CN106555848B - Power-driven system and vehicle with it - Google Patents

Abstract

The invention discloses a kind of power-driven system and vehicles.The power-driven system includes: differential mechanism, differential mechanism includes: the 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 planetary gear, and the first planetary gear is different from the revolution-radius of the second planetary gear；Power output shaft, power output shaft are arranged to link with the power intake of differential mechanism；Multiple input shafts, each input shaft are arranged to 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 motor generators, the first and second motor generators link with the first and second output sections respectively.The differential mechanism of power-driven system of the invention realizes differential function using planet differential principle, compact-sized, simple.

Description

Power-driven system and vehicle with it

Technical field

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

Background technique

In a kind of differential art known for inventor, differential mechanism include main reducing gear driven gear (it is main subtract it is driven Gear), planetary gear, centre wheel etc., planetary gear is mounted on the subplate of driven gear by square shaft, axle sleeve, and and center Wheel engagement realizes its rotation and locomotive function with revolute pair and plane prismatic pair, and centre wheel passes through angular positioning pin and cylindrical pair Or spline and left and right two halves axis connection, achieve the purpose that output torque.This differential mechanism eliminates original differential mechanism or so shell The components such as body, planetary gear shaft use the subplate that planetary gear is directly mounted on the driven gear of main reducing gear by square shaft and axle sleeve instead On, the number of parts of differential mechanism is effectively reduced, structure is simplified, alleviates weight.

But this differential mechanism is utilized symmetrical bevel gear structure and realizes differential between wheel, just for traditional symmetrical The part of formula bevel differential is innovated, and excessive this differential design axial dimension, shell and cone tooth can not be really solved The shortcomings that taking turns big quality and reliability relative deviation.

Summary of the invention

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

For this purpose, the differential mechanism of the power-driven system utilizes planet differential the invention proposes a kind of power-driven system Principle realizes differential function, compact-sized, simple.

The invention also provides a kind of vehicles with the power drive system.

Power-driven system according to an embodiment of the present invention, comprising: differential mechanism, the differential mechanism include: first planet carrier, First planetary gear and the first gear ring, first planetary gear are arranged in the first planet carrier, first planetary gear and institute State the engagement of the first gear ring；Second planet carrier, the second planetary gear and the second gear ring, second planetary gear are arranged in second row In carrier, second planetary gear is engaged with second gear ring and second planetary gear is also nibbled with first planetary gear It closes；Wherein, first gear ring and second gear ring constitute two power output ends of the differential mechanism, first planet Frame and second planet carrier constitute the power intake of the differential mechanism, and first planetary gear and second planetary gear Revolution-radius it is different；Power output shaft, the power output shaft are arranged to join with the power intake of the differential mechanism It is dynamic；Multiple input shafts, each input shaft are arranged to link with the power output shaft；First output section and the second output Portion, first output section and first gear ring link, and second output section and second gear ring link；First is electronic Generator and the second motor generator, first motor generator and first output section are linked, the second electronic hair Motor and second output section are linked.

The differential mechanism of power-driven system according to an embodiment of the present invention realizes differential function, knot using planet differential principle Structure is compact, simple.

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

According to some embodiments of the present invention, the power output shaft and the first planet carrier, second planet carrier It is coaxial fixed.

According to some embodiments of the present invention, first output section is left half axle gear, and second output section is the right side Axle shaft gear；And

It is provided with the first external tooth on first gear ring, is provided with the second external tooth on second gear ring, outside described first Tooth is engaged with the left half axle gear, and second external tooth is engaged with the right axle shaft gear.

According to some embodiments of the present invention, power-driven system further include: engine, the engine are arranged to optional Engage to selecting property at least one of the multiple input shaft.

According to some embodiments of the present invention, it is passed between the input shaft and the power output shaft by shift gear pair It is dynamic.

According to some embodiments of the present invention, multiple fixed driven gears are fixedly installed on the power output shaft, often Fixed driving gear is fixedly installed on a input shaft, the fixed driven gear is nibbled with corresponding fixed driving gear It closes.

According to some embodiments of the present invention, the multiple input shaft includes:

First input shaft and the second input shaft, second input axle sleeve are located on first input shaft, the fixation Driving gear includes: the first fixed driving gear being fixed on the first input shaft and be fixed on the second input shaft second Fixed driving gear, the fixed driven gear include: the first fixed driven gear being fixed on the power output shaft and Second fixed driven gear, the described first fixed driven gear are engaged with the described first fixed driving gear, and described second is fixed Driven gear is engaged with the described second fixed driving gear.

According to some embodiments of the present invention, power-driven system further include:

Engine；And

Double clutch, the double clutch include: the first bonding part, the second bonding part and third bonding part, institute Third bonding part is stated to be arranged to be selectively engageable in first bonding part and second bonding part at least One, the engine is connected with the third bonding part, and first input shaft is connected with first bonding part, institute The second input shaft is stated to be connected with second bonding part.

According to some embodiments of the present invention, power-driven system further include: third motor generator, the third are electronic Generator is arranged to link with one of input shaft in the multiple input shaft.

According to some embodiments of the present invention, end face and second tooth of first gear ring towards second gear ring It encloses towards the endface of first gear ring in the same plane.

According to some embodiments of the present invention, each of first gear ring and second gear ring include:

The annular side wall portion in body panels portion and the outer periphery that the body panels portion is set, the annular side wall portion It is provided with multiple teeth on inner wall, cavity, first tooth are limited between the body panels portion and the annular side wall portion The cavity of the cavity of circle and second gear ring is toward each other to constitute installation space, the first planet carrier and the first row Star-wheel and second planet carrier and second planetary gear are accommodated in the installation space.

According to some embodiments of the present invention, first planetary gear and the thickness of second planetary gear in the axial direction is not Together.

According to some embodiments of the present invention, the gear teeth of relatively thin planetary gear and the gear teeth of thicker planetary gear are nibbled completely It closes, and the gear teeth of thicker planetary gear extend beyond the gear teeth or thicker planet of relatively thin planetary gear to side in the axial direction The gear teeth of wheel extend beyond the gear teeth of relatively thin planetary gear to two sides respectively in the axial direction.

According to some embodiments of the present invention, the revolution-radius of thicker planetary gear is less than the revolution half of relatively thin planetary gear Diameter.

According to some embodiments of the present invention, the corresponding gear ring of thicker planetary gear is small gear ring, relatively thin planetary gear pair The gear ring answered is bull gear, and the outer diameter of the bull gear is greater than the outer diameter of the small gear ring.

According to some embodiments of the present invention, the thickness of first planetary gear is greater than the thickness of second planetary gear, First gear ring is small gear ring, and second gear ring is bull gear, and the revolution-radius of first planetary gear is less than described the The revolution-radius of two planetary gears.

According to some embodiments of the present invention, the revolution of the revolution axis and second planetary gear of first planetary gear Axis is overlapped.

According to some embodiments of the present invention, first planetary gear and the second planetary gear are roller gear.

According to some embodiments of the present invention, each first planetary gear is configured with first planet wheel spindle, described Two ends of the first planet wheel spindle are connected with the first planet carrier and second planet carrier respectively, each second row Star-wheel be configured with second planet wheel spindle, two ends of second planet wheel spindle respectively with the first planet carrier and institute The second planet carrier is stated to be connected.

According to some embodiments of the present invention, the speed changer includes the first input shaft, the second input shaft and third input Axis, the third input axle sleeve are located on second input shaft, and second input axle sleeve is located on first input shaft, Pass through three clutch phases between the engine and first input shaft, second input shaft and the third input shaft Even.

According to some embodiments of the present invention, first gear ring and the near front wheel link, second gear ring and off-front wheel Linkage；

The power-driven system further include:

4th motor generator and the 5th motor generator, the 4th motor generator and left rear wheel link, and described the Five motor generators and off hind wheel link；And

Anti-skidding synchronizer, the anti-skidding synchronizer are arranged to optionally synchronize the left rear wheel and off hind wheel, thus So that the left rear wheel and the off hind wheel synchronous rotary.

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

Detailed description of the invention

Fig. 1 is the explosive view at a visual angle of differential mechanism according to an embodiment of the present invention；

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

Fig. 3 is the plan view schematic diagram of differential mechanism according to an embodiment of the present invention；

Fig. 4 is the perspective view after the assembly of differential mechanism according to an embodiment of the present invention；

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

Fig. 9 is the perspective view of the first planetary gear and the second planetary gear；

Figure 10 is the theory of engagement schematic diagram of the first planetary gear and the second planetary gear；

Figure 11 is the perspective view of the first gear ring or the second gear ring according to an embodiment of the present invention；

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

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 of further embodiment according to the present invention；

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

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

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

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

Figure 20 is the schematic diagram of the power-driven system of further embodiment according to the present invention；

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

Figure 22 is the schematic diagram of the power-driven system of further embodiment according to the present invention.

Specific embodiment

The embodiment of the present invention is described below in detail, examples of the embodiments are shown in the accompanying drawings, wherein from beginning to end Same or similar label indicates same or similar element or element with the same or similar functions.Below with reference to attached The embodiment of figure description is exemplary, it is intended to is used to explain the present invention, and is not considered as limiting the invention.

In the description of the present invention, it is to be understood that, term " center ", " longitudinal direction ", " transverse direction ", " length ", " width ", " thickness ", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom" "inner", "outside", " up time The orientation or positional relationship of the instructions such as needle ", " counterclockwise " is to be based on the orientation or positional relationship shown in the drawings, and is merely for convenience of The description present invention and simplified description, rather than the device or element of indication or suggestion meaning must have a particular orientation, with spy Fixed orientation construction and operation, therefore be not considered as limiting the invention.

In addition, term " first ", " second " are used for descriptive purposes only and cannot be understood as indicating or suggesting relative importance Or implicitly indicate the quantity of indicated technical characteristic.Define " first " as a result, the feature of " second " can be expressed or Implicitly include one or more of the features.In the description of the present invention, the meaning of " plurality " is at least two, such as two It is a, three etc., unless otherwise specifically defined.

In the present invention unless specifically defined or limited otherwise, term " installation ", " connected ", " connection ", " fixation " etc. Term shall be understood in a broad sense, for example, it may be being fixedly connected, may be a detachable connection, or integral；It can be mechanical connect It connects, is also possible to be electrically connected or can communicate with each other；It can be directly connected, can also indirectly connected through an intermediary, it can To be the interaction relationship of connection or two elements inside two elements.For the ordinary skill in the art, The specific meanings of the above terms in the present invention can be understood according to specific conditions.

In the present invention unless specifically defined or limited otherwise, fisrt feature second feature "upper" or "lower" It may include that the first and second features directly contact, also may include that the first and second features are not direct contacts but pass through it Between other characterisation contact.Moreover, fisrt feature includes the first spy above the second feature " above ", " above " and " above " Sign is right above second feature and oblique upper, or is merely representative of first feature horizontal height higher than second feature.Fisrt feature exists Second feature " under ", " lower section " and " following " include that fisrt feature is directly below and diagonally below the second feature, or is merely representative of First feature horizontal height is less than second feature.

Power-driven system 1000 according to an embodiment of the present invention, the power drive line are described in detail below with reference to accompanying drawings System 1000 can be applied in vehicle.

As shown in Figure 13-Figure 21, power-driven system 1000 according to some embodiments of the invention mainly includes differential mechanism 100, speed changer 104, the first motor generator 501 and the second motor generator 502.

It is described in detail first below according to specific structure of the illustrated embodiment to differential mechanism 100, for power drive Other constructions of system 1000 will describe after differential mechanism 100 is discussed in detail and constructs.

It is described in detail first below according to specific structure of the illustrated embodiment to differential mechanism 100, for power drive Other constructions of system 1000 will describe after differential mechanism 100 is discussed in detail and constructs.

Differential mechanism 100 according to an embodiment of the present invention is described in detail below with reference to Fig. 1-Figure 12, the differential mechanism 100 Differential or shaft space difference speed between can be used for taking turns, for for differential between taking turns, which can make driving wheels exist Vehicle turning traveling is rolled when driving with different angular speed in uneven road surface, pure to guarantee to make between two side drive wheels and ground Rolling movement.

As depicted in figs. 1 and 2, differential mechanism 100 according to some embodiments of the invention may include first planet carrier 11, One planetary gear 12 and the first gear ring 13 and the second planet carrier 21, the second planetary gear 22 and the second gear ring 23.

In conjunction with the embodiment of Fig. 1 and Fig. 2, first planet carrier 11 and the second planet carrier 21 are it is so structured that circular plate Structure can reduce the axial dimension of differential mechanism 100 to a certain extent in this way.In some embodiments, first planet carrier 11 It can be split type structure with the second planet carrier 21, since the molding of independent widget is relatively easy, by 11 He of first planet carrier Second planet carrier 21, which is individually processed, can simplify manufacturing process, improves machining accuracy.

Such as Fig. 3 is simultaneously combined shown in Fig. 1, Fig. 2 and Fig. 9, and the first planetary gear 12 is arranged in first planet carrier 11, for example, often A first planetary gear 12 is configured with first planet wheel spindle 14 (shown in Fig. 9), and two ends of the first planet wheel spindle 14 are distinguished It is rotatably supported in first planet carrier 11 and the second planet carrier 21, two ends of such as the first planet wheel spindle 14 can pass through axis It holds and is rotatably supported in the axis hole to correspond to each other on first planet carrier 11 and the second planet carrier 21, at this time the first planetary gear 12 are securable on corresponding first planet wheel spindle 14.Certainly, two ends of the first planet wheel spindle 14 and first planet carrier 11 Be also possible to be fixedly connected with the second planet carrier 22, for example, the first planet wheel spindle 14 two ends respectively with first planet carrier 11 and second the axis hole that corresponds to each other on planet carrier 22 be welded and fixed, the first planetary gear 12 is rotatably sleeved on corresponding at this time On first planet wheel spindle 14, such as the first planetary gear 12 can be rotatably mounted around on the first planet wheel spindle 14 by bearing. The purpose of connection first planet carrier 11 and the second planet carrier 21 may be implemented by the first planet wheel spindle 14 as a result, so that First planet carrier 11 and the second planet carrier 21 keep movement (i.e. first planet carrier 11 and the second planet carrier 21 synchronized, in the same direction It is dynamic).And this connection type is used, first planet carrier 11 and the second planet carrier 21 can be well to the first planet wheel spindles 14 Support/fix, the first planet wheel spindle 14 is prevented to be disconnected with single planet carrier and differential mechanism 100 is caused to fail.

First planetary gear 12 is engaged with the first gear ring 13, concretely internal messing form, i.e. the first planetary gear 12 is located at the The inside of one gear ring 13 and with the tooth engagement on the first gear ring 13.First planetary gear 12 is preferably several, and circumferentially etc. between Away from being distributed in the inside of the first gear ring 13, for example, as a preferred embodiment, the first planetary gear 12 can be three, and Interval angles are 120 ° between two the first planetary gears 12 of arbitrary neighborhood.

Similarly, such as shown in Fig. 3 and combination Fig. 1, Fig. 2 and Fig. 9, 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, two ends of such as the second planet wheel spindle 24 can lead to It crosses bearing and is rotatably supported in the axis hole to correspond to each other on first planet carrier 11 and the second planet carrier 21, at this time the second row Star-wheel 22 is securable on corresponding second planet wheel spindle 24.Certainly, two ends of the second planet wheel spindle 24 and the first planet What frame 11 and the second planet carrier 22 were also possible to be fixedly connected, for example, the second planet wheel spindle 24 two ends respectively with the first row The axis hole to correspond to each other in carrier 11 and the second planet carrier 22 is welded and fixed, and the second planetary gear 22 is rotatably sleeved on pair at this time On the second planet wheel spindle 24 answered, such as the second planetary gear 22 can be rotatably mounted around the second planet wheel spindle 24 by bearing On.The purpose that connection first planet carrier 11 and the second planet carrier 21 may be implemented by the second planet wheel spindle 24 as a result, to make It obtains first planet carrier 11 and the second planet carrier 21 keeps movement synchronized, in the same direction.And use this connection type, first planet carrier 11 and second planet carrier 21 well the second planet wheel spindle 24 can support/fix, prevent the second planet wheel spindle 24 with Single planet carrier is disconnected and differential mechanism 100 is caused to fail.

In addition, in other embodiments of the invention, in order to keep first planet carrier 11 and the second planet carrier 21 can At the same speed, it moves, can also be directly fixedly connected with first planet carrier 11 with the second planet carrier 21 by intermediate member, also in the same direction It is to say, synchronized, the in the same direction movement of first planet carrier 11 and the second planet carrier 21 can be through the first planet in above example Wheel shaft 14 and the second planet wheel spindle 24 are realized, and the embodiment directly can realize the first planet by setting intermediate member The movement synchronized, in the same direction of frame 11 and the second planet carrier 21, such as the intermediate member can be located at first planet carrier 11 and the second row It is welded and fixed between carrier 21 and respectively with first planet 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 22 is located at the The inside of two gear rings 23 and with the tooth engagement on the second gear ring 23.Second planetary gear 22 is preferably several, and circumferentially etc. between Away from being distributed in the inside of the second gear ring 23, for example, as a preferred embodiment, the second planetary gear 22 can be three, and Interval angles are 120 ° between two the second planetary gears 22 of arbitrary neighborhood.

Wherein, it should be noted that Fig. 3 is the plan view schematic diagram according to the differential mechanism 100 of the embodiment of the present invention, wherein Schematically show the meshing relation and the first planetary gear 12 and first between the first planetary gear 12 and the second planetary gear 22 The meshing relation of gear ring 13, the second planetary gear 22 and the second gear ring 23, since Fig. 3 is plan view, and at the same time showing above-mentioned Three kinds of meshing relations, therefore the relative positional relationship of each component is only illustrative, and is not offered as or implies the reality of each component Space layout position.

It is in multiple embodiments in the first planetary gear 12 and the second planetary gear 22, it is preferable that multiple first planetary gears 12 and multiple second planetary gears 22 respectively correspondingly engage.For example, as shown in fig. 1, fig. 2 and fig. 8, the first planetary gear 12 and second Planetary gear 22 is three, then first the first planetary gear 12 can be engaged with corresponding first the second planetary gear 22, and second First planetary gear 12 can be engaged with corresponding second the second planetary gear 22, and the first planetary gear 12 of third can be with corresponding third A second planetary gear 22 engages, and there is the first planetary gear 12 and the second planetary gear 22 that multiple groups are engaged with each other in this way, in differential mechanism 100 transmission power when, power multiple groups correspond to each other engagement the first planetary gear 12 and the second planetary gear 22 between transmitting will more Add and stablizes, is reliable.

In addition, being another multiple embodiments, multiple first planets in the first planetary gear 12 and the second planetary gear 22 Wheel 12 and the circumferentially alternating arrangement of multiple second planetary gears 22, and the first planetary gear 12 and the second planetary gear 22 of arbitrary neighborhood Engagement.That is, in this embodiment, multiple first planetary gears 12 and the circumferentially alternating arrangement of multiple second planetary gears 22 are simultaneously An annular is formed, two the second planetary gears 22 engagement adjacent thereto of each first planetary gear 12, similarly, each Second planetary gear 22, two the first planetary gears 12 engagement all adjacent thereto.

Wherein, referring to the embodiment of Fig. 3, the revolution axes O of the revolution axes O of the first planetary gear 12 and the second planetary gear 22 It is overlapped.

Particularly, as shown in Fig. 1-Fig. 3, Fig. 8-Figure 10, the first planetary gear 12 engages cooperation with the second planetary gear 22.Change speech It is not only engaged with the first gear ring 13 for the first planetary gear 12, while also being engaged with the second planetary gear 22, for It for second planetary gear 22, not only engages with the second gear ring 23, while also being engaged with the first planetary gear 12.

As shown in figure 3, the first gear ring 13 and the second gear ring 23 may be constructed two power output ends of differential mechanism 100, the One planet carrier 11 and the second planet carrier 21 then correspond to the power intake for constituting differential mechanism 100 (for example, first planet carrier 11 at this time Can be rigidly connected with the second planet carrier 21), the power of such external power supply output can be from 11 He of first planet carrier The input of second planet carrier 21 can be exported from the first gear ring 13 and the second gear ring 23 respectively after the differential action of differential mechanism 100. At this point, first planet carrier 11 and the second planet carrier 21 can connect the power such as engine, motor as optional embodiment Source, the first gear ring 13 and the second gear ring 23 can be connected by gear transmission structure and corresponding semiaxis, semiaxis again with corresponding vehicle Wheel is connected, but not limited to this.

Differential between taking turns is applied to the differential mechanism 100 below, the first gear ring 13 and the second gear ring 23 constitute differential mechanism 100 Simple declaration is poor for the power intake of power output end, first planet carrier 11 and the second planet carrier 21 composition differential mechanism 100 The working principle of fast device 100, wherein the first gear ring 13 can be connected by external tooth with left half axle at this time, left half axle can be with left side wheel It is connected, the second gear ring 23 can be connected by external tooth with right axle shaft, and right axle shaft can be connected with right side wheels, power source such as engine And/or the power of motor output can be by exporting after the decelerating effect of main reducing gear to first planet carrier 11 and the second planet carrier 21.If vehicle driving is turned on smooth road surface and not at this time, theoretically revolving speed is identical for left side wheel and right side wheels, at this time Differential mechanism 100 does not play differential action, and first planet carrier 11 and the second planet carrier are 21 synchronized, rotate in same direction, the first gear ring 13 and the Two gear rings 23 are synchronized, rotate in same direction, the first planetary gear 12 and the second planetary gear 22 revolution, not rotations.If vehicle driving at this time It is travelled on the road surface of out-of-flatness or vehicle turning, theoretically revolving speed is different for left side wheel and right side wheels, 13 He of the first gear ring The revolving speed of second gear ring 23 is also different, that is, there is rotational speed difference, and the first planetary gear 12 and the second planetary gear 22 are in the same of revolution at this time When also rotation, the first planetary gear 12 and the second planetary gear 22 from the change of team so that one in the first gear ring 13 and the second gear ring 23 Speedup, another deceleration, the rotational speed difference of the gear ring of the gear ring and deceleration of speedup is the rotational speed difference of left and right wheels, to realize difference Speed effect.

Differential mechanism 100 according to an embodiment of the present invention utilizes planet differential principle as a result, in structure and type of attachment overhead Between utilization rate it is higher, axial dimension is smaller, and production and fit on it is more advantageous.Such structure type not only can be with Avoid angular wheel axially and radially on dimensional defects, additionally can preferably using master subtract in driven gear inside Preferably space utilization rate is realized in empty space, greatly facilitates the arrangement of 100 assembly of differential mechanism and big to weight Small limitation, while also having higher reliability and more preferably transmission efficiency, be conducive to improve the reliable of power chain Property and it is excessively curved when power output fluency, this for symmetrical bevel differential have more practicability.

Particularly, the first planetary gear 12 is different from the revolution-radius of the second planetary gear 22, i.e., shown in Figure 3, the first row The revolution-radius of star-wheel 12 refers to the first planetary gear 12 around the radius R1 of revolution axes O revolution, the revolution of the second planetary gear 22 Radius refers to the second planetary gear 22 around radius R2, shown in Figure 3, the R1 ≠ R2 of revolution axes O revolution, such as R2 > R1.That is, The revolution track of first planetary gear 12 and the second planetary gear 22 is staggered radially.In example of the invention, the first row The revolution-radius of star-wheel 12 is relatively small, and the revolution-radius of the second planetary gear 22 is relatively large.

Since the first planetary gear 12 is different with the revolution-radius of the second planetary gear 22, in some embodiments, first The internal diameter of gear ring 13 and the internal diameter of the second gear ring 23 are also different, the small planetary gear of revolution-radius (such as first Planetary gear 12) corresponding gear ring internal diameter it is smaller, i.e. the relatively small small gear ring (such as the first gear ring 13) of respective radius is public The radial dimension for turning the corresponding gear ring of the biggish planetary gear of radius (such as second planetary gear 22) is larger, i.e., respective radius is biggish Bull gear (such as the second gear ring 23), this makes bull gear 23 and small gear ring 13 be staggered radially, is avoided gear ring and planetary gear etc. Movement interference occurs between moving component, to effectively reduce the axial gap of the first gear ring 12 and the second gear ring 22, such as joins According to Fig. 3, Fig. 5-Fig. 6, which is D, by reducing axial gap D, so that the axial dimension of differential mechanism 100 is more It is small, more compact structure.

The construction of the first gear ring 13 and the second gear ring 23 is described in detail in conjunction with specific embodiments below.

In some embodiments of the invention, the first gear ring 13 and the second gear ring 23 are symmetrical structure, in other words, the first tooth Circle 13 and the second gear ring 23 are symmetrical arranged, and can be increased the versatility of gear ring in this way, be reduced cost.

Referring to Fig. 5 and referring to figs. 1 and 2, the first gear ring 13 towards the second gear ring 23 end face B1 (referring to Fig. 2) and The end face B2 (referring to Fig.1) of second gear ring 23 towards the first gear ring 13 is in same plane B3 (referring to Fig. 5), in other words, should In embodiment, as shown in figure 5, end face B1, end face B2 are in plane B3 simultaneously, i.e., it is overlapped with B3, thus the first gear ring 13 and second the clearance D in the axial direction of gear ring 23 be zero (as shown in Figure 5), the axial direction of differential mechanism 100 can be greatly reduced in this way Size, makes that the volume of differential mechanism 100 is more small and exquisite, more compact structure, facilitates the arrangement of entire power drive system.

In another embodiment, as shown in fig. 7, radius relatively small one in the first gear ring 13 and the second gear ring 23 Gear ring such as small gear ring 13 are at least partially embedded in the biggish gear ring of radius size such as bull gear 23, at this time the first gear ring 13 It is understood that be negative with the clearance D of the second gear ring 23 in the axial direction, thus equally can reduce the axial dimension of differential mechanism 100, The components in two gear rings can preferably be protected by the first gear ring 13 and the second gear ring 23 simultaneously.

Optionally, of course, referring to shown in Fig. 6, the first gear ring 13 and the second gear ring 23 can also be staggered in the axial direction and between D at a certain distance.It is understood that it is single for reducing this angle of 100 axial dimension of differential mechanism, between Fig. 5 embodiment Gap D is zero and the clearance D of Fig. 7 embodiment is negative and is an advantage over (clearance D of Fig. 6 embodiment is positive) of Fig. 6 embodiment.

It should be noted that the clearance D of above-mentioned Fig. 3 and combination Fig. 1-Fig. 2, Fig. 5-Fig. 7 refer to the ring of the first gear ring 13 The distance between shape sidewall portion 162 and the annular side wall portion 162 of the second gear ring 23.For example, see the reality of Fig. 1-Fig. 3, Fig. 5-Fig. 7 Example is applied, the first gear ring 13 and the second gear ring 23 all include body panels portion 161 and annular side wall portion 162.

And in other embodiments of the invention, in the embodiment such as referring to Figure 11 and Figure 12, the first gear ring 13 and Each of two gear rings 23 still further comprise annular flange portion 163, and annular flange portion 163 is from the end of annular side wall portion 162 Extend away from the direction in body panels portion 161, in the embodiment in figure 11, the internal diameter of annular flange portion 163 can be with annular The outer diameter of sidewall portion 162 is generally equalized, and such annular flange portion 163 is diametrically opposed to be protruded outward in annular side wall portion 162 (i.e. the outer peripheral surface of the first gear ring 13 or the second gear ring 23).And in the fig. 12 embodiment, 163 outer diameter of annular flange portion can be with ring The outer diameter of shape sidewall portion 162 is generally equalized, and the internal diameter of annular flange portion 163 can be greater than the internal diameter of annular side wall portion 162, That is 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, Fig. 1-Fig. 3, Fig. 5-Fig. 7 embodiment gear ring structure in, between two gear ring between Gap D refers to the gap between the annular side wall portion 162 of two gear rings.And the gear ring structure in Figure 11 and Figure 12 embodiment, two Clearance D between a gear ring refers to the gap between the annular flange portion 163 of two gear rings.

For the embodiment of small gear ring insertion bull gear, such as Fig. 1-Fig. 2 and as shown in connection with fig. 3, the first gear ring 13 and second Each of gear ring 23 includes: the annular side wall portion in body panels portion 161 with the outer periphery that body panels portion 161 is arranged in 162, body panels portion 161 and annular side wall portion 162 can be integrated molding component.It is set on the inner wall of annular side wall portion 162 Multiple gear teeth are equipped with, wherein it is shown in Figure 4, the relatively small gear ring of radius such as the first gear ring 13 (i.e. small gear ring 13) Annular side wall portion 162 is at least partially embedded the ring of the relatively large gear ring of radius such as the second gear ring 23 (i.e. bull gear 23) In shape sidewall portion 162.

It certainly, can also be using the gear structure in Figure 11-Figure 12, example for the embodiment of small gear ring insertion bull gear If bull gear is using the gear ring structure in Figure 11 or Figure 12, i.e., bull gear has annular flange portion 163, and small gear ring then can be used The common gear ring structure (do not have annular flange portion 163) of Fig. 1-Fig. 3 embodiment, the annular side wall portion 162 of small gear ring can be at this time It is at least partially embedded in the annular flange portion of bull gear.Alternatively, small gear ring and bull gear can be using in Figure 11 and Figure 12 Gear ring structure, the annular flange portion 163 of small gear ring can be at least partially embedded in the annular flange portion of bull gear at this time, but It is without being limited thereto.

Although this is simultaneously further, it is to be appreciated that above-mentioned give the embodiment of several small gear ring insertion bull gears Non- is a kind of limitation to the scope of the present invention, and those skilled in the art are after having read specification above content, sufficiently The embedding principle for understanding gear ring, can make similar modification to above-mentioned small gear ring and/or bull gear, this equally falls in structure Enter within protection scope of the present invention.

It is shown in Figure 3, cavity A1, A2 (referring to Fig. 3) is limited between body panels portion 161 and annular side wall portion 162, Specifically, cavity A1, the second gear ring 23 are limited between the body panels portion 161 and annular side wall portion 162 of the first gear ring 13 Body panels portion 161 and annular side wall portion 162 between limit cavity A2, cavity A1 and the second gear ring in the first gear ring 13 Cavity A2 in 23 toward each other to constitute installation space A (referring to Fig. 3), wherein first planet carrier 11 and the first planetary gear 12 with And second planet carrier 21 and the second planetary gear 22 be accommodated in installation space A, such first gear ring 13 and the second gear ring 23 serve as The function of external shell can be protected and be accommodated in planet carrier and planetary gear therein, and the service life is improved.And the first gear ring 13 of cooperation End face B1 and the second gear ring 23 end face B2 is concordant or the fit dimension at least partially embedded size of lesser small gear ring 13 compared with The embodiment of big bull gear 23, can make installation space A comparatively close, and it is empty that external sundries is not easily accessible installation Between influence moving component in A, ensure that the steady operation of differential mechanism 100.

The first row star-wheel 12 and the meshing relation of the second planetary gear 22 are described in detail in conjunction with specific embodiments below.

In an embodiment of the present invention, the first planetary gear 12 it is different from the thickness of the second planetary gear 22 in the axial direction (referring to Figure 10), there is certain help to the diminution of 100 axial dimension of differential mechanism in this way.Further, relatively thin planetary gear such as the second planetary gear The gear teeth of 22 gear teeth planetary gear at a fully engaged and thicker with the gear teeth of thicker planetary gear such as the first planetary gear 12 are in axial direction On the gear teeth of relatively thin planetary gear are extended beyond to side, or the gear teeth of thicker planetary gear prolong to two sides respectively in the axial direction Stretch the gear teeth beyond relatively thin planetary gear.In example of the invention, the gear teeth of thicker planetary gear are in the axial direction only to side The gear teeth of relatively thin planetary gear are extended beyond, such as in conjunction with shown in Fig. 9 and Figure 10, the first thicker planetary gear 12 extends to the left Beyond the second relatively thin planetary gear 22, the right side of the right side of the first thicker planetary gear 12 and the second relatively thin planetary gear 22 It can be generally flush with substantially, be conducive to the control to 100 axial dimension of differential mechanism in this way.

Due to the implementation different, different for planetary gear thickness with the revolution-radius of the second planetary gear 22 of the first planetary gear 12 Example, the revolution-radius of thicker planetary gear such as the first planetary gear 12 are less than the revolution of relatively thin planetary gear such as the second planetary gear 22 Radius.Also, the thicker planetary gear such as corresponding gear ring of the first planetary gear 12 is the lesser small gear ring of radial dimension such as the first tooth Circle 13, the relatively thin planetary gear such as corresponding gear ring of the second planetary gear 22 are the relatively large bull gear of radial dimension such as the second gear ring 23, the outer diameter (outer surface) of bull gear 23 is greater than the outer diameter (outer surface) of small gear ring 13.Such as in example of the invention, first The thickness of planetary gear 12 is greater than the thickness of the second planetary gear 22, so that thicker corresponding first gear ring 13 of the first planetary gear 12 is Small gear ring, relatively thin corresponding second gear ring 23 of the second planetary gear 22 are bull gear, and the revolution-radius of the first planetary gear 12 Less than the revolution-radius of the second planetary gear 22.

In addition, it should be noted that, the lesser planetary gear of revolution-radius is engaged with the relatively small gear ring of radius, this When, the lesser planetary gear of revolution-radius is the relatively thick planetary gear of thickness, a part of the planetary gear be with radius relatively The interior tooth engagement of a small gear ring, another part is that the planetary gear i.e. relatively thin with the biggish planetary gear of revolution-radius engages 's.

As optional embodiment, the internal diameter of bull gear 23 is greater than the outer diameter of small gear ring 13, bull gear 23 here Internal diameter refers to the radial dimension of the outside circle of 23 internal tooth of bull gear, in other words, the tooth top diameter of a circle of the internal tooth of bull gear 23 It is greater than the outer diameter of small gear ring 13.Gear ring 13 small in this way can be that is, above-mentioned integrally or at least part insertion bull gear 23 Axial gap D be reduced into negative (i.e. small gear ring 13 be embedded in bull gear 23), thus i.e. two kinds of planetary gears will not for two gear rings Movement interference or swiping occurs, increases the stability of differential mechanism 100 in this way, while inner space can also be made relatively more to seal It closes, protects the components such as internal planet carrier and planetary gear.

The power intake to differential mechanism 100 and power output end are described in detail in conjunction with specific embodiments below.

In conjunction with shown in Fig. 1-Fig. 3, differential mechanism 100 further includes differential input shaft 31,32 and differential output shaft 41,42, Differential input shaft 31,32 is connected with first planet carrier 11 and the second planet carrier 21 respectively, such as in the example of fig. 3, the first row The right side of carrier 11 is connected with a differential input shaft 31, and it is defeated that the left side of the second planet carrier 21 is connected with another 32 differential mechanism Enter axis.Differential output shaft 41,42 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 tooth The right side of circle 13 is connected with a differential output shaft 41, and the left side of the second gear ring 23 is connected with another differential output shaft 42.Differential input shaft 31,32, the 41,42, first gear ring 13 of differential output shaft and the second gear ring 23 can be coaxially arranged.

Further, as shown in figure 3, differential input shaft includes: the first differential input shaft 31 and the input of the second differential mechanism Axis 32, the first differential input shaft 31 are connected with first planet carrier 11, the second differential input shaft 32 and 21 phase of the second planet carrier Even, differential output shaft may include: the first differential output shaft 41 and the second differential output shaft 42, the output of the first differential mechanism Axis 41 is connected with the first gear ring 13, and the second differential output shaft 42 is connected with the second gear ring 23,31 He of the first differential input shaft Second differential input shaft 32 and the first differential output shaft 41 and the second differential output shaft 42 can be hollow shaft structure, It is wherein used as preferred embodiment, the first differential output shaft 41 is coaxially set on the first differential input shaft 31, the Two differential output shafts 42 are coaxially set on the second differential input shaft 32, and thus 100 structure of differential mechanism is more compact, body Product is smaller.

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

According to some embodiments of the present invention, the first planetary gear 12 and the second planetary gear 22 are roller gear, compared to biography Unite symmetrical bevel differential, it is more compact using 100 structure of differential mechanism of roller gear, specifically, its in structure and Space utilization rate is higher in type of attachment, and axial dimension is smaller, and more advantageous in production and fit on.

It is briefly described referring to the specific structure of 1- Fig. 3 differential mechanism 100 for implementing to exemplify.- Fig. 3 institute referring to Fig.1 Show, multiple first planet wheel spindles 14 and multiple second planet wheel spindles are provided between first planet carrier 11 and the second planet carrier 21 24, the first planetary gear 12 is multiple and is correspondingly connected on the first planet wheel spindle 14, and the second planetary gear 22 is multiple and corresponding company It connects on the second planet wheel spindle 24.The second bigger than the thickness of the second planetary gear 22, relatively thin row of the thickness of first planetary gear 12 The gear teeth of star-wheel 22 and the gear teeth of the first thicker planetary gear 12 are at a fully engaged, and the gear teeth of the first thicker planetary gear 12 can be to the left Side extends beyond the second relatively thin planetary gear 22.Thicker corresponding first gear ring 13 of the first planetary gear 12 is small gear ring, relatively thin Corresponding second gear ring 23 of the second planetary gear 22 be bull gear, the end face B1 of small gear ring 13 can locate with the end face B2 of bull gear 23 In the same plane, so that the axial gap D of small gear ring 13 and bull gear 23 is zero, make the installation cavity A in two gear rings Relatively more close.

To sum up, differential mechanism 100 according to an embodiment of the present invention, using the planetary gear of roller gear form, in structure and Space utilization rate is higher in type of attachment, and axial dimension is smaller, and more advantageous in production and fit on.The compact is poor Fast device 100 is also by making the displacement of side planetary gear and gear ring realize the evacuation in two sides planetary gear mechanism space and size (i.e. The revolution-radius of planetary gear is different), such structure design has been greatly saved spatially as the corresponding another group of planet of evacuation The axial gap of wheel and gear ring, so that the axial dimension of the compact differential mechanism 100 is smaller and more compact.

Differential mechanism 100 according to an embodiment of the present invention has been discussed in detail above, it below will be to power-driven system 1000 Remaining structure is described in detail.

Referring to Fig.1 shown in 3- Figure 21, speed changer 104 may include multiple input shafts 101,102 and power output shaft 103. In some embodiments, the power output shaft 103 of speed changer 104 can be one, but not limited to this.Power output shaft 103 is set It is set to and links with the power intake of differential mechanism 100, i.e., power output shaft 103 is arranged to and first planet carrier 11 and the second planet Frame 21 links.Each input shaft is all provided with to be set to and link with power output shaft 103, in other words, any one as shown in Figure 13-Figure 21 The rotation of a input shaft then power output shaft 103 also follow movement or power output shaft 103 to rotate then these input shafts are also therewith Movement.

As shown in Figure 14-Figure 15, third motor generator 401 is arranged to link with one of input shaft.Such as in Figure 14 Example in, third motor generator 401 and the first input shaft 101 link.And in the example of fig. 15, third motor generator 401 and second input shaft 102 link.

For the kind of drive of input shaft 101,102 and power output shaft 103, can using traditional shift gear pair into Row transmission.

For example, multiple fixed driven gear 107a, 107b are fixedly installed on power output shaft 103, on each input shaft Be fixedly installed fixed driving gear (for example, the first fixed driving gear 106 and second fixed driving gear 105), it is fixed from Moving gear is engaged with corresponding fixed driving gear.

Such as referring to the example of Figure 13-Figure 21, fixed driven gear 107a engages a pair of of gear of composition with fixed driving gear 105 Position gear pair, fixed driven gear 107b are engaged with fixed driving gear 106 and are constituted another pair gear pair.It is appreciated that this two It is different to the transmission speed ratio of gear pair, therefore the speed changer 104 in the embodiment has the transmission gear there are two different speed ratios, this The structure of sample power-driven system 1000 is relatively easy, compact, and also can satisfy normal vehicle operation to transmission speed ratio It is required that.

As shown in Figure 13-Figure 21, multiple input shafts include the first input shaft 101 and the second input shaft 102, the first input shaft 101 can be solid shafting, and the second input shaft 102 can be hollow shaft, and the second input shaft 102 is set on the first input shaft 101, If the second input shaft 102 coaxially covers on the first input shaft 101, the axial length of the first input shaft 101 is greater than the second input One end such as right end of the axial length of axis 102, 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 fixing driving gear includes First fixed driving gear 106 and the second fixed driving gear 105, it is defeated that the first fixed driving gear 106 is fixed at first Enter on axis 101, the second fixed driving gear 105 is fixed on the second input shaft 102.Accordingly, fixed driven gear packet The first fixed fixed driven gear 107a of driven gear 107b and second is included, the first fixed driven gear 107b and first is fixed to be led Moving gear 106 engages, and the second fixed driven gear 107a is engaged with the second fixed driving gear 105.

Referring to shown in Figure 14, Figure 16-Figure 19, third motor generator 401 and the first input shaft 101 link, such as third electricity Dynamic generator 401 is linked by gear structure and the first fixed driving gear 106, and concretely third motor generator 401 is logical It crosses gear 402, gear 403 and the first fixed driving gear 106 to be driven, can be obtained by the number of teeth of reasonable design said gear Transmission speed ratio needed for obtaining third motor generator 401.

And in the example of fig. 15, third motor generator 401 passes through gear structure and the second fixed driving gear 105 Dynamic, concretely third motor generator 401 is fixed actively by gear 402, gear 403, gear 404, gear 405 and second Gear 105 is driven, and middle gear 404 and gear 405 can be fixed on same axis 406, passes through reasonable design said gear The number of teeth can obtain third motor generator 401 needed for transmission speed ratio.

Further, power-driven system 1000 can also include engine 301, and engine 301 is arranged to optionally Engaged at least one of multiple input shafts, specifically, input shaft is two, and engine 301 and two input shafts it Between be provided with double clutch 204.Double clutch 204 includes: the first bonding part 201, the second bonding part 202 and third engagement Part 203, wherein the first bonding part 201 and the second bonding part 202 can be two driven discs of double clutch 204, the Three bonding parts 203 can be the shell of double clutch 204, and at least one of two driven discs are selectively engageable shell Body, that is to say, that engage third at least one of the first bonding part 201 and the second bonding part 202 property of can choose Bonding part 203.Certainly, two driven discs can also be all off with shell, i.e. the first bonding part 201 and the second joint portion 202 are divided to be in an off state with third bonding part 203.

Referring to Figure 13-Figure 21, engine 301 is connected with third bonding part 203, and the first input shaft 101 is engaged with first Part 201 is connected, and the second input shaft 102 is connected with the second bonding part 202.In this way, the power that engine 301 generates can pass through Double clutch 204 and selectively export to the first input shaft 101, the second input shaft 102.

It referring to Figure 13-Figure 21 and combines shown in Fig. 1-Figure 12, as a preferred embodiment of the present invention mode, power is defeated Shaft 103 and first planet carrier 11 and the second planet carrier 21 are coaxial fixed, so that the company of speed changer 104 and differential mechanism 100 Socket part point is more compact, i.e., the axis 103 that directly outputs power coaxially is fixed with two planet carriers, thus at least can be in certain journey Reduce the volume of power-driven system 1000 on degree.

In a further embodiment, as shown in Figure 13-Figure 21, power-driven system 1000 further includes the first output section 601 With the second output section 602, the first output section 601 and the first gear ring 13 link, and the second output section 602 and the second gear ring 23 link. Further, the first output section 601 is left half axle gear, and the second output section 602 is right axle shaft gear, while on the first gear ring 13 It is provided with the first external tooth 603, the second external tooth 604 is provided on the second gear ring 23, the first external tooth 603 is nibbled with left half axle gear 601 It closes, the second external tooth 604 is engaged with right axle shaft gear 602, and the power thus through differential mechanism 100 can finally pass through left half axle gear 603 and right axle shaft gear 604 output to the left and right sides wheel.

Wherein, as shown in Figure 13-Figure 21, the first motor generator 501 is arranged to link with the first output section 601, the Two motor generators 502 are arranged to link with the second output section 602, can set on such as motor shaft of the first motor generator 501 It is equipped with gear 503, gear 503 is engaged with left half axle gear 601, while being provided on the motor shaft of the second motor generator 502 Gear 504, gear 504 are engaged with right axle shaft gear 602.

Referring to shown in Figure 13-Figure 21, the first motor generator 501 and the second motor generator 502 are left about differential mechanism 100 It is right symmetrical, the center of gravity of power-driven system 100 can be made in center or closer to center in this way.

The embodiment of 0 Figure 21 referring to fig. 2, in the power-driven system 1000 and Figure 13-Figure 19 embodiment in the embodiment The main distinction of power-driven system 1000 be: the quantity of input shaft.In some embodiments, input shaft includes the One input shaft 101, the second input shaft 102 and third input shaft 1003, third input shaft 1003 can be hollow shaft and be set in On second input shaft 102, the second input shaft 102 is also possible to hollow shaft and is set on the first input shaft 101, three input shafts It can be coaxially arranged.Lead between engine 301 and the first input shaft 101, the second input shaft 102 and third input shaft 1003 Cross three clutches 205 be connected, specifically, three clutches 205 have the first driven disc 206, the second driven disc 207, third from Moving plate 208 and shell 209, shell 209 optionally with the first driven disc 206, the second driven disc 207, third driven disc 208 At least one of engagement, the first input shaft 101 connect with the first driven disc 206, the second input shaft 102 and the second driven disc 207 connections, third input shaft 1003 are connect with third driven disc 208, and engine 301 is connect with shell 209.The embodiment of Figure 20 In, the first driven disc 206, the second driven disc 207, third driven disc 208 are axially distributed, in the embodiment of Figure 21, first from Moving plate 206, the second driven disc 207, third driven disc 208 are radially distributed.

The typical condition of power-driven system 1000 according to an embodiment of the present invention is briefly described below with reference to Figure 14.

Low speed pure electric vehicle: double clutch 204 is all off, the first motor generator 501 and the second motor generator 502 with Motor mode works external direct output power.Power transfer path is shorter under the mode, and transmission energy loss is small, is suitble to city City's congestion road conditions.

High speed pure electric vehicle: double clutch 204 is all off, the first motor generator 501,502 and of the second motor generator The whole external output powers that work of third motor generator 401.

Low engine speed gear: the first bonding part 201 is engaged with third bonding part 203, the second bonding part 202 and the Three bonding parts 203 disconnect, and the power that engine 301 generates at this time passes through defeated after the first input shaft 101, power output shaft 103 Out to differential mechanism 100, power is distributed to the driving wheel of two sides by differential mechanism 100.

High engine speeds gear: the second bonding part 202 is engaged with third bonding part 203, the first bonding part 201 and the Three bonding parts 203 disconnect, and the power that engine 301 generates at this time passes through defeated after the second input shaft 102, power output shaft 103 Out to differential mechanism 100, power is distributed to the driving wheel of two sides by differential mechanism 100.

Brake energy recovery: when the vehicle is braked, the first motor generator 501, the second motor generator 502 and third electricity Dynamic generator 401 all recycles braking energy.

Driving power generation: one in the first bonding part 201 and the second bonding part 202 connects with third bonding part 203 Close, a part of power that engine 301 generates can drive the first motor generator 501 and the second motor generator 502 generate electricity or Person drives third motor generator 401 to generate electricity, and can also drive three electric power generations simultaneously certainly, and at the same time, engine 301 produces Raw another part power externally exports, and drives vehicle driving.

The main distinction of Figure 13 embodiment and Figure 14 embodiment is to eliminate third motor generator 401, for remaining Construction portion is then consistent, and which is not described herein again.

For the embodiment of Figure 16-Figure 19, compared with Figure 14 embodiment, difference is to increase rear-guard differential lock.

It 6- Figure 19 and combines shown in Fig. 1-Figure 13 referring to Fig.1, the first gear ring 13 links with the near front wheel, passes through the first external tooth 603 and left half axle gear 601 and the near front wheel link, the second gear ring 23 links with off-front wheel, if the second gear ring 23 is by outside second Tooth 604 and right axle shaft gear 602 and off-front wheel link.4th motor generator 901 is joined by gear structure and left rear wheel 910c Dynamic, such as the 4th motor generator 901 is linked by gear W1, W2, W3, W4 and left rear wheel 910c, gear W1 and the 4th electronic hair Motor 901 is coaxially connected, and gear W1 is engaged with gear W2, and gear W2 is coaxially connected with gear W3, and gear W3 is engaged with gear W4, Gear W4 can be fixedly installed on left half axle 904, and left rear wheel 910c is provided on left half axle 904.Similarly, the 5th dynamoelectric and power generation Machine 902 is linked by gear structure and off hind wheel 910d, and such as the 5th motor generator 902 passes through gear X1, X2, X3, X4 and the right side Rear-wheel 910d linkage, gear X1 with the 5th motor generator 902 is coaxial is connected, gear X1 is engaged with gear X2, gear X2 and tooth Wheel X3 is coaxially connected, and gear X3 is engaged with gear X4, and gear X4 can be fixedly installed on right axle shaft 905, is arranged on right axle shaft 905 There is off hind wheel 910d.

In the example of Figure 16, anti-skidding synchronizer 903 is arranged for synchromesh gear W4 and gear X4, such as anti-skidding synchronization Device 903 is arranged on gear W4 and is used for engage gear X4.In the example of Figure 17, anti-skidding synchronizer 903 is arranged for together Gear W1 and gear X1 is walked, such as anti-skidding synchronizer 903 is arranged on gear W1 and is used for engage gear X1.In the example of Figure 18 In, anti-skidding synchronizer 903 is arranged for synchromesh gear W2 and gear X2, such as anti-skidding synchronizer 903 is arranged on gear W2 And it is used for engage gear X2.

In the example of Figure 19, anti-skidding synchronizer 903 is arranged for synchronous left half axle 904 and right axle shaft 905, such as anti-skidding Synchronizer 903 is arranged on left half axle 904 and for engaging right axle shaft 905, the 4th motor generator 901 and the in the embodiment Five motor generators 902 are wheel motor.

To sum up, anti-skidding synchronizer 903 is arranged to optionally synchronize left rear wheel 910c and off hind wheel 910d, in other words, When anti-skidding synchronizer 903 is in engagement state, left rear wheel 910c and off hind wheel 910d revolve synchronous rotary that is, at the same speed, in the same direction Turn, left rear wheel 910c and off hind wheel 910d will not differential rotation at this time.And when anti-skidding synchronizer 903 is in an off state, the Four motor generators 901 can be operated alone left rear wheel 910c, and the 5th motor generator 902 can be operated alone off hind wheel 910d, and two A rear-wheel is mutually indepedent, non-interference, to realize the differential rotating function of wheel.

In addition, for technical solution described in the various embodiments described above and/or technical characteristic, do not conflict with each other, not phase In mutual contradictory situation, those skilled in the art can be by the technical solution and/or technical characteristic progress phase in above-described embodiment Mutually combination, the technical solution after combination can be the superposition of two or more technical solutions, two or more technologies The superposition of feature or two or more technical solutions are superimposed with technical characteristic, and thus, it is possible to realize each technical solution And/or the interaction and support of technical characteristic each other functionally, and the scheme after combination is imitated with more superior technology Fruit.

For example, those skilled in the art can by the first gear ring 13 towards the second gear ring 23 end face and 23 direction of the second gear ring The scheme that the end face of first gear ring 13 is in the same plane is combined with the scheme of the first gear ring 13 and the construction of the second gear ring 23, So that the axial gap of 100 liang of gear rings of differential mechanism is zero, so that two gear rings can limit the installation space of relative closure, It adequately protects to the component in installation space, increases its service life, and reduce cost, while differential can also be effectively reduced The axial dimension of device 100.

For another example, the thickness of the first planetary gear 12 can be greater than the scheme of the thickness of the second planetary gear 22 by those skilled in the art With revolution-radius that the first gear ring 13 is small gear ring, the scheme that the second gear ring 23 is bull gear and the first planetary gear 12 less than the The scheme of the revolution-radius of two planetary gears 22 is combined, and the structure for 100 scheme of differential mechanism being consequently formed is more compact, volume It is smaller, it is more convenient for being arranged in inside the enging cabin of vehicle.

For another example, those skilled in the art can by the first gear ring 13 towards the second gear ring 23 end face and 23 direction of the second gear ring The side of the meshing relation of scheme and relatively thin planetary gear and thicker planetary gear that the end face of first gear ring 13 is in the same plane Case combination, thus on the one hand making the axial gap of 100 liang of gear rings of differential mechanism is zero, so that two gear rings can limit opposite envelope The installation space closed adequately protects to the component in installation space, increases its service life, and reduce cost, another party Face can also further reduce the axial dimension of differential mechanism 100, and differential mechanism 100 is made to have smaller volume.

However, it is to be understood that above-mentioned illustrating is only illustrative, it is special for technical solution and/or technology The combination of sign, those skilled in the art can be freely combined in the absence of conflict, and the scheme after combination has More superior technical effect, the present invention have only made above-mentioned multiple exemplary simple declarations, no longer exhaustive one by one herein.

Further it will be understood that the technical solution after said combination is equally fallen under the scope of the present invention.

Generally speaking, differential mechanism 100 according to an embodiment of the present invention, can effectively save space, and reduce weight, tool For body, for this planet gear type differential mechanism 100 compares traditional bevel gear differential, weight can be reduced about 30%, while axial dimension about reduces 70%, can not only reduce the frictional force of bearing, and can be realized left and right wheels Torque distribution is distributed the load of differential mechanism 100 more reasonable, and 100 rigidity of differential mechanism is more preferable, additionally due to using Cylinder Gear Wheel, transmission efficiency is also increased, such as traditional Bevel Gear Drive efficiency of 6 class precisions and 7 class precisions is about 0.97 ~0.98, and the column gear transmission efficiency of 6 class precisions and 7 class precisions is about 0.98~0.99, furthermore uses roller gear, also The operating noise of differential mechanism 100 is reduced, while reducing calorific value, substantially increases the service life of differential mechanism 100.In short, Differential mechanism 100 according to an embodiment of the present invention have lightweight, small size, at low cost, transmission efficiency is high, low noise, fever it is small, Many advantages, such as service life is high.

Simultaneously as differential mechanism 100 according to an embodiment of the present invention can save sun gear, and saving sun gear can have It has the following advantages:

It is analyzed from mechanics, cancel sun gear but gear ring is utilized to realize differential, because the number of teeth of gear ring compares sun gear What be can be set is more, while pitch circle is larger (pitch circle refers to a pair of circle tangent at node when gear engaged transmission), from And can be more balanced distributed load and bear torque, this is good to the raising in the service life of differential mechanism 100.Do not have simultaneously Sun gear can preferably realize the lubrication and cooling of differential mechanism 100, that is to say, that due to eliminating sun gear, planet Wheel the inside can form cavity, and it is to belong to the relationship of internal messing (sun gear belongs to outside with planetary gear that gear ring engage with planetary gear Engagement), lubricating oil can be stored in gear ring, thus cooling and lubricant effect can greatly improve.In addition, due to cancelling sun gear, Reduce components, reduce the quality and cost of differential mechanism 100, differential mechanism 100 is made to become more miniaturization, lightweight.

And for the power-driven system 1000 with differential mechanism 100 according to an embodiment of the present invention, mainly exist Spatially and in driving method there is obvious advantage, by taking space advantage as an example, the power-driven system 1000 is especially suitable For new energy vehicle, since the power assembly of new energy vehicle is typically located in enging cabin, power assembly not only has Speed changer, also has at least one motor at engine simultaneously, since enging cabin space is limited, using according to the present invention The compact differential mechanism 100 of embodiment can spatially obtain advantage, easily facilitate arrangement.For another example, in a driving manner For advantage, since the axial dimension of differential mechanism 100 according to an embodiment of the present invention greatly reduces, the more preferable cloth of axial space It sets, and differential mechanism 100 tool can be better achieved as power output end there are two gear ring and be connected by power with two motors (external tooth by gear ring as mentioned above connects motor), and this is difficult to realize on traditional circular cone differential mechanism.

Vehicle 10000 according to an embodiment of the present invention is briefly described below, as shown in figure 22, which includes upper The power-driven system 1000 in embodiment is stated, which can be used for forerunner, naturally it is also possible to after being used for It drives, the present invention is not particularly limited this.It should be understood that other constructions of vehicle 10000 according to an embodiment of the present invention Such as braking system, driving system, steering system etc. have been the prior art, and are well known to those skilled in the art, therefore Here it no longer repeats one by one.

In the description of this specification, reference term " one embodiment ", " some embodiments ", " example ", " specifically show The description of example " or " some examples " etc. means specific features, structure, material or spy described in conjunction with this embodiment or example Point is included at least one embodiment or example of the invention.In the present specification, schematic expression of the above terms are not It must be directed to identical embodiment or example.Moreover, particular features, structures, materials, or characteristics described can be in office What can be combined in any suitable manner in one or more embodiment or examples.In addition, those skilled in the art can say this Different embodiments or examples described in bright book are engaged and are combined.

Although the embodiments of the present invention has been shown and described above, it is to be understood that above-described embodiment is example Property, it is not considered as limiting the invention, those skilled in the art within the scope of the invention can be to above-mentioned Embodiment is changed, modifies, replacement and variant.

Claims (22)

1. a kind of power-driven system characterized by comprising

Differential mechanism, the differential mechanism include:

First planet carrier, the first planetary gear and the first gear ring, first planetary gear is arranged in the first planet carrier, described First planetary gear 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, described Second planetary gear is engaged with second gear ring and second planetary gear is also engaged with first planetary gear；

Wherein, first gear ring and second gear ring constitute two power output ends of the differential mechanism, the first row Carrier and second planet carrier constitute the power intake of the differential mechanism, and first planetary gear and second planet The revolution-radius of wheel is different；

Power output shaft, the power output shaft are arranged to link with the power intake of the differential mechanism；

Multiple input shafts, each input shaft are arranged to link with the power output shaft；

First output section and the second output section, first output section and first gear ring link, second output section with The second gear ring linkage；

First motor generator and the second motor generator, first motor generator and first output section are linked, institute It states the second motor generator and second output section is linked.

2. power-driven system according to claim 1, which is characterized in that first gear ring is towards second gear ring End face and second gear ring towards the endface of first gear ring in the same plane.

3. power-driven system according to claim 2, which is characterized in that in first gear ring and second gear ring Each include:

The annular side wall portion in body panels portion and the outer periphery that the body panels portion is set, the inner wall of the annular side wall portion It is provided with multiple teeth on face, cavity is limited between the body panels portion and the annular side wall portion, first gear ring The cavity of cavity and second gear ring is toward each other to constitute installation space, the first planet carrier and first planetary gear And second planet carrier and second planetary gear are accommodated in the installation space.

4. power-driven system according to claim 1, which is characterized in that first planetary gear and second planet The thickness of wheel in the axial direction is different.

5. power-driven system according to claim 4, which is characterized in that the gear teeth of relatively thin planetary gear and thicker row The gear teeth of star-wheel are at a fully engaged, and the gear teeth of thicker planetary gear extend beyond the wheel of relatively thin planetary gear to side in the axial direction The gear teeth of tooth or thicker planetary gear extend beyond the gear teeth of relatively thin planetary gear to two sides respectively in the axial direction.

6. power-driven system according to claim 4, which is characterized in that the revolution-radius of thicker planetary gear be less than compared with The revolution-radius of thin planetary gear.

7. power-driven system according to claim 4, which is characterized in that the corresponding gear ring of thicker planetary gear is small tooth Circle, the corresponding gear ring of relatively thin planetary gear are bull gear, and the outer diameter of the bull gear is greater than the outer diameter of the small gear ring.

8. power-driven system according to claim 4, which is characterized in that the thickness of first planetary gear is greater than described The thickness of second planetary gear, first gear ring are small gear ring, and second gear ring is bull gear, the public affairs of first planetary gear Turn the revolution-radius that radius is less than second planetary gear.

9. power-driven system according to claim 1, which is characterized in that the revolution axis of first planetary gear and institute The revolution axis for stating the second planetary gear is overlapped.

10. power-driven system according to claim 1, which is characterized in that first planetary gear and the second planetary gear It is roller gear.

11. power-driven system according to claim 1, which is characterized in that each first planetary gear is configured with one A first planet wheel spindle, two ends of first planet wheel spindle respectively with the first planet carrier and second planet carrier It is connected, each second planetary gear is configured with second planet wheel spindle, and two ends of second planet wheel spindle are distinguished It is connected with the first planet carrier and second planet carrier.

12. power-driven system according to claim 1, which is characterized in that the power output shaft and the first row Carrier, second planet carrier are coaxially fixed.

13. power-driven system according to claim 1, which is characterized in that first output section is left half axle gear, Second output section is right axle shaft gear；And

Be provided with the first external tooth on first gear ring, be provided with the second external tooth on second gear ring, first external tooth with The left half axle gear engagement, second external tooth are engaged with the right axle shaft gear.

14. power-driven system according to claim 1, which is characterized in that further include: engine, the engine are set It is set to and is selectively engageable at least one of the multiple input shaft.

15. power-driven system according to claim 1, which is characterized in that the input shaft and the power output shaft Between pass through shift gear auxiliary driving.

16. power-driven system according to claim 15, which is characterized in that be fixedly installed on the power output shaft Multiple fixed driven gears, are fixedly installed fixed driving gear on each input shaft, the fixed driven gear with it is right The fixation driving gear engagement answered.

17. power-driven system according to claim 16, which is characterized in that the multiple input shaft includes:

First input shaft and the second input shaft, second input axle sleeve are located on first input shaft, the fixed active Gear includes: the first fixation driving gear being fixed on the first input shaft and the second fixation being fixed on the second input shaft Driving gear, the fixed driven gear include: the first fixed driven gear and second being fixed on the power output shaft Fixed driven gear, the described first fixed driven gear are engaged with the described first fixed driving gear, and second fixation is driven Gear is engaged with the described second fixed driving gear.

18. power-driven system according to claim 17, which is characterized in that further include:

Engine；And

Double clutch, the double clutch include: the first bonding part, the second bonding part and third bonding part, and described Three bonding parts are arranged to be selectively engageable at least one of first bonding part and second bonding part, The engine is connected with the third bonding part, and first input shaft is connected with first bonding part, and described Two input shafts are connected with second bonding part.

19. power-driven system according to claim 1, which is characterized in that further include: third motor generator, it is described Third motor generator is arranged to link with one of input shaft in the multiple input shaft.

20. power-driven system according to claim 1, which is characterized in that the power-driven system further includes speed change Device and engine, the speed changer include the first input shaft, the second input shaft and third input shaft, and the third input shaft is arranged On second input shaft, second input axle sleeve is located on first input shaft, the engine and described first It is connected between input shaft, second input shaft and the third input shaft by three clutches.

21. power-driven system according to claim 1, which is characterized in that first gear ring and the near front wheel link, institute It states the second gear ring and off-front wheel links；

The power-driven system further include:

4th motor generator and the 5th motor generator, the 4th motor generator and left rear wheel link, the 5th electricity Dynamic generator and off hind wheel link；And

Anti-skidding synchronizer, the anti-skidding synchronizer are arranged to optionally synchronize the left rear wheel and off hind wheel, so that The left rear wheel and the off hind wheel synchronous rotary.

22. a kind of vehicle, which is characterized in that including power-driven system described according to claim 1 any one of -21.