CN2487920Y - Electric carrying means geartrain - Google Patents
Electric carrying means geartrain Download PDFInfo
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- CN2487920Y CN2487920Y CN 01226624 CN01226624U CN2487920Y CN 2487920 Y CN2487920 Y CN 2487920Y CN 01226624 CN01226624 CN 01226624 CN 01226624 U CN01226624 U CN 01226624U CN 2487920 Y CN2487920 Y CN 2487920Y
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Abstract
The utility model relates to an electric carrying means gear train. The utility model is put forward for providing an energy saving electric drive gear with a simple structure, low cost, convenient operation. The utility model comprises a power source, a driving axle connected with the power source, driving wheel assemblies arranged on the driving axle and a power output unit connected with wheels; the driving axle comprises a first and a second driving axles which are arranged in parallel, and a first and a second driving wheel assemblies which are perpendicular to each other and arranged on the first and the second driving axles; and driving components of the first and the second driving wheel assemblies are connected to the first and the second driving axles through a single direction bearing.
Description
The utility model belongs to the Electric actuator driving mechanism, particularly a kind of drive mechanism of electric carrier.
So-called electric carrier is to comprise electric golf cart, Segway Human Transporter, electric wheelchair, electric locomotive and electric bicycle etc.The kind of drive of known electric carrier, mostly with motor collocation fixedly the transmission system of reduction speed ratio reach the purpose of wheels.Its speed controlling is directly to control the rotating speed of the speed of motor rotation with the control wheel.The simple electric carrier kind of drive of this kind, though have advantage cheaply, but can't cooperate the fluctuating of road conditions, make motor do efficient power output, except that causing the quick consumption of battery, the enjoyment that material forfeiture drives is because fixedly the transmission system of reduction speed ratio can't be taken into account the output of two kinds of different moments of torsion on climbing and high speed.Just be set in the reducing gear of the low speed ratio that can run at high speed on the level land, when running into climbing, just do not have enough moments of torsion and deal with the steeper gradient; Otherwise the driving mechanism of high reduction speed ratio then can't produce effect preferably on speed.So the traffic tool such as automobile, locomotive even bicycle, all collocation has speed variator system, to deal with various road conditions and to save the energy.
General direct current generator has the characteristic of the high moment of torsion of the slow-speed of revolution, the low moment of torsion of high rotating speed, but from the efficiency of motor curve, the efficient of maximum speed and minimum speed is all bad, motor best efficiency interval is approximately dropped on about the 60%-85% of no-load rotating speed, therefore for reaching the target of power saving, rotating speed of motor preferably is controlled in the optimum efficiency interval, and the fixing transmission system of reduction speed ratio, often because the factor of external environment, it is a lot of to make that the rotating speed of motor scope surpasses the optimum efficiency district, also very undesirable on the saving energy.
Therefore, higher electric carrier, for improving the shortcoming of above fixedly gearing down system, all collocation has speed variator system.Electric locomotive, electric bicycle all are provided with speed change gear at present.But existing speed change gear complex structure, precision need higher manufacture cost, and this also is that the electric carrier of general low to medium price level all adopts the fixedly main cause of deceleration system.If is example with present electric bicycle, its price is low than electric locomotive, thus its speed variator system also than electric locomotive come simply.The speed variator system of electric bicycle is that the sprocket wheel that utilizes chain to drive to vary in size is to reach the purpose of speed change.It is bulky that this gear removes outward appearance, is not suitable for lighter electric carrier, outside on the Segway Human Transporter, also very inconvenient in operation.When the speed of driving by slow and when fast, reduction speed ratio begins from large to small; After brake stopped, chain also rested on the sprocket wheel of minimum deceleration ratio, and causing when starting once more needs with the manpower assistant starting.Such kind of drive is inapplicable on Segway Human Transporter, electric wheelchair and electric golf cart.
The purpose of this utility model provide a kind of simple in structure, cost is low, easy to operate, the drive mechanism of electric carrier of saving the energy.
The utility model power source, the transmission shaft that is connected with power source, the power output unit that is mounted on the driving wheel group on the transmission shaft and engages with wheel; Transmission shaft comprises first and second parallel transmission shaft and is vertical configuration and is mounted on I and II driving wheel group on first and second transmission shaft; The transmission component of I and II driving wheel group is engaged on first and second transmission shaft with unilateral bearing.
Wherein:
Power source is a motor that is engaged on one of first and second transmission shaft.
Power source comprises first and second motor that is engaged in respectively on first and second transmission shaft.
Driving wheel group is made up of plural transmission component.
Transmission component is sprocket wheel and chain.
Transmission component is belt pulley and belt.
Transmission component is a gear.
Be provided with clutch structure between power output element and the wheel.
Be provided with differential mechanism between first and second parallel transmission shaft.
The I and II driving wheel group is I and II Transmitted chains wheels; The first grade transmission chain wheels comprise the master of identical modulus,, passive sprocket wheel chain main by movable sprocket and connection; Drive sprocket with axle to wheel be clockwise transmission, to take turns axle be that the unilateral bearing of counterclockwise transmission is engaged in first transmission shaft; By movable sprocket with axle to wheel serve as contrary pin transmission, to take turns axle be that the unilateral bearing of clockwise transmission is engaged in second transmission shaft; The second grade transmission chain wheels comprise the master of identical modulus, by the movable sprocket power output sprocket and connect drive sprocket, by the chain of movable sprocket, power output sprocket; Drive sprocket with axle to wheel serve as contrary pin transmission, to take turns axle be that the unilateral bearing of clockwise transmission is engaged in first transmission shaft; By movable sprocket with axle to wheel be clockwise transmission, to take turns axle be that the unilateral bearing of counterclockwise transmission is engaged in second transmission shaft; Drive sprocket places the chain outside.
The I and II driving wheel group is the I and II driving gear with direct engagement; The one-level driving gear set comprise identical modulus but out of mesh two driving gears and simultaneously with the power output gear of two driving gears engagement; Two driving gears respectively with axle to wheel be counterclockwise transmission, wheel to axle be the unilateral bearing of clockwise transmission and axle to wheel serve as against the pin transmission, to take turns axle be that the unilateral bearing of clockwise transmission is engaged in first and second transmission shaft; Power output gear is engaged in the pto that comprises left and right half with differential mechanism; The secondary driving gear set comprises identical modulus and intermeshing little, big driving gear; Small transmission gear with axle to wheel be clockwise transmission, to take turns axle be that the unilateral bearing of counterclockwise transmission is engaged in first transmission shaft; Big driving gear with axle to wheel be clockwise transmission, to take turns axle be that the unilateral bearing of counterclockwise transmission is engaged in second transmission shaft.
Because the utility model power source, the transmission shaft that is connected with power source, the power output unit that is mounted on the driving wheel group on the transmission shaft and engages with wheel; Transmission shaft comprises first and second parallel transmission shaft and is vertical configuration and is mounted on I and II driving wheel group on first and second transmission shaft; The transmission component of I and II driving wheel group is engaged on first and second transmission shaft with unilateral bearing.The clockwise and anticlockwise of mat motor and unilateral bearing just can reach the speed change transmission as the switching of power transfer path during use, and structure is much simpler than reducing gear complicated in traditional gearbox.Not only simple in structure, cost is low, easy to operate, and save the energy, thereby reach the purpose of this utility model.
Fig. 1, be the utility model embodiment one structural representation plan view.
Fig. 2, be the utility model embodiment one structural representation front view.
Fig. 3, be the utility model embodiment two structural representation plan views.
Fig. 4, be the utility model embodiment two structural representation front views.
Fig. 5, be the utility model embodiment three structural representation plan views.
Fig. 6, be A-A sectional view among Fig. 5.
Fig. 7, be B-B sectional view among Fig. 5.
Fig. 8, be the utility model embodiment four structural representation plan views.
Fig. 9, be C-C sectional view among Fig. 8.
Figure 10, be D-D sectional view in 8 among the figure.
Figure 11, be the utility model embodiment five structural representation plan views.
Figure 12, be the utility model embodiment five structural representation front views.
Figure 13, be the utility model embodiment six structural representation plan views.
Figure 14, be the utility model embodiment six structural representation front views.
Figure 15, be the utility model embodiment seven structural representation plan views.
Figure 16, be the utility model embodiment seven structural representation front views.
Figure 17, be E-E sectional view among Figure 15.
Figure 18, be the utility model embodiment eight structural representation plan views.
Figure 19, be the utility model embodiment eight structural representation front views.
Figure 20, be F-F sectional view in 18 among the figure.
Figure 21, be the utility model embodiment nine structural representation plan views.
Figure 22, be G-G sectional view among Figure 21.
Figure 23, be H-H sectional view among Figure 21.
Figure 24, be the utility model embodiment ten structural representation plan views.
Figure 24, be J-J sectional view among Figure 24.
Figure 26, be K-K sectional view among Figure 24.
Engaging accompanying drawing below further elaborates the utility model.
Embodiment one
As shown in Figure 1 and Figure 2, the utility model comprises motor 1M1, master, involuntary speed reduction gear 1G1,1G2, parallel first and second transmission shaft 1S1,1S2 and I and II Transmitted chains wheels 1A, the 1B of vertical configuration device on first and second transmission shaft 1S1,1S2.
Initiatively reduction gear 1G1 is fixed on the motor 1N1 output shaft; Involuntary speed reduction gear 1G2 is fixed in 1S1 on first transmission shaft.
First grade transmission chain wheels 1A comprise identical modulus the master, by movable sprocket 1A1,1A2 and connect main, by the chain 1H1 of movable sprocket 1A1,1A2.
Drive sprocket 1A1 is engaged on the first transmission shaft 1S1, and adorns one group in junction point and see that toward motor 1M1 axle is the unilateral bearing 1A11 of counterclockwise transmission for clockwise transmission, wheel to axle to wheel by motor 1M1 output shaft direction.
Be engaged on the second transmission shaft 1S1 by movable sprocket 1A2, and to adorn one group of axle in junction point be the unilateral bearing 1A21 of clockwise transmission for contrary pin transmission, wheel to axle to wheel.
Second grade transmission chain wheels 1B comprises the master of identical modulus, by movable sprocket 1B1,1B2, power output sprocket 1B3 and connect drive sprocket 1B1, by the chain 1H2 of movable sprocket 1B2, power output sprocket 1B3.
Drive sprocket 1B1 is engaged on the first transmission shaft 1S1, and to adorn one group of axle in junction point be the unilateral bearing 1B11 of clockwise transmission for contrary pin transmission, wheel to axle to wheel.
Be engaged on the second transmission shaft 1S2 by movable sprocket 1B2, and to adorn one group of axle in junction point be the unilateral bearing 1B21 of counterclockwise transmission for clockwise transmission, wheel to axle to wheel.
Power output sprocket 1B3 engages with the wheel 1W of electric carrier.
Drive sprocket 1B1 places the chain 1H2 outside, so that drive sprocket 1B1 is with opposite by the sense of rotation of movable sprocket 1B2 and power output sprocket 1B3.
During transmission, motor 1M1 through first or two drive path with transmission of power to power output sprocket 1B3 that the wheel 1W of electric carrier engages on.
First kind of drive path; As shown in Figure 2, see toward motor 1M1 direction by motor 1M1 output shaft.Motor 1M1 output shaft clockwise rotates, and drive active reduction gear 1G1 clockwise rotates; Drive involuntary speed reduction gear 1G2 again and the first transmission shaft 1S1 rotates counterclockwise; Because of the drive sprocket 1A1 of first grade transmission chain wheels 1A is engaged on the first transmission shaft 1S1 for the unilateral bearing 1A11 of clockwise transmission wheel with axle, so the drive sprocket 1A1 of first grade transmission chain wheels 1A can not rotate with the first transmission shaft 1S1; Because of the drive sprocket 1B1 of second grade transmission chain wheels 1B is engaged on the first transmission shaft 1S1 for the unilateral bearing 1B11 of counterclockwise transmission wheel with axle, so the drive sprocket 1B1 of second grade transmission chain wheels 1B rotates counterclockwise with the first transmission shaft 1S1, and place the chain 1H2 outside because of the drive sprocket 1B1 of second grade transmission chain wheels 1B, so it drives chain 1H2, is clockwise rotated by movable sprocket 1B2 and the power output sprocket 1B3 that engages with the wheel 1W of electric carrier, clockwise rotate and advance with drive wheel 1W; Second grade transmission chain wheels 1B's is that the unilateral bearing 1B21 of counterclockwise transmission be engaged in second transmission shaft 1S2 on wheel to axle by movable sprocket 1B2, so the second transmission shaft 1S2 can not rotated by movable sprocket 1B2 with second grade transmission chain wheels 1B.Promptly first kind of drive path is the kind of drive without the second transmission shaft 1S2, and its drive path is the second grade transmission chain wheels 1B power output sprocket 1B3 of the chain 1H2 → clockwise rotate of the second grade transmission chain wheels 1B drive sprocket 1B1 → clockwise rotate of the first transmission shaft 1S1 → rotate counterclockwise of the involuntary speed reduction gear 1G2 → rotate counterclockwise of the active reduction gear 1G1 → rotate counterclockwise of the motor 1M1 output shaft that clockwise rotates → clockwise rotate.Its reduction speed ratio is an involuntary speed reduction gear 1G2 tooth number Z
G2With active reduction gear 1G1 tooth number Z
G1Power output sprocket 1B3 tooth number Z when
B3With second grade transmission chain wheels 1B drive sprocket 1B1 tooth number Z
B1Than sum, i.e. I=(Z
G2/ Z
G1) * (Z
B3/ Z
B1).
Second kind of drive path; See toward motor 1M1 direction by motor 1M1 output shaft.Motor 1M1 output shaft rotates counterclockwise, and drive active reduction gear 1G1 rotates counterclockwise; Drive involuntary speed reduction gear 1G2 again and the first transmission shaft 1S1 clockwise rotates; Because of the drive sprocket 1A1 of first grade transmission chain wheels 1A is engaged on the first transmission shaft 1S1 for the unilateral bearing 1A11 of clockwise transmission wheel with axle, so the drive sprocket 1A1 of first grade transmission chain wheels 1A clockwise rotates with the first transmission shaft 1S1, and drive chain 1H1 and clockwise rotated by movable sprocket 1A2; Because of the drive sprocket 1B1 of second grade transmission chain wheels 1B is engaged on the first transmission shaft 1S1 for the unilateral bearing 1B11 of counterclockwise transmission wheel with axle, so the drive sprocket 1B1 of second grade transmission chain wheels 1B can not rotate with the first transmission shaft 1S1; First grade transmission chain wheels 1A's is that the unilateral bearing 1A21 of clockwise transmission be engaged in second transmission shaft 1S2 on wheel to axle by movable sprocket 1A2, so the drive second transmission shaft 1S2 clockwise rotates; Because of with axle wheel being engaged on the second transmission shaft 1S2 for the unilateral bearing 1B21 of clockwise transmission of second grade transmission chain wheels 1B by movable sprocket 1B2, so second grade transmission chain wheels 1B is clockwise rotated with the second transmission shaft 1S2 by movable sprocket 1B2, and drive chain 1H2 and the power output sprocket 1B3 that engages with the wheel 1W of electric carrier clockwise rotates, clockwise rotate and advance with drive wheel 1W; The drive sprocket 1B1 of second grade transmission chain wheels 1B is that the unilateral bearing 1B11 of clockwise transmission is engaged on the first transmission shaft 1S1 with wheel to axle; So the relative first transmission shaft 1S1 of the drive sprocket 1B1 of second grade transmission chain wheels 1B dallies counterclockwise. to be the second drive path be kind of drive through second driving shaft 1S2, its drive path be the first grade transmission chain wheels 1A of chain 1H1 → clockwise rotate of the first grade transmission chain wheels 1A drive sprocket 1A1 → clockwise rotate of the first power transmission shaft 1S1 → clockwise rotate of the involuntary speed reduction gear 1G2 → clockwise rotate of the active reduction gearing 1G1 → clockwise rotate of the motor 1M1 output shaft that rotates counterclockwise → rotate counterclockwise by the secondary transmission chain wheel set 1B of the second driving shaft 1S2 of movable sprocket 1A1 → clockwise rotate → clockwise rotate by the secondary transmission chain wheel set 1B power output sprocket 1B3 of the chain 1H2 of movable sprocket 1B2 → clockwise rotate → clockwise rotate. Its reduction speed ratio is an involuntary speed reduction gear 1G2 tooth number ZG2With active reduction gear 1G1 tooth number Z
G1Ratio, first grade transmission chain wheels 1A are by movable sprocket 1A2 tooth number Z
A2With drive sprocket 1A1 tooth number Z
A1Power output sprocket 1B3 tooth number Z when
B3With the passive teeth number of sprocket Z of second grade transmission chain wheels 1B
B2Than sum, i.e. I=(Z
G2/ Z
G1) * (Z
A2/ Z
A1) * (Z
B3/ Z
B2).
Promptly work as Z
A2＞Z
A1The time, second kind of drive path Duoed first grade transmission chain wheels reduction speed ratio Z than first kind of drive path
A2/ Z
A1, and if Z
B2＜Z
B1The time, then can obtain bigger reduction speed ratio, with the drive path when dealing with electric carrier and need high moment of torsion.
From the above mentioned, only the clockwise and anticlockwise of mat motor and four groups of unilateral bearings just can reach two sections speed change transmissions as the switching of power transfer path to the utility model.
When electric carrier during from static startup, need bigger moment of torsion output for overcoming maximum static friction force, so the time, the utility model makes motor rotate counterclockwise, make it have second kind of drive path wheels, start with bigger torque drive electric carrier than the big retarding ratio.
Behind the electric carrier setting in motion, speed slowly increases, when motor speed is more and more high, before the height point that leaves the optimum efficiency district, control system Schilling motor stops, make motor rotate in a clockwise direction again,, wheel is advanced with high rotational speed to have first kind of drive path wheels of less deceleration warp.
In like manner, when electric carrier runs into toward upslope, speed is not enough slack-off because of moment of torsion, before electric carrier does not stop, control system Schilling motor stops, and makes motor counterclockwise to rotate, to have second kind of drive path wheels than the big retarding ratio again, can run over the abrupt slope with bigger torque drive electric carrier, electric carrier is advanced smoothly.So when the utility model is applied on the electric carrier, can cooperate circuit control, faradic output value in motor optimum efficiency district, changes the forward and backward of motor in good time, to cooperate the road conditions demand and to reach the purpose of saving the energy.
The utility model cooperates the ingenious arrangement of motor forward and backward by four groups of unilateral bearings, the switching of carrying out power transfer path is reaching the purpose of speed change transmission, so the utmost point is suitable for use on the electric carriers such as electric locomotive, electric bicycle, aiding bicycle, electric golf cart and Segway Human Transporter that need not to retreat that only need advance.
In addition, if electric carrier of the present utility model is when placing slope and motor to remain static, produce the active force that slides backward because of centrifugal force, traction wheel 1W and second grade transmission chain wheels 1B power output sprocket 1B3 are when counterclockwise rotating, and the chain 1H2 of the second grade transmission chain wheels 1B through counterclockwise rotating drives the drive sprocket 1B1 of second grade transmission chain wheels 1B and is respectively clockwise and counterclockwise by movable sprocket 1B2 and rotates; And respectively by with wheel to axle serve as clockwise and counterclockwise transmission be engaged in unilateral bearing 1B11,1B21 on first and second transmission shaft 1S1, the 1S2, first and second transmission shaft 1S1,1S2 are clockwise and rotation counterclockwise respectively; Because of the master of first grade transmission chain wheels 1A, by movable sprocket 1A1,1A2 serves as that unilateral bearing 1A11, the 1A21 that reaches counterclockwise transmission clockwise is engaged on first and second transmission shaft 1S1, the 1S2 with axle to wheel respectively, make the master, desired respectively to be clockwise and counterclockwise by movable sprocket 1A1,1A2 and rotate, cause first grade transmission chain wheels 1A to produce locking phenomenon and can't rotate, so when electric carrier placed slope and motor static, the utility model also had the effect that prevents that electric carrier is sliding backward.
Though the auto-lock function of above-mentioned first grade transmission chain wheels 1A and having prevents the effect that electric carrier is sliding backward, when move electric carrier with the manpower desire wheel 1W is retreated when obtaining preferable mobile effect, can make wheel 1W can't retreat because of self-locking.At this moment, between the utility model second grade transmission chain wheels 1B power output sprocket 1B3 and wheel 1W, engage, break away from and be free rotation state so that wheel 1W and the utility model are temporary transient, to separate the problem that must not retreat with simple clutch structure E.
But the utility model embodiment one unilateral bearing transmission direction
| Unilateral bearing | But axle is to the wheel transmission direction | But wheel is to the axle transmission direction |
| 1A11 | Clockwise | Counterclockwise |
| 1A21 | Counterclockwise | Clockwise |
| 1B11 | Counterclockwise | Clockwise |
| 1B21 | Clockwise | Counterclockwise |
Embodiment two
As shown in Figure 3, Figure 4, comprise first and second motor 1M1,1M2, first main, involuntary speed reduction gear 1G1,1G2, second main, driven gear 1G2,3,1G4, parallel first and second transmission shaft 1S1,1S2 and I and II Transmitted chains wheels 1A, the 1B of vertical configuration device on first and second transmission shaft 1S1,1S2.
Initiatively reduction gear 1G1,1G3 are fixed in respectively on first and second motor 1M1, the 1M2 output shaft for first and second; First and second involuntary speed reduction gear 1G2,1G4 are fixed in respectively on first and second transmission shaft 1S1, the 1S2.
First grade transmission chain wheels 1A comprise identical modulus the master, by movable sprocket 1A1,1A2 and connect main, by the chain 1H1 of movable sprocket 1A1,1A2.
Drive sprocket 1A1 is engaged on the first transmission shaft 1S1, and adorns one group in junction point and see that toward motor axle is the unilateral bearing 1A11 of counterclockwise transmission for clockwise transmission, wheel to axle to wheel by the motor output shaft direction.
Be engaged on the second transmission shaft 1S2 by movable sprocket 1A2, and to adorn one group of axle in junction point be the unilateral bearing 1A21 of clockwise transmission for contrary pin transmission, wheel to axle to wheel.
Second grade transmission chain wheels 1B comprises the master of identical modulus, by movable sprocket 1B1,1B2, power output sprocket 1B3 and connect drive sprocket 1B1, by the chain 1H2 of movable sprocket 1B2, power output sprocket 1B3.
Drive sprocket 1B1 is engaged on the first transmission shaft 1S1, and to adorn one group of axle in junction point be the unilateral bearing 1B11 of clockwise transmission for contrary pin transmission, wheel to axle to wheel.
Be engaged on the second transmission shaft 1S2 by movable sprocket 1B2, and to adorn one group of axle in junction point be the unilateral bearing 1B21 of counterclockwise transmission for clockwise transmission, wheel to axle to wheel.
Power output sprocket 1B3 engages with the wheel 1W of electric carrier.
Drive sprocket 1B1 places the chain 1H2 outside, so that drive sprocket 1B1 is with opposite by the sense of rotation of movable sprocket 1B2 and power output sprocket 1B3.
During transmission, can through drive path with transmission of power to power output sprocket 1B3 that the wheel 1W of electric carrier engages on.
First section speed change state
See toward first and second motor 1M1,1M2 direction by first and second motor 1M1,1M2 output shaft.First and second motor 1M1,1M2 output shaft are simultaneously counterclockwise to rotate.
The first motor 1M1 that rotates counterclockwise drives the first active reduction gear 1G1 and rotates counterclockwise; Drive the first involuntary speed reduction gear 1G2 again and the first transmission shaft 1S1 clockwise rotates; Because of the drive sprocket 1A1 of first grade transmission chain wheels 1A is engaged on the first transmission shaft 1S1 for the unilateral bearing 1A11 of clockwise transmission wheel with axle, so the drive sprocket 1A1 of first grade transmission chain wheels 1A clockwise rotates with the first transmission shaft 1S1, and drive chain 1H1 and clockwise rotated by movable sprocket 1A2; Because of first grade transmission chain wheels 1A is that the unilateral bearing 1A21 of clockwise transmission be engaged in second transmission shaft 1S2 on wheel to axle by movable sprocket 1A2, so drive the second transmission shaft 1S2 and then rotation in a clockwise direction; Because of the drive sprocket 1B1 of second grade transmission chain wheels 1B is engaged on the first transmission shaft 1S1 for the unilateral bearing 1B11 of counterclockwise transmission wheel with axle, so the drive sprocket 1B1 of second grade transmission chain wheels 1B can not rotate with the first transmission shaft 1S1; Second grade transmission chain wheels 1B2 is engaged on the second transmission shaft 1S2 for the unilateral bearing 1B21 of clockwise transmission wheel with axle by movable sprocket 1B2, so second grade transmission chain wheels 1B is clockwise rotated with the second transmission shaft 1S2 by movable sprocket 1B2, and drive chain 1H2 and the power output sprocket 1B3 that engages with the wheel 1W of electric carrier clockwise rotates, clockwise rotate and advance with drive wheel 1W.
At this moment, the drive path of the first motor 1M1 be the first motor 1M1 output shaft of rotating counterclockwise → rotate counterclockwise first initiatively the chain 1H1 of the first grade transmission chain wheels 1A drive sprocket 1A1 of the first power transmission shaft 1S1 of the first involuntary speed reduction gear 1G2 of reduction gearing 1G1 → clockwise rotate → clockwise rotate → clockwise rotate → clockwise rotate first grade transmission chain wheels 1A → clockwise rotate first grade transmission chain wheels 1A by the secondary transmission chain wheel set 1B of the second driving shaft 1S2 of movable sprocket 1A2 → clockwise rotate → clockwise rotate by the secondary transmission chain wheel set 1B power output sprocket 1B3 of the chain 1H2 of movable sprocket 1B2 → clockwise rotate secondary transmission chain wheel set 1B → clockwise rotate. Its reduction speed ratio is an one-level involuntary speed reduction gear 1G2 tooth number ZG2With one-level active reduction gear 1G1 tooth number Z
G1Ratio, first grade transmission chain wheels 1A are by movable sprocket 1A2 tooth number Z
A2With drive sprocket 1A1 tooth number Z
A1Power output sprocket 1B3 tooth number Z when
B3With second grade transmission chain wheels 1B by movable sprocket 1B2 tooth number Z
B2Than sum, i.e. I=(Z
G2/ Z
G1) * (Z
A2/ Z
A1) * (Z
B3/ Z
B2).
The second motor 1M2 that rotates counterclockwise drives the second active reduction gear 1G3 and rotates counterclockwise; Drive the second involuntary speed reduction gear 1G4 again and the second transmission shaft 1S2 clockwise rotates; Because of first grade transmission chain wheels 1A serve as that unilateral bearing 1A21 against pin transmission be engaged in second transmission shaft 1S2 on axle to wheel by movable sprocket 1A2, so can not rotated of first grade transmission chain wheels 1 with the second transmission shaft 1S2 by movable sprocket 1A2; Second grade transmission chain wheels 1B is engaged on the second transmission shaft 1S2 for the unilateral bearing 1B21 of clockwise transmission wheel with axle by movable sprocket 1B2, so second grade transmission chain wheels 1B is clockwise rotated with the second transmission shaft 1S2 by movable sprocket 1B2, and drive chain 1H2 and the power output sprocket 1B3 that engages with the wheel 1W of electric carrier clockwise rotates, clockwise rotate and advance to drive wheel 1W, the drive chain 1B1 of second grade transmission chain wheels 1B rotates counterclockwise, because of it is that the unilateral bearing 1B11 of clockwise transmission is engaged on the first transmission shaft 1S1 with wheel to axle, so its relative first transmission shaft 1S1 dallies counterclockwise.
The power transmission path of the second motor 1M2 is the kind of drive without the first transmission shaft 1S1, its drive path be the second motor 1M2 output shaft that rotates counterclockwise → rotate counterclockwise second initiatively the second grade transmission chain wheels 1B of the second transmission shaft 1S2 of the second involuntary speed reduction gear 1G4 of reduction gear 1G3 → clockwise rotate → clockwise rotate → clockwise rotate by the second grade transmission chain wheels 1B power output sprocket 1B3 of the chain 1H2 of movable sprocket 1B2 → clockwise rotate second grade transmission chain wheels 1B → clockwise rotate.Its reduction speed ratio is a secondary involuntary speed reduction gear 1G4 tooth number Z
G4With secondary active reduction gear 1G3 tooth number Z
G3Power output sprocket 1B3 tooth number Z when
B3With second grade transmission chain wheels 1B by movable sprocket 1B2 tooth number Z
B2Than sum, i.e. I=
(Z
g4/Z
g3)×(Z
b3/Z
b2)。
Suppose that the second motor 1M2 is with per minute n
21Rotating speed counterclockwise rotates, and then wheel 1W and power output sprocket 1B3 are in a clockwise direction with per minute n
W2Rotating speed advances, n
21With n
W2Relation be;
n
w2＝n
21{(Z
g4/Z
g3)×(Z
b3/Z
b2)}
Because the first motor 1M1 and the second motor 1M2 drive wheel 1W simultaneously electric carrier is advanced, suppose that the first motor 1M1 is with per minute n
11Rotating speed counterclockwise rotates, and then wheel 1W and power output sprocket 1B3 are in a clockwise direction with per minute n
W1Rotating speed advances, n
W1=n
W2Drill the Shen;
n
11{(Z
g2/Z
g1)×(Z
a2/Z
a1)×(Z
b3/Z
b2)}＝n
21{(Z
g4/Z
g3)×(Z
b3/Z
b2)}
Be reduced to n
11{ (Z
G2/ Z
G1) * (Z
A2/ Z
A1)=n
21(Z
G4/ Z
G3)
If first and second motor 1M1,1M2 are the motor of same characteristic, then n
11=n
21, so, (Z then
G2/ Z
G1) * (Z
A2/ Z
A1)=(Z
G4/ Z
G3), this is the utility model design of gear number distribution criterion.
If ignore gearing friction consumption, first and second motor 1M1,1M2 can share identical load in theory, and promptly first and second motor 1M1,1M2 power can reach superimposed effect, i.e. the function of the utility model tool power merging.
Second section speed change state
Electric carrier starts or on the abrupt slope time, is operated in power that first and second motor 1M1,1M2 all reverse with model utility and merges under the operating mode and turn round; When electric carrier when static startup has begun to advance at a slow speed or use the state that the back gradient slowed down on the abrupt slope, the moment of torsion output demand of wheel 1W reduces, based on the idea of saving electric power, utilize control system that the first motor 1M1 is closed, the second motor 1M2 continues counterclockwise to rotate, to produce second section speed change state, its drive path is that second motor 1M2 drive, the second active reduction gear 1G3 that rotates counterclockwise rotates counterclockwise; Drive the second involuntary speed reduction gear 1G4 again and the second transmission shaft 1S2 clockwise rotates; Because of first grade transmission chain wheels 1A serve as that unilateral bearing 1A21 against pin transmission be engaged in second transmission shaft 1S2 on axle to wheel by movable sprocket 1A2, so can not rotated of first grade transmission chain wheels 1A with the second transmission shaft 1S2 by movable sprocket 1A2; Second grade transmission chain wheels 1B is engaged on the second transmission shaft 1S2 for the unilateral bearing 1B21 of clockwise transmission wheel with axle by movable sprocket 1B2, so second grade transmission chain wheels 1B is clockwise rotated with the second transmission shaft 1S2 by movable sprocket 1B2, and drive chain 1H2 and the power output sprocket 1B3 that engages with the wheel 1W of electric carrier clockwise rotates, clockwise rotate and advance to drive wheel 1W, the drive sprocket 1B1 of second grade transmission chain wheels 1B rotates counterclockwise, because of it is that the unilateral bearing 1B11 of clockwise transmission is engaged on the first transmission shaft 1S1 with wheel to axle, so its relative first transmission shaft 1S1 dallies counterclockwise, can not drive the first transmission shaft 1S1 and rotate.Therefore, the second motor 1M2 power transmission path be the second motor 1M2 output shaft that rotates counterclockwise → rotate counterclockwise second initiatively the second grade transmission chain wheels 1B of the second transmission shaft 1S2 of the second involuntary speed reduction gear 1G4 of reduction gear 1G3 → clockwise rotate → clockwise rotate → clockwise rotate by the second grade transmission chain wheels 1B power output sprocket 1B3 of the chain 1H2 of movable sprocket 1B2 → clockwise rotate second grade transmission chain wheels 1B → clockwise rotate.Its reduction speed ratio is a secondary involuntary speed reduction gear 1G4 tooth number Z
G4With secondary active reduction gear 1G3 tooth number Z
G3Power output sprocket 1B3 tooth number Z when
B3With second grade transmission chain wheels 1B by movable sprocket 1B2 tooth number Z
B2Than sum, i.e. I=(Z
G4/ Z
G3) * (Z
B3/ Z
B2).
The 3rd section speed change state
When if the electric carrier operator desires to quicken again, the second motor 1M2 is continued with running counterclockwise, and make the first motor 1M1 start from static the beginning in a clockwise direction, its drive path clockwise rotates for (being seen toward the first motor 1M1 by the first motor 1M1 output shaft direction) first motor 1M1 output shaft, and drive first initiatively reduction gear 1G1 clockwise rotate; Drive the first involuntary speed reduction gear 1G2 again and the first transmission shaft 1S1 rotates counterclockwise; Because of the drive sprocket 1A1 of first grade transmission chain wheels 1A is engaged on the first transmission shaft 1S1 for the unilateral bearing 1A11 of clockwise transmission wheel with axle, so the drive sprocket 1A1 of first grade transmission chain wheels 1A can not rotate with the first transmission shaft 1S1; Because of the drive sprocket 1B1 of second grade transmission chain wheels 1B is engaged on the first transmission shaft 1S1 for the unilateral bearing 1B11 of counterclockwise transmission wheel with axle, so the drive sprocket 1B1 of second grade transmission chain wheels 1B rotates counterclockwise with the first transmission shaft 1S1, and place the chain 1H2 outside because of secondary drive sprocket 1B1, so it drives chain 1H2, is clockwise rotated by movable sprocket 1B2 and the power output sprocket 1B3 that engages with the wheel 1W of electric carrier, clockwise rotate and advance with drive wheel 1W.Its drive path is the first second grade transmission chain wheels 1B power output sprocket 1B3 of the chain 1H2 of the second grade transmission chain wheels 1B drive sprocket 1B1 of the first transmission shaft 1S1 of the first involuntary speed reduction gear 1G2 of reduction gear 1G1 → rotate counterclockwise → rotate counterclockwise → rotate counterclockwise → clockwise rotate → clockwise rotate initiatively of the first motor 1M1 output shaft that clockwise rotates → clockwise rotate.Its reduction speed ratio is the first involuntary speed reduction gear tooth number Z
G2With the first active reduction gear tooth number Z
G1Power output sprocket tooth number Z when
B3With second grade transmission chain wheels drive sprocket tooth number Z
B1Than sum, i.e. I=(Z
G2/ Z
G1) * (Z
B3/ Z
B1).
At this moment, the second motor 1M2 advances with higher reduction speed ratio wheels 1W, and the first motor 1M1 advances with low reduction speed ratio wheels 1W, obtains the 3rd section speed change situation.
The 4th section speed change state
When the first motor 1M1 drives to incorporate into than the low speed ratio, wheel 1W motion speed is more and more fast, the load reduction of the second motor 1M2 is to not meeting efficient when output, the second motor 1M2 shuts down, and the first motor 1M1 continues to rotate through clockwise direction, obtain the 4th section speed change state, continue wheels 1W and advance.
The 5th section speed change state
When electric carrier is want to advance with more speed, make the second motor 1M2 start from static the beginning in a clockwise direction, its drive path is that the second motor 1M2 output shaft clockwise rotates, and drive second initiatively reduction gear 1G3 clockwise rotate; Drive the second involuntary speed reduction gear 1G4 again and the second transmission shaft 1S2 rotates counterclockwise; Because of with axle wheel being engaged on the second transmission shaft 1S2 for the unilateral bearing 1A21 of counterclockwise transmission of first grade transmission chain wheels 1A by movable sprocket 1A2, so first grade transmission chain wheels 1A is rotated counterclockwise with the second transmission shaft 1S2 by movable sprocket 1A2, and drive chain 1H1 rotates counterclockwise; Because of the drive sprocket 1A1 of first grade transmission chain wheels 1A is that the unilateral bearing 1A11 of counterclockwise transmission is engaged on the first transmission shaft 1S1 with wheel to axle,, the drive sprocket 1A1 of first grade transmission chain wheels 1A rotates counterclockwise so driving the first transmission shaft 1S1; The drive sprocket 1B1 of second grade transmission chain wheels 1B serve as that unilateral bearing 1B11 against the pin transmission is engaged on the first transmission shaft 1S1 with axle to wheel, so the drive sprocket 1B1 of second grade transmission chain wheels 1B rotates counterclockwise with the first transmission shaft 1S1; And place the chain 1H2 outside because of the drive sprocket 1B1 of second grade transmission chain wheels 1B; So it drives chain 1H2; Is clockwise rotated by movable sprocket 1B2 and the power output sprocket 1B3 that engages with the wheel 1W of electric carrier, its drive path of clockwise rotate and advance with drive wheel 1W. be the second motor 1M2 output shaft of clockwise rotating → clockwise rotate second initiatively the first grade transmission chain wheels 1A of the second driving shaft 1S2 of the second involuntary speed reduction gear 1G4 of reduction gearing 1G3 → rotate counterclockwise → rotate counterclockwise → rotate counterclockwise by the secondary transmission chain wheel set 1B power output sprocket 1B3 of the chain 1H2 of the secondary transmission chain wheel set 1B drive sprocket 1B1 of the first power transmission shaft 1S1 of the chain 1H1 of the first grade transmission chain wheels 1A of movable sprocket 1A1 → rotate counterclockwise and drive sprocket 1A1 → rotate counterclockwise → rotate counterclockwise → clockwise rotate → clockwise rotate. Its reduction speed ratio is the second involuntary speed reduction gear 1G4 tooth number ZG4With the second active reduction gear 1G3 tooth number Z
G3Ratio, first grade transmission chain wheels 1A are by movable sprocket 1A2 tooth number Z
A2With drive sprocket 1A1 tooth number Z
A1And power output sprocket 1B3 tooth number Z
B3With second grade transmission chain wheels 1B drive sprocket 1B1 tooth number Z
B1Than sum, i.e. I=(Z
G4/ Z
G3) * (Z
A2/ Z
A1) * (Z
B3/ Z
B1).
Meanwhile, the first motor 1M1 still rotates in a clockwise direction, at this moment, is seen toward the first motor 1M1 by the first motor 1M1 output shaft direction.The first motor 1M1 output shaft clockwise rotates, and drive first initiatively reduction gear 1G1 clockwise rotate; Drive the first involuntary speed reduction gear 1G2 again and the first transmission shaft 1S1 rotates counterclockwise; Because of the drive sprocket 1A1 of first grade transmission chain wheels 1A is engaged on the first transmission shaft 1S1 for the unilateral bearing 1A11 of clockwise transmission wheel with axle, so the drive sprocket 1A1 of first grade transmission chain wheels 1A can not rotate with the first transmission shaft 1S1; Because of the drive sprocket 1B1 of second grade transmission chain wheels 1B is engaged on the first transmission shaft 1S1 for the unilateral bearing 1B11 of counterclockwise transmission wheel with axle, so the drive sprocket 1B1 of second grade transmission chain wheels 1B rotates counterclockwise with the first transmission shaft 1S1, and place the chain 1H2 outside because of second grade transmission chain wheels 1B drive sprocket 1B1, so it drives chain 1H2 and the power output sprocket 1B3 that engages with the wheel 1W of electric carrier clockwise rotates, clockwise rotate and advance with drive wheel 1W.Its drive path is the first second grade transmission chain wheels 1B power output sprocket 1B3 of the chain 1H2 of the second grade transmission chain wheels 1B drive sprocket 1B1 of the first transmission shaft 1S1 of the first involuntary speed reduction gear 1G2 of reduction gear 1G1 → rotate counterclockwise → rotate counterclockwise → rotate counterclockwise → clockwise rotate → clockwise rotate initiatively of the first motor 1M1 output shaft that clockwise rotates → clockwise rotate.Its reduction speed ratio is the first involuntary speed reduction gear 1G2 tooth number Z
G2With the first active reduction gear 1G1 tooth number Z
G1Power output sprocket 1B3 tooth number Z when
B3With second grade transmission chain wheels 1B drive sprocket 1B1 tooth number Z
B1Than sum, i.e. I=(Z
G2/ Z
G1) * (Z
B3/ Z
B1).The kinetic current of first and second motor 1M1,1M2 all compiles via the first transmission shaft 1S1 at this moment, the second grade transmission chain wheels 1B power output sprocket 1B3 of the chain 1H2 of second grade transmission chain wheels 1B drive sprocket 1B1 through rotating counterclockwise → clockwise rotate → clockwise rotate again, wheels 1W advances.
Therefore, if the load of electric carrier immobilizes, start first and second motor 1M1,1M2, on average share on first and second motor 1M1,1M2 with the load that low reduction speed ratio fast driving electric carrier advances, the load that acts on first and second motor 1M1, the 1M2 is reduced by half, the characteristic of mat direct current generator, load reduces under identical voltage, and speed then improves.
From the above mentioned, the utility model with first and second motor of simple circuit control 1M1,1M2 respectively the forward, reverse or stop mode of ending one of them motor drive and be engaged in sprocket wheel 1A1,1B1,1A2,1B2 on first and second transmission shaft 1S1, the 1S2 with four groups of unilateral bearing 1A11,1B11,1A21,1B21, just can reach the effect that five sections speed changes and power merge, much simpler than reducing gear complicated in traditional gearbox.
When electric carrier placed on the acclivity, motor is state of rest and do not have brake, carrier still had the function that can not glide by the utility model self-locking action.Its self-lock mechanism is; When wheel 1W produces the active force that slides backward because of centrifugal force, when desire traction power output sprocket 1B3 counterclockwise rotates, drive drive sprocket 1B1 and be clockwise respectively and rotation counterclockwise through chain 1H2 by movable sprocket 1B2, at this moment, because of the drive sprocket 1B1 of second grade transmission chain wheels 1B and by movable sprocket 1B2 serves as to be engaged on first and second transmission shaft 1S1, the 1S2 along the unilateral bearing 1B11, the 1B21 that reach counterclockwise transmission with wheel to axle respectively, makes first and second transmission shaft 1S1,1S2 respectively to rotate clockwise and counterclockwise; Because of the master of first grade transmission chain wheels 1A, by movable sprocket 1A1,1A2 serves as to be engaged on first and second transmission shaft 1S1, the 1S2 along the unilateral bearing 1A11, the 1A21 that reach counterclockwise transmission with axle to wheel respectively, make first grade transmission chain wheels 1A the master, by movable sprocket 1A1,1A2 respectively with difference rotate to suitable, counterclockwise rotate, make first grade transmission chain wheels 1A produce locking phenomenon and can't rotate, so when electric carrier places slope and motor static, can prevent the effect that electric carrier is sliding backward.
Though the auto-lock function of above-mentioned first grade transmission chain wheels 1A and having prevents the effect that electric carrier is sliding backward, when move electric carrier with the manpower desire wheel 1W is retreated when obtaining preferable mobile effect, can make wheel 1 can't retreat because of self-locking.At this moment, between the utility model second grade transmission chain wheels 1B power output sprocket 1B3 and wheel 1W, engage, break away from and be free rotation state so that wheel 1W and the utility model are temporary transient, to separate the problem that must not retreat with simple clutch structure 1E.
The utility model embodiment two compares with embodiment one, and both difference is only for having increased by the second motor 1M2 and second main, involuntary speed reduction gear 1G3, the 1G4.That is embodiment one is the better simply kind of drive.When electric carrier needs higher driving force output or during than the transmission system of multistage speed change, only need to install the second motor 1M2 and second main, involuntary speed reduction gear 1G3, the 1G4 on the second transmission shaft 1S2 with the utility model embodiment one additional, just constitute the utility model and implement two.Manufacturing specification, quantity in stock and stock control have so been simplified.
But the utility model embodiment two unilateral bearing transmission direction
| Unilateral bearing | But axle is to the wheel transmission direction | But wheel is to the axle transmission direction |
| 1A11 | Clockwise | Counterclockwise |
| 1A21 | Counterclockwise | Clockwise |
| 1B11 | Counterclockwise | Clockwise |
| 1B21 | Clockwise | Counterclockwise |
The utility model embodiment two motor positive and inverse directions and variable speed relationship table
| Hop count | Motor 1M1 moves direction | Motor 1M2 sense of rotation | |
| 1 | Counterclockwise | Counterclockwise | Start or climb very steep slopes |
| 2 | Stop | Counterclockwise | Climb the gentle slope |
| 3 | Clockwise | Counterclockwise | At a slow speed with the quick switching transitional period |
| 4 | Clockwise | Stop | Load not quite, the battery saving mode that advances fast |
| 5 | Clockwise | Clockwise | Extremely fast advance or load bigger quick forward mode |
Embodiment three
With I and II Transmitted chains wheels 1A, the 1B among I and II driving gear 1C, the 1D group replacement embodiment two of direct engagement.
As Fig. 5, Fig. 6, shown in Figure 7, the utility model comprises first and second motor 1M1,1M2, first main, involuntary speed reduction gear 1G1,1G2, two-stage type second master, involuntary speed reduction gear 1G3,1G4,1G5,1G6, parallel first and second transmission shaft 1S1,1S2, pto 1S3 and vertical configuration device I and II driving gear set 1C, the 1D on first and second transmission shaft 1S1,1S2.
Initiatively reduction gear 1G1,1G3 are fixed in respectively on first and second motor 1M1, the 1M2 output shaft for first and second; First and second involuntary speed reduction gear 1G2,1G6 are fixed in respectively on first and second transmission shaft 1S1, the 1S2.
One-level driving gear set 1C comprise identical modulus but out of mesh two driving gear 1C1,1C2 and simultaneously with the larger-diameter power output gear 1C3 of two driving gear 1C1,1C2 engagement.
One driving gear 1C1 is engaged on the first transmission shaft 1S1, and adorns one group in junction point and see that toward the first motor 1M1 axle is the unilateral bearing 1C11 of clockwise transmission for counterclockwise transmission, wheel to axle to wheel by the first motor 1M1 output shaft direction.
Another driving gear 1C2 is engaged on the second transmission shaft 1S2, and to adorn one group of axle in junction point be the unilateral bearing 1C21 of clockwise transmission for contrary pin transmission, wheel to axle to wheel.
Power output gear 1C3 is engaged in differential mechanism 1F on the pto 1S3 that comprises left and right half 1S31,1S32, and the other end of left and right half 1S31,1S32 engages with the left and right wheel 1W of electric carrier.
Secondary driving gear set 1D comprises identical modulus and intermeshing little, big driving gear 1D1,1D2.
Small transmission gear 1D1 is engaged on the first transmission shaft 1S1, and to adorn one group of axle in junction point be the unilateral bearing 1D11 of counterclockwise transmission for clockwise transmission, wheel to axle to wheel.
Big driving gear 1D2 is engaged on the second transmission shaft 1S2, and to adorn one group of axle in junction point be the unilateral bearing 1D21 of counterclockwise transmission for clockwise transmission, wheel to axle to wheel.
During transmission, can be on left and right half 1S31, the 1S32 of drive path extremely engages transmission of power with the wheel 1W of electric carrier pto 1S3.
First section speed change state
See toward first and second motor 1M1,1M2 direction by first and second motor 1M1,1M2 output shaft.First and second motor 1M1,1M2 output shaft are simultaneously counterclockwise to rotate.
The first motor 1M1 that rotates counterclockwise drives the first active reduction gear 1G1 and rotates counterclockwise; Drive the first involuntary speed reduction gear 1G2 again and the first transmission shaft 1S1 clockwise rotates; Because of the driving gear 1C1 of one-level driving gear set 1C is engaged on the first transmission shaft 1S1 for the unilateral bearing 1C11 of counterclockwise transmission wheel with axle, so driving gear 1C1 can not rotate with the first transmission shaft 1S1.Because of the small transmission gear 1D1 of secondary driving gear set 1D is engaged on the first transmission shaft 1S1 for the unilateral bearing 1D11 of clockwise transmission wheel with axle, so the small transmission gear 1D1 of secondary driving gear set 1D clockwise rotates with the first transmission shaft 1S1, and the big driving gear 1D2 of drive and its engagement rotates counterclockwise; Because of the big driving gear 1D2 of secondary driving gear set 1D is that the unilateral bearing 1D21 of counterclockwise transmission is engaged on the second transmission shaft 1S2 with wheel to axle, so the drive second transmission shaft 1S2 rotates counterclockwise; Because of another driving gear 1C2 of one-level driving gear set 1C serve as that unilateral bearing 1C21 against the pin transmission is engaged on the second transmission shaft 1S2 with axle to wheel, so the second transmission shaft 1S2 drives this driving gear 1C2 and rotates counterclockwise, and the rotation of the power output gear 1C3 clockwise direction of drive and its engagement, 1W advances with wheels.
At this moment, the power transmission path of the first motor 1M1 is first another driving gear 1C2 of the one-level driving gear set 1 of the second transmission shaft 1S2 of the secondary driving gear set 1D small transmission gear 1D1 of the first transmission shaft 1S1 of the first involuntary speed reduction gear 1G2 of reduction gear 1G1 → clockwise rotate → clockwise rotate → clockwise rotate → the rotate counterclockwise big driving gear 1D2 of secondary driving gear set 1D → rotate counterclockwise → rotate counterclockwise → clockwise rotate power output gear 1C3 initiatively of the first motor 1M1 output shaft that rotates counterclockwise → rotate counterclockwise.Its reduction speed ratio is the first involuntary speed reduction gear 1G2 tooth number Z
G2With the first active reduction gear 1G1 tooth number Z
G1Ratio, the big driving gear 1D2 of secondary driving gear set 1D tooth number Z
D2With small transmission gear 1D1 tooth number Z
D1Power output gear 1C3 tooth number Z when
C3With another driving gear of one-level driving gear set 1C 1C2 tooth number Z
C2Than sum, i.e. I=(Z
G2/ Z
G1) * (Z
D2/ Z
D1) * (Z
C3/ Z
C2).
The second motor 1M2 that rotates counterclockwise drives two-stage type second master in regular turn, the involuntary speed reduction gear rotates 1G3,1G4,1G5,1G6, rotates counterclockwise to drive the second transmission shaft 1S2; Because of another driving gear 1C2 of one-level driving gear set 1C serve as that the unilateral bearing 1C21 of contrary pin transmission is engaged on the second transmission shaft 1S2 with axle to wheel, so another driving gear 1C2 of second transmission shaft 1S2 drive one-level driving gear 1C rotates counterclockwise; Because of the big driving gear 1D2 of secondary driving gear set 1D is engaged on the second transmission shaft 1S2 for the unilateral bearing 1D21 of clockwise transmission wheel with axle, so the big driving gear 1D2 of secondary driving gear set 1D can not rotate with the second transmission shaft 1S2.When another driving gear of one-level driving gear set 1C 1C2 rotated counterclockwise, the power output gear 1C3 of drive and its engagement rotated in a clockwise direction, and 1W advances with wheels.
At this moment, the power transmission path of the second motor 1M2 is another driving gear 1C2 → clockwise rotate power output gear 1C3 of one-level driving gear set 1C of second motor 1M2 output shaft → two-stage type, second master's that rotates counterclockwise, involuntary speed reduction gear 1G3,1G4,1G5,1G6 → rotate counterclockwise the second transmission shaft 1S2 → rotate counterclockwise.Its reduction speed ratio is two-stage type second, main involuntary speed reduction gear 1G4,1G3,1G6,1G5 tooth number Z
G4, Z
G3, Z
G6, Z
G5Power output gear 1C3 tooth number Z when
C3With another driving gear of one-level driving gear set 1C 1C2 tooth number Z
C2Than sum, i.e. I=((Z
G4/ Z
G3) * (Z
G6/ Z
G5) * (Z
C3/ Z
C2).
Suppose that the second motor 1M2 is with per minute n
21Rotating speed counterclockwise rotates, and then wheel 1W and power output gear 1C3 are in a clockwise direction with per minute n
W2Rotating speed advances, n
21With n
W2Relation be;
n
w2＝n
21{(Z
g4/Z
g3)×(Z
g6/Z
g5)×(Z
c3/Z
c2)}
Because the first motor 1M1 and the second motor 1M2 drive wheel 1W simultaneously electric carrier is advanced, suppose that the first motor 1M1 is with per minute n
11Rotating speed counterclockwise rotates, and then wheel 1W and power output gear 1C3 are in a clockwise direction with per minute n
W1Rotating speed advances, n
W1=n
W2Drill the Shen;
n
11{(Z
g2/Z
g1)×(Z
d2/Z
d1)×(Z
c3/Z
c2)}＝n
21{(Z
g4/Z
g3)×(Z
g6/Z
g5)×(Z
c3/Z
c2)}
Be reduced to n
11{ (Z
G2/ Z
G1) * (Z
D2/ Z
D1)=n
21{ (Z
G4/ Z
G3) * (Z
G6/ Z
G5)
If first and second motor 1M1,1M2 are the motor of same characteristic, then n
11=n
21, so, (Z then
G2/ Z
G1) * (Z
D2/ Z
D1)=(Z
G4/ Z
G3) * (Z
G6/ Z
G5), this is the utility model design of gear number distribution criterion.
If ignore gearing friction consumption, first and second motor 1M1,1M2 can share identical load in theory, and promptly first and second motor 1M1,1M2 power can reach superimposed effect, i.e. the function of the utility model tool power merging.
Second section speed change state
Electric carrier starts or on the abrupt slope time, is operated in power that first and second motor 1M1,1M2 all reverse with model utility and merges under the operating mode and turn round; When electric carrier when static startup has begun to advance at a slow speed or use the state that the back gradient slowed down on the abrupt slope, the moment of torsion output demand of wheel 1W reduces, based on the idea of saving electric power, utilize control system that the first motor 1M1 is closed, the second motor 1M2 continues counterclockwise to rotate, to produce second section speed change state, its drive path is that the second motor 1M2 that rotates counterclockwise drives two-stage type second master, involuntary speed reduction gear 1G3,1G4,1G5,1G6 rotation in regular turn, rotates counterclockwise to drive the second transmission shaft 1S2; Because of another driving gear 1C2 of one-level driving gear set 1C serve as that unilateral bearing 1C21 against the pin transmission is engaged on the second transmission shaft 1S2 with axle to wheel,, the second transmission shaft 1S2 rotates counterclockwise so driving another driving gear 1C2; Because of the big driving gear 1D2 of secondary driving gear set 1D is engaged on the second transmission shaft 1S2 for the unilateral bearing 1D21 of clockwise transmission wheel with axle, so the big driving gear 1D2 of secondary driving gear set 1D can not rotate with the second transmission shaft 1S2.Another driving gear of one-level driving gear set 1C1 1C2 rotates counterclockwise, and the power output gear 1C3 of drive and its engagement rotates in a clockwise direction, and 1W advances with wheels.
At this moment, the power transmission path of the second motor 1M2 is another driving gear 1C2 → clockwise rotate power output gear 1C3 of one-level driving gear set 1C of second motor 1M2 output shaft → two-stage type, second master's that rotates counterclockwise, involuntary speed reduction gear 1G3,1G4,1G5,1G6 → rotate counterclockwise the second transmission shaft 1S2 → rotate counterclockwise.Its reduction speed ratio is two-stage type second, main involuntary speed reduction gear 1G4,1G3,1G6,1G5 tooth number Z
G4, Z
G3, Z
G6, Z
G5And power output gear 1
C3Tooth number Z
C3With another driving gear of one-level driving gear set 1C 1C2 tooth number Z
C2Than sum, i.e. I=((Z
G4/ Z
G3) * (Z
G6/ Z
G5) * (Z
C3/ Z
C2).
The 3rd section speed change state
When if the electric carrier operator desires to quicken again, the second motor 1M2 is continued with running counterclockwise, and make the first motor 1M1 start from static the beginning in a clockwise direction, the drive path of the first motor 1M1 clockwise rotates for (being seen toward first motor by the first motor 1M1 output shaft direction) first motor 1M1 output shaft, and drive first initiatively reduction gear 1G1 clockwise rotate; Drive the first involuntary speed reduction gear 1G2 again and the first transmission shaft 1S1 rotates counterclockwise; Because of the driving gear 1C1 of one-level driving gear set 1C is engaged on the first transmission shaft 1S1 for the unilateral bearing 1C11 of counterclockwise transmission wheel with axle, so driving gear 1C1 rotates counterclockwise with the first transmission shaft 1S1, and drive and the power output gear 1C3 of its engagement rotates in a clockwise direction, 1W advances with wheels.Because of the small transmission gear 1D1 of secondary driving gear set 1D is engaged on the first transmission shaft 1S1 for the unilateral bearing 1D11 of clockwise transmission wheel with axle, so the small transmission gear 1D1 of secondary driving gear set 1D can not rotate with the first transmission shaft 1S1.Though the power output gear 1C3 that another driving gear 1C2 of one-level driving gear set 1C is rotated by the clockwise direction with its engagement drives counterclockwise to rotate, but because of another driving gear 1C2 serve as that the unilateral bearing 1C21 of suitable pin transmission is engaged on the second transmission shaft 1S2 with wheel to axle, so the second transmission shaft 1S2 can not rotate with another driving gear 1C2.Make the first motor 1M1 drive path be transmission without the second transmission shaft 1S2.Its drive path is the first pto 1S3 of the one-level driving gear set 1C driving gear 1C1 of the first transmission shaft 1S1 of the first involuntary speed reduction gear 1G2 of reduction gear 1G1 → rotate counterclockwise → rotate counterclockwise → rotate counterclockwise → clockwise rotate power output gear 1C3 → clockwise rotate initiatively of the first motor 1M1 output shaft that clockwise rotates → clockwise rotate.Its reduction speed ratio is the first involuntary speed reduction gear 1G2 tooth number Z
G2With the first active reduction gear 1G1 tooth number Z
G1Power output gear 1C3 tooth number Z when
C3With one-level driving gear set 1C driving gear 1C1 tooth number Z
C1Than sum, i.e. I=(Z
G2/ Z
G1) * (Z
C3/ Z
C1).
At this moment, the second motor 1M2 advances with higher reduction speed ratio wheels 1W, and the first motor 1M1 advances with low reduction speed ratio wheels 1W, obtains the 3rd section speed change state.
The 4th section speed change state
When the first motor 1M1 drives to incorporate into than the low speed ratio, wheel 1W speed is more and more fast, the load reduction of the second motor 1M2 is to not meeting efficient when output, the second motor 1M2 shuts down, and the first motor 1M1 continues to rotate through clockwise direction, obtain the 4th section speed change state, continue wheels 1W and advance.
Under the 4th section speed change state, the first motor 1M1 still rotates in a clockwise direction, drives the first active reduction gear 1G1 and clockwise rotates; Drive the first involuntary speed reduction gear 1G2 again and the first transmission shaft 1S1 rotates counterclockwise; Because of the driving gear 1C1 of one-level driving gear set 1C is engaged on the first transmission shaft 1S1 for the unilateral bearing 1C11 of counterclockwise transmission wheel with axle, so driving gear 1C1 rotates counterclockwise with the first transmission shaft 1S1, and drive and the power output gear 1C3 of its engagement rotates in a clockwise direction, 1W advances with wheels.Because of the small transmission gear 1D1 of secondary driving gear set 1D is engaged on the first transmission shaft 1S1 for the unilateral bearing 1D11 of clockwise transmission wheel with axle, so the small transmission gear 1D1 of secondary driving gear set 1D can not rotate with the first transmission shaft 1S1.Though the power output gear 1C3 that another driving gear 1C2 of one-level driving gear set 1C is rotated by the clockwise direction with its engagement drives counterclockwise to rotate, but because of another driving gear 1C2 serve as that the unilateral bearing 1C21 of suitable pin transmission is engaged on the second transmission shaft 1S2 with wheel to axle, so the second transmission shaft 1S2 can not rotate with another driving gear 1C2.Make the first motor 1M1 drive path be transmission without the second transmission shaft 1S2.Its drive path is the first pto 1S3 of the one-level driving gear set 1C driving gear 1C1 of the first transmission shaft 1S1 of the first involuntary speed reduction gear 1G2 of reduction gear 1G1 → rotate counterclockwise → rotate counterclockwise → rotate counterclockwise → clockwise rotate power output gear 1C3 → clockwise rotate initiatively of the first motor 1M1 output shaft that clockwise rotates → clockwise rotate.Its reduction speed ratio is the first involuntary speed reduction gear 1G2 tooth number Z
G2With the first active reduction gear 1G1 tooth number Z
G1Power output gear 1C3 tooth number Z when
C3With one-level driving gear set 1C driving gear 1C1 tooth number Z
C1Than sum, i.e. I=(Z
G2/ Z
G1) * (Z
C3/ Z
C1).
The 5th section speed change state
When electric carrier was want to advance with more speed, the first motor 1M1 still rotated in a clockwise direction; The second motor 1M2 starts from static the beginning in a clockwise direction, to enter the 5th section speed change state.The drive path of the second motor 1M2 is that the second motor 1M2 that clockwise rotates drives two-stage type second master, involuntary speed reduction gear 1G3,1G4,1G5,1G6 rotation in regular turn, clockwise rotates to drive the second transmission shaft 1S2; Because of another driving gear 1C2 of one-level driving gear set 1C serve as that unilateral bearing 1C21 against the pin transmission is engaged on the second transmission shaft 1S2 with axle to wheel, so another driving gear of one-level driving gear set 1C 1C2 can not rotate with the second transmission shaft 1S2; Because of the big driving gear 1D2 of secondary driving gear set 1D is engaged on the second transmission shaft 1S2 for the unilateral bearing 1D21 of clockwise transmission wheel with axle, so the big driving gear 1D2 of secondary driving gear set 1D clockwise rotates with the second transmission shaft 1S2, and the small transmission gear 1D1 of the secondary driving gear set 1D of drive and its engagement rotates counterclockwise, because of the small transmission gear 1D1 of secondary driving gear set 1D is that the unilateral bearing 1D11 of counterclockwise transmission engages on the first transmission shaft 1S1 with wheel to axle, so the drive first transmission shaft 1S1 rotates counterclockwise; Because of one-level driving gear set 1C driving gear 1C1 is incorporated on the first transmission shaft 1S1 for the unilateral bearing 1C11 of counterclockwise transmission wheel with axle, so one-level driving gear set 1C driving gear 1C1 rotates counterclockwise with the first transmission shaft 1S1, and drive and the power output gear 1C3 of its engagement rotates in a clockwise direction, 1W advances with wheels.
At this moment, the power transmission path of the second motor 1M2 is the power output gear 1C3 of one-level driving gear set 1C driving gear 1C1 → clockwise rotate of the first transmission shaft 1S1 → rotate counterclockwise of small transmission gear 1D1 → rotate counterclockwise of big driving gear 1D2 → rotate counterclockwise secondary driving gear set 1D of secondary driving gear set 1D of second motor 1M2 output shaft → two-stage type, second master's that clockwise rotates, involuntary speed reduction gear 1G3,1G4,1G5,1G6 → clockwise rotate the second transmission shaft 1S2 → clockwise rotate.Its reduction speed ratio is two-stage type second, main involuntary speed reduction gear 1G4,1G3,1G6,1G5 tooth number Z
G4, Z
G3, Z
G6Z
G5Ratio, the big driving gear 1D2 of secondary driving gear set 1D tooth number Z
D2With small transmission gear 1D1 tooth number Z
D1Power output gear 1C3 tooth number Z when
C3With one-level driving gear set 1C driving gear 1C1 tooth number Z
C1Than sum, i.e. I=((Z
G4/ Z
G3) * (Z
G6/ Z
G5) * (Z
D2/ Z
D1) * (Z
C3/ Z
C1).
This moment, the kinetic current of first and second motor 1M1,1M2 all compiled via the first transmission shaft 1S1, the power output gear 1C3 of the one-level driving gear set 1C driving gear 1C1 through rotating counterclockwise → clockwise rotate again, and wheels 1W advances.
Therefore, if the load of electric carrier immobilizes, start first and second motor 1M1,1M2, on average share on first and second motor 1M1,1M2 with the load that low reduction speed ratio fast driving electric carrier advances, the load that acts on first and second motor 1M1, the 1M2 is reduced by half, the characteristic of mat direct current generator, load reduces under identical voltage, and speed then improves.
From the above mentioned, the utility model embodiment three with first and second motor of simple circuit control 1M1,1M2 respectively the forward, reverse or stop mode of ending one of them motor drive and be engaged in driving gear 1C1, small transmission gear 1D1, another driving gear 1C2, big driving gear 1D2 on first and second transmission shaft 1S1, the 1S2 with four groups of unilateral bearing 1C11,1D11,1C21,1D21, just can reach the effect that five sections speed changes and power merge, identical with the utility model embodiment two functions, much simpler than reducing gear complicated in traditional gearbox.
When electric carrier placed on the acclivity, motor is state of rest and do not have brake, carrier still had the function that can not glide by the utility model self-locking action.Its self-lock mechanism is; When wheel 1W produces the active force that slides backward because of centrifugal force, when desire traction power output gear 1C3 counterclockwise rotates, drive one-level driving gear set 1 liang of driving gear 1C1,1C2 and be the clockwise direction rotation, at this moment, because of two driving gear 1C1, the 1C2 of one-level driving gear set 1C are that unilateral bearing 1C11, the 1C21 of clockwise transmission is engaged in respectively on first and second transmission shaft 1S1, the 1S2 with wheel to axle all, one, two transmission shaft 1S1,1S2 are rotated all in a clockwise direction; Because of little, big driving gear 1D1, the 1D2 of secondary driving gear set 1D all are engaged on first and second transmission shaft 1S1, the 1S2 for unilateral bearing 1D11, the 1D21 of clockwise transmission wheel with axle, little, big driving gear 1D1,1D2 that secondary driving gear set 1D is meshed rotate in a clockwise direction, thereby make secondary driving gear set 1D produce locking phenomenon and can't rotate, so when electric carrier places slope and motor static, can prevent the effect that electric carrier is sliding backward.
Though the auto-lock function of above-mentioned secondary driving gear set and having prevents the effect that electric carrier is sliding backward, when move electric carrier with the manpower desire wheel 1W is retreated when obtaining preferable mobile effect, can make wheel 1W can't retreat because of self-locking.At this moment, between the left half axle 1S31 of the utility model pto 1S3 or right axle shaft 1S32 and wheel 1W, engage with simple clutch structure 1E, break away from and be free rotation state so that wheel 1W and left half axle 1S31 or right axle shaft 1S32 are temporary transient, to separate the problem that must not retreat.
But embodiment's three unilateral bearing transmission direction
Embodiment's three motor positive and inverse directions and variable speed relationship table
| Unilateral bearing | But axle is to the wheel transmission direction | But wheel is to the axle transmission direction |
| 1C11 | Counterclockwise | Clockwise |
| 1C21 | Counterclockwise | Clockwise |
| 1D11 | Clockwise | Counterclockwise |
| 1D21 | Clockwise | Counterclockwise |
| Hop count | Motor 1M1 sense of rotation | Motor 1M2 sense of rotation | |
| 1 | Counterclockwise | Counterclockwise | Start or climb very steep slopes |
| 2 | Stop | Counterclockwise | Climb the gentle slope |
| 3 | Clockwise | Counterclockwise | At a slow speed with the quick switching transitional period |
| 4 | Clockwise | Stop | Load not quite, the battery saving mode that advances fast |
| 5 | Clockwise | Clockwise | Extremely fast advance or load bigger quick forward mode |
Embodiment four
Also the utility model embodiment three gear-driven modes can be mounted on the transmission system of the single motor only of similar embodiment one.As Fig. 8, Fig. 9, shown in Figure 10, second motor in pulling down embodiment three and two-stage type second main, the involuntary speed reduction gear is just constitute the simple kind of drive that single motor gear drives
Embodiment four.
Be set at the transmission system of lower-order when electric carrier, promptly do not need than high-drive torque lubricating output or during than the transmission system of multistage speed change, as long as pull down the second motor 1M2 among the embodiment three and two-stage type second master, involuntary speed reduction gear 1G3,1G4,1G5,1G6, make it possess two sections speed changes, make the utility model simplify manufacturing specification, quantity in stock and stock control.
Take a broad view of above four kinds of embodiments, its common trait is to have parallel first and second transmission shaft 1S1,1S2 and is vertical configuration assembling I and II driving wheel group 1A, 1B (or 1C, 1D) thereon; I and II driving wheel group 1A, 1B (or 1C, 1D) comprise respectively more than two respectively with unilateral bearing 1A11,1B11,1A21,1B21 (or 1C11,1D11,1C21,1D21) and are engaged in transmission component 1A1,1B1 on first and second transmission shaft 1S1, the 1S2,1A2,1B2 (or 1C1,1D1,1C2,1D2); Have a transmission shaft rear end among first and second transmission shaft 1S1, the 1S2 at least and be connected for the motor of power source.The main kind of drive of total system cooperates unilateral bearing to switch power transmission path and to merge power for the forward, reverse or stop of control motor end.Wherein driving wheel group is advised the belt transmission wheels in the time of also can utilizing except making up for Transmitted chains wheels, driving gear set mode.
In conjunction with following table to being described to each embodiment of the utility model that derives shown in Figure 26 as Figure 11.
| The type body | The motor number | The one-level driving wheel group | The stage transmission wheel group | The output gear unit | The speed change hop count | Corresponding diagram | ||
| One | 1 | Sprocket wheel 1A1 | Sprocket wheel 1A2 | Sprocket wheel 1B1 | Sprocket wheel 1B2 | Power output sprocket 1B3 | 2 | 1 2 |
| The unilateral bearing that axle can drive clockwise to wheel | The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive clockwise to wheel | |||||
| Two | 2 | Sprocket wheel 1A1 | Sprocket wheel 1A2 | Sprocket wheel 1B1 | Sprocket wheel 1B2 | Sprocket wheel 1B3 | 5 | 3 4 |
| The unilateral bearing that axle can drive clockwise to wheel | The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive clockwise to wheel | |||||
| Three | 2 | Gear 1C1 | Gear 1C2 | Gear 1D1 | Gear 1D2 | Gear 1C3 | 5 | 5 6 7 |
| The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive clockwise to wheel | The unilateral bearing that axle can drive clockwise to wheel | |||||
| Four | 1 | Gear 1C1 | Gear 1C2 | Gear 1D1 | Gear 1D2 | Gear 1C3 | 2 | 8 9 10 |
| The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive clockwise to wheel | The unilateral bearing that axle can drive clockwise to wheel | |||||
| Five | 2 | Belt pulley | Belt pulley | Sprocket wheel 1B1 | Sprocket wheel 1B2 | Sprocket wheel 1B3 | 5 | 1 2 |
| The unilateral bearing that axle can drive clockwise to wheel | The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive clockwise to wheel | |||||
| Six | 1 | Belt pulley | Belt pulley | Sprocket wheel 1B1 | Sprocket wheel 1B2 | Sprocket wheel 1B3 | 2 | 3 4 |
| The unilateral bearing that axle can drive clockwise to wheel | The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive clockwise to wheel | |||||
| The type body | The motor number | The one-level driving wheel group | The stage transmission wheel group | The output gear unit | The speed change hop count | Corresponding diagram | |||
| Seven | 2 | Gear 1C1 | Gear 1C2 | Sprocket wheel 1B1 | Sprocket wheel 1B2 | Sprocket wheel 1B3 | 5 | 11 12 | |
| The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive clockwise to wheel | The unilateral bearing that axle can drive clockwise to wheel | ||||||
| Eight | 1 | Gear 1C1 | Gear 1C2 | Sprocket wheel 1B1 | Sprocket wheel 1B2 | Sprocket wheel 1B3 | 2 | 13 14 | |
| The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive clockwise to wheel | The unilateral bearing that axle can drive clockwise to wheel | ||||||
| Nine | 2 | Gear 1C1 | Gear 1C2 | Idle pulley 1C4 | Sprocket wheel 1B1 | Sprocket wheel 1B2 | Sprocket wheel 1B3 | 5 | 15 16 17 |
| The unilateral bearing that axle can drive clockwise to wheel | The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive clockwise to wheel | ||||||
| Ten | 1 | Gear 1C1 | Gear 1C2 | Idle pulley 1C4 | Sprocket wheel 1B1 | Sprocket wheel 1B2 | Sprocket wheel 1B3 | 2 | 18 19 20 |
| The unilateral bearing that axle can drive clockwise to wheel | The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive clockwise to wheel | ||||||
| 11 | 2 | Gear 1C1 | Gear 1C2 | Gear 1D1 | Gear 1D2 | Gear 1C3+ sprocket wheel 1B0+ sprocket wheel 1B3 | 5 | 21 22 23 | |
| The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive clockwise to wheel | The unilateral bearing that axle can drive clockwise to wheel | ||||||
| 12 | 1 | Gear 1C1 | Gear 1C2 | Gear 1D1 | Gear 2D2 | Gear 1C3+ sprocket wheel 1B0+ sprocket wheel 1B3 | 2 | 24 25 26 | |
| The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive counterclockwise to wheel | The unilateral bearing that axle can drive clockwise to wheel | The unilateral bearing that axle can drive clockwise to wheel | ||||||
Claims (11)
1, a kind of drive mechanism of electric carrier, the power output unit that it comprises power source, the transmission shaft that is connected with power source, is mounted on the driving wheel group on the transmission shaft and engages with wheel; It is characterized in that described transmission shaft comprises first and second parallel transmission shaft and is vertical configuration is mounted on I and II driving wheel group on first and second transmission shaft; The transmission component of I and II driving wheel group is engaged on first and second transmission shaft with unilateral bearing.
2, drive mechanism of electric carrier according to claim 1 is characterized in that described power source is a motor that is engaged on one of first and second transmission shaft.
3, drive mechanism of electric carrier according to claim 1 is characterized in that described power source comprises first and second motor that is engaged in respectively on first and second transmission shaft.
4, drive mechanism of electric carrier according to claim 1 is characterized in that described driving wheel group is made up of plural transmission component.
5,, it is characterized in that described transmission component is sprocket wheel and chain according to claim 1 or 4 described drive mechanism of electric carrier.
6,, it is characterized in that described transmission component is belt pulley and belt according to claim 1 or 4 described drive mechanism of electric carrier.
7,, it is characterized in that described transmission component is a gear according to claim 1 or 4 described drive mechanism of electric carrier.
8, drive mechanism of electric carrier according to claim 1 is characterized in that being provided with clutch structure between described power output element and the wheel.
9, drive mechanism of electric carrier according to claim 1 is characterized in that being provided with differential mechanism between described first and second parallel transmission shaft.
10, drive mechanism of electric carrier according to claim 1 is characterized in that described I and II driving wheel group is I and II Transmitted chains wheels; The first grade transmission chain wheels comprise the master of identical modulus,, passive sprocket wheel chain main by movable sprocket and connection; Drive sprocket with axle to wheel be clockwise transmission, to take turns axle be that the unilateral bearing of counterclockwise transmission is engaged in first transmission shaft; By movable sprocket with axle to wheel serve as contrary pin transmission, to take turns axle be that the unilateral bearing of clockwise transmission is engaged in second transmission shaft; The second grade transmission chain wheels comprise the master of identical modulus, by the movable sprocket power output sprocket and connect drive sprocket, by the chain of movable sprocket, power output sprocket; Drive sprocket with axle to wheel serve as contrary pin transmission, to take turns axle be that the unilateral bearing of clockwise transmission is engaged in first transmission shaft; By movable sprocket with axle to wheel be clockwise transmission, to take turns axle be that the unilateral bearing of counterclockwise transmission is engaged in second transmission shaft; Drive sprocket places the chain outside.
11, drive mechanism of electric carrier according to claim 1 is characterized in that described I and II driving wheel group is the I and II driving gear with direct engagement; The one-level driving gear set comprise identical modulus but out of mesh two driving gears and simultaneously with the power output gear of two driving gears engagement; Two driving gears respectively with axle to wheel be counterclockwise transmission, wheel to axle be the unilateral bearing of clockwise transmission and axle to wheel serve as against the pin transmission, to take turns axle be that the unilateral bearing of clockwise transmission is engaged in first and second transmission shaft; Power output gear is engaged in the pto that comprises left and right half with differential mechanism; The secondary driving gear set comprises identical modulus and intermeshing little, big driving gear; Small transmission gear with axle to wheel be clockwise transmission, to take turns axle be that the unilateral bearing of counterclockwise transmission is engaged in first transmission shaft; Big driving gear with axle to wheel be clockwise transmission, to take turns axle be that the unilateral bearing of counterclockwise transmission is engaged in second transmission shaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 01226624 CN2487920Y (en) | 2001-06-11 | 2001-06-11 | Electric carrying means geartrain |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 01226624 CN2487920Y (en) | 2001-06-11 | 2001-06-11 | Electric carrying means geartrain |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2487920Y true CN2487920Y (en) | 2002-04-24 |
Family
ID=33642226
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 01226624 Expired - Fee Related CN2487920Y (en) | 2001-06-11 | 2001-06-11 | Electric carrying means geartrain |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2487920Y (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2005035348A1 (en) * | 2003-09-16 | 2005-04-21 | Ji-Rong Hu | A universal transmission for the scooter with gasoline engine |
| CN102506141A (en) * | 2010-01-02 | 2012-06-20 | 沈维聪 | Low-speed reversion synchronizer |
-
2001
- 2001-06-11 CN CN 01226624 patent/CN2487920Y/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2005035348A1 (en) * | 2003-09-16 | 2005-04-21 | Ji-Rong Hu | A universal transmission for the scooter with gasoline engine |
| CN102506141A (en) * | 2010-01-02 | 2012-06-20 | 沈维聪 | Low-speed reversion synchronizer |
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