CN104100684A - Balance type planetary continuously variable transmission - Google Patents
Balance type planetary continuously variable transmission Download PDFInfo
- Publication number
- CN104100684A CN104100684A CN201410351774.9A CN201410351774A CN104100684A CN 104100684 A CN104100684 A CN 104100684A CN 201410351774 A CN201410351774 A CN 201410351774A CN 104100684 A CN104100684 A CN 104100684A
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- Prior art keywords
- taper
- cylindrical
- planetary gear
- gear
- planetary
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 230000005540 biological transmission Effects 0.000 title claims abstract description 13
- 238000013016 damping Methods 0.000 claims abstract description 22
- FGRBYDKOBBBPOI-UHFFFAOYSA-N 10,10-dioxo-2-[4-(N-phenylanilino)phenyl]thioxanthen-9-one Chemical compound O=C1c2ccccc2S(=O)(=O)c2ccc(cc12)-c1ccc(cc1)N(c1ccccc1)c1ccccc1 FGRBYDKOBBBPOI-UHFFFAOYSA-N 0.000 claims description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Classifications
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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
- F16H3/68—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion in which an orbital gear has an axis crossing the main axis of the gearing and has helical teeth or is a worm
-
- 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
- F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
-
- 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
- F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
- F16H3/721—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously with an energy dissipating device, e.g. regulating brake or fluid throttle, in order to vary speed continuously
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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
- F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
- F16H3/724—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously using external powered electric machines
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Abstract
本发明提供的平衡式行星齿轮无极变速器，属于变速器技术领域，主要解决现有技术有极变速器成本高结构复杂、无极变速器传送带打滑的问题。包括输入轴、中间轴、输出轴、锥形行星齿轮系、圆柱形行星齿轮系、圆柱形行星齿轮架、平衡齿轮、阻尼装置及支座，其特点是：所述锥形行星齿轮系通过中间轴与所述圆柱形行星齿轮系连接，再通过调节所述平衡齿轮或圆柱形行星齿轮架的转速及转动方向，进而达到变速的目的。本发明传动效率高、承载扭矩大、变速平稳、结构简单效率高，无打滑现象。
The balanced planetary gear stepless transmission provided by the invention belongs to the technical field of transmissions, and mainly solves the problems of high cost and complex structure of the conventional stepless transmission and slippage of the conveyor belt of the stepless transmission. It includes an input shaft, an intermediate shaft, an output shaft, a conical planetary gear train, a cylindrical planetary gear train, a cylindrical planetary gear carrier, a balance gear, a damping device and a support, and its characteristic is that the conical planetary gear train passes through the middle The shaft is connected with the cylindrical planetary gear train, and then the purpose of speed change is achieved by adjusting the rotational speed and direction of rotation of the balance gear or the cylindrical planetary gear carrier. The invention has high transmission efficiency, large bearing torque, stable speed change, simple structure, high efficiency and no slipping phenomenon.
Description
Technical field
The invention belongs to speed changer technical field, be specifically related to balanced planetary gear buncher.
Background technique
What in transmission device, speed changer used now is direct shift transmission (DSG) and stepless speed variator (CVT).DSG advantage is that gear-driven efficiency is high, bearing torque is large, speed change is steady, and shortcoming is that complex structure cost is high, belongs to multi-change speed.The advantage of CVT is to have realized electrodeless variable-speed, and efficiency simple in structure is high.Shortcoming is that moment of torsion transmits with skidding when large.
Summary of the invention
Problem to be solved by this invention is to realize stepless change and moment of torsion is non-slip greatly, and balanced planetary gear buncher is provided.
The present invention solves the problems of the technologies described above the technological scheme of taking to be:
Balanced planetary gear buncher, comprises input shaft, jack shaft, output shaft, taper epicyclic train, cylindrical planetary train of gearings, cylindrical planetary gear carrier and bearing, is characterized in:
Described taper epicyclic train is connected by cylindrical planetary gear carrier and jack shaft with cylindrical planetary train of gearings, wherein cylindrical planetary gear carrier can be controlled by external force in transmission process, can control inputs axle and the speed discrepancy of output shaft by controlling the rotational velocity of cylindrical planetary gear carrier and sense of rotation.
Described taper epicyclic train comprises taper planetary gear carrier, the longitudinal axis, the first taper sun gear, the second taper sun gear, the first taper planetary pinion, the second taper planetary pinion, taper sun gear ring; Described taper planetary gear carrier middle part is slidably connected with input shaft, and its two ends and the described longitudinal axis are slidably connected; Described the first taper sun gear is connected with described input shaft, engages with the first taper planetary pinion; Described the second taper planetary pinion is connected with the first taper planetary pinion parallel coaxial by the longitudinal axis; Described taper sun gear ring engages with the second taper planetary pinion, and is connected with cylindrical planetary gear carrier; Described the second taper sun gear is connected with the cylindrical sun gear in cylindrical planetary train of gearings by described jack shaft;
Described cylindrical planetary train of gearings comprises cylindrical planetary gear carrier, the cylindrical sun gear of internal tooth, cylindrical planetary gear and cylindrical sun gear; Described cylindrical planetary gear carrier is connected with taper sun gear ring; Described cylindrical planetary gear engages with cylindrical sun gear; Described internal tooth sun gear engages with cylindrical planetary gear, and its middle part is connected with output shaft;
Described bearing comprises the input shaft bearing that is positioned at speed changer input end and the output shaft bearing that is positioned at speed changer output terminal;
Described input shaft is connected with input shaft bearing sliding; Described output shaft is connected with output shaft bearing sliding; Described jack shaft one end and input shaft are slidably connected by connection set, and the other end and output shaft are slidably connected by connection set;
Also comprise balance gear and damping device, middle part and the jack shaft of described balance gear are slidably connected, and are connected with cylindrical planetary gear carrier;
Described damping device input end is connecting damping gear, and described damping gear engages with described balance gear.
Described damping device is gear pump arrangement or variable speed electric motors, particularly.
The present invention compared with prior art, has following beneficial effect:
The present invention adopts taper epicyclic train, cylindrical planetary train of gearings, balance gear, jack shaft and damping device, by rotating speed and the sense of rotation of damping device or variable speed electric motors, particularly adjustment gear or cylindrical planetary gear carrier, thereby realize stepless change, transmission efficiency is high, bearing torque is large, speed change is steady, efficiency simple in structure is high, without skidding.
Brief description of the drawings
Fig. 1 is structural representation of the present invention.
In figure: 1-input shaft; The 2-the first taper sun gear; The 3-the first taper planetary pinion; The 4-the second taper planetary pinion; 5-taper sun gear ring; 6-balance gear; The 7-the second taper sun gear; 8-connection set; 9-cylindrical planetary gear carrier; The cylindrical sun gear of 10-internal tooth; 11-cylindrical planetary gear; 12-output shaft bearing; 13-output shaft; 14-cylindrical sun gear; 15-jack shaft; 16-damping device; 17-damping gear; 18-longitudinal axis; 19-taper planetary gear carrier; 20-input shaft bearing.
Embodiment
As shown in Figure 1, balanced planetary gear buncher, comprises input shaft 1, jack shaft 15, output shaft 13, taper epicyclic train, cylindrical planetary train of gearings, cylindrical planetary gear carrier 9 and bearing;
Described taper epicyclic train is connected by cylindrical planetary gear carrier 9 and jack shaft 15 with cylindrical planetary train of gearings, wherein cylindrical planetary gear carrier 9 can be controlled by external force in transmission process, can control inputs axle 1 and the speed discrepancy of output shaft 13 by controlling the rotational velocity of cylindrical planetary gear carrier 9 and sense of rotation.
Described taper epicyclic train comprises taper planetary gear carrier 19, the longitudinal axis 18, the first taper sun gear 2, the second taper sun gear 7, the first taper planetary pinion 3, the second taper planetary pinion 4, taper sun gear ring 5; Described taper planetary gear carrier 19 middle parts and input shaft 1 are slidably connected, and its two ends and the described longitudinal axis 18 are slidably connected; Described the first taper sun gear 2 is connected with described input shaft 1, engages with the first taper planetary pinion 3; Described the second taper planetary pinion 4 is connected with the first taper planetary pinion 3 parallel coaxial by the longitudinal axis 18; Described taper sun gear ring 5 engages with the second taper planetary pinion 4, and is connected with cylindrical planetary gear carrier 9; Described the second taper sun gear 7 is connected with the cylindrical sun gear 14 in cylindrical planetary train of gearings by described jack shaft 15;
Described cylindrical planetary train of gearings comprises cylindrical planetary gear carrier 9, the cylindrical sun gear 10 of internal tooth, cylindrical planetary gear 11 and cylindrical sun gear 14; Described cylindrical planetary gear carrier 9 is connected with taper sun gear ring 5; Described cylindrical planetary gear 11 engages with cylindrical sun gear 14; Described internal tooth sun gear 10 engages with cylindrical planetary gear 11, and its middle part is connected with output shaft 13;
Described bearing comprises the input shaft bearing 20 that is positioned at speed changer input end and the output shaft bearing 12 that is positioned at speed changer output terminal;
Described input shaft 1 is slidably connected with input shaft bearing 20; Described output shaft 13 is slidably connected with output shaft bearing 12; Described jack shaft 15 one end and input shaft 1 are slidably connected by connection set 8, and the other end and output shaft 13 are slidably connected by connection set 8;
Also comprise balance gear 6 and damping device 16, the middle part of described balance gear 6 and jack shaft 15 are slidably connected, and are connected with cylindrical planetary gear carrier 9;
Described damping device 16 input ends are connecting damping gear 17, and described damping gear 17 engages with described balance gear 6.
Described damping device 16 is gear pump arrangement or variable speed electric motors, particularly.
Working principle:
When work, input shaft 1 drives the first taper sun gear 2 postive directions to rotate, and the first taper sun gear 2 drives the first taper planetary pinion 3 and the second taper planetary pinion 4 to rotate.Now, suppose that taper sun gear ring 5 does not rotate.When the first taper planetary pinion 3 and the second taper planetary pinion 4 rotation, postive direction revolves round the sun and drives the second taper sun gear 7 to reverse, the power of rotating simultaneously to 5 one postive directions of taper sun gear ring.The second taper sun gear 7 drives cylindrical sun gear 14 counter-rotation.Cylindrical sun gear 14 drives cylindrical planetary gear 11 to rotate, and has given the power of 9 one counter-rotation of cylindrical planetary gear carrier simultaneously.The power that now taper sun gear ring 5 postive directions are rotated and the contrary equal and opposite in direction of force direction of cylindrical planetary gear carrier 9 counter-rotation, thus balance formed.So cylindrical planetary gear carrier 9 and taper sun gear ring 5 are not rotated.Cylindrical sun gear 14 changes sense of rotation by cylindrical planetary gear 11 and drives internal tooth sun gear 10 forward rotation and slow down, then exports the power of low rotation speed large torque by output shaft 13.If the cylindrical planetary gear carrier now on equinoctial point 9 rotates with taper sun gear ring 5 postive directions and speed change just can make output shaft 13 realize speed change.In real work due to thereby the frictional force between gear can make cylindrical planetary gear carrier on equinoctial point 9 and taper sun gear ring 5 postive directions rotate to cause speed changer can not speed change.Thereby realize electrodeless variable-speed so need manual control cylindrical planetary gear carrier 9 and the rotating speed of taper sun gear ring 5.
The power that can utilize cylindrical planetary gear carrier 9 postive directions to rotate makes it pass through balance gear 6 and engage a damping device 16 of drive with damping gear 17, thereby realizes speed change by the rotating speed of resistance switch control cylindrical planetary gear carrier 9 of control damping device 16.
Thereby the rotating speed that can control cylindrical planetary gear carrier 9 by variable speed electric motors, particularly is realized speed change.Thereby motor can also make cylindrical planetary gear carrier 9 reverse does not rotate output shaft 13, realizes the function of clutch.
In straight-tooth gear transmission process, because the fluctuation of power can make equinoctial point unstable, make cylindrical planetary gear carrier 9 and taper sun gear ring 5 occur reversal phenomenon, increase the difficulty of controlling its rotating speed.Thereby so installing all gears, this all need to use angular gear to improve the stability of equinoctial point.
This function also can be realized in the left side that in Fig. 1, taper sun gear ring 5 is arranged on taper planetary pinion 3 and 4.
Claims (3)
1. balanced planetary gear buncher, comprises input shaft 1, jack shaft 15, output shaft 13, taper epicyclic train, cylindrical planetary train of gearings, cylindrical planetary gear carrier 9 and bearing; It is characterized in that:
Described taper epicyclic train is connected by cylindrical planetary gear carrier 9 and jack shaft 15 with cylindrical planetary train of gearings, wherein cylindrical planetary gear carrier 9 can be controlled by external force in transmission process, can control inputs axle 1 and the speed discrepancy of output shaft 13 by controlling the rotational velocity of cylindrical planetary gear carrier 9 and sense of rotation.
2. balanced planetary gear buncher according to claim 1, is characterized in that: described taper epicyclic train comprises taper planetary gear carrier 19, the longitudinal axis 18, the first taper sun gear 2, the second taper sun gear 7, the first taper planetary pinion 3, the second taper planetary pinion 4, taper sun gear ring 5; Described taper planetary gear carrier 19 middle parts and input shaft 1 are slidably connected, and its two ends and the described longitudinal axis 18 are slidably connected; Described the first taper sun gear 2 is connected with described input shaft 1, engages with the first taper planetary pinion 3; Described the second taper planetary pinion 4 is connected with the first taper planetary pinion 3 parallel coaxial by the longitudinal axis 18; Described taper sun gear ring 5 engages with the second taper planetary pinion 4, and is connected with cylindrical planetary gear carrier 9; Described the second taper sun gear 7 is connected with the cylindrical sun gear 14 in cylindrical planetary train of gearings by described jack shaft 15;
Described cylindrical planetary train of gearings comprises cylindrical planetary gear carrier 9, the cylindrical sun gear 10 of internal tooth, cylindrical planetary gear 11 and cylindrical sun gear 14; Described cylindrical planetary gear carrier 9 one end are connected with taper sun gear ring 5, and the other end is as the axis of rotation of cylindrical planetary gear 11; Described cylindrical planetary gear 11 engages with cylindrical sun gear 14; Described internal tooth sun gear 10 engages with cylindrical planetary gear 11, and its middle part is connected with output shaft 13;
Described bearing comprises the input shaft bearing 20 that is positioned at speed changer input end and the output shaft bearing 12 that is positioned at speed changer output terminal;
Described input shaft 1 is slidably connected with input shaft bearing 20; Described output shaft 13 is slidably connected with output shaft bearing 12; Described jack shaft 15 one end and input shaft 1 are slidably connected by connection set 8, and the other end and output shaft 13 are slidably connected by connection set 8.
3. balanced planetary gear buncher according to claim 2, is characterized in that: also comprise balance gear 6 and damping device 16, the middle part of described balance gear 6 and jack shaft 15 are slidably connected, and are connected with cylindrical planetary gear carrier 9; Described damping device 16 input ends are connecting damping gear 17, and described damping gear 17 engages with described balance gear 6.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410351774.9A CN104100684A (en) | 2014-07-23 | 2014-07-23 | Balance type planetary continuously variable transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410351774.9A CN104100684A (en) | 2014-07-23 | 2014-07-23 | Balance type planetary continuously variable transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104100684A true CN104100684A (en) | 2014-10-15 |
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ID=51669108
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410351774.9A Pending CN104100684A (en) | 2014-07-23 | 2014-07-23 | Balance type planetary continuously variable transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104100684A (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104455243A (en) * | 2014-11-28 | 2015-03-25 | 杨晋杰 | Balanced type planetary gear mechanism continuously variable transmission |
| CN104728369A (en) * | 2015-03-20 | 2015-06-24 | 杨晋杰 | Balanced type infinitely variable transmission |
| CN104728367A (en) * | 2015-01-15 | 2015-06-24 | 杨晋杰 | Continuously variable transmission used for front drive sedan |
| CN104847853A (en) * | 2015-05-18 | 2015-08-19 | 杨晋杰 | Gear type self-adapting transmission |
| CN105134892A (en) * | 2015-06-17 | 2015-12-09 | 杨晋杰 | Asymmetric gear type self-adaptation speed changer |
| CN105570402A (en) * | 2016-02-17 | 2016-05-11 | 董克军 | Gear stepless speed change mechanism |
| CN108779836A (en) * | 2016-02-18 | 2018-11-09 | 瓦里博克斯Ip股份有限公司 | Buncher with radial drive |
| CZ309290B6 (en) * | 2020-11-23 | 2022-07-27 | CSc. Rudněv Alexandr Ing. | Gearbox with smooth transmission |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20060052199A1 (en) * | 2004-09-08 | 2006-03-09 | Tejinder Singh | Electrically variable transmission with improved gradeability |
| CN101317026A (en) * | 2005-04-22 | 2008-12-03 | 通用汽车环球科技运作公司 | Electrically variable transmission having two planetary gearsets |
| CN102011840A (en) * | 2009-09-04 | 2011-04-13 | 国立中山大学 | The transmission mechanism can be independently controlled |
| CN102050003A (en) * | 2009-11-09 | 2011-05-11 | 现代自动车株式会社 | Transmission device for hybrid vehicle |
| US20120021865A1 (en) * | 2009-08-26 | 2012-01-26 | Guan-Shyong Hwang | Independently Controllable Transmission Mechanism with Series Types |
-
2014
- 2014-07-23 CN CN201410351774.9A patent/CN104100684A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20060052199A1 (en) * | 2004-09-08 | 2006-03-09 | Tejinder Singh | Electrically variable transmission with improved gradeability |
| CN101317026A (en) * | 2005-04-22 | 2008-12-03 | 通用汽车环球科技运作公司 | Electrically variable transmission having two planetary gearsets |
| US20120021865A1 (en) * | 2009-08-26 | 2012-01-26 | Guan-Shyong Hwang | Independently Controllable Transmission Mechanism with Series Types |
| CN102011840A (en) * | 2009-09-04 | 2011-04-13 | 国立中山大学 | The transmission mechanism can be independently controlled |
| CN102050003A (en) * | 2009-11-09 | 2011-05-11 | 现代自动车株式会社 | Transmission device for hybrid vehicle |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104455243A (en) * | 2014-11-28 | 2015-03-25 | 杨晋杰 | Balanced type planetary gear mechanism continuously variable transmission |
| CN104728367A (en) * | 2015-01-15 | 2015-06-24 | 杨晋杰 | Continuously variable transmission used for front drive sedan |
| CN104728369A (en) * | 2015-03-20 | 2015-06-24 | 杨晋杰 | Balanced type infinitely variable transmission |
| CN104847853A (en) * | 2015-05-18 | 2015-08-19 | 杨晋杰 | Gear type self-adapting transmission |
| CN105134892A (en) * | 2015-06-17 | 2015-12-09 | 杨晋杰 | Asymmetric gear type self-adaptation speed changer |
| CN105134892B (en) * | 2015-06-17 | 2017-11-14 | 山西能源学院 | Unsymmetric gear formula adaptive transmission |
| CN105570402A (en) * | 2016-02-17 | 2016-05-11 | 董克军 | Gear stepless speed change mechanism |
| CN108779836A (en) * | 2016-02-18 | 2018-11-09 | 瓦里博克斯Ip股份有限公司 | Buncher with radial drive |
| CZ309290B6 (en) * | 2020-11-23 | 2022-07-27 | CSc. Rudněv Alexandr Ing. | Gearbox with smooth transmission |
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Application publication date: 20141015 |