CN106915239A

CN106915239A - Power-driven system and the vehicle with the power-driven system

Info

Publication number: CN106915239A
Application number: CN201510991179.6A
Authority: CN
Inventors: 杨冬生; 廉玉波; 张金涛; 罗红斌
Original assignee: BYD Co Ltd
Current assignee: BYD Co Ltd
Priority date: 2015-12-25
Filing date: 2015-12-25
Publication date: 2017-07-04
Anticipated expiration: 2035-12-25
Also published as: CN106915239B; WO2017107846A1

Abstract

The invention discloses a kind of power-driven system and vehicle.Power-driven system includes：Dynamic coupling device, dynamic coupling device includes：First sun gear, the first planet carrier and the first gear ring and the second sun gear, the second planet carrier and the second gear ring, wherein the first gear ring is coaxially connected with the second gear ring；Input shaft, input shaft is arranged to optionally be linked with the first gear ring and the second gear ring；Power source, power source is arranged to be linked with input shaft；First dynamotor, the second dynamotor, the first dynamotor and the first sun gear link, and the second dynamotor and the second sun gear link；And the first brake apparatus directly or indirectly braked to the first gear ring and the second gear ring.Power-driven system of the invention realizes differential function on the premise of tradition machinery formula differential mechanism is eliminated, while having abundant transmission mode.

Description

Power-driven system and the vehicle with the power-driven system

Technical field

The present invention relates to automobile technical field, more particularly, to a kind of power-driven system and the vehicle with the power-driven system.

Background technology

In a kind of correlation technique on transmission device for vehicle known for inventor, the transmission device is provided with a pair of differential mechanism and a pair of motors, and differential attachment has Sun gear, planetary gear, planet carrier and ring gear.Engine is by inputing to the sun gear of a pair of differential mechanism after the speed change of intermediate transmission structure.A pair of motors will drive Power inputs to the ring gear of a pair of differential mechanism respectively.The transmission device eliminates tradition machinery formula differential mechanism element, and two motors are realized using two groups of planetary gears With the coupling of engine power.

But, above-mentioned transmission device is applied to working truck (such as snow sweeper), and its motor output mechanism is worm-and-wheel gear, realizes that motor power is driven by self-locking One-way, act only on vehicle it is excessively curved when steering differential use, the operating modes such as pure electronic, mixed dynamic and power generation in parking can not be realized.

The content of the invention

It is contemplated that at least solving one of above-mentioned technical problem of the prior art to a certain extent.

The present invention proposes a kind of power-driven system, and the power-driven system realizes differential function on the premise of tradition machinery formula differential mechanism is eliminated, while having Abundant transmission mode.

The invention allows for a kind of vehicle, the vehicle has above-mentioned power-driven system.

Power-driven system according to embodiments of the present invention, including：Dynamic coupling device, the dynamic coupling device includes：First sun gear, the first planet carrier and One gear ring and the second sun gear, the second planet carrier and the second gear ring, wherein first gear ring is coaxially connected with second gear ring；Input shaft, the input shaft sets It is set to and is optionally linked with first gear ring and second gear ring；Power source, the power source is arranged to be linked with the input shaft；First dynamotor, Second dynamotor, first dynamotor links with first sun gear, and second dynamotor links with second sun gear；And directly Or the first brake apparatus braked to first gear ring and second gear ring indirectly.

Power-driven system according to embodiments of the present invention realizes differential function on the premise of tradition machinery formula differential mechanism is eliminated, while having abundant transmission mode.

The vehicle of embodiment, including the power-driven system in above-described embodiment according to a further aspect of the invention.

Brief description of the drawings

Fig. 1 is the schematic diagram of power-driven system according to embodiments of the present invention；

Fig. 2 is the partial schematic diagram of the power-driven system in Fig. 1, mainly illustrates dynamic coupling device part；

Fig. 3 is the schematic diagram of power-driven system in accordance with another embodiment of the present invention；

Fig. 4 is the schematic diagram of power-driven system in accordance with another embodiment of the present invention；

Fig. 5 is the schematic diagram of power-driven system in accordance with another embodiment of the present invention；

Fig. 6-Figure 16 is the partial schematic diagram of power-driven system according to embodiments of the present invention, and its part illustrated can be as vehicle rear-guard；

Figure 17-Figure 18 is the schematic diagram of vehicle according to embodiments of the present invention.

Specific embodiment

Embodiments of the invention are described below in detail, the example of the embodiment is shown in the drawings, wherein same or similar label represents same or like from start to finish Element or the element with same or like function.Embodiment below with reference to Description of Drawings is exemplary, it is intended to for explaining the present invention, without being understood that It is limitation of the present invention.

In the description of the invention, it is to be understood that term " " center ", " longitudinal direction ", " transverse direction ", " length ", " width ", " thickness ", " on ", D score, " preceding ", " afterwards ", the orientation or position relationship of the instruction such as "left", "right", " vertical ", " level ", " top ", " bottom " " interior ", " outward ", " clockwise ", " counterclockwise " be based on Orientation shown in the drawings or position relationship, are for only for ease of the description present invention and simplify description, must have rather than the device or element for indicating or implying meaning specific Orientation, with specific azimuth configuration and operation, therefore be not considered as limiting the invention.

Additionally, term " first ", " second " are only used for describing purpose, and it is not intended that indicating or implying relative importance or imply to indicate that indicated technology is special The quantity levied.Thus, " first " is defined, one or more this feature can be expressed or be implicitly included to the feature of " second ".In the description of the invention, " multiple " is meant that at least two, such as two, three etc., unless otherwise expressly limited specifically.

In the present invention, unless otherwise clearly defined and limited, the term such as term " installation ", " connected ", " connection ", " fixation " should be interpreted broadly, for example, Can be fixedly connected, or be detachably connected, or integrally；Can mechanically connect, or electrically connect or can communicate with one another；It can be direct phase Even, it is also possible to be indirectly connected to by intermediary, can be two element internals connection or two interaction relationships of element.For the ordinary skill people of this area For member, above-mentioned term concrete meaning in the present invention can be as the case may be understood.

In the present invention, unless otherwise clearly defined and limited, fisrt feature second feature it " on " or D score can include the first and second features Directly contact, it is also possible to including the first and second features be not directly contact but by the other characterisation contact between them.And, fisrt feature is Two features " on ", " top " and " above " include fisrt feature directly over second feature and oblique upper, or be merely representative of fisrt feature level height Higher than second feature.Fisrt feature second feature " under ", " lower section " and " below " include fisrt feature immediately below second feature and obliquely downward, Or fisrt feature level height is merely representative of less than second feature.

Below with reference to the accompanying drawings power-driven system 1000 according to embodiments of the present invention is described, the power-driven system 1000 mixes dynamic suitable for vehicle 10000, such as Power vehicle 10000, the power that the power-driven system 1000 can be as the power source of vehicle 10000 and needed for providing the normally travel of vehicle 10000.

Power-driven system 1000 is described in detail with reference to the embodiment of Fig. 1-Fig. 5.

Reference picture 1 and combine shown in Fig. 2, power-driven system 1000 according to embodiments of the present invention can include dynamic coupling device 100, the first dynamotor 51, Second dynamotor 52, the brake apparatus 41 of power source 55 and first.

Dynamic coupling device 100 is described in detail first below in conjunction with the accompanying drawings.Shown in Figure 2, dynamic coupling device 100 mainly includes two single planet teeth Wheel mechanism 1,2.

Each planetary gears 1,2 (i.e. the first planetary gears 1 and the second planetary gears 2) includes sun gear, planetary gear, planet carrier and gear ring, That is, dynamic coupling device 100 can include the first planetary gears 1 and the second planetary gears 2, the first planetary gears 1 includes the first sun gear 11st, the first planetary gear 12, the first planet carrier 14 and the first gear ring 13, the second planetary gears 2 include the second sun gear 21, the second planetary gear 22, the second planet The gear ring 23 of frame 24 and second.

First planetary gear 12 is arranged on the first planet carrier 14 and is arranged between the first sun gear 11 and the first gear ring 13, the first planetary gear 12 respectively with first sun The gear ring 13 of wheel 11 and first is engaged.First planetary gear 12 can be arranged on the first planet carrier 14 by planet wheel spindle, and the first planetary gear 12 can be multiple, and along the One the circumferentially-spaced of sun gear 11 is uniformly distributed, such as, in view of the stability and manufacturing cost of power transmission, the first planetary gear 12 can be three and be distributed on the The outside of one sun gear 11, about 120 ° are spaced between two adjacent the first planetary gears 12.

The engagement system of the first planetary gear 12 and the first sun gear 11 is external toothing.The engagement system of the first planetary gear 12 and the first gear ring 13 is internal messing, that is, Say, form with teeth on the inner peripheral surface of the first gear ring 13, the first planetary gear 12 engages cooperation with the tooth on the inner peripheral surface of the first gear ring 13.First planetary gear 12 can be around The axis rotation of planet wheel spindle, it is also possible to revolved round the sun around the first sun gear 11.

Similarly, shown in reference picture 2, the second planetary gear 22 is arranged on the second planet carrier 24 and is arranged between the second sun gear 21 and the second gear ring 23, second Planetary gear 22 is engaged with the second sun gear 21 and the second gear ring 23 respectively.Second planetary gear 22 can be arranged on the second planet carrier 24 by planet wheel spindle, the second planet Wheel 22 can be multiple, and be uniformly distributed along the second the circumferentially-spaced of sun gear 21, such as in view of the stability and manufacturing cost of power transmission, the second planetary gear 22 can be three and be distributed on the outside of the second sun gear 21, and about 120 ° are spaced between two adjacent the second planetary gears 22.

The engagement system of the second planetary gear 22 and the second sun gear 21 is external toothing.The engagement system of the second planetary gear 22 and the second gear ring 23 is internal messing, that is, Say, form with teeth on the inner peripheral surface of the second gear ring 23, the second planetary gear 22 engages cooperation with the tooth on the inner peripheral surface of the second gear ring 23.Second planetary gear 22 can be around The axis rotation of planet wheel spindle, it is also possible to revolved round the sun around the second sun gear 21.

Wherein, the first gear ring 13 is coaxially connected with the second gear ring 23, so that the first gear ring 13 and the synchronization action of the second gear ring 23, that is to say, that the He of the first gear ring 13 The motion state moment of the second gear ring 23 is consistent, such as the first gear ring 13 and synchronized, the equidirectional rotation of the second gear ring 23.As a kind of implementation method, the first tooth The gear ring 23 of circle 13 and second can form as one structure, so that shared gear ring 1323 is constituted, and by two planetary gears 1,2 are shared.

In further embodiments, as shown in Fig. 2 dynamic coupling device 100 may further include gear ring connecting portion 31, the gear ring 13 of gear ring connecting portion 31 and first With the coaxial linkage of the second gear ring 23, in other words, gear ring connecting portion 31 is coaxially arranged with the first gear ring 13 and the second gear ring 23, and the tooth of gear ring connecting portion 31 and first The gear ring 23 of circle 13 and second can be linked so as to be synchronized with the movement.Such as, gear ring connecting portion 31 be located at the first gear ring 13 and the second gear ring 23 inside and with the first tooth Circle 13 is fixedly connected with the second gear ring 23.

However, it is to be understood that realize that the first gear ring 13 and the mode of the same movement state of the second gear ring 23 (as rotated in the same direction, at the same speed) can have various, such as It is presented here that first gear ring 13 and the second gear ring are made into a single integrated structure to form shared gear ring 1323.Or first gear ring 13 and the second gear ring 23 can also be by tooth Circle connecting portion 31 is attached.Furthermore, above two mode can be combined, that is, shown in Fig. 1-Fig. 3 embodiments, the first gear ring 13 and the second gear ring 23 not only into Integrative-structure is to form shared gear ring 1323, while the first gear ring 13 and the second gear ring 23 are also fixed by gear ring connecting portion 31.

It should be noted that above-mentioned " linkage " can be understood as multiple parts (for example, two) coupled movements, and by taking two part linkages as an example, one wherein When part is moved, another part is also moved therewith.

For example, in some embodiments of the invention, the axle that gear can be understood as being linked with it when gear rotates with axle linkage will also rotate, or in the axle The gear linked with it during rotation also will rotation.

And for example, another axle that axle can be understood as being linked with it when an axle rotates wherein with axle linkage also will rotation.

For another example, another gear that gear can be understood as being linked with it when a gear rotates wherein with gear-linked also will rotation.

However, it is to be understood that two parts of linkage wherein a part geo-stationary when, another part can also geo-stationary therewith.

Shown in reference picture 1, Fig. 3-Fig. 5, input shaft 63 is arranged to optionally be linked with the first gear ring 13 and the second gear ring 23.In the tooth of input shaft 63 and first Circle 13 and the second gear ring 23 link when, can be driven to the first gear ring 13 and the second gear ring 23 through the power of input shaft 63, and input shaft 63 not with the first gear ring 13 When being linked with the second gear ring 23, input shaft 63 disconnects with the first gear ring 13 and the second gear ring 23.For the choosing of the gear ring 13 of input shaft 63 and first and the second gear ring 23 Selecting property linked manner will be described in conjunction with specific embodiments below.

As shown in figure 1, power source 55 is arranged to be linked with input shaft 63, the power output that thus power source 55 can be produced, and can be by being input into input shaft 63 Axle 63 is acted on by the linkage of the gear ring 13 of input shaft 63 and first and the second gear ring 23 when needing and exported to two gear rings.Alternatively, power source 55 can With including engine 54 and a dynamotor (the 3rd dynamotor 53).

Such as shown in Fig. 1 and combination Fig. 2, the first dynamotor 51 links with the first sun gear 11, and such as the first dynamotor 51 can be by first gear mechanism 58 Linked with the first sun gear 11.First gear mechanism 58 can serve as reducing gear to realize that the deceleration to the first dynamotor 51 increases torsion.First gear mechanism 58 Gear 581, gear 582 can be included, gear 581 and gear 582 engage, gear 581 coaxial with the first dynamotor 51 can be connected, and gear 582 can pass through Axle 583 is coaxial with the first sun gear 11 to be connected.

Second dynamotor 52 is linked with the second sun gear 21, and such as the second dynamotor 52 can be linked by second gear mechanism 59 with the second sun gear 21.The Two gear mechanisms 59 can serve as reducing gear to realize that the deceleration to the second dynamotor 52 increases torsion.Second gear mechanism 59 can include gear 591, gear 592, Gear 591 and gear 592 are engaged, and gear 591 coaxial with the second dynamotor 52 can be connected, and gear 592 can be by axle 593 and the coaxial phase of the second sun gear 21 Even.

As one kind preferred embodiment, first gear mechanism 58 is identical with the construction of second gear mechanism 59, i.e. first gear mechanism 58 and second gear mechanism 59 Gear quantity is identical, meshing relation is identical and the number of teeth of each corresponding gear is also identical.Thus the versatility of part is substantially increased, power-driven system 1000 is reduced Cost.

Thus, power-driven system 1000 according to embodiments of the present invention at least has three power sources (two dynamotor and power source), so as to greatly enrich The transmission mode and transmission efficiency of power-driven system 1000, and on specific typical condition, will be described in detail in conjunction with specific embodiments below, do not say again here It is bright.

Here, it is necessary to illustrate a bit, in description of the present invention about " dynamotor ", if without specified otherwise, the dynamotor can be understood as tool There is the motor of generator and motor function.

First brake apparatus 41 is arranged for braking gear ring, i.e., for being braked to the first gear ring 13 or the second gear ring 23.It is appreciated that of the invention specific Embodiment part a, part (such as brake apparatus or brake) is braked to another part and can be broadly understood, that is, be interpreted as directly braking or indirect Braking.In other words, the first brake apparatus 41 can be braked directly to the first gear ring 13 or the second gear ring 23, and certain first brake apparatus 41 can also be by system The jackshaft 61 that dynamic other parts such as will be noted below is braked to the first gear ring 13 and the second gear ring 23 indirectly.It is understood that due to the first gear ring 13 Coaxially to be connected and motion state identical with the second gear ring 23, as long as therefore wherein any one gear ring is braked, then the gear ring that another links therewith also will be by Braking.

In short, the first brake apparatus 41 can be braked to the first gear ring 13 or the second gear ring 23 or other parts such as jackshaft 61 linked with two gear rings, So due to the interaction relation between each part, it is achieved that the purpose of the first gear ring 13 of (direct or indirect) braking and the second gear ring 23 simultaneously.

Such as the first brake apparatus 41 can directly brake shared gear ring 1323, or the first brake apparatus 41 can be with brake intermediate shaft 61, the thus He of the first gear ring 13 Second gear ring 23 (sharing gear ring 1323) is braked indirectly.Alternatively, the first brake apparatus 41 can be brake, naturally it is also possible to be synchronizer.

First planet carrier 14 and the second planet carrier 24 of dynamic coupling device 100 can be as the clutch ends of dynamic coupling device 100, so as in the first braking dress When putting 41 realizations to the braking action of the first gear ring 13 and the second gear ring 23, from corresponding first sun gear 11 can be input into the power of generation by the first dynamotor 51, Exported by the first planet carrier 14 again and give corresponding wheel such as left side wheel 73, from the second sun gear 21 can be input into the power of generation, lead to again by the second dynamotor 52 Cross the second planet carrier 24 and export and give corresponding wheel such as right side wheels 74.

Now, the wheel 73,74 of both sides is associated with the first dynamotor 51 and the second dynamotor 52 respectively, by the first dynamotor 51 and second The control of the rotating speed of dynamotor 52, it is possible to achieve independent to two controls of vehicle wheel rotational speed, is achieved in differential principle.

For example, being travelled in flat road surface when vehicle 10000 and during along straight ahead, the first dynamotor 51 and the second dynamotor 52 can be defeated with identical rotating speed Go out power, so by the decelerating effect of respective planetary gears, it is theoretically equal that correspondence wheel obtains rotating speed, thereby guarantees that vehicle 10000 can be smoothly Advanced along straight line.

And for example, when vehicle 10000 is travelled in uneven road surface or turning driving, now can there is speed discrepancy in the rotating speed of the wheel of both sides in theory, by taking left-hand bend as an example, The radius of turn of left side wheel 73 is smaller and radiuss of turn of right side wheels 74 are larger, and in order to ensure to make PURE ROLLING between wheel and ground, left side wheel 73 turns Speed is less than the rotating speed of right side wheels 74, and now the output speed of the first dynamotor 51 can be less than the output speed of the second dynamotor 52, and specifically turn Speed difference can indirectly be calculated by the steering angle of steering wheel, and such as driver rotates counterclockwise steering wheel (turning left) certain angle, the controller base of vehicle 10000 The radius of turn of vehicle 10000 can be calculated in the steering angle, after the radius of turn of vehicle 10000 determines, the relative rotation speed difference of both sides wheel is also determined, this When controllable first dynamotor 51 of controller and the second dynamotor 52 power is externally exported with the rotating speed for matching respectively so that the speed discrepancy of the two can be with car Speed discrepancy matching needed for wheel, so by the way that after two decelerating effects of planetary gears, two wheels are obtained in that desired rotating speed, so as to realize that pure rolling is turned Traveling.

It is above-mentioned be using the first dynamotor 51 and the second dynamotor 52 as motor as a example by illustrate, the dynamoelectric and power generation of certain first dynamotor 51 and second Machine 52 can also such as reclaim wheel braking energy as generator operation.

It is understood that the first above-mentioned planetary gears 1 and the second planetary gears 2 can use identical gearratio, for example, being with sun crop rotation For power input and planet carrier (the first planet carrier 14 and the second planet carrier 24) are as clutch end, two planetary gears can use identical gearratio. That is, the number of teeth of the first sun gear 11 and the second sun gear 21, the number of teeth of the first planetary gear 12 and the second planetary gear 22 and the first gear ring 13 and the second gear ring 23 The number of teeth (internal tooth) can be identical respectively.

To sum up, power-driven system 1000 according to embodiments of the present invention, by the braking action of the first brake apparatus 41, it is possible to achieve the He of the first dynamotor 51 The electric-only mode or Brake energy recovery pattern of the second dynamotor 52, and by individually control the first dynamotor 51 and the second dynamotor 52 it is defeated Go out rotating speed, the wheel of both sides can be made to obtain different moments of torsion, realize differential function.And after the braking action of the first brake apparatus 41 is released, power source 55 also may be used With intervene and with the first dynamotor 51 and the power coupling of the second dynamotor 52 after common externally output power, so as to significantly lift power-driven system 1000 Dynamic property and by property.

Further, since the power of the first dynamotor 51 and the second dynamotor 52 is input into from the first sun gear 11 and the second sun gear 21 respectively, power source 55 Power be input into from the first gear ring 13 and the second gear ring 23, and the power of dynamic coupling device 100 is finally exported from the first planet carrier 14 and the second planet carrier 24, This power input, the mode of output cause that the first dynamotor 51 and the second dynamotor 52 are obtained in that preferably transmission speed ratio under different operating modes, are lifted Drive efficiency when as motor of first dynamotor 51 and the second dynamotor 52 and generating efficiency during as generator.

Input shaft 63 is described in detail in conjunction with specific embodiments with the kind of drive of the first gear ring 13 and the second gear ring 23 below.

In certain embodiments, as shown in Fig. 1 and Fig. 3-Fig. 5, input shaft 63 is arranged to optionally be linked with jackshaft 61, and jackshaft 61 then with the first tooth The gear ring 23 of circle 13 and second is linked, and thus input shaft 63 optionally can be linked by jackshaft 61 with the first gear ring 13 and the second gear ring 23.

For input shaft 63 and the selective linked manner of jackshaft 61, can be realized by the element with engagement and break function.For example, in certain embodiments, As shown in Fig. 1, Fig. 3-Fig. 5, input shaft 63 is optionally linked with jackshaft 61 by the synchronous effect of synchronizer 42, it is to be understood that same at this When step device 42 is in engagement state, input shaft 63 links with jackshaft 61, and when synchronizer 42 is off, then input shaft 63 is also located with jackshaft 61 In off-state.

Further, as a kind of optional implementation method, as shown in Fig. 1, Fig. 3-Fig. 5, the overhead of input shaft 63 set sets input shaft free gear 631, jackshaft 61 On be fixedly installed the first fixed gear of jackshaft 611, input shaft free gear 631 is engaged with the first fixed gear of jackshaft 611, and synchronizer 42 can be arranged on defeated Enter on axle 63 and for engaging input shaft free gear 631.

Power source 55 according to embodiments of the present invention is described in detail in conjunction with specific embodiments below.

Shown in reference picture 1, Fig. 3-Fig. 5, power source 55 can include the dynamotor 53 of engine 54 and the 3rd, 53 points of the dynamotor of engine 54 and the 3rd Do not linked with input shaft 63.For example, used as a kind of feasible implementation method, engine 54, input shaft 63 are coaxially connected with the 3rd dynamotor 53, thus make The structure of power-driven system 100 is compacter, and volume is smaller, convenient arrangement.Simultaneously as by an input between the dynamotor 53 of engine 54 and the 3rd Axle 63 is rigidly connected, and when the gear ring 13 of input shaft 63 and first and the second gear ring 23 are off (synchronizer 42 disconnects), it is dynamic that engine 54 is produced Power can be exported all to the 3rd dynamotor 53, so as to drive the 3rd dynamotor 53 to generate electricity, now dynamic coupling device 100 is moved with the onrelevant of engine 54, Therefore the power that engine 54 is produced can be completely used for driving the 3rd dynamotor 53 to generate electricity, and substantially increase charge efficiency and charging is ageing, additionally, due to biography Dynamic chain is most short, and transmission energy loss is small, farthest improves the utilization rate that power is exported to engine 54.

Jackshaft 61 is described with the kind of drive of the first gear ring 13 and the second gear ring 23 below.

In certain embodiments, jackshaft 61 is linked by intermediate gearing 62 with the first gear ring 13 and the second gear ring 23.

Used as a kind of implementation method, intermediate gearing 62 can be gear drive.Such as, intermediate gearing 62 includes that outer toothed portion 621 and jackshaft second are solid Fixed gear 612, the gear ring 13 of outer toothed portion 621 and first and the coaxial linkage of the second gear ring 23, such as outer toothed portion 621, the first gear ring 13, the motion shape of the second gear ring 23 State is identical, that is, be synchronized with the movement, such as synchronized, equidirectional rotation.First gear ring 13, the second gear ring 23 and outer toothed portion 621 can form as one structure, that is to say, that May be integrally formed external tooth to form outer toothed portion 621 on the outer peripheral face for sharing gear ring 1323.

The second fixed gear of jackshaft 612 can be fixed on jackshaft 61 and is spaced apart from each other in the axial direction with the first fixed gear of jackshaft 611.Jackshaft second is consolidated Fixed gear 612 is engaged with outer toothed portion 621.

Intermediate gearing 62 shown in Fig. 1 embodiments uses gear drive, compact conformation, simple, low cost, and reliable transmission, and can be according to engine 54 And the number of teeth of the 3rd gearratio adaptability design gear needed for dynamotor 53, so as to meet the transmission requirement of the dynamotor 53 of engine 54 and the 3rd.

Certainly, the present invention is not limited thereto, and in other embodiments of the invention, as shown in fig. 4-5, intermediate gearing 62 can also be tape handler, chain Transmission mechanism or CVT (Continuously Variable Transmission, such as continuous variable transmission, infinitely variable transmission) transmission mechanism.

As shown in Fig. 1, Fig. 3-Fig. 5, the first brake apparatus 41 can be arranged on jackshaft 61 and be realized to the first gear ring 13 and second by brake intermediate shaft 61 The indirect braking of gear ring 23.Certainly, the first brake apparatus 41 can also directly brake shared gear ring 1323.In certain embodiments, as shown in Figure 3 and Figure 5, One brake apparatus 41 can be brake.And in further embodiments, as shown in Figure 1 and Figure 4, the first brake apparatus 41 can be synchronizer.

Due to the first planet carrier 14 and the second planet carrier 24 can as the clutch end of power-driven system 1000, therefore can with set in planet carrier gear so as to Power is externally exported in planet carrier.As shown in Fig. 2 as a kind of implementation method, the first planet carrier output gear 141 has been coaxially disposed on the first planet carrier 14, the The second planet carrier output gear 241 has been coaxially disposed on two planet carriers 24.Further, the first planet carrier output gear 141 is outside positioned at the footpath of the first planet carrier 14 Side, the second planet carrier output gear 241 is located at the radial outside of the second planet carrier 24, because the first planet carrier 14 and the second planet carrier 24 have relatively large radial direction Size, and two output gears 141,241 are separately positioned on the radial outside of respective planet carrier, therefore two output gears 141,241 have relatively big turning Dynamic radius, is so easy to carry out cooperation transmission with the axle shaft gear 711,721 on the semiaxis 71,72 of vehicle 10000 or semiaxis 71,72, improves the reliability of transmission.

Reference picture 1 and combine Fig. 2 embodiment, dynamic coupling device 100 have two planetary gears 1,2, while the first dynamotor 51 (rotor) and Second dynamotor 52 (rotor) is driven with the first sun gear 11 and the second sun gear 21 respectively.The stator and the second dynamotor of the first dynamotor 51 52 stator is located at the outside of respective rotor, and the housing of the first dynamotor 51 and the second dynamotor 52 is located at outermost, therefore as preferred implementation It is shared outer to be formed that the housing of mode, the first dynamotor 51 and the second dynamotor 52 may be constructed integrative-structure, and two planetary gears 1,2 of cladding Shell, that is to say, that the common enclosure be able to can be accommodated in as the big shell of dynamic coupling device 100, two planetary gears, 1,2, two motors 51,52 In the common enclosure, so as to reduce amount of parts, make that the structure of power-driven system 1000 is compacter, volume is smaller, processing and manufacturing of being more convenient for is greatlyd save Manufacturing cost, realizes the Highgrade integration design of product, power-driven system 1000 is realized that high-efficiency modularized is produced, and is all greatly improved in manufacture, assembling link Efficiency.

Certainly, as a kind of similar modified example, it is electronic that the first sun gear 11, the first planet carrier 14, the first planetary gear 12 and the first gear ring 13 can be accommodated in first Inside generator 51, i.e. the enclosure interior of the first dynamotor 51, the second sun gear 21, the second planetary gear 22, the second planet carrier 24 and the second gear ring 23 can be with It is accommodated in inside the second dynamotor 52, such as the enclosure interior of the second dynamotor 52.

Thus, the Highgrade integration design of product can be equally realized, power-driven system 1000 is realized that high-efficiency modularized is produced, in manufacture, assembling link all significantly Improve efficiency, effective reduces cost.

The detailed configuration and typical condition of the power-driven system 1000 in Fig. 1 embodiments are described in detail with reference to Fig. 1.

Shown in reference picture 1 (with reference to Fig. 2), the first planetary gears 1, the second planetary gears 2 are coaxially arranged.

First planetary gears 1 includes the first sun gear 11, the first planetary gear 12, the first planet carrier 14 and the first gear ring 13, and the first sun gear 11 is in interposition Put, the first planetary gear 12 is engaged with the first sun gear 11 and the first gear ring 13 respectively, the first planetary gear 12 is arranged on the first planet carrier 14, the first planet carrier 14 On be coaxially fixed with the first planet carrier output gear 141, the first planet carrier output gear 141 is engaged with the axle shaft gear 711 on left half axle 71, the outside of left half axle 71 It is connected with left side wheel 73.

Second planetary gears 2 includes the second sun gear 21, the second planetary gear 22, the second planet carrier 24 and the second gear ring 23, and the second sun gear 21 is in interposition Put, the second planetary gear 22 is engaged with the second sun gear 21 and the second gear ring 23 respectively, the second planetary gear 22 is arranged on the second planet carrier 24, the second planet carrier 24 On be coaxially fixed with the second planet carrier output gear 241, the second planet carrier output gear 241 is engaged with the axle shaft gear 721 on right axle shaft 72, the outside of right axle shaft 72 It is connected with right side wheels 74.

Each kinematic pair of first planetary gears 1 can be with identical, so that the first planetary gears 1 with the number of teeth of corresponding each kinematic pair in the second planetary gears 2 The gearratio obtained when transmitting power according to identical bang path with the second planetary gears 2 is identical.

First gear ring 13 and the second gear ring 23 can form as one structure, so as to constitute shared gear ring 1323.

Outer toothed portion 621 can be provided with the outer peripheral face for sharing gear ring 1323, the first fixed gear of jackshaft 611 and the tooth of jackshaft second are fixedly installed on jackshaft 61 Wheel 612, the second fixed gear of jackshaft 612 is engaged with outer toothed portion 621.First brake apparatus 41 is synchronizer and is arranged on jackshaft 61, the first brake apparatus 41 jackshaft 61 can be bonded on fixed part (such as housing, can be the housing of dynamotor or the housing of dynamic coupling device or power drive line Housing of system etc.), thus it is achieved thereby that the direct braking to jackshaft 61 and the indirect braking to the first gear ring 13 and the second gear ring 23 after the engagement of synchronizer 41.

The overhead of input shaft 63 set is provided with input shaft free gear 631, and synchronizer 42 is provided with input shaft 63, and synchronizer 42 is used to engage input shaft free gear 631, Input shaft free gear 631 is engaged with the first fixed gear of jackshaft 611.

The dynamotor 53 of engine 54 and the 3rd is coaxially attached to the two ends of input shaft 63.

First dynamotor 51 links with the first sun gear 11, and such as by first gear mechanism 58, the second dynamotor 52 links with the second sun gear 21, such as By second gear mechanism 59.

The power-driven system 1000 is can be seen that from the structure of Fig. 1 embodiments eliminate tradition machinery formula differential mechanism, but both can optionally by engine 54 It is input into shared gear ring 1323 with the power of the 3rd dynamotor 53, it is also possible to share gear ring 1323 optionally through the indirect locking of the first brake apparatus 41, so The sun gear of both sides planetary gears then separately accesses the first dynamotor 51 and the second dynamotor 52, finally by two groups of planets of planetary gears Frame exports power as clutch end.That is, by synchronizer 42, the first brake apparatus 41 and three dynamotor different working modes and rotational speed regulation, can be with Realize various driving operating modes.

Pure electronic operating mode：

The dynamotor 53 of engine 54 and the 3rd does not work, and synchronizer 42 is off.The braking of first brake apparatus 41 shares gear ring 1323, so that first The dynamotor 52 of dynamotor 51 and second independently works to drive the wheel of respective side.

Mixed condition of starting building：

Synchronizer 42 is in engagement state, and the first brake apparatus 41 is off.Engine 54 output power exported after input shaft 63, synchronizer 42 to Gear ring 1323 is shared, the 3rd dynamotor 53 now can utilize the partial power from engine 54 to enter with generator forms work (from the power taking of input shaft 63) Row generates electricity, and the electric energy of acquisition can supply the first dynamotor 51 and the second dynamotor 52, that is to say, that now the first dynamotor 51 and second is electronic Generator 52 with motorjbrm work, and with the power coupling of engine 54 after from respective planet carrier export.

Or now the 3rd dynamotor 53 can also export power as motor, supplement the moment of torsion of engine 54, now the first dynamotor 51 and second is electronic Generator 52 is also worked with motorjbrm, and power is exported to respective wheel respectively after the first planet carrier 14 and the second planet carrier 24 are coupled.

Because three dynamotor and engine 54 are the relations of rotating speed coupling, when speed needs the short time to be continually changing, can be completed by the speed governing of motor, such as Speed governing is carried out with motorjbrm by the 3rd dynamotor 53, or speed governing is carried out by the first dynamotor 51 and the second dynamotor 52, also may be used certainly To be three motors while carrying out speed governing, so as to ensure that engine 54 can drive work under a more efficient rotating speed all the time, preferably fuel economy is realized.

Driving generating operation mode：

The brake intermediate shaft 61 of first brake apparatus 41, synchronizer 42 is off, and engine 54 produces the dynamotor 53 of power drive the 3rd to be generated electricity. The first dynamotor 51 and the second dynamotor 52 are worked with motorjbrm respectively simultaneously, and its power for producing is exported by respective planet carrier.

Power generation in parking operating mode：

Synchronizer 42 is off, and the power that engine 54 is produced directly is exported by input shaft 63 and generated electricity to the 3rd dynamotor 53, is thus driven Chain is most short, is driven Minimal energy loss.

Power-driven system 1000 in Fig. 1 embodiments possesses engine 54 and three dynamotor, with abundant transmission mode, while being braked by by first Device 41 is set to synchronizer and at least can to a certain extent reduce the volume of power-driven system 1000, makes power-driven system 1000 be more convenient for arranging.

Fig. 3 is illustrated that the implementation method of another power-driven system 1000, compared with Fig. 1 embodiments, of power-driven system 1000 in Fig. 3 embodiments One brake apparatus 41 is brake, and the construction and typical condition of remainder are then substantially the same with Fig. 1 embodiments, repeat no more here.

Fig. 4 is illustrated that the implementation method of another power-driven system 1000, compared with Fig. 1 embodiments, in the power-driven system 1000 in Fig. 4 embodiments Between transmission device 62 be CVT transmission mechanisms or tape handler, the construction and typical condition of remainder are then substantially the same with Fig. 1 embodiments, repeat no more here.

Fig. 5 is illustrated that the implementation method of another power-driven system 1000, compared with Fig. 4 embodiments, of power-driven system 1000 in Fig. 5 embodiments One brake apparatus 41 is brake, and the construction and typical condition of remainder are then substantially the same with Fig. 4 embodiments, repeat no more here.

To sum up, generally speaking, power-driven system 1000 according to embodiments of the present invention, speed governing is carried out using the first dynamotor 51 and the second dynamotor 52 Bending moment and two groups of planetary gears carry out power coupling, make every effort to for whole power-driven system 1000 to become most simple, most compact.Such series parallel type power drive System 1000, can not only realize the independent control of the first dynamotor 51 and the respective side wheel of the second dynamotor 52 pairs, can also farthest ensure hair Rotating speed interval work of the motivation 54 in fuel economy high.And because the first dynamotor 51 and the second dynamotor 52 can independently control correspondence wheel, from And the active safety and mobility of the system of vehicle 10000 are considerably improved, significantly improve the handling and driving experience of system.Meanwhile, the system has concurrently 3rd dynamotor 53 is turned round and generating function to the benefit of engine 54, and each power source is more scientific and reasonable than realizing of requiring to speed, and the mechanical control element such as gearshift is less, Simple and compact for structure, space availability ratio is high.

Further, since the power of the first dynamotor 51 and the second dynamotor 52 is from sun gear introducing, and the power of engine 54 is introduced from gear ring, this power Input, the mode of output cause that the first dynamotor 51 and the second dynamotor 52 are obtained in that preferably transmission speed ratio under different operating modes, improve the first electricity Drive efficiency of the dynamic dynamotor 52 of generator 51 and second when as motor and charge efficiency during as generator.

It is understood that power-driven system described above 1000 can be as the forerunner of vehicle or rear-guard, preferably as the forerunner of vehicle.Driven in above-mentioned power When dynamic system 1000 is as forerunner, the drive system 100a shown in FIG. 6 below-Figure 16 then can be as rear-guard, so as to drive vehicle traveling jointly.

In short, the dynamic coupling device 100 of above-mentioned power-driven system 1000 can drive a pair of front-wheels of vehicle, and the drive system 100a shown in Fig. 6-Figure 16 A pair of rear wheels of vehicle can then be driven.But the present invention is not limited thereto, such as dynamic coupling device 100 can also drive a pair of rear wheels of vehicle, and Fig. 6-Figure 16 Shown drive system 100a can then drive a pair of front-wheels.

It is described in detail in conjunction with specific embodiments for the drive system 100a shown in Fig. 6-Fig. 8 first below.

As Figure 6-Figure 8, drive system 100a according to embodiments of the present invention can include the first planetary gears 1a, the second planetary gears 2a, the 4th Dynamotor 31a, the 5th dynamotor 32a, the second brake apparatus 63a, the 3rd brake apparatus 64a and power engagement device 65a.

As Figure 6-Figure 8, the first planetary gears 1a can be simple planetary arrangement, the first planetary gears 1a can include the 3rd sun gear 11a, The third line star-wheel 12a, the third line carrier 14a and the 3rd gear ring 13a.The third line star-wheel 12a be arranged on the third line carrier 14a it is upper and be arranged on the 3rd sun gear 11a and Between 3rd gear ring 13a, the third line star-wheel 12a is engaged with the 3rd sun gear 11a and the 3rd gear ring 13a respectively.The third line star-wheel 12a can be installed by planet wheel spindle On the third line carrier 14a, the third line star-wheel 12a can be multiple, and be uniformly distributed along the 3rd the circumferentially-spaced of sun gear 11a, such as in view of power transmission Stability and manufacturing cost, the third line star-wheel 12a can be three and be distributed on the outside of the 3rd sun gear 11a, between two adjacent the third line star-wheel 12a between Every about 120 °.

The engagement system of the third line star-wheel 12a and the 3rd sun gear 11a is external toothing.The engagement system of the third line star-wheel 12a and the 3rd gear ring 13a is internal messing, That is, forming with teeth on the inner peripheral surface of the 3rd gear ring 13a, the third line star-wheel 12a engages cooperation with the tooth on the inner peripheral surface of the 3rd gear ring 13a.The third line star-wheel 12a Can be around the axis rotation of planet wheel spindle, it is also possible to revolved round the sun around sun gear.

Similarly, as Figure 6-Figure 8, the second planetary gears 2a can be simple planetary arrangement, and the second planetary gears 2a can include the 4th too Sun wheel 21a, fourth line star-wheel 22a, fourth line carrier 24a and the 4th gear ring 23a.Fourth line star-wheel 22a is arranged on fourth line carrier 24a and is arranged on the 4th too Between sun wheel 21a and the 4th gear ring 23a, fourth line star-wheel 22a is engaged with the 4th sun gear 21a and the 4th gear ring 23a respectively.Fourth line star-wheel 22a can be by row Spider gear shaft is arranged on fourth line carrier 24a, and fourth line star-wheel 22a can be multiple, and be uniformly distributed along the 4th the circumferentially-spaced of sun gear 21a, for example, consider The stability and manufacturing cost of power transmission, fourth line star-wheel 22a can be three and be distributed on the outside of the 4th sun gear 21a, two adjacent fourth line star-wheels About 120 ° are spaced between 22a.

The engagement system of fourth line star-wheel 22a and the 4th sun gear 21a is external toothing.The engagement system of fourth line star-wheel 22a and the 4th gear ring 23a is internal messing, That is, forming with teeth on the inner peripheral surface of the 4th gear ring 23a, fourth line star-wheel 22a engages cooperation with the tooth on the inner peripheral surface of the 4th gear ring 23a.Fourth line star-wheel 22a Can be around the axis rotation of planet wheel spindle, it is also possible to revolved round the sun around sun gear.

Used as preferred embodiment, the third line star-wheel 12a can include coaxially arranged and synchronous axial system first gear portion 121a and second gear portion 122a, the first tooth Wheel portion 121a is engaged with the 3rd sun gear 11a, and second gear portion 122a is engaged with the 3rd gear ring 13a.First gear portion 121a can lead to second gear portion 122a Same axis is crossed to be fixedly connected.First gear portion 121a can be small teeth portion and second gear portion 122a can be big gearing part, that is to say, that first gear portion 121a's The number of teeth less than second gear portion 122a the number of teeth, thus the 4th dynamotor 31a output power when being transmitted through first gear portion 121a, second gear portion 122a, First gear portion 121a and second gear portion 122a constitute reducing gear, realize to increase the deceleration of the 4th dynamotor 31a and turn round effect.Optionally, of course, First gear portion 121a can also be big gearing part and second gear portion 122a can be small teeth portion.

Similarly, fourth line star-wheel 22a can include coaxially arranged and synchronous axial system the 3rd gear part 221a and the 4th gear part 222a, the 3rd gear part 221a with 4th sun gear 21a is engaged, and the 4th gear part 222a is engaged with the 4th gear ring 23a.3rd gear part 221a and the 4th gear part 222a can be solid by same axis Fixed connection.3rd gear part 221a can be small teeth portion and the 4th gear part 222a can be big gearing part, that is to say, that the number of teeth of the 3rd gear part 221a is less than the 4th The number of teeth of gear part 222a, thus the 5th dynamotor 32a output power when being transmitted through the 3rd gear part 221a, the 4th gear part 222a, the 3rd gear part 221a and the 4th gear part 222a constitute reducing gear, realize to increase the deceleration of the 5th dynamotor 32a and turn round effect.Optionally, of course, the 3rd gear part 221a can also be big gearing part and the 4th gear part 222a can be small teeth portion.

Used as a kind of preferred embodiment, first gear portion 121a and second gear portion 122a can be with into a single integrated structure so as to form duplex gear.Similarly, the 3rd Gear part 221a and the 4th gear part 222a can also be into a single integrated structure so as to form duplex gear.Thus simple structure, compact, and reliable transmission.

Wherein, above-mentioned the third line carrier 14a and fourth line carrier 24a can be as the clutch end of drive system 100a, such as the third line carrier 14a and the 4th Planet carrier 24a can the power of ultromotivity in future source such as the 4th dynamotor 31a and/or the 5th dynamotor 32a externally export, such as output is to wheel 41a, 42a. Alternatively, dynamic coupling device 100 drive pair of wheels when, the third line carrier 14a and fourth line carrier 24a can with two wheel 41a in second pair of wheel, 42a links respectively, so that the power output of drive system 100a can be given second couple of wheel 41a, 42a by the third line carrier 14a and fourth line carrier 24a so that Vehicle 10000 being capable of normally travel.Pair of wheels is a pair in a pair of front-wheels and a pair of rear wheels, and second pair of wheel is another right in a pair of front-wheels and a pair of rear wheels.

As Figure 6-Figure 8, the 4th dynamotor 31a and the 3rd sun gear 11a links, and the rotor of such as the 4th dynamotor 31a can be with the 3rd sun gear 11a It is coaxial to be connected, but not limited to this.

In description below the present invention about " linkage ", if without specified otherwise, be understood in this way.

Similarly, the 5th dynamotor 32a and the 4th sun gear 21a links, and the rotor of such as the 5th dynamotor 32a can coaxially be connected with the 4th sun gear 21a, But not limited to this.

Second brake apparatus 63a is arranged for braking the 3rd gear ring 13a, and the 3rd brake apparatus 64a is arranged for braking the 4th gear ring 23a.Alternatively, Second brake apparatus 63a and the 3rd brake apparatus 64a can be brakes, but not limited to this.

Drive system 100a can include the first power output shaft 43a and the second power output shaft 44a, the first power output shaft 43a be arranged on the third line carrier 14a with Between a wheel 41a in second pair of wheel of vehicle 10000, the second power output shaft 44a is arranged on another in second pair of wheel of fourth line carrier 24a and this Between individual wheel 42a, second pair of wheel can be a pair of front-wheels, naturally it is also possible to be a pair of rear wheels.

As Figure 6-Figure 8, power engagement device 65a is arranged for engaging the first power output shaft 43a and the second power output shaft 44a, so that the Formed between one power output shaft 43a and the second power output shaft 44a and be rigidly connected, and then the first power output shaft 43a and the second power output shaft 44a energy It is enough to rotate in the same direction, at the same speed.That is, when power engagement device 65a is in engagement state, the first power output shaft 43a and the second power output shaft 44a Synchronization action state is kept, when power engagement device 65a is off, the first power output shaft 43a can be carried out with the second power output shaft 44a Differential is rotated, i.e. the first power output shaft 43a and the second power output shaft 44a can respectively with different rotational speed (can certainly same rotational speed rotation).

Here, it is necessary to explanation, power engagement device 65a should make broad sense for engagement the first power output shaft 43a and the second power output shaft 44a to be managed Solution, such as power engagement device 65a can directly engage or disconnect the first power output shaft 43a and the second power output shaft 44a, and alternatively of course, power connects Attach together put 65a can also indirectly be realized by engaging or disconnecting other two parts the engagement of the first power output shaft 43a and the second power output shaft 44a with Disconnect, two parts can be the part being connected with the second power output shaft 44a with the first power output shaft 43a, such as the third line carrier 14a and the 4th Planet carrier 24a.

Vehicle with drive system 100a according to embodiments of the present invention, such as when vehicle 10000 is travelled in flat road surface and along straight ahead, the second braking dress Putting 63a and the 3rd brake apparatus 64a can respectively brake the 3rd gear ring 13a and the 4th gear ring 23a, and the 4th dynamotor 31a and the 5th dynamotor 32a can Power is exported with identical rotating speed, so by the decelerating effect of respective planetary gears, it is theoretically equal that correspondence wheel obtains rotating speed, thereby guarantees that vehicle 10000 Smoothly can be advanced along straight line.

And for example, when vehicle 10000 is travelled in uneven road surface or turning driving, the second brake apparatus 63a and the 3rd brake apparatus 64a can respectively brake the 3rd gear ring 13a and the 4th gear ring 23a, now the rotating speed of the wheel of both sides can there is speed discrepancy in theory, by taking left-hand bend as an example, the radius of turn of left side wheel is smaller and right side wheels Radius of turn it is larger, in order to ensure to make PURE ROLLING between wheel and ground, the rotating speed of left side wheel is less than the rotating speed of right side wheels, now the 4th dynamoelectric and power generation The output speed of machine 31a can be less than the output speed of the 5th dynamotor 32a, and specific speed discrepancy can indirectly be calculated by the steering angle of steering wheel, such as Driver rotates counterclockwise steering wheel (turning left) certain angle, and the controller of vehicle 10000 is based on the steering angle can calculate the turning half of vehicle 10000 Footpath, after the radius of turn of vehicle 10000 determines, the relative rotation speed difference of both sides wheel is also determined, now the controllable electricity of 4th dynamotor 31a and the 5th of controller Dynamic generator 32a externally exports power with the rotating speed for matching respectively so that the speed discrepancy of the two can be matched with the speed discrepancy needed for wheel, so pass through two planet teeth After taking turns the decelerating effect of mechanism, two wheels are obtained in that desired rotating speed, so as to realize pure rolling turning driving.

It is above-mentioned be using the 4th dynamotor 31a and the 5th dynamotor 32a as motor as a example by illustrate, certain 4th dynamotor 31a and the 5th electronic Generator 32a can also be used as generator operation.Now, similarly, the second brake apparatus 63a and the 3rd brake apparatus 64a can respectively brake the 3rd gear ring 13a With the 4th gear ring 23a, the 4th dynamotor 31a and the 5th dynamotor 32a can then be worked with generator forms, so as to reclaim braking energy.

It is, of course, understood that the first above-mentioned planetary gears 1a and the second planetary gears 2a can use identical gearratio, for example, with the sun Wheel as power intake and planet carrier as clutch end for, two planetary gears can use identical gearratio.That is, the 3rd sun gear 11a and The number of teeth (internal tooth) of the number of teeth, the number of teeth of the third line star-wheel 12a and fourth line star-wheel 22a and the 3rd gear ring 13a and the 4th gear ring 23a of four sun gear 21a can be with It is identical respectively.

Especially, when vehicle 10000 is travelled under poor load conditions, such as vehicle 10000 is on the road surfaces such as more muddy or soft gravel road or sandy soil During traveling, by taking muddy road conditions as an example, vehicle 10000 may be absorbed in soil and cause idle running, that is to say, that vehicle 10000 there occurs skidding (skidding And the reason for cause skidding be well known to a person skilled in the art).

For differential mechanism of the tradition with auto-lock function, after skidding occurs in wheel, differential mechanism self-lock only need to be controlled, so that at least can be to a certain extent Improve the ability of getting rid of poverty of vehicle 10000.

There is bigger difference with conventional carrier again because drive system 100a according to embodiments of the present invention has on differential function, but structure, it is impossible to using traditional differential Self-locking structure.In order to improve vehicle 10000 by property, improve adaptability of the vehicle 10000 to poor road conditions, the drive system 100a of some embodiments of the invention On the premise of differential function is realized, moreover it is possible to further realize auto-lock function.

Some embodiments of the invention, as Figure 6-Figure 8, when single wheel skidding occurs in vehicle, power engagement device 65a engages the first power output shaft 43a and the second power output shaft 44a, and the second brake apparatus 63a and the 3rd brake apparatus 64a brake the 3rd gear ring 13a and the 4th gear ring 23a respectively, Thus the single wheel output that the 4th dynamotor 31a and the 5th dynamotor 32a can never skid the power of generation, improves wheel-slip phenomenon, carries The handling capacity of vehicle high.

To sum up, drive system 100a according to embodiments of the present invention, by the second brake apparatus 63a and the 3rd brake apparatus 64a braking actions, it is possible to achieve the 4th The electric-only mode or Brake energy recovery pattern of dynamotor 31a and the 5th dynamotor 32a, and by individually the 4th dynamotor 31a of control and the Five dynamotor 32a output speeds, can make the wheel of both sides obtain different moments of torsion, realize differential function.Additionally, drive system according to embodiments of the present invention 100a parts are few, compact conformation simple, take small volume, arrangement of being more convenient for.

Especially, drive system 100a according to embodiments of the present invention can be not provided with the mechanical no-spin lockup structure of conventional power transmission system, but functionally The function of tradition machinery formula no-spin lockup can but be realized by the synchronous effect of power engagement device 65a, so that PWTN according to embodiments of the present invention Unite 100a structure is compacter, cost is lower.

Used as optional implementation method, power engagement device 65a can be clutch.Clutch includes the active part 651a and secondary part that can be engaged with each other and be separate 652a, active part 651a are connected with the first power output shaft 43a, and secondary part 652a is connected with the second power output shaft 44a.

Certainly, the present invention is not limited thereto, and in further embodiments, power engagement device 65a can be synchronizer, and synchronizer is arranged on the first power output shaft 43a With in the second power output shaft 44a above and for engaging another.

Used as optional implementation method, the 4th dynamotor 31a and the 3rd sun gear 11a can coaxially empty set be on the first power output shaft 43a, and the 5th is electronic Generator 32a and the 4th sun gear 21a can coaxially empty set on the second power output shaft 44a so that the structure of drive system 100a is compacter.

In addition, the 4th dynamotor 31a and the 5th dynamotor 32a can be such as arranged symmetrically, the first row with symmetrical distribution on power engagement device 65a Star gear mechanism 1a symmetrical can also be distributed with the second planetary gears 2a, is such as arranged symmetrically on power engagement device 65a, and the 4th dynamotor 31a and the 5th dynamotor 32a can respectively positioned at the opposite exterior lateral sides of the first planetary gears 1a and the second planetary gears 2a, that is to say, that for example scheming As a example by 1, the outside that the 4th dynamotor 31a is located at the first planetary gears 1a is left side, and the 5th dynamotor 32a is located at the second planetary gears 2a Outside be right side.

Used as optional implementation method, the first power output shaft 43a and the second power output shaft 44a can be semiaxis, and such as the first power output shaft 43a can be left half Axle, the second power output shaft 44a can be right axle shaft.

Construction below in conjunction with the accompanying drawings to the drive system 100a in Fig. 6 embodiments, annexation and typical condition are described.

Shown in reference picture 6, the drive system 100a that the implementation is exemplified mainly includes two simple planetary arrangement 1a, 2a, two dynamotor 31a, 32a And brake apparatus 63a, 64a and power engagement device 65a etc..

Specifically, the first planetary gears 1a in left side includes the 3rd sun gear 11a, the third line star-wheel 12a and the 3rd gear ring 13a, and the 3rd sun gear 11a is empty It is set on the first power output shaft 43a, and the 3rd sun gear 11a is connected with the 4th dynamotor 31a, also empty set is arranged on to the 4th dynamotor 31a On one power output shaft 43a.The third line star-wheel 12a is duplex gear and on the third line carrier 14a, the third line star-wheel 12a respectively with the 3rd sun gear 11a Engaged with the 3rd gear ring 13a.

Similarly, the second planetary gears 2a on right side includes the 4th sun gear 21a, fourth line star-wheel 22a and the 4th gear ring 23a, the 4th sun gear 21a empty sets It is arranged on the second power output shaft 44a, and the 4th sun gear 21a is connected with the 5th dynamotor 32a, also empty set is arranged on second to the 5th dynamotor 32a On power output shaft 44a.Fourth line star-wheel 22a is duplex gear and on fourth line carrier 24a, fourth line star-wheel 22a respectively with the 4th sun gear 21a Engaged with the 4th gear ring 23a.

Second brake apparatus 63a is used to brake the 3rd gear ring 13a, and the 3rd brake apparatus 64a is used to brake the 4th gear ring 23a, and power engagement device 65a is arranged on first Between planetary gears 1a and the second planetary gears 2a and for being selectively engaged the first power output shaft 43a and the second power output shaft 44a.

First power output shaft 43a is connected with left side wheel 41a and the third line carrier 14a, the second power output shaft 44a and right side wheels 42a and fourth line carrier 24a It is connected.

The typical condition of the drive system 100a in Fig. 6 embodiments is described below.

Pure electronic operating mode (relying on the 4th dynamotor 31a and the 5th dynamotor 32a)：

Second brake apparatus 63a brakes the 3rd gear ring 13a and the 3rd brake apparatus 64a brakes the 4th gear ring 23a, and power engagement device 65a is off.4th Dynamotor 31a and the 5th dynamotor 32a can be worked with motorjbrm respectively.Thus, the power that the 4th dynamotor 31a is produced passes through the 3rd sun Wheel 11a, the third line star-wheel 12a, the third line carrier 14a, the first power output shaft 43a are transferred to the wheel 41a in left side, the rotating speed of the 4th dynamotor 31a with The rotating speed of left side wheel 41a changes with being proportionate.The power that 5th dynamotor 32a is produced passes through the 4th sun gear 21a, fourth line star-wheel 22a, fourth planet Frame 24a, the second power output shaft 44a are transferred to the wheel 42a on right side, and the rotating speed of the 5th dynamotor 32a becomes with being proportionate with the rotating speed of the wheel 42a on right side Change.

Because the 4th dynamotor 31a and the 5th dynamotor 32a now independently work, the two is non-interference, therefore two motors can be according to each right Answer moment of torsion needed for wheel and adaptively adjust output speed, realize differential function.

It is appreciated that under the operating mode, the 4th dynamotor 31a and the 5th dynamotor 32a can be rotated clockwise or rotated counterclockwise, pure electricity is achieved in It is dynamic to advance or pure electronic reversing.

Skidding operating mode：

Schematically illustrate by taking left side wheel 41a skiddings as an example, the second brake apparatus 63a brakes the 3rd gear ring 13a and the 3rd brake apparatus 64a brakes the 4th gear ring 23a, moves Power engagement device 65a is in engagement state, and the power that the 4th dynamotor 31a is produced can be exported to the of right side by the conjugation of power engagement device 65a The wheel 42a that common output is not skidded to right side after two planetary gears 2a, and the power coupling that can be produced with the 5th dynamotor 32a.

Thus, when left side wheel is skidded, the 4th dynamotor 31a in left side remains to the wheel output that power does not skid from right side, and the 4th dynamotor 31a substantially increases the ageing and success rate got rid of poverty without commutation.

Neutral position sliding：

Second brake apparatus 63a, the 3rd brake apparatus 64a and power engagement device 65a are completely in off-state, the 4th dynamotor 31a and the 5th dynamoelectric and power generation Machine 32a is in servo-actuated state.

Brake energy recovery：

Second brake apparatus 63a brakes the 3rd gear ring 13a and the 3rd brake apparatus 64a brakes the 4th gear ring 23a, and power engagement device 65a can be at off-state, makes Energy after respective power output shaft, planetary gears by exporting to corresponding dynamotor, so as to drive dynamotor to be generated electricity.

Drive system 100a in other embodiments is described referring to Fig. 9-Figure 11.

As Figure 9-Figure 11, the drive system 100a according to other embodiments of the invention can include the 4th dynamotor 31a and the 5th dynamotor 32a, First power output shaft 43a and the second power output shaft 44a, multigroup first planetary gears 1a and multigroup second planetary gears 2a and the second brake apparatus 63a, the 3rd brake apparatus 64a and power engagement device 65a.

As Figure 9-Figure 11, multigroup first planetary gears 1a (A1, A2 shown in Fig. 9-Figure 11) be arranged in series in the 4th dynamotor 31a with Between first power output shaft 43a, multigroup first planetary gears 1a is arranged to make the power from the 4th dynamotor 31a by speed change With it is rear output to the first power output shaft 43a, because multigroup first planetary gears 1a is arranged in series, thus the 4th dynamotor 31a power During output to the first power output shaft 43a, multigroup first planetary gears 1a can carry out chronotropic action to this partial power successively, play multistage Speed changing function.For example, each first planetary gears plays deceleration increases torsion effect, therefore multigroup first planetary gears 1a forms multi-stage speed-reducing effect Really, so as to improve the output torque of the 4th dynamotor 31a.

Similarly, multigroup second planetary gears 2a is arranged in series between the 5th dynamotor 32a and the second power output shaft 44a, and this multigroup second Planetary gears 2a is arranged to the power from the 5th dynamotor 32a by being exported after chronotropic action to the second power output shaft 44a, due to Multigroup second planetary gears 2a is arranged in series, thus the 5th dynamotor 32a power in output to during the second power output shaft 44a, should Multigroup second planetary gears 2a can carry out chronotropic action to this partial power successively, play multi-change speed function.For example, each second planetary gear machine Structure plays deceleration and increases torsion effect, therefore multigroup second planetary gears 2a forms multi-stage speed-reducing effect, so as to improve the 5th dynamotor 32a Output torque.

Multigroup first planetary gears 1a can be with coaxially arranged, and multigroup second planetary gears 2a can also be coaxially arranged, and multigroup first planetary gears 1a can overlap with the central axis of multigroup second planetary gears 2a.

First power output shaft 43a can be connected with a wheel 41a in the second of vehicle pair of wheel, the second power output shaft 44a can with second pair of wheel in it is another One wheel 42a is connected, and now dynamic coupling device 100 is used to drive pair of wheels.Wherein pair of wheels is a pair in a pair of front-wheels and a pair of rear wheels, the Two pairs of wheels are remaining a pair.

As Figure 9-Figure 11, each in the first planetary gears 1a and the second planetary gears 2a may each be simple planetary arrangement, the first planet Gear mechanism 1a can include sun gear, planetary gear, planet carrier and gear ring (multigroup first planetary gears 1a shares the gear ring, i.e., first and shares gear ring 13a).

Planetary gear is installed in planet carrier and is arranged between sun gear and gear ring, and planetary gear is engaged with sun gear and gear ring respectively.Planetary gear can be installed by planet wheel spindle In planet carrier, planetary gear can be multiple, and be uniformly distributed along the circumferentially-spaced of sun gear, such as in view of the stability and manufacturing cost of power transmission, planet Wheel can be three and be distributed on the outside of sun gear, and about 120 ° are spaced between two adjacent planetary gears.

Planetary gear is external toothing with the engagement system of sun gear.Planetary gear is internal messing with the engagement system of gear ring, that is to say, that form with teeth on the inner peripheral surface of gear ring, Planetary gear engages cooperation with the tooth on the inner peripheral surface of gear ring.Planetary gear can be around the axis rotation of planet wheel spindle, it is also possible to revolved round the sun around sun gear.

Similarly, the second planetary gears 2a can also include sun gear, planetary gear, planet carrier and gear ring (multigroup second planetary gears 2a shares the gear ring, I.e. second shares gear ring 23a).Also, relative position relation, annexation, interactively between each part etc. can be consistent with the first planetary gears 1a, therefore It is not detailed herein.Additionally, will also be combined below for multigroup first planetary gears 1a, annexation of multigroup second planetary gears 2a etc. specific Embodiment be described in detail.

As Figure 9-Figure 11, multigroup first planetary gears 1a share same first share gear ring 13a, multigroup second planetary gears 2a share same Second shares gear ring 23a.As a result, the structure of drive system 100a is compacter, volume is smaller, is more convenient arrangement.

Second brake apparatus 63a is arranged for braking first shared gear ring 13a, the 3rd brake apparatus 64a and is arranged for the shared gear ring 23a of braking second. Alternatively, the second brake apparatus 63a and the 3rd brake apparatus 64a can be brakes, but not limited to this.

As Figure 9-Figure 11, power engagement device 65a is arranged for engaging the first power output shaft 43a and the second power output shaft 44a, so that Formed between first power output shaft 43a and the second power output shaft 44a and be rigidly connected, and then the first power output shaft 43a and the second power output shaft 44a Can rotate in the same direction, at the same speed.That is, when power engagement device 65a is in engagement state, the first power output shaft 43a and the second power output shaft 44a keeps synchronization action state, and when power engagement device 65a is off, the first power output shaft 43a and the second power output shaft 44a can Carry out differential rotation, i.e. the first power output shaft 43a and the second power output shaft 44a can respectively with different rotational speed (can certainly same rotational speed turn It is dynamic).

Here, it is necessary to explanation, power engagement device 65a should make broad sense for engagement the first power output shaft 43a and the second power output shaft 44a to be managed Solution, such as power engagement device 65a can directly engage or disconnect the first power output shaft 43a and the second power output shaft 44a, and alternatively of course, power connects Attach together put 65a can also indirectly be realized by engaging or disconnecting other two parts the engagement of the first power output shaft 43a and the second power output shaft 44a with Disconnect, two parts can be the part being connected with the second power output shaft 44a with the first power output shaft 43a, such as planet carrier A23 and planet carrier B23.

Vehicle with drive system 100a according to embodiments of the present invention, such as when vehicle 10000 is travelled in flat road surface and along straight ahead, the second braking dress Putting 63a and the 3rd brake apparatus 64a can respectively brake the first shared gear ring 13a and second shared gear ring 23a, the 4th dynamotor 31a and the 5th dynamoelectric and power generation Machine 32a can with identical rotating speed export power, so by the decelerating effect of respective multigroup planetary gears, correspondence wheel obtain rotating speed be theoretically it is equal, Thereby guarantee that vehicle 10000 smoothly can advance along straight line.

And for example, when vehicle 10000 is travelled in uneven road surface or turning driving, the second brake apparatus 63a and the 3rd brake apparatus 64a can respectively brake first and share Gear ring 13a and second shares gear ring 23a, and now the rotating speed of the wheel of both sides can have speed discrepancy in theory, and by taking left-hand bend as an example, the radius of turn of left side wheel is smaller And the radius of turn of right side wheels is larger, in order to ensure to make PURE ROLLING between wheel and ground, the rotating speed of left side wheel is less than the rotating speed of right side wheels, now The output speed of four dynamotor 31a can be less than the output speed of the 5th dynamotor 32a, and specific speed discrepancy can come indirect by the steering angle of steering wheel Calculate, such as driver rotates counterclockwise steering wheel (turning left) certain angle, and the controller of vehicle 10000 can calculate vehicle 10000 based on the steering angle Radius of turn, after the radius of turn of vehicle 10000 determines, the relative rotation speed of both sides wheel difference is also determined, now the controllable 4th dynamotor 31a of controller Power is externally exported with the rotating speed for matching respectively with the 5th dynamotor 32a so that the speed discrepancy of the two can be matched with the speed discrepancy needed for wheel, so by two After the decelerating effect of group planetary gears, two wheels are obtained in that desired rotating speed, so as to realize pure rolling turning driving.

It is above-mentioned be using the 4th dynamotor 31a and the 5th dynamotor 32a as motor as a example by illustrate, certain 4th dynamotor 31a and the 5th electronic Generator 32a can also be used as generator operation.Now, similarly, the second brake apparatus 63a and the 3rd brake apparatus 64a can respectively brake first and share tooth Circle 13a and second shares gear ring 23a, and the 4th dynamotor 31a and the 5th dynamotor 32a can then be worked with generator forms, so as to reclaim braking energy. That is, externally exporting power as motor or as generator recovering energy and sent out in the 4th dynamotor 31a and the 5th dynamotor 32a When electric, the second brake apparatus 63a and the 3rd brake apparatus 64a brakes corresponding shared gear ring respectively all in on-position, and power engagement device 65a then locates In released state.

It is, of course, understood that above-mentioned multigroup first planetary gears 1a and multigroup second planetary gears 2a can use identical gearratio, also It is to say, using sun crop rotation as power intake and planet carrier is used as clutch end, two groups of planetary gears can use identical gearratio.Such as sun gear A11 With the sun gear B11 numbers of teeth, planetary gear A12 and the planetary gear B12 numbers of teeth, sun gear A21 and the sun gear B21 numbers of teeth, planetary gear A22 and the planetary gear B22 numbers of teeth, One shares the shared gear ring 23a numbers of teeth of gear ring 13a and second can be identical respectively.

Some embodiments of the invention, as Figure 9-Figure 11, when single wheel skidding occurs in vehicle, power engagement device 65a engages the first power output Axle 43a and the second power output shaft 44a, and the second brake apparatus 63a and the 3rd brake apparatus 64a brake respectively first share gear ring 13a and second be total to Gear ring 23a is used, the single wheel output that thus the 4th dynamotor 31a and the 5th dynamotor 32a can never skid the power of generation improves car Wheel skidding, improves the handling capacity of vehicle.

As Figure 9-Figure 11, the series system below to multigroup first planetary gears 1a and multigroup second planetary gears 2a is described in detail.Can be with Understand, the series system of multigroup first planetary gears 1a and multigroup second planetary gears 2a can so enable to drive system 100a to have with identical Have high symmetry, make drive system 100a center of gravity be more biased towards in drive system 100a zone line or be directly in zone line, thus, it is possible to improve vehicle Stability and front and rear weight than more reasonable.

Sun gear A11 and the 4th dynamotor the 31a linkage of first group of first planetary gears A1 in multigroup first planetary gears 1a, such as the 4th is electronic The rotor of generator 31a can coaxially be connected with sun gear A11,

Further, the planet carrier A23 of the first planetary gears A2 of last group in multigroup first planetary gears 1a is connected with the first power output shaft 43a, It is connected as coaxial.

Similarly, sun gear B11 and the 5th dynamotor the 32a linkage of first group of second planetary gears B1 in multigroup second planetary gears 2a, such as The rotor of the 5th dynamotor 32a can coaxially be connected with sun gear B11.The second planetary gears B2 of last group in multigroup second planetary gears 2a Planet carrier B23 be connected with the second power output shaft 44a, it is such as coaxial to be connected.

In a further embodiment, in multigroup first planetary gears 1a, the planet carrier A13 and later group planetary gear machine of the first planetary gears of previous group A1 The sun gear A21 of structure A2 is connected, such as coaxial to be connected, and in multigroup second planetary gears 2a, the planet carrier B13 of the second planetary gears of previous group B1 with The sun gear B21 of the second planetary gears of later group B2 is connected, such as coaxial to be connected.

For example, as Figure 9-Figure 11, the first planetary gears 1a and the second planetary gears 2a is two groups, first group of first planetary gears A1's Planet carrier A13 is connected with the sun gear A21 of the first planetary gears A2 of last group (namely second group).Equally, first group of second planetary gears B1 Planet carrier B13 be connected with the sun gear B21 of the second planetary gears B2 of last group (namely second group).

It should be noted that, although a kind of feasible planetary gears series system is given in above-described embodiment, but this feasible implementation method is only one kind to be shown Meaning explanation, it is impossible to be not understood as one kind limitation to the scope of the present invention, or imply required in this invention using above-mentioned series system.Those skilled in the art are reading On the basis of specification the above, above-mentioned series system can be modified and/or combined, and the new departure for being formed should belong to above-mentioned series system etc. Same implementation method, should fall under the scope of the present invention.

In addition it is also necessary to explanation, in description of the present invention about " dynamotor ", if without specified otherwise, the dynamotor can be understood as Motor with generator Yu motor function.

Used as optional implementation method, as shown in Fig. 9-Figure 10, power engagement device 65a can be clutch.Clutch includes the initiative part that can be engaged with each other and be separate 651a and secondary part 652a, active part 651a is divided to be connected with the first power output shaft 43a, secondary part 652a is connected with the second power output shaft 44a.

Certainly, the present invention is not limited thereto, and in further embodiments, as shown in figure 11, power engagement device 65a can be synchronizer, and synchronizer is arranged on first One in power output shaft 43a and the second power output shaft 44a is upper and for engaging another.

In addition, the 4th dynamotor 31a and the 5th dynamotor 32a can be such as arranged symmetrically, Duo Zu with symmetrical distribution on power engagement device 65a One planetary gears 1a symmetrical can also be distributed with multigroup second planetary gears 2a, is such as arranged symmetrically on power engagement device 65a, and the 4th electricity Dynamic generator 31a and the 5th dynamotor 32a can respectively be located at the opposite exterior lateral sides of multigroup first planetary gears 1a and multigroup second planetary gears 2a, That is, for example by taking Fig. 6 as an example, the outside that the 4th dynamotor 31a is located at multigroup first planetary gears 1a is left side, the 5th dynamotor 32a On the right side of the outside of multigroup second planetary gears 2a is.

Construction below in conjunction with the accompanying drawings to the drive system 100a in Fig. 9 embodiments, annexation and typical condition are described.

Shown in reference picture 9, the drive system 100a that the implementation is exemplified mainly includes two simple planetary arrangement A1, A2, two single planets on right side in left side Gear mechanism B1, B2, two dynamotor 31a, 32a and brake apparatus 63a, 64a and power engagement device 65a etc..

Specifically, two first planetary gears A1, the A2 in left side are arranged in series and share same first and share gear ring 13a, first group of first planetary gear The sun gear A11 of mechanism A1 is coaxially connected with the 4th dynamotor 31a, and first group of first planetary gear A12 of planetary gears A1 is installed on planet carrier A13, Planetary gear A12 shares gear ring 13a and engages with sun gear A11 and first respectively, planet carrier A13 and second group of first coaxial phase of sun gear A21 of planetary gears A2 Even, second group of first planetary gear A22 of planetary gears A2 is installed on planet carrier A23, and planetary gear A22 shares gear ring 13a with sun gear A21 and first respectively Engagement, planet carrier A23 is coaxially connected with the first power output shaft 43a, the first power output shaft 43a connection left side wheels 41a.Wherein, the first dynamotor 43a, Sun gear A11, sun gear A21 coaxially empty set on the first power output shaft 43a, the first power output shaft 43a can be left half axle.

Two second planetary gears 2a on right side are arranged in series and share same second and share gear ring 23a, first group of second sun gear of planetary gears B1 B11 is coaxially connected with the 5th dynamotor 32a, and first group of second planetary gear B12 of planetary gears B1 is installed on planet carrier B13, planetary gear B12 difference Gear ring 23a is shared with sun gear B11 and second to engage, planet carrier B13 is coaxially connected with the sun gear B21 of second group of second planetary gears B2, second group second The planetary gear B22 of planetary gears B2 is installed on planet carrier B23, and planetary gear B22 shares gear ring 23a and engages with sun gear B21 and second respectively, planet carrier B23 Coaxially it is connected with the second power output shaft 44a, the second power output shaft 44a connection right side wheels 42a.Wherein, the 5th dynamotor 32a, sun gear B11, too Sun wheel B21 coaxially empty set on the second power output shaft 44a, the second power output shaft 44a can be right axle shaft.

Second brake apparatus 63a shares gear ring 13a, the 3rd brake apparatus 64a for the shared gear ring 23a of braking second for braking first, and power engagement device 65a sets Put between multigroup first planetary gears 1a and multigroup second planetary gears 2a and defeated for being selectively engaged the first power output shaft 43a and the second power Shaft 44a.

The typical condition of the drive system 100a in Fig. 9 embodiments is described below.

Second brake apparatus 63a brakings first share gear ring 13a and the 3rd brake apparatus 64a brakes the second shared gear ring 23a, and power engagement device 65a is in and disconnects shape State.4th dynamotor 31a and the 5th dynamotor 32a can be worked with motorjbrm respectively.Thus, the power that the 4th dynamotor 31a is produced passes through The decelerating effect of two group of first planetary gears 1a is exported to the wheel 41a in left side, and the rotating speed of the 4th dynamotor 31a is in positive with the rotating speed of left side wheel 41a Close ground change.The power that 5th dynamotor 32a is produced after two group of second decelerating effect of planetary gears 2a by exporting to the wheel 42a on right side, the 5th electricity The rotating speed of dynamic generator 32a changes with being proportionate with the rotating speed of the wheel 42a on right side.

Skidding operating mode：

Schematically illustrate by taking left side wheel 41a skiddings as an example, the second brake apparatus 63a brakings first share gear ring 13a and the 3rd brake apparatus 64a brakings second share tooth Circle 23a, power engagement device 65a be in engagement state, the 4th dynamotor 31a produce power can be exported by the conjugation of power engagement device 65a to The wheel that common output is not skidded to right side after being coupled at second planetary gears on right side, and the power planet carrier B23 that can be produced with the 5th dynamotor 32a 42a。

Neutral position sliding：

Brake energy recovery：

Second brake apparatus 63a brakings first share gear ring 13a and the 3rd brake apparatus 64a brakings second share gear ring 23a, power engagement device 65a and can be at disconnection State, braking energy after respective power output shaft, planetary gears by exporting to corresponding dynamotor, so as to drive dynamotor to be generated electricity.

The drive system 100a of other embodiments is described in detail referring to Figure 12-Figure 16.

Shown in reference picture 12- Figure 16, power-driven system 100a according to embodiments of the present invention can include the first planetary gears 1a, the second planetary gears 2a, the 4th dynamotor 31a, the 5th dynamotor 32a, intermediate transmission component 4b and the second brake apparatus 61a.

Shown in reference picture 12- Figure 16, the first planetary gears 1a can be simple planetary arrangement, and the first planetary gears 1a can include the 3rd sun gear 11a, the third line star-wheel 12a, the third line carrier 14a and the 3rd gear ring 13a.The third line star-wheel 12a is arranged on the third line carrier 14a and is arranged on the 3rd sun gear Between 11a and the 3rd gear ring 13a, the third line star-wheel 12a is engaged with the 3rd sun gear 11a and the 3rd gear ring 13a respectively.The third line star-wheel 12a can be by planet wheel spindle On the third line carrier 14a, the third line star-wheel 12a can be multiple, and be uniformly distributed along the 3rd the circumferentially-spaced of sun gear 11a, for example, passed in view of power The stability and manufacturing cost passed, the third line star-wheel 12a can be three and be distributed on the outside of the 3rd sun gear 11a, adjacent two the third line star-wheel 12a it Between be spaced about 120 °.

Similarly, shown in reference picture 12- Figure 16, the second planetary gears 2a can be simple planetary arrangement, and the second planetary gears 2a can include the Four sun gear 21a, fourth line star-wheel 22a, fourth line carrier 24a and the 4th gear ring 23a.Fourth line star-wheel 22a is arranged on fourth line carrier 24a and is arranged on the Between four sun gear 21a and the 4th gear ring 23a, fourth line star-wheel 22a is engaged with the 4th sun gear 21a and the 4th gear ring 23a respectively.Fourth line star-wheel 22a can lead to Planet wheel spindle is crossed on fourth line carrier 24a, fourth line star-wheel 22a can be multiple, and be uniformly distributed along the 4th the circumferentially-spaced of sun gear 21a, for example, examine Consider the stability and manufacturing cost of power transmission, fourth line star-wheel 22a can be three and be distributed on the outside of the 4th sun gear 21a, two adjacent fourth lines About 120 ° are spaced between star-wheel 22a.

Used as preferred embodiment, as shown in figure 12, the third line star-wheel 12a can include coaxially arranged and synchronous axial system first gear portion 121a and second gear Portion 122a, first gear portion 121a is engaged with the 3rd sun gear 11a, and second gear portion 122a is engaged with the 3rd gear ring 13a.First gear portion 121a and second gear Portion 122a can be fixedly connected by same axis.First gear portion 121a can be small teeth portion and second gear portion 122a can be big gearing part, that is to say, that first The number of teeth of gear part 121a can be less than the number of teeth of second gear portion 122a, and thus the power of the 4th dynamotor 31a outputs is through first gear portion 121a, second When gear part 122a is transmitted, first gear portion 121a and second gear portion 122a constitute reducing gear, realize to increase the deceleration of the 4th dynamotor 31a and turn round effect Really.Optionally, of course, first gear portion 121a can also be big gearing part and second gear portion 122a can be small teeth portion.

Similarly, as shown in figure 12, fourth line star-wheel 22a can include coaxially arranged and synchronous axial system the 3rd gear part 221a and the 4th gear part 222a, the 3rd Gear part 221a is engaged with the 4th sun gear 21a, and the 4th gear part 222a is engaged with the 4th gear ring 23a.3rd gear part 221a and the 4th gear part 222a can be with It is fixedly connected by same axis.3rd gear part 221a can be small teeth portion and the 4th gear part 222a can be big gearing part, that is to say, that the 3rd gear part 221a The number of teeth can be less than the 4th gear part 222a the number of teeth, thus the 5th dynamotor 32a output power through the 3rd gear part 221a, the 4th gear part 222a During transmission, the 3rd gear part 221a and the 4th gear part 222a constitute reducing gear, realize to increase the deceleration of the 5th dynamotor 32a and turn round effect.Certainly, Alternatively, the 3rd gear part 221a can also be big gearing part and the 4th gear part 222a can be small teeth portion.

Wherein, above-mentioned the third line carrier 14a and fourth line carrier 24a can as the clutch end of power-driven system 100a, such as the third line carrier 14a and Fourth line carrier 24a can the power of ultromotivity in future source such as the 4th dynamotor 31a and/or the 5th dynamotor 32a externally export, such as output to wheel 41a, 42a.Alternatively, the third line carrier 14a and fourth line carrier 24a can respectively link with two wheels 41a, 42a in second pair of wheel, so that third planet The power output of power-driven system 100a can be given wheel 41a, 42a by frame 14a and fourth line carrier 24a so that vehicle 10000 being capable of normally travel.

For example, above-mentioned dynamic coupling device 100 can drive the pair of wheels, the third line carrier 14a and fourth line carrier 24a can respectively to drive second pair of wheel, Wherein pair of wheels is a pair in a pair of front-wheels and a pair of rear wheels, and second pair of wheel is remaining a pair.

Shown in reference picture 12- Figure 16, the 4th dynamotor 31a and the 3rd sun gear 11a links, and the rotor of such as the 4th dynamotor 31a can be with the 3rd sun gear 11a is coaxially connected, but not limited to this.

Shown in reference picture 12- Figure 16, intermediate transmission component 4b is arranged to be linked with the 3rd gear ring 13a and the 4th gear ring 23a respectively, and intermediate transmission component 4b can set Put between the 3rd gear ring 13a and the 4th gear ring 23a, the 3rd gear ring 13a, intermediate transmission component 4b and the 4th gear ring 23a are acted or geo-stationary simultaneously.

Second brake apparatus 61a is arranged for braking intermediate transmission component 4b, when the second brake apparatus 61a brakes intermediate transmission component 4b, the 3rd gear ring 13a Also it is braked indirectly with the 4th gear ring 23a, and after the second brake apparatus 61a release intermediate transmission components 4b, intermediate transmission component 4b, the 3rd gear ring 13a and the 4th Gear ring 23a can coupled movements.

Thus, when the second brake apparatus 61a is in on-position, intermediate transmission component 4b, the 3rd gear ring 13a and the 4th gear ring 23a are braked, and the 4th is electronic The power that generator 31a is produced can be exported to the wheel 41a in corresponding wheel such as left side after the 3rd sun gear 11a, the third line star-wheel 12a from the third line carrier 14a, The power that 5th dynamotor 32a is produced can be exported to corresponding wheel such as right side after the 4th sun gear 21a, fourth line star-wheel 22a from fourth line carrier 24a Wheel 42a, two motors separately control the rotating speed of correspondence wheel, it is achieved thereby that differential function.

For example, being travelled in flat road surface when vehicle 10000 and during along straight ahead, the 4th dynamotor 31a and the 5th dynamotor 32a can be with identical rotating speeds Output power, so by the decelerating effect of respective planetary gears, it is theoretically equal that correspondence wheel obtains rotating speed, thereby guarantees that vehicle 10000 can be smoothed out Advanced along straight line on ground.

And for example, when vehicle 10000 is travelled in uneven road surface or turning driving, now can there is speed discrepancy in the rotating speed of the wheel of both sides in theory, by taking left-hand bend as an example, The radius of turn of left side wheel is smaller and the radius of turn of right side wheels is larger, and in order to ensure to make PURE ROLLING between wheel and ground, the rotating speed of left side wheel is less than The rotating speed of right side wheels, now the output speed of the 4th dynamotor 31a can be less than the output speed of the 5th dynamotor 32a, and specific speed discrepancy can be by The steering angle of steering wheel is calculated indirectly, and such as driver rotates counterclockwise steering wheel (turning left) certain angle, and the controller of vehicle 10000 is based on the steering Angle can calculate the radius of turn of vehicle 10000, and after the radius of turn of vehicle 10000 determines, the relative rotation speed difference of both sides wheel is also determined, now controller Controllable 4th dynamotor 31a and the 5th dynamotor 32a externally exports power with the rotating speed for matching respectively so that the speed discrepancy of the two can with needed for wheel Speed discrepancy matching, so by the way that after two decelerating effects of planetary gears, two wheels are obtained in that desired rotating speed, so as to realize pure rolling turning driving.

It is above-mentioned be using the 4th dynamotor 31a and the 5th dynamotor 32a as motor as a example by illustrate, certain 4th dynamotor 31a and the 5th electronic Generator 32a can also be used as generator operation.Now, similarly, the second brake apparatus 61a still can brake intermediate transmission component 4b, the 4th dynamotor 31a and the 5th dynamotor 32a can then be worked with generator forms, so as to reclaim braking energy.

It is, of course, understood that the first above-mentioned planetary gears 1a and the second planetary gears 2a can use identical gearratio, that is to say, that with Sun gear as power intake and planet carrier as clutch end for, two planetary gears can use identical gearratio.That is, the 3rd sun gear 11a The number of teeth and the number of teeth (internal tooth) of the 3rd gear ring 13a and the 4th gear ring 23a of the number of teeth, the third line star-wheel 12a and fourth line star-wheel 22a with the 4th sun gear 21a Can be identical respectively.

To sum up, power-driven system 100a according to embodiments of the present invention, by the braking action of the second brake apparatus 61a, it is possible to achieve the 4th dynamotor 31a With the electric-only mode or Brake energy recovery pattern of the 5th dynamotor 32a, and by individually control the 4th dynamotor 31a and the 5th dynamotor 32a Output speed, can make the wheel of both sides obtain different moments of torsion, realize differential function.Additionally, power-driven system 100a parts according to embodiments of the present invention it is few, Compact conformation is simple, takes small volume, arrangement of being more convenient for.

The power-driven system 100a according to further embodiment of the present invention is described in detail below in conjunction with Figure 12-Figure 16.

When vehicle 10000 is travelled under poor load conditions, such as vehicle 10000 is travelled on the road surfaces such as more muddy or soft gravel road or sandy soil, By taking muddy road conditions as an example, vehicle 10000 may be absorbed in soil and cause idle running, that is to say, that vehicle 10000 there occurs that skidding (skidding and causes The reason for skidding be well known to a person skilled in the art).

There is bigger difference with conventional carrier again because power-driven system 100a according to embodiments of the present invention has on differential function, but structure, it is impossible to using tradition Differential self-locking structure.In order to improve vehicle 10000 by property, improve adaptability of the vehicle 10000 to poor road conditions, the power drive of some embodiments of the invention System 100a is on the premise of differential function is realized, moreover it is possible to further realize auto-lock function.

Some embodiments of the invention, for example, can combine shown in Figure 15 and Figure 16, and power-driven system 100a also includes the 3rd brake apparatus 62a, the 3rd system Dynamic device 62a is arranged for braking the third line carrier 14a or fourth line carrier 24a, that is to say, that as skidding occurs in vehicle 10000 under some specific operations, 3rd brake apparatus 62a can optionally brake the third line carrier 14a or fourth line carrier 24a, more specifically, the 3rd brake apparatus 62a now brake slip one The corresponding planet carrier of side wheel.

So that two wheels 41a, 42a in the third line carrier 14a and fourth line carrier 24a second pair of wheel respectively with vehicle 10000 are connected as an example, one wherein When there is skidding in wheel, the corresponding planet carrier of the 3rd brake apparatus 62a brake slip single wheels so that the dynamotor of skidding side will can be produced Power exported to the wheel of other side by intermediate transmission component 4b, so it is common with after the dynamotor power coupling of other side will couple power output extremely this Other side is the wheel not skidded, so as to improve the ability of getting rid of poverty of vehicle 10000.

The wheel 41a of reference picture 15- Figure 16, such as left side skids, then the third line carrier 14a on the left of the 3rd brake apparatus 62a brakings, according to the fortune of planetary gears Dynamic characteristic, the power that now the 4th dynamotor 31a in left side is produced can be exported by the 3rd gear ring 13a, and the 3rd gear ring 13a passes through intermediate transmission component 4b Linked with the 4th gear ring 23a on right side, therefore the power that produces of the 4th dynamotor 31a can be transferred to the 4th gear ring 23a on right side, now the 5th electronic hair on right side Motor 32a can equally export power, and two parts power is exported to the non-slip wheel 42a on right side after the fourth line carrier 24a couplings on right side, that is to say, that two Motor can export power by non-slip single wheel, so as to substantially increase the ability of getting rid of poverty of vehicle 10000.

It is understood that now the second brake apparatus 61a discharges intermediate transmission component 4b, i.e. the second brake apparatus 61a now not braking intermediate transmission component 4b.

In the embodiment that can realize differential auto-lock function more of the invention, the 3rd brake apparatus 62a can be the parking braking system (not shown) of vehicle 10000, The parking braking system is arranged to optionally individually to a wheel system in (with the third line carrier 14a and fourth line carrier 24a linkages) pair of wheels It is dynamic, so as to realize the braking action pair the planet carrier being connected with the wheel.For example, when left side wheel is skidded, parking braking system can an independent brake left side wheel Corresponding left side planet carrier (e.g., the third line carrier 14a), or when right side wheels are skidded, parking braking system can a corresponding right side of independent brake right side wheels Planet carrier (e.g., fourth line carrier 24a).

Certainly, the present invention is not limited thereto, and such as the 3rd brake apparatus 62a can also be the service braking system of vehicle 10000, its realize differential auto-lock function with it is upper State parking braking system basically identical, be not described in detail for purposes of brevity here.

Need explanation a bit, above-mentioned parking braking system or service braking system may have with existing known and widely used parking braking system or service braking system Institute is different.Schematically illustrate by taking parking braking system as an example, existing widely used parking braking system is usually the (example while being braked to pair of wheels such as a pair of rear wheels Such as braked by cable pull rear wheel brake hoof), and parking braking system according to embodiments of the present invention is required to two lists of wheel in realizing to pair of wheels Solely braking, such as independent brake left rear wheel (now off hind wheel can be non-brake state) or independent brake off hind wheel (now left rear wheel can be non-brake state).Due to this Field those of ordinary skill has known the construction and operation principle of traditional parking braking system, therefore those of ordinary skill in the art only need to make letter to traditional parking braking system Single deformation and/or modification, so that two wheels that parking braking system according to embodiments of the present invention can be individually to pair of wheels carry out optionally individually system Dynamic, such as parking braking system has two subsystems, each subsystem one wheel of independent correspondence, such as one of subsystem can be by a cable pull left side Rear wheel brake hoof is braked, and another subsystem can be then that to be braked by another cable pull off hind wheel brake shoe (be only here to illustrate by taking drag-line as an example Property, can for example use other any existing modes and its equivalent way that can be realized, naturally it is also possible to use powered version).

Based on it is similar the reasons why, service braking system may be also different from existing widely used service braking system, and certainly, those skilled in the art are knowing the present invention During the difference of the parking braking system of embodiment and traditional parking braking system, have for service braking system and traditional service braking system of the embodiment of the present invention Difference be also it will be appreciated that and can realize, therefore be not detailed herein.

Used as the embodiment of still further aspect, power-driven system 100a has zero of braking function when differential auto-lock function is realized, or by setting other Part is realized.

As in certain embodiments, as shown in figure 15, the 3rd brake apparatus 62a is arranged to optionally be bonded to the third line carrier 14a or fourth line carrier 24a On the housing of power-driven system 100a, so as to realize the braking action to the third line carrier 14a or fourth line carrier 24a.

Further, as shown in figure 16, the 3rd brake apparatus 62a can be two such as the 3rd brake apparatus 621a, 622a, and correspond to the third line carrier 14a and the respectively Four planet carrier 24a, that is to say, that each planet carrier one the second brake apparatus of correspondence, two the 3rd brake apparatus 621a, the 622a can not do independently of one another, mutually Work with relating to.Certainly, as shown in figure 15, the third line carrier 14a and fourth line carrier 24a can also share same 3rd brake apparatus 62a.Alternatively, the 3rd Brake apparatus 62a can be synchronizer or brake etc., but not limited to this.

Mistake presented hereinbefore, vehicle 10000 can be braked, so as to realize by the 3rd brake apparatus 62a when skidding to the corresponding planet carrier of skidding single wheel The purpose that skidding side motor exports power by the non-slip wheel of opposite side, now skidding side motor with do not skid side motor may while externally export power, by , used as preferred embodiment, when single wheel skidding occurs in wheel, each dynamotor is worked and from start to finish according to same direction rotation with motorjbrm for this. Thus, the motor of two motor particularly skidding sides need not commutate reversion, which not only simplifies control strategy, while it is stranded also to shorten vehicle 10000 Time, contribute to it is quick, efficiently get rid of poverty.

It is, of course, understood that when the 4th dynamotor 31a and the 5th dynamotor 32a participates in driving vehicle 10000 to advance, two dynamotor Can also be rotated according to same direction from start to finish.

So, when wheel moves ahead and traveling enters poor road conditions suddenly, such as there is single wheel skidding, then by controlling the 3rd brake apparatus 62a to skidding side The corresponding planet carrier of wheel is braked so that power is run through intermediate transmission component 4b and is transferred to opposite side by the dynamotor of the side, and electronic with opposite side Directly exported after generator power coupling, during this period, because the motor of skidding side is without reversion, i.e., without stopping, commutating rotation again, therefore is beaten there is wheel During sliding phenomenon, two motors can quickly carry out power coupling, and drive the wheel of side of not skidding jointly, and substantially increase that vehicle 10000 gets rid of poverty is ageing.

When quickly realizing power coupling by how realizing motor without commutation, those skilled in the art should be designed full based on principle disclosed herein The intermediate transmission component 4b that foot is required.The present invention is schematically illustrated with a specific embodiment here, however, it is to be understood that following embodiments is only Schematically, a kind of limitation to the scope of the present invention is not to be construed as, or implies that power-driven system 100a must be using the middle biography with following constructions Dynamic component 4b.Those skilled in the art, should be to following embodiments and its equivalent after the above-mentioned principle of specification and following specific embodiments has been read In technical characteristic modify and/or replace, and after modification formed embodiment should also be as falling under the scope of the present invention.

For example, referring to shown in Figure 12-Figure 16, intermediate transmission component 4b can include jackshaft 41b, be provided with jackshaft 41b jackshaft first gear 42b and in Countershaft second gear 44b, wherein jackshaft first gear 42b can be by intermediate idler 43b and the 3rd gear ring 13a linkages, jackshaft second gear 44b and the 4th gear rings 23a links.Certainly, as a kind of modification, alternatively, jackshaft second gear 44b can be linked by intermediate idler 43b and the 4th gear ring 23a, then jackshaft first Gear 42b and the 3rd gear ring 13a links.

Jackshaft first gear 42b and jackshaft second gear 44b can be fixedly installed on jackshaft 41b, and jackshaft first gear 42b and jackshaft second The radial dimension of gear 44b is preferably difference, and the radial dimension of the countershaft-gear for for example being engaged with intermediate idler 43b is relatively small, such as in the embodiment of Fig. 9-Figure 13 In, the radial dimension of the radial dimension less than jackshaft second gear 44b of jackshaft first gear 42b.Axial direction thereby, it is possible to ensure jackshaft 41b is defeated with power The reliability and stability for axially retaining consistent, improve transmission of shaft (semiaxis) or motor.

Further, external tooth 131a, 231a are respectively arranged with the outer peripheral face of the 3rd gear ring 13a and the 4th gear ring 23a, jackshaft first gear 42b passes through intermediate idler The external tooth 131a linkages of 43b and the 3rd gear ring 13a, such as external tooth 131as of the intermediate idler 43b respectively with jackshaft first gear 42b and the 3rd gear ring 13a is engaged.In The external tooth 231a linkages of countershaft second gear 44b and the 4th gear ring 23a, such as jackshaft second gear 44b is directly engaged with the external tooth 231a of the 4th gear ring 23a.

In the embodiment of Figure 12-Figure 16, the second brake apparatus 61a can be brake and for brake intermediate shaft 41b.So that power-driven system 100a is tied Structure is relatively more compact, is easy to arrangement.

The kind of drive between planet carrier and wheel is carried out below schematically illustrate.

Power-driven system 100a can be arranged on the third line carrier 14a including the first power output shaft 43a and the second power output shaft 44a, the first power output shaft 43a Between a wheel 41a in second pair of wheel of vehicle 10000, the second power output shaft 44a is arranged on another in second pair of wheel of fourth line carrier 24a and this Between one wheel 42a, the pair of wheels can be a pair of front-wheels, naturally it is also possible to be a pair of rear wheels.

Used as optional implementation method, the 4th dynamotor 31a and the 3rd sun gear 11a can coaxially empty set be on the first power output shaft 43a, and the 5th is electronic Generator 32a and the 4th sun gear 21a can coaxially empty set on the second power output shaft 44a so that the structure of power-driven system 100a is compacter. In addition, the 4th dynamotor 31a and the 5th dynamotor 32a can be with symmetrical distribution, the first planetary gears 1a and the second planetary gears 2a Can be with symmetrical distribution, and the 4th dynamotor 31a and the 5th dynamotor 32a can respectively be located at the first planetary gears 1a and the second planetary gear The opposite exterior lateral sides of mechanism 2a, that is to say, that for example by taking Figure 12 as an example, the outside that the 4th dynamotor 31a is located at the first planetary gears 1a is left side, the 5th The outside that dynamotor 32a is located at the second planetary gears 2a is right side.

As optional implementation method, as shown in figure 11, the first reduction gear component 51a is also provided between the first power output shaft 43a and the third line carrier 14a, The second reduction gear component 52a is additionally provided between second power output shaft 44a and fourth line carrier 24a.The structure of the first reduction gear component 51a and the second reducing gear The structure of wheel assembly 52a can be with identical, it is possible thereby to improve the versatility of reduction gear component, reduces cost.And it is defeated by the power in power-driven system 100a Go out between end and wheel and such gear reduction assemblies are set, additionally it is possible to preferably play the effect slowed down and increase and turn round.

Construction below in conjunction with the accompanying drawings to the power-driven system 100a in Figure 12 embodiments, annexation and typical condition are described.

Shown in reference picture 12, the power-driven system 100a that the implementation is exemplified mainly include two simple planetary arrangement 1a, 2a, two dynamotor 31a, 32a and intermediate transmission component 4b, brake apparatus 61a, 62a etc..

Jackshaft first gear 42b is fixedly installed on jackshaft 41b and jackshaft second gear 44b, the second brake apparatus 61a can be for brakes and for braking centre Axle 41b, jackshaft first gear 42b can be linked by the external tooth 131a of intermediate idler 43b and the 3rd gear ring 13a, and jackshaft second gear 44b can directly with the The external tooth 231a linkages of four gear ring 23a.

3rd brake apparatus 62a is arranged for optionally braking the third line carrier 14a or fourth line carrier 24a, it is to be understood that this braking can To be directly braking, can certainly be braking indirectly.

The typical condition of the power-driven system 100a in Figure 12 embodiments is described below.

Second brake apparatus 61a brake intermediate shaft 41b, so that the 3rd gear ring 13a and the 4th gear ring 23a are braked indirectly.4th dynamotor 31a and the 5th electronic Generator 32a can be worked with motorjbrm respectively.Thus, the power that the 4th dynamotor 31a is produced is by the 3rd sun gear 11a, the third line star-wheel 12a, the Rotating speed and the rotating speed of left side wheel 41a that three planet carrier 14a, the first power output shaft 43a are transferred to the wheel 41a, the 4th dynamotor 31a in left side are proportionate Ground change.The power that 5th dynamotor 32a is produced passes through the 4th sun gear 21a, fourth line star-wheel 22a, fourth line carrier 24a, the second power output shaft 44a The wheel 42a on right side is transferred to, the rotating speed of the 5th dynamotor 32a changes with being proportionate with the rotating speed of the wheel 42a on right side.

Skidding operating mode：

Schematically illustrate by taking left side wheel 41a skiddings as an example, the 3rd brake apparatus 62a will brake the third line carrier 14a, while the second brake apparatus 61a is off. 4th dynamotor 31a will produce power by the 3rd sun gear 11a, the third line star-wheel 12a, the third line carrier 14a, the 3rd gear ring 13a, intermediate idler 43b, Jackshaft first gear 42b, jackshaft 41b, jackshaft second gear 44b, the 4th gear ring 23a are exported to fourth line carrier 24a, are simultaneously from the 5th electronic hair The power of motor 32a is also exported to fourth line carrier 24a, is exported from the second power output shaft 44a after two parts power coupling to the wheel 42a on right side.Thus, on a left side During the wheel-slip of side, the 4th dynamotor 31a in left side remains to the wheel output that power does not skid from right side, and the 4th dynamotor 31a is without commutation, Substantially increase the ageing and success rate got rid of poverty.

Neutral position sliding：

Second brake apparatus 61a and the 3rd brake apparatus 62a are completely in off-state, and the 4th dynamotor 31a and the 5th dynamotor 32a is in servo-actuated shape State.

Brake energy recovery：

Second brake apparatus 61a brake intermediate shafts 41b, the 3rd brake apparatus 62a are off, and braking energy passes through respective power output shaft, planetary gear machine Exported after structure to corresponding dynamotor, so as to drive dynamotor to be generated electricity.

Vehicle 10000 according to embodiments of the present invention is briefly described below, shown in Figure 17, the vehicle 10000 includes the power-driven system 1000 in above-described embodiment With drive system 100a, the power-driven system 1000 in Fig. 1-Fig. 5 can serve as forerunner, so that the dynamic coupling device 100 of power-driven system 1000 drives one To front-wheel, and the drive system 100a in Fig. 6-Figure 16 then can be used for rear-guard.Additionally, vehicle 10000 shown in Figure 18, it can only include power drive line The predecessor portions of system 1000.Certainly, the present invention is not limited thereto.It should be appreciated that other construction such as braking systems of vehicle 10000 according to embodiments of the present invention System, driving system, steering etc. have been prior art, and are well known to those skilled in the art, therefore are no longer repeated one by one here.

In the description of this specification, the description of reference term " one embodiment ", " some embodiments ", " example ", " specific example " or " some examples " etc. Mean that the specific features, structure, material or the feature that are described with reference to the embodiment or example are contained at least one embodiment of the invention or example.In this specification In, the schematic representation to above-mentioned term is necessarily directed to identical embodiment or example.And, the specific features of description, structure, material or feature can be with Combined in an appropriate manner in one or more any embodiments or example.Additionally, those skilled in the art can be by the different embodiments described in this specification Or example is engaged and combined.

Although embodiments of the invention have been shown and described above, it is to be understood that above-described embodiment is exemplary, it is impossible to be interpreted as limitation of the present invention, One of ordinary skill in the art can be changed to above-described embodiment, change, replacing and modification within the scope of the invention.

Claims

1. a kind of power-driven system, it is characterised in that including：

Dynamic coupling device, the dynamic coupling device includes：

First sun gear, the first planet carrier and the first gear ring and the second sun gear, the second planet carrier and the second gear ring, wherein first gear ring with Second gear ring is coaxially connected；

Input shaft, the input shaft is arranged to optionally be linked with first gear ring and second gear ring；

Power source, the power source is arranged to be linked with the input shaft；

First dynamotor, the second dynamotor, first dynamotor link with first sun gear, second dynamotor and described second Sun gear links；And

The first brake apparatus directly or indirectly braked to first gear ring and second gear ring.

2. power-driven system according to claim 1, it is characterised in that also include：

Jackshaft, the jackshaft links with first gear ring and second gear ring, and the input shaft optionally links with the jackshaft.

3. power-driven system according to claim 2, it is characterised in that the input shaft and the jackshaft by the synchronous effect of synchronizer optionally Linked.

4. power-driven system according to claim 3, it is characterised in that the input shaft overhead set is provided with input shaft free gear, solid on the jackshaft Surely the fixed gear of jackshaft first is provided with, the input shaft free gear is engaged with the fixed gear of the jackshaft first, and the synchronizer is arranged on the input shaft And for engaging the input shaft free gear.

5. power-driven system according to claim 1, it is characterised in that the power source includes：Engine and the 3rd dynamotor, the engine with 3rd dynamotor links with the input shaft respectively.

6. power-driven system according to claim 2, it is characterised in that also include：Intermediate gearing, the jackshaft passes through the intermediate gearing Linked with first gear ring and second gear ring.

7. power-driven system according to claim 6, it is characterised in that the intermediate gearing is gear drive.

8. power-driven system according to claim 7, it is characterised in that the intermediate gearing includes：

Outer toothed portion, the outer toothed portion and first gear ring and the second gear ring coaxial linkage；With

The fixed gear of jackshaft second on the jackshaft is fixedly installed on, the outer toothed portion is engaged with the fixed gear of the jackshaft second.

9. power-driven system according to claim 6, it is characterised in that the intermediate gearing is tape handler, chain-drive mechanism or CVT drivers Structure.

10. power-driven system according to claim 2, it is characterised in that first brake apparatus be arranged on the jackshaft and by brake it is described in Countershaft is braked indirectly to first gear ring and second gear ring.

11. power-driven systems according to claim 1, it is characterised in that first planet carrier and second planet carrier are used as the power-driven system Clutch end.

12. power-driven systems according to claim 11, it is characterised in that the first planet carrier output gear, institute have been coaxially disposed on first planet carrier State and the second planet carrier output gear has been coaxially disposed on the second planet carrier.

13. power-driven systems according to claim 1, it is characterised in that first dynamotor passes through first gear mechanism with first sun gear Linkage, second dynamotor is linked with second sun gear by second gear mechanism.

14. power-driven systems according to claim 13, it is characterised in that the first gear mechanism is identical with the construction of the second gear mechanism.

15. power-driven systems according to claim 1, it is characterised in that first sun gear is identical with the number of teeth of second sun gear, described first The first planetary gear is provided between sun gear and first gear ring, the second planetary gear, first planet are provided between second sun gear and second gear ring Wheel is identical with the number of teeth of second planetary gear, and first gear ring is identical with the number of teeth of second gear ring.

16. power-driven systems according to claim 1, it is characterised in that first sun gear, first planet carrier and first gear ring are accommodated in Inside first dynamotor, second sun gear, second planet carrier and second gear ring are accommodated in inside second dynamotor.

17. power-driven system according to any one of claim 1-16, it is characterised in that

The dynamic coupling device is used to drive the pair of wheels of vehicle；

The power-driven system also includes：

4th dynamotor and the 5th dynamotor；

First power output shaft and the second power output shaft and multigroup first planetary gears and multigroup second planetary gears, multigroup first planet gear mechanism Structure is arranged in series between the 4th dynamotor and first power output shaft and can be by the power from the 4th dynamotor by after chronotropic action Output to first power output shaft, multigroup second planetary gears be arranged in series between the 5th dynamotor and second power output shaft and Can be by the power from the 5th dynamotor by being exported after chronotropic action to second power output shaft, wherein multigroup first planetary gears is common Gear ring is shared with same first, multigroup second planetary gears shares same second and shares gear ring, and first power output shaft is suitable to second with vehicle A wheel in wheel is connected, and second power output shaft is suitable to be connected with another wheel in second pair of wheel, and the pair of wheels is for before a pair A pair in wheel and a pair of rear wheels, second pair of wheel is the another pair in a pair of front-wheels and a pair of rear wheels；

Second brake apparatus and the 3rd brake apparatus, second brake apparatus are arranged for braking described first and share gear ring, and the 3rd brake apparatus is arranged to use Gear ring is shared in braking described second；And

Power engagement device, the power engagement device is arranged for engagement first power output shaft and second power output shaft.

18. power-driven system according to any one of claim 1-16, it is characterised in that

The dynamic coupling device is used to drive the pair of wheels of vehicle；

The power-driven system also includes：

First planetary gears and the second planetary gears, first planetary gears include：3rd sun gear, the third line carrier and the 3rd gear ring, institute Stating the second planetary gears includes：4th sun gear, fourth line carrier and the 4th gear ring；

4th dynamotor and the 5th dynamotor, the 4th dynamotor and the 3rd sun gear link, and the 5th dynamotor and the 4th sun gear join It is dynamic；

First power output shaft and the second power output shaft, first power output shaft are arranged on a wheel in second pair of wheel of the third line carrier and vehicle Between, second power output shaft is arranged between another wheel in the fourth line carrier and second pair of wheel, and the pair of wheels is a pair of front-wheels With a pair in a pair of rear wheels, second pair of wheel is the another pair in a pair of front-wheels and a pair of rear wheels；

Second brake apparatus and the 3rd brake apparatus, second brake apparatus are arranged for braking the 3rd gear ring, and the 3rd brake apparatus is arranged for system Move the 4th gear ring；And

19. power-driven system according to any one of claim 1-16, it is characterised in that

The dynamic coupling device is used to drive the pair of wheels of vehicle；

The power-driven system also includes：

First planetary gears and the second planetary gears, first planetary gears include：3rd sun gear, the third line carrier and the 3rd gear ring, institute Stating the second planetary gears includes：4th sun gear, fourth line carrier and the 4th gear ring, wherein the third planet frame and the fourth line carrier are defeated as power Go out end to drive second pair of wheel, the pair of wheels is a pair in a pair of front-wheels and a pair of rear wheels, during second pair of wheel is a pair of front-wheels and a pair of rear wheels Another pair；

Intermediate transmission component, the intermediate transmission component is arranged to be linked with the 3rd gear ring and the 4th gear ring respectively；

Second brake apparatus, second brake apparatus is arranged for braking the intermediate transmission component.

20. a kind of vehicles, it is characterised in that including the power-driven system according to any one of claim 1-19.