CN107387703A - Buncher - Google Patents
Buncher Download PDFInfo
- Publication number
- CN107387703A CN107387703A CN201710707871.0A CN201710707871A CN107387703A CN 107387703 A CN107387703 A CN 107387703A CN 201710707871 A CN201710707871 A CN 201710707871A CN 107387703 A CN107387703 A CN 107387703A
- Authority
- CN
- China
- Prior art keywords
- gear
- clutch
- differential
- shaft
- stepless speed
- 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.)
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
- F16H37/022—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing the toothed gearing having orbital motion
-
- 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
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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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/035—Gearboxes for gearing with endless flexible members
-
- 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
- F16H57/037—Gearboxes for accommodating differential gearings
-
- 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
- F16H2057/02039—Gearboxes for particular applications
- F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
Abstract
The present invention discloses buncher, mainly include input shaft, differential mechanism, first clutch, second clutch, direct drive clutch, bottom gear clutch, first epicyclic train, second epicyclic train, stepless speed changing mechanism, first gear transmission mechanism, second gear transmission mechanism, 3rd gear drive, present invention incorporates buncher for 4th gear drive and output shaft, the advantages of double-clutch automatic gearbox and differential mechanism, considerably increase the moment of torsion of buncher transmission, impact, slewing range and efficiency, it is and simple in construction, cost is cheap, it can widely use.
Description
Technical field
The present invention relates to buncher, more particularly to buncher.
Background technology
Buncher is widely used in industry（Particularly auto industry）At present, buncher has a variety of.Such as
Hydraulic pressure buncher, electric power buncher, mechanical stepless speed changing device etc..Because fluid power buncher efficiency is low, processing
It is it is required that high.The material requirements of electric power buncher is high, complicated etc., and mechanical pole-free speed variator is not suitable for high pulling torque, carries energy
Power poor impact resistance, speed is smaller etc. than excursion, therefore is generally adapted the transmission of middle low power and is difficult to be adapted to high-power transmission.
The content of the invention
The purpose of the present invention is for existing above mentioned problem, there is provided a kind of double clutch differential speed type bunchers.
The technical solution adopted by the present invention is as follows：
Buncher, including input shaft, differential mechanism, first clutch, second clutch, direct drive clutch, bottom gear from
Clutch, the first epicyclic train, the second epicyclic train, stepless speed changing mechanism, first gear transmission mechanism, second gear transmission
Mechanism, the 3rd gear drive, the 4th gear drive and output shaft, input shaft are connected with input shaft gear, input shaft
Gear is engaged with differential mechanism input gear and is connected with differential spider pinion shaft, the difference being connected with differential spider pinion shaft
Fast device planetary gear can be rotated each around differential spider pinion shaft, axle shaft gear under axle shaft gear and differential mechanism on differential mechanism
Engaged with differential spider wheel；Bevel gear A and bevel gear B consolidates with axle shaft gear under axle shaft gear on differential mechanism and differential mechanism respectively
Fixed connection, bevel gear A and bevel gear B also engage with bevel gear C and bevel gear D respectively；Bevel gear D by axle respectively with double clutches
Mechanism first clutch is connected with double-clutch mechanism second clutch, double-clutch mechanism first clutch and and stepless speed change mechanism
The moving part of driving wheel and the fixed part of driving wheel be connected；The moving part of stepless speed change mechanism driving wheel with it is electrodeless
The fixed part of gear driving wheel is connected with stepless speed change mechanism steel band；Stepless speed change mechanism steel band and stepless speed change mechanism
The moving part of driven pulley connects with the fixed part of stepless speed change mechanism driven pulley；The stepless speed change mechanism driving wheel it is movable
The fixed part of part and stepless speed change mechanism driven pulley is connected by axle with the sun gear of the first epicyclic train, and sun gear is again
Engaged by planetary gear, planetary gear planet carrier is linked by shaft bevel gears C；Double-clutch mechanism second clutch and gear A link；
Gear A engages with idle pulley, and idle pulley engages with gear B；Gear B passes through axis connection with bevel gear C；Bevel gear A passes through axle and second
The gear ring connection of epicyclic train；The sun gear of second epicyclic train and output axis connection.
The invention has the advantages that：
Clutch differential stepless speed variators of the invention double, be in existing buncher, such as：Machinery, electrical equipment, hydraulic pressure or
The bunchers such as fluid power, above add a differential mechanism, shunted power using two semiaxis of differential mechanism, make a part dynamic
Power passes to wheel by efficient gear；Then power is rationally alternately transmitted to stepless by another part power by double-clutch mechanism
Speed changer and gear mechanism, two power are merged finally by gear mechanism, can bearing capacity and wide scope change so as to improve
Fast bending moment etc..
Double clutch differential speed type bunchers of the invention are the driving and driven active wheels by Repetitive controller stepless speed changing mechanism
The radius of clean-up so as to change the gearratio of metal belt transmission, the axial movement of the moving part of driving and driven active wheel is basis
The driving cycle of automobile, continuously adjusted by hydraulic control system to realize this part of variable transmission and existing
Buncher principle it is similar.
Present invention incorporates the advantages of buncher, double-clutch automatic gearbox and differential mechanism, considerably increase
Moment of torsion, impact, slewing range and the efficiency of buncher transmission, and it is simple in construction, and cost is cheap, can make extensively
With.
Brief description of the drawings
The structural representation that Fig. 1 present invention is implemented.
Embodiment
The present invention is described further below in conjunction with the accompanying drawings：
As shown in figure 1, buncher, including input shaft, differential mechanism 31, first clutch, second clutch, direct gear clutch
Device, bottom gear clutch 9, the first epicyclic train, the second epicyclic train, stepless speed changing mechanism, first gear transmission mechanism,
Second gear transmission mechanism, the 3rd gear drive, the 4th gear drive and output shaft, input shaft 1 and input shaft tooth
The connection of wheel 2, input shaft gear 2 is engaged with differential mechanism input gear 3 and is connected with differential spider pinion shaft 4, with differential mechanism row
The differential pinion gear 21 that star gear shaft 4 is connected can be rotated each around differential spider pinion shaft 4, semiaxis on differential mechanism
Axle shaft gear 20 engages with differential spider wheel 21 under gear 5 and differential mechanism；Bevel gear A6 and bevel gear B19 respectively with differential mechanism
Upper axle shaft gear 5 is fixedly connected with axle shaft gear under differential mechanism 20, bevel gear A6 and bevel gear B19 also respectively with bevel gear C8 and
Bevel gear D18 is engaged；Bevel gear D18 by axle respectively with double-clutch mechanism first clutch 16 and the clutch of double-clutch mechanism second
Device 22 is connected, the moving part 14 with the driving wheel of stepless speed change mechanism 28 and the active again of double-clutch mechanism first clutch 16
The fixed part 15 of wheel is connected；The moving part 14 of stepless speed change mechanism driving wheel and the fixed part of stepless speed change mechanism driving wheel
15 are divided to be connected with stepless speed change mechanism steel band 13；The moving part of stepless speed change mechanism steel band 13 and stepless speed change mechanism driven pulley
10 and the fixed part 12 of stepless speed change mechanism driven pulley connect；The moving part 10 of the stepless speed change mechanism driving wheel and electrodeless
The fixed part 12 of gear driven pulley is connected by axle with the sun gear of the first epicyclic train 29, and sun gear is further through row
Star-wheel is engaged, and planetary gear planet carrier is linked by shaft bevel gears C8；Double-clutch mechanism second clutch 22 and gear A 17 link；
Gear A 17 engages with idle pulley 23, and idle pulley 23 engages with gear B 24；Gear B 24 and bevel gear C8 passes through axis connection；Bevel gear A6
It is connected by axle with the gear ring of the second epicyclic train 30；The sun gear of second epicyclic train 30 is connected with output shaft 25.
Embodiment：
（1）When automobile wants idling, double-clutch mechanism first clutch 16 and double-clutch mechanism second clutch 22 are all located to separate shape
State or direct drive clutch B26 and reverse clutch 7 locate released state.The moment of torsion that engine transmits passes through the He of input shaft 1
Input shaft gear 2 is transmitted to differential mechanism 31, because output shaft 25 does not turn so axle shaft gear 5 does not turn on differential mechanism, according to differential mechanism
The principle most fast differential mechanism that now planetary gear turns under the rotating speed of axle shaft gear 20 be twice of differential mechanism input gear 3, again
Because double-clutch mechanism first clutch 16 and double-clutch mechanism second clutch 22 all locate released state power can not pass
Pass so as to reach idling requirement.Or direct drive clutch B26 and all released states of reverse clutch 7.Now epicyclic train
Planetary gear be in free rotational power and can not also pass to output shaft 25, so as to reach idling requirement.
（2）When automobile ground zero, double-clutch mechanism first clutch 16 is in the clutch of bonding state double-clutch mechanism second
Device 22 is in released state, and power passes through stepless speed change mechanism 28 without gear A 17；And stepless speed change mechanism master
The distance between the moving part 14 of driving wheel and the fixed part 15 of stepless speed change mechanism driving wheel are farthest, stepless speed change mechanism from
The distance between the moving part 10 of driving wheel and the fixed part 12 of stepless speed change mechanism driven pulley are nearest, that is to say, that electrodeless change
Effective gearratio of fast mechanism is maximum；And the low regime clutch 9 of the first epicyclic train 29 is in and combines direct drive clutch
From state at A11；And the direct drive clutch B26 of the second epicyclic train 30, which is in, combines reverse clutch 7 in separation
State.Power transmission line divides two parts order to be followed successively by：It is 1. input shaft 1, input shaft gear 2, differential mechanism input gear 3, poor
Axle shaft gear 5, bevel gear A6, the second epicyclic train 30, direct drive clutch B26 in fast device planetary gear shaft 4, differential mechanism,
It is finally output shaft 25；2. input shaft 1, input shaft gear 2, differential mechanism input gear 3, differential spider pinion shaft 4, differential
Axle shaft gear 20 under device, bevel gear B19, bevel gear D18, double-clutch mechanism 27, double-clutch mechanism first clutch 16 are electrodeless
The moving part 14 of gear driving wheel, the moving part 10 of stepless speed change mechanism driven pulley, epicyclic train 29, bore tooth
Take turns C8, bevel gear A6, the second epicyclic train 30, direct drive clutch B26, output shaft 25.
（3）When vehicle starting and when also accelerating to certain speed, that is, stepless speed change mechanism driving wheel is movable
The distance between fixed part 15 of part 14 and stepless speed change mechanism driving wheel is nearest, stepless speed change mechanism driven pulley it is movable
The distance between fixed part 12 of part 10 and stepless speed change mechanism driven pulley is farthest, that is, stepless speed change mechanism is effective
During gearratio minimum, double-clutch mechanism first clutch 16 is rapidly separated, and double-clutch mechanism second clutch 22 combines rapidly dynamic
Power is sequentially successively without stepless speed change mechanism, now power transmission：1. input shaft 1, input shaft gear 2, differential mechanism input
Axle shaft gear 20 under gear 3, differential spider pinion shaft 4, differential mechanism, bevel gear B19, bevel gear D18, double-clutch mechanism 27,
Double-clutch mechanism second clutch 22, gear A 17, idle pulley 23, gear B 24, bevel gear C8, bevel gear A6, direct drive clutch
B26 is finally output shaft 25；It is 2. input shaft 1, input shaft gear 2, differential mechanism input gear 3, differential spider pinion shaft 4, poor
Axle shaft gear 5, bevel gear A6, the second planetary planet gear are 30, direct drive clutch B26 on fast device, output shaft 25, now,
28 no power of stepless speed change mechanism is flowed through, and at this moment bottom gear clutch 9 is rapidly separated, and direct drive clutch A11 is combined rapidly,
Stepless speed change mechanism is transferred to seat during starting again, that is, effective gearratio of stepless speed change mechanism is maximum, above this mistake
Journey is moment while completed, and when completing this process gearbox computer double-clutch mechanism first clutch 16 can be controlled to tie rapidly
Close, double-clutch mechanism second clutch 22 is rapidly separated, and power passes through stepless speed change mechanism 28 again；Now power is divided to two again
Point：1. axle shaft gear 5 on input shaft 1, input shaft gear 2, differential mechanism input gear 3, differential spider pinion shaft 4, differential mechanism,
Bevel gear A6, the second planetary planet gear are 30, direct drive clutch B26, are finally output shafts 25；2. input shaft 1, input shaft
Axle shaft gear 20, bevel gear B19, bevel gear under gear 2, differential mechanism input gear 3, differential spider pinion shaft 4, differential mechanism
D18, double-clutch mechanism 27, double-clutch mechanism first clutch 16, stepless speed change mechanism driving wheel, stepless speed change mechanism are driven
Wheel, epicyclic train 29, direct drive clutch A11, bevel gear C8, bevel gear A6, the second planetary planet gear are 30, direct gear
Clutch B26, it is finally output shaft 25.
（4）As long as when reversing automobile according to vehicle starting in the case of direct drive clutch B26 separate, reverse gear from
Clutch 7 slowly combines can.
（5）Only need to combine the second clutch in double-clutch mechanism when needing engine braking when automobile lower long slope
22, separate the first clutch can in double-clutch mechanism.
On rotational speed and torque situation analysis：Illustrate with working condition explanation in detail according to construction and set the rotating speed of input shaft 1
28n, torque M.So when the first clutch 16 in automobile ground zero double-clutch mechanism and direct drive clutch B26 are complete
With reference to when differential mechanism input gear 3 rotating speed 14n, torque 2M；The He of axle shaft gear 5 on differential mechanism is understood according to differential mechanism principle again
The torque of axle shaft gear 20 is all M under differential mechanism；It is again 3 according to the gearratio of the situation stepless speed change mechanism 28 of automobile ground zero,
The gearratio of epicyclic train 29 is 9, so bevel gear D18 and bevel gear C8 rotating ratio 27, the ∕ 27 of torque ratio 1.Again because cone
Gear A 6, bevel gear C8, bevel gear D18, bevel gear B19 reference diameters are equal, thus on differential mechanism axle shaft gear 5 rotating speed
For n, the rotating speed of axle shaft gear 20 is 27n under differential mechanism, and stepless speed change mechanism active wheel speed 27 is n, torque M, electrodeless variable-speed
Mechanism secondary speed is 9n, and torque 3M, bevel gear C8 rotating speeds are n, torque 27M, so bevel gear A6 rotating speeds are n, is turned
Square is 28M, so the rotating speed of output shaft 25 is n, torque 28M.When fast minimum 1 is arrived in effective gearratio regulation of stepless speed change mechanism
During ∕ 3, if also wanting speed change to divide three processes：Bevel gear when 1. 1 ∕ 3 of minimum is arrived in effective gearratio regulation of stepless speed change mechanism
D18 and bevel gear C8 rotating ratio are 3, the ∕ 3 of torque ratio 1, can similarly be obtained, and the rotating speed of axle shaft gear 5 is 7n on differential mechanism, differential
The rotating speed of axle shaft gear 20 is 21n under device, and stepless speed change mechanism active wheel speed is 21n, torque M, and stepless speed change mechanism is driven
Wheel speed is 63n, and torque is 1 ∕ 3M, and bevel gear C8 rotating speeds are 7n, torque 3M, so bevel gear A6 rotating speeds are 7n, torque is
4M, so the rotating speed of output shaft 25 is 7n, torque 4M, this is a power continuously continual process.2. double-clutch mechanism
One clutch 16 is rapidly separated, and double-clutch mechanism second clutch 22 combines rapidly power without stepless speed change mechanism, and because
It is 1 ∕ 3 for gear A 17 and the reference diameter ratio of gear B 24, so bevel gear 18 and bevel gear C8 rotating ratio are 3, torque ratio 1
∕ 3, the rotating speed of axle shaft gear 5 is 7n on differential mechanism, and the rotating speed of axle shaft gear 20 is 21n under differential mechanism, and bevel gear C8 rotating speeds are 7n,
Torque is 3M, so bevel gear A6 rotating speeds are 7n, torque 4M, so the rotating speed of output shaft 25 is 7n, torque be 4M it can thus be appreciated that
This is also power continuously continual process and when 1 ∕ 3 of minimum is arrived in effective gearratio regulation of stepless speed change mechanism when starting
It is the same, has only changed bar power path.3. but be just rapidly separated in this of short duration time, bottom gear clutch 9, directly
Meet gear clutch A11 to combine rapidly, gearratio maximum seat stepless speed change mechanism is transferred to starting again when, at this moment, double clutches
Structure second clutch 22 is rapidly separated, and double-clutch mechanism first clutch 16 combines rapidly, and power passes through electrodeless variable-speed motor again
Structure 28, the gearratio of stepless speed change mechanism 28 are 3, and the gearratio of planetary gear train 29 is 1, so bevel gear D18 and bevel gear
C8 rotating ratio is also 3, and torque ratio is also 1 ∕ 3.The rotating speed of axle shaft gear 5 is 7n on differential mechanism, axle shaft gear 20 under differential mechanism
Rotating speed is 21n, and stepless speed change mechanism active wheel speed is 21n, torque M, and stepless speed change mechanism secondary speed is 7n, torque
For 3M, bevel gear C8 rotating speeds are 7n, torque 3M, so bevel gear A6 rotating speeds are 7n, torque 4M, so the rotating speed of output shaft 25
For 7n, torque 4M, as long as finally regulation stepless speed change mechanism, adjust effective gearratio of stepless speed change mechanism and arrive 1 ∕ of minimum
The rotating speed of axle shaft gear 5 is 21n on differential mechanism when 3, and the rotating speed of axle shaft gear 20 is 7n under differential mechanism, stepless speed change mechanism driving wheel
Rotating speed 7 is n, torque M, and stepless speed change mechanism secondary speed is 21n, and torque is M ∕ 3, and bevel gear C8 rotating speeds are 21n, torque
For M ∕ 3, so bevel gear A6 rotating speeds are 21n, torque is 4M ∕ 3, so the rotating speed of output shaft 25 is 21n, torque is 4M ∕ 3.At this
During three the 2. the suitable special gear of individual all-gear drive, this process allow the rotating speed of input shaft 1 to raise because this
Do not influence electrodeless variable-speed.It is to the most high-grade rotating speed 21n of output shaft 25, torque from the starting rotating speed n torques 28M of deep low gear output shaft 25
The process power of 4M ∕ 3 is continuous continual, and this completes total speed-change process.
According to rotational speed and torque situation analysis, when vehicle starting, the maximum of stepless speed change mechanism 28 is solely subjected to 3M torques, and defeated
Shaft 25, which is cut, bears 28M torques, bears torque and improves more than 9 times, that is to say, that with the stepless gearbox of two same bearer abilities,
One on automobile, another kind be to be mounted directly on automobile for design and installation in this manner, it is assumed that below this can be held
By the engine of 2.0L discharge capacities, then can at least bear starting for 18L discharge capacities in design and installation to automobile in this manner
Machine, well imagine that this double clutch differential speed type stepless gearboxes can be adapted to the huge discharge vapour such as all cars, car, lorry
Car, and impact resistance can be greatly improved.
According to rotational speed and torque situation analysis, the rotating speed of input shaft 1 is 28 n during vehicle starting, and the rotating speed of output shaft 25 is n,
The rotating speed of input shaft 1 is set when changing to top gear also as 28 n, the rotating speed of output shaft 25 is 21n, and this is present electrodeless variable-speed model
Several times enclosed, such engine can make engine more fuel-efficient by speed change displacement in the larger context.
So this pair of clutch differential speed type buncher can be used for it is various it is small, in, oversize vehicle and need the big of speed change
In type plant equipment, the bottleneck that current this " frictional electrodeless variable-speed can not torque output greatly " be gone out at bottom is surveyed.
The foregoing is only a specific embodiment of the invention, but the protection domain invented is not limited thereto, any ripe
Know those skilled in the art the invention discloses technical scope in, the change or replacement that can readily occur in should all be covered
Within the protection domain of invention.
Claims (1)
1. buncher, including it is input shaft, differential mechanism (31), first clutch, second clutch, direct drive clutch, low
Speed gear clutch (9), the first epicyclic train, the second epicyclic train, stepless speed changing mechanism, first gear transmission mechanism,
Two gear drives, the 3rd gear drive, the 4th gear drive and output shaft, it is characterised in that：Input shaft (1)
It is connected with input shaft gear (2), input shaft gear (2) is engaged with differential mechanism input gear (3) and and differential spider pinion shaft
(4) it is connected, the differential pinion gear (21) being connected with differential spider pinion shaft (4) can be each around differential spider tooth
Wheel shaft (4) rotates, and axle shaft gear (20) engages with differential spider wheel (21) under axle shaft gear (5) and differential mechanism on differential mechanism；
Bevel gear A (6) and bevel gear B (19) fixes with axle shaft gear (20) under axle shaft gear on differential mechanism (5) and differential mechanism respectively to be connected
Connect, bevel gear A (6) and bevel gear B (19) also engage with bevel gear C (8) and bevel gear D (18) respectively；Bevel gear D (18) passes through
Axle is connected with double-clutch mechanism first clutch (16) and double-clutch mechanism second clutch (22) respectively, double-clutch mechanism first
Clutch (16) but with the moving part (14) of the driving wheel of stepless speed change mechanism (28) and the fixed part (15) of driving wheel
It is connected；The moving part (14) of stepless speed change mechanism driving wheel and the fixed part (15) of stepless speed change mechanism driving wheel with it is electrodeless
Gear steel band (13) connects；The moving part (10) of stepless speed change mechanism steel band (13) and stepless speed change mechanism driven pulley and
Fixed part (12) connection of stepless speed change mechanism driven pulley；The moving part (10) of the stepless speed change mechanism driving wheel and electrodeless
The fixed part (12) of gear driven pulley is connected by axle with the sun gear of the first epicyclic train (29), and sun gear leads to again
Planetary gear engagement is crossed, planetary gear planet carrier is linked by shaft bevel gears C (8)；Double-clutch mechanism second clutch (22) and gear A
(17) link；Gear A (17) engages with idle pulley (23), and idle pulley (23) engages with gear B (24)；Gear B (24) and bevel gear C
(8) axis connection is passed through；Bevel gear A (6) is connected by axle with the gear ring of the second epicyclic train (30)；Second epicyclic train
(30) sun gear is connected with output shaft (25).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710707871.0A CN107387703A (en) | 2017-08-17 | 2017-08-17 | Buncher |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710707871.0A CN107387703A (en) | 2017-08-17 | 2017-08-17 | Buncher |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN107387703A true CN107387703A (en) | 2017-11-24 |
Family
ID=60353593
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710707871.0A Pending CN107387703A (en) | 2017-08-17 | 2017-08-17 | Buncher |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN107387703A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108317230A (en) * | 2018-02-06 | 2018-07-24 | 董博 | With multichain CVT speed changers and the transmission ratio adjusting of differential mechanism and detection method |
| CN111677832A (en) * | 2018-12-03 | 2020-09-18 | 劳伦迪勒（昆山）机械工程有限公司 | Rolling type continuously variable transmission |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5554079A (en) * | 1994-04-06 | 1996-09-10 | Hyundai Motor Company | Gear train of an automatic five-speed transmission for a vehicle |
| CN103322145A (en) * | 2012-03-21 | 2013-09-25 | 李青山 | Planetary continuous variable transmission |
| CN205479217U (en) * | 2015-11-06 | 2016-08-17 | 欧阳恒 | Two separation and reunion differential formula buncher |
| CN205841645U (en) * | 2016-07-28 | 2016-12-28 | 北京汽车动力总成有限公司 | A kind of ST and automobile |
-
2017
- 2017-08-17 CN CN201710707871.0A patent/CN107387703A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5554079A (en) * | 1994-04-06 | 1996-09-10 | Hyundai Motor Company | Gear train of an automatic five-speed transmission for a vehicle |
| CN103322145A (en) * | 2012-03-21 | 2013-09-25 | 李青山 | Planetary continuous variable transmission |
| CN205479217U (en) * | 2015-11-06 | 2016-08-17 | 欧阳恒 | Two separation and reunion differential formula buncher |
| CN205841645U (en) * | 2016-07-28 | 2016-12-28 | 北京汽车动力总成有限公司 | A kind of ST and automobile |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108317230A (en) * | 2018-02-06 | 2018-07-24 | 董博 | With multichain CVT speed changers and the transmission ratio adjusting of differential mechanism and detection method |
| CN111677832A (en) * | 2018-12-03 | 2020-09-18 | 劳伦迪勒（昆山）机械工程有限公司 | Rolling type continuously variable transmission |
| CN111692306A (en) * | 2018-12-03 | 2020-09-22 | 劳伦迪勒（昆山）机械工程有限公司 | Rolling type continuously variable transmission |
| CN111677832B (en) * | 2018-12-03 | 2023-08-11 | 南京允正工业设备有限公司 | Rolling type stepless speed changer |
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Application publication date: 20171124 |