CN104859419B

CN104859419B - Change-speed box, Power Train are unified vehicle

Info

Publication number: CN104859419B
Application number: CN201510024082.8A
Authority: CN
Inventors: 刘静; 华煜
Original assignee: BYD Co Ltd
Current assignee: BYD Co Ltd
Priority date: 2015-01-16
Filing date: 2015-01-16
Publication date: 2016-04-13
Anticipated expiration: 2035-01-16
Also published as: CN104859419A

Abstract

The invention discloses a kind of change-speed box, power drive system, vehicle, change-speed box comprises: multiple input shaft; Multiple output shaft; Motor mechanical axis, motor mechanical axis overhead cover is provided with motor power axle first gear and motor mechanical axis second gear, motor mechanical axis first gear is arranged to link with in input shaft, and motor mechanical axis second gear is arranged to link with in output shaft; Auxiliary output shaft, auxiliary output shaft is provided with multiple auxiliary gear driven gear, and each auxiliary gear driven gear is all by the gear driven gear transmission on intermediate idler and output shaft.Change-speed box of the present invention, has enriched transmission mode, can realize the various working such as parking charging and the driving limit charging of driving engine limit.

Description

Change-speed box, Power Train are unified vehicle

Technical field

The present invention relates to technical field of vehicle, the vehicle especially relating to a kind of change-speed box, there is the power drive system of this change-speed box, there is this power drive system.

Background technology

Along with the continuous consumption of the energy, the development and utilization of new forms of energy vehicle becomes a kind of trend gradually.Hybrid vehicle, as the one in new forms of energy vehicle, is driven by driving engine and/or motor, has various modes, can improve driving efficiency and fuel economy.

But in correlation technique known for inventor, the change-speed box general structure in hybrid vehicle is complicated, and transmission mode is few, and driving efficiency is on the low side.Such as, for most hybrid vehicle, it often realizes process of charging when driving, and charge mode, charge path etc. are comparatively single, and charge efficiency is poor.

Summary of the invention

The present invention is intended to solve one of above-mentioned technical matters of the prior art at least to a certain extent.

For this reason, the present invention proposes a kind of change-speed box, this change-speed box can enrich the transmission mode of power drive system at least to a certain extent.

The invention allows for a kind of power drive system with above-mentioned change-speed box, this power drive system has abundant transmission mode.

The invention allows for a kind of vehicle, this vehicle comprises above-mentioned power drive system.

According to the change-speed box for vehicle of the embodiment of the present invention, comprising: multiple input shaft, each described input shaft is provided with gear driving gear; Multiple output shaft, each described output shaft is provided with gear driven gear, and described gear driven gear engages accordingly with described gear driving gear; Motor mechanical axis, described motor mechanical axis is provided with motor mechanical axis first gear, described motor mechanical axis first gear empty set is on described motor mechanical axis, described motor mechanical axis first gear is arranged to optionally engage described motor mechanical axis with synchronous axial system, and described motor mechanical axis first gear is also arranged to link with in described input shaft; And auxiliary output shaft, described auxiliary output shaft is provided with multiple auxiliary gear driven gear, gear driven gear on each described auxiliary gear driven gear and described output shaft links, and each described auxiliary gear driven gear is identical with the hand of rotation of the corresponding gear driven gear linked.

According to the change-speed box of the embodiment of the present invention, enrich transmission mode, the various working such as parking charging and the driving limit charging of driving engine limit can have been realized.

The power drive system of embodiment according to a further aspect of the invention, comprises the change-speed box in above-described embodiment and the first dynamotor, and described first dynamotor is arranged to link with described motor mechanical axis.

According to the power drive system of the embodiment of the present invention, there is abundant transmission mode.

The vehicle of embodiment according to a further aspect of the present invention, comprises the power drive system in above-described embodiment.

Accompanying drawing explanation

Fig. 1 is the schematic diagram of the change-speed box according to the embodiment of the present invention;

Fig. 2 is the schematic diagram of power drive system according to an embodiment of the invention;

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

Fig. 4 is the schematic diagram of the power drive system according to another embodiment of the present invention;

Fig. 5 is the schematic diagram of the power drive system according to another embodiment of the present invention;

Fig. 6 is the schematic diagram of change-speed box according to an embodiment of the invention.

Detailed description of the invention

Be described below in detail embodiments of the invention, the example of described embodiment is shown in the drawings, and wherein same or similar label represents same or similar element or has element that is identical or similar functions from start to finish.Be exemplary below by the embodiment be described with reference to the drawings, be intended to for explaining the present invention, and can not limitation of the present invention be interpreted as.

In describing the invention, it will be appreciated that, term " " center ", " longitudinal direction ", " transverse direction ", " length ", " width ", " thickness ", " on ", D score, " front ", " afterwards ", " left side ", " right side ", " vertically ", " level ", " top ", " end " " interior ", " outward ", " cw ", orientation or the position relationship of the instruction such as " conter clockwise " are based on orientation shown in the drawings or position relationship, only the present invention for convenience of description and simplified characterization, instead of indicate or imply that the device of indication or element must have specific orientation, with specific azimuth configuration and operation, therefore limitation of the present invention can not be interpreted as.

In addition, term " first ", " second " only for describing object, and can not be interpreted as instruction or hint relative importance or imply the quantity indicating indicated technical characteristic.Thus, be limited with " first ", the feature of " second " can express or impliedly comprise one or more these features.In describing the invention, the implication of " multiple " is 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 ", " being connected ", " connection ", " fixing " should be interpreted broadly, and such as, can be fixedly connected with, also can be removably connect, or integral; Can be mechanical connection, also can be electrically connected maybe can communicate with one another; Can be directly be connected, also indirectly can be connected by intermediary, can be the connection of two element internals or the interaction relationship of two elements.For the ordinary skill in the art, above-mentioned term concrete meaning in the present invention can be understood as the case may be.

In the present invention, unless otherwise clearly defined and limited, fisrt feature second feature it " on " or D score can comprise the first and second features and directly contact, also can comprise the first and second features and not be directly contact but by the other characterisation contact between them.And, fisrt feature second feature " on ", " top " and " above " comprise fisrt feature directly over second feature and oblique upper, or only represent that fisrt feature level height is higher than second feature.Fisrt feature second feature " under ", " below " and " below " comprise fisrt feature immediately below second feature and tiltedly below, or only represent that fisrt feature level height is less than second feature.

Below in conjunction with Fig. 1-Fig. 5, the power drive system 100 according to the embodiment of the present invention is described in detail, this power drive system 100 is applicable in the vehicle of such as hybrid vehicle, and as the power system of vehicle, for normal vehicle operation provides sufficient power and electric energy.

Power drive system 100 according to the embodiment of the present invention mainly comprises two large divisions, one can be propulsion source, propulsion source can be driving engine 4, dynamotor etc., it two can be change-speed box 101, change-speed box 101, for realizing the speed changing function to propulsion source outputting power, meets vehicle driving requirements or charging requirement etc.

Such as, in certain embodiments, as Figure 1-Figure 5, power drive system 100 can comprise driving engine 4, first dynamotor 51 and change-speed box 101, but is not limited thereto.

Shown in composition graphs 1, in certain embodiments, change-speed box 101 mainly comprises multiple input shaft (such as, first input shaft 11, second input shaft 12), multiple output shaft (such as, first output shaft 21, second output shaft 22), associated gear and shifting element (e.g., synchro) on motor mechanical axis 3, auxiliary output shaft 85 and each axle.

When carrying out transmission of power between driving engine 4 and input shaft, driving engine 4 is arranged to optionally engage at least one in multiple input shaft.In other words, such as, when driving engine 4 is to input shaft transmission power, driving engine 4 optionally can engage to transmit power with in multiple input shaft, or driving engine 4 can also optionally engage to transmit power with two or more input shafts in multiple input shaft simultaneously.

Such as, in the example of Fig. 1-Fig. 5, multiple input shaft can comprise the first input shaft 11 and the second input shaft 12 two input shafts, and driving engine 4 optionally can engage to transmit power with one of the first input shaft 11 and second input shaft 12.Or especially, driving engine 4 can also engage to transmit power with the first input shaft 11 and the second input shaft 12 simultaneously.Certainly, should be understood that, driving engine 4 also can disconnect with the first input shaft 11 and the second input shaft 12 simultaneously.

For the ordinary skill in the art, driving engine 4 is relevant with the concrete operating mode of power drive system 100 to the engagement state of input shaft, and this will describe in detail below in conjunction with specific embodiments, no longer describes in detail here.

Transmission can be carried out by shift gear pair between input shaft and output shaft.Such as, each input shaft is provided with gear driving gear, each output shaft is provided with gear driven gear, gear driven gear engages accordingly with gear driving gear, thus forms the different gear pair of multipair speed ratio.

As Figure 1-Figure 5, auxiliary output shaft 85 is provided with multiple auxiliary gear driven gear (such as nine gear driven gear 9b, ten gear driven gear 10b, 11 gear driven gear 11b), each auxiliary gear driven gear is all by the gear driven gear transmission on intermediate idler and output shaft.

Such as, in the example of Fig. 1-Fig. 5, auxiliary gear driven gear can be three, these three auxiliary gear driven gears are respectively by three the gear driven gears transmission on an intermediate idler and the second output shaft 22, thus three gear driven gears on this second output shaft 22, the shift gear that formation three groups is had different speed ratio by corresponding intermediate idler and above-mentioned three auxiliary gear driven gears is secondary, like this when increase output shaft and auxiliary output shaft 85, the quantity of shift gear pair can be increased further, make change-speed box 101 have more gear to select.

Such as, in certain embodiments, change-speed box 101 can be 11 forward gear change-speed boxs 101, namely has first gear pair, second gear is secondary, three gear gear pairs, four gear gear pairs, five gear gear pairs, six gear gear pairs, seven gear gear pairs, eight gear gear pairs, nine gear gear pairs, ten gear gear pairs, ten first gears are secondary.But the present invention is not limited to this, for the ordinary skill in the art, can increase or reduce the number of shift gear pair by comformability according to transmission needs, be not limited to 11 forward gear transmissions shown in the embodiment of the present invention.

Secondary about concrete shift gear, will be described in detail in conjunction with specific embodiments below, no longer describe in detail here.

Below in conjunction with Fig. 1-Fig. 5, the structure of motor mechanical axis 3 is described in detail.Motor mechanical axis 3 can be provided with motor mechanical axis synchro 33c, motor mechanical axis first gear 31 and motor mechanical axis second gear 32.

Specifically, motor mechanical axis first gear 31 and the equal empty set of motor mechanical axis second gear 32 are arranged on motor mechanical axis 3, that is, motor mechanical axis 3 and motor mechanical axis first gear 31 can rotate by differential, similarly, motor mechanical axis 3 and motor mechanical axis second gear 32 also can rotate by differential.

Further, motor mechanical axis synchro 33c is arranged between motor mechanical axis first gear 31 and motor mechanical axis second gear 32, the sliding hub of motor mechanical axis synchro 33c can along the axial motion of motor mechanical axis 3, such as in the example of Fig. 1-Fig. 5, the sliding hub of motor mechanical axis synchro 33c can the axis along motor mechanical axis 3 under the driving of shifting fork mechanism move to the left or to the right.

Motor mechanical axis synchro 33c is owing to being arranged between motor mechanical axis first gear 31 and motor mechanical axis second gear 32, and therefore one of motor mechanical axis first gear 31 and motor mechanical axis second gear 32 can optionally engage with motor mechanical axis 3 by motor mechanical axis synchro 33c.

The example of composition graphs 1-Fig. 5, motor mechanical axis first gear 31 can engage with motor mechanical axis 3 to left movement by the sliding hub of motor mechanical axis synchro 33c vertically, thus makes motor mechanical axis 3 and motor mechanical axis first gear 31 can synchronous axial system.The sliding hub of motor mechanical axis synchro 33c moves right vertically and motor mechanical axis second gear 32 can be engaged with motor mechanical axis 3, thus makes motor mechanical axis 3 and motor mechanical axis second gear 32 can synchronous axial system.

Certainly, be understandable that, the sliding hub of motor mechanical axis synchro 33c also can remain on center position (such as, initial position), and now the sliding hub of motor mechanical axis synchro 33c and motor mechanical axis first gear 31 and motor mechanical axis second gear 32 disconnect respectively.

In addition, need to illustrate a bit, engage with motor mechanical axis synchro 33c for the ease of motor mechanical axis first gear 31, motor mechanical axis second gear 32, the side towards motor mechanical axis synchro 33c of motor mechanical axis first gear 31 and motor mechanical axis second gear 32 can be provided with joint gear ring, this should be all easy understand for the ordinary skill in the art.

As Figure 1-Figure 5, motor mechanical axis first gear 31 is arranged to link with in input shaft (such as the second input shaft 12), and motor mechanical axis second gear 32 is arranged to link with in output shaft (such as the second output shaft 22).

It should be noted that, above-mentioned " interlock " can be understood as multiple parts (such as, two) coupled movements, and for two parts interlocks, wherein during a component movement, another parts also move thereupon.

Such as, in some embodiments of the invention, gear and axle link and can be understood as is also will rotate when gear rotates, with the axle of its interlock, or also will rotate when this axle rotates, with the gear of its interlock.

And for example, axle and axle link can be understood as and are when an axle rotates wherein, also will rotate with another root axle of its interlock.

For another example, gear and gear-linked can be understood as is also will rotate when a gear rotates wherein, with another gear of its interlock.

Under the invention in the description of face about " interlock ", if there is no specified otherwise, be all understood in this way.

Thus, motor mechanical axis 3 by motor mechanical axis synchro 33c synchronous (synchronous namely to motor mechanical axis first gear 31 or motor mechanical axis second gear 32) and optionally link with one of input shaft or link with one of output shaft.Specifically, motor mechanical axis synchro 33c can carry out synchronously to motor mechanical axis first gear 31, namely motor mechanical axis synchro 33c can engage motor mechanical axis first gear 31 and motor mechanical axis 3, thus motor mechanical axis 3 can link with in input shaft (such as, second input shaft 12).And for example, in some instances, motor mechanical axis synchro 33c can carry out synchronously to motor mechanical axis second gear 32, namely motor mechanical axis synchro 33c can engage motor mechanical axis second gear 32 and motor mechanical axis 3, thus motor mechanical axis 3 can link with in output shaft (such as, second output shaft 22).

Similarly, the first dynamotor 51 is arranged to link with motor mechanical axis 3.Such as, the first dynamotor 51, can by the Power output of generation to motor mechanical axis 3 when working as electrical motor.And for example, when the first dynamotor 51 is as generator operation, the power from motor mechanical axis 3 can export the first dynamotor 51 to, thus drives the first dynamotor 51 to generate electricity.

Here, need to illustrate a bit, in the description of the present invention about " dynamotor ", if do not have specified otherwise, it is the motor with electrical generator and motor function that this dynamotor can be understood as.

Also need to illustrate a bit, in describing the invention, motor mechanical axis 3 can be the motor shaft of the first dynamotor 51 self.Certainly, be understandable that, the motor shaft of motor mechanical axis 3 and the first dynamotor 51 also can be two independent axles.

As mentioned above, motor mechanical axis first gear 31 links with in input shaft, especially, one in motor mechanical axis first gear 31 with input shaft when link, the first dynamotor 51 can utilize at least part of power exported from driving engine 4 to generate electricity when vehicle traveling and parking.

In other words, when vehicle is in motoring condition, at least part of power of driving engine 4 can export the first dynamotor 51 to by the first motor gear 71, motor mechanical axis first gear 31, thus drives the first dynamotor 51 to generate electricity, and realizes driving limit, driving engine 4 limit charging operating mode.And when vehicle is in parking (vehicle stops but driving engine 4 is still in running order), at least part of power of driving engine 4 can export the first dynamotor 51 to by the first motor gear 71, motor mechanical axis first gear 31, thus drive the first dynamotor 51 to generate electricity, realize parking charge function (i.e. " STOP " charging).

Thus, according to the power drive system 100 of the embodiment of the present invention, charge function can be realized when vehicle traveling and parking, enrich charge mode, at least to some extent solved the problems such as existing power drive system charging modes is single, charge efficiency is low.In brief, driving charging can be realized according to the power drive system 100 of the embodiment of the present invention and parking is charged two class charge modes.

Be described below in conjunction with the linked manner of accompanying drawing to motor mechanical axis first gear 31 and input shaft and motor mechanical axis second gear 32 and output shaft.

In certain embodiments, described one (as the second input shaft 12) in input shaft is fixedly installed the first motor gear 71, motor mechanical axis first gear 31 is arranged to link with the first motor gear 71.Further, motor mechanical axis first gear 31 by intermediate drive gear 84 and the first motor gear 71 transmission, in other words, intermediate drive gear 84 respectively with motor mechanical axis first gear 31 and the first motor gear 71 engaged transmission.In the example of Fig. 1-Fig. 5, intermediate drive gear 84 can empty set on the second output shaft 22, but to be not limited thereto.

Described one (as the second output shaft 22) in output shaft is fixedly installed the second motor gear 72, and motor mechanical axis second gear 32 engages with the second motor gear 72.

Below in conjunction with Fig. 1-Fig. 5, structure of reversing gear is described in detail.Structure of reversing gear mainly comprises reverse output gear 86, and reverse output gear 86 is arranged to link with one of them gear driven gear, and such as reverse output gear 86 can keep off driven gear 2b engaged transmission with two, but is not limited thereto.

Further, reverse output gear 86 can empty set on auxiliary output shaft 85, can reverse gear shaft be omitted thus, make the structure of change-speed box 101 compacter.Auxiliary output shaft 85 is also provided with reverse gear synchronizer 86c, and reverse gear synchronizer 86c is arranged at least for engaging reverse output gear 86 and auxiliary output shaft 85, thus the power that reverses gear through reverse output gear 86 can be exported by auxiliary output shaft 85.

As preferred embodiment, described in linking with reverse output gear 86, one of them gear driven gear can be dual gear, a gear pair 22b of this dual gear engages with corresponding gear driving gear (such as 24 keep off driving gear 24a), another gear pair 21b of dual gear engages with reverse output gear 86, reverse output gear 86 and one of them gear driven gear described is so not only facilitated to link, avoid interfering with other parts, and pass through the number of teeth of reasonable design dual gear, the required speed ratio that reverses gear can also be obtained.

Embodiment below in conjunction with Fig. 1-Fig. 5 is described in detail input shaft, output shaft and each shift gear.

In some embodiments of the present invention, as Figure 1-Figure 5, input shaft can be two, namely input shaft comprises the first input shaft 11 and the second input shaft 12, second input shaft 12 can be hollow shaft, and the first input shaft 11 can be solid axle, and a part for the first input shaft 11 can be embedded in the second hollow input shaft 12, another part of first input shaft 11 can be protruding vertically in the second input shaft 12, and the first input shaft 11 and the second input shaft 12 can be coaxially arranged.

Output shaft can be multiple, and as the first output shaft 21 and the second output shaft 22, first output shaft 21 and the second output shaft 22 are arranged in parallel with input shaft, the first output shaft 21 and the second output shaft 22 can be solid axle.

11 advance gears can be had according to the power drive system 100 of the embodiment of the present invention, particularly, first input shaft 11 can be arranged odd number gear driving gear, second input shaft 12 can be arranged even number gear driving gear, thus the first input shaft 11 is responsible for the transmission of power of odd number shift gear pair, the second input shaft 12 is responsible for the transmission of power of even number shift gear pair.

More specifically, as Figure 1-Figure 5, first input shaft 11 can be furnished with a gear driving gear 1a, three or five gear driving gear 35a and seven gear driving gear 7a, second input shaft 12 can be furnished with two or four gear driving gear 24a, six or eight gear driving gear 68a, each gear driving gear is all with the input shaft synchronous axial system of correspondence.

Accordingly, first output shaft 21 is provided with a gear driven gear 1b, four gear driven gear 4b, five gear driven gear 5b, eight gear driven gear 8b, second output shaft 22 is provided with two gear driven gear 2b, three gear driven gear 3b, six gear driven gear 6b and seven gear driven gear 7b, the equal empty set of each driven gear is on the output shaft of correspondence, and namely each driven gear can rotate by differential relative to the output shaft of correspondence.

Wherein, one gear driven gear 1b and keeps off driving gear 1a and engages thus form first gear pair, two gear driven gear 2b and two or four keep off driving gear 24a and engage thus form second gear pair, three gear driven gear 3b and three or five keep off driving gear 35a and engage thus form three and keep off gear pair, four gear driven gear 4b and two or four keep off driving gear 24a and engage thus form four and keep off gear pair, five gear driven gear 5b and three or five keep off driving gear 35a and engage thus form five and keep off gear pair, six gear driven gear 6b and six or eight keep off driving gear 68a and engage thus form six and keep off gear pair, seven gear driven gear 7b and seven keep off driving gear 7a and engage thus form seven and keep off gear pair, eight gear driven gear 8b and six or eight keep off driving gear 68a and engage thus form eight and keep off gear pair.

Because second gear is secondary and four gear gear pairs share two or four gear driving gear 24a, six gear gear pairs and eight gear gear pairs share six or eight gear driving gear 68a, therefore can reduce by two driving gears, such that the structure of power drive system 100 is compacter, size is less, be convenient to arrange.

Owing to being empty set structure between driven gear and output shaft, therefore needing, synchro is set and carries out synchronous to corresponding driven gear with output shaft, to realize the output of power.

In certain embodiments, shown in composition graphs 1-Fig. 5, power drive system 100 comprises First Five-Year Plan gear synchro 15c, two or six gear synchro 26c, pseudo-ginseng gear synchro 37c and four or eight gear synchro 48c.

As shown in Figure 1, First Five-Year Plan gear synchro 15c to be arranged on the first output shaft 21 and to keep off between driven gear 5b at a gear driven gear 1b and five, one gear driven gear 1b or five gear driven gear 5b can engage with the first output shaft 21 by First Five-Year Plan gear synchro 15c, thus enables this driven gear and output shaft synchronous axial system.

Such as, shown in composition graphs 1, the sliding hub of First Five-Year Plan gear synchro 15c is moved to the left and five gear driven gear 5b can be engaged with the first output shaft 21, thus five gear driven gear 5b and the first output shaft 21 can synchronous axial system.The sliding hub of First Five-Year Plan gear synchro 15c moves right and a gear driven gear 1b can be engaged with the first output shaft 21, thus a gear driven gear 1b and the first output shaft 21 can synchronous axial system.

As shown in Figure 1, four or eight gear synchro 48c are arranged on the first output shaft 21, four or eight gear synchro 48c are between four gear driven gear 4b and eight gear driven gear 8b, four or eight gear synchro 48c are used for four gear driven gear 4b or eight gear driven gear 8b to engage with the first output shaft 21, such as the sliding hub of four or eight gear synchro 48c moves right, then eight gear driven gear 8b can be engaged with the first output shaft 21, thus eight gear driven gear 8b and the first output shaft 21 synchronous axial system, the sliding hub of four or eight gear synchro 48c is moved to the left, then four gear driven gear 4b can be engaged with the first output shaft 21, thus four gear driven gear 4b and the first output shaft 21 synchronous axial system.

As shown in Figure 1, similarly, two or six gear synchro 26c to be arranged on the second output shaft 22 and to keep off between driven gear 6b at two gear driven gear 2b and six, two gear driven gear 2b or six gear driven gear 6b can engage with the second output shaft 22 by two or six gear synchro 26c, thus enable this driven gear and output shaft synchronous axial system.

Such as, shown in composition graphs 1, the sliding hub of two or six gear synchro 26c is moved to the left and two gear driven gear 2b can be engaged with the second output shaft 22, thus two gear driven gear 2b and the second output shaft 22 synchronous axial system.The sliding hub of two or six gear synchro 26c moves right and six gear driven gear 6b can be engaged with the second output shaft 22, thus six gear driven gear 6b and the second output shaft 22 synchronous axial system.

As shown in Figure 1, similarly, pseudo-ginseng gear synchro 37c is arranged on the second output shaft 22, pseudo-ginseng gear synchro 37c is between three gear driven gear 3b and seven gear driven gear 7b, pseudo-ginseng gear synchro 37c is used for three gear driven gear 3b or seven gear driven gear 7b to engage with the second output shaft 22, such as the sliding hub of pseudo-ginseng gear synchro 37c is moved to the left, then three gear driven gear 3b can be engaged with the second output shaft 22, thus three gear driven gear 3b and the second output shaft 22 synchronous axial system, the sliding hub of pseudo-ginseng gear synchro 37c moves right, then seven gear driven gear 7b can be engaged with the second output shaft 22, thus seven gear driven gear 7b and the second output shaft 22 synchronous axial system.

Further, auxiliary gear driven gear comprises nine gear driven gear 9b, ten gear driven gear 10b and 11 gear driven gear 11b, and intermediate idler comprises the first intermediate idler 81, second intermediate idler 82 and the 3rd intermediate idler 83, wherein ten gear driven gear 10b keep off driven gear 6b by the first intermediate idler 81 and six and engage to form ten gear gear pairs, nine gear driven gear 9b keep off driven gear 3b by the second intermediate idler 82 and three and engage to form nine gear gear pairs, 11 gear driven gear 11b keep off driven gear 7b by the 3rd intermediate idler 83 and seven and engage to form ten first gears pairs.

Thus, nine gear gear pairs, ten gear gear pairs, ten first gear pairs utilize three gear driven gears, six gear driven gears and seven gear driven gears to serve as driving gear respectively, and the adjustment of gear rotational speed is realized by setting up intermediate idler, change-speed box 101 is made to add three gears, simultaneously structure relative compact.

Further, as preferred embodiment, ten gear driven gear 10b and reverse output gear 86 share reverse gear synchronizer 86c, and in other words, reverse output gear 86 or ten gear driven gear 10b can optionally engage with auxiliary output shaft 85 by reverse gear synchronizer 86c.The such as embodiment of composition graphs 1-Fig. 5, the sliding hub of reverse gear synchronizer 86c is moved to the left and can engages auxiliary output shaft 85 and reverse output gear 86, and the sliding hub of reverse gear synchronizer 86c moves right and can engage auxiliary output shaft 85 and ten gear driven gear 10b.

Similarly, be provided with 91 gear synchro 911c between nine gear driven gear 9b and 11 gear driven gear 11b, nine gear driven gear 9b or 11 gear driven gear 11b can optionally engage with auxiliary output shaft 85 by 91 gear synchro 911c.The such as embodiment of composition graphs 1-Fig. 5, the sliding hub of 91 gear synchro 911c is moved to the left and can engages auxiliary output shaft 85 and nine gear driven gear 9b, and the sliding hub of 91 gear synchro 911c moves right and can engage auxiliary output shaft 85 and 11 gear driven gear 11b.

Wherein, all empty set is on motor mechanical axis 3 for the first intermediate idler 81, second intermediate idler 82 and the 3rd intermediate idler 83, and compact conformation thus, is convenient to gear transmission.

In some embodiments of the invention, can transmission of power be carried out by double-clutch 2d or be separated between the first input shaft 11 of driving engine 4 and change-speed box 101 and the second input shaft 12.

Shown in Fig. 1-Fig. 5, double-clutch 2d has input end 23d, the first mouth 21d and the second mouth 22d, driving engine 4 is connected with the input end 23d of double-clutch 2d, specifically, driving engine 4 can pass through the various ways such as flywheel, bumper or reverse plate and is connected with the input end 23d of double-clutch 2d.

The first mouth 21d of double-clutch 2d is connected with the first input shaft 11, thus this first mouth 21d and the first input shaft 11 synchronous rotary.The second mouth 22d of double-clutch 2d is connected with the second input shaft 12, thus this second mouth 22d and the second input shaft 12 synchronous rotary.

Wherein, the input end 23d of double-clutch 2d can be the housing of double-clutch 2d, and its first mouth 21d and the second mouth 22d can be two clutch plates.Usually, housing and two clutch plates can all disconnect, namely input end 23d and the first mouth 21d and the second mouth 22d all disconnects, when needs engage one of them clutch plate, housing can be controlled carry out engaging thus synchronous rotary with corresponding clutch plate, namely input end 23d engages with one of the first mouth 21d and the second mouth 22d, thus the power that input end 23d transmits can by an output in the first mouth 21d and the second mouth 22d.

Especially, housing also can engage with two clutch plates simultaneously, namely input end 23d also can engage with the first mouth 21d and the second mouth 22d simultaneously, thus the power that input end 23d transmits can be exported by the first mouth 21d and the second mouth 22d simultaneously.

Be to be understood that, the concrete engagement state of double-clutch 2d is controlled the impact of strategy, for a person skilled in the art, can transmission mode needed for reality and adaptive settings control policy, thus can switch in the various modes that input end 23d all disconnects with two mouths and input end 23d and two mouths one of at least engage.

Below in conjunction with Fig. 1-Fig. 5, the annexation between three power take-off shafts (i.e. the first output shaft 21, second output shaft 22 and auxiliary output shaft 85) and differential for vehicles 75 is described in detail.

The diff 75 of vehicle can be arranged between a pair front-wheel 76 or between pair of rear wheels 77, and in examples more of the present invention, diff 75 is between a pair front-wheel 76.The function of diff 75 is when turn inside diameter travels or travels on uneven road surface, and driving wheels is rolled with different cireular frequencys, to ensure two side drive wheel and ground intercropping PURE ROLLING.Diff 75 is provided with main reduction gear driven gear 74, such as main reduction gear driven gear 74 can be arranged on the housing of diff 75.Main reduction gear driven gear 74 can be finishing bevel gear cuter, but is not limited thereto.

Further, first output shaft 21 is fixedly installed the first output shaft output gear 211, first output shaft output gear 211 is with the first output shaft 21 synchronous axial system, first output shaft output gear 211 and main reduction gear driven gear 74 engaged transmission, thus main reduction gear driven gear 74 and diff 75 can be passed to from the first output shaft output gear 211 from the power of the first output shaft 21.

Similarly, second output shaft 22 is fixedly installed the second output shaft output gear 221, second output shaft output gear 221 is with the second output shaft 22 synchronous axial system, second output shaft output gear 221 and main reduction gear driven gear 74 engaged transmission, thus main reduction gear driven gear 74 and diff 75 can be passed to from the second output shaft output gear 221 from the power of the second output shaft 22.

Auxiliary output shaft 85 is fixedly installed auxiliary output shaft output gear 851, auxiliary output shaft output gear 851 is with auxiliary output shaft 85 synchronous axial system, auxiliary output shaft output gear 851 and main reduction gear driven gear 74 engaged transmission, thus main reduction gear driven gear 74 and diff 75 can be passed to from auxiliary output shaft output gear 851 from the power of auxiliary output shaft 85.

Driving limit, limit charging operating mode simultaneously in joint situation of power generation in parking, double-clutch 2d and operating mode of reversing gear is comprised according to some typical conditions of the power drive system 100 of the embodiment of the present invention.

First describe this typical condition of power generation in parking, when vehicle is in parked state, driving engine 4 is arranged to export the power of generation to first dynamotor 51 by the first motor gear 71, thus drives the first dynamotor 51 to generate electricity.

Specifically, specific embodiment shown in composition graphs 1-Fig. 5, the power of generation can generate electricity as electrical generator to drive the first dynamotor 51 by exporting to the first dynamotor 51 after the second input shaft 12, first motor gear 71, motor mechanical axis first gear 31, motor mechanical axis 3 by driving engine 4.

Thus, achieve power generation in parking function, enriched charge mode, and under power generation in parking operating mode, vehicle remains static, the power of driving engine 4 all for charging, can improve charge efficiency, realizes quick function of supplying power.

Secondly the limit driving limit charging operating mode of double-clutch 2d simultaneously in joint situation is described, under this operating mode, wherein a part of power can be exported to wheel using the power travelled as vehicle by a wherein output shaft by conjugation while input end 23d and the first mouth 21d and the second mouth 22d by driving engine 4, and another part power is exported to the first dynamotor 51 by the first motor gear 71, thus the first dynamotor 51 is driven to generate electricity.

Specifically, the specific embodiment of composition graphs 1-Fig. 5 example, under this operating mode, a part of power of driving engine 4 generates electricity as electrical generator to drive the first dynamotor 51 by exporting to the first dynamotor 51 after the second input shaft 12, first motor gear 71, motor mechanical axis first gear 31, motor mechanical axis 3.

Simultaneously, another part power of driving engine 4 exports from the first output shaft 21 by the first input shaft 11, first gear pair or five gear gear pairs, or exported from the second output shaft 22 by three gear gear pairs or seven gear gear pairs, or exported from auxiliary output shaft 85 by nine gear gear pairs or ten first gears pair.

Because tradition has in the power drive system of double-clutch, double-clutch 2d only has a power-transfer clutch in running order at synchronization, and achieve the breakthrough application to double-clutch 2d according to the power drive system 100 of the embodiment of the present invention, i.e. under two whole engagement states of power-transfer clutch of double-clutch 2d (input end 23d engages the first mouth 21d and the second mouth 22d simultaneously), a part of power of driving engine 4 is exported by an output shaft drives vehicle to travel, another part power then exports to the first dynamotor 51, drive motor generates electricity, enrich transmission mode, take into account vehicle to travel and charging requirement.

Again describe and to reverse gear pattern, especially, according to the power drive system 100 of the embodiment of the present invention, there is machinery and to reverse gear pattern, electronic pattern and mixed dynamic pattern three kinds of patterns of reversing gear of reversing gear of reversing gear.

The machinery pattern of reversing gear is the car-backing function utilizing the power of driving engine 4 to realize vehicle, vehicle be in machinery reverse gear pattern time, the power of generation is exported from reverse output gear 86 synchronous effect of reverse output gear 86 by reverse gear synchronizer 86c as propulsion source by driving engine 4.

Specifically, shown in composition graphs 1-Fig. 5, driving engine 4 exports by the second input shaft 12, dual gear (two gear driven gear 2b) power produced to reverse output gear 86, by the synchronous effect of reverse gear synchronizer 86c to reverse output gear 86, the power that reverses gear that driving engine 4 is exported exports eventually through auxiliary output shaft 85.

In brief, vehicle be in machinery reverse gear pattern time, as shown in Figure 1, only have reverse gear synchronizer 86c engage reverse output gear 86.

The electronic pattern of reversing gear is the car-backing function utilizing the first dynamotor 51 to realize vehicle, vehicle be in electronic reverse gear pattern time, the power of generation is exported from the second motor gear 72 synchronous effect of motor mechanical axis second gear 32 by motor mechanical axis synchro 33c as propulsion source by the first dynamotor 51.Particularly, as Fig. 1-Fig. 5 so, motor mechanical axis synchro 33c engages motor mechanical axis second gear 32, thus the power that the first dynamotor 51 produces is successively by exporting from the second output shaft 22 after motor mechanical axis 3, motor mechanical axis second gear 32, second motor gear 72.Now, motor mechanical axis synchro 33c is only had to engage motor mechanical axis second gear 32.

Or the power of generation is exported from reverse output gear 86 synchronous effect of reverse output gear 86 synchronous effect of motor mechanical axis first gear 31 and reverse gear synchronizer 86c by motor mechanical axis synchro 33c as propulsion source by the first dynamotor 51.

Specifically, under this path, motor mechanical axis synchro 33c engages motor mechanical axis first gear 31 and reverse gear synchronizer 86c engages power that reverse output gear 86, first dynamotor 51 produces by exporting from the second output shaft 22 after motor mechanical axis 3, motor mechanical axis first gear 31, first motor gear 71, second input shaft 12, two gear driven gear 2b, reverse output gear 86.

The mixed dynamic pattern of reversing gear is the car-backing function simultaneously utilizing driving engine 4 and the first dynamotor 51 to realize vehicle, and the mixed dynamic pattern of reversing gear is that above-mentioned machinery reverses gear the combination of pattern and the first electronic pattern of reversing gear.

Vehicle be in mixed dynamic reverse gear pattern time, be divided into two kinds of mixed conditions of starting building:

The first mixed condition of starting building is: the power of generation is exported from reverse output gear 86 synchronous effect of reverse output gear 86 by reverse gear synchronizer 86c as dynamic origin by driving engine 4.

Meanwhile, the power of generation is exported from the second motor gear 72 synchronous effect of motor mechanical axis second gear 32 by motor mechanical axis synchro 33c as another propulsion source by the first dynamotor 51.

Thus the power from driving engine 4 and the first dynamotor 51 finally can export after the coupling of main reduction gear driven gear 74 place.

Now, the first dynamotor 51 can carry out speed governing, makes main reduction gear driven gear 74 synchronously can receive power from driving engine 4 and the first dynamotor 51 evenly, improves ride comfort, the harmony of transmission.

The mixed condition of starting building of the second is: the power of generation is exported from reverse output gear 86 synchronous effect of reverse output gear 86 by reverse gear synchronizer 86c as dynamic origin by driving engine 4.That is, to export the path of power of reversing gear constant for driving engine 4.

Meanwhile, the power of generation is exported from reverse output gear 86 synchronous effect of reverse output gear 86 synchronous effect of motor mechanical axis first gear 31 and reverse gear synchronizer 86c by motor mechanical axis synchro 33c as another propulsion source by the first dynamotor 51.

In other words, first the power that reverses gear from reverse gear power and first dynamotor 51 of driving engine 4 be coupled at the second input shaft 12 place, and the power after coupling is exported from reverse output gear 86 by two gear driven gear 2b.

Now, the first dynamotor 51 can carry out speed governing, makes the second input shaft 12 synchronously can receive power from driving engine 4 and the first dynamotor 51 evenly, improves ride comfort, the harmony of transmission.

Thus, this power drive system 100 can realize three kinds of patterns of reversing gear, and namely machinery reverses gear pattern, electronic pattern and the mixed dynamic pattern of reversing gear of reversing gear, and has enriched operating mode of reversing gear, can switch in these three kinds of patterns of reversing gear flexibly according to actual conditions, meet driving demand.

Such as, when Vehicular battery carrying capacity abundance, electronic pattern of reversing gear can be adopted, so not only can not discharge of noxious gases when moveing backward, and can also energy consumption be reduced, move backward for position for new chaufeur especially, operation may be needed repeatedly could to pour vehicle into assigned address, and driving engine 4 is owing to can produce more pernicious gas when low-reverse, driving engine 4 is generally in non-economy rotary speed area when moveing backward simultaneously, oil consumption is relatively high, now adopt the electronic pattern of reversing gear can improve this problem well, discharge can not only be reduced, adopt motor to realize low-reverse energy consumption as power lower simultaneously, certain improvement is had to the fuel economy of driving engine 4.

And for example, when Vehicular battery carrying capacity inadequate or lower, machinery can be adopted to reverse gear pattern.For another example, under needs are moveed backward fast or needed the operating modes such as high-power reversing, then can adopt mixed dynamic pattern of reversing gear, increase the dynamic property of vehicle, convenient reversing.

Certainly, the above-mentioned description about three kinds of model application environment that reverse gear is only schematic, can not be interpreted as it is the pattern of reversing gear that must adopt above-mentioned correspondence to a kind of restriction of the present invention or hint under vehicle is in above-mentioned environment.For the ordinary skill in the art, obviously can as required or actual conditions specifically set pattern of reversing gear required under corresponding reversing environment.

Thus, enrich the pattern of reversing gear of power drive system 100 further, more selected to chaufeur, fully improve Driving, meet the requirement of reversing gear of different road conditions better.

According to the power drive system 100 of some embodiments of the present invention, the second dynamotor 52 can also be set up to increase the dynamic property of power drive system 100, enrich transmission mode.

Such as, wherein in some embodiments, the second dynamotor 52 can with main reduction gear driven gear 74 transmission, the motor shaft of the second dynamotor 52 such as, can arrange gear, and this gear and main reduction gear driven gear 74 be engaged transmission directly.And for example, in further embodiments, the second dynamotor 52 also can be arranged to be connected with the first input shaft 11 or be connected with the first output shaft 21.For another example, in some embodiments again, the second dynamotor 52 is two and is separately positioned on the both sides of diff 75, and such as these two the second dynamotors 52 can become one with diff 75.Or, aforesaid driving engine 4 and the first dynamotor 51 are for driving front-wheel, second dynamotor 52 also can be wheel motor and for trailing wheel, or the second dynamotor 52 can drive two trailing wheels by a speed reduction gearing, or the second dynamotor 52 is two and drives a trailing wheel respectively by a speed reduction gearing.

Describe the electronic differential lock construction according to the embodiment of the present invention in detail below with reference to Fig. 2-Fig. 5, this structure can realize the pair of driving wheels that locking skids when there is tyre skidding phenomenon, thus improves skidding, improves trafficability energy.

As Figure 2-Figure 5, this electronic differential lock construction comprises the 3rd dynamotor 201, the 4th dynamotor 301 and anti-skidding synchro 503.Wherein, driving engine 4 and/or the first dynamotor 51 are for driving pair of wheels 76,3rd dynamotor 201 and the 4th dynamotor 301 are arranged for driving second pair of wheel 77, wherein pair of wheels 76 is a pair in front-wheel and trailing wheel, and the second pair of wheel 77 is other a pair in front-wheel and trailing wheel.In the example of Fig. 2-Fig. 5, driving engine 4 and the first dynamotor 51 drive front-wheel, and the 3rd dynamotor 201 and the 4th dynamotor 301 are respectively used to driving two trailing wheels.

Shown in composition graphs 2-Fig. 5,3rd dynamotor 201 is arranged to link with in second pair of wheel 77, in other words, 3rd dynamotor 201 can output power to this wheel to drive this vehicle wheel rotation, or the 3rd dynamotor 201 also can absorb energy from this wheel, thus generates electricity.

Similarly, 4th dynamotor 301 is arranged to link with another in second pair of wheel 77, in other words, 4th dynamotor 301 can output power to this another wheel to drive this another vehicle wheel rotation, or the 4th dynamotor 301 also can absorb energy from this another wheel, thus generates electricity.In the example of Fig. 2-Fig. 5, the 3rd dynamotor 201 links with left rear wheel, and the 4th dynamotor 301 links with off hind wheel, but the present invention is not limited to this.

Anti-skidding synchro 503 is arranged to optionally synchronous second pair of wheel 77, thus make second pair of wheel 77 synchronous rotary, in other words, the synchronous second pair of wheel 77 (namely anti-skidding synchro 503 is in engagement state) of anti-skidding synchro 503, formed between second pair of wheel 77 and connect firmly form, thus synchronous rotary, can not rotate by differential.

And when anti-skidding synchro 503 is in off-state, 3rd dynamotor 201 and the 4th dynamotor 301 can drive corresponding wheel with different rotational speed respectively, realize the differential rotating function of two wheels, certainly, when anti-skidding synchro 503 is in off-state, the 3rd dynamotor 201 and the 4th dynamotor 301 also can drive this second pair of wheel 77 with identical rotational speed.

Thus, by arranging the 3rd dynamotor 201 and the 4th dynamotor 301 individually drives second pair of wheel 77, thus the differential that can realize second pair of wheel 77 rotates, and when there is one of them tyre skidding phenomenon, anti-skidding synchro 503 can synchronous second pair of wheel 77 to make second pair of wheel 77 synchronous rotary, jointly after realizing the power coupling that two motors (can certainly be) export drive second pair of wheel 77 operation, improve tyre skidding phenomenon, improve the carrying capacity of vehicle.

In brief, according to the power drive system 100 of the embodiment of the present invention, owing to being provided with the cause of anti-skidding synchro 503, therefore corresponding vehicle bridge can be cancelled (such as, back axle) the mechanical type self-locking differential structure that has, but functionally but can be realized the function of traditional mechanical type self-locking differential by the synchronous effect of anti-skidding synchro 503, make thus compacter according to the structure of the power drive system 100 of the embodiment of the present invention, cost is lower.

Below the example of type of drive composition graphs 2-Fig. 5 of the 3rd dynamotor 201, the 4th dynamotor 301 and wheel is described in detail.

In certain embodiments, as shown in figs 2-4, by gear structure indirect drive between the 3rd dynamotor 201 and corresponding wheel, similarly, between the 4th dynamotor 301 and corresponding wheel, also this gear structure indirect drive can be passed through.

Carry out transmission by gear structure to be easy to realize and structure is simple, and required transmitting ratio can be obtained, reliable transmission.And, 3rd dynamotor 201 carries out power transmission with corresponding wheel by identical gear structure with the 4th dynamotor 301, also improve the commonality of gear structure, also make power drive system 100 have higher symmetry simultaneously, center of gravity is avoided too to depart to side, enable center of gravity be in the midway location of two wheels or the position near centre better, improve stability and the reliability of power drive system 100.

Further, as optional embodiment, as shown in Figure 3-Figure 5, the gear structure adopted between the 3rd dynamotor 201 and corresponding wheel can comprise the first gear 401, second gear 402, the 3rd gear 403 and the 4th gear 404 4 gears.

First gear 401 can be arranged on the first power take-off shaft 202 of the 3rd dynamotor 201 correspondence, and the first gear 401 can with the first power take-off shaft 202 synchronous rotary.Wherein, first power take-off shaft 202 can be used for exporting the power produced from the 3rd dynamotor 201, or counter for the wheel Power output dragged can be same structure to the motor shaft of the 3rd dynamotor 201, first power take-off shaft 202 and the 3rd dynamotor 201 by the first power take-off shaft 202.Certainly alternatively, the motor shaft of the first power take-off shaft 202 and the 3rd dynamotor 201 also can be two independent parts, and now the first power take-off shaft 202 is connected with the motor of the 3rd dynamotor 201.

The wheel corresponding with the 3rd dynamotor 201 is connected with the first semiaxis 204, second gear 402 to be arranged on the first semiaxis 204 and can with the first semiaxis 204 synchronous rotary, 3rd gear 403 engages with the first gear 401 and the 4th gear 404 engages with the second gear 402, and the 3rd gear 403 and the 4th gear 404 coaxially arranged and can synchronous rotary.

Similarly, as shown in figs 2-4, the gear structure adopted between the 4th dynamotor 301 and corresponding wheel can comprise the 5th gear 405, the 6th gear 406, the 7th gear 407 and octadentate and take turns 408 totally four gears.On the second power take-off shaft 302 that 5th gear 405 can be arranged on the 4th dynamotor 301 correspondence and can with the second power take-off shaft 302 synchronous rotary.Wherein, second power take-off shaft 302 can be used for exporting the power produced from the 4th dynamotor 301, or counter for the wheel Power output dragged can be same structure to the motor shaft of the 4th dynamotor 301, second power take-off shaft 302 and the 4th dynamotor 301 by the second power take-off shaft 302.Certainly alternatively, the motor shaft of the second power take-off shaft 302 and the 4th dynamotor 301 also can be two independent parts, and now the second power take-off shaft 302 is connected with the motor shaft of the 4th dynamotor 301.

The wheel corresponding with the 4th dynamotor 301 is connected with the second semiaxis 304,6th gear 406 to be arranged on the second semiaxis 304 and can with the second semiaxis 304 synchronous rotary, 7th gear 407 engages with the 5th gear 405 and octadentate is taken turns 408 and engaged with the 6th gear 406, and the 7th gear 407 and octadentate are taken turns 408 synchronization arrangement and can synchronous rotary.

Alternatively, first gear 401 and the 5th gear 405, second gear 402 and the 6th gear 406, the 3rd gear 403 and the 7th gear 407 and the 4th gear 404 and octadentate take turns 408 size can be identical respectively with the number of teeth, thus improve the commonality of gear structure.

As optional embodiment, the 3rd gear 403 and the 4th gear 404 can be fixed on the first gear wheel shaft 501, and the 7th gear 407 and octadentate are taken turns 408 and can be fixed on the second gear wheel shaft 502.Certainly, the 3rd gear 403 and the 4th gear 404 also can be configured to stepped gear or connection gear structure.Similarly, the 7th gear 407 and octadentate are taken turns 408 and also can be configured to stepped gear or join gear structure.

In some instances, as shown in Figure 2, anti-skidding synchro 503 can be arranged on the first semiaxis 204 and to be arranged to optionally engage the 6th gear 406, such as, 6th gear 406 can arrange joint gear ring towards the side of anti-skidding synchro 503, the sliding hub of anti-skidding synchro 503 and this joint gear ring adaptation.Thus, after anti-skidding synchro 503 engages, this second pair of wheel 77 is by synchronous rotary.

In other examples, as shown in Figure 3, anti-skidding synchro 503 to be arranged on the first power take-off shaft 202 and to be arranged to optionally engage the 5th gear 405, such as, 5th gear 405 can arrange joint gear ring towards the side of anti-skidding synchro 503, the sliding hub of anti-skidding synchro 503 and this joint gear ring adaptation.Thus, after anti-skidding synchro 503 engages, this second pair of wheel 77 is by synchronous rotary.

In other example, as shown in Figure 4, anti-skidding synchro 503 to be arranged on the first gear wheel shaft 501 and to be arranged to optionally engage the 7th gear 407, such as, 7th gear 407 can arrange joint gear ring towards the side of anti-skidding synchro 503, the sliding hub of anti-skidding synchro 503 and this joint gear ring adaptation.Thus, after anti-skidding synchro 503 engages, this second pair of wheel 77 is by synchronous rotary.

Alternatively, in the example of hgure 5, the 3rd dynamotor 201 and corresponding wheel be coaxially connected and the 4th dynamotor 301 be coaxially connected with corresponding wheel.Further, the 3rd dynamotor 201 and the 4th dynamotor 301 can be all wheel motors, and messenger chain is short thus, and transmission degradation of energy is few, and driving efficiency is high.

Further, as shown in Figure 5, anti-skidding synchro 503 can be arranged on the 3rd dynamotor 201 correspondence the first power take-off shaft 202 on and be arranged to optionally engage the second power take-off shaft 302 of the 4th dynamotor 301 correspondence.Thus, after anti-skidding synchro 503 engages, this second pair of wheel 77 is by synchronous rotary.

Structure and the typical condition of each specific embodiment medium power driving system 100 are simply described referring to Fig. 1-Fig. 5.

Embodiment one:

As shown in Figure 1, driving engine 4 is connected with the input end 23d of double-clutch 2d, the first mouth 21d of double-clutch 2d is connected with the first input shaft 11, the second mouth 22d of double-clutch 2d is connected with the second input shaft 12, the input end 23d of double-clutch 2d and the first mouth 21d of double-clutch 2d and the second mouth 22d can be in off-state simultaneously, or the input end 23d of double-clutch 2d can engage with one of the first mouth 21d and the second mouth 22d of double-clutch 2d, or the input end 23d of double-clutch 2d can engage with the first mouth 21d of double-clutch 2d and the second mouth 22d simultaneously.

Second input shaft 12 is hollow shaft structure, and the first input shaft 11 is solid axle, and the second input shaft 12 is set on the first input shaft 11 coaxially, and a part for the first input shaft 11 is protruding vertically in the second input shaft 12.

First input shaft 11 is provided with and can arranges in turn from right to left with a gear driving gear 1a of the first input shaft 11 synchronous axial system, three or five gear driving gear 35a and seven gear driving gear 7a, seven gear driving gear 7a, a gear driving gear 1a, three or five gear driving gear 35a.

Second input shaft 12 is provided with can with two or four gear driving gear 24a of the second input shaft 12 synchronous axial system, six or eight gear driving gear 68a.

First output shaft 21 and two input shafts are arranged in parallel, first output shaft 21 is set with a gear driven gear 1b, four gear driven gear 4b, five gear driven gear 5b and eight gear driven gear 8b, one gear driven gear 1b and one keeps off driving gear 1a and engages, four gear driven gear 4b and two or four keep off driving gear 24a and engage, five gear driven gear 5b and three or five keep off driving gear 35a and engage, and eight gear driven gear 8b and six or eight keep off driving gear 68a and engage.

First output shaft 21 is also provided with First Five-Year Plan gear synchro 15c and four or eight gear synchro 48c, First Five-Year Plan, gear synchro 15c kept off between driven gear 5b at a gear driven gear 1b and five, and optionally by synchronous with the first output shaft 21 for a gear driven gear 1b or five gear driven gear 5b, four or eight gear synchro 48c are used for synchronous with the first output shaft 21 for four gear driven gear 4b or eight gear driven gear 8b.

Second output shaft 22 is same to be arranged in parallel with two input shafts, second output shaft 22 is set with two gear driven gear 2b, three gear driven gear 3b, six gear driven gear 6b and seven gear driven gear 7b, two gear driven gear 2b and two or four keep off driving gear 24a and engage, three gear driven gear 3b and three or five keep off driving gear 35a and engage, six gear driven gear 6b and six or eight keep off driving gear 68a and engage, and seven gear driven gear 7b and seven keep off driving gear 7a and engage.

Second output shaft 22 is also provided with two or six gear synchro 26c and pseudo-ginseng gear synchro 37c, pseudo-ginseng gear synchro 37c is used for synchronous with the second output shaft 22 for three gear driven gear 3b or seven gear driven gear 7b.Two or six gear synchro 26c keep off between driven gear 6b at two gear driven gear 2b and six, and optionally by synchronous with the second output shaft 22 for two gear driven gear 2b or six gear driven gear 6b.

Motor mechanical axis 3 and two input shafts, two output shafts be arranged in parallel, motor mechanical axis 3 is set with motor mechanical axis first gear 31 and motor mechanical axis second gear 32, motor mechanical axis first gear 31 by intermediate drive gear 84 and the first motor gear 71 transmission be fixedly installed on the second input shaft 12, motor mechanical axis second gear 32 and the second motor gear 72 engaged transmission be fixed on the second output shaft 22.Between motor mechanical axis first gear 31 and motor mechanical axis second gear 32, be also provided with motor mechanical axis synchro 33c, motor mechanical axis synchro 33c is used for optionally motor mechanical axis first gear 31 or motor mechanical axis second gear 32 being engaged with motor mechanical axis 3.Wherein, intermediate drive gear 84 can empty set on the second output shaft 22.

First dynamotor 51 is coaxially connected with motor mechanical axis 3.

Auxiliary output shaft 85 and motor mechanical axis 3, two input shafts, two output shafts be arranged in parallel, auxiliary output shaft 85 is set with reverse output gear 86 and auxiliary gear driven gear, the gear part 21b that reverse output gear 86 and two keeps off driven gear 2b engages, and another gear part 22b and two or four of two gear driven gear 2b keeps off driving gear 24a and engages.

Auxiliary gear driven gear comprises nine gear driven gear 9b, ten gear driven gear 10b and 11 gear driven gear 11b, ten gear driven gear 10b keep off driven gear 6b transmission to form ten gear gear pairs by first intermediate idler 81 and six of empty set on motor mechanical axis 3, nine gear driven gear 9b keep off driven gear 3b transmission to form nine gear gear pairs by second intermediate idler 82 and three of empty set on motor mechanical axis 3, 11 gear driven gear 11b keep off driven gear 7b transmission to form ten first gears pairs by the 3rd intermediate idler 83 and seven of empty set on motor mechanical axis 3.

Auxiliary output shaft 85 is also provided with reverse gear synchronizer 86c and 91 gear synchro 911c, reverse gear synchronizer 86c keeps off between driven gear 10b at reverse output gear 86 and ten, and for optionally reverse output gear 86 or ten gear driven gear 10b being engaged with auxiliary output shaft 85.91 gear synchro 911c between nine gear driven gear 9b and 11 gear driven gear 11b, and engage with auxiliary output shaft 85 for optionally nine gear driven gear 9b or 11 being kept off driven gear 11b.

First output shaft 21 is fixedly installed the first output shaft output gear 211, second output shaft 22 is fixedly installed the second output shaft output gear 221, auxiliary output shaft 85 is fixedly installed auxiliary output shaft output gear 851, first output shaft output gear 211, second output shaft output gear 221 and auxiliary output shaft output gear 851 respectively with main reduction gear driven gear 74 engaged transmission.

Below the typical condition of power drive system 100 shown in Fig. 1 is described in detail.

Parking charging operating mode:

Under parking charging operating mode, motor mechanical axis synchro 33c engages motor mechanical axis first gear 31, the power that driving engine 4 exports by exporting to the first dynamotor 51 after the second input shaft 12, first motor gear 71, intermediate drive gear 84, motor mechanical axis first gear 31, thus drives the first dynamotor 51 to generate electricity.

Constant-speed ratio charging can be realized under this operating mode, energy transfer efficiency is higher, and selecting about speed ratio, the maximum speed of revolution allowed with the additional components such as type selecting and periphery bearing of rotating speed during driving engine 4 parking, the first dynamotor 51 has direct relation, for the ordinary skill in the art, can comprehensively above etc. factor consider, the corresponding transmission speed ratio of flexible design, make power drive system 100 can utilize the energy of driving engine 4 substantially when power generation in parking, reach fast charge object.

Pure electronic operating mode:

Motor mechanical axis synchro 33c engages the power of motor mechanical axis second gear 32, first dynamotor 51 generation by exporting from the second output shaft 22 after motor mechanical axis 3, motor mechanical axis second gear 32, second motor gear 72.Certainly, motor mechanical axis synchro 33c also can engage motor mechanical axis first gear 31, first dynamotor 51 can output power to the second input shaft 12, or six gear gear pairs secondary by second gear export from the second output shaft 22 again, or exported from the first output shaft 21 by four gear gear pairs or eight gear gear pairs, or exported from auxiliary output shaft 85 by ten gear gear pairs.

Thus, under power drive system 100 is in pure electronic operating mode, the path that the first dynamotor 51 can have different speed ratio by above-mentioned many outputs power to wheel, thus drives vehicle to travel.In brief, being undertaken by the first dynamotor 51 starting to walk, suddenly to accelerate, climb, the situation such as to run at a constant speed under, different optimum speed ratios can be selected respectively, thus make the first dynamotor 51 work efficiency the highest.

The mixed condition of starting building of each gear:

Motor mechanical axis synchro 33c engages the power of motor mechanical axis second gear 32, first dynamotor 51 generation by exporting from the second output shaft 22 after motor mechanical axis 3, motor mechanical axis second gear 32, second motor gear 72.

Driving engine 4 now, four gear gear pairs, five gear gear pairs or eight secondary by first gear keeps off gear pairs from the first output shaft 21 outputting power, exports after two parts power is coupled on main reduction gear driven gear 74.Now the first dynamotor 51 can carry out speed governing, thus makes main reduction gear driven gear 74 synchronously can receive power from driving engine 4 and the first dynamotor 51 evenly, improves ride comfort, the harmony of transmission.

Or driving engine 4 now also keeps off gear pairs from the second output shaft 22 outputting power by second gear pair, three gear gear pairs, six gear gear pairs or seven, and two parts power exports from the second output shaft output gear 221 after being coupled on the second output shaft 22.Now the first dynamotor 51 can carry out speed governing, thus makes the second output shaft 22 synchronously can receive power from driving engine 4 and the first dynamotor 51 evenly, improves ride comfort, the harmony of transmission.

Moreover driving engine 4 is secondary from auxiliary output shaft 85 outputting power by nine gear gear pairs, ten gear gear pairs or ten first gears, exports after two parts power is coupled on main reduction gear driven gear 74.Now the first dynamotor 51 can carry out speed governing, thus makes main reduction gear driven gear 74 synchronously can receive power from driving engine 4 and the first dynamotor 51 evenly, improves ride comfort, the harmony of transmission.

To sum up, for the ordinary skill in the art, can be according to actual needs, any mixing of starting building in condition moves path to select above-mentioned each gear to mix neatly, greatly enrich the transmission mode of power drive system 100, improve Driving, enable vehicle adapt to different road conditions better, improve dynamic property, the fuel economy of vehicle.

Driving limit, driving engine limit charging operating mode scheme one:

Motor mechanical axis synchro 33c engages motor mechanical axis first gear 31, driving engine 4 is by two gears or four gears or six gears or eight keep off or ten gears export a part of power, another part power of driving engine 4 by exporting to the first dynamotor 51 after the second input shaft 12, first motor gear 71, motor mechanical axis first gear 31, thus drives the first dynamotor 51 to generate electricity.

Or, motor mechanical axis synchro 33c engages motor mechanical axis second gear 32, driving engine 4 keeps off from the first output shaft 21 outputting power by a gear, four gears, five gears or eight, or by nine gears, ten gears or 11 gears from auxiliary output shaft 85 outputting power, the second output shaft 22, second motor gear 72, motor mechanical axis second gear 32 is dragged by wheel is counter, make the anti-energy that drags of wheel finally can export to the first dynamotor 51, thus drive the first dynamotor 51 to generate electricity.

Or, motor mechanical axis synchro 33c engages motor mechanical axis second gear 32, driving engine 4 also outputs power to the second output shaft 22 by two gears, three gears, six gears or seven gears, this part power part directly can export from the second output shaft output gear 221, another part by exporting to the first dynamotor 51 after the second motor gear 72, motor mechanical axis second gear 32, thus drives the first dynamotor 51 to generate electricity.

Driving limit, driving engine 4 limit charging operating mode scheme two:

In driving limit, driving engine 4 limit charging operating mode scheme one presented hereinbefore, double-clutch 2d all only has a power-transfer clutch to carry out engaging work when transmission, such as its input end 23d engages with the first mouth 21d or input end 23d engages with the second mouth 22d, especially, according to the power drive system 100 of the embodiment of the present invention, when the input end 23d of double-clutch 2d engages with the first mouth 21d and the second mouth 22d simultaneously, driving limit, limit charging operating mode also can be realized.

Now, a part of power that driving engine 4 produces by exporting to the first dynamotor 51 after the second input shaft 12, first motor gear 71, motor mechanical axis first gear 31, motor mechanical axis 3, thus drives the first dynamotor 51 to generate electricity.Another part power that driving engine 4 produces keeps off by the first input shaft 11, three gears, five gears, seven gears, nine keep off or the external outputting power of 11 gear.

To sum up, for the ordinary skill in the art, can be according to actual needs, select any drive path charged in operating mode scheme one and driving limit, driving engine limit charging operating mode scheme two in driving limit, above-mentioned driving engine limit neatly, greatly enrich the transmission mode of power drive system 100, improve Driving, enable vehicle adapt to different road conditions better, improve dynamic property, the fuel economy of vehicle.

To reverse gear operating mode:

First describe machinery to reverse gear, reverse gear synchronizer 86c engages reverse output gear 86, and the power that driving engine 4 produces exports from auxiliary output shaft 85 after keeping off driven gear 2b, reverse output gear 86 by the second input shaft 12, two.

Secondly pure electronicly to reverse gear is described, motor mechanical axis synchro 33c engages motor mechanical axis second gear 32, first dynamotor 51 by power by exporting from the second output shaft 22 after motor mechanical axis 3, motor mechanical axis second gear 32, second motor gear 72.Or motor mechanical axis synchro 33c engages motor mechanical axis first gear 31, power is outputted power to the second input shaft 12 by motor mechanical axis 3, motor mechanical axis first gear 31 by the first dynamotor 51, engaging reverse output gear 86 by reverse gear synchronizer 86c again, making the power that reverses gear of motor by exporting from auxiliary output shaft 85 after two gear driven gear 2b, reverse output gear 86.

Again describe mixed moving to reverse gear, driving engine 4 still reverses gear by above-mentioned machinery, and power is kept off driven gear 2b by the second input shaft 12, two by path, reverse output gear 86 exports from auxiliary output shaft 85.First dynamotor 51 by after motor mechanical axis second gear 32 from the second output shaft 22 outputting power, two parts power can main reduction gear driven gear 74 place coupling after export.Now, the first dynamotor 51 can carry out speed governing equally, thus makes main reduction gear driven gear 74 synchronously can receive power from driving engine 4 and the first dynamotor 51 evenly, improves ride comfort, the harmony of transmission.

Or the first dynamotor 41 also can export power to second input shaft 12 by motor mechanical axis first gear 31, first motor gear 71, thus with driving engine 4 power coupling after keep off driven gear 2b by two and export from reverse output gear 86.Now, the first dynamotor 51 can carry out speed governing equally, thus makes the second input shaft 12 synchronously can receive power from driving engine 4 and the first dynamotor 51 evenly, improves ride comfort, the harmony of transmission.

Especially, in parking charging operating mode, driving limit, driving engine limit charging operating mode, the power of driving engine 4 exports to the first dynamotor 51 (in driving limit, driving engine limit charging operating mode by the first motor gear 71, motor mechanical axis first gear 31, driving engine 4 also exports to the first dynamotor 51 power by the second motor gear 72, motor mechanical axis second gear 32), now the first dynamotor 51 can rotate along same predetermined direction, such as, rotate forward.Such as, such as, and at the first dynamotor 51 as in the operating mode of propulsion source, pure electronic operating mode or mixed condition of starting building, the first dynamotor 51 still can rotate according to above-mentioned same predetermined direction, rotates forward.Further, under the operating mode of reversing gear having the first dynamotor 51 to participate in, during the power that relates to that the first dynamotor 51 is secondary by motor mechanical axis first gear 31, first motor gear 71, second gear, this path output motor of reverse output gear 86 reverses gear, first dynamotor 51 still can rotate along above-mentioned same predetermined direction, such as, rotate forward.

In brief, under each operating mode presented hereinbefore, first dynamotor 51 rotates according to same predetermined direction from start to finish, namely the first dynamotor 51 is when as electrical motor work and generator operation, can rotate according to same direction always, especially for from pure electronic operating mode, charging operating mode, mixed conditions of starting building etc. are in the process of reversing gear operating mode switching, first dynamotor 51 is also without the need to commutation, thus make the first dynamotor 51 all can rotating Vortex from start to finish under the above-mentioned operating mode of the work of participation, motor is without the need to commutation, and then the impact sense improved because motor commutation brings, pause and transition in rhythm or melody sense etc., improve the life-span of power drive system 100.

Embodiment two-embodiment five:

As Figure 2-Figure 5, power drive system 100 in these some embodiments is to add rear wheel drive structure with the key distinction of the power drive system 100 shown in Fig. 1, mainly add the structures such as the 3rd genemotor 201, the 4th dynamotor 301 and anti-skidding synchro 503, specifically see the above-mentioned description to electronic differential lock construction, can repeat no more here.

Embodiment six:

As shown in Figure 6, change-speed box 101 in this embodiment is to eliminate the structures such as driving engine 4, double-clutch 2d, the first dynamotor 51 and diff with the key distinction of the power drive system 100 shown in Fig. 1, remainder is substantially identical with Fig. 1 embodiment, repeats no more here.

In addition, the vehicle comprising power drive system 100 as above is further provided according to embodiments of the invention.Should be understood that, all be well known for ordinary skill in the art for prior art as driving system, steering swivel system, brake system etc. according to other configuration example of the vehicle of the embodiment of the present invention, therefore the detailed description of conventional construction omitted herein.

In the description of this specification sheets, specific features, structure, material or feature that the description of reference term " embodiment ", " some embodiments ", " example ", " concrete example " or " some examples " etc. means to describe in conjunction with this embodiment or example are contained at least one embodiment of the present invention or example.In this manual, to the schematic representation of above-mentioned term not must for be identical embodiment or example.And the specific features of description, structure, material or feature can combine in an appropriate manner in any one or more embodiment or example.In addition, the different embodiment described in this specification sheets or example can carry out engaging and combining by those skilled in the art.

Although illustrate and describe embodiments of the invention above, be understandable that, above-described embodiment is exemplary, can not be interpreted as limitation of the present invention, and those of ordinary skill in the art can change above-described embodiment within the scope of the invention, revises, replace and modification.

Claims

1. for a change-speed box for vehicle, it is characterized in that, comprising:

Multiple input shaft, each described input shaft is provided with gear driving gear;

Multiple output shaft, each described output shaft is provided with gear driven gear, and described gear driven gear engages accordingly with described gear driving gear;

Motor mechanical axis, described motor mechanical axis is provided with motor mechanical axis first gear and motor mechanical axis second gear, described motor mechanical axis first gear empty set on described motor mechanical axis and described motor mechanical axis first gear be arranged to optionally engage described motor mechanical axis with synchronous axial system, described motor mechanical axis first gear is also arranged to link with in described input shaft, described motor mechanical axis second gear empty set on described motor mechanical axis and described motor mechanical axis second gear be arranged to optionally engage described motor mechanical axis with synchronous axial system, and

Auxiliary output shaft, described auxiliary output shaft is provided with multiple auxiliary gear driven gear, gear driven gear on each described auxiliary gear driven gear and described output shaft links, and each described auxiliary gear driven gear is identical with the hand of rotation of the corresponding gear driven gear linked;

One in described output shaft is fixedly installed the second motor gear, and described motor mechanical axis second gear engages with described second motor gear.

2. the change-speed box for vehicle according to claim 1, is characterized in that, described motor mechanical axis is also provided with the motor mechanical axis synchro between described motor mechanical axis first gear and described motor mechanical axis second gear.

3. the change-speed box for vehicle according to claim 2, is characterized in that, described one in described input shaft is fixedly installed the first motor gear, and described motor mechanical axis first gear is arranged to link with described first motor gear.

4. the change-speed box for vehicle according to claim 3, is characterized in that, described motor mechanical axis first gear is by intermediate drive gear and described first motor gear transmission.

5. the change-speed box for vehicle according to claim 3, is characterized in that, also comprise: reverse output gear, and described reverse output gear is arranged to link with one of them gear driven gear.

6. the change-speed box for vehicle according to claim 5, is characterized in that, described reverse output gear empty set on described auxiliary output shaft, and described auxiliary output shaft is also provided with at least for engaging the reverse gear synchronizer of described reverse output gear.

7. the change-speed box for vehicle according to claim 5, it is characterized in that, one of them gear driven gear described is dual gear, a gear part of described dual gear engages with corresponding gear driving gear, and another gear part of described dual gear engages with described reverse output gear.

8. the change-speed box for vehicle according to claim 6, is characterized in that, each described auxiliary gear driven gear is all linked by the gear driven gear on intermediate idler and described output shaft.

9. the change-speed box for vehicle according to claim 8, is characterized in that, described input shaft comprises: the first input shaft and the second input shaft, and described second input shaft is set on described first input shaft coaxially;

Described multiple output shaft comprises: the first output shaft and the second output shaft, and described first output shaft and described second output shaft and input shaft be arranged in parallel.

10. the change-speed box for vehicle according to claim 9, it is characterized in that, described first input shaft is provided with a gear driving gear, three or five gear driving gears and seven gear driving gears, described second input shaft is provided with two or four gear driving gears and six or eight gear driving gears;

Described first output shaft is provided with a gear driven gear, four gear driven gears, five gear driven gears and eight gear driven gears, described second output shaft is provided with two gear driven gears, three gear driven gears, six gear driven gears and seven gear driven gears; And

A described gear driven gear and described five keeps off and to be provided with the First Five-Year Plan between driven gear and to keep off synchro, described four gear driven gears and described eight keep off and are provided with four or eight between driven gear and keep off synchro, described three gear driven gears and described seven keep offs and are provided with pseudo-ginseng between driven gear and keep off synchro, and described two keep off driven gears and described six keeps off and be provided with two or six between driven gear and keep off synchro.

11. change-speed boxs for vehicle according to claim 10, is characterized in that,

Described auxiliary gear driven gear comprises: nine gear driven gears, ten gear driven gears and 11 gear driven gears,

And described intermediate idler comprises: the first intermediate idler, the second intermediate idler and the 3rd intermediate idler, described ten gear driven gears keep off driven gear by described first intermediate idler and described six and engage to form ten gear gear pairs, described nine and keep off driven gear and keep off driven gear by described second intermediate idler and described three and engage to form nine gear gear pairs, described 11 and keep off driven gear and keep off driven gear by described 3rd intermediate idler and described seven and engage to form ten first gears pairs.

12. change-speed boxs for vehicle according to claim 11, it is characterized in that, described ten gear driven gears and described reverse output gear share described reverse gear synchronizer, and described nine keep off driven gears and described 11 keeps off and be provided with 91 between driven gear and keep off synchro.

13. change-speed boxs for vehicle according to claim 11, is characterized in that, described first intermediate idler, described second intermediate idler and the equal empty set of described 3rd intermediate idler are on described motor mechanical axis.

14. change-speed boxs for vehicle according to claim 10, it is characterized in that, described first motor gear is fixedly installed on described second input shaft, and described second motor gear is fixedly installed on described second output shaft, and described reverse output gear and described two keeps off driven gear transmission.

15. change-speed boxs for vehicle according to claim 9, it is characterized in that, described first output shaft is fixedly installed the first output shaft output gear, described second output shaft is fixedly installed the second output shaft output gear, described auxiliary output shaft is fixedly installed auxiliary output shaft output gear, described first output shaft output gear, described second output shaft output gear and described auxiliary output shaft output gear engage with the main reduction gear driven gear of described vehicle respectively.

16. 1 kinds for the power drive system of vehicle, is characterized in that, comprising:

Change-speed box, described change-speed box is the change-speed box according to any one of claim 1-15; And

First dynamotor, described first dynamotor is arranged to link with described motor mechanical axis.

17. power drive systems for vehicle according to claim 16, is characterized in that,

Described change-speed box is for according to the change-speed box described in claim 9; And

Described power drive system also comprises:

Driving engine and double-clutch, described double-clutch has input end, the first mouth and the second mouth, described driving engine is connected with described input end, and described first mouth is connected with described first input shaft, and described second mouth is connected with described second input shaft.

18. power drive systems for vehicle according to claim 17, it is characterized in that, wherein a part of power can be exported to wheel using the power travelled as described vehicle by wherein output shaft by conjugation while described input end and described first mouth and described second mouth and another part power is exported to described first dynamotor by described first motor gear generate electricity to drive described first dynamotor by described driving engine.

19. power drive systems for vehicle according to claim 17, it is characterized in that, when described vehicle is in parked state, described driving engine is arranged to export the power of generation to described first dynamotor by described first motor gear and is generated electricity to drive described first dynamotor.

20. power drive systems for vehicle according to claim 17, is characterized in that, described vehicle has machinery and to reverse gear pattern, electronic pattern and the mixed dynamic pattern of reversing gear of reversing gear,

Described vehicle be in described machinery reverse gear pattern time, the power of generation is exported from described reverse output gear the synchronous effect of described reverse output gear by described reverse gear synchronizer as propulsion source by described driving engine,

Described vehicle be in described electronic reverse gear pattern time, the power produced is exported from described second motor gear the synchronous effect of described motor mechanical axis second gear by described motor mechanical axis synchro as propulsion source by described first dynamotor, or the power of generation is exported from described reverse output gear the synchronous effect of described reverse output gear the synchronous effect of described motor mechanical axis first gear and described reverse gear synchronizer by described motor mechanical axis synchro as propulsion source by described first dynamotor

Described vehicle be in described mixed dynamic reverse gear pattern time, the power of generation is exported from described reverse output gear the synchronous effect of described reverse output gear by described reverse gear synchronizer as dynamic origin by described driving engine, the power produced is exported from described second motor gear the synchronous effect of described motor mechanical axis second gear by described motor mechanical axis synchro as another propulsion source by described first dynamotor, or the power of generation is exported from described reverse output gear the synchronous effect of described reverse output gear the synchronous effect of described motor mechanical axis first gear and described reverse gear synchronizer by described motor mechanical axis synchro as another propulsion source by described first dynamotor.

21. power drive systems for vehicle according to claim 17, is characterized in that, described first dynamotor is can rotate according to same predetermined direction from start to finish as when electrical motor and generator operation.

22. power drive systems for vehicle according to claim 17, is characterized in that, also comprise: the second dynamotor, wherein

The main reduction gear driven gear transmission of described second dynamotor and described vehicle; Or

Described second dynamotor is connected with the first output shaft; Or

Described second dynamotor is connected with described first input shaft; Or

The main reduction gear driven gear of described vehicle is arranged on diff, and described second dynamotor is two and is separately positioned on the both sides of described diff.

23. power drive systems for vehicle according to claim 17, is characterized in that,

Described driving engine and/or described first dynamotor are for driving pair of wheels; And

The described power drive system for vehicle also comprises:

3rd dynamotor and the 4th dynamotor, described 3rd dynamotor is arranged to link with in second pair of wheel, described 4th dynamotor is arranged to link with another in described second pair of wheel, described pair of wheels is a pair in front-wheel and trailing wheel, and described second pair of wheel is other a pair in described front-wheel and described trailing wheel;

Anti-skidding synchro, described anti-skidding synchro is arranged to optionally synchronously described second pair of wheel, thus makes described second pair of wheel synchronous rotary.

24. power drive systems for vehicle according to claim 23, is characterized in that,

The first power take-off shaft that described 3rd dynamotor is corresponding is provided with the first gear, and the described wheel that described 3rd dynamotor is corresponding is connected with the first semiaxis, and described first semiaxis is provided with the second gear; The described power drive system for vehicle also comprises the 3rd gear and the 4th gear, described 3rd gear and described first gears meshing and described 4th gear and described second gears meshing, described 3rd gear and described 4th gear coaxially arranged and can synchronous rotary; And

The second power take-off shaft that described 4th dynamotor is corresponding is provided with the 5th gear, and the described wheel that described 4th dynamotor is corresponding is connected with the second semiaxis, described second semiaxis is provided with the 6th gear; The described power drive system for vehicle also comprises the 7th gear and octadentate wheel, described 7th gear and described 5th gears meshing and described octadentate are taken turns and described 6th gears meshing, and described 7th gear and described octadentate are taken turns coaxially arranged and can synchronous rotary; Wherein

Described anti-skidding synchro to be arranged on described first semiaxis and to be arranged to optionally engage described 6th gear; Or

Described anti-skidding synchro to be arranged on described first power take-off shaft corresponding to the 3rd dynamotor and to be arranged to optionally engage described 5th gear; Or

Described 3rd gear and described 4th gear are fixed on the first gear wheel shaft, and described 7th gear and described octadentate are taken turns and be fixed on the second gear wheel shaft; And described anti-skidding synchro to be arranged on described first gear wheel shaft and to be arranged to optionally engage described 7th gear.

25. power drive systems for vehicle according to claim 23, it is characterized in that, first power take-off shaft corresponding to described 3rd dynamotor and corresponding described wheel are coaxially connected and the second power take-off shaft corresponding to described 4th dynamotor is coaxially connected with corresponding described wheel, and described anti-skidding synchro to be arranged on the first power take-off shaft corresponding to described 3rd dynamotor and to be arranged to optionally engage the second power take-off shaft corresponding to described 4th dynamotor.

26. 1 kinds of vehicles, is characterized in that, comprise the power drive system for vehicle according to any one of claim 16-25.