CN109163065A - A kind of decoupling wheel hem retarding mechanism suitable for distributed electric drive automobile - Google Patents
A kind of decoupling wheel hem retarding mechanism suitable for distributed electric drive automobile Download PDFInfo
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- CN109163065A CN109163065A CN201811120492.2A CN201811120492A CN109163065A CN 109163065 A CN109163065 A CN 109163065A CN 201811120492 A CN201811120492 A CN 201811120492A CN 109163065 A CN109163065 A CN 109163065A
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/037—Gearboxes for accommodating differential gearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Abstract
The invention proposes a kind of decoupling wheel hem retarding mechanisms suitable for distributed electric drive automobile, while being intended to reduce distributed-driving electric automobile unsprung mass, the transmitting discontinuity of the power due to caused by power output end irregular bounce and movement interference are solved, guarantees that dynamical stability is reliably transmitted.The present invention includes differential assembly, dual-idle gear formula planetary gear pair, planetary gear carrier input terminal connection rod set, planetary gear carrier output end connection rod set, reducer shell and output shaft.Deceleration output end vertical direction linear translation freedom degree and deceleration output end pivoting freedom decoupling may be implemented in the mechanism, and realizes small unsprung mass, dynamical stability transmission and the requirement of without motion interference.The mechanism structure is compact, quality is small, transmission efficiency is high.
Description
Technical field
The invention belongs to mechanical engineering fields, and in particular to it is a kind of suitable for distributed electric drive automobile wheel edge driving,
The power of deceleration output end vertical direction linear translation freedom degree Yu deceleration output end pivoting freedom decoupling may be implemented
Transfer device.
Background technique
Distributed-driving electric automobile suspends to reduce nonspring carried mass for motor, when taking common hub reduction gear
Not in view of motor and the coupling between output end is rotated, power transmitting is may cause when rotating output end and beating and does not connect
Continuous or movement interference.At the same time, in the irregular bounce of distributed-driving electric automobile wheel, it is difficult to control by other
Means solve deceleration output end with the contradiction of wheel hop and the pivoting of deceleration output end.From existing decoupling wheel side speed reducer
Structure can be seen that following problem: partly decoupled hub reduction gear cannot fully achieve freedom decoupling, or even will appear movement and do
It relates to；Partly decoupled hub reduction gear occupied space is larger, and quality is larger, to bring, passability lowers, nonspring carried mass increases
The problem of adding.
Summary of the invention
To solve the above problems, devising a kind of decoupling wheel side speed reducer suitable for distributed electric drive automobile herein
Structure, it is intended to overcome retarder output end with the irregular bounce of wheel and contradiction between driving force reliable delivery and movement interference,
Suitable for distributed-driving electric automobile, stable power output can be obtained while reducing suspension unsprung mass,
Solve the adverse effect that wheel motor is coupled with wheel movement.
Technical solution of the present invention is described with reference to the drawings as follows:
A kind of decoupling wheel hem retarding mechanism suitable for distributed electric drive automobile, mainly by differential assembly, double lazy
Wheeled planetary gear is secondary, reducer shell is constituted, the double centre wheel dual-idle gear formula planetary gear pairs of reduction gear portion use, and two
The planet idle 46 being symmetrically installed along retarder center line C-C engages the same gear ring 40, gear ring 40 and reducer output shaft 26
Connection, reducer output shaft 26 keep coaxial by bearing 29,48 and reducer shell 20；In the both ends planet of planet gear pair
It is all each fitted with flange shaft sleeve between rack rod, is connected between connecting rod and planet idle axis by rolling bearing；Differential mechanism output
Axis 6,15 pass through with through slot reducer shell capping 18, differential output shaft 6,15 can in through slot vertical along center
Line C-C translation；The guide and limit pin 19 and reducer shell being fixedly mounted on retarder input terminal planet stent connecting rod 21 cover
Guide and limit slot on 18 matches；Two coaxial lines of differential mechanism are the same as output end output output shaft 6,15 and sun spur gear 49
Connection is offset while input power since two planet idles 46 occur etc. in power output end bounce irregular with wheel
Big reversed displacement and the speed difference generated, differential mechanism are fixed in frame chassis by bracket 3, guarantee the axis of power intake
The axis A-A coaxial line of line, differential mechanism axis and two differential output shafts.
The differential mechanism input terminal is not limited to spline auxiliary input, is also possible to other forms, for example gear pair, belt pass
Dynamic, chain drive and flange flange transmission etc..
After the differential mechanism receives power by differential casing, power is divided into two transmitting by bevel planet gear
To coaxial line with two differential output shafts 6,15 of output end, can in the sliding slot that reducer shell covers 18 axis along the chute
Line C-C translation, i.e., differential output shaft 6,15 is opposing stationary with frame chassis always.
Two sun spur gears 15,49 and two output shafts of differential mechanism 6,15 of the planetary gear of decelerator pair are fixed
Connection, two sun spur gears and differential mechanism coaxial line A-A, two sun spur gears 15,49 are respectively lazy with a planet
46 engagement of wheel, the axis moment of two planet idles 46 are parallel and when reducer output shaft 26 and differential output shaft 6,15 are coaxial
The axis of (original installation condition) and two sun spur gears 15,49 is in same horizontal line when line.Two planet idles 46 will be moved
Power is transmitted to same gear ring 40, and gear ring 40 is fixedly connected with reducer output shaft 26, and output shaft transfers power to next stage.
The retarder planet idle 46 is connect by idler shaft 23,41 with planetary gear carrier connection rod set, planet tooth
Wheel support connecting rod can around mounting axis A-A (B-B) and group inner link between relatively rotate, be achieved in when power output end with
Wheel is irregular when moving up and down, and the position of planet idle 46 also changes correspondingly, and guarantees two 46 moment of planet idle and the sun
Spur gear 15,49 and gear ring 40 are at a fully engaged.
Guide and limit pin 19 is fixedly mounted in the input terminal planetary gear carrier connecting rod a21, covers with reducer shell
Guide and limit sliding slot on 18 matches, and solves the freedom degree contradiction of planetary gear carrier, i.e. planet stent at any time
Can not around mounting axis A-A ceaselessly pitch of the laps rotation with when power output end is moved up and down with wheel is irregular planet stent connect
Bar needs the contradiction to turn an angle around mounting axis A-A.
The planet stent connecting rod when power output end is moved up and down with wheel is irregular, in same connection rod set two
Root connecting rod the big reversed angle such as can symmetrically rotate around mounting axis A-A (or B-B) with retarder center line C-C.
The reducer shell 20 should design the connecting rod that installation is connect with frame chassis according to installation environment, and guaranteeing should
Reducer shell and frame brackets only have the vertical direction of relative frame to have translational degree of freedom, and the transverse direction of relative frame does not have
There is any rotary freedom.
The retarder parts can relative frame vertical direction occur moderate jerk value, the row that retarder parts use
Star gear pair reduces the bulk of retarder, reduces total quality, is reduced simultaneously by the load of outer link non-
Spring carried mass.
Detailed description of the invention
Fig. 1 is the composition schematic elevation view of device provided by the present invention.
Fig. 2 is the composition schematic top plan view of device provided by the present invention.
Fig. 3 is the composition schematic side view of device provided by the present invention.
Fig. 4 is planetary gear of decelerator rack rod rough schematic view provided by the present invention.
Fig. 5, Fig. 6 and Fig. 7 are planetary gear of decelerator rack rod motion principle figure provided by the present invention.
Fig. 8 is that reducer shell of the present invention covers guide and limit slot track schematic diagram.
Fig. 9 is power transmission route schematic diagram of the present invention.
In figure: 1 be differential mechanism active casing, 2,17,34,44,50,53 be hole card, 3 be differential mechanism bracket, 4,16,29,
33,48,55 be rolling bearing, and 5,14 be sliding bearing, and 6 be differential output shaft, and 7,37 be bolt, and 8 be differential spider tooth
Wheel shaft, 9,11,24,36,38,51,54 be gasket, and 10 be differential pinion gear, and 12 be differential mechanism output bevel gear wheel, and 13 be poor
The fast passive shell of device, 15 be differential mechanism hollow output shaft, and 18 cover for reducer shell, and 19 guide and limit pins, 20 be retarder
Shell, 21 be input terminal planetary gear carrier connecting rod a, and 22 be input terminal planetary gear carrier connecting rod b, and 23,41 be planet idle
Axis, 25 be end cap, and 26 be reducer output shaft, and 27 be outside framework oil seal, and 28,31,43,47,55 be axis card, and 30 be output end planet
Gear stand connecting rod a, 32,39 be flange bearing, and 35 be output end planetary gear carrier connecting rod b, and 40 be gear ring, and 42 keep off for idle pulley
Ring, 45 be needle bearing, and 46 be planet idle, and 49 be sun spur gear, and 58 be differential spider pinion shaft lock pin, and A-A is poor
Fast device output shaft axis, B-B are reducer output shaft axis, and C-C is retarder center line (through slot axis).
Specific embodiment
It is described with reference to the accompanying drawing to implement to further illustrate particular content and its specific embodiment of the invention:
Device provided by the present invention relies primarily on differential assembly, dual-idle gear formula planet to the realization of freedom decoupling function
The mechanisms such as gear pair, reducer shell specifically include that the passive shell 13 of differential mechanism active casing 1, differential mechanism, differential spider
Gear shaft 8, differential spider bevel gear 11 and differential mechanism device output bevel gear wheel 12, differential spider pinion shaft lock pin 58, the sun
Spur gear 49,15, two input connecting rods 21,22 of differential mechanism hollow output shaft and corresponding ball bearing and flange shaft sleeve, guiding limit
Position 19, two idler shafts of pin, 23,41, two planet idles 46 and corresponding 42, two needle bearing 45, idle pulley baffle ring output ends
Planetary gear carrier connecting rod 30,35 and corresponding ball bearing and flange shaft sleeve, gear ring 40, reducer output shaft 26, reducing gearbox
Body 20, reducer shell capping 18, outside framework oil seal 27, end cap 25, each positioning snap ring and each fixing bolt and mating gasket.
Differential output shaft 6 passes through inside differential mechanism hollow output shaft 15, hollow by flange shaft sleeve 57 and differential mechanism
Output shaft 15 matches, while supporting as the rear end of the differential output shaft 6.The end of differential output shaft 6 is by gradually opening
Line spline and sun spur gear 49 cooperate, and sun spur gear 49 is fixed on differential output shaft 6 by axis card 43.Sun spur gear
Symmetrically one straight-tooth planet idle of external toothing is distinguished in the horizontal plane with the sun spur gear in differential mechanism hollow output shaft 15
46.Planet idle 46 is mounted on planet idle axis 23,41 by needle bearing 45, and needle bearing 45 is solid by snap ring 44,47
It is scheduled on straight-tooth idle pulley 46 and planet idle axis 23,41, the idle pulley baffle ring 42 of side is positioned by planet idle axis platform shoulder, the other side
Idle pulley baffle ring 42 be fixed on planet idle axis by snap ring.Two planet idles 46 are engaged with a gear ring 40 simultaneously, the tooth
Circle is matched by hexagon socket head cap screw with the flange of reducer output shaft 26.
Input terminal planetary gear carrier connecting rod a 21 is mounted in differential mechanism hollow output shaft 15 by ball bearing.Input terminal
Planetary gear carrier connecting rod b 22 is assembled by flange shaft sleeve 56 and input terminal planetary gear carrier connecting rod a21, flange shaft sleeve 56
Flange end is fixed on the outer ring of input terminal planetary gear carrier connecting rod a 21 by snap ring.Input terminal planetary gear carrier connecting rod
B22 is limited by 56 flange end of flange shaft sleeve.Planet idle on planet idle axis 23,41 and input terminal planetary gear carrier connecting rod
Axis hole is interference fitted fixed one end.Two input terminal planetary gear carrier connecting rod interference are installed with two guide and limit pins 19.
Output end planetary gear carrier connecting rod a 30 is mounted on reducer output shaft 26 by ball bearing.Output end planet
Gear stand connecting rod b 35 is connected by flange shaft sleeve 32 with output end planetary gear carrier connecting rod a 30,32 method of flange shaft sleeve
Lan Duan is fixed on the outer ring of output end planetary gear carrier connecting rod a 30 by snap ring.One end of planet idle axis 23,41 is logical
Flange shaft sleeve is crossed to connect with output end planetary gear carrier connecting rod.
Accelerator output shaft 26 is installed by ball bearing and reducer shell 20, is fixed with snap ring.Ball bearing 29 leans on oil sealing
The limit of end cap 25 is fixed.Reducer shell covers 18 housing differential mechanism hollow output shafts 15, which passes through hex bolts and subtract
Fast device shell 20 matches.Guide and limit sliding rail in reducer shell capping 18 connects with input terminal planetary gear carrier is mounted on
19 clearance fit of guide and limit pin on bar, completes the guide and limit of Uncoupled procedure.
1 leading portion of differential mechanism active casing is interior involute spline, matches with the external splines of motor output shaft, power is passed
To differential mechanism active casing 1.Differential mechanism active casing 1 is connected with the passive shell 13 of differential mechanism by bolt, built-in adjustment gasket
9.Differential spider pinion shaft 8 is installed inside housings, and is fixed on shell by differential spider pinion shaft lock pin 58, is prevented
Only planetary gear shaft rotates.Two differential pinion gears 10 are mounted on 8 both ends of differential spider pinion shaft, by having adjustment
The bevel planet gear gasket 11 and shell of back lash effect position.The front end axis of differential output shaft 6 by sliding shaft sleeve 5 with
Differential mechanism active casing 1 matches, and the front support of the differential output shaft 6 is differential mechanism active casing 1.On the gear shaft
Bevel gear wheel is positioned by the inner cavity end face of differential mechanism active casing 1, and is engaged with planetary gear.Differential mechanism hollow output shaft 15
It is matched by sliding shaft sleeve 14 with the passive shell 13 of differential mechanism.Differential mechanism device output bevel gear wheel 12 and differential mechanism hollow output shaft
15 front end external splines is matched by the internal spline of the output bevel gear wheel.6 rear end of differential output shaft passes through flange shaft sleeve 52
It is matched with differential mechanism hollow output shaft 15, that is, does the rear end support of differential output shaft 6, while doing the hollow output of differential mechanism again
The rear end of axis 15 supports.
As shown in figure 9, power is inputted from differential mechanism active casing 1, it is defeated with output end by two coaxial lines of differential mechanism
Power is divided into two by output shaft out, two sun spur gears 15,49 of retarder is passed to, by the planet respectively engaged
Idle pulley 46 transfers power to gear ring 40, finally 26 output power of reducer output shaft by connecting with gear ring 40.
Planetary gear of decelerator bracket is inputted to connecting rod mounting axis, planet idle axis axis and the guiding limit in connection rod set
Position pin axis is simplified to simple geometry triangle, as shown in Figure 4.Wherein, planet idle axis hole axis to input shaft axis away from
It is b from the distance for a, planet idle axis hole axis to guide and limit pin hole axis, respectively simplified right angled triangle is straight
The arm of angle.In order to facilitate expression, the center of circle of reducer shell closure surface is set as cross coordinate axis origin, reducer shell capping
Surface transverse direction is X-axis, and reducer shell closure surface vertical direction (C-C centerline direction) is Y-axis, then planet stent connects
Position of the guide and limit pin 19 in cross coordinate system on bar can be expressed as (x, y), at connecting rod home position, guiding limit
The position at position 19 center of pin is (a, b).
When retarder output end is not beated, retarder is in normal condition, and planet stent connecting rod is also at this time
Normal condition, as shown in Figure 5.Since the guide and limit slot in reducer shell capping 18 and planet stent connecting rod at this time are around difference
The track of fast device output shaft axis A-A rotation is inconsistent, and the track of the two covers the projection on 18 surfaces in reducer shell
Only intersect at the subpoint that current spacer pin covers 18 surfaces in reducer shell.Two trajectory lines only intersect at a point, at this time
Guide and limit slot in reducer shell capping 18 is not because transverse direction of the reducer shell on relative frame chassis rotates
Freedom degree and fix, guide and limit pin 19 cannot around differential output shaft axis A-A rotate track rotate；Simultaneously because slowing down
Bounce vertically does not occur for device output end so that position of the guide and limit pin 19 in guide and limit slot is fixed, and then leads
It cannot be moved to spacer pin along guide and limit grooved rail mark.Under the two collective effect, so that guide and limit pin i.e. cannot be around differential mechanism
The track rotation of output shaft axis A-A rotation, can not move along guide and limit grooved rail mark, realize complete degree of freedom.
When irregular bounce occurs for retarder output end, divide two states, i.e. retarder output end is defeated with respect to retarder
Enter bounce and retarder output end in axial direction to beat downwards with respect to reducer input shaft.When retarder output end is defeated with respect to differential mechanism
When shaft axis A-A is beated upwards, the through slot axis C-C that differential output shaft 6,15 can cover on 18 along reducer shell is straight
Line translation, a certain position therein are as shown in Figure 5.As seen from the figure, two planet stents input end link relative mistake speed device
While output shaft axis A-A has rotated certain angle, two planet stent input end links have also relatively rotated certain angle
Degree.Similar change also has occurred in two planet stent output end links, and the two has rotated certain angle with respect to reducer output shaft
While spending, certain angle has also been relatively rotated.And position of the planet idle 46 in planet gear pair is also with connecting rod position
Change with angle and change position so that input end link, planet idle and output end link three form one with
The diamond structure that connecting rod is side, planet idle is vertex.During forming this structure, on input terminal planet stent connecting rod
Guide and limit pin 19 and reducer shell capping 18 guide and limit slot device play conclusive effect.In retarder output end
During bounce, link rotatable, if retarder output end and the relative bounce amount of differential output shaft axis A-A are △ y, root
Available according to similar triangles, guide and limit pin 19 is when retarder exports ending pulsation in the guiding of reducer shell capping 18
Motion profile in limiting slot, the i.e. track of guide and limit slot:
When retarder output end is beated downwards with respect to differential output shaft axis A-A, differential output shaft 6,15 can be with
Through slot axis C-C linear translation in reducer shell capping 18, a certain position therein are as shown in Figure 6.It can be with from figure
Find out, retarder output end with respect to differential output shaft axis A-A beat downwards when inside planet stent connecting rod, idle pulley all send out
The phenomenon that having given birth to when similar wheel is beated upwards with respect to differential output shaft axis A-A.In the cross coordinate system of setting according to
The parameter parsing guide and limit pin 19 of setting leading in reducer shell capping 18 when retarder output end follows wheel hop
Motion profile into limiting slot, are as follows:
When irregular bounce occurs for retarder output end, two planet idles 46 of retarder can be with retarder center line C-
C such as is symmetrically generated at the big reversed rotational speed difference, which is balanced out by the differential mechanism of front end.
In conclusion the decoupling retarder is in bounce irregular with retarder output end, by box of tricks and deceleration
After the relative translational movement movement of mechanism and box of tricks offset two process collective effects of rotational speed difference, retarder output end is along vertical
Direction (direction retarder center line C-C) translational degree of freedom and between installation axle axis (axis A-A, B-B) rotational freedom
Movement it is unrelated, and can guarantee that dynamical stability is reliably transmitted, realize decoupling function.
Claims (7)
1. a kind of decoupling wheel hem retarding mechanism suitable for distributed electric drive automobile, mainly by differential assembly, dual-idle gear
Formula planetary gear is secondary, reducer shell is constituted, it is characterized in that: two output shaft coaxial lines (A-A) of differential mechanism are defeated with output end
Out, wherein differential mechanism hollow output shaft (15) is hollow gear shaft, is connect with differential mechanism output bevel gear wheel (12) by spline pair,
By sliding bearing (14) inner sleeve differential output shaft (6), two differential output shafts pass through reducer shell capping (18)
Sliding slot, feature can cover sliding slot axis (C-C) translation of (18) in two coaxial differential output shafts along reducer shell,
Two output shaft ends are each to fix a sun spur gear (49), and power is divided into two and is passed to along sun straight-tooth wheel axis pair
Claim the planet idle (46) of installation, two planet idles are separately mounted on planet idle axis (23,41), engage the same gear ring
(40), wherein two planet idle axis front ends are mounted on planet stent input connection rod set (21,23,56), rear end is mounted on planet
Bracket exports connection rod set (30,32,35), its main feature is that the moment is the characteristics of keeping every coaxial, above-mentioned planet stent connecting rod
It can be relatively rotated around mounting axis, gear ring (40) and reducer output shaft (26) connection, reducer shell (20) are coaxially mounted to
On reducer output shaft.
2. according to the decoupling wheel hem retarding mechanism for being suitable for distributed electric drive automobile described in right 1, it is characterised in that: outer
Portion's power source is motor, and power is input to differential mechanism by output shaft by motor, and the kind of drive is also possible to other modes, such as
Belt, gear pair etc..
3. according to the decoupling wheel hem retarding mechanism for being suitable for distributed electric drive automobile described in right 1, it is characterised in that: poor
Fast device is mounted in frame chassis by outside support suspension, and the differential mechanism is as power source receiving element, differential mechanism and electricity
Machine output shaft coaxial line (A-A)；Power is divided into two branches by the differential mechanism, and the differential output shaft by two coaxial lines is same
End is input to deceleration link.
4. according to the decoupling wheel hem retarding mechanism for being suitable for distributed electric drive automobile described in right 1, it is characterised in that: subtract
Fast link receives the power that differential mechanism transmits by two sun spur gears (15,49), and symmetrically nibbles in horizontal position respectively
Unify a planet idle (46)；Planet idle (46) is mounted on planet idle axis (23,41), planet idle axis front and back and planet
The connection of rack rod group, the planet stent connection rod set can be rotated around mounting axis (A-A, B-B)；Input terminal planet stent connection rod set
(21,23,56) and output end planet stent connection rod set (30,32,35) guarantee planet idle axis axis always with original installation axle
Line is parallel；Two planet idles (46) engage a gear ring (40) jointly.
5. according to the decoupling wheel hem retarding mechanism for being suitable for distributed electric drive automobile described in right 1, it is characterised in that: subtract
Fast device shell (20) need to design external connection connecting rod according to wheel or specific installation environment, guarantee that reducer shell can be servo-actuated
The irregular bounce of power output end, but without around shell axis rotational freedom.
6. according to the decoupling wheel hem retarding mechanism for being suitable for distributed electric drive automobile described in right 1, it is characterised in that: subtract
Fast device shell capping (18) design has guide and limit sliding slot, the guide and limit pin installed on the sliding slot and planet stent input connecting rod
(19) cooperate；Passing through guide and limit slot --- spacer pin solves planet stent freedom degree conversion requirement；The guide and limit of proposition
Grooved rail mark can also be transformed into other coordinate systems or the expression of other equations.
7. according to the decoupling wheel hem retarding mechanism for being suitable for distributed electric drive automobile described in right 1, it is characterised in that: subtract
Fast device output shaft (26) outputs power to next stage by spline, and reducer shell (20) is with the irregular bounce of power output end
When, not with bounce, input terminal planetary gear carrier connecting rod a, b (21,22) are exported differential output shaft (6,15) around differential mechanism
Axis (6,15) rotation, output end planetary gear carrier connecting rod a, b (30,35) are rotated around reducer output shaft (26), drive two
Planet idle (46) is symmetrically mobile along retarder center line (C-C), and three forms certain mathematics geometrical relationship, while planet branch
Frame inputs the movement in the guide and limit slot of the reducer shell capping (18) of translation of the guide and limit pin (19) on connecting rod；Upper
During stating, the rotational speed difference that two planet idles generate will be offset by differential mechanism, it is thus achieved that retarder rotation and translation
Decoupling, and between part without motion interfere.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811120492.2A CN109163065A (en) | 2018-09-26 | 2018-09-26 | A kind of decoupling wheel hem retarding mechanism suitable for distributed electric drive automobile |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811120492.2A CN109163065A (en) | 2018-09-26 | 2018-09-26 | A kind of decoupling wheel hem retarding mechanism suitable for distributed electric drive automobile |
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|---|---|
| CN109163065A true CN109163065A (en) | 2019-01-08 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811120492.2A Pending CN109163065A (en) | 2018-09-26 | 2018-09-26 | A kind of decoupling wheel hem retarding mechanism suitable for distributed electric drive automobile |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109780148A (en) * | 2019-01-16 | 2019-05-21 | 西华大学 | Planetary speed variator |
| CN110173553A (en) * | 2019-06-10 | 2019-08-27 | 杨巍 | Differential mechanism, hub-type differential mechanism and the motor cycle combination with hub-type differential mechanism |
| CN112737280A (en) * | 2021-01-21 | 2021-04-30 | 无锡开放大学 | Electric power variable torque type new energy automobile differential mechanism |
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| CN208935301U (en) * | 2018-09-26 | 2019-06-04 | 吉林大学 | A kind of automobile-used two-free-degree decoupling hub reduction transmission mechanism |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109780148A (en) * | 2019-01-16 | 2019-05-21 | 西华大学 | Planetary speed variator |
| CN110173553A (en) * | 2019-06-10 | 2019-08-27 | 杨巍 | Differential mechanism, hub-type differential mechanism and the motor cycle combination with hub-type differential mechanism |
| CN112737280A (en) * | 2021-01-21 | 2021-04-30 | 无锡开放大学 | Electric power variable torque type new energy automobile differential mechanism |
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