CN105299154A - Limitless transmission with differential-speed combined gears - Google Patents
Limitless transmission with differential-speed combined gears Download PDFInfo
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- CN105299154A CN105299154A CN201410263336.7A CN201410263336A CN105299154A CN 105299154 A CN105299154 A CN 105299154A CN 201410263336 A CN201410263336 A CN 201410263336A CN 105299154 A CN105299154 A CN 105299154A
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Abstract
The invention provides a limitless transmission with differential-speed combined gears, relates to an automobile device, in particular to the field of automobile speed change. The transmission solves the problem that limitless speed change capacity cannot be achieved through gears for an automobile transmission through the differential-speed combined gears and transmission is the real sense of gear limitless transmission. The transmission for an automobile can conduct limitless speed change through the gears, multiple sets of differential-speed gears (see the attached drawing of the abstract) are adopted for the transmission and in cooperation with one another to work, speed change is conducted through differential speeds generated among the gears, the speed change range can be adjusted by changing the size of the gears, the problem that limitless speed change cannot be achieved through the gears for the automobile transmission is solved, no hydraulic pressure or electric control needs to be used for speed change, the power of an engine can be fully played, the span of the speed change is large, the starting speed is high, and the limitless and oil saving functions are achieved. The limitless transmission is mainly used for various large-medium-small size cars, SUVs, pickup trucks and heavy trucks.
Description
Technical field
The present invention relates to automobile equipment, especially relate to automobile variable speed field, being a kind of speed changer utilizing differential gear combination solution automotive transmission gear to carry out electrodeless variable-speed ability, is the gear buncher of real meaning.
Background technique
Automobile transmission from manual gear speed change to automatic gear speed-changing, then to friction electrodeless variable-speed, all exists and utilizes external force to carry out push-and-pull or extruding completes speed change, as.Above-mentionedly have oil consumption, friction slip respectively, be short of power, the deficiencys such as speed change span is little, can not perform to the optimum state by engine power.
Summary of the invention
The object of this invention is to provide a kind of vehicular transmission that gear can be used to carry out electrodeless variable-speed.Speed changer adopts many group differential gears to cooperatively interact work, utilizes the differential produced between gear to carry out speed change, without using hydraulic pressure, automatically controlled.Can give full play to the power of engine, speed change span is large, starts rapidly, electrodeless and fuel-efficient.(Fig. 1)
The object of the present invention is achieved like this: a kind of vehicular transmission that gear can be used to carry out electrodeless variable-speed.Its parts comprise: walk abreast Gear combination, 2 parallel dish-type Gear combination of the combination of 3 groups of differential mechanisms, 6 one side of something combine with 2 transmission shafts and bearing respectively.Wherein differential mechanism combination is made up of the cross axle of ring gear, a band bearing, two or four planetary pinions.First planetary pinion to be arranged on cross axle and to install bearing additional, and the cross axle protuberance then having installed planetary pinion and bearing embeds in ring gear outer annular recess, and is fixed by pin and steel loop, and 3 groups of composite structures are identical, measure-alike; Half of parallel Gear combination, be that in being combined by differential mechanism, the right and left half side gear and dish-type gear are cast and formed, 6 groups of identical, half of gear size of composite structure are identical, but dish-type gear size is different, are arranged on the both sides that 3 groups of differential mechanisms combine respectively; 2 parallel dish-type Gear combination, are synthesized by 3 dish-type gear trains respectively, and structure is different, and size is different; Transmission shaft is made up of the ladder type axle of two ladder type teeth groove and one one long ladder type teeth groove respectively, and diaxon walks abreast.(Fig. 2) (Fig. 3)
Working principle: (Fig. 4)
Minimum differential, first power is inputted 8 ring gears by motor, and 8 ring gears drive 5 cross axles, and 5 cross axles drive 7 planetary pinions, and 7 planetary pinions drive 2,9 half of parallel Gear combination to move to 8 ring gear moving direction.Meanwhile, 8 ring gears drive 32 ring gear motions on 38 driven axles, 12 driving shafts and 38 axles have same structure and size in three cover combinations, therefore 38 driven axles combinations also have 12 driving shafts combines identical power, working principle and both moving direction is contrary; Then, 2,9 half of parallel Gear combination resistances when vehicle start are excessive as shown in the figure, and wherein 9 half of parallel Gear combination are hampered and do not turn, according to differential mechanism working principle, now, 2 half of parallel Gear combination are by 2 times of rotations to 8 ring gears, and 26 half of parallel Gear combination in like manner.But, 2 half of parallel Gear combination and 26 half of parallel Gear combination gear meshs, and 26 half of parallel Gear combination girths or the number of teeth are greater than 2, 9 half of parallel Gear combination and 16 half of Gear combination and 12 axles meshing fixing (X1 axle is single direction rotation axle) of walking abreast, therefore, can illustrate that 26 half of parallel Gear combination cannot complete 2 times to the revolution of 32 ring gears, 38 driven axle differential mechanism combinations are managed with 12 driving shaft differential cluster contracts again, the excess power that its differential produces is by parallel for imparting 33 one side of something Gear combination, motion so far, 12 driving shaft differential mechanism combinations are combined with 38 driven axle differential mechanisms and are utilized differential mechanism working principle, complete the extraction of the 33 half of parallel minimum differentials of Gear combination, finally, the revolution that speed change schedule of proportion can extrapolate 33 half of parallel Gear combination=0.05 ring gears is consulted.
Maximum differential, above-mentioned the extraction completing the 33 half of parallel minimum differentials of Gear combination, your vehicle right is moving on, along with the increasing of throttle, the increase of vehicle inertia, the reduction of resistance, 9 half of parallel Gear combination are setting in motion (16 teeth, 12 axles move simultaneously in the same way) under planetary effect, 2,26 half of parallel Gear combination are constantly slowed down under differential mechanism working principle simultaneously, until 2,9 half of parallel Gear combination and the equal 1:1:1 of 12 axle left side ring gear rotating speed, 38 driven axle combinations in like manner.Now, due to 2 and 26 gear meshs, 26 girths or the number of teeth are greater than 2, therefore, illustrate that 26 half of parallel Gear combination cannot complete the equal revolution with 32 ring gears, and release the extraction that 33 obtain maximum differential, finally, consult the revolution that speed change schedule of proportion can extrapolate 33 half of parallel Gear combination=1.05 ring gears.
Can find out in above-mentioned explanation that 9,16 gears are critical components of this speed changer, the equal revolution from transfixion to ring gear, play a part governing speed and be electrodeless.
Slewing range, in order to more meet vehicle operationally required speed change, speed changer has installed the differential mechanism combination on the right side of 1 cover 3 times of gear teeth wheels 14 dish-type Gear combination and 35 dish-type Gear combination and 12 axles additional, first obtain 33 minimum with maximum differential and 14,35 and 12 axles on the right side of differential mechanism combine and carry out work, then the revolution of 16 gears is deducted according to differential mechanism working principle, finally draw the revolution of minimum difference=0.3 ring gear, the revolution of maximum differential=5.3 ring gear.Contrast (speed change schedule of proportion).
Unit number and erection sequence: (Fig. 5)
1 ladder type bearing, 3 pins, 4 steel loops, 5 cross axles, 6 bearings, 7 planetary pinions, 8 ring gears, 9 half of parallel Gear combination, 10 ladder type bearings, 11 left ladder type teeth groove, 12 main drive shafts, 13 right ladder type teeth groove, 14 dish-type Gear combination, 15 ladder type bearings, 16 half of parallel Gear combination, 17 pins, 18 steel loops, 19 cross axles, 20 bearings, 21 planetary pinions, 22 ring gears, 23 half of parallel Gear combination, 24 ladder type bearings, 25 ladder type bearings, 26 half of parallel Gear combination, 27 pins, 28 steel loops, 29 cross axles, 30 bearings, 31 planetary pinions, 32 ring gears, 33 half of parallel Gear combination, 34 ladder type bearings, 35 dish-type Gear combination, 36 ladder type bearings, 37 left ladder type teeth groove, 38 driven axles.
7 planetary pinions and 6 bearings are loaded 5 cross axles on the left of 12 main drive shafts by the first step, be fixed and embed in 8 ring gear outer annular recess with 3 pins, 4 steel loops, the combination of composition differential mechanism.On the right side of 12 main drive shafts, 17,18,19,20,21,22 is 27,28,29,30,31,32 identical with 12 main drive shaft left-side differential composite structures with on the left of 38 driven axles, and assembling method is identical.
Second step, 10 ladder type bearings, 9 half of parallel Gear combination internal tooths and 11 left ladder type teeth groove are installed on the left of 12 main drive shafts meshing fixing successively, again above-mentioned first set differential cluster of having assembled is attached together into axle, and adjust 7 planetary pinions and 2 half of parallel Gear combination are coincide, load 9 half of parallel Gear combination and 10 ladder type bearings, ensure that Gear combination is coincide.
3rd step, 14 dish-type Gear combination and 15 ladder type bearings are installed successively on the right side of 12 main drive shafts, 16 half of parallel Gear combination internal tooths are fixed with 13 right ladder type teeth groove are meshing, again above-mentioned second cover differential cluster of having assembled is attached together into axle, and adjust 21 planetary pinions and 16 half of parallel Gear combination are coincide, load 23 half of parallel Gear combination and 24 ladder type bearings, ensure that Gear combination is coincide.
4th step, installs 36 ladder type bearings, 35 dish-type Gear combination, 34 ladder type bearings and 33 half of parallel Gear combination successively on the left of 38 driven axles, and 33 half of parallel Gear combination internal tooths are fixed with 37 left ladder type teeth groove are meshing.Again above-mentioned 3rd cover differential cluster of having assembled is attached together into axle, and adjust 31 planetary pinions and coincide with 33 half of parallel Gear combination, load 26 half of parallel Gear combination and 25 ladder type bearings, ensure that Gear combination is identical.
Figure of description 1: differential built-up gear buncher constitutional diagram
Figure of description 2: differential mechanism exploded view
Figure of description 3: differential mechanism combination decomposition figure
Figure of description 4: differential built-up gear buncher sectional drawing
Figure of description 5: differential built-up gear buncher exploded view
Speed change schedule of proportion: following equipment can be changed according to different automobile and discharge capacity, allows automobile obtain best power source.
Claims (3)
1. the object of this invention is to provide a kind of vehicular transmission that gear can be used to carry out electrodeless variable-speed, speed changer adopts many group differential gears to cooperatively interact work, the differential produced between gear is utilized to carry out speed change, without using hydraulic pressure, automatically controlled, the power of engine can be given full play to, speed change span is large, start rapidly, electrodeless and fuel-efficient, (Fig. 1) the object of the present invention is achieved like this: a kind of vehicular transmission that gear can be used to carry out electrodeless variable-speed, its parts comprise: 3 groups of differential mechanism combinations, 6 one side of something walk abreast Gear combination, 2 parallel dish-type Gear combination combine with 2 transmission shafts and bearing respectively, wherein differential mechanism combination is by ring gear, the cross axle of a band bearing, two or four planetary pinion compositions.
2. first planetary pinion to be arranged on cross axle and to install bearing additional, and the cross axle protuberance then having installed planetary pinion and bearing embeds in ring gear outer annular recess, and is fixed by pin and steel loop, and 3 groups of composite structures are identical, measure-alike; Half of parallel Gear combination, be that in being combined by differential mechanism, the right and left half side gear and dish-type gear are cast and formed, 6 groups of identical, half of gear size of composite structure are identical, but dish-type gear size is different, are arranged on the both sides that 3 groups of differential mechanisms combine respectively; 2 parallel dish-type Gear combination, are synthesized by 3 dish-type gear trains respectively, and structure is different, and size is different; Transmission shaft is made up of the ladder type axle of two ladder type teeth groove and one one long ladder type teeth groove respectively, the parallel figure of diaxon (2) (Fig. 3).
3. working principle: (Fig. 4)
Minimum differential, first power is inputted 8 ring gears by motor, 8 ring gears drive 5 cross axles, 5 cross axles drive 7 planetary pinions, 7 planetary pinions drive 2,9 half of parallel Gear combination to move to 8 ring gear moving direction, meanwhile, 8 ring gears drive 32 ring gear motions on 38 driven axles, 12 driving shafts and 38 axles have same structure and size in three cover combinations, therefore 38 driven axles combinations also have 12 driving shafts combines identical power, working principle and both moving direction is contrary, then, as shown in the figure 2, 9 half of parallel Gear combination resistances when vehicle start are excessive, wherein 9 half of parallel Gear combination are hampered and do not turn, according to differential mechanism working principle, now, 2 half of parallel Gear combination are by 2 times of rotations to 8 ring gears, 26 half of parallel Gear combination in like manner, but, 2 half of parallel Gear combination and 26 half of parallel Gear combination gear meshs, and 26 half of parallel Gear combination girths or the number of teeth are greater than 2, 9 half of parallel Gear combination and 16 half of Gear combination and 12 axles meshing fixing (X1 axle is single direction rotation axle) of walking abreast, therefore, can illustrate that 26 half of parallel Gear combination cannot complete 2 times to the revolution of 32 ring gears, 38 driven axle differential mechanism combinations are managed with 12 driving shaft differential cluster contracts again, the excess power that its differential produces is by parallel for imparting 33 one side of something Gear combination, motion so far, 12 driving shaft differential mechanism combinations are combined with 38 driven axle differential mechanisms and are utilized differential mechanism working principle, complete the extraction of the 33 half of parallel minimum differentials of Gear combination, finally, consult the revolution that speed change schedule of proportion can extrapolate 33 half of parallel Gear combination=0.05 ring gears, maximum differential, above-mentioned the extraction completing the 33 half of parallel minimum differentials of Gear combination, your vehicle right is moving on, along with the increasing of throttle, the increase of vehicle inertia, the reduction of resistance, 9 half of parallel Gear combination setting in motion (16 teeth under planetary effect, 12 axles move simultaneously in the same way), simultaneously 2, 26 half of parallel Gear combination are constantly slowed down under differential mechanism working principle, until 2, 9 half of parallel Gear combination and the equal 1:1:1 of 12 axle left side ring gear rotating speed, 38 driven axle combinations in like manner, now, due to 2 and 26 gear meshs, 26 girths or the number of teeth are greater than 2, therefore, illustrate that 26 half of parallel Gear combination cannot complete the equal revolution with 32 ring gears, and release the extraction that 33 obtain maximum differential, finally, consult the revolution that speed change schedule of proportion can extrapolate 33 half of parallel Gear combination=1.05 ring gears, can 9 be found out in above-mentioned explanation, 16 gears are critical components of this speed changer, equal revolution from transfixion to ring gear, play a part governing speed and be electrodeless, slewing range, in order to more meet vehicle operationally required speed change, speed changer has installed the differential mechanism combination on the right side of 1 cover 3 times of gear teeth wheels 14 dish-type Gear combination and 35 dish-type Gear combination and 12 axles additional, first obtain minimum with maximum differential and 14 by 33, work is carried out in differential mechanism combination on the right side of 35 and 12 axles, then the revolution of 16 gears is deducted according to differential mechanism working principle, finally draw the revolution of minimum difference=0.3 ring gear, the revolution of maximum differential=5.3 ring gear, contrast (speed change schedule of proportion).
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| Application Number | Priority Date | Filing Date | Title |
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| CN201410263336.7A CN105299154B (en) | 2014-06-15 | 2014-06-15 | Differential built-up gear buncher |
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| CN201410263336.7A CN105299154B (en) | 2014-06-15 | 2014-06-15 | Differential built-up gear buncher |
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| CN105299154A true CN105299154A (en) | 2016-02-03 |
| CN105299154B CN105299154B (en) | 2019-02-22 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109274248A (en) * | 2018-11-15 | 2019-01-25 | 赵克中 | Multi-combined permanent magnet continuously variable transmission |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2597945A1 (en) * | 1986-04-24 | 1987-10-30 | Combastet Michel | MECHANICAL SYSTEM FOR CONTINUOUS AND CONTINUOUS TORQUE CONVERSION |
| CN1063342A (en) * | 1991-10-12 | 1992-08-05 | 刘英伟 | Automatic stepless planetary gear speed variator |
| CN2180829Y (en) * | 1994-01-22 | 1994-10-26 | 李岳厚 | Differential wheel system automatic gearing box for vehicles |
| US6053840A (en) * | 1998-12-22 | 2000-04-25 | Jones; Edward B. | Gear transmission with automatic continuously variable mechanical advantage |
| GR20030100272A (en) * | 2003-06-23 | 2005-02-18 | Αθανασιος Γεωργιου Βλαχος | Differential gear box of continuously variable transmission ratio |
| CN1673578A (en) * | 2004-08-31 | 2005-09-28 | 叶建峰 | Method for realizing stepless speed changing and gear stepless speed changer for realizing the same method |
| CN103363057A (en) * | 2012-04-06 | 2013-10-23 | 高则行 | Transmission system |
-
2014
- 2014-06-15 CN CN201410263336.7A patent/CN105299154B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2597945A1 (en) * | 1986-04-24 | 1987-10-30 | Combastet Michel | MECHANICAL SYSTEM FOR CONTINUOUS AND CONTINUOUS TORQUE CONVERSION |
| CN1063342A (en) * | 1991-10-12 | 1992-08-05 | 刘英伟 | Automatic stepless planetary gear speed variator |
| CN2180829Y (en) * | 1994-01-22 | 1994-10-26 | 李岳厚 | Differential wheel system automatic gearing box for vehicles |
| US6053840A (en) * | 1998-12-22 | 2000-04-25 | Jones; Edward B. | Gear transmission with automatic continuously variable mechanical advantage |
| GR20030100272A (en) * | 2003-06-23 | 2005-02-18 | Αθανασιος Γεωργιου Βλαχος | Differential gear box of continuously variable transmission ratio |
| CN1673578A (en) * | 2004-08-31 | 2005-09-28 | 叶建峰 | Method for realizing stepless speed changing and gear stepless speed changer for realizing the same method |
| CN103363057A (en) * | 2012-04-06 | 2013-10-23 | 高则行 | Transmission system |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109274248A (en) * | 2018-11-15 | 2019-01-25 | 赵克中 | Multi-combined permanent magnet continuously variable transmission |
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