CN205479217U - Two separation and reunion differential formula buncher - Google Patents
Two separation and reunion differential formula buncher Download PDFInfo
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- CN205479217U CN205479217U CN201520881786.2U CN201520881786U CN205479217U CN 205479217 U CN205479217 U CN 205479217U CN 201520881786 U CN201520881786 U CN 201520881786U CN 205479217 U CN205479217 U CN 205479217U
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Abstract
The utility model relates to a derailleur field especially relates to a two separation and reunion differential formula buncher, and two separation and reunion differential formula buncher mainly includes input shaft, box of tricks, two clutching mechanism, an epicyclie gear, the 2nd epicyclie gear, continuously variable transmission, drive mechanism and output shaft. The utility model discloses two separation and reunion differential formula buncher is according to the certain two clutching mechanism of rule control, epicyclie gear and continuously variable transmission, through the twice control continuously variable transmission's that circulate owner, the working radius of slave operation wheel to it changes driven drive ratio widely to reach. The utility model discloses combine the advantage of buncher, double -clutch gearbox and box of tricks, increased moment of torsion, impact nature, speed range and the efficiency of buncher transmission widely to simple structure, low cost can a widely used two separation and reunion differential formula buncher.
Description
Technical field
This utility model relates to buncher, particularly relates to a kind of double clutch differential speed type buncher.
Background technology
It is current that buncher is widely used in industry (particularly auto industry), and buncher has multiple.Such as hydraulic pressure buncher,
Electric power buncher, mechanical stepless speed changing device etc..Because fluid power buncher efficiency is low, processing request is high.Electric power buncher material is wanted
Asking high, structure is complicated, and mechanical pole-free speed variator is not suitable for high pulling torque, bearing capacity poor impact resistance, and speed ratio excursion is little, therefore the suitableeest
Close the transmission of middle low power and be difficult to be suitable for high-power transmission.
Utility model content
The purpose of this utility model is for the problems referred to above existed, it is provided that a kind of double clutch differential speed type bunchers.
The technical solution adopted in the utility model is as follows:
Double clutch differential speed type bunchers, including power shaft, output shaft, box of tricks, double-clutch mechanism, stepless speed changing mechanism, first planet
Gear train, the second epicyclic train and drive mechanism；
Described power shaft is connected with described box of tricks by described drive mechanism；
Described box of tricks one end is connected with double-clutch mechanism by described drive mechanism；
The described box of tricks other end is connected by described drive mechanism and the second epicyclic train；
Described double-clutch mechanism one end connects described stepless speed change mechanism；
The described double-clutch mechanism other end is also connected with the second epicyclic train by described drive mechanism；
Described stepless speed change mechanism connects described first planet gear train；
Described first planet gear train is connected by described drive mechanism and the second epicyclic train；
Described second epicyclic train connects described output shaft；
Described drive mechanism is gear and axle construction.
Described box of tricks mainly include semiaxis on box of tricks input, box of tricks planetary gear axle, box of tricks planetary gear, box of tricks,
Semiaxis under box of tricks；
Described box of tricks can be central gear box of tricks；
Described gear drive includes input shaft gear, bevel gear A, bevel gear B, bevel gear C, bevel gear D, gear A, idle pulley and gear
B；
Described input shaft gear connects the input of told box of tricks；The input of box of tricks is connected with box of tricks planetary gear axle；
Described box of tricks planetary gear can freely rotate around box of tricks planetary gear axle；
On described box of tricks, under axle shaft gear and box of tricks, axle shaft gear engages with box of tricks planetary gear；
Described bevel gear A and bevel gear B is connected with axle shaft gear under axle shaft gear on box of tricks and box of tricks respectively；
Described bevel gear A and bevel gear B engages with bevel gear C and bevel gear D the most respectively；
Described bevel gear A, bevel gear B, bevel gear C, bevel gear D simply transmission power and the direction of transfer of change power, gear ratio between them
Can change through needs.
Described double-clutch mechanism has two clutches as the double-clutch mechanism operation principle in double disengaging type automatic transmission；Or first clutch
Engaging, second clutch separates, and second clutch engages, and first clutch separates, and does not has the state that two clutches concurrently separate；
Described double-clutch mechanism first clutch connects the drivewheel of described stepless speed change mechanism；
Described double-clutch mechanism second clutch connects described gear A；
Described gear A engages with idle pulley；
Described idle pulley engages with gear B；
Described idle pulley is individual gears or Double-gear idle pulley；
Described gear A, rotation speed relation and drivewheel during described stepless speed change mechanism maximum transmission ratio of gear B, identical from the rotating speed of the wheel of power.
Described stepless speed change mechanism mainly includes drivewheel, driven pulley, driving member, control piece；
Described stepless speed change mechanism is the existing buncher that can not be suitable for high-power high pulling torque, such as: KRG conical ring formula buncher, metal tape
Formula buncher, metal chain type buncher etc.；
Described stepless speed change mechanism is the radius of clean-up of the driving and driven active wheel by circulating two secondary control stepless speed changing mechanisms thus changes the biography of transmission
Dynamic ratio.
Described first planet gear train mainly includes sun gear, planetary gear, planet carrier, gear ring, direct drive clutch A, brake；
Described stepless speed change mechanism driven pulley connects the sun gear of described first planet gear train；
Described first planet gear train sun gear engages with described first planet gear train planetary gear, is connected with described direct drive clutch A；
Described first planet gear train planetary gear engages with described first planet gear train sun gear and described first planet gear train gear ring；
Described first planet gear train gear ring is connected with described brake and described direct drive clutch A；
Described first planet gear train planet carrier links with bevel gear C；
Described first planet gear train is a kind of feasible device, is not necessarily epicyclic train, can be fixed shaft gear train；
Described brake, described direct drive clutch A separates, and described first planet train ratios is that described stepless speed change mechanism maximum passes
Dynamic ratio square；
Described direct drive clutch A engages, and it is 1 that described brake separates described first planet train ratios.
Described second epicyclic train mainly includes sun gear, planetary gear, planet carrier, gear ring, direct drive clutch B, brake of reversing gear；
Described second epicyclic train gear ring is power intake；
Described second epicyclic train gear ring and the engagement of the second epicyclic train planetary gear；
Described second epicyclic train planetary gear engages with described second epicyclic train sun gear；
Described second epicyclic train planet carrier is connected with direct drive clutch B and brake of reversing gear；
Described second epicyclic train sun gear is connected with direct drive clutch B and output shaft；
Described second epicyclic train is a kind of feasible device that reverses gear, and is not necessarily epicyclic train, can be fixed shaft gear train.
This utility model has the advantages that
The double clutch differential stepless speed variator of this utility model, is at existing buncher, such as: machinery, electrical equipment, hydraulic pressure or fluid power etc.
Buncher, above adds a box of tricks, utilizes two semiaxis of box of tricks to be shunted by power, makes a part of power by high efficiency
Gear passes to wheel；Then power is the most alternately passed to buncher and gear mechanism, finally by tooth by double-clutch mechanism by another part power
Two power are merged by wheel mechanism, thus raising can bearing capacity and wide scope variable-speed torque-converting etc..
The double clutch differential speed type buncher of this utility model is the radius of clean-up of the driving and driven active wheel by circulating two secondary control stepless speed changing mechanisms
Thus change the gear ratio of metal belt transmission.Moving axially of the moving part of driving and driven active wheel is the driving cycle according to automobile, passes through hydraulic pressure
Control system regulates continuously and realizes this part of variable transmission and existing buncher principle is similar.
This utility model combines the advantage of buncher, double-clutch automatic gearbox and box of tricks, considerably increases buncher and passes
Moment of torsion, impact, slewing range and the efficiency passed, and simple in construction, with low cost, can be widely used.
Accompanying drawing explanation
The structural representation that Fig. 1 this utility model is implemented；
In figure, 1: power shaft；2: input shaft gear；3: box of tricks input gear；4: box of tricks planetary gear axle；5: box of tricks upper half
Shaft gear；6: bevel gear A；7: brake of reversing gear；8: bevel gear C；9: brake；10: the driven moving part of stepless speed change mechanism；11:
Direct drive clutch A；12: the driven standing part of stepless speed change mechanism；13: stepless speed change mechanism steel band；14: stepless speed change mechanism is the most movable
Part；15: stepless speed change mechanism actively standing part；16: double-clutch mechanism first clutch；17: gear A；18: bevel gear D；19 cones
Gear B；20: axle shaft gear under box of tricks；21: box of tricks planetary gear；22: double-clutch mechanism second clutch；23: idle pulley；24:
Gear B；25: output shaft；26: direct drive clutch B；27: double-clutch mechanism；28: stepless speed change mechanism；29: first planet gear train；
30: the second epicyclic trains；31: box of tricks；
Detailed description of the invention
In order to make the purpose of this utility model, technical scheme and advantage more clear a part of technical scheme of the present utility model will be entered below clear,
Complete description.Obviously, described is a part of embodiment.Based on the embodiment in this utility model, this area ordinary person does not make wound
All other embodiments obtained by the premise of the property made work, broadly fall into the scope that this utility model is protected.
In this utility model describes, it should be noted that term " first ", " second ", " on ", D score be for describing purpose and accompanying drawing institute
The orientation shown, is merely to distinguish description and being easy to describe rather than indicate importance and specificity.
In this utility model describes, it should be noted that unless otherwise clearly defined and limited, term " is connected ", " connection " should do extensively
Justice is explained, can be connection, it is also possible to be that dismounting connects, or one connects, can be mechanical connection or frictional connection etc..General for this area
Logical technical staff, can understand above-mentioned term concrete meaning in this utility model with concrete condition.
Below in conjunction with the accompanying drawings this utility model is described further:
As it is shown in figure 1, double clutch differential speed type bunchers, including power shaft 1, box of tricks 31, first clutch 16, second clutch
22, direct drive clutch 11, brake 9, first planet gear train the 29, second epicyclic train 30, stepless speed changing mechanism 28, gear drive
Mechanism and output shaft 25.Power shaft 1 is connected with input shaft gear 2, and input shaft gear 2 engages with box of tricks input gear 3 and (sets reference circle
Diameter ratio 1: 2) and be connected with box of tricks planetary gear axle 4, the box of tricks planetary gear 21 being connected with box of tricks planetary gear axle 4
Can be each the most freely rotatable around box of tricks planetary gear axle 4, on box of tricks under axle shaft gear 5 and box of tricks axle shaft gear 20 with poor
Speed mechanism planetary gear 21 engages (setting reference diameter ratio 1: 1)；Bevel gear A 6 and bevel gear B 19 respectively with axle shaft gear on box of tricks 5
Being connected by axle with axle shaft gear under box of tricks 20, bevel gear A 6 engages (setting reference diameter ratio 1: 1) with bevel gear C 8；Bevel gear B
19 engage (setting reference diameter ratio 1: 1) with bevel gear D 18；Bevel gear D 18 by axle respectively with double-clutch mechanism first clutch 16 and
Double-clutch mechanism second clutch 22 is connected, double-clutch mechanism first clutch 16 again with the moving part 14 of the drivewheel of stepless speed change mechanism 28
And the standing part 15 of drivewheel is connected；The moving part 14 of stepless speed change mechanism drivewheel and the standing part 15 of stepless speed change mechanism drivewheel
It is connected with stepless speed change mechanism steel band 13 by frictional force；The moving part 10 of stepless speed change mechanism steel band 13 and stepless speed change mechanism driven pulley and
The standing part 12 of stepless speed change mechanism driven pulley (sets the maximum effectively gear ratio 3 of stepless speed change mechanism, minimum effectively gear ratio by frictional force connection
1/3)；The moving part 10 of stepless speed change mechanism driven pulley and the standing part 12 of stepless speed change mechanism driven pulley are by axle and first planet gear
Being the sun gear connection of 29, sun gear engages further through planetary gear, and planetary gear engages with gear ring again, and planet carrier is fixing with bevel gear C 8 by axle
Link；Double-clutch mechanism second clutch 22 and gear A 17 link, and gear A 17 engages with idle pulley 23, and idle pulley 23 engages with gear B 24.
Gear B 24 is connected by axle with bevel gear C 8；Bevel gear A 6 is connected by the gear ring of axle and the second epicyclic train 30；Second planetary gear
Be 30 sun gear be connected with output shaft 25.
Setting according to described above, the maximum effectively gear ratio 3 of stepless speed change mechanism, minimum effectively gear ratio 1/3 may determine that gear 17 and gear
24 rotating ratios are 3, if the maximum effectively gear ratio 2.5 of stepless speed change mechanism, minimum effectively gear ratio 2/5 may determine that gear 17 and gear 24
Rotating ratio is 2.5, say, that gear 17 and the ratio of gear 24 rotating speed and the maximum effectively gear ratio of stepless speed change mechanism are equal.When brake 9 is made
Dynamic, direct drive clutch 11 may determine that when separating the gear ratio of epicyclic train 29 be 9 (namely 3 square), if stepless speed change mechanism
Maximum effectively gear ratio 2.5, during minimum effectively gear ratio 2/5, brake 9 is braked, and direct drive clutch 11 may determine that planetary gear when separating
Be 29 gear ratio be 6.25 (namely 2.5 square), say, that when brake 9 combines planetary gear when direct drive clutch 11 separates
Be 29 gear ratio be the maximum effectively gear ratio of stepless speed change mechanism square.
Embodiment:
(1) when idling wanted by automobile, double-clutch mechanism first clutch 16 and double-clutch mechanism second clutch 22 all locate released state or directly
Released state is all located in gear clutch B 26 and brake 7 of reversing gear.The moment of torsion that electromotor transmits passes to differential through power shaft 1 and input shaft gear 2
Mechanism 31, owing to output shaft 25 does not turns so axle shaft gear 5 does not turns on box of tricks, turns according to the principle now planetary gear of box of tricks
Under fast box of tricks, the rotating speed of axle shaft gear 20 is the twice of box of tricks input gear 3, again because double-clutch mechanism first clutch 16 and double from
Close mechanism's second clutch 22 and all locate released state so power cannot transmit thus reach idling requirement.Or direct drive clutch B 26 and reversing gear
Brake 7 all released states.Now the planetary gear of epicyclic train is in freely rotatable, and therefore power also cannot pass to output shaft 25, thus reaches
Idling requirement.
(2) when automobile ground zero, double-clutch mechanism first clutch 16 is in bonding state double-clutch mechanism second clutch 22 and is in released state,
Power is without gear A 17, but through stepless speed change mechanism 28；And the moving part 14 of stepless speed change mechanism drivewheel and electrodeless variable-speed motor
Distance between the standing part 15 of structure drivewheel is farthest, the moving part 10 of stepless speed change mechanism driven pulley and consolidating of stepless speed change mechanism driven pulley
That determines between part 12 is closest, say, that effective gear ratio of stepless speed change mechanism is maximum；And the brake of first planet gear train 29
9 are in released state at on-position direct drive clutch A 11；And the direct drive clutch B 26 of the second epicyclic train 30 is in combination and falls
Gear brake 7 is in released state.Power transmission line divides two parts order to be followed successively by: 1. power shaft 1, input shaft gear 2, box of tricks are defeated
Enter axle shaft gear 5 on gear 3, box of tricks planetary gear axle 4, box of tricks, bevel gear A6, the second epicyclic train 30, directly keep off clutch
Device B 26, is finally output shaft 25；2. power shaft 1, input shaft gear 2, box of tricks input gear 3, box of tricks planetary gear axle 4, differential
Axle shaft gear 20 under mechanism, bevel gear B 19, bevel gear D 18, double-clutch mechanism 27, double-clutch mechanism first clutch 16, stepless speed change mechanism master
The moving part 14 of driving wheel, the moving part 10 of stepless speed change mechanism driven pulley, epicyclic train 29, bevel gear C 8, bevel gear A 6, the second planet
Gear train 30, direct drive clutch B 26, output shaft 25.
(3) when vehicle starting and to certain speed to be accelerated time, the namely moving part 14 of stepless speed change mechanism drivewheel and electrodeless variable-speed
Closest between the standing part 15 of mechanism's drivewheel, the moving part 10 of stepless speed change mechanism driven pulley and stepless speed change mechanism driven pulley
Distance between standing part 12 is farthest, and during effective gear ratio minimum of namely stepless speed change mechanism, double-clutch mechanism first clutch 16 is rapid
Separating, double-clutch mechanism second clutch 22 combines rapidly power without stepless speed change mechanism, and now power transmission order successively is: 1. input
Axle shaft gear 20 under axle 1, input shaft gear 2, box of tricks input gear 3, box of tricks planetary gear axle 4, box of tricks, bevel gear B 19,
Bevel gear D 18, double-clutch mechanism 27, double-clutch mechanism second clutch 22, gear A 17, idle pulley 23, gear B 24, bevel gear C 8,
Bevel gear A 6, direct drive clutch B26 are finally output shafts 25；2. power shaft 1, input shaft gear 2, box of tricks input gear 3, differential
Axle shaft gear 5 on mechanism's planetary gear axle 4, box of tricks, bevel gear A the 6, second planetary planet gear are 30, direct drive clutch B 26,
Output shaft 25, now, stepless speed change mechanism 28 does not has power to flow through, and at this moment brake 9 is rapidly separated, and direct drive clutch A 11 ties rapidly
Closing, stepless speed change mechanism is transferred to again seat during starting, and namely effective gear ratio of stepless speed change mechanism is maximum, above this process be moment with
Time complete, double-clutch mechanism first clutch 16 can be controlled combine rapidly when completing this process change speed gear box computer, double-clutch mechanism the second clutch
Device 22 is rapidly separated, and power is again through stepless speed change mechanism 28；Now power divides again two parts: 1. power shaft 1, input shaft gear 2, differential
Axle shaft gear 5 on mechanism's input gear 3, box of tricks planetary gear axle 4, box of tricks, bevel gear A the 6, second planetary planet gear be 30,
Direct drive clutch B 26, is finally output shaft 25；2. power shaft 1, input shaft gear 2, box of tricks input gear 3, box of tricks planet
Axle shaft gear 20, bevel gear B 19, bevel gear D 18, double-clutch mechanism 27, double-clutch mechanism first clutch under gear shaft 4, box of tricks
16, stepless speed change mechanism drivewheel, stepless speed change mechanism driven pulley, first planet gear train 29, direct drive clutch A 11, bevel gear C 8,
Bevel gear A the 6, second planetary planet gear is 30, direct drive clutch B 26, is finally output shaft 25.
(4) as long as direct drive clutch B 26 being separated in the case of during vehicle starting when reversing automobile, brake 7 of reversing gear slowly is braked
That's all.
(5) need the second clutch 22 having only to combine in double-clutch mechanism during engine braking when automobile lower long slope, separate double-clutch mechanism
In first clutch or separate direct drive clutch A 11, brake 9 is braked.
About rotational speed and torque situation analysis: the rotating speed setting power shaft 1 is M as 28n, torque, no power waste.When the double clutch of automobile ground zero
Box of tricks input gear 3 rotating speed 14n when first clutch 16 in structure and direct drive clutch B26 are completely combined, torque is 2M；Basis again
It is all M that box of tricks principle understands on box of tricks axle shaft gear 20 torque under axle shaft gear 5 and box of tricks；Again according to the situation of automobile ground zero
The gear ratio of stepless speed change mechanism 28 is 3, and the gear ratio of epicyclic train 29 is 9, so the rotating ratio 27 of bevel gear D 18 and bevel gear C 8,
Torque ratio 1/27.Equal because having set bevel gear A 6, bevel gear C 8, bevel gear D 18, bevel gear B 19 reference diameter again, thus poor
In speed mechanism, the rotating speed of axle shaft gear 5 is n, and under box of tricks, axle shaft gear 20 rotating speed is 27n, and stepless speed change mechanism drivewheel rotating speed 27 is n,
Torque is M, and stepless speed change mechanism secondary speed is 9n, and torque is 3M, and bevel gear C 8 rotating speed is n, and torque is 27M, so bevel gear A 6
Rotating speed is n, and torque is 28M, so output shaft 25 rotating speed is n, torque is 28M.When effective gear ratio of stepless speed change mechanism is adjusted to
When little 1/3, if also wanting speed change can divide Four processes: the most effective gear ratio of stepless speed change mechanism is adjusted to bevel gear D 18 when minimum 1/3
Being 3 with the rotating ratio of bevel gear C 8, torque ratio 1/3, on box of tricks, the rotating speed of axle shaft gear 5 is 7n, axle shaft gear 20 under box of tricks
Rotating speed is 21n, and stepless speed change mechanism drivewheel rotating speed is 21n, and torque is M, and stepless speed change mechanism secondary speed is 63n, and torque is 1/3M,
Bevel gear C 8 rotating speed is 7n, and torque is 3M, and bevel gear A 6 rotating speed is 7n, and torque is 4M, and output shaft 25 rotating speed is 7n, when torque is 4M.
The most then double-clutch mechanism first clutch 16 is rapidly separated, and double-clutch mechanism second clutch 22 combines rapidly power without stepless speed change mechanism,
Because gear A 17 and gear B 24 rotating ratio are 3, torque ratio 1/3, on box of tricks, the rotating speed of axle shaft gear 5 is 7n, box of tricks lower half
Shaft gear 20 rotating speed is 21n, and bevel gear C 8 rotating speed is 7n, and torque is 3M, so bevel gear A 6 rotating speed is 7n, torque is 4M, thus defeated
Shaft 25 rotating speed is 7n, and torque is 4M, and being now adjusted to minimum 1/3 moment with gear ratio before stepless speed change mechanism is the same, only
Forward the power of stepless speed change mechanism to gear drive.But just in this process, stepless speed change mechanism is transferred to again the position that during starting, gear ratio is maximum
Son, brake 9 is rapidly separated, and direct drive clutch A 11 combines rapidly.The most subsequently double-clutch mechanism second clutch 22 is rapidly separated, double
Clutch first clutch 16 combines rapidly, and power is again through stepless speed change mechanism 28, and stepless speed change mechanism 28 gear ratio is 3, planet tooth
The gear ratio of wheel train 29 is 1, so the rotating ratio of bevel gear D 18 and bevel gear C 8 is also 3, torque ratio is also 1/3.On box of tricks
The rotating speed of axle shaft gear 5 is 7n, and under box of tricks, axle shaft gear 20 rotating speed is 21n, and stepless speed change mechanism drivewheel rotating speed is 21n, and torque is M,
Stepless speed change mechanism secondary speed is 7n, and torque is 3M, and bevel gear C 8 rotating speed is 7n, and torque is 3M, so bevel gear A 6 rotating speed is 7n,
Torque is 4M, so output shaft 25 rotating speed is 7n, torque is 4M.As long as 4. last re-adjustments stepless speed change mechanism again, makes electrodeless variable-speed motor
Effective gear ratio of structure, when maximum 3 is adjusted to minimum 1/3, this completes total speed-change process.Calculate this process box of tricks last
The rotating speed of upper axle shaft gear 5 is 21n, and under box of tricks, axle shaft gear 20 rotating speed is 7n, and stepless speed change mechanism drivewheel rotating speed 7 is n, and torque is
M, stepless speed change mechanism secondary speed is 21n, and torque is M/3, and bevel gear C 8 rotating speed is 21n, and torque is M/3, so bevel gear A 6
Rotating speed is 21n, and torque is 4M/3, so output shaft 25 rotating speed is 21n, torque is 4M/3.
Because the suitable fixing gear of all-gear drive during second, this process allows power shaft 1 rotating speed to raise, because this not shadow
Ring whole speed-change process.
When power shaft 1 rotating speed, torque are constant, during deep low gear output shaft 25 rotating speed be n torque be 28M be 21n to the most high-grade output shaft 25 rotating speed,
Torque is 4M/3.
According to rotational speed and torque situation analysis, when vehicle starting, stepless speed change mechanism 28 maximum is solely subjected to 3M torque, and output shaft 25 maximum is cut and held
By 28M torque, bear torque and improve more than 9 times, say, that with the stepless gearbox of two same bearer abilities, one is designed in this manner
Being installed on automobile, another kind to be mounted directly on automobile, it is assumed that this electromotor that can bear 2.0L discharge capacity being mounted directly below, that
Design and installation is to the electromotor that can bear 18L discharge capacity minimum on automobile in this manner, well imagines this pair of clutch differential speed type electrodeless variable-speed
Case can be suitable for the huge discharge automobiles such as all of car, passenger vehicle, lorry, and can be greatly improved resistance to impact.
According to speed conditions analysis, during vehicle starting, the rotating speed of power shaft 1 is 28n, and the rotating speed of output shaft 25 is n, sets when changing to top gear
The rotating speed of power shaft 1 is also 28n, then the rotating speed of output shaft 25 is 21n, and this is several times of slewing range of present stepless gearbox, so
Electromotor can also avoid the need for fluid torque-converter by speed change displacement in the range of beyond the most several times, makes electromotor in the scope exceeding the most several times
The work of interior " comfortable " so can more fuel-efficient raising fuel efficiency.
So this pair of clutch differential speed type buncher may be used for various little, in, oversize vehicle and need on the heavy mechanical equipment of speed change, survey the end
Go out the bottleneck of the most this " friction-type electrodeless variable-speed can not greatly torque output ".
Described embodiment of the present utility model, it is also possible to the second epicyclic train is put into input shaft end, so have no effect on double clutch differential speed type without
The work of pole variator, because it only does gear reversing function.
The foregoing is only embodiment of the present utility model, but the protection domain of utility model is not limited thereto, any be familiar with this area
Technical staff in the technical scope that this utility model discloses, the change that can readily occur in or replacement, all should contain utility model protection domain it
In.
Claims (6)
1. pair clutch differential speed type buncher, it is characterised in that: include power shaft, output shaft, box of tricks, double-clutch mechanism, stepless speed changing mechanism, first planet gear train, the second epicyclic train and drive mechanism；
Described power shaft is connected with described box of tricks by described drive mechanism；
Described box of tricks one end is connected with double-clutch mechanism by described drive mechanism；
The described box of tricks other end is connected by described drive mechanism and the second epicyclic train；
Described double-clutch mechanism one end connects described stepless speed change mechanism；
The described double-clutch mechanism other end is also connected with the second epicyclic train by described drive mechanism；
Described stepless speed change mechanism connects described first planet gear train；
Described first planet gear train is connected by described drive mechanism and the second epicyclic train；
Described second epicyclic train connects described output shaft；
Described drive mechanism is gear and axle construction.
The most according to claim 1 pair of clutch differential speed type buncher, it is characterised in that: described box of tricks is conventional carrier；Described gear drive includes bevel gear A, B, C, D；Described power shaft connected with differential shell, differential mechanism two-semiaxle is connected with described bevel gear A, B respectively；Described bevel gear A, B engage with described bevel gear C, D respectively.
The most according to claim 1 pair of clutch differential speed type buncher, it is characterised in that: described double-clutch mechanism has two clutches as the double-clutch mechanism operation principle in double disengaging type automatic transmission；Or first clutch engages, second clutch separates, and second clutch engages, and first clutch separates, and does not has the state that two clutches concurrently separate；
Described drive mechanism is gear A, gear B, idle pulley；
Described double-clutch mechanism first clutch connects the drivewheel of described stepless speed change mechanism；
Described double-clutch mechanism second clutch connects described gear A；
Described gear A engages with idle pulley；
Described idle pulley engages with gear B；
Described idle pulley is individual gears or Double-gear idle pulley；
Described gear A, gear B rotation speed relation identical with the rotating speed of driven wheel during described stepless speed change mechanism maximum transmission ratio.
The most according to claim 1 pair of clutch differential speed type buncher, it is characterised in that: described stepless speed change mechanism includes drivewheel, driven pulley, driving member, control piece；
Described stepless speed change mechanism is the existing buncher that can not be suitable for high-power high pulling torque；
Described stepless speed change mechanism is the radius of clean-up of the driving and driven active wheel by circulating two secondary control stepless speed changing mechanisms thus changes the gear ratio of transmission.
The most according to claim 1 and 2 pair of clutch differential speed type buncher, it is characterised in that: described first planet gear train includes sun gear, planetary gear, planet carrier, gear ring, direct drive clutch A, brake；
Described stepless speed change mechanism driven pulley connects the sun gear of described first planet gear train；
Described first planet gear train sun gear engages with described first planet gear train planetary gear, is connected with described direct drive clutch A；
Described first planet gear train planetary gear engages with described first planet gear train sun gear and described first planet gear train gear ring；
Described first planet gear train gear ring is connected with described brake and described direct drive clutch A；
Described first planet gear train planet carrier links with bevel gear C；
Described brake, described direct drive clutch A separate, described first planet train ratios be described stepless speed change mechanism maximum transmission ratio square；
Described direct drive clutch A engages, and it is 1 that described brake separates described first planet train ratios.
The most according to claim 1 pair of clutch differential speed type buncher, it is characterised in that: described second epicyclic train includes sun gear, planetary gear, planet carrier, gear ring, direct drive clutch B, brake of reversing gear；
Described second epicyclic train gear ring is power intake；
Described second epicyclic train gear ring and the engagement of the second epicyclic train planetary gear；
Described second epicyclic train planetary gear engages with described second epicyclic train sun gear；
Described second epicyclic train planet carrier is connected with direct drive clutch B and brake of reversing gear；
Described second epicyclic train sun gear is connected with direct drive clutch B and output shaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520881786.2U CN205479217U (en) | 2015-11-06 | 2015-11-06 | Two separation and reunion differential formula buncher |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520881786.2U CN205479217U (en) | 2015-11-06 | 2015-11-06 | Two separation and reunion differential formula buncher |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205479217U true CN205479217U (en) | 2016-08-17 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520881786.2U Expired - Fee Related CN205479217U (en) | 2015-11-06 | 2015-11-06 | Two separation and reunion differential formula buncher |
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| CN (1) | CN205479217U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107387703A (en) * | 2017-08-17 | 2017-11-24 | 芜湖通全科技有限公司 | Buncher |
| CN109707806A (en) * | 2017-10-25 | 2019-05-03 | Zf 腓德烈斯哈芬股份公司 | The stepless drive apparatus of power dividing type |
| CN112049915A (en) * | 2019-06-05 | 2020-12-08 | 哈尔滨工业大学 | Multi-shaft differential device |
-
2015
- 2015-11-06 CN CN201520881786.2U patent/CN205479217U/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107387703A (en) * | 2017-08-17 | 2017-11-24 | 芜湖通全科技有限公司 | Buncher |
| CN109707806A (en) * | 2017-10-25 | 2019-05-03 | Zf 腓德烈斯哈芬股份公司 | The stepless drive apparatus of power dividing type |
| CN109707806B (en) * | 2017-10-25 | 2023-02-28 | Zf 腓德烈斯哈芬股份公司 | Power dividing type stepless transmission device |
| CN112049915A (en) * | 2019-06-05 | 2020-12-08 | 哈尔滨工业大学 | Multi-shaft differential device |
| CN112049915B (en) * | 2019-06-05 | 2022-04-22 | 哈尔滨工业大学 | Multi-shaft differential device |
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| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20160817 Termination date: 20171106 |
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| CF01 | Termination of patent right due to non-payment of annual fee |