CN105437948A - Hybrid electric vehicle and reverse gear control method and power transmission system - Google Patents

Hybrid electric vehicle and reverse gear control method and power transmission system Download PDF

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Publication number
CN105437948A
CN105437948A CN201410505701.0A CN201410505701A CN105437948A CN 105437948 A CN105437948 A CN 105437948A CN 201410505701 A CN201410505701 A CN 201410505701A CN 105437948 A CN105437948 A CN 105437948A
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China
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gear
mechanical axis
motor mechanical
dynamotor
hybrid vehicle
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CN201410505701.0A
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Chinese (zh)
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CN105437948B (en
Inventor
廉玉波
阮鸥
陈昊
程华
黄鹏
王品
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比亚迪股份有限公司
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Abstract

The invention discloses a reverse gear control method for a hybrid electric vehicle. The reverse gear control method for the hybrid electric vehicle comprises the following steps of judging a demand torque of the hybrid electric vehicle during reversing the hybrid electric vehicle; and controlling a power transmission system according to the demand torque of the hybrid electric vehicle so as to control the hybrid electric vehicle to run in a pure electric reverse gear mode or a hybrid reverse gear mode. Therefore, during controlling the reversing of the hybrid electric vehicle, power performance, economic efficiency and control difficulty can be all taken into account by using the control method so as to provide good reversing experience to users. The invention further discloses the power transmission system for the hybrid electric vehicle and the hybrid electric vehicle.

Description

Hybrid vehicle and reverse gear control method and power drive system

Technical field

The present invention relates to automobile technical field, particularly a kind of control method of reversing gear of hybrid vehicle, a kind of power drive system of hybrid vehicle and a kind of hybrid vehicle.

Background technology

The mode of reversing gear of relevant hybrid vehicle comprises motor by directly keeping off driving, motor by gearshift driving and pure fuel oil type of drive, also has hybrid power type of drive etc.Wherein, the reversing mode of pure fuel oil driving is comparatively ripe; The reversing mode of pure motorized motions controls simply, easily to realize, have good economy; The reversing mode that hybrid power drives has good dynamic property.

But, because hybrid vehicle is in reversing process, the speed of a motor vehicle is lower, it is also intermittent for travelling, relevant reversing mode has following shortcoming: the reversing mode that pure fuel oil drives has poor economy, higher discharge, power-transfer clutch is in sliding wear for a long time simultaneously, causes serious mechanical wear; The reversing mode of pure motorized motions, dynamic property is on the weak side, and select direct gear to travel (speed ratio is little), motor speed is less, and machine operation is in uneconomic region, and economy also can be subject to certain impact simultaneously; The reversing mode that hybrid power drives, consider the problems such as the power coupling in different dynamic source and speed governing gearshift, controls relative complex.Therefore, there are the needs improved in correlation technique.

Summary of the invention

The present invention is intended to solve one of technical matters in correlation technique at least to a certain extent.

For this reason, first object of the present invention is the control method of reversing gear proposing a kind of hybrid vehicle, can take into account dynamic property, economy and control difficulty, for user provides experience of better reversing gear.

Second object of the present invention is the power drive system proposing a kind of hybrid vehicle.3rd object of the present invention is to propose a kind of hybrid vehicle.

The control method of reversing gear of the hybrid vehicle of embodiment proposition according to a first aspect of the present invention, the power drive system of described hybrid vehicle comprises driving engine, multiple input shaft, multiple output shaft, motor mechanical axis and the first dynamotor, wherein, described driving engine is arranged to optionally engage at least one in described multiple input shaft, each described input shaft is provided with gear driving gear, each described output shaft is provided with gear driven gear, described gear driven gear engages accordingly with described gear driving gear, described motor mechanical axis is arranged to link with in described input shaft, described first dynamotor is arranged to link with described motor mechanical axis, and described one when linking in described motor mechanical axis and described input shaft, described first dynamotor can utilize at least part of power of exporting from described driving engine described hybrid electric vehicle sail and parking time generate electricity, described control method of reversing gear comprises the following steps: when described hybrid vehicle reverse travel, judge the demand torque of described hybrid vehicle, control described hybrid vehicle according to the demand torque of described hybrid vehicle to described power drive system to reverse gear mode operation with pure electronic reverse gear pattern or hybrid power.

According to the control method of reversing gear of the hybrid vehicle that the embodiment of the present invention proposes, when hybrid vehicle reverse travel, judge the demand torque of hybrid vehicle, and according to the demand torque of hybrid vehicle, hybrid vehicle is controlled to power drive system and to reverse gear mode operation with pure electronic reverse gear pattern or hybrid power, thus, when controlling hybrid vehicle reverse travel, dynamic property, economy and control difficulty can be taken into account, for user provides experience of better moveing backward.

The power drive system of the hybrid vehicle of embodiment proposition, comprising: driving engine according to a second aspect of the present invention; Multiple input shaft, described driving engine is arranged to optionally engage at least one in described multiple input shaft, and 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 arranged to link with in described input shaft; First dynamotor, described first dynamotor is arranged to link with described motor mechanical axis, described one when linking wherein in described motor mechanical axis and described input shaft, described first dynamotor can utilize at least part of power of exporting from described driving engine described hybrid electric vehicle sail and parking time generate electricity; Control module, described control module judges the demand torque of described hybrid vehicle when described hybrid vehicle reverse travel, and controls described hybrid vehicle according to the demand torque of described hybrid vehicle to described power drive system and to reverse gear mode operation with pure electronic reverse gear pattern or hybrid power.

According to the power drive system of the hybrid vehicle that the embodiment of the present invention proposes, when hybrid vehicle reverse travel, judge the demand torque of hybrid vehicle, and according to the demand torque of hybrid vehicle, hybrid vehicle is controlled to power drive system and to reverse gear mode operation with pure electronic reverse gear pattern or hybrid power, thus, when controlling hybrid vehicle reverse travel, dynamic property, economy and control difficulty can be taken into account, for user provides experience of better moveing backward.

The hybrid vehicle of embodiment proposition, comprises the power drive system of described hybrid vehicle according to a third aspect of the present invention.

According to the hybrid vehicle that the embodiment of the present invention proposes, in reversing process, dynamic property, economy and control difficulty can be taken into account, for user provides experience of better moveing backward.

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 the power drive system according to another embodiment of the present invention;

Fig. 7 is the schematic diagram of the power drive system according to another embodiment of the present invention;

Fig. 8 is the schematic diagram of the power drive system according to another embodiment of the present invention;

Fig. 9 is the schematic diagram of the power drive system according to another embodiment of the present invention;

Figure 10 is the schematic diagram of the power drive system according to another embodiment of the present invention;

Figure 11 is the schematic diagram of the power drive system according to another embodiment of the present invention;

Figure 12 is the schematic diagram of the power drive system according to another embodiment of the present invention.

Figure 13 is the diagram of circuit of the control method of reversing gear of hybrid vehicle according to the embodiment of the present invention;

Figure 14 is the power transmission line of pure electronic pattern of reversing gear in the control method of reversing gear of hybrid vehicle according to an embodiment of the invention;

Figure 15 is the power transmission line of hybrid power reverse gear mode in the control method of reversing gear of hybrid vehicle according to an embodiment of the invention;

Figure 16 is the power transmission line of the control method of reversing gear of hybrid vehicle in accordance with another embodiment of the present invention; And

Figure 17 is the power transmission line of the control method of reversing gear of hybrid vehicle according to another embodiment of the present 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.

First below in conjunction with Fig. 1-Figure 12, 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 (as shown in Figure 1), change-speed box, 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 shown in Fig. 2-Figure 12, power drive system 100 can comprise driving engine 4, first dynamotor 51 and change-speed box, but is not limited thereto.

For driving engine 4, it directly inputs combustion chamber after utilizing liquid fuel (such as, gasoline, diesel oil etc.) and air mixing more and burns and produce power, and then is transformed into mechanical energy.Driving engine 4 generally can comprise body group, piston crank mechanism, feed system, ignition system, cooling system and lubricating system etc.Body group is the assembling body of each mechanism of driving engine 4, system, and the straight reciprocating motion of piston can be changed into the rotary motion of bent axle and exportable power by piston crank mechanism.Valve mechanism is used for timing air inlet, exhaust, ensures carrying out smoothly of each circulation of driving engine 4.Feed system can will be used for burning in gas mixture supply cylinder.Cooling system is used for cooled engine 4, ensures that the operating temperature of driving engine 4 is in suitable temperature range.Lubricating system is used for each kinematic pair in lubricating engine 4, reduces wear and waste of power.

Should be understood that, above-mentioned concrete structure, principle of work etc. about driving engine 4 and subsystems thereof, clamp mechanism has been prior art all, and is well known to those of ordinary skill in the art, here for succinct object, describes in detail no longer one by one.

Shown in composition graphs 1, in certain embodiments, change-speed box 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) and motor mechanical axis 3 and each axle on associated gear and shifting element (e.g., synchro).

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-Figure 12, 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.

In some embodiments of the invention, change-speed box can be five forward gear change-speed boxs, namely has first gear pair, second gear is secondary, three keep off gear pairs, four gear gear pairs and five keep off gear pairs.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 five gear transmissions shown in the embodiment of the present invention.

As shown in Fig. 1-Figure 12, motor mechanical axis 3 is arranged to link with in input shaft (such as, second input shaft 12).In other words, from the power of this input shaft when needs transmit to motor mechanical axis 3, motor mechanical axis 3 and this input shaft link to transmit power, or from the power of this motor mechanical axis 3 when needs transmit to this input shaft, this input shaft then links to transmit power with motor mechanical axis 3.

In brief, have be in some operating mode according to the vehicle of the power drive system 100 of the embodiment of the present invention time (concrete operating mode will describe in detail below in conjunction with specific embodiments), and power needs when transmitting between motor mechanical axis 3 and this input shaft, then this input shaft and motor mechanical axis 3 link.

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.

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.

As mentioned above, motor mechanical axis 3 can link with in input shaft, especially, one in motor mechanical axis 3 with this input shaft when linking, the first dynamotor 51 can utilize at least part of power of exporting from driving engine 4 vehicle travel and parking time generate electricity.

In other words, when vehicle is in motoring condition and motor mechanical axis 3 links with in this input shaft, at least part of power of driving engine 4 can export the first dynamotor 51 to by motor mechanical axis 3, thus drive the first dynamotor 51 to generate electricity, realize 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) state and motor mechanical axis 3 links with in this input shaft, at least part of power of driving engine 4 can export the first dynamotor 51 to by motor mechanical axis 3, thus drive the first dynamotor 51 to generate electricity, realize parking charge function (i.e. " STOP " charging).

Further, motor mechanical axis 3 is also arranged to link with in output shaft (such as, second output shaft 22).Such as, from the power of motor mechanical axis 3 when needs transmit to this output shaft, motor mechanical axis 3 and this output shaft link to transmit power.Especially, described one when linking in motor mechanical axis 3 with output shaft, the power produced described one by output shaft can export by the first dynamotor 51, thus driving vehicle traveling.In brief, when motor mechanical axis 3 links with this output shaft, the first dynamotor 51 can as electrical motor and outputting power travel to drive vehicle.

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.

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.

Referring to Fig. 1 and the concrete structure of composition graphs 2-Figure 12 to change-speed box be described in detail in conjunction with specific embodiments.

First motor mechanical axis synchro 33c, motor mechanical axis first gear 31 and motor mechanical axis second gear 32 on motor mechanical axis 3 are described in detail.

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.

As Fig. 1 and can composition graphs 2-Figure 12, motor mechanical axis first gear 31 be arranged to link with described one of input shaft, and motor mechanical axis second gear 32 is arranged to link with described one of output shaft.In some examples of Fig. 1-Figure 12, motor mechanical axis first gear 31 and the second input shaft 12 link, and motor mechanical axis second gear 32 and the second output shaft 22 link, but the present invention is not limited to this.

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-Figure 12, 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 motor mechanical axis first gear 31 can optionally engage with motor mechanical axis 3 with one of motor mechanical axis second gear 32 by motor mechanical axis synchro 33c.

The example of composition graphs 1-Figure 12, 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 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.

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 described one of input shaft or link with described 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 described (such as, the second input shaft 12) in input shaft.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 described (such as, the second output shaft 22) in output shaft.

Be described in detail below in conjunction with the structure of reversing gear of accompanying drawing to the power drive system 100 according to the embodiment of the present invention.

As mentioned above, described one of motor mechanical axis first gear 31 and input shaft is linked.And in some embodiments shown in the present invention, motor mechanical axis first gear 31 is with the driving gear direct-drive on described of input shaft or indirect drive, thus realize the object that links with this input shaft.Such as in the example of Fig. 1-Figure 12, motor mechanical axis first gear 31 and corresponding driving gear such as two keep off driving gear 2a by intermediate idler 73 indirect drive, in other words, intermediate idler 73 engages with corresponding driving gear and motor mechanical axis first gear 31 respectively.

Further, reverse gear 71 empty set is on motor mechanical axis 3, and reverse idler gear 72 engages with reverse gear 71, and reverse idler gear 72 is arranged to optionally link with intermediate idler 73.The embodiment of composition graphs 1-Figure 12, reverse idler gear 72 empty set is arranged on the second output shaft 22, and it can rotate and can engage with synchronous axial system when needed by differential with intermediate idler 73.

Further, intermediate idler 73 and reverse idler gear 72 are undertaken linking by the synchronous effect of reverse gear synchronizer 74c, and that is, reverse gear synchronizer 74c is arranged for synchronous reverse idler gear 72 and intermediate idler 73.

About the setting position of reverse gear synchronizer 74c, be described in conjunction with different embodiments here.First, shown in Fig. 1-Fig. 2, Fig. 5-Fig. 8, reverse idler gear 72 is provided with tooth cover 721, this tooth cover 721 can be that empty set is arranged on the second output shaft 22, and intermediate idler 73 empty set is on this tooth cover 721.Reverse gear synchronizer 74c be arranged on tooth cover 721 on and for engaging intermediate idler 73.

Secondly, (not shown) in further embodiments, reverse idler gear 72 is provided with tooth cover 721, this tooth cover 721 can be that empty set is arranged on the second output shaft 22, intermediate idler 73 empty set is on this tooth cover 721, and reverse gear synchronizer 74c to be arranged on intermediate idler 73 and for soldered tooth cover 721 or for engaging reverse idler gear 72.

Again, as shown in Fig. 3-Fig. 4, Fig. 9-Figure 12, in some embodiments again, reverse idler gear 72 and the equal empty set of intermediate idler 73 are on described one of output shaft, the equal empty set of such as reverse idler gear 72 and intermediate idler 73 is on the second output shaft 22, and reverse idler gear 72 and intermediate idler 73 adjacent one another are, reverse gear synchronizer 74c to be arranged on intermediate idler 73 and for engaging reverse idler gear 72.Certainly, alternatively, reverse gear synchronizer 74c also can be arranged on reverse idler gear 72 and for engaging intermediate idler 73 (not shown).

For the power drive system 100 according to the embodiment of the present invention, owing to have employed above-mentioned structure of reversing gear, to reverse gear pattern, electronic pattern and the mixed dynamic pattern of reversing gear of reversing gear therefore, it is possible to realize machinery.

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, driving engine 4 as propulsion source by the Power output that produces to described of input shaft, namely the input shaft linked with intermediate idler 73 (such as, second input shaft 12), and by reverse gear synchronizer 74c, with the synchronous of reverse idler gear 72, reverse gear 71 is outputted power to intermediate idler 73, reverse gear 71 finally can output power to wheel, realizes reversing.In brief, vehicle be in machinery reverse gear pattern time, reverse gear synchronizer 74c engages intermediate idler 73 and reverse idler gear 72.

The electronic pattern of reversing gear is the car-backing function utilizing the first dynamotor 51 to realize vehicle, electronic pattern of reversing gear is at vehicle, first dynamotor 51 is as propulsion source and output power to reverse gear 71 to intermediate idler 73 and the synchronous of reverse idler gear 72 and motor mechanical axis synchro 33c to the synchronous of motor mechanical axis first gear 31 by reverse gear synchronizer 74c, reverse gear 71 finally can output power to wheel, realizes reversing.

Namely, first dynamotor 51 is now as electrical motor work, and its power produced can be passed to reverse gear 71 by motor mechanical axis 3, motor mechanical axis synchro 33c, motor mechanical axis first gear 31, intermediate idler 73, reverse gear synchronizer 74c, reverse idler gear 72 successively.

In brief, be in electronic pattern of reversing gear at vehicle, reverse gear synchronizer 74c engages intermediate idler 73 and reverse idler gear 72, and motor mechanical axis synchro 33c engages motor mechanical axis 3 and motor mechanical axis first gear 31.

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 electronic pattern of reversing gear.

Specifically, vehicle be in mixed dynamic reverse gear pattern time, driving engine 4 as dynamic origin by the Power output that produces to described of input shaft, and synchronously output power to described reverse gear 71 by reverse gear synchronizer 74c.

Meanwhile, the first dynamotor 51 outputs power to described reverse gear 71 by the synchronous of reverse gear synchronizer 74c and motor mechanical axis synchro 33c to the synchronous of motor mechanical axis first gear 31 as another propulsion source.That is, the two-part power from driving engine 4 and the first dynamotor 51 finally all exports from reverse gear 71.

Under this pattern, reverse gear synchronizer 74c engages intermediate idler 73 and reverse idler gear 72, and motor mechanical axis synchro 33c engages motor mechanical axis 3 and motor mechanical axis first gear 31.

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.

In addition, it should be noted that, according to the power drive system 100 of the embodiment of the present invention, its electronic pattern and mixed dynamic pattern another kind of way of realization in addition of reversing gear of reversing gear, this will introduce below in conjunction with specific embodiments in detail.

Embodiment below in conjunction with Fig. 1-Figure 12 is described in detail input shaft, output shaft and each shift gear.

In some embodiments of the present invention, as shown in Fig. 1-Figure 12, 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 two, and namely 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, and the first output shaft 21 and the second output shaft 22 can be solid axle.

Five 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 and arrange 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 shown in Fig. 1-Figure 12, first input shaft 11 can be furnished with a gear driving gear 1a, three gear driving gear 3a and five gear driving gear 5a, second input shaft 12 can be furnished with two gear driving gear 2a and four gear driving gear 4a, 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, two gear driven gear 2b, three gear driven gear 3b and four gear driven gear 4b, second output shaft 22 is provided with five gear driven gear 5b, 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 keep off driving gear 2a and engage thus form second gear pair, three gear driven gear 3b and three keep off driving gear 3a and engage thus form three and keep off gear pair, four gear driven gear 4b and four keep off driving gear 4a and engage thus form four and keep off gear pair, and five keep off driven gear 5b and five keeps off driving gear 5a and engage thus form five and keep off gear pair.

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-Figure 12, power drive system 100 comprises one or three gear synchro 13c, two or four gear synchro 24c and five gear synchro 5c.

As shown in Figure 1, one or three gear synchro 13c to be arranged on the first output shaft 21 and to keep off between driven gear 3b at a gear driven gear 1b and three, one gear driven gear 1b or three gear driven gear 3b can engage with the first input shaft 11 by one or three gear synchro 13c, thus enables this driven gear and output shaft synchronous axial system.

Such as, shown in composition graphs 1, the sliding hub of one or three gear synchro 13c is moved to the left and three gear driven gear 3b can be engaged with the first input shaft 11, thus three gear driven gear 3b and the first output shaft 21 can synchronous axial system.The sliding hub of one or three gear synchro 13c moves right and a gear driven gear 1b can be engaged with the first input shaft 11, thus a gear driven gear 1b and the first output shaft 21 can synchronous axial system.

As shown in Figure 1, similarly, two or four gear synchro 24c to be arranged on the first output shaft 21 and to keep off between driven gear 4b at two gear driven gear 2b and four, two gear driven gear 2b or four gear driven gear 4b can engage with the first input shaft 11 by two or four gear synchro 24c, thus enable this driven gear and output shaft synchronous axial system.

Such as, shown in composition graphs 1, the sliding hub of two or four gear synchro 24c is moved to the left and two gear driven gear 2b can be engaged with the first output shaft 21, thus two gear driven gear 2b and the first output shaft 21 synchronous axial system.The sliding hub of two or four gear synchro 24c moves right and four gear driven gear 4b can be combined 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, five gear synchro 5c are arranged on the second output shaft 22, five gear synchro 5c are positioned at the side of five gear driven gear 5b, such as left side, five gear synchro 5c are used for five gear driven gear 5b to engage with the second output shaft 22, and such as the sliding hub of five gear synchro 5c moves right, then five gear driven gear 5b can be engaged with the second output shaft 22, thus five gear driven gear 5b and the second output shaft 22 synchronous axial system.

With reference to the embodiment of Fig. 1-Figure 12, because reverse idler gear 72, intermediate idler 73 are all positioned on the second output shaft 22, and five gear driven gear 5b are also positioned on the second output shaft 22, and five gear synchro 5c are only for engaging five gear driven gear 5b, reverse gear synchronizer 74c only for engaging intermediate idler 73 and reverse idler gear 72.Therefore as one preferred embodiment, reverse gear synchronizer 74c and five keeps off synchro 5c and shares a shifting fork mechanism, thereby reduces a set of shifting fork mechanism, such that the structure of power drive system 100 is compacter, size is less.

Be understandable that, when being driven the sliding hub action of five gear synchro 5c and reverse gear synchronizer 74c by this shifting fork mechanism, shown in composition graphs 1, when the shift fork of this shifting fork mechanism drives the sliding hub of five gear synchro 5c to move right, five gear synchro 5c can engage five gear driven gear 5b, and now the sliding hub of reverse gear synchronizer 74c does not engage reverse idler gear 72 and intermediate idler 73.When the shift fork of this shifting fork mechanism drives the sliding hub of reverse gear synchronizer 74c to engage reverse idler gear 72 with intermediate idler 73, the sliding hub of five gear synchro 5c does not engage five gear driven gear 5b.Certainly, the course of action driving the sliding hub of reverse gear synchronizer 74c and five gear synchro 5c here about shifting fork mechanism is only schematic, can not be interpreted as it is to one restriction of the present invention.

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 and the second input shaft 12.

Shown in Fig. 2-Figure 12, 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.

About motor mechanical axis second gear 32, as mentioned above, it carries out linking with described in output shaft.Particularly, in certain embodiments, the second output shaft 22 is fixedly installed transmission gear 6, transmission gear 6 directly engages with motor mechanical axis second gear 32.Mention above, another electronic pattern and mixed dynamic pattern of reversing gear of reversing gear is also had according to the power drive system 100 of the embodiment of the present invention, because motor mechanical axis second gear 32 engages with the transmission gear 6 be fixed on the second output shaft 22, therefore the power from the first dynamotor 51 can be exported by this paths, realizes gear reversing function.

Particularly, another kind of electronic pattern of reversing gear is at vehicle, first dynamotor 51 is as propulsion source and by motor mechanical axis synchro 33c synchronously exporting power from the second output shaft 22 motor mechanical axis second gear 32, power finally exports wheel to by the second output shaft 22, thus realizes reversing.

That is, the first dynamotor 51 is now as electrical motor work, and its power produced can successively by finally exporting to wheel after motor mechanical axis 3, motor mechanical axis synchro 33c, motor mechanical axis second gear 32, transmission gear 6, second output shaft 22.

In brief, above-mentioned electronic pattern of reversing gear is at vehicle, motor mechanical axis synchro 33c engages motor mechanical axis 3 and motor mechanical axis second gear 32, and reverse gear synchronizer 74c does not engage intermediate idler 73 and reverse idler gear 72, and the power that reverses gear also does not export from reverse gear 71.

Vehicle be in another kind of mixed dynamic reverse gear pattern time, driving engine 4 as dynamic origin by the Power output that produces to described of input shaft, and synchronously output power to reverse gear 71 by reverse gear synchronizer 74c.

Meanwhile, first dynamotor 51 is as propulsion source and by motor mechanical axis synchro 33c synchronously exporting power from the second output shaft 22 motor mechanical axis second gear 32, power finally exports wheel to by the second output shaft 22, thus realizes reversing.

Certainly, because power of moveing backward under this pattern is from driving engine 4 and the first dynamotor 51, therefore power needed to be coupled before exporting wheel to, such as this two parts power can carry out power coupling at main reduction gear driven gear 74 place of vehicle, power after coupling finally exports to wheel, thus realizes mixed dynamic reversing.

Under this pattern, reverse gear synchronizer 74c engages intermediate idler 73 and reverse idler gear 72, motor mechanical axis synchro 33c engages motor mechanical axis 3 and motor mechanical axis second gear 32, and reversing gear, a power part exports from reverse gear 71, another part exports from the second output shaft 22.

A kind of electromotive inverted gear pattern before contrast, electronic its power resources of pattern of reversing gear of rear one are constant, namely be still the first dynamotor 51, different places is, in front a kind of electromotive inverted gear pattern, the power that reverses gear that first dynamotor 51 exports exports reverse gear 71 to, by reverse gear 71 output power to wheel realize reverse gear, then a kind ofly electronicly reverse gear in pattern, the power that reverses gear of the first dynamotor 51 exports from the second output shaft 22, export to wheel by the second output shaft 22 to realize reversing gear, namely the power that reverses gear of this pattern is without reverse gear 71.

Similarly, for front one mixed dynamic reverse gear pattern and rear a kind of mixed dynamic pattern of reversing gear, it all combines the path of reversing gear of reverse gear path and first dynamotor 51 of driving engine 4, and difference and the above-mentioned electronic pattern similarity that reverses gear, repeat no more here.

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.

Below in conjunction with Fig. 2-Figure 12, the relation between three power take-off shafts (i.e. the first output shaft 21, second output shaft 22 and motor mechanical axis 3) and differential for vehicles 75 is described in detail.

The diff 75 of vehicle can be arranged between a pair front-wheel or between pair of rear wheels, and in examples more of the present invention, diff 75 is between a pair front-wheel.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.

As mentioned above, reverse gear 71 is the clutch ends of pattern of reversing gear as major part, and therefore this reverse gear 71 engages with main reduction gear driven gear 74 equally.And also engage with reverse idler gear 72 due to reverse gear 71 simultaneously, simultaneously in order to obtain the suitable speed ratio that reverses gear, as optional a kind of embodiment, reverse gear 71 is configured to dual gear, a part for the reverse gear 71 of this duplex-gear structure engages with reverse idler gear 72, and another part of the reverse gear 71 of this duplex-gear structure engages with main reduction gear driven gear 74.In other words, one of them gear part 712 of reverse gear 71 to engage with reverse idler gear 72 and another gear part 711 engages with main reduction gear driven gear 74.The good speed ratio that reverses gear can not only be obtained thus, reverse gear simultaneously transmission of power time each gear can not interfere, ensure that the transmission of power that reverses gear is reliable.

Driving limit, limit charging simultaneously in joint situation of power generation in parking, double-clutch 2d and the speed governing of the first dynamotor 51 2 gear is comprised according to some typical conditions of the power drive system 100 of the embodiment of the present invention.

First this typical condition of power generation in parking is described, when vehicle is in parked state, driving engine 4 is arranged to the Power output that produces to the described one (input shaft namely carrying out linking with motor mechanical axis first gear 31 of input shaft, such as the second input shaft 12), and output power to the first dynamotor 51 by motor mechanical axis synchro 33c to the synchronous of motor mechanical axis first gear 31, thus the first dynamotor 51 is driven to generate electricity.

Specifically, the specific embodiment of composition graphs 2-Figure 12 example, power can be exported to the second input shaft 12 by double-clutch 2d by driving engine 4 after vehicle parking, this second input shaft 12 is link with motor mechanical axis first gear 31 on motor mechanical axis 3, control motor mechanical axis synchro 33c and engage motor mechanical axis 3 and motor mechanical axis first gear 31, the power that then driving engine 4 exports will from the second input shaft 12, intermediate idler 73, motor mechanical axis first gear 31 and motor mechanical axis synchro 33c export motor mechanical axis 3 to, this part power final exports to the first dynamotor 51 from motor mechanical axis 3, thus drive the first dynamotor 51 to generate electricity as electrical generator.

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 motor mechanical axis 3, thus the first dynamotor 51 is driven to generate electricity.

Specifically, the specific embodiment of composition graphs 2-Figure 12 example, under this operating mode, a part of power of driving engine 4 can export from the first output shaft 21 or the second output shaft 22, such as, three gear gear pairs or five secondary by first gear keep off gear pairs and export, another part power of driving engine 4 can export to the first dynamotor 51 from motor mechanical axis first gear 31, motor mechanical axis synchro 33c, this path of motor mechanical axis 3, thus drives the first dynamotor 51 to generate electricity.

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.

Two gear speed-regulating functions of the first dynamotor 51 are described again, particularly, shown in composition graphs 2-Figure 12, because motor mechanical axis synchro 33c is arranged between motor mechanical axis first gear 31 and motor mechanical axis second gear 32, first dynamotor 51 is when as electrical motor outputting power, optionally can be exported by motor mechanical axis first gear 31 or motor mechanical axis second gear 32, in the transition period, need the synchronism switching of motor mechanical axis synchro 33c.

Such as, be from the process of motor mechanical axis second gear 32 outputting power from motor mechanical axis first gear 31 output motor powershift, the sliding hub of motor mechanical axis synchro 33c needs to be switched to from the position engaged with motor mechanical axis first gear 31 position engaged with motor mechanical axis second gear 32, because the speed ratio of bang path between motor mechanical axis first gear 31 to main reduction gear driven gear 74 is different from the speed ratio of drive path between motor mechanical axis second gear 32 and main reduction gear driven gear 74, therefore in the process of handoff synchronizer synchronous dynamo dynamical axis second gear 32, motor mechanical axis second gear 32 and motor mechanical axis 3 are that differential rotates, the synchronization time of synchro can be increased like this, too increase the wearing and tearing of synchro simultaneously, reduce driving efficiency, easily there is power interruption or for a long time cannot the synchronously pause and transition in rhythm or melody sense caused.

Now, the first dynamotor 51 regulates motor mechanical axis 3 rotating speed based on the rotating speed of motor mechanical axis second gear 32 can be controlled, namely to promote for target with the rotating speed of motor mechanical axis second gear 32 or reduce the rotating speed of motor mechanical axis 3, the rotating speed of motor mechanical axis 3 can be mated (namely roughly equal or close) with motor mechanical axis second gear 32 within the shortest time, thus make motor mechanical axis synchro 33c can engage motor mechanical axis second gear 32 and motor mechanical axis 3 fast, reduce the motor mechanical axis synchro 33c synchronous required time, drastically increase the driving efficiency of vehicle, synchronous controllability and synchronous real-time.In addition, the life-span of motor mechanical axis synchro 33c is able to further prolongation, thus reduces the cost of car load maintenance.

Similarly, be from the process of motor mechanical axis first gear 31 outputting power from motor mechanical axis second gear 32 output motor powershift, first dynamotor 51 can based on the rotating speed of the speed adjustment motor mechanical axis 3 of motor mechanical axis first gear 31, namely to promote for target with motor mechanical axis first gear 31 rotating speed or reduce the rotating speed of motor mechanical axis 3, the rotating speed of motor mechanical axis 3 can be mated with motor mechanical axis first gear 31 within the shortest time, thus improve the joint efficiency of motor mechanical axis synchro 33c.

To sum up, in brief, the joint of motor mechanical axis synchro 33c in motor mechanical axis first gear 31 and motor mechanical axis second gear 32 switches to and between another joint aging time, the first dynamotor 51 is arranged to another the rotating speed in motor mechanical axis first gear 31 and motor mechanical axis second gear 32 as target carries out speed governing to motor mechanical axis 3.

For first this function of dynamotor 51 speed governing, typical condition is under electric-only mode, when namely the first dynamotor 51 drives vehicle to travel.Certainly, the present invention is not limited to this, for other pattern such as mixed dynamic model formula, when needing motor mechanical axis synchro 33c to come switch motor dynamical axis first gear 31 and motor mechanical axis the second gear 32, the first dynamotor 51 pairs of motor mechanical axis 3 all can be adopted to carry out speed governing.

Thus, according to the power drive system 100 of the embodiment of the present invention, when motor mechanical axis synchro 33c switches engage position between motor mechanical axis first gear 31 and motor mechanical axis second gear 32, by the speed governing of the first dynamotor 51 pairs of motor mechanical axis 3, make the rotating speed of motor mechanical axis 3 can with gear (such as motor mechanical axis first gear 31 or motor mechanical axis second gear 32) rotational speed matches to be joined, namely the first dynamotor 51 can with the rotating speed of gear to be joined for the rotating speed of target to motor mechanical axis 3 regulates, the rotating speed of motor mechanical axis 3 is mated at short notice with the rotating speed of gear to be joined, facilitate the joint of motor mechanical axis synchro 33c, thus substantially increase driving efficiency, reduce the transmission loss of intermediate energy.

According to the power drive system 100 of some embodiments of the present invention, a 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, dynamotor 52 can with main reduction gear driven gear 74 transmission, the motor shaft of 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, 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, dynamotor 52 is two and is separately positioned on the both sides of diff 75, and such as these two dynamotors 52 can become one with diff 75.Or, aforesaid driving engine 4 and the first dynamotor 51 are for driving front-wheel, dynamotor 52 also can be wheel motor and for trailing wheel, or dynamotor 52 can drive two trailing wheels by a speed reduction gearing, or 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. 5-Figure 12, 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 shown in Fig. 5-Figure 12, 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. 5-Figure 12, 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 5-Figure 12,3rd 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. 5-Figure 12, 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 5-Figure 12 of the 3rd dynamotor 201, the 4th dynamotor 301 and wheel is described in detail.

In certain embodiments, as shown in Fig. 5-Fig. 7, Fig. 9-Figure 11, by gear structure indirect drive between 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 Fig. 5-Fig. 7, Fig. 9-Figure 11, 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 Fig. 5-Fig. 7, Fig. 9-Figure 11, 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 figs. 5 and 9, 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 figs. 6 and 10, 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 seen in figs. 7 and 11, 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 Fig. 8 and Figure 12, the 3rd dynamotor 201 and corresponding wheel are coaxially connected and the 4th dynamotor 301 is 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 figs. 8 and 12, 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. 2-Figure 12.

Embodiment one:

As shown in Figure 2, 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 can with a gear driving gear 1a of the first input shaft 11 synchronous axial system, three gear driving gear 3a and five gear driving gear 5a, one gear driving gear 1a is positioned at the right side of five gear driving gear 5a, and three gear driving gear 3a are positioned at the left side of five gear driving gear 5a.

Second input shaft 12 is provided with can with two gear driving gear 2a and four gear driving gear 4a of the second input shaft 12 synchronous axial system, and two gear driving gear 2a are positioned at left side and four gear driving gear 4a are positioned at right side.

First output shaft 21 and two input shafts are arranged in parallel, first output shaft 21 is set with a gear driven gear 1b, two gear driven gear 2b, three gear driven gear 3b and four gear driven gear 4b, one gear driven gear 1b and one keeps off driving gear 1a and directly engages, two gear driven gear 2b and two keep off driving gear 2a and directly engage, three gear driven gear 3b and three keep off driving gear 3a and directly engage, and four gear driven gear 4b and four keep off driving gear 4a and directly engage.

First output shaft 21 is also provided with one or three gear synchro 13c and two or four gear synchro 24c, one or three gear synchro 13c keep off between driven gear 3b at a gear driven gear 1b and three, and optionally by synchronous with the first output shaft 21 for a gear driven gear 1b or three gear driven gear 3b, two or four gear synchro 24c keep off between driven gear 4b at two gear driven gear 2b and four, and optionally by synchronous with the first output shaft 21 for two gear driven gear 2b or four gear driven gear 4b.

Second output shaft 22 is same to be arranged in parallel with two input shafts, second output shaft 22 is set with five gear driven gear 5b, five gear driven gear 5b and five keep off driving gear 5a and directly engage, second output shaft 22 is also provided with five gear synchro 5c, five gear synchro 5c are used for synchronous with the second output shaft 22 for five gear driven gear 5b.

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 is positioned at left side, and motor mechanical axis second gear 32 is positioned at right side.Motor mechanical axis 3 is also provided with motor mechanical axis synchro 33c, motor mechanical axis synchro 33c between motor mechanical axis first gear 31 and motor mechanical axis second gear 32, motor mechanical axis synchro 33c be used for optionally by synchronous with motor mechanical axis 3 for motor mechanical axis first gear 31 or by motor mechanical axis second gear 32 and motor mechanical axis 3 synchronous.

In addition, as shown in Figure 2, second output shaft 22 is also provided with and the transmission gear 6 of the second output shaft 22 synchronous axial system and empty set can be provided with reverse idler gear 72, transmission gear 6 directly engages with motor mechanical axis second gear 32, the side of reverse idler gear 72 is formed with tooth cover 721, tooth cover 721 same empty sets are on the second output shaft 22, intermediate idler 73 empty set is on tooth cover 721, intermediate idler 73 keeps off driving gear 2a with two respectively and motor mechanical axis first gear 31 engages, reverse gear synchronizer 74c be arranged in tooth cover 721 on and can be used for engage intermediate idler 73.

Reverse gear 71 is configured to dual gear, a gear part 712 of reverse gear 71 engages with reverse idler gear 72, another gear part 711 of reverse gear 71 directly engages with main reduction gear driven gear 74, the first output shaft 21 is fixedly installed on the first output shaft output gear 211, second output shaft 22 engaged with main reduction gear driven gear 74 simultaneously and is fixedly installed the second output shaft output gear 221 engaged with main reduction gear driven gear 74.

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

Below the typical condition of power drive system 100 shown in Fig. 2 is described in detail.

Parking charging operating mode:

The input end 23d of double-clutch 2d engages the second mouth 22d and disconnects with the first mouth 21d, motor mechanical axis synchro 33c engages motor mechanical axis first gear 31, thus the power that driving engine 4 exports passes to the first dynamotor 51 through the input end 23d of double-clutch 2d, the second mouth 22d, the second input shaft 12, two after keeping off driving gear 2a, intermediate idler 73, motor mechanical axis first gear 31, motor mechanical axis synchro 33c, motor mechanical axis 3 successively, thus the first dynamotor 51 is driven 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:

Path one: motor mechanical axis synchro 33c engages motor mechanical axis first gear 31, the power that first dynamotor 51 exports exports the second input shaft 12 to by motor mechanical axis first gear 31, intermediate idler 73, two or four gear synchro 24c engage two gear driven gear 2b or four gear driven gear 4b, thus the power of the first dynamotor 51 exports by second gear pair or four gear gear pairs.

Path two: the power that motor mechanical axis synchro 33c engages the output of motor mechanical axis second gear 32, first dynamotor 51 is exported from the second output shaft 22 by motor mechanical axis second gear 32, transmission gear 6.

Thus, under power drive system 100 is in pure electronic operating mode, the first dynamotor 51 can output power to wheel by above-mentioned two paths with different speed ratio, thus drives vehicle to travel.

Preferably, when switching above-mentioned path, the first dynamotor 51 can carry out speed governing to motor mechanical axis 3.

First describe and switch to path two from path one: now motor mechanical axis synchro 33c moves to the position engaged with motor mechanical axis second gear 32 from the position engaged with motor mechanical axis first gear 31, during this period, first dynamotor 51 can with the rotating speed of motor mechanical axis second gear 32 for target, the rotating speed of motor mechanical axis 3 is regulated, the rotating speed of motor mechanical axis 3 is mated with motor mechanical axis second gear 32, thus motor mechanical axis synchro 33c can engage motor mechanical axis second gear 32 fast, improve synchronous efficiency.

Secondly describe and switch to path one from path two: now motor mechanical axis synchro 33c moves to the position engaged with motor mechanical axis first gear 31 from the position engaged with motor mechanical axis second gear 32, during this period, first dynamotor 51 can with the rotating speed of motor mechanical axis first gear 31 for target, the rotating speed of motor mechanical axis 3 is regulated, the rotating speed of motor mechanical axis 3 is mated with motor mechanical axis first gear 31, thus motor mechanical axis synchro 33c can engage motor mechanical axis first gear 31 fast, improve synchronous efficiency.

Certainly, should be understood that, above-mentioned speed-regulating mode is not only applicable to pure electronic operating mode, other operating modes can also be applicable to, such as mixed condition etc. of starting building, as long as the operating mode that the engagement state relating to motor mechanical axis synchro 33c changes (such as engage with motor mechanical axis second gear 32 from engaging with motor mechanical axis first gear 31 to switch to or engage with motor mechanical axis first gear 31 from engaging to switch to motor mechanical axis second gear 32), is all applicable to above-mentioned speed-regulating mode.

The mixed condition scheme one of starting building of each gear:

Power drive system 100 be in a gear mixed start building condition time, one or three gear synchro 13c engage a gear driven gear 1b, the input end 23d of double-clutch 2d engages the first mouth 21d and disconnects with the second mouth 22d, and motor mechanical axis synchro 33c engages motor mechanical axis second gear 32.Thus the power that driving engine 4 exports is exported from the first output shaft 21 by the first input shaft 11, first gear pair, the power that first dynamotor 51 exports is exported from the second output shaft 22 by motor mechanical axis second gear 32, transmission gear 6, two parts power is finally coupled at main reduction gear driven gear 74 place, and the power after coupling distributes to the wheel of both sides from diff 75.

Under the mixed condition of starting building of this gear, 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.

Power drive system 100 be in two gears mixed start building condition time, two or four gear synchro 24c engage two gear driven gear 2b, the input end 23d of double-clutch 2d engages the second mouth 22d and disconnects with the first mouth 21d, and motor mechanical axis synchro 33c engages motor mechanical axis second gear 32.Thus the power that driving engine 4 exports is exported from the first output shaft 21 by the second input shaft 12, second gear pair, the power that first dynamotor 51 exports is exported from the second output shaft 22 by motor mechanical axis second gear 32, transmission gear 6, two parts power is finally coupled at main reduction gear driven gear 74 place, and the power after coupling distributes to the wheel of both sides from diff 75.

Under the mixed condition of starting building of this gear, 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.

Power drive system 100 be in three gears mixed start building condition time, to be in the mixed condition of starting building of a gear similar with power drive system 100, difference is that one or three gear synchro 13c engage three gear driven gear 3b, the power of driving engine 4 is exported by three gear gear pairs, all the other keep off mixed dynamic transmission substantially with one roughly the same, repeat no more here.

Power drive system 100 be in four gears mixed start building condition time, to be in the mixed condition of starting building of two gears similar with power drive system 100, difference is that two or four gear synchro 24c engage four gear driven gear 4b, the power of driving engine 4 is exported by four gear gear pairs, all the other keep off mixed dynamic transmission substantially with two roughly the same, repeat no more here.

Power drive system 100 be in five gears mixed start building condition time, five gear synchro 5c engage five gear driven gear 5b, the input end 23d of double-clutch 2d engages the first mouth 21d and disconnects with the second mouth 22d, and motor mechanical axis synchro 33c engages motor mechanical axis second gear 32.Thus the power that driving engine 4 exports is exported from the second output shaft 22 by the first input shaft 11, five gear gear pair, the power that first dynamotor 51 exports is exported from the second output shaft 22 by motor mechanical axis second gear 32, transmission gear 6, two parts power is coupled on the second output shaft 22, and the power after coupling distributes to the wheel of both sides from diff 75.

Under the mixed condition of starting building of this gear, 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.

The mixed condition scheme two of starting building of each gear:

Power drive system 100 be in a gear mixed start building condition time, one or three gear synchro 13c engage a gear driven gear 1b, two or four gear synchro 24c engage two gear driven gear 2b and (export from second gear pair for the first dynamotor 51 power, certainly also can export from four gear gear pairs), the input end 23d of double-clutch 2d engages the first mouth 21d and disconnects with the second mouth 22d, and motor mechanical axis synchro 33c engages motor mechanical axis first gear 31.

Thus the power that driving engine 4 exports exports the first output shaft 21 to by the first input shaft 11, first gear pair, the power that first dynamotor 51 exports exports the first output shaft 21 to by motor mechanical axis first gear 31, intermediate idler 73, second gear pair, two or four gear synchro 24c, two parts power is coupled on the first output shaft 21, and the power after coupling distributes to the wheel of both sides from diff 75.

Under the mixed condition of starting building of this gear, the first dynamotor 51 can carry out speed governing, thus makes the first output shaft 21 synchronously can receive power from driving engine 4 and the first dynamotor 51 evenly, improves ride comfort, the harmony of transmission.

Power drive system 100 be in two gears mixed start building condition time, two or four gear synchro 24c engage two gear driven gear 2b, the input end 23d of double-clutch 2d engages the second mouth 22d and disconnects with the first mouth 21d, and motor mechanical axis synchro 33c engages motor mechanical axis first gear 31.Thus the power that driving engine 4 exports exports second gear pair to by the second input shaft 12, the power that first dynamotor 51 exports exports second gear pair to by motor mechanical axis first gear 31, intermediate idler 73, two parts power is coupled in second gear pair, and power first output shaft 21 after coupling exports.

Under the mixed condition of starting building of this gear, the first dynamotor 51 can carry out speed governing, thus makes the secondary power that can synchronously receive evenly from driving engine 4 and the first dynamotor 51 of second gear, improves ride comfort, the harmony of transmission.

Power drive system 100 be in three gears mixed start building condition time, to be in the mixed condition of starting building of a gear similar with power drive system 100, difference is that one or three gear synchro 13c engage three gear driven gear 3b, the power of driving engine 4 is exported by three gear gear pairs, all the other keep off mixed dynamic transmission substantially with one roughly the same, repeat no more here.

For the mixed condition of starting building of four gears, because two or four gear gear pairs share two or four gear synchro 24c, therefore cannot realize the mixed condition of starting building of four gears in this mode.

Power drive system 100 be in five gears mixed start building condition time, five gear synchro 5c engage five gear driven gear 5b, two or four gear synchro 24c engage two gear driven gear 2b, the input end 23d of double-clutch 2d engages the first mouth 21d and disconnects with the second mouth 22d, and motor mechanical axis synchro 33c engages motor mechanical axis first gear 31.

Thus the power that driving engine 4 exports exports the second output shaft 22 to by the first input shaft 11, five gear gear pair, the power that first dynamotor 51 exports exports the first output shaft 21 to by motor mechanical axis first gear 31, intermediate idler 73, second gear pair, two or four gear synchro 24c, two parts power is coupled at main reduction gear driven gear 74 place, and the power after coupling distributes to the wheel of both sides from diff 75.

Under the mixed condition of starting building of this gear, 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.

It should be noted that, above-mentioned each gear mixes condition scheme two of starting building and illustrates for two or four gear synchro 24c joint two gear driven gear 2b, certainly under this pattern, two or four gear synchro 24c also can engage four gear driven gear 4b, the now mixed dynamic principle of each gear and above-mentioned unanimous on the whole, repeats here no longer one by one.And be understandable that, cannot realize the mixed condition of starting building of two gears engage the pattern of four gear driven gear 4b at two or four gear synchro 4c under, it is mixed dynamic consistent that principle and above-mentioned pattern cannot realize four gears.

To sum up, for the ordinary skill in the art, can be according to actual needs, the mixed arbitrarily dynamic path selecting above-mentioned any each gear to mix neatly to start building condition scheme one and each gear to mix to start building in condition scheme two, 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:

When power drive system 100 is in a rib driving limit charging operating mode, one or three gear synchro 13c engage a gear driven gear 1b, the input end 23d of double-clutch 2d engages with the first mouth 21d and disconnects with the second mouth 22d, and motor mechanical axis synchro 33c engages motor mechanical axis second gear 32.Thus the power that driving engine 4 exports is exported from the first output shaft 21 by the first input shaft 11, first gear pair, simultaneously from the anti-energy that drags of wheel by exporting the first dynamotor 51 to after the second output shaft 22, transmission gear 6, motor mechanical axis second gear 32, motor mechanical axis 3, thus drive the first dynamotor 51 to generate electricity.

When power drive system 100 is in two ribs driving limit charging operating modes, two or four gear synchro 24c engage two gear driven gear 2b, the input end 23d of double-clutch 2d engages with the second mouth 22d and disconnects with the first mouth 21d, and motor mechanical axis synchro 33c engages motor mechanical axis first gear 31.Thus a part of power that driving engine 4 exports is exported from the first output shaft 21 by the second input shaft 12, second gear pair, another part power that driving engine 4 exports by exporting to the first dynamotor 51 after the second input shaft 12, intermediate idler 73, motor mechanical axis first gear 31, motor mechanical axis 3, thus drives the first dynamotor 51 to generate electricity.

Power drive system 100 be in three ribs drive limits charging operating mode time, with power drive system 100 be in a rib drives limit charge operating mode time basically identical, difference is that now one or three gear synchro 13c joints three keep off driven gear 3b.

Power drive system 100 be in four ribs drive limits charging operating mode time, with power drive system 100 be in two ribs drives limit charge operating mode time basically identical, difference is that now two or four gear synchro 24c joints four keep off driven gear 4b.

When power drive system 100 is in five ribs driving limit charging operating modes, five gear synchro 5c engage five gear driven gear 5b, the input end 23d of double-clutch 2d engages with the first mouth 21d and disconnects with the second mouth 22d, and motor mechanical axis synchro 33c engages motor mechanical axis second gear 32.Thus the power that driving engine 4 exports is exported from the second output shaft 22 by the first input shaft 11, five gear gear pair, partial power simultaneously on the second output shaft 22 also by exporting the first dynamotor 51 to after transmission gear 6, motor mechanical axis second gear 32, motor mechanical axis 3, 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.

With this understanding, when power drive system 100 is in a rib driving limit charging operating mode, the input end 23d of double-clutch 2d engages the first mouth 21d and the second mouth 22d simultaneously, one or three gear synchro 13c engage a gear driven gear 1b, motor mechanical axis synchro 33c engages motor mechanical axis first gear 31, thus a part of power that driving engine 4 exports is by the first input shaft 11, first gear pair exports from the first output shaft 21, another part power that driving engine 4 exports is from the second input shaft 12, intermediate idler 73, motor mechanical axis first gear 31, the first dynamotor 51 exported in motor mechanical axis 3, thus drive the first dynamotor 51 to generate electricity.

With this understanding, when power drive system 100 is in three ribs driving limit charging operating modes or is in five ribs driving limits charging operating modes, being in a rib with above-mentioned power drive system 100 drives limit operating mode of charging roughly the same, difference is, during three gear transmissions, one or three gear synchro 13c engage three gear driven gear 3b, and during five gear transmissions, five keep off synchro 5c and engage five gear driven gear 5b and power exports from the second output shaft 22.

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:

Power drive system 100 be in machinery reverse gear operating mode time, the synchronous reverse idler gear 72 of reverse gear synchronizer 74c and intermediate idler 73, the input end 23d of double-clutch 2d engages the second mouth 22d and disconnects with the first mouth 21d, and the power that driving engine 4 exports is by exporting from reverse gear 71 after the second input shaft 12, intermediate idler 73, reverse idler gear 72.

Power drive system 100 be in electronic reverse gear pattern time, the power that motor mechanical axis synchro 33c synchronous dynamo dynamical axis 3 and motor mechanical axis first gear 31, the synchronous reverse idler gear 72 of reverse gear synchronizer 74c and intermediate idler 73, first dynamotor 51 export is by exporting from reverse gear 71 after motor mechanical axis 3, motor mechanical axis first gear 31, intermediate idler 73, reverse idler gear 72.

Power drive system 100 be in mixed dynamic reverse gear pattern time, motor mechanical axis synchro 33c synchronous dynamo dynamical axis 3 and motor mechanical axis first gear 31, the synchronous reverse idler gear 72 of reverse gear synchronizer 74c and intermediate idler 73, the power that driving engine 4 exports exports intermediate idler 73 to by the second input shaft 12, the power that first dynamotor 51 exports exports intermediate idler 73 to by motor mechanical axis 3, motor mechanical axis first gear 31, and two parts power is exported from reverse gear 71 by reverse idler gear 72 after the coupling of intermediate idler 73 place again.

In parking presented hereinbefore charging operating mode, pure electronic operating mode, the mixed condition scheme one of starting building of each gear, the mixed condition scheme two of starting building of each gear, driving limit, driving engine limit charging operating mode scheme one, driving limit, driving engine limit charging operating mode scheme two and reverse gear in operating mode, 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, the mixed condition scheme one of starting building of each gear, each gear mixes condition scheme two of starting building 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 any operating mode of the work of participation, improve the impact sense because motor commutation brings, pause and transition in rhythm or melody sense etc., improve the life-span of power drive system 100.

Embodiment two:

As shown in Figure 3, the power drive system 100 in this embodiment is reverse idler gear 72, intermediate idler 73 and reverse gear synchronizer 74c place with the key distinction of the power drive system 100 shown in Fig. 2.In this embodiment, reverse idler gear 72 and intermediate idler 73 are that adjacent vacant is enclosed within the second output shaft 22, and reverse gear synchronizer 74c to be arranged on intermediate idler 73 and for engaging reverse idler gear 72.Then can be basically identical with the power drive system 100 in Fig. 2 embodiment for remainder, repeat no more here.

Embodiment three:

As shown in Figure 4, the power drive system 100 in this embodiment and the key distinction of the power drive system 100 shown in Fig. 3 are the structure of intermediate idler 73.In this embodiment, intermediate idler 73 is configured to dual gear, and there is gear part 731,732, one of them gear part 731 and two is kept off driving gear and is engaged (namely with the gear driving gear on described of input shaft), and another gear part 732 engages with motor mechanical axis first gear 31.Then can be basically identical with the power drive system 100 in Fig. 3 embodiment for remainder, repeat no more here.

Embodiment four-embodiment seven:

As shown in Figure 5-Figure 8, 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. 2, 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 eight-embodiment 11:

As shown in Fig. 9-Figure 12, 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. 3, 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.

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 well known structures omitted herein.

Based on above-described embodiment power drive system and there is the vehicle of this power drive system, the embodiment of the present invention proposes a kind of control method of reversing gear of hybrid vehicle, wherein, the control method of reversing gear of the hybrid vehicle of the embodiment of the present invention performs based on the hybrid vehicle with above-mentioned power drive system.Describe the control method of reversing gear of hybrid vehicle according to embodiment of the present invention proposition with reference to the accompanying drawings, the Power Train of hybrid vehicle unifies hybrid vehicle.

Figure 13 is the diagram of circuit of the control method of reversing gear of hybrid vehicle according to the embodiment of the present invention.The power drive system of hybrid vehicle comprises driving engine, multiple input shaft, multiple output shaft, motor mechanical axis and the first dynamotor, wherein, driving engine is arranged to optionally engage at least one in multiple input shaft, 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, motor mechanical axis is arranged to link with in input shaft, first dynamotor is arranged to link with motor mechanical axis, and one in motor mechanical axis and input shaft when linking, first dynamotor can utilize from driving engine export at least part of power hybrid electric vehicle sail and parking time generate electricity.As shown in figure 13, this control method of reversing gear comprises the following steps:

S1: when hybrid vehicle reverse travel, judge the demand torque of hybrid vehicle.

S2: according to the demand torque of hybrid vehicle, hybrid vehicle is controlled to power drive system and to reverse gear mode operation with pure electronic reverse gear pattern or hybrid power.

In addition, according to one embodiment of present invention, first dynamotor can have the first gear and the second gear, wherein, power drive system also comprises motor mechanical axis synchro, motor mechanical axis first gear and motor mechanical axis second gear, the joint of motor mechanical axis synchro in motor mechanical axis first gear and motor mechanical axis second gear switches to and between another joint aging time, first dynamotor is arranged to another the rotating speed in motor mechanical axis first gear and motor mechanical axis second gear as target carries out speed governing to motor mechanical axis, switch between the first gear and the second gear to make the gear of the first dynamotor.

Wherein, the difference of the first gear and the second gear is embodied on speed ratio, forms two kinds of speed ratios by the power drive system of the present embodiment, and different speed ratios can change rotating speed and the wheel end output torque of the first dynamotor.Wherein, the speed ratio of the first gear is greater than the speed ratio of the second gear.

Thus, first dynamotor is by the automatic switchover of two gear gears, both ensure that the high pulling torque demand of hybrid vehicle during low speed, when can ensure again high speed, dynamotor rotating speed can not be too high, also can improve the work efficiency of the first dynamotor well simultaneously.

The hybrid vehicle describing the embodiment of the present invention in detail below by four embodiments reverses gear control method.

According to one embodiment of present invention, when the demand torque of hybrid vehicle be less than or equal to default reverse gear moment of torsion time, control hybrid vehicle with the pure electronic mode operation that reverses gear, wherein, stirred to first direction by two or four gear synchros in control power drive system and motor mechanical axis synchro, select the first gear to make the first dynamotor 51.

According to a concrete example of the present invention, stirring to first direction can for stir left, and the first dynamotor 51 can be used for driving front vehicle wheel running.

Specifically, as shown in figure 14, when the demand torque of hybrid vehicle be less than or equal to default reverse gear moment of torsion time, two or four gear synchro 24c and motor mechanical axis synchro 33c can be controlled all be moved to the left, namely say, control motor mechanical axis synchro 33c and engage motor mechanical axis first gear 31, the power that first dynamotor 51 exports exports the second input shaft 12 to by motor mechanical axis first gear 31, intermediate idler 73, two or four gear synchro 24c engage two gear driven gear 2b, thus the power of the first dynamotor 51 exports by second gear pair.Thus, make the first dynamotor 51 select the first gear, thus power is reached wheel by the first gear by the first dynamotor 51, thus realize reversing, concrete power transmission line is as shown in curve in Figure 14 1.

Further, according to one embodiment of present invention, when the demand torque of hybrid vehicle be greater than default reverse gear moment of torsion time, control hybrid vehicle to reverse gear mode operation with hybrid power, wherein, control two or four gear synchros and remain on predeterminated position such as midway location, and control motor mechanical axis synchro and stir to second direction, to make the first dynamotor select the second gear, the reverse gear synchronizer controlled in power drive system is stirred to first direction simultaneously.

Wherein, according to a concrete example of the present invention, stirring to second direction can for stir to the right.

Specifically, as shown in figure 15, when two or four gear synchro 24c are retained to midway location, and motor mechanical axis synchro 33c is when moving right, two or four gear synchro 24c do not engage two gear driven gear 2b and four gear driven gear 4b, motor mechanical axis synchro 33c engages motor mechanical axis second gear 32, the power that first dynamotor 51 exports exports the second output shaft 22 to by motor mechanical axis second gear 32, transmission gear 6, power finally exports wheel to by the second output shaft 22, and concrete power transmission line is as shown in curve in Figure 15 2.

When reverse gear synchronizer 74c is moved to the left, the power that driving engine 4 exports reaches wheel by double-clutch 2d, the second input shaft 12, the i.e. synchronous reverse idler gear 72 of reverse gear synchronizer 74c and intermediate idler 73, the input end 23d of double-clutch 2d engages the second mouth 22d and disconnects with the first mouth 21d, the power that driving engine 4 exports is by exporting wheel to from reverse gear 71 after the second input shaft 12, intermediate idler 73, reverse idler gear 72, and concrete power transmission line is as shown in curve in Figure 15 3.

Like this, when the demand torque of hybrid vehicle be greater than default reverse gear moment of torsion time, control two or four gear synchro 24c and move right to midway location, and control motor mechanical axis synchro 33c and move right, meanwhile, control reverse gear synchronizer 74c and be moved to the left and control driving engine 4 outputting power.Namely say, power is exported from the second output shaft 22 the synchronous of motor mechanical axis second gear 32 by motor mechanical axis synchro 33c by the power of the first dynamotor, simultaneously, the synchronous reverse idler gear 72 of reverse gear synchronizer 74c and intermediate idler 73, the power that driving engine 4 exports is by the second input shaft 12, intermediate idler 73, reverse idler gear 72 exports from reverse gear 71, two parts power needed to be coupled before exporting wheel to, such as this two parts power can carry out power coupling at main reduction gear driven gear 74 place of vehicle, power after coupling finally exports to wheel, thus realize mixed dynamic reversing.

It can thus be appreciated that, in the present embodiment, when hybrid vehicle reverse travel, if demand torque is less than or equal to the default moment of torsion that reverses gear, with the pure electronic mode operation that reverses gear, the first dynamotor selects larger the first gear of speed ratio, thus has realized dynamic property better; If demand torque is greater than the default moment of torsion that reverses gear, engine starting assists the first dynamotor to drive running car, and the gear speed governing gearshift of the first dynamotor is to the second gear.Like this, the control method of reversing gear of the present embodiment can realize good dynamic property.

Further, when the gear of the first dynamotor switches to the second gear from the first gear, by the impact that can cause power interruption in short-term in shift process can be avoided on electric machine speed regulation, the ride comfort of hybrid vehicle is ensured.

According to another embodiment of the invention, when the demand torque of hybrid vehicle be less than or equal to default reverse gear moment of torsion time, control hybrid vehicle with the pure electronic mode operation that reverses gear, wherein, stirring to second direction by controlling motor mechanical axis synchro, selecting the second gear to make the first dynamotor.

Specifically, as shown in figure 16, when the demand torque of hybrid vehicle be less than or equal to default reverse gear moment of torsion time, motor power axle synchro 33c can be controlled move right, namely say, control motor mechanical axis synchro 33c and engage motor mechanical axis second gear 32, the power that first dynamotor 51 exports exports wheel to by motor mechanical axis second gear 32, transmission gear 6, second output shaft 22, thus, make the first dynamotor 51 select the second gear, thus power is reached wheel by the second gear by the first dynamotor 51.Concrete power transmission line is as shown in curve in Figure 16 2.

Further, according to another embodiment of the invention, when the demand torque of hybrid vehicle be greater than default reverse gear moment of torsion time, control hybrid vehicle to reverse gear mode operation with hybrid power, wherein, stir to second direction by controlling motor mechanical axis synchro, to make the first dynamotor select the second gear, the reverse gear synchronizer controlled in power drive system is stirred to first direction simultaneously.

Specifically, as shown in figure 16, when controlling reverse gear synchronizer 74c and being moved to the left, the power that driving engine 4 exports reaches wheel by double-clutch 2d, the second input shaft 12, the i.e. synchronous reverse idler gear 72 of reverse gear synchronizer 74c and intermediate idler 73, the input end 23d of double-clutch 2d engages the second mouth 22d and disconnects with the first mouth 21d, the power that driving engine 4 exports is by exporting from reverse gear 71 after the second input shaft 12, intermediate idler 73, reverse idler gear 72, and concrete power transmission line is as shown in curve in Figure 16 3.

Like this, when the demand torque of hybrid vehicle be greater than default reverse gear moment of torsion time, motor power axle synchro 33c can be controlled and move right, control reverse gear synchronizer 74c simultaneously and be moved to the left and control driving engine 4 outputting power.Namely say, power is exported from the second output shaft 22 the synchronous of motor mechanical axis second gear 32 by motor mechanical axis synchro 33c by the power of the first dynamotor 51, simultaneously, the synchronous reverse idler gear 72 of reverse gear synchronizer 74c and intermediate idler 73, the power that driving engine 4 exports is by the second input shaft 12, intermediate idler 73, reverse idler gear 72 exports from reverse gear 71, two parts power needed to be coupled before exporting wheel to, such as this two parts power can carry out power coupling at main reduction gear driven gear 74 place of vehicle, power after coupling finally exports to wheel, thus realize mixed dynamic reversing.

It can thus be appreciated that, in the present embodiment, when hybrid vehicle reverse travel, if demand torque is less than or equal to the default moment of torsion that reverses gear, with the pure electronic mode operation that reverses gear, the second gear that the first dynamotor selects speed smaller, thus dynamic property is more weak; If demand torque is greater than the default moment of torsion that reverses gear, engine starting drives running car to assist the first dynamotor.Like this, the control method of reversing gear of the present embodiment is not shifted gears, power is without interruption, good ride comfort can be realized, control simply, but, time in reversing process, gear due to the first dynamotor is in the second gear, dynamic property is more weak, and the first dynamotor operates in the lower uneconomical region of rotating speed simultaneously, reduces the economy of automobile.

According to still another embodiment of the invention, when the demand torque of hybrid vehicle be less than or equal to default reverse gear moment of torsion time, control hybrid vehicle with the pure electronic mode operation that reverses gear, wherein, first dynamotor also has the gear that reverses gear, and stirred to first direction by the reverse gear synchronizer controlled in motor mechanical axis synchro and power drive system, select to reverse gear gear to make the first dynamotor.

Specifically, as shown in figure 17, when the demand torque of hybrid vehicle be less than or equal to default reverse gear moment of torsion time, motor power axle synchro 33c and reverse gear synchronizer 74c can be controlled and be all moved to the left.Namely say, control the power of motor mechanical axis synchro 33c synchronous dynamo dynamical axis 3 and the output of motor mechanical axis first gear 31, the synchronous reverse idler gear 72 of reverse gear synchronizer 74c and intermediate idler 73, first dynamotor 51 by exporting from reverse gear 71 after motor mechanical axis 3, motor mechanical axis first gear 31, intermediate idler 73, reverse idler gear 72.Thus, make the first dynamotor 51 select to reverse gear gear, thus power is reached wheel by the gear that reverses gear by the first dynamotor 51.Concrete power transmission line is as shown in curve in Figure 17 4.

Further, according to still another embodiment of the invention, when the demand torque of hybrid vehicle be greater than default reverse gear moment of torsion time, control hybrid vehicle to reverse gear mode operation with hybrid power, wherein, stirred to first direction by control motor mechanical axis synchro and reverse gear synchronizer, to make the first dynamotor select to reverse gear gear, control engine output power simultaneously.

Specifically, as shown in figure 17, when controlling driving engine 4 outputting power, the synchronous reverse idler gear 72 of reverse gear synchronizer 74c and intermediate idler 73, the input end 23d of double-clutch 2d engages the second mouth 22d and disconnects with the first mouth 21d, the power that driving engine 4 exports is by exporting from reverse gear 71 after the second input shaft 12, intermediate idler 73, reverse idler gear 72, and concrete power transmission line is as shown in curve in Figure 17 3.

Like this, when the demand torque of hybrid vehicle be greater than default reverse gear moment of torsion time, motor power axle synchro 33c and reverse gear synchronizer 74c can be controlled and be all moved to the left, control driving engine 4 outputting power simultaneously.Namely say, motor mechanical axis synchro 33c synchronous dynamo dynamical axis 3 and motor mechanical axis first gear 31, the synchronous reverse idler gear 72 of reverse gear synchronizer 74c and intermediate idler 73, the power that driving engine 4 exports exports intermediate idler 73 to by the second input shaft 12, the power that first dynamotor 51 exports exports intermediate idler 73 to by motor mechanical axis 3, motor mechanical axis first gear 31, and two parts power is exported from reverse gear 71 by reverse idler gear 72 after the coupling of intermediate idler 73 place again.

It can thus be appreciated that in the present embodiment, when hybrid vehicle reverse travel, if demand torque is less than or equal to the default moment of torsion that reverses gear, with the pure electronic mode operation that reverses gear, the first dynamotor selects the gear that reverses gear that speed ratio is larger, thus dynamic property is better; If demand torque is greater than the default moment of torsion that reverses gear, engine starting drives running car to assist the first dynamotor.Like this, the dynamotor of the control method of reversing gear of the present embodiment and the speed ratio of driving engine all larger, avoid slow-revving uneconomical region, do not relate to speed governing gearshift in whole control process simultaneously, power, without interruption, can realize good economy, dynamic property and ride comfort, controls simple, functional realiey is easy, has best control effects.

To sum up, according to the control method of reversing gear of the hybrid vehicle that the embodiment of the present invention proposes, when hybrid vehicle reverse travel, judge the demand torque of hybrid vehicle, and according to the demand torque of hybrid vehicle, hybrid vehicle is controlled to power drive system and to reverse gear mode operation with pure electronic reverse gear pattern or hybrid power, thus, when controlling hybrid vehicle reverse travel, dynamic property, economy and control difficulty can be taken into account, for user provides experience of better moveing backward.

The embodiment of the present invention also proposes a kind of power drive system performing the hybrid vehicle of this control method.The power drive system of this hybrid vehicle comprises: driving engine, multiple input shaft, multiple output shaft, motor mechanical axis, the first dynamotor and control module.

Wherein, driving engine is arranged to optionally engage at least one in multiple input shaft, 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; Motor mechanical axis is arranged to link with in input shaft; First dynamotor is arranged to link with motor mechanical axis, one wherein in motor mechanical axis and input shaft when linking, the first dynamotor can utilize at least part of power of exporting from driving engine hybrid electric vehicle sail and parking time generate electricity; Control module judges the demand torque of hybrid vehicle when hybrid vehicle reverse travel, and controls hybrid vehicle according to the demand torque of hybrid vehicle to power drive system and to reverse gear mode operation with pure electronic reverse gear pattern or hybrid power.

According to a specific embodiment of the present invention, control module can comprise electric machine controller and motion control unit, and wherein, the communication network by hybrid vehicle between electric machine controller and motion control unit communicates mutually.

According to one embodiment of present invention, motor mechanical axis is also arranged to link with in output shaft, one in motor mechanical axis and output shaft when linking, the power produced one by output shaft can export by the first dynamotor; Power drive system also comprises: motor mechanical axis synchro, motor mechanical axis synchro is arranged on motor mechanical axis, and synchronously and optionally linking with of input shaft or linking with of output shaft by motor mechanical axis synchro be arranged in motor mechanical axis.

Further, the power drive system of hybrid vehicle according to an embodiment of the invention, it is characterized in that, also comprise: motor mechanical axis first gear and motor mechanical axis second gear, motor mechanical axis first gear and the equal empty set of motor mechanical axis second gear are arranged on motor mechanical axis, motor mechanical axis first gear is arranged to link with one of input shaft, and motor mechanical axis second gear is arranged to link with one of output shaft; Motor mechanical axis synchro is arranged between motor mechanical axis first gear and motor mechanical axis second gear.

Wherein, according to one embodiment of present invention, first dynamotor has the first gear and the second gear, wherein, the joint of motor mechanical axis synchro in motor mechanical axis first gear and motor mechanical axis second gear switches to and between another joint aging time, first dynamotor is arranged to carry out speed governing for target to motor mechanical axis with another the rotating speed in motor mechanical axis first gear and motor mechanical axis second gear, switches between the first gear and the second gear to make the gear of the first dynamotor.

The power drive system of the hybrid vehicle of the embodiment of the present invention is described in detail referring to four embodiments.

According to one embodiment of present invention, when the demand torque of hybrid vehicle be less than or equal to default reverse gear moment of torsion time, motor controller controls hybrid vehicle is with the pure electronic mode operation that reverses gear, wherein, two or four gear synchros in motion control unit control power drive system and motor mechanical axis synchro are stirred to first direction, select the first gear to make motor controller controls first dynamotor.

Further, according to one embodiment of present invention, when the demand torque of hybrid vehicle be greater than default reverse gear moment of torsion time, motor controller controls hybrid vehicle to reverse gear mode operation with hybrid power, wherein, motion control unit controls the second synchro and remains on predeterminated position, and control motor mechanical axis synchro and stir to second direction, to make motor controller controls first dynamotor select the second gear, the reverse gear synchronizer that motion control unit also controls in power drive system is simultaneously stirred to first direction.

According to another embodiment of the invention, when the demand torque of hybrid vehicle be less than or equal to default reverse gear moment of torsion time, motor controller controls hybrid vehicle is with the pure electronic mode operation that reverses gear, wherein, motion control unit controls motor mechanical axis synchro and stirs to second direction, selects the second gear to make motor controller controls first dynamotor.

Further, according to another embodiment of the invention, when the demand torque of hybrid vehicle be greater than default reverse gear moment of torsion time, motor controller controls hybrid vehicle to reverse gear mode operation with hybrid power, wherein, motion control unit controls motor mechanical axis synchro and stirs to second direction, and to make the first dynamotor select the second gear, the reverse gear synchronizer that motion control unit controls in power drive system is simultaneously stirred to first direction.

According to still another embodiment of the invention, when the demand torque of hybrid vehicle be less than or equal to default reverse gear moment of torsion time, motor controller controls hybrid vehicle is with the pure electronic mode operation that reverses gear, wherein, first dynamotor also has the gear that reverses gear, and the reverse gear synchronizer that motion control unit controls in motor mechanical axis synchro and power drive system is stirred to first direction, select to reverse gear gear to make motor controller controls first dynamotor.

Further, according to still another embodiment of the invention, when the demand torque of hybrid vehicle be greater than default reverse gear moment of torsion time, motor controller controls hybrid vehicle to reverse gear mode operation with hybrid power, wherein, motion control unit controls motor mechanical axis synchro and reverse gear synchronizer is stirred to first direction, to make the first dynamotor select to reverse gear gear, and motor controller controls engine output power simultaneously.

To sum up, according to the power drive system of the hybrid vehicle that the embodiment of the present invention proposes, when hybrid vehicle reverse travel, judge the demand torque of hybrid vehicle, and according to the demand torque of hybrid vehicle, hybrid vehicle is controlled to power drive system and to reverse gear mode operation with pure electronic reverse gear pattern or hybrid power, thus, when controlling hybrid vehicle reverse travel, dynamic property, economy and control difficulty can be taken into account, for user provides experience of better moveing backward.

The invention allows for a kind of hybrid vehicle, comprise the power drive system of above-mentioned hybrid vehicle.

According to the hybrid vehicle that the embodiment of the present invention proposes, in reversing process, dynamic property, economy and control difficulty can be taken into account, for user provides experience of better moveing backward.

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 ", " conter clockwise ", " axis ", " radial direction ", orientation or the position relationship of the instruction such as " circumference " 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 at least one this feature.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 electrical connection; 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, unless otherwise clear and definite restriction.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 " on " or D score can be that the first and second features directly contact, or the first and second features are by intermediary indirect contact.And, fisrt feature second feature " on ", " top " and " above " but fisrt feature directly over second feature or oblique upper, or only represent that fisrt feature level height is higher than second feature.Fisrt feature second feature " under ", " below " and " below " can be fisrt feature immediately below second feature or tiltedly below, or only represent that fisrt feature level height is less than second feature.

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 one or more embodiment in office or example in an appropriate manner.In addition, when not conflicting, the feature of the different embodiment described in this specification sheets or example and different embodiment or example can carry out combining 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 (13)

1. the control method of reversing gear of a hybrid vehicle, it is characterized in that, the power drive system of described hybrid vehicle comprises driving engine, multiple input shaft, multiple output shaft, motor mechanical axis and the first dynamotor, wherein, described driving engine is arranged to optionally engage at least one in described multiple input shaft, each described input shaft is provided with gear driving gear, each described output shaft is provided with gear driven gear, described gear driven gear engages accordingly with described gear driving gear, described motor mechanical axis is arranged to link with in described input shaft, described first dynamotor is arranged to link with described motor mechanical axis, and described one when linking in described motor mechanical axis and described input shaft, described first dynamotor can utilize at least part of power of exporting from described driving engine described hybrid electric vehicle sail and parking time generate electricity, described control method of reversing gear comprises the following steps:
When described hybrid vehicle reverse travel, judge the demand torque of described hybrid vehicle;
Control described hybrid vehicle according to the demand torque of described hybrid vehicle to described power drive system to reverse gear mode operation with pure electronic reverse gear pattern or hybrid power.
2. the control method of reversing gear of hybrid vehicle as claimed in claim 1, it is characterized in that, described first dynamotor has the first gear and the second gear, wherein, described power drive system also comprises motor mechanical axis synchro, motor mechanical axis first gear and motor mechanical axis second gear, the joint of described motor mechanical axis synchro in described motor mechanical axis first gear and described motor mechanical axis second gear switches to and between another joint aging time, described first dynamotor is arranged to carry out speed governing to described motor mechanical axis with another rotating speed described in described motor mechanical axis first gear and described motor mechanical axis second gear for target, switch between described first gear and described second gear to make the gear of described first dynamotor.
3. the control method of reversing gear of hybrid vehicle as claimed in claim 2, is characterized in that,
When the demand torque of described hybrid vehicle be less than or equal to default reverse gear moment of torsion time, control described hybrid vehicle with the described pure electronic mode operation that reverses gear, wherein, by control in described power drive system two or four gear synchros and described motor mechanical axis synchro stir to first direction, with make described first dynamotor select described first gear;
When the demand torque of described hybrid vehicle be greater than described default reverse gear moment of torsion time, control described hybrid vehicle to reverse gear mode operation with described hybrid power, wherein, control described two or four gear synchros and remain on predeterminated position, and control described motor mechanical axis synchro and stir to second direction, to make described first dynamotor select described second gear, the reverse gear synchronizer simultaneously controlled in described power drive system is stirred to first direction.
4. the control method of reversing gear of hybrid vehicle as claimed in claim 2, is characterized in that,
When the demand torque of described hybrid vehicle be less than or equal to default reverse gear moment of torsion time, control described hybrid vehicle with the described pure electronic mode operation that reverses gear, wherein, stirring to second direction by controlling described motor mechanical axis synchro, selecting described second gear to make described first dynamotor;
When the demand torque of described hybrid vehicle be greater than described default reverse gear moment of torsion time, control described hybrid vehicle to reverse gear mode operation with described hybrid power, wherein, stir to second direction by controlling described motor mechanical axis synchro, to make described first dynamotor select described second gear, the reverse gear synchronizer simultaneously controlled in described power drive system is stirred to first direction.
5. the control method of reversing gear of hybrid vehicle as claimed in claim 2, is characterized in that,
When the demand torque of described hybrid vehicle be less than or equal to default reverse gear moment of torsion time, control described hybrid vehicle with the described pure electronic mode operation that reverses gear, wherein, described first dynamotor also has the gear that reverses gear, and stirred to first direction by the reverse gear synchronizer controlled in described motor mechanical axis synchro and described power drive system, to make to reverse gear described in described first dynamotor selection gear;
When the demand torque of described hybrid vehicle be greater than described default reverse gear moment of torsion time, control described hybrid vehicle to reverse gear mode operation with described hybrid power, wherein, by controlling described motor mechanical axis synchro and described reverse gear synchronizer is stirred to first direction, to make to reverse gear described in described first dynamotor selection gear, control described engine output power simultaneously.
6. a power drive system for hybrid vehicle, is characterized in that, comprising:
Driving engine;
Multiple input shaft, described driving engine is arranged to optionally engage at least one in described multiple input shaft, and 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 arranged to link with in described input shaft;
First dynamotor, described first dynamotor is arranged to link with described motor mechanical axis, described one when linking wherein in described motor mechanical axis and described input shaft, described first dynamotor can utilize at least part of power of exporting from described driving engine described hybrid electric vehicle sail and parking time generate electricity;
Control module, described control module judges the demand torque of described hybrid vehicle when described hybrid vehicle reverse travel, and controls described hybrid vehicle according to the demand torque of described hybrid vehicle to described power drive system and to reverse gear mode operation with pure electronic reverse gear pattern or hybrid power.
7. the power drive system of hybrid vehicle as claimed in claim 6, it is characterized in that, described motor mechanical axis is also arranged to link with in described output shaft, described one when linking in described motor mechanical axis and described output shaft, the power produced described one by described output shaft can export by described first dynamotor; And
Described power drive system also comprises:
Motor mechanical axis synchro, described motor mechanical axis synchro is arranged on described motor mechanical axis, and synchronously and optionally linking with described of described input shaft or linking with described of described output shaft by described motor mechanical axis synchro be arranged in described motor mechanical axis.
8. the power drive system of hybrid vehicle as claimed in claim 6, is characterized in that, also comprise:
Motor mechanical axis first gear and motor mechanical axis second gear, described motor mechanical axis first gear and the equal empty set of described motor mechanical axis second gear are arranged on described motor mechanical axis, described motor mechanical axis first gear is arranged to link with described one of described input shaft, and described motor mechanical axis second gear is arranged to link with described one of described output shaft; And
Described motor mechanical axis synchro is arranged between described motor mechanical axis first gear and described motor mechanical axis second gear.
9. the power drive system of hybrid vehicle as claimed in claim 8, it is characterized in that, described first dynamotor has the first gear and the second gear, wherein, the joint of described motor mechanical axis synchro in described motor mechanical axis first gear and described motor mechanical axis second gear switches to and between another joint aging time, described first dynamotor is arranged to carry out speed governing to described motor mechanical axis with another rotating speed described in described motor mechanical axis first gear and described motor mechanical axis second gear for target, switch between described first gear and described second gear to make the gear of described first dynamotor.
10. the power drive system of hybrid vehicle as claimed in claim 9, is characterized in that,
When the demand torque of described hybrid vehicle be less than or equal to default reverse gear moment of torsion time, hybrid vehicle described in described motor controller controls is with the described pure electronic mode operation that reverses gear, wherein, described motion control unit controls two or four gear synchros in described power drive system and described motor mechanical axis synchro is stirred to first direction, selects described first gear to make described in described motor controller controls the first dynamotor;
When the demand torque of described hybrid vehicle be greater than described default reverse gear moment of torsion time, hybrid vehicle described in described motor controller controls to reverse gear mode operation with described hybrid power, wherein, described motion control unit controls described two or four gear synchros and remains on predeterminated position, and control described motor mechanical axis synchro and stir to second direction, to make the first dynamotor described in described motor controller controls select the second gear, the reverse gear synchronizer that described motion control unit also controls in described power drive system is simultaneously stirred to first direction.
The power drive system of 11. hybrid vehicles as claimed in claim 9, is characterized in that,
When the demand torque of described hybrid vehicle be less than or equal to default reverse gear moment of torsion time, hybrid vehicle described in described motor controller controls is with the described pure electronic mode operation that reverses gear, wherein, described motion control unit controls described motor mechanical axis synchro and stirs to second direction, selects described second gear to make the first dynamotor described in described motor controller controls;
When the demand torque of described hybrid vehicle be greater than described default reverse gear moment of torsion time, hybrid vehicle described in described motor controller controls to reverse gear mode operation with described hybrid power, wherein, described motion control unit controls described motor mechanical axis synchro and stirs to second direction, to make described first dynamotor select described second gear, the reverse gear synchronizer that described motion control unit controls in described power drive system is simultaneously stirred to first direction.
The power drive system of 12. hybrid vehicles as claimed in claim 9, is characterized in that,
When the demand torque of described hybrid vehicle be less than or equal to default reverse gear moment of torsion time, hybrid vehicle described in described motor controller controls is with the described pure electronic mode operation that reverses gear, wherein, described first dynamotor also has the gear that reverses gear, and the reverse gear synchronizer that described motion control unit controls in described motor mechanical axis synchro and described power drive system is stirred to first direction, to make to reverse gear described in the first dynamotor selection described in described motor controller controls gear;
When the demand torque of described hybrid vehicle be greater than described default reverse gear moment of torsion time, hybrid vehicle described in described motor controller controls to reverse gear mode operation with described hybrid power, wherein, described motion control unit controls described motor mechanical axis synchro and described reverse gear synchronizer is stirred to first direction, to make to reverse gear described in described first dynamotor selection gear, simultaneously engine output power described in described motor controller controls.
13. 1 kinds of hybrid vehicles, is characterized in that, comprise the power drive system of the hybrid vehicle according to any one of claim 6-12.
CN201410505701.0A 2014-09-26 2014-09-26 Hybrid vehicle and its reverse gear control method and power drive system CN105437948B (en)

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