WO2016165581A1 - Transmission à variation continue pour engrenages orbitaux de régulation de vitesse différentiels - Google Patents

Transmission à variation continue pour engrenages orbitaux de régulation de vitesse différentiels Download PDF

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Publication number
WO2016165581A1
WO2016165581A1 PCT/CN2016/078742 CN2016078742W WO2016165581A1 WO 2016165581 A1 WO2016165581 A1 WO 2016165581A1 CN 2016078742 W CN2016078742 W CN 2016078742W WO 2016165581 A1 WO2016165581 A1 WO 2016165581A1
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WIPO (PCT)
Prior art keywords
stage
gear
speed control
planetary
control mechanism
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PCT/CN2016/078742
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English (en)
Chinese (zh)
Inventor
张志康
谢斌
石祥鹏
朱建
Original Assignee
南京康尼精密机械有限公司
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Publication of WO2016165581A1 publication Critical patent/WO2016165581A1/fr

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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
    • 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
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • 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
    • F16H2700/00—Transmission housings and mounting of transmission components therein; Cooling; Lubrication; Flexible suspensions, e.g. floating frames

Definitions

  • the present invention relates to the field of gearboxes, and more particularly to a differential speed-regulating planetary gear continuously variable transmission.
  • the transmissions currently used in automobiles can be classified into two categories: manual transmissions and automatic transmissions. There are: MT (manual transmission) and AT, AMT, DSG, CVT, etc. (automatic transmission), and ECVT for hybrid vehicles. Except for CVT and ECVT, the other transmissions are graded. The power is disconnected during the shifting process. There are quality problems associated with the engine and dynamic regulation. If the matching is not good, the impact will occur. Due to the rapid development of electronic technology, automotive automatic transmissions have also developed rapidly, which is already the development direction of automotive transmissions. However, the hydraulic transmission efficiency is low; other automatic transmissions are complicated in structure, high in manufacturing cost, difficult to maintain, and expensive. Moreover, the core technology of automotive automatic transmissions is a foreign monopoly.
  • the continuously variable transmission for automobiles is a product that people have been pursuing since the advent of the automobile. The reason is that it can be perfectly matched with the vehicle power system, improve the performance of the car, and has many advantages such as energy saving, environmental protection, stable shifting, and simple operation.
  • the existing automotive CVT is a combination of a steel belt (or chain), a friction wheel and a hydraulic system. Due to the friction transmission, the transmission power is small and the application is limited. Currently, it is used in small displacement vehicles. Therefore, it is particularly important to study a continuously variable transmission that can break through the performance limitations of friction mechanisms and can also be used in high-powered vehicles.
  • the technical problem to be solved by the present invention is to design a continuously variable transmission with continuous power transmission, high gear ratio, strong transmission power capability and wide application range.
  • the differential speed-adjusting planetary gear continuously variable transmission of the present invention comprises a two-stage planetary mechanism in series to form a differential gear train.
  • the first-stage planetary mechanism includes a first-stage internal gear, a first-stage sun gear, and a first Planetary wheel and first Stage carrier, the first stage internal gear is connected to the input shaft as an input, the first stage sun gear and the first stage planet carrier are outputs;
  • the second stage planetary mechanism includes a second stage sun gear, a second stage planetary wheel, and a second stage The stage carrier and the second stage internal gear; the first stage carrier and the second stage sun wheel are connected, the first stage sun gear is connected to the second stage planet carrier; the second stage inner gear is connected to the output shaft as an output.
  • a rotational speed control mechanism is provided between the first stage planetary mechanism and the second stage planetary mechanism, and the rotational speed control mechanism includes an input end and an output end, the input end is connected to the speed regulating motor, and the output end is connected to the first stage sun gear and the second end.
  • a shifting mechanism is arranged between the input end and the output end of the speed control mechanism, and the speed of the speed regulating motor is within a suitable range through the shifting mechanism; the speed control is controlled by a speed regulating motor connected to the input end.
  • the mechanism has stepless speed change; the speed of the first stage sun gear and the second stage planet carrier connecting shaft is locked by a lockable mechanism, the circulating power flow is blocked and the speed is adjusted, thereby realizing the stepless speed change and the maximum torque output and the maximum speed output. Change and power balance.
  • the rotation speed control mechanism connects the input end and the output end through a planetary mechanism and a worm gear mechanism, or a gear mechanism and a lockable mechanism, or a sprocket mechanism and a lockable mechanism, or a gear belt mechanism and a lockable mechanism.
  • the structure of the speed control mechanism is: the speed control mechanism includes a first stage planetary mechanism of the speed control mechanism, a second stage planetary mechanism of the rotational speed control mechanism, and a worm gear mechanism, and the worm gear mechanism includes a worm, a worm wheel and a worm bearing seat;
  • the planetary mechanism includes a first-stage sun gear of a rotational speed control mechanism, a first-stage planetary gear of a rotational speed control mechanism, a first-stage planetary carrier of a rotational speed control mechanism, and a fixed inner ring gear, and the first-stage sun gear of the rotational speed control mechanism is connected to the first-stage sun.
  • the first-stage planetary gear of the rotational speed control mechanism meshes with the fixed internal ring gear;
  • the second-stage planetary mechanism of the rotational speed control mechanism includes the second-stage sun gear of the rotational speed control mechanism and the second rotational speed control mechanism Stage planetary gear, speed control mechanism second stage carrier and fixed ring gear, speed control mechanism second stage sun gear is connected on the connecting shaft of the first stage sun gear and the second stage planet carrier, the second stage of the speed control mechanism
  • the planetary gear meshes with the fixed inner ring gear;
  • the first-stage planetary carrier of the rotational speed control mechanism is connected with the second-stage sun gear of the rotational speed control mechanism, and the worm gear and Speed control means of the second stage planet carrier is integrally connected, the connecting shaft set in a first stage sun gear and a second stage planet carrier.
  • the fixed ring gear and the worm bearing housing are fixed to the casing of the transmission, and the speed regulating motor is connected to the worm.
  • first stage planetary gear of the rotational speed control mechanism and the second stage planetary gear of the rotational speed control mechanism mesh with the same fixed inner ring gear.
  • first stage planetary mechanism of the rotational speed control mechanism and the first stage planetary mechanism may share the same sun gear, that is, the first stage planetary gear of the rotational speed control mechanism meshes with the first stage sun gear.
  • first stage carrier of the speed control mechanism and the second stage sun wheel of the speed control mechanism are connected by a key connection, a pin connection, a screw connection, an expansion sleeve or a spline connection.
  • the structure of the speed control mechanism may also be: the speed control mechanism includes a worm gear mechanism and a planetary mechanism, the worm wheel mechanism includes a worm, a worm wheel and a worm bearing seat, and the planetary mechanism includes a speed control mechanism sun wheel, a large planet wheel, a small planet wheel, and a connection.
  • the shaft, the planet carrier and the fixed ring gear or the fixed external gear, the large planet wheel and the small planet wheel are connected by the connecting shaft and mounted on the planet carrier; the large planet wheel meshes with the sun gear of the speed control mechanism; the small planet wheel and the fixed internal tooth
  • the ring or fixed external gear meshes, the speed control mechanism sun gear is connected to the connecting shaft of the first stage sun gear and the second stage planet carrier, and the worm wheel is connected with the planetary frame of the planetary mechanism, and is assembled in the first stage sun wheel and the first stage The connecting shaft of the secondary planet carrier.
  • the fixed ring gear or the fixed external gear and the worm bearing housing are fixed to the casing of the transmission, and the speed regulating motor is connected to the worm.
  • the planetary mechanism of the rotational speed control mechanism and the first-stage planetary mechanism may share the same sun gear, that is, the large planetary gear of the planetary mechanism meshes with the first-stage sun gear.
  • the structure of the speed control mechanism may further be: the speed control mechanism comprises a gear mechanism and a lockable mechanism, wherein the input end and the output end of the speed control mechanism are geared by a gear transmission, and the output end of the speed control mechanism is geared to the first stage sun gear And the connecting shaft of the second-stage planet carrier, the gear shaft of the input end gear of the rotational speed control mechanism is connected with the speed regulating motor; the rotational speed control mechanism realizes the connecting shaft of the first-stage sun gear and the second-stage planetary carrier through the lockable mechanism Lockable and adjustable.
  • the structure of the speed control mechanism may also be: the speed control mechanism comprises a large gear, a pinion gear, a gear belt and a lockable mechanism, the gear shaft of the large gear is connected with the speed control motor, the pinion gear is connected to the first stage sun wheel and the second gear Planetary On the connecting shaft, the large gear and the pinion are connected by the gear belt; the speed control mechanism realizes the lockable and adjustable speed of the connecting shaft of the first stage sun gear and the second stage planet carrier through the lockable mechanism.
  • the structure of the speed control mechanism may also be: the speed control mechanism comprises a large sprocket, a small sprocket, a chain and a lockable mechanism, the sprocket shaft of the large sprocket is connected with the speed control motor, and the small sprocket is connected to the first stage sun gear.
  • the speed control mechanism realizes the lockable connection of the first-stage sun gear and the second-stage carrier connecting shaft through the lockable mechanism Speed regulation.
  • the structure of the speed control mechanism may also be: the speed control mechanism comprises a bevel gear mechanism and a lockable mechanism, the input end and the output end of the speed control mechanism are realized by a bevel gear transmission, and the output end bevel gear of the speed control mechanism is connected at the first On the connecting shaft of the stage sun gear and the second stage planet carrier, the gear shaft of the input end bevel gear of the speed control mechanism is connected with the speed regulating motor; the speed control mechanism realizes the first stage sun wheel and the second stage by the lockable mechanism The planet carrier can be locked and adjusted.
  • first stage carrier and the second stage sun wheel are connected by a key connection, a pin connection, a screw connection, an expansion sleeve or a spline connection.
  • first stage sun gear is connected to the second stage planet carrier by a key connection, a pin connection, a screw connection, an expansion sleeve or a spline connection.
  • the first stage internal gear includes an input shaft and an internal ring gear
  • the second stage internal gear includes an output shaft and an internal ring gear
  • the input shaft and the ring gear, the output shaft and the ring gear are integrally connected or separated .
  • the split connection of the input shaft and the ring gear, the output shaft and the ring gear is a spline connection, a key connection, a bolt connection, an expansion sleeve or a pin connection.
  • the differential speed-adjusting planetary gear continuously variable transmission of the present invention further comprises a third-stage planetary mechanism, a clutch and a lockable mechanism, and the third-stage planetary mechanism includes a third-stage sun gear, a third-stage planetary gear, The third stage planet carrier and the third stage inner gear are connected to the second stage inner gear.
  • the third-stage planetary carrier is integrally designed with a clutch and a lockable mechanism to realize the forward speed of the transmission, Neutral and reverse functions.
  • the third stage internal gear includes an output shaft and an inner ring gear, and the output shaft and the inner ring gear are integrally connected or separated.
  • the split connection of the output shaft and the ring gear is a spline connection, a key connection, a bolt connection, an expansion sleeve or a pin connection.
  • the beneficial effects of the invention after adopting such a design, the shifting process is continuous stepless speed change, the power transmission is not interrupted; the gear transmission efficiency is relatively high, the friction transmission limitation is overcome, the power transmission capability is relatively strong, and the structure is compact. Small size, light weight; convenient automatic servo control; wide application range, can meet the requirements of various variable speed transmission; the market prospect is broad.
  • FIG. 1(a) is a schematic view showing the principle of a differential speed-adjusting planetary gear continuously variable transmission in Embodiment 1;
  • 1(b) is a schematic diagram showing the principle of a differential speed-adjusting planetary gear continuously variable transmission in which the first-stage planetary mechanism of the rotational speed control mechanism and the first-stage planetary mechanism share the sun gear in the first embodiment;
  • 2(a) is a schematic view showing the principle of the differential speed planetary gear continuously variable transmission in the second embodiment
  • 2(b) is a schematic diagram showing the principle of a differential speed-adjusting planetary gear continuously variable transmission in which the planetary mechanism of the rotational speed control mechanism and the first-stage planetary mechanism share the sun gear in the second embodiment;
  • FIG. 2(c) is a schematic view showing the principle of a differential speed-adjusting planetary gear continuously variable transmission in which a fixed external gear replaces a fixed ring gear in a planetary mechanism of the rotational speed control mechanism in Embodiment 2;
  • Embodiment 3 is a schematic diagram showing the principle of a differential speed-adjusting planetary gear continuously variable transmission in Embodiment 3;
  • Embodiment 4 is a schematic diagram showing the principle of a differential speed-adjusting planetary gear continuously variable transmission in Embodiment 4;
  • Embodiment 5 is a schematic diagram showing the principle of a differential speed-adjusting planetary gear continuously variable transmission in Embodiment 5;
  • Figure 6 (a) is the differential governing planetary gear with the third-stage planetary mechanism and the clutch and the locking mechanism in the sixth embodiment. Schematic diagram of the stage transmission;
  • Figure 6 (b) is a schematic structural view of the differential speed-adjusting planetary gear continuously variable transmission with the third-stage planetary mechanism, the clutch and the locking mechanism in the sixth embodiment;
  • Figure 8 (a) is a schematic view showing the rotation direction of the components of the first two stages of the planetary mechanism of the differential speed planetary gear continuously variable transmission of the present invention when the rotation speed control mechanism is not in operation;
  • Figure 8 (b) is a schematic view showing the rotation direction of the components of the first two stages of the planetary mechanism of the differential speed planetary gear continuously variable transmission of the present invention when the speed control mechanism is operated;
  • 9(a) is a schematic view showing the rotation directions of the components of the third-stage planetary mechanism when the differential speed planetary gear continuously variable transmission with the third-stage planetary mechanism, the clutch and the lock mechanism is added in the sixth embodiment;
  • 9(b) is a schematic view showing the rotation directions of the components of the third-stage planetary mechanism when the differential speed planetary gear continuously variable transmission with the third-stage planetary mechanism, the clutch and the locking mechanism is reversed in the sixth embodiment;
  • Figure 9 (c) is a schematic view showing the rotation directions of the components of the third-stage planetary mechanism when the differential speed planetary gear continuously variable transmission with the third-stage planetary mechanism and the clutch and the lock mechanism is added in the sixth embodiment.
  • Second-stage planet carrier Second-stage internal gear 9. Second-stage planetary gear 10. Secondary sun gear 11, lockable mechanism 12, third stage carrier 13, clutch 14, first stage internal gear 15, first stage planet carrier 16, first stage sun gear
  • the differential speed-regulating planetary gear continuously variable transmission of the present invention comprises a two-stage planetary mechanism in series to form a differential gear train.
  • the first-stage planetary mechanism includes a first-stage internal gear 14 and a first-stage sun gear 16 .
  • the second stage planetary mechanism includes a second stage sun gear 10, a second stage planet gear 9, a second stage planet carrier 7 and a second stage inner gear 8; the first stage planet carrier 15 and the second stage sun gear 10 are connected, the first stage sun gear 16 and The second stage carrier 7 is connected; the second stage internal gear 8 is connected to the output shaft as an output.
  • a rotation speed control mechanism is provided between the first stage planetary mechanism and the second stage planetary mechanism, and the rotation speed control mechanism includes an input end and an output end, the input end is connected to the speed regulating motor, and the output end is connected to the first stage sun gear 16 and the second stage planet
  • a shifting mechanism is arranged between the input end and the output end of the speed control mechanism, and the speed of the speed regulating motor is within a suitable range through the shifting mechanism; the speed control mechanism is controlled by a speed regulating motor connected to the input end. Stepless speed change; lock the rotation speed of the first stage sun gear 16 and the second stage planet carrier 7 through the lockable mechanism, block the circulating power flow and adjust the speed, thereby achieving stepless speed change and maximum torque output and maximum speed output Changes and power balance.
  • the first stage internal gear 14 inputs power, and is input to the second stage planetary mechanism by the first stage carrier 15 - the second stage sun gear 10 and the first stage sun gear 16 - the second stage planet carrier 7;
  • the second stage internal gear 8 of the planetary mechanism outputs.
  • the transmission of the first stage sun gear 16 - the second stage carrier 7 is a small torque increase, and the transmission of the first stage carrier 15 - the second stage sun gear 10 is a large torque deceleration.
  • the first stage sun gear 16 - the second stage planet carrier 7 is designed with a speed control mechanism, and the speed of the first stage sun gear 16 is controlled by a speed control motor.
  • the speed control mechanism comprises a first stage planetary mechanism of the rotational speed control mechanism, a second stage planetary mechanism of the rotational speed control mechanism and a worm gear mechanism, the worm gear mechanism comprises a worm 5, a worm wheel 6 and a worm bearing seat;
  • the first stage planetary mechanism of the rotational speed control mechanism comprises a rotational speed
  • the first stage sun gear 27 of the control mechanism, the first stage planetary gear 28 of the rotational speed control mechanism, the first stage planet carrier 29 of the rotational speed control mechanism and the fixed inner ring gear 20, and the first stage sun gear 27 of the rotational speed control mechanism are connected to the first stage sun On the connecting shaft of the wheel 16 and the second stage carrier 7, the first stage planetary gear 28 of the rotational speed control mechanism meshes with the fixed inner ring gear 20;
  • the second stage planetary mechanism of the rotational speed control mechanism includes a second stage sun gear 30 of the rotational speed control mechanism, The second stage planetary gear 31 of the rotational speed control mechanism, the second stage planetary carrier 32 of the rotation
  • the fixed ring gear 20 and the worm bearing housing are fixed to the casing 1 of the transmission, and the worm 5 is connected with a speed regulating motor.
  • the connection mode of the first-stage planet carrier 29 of the rotational speed control mechanism and the second-stage sun gear 30 of the rotational speed control mechanism is a key connection, a pin connection, a screw connection, an expansion sleeve or a spline connection.
  • the first stage planetary gear 28 of the rotational speed control mechanism and the second stage planetary gear 31 of the rotational speed control mechanism mesh with the same fixed ring gear 20.
  • the first stage carrier 15 and the second stage sun gear 10 are connected by a key connection, a pin connection, a screw connection, an expansion sleeve or a spline connection.
  • the first stage sun gear 16 is connected to the second stage planet carrier 7 by a key connection, a pin connection, a screw connection, an expansion sleeve or a spline connection.
  • the first stage internal gear 14 includes an input shaft and an internal ring gear
  • the second stage internal gear 8 includes an output shaft and an internal ring gear.
  • the input shaft and the ring gear, the output shaft and the ring gear are integrally connected or separated.
  • the split connection of the input shaft and the ring gear, the output shaft and the ring gear is a spline connection, a key connection, a bolt connection, an expansion sleeve or a pin connection.
  • two planetary differential gear trains of the first-stage planetary mechanism and the second-row planetary mechanism The combination of the maximum torque output and the maximum speed output is combined with the maximum speed output and the maximum speed output under the control of the speed control mechanism.
  • the power transmission can have two paths: by the first stage internal gear 14 (input) - the first stage planet carrier 15 - the second stage sun gear 10 - the second stage internal gear 8 (output) and The first stage internal gear 14 (input) - the first stage sun gear 16 - the second stage planet carrier 7 - the second stage internal gear 8 (output).
  • the first stage internal gear 14 (input) - the first stage carrier 15 - the second stage sun gear 10 - the second stage internal gear 8 (output) delivers a low speed high torque path;
  • Gear 14 (input) - first stage sun gear 16 - second stage planet carrier 7 - second stage internal gear 8 (output) delivers a low torque high speed path.
  • the second stage planetary mechanism has two input of continuously variable transmission; under the control of the speed control mechanism, the speed adjustment and the power distribution balance are realized, thereby achieving the purpose of the stepless speed change transmission of the second stage planetary mechanism output.
  • n b1 Z a1 /Z b1 (n a1 +(1+Z b1 /z a1 )n h1 )
  • n b2 Z a2 /Z b2 (n a2 +(1+Z b2 /Z a2 )n h2 )
  • n b2 (Z a2 /Z b2 )(n a2 +(1+Z b2 /Z a2 )n h2 )
  • T b (Z b /Z a )(T a +T h /(1+Z b /Z a ))/2
  • T b2 (Z b2 /Z a2 )(T a2 +T h2 /(1+Z b2 /Z a2 ))/2
  • the oblique line 1 indicates the power output state of the transmission when the speed control mechanism is not operating, and the transmission is operated at two stages of deceleration, high torque and low speed.
  • the slanted line 2 and the slanted line 3 indicate the case where the power transmission changes of the superimposed moving wheel train under the condition of the operation of the speed control mechanism, so that the two differential gear trains constitute a superimposed transmission combining the maximum torque output and the highest speed output. Wheel train.
  • the total power transfer is a superposition of the curves, enabling automatic adjustment of the power distribution.
  • the output rotation direction of the second stage internal gear 8 is opposite to the direction of the input first stage internal gear 14, and the specific turning of the components of the first two stages of the planetary mechanism is as shown in Fig. 8(a).
  • the power transmission has two paths synthesized: under the control of the speed control mechanism, the first-stage sun gear 16 - the second-stage planet carrier 7 controls the rotational speed step by step.
  • the first stage planet carrier 15 - the second stage sun gear 10 drive speed is gradually reduced; as the first stage sun gear 16 - the second stage planet carrier 7 controls the rotational speed to gradually decrease, the first stage planet carrier 15 -
  • the speed of the second stage sun gear 10 is gradually increased.
  • the output is the combined speed and torque of the two paths, and the transmission is in the transmission state of the superimposed moving train.
  • the two differential gear trains constitute a superimposed motion train that combines the maximum torque output and the highest speed output.
  • the maximum torque output and the maximum speed output are converted and balanced.
  • the speed of the speed regulating motor is in a suitable range by a shifting mechanism; the speed control motor is connected to the input end to control the stepless speed change; the lockable mechanism locks the first stage sun gear 16 and the second stage planet carrier 7 Connect the speed of the shaft, block the circulating power flow and adjust the speed, thus achieving the stepless shifting and the change and power balance of the maximum torque output and the maximum speed output.
  • the first stage planetary mechanism and the first stage planetary mechanism of the rotational speed control mechanism can share the same sun gear, that is, the first stage planetary gear 28 of the rotational speed control mechanism meshes with the first stage sun gear 16.
  • the differential speed-adjusting planetary gear continuously variable transmission of the present invention comprises a two-stage planetary mechanism in series to form a differential gear train.
  • the first-stage planetary mechanism includes a first-stage internal gear 14 and a first-stage sun gear 16 .
  • the second stage planetary mechanism includes a second stage sun gear 10, a second stage planet gear 9, a second stage planet carrier 7 and a second stage inner gear 8; the first stage planet carrier 15 and the second stage sun gear 10 are connected, the first stage sun gear 16 and The second stage carrier 7 is connected; the second stage internal gear 8 is connected to the output shaft as an output.
  • a rotation speed control mechanism is provided between the first stage planetary mechanism and the second stage planetary mechanism, and the rotation speed control mechanism includes an input end and an output end, the input end is connected to the speed regulating motor, and the output end is connected to the first stage sun gear 16 and the second stage planet
  • a shifting mechanism is arranged between the input end and the output end of the speed control mechanism, and the speed of the speed regulating motor is within a suitable range through the shifting mechanism; the speed control mechanism is controlled by a speed regulating motor connected to the input end.
  • Infinitely variable speed through lockable The mechanism locks the speed of the first stage sun gear 16 and the second stage planet carrier 7 to connect the shaft, blocks the circulating power flow and regulates the speed, thereby achieving the stepless shifting and the change and power balance of the maximum torque output and the maximum speed output.
  • the first stage internal gear 14 inputs power, and is input to the second stage planetary mechanism by the first stage carrier 15 - the second stage sun gear 10 and the first stage sun gear 16 - the second stage planet carrier 7;
  • the second stage internal gear 8 of the planetary mechanism outputs.
  • the transmission of the first stage sun gear 16 - the second stage carrier 7 is a small torque increase, and the transmission of the first stage carrier 15 - the second stage sun gear 10 is a large torque deceleration.
  • the first stage sun gear 16 - the second stage planet carrier 7 is designed with a speed control mechanism, and the speed of the first stage sun gear 16 is controlled by a speed control motor.
  • the speed control mechanism includes a worm gear mechanism and a planetary mechanism.
  • the worm gear mechanism includes a worm 5, a worm wheel 6 and a worm bearing seat.
  • the planetary mechanism includes a speed control mechanism sun gear 26, a large planet wheel 19, a small planet wheel 21, a connecting shaft, and a planet carrier.
  • the fixed ring gear 20, the large planet gear 19 and the small planet wheel 21 are connected by a connecting shaft and mounted on the planet carrier; the large planet gear 19 meshes with the speed control mechanism sun gear 26; the small planet gear 21 and the fixed ring gear 20 Engagement, the speed control mechanism sun gear 26 is connected to the connecting shaft of the first stage sun gear 16 and the second stage planet carrier 7, and the worm wheel 6 is integrally connected with the planet carrier of the planetary mechanism, and is assembled in the first stage sun gear 16 and The connecting shaft of the secondary carrier 7 is on the shaft.
  • the fixed ring gear 20 and the worm bearing housing are fixed to the casing 1 of the transmission, and the worm 5 is connected with a speed regulating motor.
  • the first stage carrier 15 and the second stage sun gear 10 are connected by a key connection, a pin connection, a screw connection, an expansion sleeve or a spline connection.
  • the first stage sun gear 16 is connected to the second stage planet carrier 7 by a key connection, a pin connection, a screw connection, an expansion sleeve or a spline connection.
  • the first stage internal gear 14 includes an input shaft and an internal ring gear
  • the second stage internal gear 8 includes an output shaft and an internal ring gear.
  • the input shaft and the ring gear, the output shaft and the ring gear are integrally connected or separated.
  • the split connection of the input shaft and the ring gear, the output shaft and the ring gear is a spline connection, a key connection, a bolt connection, an expansion sleeve or a pin connection.
  • two planetary differential gear trains of the first-stage planetary mechanism and the second-row planetary mechanism The combination of the maximum torque output and the maximum speed output is combined with the maximum speed output and the maximum speed output under the control of the speed control mechanism.
  • the power transmission can have two paths: by the first stage internal gear 14 (input) - the first stage planet carrier 15 - the second stage sun gear 10 - the second stage internal gear 8 (output) and The first stage internal gear 14 (input) - the first stage sun gear 16 - the second stage planet carrier 7 - the second stage internal gear 8 (output).
  • the first stage internal gear 14 (input) - the first stage carrier 15 - the second stage sun gear 10 - the second stage internal gear 8 (output) delivers a low speed high torque path;
  • Gear 14 (input) - first stage sun gear 16 - second stage planet carrier 7 - second stage internal gear 8 (output) delivers a low torque high speed path.
  • the second stage planetary mechanism has two input of continuously variable transmission; under the control of the speed control mechanism, the speed adjustment and the power distribution balance are realized, thereby achieving the purpose of the stepless speed change transmission of the second stage planetary mechanism output.
  • n b1 Z a1 /Z b1 (n a1 +(1+Z b1 /z a1 )n h1 )
  • n b2 Z a2 /Z b2 (n a2 +(1+Z b2 /Z a2 )n h2 )
  • n b2 (Z a2 /Z b2 )(n a2 +(1+Z b2 /Z a2 )n h2 )
  • T b (Z b /Z a )(T a +T h /(1+Z b /Z a ))/2
  • T b2 (Z b2 /Z a2 )(T a2 +T h2 /(1+Z b2 /Z a2 ))/2
  • the oblique line 1 indicates the power output state of the transmission when the speed control mechanism is not operating, and the transmission is operated at two stages of deceleration, high torque and low speed.
  • the slanted line 2 and the slanted line 3 indicate the case where the power transmission changes of the superimposed moving wheel train under the condition of the operation of the speed control mechanism, so that the two differential gear trains constitute a superimposed transmission combining the maximum torque output and the highest speed output. Wheel train.
  • the total power transfer is a superposition of the curves, enabling automatic adjustment of the power distribution.
  • the power transmission has two paths synthesized: under the control of the speed control mechanism, the first-stage sun gear 16 - the second-stage planet carrier 7 controls the rotational speed step by step.
  • the first stage planet carrier 15 - the second stage sun gear 10 drive speed is gradually reduced; as the first stage sun gear 16 - the second stage planet carrier 7 controls the rotational speed to gradually decrease, the first stage planet carrier 15 -
  • the speed of the second stage sun gear 10 is gradually increased.
  • the output is the combined speed and torque of the two paths, and the transmission is in the transmission state of the superimposed moving train.
  • the two differential gear trains constitute a superimposed motion train that combines the maximum torque output and the highest speed output.
  • the maximum torque output and the maximum speed output are converted and balanced.
  • the speed of the speed regulating motor is in a suitable range by a shifting mechanism; the speed control motor is connected to the input end to control the stepless speed change; the lockable mechanism locks the first stage sun gear 16 and the second stage planet carrier 7 Connect the speed of the shaft, block the circulating power flow and adjust the speed, thus achieving the stepless shifting and the change and power balance of the maximum torque output and the maximum speed output.
  • the planetary mechanism of the rotational speed control mechanism and the first-stage planetary mechanism can share the same sun gear, that is, the large planetary gear 19 of the planetary mechanism meshes with the first-stage sun gear 16.
  • the fixed ring gear 20 in the planetary mechanism of the rotational speed control mechanism of the present embodiment, can be replaced by a fixed external gear 33, the small planetary gear 21 meshes with the fixed external gear 33, and the fixed external gear 33 and the worm bearing seat are fixed.
  • the housing 1 of the transmission In the housing 1 of the transmission.
  • the differential speed-adjusting planetary gear continuously variable transmission of the present invention comprises a two-stage planetary mechanism in series to form a differential gear train.
  • the first-stage planetary mechanism includes a first-stage internal gear 14, a first-stage sun gear 16, and a first Stage planetary gear 17 and first stage carrier 15, first stage internal gear 14 is connected to input shaft as input, first stage sun gear 16 and first stage carrier 15 are outputs;
  • second stage planetary mechanism includes second stage The sun gear 10, the second stage planetary gear 9, the second stage planet carrier 7 and the second stage inner gear 8; the first stage planet carrier 15 and the second stage sun gear 10 are connected, the first stage sun gear 16 and the second stage The planet carrier 7 is connected; the second stage internal gear 8 is connected to the output shaft as an output.
  • a rotation speed control mechanism is provided between the first stage planetary mechanism and the second stage planetary mechanism, and the rotation speed control mechanism includes an input end And the output end, the input end is connected to the speed regulating motor, and the output end is connected to the connecting shaft of the first stage sun gear 16 and the second stage planet carrier 7, and a shifting mechanism is provided between the input end and the output end of the speed control mechanism,
  • the shifting mechanism makes the speed of the speed regulating motor within a suitable range; the speed control motor connected to the input end controls the stepless speed change of the speed control mechanism; and the lockable mechanism locks the first stage sun gear 16 and the second stage planet carrier 7 Connects the speed of the shaft, blocks the circulating power flow and regulates the speed, thus achieving stepless shifting and maximum torque output and maximum speed output change and power balance.
  • the first stage internal gear 14 inputs power, and is input to the second stage planetary mechanism by the first stage carrier 15 - the second stage sun gear 10 and the first stage sun gear 16 - the second stage planet carrier 7;
  • the second stage internal gear 8 of the planetary mechanism outputs.
  • the transmission of the first stage sun gear 16 - the second stage carrier 7 is a small torque increase, and the transmission of the first stage carrier 15 - the second stage sun gear 10 is a large torque deceleration.
  • the first stage sun gear 16 - the second stage planet carrier 7 is designed with a speed control mechanism, and the speed of the first stage sun gear 16 is controlled by a speed control motor.
  • the speed control mechanism includes a gear mechanism and a lockable mechanism 11.
  • the input end and the output end of the speed control mechanism are geared by gear transmission, and the output end of the speed control mechanism is geared to the first stage sun gear 16 and the second stage planet carrier 7
  • the gear shaft of the input end gear of the speed control mechanism is connected with the speed regulating motor; the speed control mechanism locks the connecting shaft of the first stage sun gear 16 and the second stage planet carrier 7 through the lockable mechanism 11 stop.
  • the first gear 101 is an output end gear connected to the connecting shaft of the first stage sun gear 16 and the second stage carrier 7, the second gear 102 meshes with the first gear 101, and the third gear 103 is The input end gear, the gear shaft of the third gear 103 is connected to the speed regulating motor, the third gear 103 meshes with the second gear 102, and the lockable mechanism 11 realizes the first stage sun gear 16 by locking the third gear 103. It can be locked and adjusted with the shaft of the second-stage carrier 7.
  • the first stage carrier 15 and the second stage sun gear 10 are connected by a key connection, a pin connection, a screw connection, an expansion sleeve or a spline connection.
  • the first stage sun gear 16 is connected to the second stage planet carrier 7 by a key connection, a pin connection, a screw connection, an expansion sleeve or a spline connection.
  • the first stage internal gear 14 includes an input shaft and an internal ring gear
  • the second stage internal gear 8 includes an output shaft and an internal ring gear.
  • the input shaft and the ring gear, the output shaft and the ring gear are either an integral connection or a split connection.
  • the split connection of the input shaft and the ring gear, the output shaft and the ring gear is a spline connection, a key connection, a bolt connection, an expansion sleeve or a pin connection.
  • the two planetary differential gear trains of the first-stage planetary mechanism and the second-stage planetary mechanism are connected in series to form a superimposed transmission gear train combining the maximum torque output and the maximum rotational speed output, and the control of the rotational speed control mechanism The maximum torque output and the maximum speed output are respectively achieved.
  • the power transmission can have two paths: by the first stage internal gear 14 (input) - the first stage planet carrier 15 - the second stage sun gear 10 - the second stage internal gear 8 (output) and The first stage internal gear 14 (input) - the first stage sun gear 16 - the second stage planet carrier 7 - the second stage internal gear 8 (output).
  • the first stage internal gear 14 (input) - the first stage carrier 15 - the second stage sun gear 10 - the second stage internal gear 8 (output) delivers a low speed high torque path;
  • Gear 14 (input) - first stage sun gear 16 - second stage planet carrier 7 - second stage internal gear 8 (output) delivers a low torque high speed path.
  • the second stage planetary mechanism has two input of continuously variable transmission; under the control of the speed control mechanism, the speed adjustment and the power distribution balance are realized, thereby achieving the purpose of the stepless speed change transmission of the second stage planetary mechanism output.
  • n b1 Z a1 /Z b1 (n a1 +(1+Z b1 /z a1 )n h1 )
  • n b2 Z a2 /Z b2 (n a2 +(1+Z b2 /Z a2 )n h2 )
  • n b2 (Z a2 /Z b2 )(n a2 +(1+Z b2 /Z a2 )n h2 )
  • T b (Z b /Z a )(T a +T h /(1+Z b /Z a ))/2
  • T b2 (Z b2 /Z a2 )(T a2 +T h2 /(1+Z b2 /Z a2 ))/2
  • the oblique line 1 indicates the power output state of the transmission when the speed control mechanism is not operating, and the transmission is operated at two stages of deceleration, high torque and low speed.
  • the slanted line 2 and the slanted line 3 indicate the case where the power transmission changes of the superimposed moving wheel train under the condition of the operation of the speed control mechanism, so that the two differential gear trains constitute a superimposed transmission combining the maximum torque output and the highest speed output. Wheel train.
  • the total power transfer is a superposition of the curves, enabling automatic adjustment of the power distribution.
  • the output rotation direction of the second stage internal gear 8 is opposite to the direction of the input first stage internal gear 14, and the specific turning of the components of the first two stages of the planetary mechanism is as shown in Fig. 8(a).
  • the lockable mechanism 11 of the speed control mechanism releases the locking of the connecting shaft of the first stage sun gear 16 and the second stage planet carrier 7, and at this time, the power transmission has two paths synthesized: in the speed control Under the control of the institution, As the first stage sun gear 16 - the second stage planet carrier 7 controls the rotational speed gradually, the first stage planet carrier 15 - the second stage sun gear 10 drive speed is gradually reduced; with the first stage sun gear 16 - - The second stage carrier 7 controls the gradual reduction of the rotational speed, and the rotational speed of the first stage carrier 15 - the second stage sun gear 10 is gradually increased.
  • the output is the combined speed and torque of the two paths, and the transmission is in the transmission state of the superimposed moving train.
  • the two differential gear trains constitute a superimposed motion train that combines the maximum torque output and the highest speed output.
  • the maximum torque output and the maximum speed output are converted and balanced.
  • the speed of the speed regulating motor is in a suitable range by a shifting mechanism; the speed control motor is connected to the input end to control the stepless speed change; the lockable mechanism locks the first stage sun gear 16 and the second stage planet carrier 7 Connect the speed of the shaft, block the circulating power flow and adjust the speed, thus achieving the stepless shifting and the change and power balance of the maximum torque output and the maximum speed output.
  • the setting of the input end and the output end gear of the rotational speed control mechanism is not limited to the embodiment, and the shifting of the input end and the output end of the rotational speed control mechanism by the gear mechanism and the first stage sun gear 16 by the lockable mechanism 11 are generally not limited.
  • the lockable design of the connecting shaft with the second stage planet carrier 7 falls within the scope of protection of the present application.
  • the differential speed-adjusting planetary gear continuously variable transmission of the present invention comprises a two-stage planetary mechanism in series to form a differential gear train.
  • the first-stage planetary mechanism includes a first-stage internal gear 14, a first-stage sun gear 16, and a first Stage planetary gear 17 and first stage carrier 15, first stage internal gear 14 is connected to input shaft as input, first stage sun gear 16 and first stage carrier 15 are outputs;
  • second stage planetary mechanism includes second stage The sun gear 10, the second stage planetary gear 9, the second stage planet carrier 7 and the second stage inner gear 8; the first stage planet carrier 15 and the second stage sun gear 10 are connected, the first stage sun gear 16 and the second stage Planet carrier 7 is connected;
  • the second stage internal gear 8 is connected to the output shaft as an output.
  • a rotation speed control mechanism is provided between the first stage planetary mechanism and the second stage planetary mechanism, and the rotation speed control mechanism includes an input end and an output end, the input end is connected to the speed regulating motor, and the output end is connected to the first stage sun gear 16 and the second stage planet
  • a shifting mechanism is arranged between the input end and the output end of the speed control mechanism, and the speed of the speed regulating motor is within a suitable range through the shifting mechanism; the speed control mechanism is controlled by a speed regulating motor connected to the input end. Stepless speed change; lock the rotation speed of the first stage sun gear 16 and the second stage planet carrier 7 through the lockable mechanism, block the circulating power flow and adjust the speed, thereby achieving stepless speed change and maximum torque output and maximum speed output Changes and power balance.
  • the first stage internal gear 14 inputs power, and is input to the second stage planetary mechanism by the first stage carrier 15 - the second stage sun gear 10 and the first stage sun gear 16 - the second stage planet carrier 7;
  • the second stage internal gear 8 of the planetary mechanism outputs.
  • the transmission of the first stage sun gear 16 - the second stage carrier 7 is a small torque increase, and the transmission of the first stage carrier 15 - the second stage sun gear 10 is a large torque deceleration.
  • the first stage sun gear 16 - the second stage planet carrier 7 is designed with a speed control mechanism, and the speed of the first stage sun gear 16 is controlled by a speed control motor.
  • the rotation speed control mechanism includes a large gear 202, a pinion gear 201, a gear belt and a lockable mechanism 11.
  • the gear shaft of the large gear 202 is connected with the speed control motor, and the pinion gear 201 is connected to the first stage sun gear 16 and the second stage planet carrier.
  • the speed control mechanism realizes the lockable and adjustable connection of the connecting shafts of the first stage sun gear 16 and the second stage planet carrier 7 through the lockable mechanism 11. speed.
  • the first stage carrier 15 and the second stage sun gear 10 are connected by a key connection, a pin connection, a screw connection, an expansion sleeve or a spline connection.
  • the first stage sun gear 16 is connected to the second stage planet carrier 7 by a key connection, a pin connection, a screw connection, an expansion sleeve or a spline connection.
  • the first stage internal gear 14 includes an input shaft and an internal ring gear
  • the second stage internal gear 8 includes an output shaft and an internal ring gear.
  • the input shaft and the ring gear, the output shaft and the ring gear are integrally connected or separated.
  • the split connection of the input shaft and the ring gear, the output shaft and the ring gear is spline connection, key connection, bolt connection Connection, expansion sleeve or pin connection.
  • the two planetary differential gear trains of the first-stage planetary mechanism and the second-row planetary mechanism are connected in series, and constitute a superimposed transmission gear train combining the maximum torque output and the maximum rotational speed output, in the rotational speed control mechanism. Under control, maximum torque output and maximum speed output are achieved respectively.
  • the power transmission can have two paths: by the first stage internal gear 14 (input) - the first stage planet carrier 15 - the second stage sun gear 10 - the second stage internal gear 8 (output) and The first stage internal gear 14 (input) - the first stage sun gear 16 - the second stage planet carrier 7 - the second stage internal gear 8 (output).
  • the first stage internal gear 14 (input) - the first stage carrier 15 - the second stage sun gear 10 - the second stage internal gear 8 (output) delivers a low speed high torque path;
  • Gear 14 (input) - first stage sun gear 16 - second stage planet carrier 7 - second stage internal gear 8 (output) delivers a low torque high speed path.
  • the second stage planetary mechanism has two input of continuously variable transmission; under the control of the speed control mechanism, the speed adjustment and the power distribution balance are realized, thereby achieving the purpose of the stepless speed change transmission of the second stage planetary mechanism output.
  • n b1 Z a1 /Z b1 (n a1 +(1+Z b1 /z a1 )n h1 )
  • n b2 Z a2 /Z b2 (n a2 +(1+Z b2 /Z a2 )n h2 )
  • n b2 (Z a2 /Z b2 )(n a2 +(1+Z b2 /Z a2 )n h2 )
  • T b (Z b /Z a )(T a +T h /(1+Z b /Z a ))/2
  • T b2 (Z b2 /Z a2 )(T a2 +T h2 /(1+Z b2 /Z a2 ))/2
  • the oblique line 1 indicates the power output state of the transmission when the speed control mechanism is not operating, and the transmission is operated at two stages of deceleration, high torque and low speed.
  • the slanted line 2 and the slanted line 3 indicate the case where the power transmission changes of the superimposed moving wheel train under the condition of the operation of the speed control mechanism, so that the two differential gear trains constitute a superimposed transmission combining the maximum torque output and the highest speed output. Wheel train.
  • the total power transfer is a superposition of the curves, enabling automatic adjustment of the power distribution.
  • the output rotation direction of the second stage internal gear 8 is opposite to the direction of the input first stage internal gear 14, and the specific turning of the components of the first two stages of the planetary mechanism is as shown in Fig. 8(a).
  • the lockable mechanism 11 of the speed control mechanism releases the locking of the connecting shaft of the first stage sun gear 16 and the second stage planet carrier 7, and at this time, the power transmission has two paths synthesized: Under the control of the control mechanism, as the first-stage sun gear 16 - the second-stage planet carrier 7 controls the rotational speed, the rotational speed of the first-stage carrier 15 - the second-stage sun gear 10 is gradually reduced; First stage sun gear 16 - second stage planet carrier 7 control speed The gradual reduction of the first-stage planet carrier 15 - the second-stage sun gear 10 transmission speed is gradually increased. The output is the combined speed and torque of the two paths, and the transmission is in the transmission state of the superimposed moving train.
  • the two differential gear trains constitute a superimposed motion train that combines the maximum torque output and the highest speed output.
  • the maximum torque output and the maximum speed output are converted and balanced.
  • the speed of the speed regulating motor is in a suitable range by a shifting mechanism; the speed control motor is connected to the input end to control the stepless speed change; the lockable mechanism locks the first stage sun gear 16 and the second stage planet carrier 7 Connect the speed of the shaft, block the circulating power flow and adjust the speed, thus achieving the stepless shifting and the change and power balance of the maximum torque output and the maximum speed output.
  • the large gear 202, the pinion 201 and the gear belt of the rotational speed control mechanism in this embodiment can be replaced by a large sprocket, a small sprocket and a chain, respectively, and the sprocket shaft of the large sprocket is connected with the speed regulating motor, and the small sprocket is connected.
  • the large sprocket and the small sprocket are connected by a chain; the rotation speed control mechanism realizes the first stage sun gear 16 and the second by the lockable mechanism 11
  • the stage carrier 7 is connected to the shaft for locking and speed regulation.
  • the differential speed-adjusting planetary gear continuously variable transmission of the present invention comprises a two-stage planetary mechanism in series to form a differential gear train.
  • the first-stage planetary mechanism includes a first-stage internal gear 14, a first-stage sun gear 16, and a first Stage planetary gear 17 and first stage carrier 15, first stage internal gear 14 is connected to input shaft as input, first stage sun gear 16 and first stage carrier 15 are outputs;
  • second stage planetary mechanism includes second stage The sun gear 10, the second stage planetary gear 9, the second stage planet carrier 7 and the second stage inner gear 8; the first stage planet carrier 15 and the second stage sun gear 10 are connected, the first stage sun gear 16 and the second stage Planet carrier 7 is connected;
  • the second stage internal gear 8 is connected to the output shaft as an output.
  • a rotation speed control mechanism is provided between the first stage planetary mechanism and the second stage planetary mechanism, and the rotation speed control mechanism includes an input end and an output end, the input end is connected to the speed regulating motor, and the output end is connected to the first stage sun gear 16 and the second stage planet
  • a shifting mechanism is arranged between the input end and the output end of the speed control mechanism, and the speed of the speed regulating motor is within a suitable range through the shifting mechanism; the speed control mechanism is controlled by a speed regulating motor connected to the input end. Stepless speed change; lock the rotation speed of the first stage sun gear 16 and the second stage planet carrier 7 through the lockable mechanism, block the circulating power flow and adjust the speed, thereby achieving stepless speed change and maximum torque output and maximum speed output Changes and power balance.
  • the first stage internal gear 14 inputs power, and is input to the second stage planetary mechanism by the first stage carrier 15 - the second stage sun gear 10 and the first stage sun gear 16 - the second stage planet carrier 7;
  • the second stage internal gear 8 of the planetary mechanism outputs.
  • the transmission of the first stage sun gear 16 - the second stage carrier 7 is a small torque increase, and the transmission of the first stage carrier 15 - the second stage sun gear 10 is a large torque deceleration.
  • the first stage sun gear 16 - the second stage planet carrier 7 is designed with a speed control mechanism, and the speed of the first stage sun gear 16 is controlled by a speed control motor.
  • the rotation speed control mechanism comprises a bevel gear mechanism and a lockable mechanism 11.
  • the input end and the output end of the rotation speed control mechanism are shifted by a bevel gear transmission, and the output end bevel gear of the rotation speed control mechanism is connected to the first stage sun gear 16 and the second stage.
  • the gear shaft of the input end bevel gear of the rotation speed control mechanism is connected with the speed regulating motor; the rotation speed control mechanism realizes the connection of the first stage sun gear 16 and the second stage planet carrier 7 through the lockable mechanism 11.
  • the shaft can be locked.
  • the first bevel gear 301 is an output end bevel gear connected to the connecting shaft of the first stage sun gear 16 and the second stage planet carrier 7
  • the second bevel gear 302 is an input end bevel gear
  • the second cone The gear shaft of the gear 302 is connected to the speed regulating motor
  • the second bevel gear 302 meshes with the first bevel gear 301
  • the lockable mechanism 11 realizes the first stage sun gear 16 and the second by locking the second bevel gear 302.
  • the stage carrier 7 is connected to the shaft for locking and speed regulation.
  • the first stage carrier 15 and the second stage sun gear 10 are connected by a key connection, a pin connection, a screw connection, an expansion sleeve or a spline connection.
  • connection between the first stage sun gear 16 and the second stage planet carrier 7 is a key connection, a pin connection, a screw connection, and an expansion Expansion sleeve or spline connection.
  • the first stage internal gear 14 includes an input shaft and an internal ring gear
  • the second stage internal gear 8 includes an output shaft and an internal ring gear.
  • the input shaft and the ring gear, the output shaft and the ring gear are integrally connected or separated.
  • the split connection of the input shaft and the ring gear, the output shaft and the ring gear is a spline connection, a key connection, a bolt connection, an expansion sleeve or a pin connection.
  • the two planetary differential gear trains of the first-stage planetary mechanism and the second-row planetary mechanism are connected in series, and constitute a superimposed transmission gear train combining the maximum torque output and the maximum rotational speed output, in the rotational speed control mechanism. Under control, maximum torque output and maximum speed output are achieved respectively.
  • the power transmission can have two paths: by the first stage internal gear 14 (input) - the first stage planet carrier 15 - the second stage sun gear 10 - the second stage internal gear 8 (output) and The first stage internal gear 14 (input) - the first stage sun gear 16 - the second stage planet carrier 7 - the second stage internal gear 8 (output).
  • the first stage internal gear 14 (input) - the first stage carrier 15 - the second stage sun gear 10 - the second stage internal gear 8 (output) delivers a low speed high torque path;
  • Gear 14 (input) - first stage sun gear 16 - second stage planet carrier 7 - second stage internal gear 8 (output) delivers a low torque high speed path.
  • the second stage planetary mechanism has two input of continuously variable transmission; under the control of the speed control mechanism, the speed adjustment and the power distribution balance are realized, thereby achieving the purpose of the stepless speed change transmission of the second stage planetary mechanism output.
  • n b1 Z a1 /Z b1 (n a1 +(1+Z b1 /z a1 )n h1 )
  • n b2 Z a2 /Z b2 (n a2 +(1+Z b2 /Z a2 )n h2 )
  • n b2 (Z a2 /Z b2 )(n a2 +(1+Z b2 /Z a2 )n h2 )
  • T b (Z b /Z a )(T a +T h /(1+Z b /Z a ))/2
  • T b2 (Z b2 /Z a2 )(T a2 +T h2 /(1+Z b2 /Z a2 ))/2
  • the oblique line 1 indicates the power output state of the transmission when the speed control mechanism is not operating, and the transmission is operated at two stages of deceleration, high torque and low speed.
  • the slanted line 2 and the slanted line 3 indicate the case where the power transmission changes of the superimposed moving wheel train under the condition of the operation of the speed control mechanism, so that the two differential gear trains constitute a superimposed transmission combining the maximum torque output and the highest speed output. Wheel train.
  • the total power transfer is a superposition of the curves, enabling automatic adjustment of the power distribution.
  • the output rotation direction of the second stage internal gear 8 is opposite to the direction of the input first stage internal gear 14, and the specific turning of the components of the first two stages of the planetary mechanism is as shown in Fig. 8(a).
  • the lockable mechanism 11 of the speed control mechanism releases the locking of the connecting shaft of the first stage sun gear 16 and the second stage planet carrier 7, and at this time, the power transmission has two paths synthesized: Under the control of the control mechanism, as the first-stage sun gear 16 - the second-stage planet carrier 7 controls the rotational speed, the rotational speed of the first-stage carrier 15 - the second-stage sun gear 10 is gradually reduced; The first-stage sun gear 16 - the second-stage planet carrier 7 controls the gradual reduction of the rotational speed, and the first-stage carrier 15 - the second-stage sun gear 10 is gradually increased in rotational speed.
  • the output is the combined speed and torque of the two paths, and the transmission is in the transmission state of the superimposed moving train.
  • the two differential gear trains constitute a superimposed motion train that combines the maximum torque output and the highest speed output.
  • the maximum torque output and the maximum speed output are converted and balanced.
  • the speed of the speed regulating motor is in a suitable range by a shifting mechanism; the speed control motor is connected to the input end to control the stepless speed change; the lockable mechanism locks the first stage sun gear 16 and the second stage planet carrier 7 Connect the speed of the shaft, block the circulating power flow and adjust the speed, thus achieving the stepless shifting and the change and power balance of the maximum torque output and the maximum speed output.
  • the setting of the input end and the output end gear of the rotational speed control mechanism is not limited to the embodiment, and the shifting of the input end and the output end of the rotational speed control mechanism by the bevel gear mechanism and the first stage sun gear by the lockable mechanism 11 are generally not limited.
  • the lockable design of the connecting shaft of the 16 and the second stage carrier 7 is within the scope of protection of the present application.
  • the differential speed planetary gear continuously variable transmission of the present invention is in Embodiment 1 or Embodiment 2 or Embodiment 3 or Embodiment 4 or On the basis of Embodiment 5, there is also a third Stage planetary mechanism, clutch 13 and lockable mechanism 11, third stage planetary mechanism including third stage sun gear 23, third stage planetary gear 24, third stage planet carrier 12 and third stage internal gear 25, third stage
  • the sun gear 23 is coupled to the second stage internal gear 8 and the transmission includes six parts of a first stage planetary mechanism, a rotational speed control mechanism, a second stage planetary mechanism, a clutch, a lockable mechanism 11, and a third stage planetary mechanism, each of which
  • the first-stage planetary mechanism is provided with a first bearing set 2 for supporting the rotation of the internal gear of the stage and the housing 1, a small shaft 3 supporting the planetary gear of the stage and a carrier, and a rotating shaft supporting the planetary gear and the small shaft 3 of the stage.
  • Two bearing sets 4 4.
  • the third stage carrier 12 is integrally designed with a clutch 13 and a lockable mechanism 11 for implementing the forward, neutral and reverse functions of the transmission.
  • the third stage internal gear 25 includes an output shaft and an internal ring gear, and the output shaft and the ring gear are integrally connected or separated.
  • the split connection of the output shaft and the ring gear is a spline connection, a key connection, a bolt connection, an expansion sleeve or a pin connection.
  • the power is input to the third-stage planetary mechanism through the third-stage inner gear 8 of the second-stage inner gear 8 of the second-stage planetary mechanism.
  • the third-stage carrier 12 is integrally designed with the clutch 13 and lockable.
  • the mechanism 11 realizes the neutral, reverse and forward gear functions of the transmission, and thus has the following three working states:
  • the third-stage planetary mechanism When the clutch is working and the lockable mechanism 11 is not working, the third-stage planetary mechanism is self-locking, and the output of the third-stage internal gear 25 is For the output of the second stage internal gear 8, that is, the rotation direction of the third stage internal gear 25 is the same as the rotation direction of the second stage internal gear 8, the rotation speed control mechanism controls the transmission to be in the shift forward position, and the third stage planet
  • the specific components of the mechanism are specifically turned as shown in Figure 9(c).
  • the present embodiment merely provides the third-stage planetary mechanism, the clutch 13 and the lockable mechanism 11 on the basis of the second embodiment to realize the function of the vehicle transmission. It should be noted that in the first embodiment or the third embodiment The design of the third stage planetary mechanism, the clutch 13 and the lockable mechanism 11 based on the design of the similar or equivalent structure of the embodiment 4 or the embodiment 5 or the foregoing embodiment is all within the scope of protection of the present application.

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Abstract

L'invention concerne une transmission à variation continue pour des engrenages orbitaux de régulation de vitesse différentiels. Deux étages de mécanismes orbitaux sont raccordés en série pour former un train d'engrenages différentiel. Un engrenage interne de premier étage (14) est utilisé comme entrée et un planétaire de premier étage (16) et un porte-satellites de premier étage (15) sont utilisés comme sortie. Le porte-satellites de premier étage est raccordé à un planétaire de deuxième étage (10) et le planétaire de premier étage est raccordé à un porte-satellites de deuxième étage (7). Un engrenage interne de deuxième étage (8) est utilisé comme sortie. Un mécanisme de commande de vitesse de rotation est disposé entre un mécanisme orbital de premier étage et un mécanisme orbital de deuxième étage. L'extrémité d'entrée du mécanisme de commande de vitesse de rotation est raccordée à un moteur de régulation de vitesse et l'extrémité de sortie est raccordée à un arbre de raccordement entre le planétaire de premier étage et le porte-satellites de deuxième étage. Un mécanisme de changement de vitesse est disposé entre l'extrémité d'entrée et l'extrémité de sortie du mécanisme de commande de vitesse de rotation. Afin de réaliser la fonction de boîte de vitesses d'un véhicule automobile, un mécanisme orbital de troisième étage est disposé; un planétaire de troisième étage (23) est raccordé à un engrenage interne de deuxième étage; et un embrayage (13) et un frein sont disposés d'un seul tenant sur un porte-satellites de troisième étage (12). Une fois la conception adoptée, la transmission à variation continue présente les avantages suivants: une transmission de puissance continue, une grande efficacité de transmission d'engrenages, un faible volume, un poids léger, une commande pratique et un large champ d'application.
PCT/CN2016/078742 2015-04-13 2016-04-07 Transmission à variation continue pour engrenages orbitaux de régulation de vitesse différentiels WO2016165581A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201510171866.3 2015-04-13
CN201510171866.3A CN104747668B (zh) 2015-04-13 2015-04-13 一种差动调速行星齿轮无级变速器

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WO2016165581A1 true WO2016165581A1 (fr) 2016-10-20

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Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106884958A (zh) * 2017-04-21 2017-06-23 吉林大学 一种带有转矩定向分配功能的电动差速器
CN107061682A (zh) * 2017-04-21 2017-08-18 吉林大学 一种带有转矩定向分配功能的电动差速器
CN107061676A (zh) * 2017-04-21 2017-08-18 吉林大学 一种带有转矩定向分配功能的电动差速器
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CN106884958B (zh) * 2017-04-21 2023-04-07 吉林大学 一种带有转矩定向分配功能的电动差速器
CN107061682A (zh) * 2017-04-21 2017-08-18 吉林大学 一种带有转矩定向分配功能的电动差速器
CN107061676A (zh) * 2017-04-21 2017-08-18 吉林大学 一种带有转矩定向分配功能的电动差速器
CN106884958A (zh) * 2017-04-21 2017-06-23 吉林大学 一种带有转矩定向分配功能的电动差速器
CN107061682B (zh) * 2017-04-21 2023-04-21 吉林大学 一种带有转矩定向分配功能的电动差速器
CN107061676B (zh) * 2017-04-21 2023-04-07 吉林大学 一种带有转矩定向分配功能的电动差速器
CN108468759A (zh) * 2018-05-31 2018-08-31 郑州机械研究所有限公司 一种石油钻机绞车用可换挡式行星齿轮减速箱
CN108591385A (zh) * 2018-07-11 2018-09-28 黄文化 一种发电式无级齿轮变速器
CN109899478A (zh) * 2019-04-11 2019-06-18 湖北恒欣传动设备股份有限公司 一种高精度行星少齿差双差速减速机构
CN109899478B (zh) * 2019-04-11 2024-05-03 深圳市金鸿达传动设备有限公司 一种高精度行星少齿差双差速减速机构
CN112049915A (zh) * 2019-06-05 2020-12-08 哈尔滨工业大学 一种多轴差速装置
CN112728019A (zh) * 2021-01-13 2021-04-30 深圳市恒驱电机股份有限公司 一种内置齿差行星轮齿轮箱的电机
CN112728020A (zh) * 2021-01-15 2021-04-30 深圳市恒驱电机股份有限公司 一种具有新型齿差行星轮齿轮箱的电机
CN114060481A (zh) * 2021-12-17 2022-02-18 山东江华机械制造有限公司 一种收获机无级调速变速器
CN115447665A (zh) * 2022-10-24 2022-12-09 吉林大学 一种安全冗余的电动汽车双电机转向***及其控制方法
CN115447665B (zh) * 2022-10-24 2023-11-28 吉林大学 一种安全冗余的电动汽车双电机转向***及其控制方法

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