comprises a fixing plate component, a coupling component, a swinging planetary gear component, a swinging planetary support component, a sliding rail support component and a balance wheel component, the fixing plate component comprises a fixing plate I (20), a fixing plate II (34), an adjusting plate (27), a guide fixing column (26), an adjusting gear (18), an adjusting rack (19) and a parallel output gear (10), the coupling component comprises a concentric slide block (1), a cross slide block (2), a swinging slide block (3) and a transmission pin (33), the swinging planetary gear component comprises a swinging gear ring (32), a gear fixing shaft (4), a sun gear (12), a transition gear (67), a planetary gear (31) and a hinge component, and the hinge component comprises a gear connecting plate I (69), a gear connecting plate II (38, The device comprises a gear connecting plate III (65), a gear connecting plate IV (66), a positioning shaft (68) and a planetary gear pin shaft (30), wherein the swinging planetary support component comprises a swinging planetary support (14), a swinging limiting roller (13) and a limiting roller pin shaft (39), the sliding rail support component comprises a sliding rail support (24), a sliding rail II (37), a linkage gear (29), a linkage gear shaft (88) and a spring stop lever (15), the balance wheel component comprises a balance wheel (28), an adjusting roller pin shaft (21), a profiling adjusting roller (22) and a reset spring (16), and the coupling component, the swinging planetary gear component, the swinging planetary support component, the sliding rail support component and the balance wheel component are sequentially arranged on the inner side of the fixed plate component in the axial direction; the input end of the continuously variable transmission is a first external spline (95) of a sliding rail bracket (24), the output end of the continuously variable transmission is a second external spline (106) of a parallel output gear (10), and the adjusting end of the continuously variable transmission is an adjusting gear shaft of an adjusting gear (18); the swing planet carrier component and the swing planet gear component form a gear ring eccentric rotation planet gear reducer, a fixed part of the gear ring eccentric rotation planet gear reducer is a sun gear (12), a driving part is a swing planet carrier (14), a driven part is a swing gear ring (32), and the gear ring eccentric rotation planet gear reducer performs speed reduction transmission;
the gear ring eccentric rotation planetary gear reducer has two working states of a concentric operation state and an eccentric operation state; when the gear ring eccentric rotation planetary gear reducer is in an eccentric operation state, the swinging gear ring (32) and the sun gear (12) are not concentric, the swinging planet support (14) drives the swinging gear ring (32) to rotate around the swinging gear ring axis (111), the swinging gear ring (32) also revolves around the sun gear axis (110), if the swinging planet support (14) rotates a quarter turn along the swinging planet support forward rotation direction (114) at a certain moment, the number of teeth of the swinging planet support (14) driving the swinging gear ring (32) to revolve around the sun gear axis (110) along the swinging gear ring forward rotation direction (115) is equal to the sum of the number b of the quarter teeth of the swinging gear ring and the eccentric distance of the swinging gear ring (32) during eccentric movement divided by the tooth pitch, and meanwhile, the transition gear (67) is meshed with the sun gear (12) and drives the planet gear (31) to rotate, the number of teeth of the swinging gear ring (32) which is driven by the planet gear (31) to rotate around the axis (111) of the swinging gear ring along the reverse direction of the forward rotation direction (115) of the swinging gear ring is equal to the quarter tooth number a of the sun gear, because the rotation direction of the swinging gear ring (32) is reverse to the revolution direction, and the quarter tooth number b of the swinging gear ring is larger than the quarter tooth number a of the sun gear, the actual rotation direction of the swinging gear ring (32) is the same as the revolution direction, if the swinging planet support (14) rotates for a quarter turn at a certain moment, the actual rotation number of teeth of the swinging gear ring (32) along the forward rotation direction (115) of the swinging gear ring is equal to the quarter tooth number b of the swinging gear ring plus the eccentric tooth number c of the swinging gear ring minus the quarter tooth number a of the sun gear, and the eccentric distance when the swinging gear ring (, namely, the rotating speed of the swinging gear ring (32) is increased or reduced, and the purpose of stepless speed change of the stepless speed changer is achieved;
the second fixing plate (34) is rectangular, or the second fixing plate (34) is disc-shaped, a first cylindrical boss (42) is arranged at the radial center of one axial end of the second fixing plate, a first axial boss shaft hole (43) is arranged at the radial center of the first boss (42), a fourth radial fixing hole (44) is arranged on the radial outer surface of the first boss (42), a second cylindrical boss (46) is arranged on the axial end face of the second fixing plate (34) at the radial outer side of the first boss (42), a second axial boss shaft hole (45) is arranged at the radial center of the second boss (46), a fourth bearing mounting hole (116) is respectively arranged at each axial two ends of the second boss (46), the fourth bearing mounting hole (116) is concentric with the second boss shaft hole (45), a plurality of second guide fixing holes (41) are distributed on the radial outer axial end face of the second fixing plate (34), and each second guide fixing hole (41) is provided with a, one end of the second fixing hole (47) is positioned on the radial outer surface of the second fixing plate (34);
the first fixing plate (20) is rectangular, or the first fixing plate (20) is disc-shaped, an axial first fixing plate center hole (53) is formed in the radial center of the first fixing plate (20), a first bearing mounting hole (117) is formed in one axial end of the first fixing plate (20), the first bearing mounting hole (117) is concentric with the first fixing plate center hole (53), a first fixing plate guide hole (54) is formed in the axial end face of the first fixing plate (20) on the radial outer side of the first bearing mounting hole (117), a plurality of first guide fixing holes (52) are distributed in the axial end face of the radial outer side of the first fixing plate (20), each first guide fixing hole (52) is provided with a first fixing hole (55) which is perpendicularly intersected with the first guide fixing hole, and one end of each first fixing hole;
the adjusting plate (27) is rectangular, or the adjusting plate (27) is disc-shaped, a conical adjusting cone (40) is arranged at the radial center of the adjusting cone (40), an axial adjusting plate center hole (49) is formed in the radial center of the adjusting cone (40), a third guide fixing hole (50) is formed in the axial end face of the adjusting plate (27) on the radial outer side of the adjusting cone (40), a third fixing hole (51) which is vertically intersected with the third guide fixing hole is formed in the third guide fixing hole (50), one end of the third fixing hole (51) is located on the radial outer surface of the adjusting plate (27), and a plurality of adjusting plate guide holes (48) are distributed in the axial end face on the;
the guide fixing column (26) is cylindrical, and two ends of the guide fixing column are respectively provided with a radial fixing column pin hole; one axial end of the adjusting gear (18) is provided with a cylindrical gear tooth I, and the other end of the adjusting gear (18) is provided with an adjusting gear shaft; the axial middle of the adjusting rack (19) is provided with a rack, the two axial ends of the adjusting rack (19) are cylindrical, and one axial end of the adjusting rack (19) is provided with a radial positioning pin hole I (105); a second external spline (106), a fourth journal (108), a fourth positioning shaft shoulder (109) and a second cylindrical gear tooth are sequentially arranged from one end to the other end of the parallel output gear (10) in the axial direction, and a third radial positioning pin hole (107) is formed between the second external spline (106) and the fourth journal (108);
the concentric sliding block (1) is disc-shaped, an axial sliding block central hole III (58) is formed in the radial center of the concentric sliding block, a second track groove (56) is arranged at one axial end of the concentric sliding block (1), the second track groove (56) penetrates through the sliding block central hole III (58) to be distributed in the radial direction, a third bearing mounting hole (118) is formed in the other axial end of the concentric sliding block (1), the third bearing mounting hole (118) is concentric with the third sliding block central hole (58), a coupler gear (57) is arranged on the outer radial side of the other axial end of the concentric sliding block (1), and the coupler gear (57);
the swing sliding block (3) is disc-shaped, an axial sliding block center hole I (63) is formed in the radial center of the swing sliding block, a track groove I (62) is arranged at one axial end of the swing sliding block (3), the track groove I (62) penetrates through the sliding block center hole I (63) to be distributed radially, and a plurality of transmission pin holes II (64) are uniformly distributed on the radial outer surface of the swing sliding block (3);
the cross sliding block (2) is disc-shaped, an axial sliding block center hole II (59) is formed in the radial center of the cross sliding block, a track boss II (61) is arranged at one axial end of the cross sliding block (2), the track boss II (61) penetrates through the sliding block center hole II (59) and is distributed radially, the radial section profile of the track boss II (61) is meshed with the radial section profile of a track groove II (56) of the concentric sliding block (1), a track boss I (60) is arranged at the other axial end of the cross sliding block (2), the track boss I (60) penetrates through the sliding block center hole II (59) and is distributed radially, the radial section profile of the track boss I (60) is meshed with the radial section profile of a track groove I (62) of the swing sliding block (3), and the track boss II (61) is perpendicular to the;
the transmission pin (33), the first fixing pin (36), the second fixing pin (35), the third fixing pin (17), the fourth fixing pin (5) and the fifth fixing pin (7) are cylindrical; the positioning retainer ring (8) is cylindrical, a positioning retainer ring shaft hole is arranged at the radial center of the positioning retainer ring, and a radial positioning retainer ring pin hole is formed in the radial outer surface of the positioning retainer ring (8);
the swing gear ring (32) is cylindrical, a cylindrical inner gear is arranged on the radial inner surface of one axial end of the swing gear ring, and a plurality of radial transmission pin holes I (70) are uniformly distributed from the radial inner surface to the outer surface of the other axial end of the swing gear ring (32); the sun gear (12), the transition gear (67) and the planet gear (31) are cylindrical external gears, the radial center of the sun gear (12) is a sun gear shaft hole, an inner key groove is formed in the inner surface of the sun gear shaft hole, the radial center of the transition gear (67) is a transition gear shaft hole, and the radial center of the planet gear (31) is a planet gear shaft hole;
the gear fixing shaft (4) is cylindrical, a shaft section III (72), a positioning shaft shoulder III (73), a shaft neck III (74), a shaft section II (75) and a shaft neck II (77) are sequentially arranged from one axial end to the other axial end of the gear fixing shaft, a positioning pin hole II (71) is formed in the radial outer surface of one end, far away from the positioning shaft shoulder III (73), of the shaft section III (72), an outer key groove (76) is formed in the radial outer surface of the shaft section II (75), the diameter of the shaft neck II (77) is smaller than that of the shaft section II (75), and a positioning shaft shoulder II is formed between the shaft neck II (77) and the shaft section II; the positioning shaft (68) is cylindrical, the diameters of the two ends of the positioning shaft (68) are smaller than the diameter of the middle position of the positioning shaft (68), and a positioning shaft shoulder V is formed between each of the two ends of the positioning shaft (68) and the middle position of the positioning shaft (68); the planet gear pin shaft (30) is cylindrical, and one axial end of the planet gear pin shaft is provided with a planet gear pin shaft shoulder;
the first gear connecting plate (69) and the second gear connecting plate (38) are identical in structure, the first gear connecting plate (69) and the second gear connecting plate (38) are in an oblong shape, one radial end of the first gear connecting plate is provided with a first hinge hole (80), and the other radial end of the first gear connecting plate is distributed with a second hinge hole (78) and a third hinge hole (79) in parallel; the gear connecting plate III (65) is in an oblong shape, one radial end of the gear connecting plate III is provided with a hinge hole IV (81), the other radial end of the gear connecting plate III is provided with a hinge shaft (82), and the hinge shaft (82) is vertical to the plate surface of the gear connecting plate III (65); the gear connecting plate four (66) is in an oblong shape, one end in the radial direction of the gear connecting plate four (66) is provided with a hinge hole six (120), the other end in the radial direction of the gear connecting plate four (66) is provided with a hinge hole five (119), the position of the hinge hole five (119) of the gear connecting plate four (66) corresponds to the position of a hinge shaft (82) of the gear connecting plate three (65), and the position of the hinge hole six (120) of the gear connecting plate four (66) corresponds to the position of a hinge hole four (81) of the gear connecting plate three;
the swing planet carrier (14) is disc-shaped, an axial planet carrier central hole (85) is formed in the radial center of the swing planet carrier (14), two planet carrier dovetail grooves (84) which are parallel to each other are formed in one axial end of the swing planet carrier (14), the two planet carrier dovetail grooves (84) are respectively located on two radial sides of the planet carrier central hole (85), a linkage rack II (87) is arranged between the two planet carrier dovetail grooves (84), a planet gear pin shaft fixing hole (86) is formed in the axial end face, close to the planet carrier central hole (85), of the swing planet carrier (14) between the two planet carrier dovetail grooves (84), and a plurality of limiting roller pin shaft fixing holes (83) are distributed in the axial end face of the radial outer side of the swing; the swing limiting roller (13) is cylindrical, and an axial limiting roller shaft hole is formed in the radial center of the swing limiting roller; the limiting roller pin shaft (39) is cylindrical, and one axial end of the limiting roller pin shaft is provided with a limiting roller pin shaft shoulder;
the balance wheel (28) is disc-shaped, an axial balance wheel center hole (100) is formed in the radial center of the balance wheel, two balance wheel dovetail grooves (99) which are parallel to each other are formed in one axial end of the balance wheel (28), the two balance wheel dovetail grooves (99) are located on two radial sides of the balance wheel center hole (100) respectively, a linkage rack I (98) is arranged between the two balance wheel dovetail grooves (99), a triangular roller support (102) is arranged at the other axial end of the balance wheel (28), a roller mounting groove (104) is formed in the triangular oblique edge of the roller support (102), an adjusting roller pin fixing hole (103) is formed in the triangular oblique edge direction of the roller support (102), the adjusting roller pin fixing hole (103) penetrates through the roller mounting groove (104), the roller support (102) and the linkage rack I (98) are located on two radial sides of the balance wheel center hole (100) respectively, and a spring is arranged on the radial outer surface, close to the roller support (102 The spring mounting groove (101) is provided with two open ends, the radial outer surface direction of the balance wheel (28) is an open end I, and the axial end surface direction of the spring mounting groove (101) of the balance wheel (28) far away from the roller bracket (102) is an open end II; the profiling adjusting roller (22) is cylindrical, and the radial center of the profiling adjusting roller is provided with an axial adjusting roller shaft hole; the adjusting roller pin shaft (21) is cylindrical, and one axial end of the adjusting roller pin shaft is provided with an adjusting roller pin shaft shoulder;
the axial end of the sliding rail bracket (24) is sequentially provided with a first external spline (95), a first journal (96), a first shaft section (97) and a sliding rail bracket disc from one axial end to the other axial end, the diameter of the first journal (96) is smaller than that of the first shaft section (97), a first positioning shaft shoulder is formed between the first journal (96) and the first shaft section (97), the sliding rail bracket disc is disc-shaped, the radial center of the sliding rail bracket disc is provided with a second axial bearing mounting hole (91), the second bearing mounting hole (91) is concentric with the first journal (96), the second bearing mounting hole (91) and the first shaft section (97) are respectively positioned at the two axial ends of the sliding rail bracket disc, the axial end faces of the sliding rail bracket discs at the two radial sides of the second bearing mounting hole (91) are respectively provided with a first sliding rail (92), the radial section of the first sliding rail (92) is tail-shaped, the section of the first sliding rail (92) is meshed with the section of the dovetail groove planetary bracket (84), the axial end faces of the sliding rail bracket discs on the radial two sides of the first shaft section (97) are respectively provided with a sliding rail bracket dovetail groove (93), the radial cross section of each sliding rail bracket dovetail groove (93) is in a dovetail shape, the two sliding rail bracket dovetail grooves (93) are parallel to each other, the sliding rail bracket dovetail grooves (93) are parallel to the first sliding rails (92), the axial end face of the sliding rail bracket disc between the two sliding rails (92) is provided with a rectangular gear groove hole (89), the gear groove hole (89) is provided with a linkage gear shaft fixing hole (90) which is vertically crossed with the gear groove hole, the linkage gear shaft fixing hole (90) is vertically crossed with the two sliding rail bracket dovetail grooves (93), the two outer ends of the linkage gear shaft fixing hole (90) are positioned on the radial outer surface of the sliding rail bracket disc, the two inner ends of the linkage gear shaft fixing hole (90) are positioned in the gear groove holes (89), the axial end face of the sliding, the spring stop lever fixing hole (94) and the gear groove hole (89) are respectively positioned at the radial two sides of the first shaft section (97);
the sliding rail bracket part comprises two sliding rails II (37), the sections of the sliding rails II (37) are in a double-dovetail shape, one dovetail-shaped profile of the section of each sliding rail II (37) is meshed with the section profile of a sliding rail bracket dovetail groove (93) of the sliding rail bracket (24), and the other dovetail-shaped profile of the section of each sliding rail II (37) is meshed with the section profile of a balance wheel dovetail groove (99) of the balance wheel (28); the linkage gear (29) is a cylindrical external gear, and the radial center of the linkage gear is a linkage gear shaft hole; the linkage gear shaft (88) is cylindrical; the spring stop lever (15) is L-shaped, and the section of the spring stop lever is circular;
the axial middle positions of a plurality of guide fixing columns (26) of the fixed plate component are arranged in an adjusting plate guide hole (48) of an adjusting plate (27), the axial two ends of each guide fixing column (26) are respectively arranged in a guide fixing hole I (52) of a fixed plate I (20) and a guide fixing hole II (41) of a fixed plate II (34), a fixing pin I (36) is arranged in a fixing hole I (55) of the fixed plate I (20) and a fixing column pin hole at one axial end of the guide fixing column (26), and a fixing pin II (35) is arranged in a fixing hole II (47) of the fixed plate II (34) and a fixing column pin hole at the other axial end of the guide fixing column (26); the bearing I (23) is arranged in a bearing mounting hole I (117) of the fixing plate I (20); one axial end of the adjusting rack (19) is arranged in a guide fixing hole III (50) of the adjusting plate (27), a fixing pin III (17) is arranged in a fixing hole III (51) of the adjusting plate (27) and a positioning pin hole I (105) at one axial end of the adjusting rack (19), and the other axial end of the adjusting rack (19) is arranged in a fixing plate guide hole (54) of the fixing plate I (20); the cylindrical gear teeth I of the adjusting gear (18) are meshed with the rack in the axial middle of the adjusting rack (19); two bearings IV (9) are respectively installed in a bearing installation hole IV (116) of a fixed plate II (34), an external spline II (106) of a parallel output gear (10) penetrates through a boss shaft hole II (45) of the fixed plate II (34) to be located on the axial outer side of the fixed plate II (34), a shaft neck IV (108) of the parallel output gear (10) penetrates through a boss shaft hole II (45) of the fixed plate II (34) to be installed in a shaft hole of the bearing IV (9), a cylindrical gear tooth II of the parallel output gear (10) is located between the fixed plate II (34) and an adjusting plate (27) in the axial direction, a positioning retainer ring shaft hole of a positioning retainer ring (8) is installed on the radial outer surface of the shaft neck IV (108) of the parallel output gear (10), a fixing pin V (7) is installed in a positioning pin hole III (107) of the parallel output gear (10) and a positioning retainer ring pin hole of the positioning retainer ring (8), a shaft section III (72) of a gear fixing shaft (4) is installed in A fixing pin IV (5) is arranged in a fixing hole IV (44) of the fixing plate II (34) and a positioning pin hole II (71) of the gear fixing shaft (4);
a first track boss (60) of an Oldham key (2) of the coupling part is arranged in a first track groove (62) of the swing slider (3), a second track boss (61) of the Oldham key (2) is arranged in a second track groove (56) of the concentric slider (1), a third bearing (6) is arranged in a third bearing mounting hole (118) of the concentric slider (1), a shaft hole of the third bearing (6) is arranged on the radial outer surface of a third journal (74) of the gear fixing shaft (4), the gear fixing shaft (4) sequentially passes through a third slider central hole (58) of the concentric slider (1), a second slider central hole (59) of the Oldham key (2) and a first slider central hole (63) of the swing slider (3), and a coupling gear (57) of the concentric slider (1) is meshed with a second cylindrical gear tooth of the parallel output gear (10);
the sun gear (12) of the swing planet gear part is arranged on the radial outer surface of a second shaft section (75) of the gear fixing shaft (4) through a key strip (11), namely the key strip (11) is arranged in an outer key groove (76) of the gear fixing shaft (4) and an inner key groove of the sun gear (12), a first gear connecting plate (69) and a second gear connecting plate (38) are respectively arranged at the two axial ends of the sun gear (12), hinge holes (80) of the first gear connecting plate (69) and the second gear connecting plate (38) are respectively arranged on the radial outer surface of the second shaft section (75) of the gear fixing shaft (4), two axial ends of a positioning shaft (68) are respectively arranged in hinge holes (79) of the first gear connecting plate (69) and the second gear connecting plate (38), hinge shafts (82) of the third gear connecting plate (65) are respectively arranged in hinge holes (78) of the first gear connecting plate (69) and the second gear connecting plate (38), the transition gear (67) is arranged at a position between the first gear connecting plate (69) and the second gear connecting plate (38) in the axial direction, a transition gear shaft hole of the transition gear (67) is arranged on the radial outer surface of a hinge shaft (82) of the third gear connecting plate (65), a hinge hole five (119) of the fourth gear connecting plate (66) is arranged at one end of the axial outer side of the hinge shaft (82) of the third gear connecting plate (65), the fourth gear connecting plate (66) is positioned at one end of the axial outer side of the second gear connecting plate (38), the planetary gear pin shafts (30) are respectively arranged in a hinge hole six (120) of the fourth gear connecting plate (66) and a hinge hole four (81) of the third gear connecting plate (65), a planetary gear pin shaft shoulder of the planetary gear pin shaft (30) is contacted and arranged with the fourth gear connecting plate (66), and the planetary gear (31) is arranged at a position between the third gear connecting plate (65), a planet gear shaft hole of the planet gear (31) is arranged on the radial outer surface of the planet gear pin shaft (30), the swinging gear ring (32) is arranged on the radial outer side of the planet gear (31), the transition gear (67) and the sun gear (12), the swinging gear ring (32), the planet gear (31), the transition gear (67) and the sun gear (12) are meshed in sequence, and the two axial ends of the transmission pin (33) are respectively arranged in a transmission pin hole I (70) of the swinging gear ring (32) and a transmission pin hole II (64) of the swinging slide block (3);
the axial middle position of a limit roller pin shaft (39) of the swing planet support component is arranged in a limit roller shaft hole of a swing limit roller (13), a limiting roller pin shaft shoulder of a limiting roller pin shaft (39) is in contact installation with one axial end of a swinging limiting roller (13), one axial outer side end of the limiting roller pin shaft (39) is installed in a limiting roller pin shaft fixing hole (83) of a swinging planet support (14), a plurality of swinging limiting rollers (13) are located at one axial end of the swinging planet support (14) without a linkage rack II (87), a gear fixing shaft (4) penetrates through a planet support center hole (85) of the swinging planet support (14), the radial outer surfaces of the plurality of swinging limiting rollers (13) are in contact installation with the radial outer surface of a swinging gear ring (32), and one axial outer side end of a planet gear pin shaft (30) is installed in a planet gear pin shaft fixing hole (86) of the swinging planet support (14);
one axial end of a spring stop rod (15) of the slide rail bracket component is arranged in a spring stop rod fixing hole (94) of the slide rail bracket (24), a linkage gear (29) is arranged in a gear groove hole (89) of the slide rail bracket (24), a linkage gear shaft (88) is arranged in a linkage gear shaft fixing hole (90) of the slide rail bracket (24) and a linkage gear shaft hole of the linkage gear (29), the semi-radial section profile of each slide rail II (37) is arranged in a slide rail bracket dovetail groove (93) of the slide rail bracket (24) to ensure that the linkage gear shaft (88) cannot fall off from the linkage gear shaft fixing hole (90) of the slide rail bracket (24), a bearing II (25) is arranged in a bearing mounting hole II (91) of the slide rail bracket (24), an external spline I (95) of the slide rail bracket (24) sequentially passes through an adjusting plate center hole (49) of an adjusting plate (27) and a fixing plate center hole I (53) of a fixing plate (20) to be positioned at the axial outer, a first journal (96) of the slide rail bracket (24) is arranged in a shaft hole of the first bearing (23), a second journal (77) of the gear fixing shaft (4) is arranged in a shaft hole of the second bearing (25), two first slide rails (92) of the slide rail bracket (24) are respectively arranged in a planet bracket dovetail groove (84) of the swinging planet bracket (14), and a linkage gear (29) is meshed with a linkage rack second (87) of the swinging planet bracket (14);
a profiling adjusting roller (22) of a balance wheel component is arranged in a roller mounting groove (104) of a balance wheel (28), an adjusting roller pin shaft (21) is arranged in an adjusting roller pin shaft fixing hole (103) of the balance wheel (28) and an adjusting roller shaft hole of the profiling adjusting roller (22), the radial outer surface of the profiling adjusting roller (22) is in contact installation with the radial outer surface of an adjusting cone (40) of an adjusting plate (27), a return spring (16) is arranged in a spring mounting groove (101) of the balance wheel (28), a first shaft section (97) of a slide rail bracket (24) penetrates through a balance wheel center hole (100) of the balance wheel (28), the other half radial section profile of each second slide rail (37) is arranged in a dovetail groove (99) of the balance wheel (28), and the other axial end of a spring stop lever (15) is arranged in the spring mounting groove (101) of the balance wheel (28), the other axial end of the spring stop lever (15) is in contact with the axial end face of the return spring (16) and is arranged together, and the linkage gear (29) is meshed with a first linkage rack (98) of the balance wheel (28);
the main reducer (213) comprises a main planet support component, a second input bevel gear (301), a second reducer input shaft (302), a first input bevel gear (303), a first reducer input shaft (304), a first double bevel gear (305), a first shaft sleeve (307), a first retainer ring (308), a first pin (309), a second double bevel gear (314), a second shaft sleeve (315), a second retainer ring (316) and a second pin (317), and the main planet support component comprises a main planet support transmission shaft (306), a main planet bevel gear (310), a main planet shaft (311), a main planet support (312) and a third shaft sleeve (313); the input bevel gear II (301), the reducer input shaft II (302), the input bevel gear I (303) and the reducer input shaft I (304) are respectively arranged on the radial outer side of the main planetary carrier component, and the two axial ends of a transmission shaft (306) of the main planetary carrier are not only output shafts of the main reducer (213) but also output shafts of the stepless speed change system;
the main planet carrier (312) is annular, a plurality of carrier mounting planes are uniformly distributed on the radial inner surface of the main planet carrier (312), and a carrier fixing shaft hole is formed in the center of each carrier mounting plane; a plurality of radial fixed shaft holes are uniformly distributed on the radial outer surface of a fixed shaft shoulder in the axial middle of a main planetary support transmission shaft (306), one end of a main planetary shaft (311) is installed in the fixed shaft hole of the main planetary support transmission shaft (306), the other end of the main planetary shaft (311) is installed in a support fixed shaft hole of a main planetary support (312), a third shaft sleeve (313) is installed in the axial middle of the main planetary shaft (311), and a main planetary bevel gear (310) is installed on the radial outer surface of the third shaft sleeve (313);
a first double-bevel gear shaft hole (330) is formed in the radial middle of the first double-bevel gear (305), and a first inner gear tooth (331) and a first outer gear tooth (332) are respectively formed at the two axial ends of the radial outer side of the first double-bevel gear (305); a second double-bevel gear shaft hole (333) is formed in the radial middle of the second double-bevel gear (314), and an inner gear tooth (334) and an outer gear tooth (335) are respectively formed at two axial ends of the radial outer side of the second double-bevel gear (314); a first double bevel gear (305) and a second double bevel gear (314) are respectively arranged at two axial ends of the main planetary carrier component, a first internal gear tooth (331) of the first double bevel gear (305) is meshed with the main planetary bevel gear (310) of the main planetary carrier component, and a second internal gear tooth (334) of the second double bevel gear (314) is meshed with the main planetary bevel gear (310) of the main planetary carrier component; a first shaft sleeve (307) is arranged at the right side of a fixed shaft shoulder shaft of a transmission shaft (306) of the main planet carrier, a first double-bevel gear (305) is arranged on the radial outer surface of the first shaft sleeve (307), and a first retainer ring (308) and a first pin (309) are arranged and fixed on the radial outer surface of the transmission shaft (306) of the main planet carrier at the axial right side of the first shaft sleeve (307); a second shaft sleeve (315) is arranged at the left side of a fixed shaft shoulder shaft of the main planet carrier transmission shaft (306), a second double-bevel gear (314) is arranged on the radial outer surface of the second shaft sleeve (315), and a second retainer ring (316) and a second pin (317) are arranged and fixed on the radial outer surface of the main planet carrier transmission shaft (306) at the axial left side of the second shaft sleeve (315); one axial end of the first input shaft (304) of the speed reducer is provided with a first input bevel gear (303), the first input bevel gear (303) is meshed with first outer gear teeth (332) of a first double bevel gear (305), one axial end of the second input shaft (302) of the speed reducer is provided with a second input bevel gear (301), and the second input bevel gear (301) is meshed with second outer gear teeth (335) of a second double bevel gear (314).
2. The use method of a ring gear eccentric rotation continuously variable transmission system according to claim 1, characterized in that: the operation process of the first continuously variable transmission (208) and the second continuously variable transmission (210) is as follows: when the continuously variable transmission is in a concentric operation state, the swinging gear ring (32) is concentric with the sun gear (12), and the axis (111) of the swinging gear ring is superposed with the axis (110) of the sun gear; an internal combustion engine (201) drives a sliding rail support (24) to rotate through a first connecting gear component (206) or a second connecting gear component (203), the sliding rail support (24) drives a balance wheel (28) to rotate through a second sliding rail (37), a profile modeling adjusting roller (22) rotates along the radial outer surface of an adjusting cone (40) of an adjusting plate (27), meanwhile, the sliding rail support (24) drives a swinging planet support (14) to rotate through a first sliding rail (92), in a gear ring eccentric rotation planet gear reducer, a sun gear (12) is a fixed part, the swinging planet support (14) is a driving part, a swinging gear ring (32) is a driven part, the swinging gear ring (32), a planet gear (31), a transition gear (67) and the sun gear (12) are meshed in sequence, if the swinging planet support (14) rotates for a quarter turn along the forward direction (114) of the planet support at a certain moment, the swing planet carrier (14) drives a swing ring gear (32) to revolve around a sun gear axis (110) along a swing ring gear positive rotation direction (115) through a planet gear pin shaft (30) and a planet gear (31), the number of teeth of the swing ring gear (32) rotating from a point D to a point E is equal to a swing ring gear quarter tooth number b, meanwhile, the swing planet carrier (14) drives a transition gear (67) to rotate around a sun gear (12) through the planet gear pin shaft (30) and the planet gear (31), so that the transition gear (67) rotates along a transition gear positive rotation direction (112), the transition gear (67) drives the planet gear (31) to rotate along a planet gear positive rotation direction (113), the planet gear (31) drives the swing ring gear (32) to rotate along a swing ring gear positive rotation direction (115) around a swing ring gear axis (111), the number of rotation teeth is equal to the quarter tooth number a of the sun gear, and as the rotation direction of the swinging gear ring (32) is opposite to the revolution direction, and the quarter tooth number b of the swinging gear ring is greater than the quarter tooth number a of the sun gear, the actual rotation direction of the swinging gear ring (32) is the same as the revolution direction, and the gear ring eccentrically rotates the planetary gear reducer for speed reduction; when the continuously variable transmission is in a concentric operation state, if the swinging planet carrier (14) rotates for a quarter turn along the forward rotation direction (114) of the swinging planet carrier at a certain moment, the actual rotating tooth number of the swinging ring gear (32) along the forward rotation direction (115) of the swinging ring gear is equal to the quarter tooth number b of the swinging ring gear minus the quarter tooth number a of the sun gear; the swing gear ring (32) sequentially passes through the transmission pin (33), the swing sliding block (3), the crosshead shoe (2) and the concentric sliding block (1) to drive the coupler gear (57) to rotate, and the coupler gear (57) drives the parallel output gear (10) to rotate;
when the continuously variable transmission is in an eccentric operation state, a first adjusting mechanism power device (207) or a second adjusting mechanism power device (209) drives an adjusting gear shaft of an adjusting gear (18) to rotate, the adjusting gear (18) sequentially passes through an adjusting rack (19) and a third fixing pin (17) to drive an adjusting plate (27) to move along a forward adjusting direction (121), an adjusting cone (40) of the adjusting plate (27) sequentially passes through a profiling adjusting roller (22), an adjusting roller pin shaft (21) and a balance wheel (28) to compress a return spring (16) and drive the balance wheel (28) to move towards the radial outer side of a roller support (102), a first linkage rack (98) of the balance wheel (28) sequentially passes through a linkage gear (29) and a second linkage rack (87) of a swinging planetary support (14) to drive the swinging planetary support (14) and a swinging gear ring (32) to move towards the opposite direction of the movement of the balance wheel (28), at the moment, the swinging gear ring (32) is not concentric with the sun gear (12), an eccentric distance exists between the axis (111) of the swinging gear ring and the axis (110) of the sun gear, and the eccentric distance is divided by the tooth pitch to obtain the eccentric tooth number c of the swinging gear ring; an internal combustion engine (201) drives a sliding rail support (24) to rotate through a first connecting gear component (206) or a second connecting gear component (203), the sliding rail support (24) drives a balance wheel (28) to rotate through a second sliding rail (37), a profile modeling adjusting roller (22) rotates along the radial outer surface of an adjusting cone (40) of an adjusting plate (27), meanwhile, the sliding rail support (24) drives a swinging planet support (14) to rotate through a first sliding rail (92), in a gear ring eccentric rotation planet gear reducer, a sun gear (12) is a fixed part, the swinging planet support (14) is a driving part, a swinging gear ring (32) is a driven part, the swinging gear ring (32), a planet gear (31), a transition gear (67) and the sun gear (12) are meshed in sequence, if the swinging planet support (14) rotates for a quarter turn along the forward direction (114) of the planet support at a certain moment, the swing planet carrier (14) drives a swing ring gear (32) to revolve around a sun gear axis (110) along a swing ring gear positive rotation direction (115) through a planet gear pin shaft (30) and a planet gear (31), the number of teeth of the swing ring gear (32) rotating from a point D to a point E is equal to the sum of a swing ring gear quarter tooth number b and a swing ring gear eccentric tooth number c, meanwhile, the swing planet carrier (14) drives a transition gear (67) to rotate around the sun gear (12) through the planet gear pin shaft (30) and the planet gear (31), the transition gear (67) rotates along a transition gear positive rotation direction (112), the transition gear (67) drives the planet gear (31) to rotate along a planet gear positive rotation direction (113), the planet gear (31) drives the swing ring gear (32) to rotate around a swing ring gear axis (111) along the opposite direction of the swing ring gear positive rotation direction (115), the number of rotation teeth is equal to the quarter tooth number a of the sun gear, and as the rotation direction of the swinging gear ring (32) is opposite to the revolution direction, and the quarter tooth number b of the swinging gear ring is greater than the quarter tooth number a of the sun gear, the actual rotation direction of the swinging gear ring (32) is the same as the revolution direction, and the gear ring eccentrically rotates the planetary gear reducer for speed reduction; when the continuously variable transmission is in an eccentric operation state, if the swinging planet carrier (14) rotates for a quarter turn along the forward rotation direction (114) of the swinging planet carrier at a certain moment, the actual rotating tooth number of the swinging gear ring (32) along the forward rotation direction (115) of the swinging gear ring is equal to the quarter tooth number b of the swinging gear ring, the eccentric tooth number c of the swinging gear ring and the quarter tooth number a of the sun gear; the eccentric distance of the swing gear ring (32) during eccentric movement is increased or reduced, so that the eccentric tooth number c of the swing gear ring can be increased or reduced, namely the rotation speed of the swing gear ring (32) is increased or reduced, the rotation speed of the swing gear ring (32) can be subjected to stepless speed change, the swing gear ring (32) sequentially passes through the transmission pin (33), the swing slider (3), the cross slider (2) and the concentric slider (1) to drive the coupling gear (57) to rotate, the coupling gear (57) drives the parallel output gear (10) to rotate, and the purpose of stepless speed change of the stepless speed changer is achieved;
when the swing planet carrier component of the continuously variable transmission drives the swing planet gear component to rotate, the swing limiting idler wheel (13) rolls on the radial outer surface of the swing gear ring (32) to ensure that the swing gear ring (32) rotates according to the eccentric distance set by the adjusting gear (18); the shaft coupling parts form an Oldham coupling, when the swinging gear ring (32) eccentrically rotates, the eccentric distance between the axis (111) of the swinging gear ring and the axis (110) of the sun gear is offset by the sliding between the track boss I (60) of the Oldham (2) and the track groove I (62) of the swinging slider (3) and the sliding between the track boss II (61) of the Oldham (2) and the track groove II (56) of the concentric slider (1), so that the concentric slider (1) and the sun gear (12) are ensured to be concentric;
the operation process of the main speed reducer (213) is as follows: the output end of the first continuously variable transmission (208) drives a first reducer input shaft (304) of a main reducer (213) to rotate along a first input shaft rotating direction (318), the first reducer input shaft (304) drives a first double bevel gear (305) to rotate along a first double bevel gear rotating direction (329) around an output shaft axis (324) through a first input bevel gear (303), the output end of the second continuously variable transmission (210) drives a second reducer input shaft (302) of the main reducer (213) to rotate along a second input shaft rotating direction (319), the second reducer input shaft (302) drives a second double bevel gear (314) to rotate along a second double bevel gear rotating direction (323) around the output shaft axis (324) through a second input bevel gear (301), and the first double bevel gear rotating direction (329) is opposite to the second double bevel gear rotating direction (323); if the rotating speed of the first reducer input shaft (304) is equal to the rotating speed of the second reducer input shaft (302), the main planetary bevel gear (310) rotates around the axis (326) of the main planetary shaft, the main planetary carrier (312) is in a static state, and the rotating speed of a transmission shaft (306) of the main planetary carrier is zero;
if the rotational speed of the first reducer input shaft (304) is greater than the rotational speed of the second reducer input shaft (302), the first double bevel gear (305) drives the main bevel gear (310) to rotate around the main planetary shaft axis (326) in the main bevel gear rotational direction (325) at a rotational speed greater than the second double bevel gear (314) drives the main bevel gear (310) to rotate around the main planetary shaft axis (326) in the main bevel gear rotational direction (325), in order to offset the speed difference between the first double bevel gear (305) and the second double bevel gear (314) driving the main bevel gear (310), the main bevel gear (310) also revolves around the output shaft axis (324), the main bevel gear (310) drives the main planetary carrier (312) to rotate at a low rotational speed, the linear speed of the main planetary carrier (312) is equal to half of the difference between the linear speed of the first double bevel gear (305) and the linear speed of the second double bevel gear (314), the rotation direction (320) of the main planet carrier is the same as the rotation direction (329) of the double bevel gear, and the main planet carrier (312) drives a transmission shaft (306) of the main planet carrier to rotate in the same direction at a low rotating speed through a main planet shaft (311);
if the rotational speed of the first reducer input shaft (304) is less than the rotational speed of the second reducer input shaft (302), the first double bevel gear (305) drives the main bevel gear (310) to rotate around the main planetary shaft axis (326) in the main bevel gear rotational direction (325) at a rotational speed that is less than the rotational speed of the second double bevel gear (314) driving the main bevel gear (310) to rotate around the main planetary shaft axis (326) in the main bevel gear rotational direction (325), in order to offset the speed difference at which the first double bevel gear (305) and the second double bevel gear (314) respectively drive the main bevel gear (310), the main bevel gear (310) also revolves around the output shaft axis (324), the main bevel gear (310) drives the main planetary carrier (312) to rotate at a low rotational speed, the linear speed of the main planetary carrier (312) is equal to half the difference between the linear speed of the second double bevel gear (314) and the linear speed of the first double bevel gear (305), the rotation direction (320) of the main planet carrier is the same as the rotation direction (323) of the double bevel gear, and the main planet carrier (312) drives a transmission shaft (306) of the main planet carrier to rotate in the same direction at low rotating speed through a main planet shaft (311);
the operation process of the stepless speed change system is as follows: if the gear ratio of the first connecting gear part (206) is set to be equal to the gear ratio of the second connecting gear part (203), if the gear ratio between the first input bevel gear (303) of the main speed reducer (213) and the first outer gear teeth (332) of the first double bevel gear (305) is set to be equal to the gear ratio between the second input bevel gear (301) of the main speed reducer (213) and the second outer gear teeth (335) of the second double bevel gear (314); if the main planetary carrier rotating direction (320) of the main speed reducer (213) is set to be the same as the double bevel gear one rotating direction (329), the automobile is in a forward driving state, and if the main planetary carrier rotating direction (320) of the main speed reducer (213) is set to be the same as the double bevel gear two rotating direction (323), the automobile is in a backward driving state;
before the continuously variable transmission system runs, a first clutch (202) and a second clutch (214) are in a separated state; when the continuously variable transmission system is started, the first continuously variable transmission (208) is in a concentric operation state by operating the first adjusting mechanism power device (207), the second continuously variable transmission (210) is in a concentric operation state by operating the second adjusting mechanism power device (209), the transmission ratio of the first continuously variable transmission (208) is equal to that of the second continuously variable transmission (210), the internal combustion engine (201) is started and operates in an economic rotation speed region, the automobile control module gives a command to enable the first clutch (202) to be in an engagement state, the output torque of the internal combustion engine (201) is transmitted to the output shaft of the first clutch (202), a part of the output torque of the internal combustion engine (201) is transmitted to the first torque transmission channel through the first connecting gear component (206), and the part of the output torque is transmitted to the first reducer input shaft (304) of the main reducer (213) through the first continuously variable transmission (208), meanwhile, a part of output torque of the internal combustion engine (201) is transmitted to a second torque transmission channel through a second connecting gear component (203), the part of output torque is transmitted to a second reducer input shaft (302) of the main reducer (213) through a second continuously variable transmission (210), the rotating speed of the first reducer input shaft (304) is equal to that of the second reducer input shaft (302), the rotating speed of a transmission shaft (306) of the main planet carrier is zero, the main reducer (213) is in a running stop state, namely the automobile is in a running stop state, and zero rotating speed output is realized when the internal combustion engine (201) is not stopped;
if the main speed reducer (213) is in a stop running state and operates the automobile to run, the speed measuring device (211) detects that the rotating speed of a transmission shaft (306) of the main planet carrier is zero, the automobile control module sends a command to enable a clutch II (214) to be in an engaged state, a continuously variable transmission I (208) is in an eccentric running state by operating a regulating mechanism power device I (207), the rotating speed of a driving speed reducer input shaft I (304) of the continuously variable transmission I (208) is larger than the rotating speed of a driving speed reducer input shaft II (302) of the continuously variable transmission II (210), the rotating direction (320) of the main planet carrier of the main speed reducer (213) is the same as the rotating direction (329) of a double bevel gear I, the main speed reducer (213) is in a forward running state, and the eccentric distance between the swinging gear ring axis (111) of the continuously variable transmission I (208) and the sun gear axis (, the difference between the rotating speed of the first speed reducer input shaft (304) and the rotating speed of the second speed reducer input shaft (302) is increased, namely the difference between the linear rotating speed of the first double bevel gear (305) and the linear rotating speed of the second double bevel gear (314) is increased, because the linear rotating speed of the main planetary support (312) is equal to half of the difference between the linear rotating speed of the first double bevel gear (305) and the linear rotating speed of the second double bevel gear (314), the output rotating speed of a main planetary support transmission shaft (306) of the main speed reducer (213) is increased, zero rotating speed output when the internal combustion engine (201) is not stopped is realized, the output rotating speed can be gradually increased to cruise speed from zero rotating speed, and the automobile is in a;
if the main reducer (213) is in a stop running state and the automobile is operated to run, the speed measuring device (211) detects that the rotating speed of a transmission shaft (306) of the main planet carrier is zero, the automobile control module sends a command to enable a clutch II (214) to be in an engaged state, a continuously variable transmission II (210) is in an eccentric running state by operating a regulating mechanism power device II (209), the rotating speed of a first continuously variable transmission I (208) driving a first reducer input shaft (304) is smaller than the rotating speed of a second continuously variable transmission II (210) driving a second reducer input shaft (302), the rotating direction (320) of the main planet carrier of the main reducer (213) is the same as the rotating direction (323) of the double bevel gears, the main reducer (213) is in a backward running state, and the eccentric distance between the swinging gear ring axis (111) of the second continuously variable transmission II (210) and the sun gear axis (110) is increased, the difference between the rotating speed of the second reducer input shaft (302) and the rotating speed of the first reducer input shaft (304) is increased, namely the difference between the linear rotating speed of the second double-bevel gear (314) and the linear rotating speed of the first double-bevel gear (305) is increased, because the linear rotating speed of the main planetary support (312) is equal to half of the difference between the linear rotating speed of the second double-bevel gear (314) and the linear rotating speed of the first double-bevel gear (305), the output rotating speed of a main planetary support transmission shaft (306) of the main reducer (213) is increased, zero rotating speed output when the internal combustion engine (201) is not stopped is realized, the output rotating speed can be gradually increased to cruise speed from zero rotating speed, the automobile is in a backward driving state, and the rotating direction of the output shaft of the main reducer (213) is changed when the input shaft of the main.
CN201911388861.0A 2019-12-30 2019-12-30 Gear ring eccentric rotation stepless speed change system Active CN110953311B (en)

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CN110953311A CN110953311A (en) 2020-04-03
CN110953311B true CN110953311B (en) 2020-10-09

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CN112503143B (en) * 2020-12-17 2021-10-08 大连碧蓝节能环保科技有限公司 Variable-position mixed bevel gear differential speed reduction method
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CN1041433A (en) * 1988-09-30 1990-04-18 李培基 Constant-power stepless speed variator
EP0380209A2 (en) * 1989-01-21 1990-08-01 Jaguar Cars Limited Transmission systems
CN1109567A (en) * 1994-03-30 1995-10-04 肖有义 Gear type stepless speed variator
CN1158392A (en) * 1995-12-08 1997-09-03 刘涛 Gear stepless speed variator
CN1873255A (en) * 2005-06-02 2006-12-06 商春荣 Stepless automatic gear shifting in gear drive
CN201031942Y (en) * 2007-06-14 2008-03-05 北京航空航天大学 Satellite gear stepless gear based on variable crank length crank-rocker mechanism
CN102022490A (en) * 2009-09-22 2011-04-20 李睿 Stepless speed changer with no-pressure friction transmission
WO2013050353A1 (en) * 2011-10-03 2013-04-11 Ivan Peeters Improved continuous variable transmission system and use thereof

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1041433A (en) * 1988-09-30 1990-04-18 李培基 Constant-power stepless speed variator
EP0380209A2 (en) * 1989-01-21 1990-08-01 Jaguar Cars Limited Transmission systems
CN1109567A (en) * 1994-03-30 1995-10-04 肖有义 Gear type stepless speed variator
CN1158392A (en) * 1995-12-08 1997-09-03 刘涛 Gear stepless speed variator
CN1873255A (en) * 2005-06-02 2006-12-06 商春荣 Stepless automatic gear shifting in gear drive
CN201031942Y (en) * 2007-06-14 2008-03-05 北京航空航天大学 Satellite gear stepless gear based on variable crank length crank-rocker mechanism
CN102022490A (en) * 2009-09-22 2011-04-20 李睿 Stepless speed changer with no-pressure friction transmission
WO2013050353A1 (en) * 2011-10-03 2013-04-11 Ivan Peeters Improved continuous variable transmission system and use thereof

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