CN106553537A

CN106553537A - Power-driven system and the vehicle with which

Info

Publication number: CN106553537A
Application number: CN201510627079.5A
Authority: CN
Inventors: 杨冬生; 廉玉波; 张金涛; 罗红斌
Original assignee: BYD Co Ltd
Current assignee: BYD Co Ltd
Priority date: 2015-09-25
Filing date: 2015-09-25
Publication date: 2017-04-05
Anticipated expiration: 2035-09-25
Also published as: CN106553537B; WO2017050101A1

Abstract

The invention discloses a kind of power-driven system and vehicle, the power-driven system includes：Differential mechanism, differential mechanism include：First and second planet carriers, the first and second planetary gears and the first and second gear rings, first and second planetary gears are connected with the first and second planet carriers respectively, first and second planetary gears are engaged with the first and second gear rings respectively, and the second planetary gear is also engaged with the first row star-wheel；Input unit, input unit, the first and second planet carrier coaxial linkages；Power output shaft, power output shaft are arranged to link with input unit；Multiple input shafts, the one of input shaft in multiple input shafts are arranged to optionally link with power output shaft, and remaining input shaft is arranged to link with power output shaft；First dynamotor, the first dynamotor are arranged to link with one of input shaft.The differential mechanism of the power-driven system of the present invention realizes differential function using planet differential principle, compact conformation, simple.

Description

Power-driven system and the vehicle with which

Technical field

The present invention relates to a kind of power-driven system for vehicle, the vehicle with the power-driven system.

Background technology

In a kind of differential art known for inventor, differential mechanism includes that the driven gear of main reducing gear is (main Subtract driven gear), planetary gear, centre wheel etc., planetary gear is arranged on driven tooth by square shaft, axle sleeve On the subplate of wheel, and engage with centre wheel, realize which rotates and locomotive function with secondary and plane moving sets are rotated, Centre wheel passes through angular alignment pin and cylindrical pair or spline is connected with left and right two-semiaxle, reaches the mesh of output torque 's.This differential mechanism eliminates the components such as original differential mechanism or so housing, planetary gear shaft, uses square shaft instead Directly planetary gear is arranged on the subplate of driven gear of main reducing gear with axle sleeve, effectively reduces differential The number of parts of device, simplifies structure, alleviates weight.

But, this differential mechanism make use of symmetrical expression bevel gear structure to realize differential between wheel, just for tradition Symmetrical expression bevel differential part innovation, can not really solve this differential design axial dimension Excessive, housing and bevel gear quality be big and the shortcoming of reliability relative deviation.

The content of the invention

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

For this purpose, the present invention proposes a kind of power-driven system, the differential mechanism of the power-driven system is using row Star differential principle realizes differential function, compact conformation, simple.

The invention allows for a kind of vehicle with the power drive system.

Power-driven system according to embodiments of the present invention, including：Differential mechanism, the differential mechanism include：The One planet carrier, the first row star-wheel and the first gear ring, the first row star-wheel are connected with the first row carrier, The first row star-wheel is engaged with first gear ring；Second planet carrier, the second planetary gear and the second gear ring, Second planetary gear is connected with second planet carrier, and second planetary gear is engaged with second gear ring And second planetary gear is also engaged with the first row star-wheel, wherein, first gear ring and described second Gear ring constitutes two clutch ends of the differential mechanism；Input unit, the input unit, the first planet Frame and second planet carrier is coaxially arranged and the input unit and the first row carrier and second row Carrier links；Power output shaft, the power output shaft are arranged to link with the input unit；Multiple inputs Axle, the one of input shaft in the plurality of input shaft be arranged to optionally with the power output shaft Linkage, remaining described input shaft are arranged to link with the power output shaft；First dynamotor, institute State the first dynamotor to be arranged to link with one of input shaft.

The differential mechanism of power-driven system according to embodiments of the present invention realizes differential using planet differential principle Function is compact conformation, simple.

Power-driven system according to embodiments of the present invention, can also have following additional technical feature：

Some embodiments of the invention, power-driven system also include：Engine, the engine set It is set to and is selectively engageable at least one of the plurality of input shaft.

Some embodiments of the invention, are provided with power output shaft output gear on the power output shaft Wheel, the power output shaft output gear and the input unit engaged transmission.

Some embodiments of the invention, the power output shaft output gear are constituted with the input unit and are led Decelerator, wherein the power output shaft output gear is configured to main reducing gear driving gear, the input unit It is configured to main reducing gear driven gear.

Some embodiments of the invention, the power output shaft overhead set are provided with empty set driven gear, The empty set driven gear is linked with one of input shaft, and the power-driven system also includes synchronous Device, the synchronized are arranged for the synchronous power output shaft and the empty set driven gear.

Some embodiments of the invention, the synchronized are arranged on the power output shaft and for connecing Close the empty set driven gear.

Some embodiments of the invention, are fixedly installed fixed driven gear on the power output shaft, The fixed driven gear is linked with described remaining input shaft.

Some embodiments of the invention, power output shaft overhead set be provided with empty set driven gear with And fixed driven gear is fixedly installed, the power-driven system also includes synchronized：The synchronized sets It is set to for the synchronous power output shaft and the empty set driven gear；

It is fixedly installed fixed driving gear on each described input shaft, the empty set driven gear and described solid Determine driven gear to engage with corresponding fixed driving gear respectively.

Some embodiments of the invention, the plurality of input shaft include：

First input shaft and the second input shaft, second input shaft are set on first input shaft, institute Stating fixed driving gear includes：The first fixation driving gear for being fixed on the first input shaft and it is fixed on the The second fixation driving gear on two input shafts.

Some embodiments of the invention, first input shaft are one of input shaft, described First dynamotor fixes driving gear linkage with described first by gear structure；Or

Second input shaft is one of input shaft, and first dynamotor is by gear knot Structure fixes driving gear linkage with described second.

Some embodiments of the invention, power-driven system also include：

Engine；And

Double clutch, the double clutch include：First bonding part, the second bonding part and the 3rd engagement Part, the 3rd bonding part are arranged to be selectively engageable first bonding part and described second At least one of bonding part, the engine are connected with the 3rd bonding part, first input Axle is connected with first bonding part, and second input shaft is connected with second bonding part.

Some embodiments of the invention, the first row star-wheel and second planetary gear portion in the axial direction Divide and overlap.

Some embodiments of the invention, the first row star-wheel include：First teeth portion and the second teeth portion, Second planetary gear includes：3rd teeth portion and the 4th teeth portion, first teeth portion are nibbled with first gear ring Close, second teeth portion and the 3rd teeth portion corresponding overlap and engage cooperation on the axial direction, described the Four teeth portion are engaged with second gear ring.

Some embodiments of the invention, the first row star-wheel and the second planetary gear are roller gear.

Some embodiments of the invention, first gear ring and second gear ring be symmetrical structure, institute Each stated in the first gear ring and second gear ring includes：

Body panels portion and be arranged on the body panels portion periphery edge annular side wall portion, the annular side Multiple teeth are provided with the internal face of wall portion, are limited between the body panels portion and the annular side wall portion The cavity of cavity, the cavity of first gear ring and second gear ring toward each other to constitute installing space, The first row carrier and the first row star-wheel and second planet carrier and second planetary gear receipts It is contained in the installing space.

Some embodiments of the invention, the input unit are configured to input end gear, the input end tooth Wheel construction is for annular and is set in first gear ring and the second gear ring outer surface.

Some embodiments of the invention, between being provided between first gear ring and second gear ring Gap, the input end gear surround and cover the gap.

Some embodiments of the invention, power-driven system also include：Intermediate connection structure, it is described in Between attachment structure for the first row carrier, second planet carrier are connected to the input unit, it is described Intermediate connection structure includes：First connecting bracket and the second connecting bracket, first connecting bracket are used to connect The first row carrier and the input unit are connect, second connecting bracket is used to connect second planet carrier With the input unit, wherein each in first connecting bracket and second connecting bracket is wrapped Include：

Central body portion and extension arm, the extension arm are multiple and are arranged on the central body portion On outer peripheral face, arm is centered on the central body portion and radially distributes for the plurality of extension, wherein The arm that extends is for being connected with the input unit.

Some embodiments of the invention, each described the first row star-wheel are configured with a first row star-wheel Axle, two ends of the first planet wheel shaft respectively with the first row carrier and the second planet carrier phase Even, each described second planetary gear is configured with second planet wheel spindle, two of second planet wheel spindle End is connected with the first row carrier and second planet carrier respectively.

Some embodiments of the invention, the revolution-radius of the first row star-wheel and second planetary gear Revolution-radius it is identical.

Some embodiments of the invention, power-driven system also include：Second dynamotor and the 3rd Dynamotor, second dynamotor are linked with first gear ring, the 3rd dynamotor Link with second gear ring.

Some embodiments of the invention, are provided with the first external tooth, institute on the outer peripheral face of first gear ring The second external tooth, second dynamotor and first external tooth are provided with the outer peripheral face for stating the second gear ring Linkage, the 3rd dynamotor are linked with second external tooth.

Some embodiments of the invention, the speed changer include the first input shaft, the second input shaft and Three input shafts, the 3rd input shaft are set on second input shaft, and second input shaft is set in On first input shaft, the engine and first input shaft, second input shaft and described It is connected by three clutches between three input shafts.

Some embodiments of the invention, first gear ring and the near front wheel link, second gear ring with Off-front wheel links；

The power-driven system also includes：

4th dynamotor and the 5th dynamotor, the 4th dynamotor are linked with left rear wheel, 5th dynamotor is linked with off hind wheel；And

Anti-skidding synchronized, after the anti-skidding synchronized is arranged to the optionally synchronous left rear wheel and the right side Wheel, so that the left rear wheel and the off hind wheel synchronous rotary.

Vehicle according to embodiments of the present invention, including the power-driven system of above-described embodiment.

Description of the drawings

Fig. 1 is the explosive view of differential mechanism according to embodiments of the present invention；

Fig. 2 is the explosive view at another visual angle of differential mechanism according to embodiments of the present invention；

Fig. 3 is the stereogram of differential mechanism according to embodiments of the present invention；

Fig. 4 is the plan view sketch of differential mechanism according to embodiments of the present invention；

Fig. 5 is the stereogram of differential mechanism according to embodiments of the present invention, the second planet carrier and not shown in which Two gear rings etc.；

Fig. 6 is the mesh schematic representation of the first row star-wheel and the second planetary gear；

Fig. 7 is the theory of engagement sketch of the first row star-wheel and the second planetary gear；

Fig. 8 is the stereogram of the first gear ring according to embodiments of the present invention or the second gear ring；

Fig. 9 is the stereogram of the first gear ring in accordance with another embodiment of the present invention or the second gear ring；

Figure 10 is the schematic diagram of power-driven system according to an embodiment of the invention；

Figure 11 is the schematic diagram of power-driven system in accordance with another embodiment of the present invention；

Figure 12 is the schematic diagram of the power-driven system according to further embodiment of the present invention；

Figure 13 is the schematic diagram of the power-driven system according to further embodiment of the present invention；

Figure 14 is the schematic diagram of the power-driven system according to further embodiment of the present invention；

Figure 15 is the schematic diagram of the power-driven system according to further embodiment of the present invention；

Figure 16 is the schematic diagram of the power-driven system according to further embodiment of the present invention；

Figure 17 is the schematic diagram of the power-driven system according to further embodiment of the present invention；

Figure 18 is the schematic diagram of the power-driven system according to further embodiment of the present invention；

Figure 19 is the schematic diagram of the power-driven system according to further embodiment of the present invention；

Figure 20 is the schematic diagram of vehicle according to embodiments of the present invention.

Specific embodiment

Embodiments of the invention are described below in detail, the example of the embodiment is shown in the drawings, wherein certainly Begin to same or similar label eventually to represent same or similar element or the unit with same or like function Part.It is exemplary below with reference to the embodiment of Description of Drawings, it is intended to for explaining the present invention, and not It is understood that as limitation of the present invention.

In describing the invention, it is to be understood that term " " center ", " longitudinal direction ", " horizontal ", " length Degree ", " width ", " thickness ", " on ", D score, "front", "rear", "left", "right", " vertical ", The orientation or position of the instruction such as " level ", " top ", " bottom " " interior ", " outward ", " clockwise ", " counterclockwise " The relation of putting is, based on orientation shown in the drawings or position relationship, to be for only for ease of the description present invention and simplification is retouched State, rather than indicate or imply that the device or element of indication must be with specific orientation, with specific orientation Construction and operation, therefore be not considered as limiting the invention.

Additionally, term " first ", " second " are only used for describing purpose, and it is not intended that indicating or implying Relative importance or the implicit quantity for indicating indicated technical characteristic.Thus, define " first ", The feature of " second " can be expressed or implicitly include one or more this feature.The present invention's In description, " multiple " are meant that at least two, such as two, three etc., unless otherwise clearly concrete Restriction.

In the present invention, unless otherwise clearly defined and limited, term " installation ", " being connected ", " connection ", Terms such as " fixations " should be interpreted broadly, for example, it may be fixedly connected, or be detachably connected, Or it is integral；Can be mechanically connected, or electrically connect or can communicate with one another；It can be direct phase Even, it is also possible to be indirectly connected to by intermediary, can be two element internals connection or two elements Interaction relationship.For the ordinary skill in the art, can understand above-mentioned as the case may be Term concrete meaning in the present invention.

In the present invention, unless otherwise clearly defined and limited, fisrt feature second feature it " on " Or D score can include the first and second feature directly contacts, it is also possible to it is special including first and second Levying is not directly contact but by the other characterisation contact between them.And, fisrt feature exists Second feature " on ", " top " and " above " including fisrt feature directly over second feature And oblique upper, or fisrt feature level height is merely representative of higher than second feature.Fisrt feature is second Feature " under ", " lower section " and " below " including fisrt feature immediately below second feature and tiltedly Lower section, or fisrt feature level height is merely representative of less than second feature.

Describe power-driven system 1000 according to embodiments of the present invention below with reference to accompanying drawings in detail, should Power-driven system 1000 is can be applicable in vehicle.

As shown in Figure 10-Figure 15, power-driven system 1000 according to some embodiments of the invention is main Including differential mechanism 100, speed changer 104 and the first dynamotor 401, speed changer 104 is connected to difference Between fast device 100 and the first dynamotor 401.

The concrete structure of differential mechanism 100 is described in detail according to diagram embodiment first below, it is right To describe after differential mechanism 100 being discussed in detail and constructs in other constructions of power-driven system 1000.

Differential mechanism 100 according to embodiments of the present invention is described in detail with reference to Fig. 1-Fig. 9, The differential mechanism 100 can be used for differential or shaft space difference speed between wheel, as a example by differential between wheel, the difference Fast device 100 can be such that driving wheels travel in turn inside diameter or when uneven road surface is travelled with difference Angular speed roll, to ensure to make PURE ROLLING between two side drive wheels and ground.

As shown in figure 1, differential mechanism 100 according to some embodiments of the invention can include the first row carrier 11st, the first row star-wheel 12 and the first gear ring 13 and including the second planet carrier 21,22 and of the second planetary gear Second gear ring 23.

With reference to the embodiment of Fig. 1 and Fig. 2, the first row carrier 11 and the second planet carrier 21 it is so structured that Circular platy structure, so can reduce the axial dimension of differential mechanism 100 to a certain extent.At some In embodiment, the first row carrier 11 and the second planet carrier 21 can be split-type structural, due to independent widget Shaping is relatively easy, therefore the first row carrier 11 and the second planet carrier 21 are individually processed and can be simplified Manufacturing process, raising machining accuracy.

Such as Fig. 1-Fig. 2 and with reference to shown in Fig. 6, the first row star-wheel 12 is arranged in the first row carrier 11, For example, each the first row star-wheel 12 is configured with a first planet wheel shaft 14, first planet wheel shaft 14 Two ends are rotatably supported in the first row carrier 11 and the second planet carrier 21 respectively, such as first planet Two ends of wheel shaft 14 can be rotatably supported in the first row carrier 11 and the second planet carrier by bearing In the axis hole corresponded to each other on 21, now the first row star-wheel 12 is securable to corresponding first planet wheel shaft 14 On.Certainly, two ends of first planet wheel shaft 14 and the first row carrier 11 and the second planet carrier 21 Can be fixedly connected, for example the two of first planet wheel shaft 14 end respectively with the first row carrier 11 It is welded and fixed with the axis hole corresponded to each other on the second planet carrier 21, now the first row star-wheel 12 rotationally covers It is located on corresponding first planet wheel shaft 14, for example the first row star-wheel 12 can be rotationally covered by bearing It is mounted on first planet wheel shaft 14.Thus, can realize connecting first planet by first planet wheel shaft 14 The purpose of frame 11 and the second planet carrier 21, so that the first row carrier 11 and the second planet carrier 21 keep At the same speed, motion (i.e. the first row carrier 11 and the second planet carrier 21 link) in the same direction, and adopt this company Mode is connect, the first row carrier 11 and the second planet carrier 21 can be carried out to first planet wheel shaft 14 well Supporting/fixed, prevents first planet wheel shaft 14 to be disconnected with single planet carrier and cause differential mechanism 100 Failure.Referring to shown in Fig. 1 and Fig. 2, the first row star-wheel 12 is engaged with the first gear ring 13, concretely interior Mesh form, i.e. the first row star-wheel 12 be located at the first gear ring 13 inner side and with the first gear ring 13 on tooth Engagement.The first row star-wheel 12 is preferably several, and circumferentially equidistantly distributed on the inside of the first gear ring 13, For example, as one kind preferred embodiment, the first row star-wheel 12 can be three, and arbitrary neighborhood Between two the first row star-wheels 12, interval angles are 120 °.

Such as Fig. 1-Fig. 2 and with reference to shown in Fig. 6, the second planetary gear 22 is arranged on the second planet carrier 21, For example, each second planetary gear 22 is configured with second planet wheel spindle 24, such as the second planet wheel spindle 24 Two ends that can be rotatably supported on the first row carrier 11 and the second planet carrier 21 by bearing In this corresponding axis hole, now the second planetary gear 22 is securable on corresponding second planet wheel spindle 24.When So, two ends of the second planet wheel spindle 24 with the first row carrier 11 and the second planet carrier 21 can also be Be fixedly connected, two ends of such as the second planet wheel spindle 24 respectively with the first row carrier 11 and the second row The axis hole corresponded to each other in carrier 21 is welded and fixed, and now the second planetary gear 22 is rotatably sleeved on correspondence The second planet wheel spindle 24 on, for example the second planetary gear 22 can be rotatably mounted around second by bearing On planet wheel spindle 24.Thus, can realize connecting 11 He of the first row carrier by the second planet wheel spindle 24 The purpose of the second planet carrier 21 so that the first row carrier 11 and the second planet carrier 21 keep at the same speed, Move in the same direction, and adopt this connected mode, the first row carrier 11 and the second planet carrier 21 can be fine Ground carries out supporting/fixing to the second planet wheel spindle 24, prevents the second planet wheel spindle 24 de- with single planet carrier Differential mechanism 100 is caused to fail from connection.

Additionally, in other embodiments of the present invention, in order to keep the first row carrier 11 and the second planet Frame 21 can be moved at the same speed, in the same direction, not only can be using above by first planet wheel shaft 14 and/or The mode of two planet wheel spindles 24 is realized, while intermediate connection structure 6 can also be passed through by the first row carrier 11 Directly it is fixedly connected with the second planet carrier 21, or while is connected with intermediate connection structure 6 using planet wheel spindle The first row carrier 11 and the second planet carrier 21 are connect, and will be under with regard to the specific configuration of intermediate connection structure 6 Face describes in detail.

Referring to shown in Fig. 1 and Fig. 2, the second planetary gear 22 is engaged with the second gear ring 23, concretely interior to nibble Conjunction form, i.e. the second planetary gear 22 are located at the inner side of the second gear ring 23 and are nibbled with the tooth on the second gear ring 23 Close.Second planetary gear 22 is preferably several, and circumferentially equidistantly distributed on the inside of the second gear ring 23, For example, as one kind preferred embodiment, the second planetary gear 22 can be three, and arbitrary neighborhood Between two the second planetary gears 22, interval angles are 120 °.

, wherein it is desired to explanation, Fig. 4 is the plan view of the differential mechanism 100 according to the embodiment of the present invention Sketch, which schematically illustrates meshing relation between the first row star-wheel 12 and the second planetary gear 22 with And the meshing relation of the first row star-wheel 12 and the first gear ring 13, the second planetary gear 22 and the second gear ring 23, As Fig. 4 is plan, and also show above-mentioned three kinds of meshing relations, therefore the relative position of each part The relation of putting is only illustrative, and is not offered as or implies the practical spatial arrangement position of each part.

It is in multiple embodiments in the first row star-wheel 12 and the second planetary gear 22, it is preferable that Duo Ge One planetary gear 12 and multiple second planetary gears 22 are respectively correspondingly engaged.For example, as shown in Figure 1, Figure 2 and figure Shown in 5, the first row star-wheel 12 and the second planetary gear 22 are three, then first the first row star-wheel 12 Can engage with corresponding first the second planetary gear 22, second the first row star-wheel 12 can be with corresponding second Individual second planetary gear 22 is engaged, and the 3rd the first row star-wheel 12 can be with corresponding 3rd the second planetary gear , so there is multigroup the first row star-wheel 12 being engaged with each other and the second planetary gear 22, in differential mechanism in 22 engagements During 100 transmission power, the first row star-wheel 12 and second planetary gear 22 of the power in multigroup engagement that corresponds to each other Between transmission more will stablize, it is reliable.

Wherein, with reference to the embodiment of Fig. 4, the revolution axes O of the first row star-wheel 12 and the second planetary gear 22 Revolution axes O overlap, and revolution-radius (the i.e. planet of the first row star-wheel 12 and the second planetary gear 22 The distance of the central axis distance revolution axes O of wheel) it is identical.

Especially, as shown in Fig. 1-Fig. 2, Fig. 4-Fig. 7, the first row star-wheel 12 and the second planetary gear 22 Engagement coordinates.In other words, for the first row star-wheel 12, which is not only engaged with the first gear ring 13, together When also engage with the second planetary gear 22, for the second planetary gear 22, its not only with the second gear ring 23 Engagement, while also engaging with the first row star-wheel 12.

As Figure 1-Figure 4, the first gear ring 13 and the second gear ring 23 may be constructed the two of differential mechanism 100 Individual clutch end, the first row carrier 11 and the second planet carrier 21 then correspond to the power for constituting differential mechanism 100 Input, for example in one embodiment of the invention, the first row carrier 11, the second planet carrier 21 with it is defeated Enter portion 3 to link, in other words, the motion state of input unit 3, the first row carrier 11 and the second planet carrier 21 It is identical (i.e. synchronized, motion in the same direction).As preferred embodiment, input unit 3, first planet Frame 11 and the second planet carrier 21 are coaxially arranged.The power of so external power supply output can be from input unit 3 Input, can be exported from the first gear ring 13 and the second gear ring 23 after the differential action of differential mechanism 100 respectively.

It is applied between wheel, as a example by differential, briefly describe the work original of differential mechanism 100 by the differential mechanism 100 below Reason, now the first gear ring 13 can be connected with left half axle, and left half axle can be connected with left side wheel, the second gear ring 23 can be connected with right axle shaft, and right axle shaft can be connected with right side wheels, and power source such as engine and/or motor is defeated The power for going out can be exported after the decelerating effect of main reducing gear to input unit 3, and input unit 3 drives the first row 21 synchronous rotary of carrier 11 and the second planet carrier.If now vehicle traveling is on smooth road surface and without turning, Rotating speed is identical in theory with right side wheels for left side wheel, and now differential mechanism 100 does not play differential action, the first row Carrier 11 and the second planet carrier 21 is synchronized, rotating in same direction, the first gear ring 13 and the second gear ring it is 23 synchronized, Rotating in same direction, the first row star-wheel 12 and the second planetary gear 22 revolution, not rotations.If now vehicle is travelled Travel on irregular road surface or turn inside diameter, rotating speed is different in theory with right side wheels for left side wheel, the The rotating speed of one gear ring 13 and the second gear ring 23 is also different, that is, there is speed discrepancy, now the first row star-wheel 12 With the second planetary gear 22 revolution while also rotation, the first row star-wheel 12 and the second planetary gear 22 from The change of team cause the first gear ring 13 and the second gear ring 23 in a speedup, another deceleration, the gear ring of speedup The speed discrepancy of left and right wheelses is with the speed discrepancy of the gear ring for slowing down, so as to realize differential action.

To sum up, differential mechanism 100 according to embodiments of the present invention utilizes planet differential principle, in structure and connection Space availability ratio is higher in form, and axial dimension is less, and more advantageous in production and fit on.This The version of sample can not only avoid the dimensional defects that angular wheel is axially and radially gone up, and additionally may be used To better profit from the space that master subtracts driven gear inner hollow, preferably space availability ratio is realized, greatly The arrangement of 100 assembly of differential mechanism and the restriction to weight size are facilitated, while also possessing higher Reliability and more preferably transmission efficiency, be conducive to improving the reliability of power chain and it is excessively curved when power Output fluency, this has more practicality for symmetrical expression bevel differential.

Below the meshing relation of first planet wheel 12 and the second planetary gear 22 is carried out in conjunction with specific embodiments in detail It is thin to describe.

Reference picture 1- Fig. 2 and Fig. 6-Fig. 7 is combined, the first row star-wheel 12 and the second planetary gear 22 are in axial direction Partly overlap on (left and right directions in Fig. 6-Fig. 7), that is to say, that the first row star-wheel 12 and the second planet 22, wheel overlaps, and part in addition is staggered, and the first row star-wheel 12 and the second planetary gear 22 are overlapped Part can be engaged with each other, and the part staggered then can be engaged with respective gear ring.

Specifically, with reference to shown in Fig. 6 and Fig. 7, the first row star-wheel 12 can include 151 He of the first teeth portion Second teeth portion 152 (K2 dotted lines are as line of demarcation with Fig. 7), the second planetary gear 22 can include the 3rd tooth Portion 153 and the 4th teeth portion 154 (K1 dotted lines are as line of demarcation with Fig. 7), the second teeth portion 152 and the 3rd tooth Portion 153 constitutes lap, i.e. the second teeth portion 152 with the 3rd teeth portion 153 overlap corresponding in the axial direction and nibbles Close and coordinate, the first teeth portion 151 and the 4th teeth portion 154 are staggered in the axial direction and engaged with each self-corresponding gear ring, I.e. the first teeth portion 151 is engaged with the first gear ring 13, and the 4th teeth portion 154 is engaged with the second gear ring 23.

As a result, the axial dimension of differential mechanism 100 is compacter, the volume of differential mechanism 100 is more compact, Installation, arrangement beneficial to differential mechanism 100.

Some embodiments of the invention, the number of teeth of the first gear ring 13 are equal with the number of teeth of the second gear ring 23, The number of teeth of the first row star-wheel 12 is equal with the number of teeth of the second planetary gear 22.

Some embodiments of the invention, the first row star-wheel 12 and the second planetary gear 22 are roller gear, Conventional symmetrical formula bevel differential is compared, 100 structure of differential mechanism using roller gear is compacter, had For body, in structure and type of attachment, space availability ratio is higher for which, and axial dimension is less, and in production It is more advantageous with fit on.

The structure of the first gear ring 13 and the second gear ring 23 is described in detail with reference to specific embodiment.

In some embodiments of the invention, the first gear ring 13 and the second gear ring 23 are symmetrical structure, change speech It, the first gear ring 13 and the second gear ring 23 are symmetrical arranged, and can so increase the versatility of gear ring, reduce Cost.

Specifically, as Figure 1-Figure 2, each in the first gear ring 13 and the second gear ring 23 is wrapped Include：Body panels portion 161 and the annular side wall portion 162 on the periphery edge for being arranged on body panels portion 161, lead Body flat part 161 and annular side wall portion 162 can be integrally formed part.The inwall of annular side wall portion 162 Multiple gear teeth are provided with face, limit between body panels portion 161 and annular side wall portion 162 cavity A1, A2, i.e., limit cavity A1 between the body panels portion 161 of the first gear ring 13 and annular side wall portion 162, Cavity A2 (such as Fig. 4) is limited between the body panels portion 161 of the second gear ring 23 and annular side wall portion 162, The cavity A2 in cavity A1 and the second gear ring 23 in first gear ring 13 is toward each other constituting installing space A (such as Fig. 4), wherein the first row carrier 11 and the first row star-wheel 12 and the second planet carrier 21 and second Planetary gear 22 is accommodated in installing space A, so that the structure of differential mechanism 100 is relatively more compact, Take volume less, it is easier to arrange, while the first gear ring 13 and the second gear ring 23 serve as external shell Function, can protect and be accommodated in planet carrier therein and planetary gear, improve the life-span.Additionally, the first gear ring 13 and second the installing space A that limited of gear ring 23 comparatively close, outside debris are not easily accessible Moving component is affected in installing space A, it is ensured that the steady operation of differential mechanism 100.

Below the specific configuration of input unit 3 is described in detail in conjunction with specific embodiments.

Some embodiments of the invention, input unit 3 are configured to input end gear.Further, as schemed Shown in 1- Fig. 3, input end gear 3 is configured to annular (tooth of the input end gear 3 is formed on outer peripheral face) And it is set in the outer surface of the first gear ring 13 and the second gear ring 23, it is to be understood that input end gear 3 internal diameter size can be more than the external diameter of the first gear ring 13 and the second gear ring 23, so by by input Gear 3 is enclosed within the outside of the first gear ring 13 and the second gear ring 23 so that positioned at the part of two gear ring inners It is not exposed from coming, protects the part of gear ring inner.

With reference to shown in Fig. 4, the first gear ring 13 and the second gear ring 23 are provided with clearance D in the axial direction, also It is to say, the first gear ring 13 is spaced apart from each other in the axial direction with the second gear ring 23, is not brought into close contact.For For those skilled in the art, due to the first row star-wheel 12 and the width of the mate of the second planetary gear 22 Determine the size of the clearance D (in addition, the thickness for extending arm 63 can also be determined to a certain extent The clearance D, this will be described hereinafter, and first only be determined with the width of the mate of two planetary gears 22 here Illustrate as a example by fixed gap D), i.e. the width of the mate of the first row star-wheel 12 and the second planetary gear 22 can With equal with the minimum of a value of the clearance D, therefore by controlling the first row star-wheel 12 and the second planetary gear 22 The width of mate, can with the size of the indirect control clearance D, to those skilled in the art, Ensureing that the first row star-wheel 12 and the second planetary gear 22 being capable of stable delivery power and the first row star-wheels 12 On the premise of the service life of the second planetary gear 22, can be by the first row star-wheel 12 and the second planetary gear 22 Mate width arrange relative narrower, so can effectively reduce the clearance D so that differential mechanism 100 axial dimension is less, more compact, it is easy to arrange.

Further, input end gear 3 surround and covers the clearance D.As a result, the envelope of installing space A More preferably, outside debris are more difficult to enter in installing space A and affect moving component closing property, further ensure The steady operation of differential mechanism 100, at the same at least can also save to a certain extent differential mechanism axial space and Radial space.

Additionally, conduct is preferred embodiment, retarder driven gearwheel based on input end gear 3.Thus, The space that master subtracts driven gear inner hollow can be better profited from, preferably space availability ratio is realized, greatly Facilitate the arrangement of 100 assembly of differential mechanism and the restriction to weight size.

It should be noted that the clearance D of above-mentioned Fig. 4 (with reference to Fig. 1-Fig. 2) refers to the first gear ring 13 Annular side wall portion 162 and the second gear ring 23 the distance between annular side wall portion 162.For example, see figure 1st, the embodiment of Fig. 2 and Fig. 4, the first gear ring 13 and the second gear ring 23 all include body panels portion 161 With annular side wall portion 162.

And the present invention other embodiments in, such as referring to the embodiment of Fig. 8 and Fig. 9 in, the first gear ring 13 and second each in gear ring 23 still further comprise annular flange portion 163, annular flange portion 163 Extend from direction of the end of annular side wall portion 162 away from body panels portion 161, in the embodiment of Fig. 8 In, the internal diameter of annular flange portion 163 can be generally equalized with the external diameter of annular side wall portion 162, such convex annular Edge 163 is diametrically equivalent to outwardly annular side wall portion 162 (i.e. the first gear ring 13 or the second tooth The outer peripheral face of circle 23).And in the embodiment in fig. 9,163 external diameter of annular flange portion can be with annular side wall portion 162 external diameter is generally equalized, and the internal diameter of annular flange portion 163 can be more than the interior of annular side wall portion 162 Footpath, that is to say, that the thickness of annular flange portion 163 is more thinner than the thickness of annular side wall portion 162.

However, it is desirable to illustrate, in the gear ring structure of Fig. 1, Fig. 2 and Fig. 4 embodiment, two gear ring Between clearance D refer to the gap between the annular side wall portion 162 of two gear rings.And Fig. 8 and Fig. 9 is implemented Gear ring structure in example, the clearance D between two gear ring refer to the annular flange portion 163 of two gear rings Between gap.

For the clearance D, between the engaging width of two planetary gears mentioned above can be determined to a certain extent The size of gap D, at the same time, the thickness for extending arm 63 also determines clearance D to a certain extent Size.Specifically, when the engaging width of two planetary gears is equal with the thickness for extending arm 63, should The big I of clearance D is generally equalized with the thickness of the engaging width of two planetary gears or extension arm 63. And extend arm 63 thickness more than two planetary gears engaging width when, the big I of the clearance D with The thickness for extending arm 63 is generally equalized.And extending the engagement of the thickness less than two planetary gears of arm 63 During width, the big I of the clearance D is generally equalized with the engaging width of two planetary gears.

Intermediate connection structure 6 is described in detail with reference to specific embodiment.

As depicted in figs. 1 and 2, the effect of intermediate connection structure 6 be for by the first row carrier 11, Two planet carriers 21 are connected to input unit 3 so that the first row carrier 11, the second planet carrier 21 and input unit 3 Being capable of coaxial linkage.In addition, intermediate connection structure 6 can also respectively with the first row carrier 11, the second row Carrier 21 is fixedly connected, and the input unit 3 is fixed on the outer surface of intermediate connection structure 6, equally may be used So that the first row carrier 11, the second planet carrier 21 and input unit 3 being capable of coaxial linkages.

For the specific configuration of intermediate connection structure 6, The present invention gives a kind of feasible embodiment, when So this intermediate connection structure 6 for being not offered as or implying the present invention can only adopt the structure in the embodiment. That is, the intermediate connection structure 6 that will be introduced in example below is only a kind of feasible embodiment, not It is that the one kind to the scope of the present invention is limited.

Specifically, referring to shown in Fig. 1 and Fig. 2, the input unit 3 in the embodiment is annular input end tooth Wheel 3, intermediate connection structure 6 include the first connecting bracket 61 and the second connecting bracket 62, the first connection Frame 61 is used to connect the first row carrier 11 and input unit 3 (i.e. input end gear 3), the second connecting bracket 62 are used for the second planet carrier of connection 21 and input unit 3 (i.e. input end gear 3), wherein the first connecting bracket 61 with identical, and can may comprise each with the structure of the second connecting bracket 62：Central body portion 64 And extend arm 63 (with reference to Fig. 5), wherein the central body portion of the first connecting bracket 61 and the second connection The central body portion of support 62 can with into a single integrated structure, to form shared central body portion 64, but Not limited to this.

With reference to shown in Fig. 5, on the outer peripheral face for extending arm 63 for multiple and centrally disposed body 64, Multiple extension arms 63 and central body portion 64 can be integrative-structures, but not limited to this.Multiple adjutages Portion 63 is centered on central body portion 64 and substantially radially distributes, in the example of hgure 5, adjutage Portion 63 is three and equidistantly distributed.Extend arm 63 for being connected with input unit 3, specifically, extend The outer end of arm 63 is may extend at the inner peripheral surface of for example annular main reducing gear driven gear of input unit 3 simultaneously Fix with inner circumferential surface.

The first row star-wheel 12 of each group of correspondence engagement and the second planetary gear 22 are located at two adjacent adjutages Between portion 63, such as in the example of hgure 5, it is three to extend arm 63, and this three extend arm 63 and limit Make three accommodating chambers (to extend arm 63 per adjacent two to limit with the inner peripheral surface of input end gear 3 One accommodating chamber), the first row star-wheel 12 and the second planet of a pair of meshing can be set in each accommodating chamber Wheel 22, so that the overall structure of differential mechanism 100 is compacter, while so that the weight of differential mechanism 100 The heart is closer or is located at center, substantially improves when differential mechanism 100 runs up due to eccentric or eccentric It is larger to cause 100 fluctuation of service of differential mechanism, life-span low situation.

In a further embodiment, as shown in Figure 3 and Figure 4, the first gear ring 13 coaxially can be connected with First output shaft 41, the second gear ring 23 can coaxially be connected with the second output shaft 42.Such as Fig. 2 and Fig. 4 Shown, while the first row carrier 11 is coaxially connected with the first row carrier axle 111, the second planet carrier 21 is same It is connected with the second planet carrier shaft 211, the first output shaft 41 can be hollow shaft and coaxially can be enclosed within axle On the first row carrier axle 111, the second output shaft 42 can equally be hollow shaft and coaxially be set in the second row On carrier axle 211.Wherein, the central body portion 64 of the first row carrier axle 111 and the first connecting bracket 61 Coaxial fixed, the second planet carrier shaft 211 can be coaxial with the central body portion 64 of the second connecting bracket 62 fixed, But not limited to this.

Additionally, used as optional embodiment, the first gear ring 13 is identical with the radial dimension of the second gear ring 23, And first each in gear ring 13 and the second gear ring 23 may each be and be integrally formed part.

Differential mechanism 100 according to embodiments of the present invention has been discussed in detail above, below will be to power drive line Remaining structure of system 1000 is described in detail.

Shown in reference picture 10- Figure 15, speed changer 104 can include multiple input shafts 101,102 and move Power output shaft 103.In certain embodiments, the power output shaft 103 of speed changer 104 can be one It is individual, but not limited to this.Power output shaft 103 is arranged to link with input unit 3, such as power output Be provided with power output shaft output gear 110 on axle 103, power output shaft output gear 110 with it is defeated Enter 3 engaged transmission of portion.As preferred embodiment, power output shaft output gear 110 and input Portion 3 constitutes main reducing gear, and wherein power output shaft output gear 110 is configured to main reducing gear driving tooth Wheel, input unit 3 are then corresponded to and are configured to main reducing gear driven gear.So so that power-driven system 1000 structures are compacter, and differential mechanism 100 is built in inside main reducing gear driven gear, can be with Make differential mechanism 100 better profit from the inner space, facilitate the arrangement of whole power-driven system 1000.

One of input shaft in multiple input shafts 101,102 is arranged to optionally defeated with power Shaft 103 links, in other words, as shown in Figure 10, one of input shaft such as the first input shaft 101 (they being the second input shaft 102 in Figure 11) can be linked with power output shaft 103, while One of input shaft such as the first input shaft 101 also can be disconnected with power output shaft 103.For which Remaining input shaft, then be all provided with being set to and linked with power output shaft 103, i.e. these input shaft actions are then moved Power output shaft 103 also follows action or 103 action of power output shaft, and then these input shafts are also therewith Action.

As shown in Figure 10, the first dynamotor 401 is arranged to defeated with one of input shaft such as first Enter axle 101 to link, i.e., the input shaft 101 linked by with the first dynamotor 401 is defeated with power The input shaft 101 of 103 selective linkage of shaft.In a further embodiment, 103 overhead of power output shaft Set is provided with empty set driven gear 108, empty set driven gear 108 and above-mentioned one of input shaft linkage, Synchronized 109 is arranged for synchronous dynamic output shaft 103 and empty set driven gear 108.May be appreciated It is, when synchronized 109 is in engagement state, the synchronous empty set driven gear 108 of synchronized 109 and power Output shaft 103, the so power from the first dynamotor 401 can be made in the engagement of synchronized 109 Export to differential mechanism 100, and when synchronized 109 is off from power output shaft 103 with, First dynamotor 401 is equivalent to disconnecting with power output shaft 103.Thus, synchronized 109 serves as The power switch of one dynamotor 401, can control the output of 401 power of the first dynamotor and break Open.

Used as a kind of optional embodiment, synchronized 109 is arranged on power output shaft 103 and for connecing Close empty set driven gear 108.Thus, simple structure, it is easy to accomplish.

For remaining input shaft and the kind of drive of power output shaft 103, gear transmission mode reality can be passed through It is existing.For example, fixed driven gear 107, fixed driven gear 107 are fixedly installed on power output shaft 103 Link with remaining input shaft, that is, the input shaft 101 or Figure 11 removed in above-mentioned Figure 10 embodiments is implemented Input shaft 102 in example.

For example, see the specific embodiment of Figure 10 and Figure 11, on power output shaft 103, fixation sets simultaneously Fixed driven gear 107 is equipped with, and is set with empty set driven gear 108, and it is accordingly solid on input shaft Surely fixed driving gear 105,106, empty set driven gear 108 and fixed driven gear 107 are provided with Engage with corresponding fixed driving gear respectively.Such as, empty set driven gear 108 and fixed driven gear 107 total sum is identical with the quantity of fixed driving gear.

Referring to the number of the example of Figure 10-Figure 11, empty set driven gear 108 and fixed driven gear 107 Amount is one, and accordingly, the quantity of fixed driving gear is two, empty set driven gear 108 with One fixed driving gear engagement constitutes a pair of gear pairs, and fixed driven gear 107 is fixed with another Driving gear engagement constitutes another to gear pair, it will be understood that the transmission speed ratio of two pairs of gear pairs is not Together, transmission gear of the speed changer 104 therefore in the embodiment with two not synchronized ratios, it is so dynamic The structure of power-driven system 1000 is relatively easy, compact, and also disclosure satisfy that normal vehicle operation pair The requirement of transmission speed ratio.

As shown in Figure 10-Figure 15, multiple input shafts include the first input shaft 101 and the second input shaft 102, First input shaft 101 can be solid shafting, and the second input shaft 102 can be hollow shaft, and second is input into Axle 102 is set on the first input shaft 101, and such as the second input shaft 102 is coaxially enclosed within the first input On axle 101, the axial length of the first input shaft 101 is more than the axial length of the second input shaft 102, One end such as right-hand member of the first input shaft 101 can be internally extended from the second input shaft 102.

Each input shaft can only be fixedly installed a fixed driving gear, that is to say, that fixed master Moving gear includes that the first fixation driving gear 106 and second fixes driving gear 105, and first fixes master Moving gear 106 is fixedly installed on the first input shaft 101, and the second fixation driving gear 105 is fixed and set Put on the second input shaft 102.

In the example of Figure 10, Figure 12-Figure 15, empty set driven gear 108 and first fixes driving tooth Wheel 106 is engaged, and fixed driven gear 107 is engaged with the second fixation driving gear 105, while first Dynamotor 401 is linked with the first input shaft 101, and such as the first dynamotor 401 passes through gear Structure is linked with the first fixation driving gear 106, and concretely the first dynamotor 401 passes through tooth Wheel 402, gear 403 is driven with the first fixation driving gear 106, by the above-mentioned tooth of reasonable design The number of teeth of wheel can obtain the transmission speed ratio needed for the first dynamotor 401.

And in the example of fig. 11, empty set driven gear 108 is engaged with the second fixation driving gear 105, Fixed driven gear 107 is engaged with the first fixation driving gear 106, while the first dynamotor 401 Link with the second input shaft 102, such as the first dynamotor 401 passes through gear structure and second to be fixed Driving gear 105 links, concretely the first dynamotor 401 by gear 402, gear 403, Gear 404, gear 405 are driven with the second fixation driving gear 105, its middle gear 404 and gear 405 can be fixed on same axle 406, can be obtained by the number of teeth of reasonable design said gear Transmission speed ratio needed for first dynamotor 401.

Further, power-driven system 1000 can also include engine 301, and engine 301 is arranged Into optionally engaging with least one of multiple input shafts, specifically, input shaft is two, And double clutch 204 is provided between engine 301 and two input shafts.Double clutch 204 includes： First bonding part 201, the second bonding part 202 and the 3rd bonding part 203, wherein the first junction surface Be divided to 201 and second bonding part 202 can be double clutch 204 two clutch plates, the 3rd bonding part 203 can be the housing of double clutch 204, and at least one of two clutch plates are selectively engageable shell Body, that is to say, that at least one of the first bonding part 201 and the second bonding part 202 can select Property ground engagement the 3rd bonding part 203.Certainly, two clutch plates can also be all off with housing, i.e., and One bonding part 201 and the second bonding part 202 are off with the 3rd bonding part 203.

Referring to Figure 10-Figure 15, engine 301 is connected with the 3rd bonding part 203, the first input shaft 101 It is connected with the first bonding part 201, the second input shaft 102 is connected with the second bonding part 202.So, The power that engine 301 is produced can be optionally exported to the first input shaft by double clutch 204 101st, the second input shaft 102.

According to one embodiment of present invention, referring to shown in Figure 16-Figure 17 and with reference to shown in Fig. 1-Fig. 9, Second dynamotor 501 is linked with the first gear ring 13, the 3rd dynamotor 503 and the second gear ring 23 Linkage.Further, the first external tooth 505, the first external tooth 505 are provided with the outer peripheral face of the first gear ring 13 May be integrally formed on the outer peripheral face of the first gear ring 13.Second is provided with the outer peripheral face of the second gear ring 23 External tooth 506, the second external tooth 506 are may be integrally formed on the outer peripheral face of the second gear ring 23.Second is electronic Generator 501 is linked with the first external tooth 505, and the 3rd dynamotor 503 is and the second external tooth 506 Linkage.

Further, gear 502, gear 502 can be provided with the motor shaft of the second dynamotor 501 Engage with the first external tooth 505, gear 504, tooth on the motor shaft of the 3rd dynamotor 503, can be provided with Wheel 504 is engaged with the second external tooth 506.However, it will be understood that the second dynamotor 501 and One gear ring 13 and the 3rd dynamotor 503 are not limited to retouch here with the linked manner of the second gear ring 23 The mode stated.

Referring to shown in Figure 16-Figure 17, the second dynamotor 501 and the 3rd dynamotor 503 with regard to 100 symmetrical distribution of differential mechanism, can so cause the center of gravity of power-driven system 100 in centre bit Put or closer to center.

Referring to the embodiment of Figure 18-Figure 19, the power-driven system 1000 and Figure 10-figure in the embodiment One of power-driven system 1000 in 17 embodiments differs primarily in that：The quantity of input shaft.This one In a little embodiments, input shaft includes the first input shaft 101, the second input shaft 102 and the 3rd input shaft 1003, 3rd input shaft 1003 can be hollow shaft and be set on the second input shaft 102, the second input shaft 102 Can also be hollow shaft and be set on the first input shaft 101, three input shafts can be coaxially arranged. Pass through between engine 301 and the first input shaft 101, the second input shaft 102 and the 3rd input shaft 1003 Three clutches 205 are connected, and specifically, three clutches 205 have the first clutch plate 206, second driven Disk 207, the 3rd clutch plate 208 and housing 209, housing 209 optionally with the first clutch plate 206, At least one of second clutch plate 207, the 3rd clutch plate 208 are engaged, the first input shaft 101 and first Clutch plate 206 connects, and the second input shaft 102 is connected with the second clutch plate 207, the 3rd input shaft 1003 It is connected with the 3rd clutch plate 208, engine 301 is connected with housing 209.In the embodiment of Figure 20, the One clutch plate 206, the second clutch plate 207, the 3rd clutch plate 208 are axially distributed, the embodiment of Figure 21 In, the first clutch plate 206, the second clutch plate 207, the 3rd clutch plate 208 are radially distributed.

The typical work of power-driven system 1000 according to embodiments of the present invention is briefly described with reference to Figure 10 Condition.

For example, the first bonding part 201 is combined with the 3rd bonding part 203, the second bonding part 202 with 3rd bonding part 203 disconnects, and synchronized 109 is in engagement state, and what now engine 301 was produced moves Power is exported to differential mechanism 100 after passing through the first input shaft 101, power output shaft 103, by differential mechanism 100 Power is distributed to into the driving wheel of both sides.

And for example, the second bonding part 202 is combined with the 3rd bonding part 203, the first bonding part 201 with 3rd bonding part 203 disconnects, and synchronized 109 is off, and what now engine 301 was produced moves Power is exported to differential mechanism 100 after passing through the second input shaft 102, power output shaft 103, by differential mechanism 100 Power is distributed to into the driving wheel of both sides.

For another example, double clutch 204 is all off, and synchronized 109 is in engagement state, the first dynamoelectric and power generation The power that machine 401 is produced is exported to differential mechanism 100 after passing through the first input shaft 101, power output shaft 103, Power is distributed to the driving wheel of both sides by differential mechanism 100.

For another example, the first bonding part 201 is combined with the 3rd bonding part 203, the second bonding part 202 with 3rd bonding part 203 disconnects, and synchronized 109 is off, and what now engine 301 was produced moves Power is exported to the first dynamotor 401 by the first input shaft 101, drives the first dynamotor 401 Generated electricity as motor, realized power generation in parking function.

With Figure 10 embodiments, Figure 11 embodiments differ primarily in that the first dynamotor 401 is defeated with second Enter axle 102 to link, and Figure 10 embodiments are then the first dynamotor 401 and the first input shaft 101 It is dynamic, for remainder is then repeated no more.

For the embodiment of Figure 12-Figure 15, compared with Figure 10 embodiments, difference is that to increased rear-guard poor Speed lock.

Reference picture 12- Figure 15 is simultaneously combined shown in Fig. 1-Fig. 9, and the first gear ring 13 is linked with the near front wheel 910a, As the first gear ring 13 is coaxially connected with the near front wheel 910a, the second gear ring 23 is linked with off-front wheel 910b, such as Second gear ring 23 is coaxially connected with off-front wheel 910b.4th dynamotor 901 is by gear structure and a left side Trailing wheel 910c links, and such as the 4th dynamotor 901 passes through gear W1, W2, W3, W4 and left rear wheel 910c links, and gear W1 is coaxial with the 4th dynamotor 901 to be connected, and gear W1 is engaged with gear W2, Gear W2 is coaxially connected with gear W3, and gear W3 is engaged with gear W4, and gear W4 can be fixedly installed on On left half axle 904, left rear wheel 910c on left half axle 904, is provided with.Similarly, the 5th dynamotor 902 are linked by gear structure and off hind wheel 910d, such as the 5th dynamotor 902 by gear X1, X2, X3, X4 and off hind wheel 910d linkages, gear X1 is coaxial with the 5th dynamotor 902 to be connected, Gear X1 is engaged with gear X2, and gear X2 is coaxially connected with gear X3, and gear X3 is engaged with gear X4, Gear X4 can be fixedly installed on right axle shaft 905, and off hind wheel 910d is provided with right axle shaft 905.

In the illustration in fig 12, anti-skidding synchronized 903 is arranged for synchromesh gear W4 and gear X4, Such as anti-skidding synchronized 903 is arranged on gear W4 and for engage gear X4.In the example in figure 13, Anti-skidding synchronized 903 is arranged for synchromesh gear W1 and gear X1, and for example anti-skidding synchronized 903 is arranged On gear W1 and for engage gear X1.In the example in figure 14, anti-skidding synchronized 903 is arranged to For synchromesh gear W2 and gear X2, for example anti-skidding synchronized 903 is arranged on gear W2 on and is used to connect Close gear X2.

In the example of fig. 15, anti-skidding synchronized 903 is arranged for synchronous left half axle 904 and right axle shaft 905, such as anti-skidding synchronized 903 is arranged on left half axle 904 and for engaging right axle shaft 905, the enforcement In example, the 4th dynamotor 901 and the 5th dynamotor 902 are wheel motor.

To sum up, anti-skidding synchronized 903 is arranged to optionally synchronization left rear wheel 910c and off hind wheel 910d, In other words, when anti-skidding synchronized 903 is in engagement state, left rear wheel 910c and off hind wheel 910d will be same Step rotation, i.e., at the same speed, rotating Vortex, now left rear wheel 910c and off hind wheel 910d will not differential rotate. And when anti-skidding synchronized 903 is off, the 4th dynamotor 901 can be operated alone left rear wheel 910c, the 5th dynamotor 902 can be operated alone off hind wheel 910d, and two trailing wheels are separate, mutual Do not interfere, so as to realize the differential rotating function of wheel.

Additionally, for technical scheme and/or technical characteristic described in the various embodiments described above, mutually not rushing In the case of prominent, not conflicting, those skilled in the art can by the technical scheme in above-described embodiment and / or technical characteristic be mutually combined, the technical scheme after combination can be two or more technical sides The superposition of case, the superposition of two or more technical characteristics or two or more technical schemes with The superposition of technical characteristic, thus, it is possible to realize each technical scheme and/or technical characteristic phase each other functionally Interaction and support, and the scheme after combining has more superior technique effect.

For example, those skilled in the art can be by 22 partly overlapping side of the first row star-wheel 12 and the second planetary gear Case is combined for the scheme of platy structure with the first row carrier 11 and the second planet carrier 21, so effectively can be subtracted The axial dimension of few differential mechanism 100, so that the volume of differential mechanism 100 is less.

And for example, those skilled in the art can be by 22 partly overlapping side of the first row star-wheel 12 and the second planetary gear The scheme that case is accommodated in planetary gear and planet carrier in installing space is combined, and so effectively not only can be reduced The axial dimension of differential mechanism 100, and planetary gear and planet carrier can also be made to be hidden in installing space and avoid Sudden and violent leakage is damaged outside, so as to increased service life, reduces maintenance cost.

For another example, those skilled in the art can be by the revolution axis of the first row star-wheel 12 and second planetary gear 22 The scheme of revolution dead in line and the revolution-radius and the revolution-radius of the second planetary gear 22 of the first row star-wheel 12 Identical scheme is combined, so that the structure of differential mechanism 100 is compacter, it is less to take volume, more just In arrangement.

For another example, input unit 3 can be configured to annular input end gear and be enclosed within the first tooth by those skilled in the art The side of retarder driven gearwheel based on the scheme and input end gear 3 of the outer peripheral face of circle 13 and the second gear ring 23 Case is combined, and thus differential mechanism 100 can better profit from the space that master subtracts driven gear inner hollow, Preferably space availability ratio is realized, the arrangement of differential assembly is very easy to and to weight size Restriction, and by by input unit 3 be directly disposed as annular main reducing gear driven gear, without independent Main reducing gear driven gear is set again, the parts of whole power-driven system thus not only can be reduced, is dropped Low cost, but also make the structure of differential mechanism 100 more compact, compact.

For another example, input unit 3 can be configured to annular input end gear and input end gear by those skilled in the art On the one hand the 3 scheme combinations for surrounding and covering gap, so cause the structure relative compact of differential mechanism 100, And gap is covered by input end gear 3, moreover it is possible to the installing space for limiting the housing of two planet circular systems Relatively more closed, inside the installing space that adequately protects part, improves its service life.

However, it is to be understood that above-mentioned illustrating is only illustrative, for technical scheme and/ Or the combination of technical characteristic, those skilled in the art can carry out independent assortment in the case where not conflicting, and And the scheme after combining possesses more superior technique effect, the present invention has only made above-mentioned multiple examples briefly Bright, here is no longer exhaustive one by one.

Further it will be understood that the technical scheme after combinations thereof equally falls into protection scope of the present invention Within.

Generally speaking, differential mechanism 100 according to embodiments of the present invention, can effective save space, and reduce Weight, specifically, for this planet gear type differential mechanism 100 compares traditional bevel gear differential, Weight can reduce about 30%, while axial dimension about reduces 70%, can not only reduce bearing Frictional force, and the moment of torsion distribution of left and right wheelses can be realized, make the load of differential mechanism 100 be distributed more adduction Reason, more preferably, additionally due to adopting roller gear, transmission efficiency is also increased 100 rigidity of differential mechanism, Traditional Bevel Gear Drive efficiency of such as 6 class precisions and 7 class precisions about 0.97～0.98, and 6 grades are smart The column gear transmission efficiency of degree and 7 class precisions about 0.98～0.99, in addition using roller gear, also drops The low operating noise of differential mechanism 100, while reducing caloric value, substantially increases the longevity of differential mechanism 100 Life.In short, differential mechanism 100 according to embodiments of the present invention have lightweight, small size, low cost, Many advantages, such as transmission efficiency, noise are low, heating is little, the life-span is high.

Simultaneously as differential mechanism 100 according to embodiments of the present invention can save sun gear, and save the sun Wheel can have the advantage that：

Analyze from mechanics, cancel sun gear but differential is realized using gear ring, because the number of teeth of gear ring is compared It is more that sun gear can be arranged, while pitch circle is larger (when pitch circle refers to meshed transmission gear at node Tangent a pair of circles), such that it is able to distributed load more in a balanced way and torque is born, this is to differential mechanism 100 The raising in life-span is good.No sun gear, can preferably realize the lubrication of differential mechanism 100 simultaneously And cooling, that is to say, that can be formed inside sun gear, therefore planetary gear cavity due to eliminating, and tooth Circle engages the relation (sun gear belongs to external toothing with planetary gear) for being belonging to internal messing with planetary gear, in gear ring Lubricating oil can be stored, thus cooling and lubricant effect can be greatly improved.Further, since cancel sun gear, Parts are reduced, the quality and cost of differential mechanism 100 is reduced, makes differential mechanism 100 become more small-sized Change, lightweight.

And for the power-driven system 1000 with differential mechanism 100 according to embodiments of the present invention, Which mainly has spatially and in type of drive obvious advantage, by taking space advantage as an example, the power Drive system 1000 is particularly well-suited to new energy vehicle, as the power assembly of new energy vehicle is typically arranged In enging cabin, power assembly not only have speed changer, engine, while also have at least one motor, Due to enging cabin limited space, therefore can using compact differential mechanism 100 according to embodiments of the present invention Advantage is spatially obtained, arrangement is easily facilitated.And for example, as a example by the advantage for going up in a driving manner, due to root Greatly reduce according to the axial dimension of the differential mechanism 100 of the embodiment of the present invention, therefore axial space more preferably arranged, And there are differential mechanism 100 two gear rings can be better achieved and two motors as clutch end Power connector (as mentioned above that motor is connected by the external tooth of gear ring), and this is in traditional circular cone differential mechanism On be difficult to.

Vehicle 10000 according to embodiments of the present invention is briefly described below, as shown in figure 20, the vehicle 10000 Including the power-driven system 1000 in above-described embodiment, the power-driven system 1000 can be used for forerunner, Rear-guard is may naturally be used for, the present invention is not particularly limited to this.It should be appreciated that according to the present invention Other of the vehicle 10000 of embodiment construct such as brakes, driving system, steering etc. Prior art, and be well known to those skilled in the art, therefore no longer repeat one by one here.

In the description of this specification, reference term " one embodiment ", " some embodiments ", " example ", " specific example ", or " some examples " etc. description mean with reference to the embodiment or example describe it is concrete Feature, structure, material or feature are contained at least one embodiment or example of the present invention.In this theory In bright book, identical embodiment or example are necessarily directed to the schematic representation of above-mentioned term.And, The specific features of description, structure, material or feature can be in one or more any embodiment or examples In combine in an appropriate manner.Additionally, those skilled in the art can be by the difference described in this specification Embodiment or example are engaged and are combined.

Although embodiments of the invention have been shown and described above, it is to be understood that above-described embodiment It is exemplary, it is impossible to be interpreted as limitation of the present invention, one of ordinary skill in the art is the present invention's In the range of above-described embodiment can be changed, change, replace and modification.

Claims

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

Differential mechanism, the differential mechanism include：

The first row carrier, the first row star-wheel and the first gear ring, the first row star-wheel with it is described The first row carrier connects, and the first row star-wheel is engaged with first gear ring；

Second planet carrier, the second planetary gear and the second gear ring, second planetary gear with it is described Second planet carrier connects, and second planetary gear is engaged with second gear ring and second row Star-wheel is also engaged with the first row star-wheel, wherein, first gear ring and second gear ring Constitute two clutch ends of the differential mechanism；

Input unit, the input unit, the first row carrier and second planet carrier are coaxial Arrange and the input unit is linked with the first row carrier and second planet carrier respectively；

Power output shaft, the power output shaft are arranged to link with the input unit；

Multiple input shafts, the one of input shaft in the plurality of input shaft be arranged to optionally with institute Power output shaft linkage is stated, remaining described input shaft is arranged to link with the power output shaft；

First dynamotor, first dynamotor are arranged to join with one of input shaft It is dynamic.

2. power-driven system according to claim 1, it is characterised in that the first row star-wheel Partly overlapped with second planetary gear in the axial direction.

3. power-driven system according to claim 2, it is characterised in that the first row star-wheel Including：First teeth portion and the second teeth portion, second planetary gear include：3rd teeth portion and the 4th teeth portion, institute State the first teeth portion to engage with first gear ring, second teeth portion is with the 3rd teeth portion on the axial direction Correspondence is overlapped and is engaged and coordinates, and the 4th teeth portion is engaged with second gear ring.

4. power-driven system according to claim 1, it is characterised in that the first row star-wheel Roller gear is with the second planetary gear.

5. power-driven system according to claim 1, it is characterised in that first gear ring and Second gear ring is symmetrical arranged, and each in first gear ring and second gear ring includes：

6. power-driven system according to claim 1, it is characterised in that the input cage structure For input end gear, the input end gear is configured to annular and is set in first gear ring and described second Gear ring outer surface.

7. power-driven system according to claim 6, it is characterised in that first gear ring with Gap is provided between second gear ring, the input end gear surround and covers the gap.

8. power-driven system according to claim 1, it is characterised in that also include：Centre connects Binding structure, the intermediate connection structure is for being connected to institute by the first row carrier, second planet carrier Input unit is stated, the intermediate connection structure includes：First connecting bracket and the second connecting bracket, described first Connecting bracket is used to connect the first row carrier and the input unit, and second connecting bracket is used to connect Second planet carrier and the input unit, wherein in first connecting bracket and second connecting bracket Each include：

9. power-driven system according to claim 1, it is characterised in that each described the first row Star-wheel is configured with a first planet wheel shaft, and two ends of the first planet wheel shaft are respectively with described first Planet carrier is connected with second planet carrier, and each described second planetary gear is configured with second planetary gear Axle, two ends of second planet wheel spindle respectively with the first row carrier and the second planet carrier phase Even.

10. power-driven system according to claim 1, it is characterised in that the first row star-wheel Revolution-radius it is identical with the revolution-radius of second planetary gear.

11. power-driven systems according to claim 1, it is characterised in that also include：Engine, The engine is arranged to be selectively engageable at least one of the plurality of input shaft.

12. power-driven systems according to claim 1, it is characterised in that the power output shaft On be provided with power output shaft output gear, the power output shaft output gear engages biography with the input unit It is dynamic.

13. power-driven systems according to claim 12, it is characterised in that the power output Axle output gear constitutes main reducing gear with the input unit, wherein the power output shaft output gear is configured to Main reducing gear driving gear, the input unit are configured to main reducing gear driven gear.

14. power-driven systems according to claim 1, it is characterised in that the power output shaft Overhead set is provided with empty set driven gear, and the empty set driven gear is linked with one of input shaft, The power-driven system also includes synchronized, and the synchronized is arranged for the synchronous power output shaft With the empty set driven gear.

15. power-driven systems according to claim 14, it is characterised in that the synchronized sets Put on the power output shaft and for engaging the empty set driven gear.

16. power-driven systems according to claim 15, it is characterised in that the power output Fixed driven gear is fixedly installed on axle, the fixed driven gear is linked with described remaining input shaft.

17. power-driven systems according to claim 1, it is characterised in that the power output shaft Overhead set is provided with empty set driven gear and is fixedly installed fixed driven gear, the power-driven system Also include synchronized：The synchronized is arranged for the synchronous power output shaft and the empty set driven tooth Wheel；

18. power-driven systems according to claim 17, it is characterised in that the plurality of input Axle includes：

19. power-driven systems according to claim 18, it is characterised in that first input Axle is one of input shaft, and first dynamotor is by gear structure and the described first fixation Driving gear links；Or

20. power-driven systems according to claim 18, it is characterised in that also include：

Engine；And

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

Second dynamotor and the 3rd dynamotor, second dynamotor and first gear ring Linkage, the 3rd dynamotor are linked with second gear ring.

22. power-driven systems according to claim 21, it is characterised in that first gear ring Outer peripheral face on be provided with the first external tooth, the second external tooth is provided with the outer peripheral face of second gear ring, it is described Second dynamotor is linked with first external tooth, and the 3rd dynamotor is joined with second external tooth It is dynamic.

23. power-driven systems according to claim 1, it is characterised in that the speed changer includes First input shaft, the second input shaft and the 3rd input shaft, the 3rd input shaft are set in second input On axle, second input shaft is set on first input shaft, and the engine and described first is input into It is connected by three clutches between axle, second input shaft and the 3rd input shaft.

24. power-driven systems according to claim 1, it is characterised in that first gear ring with The near front wheel links, and second gear ring is linked with off-front wheel；

The power-driven system also includes：

25. a kind of vehicles, it is characterised in that include dynamic according to any one of claim 1-24 Power-driven system.