CN106553534B - Power-driven system and vehicle with it - Google Patents

Power-driven system and vehicle with it Download PDF

Info

Publication number
CN106553534B
CN106553534B CN201510626301.XA CN201510626301A CN106553534B CN 106553534 B CN106553534 B CN 106553534B CN 201510626301 A CN201510626301 A CN 201510626301A CN 106553534 B CN106553534 B CN 106553534B
Authority
CN
China
Prior art keywords
gear
power
planet carrier
gear ring
driven system
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN201510626301.XA
Other languages
Chinese (zh)
Other versions
CN106553534A (en
Inventor
杨冬生
廉玉波
张金涛
罗红斌
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BYD Co Ltd
Original Assignee
BYD Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by BYD Co Ltd filed Critical BYD Co Ltd
Priority to CN201510626301.XA priority Critical patent/CN106553534B/en
Publication of CN106553534A publication Critical patent/CN106553534A/en
Application granted granted Critical
Publication of CN106553534B publication Critical patent/CN106553534B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Landscapes

  • Retarders (AREA)

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 connect with the first and second planet carriers respectively, first and second planetary gears are engaged with the first and second gear rings respectively, and the second planetary gear is also engaged with the first planetary gear；Input unit, input unit, first planet carrier and the second planet carrier coaxial linkage；Power output shaft, power output shaft are arranged to link with input unit；Multiple input shafts, one of input shaft in multiple input shafts optionally link with power output shaft, remaining input shaft is arranged to and power output shaft links；First and second motor generators, the first motor generator and the first gear ring link, and the second motor generator and the second gear ring link.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 connect with the first planet carrier, first planetary gear with it is described The engagement of first gear ring；Second planet carrier, the second planetary gear and the second gear ring, second planetary gear and second planet carrier connect It connecing, second planetary gear is engaged with second gear ring and second planetary gear is also engaged with first planetary gear, In, first gear ring and second gear ring constitute two power output ends of the differential mechanism；Input unit, the input Portion, the first planet carrier and second planet carrier is coaxially arranged and the input unit and the first planet carrier and described the The linkage of two planet carriers；Power output shaft, the power output shaft are arranged to link with the input unit；Multiple input shafts, it is described One of input shaft in multiple input shafts is arranged to optionally link with the power output shaft, remaining is described defeated Enter axis to be arranged to link with the power output shaft；First motor generator and the second motor generator, the first electronic hair Motor and first gear ring link, and second motor generator and second gear ring link.
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, 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, power output shaft output gear is provided on the power output shaft, it is described Power output shaft output gear and input unit engaged transmission.
According to some embodiments of the present invention, the power output shaft output gear and the input unit constitute main deceleration Device, wherein the power output shaft output gear is configured to main reducing gear driving gear, the input unit is configured to main reducing gear Driven gear.
According to some embodiments of the present invention, the power output shaft overhead set is provided with empty set driven gear, the sky It covers driven gear and one of input shaft links, the power-driven system further includes synchronizer, and the synchronizer is set It is set to for synchronizing the power output shaft and the empty set driven gear.
According to some embodiments of the present invention, the synchronizer is arranged on the power output shaft and is used to engage described Empty set driven gear.
According to some embodiments of the present invention, fixed driven gear is fixedly installed on the power output shaft, it is described solid Determine driven gear and remaining described input shaft links.
According to some embodiments of the present invention, the power output shaft overhead set is provided with empty set driven gear and fixation Be provided with fixed driven gear, the power-driven system further includes synchronizer: the synchronizer is arranged for synchronizing described Power output shaft and the empty set driven gear；
Fixed driving gear is fixedly installed on each input shaft, the empty set driven gear and the fixation are driven Gear is engaged with corresponding fixed driving gear respectively.
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.
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, it is provided with the first external tooth on the outer peripheral surface of first gear ring, described second The second external tooth is provided on the outer peripheral surface of gear ring, first motor generator and first external tooth link, second electricity Dynamic generator and second external tooth link.
According to some embodiments of the present invention, first motor generator is with second motor generator about described Differential mechanism bilateral symmetry is distributed.
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.
According to some embodiments of the present invention, first planetary gear partially weighs in the axial direction with second planetary gear It is folded.
According to some embodiments of the present invention, first planetary gear includes: the first teeth portion and the second teeth portion, and described second Planetary gear includes: third teeth portion and the 4th teeth portion, and first teeth portion is engaged with first gear ring, second teeth portion and institute It states third teeth portion to correspond to overlapping in the axial direction and engage cooperation, the 4th teeth portion is engaged with second gear ring.
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, first gear ring and second gear ring are symmetrical structure, described first Each of 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, the input unit is configured to input end gear, the input end gear construction For annular and it is set in first gear ring and second gear ring outer surface.
According to some embodiments of the present invention, it is provided with gap between first gear ring and second gear ring, it is described Input end gear surround and covers the gap.
According to some embodiments of the present invention, power-driven system further include: intermediate connection structure, the intermediate connection knot Structure is used to the first planet carrier, second planet carrier being connected to the input unit, and the intermediate connection structure includes: the One connecting bracket and the second connecting bracket, first connecting bracket are used to connect the first planet carrier and the input unit, Second connecting bracket is for connecting second planet carrier and the input unit, wherein first connecting bracket and described Each of second connecting bracket includes:
Central body portion and extension arm, the extension arm are outer peripheral surfaces multiple and that the central body portion is arranged in On, the multiple extension arm is centered on the central body portion and radially distributes, wherein the adjutage portion is used for It is connected with the input unit.
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 revolution of the revolution-radius of first planetary gear and second planetary gear Radius is identical.
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, the power-driven system including above-described embodiment.
Detailed description of the invention
Fig. 1 is the explosive view 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 perspective view of differential mechanism according to an embodiment of the present invention；
Fig. 4 is the plan view schematic diagram of differential mechanism according to an embodiment of the present invention；
Fig. 5 is the perspective view of differential mechanism according to an embodiment of the present invention, wherein the second planet carrier and the second gear ring is not shown Deng；
Fig. 6 is the mesh schematic representation of the first planetary gear and the second planetary gear；
Fig. 7 is the theory of engagement schematic diagram of the first planetary gear and the second planetary gear；
Fig. 8 is the perspective view of the first gear ring or the second gear ring according to an embodiment of the present invention；
Fig. 9 is the perspective view of the first gear ring or the second gear ring in accordance with another embodiment of the present invention；
Figure 10 is the schematic diagram of power-driven system according to an embodiment of the invention；
Figure 11 is the schematic diagram of power-driven system in accordance with another embodiment of the present invention；
Figure 12 is the schematic diagram of the power-driven system of further embodiment according to the present invention；
Figure 13 is the schematic diagram of the power-driven system of further embodiment according to the present invention；
Figure 14 is the schematic diagram of the power-driven system of further embodiment according to 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 vehicle according to an embodiment of 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 10-Figure 16, 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 503.
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-Fig. 9, 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 shown in Figure 1, differential mechanism 100 according to some embodiments of the invention may include first planet 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 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. 1-Fig. 2 and as shown in connection with fig. 6, the first planetary gear 12 is arranged in first planet carrier 11, for example, each first Planetary gear 12 is configured with first planet wheel spindle 14, and two ends of the first planet wheel spindle 14 are rotatably supported in the respectively On one planet carrier 11 and the second planet carrier 21, two ends of such as the first planet wheel spindle 14 can be rotatably supported by bearing In the axis hole to correspond to each other in first planet carrier 11 and the second planet carrier 21, the first planetary gear 12 is securable to corresponding at this time On first planet wheel spindle 14.Certainly, two ends of the first planet wheel spindle 14 and first planet carrier 11 and the second planet carrier 21 May be a fixed connection, for example, the first planet wheel spindle 14 two ends respectively with first planet carrier 11 and the second planet carrier 21 On the axis hole that corresponds to each other be welded and fixed, the first planetary gear 12 is rotatably sleeved on corresponding first planet wheel spindle 14 at this time On, such as the first planetary gear 12 can be rotatably mounted around on the first planet wheel spindle 14 by bearing.Pass through the first row as a result, The purpose of connection first planet carrier 11 and the second planet carrier 21 may be implemented in spider gear shaft 14, so that first planet carrier 11 and the Two planet carriers 21 keep movement synchronized, in the same direction (i.e. first planet carrier 11 and the linkage of the second planet carrier 21), and use this company Mode is connect, first planet carrier 11 and the second planet carrier 21 can support/fix to the first planet wheel spindle 14, be prevented well First planet wheel spindle 14 is disconnected with single planet carrier and differential mechanism 100 is caused to fail.Referring to figure 1 and figure 2, the first row Star-wheel 12 is engaged with the first gear ring 13, concretely internal messing form, i.e. the first planetary gear 12 is located at the inside of the first gear ring 13 And with the tooth engagement on the first gear ring 13.First planetary gear 12 is preferably several, and circumferentially equidistantly distributed in the first tooth 13 inside of circle, for example, as a preferred embodiment, the first planetary gear 12 can be three, and two of arbitrary neighborhood Interval angles are 120 ° between first planetary gear 12.
Such as Fig. 1-Fig. 2 and as shown in connection with fig. 6, the second planetary gear 22 is arranged on the second planet carrier 21, for example, each second Planetary gear 22 is configured with second planet wheel spindle 24, and such as two ends of the second planet wheel spindle 24 can be can be rotated by bearing Ground is supported in the axis hole to correspond to each other on first planet carrier 11 and the second planet carrier 21, and the second planetary gear 22 is securable at this time On corresponding second planet wheel spindle 24.Certainly, two ends of the second planet wheel spindle 24 and first planet carrier 11 and the second planet What frame 21 was also possible to be fixedly connected, for example, the second planet wheel spindle 24 two ends respectively with first planet carrier 11 and the second row The axis hole to correspond to each other in carrier 21 is welded and fixed, and the second planetary gear 22 is rotatably sleeved on corresponding second planetary gear at this time On axis 24, such as the second planetary gear 22 can be rotatably mounted around on the second planet wheel spindle 24 by bearing.As a result, by the The purpose of connection first planet carrier 11 and the second planet carrier 21 may be implemented in two planet wheel spindles 24, so that first planet carrier 11 Movement synchronized, in the same direction is kept with the second planet carrier 21, and uses this connection type, first planet carrier 11 and the second planet carrier 21 can support/fix to the second planet wheel spindle 24 well, and the second planet wheel spindle 24 is prevented to be detached from single planet carrier It connects 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 in the same direction, it not only can be real by the way of above by the first planet wheel spindle 14 and/or the second planet wheel spindle 24 It is existing, while can also be directly fixedly connected with first planet carrier 11 with the second planet carrier 21 by intermediate connection structure 6, Huo Zhetong Shi Caiyong planet wheel spindle connect first planet carrier 11 and the second planet carrier 21 with intermediate connection structure 6, and about centre connection knot The specific configuration of structure 6 will be discussed in more detail below.
Referring to figure 1 and figure 2, the second planetary gear 22 is engaged with the second gear ring 23, concretely internal messing form, i.e., and Two planetary gears 22 be located at the inside of the second gear ring 23 and with the tooth engagement on the second gear ring 23.Second planetary gear 22 is preferably more It is a, and circumferentially equidistantly distributed is in 23 inside of the second gear ring, for example, as a preferred embodiment, the second planet Wheel 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. 4 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. 4 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 Figure 1, Figure 2 and shown in Fig. 5, 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.
Wherein, referring to the embodiment of Fig. 4, the revolution axes O of the revolution axes O of the first planetary gear 12 and the second planetary gear 22 It is overlapped, and revolution-radius (the i.e. central axis distance revolution axes O of planetary gear of the first planetary gear 12 and the second planetary gear 22 Distance) it is identical.
Particularly, as shown in Fig. 1-Fig. 2, Fig. 4-Fig. 7, 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 Figure 1-Figure 4, the first gear ring 13 and the second gear ring 23 may be constructed two power outputs of differential mechanism 100 End, first planet carrier 11 and the second planet carrier 21 then correspond to the power intake for constituting differential mechanism 100, such as of the invention one In a embodiment, first planet carrier 11, the second planet carrier 21 link with input unit 3, in other words, input unit 3, first planet carrier 11 Motion state with the second planet carrier 21 is identical (i.e. synchronized, movement in the same direction).As preferred embodiment, input unit 3, First planet carrier 11 and the second planet carrier 21 are coaxially arranged.The power of external power supply output in this way can be inputted from input unit 3, be passed through It can be exported respectively from the first gear ring 13 and the second gear ring 23 after crossing the differential action of differential mechanism 100.
Below to briefly describe the working principle of differential mechanism 100 between the differential mechanism 100 is applied to wheel for differential, at this time the One gear ring 13 can be connected with left half axle, and left half axle can be connected with left side wheel, and the second gear ring 23 can be connected with right axle shaft, right axle shaft It can be connected with right side wheels, after power source such as engine and/or the power of motor output can be by the decelerating effects of main reducing gear Output to input unit 3, input unit 3 drives first planet carrier 11 and 21 synchronous rotary of the second planet carrier.If vehicle driving exists at this time It smooth road surface and does not turn, theoretically revolving speed is identical for left side wheel and right side wheels, and differential mechanism 100 does not play differential work at this time With, first planet carrier 11 and the second planet carrier it is 21 synchronized, rotate in same direction, the first gear ring 13 and the second gear ring are 23 synchronized, turn in the same direction It is dynamic, the first planetary gear 12 and the second planetary gear 22 revolution, not rotations.If road surface or vehicle of the vehicle driving in out-of-flatness at this time Turning driving, theoretically revolving speed is different for left side wheel and right side wheels, and the revolving speed of the first gear ring 13 and the second gear ring 23 is not yet Together, that is, there is rotational speed difference, at this time also rotation while revolution of the first planetary gear 12 and the second planetary gear 22, the first planetary gear 12 With the second planetary gear 22 from the change of team so that speedup, another deceleration in the first gear ring 13 and the second gear ring 23, speedup Gear ring and the rotational speed difference of gear ring of deceleration be the rotational speed difference of left and right wheels, to realize differential action.
To sum up, differential mechanism 100 according to an embodiment of the present invention utilizes planet differential principle, 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.
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.
- Fig. 2 and Fig. 6-Fig. 7 is combined referring to Fig.1, the first planetary gear 12 and the second planetary gear 22 are on an axial direction (left side in Fig. 6-Fig. 7 Right direction) on partly overlap, that is to say, that the first planetary gear 12 only overlaps with the second planetary gear 22, part in addition Be staggered, the part part that can be engaged with each other, and be staggered of the first planetary gear 12 and the overlapping of the second planetary gear 22 then can with it is respective Gear ring engagement.
Specifically, in conjunction with shown in Fig. 6 and Fig. 7, the first planetary gear 12 may include the first teeth portion 151 and the second teeth portion 152 (using K2 dotted line in Fig. 7 as line of demarcation), the second planetary gear 22 may include third teeth portion 153 and the 4th teeth portion 154 (in Fig. 7 K1 dotted line is line of demarcation), the second teeth portion 152 and third teeth portion 153 constitute lap, i.e. the second teeth portion 152 and third teeth portion 153 overlappings corresponding in the axial direction and engagement cooperation, the first teeth portion 151 and the 4th teeth portion 154 be staggered in the axial direction and with it is respectively right The gear ring engagement answered, i.e., the first teeth portion 151 is engaged with the first gear ring 13, and the 4th teeth portion 154 is engaged with the second gear ring 23.
As a result, the axial dimension of differential mechanism 100 is more compact, the volume of differential mechanism 100 is more compact, is conducive to differential The installation of device 100, arrangement.
According to some embodiments of the present invention, the number of teeth of the first gear ring 13 is equal with the number of teeth of the second gear ring 23, the first row The number of teeth of star-wheel 12 is equal with the number of teeth of the second planetary gear 22.
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.
The structure of the first gear ring 13 and the second gear ring 23 is described in detail combined 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.
Specifically, as Figure 1-Figure 2, each of the first gear ring 13 and the second gear ring 23 include: body panels The annular side wall portion 162 in portion 161 and the outer periphery that body panels portion 161 is set, body panels portion 161 and annular side wall portion 162 can be integrated molding component.Multiple gear teeth, body panels portion 161 and ring are provided on the inner wall of annular side wall portion 162 Cavity A1, A2 are limited between shape sidewall portion 162, i.e. between the body panels portion 161 and annular side wall portion 162 of the first gear ring 13 Cavity A1 is limited, limits cavity A2 (such as Fig. 4) between the body panels portion 161 and annular side wall portion 162 of the second gear ring 23, The cavity A2 in cavity A1 and the second gear ring 23 in first gear ring 13 toward each other to constitute installation space A (such as Fig. 4), wherein First planet carrier 11 and the first planetary gear 12 and the second planet carrier 21 and the second planetary gear 22 are accommodated in installation space A, this Sample makes the structure of differential mechanism 100 relatively more compact, and it is smaller to occupy volume, it is easier to arrange, while the first gear ring 13 and the Two gear rings 23 serve as the function of external shell, can protect and be accommodated in planet carrier and planetary gear therein, improve the service life.In addition, The installation space A that first gear ring 13 and the second gear ring 23 are limited comparatively is closed, and external sundries is not easily accessible installation Moving component is influenced in the A of space, ensure that the steady operation of differential mechanism 100.
The specific configuration of input unit 3 is described in detail in conjunction with specific embodiments below.
According to some embodiments of the present invention, input unit 3 is configured to input end gear.Further, as shown in Figure 1-Figure 3, Input end gear 3 is configured to annular (tooth of the input end gear 3 is formed on outer peripheral surface) and is set in 13 He of the first gear ring The outer surface of second gear ring 23, it is to be understood that the internal diameter of input end gear 3 can be greater than the first gear ring 13 and second The outer diameter of gear ring 23, in this way by by 3 sets of the input end gear outsides in the first gear ring 13 and the second gear ring 23, so that being located at two The component of a gear ring inner, which is not exposed from, to be come, and the component of gear ring inner is protected.
As shown in connection with fig. 4, the first gear ring 13 and the second gear ring 23 are provided with clearance D in the axial direction, that is to say, that the first tooth Circle 13 is separated from each other in the axial direction with the second gear ring 23, not fits closely.To those skilled in the art, due to The width of the engaging portion of one planetary gear 12 and the second planetary gear 22 determine to a certain extent the clearance D size (in addition, The thickness for extending arm 63 can also determine the clearance D, this will be described hereinafter, here first only with the engagement of two planetary gears 22 Partial width determines to illustrate for clearance D), i.e. the width of the engaging portion of the first planetary gear 12 and the second planetary gear 22 can be with It is equal with the minimum value of the clearance D, therefore by the width of control the first planetary gear 12 and 22 engaging portion of the second planetary gear, it can To indirectly control the size of the clearance D, to those skilled in the art, guaranteeing the first planetary gear 12 and the second planetary gear It, can be by the first row under the premise of 22 are capable of the service life of stable delivery power and the first planetary gear 12 and the second planetary gear 22 The relative narrower of the width setting of the engaging portion of star-wheel 12 and the second planetary gear 22, can effectively reduce the clearance D in this way, make The axial dimension for obtaining differential mechanism 100 is smaller, more compact, is easy to arrange.
Further, input end gear 3 surround and covers the clearance D.As a result, the closure of installation space A is more preferable, outside Portion's sundries is more difficult to enter in installation space A and influence moving component, further ensures the steady operation of differential mechanism 100, together When can also save the axial space and radial space of differential mechanism at least to a certain extent.
In addition, input end gear 3 is main retarder driven gearwheel as preferred embodiment.Thus, it is possible to preferably Using the main space for subtracting driven gear inner hollow, realizes preferably space utilization rate, greatly facilitate 100 assembly of differential mechanism Arrangement and limitation to weight size.
It should be noted that the clearance D of above-mentioned Fig. 4 (in conjunction with Fig. 1-Fig. 2) refers to the annular side wall portion of the first gear ring 13 162 and second gear ring 23 the distance between annular side wall portion 162.For example, see the embodiment of Fig. 1, Fig. 2 and Fig. 4, the first tooth Circle 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 Fig. 8 and Fig. 9, the first gear ring 13 and second Each of gear ring 23 still further comprises annular flange portion 163, and annular flange portion 163 is from the end face of annular side wall portion 162 Extend to the direction far from body panels portion 161, in the embodiment in fig. 8, the internal diameter of annular flange portion 163 can be with annular sidewall The outer diameter in portion 162 is generally equalized, and such annular flange portion 163 is equivalent to radially protrudes outward annular side wall portion 162 (i.e. The outer peripheral surface of one gear ring 13 or the second gear ring 23).And in the embodiment in fig. 9,163 outer diameter of annular flange portion can be with annular sidewall The outer diameter in 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, It says, 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, the clearance D in the gear ring structure of Fig. 1, Fig. 2 and Fig. 4 embodiment, between two gear ring Refer to the gap between the annular side wall portion 162 of two gear rings.And the gear ring structure in Fig. 8 and Fig. 9 embodiment, two gear ring Between clearance D refer to two gear rings annular flange portion 163 between gap.
For the clearance D, the engaging width of two planetary gears mentioned above can determine the big of clearance D to a certain extent Small, at the same time, the thickness for extending arm 63 also determines the size of clearance D to a certain extent.Specifically, in two rows When the engaging width of star-wheel is equal with the thickness of arm 63 is extended, the size of the clearance D can be with the engaging width of two planetary gears Or the thickness of extension arm 63 is generally equalized.And when the thickness for extending arm 63 is greater than the engaging width of two planetary gears, The size of the clearance D can be generally equalized with the thickness of extension arm 63.And in less than two planetary gears of thickness for extending arm 63 Engaging width when, the size of the clearance D can be generally equalized with the engaging width of two planetary gears.
Intermediate connection structure 6 is described in detail below with reference to specific embodiment.
As depicted in figs. 1 and 2, the effect of intermediate connection structure 6 is for connecting first planet carrier 11, the second planet carrier 21 It is connected to input unit 3, enables first planet carrier 11, the second planet carrier 21 and 3 coaxial linkage of input unit.In addition, intermediate connection Structure 6 can also be fixedly connected with first planet carrier 11, the second planet carrier 21 respectively, and the input unit 3 is fixed on centre and connects The outer surface of binding structure 6, can equally enable first planet carrier 11, the second planet carrier 21 and 3 coaxial linkage of input unit.
For the specific configuration of intermediate connection structure 6, The present invention gives a kind of feasible embodiments, this is not certainly Indicate or imply that intermediate connection structure 6 of the invention can only be using the structure in the embodiment.That is, will be situated between in following example The intermediate connection structure 6 to continue is only a kind of feasible embodiment, is not a kind of limitation to the scope of the present invention.
Specifically, referring to figure 1 and figure 2, the input unit 3 in the embodiment is the input end gear 3 of annular, and centre connects Binding structure 6 includes the first connecting bracket 61 and the second connecting bracket 62, and the first connecting bracket 61 is for connecting first planet carrier 11 With input unit 3 (i.e. input end gear 3), the second connecting bracket 62 is for connecting the second planet carrier 21 and 3 (i.e. input terminal of input unit Gear 3), wherein the structure of the first connecting bracket 61 and the second connecting bracket 62 can be identical, and each may each comprise: in Heart body part 64 and extension arm 63 (in conjunction with Fig. 5), wherein the central body portion of the first connecting bracket 61 and the second connection branch The central body portion of frame 62 can be into a single integrated structure, to form a shared central body portion 64, but not limited to this.
As shown in connection with fig. 5, extend on the outer peripheral surface that arm 63 is multiple and centrally disposed body part 64, multiple adjutages Portion 63 and central body portion 64 can be integral structure, but not limited to this.During multiple extension arms 63 with central body portion 64 are It the heart and substantially radially distributes, in the example of hgure 5, extending arm 63 is three and equidistantly distributed.Extend arm 63 to use It is connected in input unit 3, specifically, it is driven that the outer end of extension arm 63 may extend to for example annular main reducing gear of input unit 3 It is fixed at the inner peripheral surface of gear and with inner circumferential surface.
Each group of the first planetary gear 12 being engaged and the second planetary gear 22 be located at two adjacent extension arms 63 it Between, such as in the example of hgure 5, extending arm 63 is three, this three extension arms 63 limit three accommodating chambers (per adjacent Two inner peripheral surfaces for extending arms 63 and input end gear 3 limit an accommodating chamber), it can be set one in each accommodating chamber To the first planetary gear 12 and the second planetary gear 22 of engagement, so that the overall structure of differential mechanism 100 is more compact, makes simultaneously Differential mechanism 100 center of gravity closer to or be located at center, substantially improve when differential mechanism 100 runs at high speed due to eccentric or The eccentric larger situations such as cause 100 fluctuation of service of differential mechanism, service life low.
In a further embodiment, as shown in Figure 3 and Figure 4, the first gear ring 13 can coaxially be connected with the first output shaft 41, the second gear ring 23 can coaxially be connected with the second output shaft 42.As shown in Figure 2 and Figure 4, while first planet carrier 11 is coaxial Ground is connected with first planet carrier axis 111, and the second planet carrier 21 is coaxially connected with the second planet carrier shaft 211, the first output shaft 41 It can be hollow shaft and can coaxially cover on first planet carrier axis 111, the second output shaft 42 can be equally hollow shaft and coaxial Ground is set on the second planet carrier shaft 211.Wherein, the central body portion 64 of first planet carrier axis 111 and the first connecting bracket 61 Coaxial fixed, the second planet carrier shaft 211 can be coaxial fixed with the central body portion 64 of the second connecting bracket 62, but not limited to this.
In addition, the first gear ring 13 is identical with the radial dimension of the second gear ring 23, and the first tooth as optional embodiment Each of circle 13 and the second gear ring 23 may each be integrated molding component.
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 0- Figure 15, 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 input unit 3, such as be provided with power output shaft output gear 110 on power output shaft 103, power output shaft is defeated 3 engaged transmission of gear 110 and input unit out.As preferred embodiment, power output shaft output gear 110 and input unit 3 Main reducing gear is constituted, wherein power output shaft output gear 110 is configured to main reducing gear driving gear, and input unit 3 then corresponds to structure It makes as main retarder driven gearwheel.In this way, making 1000 structure of power-driven system more compact, and built in differential mechanism 100 Inside main reducing gear driven gear, differential mechanism 100 can be made preferably using the inner space, to facilitate entire power drive line The arrangement of system 1000.
One of input shaft in multiple input shafts 101,102 be arranged to optionally with power output shaft 103 Dynamic, in other words, as shown in Figure 10 and Figure 11, one of input shaft such as the first input shaft 101 (is the second input shaft in Figure 12 102) it can link with power output shaft 103, while one of input shaft such as the first input shaft 101 also can be with power Output shaft 103 disconnects.For remaining input shaft, then it is all provided with to be set to and links with power output shaft 103, i.e., these input shafts act Then power output shaft 103 also follows movement or power output shaft 103 to act then these input shafts and also acts therewith.
As shown in Figure 10 and Figure 11, third motor generator 401 is arranged to input with one of input shaft such as first Axis 101 links, i.e., the input shaft 101 to link with third motor generator 401 is to link with 103 selectivity of power output shaft Input shaft 101.In a further embodiment, 103 overhead of power output shaft set is provided with empty set driven gear 108, empty set from Moving gear 108 and above-mentioned one of input shaft link, and synchronizer 109 is arranged for synchronous dynamic output shaft 103 and sky Cover driven gear 108.It is understood that when synchronizer 109 is in engagement state, the synchronous empty set driven tooth of synchronizer 109 Wheel 108 and power output shaft 103, the power in this way from third motor generator 401 can be in the conjugation of synchronizer 109 Under from the output of power output shaft 103 to differential mechanism 100, and when synchronizer 109 is in an off state, third motor generator 401 are equivalent to and the disconnection of power output shaft 103.Synchronizer 109 serves as the power switch of third motor generator 401, energy as a result, Enough control the output and disconnection of 401 power of third motor generator.
As an alternative embodiment, synchronizer 109 be arranged on power output shaft 103 and for engage empty set from Moving gear 108.It has the advantages of simple structure and easy realization as a result,.
For the kind of drive of remaining input shaft and power output shaft 103, can be realized by gear transmission mode.Example Such as, fixed driven gear 107 is fixedly installed on power output shaft 103, fixed driven gear 107 joins with remaining input shaft It is dynamic, that is, remove the input shaft 101 in above-mentioned Figure 10 embodiment or the input shaft 102 in Figure 11 embodiment.
It is driven to be fixedly installed fixation simultaneously for example, see the specific embodiment of Figure 10 and Figure 11, on power output shaft 103 Gear 107, and be set with empty set driven gear 108, and be accordingly fixedly installed on input shaft fixed driving gear 105, 106, empty set driven gear 108 and fixed driven gear 107 are engaged with corresponding fixed driving gear respectively.Such as, empty set is driven The sum of sum of gear 108 and fixed driven gear 107 is identical as the fixed quantity of driving gear.
Referring to the example of Figure 10 and Figure 11, the quantity of empty set driven gear 108 and fixed driven gear 107 is one, Accordingly, the quantity of fixed driving gear is two, and it is a pair of that empty set driven gear 108 engages composition with a fixed driving gear Gear pair, fixed driven gear 107 fix driving gear with another and engage composition another pair gear pair, it will be understood 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 10-Figure 15, 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.
Figure 10-Figure 11, Figure 13-Figure 16 example in, empty set driven gear 108 is nibbled with the first fixed driving gear 106 It closes, fixed driven gear 107 is engaged with the second fixed driving gear 105, while third motor generator 401 and the first input shaft 101 linkages fix driving gear 106 by gear structure and first such as third motor generator 401 and link, concretely third Motor generator 401 is driven by the fixed driving gear 106 of gear 402, gear 403 and first, above-mentioned by reasonable design Transmission speed ratio needed for the number of teeth of gear can obtain third motor generator 401.
And in the illustration in fig 12, empty set driven gear 108 is engaged with the second fixed driving gear 105, fixed driven tooth Wheel 107 engage with the first fixed driving gear 106, while third motor generator 401 and the linkage of the second input shaft 102, and such as the Three motor generators 401 are linked by gear structure and the second fixed driving gear 105, concretely third motor generator 401 are driven by the fixed driving gear 105 of gear 402, gear 403, gear 404, gear 405 and second, 404 He of middle gear Gear 405 can be fixed on same axis 406, can obtain third dynamoelectric and power generation by the number of teeth of reasonable design said gear Transmission speed ratio needed for machine 401.
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 10-Figure 16, 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.
Referring to Figure 10-Figure 16 and combining shown in Fig. 1-Fig. 9, the first motor generator 501 and the first gear ring 13 link, and second Motor generator 503 and the second gear ring 23 link.Further, the first external tooth 505 is provided on the outer peripheral surface of the first gear ring 13, the One external tooth 505 may be integrally formed on the outer peripheral surface of the first gear ring 13.It is provided with outside second on the outer peripheral surface of second gear ring 23 Tooth 506, the second external tooth 506 may be integrally formed on the outer peripheral surface of the second gear ring 23.First motor generator 501 is and first What external tooth 505 linked, the second motor generator 503 is linked with the second external tooth 506.
Further, gear 502, gear 502 and the first external tooth be may be provided on the motor shaft of the first motor generator 501 505 engage, and may be provided with gear 504 on the motor shaft of the second motor generator 503, gear 504 is engaged with the second external tooth 506. However, it will be understood that the first motor generator 501 and the first gear ring 13 and the second motor generator 503 and the second tooth The linked manner of circle 23 is not limited to mode described herein.
Referring to shown in Figure 10-Figure 16, the first motor generator 501 and the second motor generator 503 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.
Referring to the embodiment of Figure 17-Figure 18, in the power-driven system 1000 and Figure 10-Figure 16 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 17 In, the first driven disc 206, the second driven disc 207, third driven disc 208 are axially distributed, in the embodiment of Figure 18, 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 11.
Low speed pure electric vehicle: double clutch 204 is all off, and synchronizer 109 disconnects, the first motor generator 501 and second Motor generator 503 is worked external direct output power in a manner of motor.Power transfer path is shorter under the mode, is driven energy Amount loss is small, is suitble to urban congestion road conditions.
High speed pure electric vehicle: double clutch 204 is all off, and synchronizer 109 is in engagement state, the first motor generator 501, the second motor generator 503 and 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 synchronizer 109 is in engagement state, and the power that engine 301 generates at this time passes through the first input shaft 101, power is distributed to the driving wheel of two sides by differential mechanism 100 to differential mechanism 100 by output after power output shaft 103.
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 synchronizer 109 is in an off state, and the power that engine 301 generates at this time passes through the second input shaft 102, power is distributed to the driving wheel of two sides by differential mechanism 100 to differential mechanism 100 by output after power output shaft 103.
Power generation in parking: the first bonding part 201 is engaged with third bonding part 203, and the second bonding part 202 connects with third It closes part 203 to disconnect, synchronizer 109 is in an off state, and the power that engine 301 generates at this time passes through the first input shaft 101 Output drives third motor generator 401 to generate electricity as motor, realizes power generation in parking to third motor generator 401 Function.
Brake energy recovery: synchronizer 109 can be at off-state, and the first motor generator 501 and second is electronic at this time Generator 503 recycles braking energy.Or synchronizer 109 is in engagement state, the first motor generator 501, second is electric at this time Dynamic generator 503 and third motor generator 401 all recycle braking energy.
Driving power generation: engine 301 can by the engagements of the different engagement states and synchronizer 109 of double clutch 204/ Off-state, and selectivity drives the first motor generator 501 and the second motor generator 503 to generate electricity or drive third electricity Dynamic generator 401 generates electricity, and can also drive three electric power generations simultaneously certainly, and at the same time, also externally output is dynamic for engine 301 Power drives vehicle driving.
Increase journey mode: the first bonding part 201 engages third bonding part 203, and the second bonding part 202 is engaged with third Part 203 disconnects, and 301 output power of engine drives third motor generator 401 to generate electricity, while the first motor generator 501 Motor output power drive vehicle driving is used as with the second motor generator 503.
The main distinction of Figure 10 embodiment and Figure 11 embodiment is to eliminate third motor generator 401, for remaining Construction portion is then consistent, and which is not described herein again.
Figure 12 embodiment and the main distinction of Figure 11 embodiment be, the third motor generator 401 in Figure 12 embodiment It links, remaining construction portion is then consistent, which is not described herein again with the second input shaft 102.
For the embodiment of Figure 13-Figure 16, compared with Figure 11 embodiment, difference is to increase rear-guard differential lock.
It 3- Figure 16 and combines shown in Fig. 1-Fig. 9 referring to Fig.1, the first gear ring 13 links with the near front wheel 910a, such as the first gear ring 13 are coaxially connected with the near front wheel 910a, and the second gear ring 23 and off-front wheel 910b links, and such as the second gear ring 23 and off-front wheel 910b are same Axis is connected.4th motor generator 901 is linked by gear structure and left rear wheel 910c, and such as the 4th motor generator 901 passes through Gear W1, W2, W3, W4 and left rear wheel 910c link, gear W1 with the 4th motor generator 901 is coaxial is connected, gear W1 and tooth W2 engagement is taken turns, gear W2 is coaxially connected with gear W3, and gear W3 is engaged with gear W4, and gear W4 can be fixedly installed on left half axle On 904, left rear wheel 910c is provided on left half axle 904.Similarly, after the 5th motor generator 902 is by gear structure and the right side 910d linkage is taken turns, such as the 5th motor generator 902 is linked by gear X1, X2, X3, X4 and off hind wheel 910d, gear X1 and the Five motor generators 902 are coaxially connected, and gear X1 is engaged with gear X2, and gear X2 is coaxially connected with gear X3, gear X3 and tooth X4 engagement is taken turns, gear X4 can be fixedly installed on right axle shaft 905, and off hind wheel 910d is provided on right axle shaft 905.
In the example in figure 13, 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 in figure 14, 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 15 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 16, 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 be by the first planetary gear 12 and the partly overlapping scheme of the second planetary gear 22 and first Planet carrier 11 and the second planet carrier 21 are that the scheme of plate structure combines, and can effectively reduce the axial ruler of differential mechanism 100 in this way It is very little, to keep the volume of differential mechanism 100 smaller.
For another example, those skilled in the art can be by the first planetary gear 12 and the partly overlapping scheme of the second planetary gear 22 and planet Wheel and planet carrier are accommodated in the combination of the scheme in installation space, not only can effectively reduce the axial ruler of differential mechanism 100 It is very little, and planetary gear and planet carrier can also be made to be hidden in installation space and avoid leaking cruelly being damaged outside, so that increasing makes With the service life, maintenance cost is reduced.
For another example, those skilled in the art can be by the revolution axis of the revolution axis and the second planetary gear 22 of the first planetary gear 12 The scheme of coincidence is combined with the revolution-radius of the first planetary gear 12 with the identical scheme of revolution-radius of the second planetary gear 22, in this way So that the structure of differential mechanism 100 is more compact, occupancy volume is smaller, is more convenient for arranging.
For another example, input unit 3 can be configured to annular input end gear and covered in 13 He of the first gear ring by those skilled in the art The scheme of the outer peripheral surface of second gear ring 23 is combined with the scheme that input end gear 3 is main retarder driven gearwheel, thus poor Fast device 100 can realize preferably space utilization rate, greatly place preferably using the main space for subtracting driven gear inner hollow The arrangement of differential assembly and the limitation to weight size, and by the way that input unit 3 is directly disposed as annular Main reducing gear driven gear thus can not only reduce entire power without main reducing gear driven gear is individually arranged again and drive The components of dynamic system, reduce cost, but also keep the structure of differential mechanism 100 more compact, small and exquisite.
For another example, input unit 3 can be configured to annular input end gear and input end gear 3 around simultaneously by those skilled in the art On the one hand the scheme combination for covering gap, makes the structure relative compact of differential mechanism 100, and pass through input end gear 3 in this way Cover gap, moreover it is possible to which the installation space for limiting the shell of two planetary gear trains is relatively more closed, and adequately protect installation space Internal component, improves its service life.
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 19, 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 (25)

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 are connect with the first planet carrier, and described One planetary gear is engaged with first gear ring；
Second planet carrier, the second planetary gear and the second gear ring, second planetary gear are connect with second planet carrier, and described Two planetary gears are engaged with second gear ring and second planetary gear is also engaged with first planetary gear, wherein described One gear ring and second gear ring constitute two power output ends of the differential mechanism；
Input unit, the input unit link with the first planet carrier and second planet carrier respectively；
Power output shaft, the power output shaft are arranged to link with the input unit；
At least one of first gear ring and second gear ring include: annular side wall portion and annular flange portion, the ring It is provided with multiple teeth for engaging with planetary gear on the inner wall of shape sidewall portion, the annular flange portion is from one of gear ring The annular side wall portion end face to the annular side wall portion of another gear ring extend or the annular flange portion set respectively It sets on the end face of the annular side wall portion of two gear rings and extends relative to one another, the internal diameter of the annular flange portion is greater than The internal diameter of the annular side wall portion；
Multiple input shafts, one of input shaft in the multiple input shaft be arranged to optionally with the power output Axis linkage, remaining described input shaft are arranged to link with the power output shaft；
First motor generator and the second motor generator, first motor generator and first gear ring link, described Second motor generator and second gear ring link.
2. power-driven system according to claim 1, which is characterized in that first planetary gear and second planet Wheel partly overlaps in the axial direction.
3. power-driven system according to claim 2, which is characterized in that first planetary gear includes: the first teeth portion With the second teeth portion, second planetary gear includes: third teeth portion and the 4th teeth portion, and first teeth portion is nibbled with first gear ring It closes, second teeth portion corresponding overlapping and engagement cooperation, the 4th teeth portion and institute in the axial direction with the third teeth portion State the engagement of the second gear ring.
4. power-driven system according to claim 1, which is characterized in that first planetary gear and the second planetary gear are equal For roller gear.
5. power-driven system according to claim 1, which is characterized in that first gear ring and second gear ring pair Claim setting, 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 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.
6. power-driven system according to claim 1, which is characterized in that the input unit is configured to input end gear, The input end gear is configured to annular and is set in first gear ring and second gear ring outer surface.
7. power-driven system according to claim 6, which is characterized in that first gear ring and second gear ring it Between be provided with gap, the input end gear surround and covers the gap.
8. power-driven system according to claim 1, which is characterized in that further include: intermediate connection structure, the centre Connection structure is used to the first planet carrier, second planet carrier being connected to the input unit, the intermediate connection structure Include: the first connecting bracket and the second connecting bracket, first connecting bracket for connect the first planet carrier with it is described Input unit, second connecting bracket is for connecting second planet carrier and the input unit, wherein the first connection branch Each of frame and second connecting bracket include:
Central body portion and extend arm, the extensions arm be it is multiple and be arranged on the outer peripheral surface in the central body portion, The multiple extension arm is centered on the central body portion and radially distributes, wherein the adjutage portion is used for and institute Input unit is stated to be connected.
9. power-driven system according to claim 1, which is characterized in that each first planetary gear is configured with one First planet wheel spindle, two ends of first planet wheel spindle respectively with the first planet carrier and the second planet carrier phase Even, each second planetary gear be configured with second planet wheel spindle, two ends of second planet wheel spindle respectively with The first planet carrier is connected with second planet carrier.
10. power-driven system according to claim 1, which is characterized in that the revolution-radius of first planetary gear with The revolution-radius of second planetary gear is identical；
The first planet carrier and second planet carrier are spaced apart, and first planetary gear and second planetary gear are with direct The form of engagement is configured between the first planet carrier and second planet carrier so that the first planet carrier and Second planet carrier is located at the opposite exterior lateral sides of first planetary gear and second planetary gear；
The outer diameter of the annular flange portion outer diameter and the annular side wall portion is generally equalized or the internal diameter of the annular flange portion It is generally equalized so that the annular flange portion protrudes outward the annular radially with the outer diameter of the annular side wall portion Sidewall portion.
11. 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.
12. power-driven system according to claim 1, which is characterized in that be arranged on the power output shaft dynamic Output shaft output gear, the power output shaft output gear and input unit engaged transmission.
13. power-driven system according to claim 12, which is characterized in that the power output shaft output gear and institute It states input unit and constitutes main reducing gear, wherein the power output shaft output gear is configured to main reducing gear driving gear, it is described defeated Entering cage structure is main retarder driven gearwheel.
14. power-driven system according to claim 1, which is characterized in that the power output shaft overhead set is provided with Empty set driven gear, the empty set driven gear and one of input shaft link, and the power-driven system further includes Synchronizer, the synchronizer are arranged for synchronizing the power output shaft and the empty set driven gear.
15. power-driven system according to claim 14, which is characterized in that the synchronizer setting is defeated in the power On shaft and for engaging the empty set driven gear.
16. power-driven system according to claim 14, which is characterized in that be fixedly installed on the power output shaft Fixed driven gear, the fixed driven gear and remaining described input shaft link.
17. power-driven system according to claim 1, which is characterized in that the power output shaft overhead set is provided with Empty set driven gear and it is fixedly installed fixed driven gear, the power-driven system further includes synchronizer: the synchronization Device is arranged for synchronizing the power output shaft and the empty set driven gear；
Fixed driving gear, the empty set driven gear and the fixed driven gear are fixedly installed on each input shaft It is engaged respectively with corresponding fixed driving gear.
18. power-driven system according to claim 17, 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.
19. power-driven system according to claim 18, 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.
20. power-driven system according to claim 1, which is characterized in that be arranged on the outer peripheral surface of first gear ring There is the first external tooth, the second external tooth, first motor generator and described first are provided on the outer peripheral surface of second gear ring External tooth linkage, second motor generator and second external tooth link.
21. power-driven system according to claim 1, which is characterized in that first motor generator and described the Two motor generators are distributed about the differential mechanism bilateral symmetry.
22. 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.
23. power-driven system according to claim 1, which is characterized in that the power-driven system includes speed changer And engine, the speed changer include the first input shaft, the second input shaft and third input shaft, the third input axle sleeve is located at On second input shaft, second input axle sleeve is located on first input shaft, the engine and described first defeated Enter and is connected between axis, second input shaft and the third input shaft by three clutches.
24. 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.
25. a kind of vehicle, which is characterized in that including power-driven system described according to claim 1 any one of -24.
CN201510626301.XA 2015-09-25 2015-09-25 Power-driven system and vehicle with it Active CN106553534B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201510626301.XA CN106553534B (en) 2015-09-25 2015-09-25 Power-driven system and vehicle with it

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201510626301.XA CN106553534B (en) 2015-09-25 2015-09-25 Power-driven system and vehicle with it

Publications (2)

Publication Number Publication Date
CN106553534A CN106553534A (en) 2017-04-05
CN106553534B true CN106553534B (en) 2019-11-22

Family

ID=58416536

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201510626301.XA Active CN106553534B (en) 2015-09-25 2015-09-25 Power-driven system and vehicle with it

Country Status (1)

Country Link
CN (1) CN106553534B (en)

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103144528A (en) * 2013-02-20 2013-06-12 上海中科深江电动车辆有限公司 Dual-clutch transmission applied to hybrid electric vehicle and application method thereof
DE102012216404A1 (en) * 2012-09-14 2014-03-20 Schaeffler Technologies AG & Co. KG Spur gear differential for use as distributor gear for distributing drive power between front and rear axles of vehicle, has axles whose angular distances are defined on pitch circle so that integral multiple of angle value represents value

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007040478A1 (en) * 2007-08-28 2009-03-05 Schaeffler Kg Differential gear with light support parts
DE102012219212A1 (en) * 2012-10-22 2014-04-24 Schaeffler Technologies Gmbh & Co. Kg Spur gear differential for use as e.g. distribution, branching, and axle differential gear box in motor car, has coupling and circulation planetary parts formed such that cladding circle is smaller than addendum circle of teeth
CN106555854B (en) * 2015-09-25 2019-11-05 比亚迪股份有限公司 Power-driven system and vehicle with it
CN106553532B (en) * 2015-09-25 2019-11-08 比亚迪股份有限公司 Power-driven system and vehicle with it
CN106553537B (en) * 2015-09-25 2019-11-05 比亚迪股份有限公司 Power-driven system and vehicle with it

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012216404A1 (en) * 2012-09-14 2014-03-20 Schaeffler Technologies AG & Co. KG Spur gear differential for use as distributor gear for distributing drive power between front and rear axles of vehicle, has axles whose angular distances are defined on pitch circle so that integral multiple of angle value represents value
CN103144528A (en) * 2013-02-20 2013-06-12 上海中科深江电动车辆有限公司 Dual-clutch transmission applied to hybrid electric vehicle and application method thereof

Also Published As

Publication number Publication date
CN106553534A (en) 2017-04-05

Similar Documents

Publication Publication Date Title
CN106553537B (en) Power-driven system and vehicle with it
CN106555844A (en) Power-driven system and the vehicle with which
CN106555851B (en) Differential mechanism, power drive system and vehicle
CN106553526A (en) Power-driven system and the vehicle with which
CN106555858B (en) Power-driven system and vehicle with it
CN106553527B (en) Differential mechanism, power drive system and vehicle
CN106553532B (en) Power-driven system and vehicle with it
CN106555854B (en) Power-driven system and vehicle with it
CN106555845B (en) Differential mechanism, power drive system and vehicle
CN106553530B (en) Power-driven system and vehicle with it
CN106553535B (en) Power driving system and vehicle with same
CN106555856B (en) Power-driven system and vehicle with it
CN106555857B (en) Power-driven system and vehicle with it
CN106553528B (en) Power driving system and vehicle with same
CN106553536B (en) Power driving system and vehicle with same
CN106555859B (en) Power-driven system and vehicle with it
CN106553538A (en) Power-driven system and the vehicle with which
CN106553533B (en) Power-driven system and vehicle with it
CN106555847B (en) Power-driven system and vehicle with it
CN106553534B (en) Power-driven system and vehicle with it
CN106555852B (en) Power-driven system and vehicle with it
CN106555853B (en) Power driving system and vehicle with same
CN106555848B (en) Power-driven system and vehicle with it
CN108237907A (en) Power-driven system and vehicle
CN106555846A (en) Power-driven system and the vehicle with which

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant