CN106555846A

CN106555846A - Power-driven system and the vehicle with which

Info

Publication number: CN106555846A
Application number: CN201510623459.1A
Authority: CN
Inventors: 凌和平; 翟震; 郑峰; 徐友彬; 罗永孟
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: CN106555846B

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, the first and second gear rings, first and second planetary gears are separately positioned on the first and second planet carriers, first and second planetary gears are engaged with the first and second gear rings respectively, second planetary gear is also engaged with the first row star-wheel, and the first row star-wheel is different from the revolution-radius of the second planetary gear；Power output shaft, power output shaft are linked with the power intake of differential mechanism；Multiple input shafts, one of input shaft are arranged to optionally link with power output shaft；First and second output sections, the first and second output sections are linked with the first and second gear rings respectively；First and second dynamotor, the first and second dynamotor are linked with the first and second output sections respectively.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 arranged in 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 arranged on second planet carrier, and second planetary gear is nibbled with second gear ring Close and second planetary gear is also engaged with the first row star-wheel；Wherein, first gear ring and described Two gear rings constitute two clutch ends of the differential mechanism, the first row carrier and second planet carrier Constitute the power intake of the differential mechanism, and the revolution half of the first row star-wheel and second planetary gear Footpath is different；Power output shaft, the power output shaft are arranged to the power intake with the differential mechanism Linkage；Multiple input shafts, 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 Output section and the second output section, first output section are linked with first gear ring, second output section Link with second gear ring；First dynamotor and the second dynamotor, first dynamoelectric and power generation Machine is linked with first output section, and second dynamotor is linked with second output section.

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.

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

Some embodiments of the invention, the power output shaft and the first row carrier, described second Planet carrier is coaxially fixed.

Some embodiments of the invention, first output section are left half axle gear, second output Portion is right axle shaft gear；And

The first external tooth is provided with first gear ring, the second external tooth on second gear ring, is provided with, it is described First external tooth is engaged with the left half axle gear, and second external tooth is engaged with the right axle shaft gear.

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, 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, 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, first dynamotor and second dynamoelectric and power generation office It is symmetrically arranged in the differential mechanism.

Some embodiments of the invention, power-driven system also include：3rd dynamotor, it is described 3rd dynamotor is arranged to link with one of input shaft.

Some embodiments of the invention, first gear ring towards second gear ring end face with it is described Second gear ring towards first gear ring end in the same plane.

Some embodiments of the invention, each in first gear ring and second gear ring are wrapped Include：

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 first row star-wheel and second planetary gear are in the axial direction Thickness is different.

Some embodiments of the invention, the gear teeth of relatively thin planetary gear are complete with the gear teeth of thicker planetary gear It is complete to engage, and the gear teeth of thicker planetary gear extend beyond the gear teeth of relatively thin planetary gear in the axial direction to side Or the gear teeth of thicker planetary gear extend beyond the gear teeth of relatively thin planetary gear in the axial direction respectively to both sides.

Some embodiments of the invention, the revolution-radius of thicker planetary gear are less than relatively thin planetary gear Revolution-radius.

Some embodiments of the invention, the corresponding gear ring of thicker planetary gear be little gear ring, relatively thin row The corresponding gear ring of star-wheel is bull gear, the external diameter of the external diameter of the bull gear more than the little gear ring.

Some embodiments of the invention, the thickness of the first row star-wheel is more than second planetary gear Thickness, first gear ring be little gear ring, second gear ring be bull gear, the public affairs of the first row star-wheel Turn revolution-radius of the radius less than second planetary gear.

Some embodiments of the invention, the revolution axis of the first row star-wheel and second planetary gear Revolution dead in line.

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

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 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 in above-described embodiment.

Description of the drawings

Fig. 1 is the explosive view at a visual angle 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 plan view sketch of differential mechanism according to embodiments of the present invention；

Fig. 4 is the stereogram after the assembling of differential mechanism according to embodiments of the present invention；

Fig. 5 is the position view of the first gear ring and the second gear ring in one of embodiment；

Fig. 6 is the position view of the first gear ring and the second gear ring in another embodiment；

Fig. 7 is the position view of the first gear ring and the second gear ring in another embodiment；

Fig. 8 is the partial schematic diagram of differential mechanism according to embodiments of the present invention；

Fig. 9 is the stereogram of the first row star-wheel and the second planetary gear；

Figure 10 is the theory of engagement sketch of the first row star-wheel and the second planetary gear；

Figure 11 is the stereogram of the first gear ring according to embodiments of the present invention or the second gear ring；

Figure 12 is the stereogram of the first gear ring in accordance with another embodiment of the present invention or the second gear ring；

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

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

Figure 21 is the schematic diagram of the power-driven system according to further embodiment of the present invention；

Figure 22 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 13-Figure 19, power-driven system 1000 according to some embodiments of the invention is main Including differential mechanism 100, speed changer 104, the first dynamotor 501 and the second dynamotor 502.

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-Figure 12, 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 depicted in figs. 1 and 2, differential mechanism 100 according to some embodiments of the invention can include the first row Carrier 11, the first row star-wheel 12 and the first gear ring 13 and the second planet carrier 21, the second planetary gear 22 With the 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. 3 is simultaneously combined shown in Fig. 1, Fig. 2 and Fig. 9, and the first row star-wheel 12 is arranged on the first row carrier On 11, for example, each the first row star-wheel 12 is configured with a first planet wheel shaft 14 (shown in Fig. 9), Two ends of first planet wheel shaft 14 are rotatably supported in the first row carrier 11 and the second planet carrier respectively On 21, two ends of such as first planet wheel shaft 14 can be rotatably supported in first planet by bearing In the axis hole corresponded to each other on frame 11 and the second planet carrier 21, now the first row star-wheel 12 is securable to right On the first planet wheel shaft 14 answered.Certainly, two ends of first planet wheel shaft 14 and the first row carrier 11 can also be fixedly connected with the second planet carrier 22, for example the two of first planet wheel shaft 14 end It is welded and fixed with the axis hole that corresponds to each other in the first row carrier 11 and the second planet carrier 22 respectively, now first Planetary gear 12 is rotatably sleeved on corresponding first planet wheel shaft 14, and for example the first row star-wheel 12 can It is rotatably mounted around by bearing on first planet wheel shaft 14.Thus, by first planet wheel shaft 14 Can realize connecting the purpose of the first row carrier 11 and the second planet carrier 21, so that the first row carrier 11 and second planet carrier 21 keep synchronized, in the same direction motion (i.e. the first row carrier 11 and the second planet carrier 21 Linkage).And this connected mode is adopted, the first row carrier 11 and the second planet carrier 21 can be well First planet wheel shaft 14 is carried out supporting/fixing, prevents first planet wheel shaft 14 from departing from single planet carrier Connect and cause differential mechanism 100 to fail.

The first row star-wheel 12 is engaged with the first gear ring 13, concretely internal messing form, i.e. the first row star-wheel Simultaneously engage with the tooth on the first gear ring 13 12 inner sides for being located at the first gear ring 13.The first row star-wheel 12 is preferred For multiple, and circumferentially equidistantly distributed on the inside of the first gear ring 13, for example, as a kind of preferred Embodiment, the first row star-wheel 12 can be between three, and two the first row star-wheels 12 of arbitrary neighborhood Interval angles are 120 °.

Similarly, such as Fig. 3 with reference to shown in Fig. 1, Fig. 2 and Fig. 9, the second planetary gear 22 are arranged on the On two planet carriers 21, for example, each second planetary gear 22 is configured with second planet wheel spindle 24, such as Two ends of the second planet wheel spindle 24 can be rotatably supported in the first row carrier 11 and by bearing In the axis hole corresponded to each other on two planet carriers 21, now the second planetary gear 22 is securable to corresponding second row On spider gear shaft 24.Certainly, two ends of the second planet wheel spindle 24 and the first row carrier 11 and the second row Carrier 22 can also be fixedly connected, two ends of such as the second planet wheel spindle 24 respectively with the first row The axis hole corresponded to each other in carrier 11 and the second planet carrier 22 is welded and fixed, and now the second planetary gear 22 can Rotationally it is set on corresponding second planet wheel spindle 24, such as the second planetary gear 22 can by bearing Rotationally it is sleeved on the second planet wheel spindle 24.Thus, connection can be realized by the second planet wheel spindle 24 The purpose of the first row carrier 11 and the second planet carrier 21, so that the first row carrier 11 and the second planet Frame 21 keeps synchronized, in the same direction motion.And adopt this connected mode, the first row carrier 11 and the second row Carrier 21 can carry out supporting/fixing to the second planet wheel spindle 24 well, prevent the second planet wheel spindle 24 It is disconnected with single planet carrier and causes differential mechanism 100 to fail.

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, it is also possible to by intermediate member by the first row carrier 11 and the second planet Frame 21 is directly fixedly connected, that is to say, that the first row carrier 11 and the second planet carrier in above example 21 synchronized, in the same direction motion can be realizing by first planet wheel shaft 14 and the second planet wheel spindle 24 , and the embodiment directly can realize the first row carrier 11 and the second planet carrier by arranging intermediate member 21 synchronized, in the same direction motion, such as intermediate member may be located at the first row carrier 11 and the second planet carrier It is welded and fixed between 21 and respectively with the first row carrier 11 and the second planet carrier 21.

Second planetary gear 22 is engaged with the second gear ring 23, concretely internal messing form, i.e. the second planetary gear Simultaneously engage with the tooth on the second gear ring 23 22 inner sides for being located at the second gear ring 23.Second planetary gear 22 is preferred For multiple, and circumferentially equidistantly distributed on the inside of the second gear ring 23, for example, as a kind of preferred Embodiment, the second planetary gear 22 can be between three, and two the second planetary gears 22 of arbitrary neighborhood Interval angles are 120 °.

, wherein it is desired to explanation, Fig. 3 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. 3 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 8, 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.

Additionally, another multiple embodiments are in the first row star-wheel 12 and the second planetary gear 22, it is multiple 22 circumferentially alternating arrangement of the first row star-wheel 12 and multiple second planetary gears, and the first row of arbitrary neighborhood Star-wheel 12 and the second planetary gear 22 are engaged.That is, in this embodiment, multiple the first row star-wheels 12 and multiple second planetary gears 22 it is circumferentially alternating arrangement and form annular, each the first row star-wheel 12 two the second planetary gears 22 being all adjacent are engaged, similarly, each second planetary gear 22 Two the first row star-wheels 12 being adjacent are engaged.

Wherein, with reference to the embodiment of Fig. 3, the revolution axes O of the first row star-wheel 12 and the second planetary gear 22 Revolution axes O overlap.

Especially, as shown in Fig. 1-Fig. 3, Fig. 8-Figure 10, 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 shown in figure 3, the first gear ring 13 and the second gear ring 23 may be constructed two power of differential mechanism 100 Output end, the first row carrier 11 and the second planet carrier 21 then correspond to the power intake for constituting differential mechanism 100 (for example, now the first row carrier 11 and the second planet carrier 21 can be rigidly connected), it is so outer The power of portion's power source output can be input into from the first row carrier 11 and the second planet carrier 21, through differential mechanism Can export from the first gear ring 13 and the second gear ring 23 respectively after 100 differential action.Now, as optional Embodiment, the first row carrier 11 and the second planet carrier 21 can connect the power such as engine, motor Source, the first gear ring 13 and the second gear ring 23 can be connected with corresponding semiaxis by gear transmission structure, semiaxis It is connected with corresponding wheel again, but not limited to this.

Differential between wheel is applied to the differential mechanism 100 below, the first gear ring 13 and the composition of the second gear ring 23 are poor The clutch end of fast device 100, the first row carrier 11 and the second planet carrier 21 constitute the dynamic of differential mechanism 100 The operation principle of differential mechanism 100 is briefly described as a example by power input, wherein now the first gear ring 13 can pass through External tooth is connected with left half axle, and left half axle can be connected with left side wheel, and the second gear ring 23 can be by external tooth and the right side Semiaxis is connected, and right axle shaft can be connected with right side wheels, the power of power source such as engine and/or motor output Can be exported after the decelerating effect of main reducing gear to the first row carrier 11 and the second planet carrier 21.If now Vehicle is travelled on smooth road surface and without turning, and rotating speed is identical in theory with right side wheels for left side wheel, this When differential mechanism 100 do not play differential action, 21 synchronized, rotating in same direction of the first row carrier 11 and the second planet carrier, First gear ring 13 and the second gear ring 23 synchronized, rotating in same direction, the first row star-wheel 12 and the second planetary gear 22 Only revolution, not rotation.If now vehicle traveling is travelled on irregular road surface or turn inside diameter, left side car Rotating speed is different in theory with right side wheels for wheel, and the rotating speed of the first gear ring 13 and the second gear ring 23 is also different, i.e., There is speed discrepancy, now also rotation while revolution of the first row star-wheel 12 and the second planetary gear 22, first One caused from the change of team in the first gear ring 13 and the second gear ring 23 of planetary gear 12 and the second planetary gear 22 Speedup, another deceleration, the gear ring of speedup are the speed discrepancy of left and right wheelses with the speed discrepancy of the gear ring of deceleration, So as to realize differential action.

Thus, 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.

Especially, the first row star-wheel 12 is different from the revolution-radius of the second planetary gear 22, i.e., referring to Fig. 3 institutes Show, the revolution-radius of the first row star-wheel 12 refer to radius of the first row star-wheel 12 around revolution axes O revolution R1, the revolution-radius of the second planetary gear 22 refer to radius of second planetary gear 22 around revolution axes O revolution R2, shown in Figure 3, R1 ≠ R2, such as R2 ＞ R1.That is, the first row star-wheel 12 and the second planetary gear 22 Revolution track diametrically stagger.In the example of the present invention, the revolution half of the first row star-wheel 12 Footpath is relatively small, and the revolution-radius of the second planetary gear 22 are relatively large.

Due to the first row star-wheel 12 it is different with the revolution-radius of the second planetary gear 22, therefore in some embodiments In, the internal diameter size of the internal diameter size of the first gear ring 13 and the second gear ring 23 is also different, revolution-radius The internal diameter size of little planetary gear (such as the first row star-wheel 12) corresponding gear ring is less, i.e. respective radius Relatively small little gear ring (such as the first gear ring 13), the larger planetary gear of revolution-radius (such as the second planet The radial dimension for taking turns 22) corresponding gear ring is larger, i.e. the larger bull gear of respective radius is (such as the second gear ring 23), this causes bull gear 23 and little gear ring 13 diametrically to stagger, it is to avoid the motion such as gear ring and planetary gear Interference is moved between part, so as to effectively reduce the axial gap of the first gear ring 12 and the second gear ring 22, Referring for example to Fig. 3, Fig. 5-Fig. 6, the axial gap is D, by reducing axial gap D, so that The axial dimension for obtaining differential mechanism 100 is less, more compact structure.

Below the construction of the first gear ring 13 and the second gear ring 23 is retouched in conjunction with specific embodiments in detail State.

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.

With reference to Fig. 5 and with reference to shown in Fig. 1 and Fig. 2, end face of first gear ring 13 towards the second gear ring 23 B1 (with reference to Fig. 2) is in together towards the end face B2 (with reference to Fig. 1) of the first gear ring 13 with the second gear ring 23 In one plane B3 (with reference to Fig. 5), in other words, in the embodiment, as shown in figure 5, end face B1, end Face B2 is in plane B3 simultaneously, i.e., overlap with B3, thus the first gear ring 13 and the second gear ring 23 clearance Ds in the axial direction are zero (as shown in Figure 5), can so greatly reduce the axle of differential mechanism 100 To size, the volume that makes differential mechanism 100 is more compact, more compact structure, facilitates whole power drive system Arrangement.

In another embodiment, as shown in fig. 7, radius is relative in the first gear ring 13 and the second gear ring 23 A less gear ring such as little gear ring 13 is at least partially embedded a larger gear ring such as canine tooth of radius size In circle 23, now the first gear ring 13 and the second gear ring 23 clearance D in the axial direction can be understood as bearing, Thus the axial dimension of differential mechanism 100 can equally be reduced, while passing through the first gear ring 13 and the second gear ring 23 can preferably protect the parts in two gear rings.

Optionally, of course, with reference to shown in Fig. 6, the first gear ring 13 and the second gear ring 23 also may be used in the axial direction With the D that staggers and keep at a certain distance away.It is understood that it is single from reduce 100 axial dimension of differential mechanism this For angle, the clearance D of Fig. 5 embodiments is zero and the clearance D of Fig. 7 embodiments is an advantage over Fig. 6 for negative (clearance D of Fig. 6 embodiments is for just) of embodiment.

It should be noted that the clearance D of above-mentioned Fig. 3 (with reference to Fig. 1-Fig. 2, Fig. 5-Fig. 7) refers to The distance between annular side wall portion 162 of the annular side wall portion 162 of one gear ring 13 and the second gear ring 23.Example Such as referring to Fig. 1-Fig. 3, the embodiment of Fig. 5-Fig. 7, the first gear ring 13 and the second gear ring 23 all include master Body flat part 161 and annular side wall portion 162.

And the present invention other embodiments in, such as referring to the embodiment of Figure 11 and Figure 12 in, the first tooth Each in circle 13 and the second gear ring 23 still further comprises 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 enforcement of Figure 11 In example, the internal diameter of annular flange portion 163 can be generally equalized with the external diameter of annular side wall portion 162, so annular Flange part 163 is diametrically equivalent to outwardly 162 (i.e. the first gear ring 13 or the second of annular side wall portion The outer peripheral face of gear ring 23).And in the fig. 12 embodiment, 163 external diameter of annular flange portion can be with annular side The external diameter of wall portion 162 is generally equalized, and the internal diameter of annular flange portion 163 can be more than annular side wall portion 162 Internal diameter, 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 Fig. 1-Fig. 3, the gear ring structure of Fig. 5-Fig. 7 embodiments, two Clearance D between gear ring refers to the gap between the annular side wall portion 162 of two gear rings.And Figure 11 and Tu Gear ring structure in 12 embodiments, the clearance D between two gear ring refer to the annular flange flange of two gear rings Gap between portion 163.

For the embodiment of the embedded bull gear of little gear ring, such as Fig. 1-Fig. 2 and with reference to shown in Fig. 3, the first tooth Each in circle 13 and the second gear ring 23 includes：Body panels portion 161 and it is arranged on body panels portion The annular side wall portion 162 on 161 periphery edge, body panels portion 161 and annular side wall portion 162 can be one Body formed part.Multiple gear teeth are provided with the internal face of annular side wall portion 162, wherein it is shown in Figure 4, The annular side wall portion 162 of a relatively small gear ring of radius such as the first gear ring 13 (i.e. little gear ring 13) to The annular of a relatively large gear ring such as the second gear ring 23 (i.e. bull gear 23) of radius is embedded in partially In side of sidewall portion 162.

Certainly, for the embodiment of the embedded bull gear of little gear ring, it would however also be possible to employ the tooth in Figure 11-Figure 12 Wheel construction, such as bull gear have annular flange flange using the gear ring structure in Figure 11 or Figure 12, i.e. bull gear Portion 163, and little gear ring can then adopt common gear ring structure (no annular flange portion of Fig. 1-Fig. 3 embodiments 163), now the annular side wall portion 162 of little gear ring can be at least partially embedded the annular flange portion of bull gear It is interior.Or, little gear ring and bull gear can adopt the gear ring structure in Figure 11 and Figure 12, now little tooth The annular flange portion 163 of circle can be at least partially embedded in the annular flange portion of bull gear, but is not limited to This.

Although further, it is to be appreciated that the above-mentioned embodiment for giving the embedded bull gear of several little gear rings, But this is not the one kind to the scope of the present invention limits, those skilled in the art are reading specification After the above, the embedding principle of gear ring is fully understood by, above-mentioned little gear ring and/or bull gear can be existed Similar modification is made in structure, this equally falls under the scope of the present invention.

It is shown in Figure 3, limit between body panels portion 161 and annular side wall portion 162 cavity A1, A2 (referring to Fig. 3), specifically, body panels portion 161 and the annular side wall portion 162 of the first gear ring 13 Between limit cavity A1, between the body panels portion 161 of the second gear ring 23 and annular side wall portion 162 limit Cavity A2 is made, the cavity A2 in cavity A1 and the second gear ring 23 in the first gear ring 13 is toward each other To constitute installing space A (referring to Fig. 3), wherein the first row carrier 11 and the first row star-wheel 12 and second Planet carrier 21 and the second planetary gear 22 are accommodated in installing space A, such first gear ring 13 and the second tooth Circle 23 serves as the function of external shell, can protect and be accommodated in planet carrier therein and planetary gear, improves the longevity Life.And coordinate the end face B2 of the end face B1 and the second gear ring 23 of the first gear ring 13 concordant or coordinate chi The embodiment of at least partially embedded larger-size bull gear of very little less little gear ring 13 23, can cause Installing space A is comparatively closed, and outside debris are not easily accessible in installing space A and affect moving component, Ensure that the steady operation of differential mechanism 100.

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.

In an embodiment of the present invention, the first row star-wheel 12 and the second planetary gear 22 thickness in the axial direction is not With (referring to Figure 10), so there is certain help to the diminution of 100 axial dimension of differential mechanism.Further, compared with The thin planetary gear such as gear teeth of the second planetary gear 22 are complete with the gear teeth of thicker planetary gear such as the first row star-wheel 12 It is complete to engage, and the gear teeth of thicker planetary gear extend beyond the wheel of relatively thin planetary gear in the axial direction to side Tooth, or the gear teeth of thicker planetary gear extend beyond the wheel of relatively thin planetary gear in the axial direction respectively to both sides Tooth.In the example of the present invention, the gear teeth of thicker planetary gear only extend beyond relatively thin in the axial direction to side Planetary gear the gear teeth, such as with reference to shown in Fig. 9 and Figure 10, thicker the first row star-wheel 12 prolongs to the left Stretch beyond the second relatively thin planetary gear 22, the right flank and the second relatively thin row of thicker the first row star-wheel 12 What the right flank of star-wheel 22 can be generally flush with substantially, be so conducive to the control to 100 axial dimension of differential mechanism System.

Due to the first row star-wheel 12 it is different with the revolution-radius of the second planetary gear 22, for planetary gear thickness not Same embodiment, the revolution-radius of its thicker planetary gear such as the first row star-wheel 12 are less than relatively thin planetary gear Such as the revolution-radius of the second planetary gear 22.Also, thicker planetary gear such as 12 corresponding tooth of the first row star-wheel Enclose as the less little gear ring of radial dimension such as the first gear ring 13, relatively thin planetary gear such as the second planetary gear 22 pairs The gear ring answered is relatively large bull gear such as the second gear ring 23 of radial dimension, and the external diameter of bull gear 23 is (outward Surface) more than the external diameter (outer surface) of little gear ring 13.For example in the example of the present invention, the first row star-wheel Thickness of 12 thickness more than the second planetary gear 22, so as to thicker the first row star-wheel 12 corresponding first Gear ring 13 is little gear ring, and relatively thin 22 corresponding second gear ring 23 of the second planetary gear is bull gear, and Revolution-radius of the revolution-radius of the first row star-wheel 12 less than the second planetary gear 22.

Furthermore, it is necessary to explanation, the less planetary gear of revolution-radius and a relatively small gear ring of radius Engagement, now, the less planetary gear of revolution-radius is the relatively thick planetary gear of thickness, the one of the planetary gear Part is that the internal tooth of relatively small with a radius gear ring is engaged, its another part be with revolution-radius compared with Big planetary gear is relatively thin planetary gear engagement.

As optional embodiment, the external diameter of the internal diameter of bull gear 23 more than little gear ring 13, here big The internal diameter of gear ring 23 refers to the radial dimension of the outside circle of 23 internal tooth of bull gear, in other words, bull gear The tooth top diameter of a circle of 23 internal tooth is greater than the external diameter of little gear ring 13.So little gear ring 13 can be overall Or in the embedded bull gear 23 of at least a portion, i.e., above-mentioned axial gap D is reduced into negative (i.e. little tooth 23), thus i.e. two kinds planetary gears of two gear rings will not move interference or sliding to 13 embedded bull gear of circle Wipe, which increase the stability of differential mechanism 100, while inner space can also relatively more closed, protect The parts such as planet carrier and planetary gear inside shield.

Below the power intake and clutch end of differential mechanism 100 are carried out in conjunction with specific embodiments in detail Description.

With reference to shown in Fig. 1-Fig. 3, differential mechanism 100 also includes that differential input shaft 31,32 and differential mechanism are defeated Shaft 41,42, differential input shaft 31,32 respectively with 21 phase of the first row carrier 11 and the second planet carrier Even, such as in the example of fig. 3, the right side of the first row carrier 11 is connected with a differential input shaft 31, The left side of the second planet carrier 21 is connected with another 32 differential input shaft.Differential output shaft 41,42 It is connected with the first gear ring 13 and the second gear ring 23 respectively, such as in the example of fig. 3, the first gear ring 13 Right side is connected with a differential output shaft 41, and it is defeated that the left side of the second gear ring 23 is connected with another differential mechanism Shaft 42.Differential input shaft 31,32, the 41,42, first gear ring of differential output shaft 13 and second Gear ring 23 can be coaxially arranged.

Further, as shown in figure 3, differential input shaft includes：First differential input shaft 31 and second Differential input shaft 32, the first differential input shaft 31 are connected with the first row carrier 11, the second differential mechanism Input shaft 32 is connected with the second planet carrier 21, and differential output shaft can include：First differential output shaft 41 and second differential output shaft 42, the first differential output shaft 41 is connected with the first gear ring 13, and second Differential output shaft 42 is connected with the second gear ring 23, and the first differential input shaft 31 and the second differential mechanism are defeated It can be hollow shaft structure to enter axle 32 and the first differential output shaft 41 and the second differential output shaft 42, Wherein as preferred embodiment, it is defeated that the first differential output shaft 41 is coaxially set in the first differential mechanism Enter on axle 31, the second differential output shaft 42 is coaxially set on the second differential input shaft 32, by This 100 structure of differential mechanism is compacter, volume is less.

However, above-mentioned differential input shaft, differential output shaft are only a kind of optional embodiments, in figure In the embodiment of the power-driven system of 13- Figure 21, differential mechanism 100 is externally exported by the external tooth of gear ring Power.

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 concrete structure of the differential mechanism 100 for implementing to exemplify referring to 1- Fig. 3 is briefly described.Reference Shown in Fig. 1-Fig. 3, multiple the first row star-wheels between the first row carrier 11 and the second planet carrier 21, are provided with Axle 14 and multiple second planet wheel spindles 24, the first row star-wheel 12 is multiple and correspondence is connected to first planet On wheel shaft 14, the second planetary gear 22 is connected on the second planet wheel spindle 24 for multiple and correspondence.The first row The thickness of star-wheel 12 is bigger than the thickness of the second planetary gear 22, the gear teeth of relatively thin the second planetary gear 22 with The gear teeth of thicker the first row star-wheel 12 are at a fully engaged, and the gear teeth of thicker the first row star-wheel 12 can be to the left Extend beyond the second relatively thin planetary gear 22.Thicker 12 corresponding first gear ring 13 of the first row star-wheel is Little gear ring, relatively thin 22 corresponding second gear ring 23 of the second planetary gear is bull gear, the end of little gear ring 13 Face B1 can locate in the same plane with the end face B2 of bull gear 23, so that little gear ring 13 and bull gear 23 axial gap D is zero, installation cavity A in two gear rings is relatively more closed.

To sum up, differential mechanism 100 according to embodiments of the present invention, using the planetary gear of roller gear form, its In structure and type of attachment, space availability ratio is higher, and axial dimension is less, and in production with fit on more With advantage.The compact differential mechanism 100 also realizes two skiddings by making the displacement of side planetary gear and gear ring Avoidance (i.e. the revolution-radius of planetary gear are different) on star-wheel mechanism space and size, such structure design It has been greatly saved spatially to avoid the axial gap of another group of corresponding planetary gear and gear ring so that this is tight Gather type differential mechanism 100 axial dimension it is less and more compact.

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 13- Figure 21, 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 the power intake of differential mechanism 100, I.e. power output shaft 103 is arranged to link with the first row carrier 11 and the second planet carrier 21.

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 13 and Figure 14, one of input shaft such as first Input shaft 101 (being the second input shaft 102 in Figure 15) can be linked with power output shaft 103, One of input shaft such as the first input shaft 101 also can be disconnected with power output shaft 103 simultaneously.It is right In remaining input shaft, then it is all provided with being set to and links with power output shaft 103, be i.e. these input shaft actions Then power output shaft 103 also follows action or 103 action of power output shaft then these input shafts Action therewith.

As shown in figure 14, the 3rd 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 for being linked with the 3rd 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 Power output shaft 103 and empty set driven gear 108.It is understood that being in joint shape in synchronized 109 During state, the synchronous empty set driven gear 108 of synchronized 109 and power output shaft 103 are so electric from the 3rd The power of dynamic generator 401 can under the conjugation of synchronized 109 from power output shaft 103 export to Differential mechanism 100, and when synchronized 109 is off, the 3rd dynamotor 401 equivalent to Power output shaft 103 disconnects.Thus, synchronized 109 serves as the power switch of the 3rd dynamotor 401, The output of 401 power of the 3rd dynamotor can be controlled and disconnected.

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 15 removed in above-mentioned Figure 14 embodiments is implemented Input shaft 102 in example.

For example, see the specific embodiment of Figure 13 and Figure 14, 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 example of Figure 13 and Figure 14, empty set driven gear 108 and fixed driven gear 107 Quantity is one, and accordingly, the quantity of fixed driving gear is two, empty set driven gear 108 A pair of gear pairs of composition are engaged with a fixed driving gear, fixed driven gear 107 is solid with another Determine driving gear engagement composition another to gear pair, it will be understood that the transmission speed ratio of two pairs of gear pairs Transmission gear of the speed changer 104 in difference, therefore the embodiment with two not synchronized ratios, so The structure of power-driven system 1000 is relatively easy, compact, and also disclosure satisfy that normal vehicle operation Requirement to transmission speed ratio.

As shown in Figure 13-Figure 21, 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 14, Figure 16-Figure 19, 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 the 3rd Dynamotor 401 is linked with the first input shaft 101, and such as the 3rd dynamotor 401 passes through gear Structure is linked with the first fixation driving gear 106, and concretely the 3rd 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 3rd dynamotor 401.

And in the example of fig. 15, 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 3rd dynamotor 401 Link with the second input shaft 102, such as the 3rd dynamotor 401 passes through gear structure and second to be fixed Driving gear 105 links, concretely the 3rd 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 3rd 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 13-Figure 21, 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.

Referring to Figure 13-Figure 21 and with reference to shown in Fig. 1-Figure 12, as a preferred embodiment of the present invention side Formula, power output shaft 103 are coaxial fixed with the first row carrier 11 and the second planet carrier 21, so that becoming Fast device 104 is compacter with the coupling part of differential mechanism 100, i.e., directly output power axle 103 and two Planet carrier is coaxially fixed, so as to the volume that at least can reduce power-driven system 1000 to a certain extent.

In a further embodiment, as shown in Figure 13-Figure 21, power-driven system 1000 also includes first Output section 601 and the second output section 602, the first output section 601 are linked with the first gear ring 13, and second is defeated Go out portion 602 to link with the second gear ring 23.Further, the first output section 601 is left half axle gear, the Two output sections 602 are right axle shaft gear, while the first external tooth 603 on the first gear ring 13, is provided with, second The second external tooth 604 is provided with gear ring 23, the first external tooth 603 is engaged with left half axle gear 601, second External tooth 604 is engaged with right axle shaft gear 602, and thus the power of Jing differential mechanisms 100 can finally pass through left half axle Gear 603 and right axle shaft gear 604 are exported to the wheel of the left and right sides.

Wherein, as shown in Figure 14-Figure 21, the first dynamotor 501 is arranged to can be with the first output section 601 linkages, the second dynamotor 502 are arranged to link with the second output section 602, and such as first is electronic Gear 503 can be provided with the motor shaft of generator 501, gear 503 is engaged with left half axle gear 601, It is provided with gear 504, gear 504 and right axle shaft gear simultaneously on the motor shaft of the second dynamotor 502 602 engagements.

As shown in Figure 14-Figure 21, the first dynamotor 501 and the second dynamotor 502 are with regard to difference The 100 symmetrical distribution of fast device, can so cause the center of gravity of power-driven system 100 in center Or closer to center.

Referring to the embodiment of Figure 20 Figure 21, the power-driven system 1000 and Figure 12-figure in the embodiment One of power-driven system 1000 in 19 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 14 Condition.

Low speed is pure electronic：Double clutch 204 is all off, and synchronized 109 disconnects, the first dynamotor 501 and second dynamotor 502 worked externally directly output power in motor mode.Move under the pattern Power bang path is shorter, and transmission energy loss is little, is adapted to urban congestion road conditions.

High speed is pure electronic：Double clutch 204 is all off, and synchronized 109 is in engagement state, and first is electric All work is externally exported for dynamic generator 501, the second dynamotor 502 and the 3rd dynamotor 401 Power.

Low engine speed is kept off：First bonding part 201 is engaged with the 3rd bonding part 203, the second junction surface 202 are divided to disconnect with the 3rd bonding part 203, synchronized 109 is in engagement state, now engine 301 The power of generation is by exporting to differential mechanism 100, by poor after the first input shaft 101, power output shaft 103 Fast device 100 is distributed to the driving wheel of both sides by power.

High engine speeds are kept off：Second bonding part 202 is engaged with the 3rd bonding part 203, the first junction surface 201 are divided to disconnect with the 3rd bonding part 203, synchronized 109 is off, now engine 301 The power of generation is by exporting to differential mechanism 100, by poor after the second input shaft 102, power output shaft 103 Fast device 100 is distributed to the driving wheel of both sides by power.

Power generation in parking：First bonding part 201 is engaged with the 3rd bonding part 203, the second bonding part 202 are disconnected with the 3rd bonding part 203, and synchronized 109 is off, and now engine 301 is produced Raw power is exported to the 3rd dynamotor 401 by the first input shaft 101, drives the 3rd dynamoelectric and power generation Machine 401 is generated electricity as motor, realizes power generation in parking function.

Brake energy recovery：Synchronized 109 can be at off-state, now 501 He of the first dynamotor Second dynamotor 502 reclaims braking energy.Or synchronized 109 is in engagement state, now first Dynamotor 501, the second dynamotor 502 and the 3rd dynamotor 401 all reclaim Brake Energy Amount.

Driving generates electricity：Engine 301 can pass through the different engagement states and synchronized of double clutch 204 109 engaging/disengaging state, and selectively drive the first dynamotor 501 and the second dynamotor 502 generate electricity or drive the 3rd dynamotor 401 to generate electricity, and three motors also can be driven certainly simultaneously to send out Electricity, at the same time, engine 301 also externally exports power, drives vehicle traveling.

Increase journey pattern：First bonding part 201 engages the 3rd bonding part 203, the second bonding part 202 Disconnect with the 3rd bonding part 203, the output power of engine 301 drives the 3rd dynamotor 401 to generate electricity, First dynamotor 501 and the second dynamotor 502 export power drive vehicle as motor simultaneously Traveling.

Figure 13 embodiments eliminate the 3rd dynamotor 401 with differring primarily in that for Figure 14 embodiments, For remaining construction part is then consistent, repeat no more here.

Figure 15 embodiments differ primarily in that with Figure 14 embodiments the 3rd in Figure 15 embodiments is electronic Generator 401 is linked with the second input shaft 102, for remaining construction part is then consistent, here no longer Repeat.

For the embodiment of Figure 16-Figure 19, compared with Figure 14 embodiments, difference is that to increased rear-guard poor Speed lock.

Reference picture 16- Figure 19 is simultaneously combined shown in Fig. 1-Figure 12, and the first gear ring 13 is linked with the near front wheel 910a, Link with the near front wheel 910a as the first gear ring 13 passes through the first external tooth 603 and left half axle gear 601, second Gear ring 23 and off-front wheel 910b linkages, such as the second gear ring 23 pass through the second external tooth 604 and right axle shaft gear 602 are coaxially connected with off-front wheel 910b with off-front wheel 910b linkages.4th dynamotor 901 passes through tooth Wheel construction is linked with left rear wheel 910c, and such as the 4th dynamotor 901 passes through gear W1, W2, W3, W4 Link with left rear wheel 910c, gear W1 is coaxial with the 4th dynamotor 901 to be connected, gear W1 and tooth Wheel W2 engagements, gear W2 are coaxially connected with gear W3, and gear W3 is engaged with gear W4, gear W4 Can be fixedly installed on left half axle 904, on left half axle 904, be provided with left rear wheel 910c.Similarly, Five dynamotor 902 are linked with off hind wheel 910d by gear structure, such as the 5th dynamotor 902 By gear X1, X2, X3, X4 and off hind wheel 910d linkages, gear X1 and the 5th dynamotor 902 Coaxial to be connected, gear X1 is engaged with gear X2, and gear X2 is coaxially connected with gear X3, gear X3 and Gear X4 is engaged, and gear X4 can be fixedly installed on right axle shaft 905, after being provided with the right side on right axle shaft 905 Wheel 910d.

In the example of Figure 16, 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 of Figure 17, 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 of Figure 18, 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 Figure 19, 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 by the first gear ring 13 towards the second gear ring 23 end face and the second tooth End scheme at grade and first gear ring 13 and second tooth of the circle 23 towards the first gear rings 13 The scheme combination of the construction of circle 23, so that the axial gap of 100 liang of gear rings of differential mechanism is zero, so as to Two gear rings can limit the installing space of relative closure, and the part in installing space is adequately protected, Increase its service life, and reduces cost, while the axial dimension of differential mechanism 100 effectively can also be reduced.

And for example, the thickness of the first row star-wheel 12 can be more than those skilled in the art the thickness of the second planetary gear 22 The scheme of degree and the first gear ring 13 is little gear ring, the second gear ring 23 is bull gear scheme and first planet The revolution-radius of wheel 12 are combined less than the scheme of the revolution-radius of the second planetary gear 22, are consequently formed The structure of 100 scheme of differential mechanism is compacter, and volume is less, is more convenient for being arranged in the enging cabin of vehicle Portion.

For another example, those skilled in the art can by the first gear ring 13 towards the second gear ring 23 end face and the second tooth End scheme at grade and relatively thin planetary gear and thicker row of the circle 23 towards the first gear rings 13 The scheme combination of the meshing relation of star-wheel, thus on the one hand so that the axial gap of 100 liang of gear rings of differential mechanism is Zero, so as to two gear rings can limit the installing space of relative closure, the part in installing space is filled Code insurance is protected, and is increased its service life, and reduces cost, on the other hand can also further be reduced differential mechanism 100 axial dimension, makes differential mechanism 100 have less volume.

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 21, 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 are arranged on In 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 are arranged on On second planet carrier, second planetary gear is engaged and described with second gear ring Second planetary gear is also engaged with the first row star-wheel；

Wherein, first gear ring and second gear ring constitute two of the differential mechanism and move Power output end, the first row carrier and second planet carrier constitute the dynamic of the differential mechanism Power input, and the first row star-wheel is different from the revolution-radius of second planetary gear；

Power output shaft, the power output shaft are arranged to the power intake connection with the differential mechanism It is dynamic；

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 output section and the second output section, first output section are linked with first gear ring, and described Link with second gear ring two output sections；

First dynamotor and the second dynamotor, first dynamotor and the described first output Portion links, and second dynamotor is linked with second output section.

2. differential mechanism according to claim 1, it is characterised in that first gear ring is towards described The end face of the second gear ring and second gear ring towards first gear ring end in the same plane.

3. differential mechanism according to claim 2, it is characterised in that first gear ring and described Each in two gear rings includes：

4. differential mechanism according to claim 1, it is characterised in that the first row star-wheel with it is described Second planetary gear thickness in the axial direction is different.

5. differential mechanism according to claim 4, it is characterised in that the gear teeth of relatively thin planetary gear with The gear teeth of thicker planetary gear are at a fully engaged, and the gear teeth of thicker planetary gear extend super to side in the axial direction The gear teeth for going out the planetary gear of the gear teeth or thicker of relatively thin planetary gear extend super to both sides in the axial direction respectively Go out the gear teeth of relatively thin planetary gear.

6. differential mechanism according to claim 4, it is characterised in that the revolution of thicker planetary gear half Revolution-radius of the footpath less than relatively thin planetary gear.

7. differential mechanism according to claim 4, it is characterised in that the corresponding tooth of thicker planetary gear Enclose as little gear ring, the corresponding gear ring of relatively thin planetary gear is bull gear, and the external diameter of the bull gear is more than described The external diameter of little gear ring.

8. differential mechanism according to claim 4, it is characterised in that the thickness of the first row star-wheel More than the thickness of second planetary gear, first gear ring is little gear ring, and second gear ring is bull gear, Revolution-radius of the revolution-radius of the first row star-wheel less than second planetary gear.

9. differential mechanism according to claim 1, it is characterised in that the revolution of the first row star-wheel The revolution dead in line of axis and second planetary gear.

10. differential mechanism according to claim 1, it is characterised in that the first row star-wheel and second Planetary gear is roller gear.

11. differential mechanisms according to claim 1, it is characterised in that each described the first row star-wheel is matched somebody with somebody Be equipped with a first planet wheel shaft, two ends of the first planet wheel shaft respectively with the first row carrier It is connected with second planet carrier, each described second planetary gear is configured with second planet wheel spindle, described Two ends of the second planet wheel spindle are connected with the first row carrier and second planet carrier respectively.

12. power-driven systems according to claim 1, it is characterised in that the power output shaft Coaxially fix with the first row carrier, second planet carrier.

13. power-driven systems according to claim 1, it is characterised in that first output section For left half axle gear, second output section is right axle shaft gear；And

14. 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.

15. 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.

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

17. 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.

18. 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；

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

20. power-driven systems according to claim 19, it is characterised in that also include：

Engine；And

21. power-driven systems according to claim 1, it is characterised in that described first electronic Motor is symmetrically arranged with regard to the differential mechanism with second dynamotor.

22. power-driven systems according to claim 1, it is characterised in that also include：3rd is electric Dynamic generator, the 3rd dynamotor are arranged to link with one of input shaft.

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.